JPH0331631B2 - - 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 capable of continuously variable speed transmission by means of a pawl that meshes with an internal ratchet is disclosed in Japanese Patent Publication No. 1722/1983. .

(Problem to be Solved by the Invention) However, in the conventional device described above, when the load applied to each pawl is sequentially relayed in the driving range at the time of eccentricity, there is a gap between the drive ratchet and the driven pawl to which the next load is applied. Due to the speed difference, a gap occurs between the tips of the teeth of the driving pawl and the driven pawl that are about to engage next, resulting in a problem that a shock occurs when the driven pawl is replaced.

The present invention has been made to solve the above-mentioned problems, and it is an object of the present invention to significantly reduce the relay shock during speed-up driving of this type of continuously variable transmission.

(Means for Solving the Problems) In order to solve the above-mentioned problems, in the present invention, multiple rows of internally toothed ratchet rings are arranged in parallel on the inner periphery of the drive rotation member on the input side via one-way clutches. and a hollow cylindrical elastic body in which planetary rollers each having a large diameter portion and a small diameter portion are rotatably fitted to a plurality of circumferences of the drive rotating member, and the large diameter portion of the planetary roller is locked to the frame body. At the same time, the small diameter portion of this planetary roller is pressed against the outer peripheral surface of the internally toothed ratchet ring, and the bases of the multiple rows of pawls that mesh with this internally toothed ratchet are aligned with respect to the central axis. The continuously variable transmission is configured to take out an output by being pivotally supported by a driven rotating body rotatably provided on an eccentric shaft whose eccentricity can be adjusted.

(Function) Since the present invention is constructed as described above, when the rotating member on the input side rotates, the planetary rollers revolve accordingly. The planetary roller rotates on its own axis, and the revolution and rotation of the planetary roller are transmitted to the internally toothed ratchet ring via the small diameter portion of the planetary roller. In this case, the rotation of the internal toothed ratchet ring is increased by about 1.5 times the rotation of the rotating member on the input side, so
Even if there is a gap between the ratchet and the tips of the teeth of the pawl during the transmission relay of the driven pawl described above, the ratchet immediately catches up with the pawl due to the accelerated rotation of the ratchet ring, so that the gap between the tips of the teeth is disappears. Therefore, according to the present invention, it is possible to prevent the occurrence of a shock when changing the driven claws described above.

(Example) An example of the present invention will be described below with reference to FIGS. 1 to 6.

In the figure, 1 is a hollow cylindrical case body, 1a is an annular outer flange provided at the input/output end of the case body 1, 1b is an annular inner flange provided on the opposite side, and 1c is an annular inner flange of the case body 1. A base integrally formed at the lower part, 2 a case lid provided on the input/output side of the case body 1, 2a a boss portion protruding outward at the center thereof, and 3 a base extending through the case lid 2 to the case body 1. These are a plurality of bolts screwed into the outer flange 1a of the. Reference numeral 4 denotes a case lid provided on the other side of the case body 1, 4a denotes a boss portion protruding inwardly, and 5 denotes a plurality of screws that pass through the case lid 4 and are screwed to the inner flange 1b of the case body 1. It's a bolt.

Further, 6 is a drive rotation member on the input side, 6a is a boss portion formed at the center thereof, and 6b is a boss portion 6.
It is an outer flange formed on the opposite side of a, and 7 is an internal gear formed inside this outer flange 6b. Reference numeral 8 denotes a hollow cylindrical drum which is a driving rotation member on the input side and is integrally connected with an outer flange 6b and one end thereof by a bolt 9, and has a stepped shape in a large diameter part 8a and a small diameter part 8b. It is formed.

The input-side driving rotation member, which is the rotation member 6 and the drum 8 integrally connected, is rotatably provided within the main body case 1. That is, 10 is a bearing provided between the case lid 2 and the boss portion 6a of the rotating member 6, 11 is an oil seal, and 12 is a bearing provided between the boss portion 4a of the case lid 4 and the end of the drum 8. be.

