JPS62113947A - Speed-change amplifier for continuously variable transmission - Google Patents

Abstract

PURPOSE:To enable the speed change in a continuously variable transmission to be performed in a wide range between the forward rotation and the reverse rotation according to the width of eccentricity of the central axis by providing, on an inner drum, internal tooth gears which engage with both a planet gear swingingly supported on its output side planet carrier and another planet gear engaging with a sun gear placed in a case. CONSTITUTION:On a planet carrier 26, as the output side member of a continuously variable transmission, is swingingly supported a planet gear 57 which engages with a sun gear 55 on an output shaft 48, and also swingingly supported a planet gear 60 which engages with a sun gear 56 inserted in the boss section 6a of a case 1. In addition, on an inner drum 63 are provided internal tooth gears 66, 67 which engage with these planet gears 57, 60. Hereupon, when a drum 9, as the input side rotating member, and a sun gear 43 rotate in the same direction, the output shaft 48 comes to operate a forward rotation, or a reverse rotation, or a zero rotation depending on whether the rotation angular velocity of the planet gear 5 at the time of its revolution around the sun gear 55 being in a state of rest, and the rotation angular velocity of the planet gear 57 at the time of its rotation on its own axis are high or low. And accordingly, even when in motion, the speed-change can be amplified in a wide range.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a variable speed amplification device for a continuously variable transmission.

(Prior Art) As this type of continuously variable transmission, there is, for example, the one in Japanese Patent Application No. 167483/1983, which was previously filed by the present applicant. An internal ratchet ring is provided via a two-way clutch, and the base of the pawl that engages with the internal ratchet is pivotally supported on a carrier rotatably mounted on an eccentric cam whose eccentricity can be adjusted with respect to the central axis. This continuously variable transmission is characterized by a combination of a step-change transmission and a planetary gear type speed increasing device.

(Problems to be Solved by the Invention) Since the above-mentioned device is a combination of a continuously variable transmission and a planetary gear type speed increasing device, for example, the gear ratio of the continuously variable transmission is from 11 to 1:1. 5, the speed ratio can be changed from 1:1 to 1:3 using the planetary gear speed increaser, but the speed ratio cannot be reduced to 1=1 or less.

That is, the above-mentioned planetary gear type speed increasing device has a problem in that even if the input rotating member is rotating, it is not possible to reduce the rotation of the output shaft to zero or to reverse the output shaft.

Continuously variable transmissions installed in industrial machinery and conveyance equipment can not only increase the speed of the output side in response to a constant rotation of the input side, but also reduce the rotation of the output shaft to zero or even reverse rotation. There is a demand for a wide range of gear shifting functions. It is an object of the present invention to provide a variable speed amplification device for a continuously variable transmission that can meet such demands.

(Means for Solving the Problems) In order to achieve the above-mentioned object, in the present invention, the central shaft 24 is fixedly provided in the case body 1, and the drum 9, which is an input side rotating member, is provided rotatably. Furthermore, a planetary carrier 26, which is an output rotating member of the continuously variable transmission, is rotatably provided on the center shaft 24, and an output shaft 48 concentric with the center shaft 24 is rotatably provided. A sun gear 55 is fitted to the side, a sun gear 56 is fitted to the boss portion 6a of the case lid 6 of the case body 1, and the sun gear 56 is fitted to the boss portion 6a of the case lid 6 of the case body 1.
A plurality of planetary gears 57 meshing with the sun gear 56 are respectively pivotally supported on the planetary carrier 26 by a shaft 59, and a plurality of planetary gears 60 meshing with the sun gear 56 are connected to the end plate portion of the drum 9 on the case lid 6 side by a shaft 62. 9c, an inner drum 63 is rotatably provided to enclose these planetary gears 57 and 60, and an internal gear 66 that meshes with the planetary gear 57 is provided on the inner circumference of the inner drum 63. An internal gear 67 that meshes with the planetary gear 60 is provided integrally with each other to constitute a variable speed amplifier of a continuously variable transmission.

