JPH0546459B2 - - Google Patents

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) An example of a continuously variable transmission device capable of steplessly variable speed transmission by means of pawls meshing with internal ratchets is disclosed in Japanese Patent Publication No. 34-1722.

(Problems to be Solved by the Invention) The conventional device described above has a two-stage speed increasing device using ratchets and pawls in order to increase the speed increasing ratio, but this transmission device using ratchets and pawls is When the load applied to each pawl is sequentially relayed in the drive range during speed increase, if there is a gap between the tips of the teeth of the drive ratchet and the driven pawl, 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, this conventional device, as shown in FIG.
If we take the phase angle (0° to 360°) of the transmission on the abscissa and the gear ratio on the ordinate, the relationship curve A between each rotational phase of the output from each claw and the gear ratio is the 11th
It forms a continuous mountain shape as shown by the thick solid line in the figure. In other words, 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 plurality of rows of internal locks are connected via one-way clutches to the inner circumference of a drum, which is a rotating member driven by an input shaft. Ring gears having gears are arranged in parallel, an inner eccentric shaft is fixed at an eccentric position with respect to the center of these ring gears, and an outer eccentric shaft having an outer peripheral surface eccentric with respect to the shaft has a self-locking function with respect to the inner eccentric shaft. A hollow cylindrical rotor is rotatably provided on the outer eccentric shaft, and external teeth are provided on the outer periphery of the arc-shaped member to form a toothed planet. The toothed planets are arranged circumferentially so as to mesh with each of the ring gears, and the bases of the toothed planets are pivoted to the rotor to extract output. Configure the transmission.

(Function) As described above, in the present invention, instead of the conventional ratchets and pawls, a ring gear having an internal gear and an arc-shaped toothed planet that presses into the ring gear are provided, and the ring gear and the toothed planet are connected to each other. 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, there is no gap between the meshing teeth. never occurs. Therefore, the relay shock unlike the conventional device does not occur at all.

In addition, 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 the 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 becomes almost smooth, as shown in the relationship curve (thick solid line) B between each rotational phase and the gear ratio shown in FIG. 10, which is shown in the same way as FIG. 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, 1b is an annular inner flange, 1
c is an annular outer flange provided at the output side end of the case body 1, 2 is an intermediate casing provided on the input side of the case body 1, 3 is a case lid provided on the outside of this intermediate casing, and 3a is the center portion thereof. A boss portion 4 protrudes outward at the case lid 3, the intermediate casing 2, and the outer flange 1 of the case body 1.
A plurality of bolts are provided through a, and 5 is a nut. 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 1c, 8 is that nut.

9 is a hollow cylindrical drum (drive rotation member on the input side) rotatably provided inside the case body 1;
In this embodiment, a plurality of members are combined and formed into one piece. 10 is a bearing for rotatably supporting the input side of the drum 9 on the inner flange 1b of the case body 1, and 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 3a of the case lid 3 via a bearing 13, and the inner end thereof is arranged in a substantially circular shape between the case lid 3 and the intermediate casing 2. 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 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 at multiple locations (three locations in this embodiment) on the same circumference relative to the center of the sun gears 16 and 17.
A shaft 19 is provided between the case lid 3 and the inner flange 1b of the case body 1, and a bearing 2 is attached to the shaft 18.
This is a transmission gear having two planetary gears 19a and 19b, each rotatably provided through a transmission gear 19a and 19b.The planetary gear 19a meshes with the sun gear 16, and the planetary gear 19
b is designed to mesh with the sun gear 17. That is, when the input shaft 12 rotates, the sun gear 16,
The drum 9 is configured to rotate via planetary gears 19a, 19b and a sun gear 17.

Reference numeral 21 denotes an inner eccentric shaft, and the inner eccentric shaft 21 is fixed to the case body 1 at an eccentric position with respect to the drum 9. That is, as shown in FIG. 1, the right end of the inner eccentric shaft 21 is fitted into the intermediate casing 2, and the key 2
2, a disk 23 concentric with the shaft 21 is integrally formed on the left end of the inner eccentric shaft 21, and a central shaft 24 located at the center of the drum 9 is attached to the left side of the disk 23. 21, formed integrally with the disk 23. A ring-shaped planetary carrier 26 is rotatably provided via a bearing 25 to 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. Rotatably provided as a driven rotating body of the transmission. A worm wheel 31 concentric with the inner eccentric shaft 21 is provided at the right end of the outer eccentric shaft 28 in FIG.
The intermediate casing 2 is provided so as to be rotatably driven through the intermediate casing 2. 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 35 is arranged in parallel on the inner periphery of the input side front half 9b of the drum 9 via a one-way clutch 34. A toothed planet 36 having external teeth 36a meshing with the internal gear 35a is formed on the outer periphery of a substantially semicircular arc having a radius of curvature smaller than that of the toothed planet 36.

