JPH10115355A - Driven biaxial continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a driven biaxial continuously variable transmission for four-wheel drive to perform smooth gear shifting, increase power transmission capacity, improve power transmission efficiency, and reduce size. SOLUTION: First and second driven shafts 11 and 13, and first and second drive wheels 18 and 19 are arranged at the two ends of a drive sleeve 17 through a torque cam 20. Five first ball roller groups 21-1 forced into pressure contact joining with the first drive wheel 18 and the first driven wheel 12-1 and a second ball roller group 21-2 brought into pressure contact engagement with the second drive wheel 19 and the second driven wheel 12-2 are radially arranged at the periphery of a drive shaft 15. First and second after rings 24 and 25 with which a half-moon-form oscillation member 22 having the plane side on which the ball roller is supported is engaged are juxtaposed. The oscillation member 22 of the first ball roller group 21-1 and the oscillation member 22 of the second ball vibrator group 21-2 are fitted in the groove of a fixed spider 27 with the oscillation members arranged back to back, and hydraulic first and second ring cylinders 32 and 33 are provided to oscillate the oscillation member 22.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a driven two-shaft continuously variable transmission for transmitting a rotational force via a plurality of ball rolling elements, which is suitable as a continuously variable transmission for a four-wheel drive vehicle.

[0002]

2. Description of the Related Art A four-wheel drive mechanism currently used connects an engine output shaft to a transmission via a torque converter and a clutch device, and drives the front and rear wheels via a driving force distribution device at the next stage of the transmission. ing.

[0003] As described above, the conventional four-wheel drive mechanism employs a form in which the engine output is shifted by one transmission, and thus requires a large transmission that matches the engine output.

[0004]

SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a four-wheel drive transmission that can be downsized and can continuously change the speed during operation. It is.

[0005]

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and two sets of continuously variable transmissions which perform transmission of rotational force via a ball rolling element are skillfully combined.
The configuration is such that the engine output is shifted in half by each of the continuously variable transmissions, thereby enabling downsizing.

That is, the first invention is characterized in that a first driven shaft provided with a first driven vehicle at an inner end and a second driven shaft provided with a second driven vehicle at an inner end are provided on both sides of the casing. Both driven vehicles are provided on the same axis so as to face each other, and a driving shaft in which a driving sleeve is loosely fitted between the both driven vehicles via a spline is provided rotatably in both driven shafts, and torque cams are provided at both ends of the driving sleeve. A first prime mover and a second prime mover are provided, and an appropriate number of first ball rolling elements that are in pressure contact with the first prime mover and the first driven vehicle are radially arranged around the prime mover shaft. In addition, the same number of second ball rolling elements as the first ball rolling elements that are pressed into engagement with the second driving wheel and the second driven wheel are radially arranged around a driving shaft, and the ball rolling is performed. The arcuate surface side of the rocking member of the semi-lunar first ball rolling element group for supporting the child with the concave part on the plane side and the second ball The swinging members of the first ball rolling element group and the swinging members of the second ball rolling element group are attached to the supporting means so as to swing freely with the arc surfaces of the swing members of the moving element group back to back. A driven two-shaft continuously variable transmission, wherein a driving means for simultaneously swinging in opposite directions is provided.

In a second aspect of the present invention, a driven vehicle having two inner and outer rims at an inner end is provided on both sides of a casing.
A driven shaft and a second driven shaft having a driven wheel having two inner and outer rims at the inner end thereof are provided on the same axis with the driven wheels facing each other, and a driving sleeve is provided between the driven wheels via a spline. Are freely rotatably provided in both driven shafts, and a first prime mover and a second prime mover are provided at both ends of the drive sleeve via torque cams. Any one of the inner and outer rims of the first driven vehicle is pressed into contact with the spherical portion, and at the stop position, an appropriate number of truncated first ball rolling elements having a shape in which the two rims of the first driven vehicle are separated from each other. Radially arranged around the driving shaft, and except for the stop position, either the inner or outer rim of the second prime mover and the second driven vehicle engages with the spherical portion by pressure, and when the stop position is at the stop position, the second driven vehicle The same number of truncated second ball rolling elements as the truncated first ball rolling elements formed in a shape in which both rims are separated from each other. The oscillating member of the half-moon-shaped group of truncated first ball rolling elements, which are radially arranged around a driving shaft and which supports the truncated ball rolling elements by recesses in a flat portion, is truncated. The swinging members of the second ball rolling element group are attached to the supporting member so that the arc surfaces of the swinging members are back-to-back, and the swinging members of the first ball rolling element group and the second ball rolling element group. A driven two-shaft continuously variable transmission including a driving unit that simultaneously swings a swing member in directions opposite to each other.

