JPS6065940A - Power equally distributing gearing using conical shaft - Google Patents

Abstract

PURPOSE:To make the uniform distribution of load to each gear easier by mounting more than one gear on a conical shaft part respectively, with thrust being provided to it in a direction toward the larger diameter side by means of a resilient member, in a gearing in which said more than one gear is meshed with a central gear. CONSTITUTION:Three supporting shafts 8 are fixed on the side of a carrier 6 which is connected to the end part of an output shaft 7, at an interval of 120 deg., forming the outer peripheral faces of their projecting parts into a taper. A collar 11, a planetary gear 5, and a collar 14 are fitted in this tapered conical shaft part 9 in order, and assembled in an integrated form by interposing a resilient member 15 such as a coned disk spring, etc. toward a receptacle ring 10 on the end of the shaft part 9. The planetary gear 5 is fitted in the shaft part through a sliding bearing metal 12 having a tapered inner surface. The planetary gear 5 is meshed with an external gear 3 as a sun gear provided on a motor shaft 2 and, by enabling each planetary gear 5 to be moved in a direction, whereby the load applied to each gear 5 can be relieved, a load is distributed uniformly.

Description

Detailed Description of the Invention Technical Field The present invention relates to a gear system in which a plurality of gears are meshed with a central gear, such as a planetary gear arrangement, in which transmitted power is equally distributed to the plurality of gears. This relates to a power equalization device that can perform

BACKGROUND ART Conventionally, as an example of this type of gear device, there is a geared motor speed reduction mechanism as shown in FIG.

In this reduction mechanism, a motor shaft 2 supported in a motor case 1 is interlocked with an external gear 3 as a sun gear, and three planetary gears 5 are meshed between the external gear 3 and a fixed internal gear 4. , a carrier 6 rotatably supporting the planetary gear 5
is linked to the output shaft 7. In this planetary gear mechanism,
As shown in FIG. 2, if the center-to-center distance L1 of each planetary gear 5 and the center-to-center distance [L2] between each planetary gear 5 and the external gear 3 completely match, each planetary gear 5 will be equally spaced. Therefore, if there is no error in each gear 3.4.5, the load will be applied to each planetary gear 5 on average, and each gear 3.4.5 will exhibit the expected strength and no vibration noise will be generated. However, in reality, the above L1. It is difficult to match L2 completely, and 8
The bearing portion of the planetary gear 5 and each gear 3, 4. .

Object The object of the present invention is to provide a plurality of gears meshing with a central gear,
For example, as mentioned above, by configuring the structure so that the load is applied equally to each planetary gear that meshes with the external gear as the central gear, the gear mechanism can be made smaller and vibration noise can be prevented. The purpose is to provide an equal distribution device.

Structure of the Invention In order to achieve this object, the present invention provides a plurality of gears 5 meshing with the central gear 3 with a thrust force by an elastic member 15 in a direction toward the larger diameter side of the conical shaft portion 9, respectively. The axial position of each gear 5 on the conical shaft part 9 is changed according to the magnitude of transmitted power, and the conical hole 13 of each gear 5 is fitted into the conical shaft part 9. By moving the gear in the axial direction, the gap S between the shaft and the hole is changed, and the misalignment distance ll1lle between the axial center of the conical shaft portion 9 and the rotational axis of the gear 5 that receives the load is changed, The load is reduced on the gear 5 that is receiving a large load, and the load is increased on the gear 5 that is receiving a small load, so that the power is evenly distributed.

Embodiment A first embodiment in which the present invention is embodied in a speed reduction mechanism for a geared motor shown in FIG. 1 will be described below with reference to FIGS. is 1
They are fixed at intervals of 20 degrees, and the outer circumferential surface of the protruding portion is formed into a tapered shape, and a receiving ring 10 is fixed to the tip of the tapered conical shaft portion 9. A planetary gear 5 is inserted into this conical shaft portion 9 via a collar 11, and is meshed between the external gear 3 and the fixed internal gear 4 of the motor @2. A sliding bearing metal 12 is fitted onto the inner periphery of the planetary gear 5, and the inner peripheral surface of the sliding bearing metal 12 forms a tapered conical hole 13 so as to be brought into close contact with the conical shaft portion 9. On the small diameter side of this conical shaft portion 9, the receiver is connected to the ring 10 and the planetary gear 5.
In the embodiment, a concave spring shown in FIGS. 18 to 21 is used, which is connected to one side of the elastic member 15 via a collar 14. ) is interposed, and this elastic member 15 causes the planetary gear 5 to
A thrust force directed toward the larger diameter side of the conical shaft portion 9 is applied to the conical shaft portion 9 .

