JPH0218456B2 - - Google Patents

Description

[Detailed Description of the Invention] Technical Field The present invention relates to a gear device in which a plurality of gears mesh with a planetary gear, such as a planetary gear device, in which transmitted power can be equally distributed among the plurality of gears. This is related to a power equalization device that can be used.

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 within 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 that rotatably supports 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 external gear 3 completely match, each planetary gear 5 will be equal. 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,
4 and 5 exhibit the expected strength and do not generate vibration noise, but in reality, it is difficult to perfectly match L1 and L2, and the bearings of each planetary gear 5, each gear 3, Since there are always errors in 4 and 5, this equal distribution is practically very difficult, and the development of an effective power equalization device is a major technical challenge.

Purpose The purpose of the present invention is to provide a structure in which a load is applied equally to a plurality of gears that mesh with a central gear, for example, as described above, to each planetary gear that meshes with an external gear as a central gear. Another object of the present invention is to provide a power equalization device that can reduce the size of a gear mechanism and prevent vibration noise.

Structure of the Invention In order to achieve this object, the present invention provides a central gear 3
and a plurality of gears 5 mounted on each conical shaft 8 so as to be movable and rotatable in the axial direction so as to mesh with the central gear 3, and supported to be swingable about the center as a fulcrum, Thrust receiving plate 1 that receives the thrust of each planetary gear at a corresponding position
1, 31 and/or levers 18A, 18B, 20,
26 and 30, and the gear 5
A balancing device is provided to balance the thrust generated in the group toward the small diameter end of the conical shaft. To give an overview of the principle, when a rotational force acts on a plurality of gears 5, a thrust is generated in proportion to the magnitude of the rotational force toward the small diameter end of the conical shaft, so if these thrusts are made equal, The rotational forces acting on the gears 5 are also equal, and the power is equally distributed. Since the plurality of gears 5 are assembled on the conical shaft 8, if the gears move toward the large diameter end of the conical shaft 8, the bearing clearance S becomes smaller, and the gears 5 from the center line of the conical shaft 8 become smaller. e1 is smaller than the other half,
Gear 5 moves against the drive direction shown by arrow A in FIG. 12, and the power share increases. On the contrary, gear 5
moves toward the small diameter end of the conical shaft 8, the bearing clearance S increases, e2 becomes larger than the part of the gear 5 from the center line of the conical shaft 8, and the gear 5
Since it escapes in the drive direction shown by arrow A in Figure 4, the power sharing decreases. As described above, in this invention, by utilizing the property that the thrust changes in proportion to the size of the power sharing, the gear 5 with a small power sharing, that is, the gear 5 with a small thrust is adjusted to the large diameter end of the conical shaft by the thrust balancing device. The gear 5 moves toward the large diameter end of the conical shaft, increasing the power share, and the gear 5 with a large power share, that is, the gear 5 with a large thrust, is moved by the thrust balancing device. The gear 5 is pushed toward the small diameter end of the conical shaft, and the gear 5 moves toward the small diameter end of the conical shaft, reducing the power sharing. By making the thrust of the plurality of gears 5 equal, the power is equally distributed. It was designed so that the

Embodiment Hereinafter, 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 with reference to FIGS. 3 to 14. As shown in FIG. Three conical shafts 8 are fixed at 120 degree intervals on one side, and the fifth and sixth conical shafts are attached to the tips of the conical shafts 8.
A receiving plate 9 shown in the figure is fixed. This receiving plate 9 is provided with a spherical concave surface 10. As shown in FIGS. 7 and 8, a spherical convex surface 1 is provided on the spherical concave surface 10 side of the receiving plate 9.
A thrust receiving plate 11 having a diameter of 2 is assembled. This thrust receiving plate 11 is provided with three spherical concave surfaces 13 on the opposite side of the spherical convex surface 12.
A spherical washer 14 is fitted into the gear 3 and brought into contact with the gear 5. A washer 15 is installed on the opposite side of the gear 5, and a coil spring 16 for removing play is installed between the gear 5 and the carrier 6.

