JPH07293645A - Planetary gear type speed change mechanism - Google Patents

Abstract

PURPOSE:To provide a speed change mechanism having a simple structure by making the axes of rotation and displacement shafts into concentric and eccentric conditions to cause the change of a transmission velocity ratio to determine a place high in the angular velocity of the displacement shaft by using a one-way transmission mechanism by a joint mechanism. CONSTITUTION:Plural displacement shafts 14 are rotatably arranged on an adjustment member 9 concentrically rotating with an output shaft 3. A gear-to-be-transmitted 16 engaging with a speed change gear 6 is arranged via a one-way transmission mechanism 17 onto respective displacement shafts 14, and plural rotation shafts 18 rotating by an arm member A are arranged opposite to the displacement shafts 14. Moreover, a joint mechanism 19, wherein a transmission velocity ratio is momentarily changed in one rotation at the time of shaft axis displacement with each other, is provided with a rotation phase displaced each other between the rotation and displacement shafts 18 and 14. The rotational frequency of the inscribed gear B of a planetary gear mechanism can be changed to change the velocity ratio between an input shaft 2 and the output shaft 3, by determining a place high in an angular velocity caused in the respective displacement shafts 14 by using the one-way transmission mechanism 17. Rotation can be surely transmitted to the inscribed gear B to perform good speed changing.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear type speed change mechanism used in, for example, automobiles and industrial machines.

[0002]

2. Description of the Related Art Heretofore, as a transmission mechanism of this kind, a gear type structure, a conical wheel type structure, a spherical wheel type structure and the like have been known.

[0003]

However, in the above-mentioned conventional structure, although the speed change mechanism having the gear type structure is excellent in reliable rotation transmission, there are some disadvantages that are contrary to the operability of speed change and the demand for downsizing. Have

[0004]

SUMMARY OF THE INVENTION An object of the present invention is to solve such an inconvenience, and the gist thereof is to dispose an input shaft and an output shaft in a butted state on a frame,
An arm member is formed on the input shaft, a sun gear is formed on the output shaft, and a transmission gear is rotatably disposed on the output shaft, and an internal gear is formed on the transmission gear. It comprises a planetary gear mechanism in which a plurality of planetary gears simultaneously meshing with the sun gear are rotatably arranged on the arm member, and the adjusting member for adjusting and rotating by the adjusting mechanism concentrically with the output shaft is made rotatable. A plurality of displacement shafts are rotatably disposed on the adjusting member, and a transmitted gear that meshes with the speed change gear is disposed on each of the displacement shafts via a one-way transmission mechanism. A plurality of rotary shafts, which are rotated by the arm members, are disposed in the frame so as to face the displacement shafts, and the transmission speed ratio during one rotation when there is a mutual axial misalignment between the rotary shafts and the displacement shafts. It was constructed by interposing a joint mechanism in which the In a planetary gear type transmission mechanism, wherein the door.

At this time, as the joint mechanism, the arm member is formed as a gear, and a plurality of transmission gears that mesh with the arm member are arranged on the rotary shaft, and the transmission gears are arranged on the crank radii of the respective transmission gears. The sliding rollers may be provided so as to be out of phase with each other in a rotational phase shift, and a driven member having a sliding groove on which the sliding rollers slide is disposed on each displacement shaft. It is also possible to use a universal joint as.

[0006]

The arm member is rotated by rotating the input shaft arranged on the frame, and this rotation causes the planetary gears to mesh with each other around the sun gear and the inscribed gear, depending on the rotation of the inscribed gear. The output shaft rotates, while the rotation of the arm member rotates the rotation shaft, the rotation of the rotation shaft rotates the displacement shaft through the joint mechanism, and the rotation of the displacement shaft rotates through the one-way transmission mechanism. Therefore, the speed change gear integrated with the internal gear rotates.

