JPS6283532A - Continuously variable transmission - Google Patents

Abstract

PURPOSE:To reduce the generation of relay shock by installing a circular-arc- shaped toothed planet which is press-contact-meshed with a ring gear and permitting the ring gear is always meshed with the toothed planet. CONSTITUTION:A circular-arc-shaped toothed planet 36 press-contact-meshed with a ring gear 35 having an internal gear 35a is provided, and the ring gear 35 and the toothed planet 36 are always meshed. Therefore, when the load applied onto each toothed planet 36 is relayed in succession in the driving range H in acceleration, the ring gear 35 and the toothed planet 36 are always in meshed state. Therefore, generation of a gap between the meshed gears is prevented, and the relay shock is not generated at all, while vibration and noise can be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a general-purpose continuously variable transmission device suitable for equipping industrial machinery, conveyance equipment, and the like.

(Prior art) As a continuously variable transmission device that can continuously change speed transmission by double feed that meshes with an internal ratchet,
For example, there is one disclosed in Japanese Patent Publication No. 34-1722.

(Problems to be Solved by the Invention) The above-mentioned conventional device is provided with a speed increasing device using a ratchet and a pawl in two stages in order to increase the speed increasing ratio, but this transmission device using a ratchet and a pawl is If there is a gap between the tooth tips of the drive ratchet and the driven pawl when relaying the load on the winter melon in the drive range during speed increase, this gap will cause shock and noise when the driven pawl changes. However, there was a problem in that this phenomenon was further amplified especially when the transmission device was made into two stages.

In addition, as shown in Fig. 11, this conventional device has the phase angle (00 to 360') of the transmission on the abscissa and the gear ratio on the ordinate, so that each rotational phase of the output from the winter melon and the gear shift are plotted. The relationship curve A with the ratio has a continuous mountain shape as shown by the thick solid line in FIG. That is, there was a problem in that the output of this conventional device became pulsating during speed increase.

(Means for Solving the Problems) In order to solve the above-mentioned problems, in the present invention, a ring gear having a plurality of rows of internal gears is arranged in parallel on the inner periphery of the drive rotation member on the input side via a one-way clutch. The base of a plurality of rows of arc-shaped toothed planets that are press-fitted with the ring gear is pivoted to a driven rotating body rotatably provided on an eccentric shaft whose eccentricity can be freely adjusted with respect to the central axis, thereby producing an output. A continuously variable transmission is constructed by taking it out.

(Function) As described above, in the present invention, instead of the conventional ratchet and pawl, a ring gear having an internal gear and an arc-shaped toothed planet that presses and meshes with the ring gear are provided.
Since the ring gear and the toothed planets are always in mesh, when the load applied to each toothed planet is sequentially relayed in the drive range during speed increase, the ring gear and the toothed planets are always in mesh. There is no gap between the teeth that engage with each other. Therefore, unlike the conventional device, no radiation shock occurs at all.

Furthermore, in the device of the present invention, during speed-up transmission, the meshing point between the ring gear and the toothed planet is not a fixed point like a conventional ratchet and pawl, but the transmission contact changes as the rotational phase changes. Because of the movement, the output from the device of the present invention is almost smooth, as shown in the relationship curve (thick solid line) B between each rotational phase and gear ratio shown in FIG. 10, which is shown in the same way as FIG. As a result, the pulsation becomes extremely small.

(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 also an annular inner flange, 1c is an annular outer 7 flange provided on the output side end of the case body 1, 2 is an intermediate casing provided on the input side of the case body 1, and 3 is provided on the outside of this intermediate casing. A case 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. It is. 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. The input shaft 12 is formed into a plate shape, and the input shaft 12 is supported at two points by a bearing 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 to the outer circumference of the disc portion 12a of the input shaft 120, and 17 is a sun gear fitted to the input side end of the drum 9. These two sun gears 16. '17 is concentric. 18 is the sun gear 16°17 as shown in Figure 2.
(in this example, 3 locations on the same circumference with respect to the center of
The shafts 19 provided between the case lid 3 and the inner flange 1b of the case body 1 have two planetary gears 19a and 19b, respectively, which are rotatably provided on the shaft 18 via bearings 20. Transmission gear, planetary gear 19
a meshes with the sun gear 16, and the planetary gear 19b meshes with the sun gear 17. That is, when the input shaft 12 rotates, the sun gear 16, planetary gears 19a, 19b
, the drum 9 is rotated via the 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-way 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 of the set) 30a is
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 the pin 38 passing through the recessed notch 35b, and the toothed planet 36 is sandwiched between these two arm plates 39, so that the arm plate 39 has no play. The ends are connected by a pin 40, and a spiral spring 41 is fitted to this pin 40, and the external teeth 3 of the toothed planet 36 are
6a is always press-fitted and engaged with the internal gear 35a of the ring gear 25. Note that the one-way clutch 34 in FIGS. 4 and 5 consists 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-way clutch using a ratchet and a pawl. It may be in a format like this.