In such a configuration, if there is a difference in the thrust forces generated in the three gears 5 toward the small diameter end of the conical shaft, the thrust receiving plate 11 swings freely, and the gear 5 with the larger thrust moves toward the small diameter end of the conical shaft. The gear 5 that moves and has a small thrust is pushed toward the large diameter end of the conical shaft.

As mentioned above, if the gear 5 moves on the conical shaft 8 toward the small diameter end of the conical shaft 8, the power sharing will be reduced and the thrust will become smaller, and if the gear 5 moves on the conical shaft 8 toward the large diameter end If the two move toward each other, the power sharing will increase and the thrust will become larger, and when the thrust becomes equal, the power sharing will also become equal, resulting in equal distribution of power.

Furthermore, the variation in power sharing due to the axial movement of the gear 5 will be explained in detail based on FIGS. 9 to 14.

At the position of the gear 5 shown in FIG. 9, the center of the gear 5 is advanced by e0 from the center of the conical shaft 8 in the driving direction shown by the arrow A in FIG.

The position of the gear 5 shown in FIG. 11, that is, the gear 5
At the position where the bearing has moved to the large diameter end of the conical shaft 8, the bearing clearance S becomes small, and the distance from the center of the conical shaft 8 to the center of the gear 5 in the driving direction shown by arrow A in FIG. 12 becomes e1. becomes smaller. Since the gear 5 moves against the driving direction, the power share increases and the thrust generated in the gear 5 toward the small diameter end of the conical shaft also increases.

The position of the gear 5 shown in FIG. 13, that is, the gear 5
At the position where the conical shaft 8 has moved to the small diameter end, the bearing clearance S becomes large, and the distance from the center of the conical shaft 8 to the center of the gear 5 in the driving direction shown by arrow A in FIG. 14 becomes e2, which increases. Become. Since the gear 5 moves in the driving direction, the power share is reduced, and the thrust generated in the gear toward the small diameter end of the conical shaft 8 is also reduced.

In addition, the gear 5 is shown in FIGS. 10, 12, and 14.
Since the conical shaft 8 is driven in the direction indicated by the arrow A in the figure, the bearing 17 of the gear 5 contacts one side circumferential surface of the conical shaft 8 via an oil film.

In the first embodiment, the number of gears 5 is three;
In the second embodiment shown in FIGS. 15 to 24, the number of gears 5 is four, and a thrust ball bearing is used as the bearing 17 of the gear 5. A needle roller bearing is adopted, and the thrust balancing device is a combination of levers 18a, 18b, and 20 with the center as a fulcrum.

In FIG. 16, the thrust force generated in the gear 5 toward the small diameter end of the conical shaft is transferred by the spherical washer 14 to the 19th,
It is transmitted to the first levers 18a and 18b shown in FIG. The first levers 18a, 18b have a spherical convex surface 19 provided at the center as shown in FIG.
The spherical concave surface 21 of the second lever 20 shown in Figures 1 and 22
The second lever 20 is inserted into the
As shown in Figure 7, a spherical convex surface 22 provided at the center
The spherical concave surface 2 of the receiving plate 23 shown in FIGS. 23 and 24 is fixed to the carrier 6 via the conical shaft 8.
It is embedded in 4.

Therefore, in FIG. 15, the thrust of the gear 5A and the thrust of the gear 5B are balanced by the first lever 18A, and the thrust of the gear 5C and the thrust of the gear 5D are balanced by the first lever 18B. . Then, a force obtained by adding the thrust of the gear 5A and the thrust of the gear 5B acts on the connecting portion 20a (spherical uneven surfaces 21, 19) between the first lever 18A and the second lever 20, and the thrust of the gear 5C and The force added to the thrust of the gear 5D acts on the connecting portion 20b (spherical uneven surfaces 21, 19) between the first lever 18B and the second lever 20, and the second lever 20 has a spherical convex surface 22 at its center. Receiving plate 2
3, one of the connecting parts 20
The force acting on a and the force acting on the other connecting portion 20b are balanced. As a result, the thrust forces generated in the four gears 5A, 5B, 5C, and 5D can be balanced, and the power is equally distributed.

