JPS63101545A - Planetary speed change gear - Google Patents

Abstract

PURPOSE:To obtain various speed change ratios by rotating the respective sun gears in the same manner, disposing two planetary gears in a 180-degree arc in each planetary gear mechanism, which are supported by a single carrier, and providing means for selectively restricting the rotation of the respective ring gears. CONSTITUTION:Two sun gears 11, 12 are respectively engaged with planetary gears 21, 22 supported by a carrier 4, and ring gears 31, 32 are provided. A lock pin 70 projected from a switching lever 7 is selectively engaged with engaging grooves 35, 36 of the ring gears 31, 32, whereby one of the ring gears is kept from rotating. Accordingly, various speed change ratios can be obtained with a small number of members.

Description

[Detailed description of the invention] 【Technical field】

The present invention relates to a planetary transmission using a planetary gear mechanism.

[Background technology]

As shown in Figure MS8, the 11-star gear mechanism is commonly called the Naro 2 -H (I) type, which consists of a planetary gear 21 and a ring gear 31 supported by a sun gear 11 and a carrier 4. Yes, and in this one, Sungear 1
If one of the 731 champions is fixed with 1, carrier 4, and ring, any one of the other two can be made the driving side and the other the driven side, and the driving side and the driven side can be It is known that various speed ratios can be obtained by combinations of and fixed selections. In addition, in the above structure, if both the driving side and the driven side are set to one of the above-mentioned kings, if the remaining members are unfixed and connected to the driving side, the planetary tooth Sa
It is also known that W becomes an integral rotating body, and the driving side and driven side are directly connected, and a speed ratio of 1:1 can be obtained. This means that the gear ratio can be changed easily. However, in this type of gear ratio switching, since one gear ratio is 1:1, there are many restrictions on usage.
11゜For this, planetary gear 8! In order to obtain a speed change position using the lateral side, a plurality of planetary gear IIL mechanisms are arranged in the axial direction, and by selectively restraining the rotation of the plurality of members in these planetary gear mechanisms, a 1:1 ratio is achieved. A variety of gear ratios have been provided in the past that are capable of obtaining a plurality of gear ratios. However, this type of conventional planetary transmission has the following problems. In other words, in a planetary gear mechanism, the idea is to disperse the transmitted torque. It's a good idea, but the main reason for this is to align the centers of the sun gear with the carrier and ring gear, and to prevent the carrier and ring gear from falling in the axial direction. ! It has a configuration in which star gears are arranged at equal intervals, and multiple planetary gears Pi! Planetary transmissions using 1v1 also used three or more planetary gears for each planetary gear mechanism for the same reason. In other words, a large number of planetary gears are required, which inevitably increases the number of structural members, which is a constraint on cost reduction and the like.

[Purpose of the invention]

The present invention has been made in view of these points, and its object is to provide a planetary transmission that can obtain various speed ratios with a small number of members.

[Disclosure of the invention]