Reference numeral 13 denotes a substantially cylindrical planetary carrier which is rotatably provided within the drive rotating member 6 and the large diameter portion 8a of the drum 8. Reference numeral 14 indicates a boss portion 13a protruding from one end of the carrier 13, and a planetary carrier 14 that is rotatably provided within the large diameter portion 8a of the drive rotating member 6 and the drum 8. A bearing 15 is a bearing provided between the other end 13b of the carrier 13 and the large diameter portion 8a of the drum 8. 1
6 is an internal gear formed integrally with the carrier 13 inside the other end 13b of the carrier 13. As shown in FIG. 6, this planetary carrier 13 has planetary gears 17 integrally formed with large diameter gears 17a and large diameter gears 17b at a plurality of locations (three locations in this embodiment), each rotated by a shaft 18. The small-diameter gears 17b are freely provided, and each small-diameter gear 17b is meshed with the internal gear 7, respectively. 19 is a bearing provided between the shaft 18 and the planetary gear 17.

Further, 20 is an inner eccentric shaft, and this inner eccentric shaft 20 is fixed to the case body 1 at an eccentric position with respect to the drum 8. That is, as shown in FIG. 1, the left end of the inner eccentric shaft 20 is fitted into the case lid 4 and fixed with the key 21, and the right end of the inner eccentric shaft 20 is
A large diameter shaft 21 concentric with the shaft 20 is integrally formed, and a central shaft 22 located at the center of the drum 8 is attached to the right side of the large diameter shaft 21 as an inner eccentric shaft 2.
0, formed integrally with the large diameter shaft 21. A bearing 23 is provided between the boss portion 13c protruding inside the planetary carrier 13 and the center shaft 22 to support the right end side of the inner eccentric shaft 20 and to make the planetary carrier 13 freely rotatable. 24 is a nut screwed into a threaded portion 20a of the inner eccentric shaft 20 that protrudes outward from the case lid 4.

A hole 22a is provided in the center shaft 22, and a protruding end 26a of the output shaft 26 is rotatably supported in the hole 22a via a bearing 25. It is rotatably supported by a bearing 27 provided in the boss portion 6a.
28 is an oil seal, 29 is a sun gear formed integrally with the output shaft 26, and this sun gear 29 meshes with the large diameter gear 17a of the planetary gear 17, respectively. (See FIG. 6) In addition, 26b shown in FIG. 1 is a key groove provided in the outward protrusion of the output shaft 26, and 30 is a key groove provided in the outward protrusion of the boss portion 6a of the drive rotation member 6 through the key 31. The input pulley is fixed.

A ring-shaped counter gear 32 is rotatably fitted onto the large-diameter shaft 21 via a bearing 33, and this gear 32 meshes with an internal gear 16 that is integrated with the planetary carrier 13. (See Fig. 5) Reference numeral 34 denotes an outer eccentric shaft that is rotatably fitted to the inner eccentric shaft 20. A substantially hollow cylindrical carrier 36 is attached to the outer periphery of the outer eccentric shaft 34 via two bearings 35. It is rotatably provided as a driven rotary body of the step change transmission. Further, a worm wheel 37 that is concentric with the inner eccentric shaft 20 is provided at the left end of the outer eccentric shaft 34 in FIG. It is set up like this. 3 shown in Figure 2
9 is its handle, and 40 is a bush of the shaft 38a.