Further, on the outer circumference of the rotor 30, a set of brackets 30a is protruded from a position facing the plural rows of ring gears 35, and these plural sets (eight sets in this embodiment) of the brackets 30a are shown in FIG. As shown, they are arranged at eight equal positions on the circumference. The base of each toothed planet 36 is pivotally supported on 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.

As this pressure welding and meshing means, a toothed planet 3 is used.
Any means may be used, such as providing a spring (not shown) on the pivot portion of 6. In this embodiment, the ring gear 35
A semicircular recess 35b is provided on both side walls of the meshing part with the toothed planet 36, and one end of the arm plate 39 is pivoted on both sides of the ring gear 35 by a pin 38 passing through the recess 35b. At the same time, a toothed planet 36 is sandwiched between these two arm plates 39, the free ends of these arm plates 39 are connected by a pin 40, a spiral spring 41 is fitted onto this pin 40, and this spiral spring 41, the external teeth 36a of the toothed planet 36 are always press-fitted and engaged with the internal gear 35a of the ring gear 35. Furthermore, the fourth
The one-way clutch 34 shown in FIGS. It can also be from.

Further, in order to rotate the rotor 30, which is a driven rotating body of the continuously variable transmission of the present invention configured as described above, around the central axis 24, a sun is attached to the left end of the rotor 30 in FIG. gear 42
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.

Further, the planetary gear device on the left side of the planetary carrier 26 in FIG. 1 is for amplifying 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. It is rotatably supported by a bearing 50 provided within the boss portion 6a and a bearing 52 provided within a bearing housing 51 provided protruding from the outside of the case lid 6. 53 is bearing 50,5
A sleeve 54 fitted between the two is 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 (four in this embodiment) planet gears 57 meshing with the sun gear 55 are connected to the planet carrier 26 by a shaft 59 via a bearing 58.
As shown in FIG. 9, a plurality of gears (in this embodiment, four
A planetary gear 60 is connected to the end plate 9c of the drum 9 on the left side in FIG.
These planetary gears 5
7 and 60 is rotatably supported on the planetary carrier 26 via a bearing 64, and the other end of the inner drum 63 is attached to the end plate portion 9c of the drum 9 via a bearing 65. An internal gear 66 that is rotatably supported and meshes with the planetary gear 57 is provided on the inner periphery of the inner drum 63, and an internal gear 66 that meshes with the planetary gear 60.
7 is provided integrally.

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 arrow D. Since the planetary gears 19a and 19b are integrally formed, when the planetary gear 19b rotates in the direction of arrow D in FIG. 3, the sun gear 17 that meshes with it rotates in the direction of arrow E.
A drum 9 integrated with this rotates in the same direction.

In FIGS. 3 to 5, O ₁ is the center point of the device that coincides with the centers of the input shaft 12 and the output shaft 48,
O ₂ is the center point of the inner eccentric shaft 21, O ₃
is the center point of the outer eccentric shaft 28. In this example, since O ₁ to O ₂ = O ₂ to O 3, O ₁ and _{O 3 match} in FIGS. 3 and 4, and
In Figure 5, O ₁ and O ₃ are the farthest apart. That is, Figures 1, 3, 4, and 6 show the outer eccentric shaft 2.
8 shows a state where the amount of eccentricity is zero, and FIG. 5 shows a case where the outer eccentric shaft 28 is in the maximum eccentric state.