At this time, when the rotary shaft and the displacement shaft have the same axis, the transmission speed ratio to the displacement shaft does not change during one rotation of the rotary shaft, and the adjustment member is adjusted and rotated. When the axes of the rotary shaft and the displacement shaft are eccentric, the transmission speed ratio to the displacement shaft during one rotation of the rotary shaft changes momentarily, and the phase of the change in the transmission speed ratio is different in each joint mechanism. The rotation phases are shifted from each other, and the rotation of the displacement shafts, which are out of phase with each other, causes the speed change gear to rotate through the one-way transmission mechanism, and the one-way transmission mechanism is a displacement that rotates at a high speed within each displacement axis. The rotation of the shaft is picked up to rotate the transmission gear in a pulsating manner, which changes the rotation speed of the transmission gear, and the rotation speed of the internal gear integrated with the transmission gear also changes the rotation speed of the output shaft. Therefore, the adjustment member is adjusted and rotated to rotate the axis of rotation and displacement. The by shifting from concentric, it is possible to change the speed ratio between the input shaft and the output shaft depending on the amount of the deviation.

At this time, the arm member is formed as a gear, and a plurality of transmission gears which mesh with the arm member are arranged on the rotary shaft, and sliding rollers are mutually provided on the crank radii of the respective transmission gears. The joint mechanism can be made compact and simple in structure by projecting the rotation phases and arranging a driven member having a sliding groove for sliding the sliding roller on each displacement shaft. it can.

[0009]

1 to 8 show an embodiment of the present invention, in which 1 is a frame, and in this case, two left and right plate members 1a and 1a
Is integrally formed with a space member 1b between them, and the input shaft 2 and the output shaft 3 are abutted on the frame 1 to form a bearing 4
5, the input shaft 2 is formed with an arm member A, the output shaft 3 is formed with a sun gear D, and the output shaft 3 is rotatably provided with a speed change gear 6. 6, an internal gear B is integrally formed, and a planetary gear C that simultaneously meshes with the internal gear B and the sun gear D is rotated by bearings 8 on each of the three pin shafts 7 installed on the arm member A. The bearings are freely supported, and thus a planetary gear mechanism including four members of an arm member A, an internal gear B, a planetary gear C, and a sun gear D is configured.

In this case, the number of teeth Zb of the internal gear B = 72,
Number of teeth Zc of planetary gear C = 20, number of teeth Zd of sun gear D
= 32, the relative speed ratio is (where the rotation speed of the input shaft 2 is Na, the rotation speed of the internal gear B is Nb, the rotation speed of the planetary gear C is Nc, and the rotation speed of the sun gear D is Nd. Nd
Since −Nb) / (Na−Nb) = 1 + (Zb / Zd), a numerical value is included in the calculation, (Nd−Nb) / (N
a-Nb) = 4/13 planetary gear mechanism is constructed, so that for example, in the case of Na = 1 and Nb = 1, Nd = 1.
Therefore, in the case of Na = 1 and Nb = 13 / 9≈1.44, Nd = 0, and it is possible to change Nd from 1 to 0 by changing Nb from 1 to 1.44. Become.

Reference numeral 9 denotes an adjusting member, which in this case is concentrically supported on the output shaft 3 by a bearing 10 so as to be rotatable.
The adjusting member 9 is rotatably provided by an adjusting mechanism 13 including a worm tooth 11 formed on the outer periphery of the adjusting member 9 and a worm 12 rotatably supported by the frame 1. The adjusting member 9 is provided with four displacement shafts 14 as bearings. A unidirectional transmission mechanism 17 having a ball or roller structure for transmitting rotation in only one direction, such as one Four rotating shafts 18 which are supported by a directional clutch and which are opposed to the displacement shaft 14 and which are rotated by the arm member A are rotatably arranged on the frame 1. The rotating shaft 18 and the displacement shaft 14 are rotatable.
And a coupling mechanism 19 in which the transmission speed ratio changes momentarily during one rotation when the axes O ₁ and O _{2 are} displaced from each other, and the rotational phases thereof are offset from each other.