Further, at the right end of the carrier 36 in FIG. 1, an internal gear 41 concentric with the carrier 36 is formed integrally with the carrier 36, and this internal gear 41 meshes with the counter gear 32. (See FIG. 4) In addition, a plurality of rows (in this embodiment, three
rows) of internal tooth ratchet rings 43, 44, 45 are arranged in parallel, and each of these internal tooth ratchet rings 43, 4
The bases of the claws 46, 47, 48, which are double rows and have a plurality of claws (three in this embodiment) in each row, mesh with the ratchets 43a, 44a, 45a of No. 4, 45, respectively.
A pin 49 is attached to the outer periphery of the cylindrical portion of the carrier 36.
(See Fig. 3) are arranged at equal positions on the circumference, that is, at 40° intervals. Also, 50 is claw 4
Always ratchet the tips of 6, 47, 48 43a,
Spring 51 for press-fitting 44a, 45a
(See Figure 1) is a retaining ring.

In addition, as shown in FIGS. 1 and 3, there are multiple locations on the circumference between the internal toothed ratchet rings 43, 44, and 45 of the small diameter portion 8b of the drum 8, which is the drive rotation member on the input side (in this embodiment, Cutout portions 8c are provided at three positions equally divided into three parts of the circumference, and the large diameter portion 52a
A planetary roller 52 having a small diameter part 52b concentrically protruding from both sides of the large diameter part 52a is rotatably fitted into the notch 8c and circumscribed to the large diameter part 52a of these planetary rollers 52. By providing a hollow cylindrical elastic ring 53 fixed to the case body 1 by ring stoppers 54 screwed into three equal parts of the circumference of the case body 1, the elasticity of the elastic ring 53 allows the planetary roller 52 to be Large diameter part 5
2a is brought into pressure contact with the elastic ring 53, and the large diameter portion 52b of the planetary roller 52 is brought into pressure contact with the shoulder portions of the outer periphery of each internally toothed ratchet ring 43, 44, 45.

Although 42a in FIG. 3 is a ball of the one-way clutch 42 and 42b is a spring, the one-way clutch 42 may be of any other type. Further, 55 in FIG. 1 is an oil cap provided on the case body 1, and 56 is an oil drain plug also provided on the case body 1.

Next, the operation of the apparatus configured as described above will be explained.

In FIG. 3, O ₁ is the input side drive rotating body 6,
8 and the center of the output shaft 26, O ₂ is the center point of the inner eccentric shaft 20 and O ₃ is the center point of the outer eccentric shaft 34. In this embodiment, since O ₁ to O ₂ = O ₂ to O ₃ , O ₁ and O ₃ are farthest apart in FIG. 3. That is, FIG. 3 shows the case where the outer eccentric shaft 34 is in the maximum eccentric state, but when the outer eccentric shaft 34 is rotated 180 degrees from this state,
O ₃ matches O ₁ and the amount of eccentricity of the outer eccentric shaft 34 becomes zero.

This amount of eccentricity can be adjusted using the handle 3 shown in Fig. 2.
9, the outer eccentric shaft 34 is rotated around the inner eccentric shaft 20 via the worm 38 and the worm wheel 37. That is, if the outer eccentric shaft 34 is rotated 180 degrees from the state shown in FIG. 3, the amount of eccentricity will be zero, and if the outer eccentric shaft 34 is rotated 180 degrees from this state, the amount of eccentricity will be maximized. .

First, to explain the operation in a state where the amount of eccentricity is zero, when the drive rotation members 6 and 8 on the input side rotate in the direction of arrow A in FIG. 3 in this state, the one-way clutch 42
through each internal tooth ratchet ring 43, 44, 4
5 also rotates in the direction of arrow A, and the carrier 36 also rotates in the direction of arrow B via the pawls 46, 47, 48 and pin 49 that engage with the internal toothed ratchet rings. When the amount of eccentricity is zero, the carrier 36 is at the center of the device, so the carrier 36 rotates integrally with the internal toothed ratchet rings 43, 44, 45. Therefore, in this case, the rotation ratio between the drum 8, which is the driving rotating member on the input side, and the carrier 36, which is the driven rotating member on the output side, is 1:1.