[0008]

According to a first aspect of the present invention, when the driving shaft rotates, the first driving wheel and the second driving wheel rotate via a spline and a driving sleeve, and the rotation of the first driving wheel and the second driving wheel via a ball rolling element are performed. According to the transmission ratio transmitted to the second driven vehicle and determined by the effective rotation diameter of the ball roller contacting the prime mover and the effective rotation diameter of the ball roller contacting the driven vehicle according to the inclination of the ball roller. Rotation is performed.

By activating the driving means of the swinging member to change the inclination of the rotation axis of the ball rolling element, and changing the effective rotation diameter of the ball rolling element contacting the driving vehicle side and the driven vehicle side, The rotation of the first driven vehicle and the second driven vehicle can be continuously variable.

The second invention is different from the first invention in that a truncated ball rolling element is used as a ball rolling element for transmitting power, and a driven wheel having two rims inside and outside is used as a driven wheel. When the outer rim of the driven wheel contacts the spherical surface of the truncated ball roller, and when the inner rim contacts the spherical surface of the truncated ball roller, the driven vehicle rotates in the opposite direction. When both the inner and outer rims are separated from the spherical surface, the rim is stopped.

[0011]

FIG. 1 is a longitudinal sectional front view of an embodiment of the first invention using five ball rolling elements, and FIG.
FIG. 3 is an exploded perspective view of a part incorporated therein.

1 to 3, reference numeral 11 denotes a first driven shaft provided with a dish-shaped first driven wheel 12-1 at an inner end, and reference numeral 13 denotes a dish-shaped second driven wheel 12-2 at an inner end. With the second driven shaft provided, the first driven wheel 12-1 and the second driven wheel 12-2 are arranged on the same axis so as to face each other, and are rotatably attached to the casing 14, respectively.

Reference numeral 15 denotes a spline 16 and a driving sleeve 17.
And the first and second driven shafts 11, 1
3 and has an end protruding toward the first driven shaft 11.

Reference numerals 18 and 19 denote first and second prime movers and 21-1 and 21-2 connected to both ends of the prime mover 17 via torque cams 20, respectively. The ball rolling element is supported by a small ball group 23 disposed in the concave portion 22a of the first driving wheel 18 or the second driving wheel 19 and the driven wheel 12-1 or 12-2 during driving. The swinging member 22 which is brought into contact with and supports the first outer ring 24 having elastic bending as shown in FIG.
And a groove 26 provided in the axial direction of the driving shaft 15 of the second outer ring 25 so as to be swingable.

Reference numeral 27 denotes a required number of separator projections 2 on both sides.
7a, and is a fixed spider for a separator of the ball rolling element 21 fixed to the casing 14, wherein the rocking member 22 is fitted in a groove 28 provided in the fixed spider 27, and rocks at a predetermined position. The moving member 22 is configured to swing.

The half-moon-shaped swing member 22 of the first ball rolling element group and the half-moon-shaped swing member 22 of the second ball rolling element group mounted on both sides of the fixed spider 27 have an arc surface side. Compressed coil springs 29 and 30 are provided between the outside and between the first outer ring 24 and the second outer ring 25 between the outer sides and between the first outer ring 24 and the second outer ring 25. In addition, 31 is a sitting ball.