(Function) If the speed change amplifying device of the present invention configured as described above is used, the speed change range of the continuously variable transmission in the preceding stage can be amplified. In other words, if the gear ratio of this planetary gear device is set appropriately, the output rotation can be obtained steplessly over a wide range from zero rotation to maximum rotation, and depending on the gear ratio setting, the rotation of the output shaft can be controlled. It can also be set in a wide range from normal rotation to reverse rotation.

Furthermore, the gear shift operation of the above-mentioned device is convenient because it can be performed easily whether the device is in operation or stopped due to its mechanism.

(Example) An example of the present invention will be described below with reference to FIGS. 1 to 9.

In the figure, 1 is a hollow cylindrical case body, 1a is an annular outer flange provided at the input side end of the case body 1, and 1b
is an annular inner flange, IC is an annular outer flange provided at the output side end of case body 1, 2 is an intermediate casing provided on the input side of case body 1, and 3 is a case provided outside of this intermediate casing. The lid, 3a is a boss portion protruding outward at the center thereof, 4 is a plurality of bolts passing through the case lid 3, the intermediate casing 2, and the outer flange 1a of the case body 1, and 5 is a nut. be. Further, 6 is a case lid provided on the output side of the case body 1, 6a is a boss portion protruding inward at the center thereof, 7 is a plurality of bolts provided through the case lid 6 and the outer flange IC, 8 is that nut.

Reference numeral 9 denotes a hollow cylindrical drum (input-side driving rotation member) rotatably provided within the case body 1, and in this embodiment, it is integrally formed by combining a plurality of members. 10
connects the input side of the drum 9 to the inner flange 1b of the case body 1.
11 is a bearing for rotatably supporting the output side of the drum 9 on the case lid 6.

Reference numeral 12 denotes an input shaft, and this input shaft 12 is supported within the boss portion a of the case lid 3 via a bearing 13, and its inner end is approximately circular between the case lid 3 and the intermediate casing 2. It is formed into a plate shape, and the input shaft 12 is supported at two points by bearings 14 inserted between the disk portion 12a and the intermediate casing 2.

Note that 15 is an oil seal.

Further, 16 is a sun gear fitted on the outer periphery of the disc portion 12a of the input shaft 12, and 17 is a sun gear fitted on the input side end of the drum 9. These two sun gears 16 and 17 are concentric. be. As shown in FIG. 2, 18 is located between the case lid 3 and the inner flange 1b of the case body 1 at multiple locations (three locations in this embodiment) on the same circumference around the center of the sun gear 16 and 17. The provided shaft, 19, is the bearing 2 on the shaft 18.
2 planetary gears 1 rotatably provided through the
9a and 19b, the planetary gear 19a meshes with the sun gear 16, and the planetary gear 19b meshes with the sun gear 17.
It is designed to mesh with the That is, when the human power shaft 12 rotates, the drum 9 rotates via the sun gear 16, planetary gears 19a, 19b, and sun gear 17.

Reference numeral 21 denotes an inner eccentric shaft, and this inner eccentric shaft 21 is arranged in the case body 1 at an eccentric position with respect to the drum 9.
be fixed to the That is, as shown in FIG. 1, the right end of the inner eccentric shaft 21 is fitted into the intermediate casing 2 and fixed with a key 22, and the left end of the inner eccentric shaft 21 has a disk 23 concentric with the shaft 21.
Furthermore, on the left side of this disk 23, a central shaft 24 located at the center of the drum 9 is connected to an inner eccentric shaft 2.
1. It is formed integrally with the disk 23. A ring-shaped planetary carrier 26 is rotatably provided via a bearing 25 on an intermediate flange portion 9a protruding inwardly at an intermediate portion of the drum 9, and a bearing is provided between the inner periphery of the planetary carrier 26 and the center shaft 24. 27 is provided to support the left side of the inner eccentric shaft 21.

Reference numeral 28 denotes an outer eccentric shaft rotatably fitted to the inner eccentric shaft 21, and a substantially hollow cylindrical rotor 30 is connected to the outer periphery of the outer eccentric shaft 28 via two bearings (tapered roller bearings) 29. It is rotatably provided as a driven rotating body of the transmission.