In this case, as the joint mechanism 19, the arm member A is formed as a gear, and the transmission gear 20 meshing with the arm member A is rotatably borne by the four rotation bearings 21 on the rotating shaft 18. Sliding rollers 22 are provided so as to project on the crank radius R of each transmission gear 20, and the rotational phase of each of the four sliding rollers 22 is changed according to the rotation as shown in FIGS. 5 and 8. Are formed so as to be shifted from each other such that the angular velocities of the sliding rollers 22 are sequentially increased, and a driven member 24 having a linear groove 23 in which the sliding roller 22 slides is formed on each displacement shaft 14. .

In this case, the number of teeth of the arm member A is 100,
The transmission gear 20 has 50 teeth, the transmitted gear 16 has 50 teeth, and the transmission gear 6 has 100 teeth. Therefore, the speed ratio between the arm member A and the transmission gear 6 is set to 1. ing.

Since this embodiment has the above-mentioned structure, when the rotary shaft 18 and the displacement shaft 14 have the same axis O ₁ · O ₂ as shown in FIG. When the sliding roller 22 having the rotation is rotated while sliding in the sliding groove 23, as shown in the left figure to the right figure of FIG.
Since the crank radius R and the rotation radius M of the displacement shaft 14 are the same, as shown in FIG. 5, the transmission speed ratio to the displacement shaft 14 during one rotation of each rotation shaft 18 does not change.
= 1 and Nb = 1, Nd = 1 corresponding to input shaft 2
And the output 3 will rotate at the same rotation speed.

Then, the adjusting member 13 is adjusted and rotated by the adjusting mechanism 13 so as to be concentric with the output shaft 3, whereby the eccentricity of the axes O ₁ and O ₂ between the rotary shaft 18 and the displacement shaft 14 is adjusted as shown in FIG. When the displacement shaft 14 is eccentric by e, the rotation radius M of the displacement shaft 14 becomes (R +
e) to (R−e), and the change of the radius of gyration M changes the transmission speed ratio to the displacement shaft 14 during one rotation of the rotation shaft 18 at a constant speed, and the phase of the change of the transmission speed ratio. 8, the rotational phases of the joint mechanisms 19 are shifted from each other, and the rotation of the displacement shafts 14 with the rotational phases deviated from each other is transmitted through the one-way transmission mechanism 17 to the transmission gear 6.
The one-way transmission mechanism 17 picks up the rotation of the displacement shaft 14 that rotates at a high angular velocity in each of the displacement shafts 14 to rotate the transmission gear 6 in a pulsating manner, whereby the rotation speed of the transmission gear 6 changes. Then, the rotation speed of the output shaft 3 changes as the rotation speed of the internal gear B integrated with the speed change gear 6 changes, and in this case, the rotation speed is increased to Na = 1, Nb = 13 / 9≈1.44. Then, Nd = 0, that is, the rotation of the output shaft 3 is stopped, and accordingly, the adjusting member 9 is adjusted and rotated to rotate the rotating shaft 18.
By shifting the axes of the displacement shaft 14 and the displacement shaft 14 from the concentric axis, the speed ratio between the input shaft 2 and the output shaft 3 can be changed according to the amount e of the deviation.

Therefore, the adjusting member 9 is adjusted and rotated so that the axes O ₁ and O ₂ of the rotary shaft 18 and the displacement shaft 14 are concentric and eccentric, and the transmission speed ratio is changed during one rotation. , The coupling mechanism 19 causes the rotational phase of the transmission speed ratio to be shifted, and the location where the angular velocity is high on each displacement shaft 14 is picked up using the one-way transmission mechanism 17, and as a component of the planetary gear mechanism. By changing the rotation speed of the internal gear B, the speed ratio between the input shaft 2 and the output shaft 3 can be changed, so that a speed change mechanism having a simple structure can be obtained, and the rotation shaft 18 and the displacement shaft 14 Since the rotation is transmitted by using the joint mechanism 19, the transmission can be surely performed, and the internal gear B can be surely rotated, so that the better gear shifting can be performed.

Further, in this case, the arm member A is formed as a gear, and four transmission gears 20 meshing with the arm member A are arranged on the rotary shaft 18, and the crank radius R of each of the transmission gears 20 is increased. The sliding rollers 22 are protruded from each other with their rotational phases shifted from each other, and a driven member 24 having a sliding groove 23 on which the sliding rollers slide is disposed on each displacement shaft 14, whereby the joint mechanism 19 is formed. Since it is configured, it is possible to make the shift structure smaller and simpler.

