JPH0272251A - Continuously variable transmission - Google Patents

Abstract

PURPOSE:To permit the continuous speed change by a pure mechanical gear mechanism by permitting the turning moment to be offset by the meshing of an outer peripheral side gear with the internal gear of a both planetary gear mechanism for dividing the power of an input shaft and reversely setting the revolution direction of the both output shafts by connecting an electric motor for control with one and connecting the other output shaft with the sun gear of the third planetary gear mechanism and taking out the power onto one output shaft. CONSTITUTION:An input shaft 1 is connected with the input shafts 5 and 5' of the planetary gear mechanisms 20 and 20' through gears 3, 4, and 4', and the power is divided into two parts and inputted into sun gears 6 and 6'. Then, the gear 9 of a prime mover 11 for control is meshed with the gear 8 of the mechanism 20, and the torque is made equal, and then each number of revolution of the output shafts 13 and 13' is increased/decreased according to the number of revolution of internal gears 7 and 7'. Then, a gear 16 is fixed onto the shaft 13', and after a reversing machine 40 is interposed, a gear 21 is fixed onto the shaft 13, and meshed with a gear 18, and then a gear 22 receives a force in an equal quantity from the gears 16 and 17, and the turning moments of the shafts 13 and 13' are integrated and transmitted to the output shaft. Therefore, when the number of revolution of the prime mover 11 varies, the power of the input shaft 1 is speed-changed in continuous form for the output shaft 2.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a continuously variable transmission having a purely mechanical structure using a gear mechanism.

[Prior art]

Conventionally, all continuously variable transmissions have consisted of a friction transmission mechanism that uses sliding friction, with the exception of those that use electrical or hydraulic mechanisms, and there are no purely mechanical structures that use gear mechanisms. .

However, those that utilize a friction transmission mechanism have the disadvantage that it is difficult to apply them to large amounts of power and operate them efficiently because they utilize slippage to achieve continuously variable speed. Therefore, if it were possible to achieve continuously variable speed using a gear mechanism that enables reliable power transmission, extremely highly efficient operation would be possible. Therefore, although such a device has been long-awaited in the industry, the reality is that it has not yet been realized.

[Purpose of the invention]

The purpose of the present invention is to meet the above-mentioned demands and provide a continuously variable transmission device that enables continuously variable transmission using a purely mechanical gear mechanism and that also enables this with an extremely small capacity control motor. It is in.

[Structure of the invention]

The continuously variable transmission of the present invention that achieves the above object is provided with two planetary gear mechanisms that divide the power of the input shaft into two halves with the same rotational speed and input the two, and the internal gears of both inverted planetary gear mechanisms can be freely rotated. At the same time, these internal gears are interlocked and connected through gears provided on the outer circumferential side so that the rotational forces cancel each other out, and furthermore, a control motor is interlocked and connected to the gear on the outer circumferential side of one of the internal gears. By driving both internal gears in opposite directions by the control prime mover, the same torque is generated on the output shafts of both inverted star gear mechanisms, and the number of rotations is increased or decreased steplessly by the same amount. The rotation direction of these two output shafts is reversed through a reversing machine, and one output shaft is connected to the sun gear of the third planetary gear mechanism that allows the internal gear to rotate freely. and the other output shaft is connected to another gear, and the gear is configured to mesh with a gear provided on the outer peripheral side of the rotatable internal gear, and one of the third planetary gear mechanisms The configuration is such that only the rotation is extracted from the planetary gear onto one output shaft, regardless of the revolution.

More specifically, a universal joint etc. Connect via a universal joint such as a quick ball joint,
It is preferable to take out only the rotation from the one planetary gear to the one output shaft without regard to the revolution.

DESCRIPTION OF THE PREFERRED EMBODIMENTS A concrete explanation will be given below using a continuously variable transmission device showing an embodiment of the present invention shown in the drawings.

Figures 1 to 3 are principle diagrams showing the continuously variable transmission of the present invention in skeleton form. In order to simplify the explanation, the pitch circles of the gears formed inside and outside of the internal gear of the planetary gear mechanism are shown in these figures. The illustration is made assuming that the diameters are the same.

In these figures, 1 is the input shaft, 2 is the output shaft,
A prime mover 10 such as an engine or a motor is connected to the input shaft l. The power of this human power shaft 1 is divided into two and transmitted to a pair of two planetary gear mechanisms 20.20', and in this embodiment, the output of both of these inverted planetary gear mechanisms 20.20' is transmitted to a third planetary gear mechanism. 30, and the combined output is taken out to the output shaft 2.