Note that 25 shown in FIG. 16 is a disc spring for removing play.

In the third embodiment shown in FIGS. 25 and 26, the number of gears 5 is two, and the thrust generated in the gear 5 is received by a lever 26 via a spherical washer 14. With a spherical convex surface 27 provided in the center,
Since it is supported by the spherical concave surface 29 of the receiving plate 28 fixed to the carrier 6 via the conical shaft 8, the 2
The thrust forces generated in the gears 5 directed toward the small diameter ends of the conical shafts can be balanced, and the power is evenly distributed.

In the fourth embodiment shown in FIGS. 27 and 28,
The thrust generated in the six gears 5 is transferred to the three levers 30.
Balance is achieved by a combination of the thrust receiving plate 31 which is swingably supported. The thrust of two gears among the six gears 5 is 30 levers each.
and the total force of the three levers is 30
The total force is applied to the center of the thrust receiving plate 31.
Take it personally. The thrust receiving plate 31 is swingable because its spherical convex surface 32 is supported by the spherical concave surface 34 of the receiving plate 33 fixed to the carrier 6 via the conical shaft 8. Therefore, the thrusts of the six gears 5 can be made equal, and the power is evenly distributed.

The sixth embodiment shown in FIGS. 29 and 30 is an application of the present invention to a gear device other than a planetary gear mechanism, in which an external gear 3 is fixed to an input shaft 2 and a movable gear is fixed to an output shaft 7. A plurality of intermediate gears 5 are meshed between the internal gears 4, and the intermediate gears 5 are rotatably supported by a fixed support shaft 8. And the third
As shown in FIG. 0, the shape of the fixed support shaft 8 and the mounting structure of the intermediate gear 5 to the fixed support shaft 8 are similar to those of the first embodiment. It is also possible to apply the second, third, and fourth embodiments to this gear device.

In each of the above embodiments, a reduction gear device is illustrated, but the input shaft and output shaft can be used in reverse to be applied as a speed increase mechanism.

Further, the present invention is not limited to the above-mentioned embodiment, and the following configuration is also possible.

(b) In the above embodiment, the interlocking from the motor shaft 2 to the external gear 3 as the central gear is achieved by forming the external gear 3 directly on the motor shaft 2. It is also possible to interpose other interlocking mechanisms. The same applies to the case of interlocking with the output shaft of the carrier 6.

(b) Although a one-stage planetary gear mechanism is illustrated, it can also be applied to a system with two or more stages of reduction.

(c) The direction of the taper of the support shaft 8 can be reversed.

(d) The bearing structure using the spherical convex surface and the spherical concave surface in each of the above embodiments may be a combination of a conical surface and a ball.

(e) The number of gears 5 is arbitrary as long as it is 2 or more,
This number will also be determined according to that number.

Effects As detailed above, according to the present invention, the central gear 3 and the plurality of conical shafts 8 which are movably and rotatably attached to each conical shaft 8 so as to mesh with the central gear 3 are provided. gears 5 and a thrust receiving plate 1 that is swingably supported around the center as a fulcrum and receives the thrust of each planetary gear at a position corresponding to the planetary gear.
1, 31 and/or lever 18A, 18b, 20,
26 and 30, and the gear 5
By simply providing a balancing device to balance the thrust generated in the group toward the small diameter end of the conical shaft, the load on each gear 5 can be easily and reliably distributed, and vibration noise can be prevented as much as possible. This is an excellent invention as a power equal distribution gear device, since the entire device can be made compact and a gear device can be provided which can provide a power equal distribution performance with great practical effects.