Next, the operation in the maximum eccentric state shown in FIG. 3 will be explained. As described above, each internal tooth ratchet ring 4
3, 44, and 45 rotate in the direction of arrow A, driving range C in Figure 3 (in this case, there are a total of 9 pawls, so
It is an angle of 40° divided into 9 equal parts of 360°. ) is the highest, the carrier 36, which is a driven rotating body, is rotated at an increased speed by this pawl 47, and the other pawls are internally toothed ratchet rings 43, 44,
It rotates in the direction of arrow B without engaging with each of the ratchets 43a, 44a, 45a of 45.

When the pawl 47 moves out of the drive range C and the next pawl 46 enters the drive range C, it is then driven at an increased speed via that pawl 46, and the transmission pawls 46, 47, 48 are sequentially transferred to the succeeding pawls. will take turns.

The speed ratio (speed increase ratio) in this case is an angle θ ₁ which is the driving range of the pawl with the center O ₁ as the starting point, and an angle θ 1 which is the driving range of the pawl with the center O ₃ of the outer eccentric shaft 34 as the starting point. The ratio is ₂ .

Next, the planetary roller 5 which is a feature of the device of the present invention
2 and the functions of the elastic ring 53 will be explained.

That is, when the drum 8, which is the rotating member on the input side, rotates in the direction of arrow A in FIG. Planetary roller 52 rotates in the direction of arrow D in FIG. That is, the planetary roller 52 rotates in the direction of arrow D due to the frictional resistance caused by the pressure contact between the large diameter portion 52a of the planetary roller 52 and the elastic ring 53. The revolution and rotation of the planetary roller 52
It is transmitted to each internal toothed ratchet ring 43, 44, 45 via the small diameter portion 52b of. In this case, the rotation of the internal toothed ratchet ring is increased approximately 1.5 times the rotation of the drum 8 on the input side. Therefore, in the transmission relay of the driven pawls 46, 47, 48, even if the ratchets 43a, 44a, 45a and pawl 4
Even if there is a gap between the tips of teeth 6, 47, and 48,
Internal tooth ratchet rings 43, 44, 45 described above
The ratchets 43a, 44a,
45a immediately catches up with the pawls 46, 47, and 48, so the gap between the tooth tips described above is eliminated.

Note that while a particular ratchet and pawl are fully engaged and driven, the planetary roller 52 will appropriately slip on each contact member to absorb the speed difference between each member.

Note that the above explanation has been made for cases where the gear ratio is 1:1 and the case where the gear ratio is at the maximum speed change state at the time of maximum eccentricity, but since this device can change the amount of eccentricity of the outer eccentric shaft 34 steplessly, It is clear that this allows continuously variable speed.

Next, the operation of the transmission system after the above-mentioned continuously variable transmission will be explained. The carrier 36 is indicated by arrow E in Figure 4.
When the internal gear 41 is rotated in the direction shown in FIG. In this case, when the outer eccentric shaft 34 rotates, the position of the internal gear 41 changes accordingly, but in this case, no matter how it changes, the internal gear 41 is always aligned with the counter gear 32.
Transmission is ensured because the gears are meshed with the gears.

Further, when the counter gear 32 rotates, the internal gear 16 formed integrally with the planetary carrier 13 rotates in the direction of arrow G by meshing with the counter gear 32, as shown in FIG. That is, according to this device, even if the carrier 36 is in an eccentric position, the rotation of the carrier 36 can be extracted as the rotation of the planetary carrier 13 about the output shaft 26 of the device.

Next, the operation of the planetary gear type speed increasing device will be explained. First, a case where the rotation ratio between the drum 8 and the planetary carrier 13 is 1:1 will be explained.