The present invention is not limited to the above embodiment, a universal joint can be used as the joint mechanism 19, and the numbers of the displacement shafts 14 and the rotary shafts 18 can be appropriately selected. By increasing this number, pulsation will be reduced.

[0019]

As described above, the present invention adjusts and rotates the adjusting member to make the axes of the rotary shaft and the displacement shaft concentric and eccentric, and to change the transmission speed ratio during one rotation. The joint mechanism is used to shift the rotational phase of the displacement axis, and the location of high angular velocity generated on each displacement axis is picked up using the one-way transmission mechanism. The speed ratio between the input shaft and the output shaft can be changed by changing the rotation speed. Therefore, a speed change mechanism having a simple structure can be obtained, and rotation is transmitted between the rotation shaft and the displacement shaft by using a joint mechanism. As a result, reliable transmission can be performed, the internal gear can be reliably rotated, and thus good gear shifting can be performed.

Further, at this time, the arm member is formed as a gear, four transmission gears which mesh with the arm member are arranged on a rotary shaft, and sliding rollers are mutually provided on a crank radius of each transmission gear. A smaller and simpler gear shifting structure is provided by projecting with the rotational phase shifted and disposing a driven member having a sliding groove on which the sliding roller slides on each displacement axis, and by configuring a joint mechanism with this. You can

The above-mentioned intended purpose can be sufficiently achieved.

[Brief description of drawings]

FIG. 1 is an overall vertical sectional view of an embodiment of the present invention.

2 is a cross-sectional view of the embodiment of the present invention shown in FIG.

FIG. 3 is an explanatory cross-sectional view of the embodiment of the present invention shown in FIG.

FIG. 4 is an explanatory sectional view of the embodiment of the present invention shown in FIG.

5 is an explanatory sectional view of the embodiment of the present invention shown in FIG.

6 is an explanatory sectional view of the embodiment of the present invention shown in FIG.

7 is an explanatory sectional view of the embodiment of the present invention shown in FIG.

8 is an explanatory sectional view of the embodiment of the present invention shown in FIG.

[Explanation of symbols]

 1 frame 2 input shaft 3 output shaft 6 speed change gear 9 adjusting member 13 adjusting mechanism 14 displacement shaft 16 transmitted gear 17 one-way transmitting mechanism 18 rotating shaft 19 joint mechanism 20 transmitting gear 22 sliding roller 23 sliding groove 24 driven member

Claims (3)

[Claims] 1. An input shaft and an output shaft are arranged in a butted state on a frame, an arm member is formed on the input shaft, a sun gear is formed on the output shaft, and a transmission gear is rotatably arranged on the output shaft. And a planetary gear mechanism in which a plurality of planetary gears that simultaneously mesh with the internal gear and the sun gear are rotatably arranged on the arm member. The adjusting member is rotatably arranged concentrically with the output shaft by an adjusting mechanism, and a plurality of displacement shafts are rotatably arranged on the adjusting member, and the shift gears are provided on the respective displacement shafts. A transmission gear that meshes with the transmission shaft is disposed through a one-way transmission mechanism, and a plurality of rotation shafts that are rotated by the arm members are disposed in the frame so as to face the displacement shaft. Transmission speed ratio during one rotation when there is mutual axial misalignment with the shaft A planetary gear type speed change mechanism, characterized in that a joint mechanism that changes from moment to moment is provided with their rotational phases shifted from each other. 2. As the joint mechanism, the arm member is formed as a gear, and a plurality of transmission gears which mesh with the arm member are arranged on the rotary shaft, and slide on the crank radius of each of the transmission gears. The moving rollers are provided so as to protrude from each other with their rotational phases shifted from each other, and a driven member having a sliding groove on which the sliding rollers slide is arranged on each of the displacement shafts. Planetary gear type transmission mechanism described 3. The planetary gear type speed change mechanism according to claim 1, wherein a universal joint is used as the joint mechanism.