Further, at the right end of the outer eccentric shaft 28 in FIG.
A worm wheel 31 is provided which is concentric with the inner eccentric shaft 21, and the worm 3 meshes with the worm wheel 31.
2 is provided so as to be rotatably driven to the intermediate casing 2 via its shaft 32a. 33 shown in FIG. 3 is its handle.

Further, a ring gear 35 having a plurality of rows (eight rows in this embodiment) of internal gears 35a is arranged in parallel on the inner circumference of the input side front half 9b of the drum 9 via a one-sided clutch 34. An external tooth 36a that meshes with the internal gear 35a has a substantially semicircular arc-shaped outer periphery having a radius of curvature smaller than that of the external tooth 36a.
A toothed planet 36 is formed.

Further, on the outer circumference of the rotor 30, a set of brackets 30a is protruded from positions facing the plural rows of ring gears 35, and a plurality of sets (in this embodiment, eight brackets) are provided.
As shown in Figure 4, the bracket l-30a of
Arrange in equal positions. The base of each toothed planet 36 is pivoted to each bracket 30a via a pin 37, and the external teeth 36a of each toothed planet 36 are always press-fitted and engaged with the internal gear 35a of the corresponding ring gear 35. .

Any means may be used as this press-fitting means, such as providing a spring (not shown) on the pivot portion of the toothed planet 36. In this embodiment, the toothed planet 36 of the ring gear 35
A semicircular recessed part 35b is provided on both side walls of the engaging part,
One end of the arm plate 39 is pivotally supported on both sides of the ring gear 35 by a pin 38 penetrating through the recessed part 35b, and the toothed planet 36 is sandwiched between these two arm plates 39. The free ends are connected by a pin 40, and a spiral spring 41 is fitted to the pin 40.
This spiral spring 41 keeps the external teeth 36a of the toothed planet 36 in contact with the internal gear 35a of the ring gear 35 at all times. The one-way clutch 34 shown in FIGS. 4 and 5 is composed of a ball 34a and a spring 34b, but this one-way clutch 34 may be any other type of clutch, such as a one-sided clutch using a ratchet and pawl. It may be in a format like this. Note that the continuously variable transmission may be of any other type.

Further, in order to rotate the rotor 30, which is a driven rotating body of the continuously variable transmission configured as described above, around the central axis 24, a sun gear 42 is attached to the left end of the rotor 30 in FIG. is provided concentrically with the rotor 30, and a sun gear 43 is provided on the right shoulder of the planetary carrier 26 in FIG. An internal gear 46 that meshes with the sun gear 42 is provided on the right side of the gear carrier 45 in FIG. 1, and an internal gear 47 that meshes with the sun gear 43 is provided on the left side of the gear carrier 45.
will be established.

Further, the planetary gear device on the left side of the planetary carrier 26 in FIG. 1 is a speed change amplification device of the present invention that amplifies the speed change by the above-mentioned continuously variable transmission device, and its configuration is as follows.

That is, 48 is an output shaft, and the right end of this output shaft 48 in FIG. A bearing 50 provided in part a, and a bearing 5 provided in a bearing housing 51 provided protruding from the outside of the case lid 6.
It is rotatably supported by 2. 53 is bearing 50
．． A sleeve 54 is fitted between 52 and an oil seal.

Further, 55 is a sun gear that is fitted and fixed to the right side of the output shaft 48 in FIG. 1, and 56 is a sun gear that is fitted and fixed to the end of the boss portion 6a of the case lid 6. As shown in FIG. 8, a plurality of planetary gears 57 (four in this embodiment) meshing with the sun gear 55 are respectively pivotally supported on the planetary carrier 26 by shafts 59 via bearings 58, and the other planetary gears 57, as shown in FIG. As shown in FIG. 1, a plurality of (four in this embodiment) planetary gears 60 meshing with the sun gear 56 are each pivoted to the left end plate portion 9c of the drum 9 in FIG. 1 by a shaft 62 via a bearing 6I. One end of the inner drum 63 that supports the planet gears 57 and 60 is rotatably supported by the planet carrier 26 via a bearing 64, and the other end of the inner drum 63 is rotatably supported by the planet carrier 26 via a bearing 65. End plate portion 9c of drum 9
The inner drum 63 is rotatably supported, and an internal gear 66 that meshes with the planetary gear 57 is provided on the inner periphery of the inner drum 63, and an internal gear 67 that meshes with the planetary gear 60 is integrally provided.