This amount of eccentricity can be adjusted using the handle 3 shown in Fig. 3.
3, the outer eccentric shaft 28 is rotated around the inner eccentric shaft 21 via the worm 32 and the worm wheel 31. That is, if the outer eccentric shaft 28 is rotated 180 degrees from the state shown in FIGS. 3 and 4, the eccentricity becomes the maximum state as shown in FIG. 5, and if the outer eccentric shaft 28 is rotated 180 degrees from this state, The eccentricity becomes 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. drum 9
rotates in the direction of arrow E, one-way clutch 34
Each ring gear 35 also rotates in the direction of the arrow F in FIG. 4 via the ring gear 35, and the rotor 30 also rotates in the direction of the arrow F via the toothed planet 36, pin 37, and bracket 30a that mesh with the ring gear 35.
When the amount of eccentricity is zero, the rotor 30 is at the center position of the device, so the rotor 30 is connected to the ring gear 35.
rotates integrally with. 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 mentioned above, when the ring gear 35 rotates in the direction of the arrow F, the rotor 30 also rotates in the same direction as the arrow G in FIG. 5 via the toothed planet 36, but in this case, the drive range H in FIG. (In the case of this embodiment, there are eight toothed planets 36, so the angle is 45 degrees, divided into eight equal parts of 360 degrees.) Since the speed increase rate is maximum due to the toothed planets 36 whose meshing point is located within The rotor 30, which is a rotating body, is rotated at an increased speed by this toothed planet 36, and the other toothed planets 36 rotate together with the ring gear 35 while being pulled by the rotor 30. This rotation of the ring gear 35 is permitted by a 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 the rotor 30 is sequentially driven. The transmission element changes to the following toothed planet.

As shown in FIG. 5, the speed ratio (speed increase ratio) in this case is determined by the angle θ 1 which is the driving range of the toothed planet 36 with the center point 0 ₁ of the drum 9 as the base point, and the angle θ ₁ which is the drive range of the toothed planet 36 and This is the ratio to the angle θ ₂ which is the drive range of the toothed planet 36 with the center point 0 ₃ as the base point.

In other words, in this device, when the amount of eccentricity is maximum, the speed increasing ratio is also the maximum, and when the amount of eccentricity is zero, the speed ratio is 1:1, but as mentioned above, this amount of eccentricity is determined by the steering wheel 3.
Since the speed can be set steplessly from zero to the maximum value by the operation in step 3, the device of the present invention is capable of stepless speed change.

Furthermore, the continuously variable transmission of the present invention is provided with a ring gear 35 having an internal gear 35a and an arc-shaped toothed planet 36 that presses into engagement with the ring gear 35, in place of the ratchet and pawl of the conventional device. Since the toothed planets 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 unlike the conventional device does not occur at all.

Further, in the device of the present invention, during speed-up transmission, the meshing point between the ring gear 35 and the toothed planet 36 is
Unlike conventional ratchets and pawls, the engagement point is not a fixed point, but the transmission contact moves as the rotational phase changes, so the output is almost constant, as shown in curve (thick solid line) B shown in Figure 10. It becomes 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 shown by arrow I in FIG. 6, and the internal gear 46 that meshes with the sun gear 42 rotates as shown by arrow J. In this case, when the outer eccentric shaft 28 rotates, the position of the sun gear 42 changes accordingly, but in this case, the sun gear 42 is always meshed with the internal gear 46 no matter how it changes. , 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 arrow K. 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, which is pivotally supported by , revolves as indicated by an arrow L. Further, since the sun gear 56 fixed to the boss portion 6a integrally connected to the case body 1 remains stationary, the planetary gear 60 meshing with the sun gear 56 rotates in the direction of the arrow L, as shown by the arrow M. It rotates on its own axis. Therefore, the internal gear 67 that meshes with the planetary gear 60 rotates in the same direction as the arrow N at a faster speed than the rotation of the drum 9 as shown by the arrow E due to the revolution of the arrow L and the rotation of the arrow M.

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 connected to the planetary carrier 26, so that the planetary carrier 26 rotates in the direction of the arrow O, which is the same rotation as the arrow E, in FIG. However, the planetary gear 57, which is pivotally supported on the planetary carrier 26 by the shaft 59, is meshed with the internal gear 66, and the rotation of the arrow N is larger than the rotation of the arrow O, as described above. , after all, the planetary gear 57 has an arrow P
Causes rotation in direction.

The sun gear 55 meshing with the planetary gear 57 rotates as the planetary gear 57 revolves as indicated by the arrow O and rotates as indicated by the arrow P, and the rotation is transmitted to the output shaft 48, but in this case it is in a stationary state. sun gear 55
Let Vo be the angular velocity of the rotation that occurs in the planetary gear 57 when it meshes with the planetary gear 57 and revolve around it as shown by the arrow O, and let Vx be the respective velocities of the rotation of the planetary gear 57 indicated by the arrow P, then Vx = Vo, the rotation of the output shaft 48 is zero, and Vx<Vo
In this case, the output shaft 48 rotates in the forward direction (rotation in the direction of arrow Q in Fig. 8), and in the case of Vx<Vo, the output shaft 48
is a reverse rotation (rotation in the direction of arrow R in FIG. 8).