Reference numerals 32 and 33 denote hydraulic first ring cylinders and hydraulic second cylinders provided on both sides, which are simultaneously driven by a hydraulic control device, and serve as swing members for the first ball rolling element group and the second ball rolling element group. It is made to swing simultaneously in opposite directions.

Reference numeral 34 denotes a front wheel axle drive shaft, and reference numeral 35 denotes a rear wheel axle drive shaft, which is pivotally mounted on the casing 14 in parallel with the driving shaft 15 and is connected to a differential gear device 36.

The front axle drive shaft 34 and the rear axle drive shaft 35 are connected to the first driven shaft 11 and the second driven shaft 13 via winding transmissions 36 and 37, respectively.

With the above configuration, the driving shaft 15
Is rotated, the driving sleeve 1 is driven through the spline 16.
7 rotates, and the first prime mover 18 and the second prime mover 19 rotate via the torque cams 20 and 20.

The rotation of the first prime mover 18 and the second prime mover 19 is transmitted to the first driven wheel 12-1 and the second driven wheel 12-2 via the ball rolling elements 21 and 21 which come into contact with each other. Further, the power is transmitted to the front wheel axle drive shaft 34 and the rear wheel axle drive shaft 35 via the winding transmissions 36 and 37. The drive shafts are connected by a differential gear device 38 for synchronization. The torque cams 20 and 20 are provided when the load is applied to the first prime mover 18 and the second prime mover 19. Is moved in the axial direction according to the load, and the first ball rolling element 12-1 is moved.
And automatically adjusts the pressure contact force between the second ball rolling element 12-2 and
This is to prevent slip and increase transmission efficiency.

In such an operating state, when the hydraulic first ring cylinder 32 and the hydraulic second ring cylinder 33 are simultaneously operated against the compression coil springs 29 and 30 by a hydraulic control device (not shown), each half-moon-shaped swing The first moving member 22 is driven and supported by the small ball group 23.
The inclination of the rotation axis of the ball rolling element 12-1 and the second ball rolling element 12-2 changes, and the first driven wheel 12-1 and the second driven wheel 12 as shown in FIG. -2 rotation is continuously variable.

That is, when the reverse rotation of both driven vehicles is [I], the speed is high, when [II] is medium, and when [III], the speed is low.

Here, a is the effective rotation diameter of the prime mover (the center of the pressure contact portion with the ball rolling element), b is the effective rotation diameter of the ball rolling element that is in pressure contact with the prime mover, and the ball is the pressure contact with the driven vehicle. if the rotation effective diameter of the rolling element c, and rotating the effective diameter of the driven wheel is d, the gear ratio V _a becomes reverse gear as is clear from the negative sign is expressed by the following equation.

[0025]

(Equation 1)

In the continuously variable transmission according to the present invention, two sets of continuously variable transmission mechanisms using ball rolling elements are arranged symmetrically to shift the input by dividing the input into two parts. As shown in FIG. 5, the first ball rolling element 21-1 and the second ball rolling element 21-2 are supported by a half-moon-shaped swinging member 22, and their arc surfaces are back to back. The force f1 in the thrust direction generated by the pressure contact force fa, fd between the driving wheel and the driven wheel and the ball rolling element is offset by the back-to-back portion, and the force f2 in the radial direction is the first outer having an elastic bending. The load is equally distributed between the ring 24 and the second outer ring 25.

The virtual cone C _a , further including the Hertz area,
Since the vertices O _a , O _b , O _c , and O _d of C _b , C _c , and C _d are located on the same side, the inner and outer rotational diameter ratio b1 in the contact width is determined.
/ A1, and b2 / a2 and d1 / c1, and d2 / c2
Is very small, so that the prime movers 18, 19,
Since the curvature of the contact rim portion of the driven wheels 12-1 and 12-2 can take a value very close to that of the ball rolling elements 21-1 and 21-2, a wide Hertz area can be obtained, and the load resistance can be improved. As a result, it is possible to obtain an efficient contact condition with a large transmission capacity.