Next, the operation of the apparatus configured as described above will be explained. When the human power shaft 12 rotates (clockwise), the sun gear 16 integrated therewith rotates in the direction of arrow C in FIG. 2, and the planetary gear 19a meshing with it rotates in the direction of the arrow. Since the planetary gears 19a and 19b are integrally formed, the third
In the figure, when the planetary gear 19b rotates in the direction of the arrow, the sun gear 17 meshing with it rotates in the direction of the arrow E, and the drum 9, which is integral with it, rotates in the same direction.

0 in Figures 3-5. is the input shaft 12 and the output shaft 48
0□ is the center point of the inner eccentric shaft 21, and 03 is the center point of the outer eccentric shaft 2.
It is the center point of 8. In this example, 01~02・0°~0
Since the setting is 3, DI and 03 match in FIGS. 3 and 4, and 0.03 in FIG. 5. and 03 are the farthest apart.

That is, Fig. 1.3.4.6 shows a state where the amount of eccentricity of the outer eccentric shaft 28 is zero, and Fig. 5 shows a case where the outer eccentric shaft 28 is in the maximum eccentric state.

The amount of eccentricity can be adjusted by operating the handle 33 shown in FIG.
the outer eccentric shaft 28 through the inner eccentric shaft 21
This is done by rotating around the center.

That is, from the state shown in Fig. 3.4, the outer eccentric shaft 28
If the outer eccentric shaft 28 is rotated 180 degrees, the eccentricity becomes maximum as shown in FIG.
If it is rotated by 80 degrees, the amount of eccentricity will be zero.

First, to explain the operation when the amount of eccentricity is zero, when the sun gear 17 rotates in the direction of arrow E in FIG. Rotate to. When the drum 9 rotates in the direction of arrow E, each ring gear 35 also rotates through the one-way clutch/Z switch 4.
A toothed planet 36, a pin 37, and a bracket 30a that rotate as shown by arrow F in the figure and mesh with this ring gear 35.
The rotor 30 also rotates in the direction of arrow F. When the amount of eccentricity is zero, the rotor 30 is located at the center of the device, so the rotor 30 rotates integrally with the ring gear 35.

Therefore, in this case, the rotation ratio between the drum 9, which is the driving rotation member on the input side, and the rotor 30, which is the driven rotation member on the output side, is 1:1.

Next, the effect of the maximum eccentricity state shown in FIG. 5 will be explained.

As described above, when the ring gear 35 rotates in the direction of the arrow F, the rotor 30 also rotates through the toothed planet 36.
It rotates in the same direction as shown by arrow G in the figure, but in this case, the fifth
Drive range H in the figure (in this example, the toothed planet 36 is 8
Since there are two angles, the angle is 45°, which is divided into 8 equal parts of 360°. ) Since the speed increase rate by the toothed planet 36 whose meshing point is located within 30 and rotates together with the ring gear 35. This rotation of the ring gear 35 is allowed by the one-way clutch 34.

Then, when the toothed planet 36 moves out of the drive range H and the meshing point of the next toothed planet 36 enters the drive range H, the rotor 30 is driven at an increased speed via the toothed planet 36, and sequentially The transmission member changes to the following toothed planet.

The gear ratio (speed increasing ratio) in this case is as shown in Figure 5.
Toothed planet 36 based on center point 01 of drum 9
This is the ratio of the angle θ1 which is the drive range of , and the angle θ2 which is the drive range of the toothed planet 36 with the center point 03 of the outer eccentric shaft 28 as the base point.

In other words, in this device, when the amount of eccentricity is maximum, the speed increasing ratio is also maximum, and when the amount of eccentricity is zero, the speed ratio is 1:1, but as mentioned above, this amount of eccentricity can be changed from the zero to the maximum by operating the handle 33. Since the value can be set steplessly, this device is capable of continuously variable speed.