The input shaft 1 is connected to the input shafts 5 and 5 of the first and second planetary gear mechanisms 20220 and 20220, respectively, through gears 3 and 4 and 4, which have the same number of teeth, so that the power at the rotational speed N0 is transmitted in the same direction. The power is separated into two powers having the same rotational speed N o and N o and input to the sun gear 6° and 6°, respectively.

The two planetary gear mechanisms 20 and 20 degrees each have their internal gears 7 and 7 degrees rotatable around the central axis, and gears 8 degrees and 8' provided on their outer circumferential sides mesh with each other. As shown in FIG. 2, the rotational forces f and f of both gears are balanced at the meshing point P.

A gear 9 provided on the output shaft of the control motor 11 meshes with either one of the gears balanced in this way, that is, in this embodiment, the outer gear 8 of the internal gear 7 of the first planetary gear mechanism 20. are doing. This control motor 11 has two internal gears 7.
．． 7'' are rotated in opposite directions, but as mentioned above, the rotational forces of the two internal gears 7 and 7'' are balanced, so
The driving force is extremely small and is equal to the frictional force of the pawl teeth. Therefore, as the control motor 11, it is sufficient to use a very small capacity control electric motor, hydraulic motor, or the like.

Therefore, if the torques of the output shafts 13.13' provided on the carriers of the planetary gears 12.12' are made equal, the rotational forces of the internal gears 7 and 7 are balanced as described above, so that these The output shaft 1'3, 13' outputs a rotational speed that is increased or decreased by the same amount of rotational speed (α), depending on the rotational speed of the internal gear 7゜7゛, as described later. Become.

Next, the power of the two output shafts 13, 13' is combined into one output shaft 2 via the third planetary gear mechanism 30.

In the third planetary gear mechanism 30, the internal gear 17 is rotatable about its central axis. Only one planetary gear 22 is provided, and a balance weight 19 is provided to form a pair with this. Further, the shaft 22a of the planetary gear 22 is connected to one output shaft 2 via a pair of universal joints 23, 23 such as a universal joint or a constant velocity ball joint. This output shaft 2 is provided coaxially with the center axis of the planetary gear mechanism 30. The output shaft 2 can be connected to the output shaft 2 arranged concentrically with the planetary gear mechanism 30 by using such a connection mechanism using a universal joint.
In this case, only the rotation of the planetary gear 22 is taken out regardless of its revolution.

The above-mentioned two output shafts 13.13° are such that the sun gear 16 is fixed to the shaft end of one of the output shafts 13'' for such a planetary gear mechanism 30. A reversing machine 40 is interposed between the two gears to reverse the direction of rotation, and another gear 21 having the same number of teeth as the sun gear 16 is fixed to the shaft end of the gear 21. It meshes with the gear 18 provided on the outer circumferential side.With this kind of connection, the planetary gear 22 receives an equal amount of force in the same direction from the sun gear 16 and the internal gear 17, and rotates by the speed difference between them. That is, due to this connection, the rotational forces of the two output shafts 13, 13' are integrated into one and transmitted to the output shaft 2.

Therefore, if the rotational speed of the control motor 11 is changed in the above-described continuously variable transmission, the power of the input shaft 1 is transmitted to the output shaft 2 while being variable in speed.

At this time, two planetary gear mechanisms 20, 20° output shaft 13
．． The torques of the internal gears 13 are the same, and the rotational forces of the internal gears 7 and 7' are balanced. Therefore, the driving force of the control motor 11 only needs to be extremely small.

Next, when the control prime mover 11 is rotated at a predetermined number of rotations and continuously variable in the continuously variable transmission, the rotation speed α of the internal gears 7, 7' is proportional to the rotation speed of the control prime mover. and,
The relationship with the output rotation speed N of the output shaft 2 will be explained in detail from the calculation.

First, the output shaft 13 of the two planetary gear mechanisms 20 and 20'
, 13' are calculated as follows. However, if the reduction ratio of the double inverted star gear mechanism 2020' is 1
/ P 1110.

Then, the above equations (■) and (■) become as follows.

Na=N-α Na’=N+α become.

Next, the sun gear 16. fixed at the output shaft 13.13°.
If the gears 21 have the same size and radius r, and the radius of the internal gear 17 is R, then the rotation speed of the internal gear 17 is (N-α) r/R1 The rotation speed of the sun gear 16 is (N+α)
becomes.