FIG. 6 is a longitudinal sectional front view of an embodiment of the second invention using four ball rolling elements, FIG. 7 is a sectional view taken along the line BB, and FIG. 8 is an exploded view of components incorporated therein. It is a perspective view.

The major difference between this embodiment and the above-described embodiment is that a truncated ball roller is used as a ball roller and a driven vehicle having two inner and outer rims is used. Thereby, along with the advantages and features of the above-described embodiment,
That is, forward and reverse rotation and stop can be performed by controlling the inclination angle of the rotation axis of the truncated ball rolling element.

Further, the design is that the swing driving means of the ball rolling element by a different mechanism is used, and the output is taken out by another mechanism.

That is, the first driven shaft 41 and the second driven shaft 43 are arranged on the same axis and are pivotally attached to the casing 44, and the first driven shaft 41 has two inner and outer rims R1 and R2 at the inner end of each driven shaft. A driven wheel 42-1 and a second driven wheel 42-2 are provided, and a driving shaft 45 having a left end protruding outside the first driven shaft 41 is connected to the first driven shaft 4
1 and the second driven shaft 43, and the spline 4
6, a driving sleeve 47 is loosely fitted, and a first driving wheel 48 is connected to both ends of the driving sleeve 47 via torque cams 50.
And a second prime mover 49, and a first truncated ball roller 51-
The first and second truncated ball rolling elements 51-2 are pivotally attached to half-moon-shaped swinging members 52, 52 which are back to back.

The swing member 52.52 is swingably fitted into the groove 55 of the first outer ring 53 and the groove 55 of the second outer ring 54 and the groove 57 of the fixed spider 56 in the same manner as in the above embodiment. However, as the swing driving means, a sector gear 521 is provided on the swing member 52, and a rack 551 meshing with the sector gear 521 is cut into grooves 55 of the first outer ring 53 and the second outer ring 54, and the first outer ring The difference is that the first hydraulic cylinder 53 and the second hydraulic cylinder 59 drive the 53 and the second outer ring 54 simultaneously.

The connection with the front axle drive shaft 60 is established by the gear 61 provided on the first driven shaft 41 and the gear 6 meshing therewith.
The second driven shaft 43 is attached to the rear wheel axle drive shaft.
The difference is that is used directly.

Each of the truncated ball rolling elements 51-1 and 51
The method of attachment to the half-moon-shaped swinging member -2 is different from that of the above embodiment.

That is, in this embodiment, the truncated ball rolling elements 51-1 and 51-2 are provided with race grooves 51-1a and 51-2a as shown in FIGS. An outer ring 63 of an angular contact ball bearing in which a group of small balls is disposed like a bearing is fitted to the outer ring 6 of the angular contact ball bearing.
3 is fitted into the concave portion 52a of the half-moon-shaped swinging member 52 containing the attracting magnet 64, and each truncated ball rolling element is mounted so as to be rotatable with respect to the swinging member 52. .

In this embodiment, the weak coil springs 65 are provided so that the first prime mover 48 and the second prime mover 49 return to the prime mover sleeve 47 side when the load is lost.

Next, the operation in the state shown in FIG. 6 will be described.
6, the driving sleeve 47 rotates, and the torque cam 5
The first prime mover 48 and the second prime mover 49 rotate through 0 and 50.

When a load is applied to the first driven shaft 43 and the driven shaft 60, the first driving wheel 48 and the second driving wheel 49 are opposed to the coil springs 65, 65 by the torque cams 50, 50.
The ball is slid on the driving shaft by the
1, 51-2, respectively, and the first prime mover 48 and the second
The rotation of the prime mover 49 is controlled by the truncated ball rolling elements 51-1 and 51.
-2 and a second driven wheel 42-2
Is transmitted to the first driven wheel 42-1 and the second driven wheel 42-2 via the outer rim R1 to rotate the first driven shaft 41 and the second driven shaft 43, and further through the gears 61 and 62. To rotate the front wheel axle drive shaft 60. In this case, the inner rim R2 of each driven vehicle is separated from the truncated ball rolling element.