Next, the operation of the transmission system after the above-mentioned continuously variable transmission will be explained. When the rotor 30 rotates, the sun gear 42 connected to the rotor 30 rotates as shown by arrow I in FIG.
An internal gear 46 meshing with the sun gear 42 rotates as shown by arrow J. In this case, if the outer eccentric shaft 28 rotates, the position of the sun gear 42 will change accordingly.
In this case, the sun gear 42 is always in mesh with the internal gear 46 no matter how much it changes, so transmission is performed reliably.

Further, when the internal gear 46 rotates, the internal gear 47 integrally connected via the gear carrier 45 rotates as shown by arrow J in FIG. 7, and the sun gear 43 meshing with this rotates as shown by the arrow. do. That is, according to this device, even if the rotor 30 is in an eccentric position, the rotation of the rotor 30 can be extracted as the rotation of the sun gear 43 about the central axis 24 of the device.

Next, the operation of the planetary gear type speed change amplifier of the present invention will be explained. First, the rotation ratio between the drum 9 and the sun gear 43 is 1.
: The case of 1 will be explained.

When the drum 9 rotates in the direction of arrow E in FIG.
A planetary gear 60 pivotally supported by a shaft 62 on an end plate 9c connected to the drum 9 revolves as shown by an arrow. Further, since the sun gear 56 fixed to the boss portion 6a integrally connected to the case body 1 remains stationary, the planetary gear 6o meshing with the sun gear 56 rotates on its own axis as shown by the arrow M as it revolves in the direction of the arrow. do.

Therefore, the internal gear 67 meshing with the planetary gear 60 rotates as shown by the arrow and rotates as shown by the arrow M, as shown by the arrow N.
The drum 9 rotates in the same direction at a faster speed than the rotation of arrow E.

When this internal gear 67 rotates, the internal gear 66 integrally connected by the inner drum 63 rotates as shown by arrow N in FIG. 8. On the other hand, the sun gear 43, which rotates in the same manner as the drum 9, is integrally coupled with the planet carrier 26, so that the planet carrier 26 rotates in the direction of arrow 0, which is the same rotation as the arrow E, in FIG. However, the planetary gear 57, which is pivotally supported by the planetary carrier 26 by the shaft 59, meshes with the internal gear 66, and the rotation of arrow N is larger than the rotation of arrow 0, as described above. Eventually, the planetary gear 57 rotates in the direction of arrow P.

The sun gear 55 that meshes with the planetary gear 57 is the planetary gear 57.
It rotates by the revolution of arrow 0 and the rotation of arrow P, and the rotation is transmitted to the output shaft 48. In this case, the planetary gear 57 meshes around the sun gear 55, which is in a stationary state, and rotates as indicated by arrow 0. If the angular velocity of rotation that occurs in the planetary gear 57 when it revolves is Vo, and the angular velocity of rotation of the planetary gear 57 indicated by the arrow P is VX, then Vx=V○
In the case of , the rotation of the output shaft 48 becomes zero, and in the case of vX<vo, the output shaft 48 rotates in the forward direction (rotation in the direction of arrow Q in FIG. 8), and Vx >V.

In this case, the output shaft 48 rotates in the opposite direction (rotation in the direction of arrow R in FIG. 8).

Further, with respect to the rotation of the drum 9, which is a driving rotation member on the input side of the continuously variable transmission, the sun gear 43, which is a driven rotation member on the output side, rotates at an increased speed, and as a result, the internal gear 66 in FIG. From the rotational angular velocity indicated by the arrow N, the planetary carrier 26
When the rotational angular velocity indicated by arrow 0 becomes large, the planetary gear 57 rotates in the direction of arrow S, so that the output shaft 48
The sun gear 55 which is fixed to rotates at an increased speed as shown by the arrow T due to the revolution of the planetary gear 57 in the direction of the arrow and the rotation of the planetary gear 57 in the direction of the arrow S. The rotational speed indicated by arrow T is naturally faster than the rotational speed indicated by arrow 0 of the planetary carrier 26 which is integrated with the sun gear 43 which is the output member of the continuously variable transmission.