In addition, with respect to the rotation of the drum 9, which is a driving rotating member on the input side of the continuously variable transmission, the sun gear 43, which is a driven rotating member on the output side, rotates at an increased speed, and as a result, the internal gear 66 in FIG. When the rotational angular velocity of the planetary carrier 26, indicated by the arrow O, becomes greater than the rotational angular velocity indicated by the arrow N, the planetary gear 57 rotates in the direction of the arrow S, so that the sun gear 55, which is fixed to the output shaft 48, Due to the revolution of the gear 57 as shown by the arrow O and the rotation of the arrow S, the gear 57 rotates at an increased speed as shown by the arrow T. 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 amplifier, it is possible to amplify and extract the speed change range of the continuously variable transmission in the preceding stage. In other words, by setting the gear ratio of this planetary gear device appropriately, the output rotation can be obtained steplessly over a wide range from zero rotation to maximum rotation. The rotation of the shaft 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) The continuously variable transmission device of the present invention using a ring gear and a toothed planet has a ring gear 35 having an internal gear 35a instead of the ratchet and pawl of the conventional device,
Since the ring gear 35 is provided with an arc-shaped toothed planet 36 that presses and meshes with the toothed planet 36 so that the ring gear 35 and the toothed planet 36 are always in mesh with each other, the gear that is applied to the square toothed planet 36 in the drive range H during speed increase is provided. When relaying loads sequentially, the ring gear 35 and the toothed planet 36 are always in mesh, so that no gap occurs between the meshing teeth. Therefore, the relay shock unlike the conventional device does not occur at all. Vibrations and noise are therefore also greatly reduced.

Further, in the device of the present invention, during speed-up transmission, the meshing point between the ring gear 35 and the toothed planet 36 is
Unlike conventional ratchets and pawls, the engagement point is not a fixed point, but the transmission contact moves as the rotational phase changes, so the output becomes almost smooth, as shown in curve B shown in Figure 10. Pulsation becomes extremely small.

As described above, the continuously variable transmission of the present invention provides excellent effects such as very low vibration and noise and smooth output without pulsation at a continuously variable speed ratio.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional view of the device of the present invention, and FIG.
Fig. 3 is a cross-sectional view of the figure, Fig. 3 is a side view showing the same cross-section and a partially cut away state, Fig. 4 is a cross-sectional view of the same, Fig. 5 is an explanatory diagram of its operation, and Fig. 6 is a side view of the same cross-section and a partially cutaway state. - Sectional view, Fig. 7 is the same - Sectional view, Fig. 8
The figure is a sectional view of the same, Figure 9 is a sectional view of the same,
Fig. 10 is a diagram showing the relationship between each rotational phase of the output and the gear ratio by the continuously variable transmission of the present invention, and Fig. 11 is a diagram showing the relationship between each rotational phase of the output and the gear ratio by the conventional claw-type continuously variable transmission. FIG. 1...Case body, 2...Intermediate casing,
3, 6...Case lid, 9...Drum (input side drive rotating member), 12...Input shaft, 16, 17...Sun gear, 19...Transmission gear, 21...Inner eccentric shaft, 23... Disk, 24... Central axis, 2
6... Planetary carrier, 28... Outer eccentric shaft, 30... Rotor (driven rotating body), 31...
Worm wheel, 32... Worm, 33...
Handle, 34... One-way clutch, 35... Ring gear, 36... Toothed planet, 39... Arm plate, 41... Spiral spring, 42, 43... Sun gear, 45... Gear carrier, 46, 47... ...Internal gear, 48... Output shaft, 55, 56... Sun gear, 57, 60... Planetary gear, 63... Inner drum, 66, 67... Internal gear.

Claims (1)

[Claims] 1 Ring gears having multiple rows of internal gears are arranged in parallel on the inner periphery of a drum, which is a rotating member driven by an input shaft, via a one-way clutch, and an inner eccentric shaft is located at an eccentric position with respect to the center of these ring gears. An outer eccentric shaft which is fixed and has an outer peripheral surface eccentric with respect to the shaft is fitted to the inner eccentric shaft so as to be rotationally adjustable via a worm having a self-locking function and a worm wheel, and the outer eccentric shaft A hollow cylindrical rotor is rotatably provided on the rotor, external teeth are provided on the outer periphery of the arc-shaped member to form a toothed planet, and the toothed planets are distributed on the circumference so as to mesh with each of the ring gears. 2. A continuously variable transmission device characterized in that the toothed planets are disposed as shown in FIG.