Now, FIG. 5.6 shows a light load state in which the planetary gear 5 is pressed against the collar 11 on the large diameter side of the conical shaft portion 9 by the elastic member 15. In this light load state, the output shaft 7 of FIG. When a large load is applied, the planetary gear 5 moves by a distance 11a toward the smaller diameter side of the conical shaft portion 9, as shown in FIG. 7.8. As a result, the gap S between the conical hole 135- of the sliding bearing metal 12 of the planetary gear 5 and the outer circumferential surface of the conical shaft portion 9 becomes larger.
The rotation axis of the planetary gear 5 is e relative to the axis of the conical shaft portion 9.
However, the planetary gear 5 is shifted to one side due to a misunderstanding. If one of the three planetary gears 5 is subjected to a larger load than the other planetary gears 5 due to a manufacturing error or the like, the axial movement distance a increases in an attempt to reduce this load. Therefore, the misalignment distance @e becomes larger than the other planetary gears 5, so the planetary gear 5 moves backward in the direction of reducing the load, and the load it bears is reduced. Gear 5 bears the burden. In this way, each planetary gear 5 is automatically adjusted to buffer its axial travel distance, and when the power is equally distributed to the three planetary gears 5, the thrust generated in the planetary gear 5 and the elastic force of the elastic member 15 are balanced. , the planetary gear 5 will rotate in its balanced position.

In the second embodiment shown in FIG. 9, a needle roller bearing 16 with a thrust ball bearing is used in place of the sliding bearing metal 12 in the first embodiment. A tapered sleeve 6-leave 17 is fitted in between, and this tapered sleeve 17 moves together with the planetary gear 5 on the conical shaft 9 to prevent the axial center of the conical shaft 9 and the rotational axis of the planetary gear 5 from being misaligned. The distance @e changes, and equal power distribution is performed as in the first embodiment. or,
In the first embodiment, a disc spring is used as the elastic member 15 that pushes the planetary gear 5 toward the larger diameter side on the conical shaft portion 9, but in this embodiment, a coil spring is used as the elastic member 15. are doing.

In the first embodiment and the second embodiment, the elastic member 15 is separately provided for each planetary gear 5, but in the tenth embodiment
In the third embodiment shown in FIGS. to 14, each of the elastic members 1
5 are integrated into one waveform ring spring 18 as shown in FIG. Although each planetary gear 5 is an independent and separate body, in this embodiment, this receiving ring 10 is also integrated into one common bearing (one pulling) as shown in FIG.

In the waveform ring spring 18, three
through-holes 20 are formed, and the conical shaft portion 9 of the support shaft 8
It is designed to be mated to the This wave ring spring 1
8 indicates each insertion hole 20 (the ridge 18a near “j” and the ridge 18
troughs 181] between a) to form a wave shape, and each trough 18
b is supported by the common receiver (pring 19), and one side of the crest 18a is the collar 1 in contact with the planetary gear 5.
4 and urges the planetary gear 5 toward the larger diameter side of the conical shaft portion 9, making this peak portion 18a an elastic portion 15 having the same function as the elastic member 15.

Now, as shown in FIG. 14, the load on one planetary gear 5B increases and the waveform ring spring 18 on the conical shaft portion 9B
When the elastic portion 15 of the wave ring spring 18 is compressed and moved toward the smaller diameter side, the elastic portion 15 of the wave ring spring 18 is deformed as shown by the broken line, and the other planetary gears 5A, 5C are connected to the conical shaft portions 9A, 9C.
This actively produces an effect of increasing the thrust force pushing back toward the larger diameter side, which is effective for equal distribution of power.

Further, instead of the waveform ring spring 18, a ring spring 18 shown in FIG. 22 may be used. Three arm parts 15 are formed on the outer periphery of this ring spring 18, and these arm parts 15 serve as elastic parts. The function of this ring spring 18 is also similar to that of the waveform ring spring 18.

The fourth embodiment shown in Figs. 15 and 16 is applied to a gear device other than a planetary gear mechanism, and there is a gap between an external gear 3 fixed to the input shaft 2 and an internal gear 4 fixed to the output shaft 7. A plurality of intermediate gears 5 are meshed together, and this intermediate gear 5 is attached to a fixed support shaft 8.
It is rotatably supported by. As shown in FIG. 16, the shape of the fixed support shaft 8 and the structure for attaching the intermediate gear 5 to the fixed support shaft 8 are the same as in the first embodiment. It is also possible to apply the second and third embodiments to this gear device.