Therefore, by using the planetary gear type speed change amplifier of the present invention, it is possible to amplify and extract the speed change range of the continuously variable transmission in the preceding stage. In other words, if the gear ratio of this planetary gear device is set appropriately, the output rotation can be obtained steplessly over a wide range from zero rotation to maximum rotation, and depending on the gear ratio setting, the rotation of the output shaft can be controlled. It can also be set in a wide range from normal rotation to reverse rotation.

Furthermore, the gear shift operation of the above-mentioned device is convenient because it can be mechanically performed easily even when the device is in operation or stopped.

(Effects of the Invention) As described above, by using the speed change amplifying device of the present invention, the speed change range of the continuously variable transmission in the preceding stage can be amplified up and down. In other words, if the gear ratio of this planetary gear device is set appropriately, the output rotation can be obtained steplessly over a wide range from zero rotation to maximum rotation,
Furthermore, depending on the gear ratio setting, the rotation of the output shaft can be set in a wide range from normal rotation to reverse rotation, so the device of the present invention significantly expands the applicable range of this type of continuously variable transmission and expands its applications. You can get excellent results by being able to do this.

Furthermore, the device of the present invention is very convenient in practice because it is mechanically capable of effortlessly shifting gears even when the device is in operation or stopped.

[Brief explanation of drawings]

Fig. 1 is a longitudinal sectional view of a continuously variable transmission equipped with the device of the present invention, Fig. 2 is a cross-sectional view taken along ■-■ of Fig. 1, and Fig. 3 is a cross-sectional view taken along ■-■ of Fig. 1, with a portion cut away. Side view, Figure 4 is a sectional view of the same IV-TV, Figure 5 is an explanatory diagram of its operation, Figure 6 is a sectional view of VI-Vl of Figure 1, Figure 7 is a sectional view of the same ■-■, Figure 8 The figure is a sectional view taken along the line ■-■, and FIG. 9 is a sectional view taken along the line IX-IX. ■...Case body 2...Intermediate casing 3
．． 6... Case lid 9... Drum (drive rotation member on the input side) 12... Input shaft 16.17... Sun gear 19...
Transmission gear 21...Inner eccentric shaft 23.
... Disk 24 ... Central shaft 26 ... Planet carrier 28 ... Outer eccentric shaft 30 ...
・Rotor (driven rotating body) 31... Worm wheel 32... Worm 33
... Handle 34 ... One-way clutch 3
5... Ring gear 36... Toothed planet 39... Arm plate 41... Spiral springs 42, 43... Sun gear 45... Gear carrier 46, 47... Internal gear 48... Output shaft 5
5, 56...Sun gear 57.60...Planetary gear 63...Inner drum 66, 67...Internal gear Patent applicant Brideston Cycle Co., Ltd. Figure 2 Figure 5 Figure 6

Claims (1)

[Claims] 1. A central shaft 24 is fixedly provided in the case body 1, and a drum 9, which is an input side rotating member, is rotatably provided,
Further, a planetary carrier 26, which is an output side rotating member of the continuously variable transmission, is rotatably provided on the center shaft 24, and an output shaft 48 concentric with the center shaft 24 is rotatably provided, and the output shaft 48 is provided on the center shaft 24 side. A sun gear 56 is fitted to the boss portion 6a of the case lid 6 of the case body 1, and a plurality of planetary gears 57 meshing with the sun gear 55 are connected to the shaft 5.
A plurality of planetary gears 60 are respectively pivotally supported to the planetary carrier 26 by 9 and meshed with the sun gear 56, and each is pivotally supported to the end plate 9c of the drum 9 on the case lid 6 side by a shaft 62.
Further, an inner drum 63 enclosing these planetary gears 57 and 60 is rotatably provided.
A variable speed amplification device for a continuously variable transmission characterized in that an internal gear 66 that meshes with a planetary gear 57 is provided on the inner circumference of the device, and an internal gear 67 that meshes with the planetary gear 60 is provided integrally with the planetary gear 60.