Furthermore, since the rotation directions of the sun gear 16 and the internal gear 17 are the same, and their tangential forces are also equal, the rotation number N of the planetary gear 22 at this time is π (R-r) −r Now, - As an example, if you substitute R:r=3:1 into the formula 0, NX = N/2+α −−−−−−・−・・−・
−・−■. Also, if α is set to (=), N X = N / 2-α −・−−−−−−−
−・・・・・−−−−−−−−■ becomes.

In other words, the rotation speed NX is a function of α from the above ■2,
Therefore, α from equation 0. is a function of This means that by controlling the rotation speed of the control motor 11, the rotation speed N of the output shaft 2 can be varied steplessly. Also, at this time, the planetary gear 2 of the third planetary gear mechanism
The torques of the sun gear 16 and the gear 21 meshing with the gear 2 become equal. Also, from Fig. 2, two internal gears 7, 7''
Since the gear loads are balanced in opposite directions at the meshing point P, the driving force of the control motor 11 only needs to be a force equivalent to the frictional force of the teeth, etc., and is less than the power of the input shaft 1. It will be extremely small.

Now, as a specific example, R: r=3: l.

Pmo=4. No = 150 Or, p, m,
Assuming that, by substituting into the cholera equations (1) and (2) above, we get the following.

N--x 1 5 0 0=3 7 5α=-×
α.

Therefore, from ■2 =187. 5+-α.

becomes. Therefore, α. - If 〇, NX-187
, 5r, p, m.

Also, α. The limit of (+) is when the output shaft 13 becomes O, so if we set Na=0 in the 0 equation, α. =173 ・No, so α. = 50 Or, p, m.

Therefore, α. = 50 When Or, p, m,
From formula 0, it becomes NX -562,5r, p, m.

That is, in the above-mentioned continuously variable transmission, the rotation speed α of the internal gear 7 of the first planetary gear mechanism 20 is controlled by the control motor 11.

, forward rotation from 0 to 500 r, p.

If the output rotation speed NX of the output shaft 2 is changed steplessly up to 187. 5r, p, m, to 562.5r, p
This means that the speed can be changed steplessly in the range up to , m.

〔Effect of the invention〕

As described above, the continuously variable transmission device of the present invention enables efficient stepless speed change using a purely mechanical gear mechanism, and is also applicable to large power.

[Brief explanation of the drawing]

Fig. 1 is a principle diagram showing a skeleton of a continuously variable transmission according to an embodiment of the present invention, Fig. 2 is a view taken along the nn arrow in Fig. 1, and Fig. 3 is a view taken along the mm arrow in Fig. 1. It is a diagram. 1.5, 5°...Input axis, 2,13.13'...
Output shaft, 6.6', 16...Sun gear, 7,7°, 1
7... Internal gear, 8,8°, 9.18.21... Gear, 10... Prime mover, 11... Control prime mover, 20.
...first planetary gear mechanism, 20"...second planetary gear mechanism, 22...'fl star gear, 23...universal joint,
3o...Third planetary gear mechanism, 40...Reversing machine.

Claims (2)

[Claims] (1) Two planetary gear mechanisms are provided that input the power of the input shaft by dividing it into two halves with the same rotational speed, and the internal gears of both planetary gear mechanisms are made rotatable, and the internal gears are provided on the outer periphery of these internal gears. The structure is such that the internal gears are interlocked and connected so that the rotational forces cancel each other out, and a control prime mover is interlocked with the gear on the outer circumferential side of one of the internal gears, and the control prime mover controls both the internal gears. By driving in opposite directions, the same torque is generated on the output shafts of both planetary gear mechanisms, and the number of rotations is increased or decreased steplessly by the same amount. The third output shaft is connected to a sun gear of a third planetary gear mechanism that is rotatable, and the other output shaft is connected to another gear, and the gear is meshed with a gear provided on the outer circumferential side of the rotatable internal gear. Moreover, the rotation direction is reversed through a reversing device on either of the two output shafts, so that only the rotation from one planetary gear of the third planetary gear mechanism is transmitted regardless of the revolution. A continuously variable transmission characterized by having a configuration in which the output is output to the output shaft. (2) 1 provided concentrically with the rotation axis of one planetary gear in the third planetary gear mechanism and the center line of the third planetary gear mechanism
A configuration in which the output shaft of the book is connected via a universal joint such as a universal joint or a constant velocity ball joint, and only rotation from the planetary gear is taken out to the single output shaft regardless of revolution. The continuously variable transmission according to claim 1.