In FIG. 6, when the drum 8 rotates in the direction of the arrow A, the internal gear 7 connected to the drum 8 also rotates in the direction of the arrow A.
Rotate like. And in this case the conversion ratio is 1:1
Therefore, since the planetary carrier 13 also rotates integrally with the drum 8 in the direction of the arrow A, each planetary gear 17 eventually revolves in the direction of the arrow A together with the drum 8, but does not rotate. Therefore, each planetary gear 17
The sun gear 29 meshing with the large diameter gear 17a also rotates integrally with the drum 8 in the direction of arrow A. Therefore, the output shaft 26, which is integral with the sun gear 29, also rotates integrally with the drum 8. That is, in this case, the rotation ratio between the drum 8, which is the drive rotation member on the input side, and the output shaft 26 is 1:1.

In addition, with respect to the rotation of the drum 8, which is a driving rotating member on the input side of the continuously variable transmission, the planetary carrier 13, which is a driven rotating member on the output side, rotates at an increased speed, and as a result, the internal gear 7 in FIG. When the rotational angular velocity of the planetary carrier 13, indicated by arrow H, becomes greater than the rotational angular velocity indicated by arrow A, the planetary gear 17 rotates in the direction of the arrow. The gear 17 rotates at increased speed in the direction shown by arrow J due to the revolution of arrow H and the rotation of arrow H. The rotational speed indicated by arrow J is naturally increased from the rotational speed indicated by arrow H of the planetary carrier 13, which is the output member of the continuously variable transmission. In this embodiment, the maximum speed increase ratio of the output shaft 26 to the input drive rotation members 6, 8 is about 1:5.

Therefore, if this planetary gear type speed increasing device is used, the maximum speed increasing ratio of the preceding continuously variable transmission can be increased several times.

(Effects of the Invention) As described above, in the device of the present invention, since the planetary rollers and the elastic ring are provided in the continuously variable transmission device, it is possible to prevent the occurrence of relay shock when the driven pawls are replaced. Therefore, according to the present invention, an excellent effect can be obtained in that it is possible to provide a continuously variable transmission device that can provide smooth rotation with less relay shock.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view of the device of the present invention, and FIG.
3 is a side view showing a part of the figure in cross section, FIG. 3 is a side view showing the - cross section in FIG. 1 with a part cut away, FIG. The figure is a partial sectional view taken along the - line in FIG. 1, and FIG. 6 is a partial sectional view taken along the - line in FIG. 1. 1... Case body, 2... Case lid, 4... Case lid, 6... Input side drive rotation member, 7... Internal gear, 8... Drum (input side drive rotation member),
13... Planetary carrier, 16... Internal gear, 17
... Planetary gear, 20 ... Inner eccentric shaft, 21
... Large diameter shaft, 22 ... Center shaft, 26 ... Output shaft (center shaft), 29 ... Sun gear, 30 ... Input pulley, 32 ... Counter gear, 34 ... Outer eccentric shaft, 36 ... Carrier (driven rotating body),
37... Worm wheel, 38... Worm,
39...Handle, 41...Internal gear, 42...
One-way clutch, 43, 44, 45... Internal tooth ratchet ring, 46, 47, 48... Pawl, 49...
... Pin, 52 ... Planetary roller, 52a ... Large diameter part, 52b ... Small diameter part, 53 ... Elastic ring, 5
4... Ring stopper.

Claims (1)

[Claims] 1. A planetary planet in which a plurality of rows of internally toothed ratchet rings are arranged in parallel on the inner periphery of a driving rotating member on the input side via a one-way clutch, and each of said driving rotating member has large diameter portions and small diameter portions at multiple locations around the circumference of said driving rotating member. A roller is loosely fitted so as to be rotatable, and the large diameter part of this planetary roller is pressed against the inner circumferential surface of a hollow cylindrical elastic ring fixed to the frame body, and the small diameter part of this planetary roller is fitted into the inner toothed ratchet. The bases of the multiple rows of pawls that press against the outer circumferential surface of the ring and engage with the internal ratchets are pivotally supported on a driven rotating body that is rotatably provided on an eccentric shaft that can freely adjust the amount of eccentricity with respect to the central axis. A continuously variable transmission characterized by extracting output.