[Brief explanation of drawings]

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 14 show the first embodiment, and Fig. 3 4 is a longitudinal sectional view of the planetary gear mechanism, FIG. 5 is a front view of the receiving plate, FIG. 6 is a sectional view of the receiving plate, FIG. 7 is a front view of the thrust receiving plate, and FIG. 8 is a front view of the planetary gear mechanism. The figure is a cross-sectional view of the thrust receiving plate, Figure 9 is a partial cross-sectional view showing the center position of the planetary gear on the conical shaft, Figure 10 is a cross-sectional view taken along the line X1-X1 in Figure 9, and Figure 11 is on the conical shaft. Figure 12 is a partial cross-sectional view showing the planetary gear moved toward the large diameter end of the conical shaft.
13 is a partial sectional view showing the planetary gear on the conical shaft moved toward the small diameter end of the conical shaft; FIG. 14 is a sectional view taken along the X3-X3 line in FIG. 13; Figures to Figure 24 show the second embodiment,
Fig. 15 is a front view showing the planetary gear mechanism, Fig. 16 is a sectional view taken along the Y1-Y1 line in Fig. 15, and Fig. 17 is a front view showing the planetary gear mechanism.
The Y2-Y2 line sectional view in Figure 5, and Figure 18 in Figure 15.
Y3-Y3 line sectional view, Fig. 19 is a front view of the first lever, Fig. 20 is a sectional view of the first lever, Fig. 21 is a front view of the second lever, and Fig. 22 is a sectional view of the second lever. ,
Fig. 23 is a front view of the receiving plate, Fig. 24 is a cross-sectional view of the receiving plate, Fig. 25 is a front view showing the assembled state of the lever and the receiving plate in the third embodiment, and Fig. 26 is a longitudinal section thereof. 27 is a front view showing the assembled state of the lever and the thrust receiving plate in the fourth embodiment, and FIG.
29 is a schematic diagram of the gear device according to the fifth embodiment, and FIG. 30 is a partial sectional view thereof. Motor case 1, motor shaft (input shaft) 2, external gear (center gear) 3, fixed internal gear (movable internal gear)
4, planetary gear (intermediate gear) 5, carrier 6, output shaft 7, conical shaft (fixed support shaft) 8, receiving plate 9, spherical concave surface 10, thrust receiving plate 11, spherical convex surface 12, spherical concave surface 13, spherical washer 14 , washer 15, playback coil spring 16, bearing 17, first lever 18A, 18B,
Spherical convex surface 19, second lever 20, spherical concave surface 21, spherical convex surface 22, receiving plate 23, spherical concave surface 24, playback disc spring 25, lever 26, spherical convex surface 27, receiving plate 2
8, spherical concave surface 29, lever 30, thrust receiving plate 31, spherical convex surface 32, receiving plate 33, spherical concave surface 34, driving force acting direction A, bearing gap S, e0, e1, e from one side
2.

Claims (1)

[Scope of Claims] 1. A central gear; a plurality of gears mounted on each conical shaft so as to be movable and rotatable in the axial direction so as to mesh with the central gear; It is composed of a thrust receiving plate and/or lever that is movably supported and receives the thrust of each planetary gear at a position corresponding to the planetary gear, and the thrust that is generated in the gear group and directed toward the small diameter end of the conical shaft. A power equal distribution gearing device using a conical shaft and a gear thrust balancing device, characterized in that it is provided with a balancing device for balancing the power. 2. The balancing device uses a conical shaft and a gear thrust balancing device as set forth in claim 1, which comprises one thrust receiving plate that corresponds to and receives the thrust of three planetary gears. A power uniform gearing device. 3 The balancing device consists of a pair of first levers that receive the thrust of adjacent planetary gears among the four planetary gears, and a second lever that is connected between these first levers and can swing around the center as a fulcrum. A power uniform gearing device using a conical shaft and a gear thrust balancing device according to claim 1. 4. A power source using a conical shaft and a gear thrust balancing device according to claim 1, wherein the balancing device is a single lever that corresponds to two planetary gears and receives their thrusts. Equidistant gear system. 5 The balancing device consists of three levers that receive the thrust of two adjacent planetary gears among six planetary gears, and a thrust receiving plate that is connected between these levers and can swing around the center as a fulcrum. A power uniform gearing device using the conical shaft and gear thrust balancing device according to claim 1.