Here, as shown in FIG. 9I, the effective rotation diameter of the first prime mover 48 and the second prime mover 49 (the center of the pressure contact portion).
To a. The effective rotation diameter between the first prime mover 48 and the second prime mover 49 and the truncated ball rotators 51-1 and 51-2 is b, and the truncated ball rotator 51 presses against the falling rim R1 of the driven vehicle. -1
C and the outer effective rim R1 of the driven vehicle
Assuming that the effective diameter of rotation is d, the speed ratio _Vb is expressed by the following equation, and the reverse rotation is reduced as is clear from the minus sign.

[0040]

(Equation 2)

Then, the first hydraulic cylinder 58 and the second hydraulic cylinder 59 are simultaneously operated by a hydraulic control device (not shown), and the first and second truncated ball rolling elements 51-1 and 51-1,
When the rotation shaft of 51-2 is swung so as to lie down as shown in [II] of FIG. 9, the first and second driven wheels 41 and 43 are reversely shifted to the low speed side.

Next, the first hydraulic cylinder 58
Further, when the hydraulic second cylinder 59 is further operated, FIG.
0, ie, the first and second states up to the stop position.
When the truncated ball rolling element 51-1 is swung, the inner and outer rims R1 and R2 of the first driven wheel 41 and the second driven wheel 43 are connected to the first truncated ball rolling element 51-1 and the second truncated ball. Ball roller 51-
2, the rotation of the first and second driven wheels 48 and 49 is not transmitted to the first and second driven wheels 41-43 even when the first and second driven wheels 48 and 49 rotate, and the first and second driven shafts 41 and 43 stop. State.

Then, when the first hydraulic cylinder 58 and the second hydraulic cylinder 59 are further operated to swing each ball rolling element beyond the stop position, as shown in [IV] of FIG. The outer rim R1 of the driven vehicle is separated from the truncated ball rolling element, and the inner rim R2 comes into contact, so that the driven vehicle rotates forward.

Here, if the effective rotation diameter of the truncated ball roller contacting the rim R2 on the inner side of the driven vehicle is c 'and the effective rotation diameter of the rim R2 is d', the speed ratio V during forward rotation is V. _b ′ is as follows.

[0045]

(Equation 3)

In the stop state of [III] in FIG.
Since each of the truncated ball rolling element magnets 64 is attracted to the half-moon-shaped swinging members 51-1 and 51-2, they do not jump out and come into contact with the rims R1 and R2 of the driven vehicle, and the prime mover 48. , 49 are truncated ball rollers with driven car rim R1,
Since it is separated from R2 and becomes a no-load state, the torque cam 50.
The function of 50 is lost, and the driving wheels 48, 49 are moved in the direction of the driving sleeve by the coil springs 65, 65,
The truncated ball rolling element that has been in pressure contact with the prime movers 48 and 49 is separated from the driving wheels 48 and 49.

As described above, in the present embodiment, the reverse stepless speed change and the normal rotation are performed at the stop position (neutral state).

[0048]

As can be seen from the above description, in both the first and second inventions, the rotation of the driving shaft is controlled by the driven 2 shaft through two sets of continuously variable transmission mechanisms using ball rolling elements. Since the shaft is continuously variable, when it is used as a continuously variable transmission for four-wheel drive, it is smaller than a conventional drive mechanism, and a transfer device, a reduction gear, etc. provided in addition to the transmission. Is unnecessary and there is an effect of simplifying the driving mechanism.

Further, according to the second aspect of the present invention, furthermore, the stepless speed change of the reverse rotation (drive traveling D), the stop (neutral N) and the forward rotation (reverse R) can be performed by one device. There is an effect that the neutral device can be omitted.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional front view of an embodiment of the first invention.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is an exploded perspective view of components incorporated inside the embodiment of the first invention.