In the fifth embodiment shown in FIG. 17, a separate elastic member 21 (in this embodiment, a separate elastic member 21 for each planetary gear 5) is also provided between the collar 11 on the large diameter side in the first embodiment and the carrier 6. A spring is used.

), the planetary gears 5 are also biased toward the smaller diameter side of the conical shaft portion 9, and each planetary gear 5 is held at a neutral position by balance with the elastic portion 15 on the smaller diameter side. Therefore,
Each planetary gear 5 can move toward both the small diameter side and the large diameter side of the conical shaft portion 9, making it easier to equally distribute the load. Moreover, this elastic member 21 is also used in the second to fourth embodiments.
may be taken in the same way.

In addition, although the reduction gear device was illustrated in each of the above embodiments,
It can also be applied as a speed increasing mechanism by using these input shafts and output shafts in reverse.

Furthermore, the structure is not limited to the embodiment described above, and the following configuration is also possible. Although the gear 3 is formed, other interlocking mechanisms may be interposed between the motor shaft 2 and the external gear 3. In addition, carrier 6
The same applies to the case of interlocking with the output shaft 7.

(b) Although a one-stage Ti star gear mechanism is illustrated, it can also be applied to a two-stage or more reduction gear mechanism.

(c) Reverse the direction of the taper of the support shaft 8.

10- Effects According to the present invention described in detail above, the plurality of gears 5 meshing with the center gear 2 are each given a thrust by the elastic member 15 to the conical shaft portion 9 in the direction toward its large diameter side. With a simple structure that requires only installation, it is possible to easily and reliably distribute the load on each gear 5 evenly, which in turn prevents vibration and noise as much as possible and makes the entire device compact, providing power, etc. with great practical effects. This is an excellent invention as a gear device that can provide distribution performance.

[Brief explanation of the drawing]

Fig. 1 is a sectional view showing a conventional geared motor speed reduction mechanism, Fig. 2 is a schematic view showing only the planetary gear mechanism part, Figs. 3 to 8 show the first embodiment, and Fig. 3 is a planetary gear mechanism. A front view showing the gear mechanism, FIG. 4 is a longitudinal sectional view thereof, FIG. 5 is a partial sectional view showing the planetary gear on the conical shaft in a light load condition, and FIG. 6 is its X 1-X i 7 is a partial sectional view showing the installation state when loaded at a large angle, FIG. 8 is a sectional view taken along the X2-x2 line, and FIG. 10 to 14 show the third embodiment, FIG. 10 is a front view showing the planetary gear mechanism, FIG. 11 is a vertical sectional view thereof, and FIG.
Fig. 2 is a perspective view of the common bearing ring, Fig. 13 is a perspective view of the wave ring spring, Fig. 14 is a developed view showing the action of the wave ring spring, and Fig. 15 is a gear device according to the fourth embodiment. Schematic diagram, FIG. 16 is a partial sectional view showing how the conical shaft part and the planetary gear are attached in this embodiment, and FIG. 17 is a vertical cross-sectional view showing how the conical shaft part and the planetary gear are attached in the fifth embodiment. 18 to 21 are perspective views showing a book spring, respectively, and FIG. 22 is a perspective view showing a separate ring spring. Motor shaft (input shaft) 2, external gear 3, fixed internal gear (internal gear) 4, planetary gear (intermediate gear) 5, output shaft 7, support shaft (fixed support shaft) 8, conical shaft part 9, bearing is ring 10. Slide bearing metal 12, conical hole 13, elastic member (elastic part) 15, needle roller bearing with thrust ball bearing 16, tapered sleeve 17, ring spring 18, common bearing is ring 19°. Open DHGO-65940 (6)

Claims (1)

[Claims] 1. A conical shaft characterized in that a plurality of gears meshing with a central gear are each attached to a conical shaft portion by applying a thrust by an elastic member in a direction toward the large diameter side of the conical shaft portion. Power uniform gearing device using. 2. The elastic member is a single ring spring common to each gear, and an elastic part is formed in a portion corresponding to each gear, and some of the gears resist the thrust of this elastic part. When the gear moves toward the small diameter side of the conical shaft part, another elastic part is configured to increase the thrust force directed toward the large diameter side of the conical shaft part with respect to other gears in conjunction with this. A power uniform gearing device using a conical shaft according to item 1. 3. An equal power gearing device using a conical shaft according to claim 1, wherein the elastic member is separate for each gear. 4. A power uniform gearing device using a conical shaft according to claim 3, wherein the elastic member is a disc spring. 5. A power uniform gearing device using a conical shaft according to claim 3, wherein the elastic member is a coil spring.