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

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

In other words, 48 is an output shaft, and the right end of each of the 48 output shafts 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 that mesh with the sun gear 56 are respectively pivoted to the end plate portion 9C on the left side of the drum 9 in FIG. 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 input 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,
In FIG. 3, when the planetary gear 19b rotates in the direction of the arrow, the sun gear 17 meshing therewith 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 human power 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, OI~0゜-0□~0
Since it is set to 3, it is set to 01 in Figures 3 and 4.
and 03 match, and in FIG. 5, 0. 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 in the direction of arrow F in FIG. Through this, the rotor 30 also rotates in the direction of arrow F. When the amount of eccentricity is zero, the rotor 30 is 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 36o0. ) 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 whose base point is the center point o1 of the drum 9
This is the ratio of the angle θ1 which is the driving range of the outer eccentric shaft 28 to the angle θ2 which is the driving range of the toothed planet 36 with the center point o3 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 reduced to zero by operating the knob 33. Since the speed can be set steplessly from to the maximum value, the device of the present invention is capable of stepless speed change.

Furthermore, the continuously variable transmission of the present invention includes a ring gear 35 having an internal gear 35a instead of the ratchet and pawl of the conventional device,
An arc-shaped toothed planet 36 that presses and meshes with the ring gear 35 is provided, and the ring gear 35 and the toothed planet 3
Since the ring gear 35 and the toothed planet 36 are always in mesh with each other, when the load applied to each toothed planet 36 is sequentially relayed in the drive range H during speed increase, the ring gear 35 and the toothed planet 36
Since they are always in mesh, there is no gap between the meshing teeth. Therefore, the relay shock that occurs in conventional devices does not occur at all.

In addition, the device of the present invention has the ring gear 3 at the time of speed-up transmission.
5 and the toothed planet 36 is not a fixed point like a conventional ratchet and pawl, but the transmission contact moves as the rotational phase changes, so the output is as shown in Fig. 10. As shown by the curve (thick solid line) B, the surface becomes almost smooth and the pulsation becomes extremely small.

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 indicated by the arrow ■ 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 out of rotation, 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 will be explained. First, a case where the rotation ratio between the drum 9 and the sun gear 43 is 1:1 will be described.

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 portion 9C coupled to the drum 9 revolves as shown by an arrow. Furthermore, since the sun gear 56 fixed to the boss portion 6a that is integrally connected to the case body 1 remains stationary, the planetary gear 60 that meshes with the sun gear 56 rotates in the direction of 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 the arrow O and the rotation of the 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 the arrow O shows. If the angular velocity of the rotation that occurs in the planetary gear 57 when it revolves is Vo, and the angular velocity of the rotation of the planetary gear 57 indicated by the arrow P is vx, then Vx=Vo
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 O increases, the planetary gear 57 rotates in the direction of arrow S, so that the output shaft 48
The sun gear 55 fixedly rotates at an increased speed as shown by the arrow T due to the revolution of the planetary gear 57 as shown by the arrow 0 and the rotation of the planetary gear 57 as shown by the arrow S. The rotational speed indicated by arrow T is naturally faster than the rotational speed indicated by arrow O 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 this planetary gear type speed change amplification device, 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,
Further, depending on the setting of the gear ratio, the rotation of the output shaft can 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.

(Effect of the invention) The continuously variable transmission device of the present invention using a ring gear and a toothed planet uses an internal gear 3 instead of the ratchet and pawl of the conventional device.
5a and an arc-shaped toothed planet 36 that presses and meshes with the ring gear 35, so that the ring gear 35 and the toothed planet 36 are always in mesh with each other. When the load applied to each toothed planet 36 is sequentially relayed, since the ring gear 35 and the toothed planet 36 are always in a meshing state, no gap is generated between the meshing teeth.

Therefore, unlike the conventional device, no radiation shock occurs at all. Vibrations and noise are therefore also greatly reduced.

In addition, the device of the present invention has the ring gear 3 at the time of speed-up transmission.
5 and the toothed planet 36 is not a fixed point like a conventional ratchet and pawl, but the transmission contact moves as the rotational phase changes, so the output is
As shown in curve B shown in Figure 0, the curve becomes almost smooth and the pulsation becomes extremely small.

As described above, according to the continuously variable transmission of the present invention,
The excellent effect is that vibration and noise are extremely small, and smooth output without pulsation can be obtained with a stepless gear ratio.

[Brief explanation of drawings]

Fig. 1 is a longitudinal cross-sectional view of the device of the present invention, Fig. 2 is a cross-sectional view along the line ■-■ of Fig. 1, Fig. 3 is a side view showing the same cross-section along the line ■-■, and a partially cut-out state; Fig. 5 is an explanatory diagram of its function, Fig. 6 is a sectional view of Vl and -VI in Fig. 1, and Fig. 7 is a sectional view of the same -
■Cross-sectional view, Figure 8 shows the same ■--■ cross-section, Figure 9 shows the same IX-IX cross-section, and Figure 10 shows the relationship between each rotational phase of the output and the gear ratio by the continuously variable transmission of the present invention. FIG. 11 is a diagram showing the relationship between each rotational phase of the output and the gear ratio of a conventional continuously variable transmission. 1...Case body 2...Intermediate casing 3
．． 6... Case lid 9... Drum (input side drive rotating member) 12... Human power 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 Fig. 2 Fig. 4 Fig. 5 Fig. 6

Claims (1)

[Claims] 1. A ring gear having multiple rows of internal gears is installed in parallel on the inner periphery of the drive rotating member on the input side via a one-way clutch, and the base of a multiple rows of arc-shaped toothed planets is press-fitted to the ring gear. 1. A continuously variable transmission device, characterized in that an eccentric shaft whose eccentricity can be freely adjusted with respect to a central axis is pivotally supported by a driven rotating body rotatably provided to extract an output.