FIG. 4 is an explanatory diagram of a shift operation according to the embodiment of the first invention.

FIG. 5 is an explanatory diagram of the advantages of the first invention.

FIG. 6 is a longitudinal sectional front view of the embodiment of the second invention.

FIG. 7 is a sectional view taken along the line BB of FIG. 6;

FIG. 8 is an exploded perspective view of components incorporated inside the embodiment of the second invention.

FIG. 9 is an operation explanatory diagram of the second invention at the time of reverse rotation.

FIG. 10 is an explanatory diagram of the operation of the second invention at the time of stop and at the time of normal rotation.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 11 1st driven shaft 12-1 1st driven wheel 12-2 2nd driven vehicle 13 2nd driven shaft 14 Casing 15 Driving shaft 16 Spline 17 Driving sleeve 18 1st driving vehicle 19 2nd driving vehicle 20 Torque cam 21-1 First 1 ball rolling element 21-2 second ball rolling element 22 swinging member 23 small ball group 24 first outer ring 25 second outer ring 26 groove 27 fixed spider 28 groove 29,10 compression coil spring 31 seat ball 32 hydraulic First ring cylinder 33 Hydraulic second cylinder 34 Front wheel axle drive shaft 35 Rear wheel axle drive shaft 36 Winding transmission device 37 Winding transmission device 38 Differential gear device

Claims (2)

[Claims] A first driven shaft provided with a first driven vehicle at an inner end and a second driven shaft provided with a second driven vehicle at an inner end on both sides of a casing. And a driving shaft with a driving sleeve loosely fitted through a spline between the driven wheels is provided rotatably in the driven shafts, and a first driving shaft is provided at both ends of the driving sleeve via a torque cam.
A prime mover and a second prime mover, and an appropriate number of first ball rolling elements that are pressed into engagement with the first prime mover and the first driven vehicle are radially arranged around the prime mover shaft; The same number of the second ball rolling element groups as the first ball rolling element groups that are pressed into engagement with the driving wheel and the second driven wheel are radially arranged around the driving shaft, and the ball rolling elements are placed on the flat side. The semicircular oscillating member supported by the concave portion of the first ball rolling element group has the arc surface side of the oscillating member of the first ball rolling element group and the arc surface side of the oscillating member of the second ball rolling element group back to back. A drive means for swingably mounting and swinging the swinging member of the first ball rolling element group and the swinging member of the second ball rolling element group simultaneously in opposite directions is provided. A driven two-axis continuously variable transmission. 2. A first driven shaft provided with a first driven vehicle having two inner and outer rims at an inner end on both sides of a casing, and a second driven vehicle provided with a second driven vehicle also having two inner and outer rims at an inner end. 2
A driven shaft is provided on the same axis with the two driven vehicles facing each other, and a driving shaft in which a driving sleeve is loosely fitted between the two driven vehicles via a spline is rotatably provided in the both driven shafts. A first prime mover and a second prime mover are provided at both ends of the first prime mover via torque cams.
Either the inner or outer rim of the driven vehicle presses into engagement with the spherical surface,
At the stop position, an appropriate number of truncated first ball rolling elements having a shape in which the two rims of the first driven vehicle are separated from each other are radially arranged around the driving shaft, and the second driving vehicle is also at a position other than the stopped position. And the second
Either the inner or outer rim of the driven vehicle presses into engagement with the spherical surface,
At the stop position, the same number of truncated second ball rolling elements as the truncated first ball rolling elements, which are formed so that both rims of the second driven vehicle are separated from each other, are arranged radially around the driving shaft. The arcuate side of the rocking member of the truncated first ball rolling element group and the truncated second ball rolling element group which support the truncated ball rolling element by the concave portion of the flat portion. The members are swingably attached to the support means with the arc surfaces of the members back to back, and the swinging member of the first ball rolling element group and the swinging member of the second ball rolling element group are simultaneously moved in opposite directions. A driven two-shaft continuously variable transmission, comprising a driving means for swinging.