Therefore, the present invention provides a planetary gear having a plurality of planetary teeth Jl'L Isokare arranged in parallel in the axial direction, which are made up of a sun gear, a ring gear arranged concentrically with the sun gear, and a planetary gear that meshes with the sun gear and the ring gear. In the transmission, each sun gear rotates at the same time, and there are two planet gears in each planetary gear PI & structure with an interval of 180°, and the planet gears placed above each "il" star gear are mounted on a single carrier. All the planetary gears are supported and arranged at equal intervals around the axis of the sun gear, and are characterized by being provided with a restraining means for selectively restraining the rotation of each ring gear which is said to be freely rotatable. Hereinafter, the present invention will be described in detail based on an illustrated embodiment. Figures 1 to 3 show an embodiment of the present invention. A motor mounting base 2 that closes one end opening of a gear case 1. Two sun gears 11 and 12 having different numbers of teeth are fixed to the output shaft 60 of the motor 6 attached to the motor 6 in the axial direction.
Two planet gears 21 supported by a carrier 4 mesh with the sun gear 11, and two planet gears 22, which are also supported by the carrier 4, mesh with the sun gear 12. A ring gear 31 is provided on the outer periphery of the planet gear 21 and is rotatably disposed concentrically with the sun gear 11 and meshes with the planet gear 21. A ring gear 32 is provided and meshes with the planetary gear 22. Each of the above! ! The carrier 4 supporting the star gears 21 and 22 by pongee 41 and 42 has an output shaft 5 integrally formed therein, and is rotatably held in the gear case 1 via a bearing 50. In the figure, 51 is a thrust plate. The above-mentioned pair of ring gears 31 and 32 arranged in the axial direction have different numbers of teeth, but have the same outer diameter, and both have a large number of engagement grooves 35 and 36 on their outer peripheral surfaces. They are formed at equal intervals in the direction. These engagement grooves 35
, 36, a lock bin 70 protruding from a switching lever 7 slidably held between the outer surface of the gear case 1 and the housing 3 is selectively engaged in accordance with the sliding of the switching lever 7. This engagement restricts the rotation of either of the ring gears 31, 32, resulting in a fixed state. Now, if the ring gear 31 is in the illustrated state, that is, the ring gear 31 is fixed, the rotation of the motor 6 is controlled by the gear ratio determined by the number of teeth of the sun gear 11 and the number of teeth of the ring gear 31. At this time, the ring gear 32 idles. Conversely, if the rotation of the ring gear 32 is restrained, the carrier 4 and the output shaft 5 will rotate at a speed ratio determined by the number of teeth of the sun gear 12 and the ring gear 32.
The ring gear 31 idles. In both cases, the output shaft 5 can be driven at a gear ratio that is not 1:1. Here, as the planetary gear 21 and the planetary gear 22,
Only two of them are used, and for this reason, problems such as centering the sun gears 11 and 12 and ring gears 31 and 32 and tilting of the ring gears 31 and 32 in the axial direction are likely to occur. However, as is clear from the vJ2 diagram, two planetary gears 21 and 21 are arranged at 180° intervals, and two 3! ! ! star gear 22.22
These four planetary gears 21 are also arranged at 180° intervals.
By supporting all of t22 by the carrier 4, it is possible to center each of these members, and the arrangement of the planetary gears 21 and 22, both of which are supported by the carrier 4, is 90 degrees around the output shaft 60. By shifting the planetary gears 21 and 22 so that they are equivalent to four planetary gears arranged at equal intervals,
This prevents not only the carrier 4 but also both ring gears 31 and 32 from falling in the axial direction. That is, since the four planetary gears 21 and 22 are attached to the carrier 4 at 90" intervals, the carrier 4 does not tilt in the axial direction, and each of the ring gears 31 and 32 !It is easy to fall down in the direction perpendicular to the direction in which the I-gear 21.21 or the planetary gear 22.22 are connected, but these four planetary gears 21.22 are supported by the same carrier 4. , and even when changing the gear ratio, all planetary gears are 21.2
Since ring gear 2 always revolves, ring gear 31
．． 32 is less likely to fall. The embodiment shown in Fig. pltJ4 and Fig. 5 can further reduce the number of component parts by making the two sun gears 11 and 12 integral and having the same number of teeth compared to the above embodiment. The only difference is that they are made as follows, and the rest are the same. It goes without saying that the ring gears 31 and 32 have different numbers of teeth so that different speed ratios can be obtained. Furthermore, FIGS. 6 and 7 show three sun gears 11°, 12.
13, two planetary gears 21, 22, 23 each and all supported by the carrier 4, and three ring gears 3.
1, 32, and 33, so that the lock pin 70 of the switching lever 7 can selectively engage the engagement grooves 35, 36, and 37 formed on the outer peripheral surfaces of the three ring gears 31, 32, and 33. This shows an embodiment in which three types of gear ratios can be switched. In this case, the arrangement of the two planet gears 21, 22, and 23 is, as is clear from diagram t57, the planet gears 21, 21, 22, 22, and the planet gears, which are all arranged at intervals of 180@. 23.
By shifting gears 23 by 60 degrees, all gears 21 and 2
2.23, the interval is 60'.

【Effect of the invention】

As described above, in the present invention, it is possible to obtain multiple speed ratios that are not 1:1, and in addition to each having two 11-star gears, a single carrier supports all the planetary gears. Because of this, it requires fewer components, and even though there are only two planetary gears each,
This is because all four or more planetary gears supported by a single carrier are lined up at equal intervals, and all the planetary gears revolve around the sun gear no matter which gear ratio is set. In addition to centering each member, it also prevents the shaft from collapsing (for this reason, it is possible to provide a device that can change the gear ratio at a low cost).

[Brief explanation of the drawing]

Figures 1 and 2 are longitudinal sectional views of an embodiment of the present invention, Pt5
3 is a sectional view taken along line A-A in FIG. 1, FIG. 4 is a longitudinal sectional view of another embodiment, FIG. 5 is a sectional view taken along line BB in FIG. 4, and FIG.
The figure is a vertical cross-sectional view of another embodiment, and FIG. 7 is C in FIG. 6.
8 is a schematic diagram showing the basic configuration of the planetary gear iso structure, 4 is a carrier, 7 is a switching lever equipped with a lock bin as a restraining means, 11.12 is a sun gear, 21 22 is a planetary gear, and 31.32 is a ring gear. Agent Patent Attorney Ishi 1) Chief 7 Figure 3 Figure 4 B Figure 5

Claims (3)

[Claims] (1) In a planetary transmission in which a plurality of planetary gear mechanisms are arranged in parallel in the axial direction, each sun gear is In addition to rotating at the same time, each planetary gear mechanism has two planetary gears spaced apart by 180 degrees, and the planetary gears in each planetary gear mechanism are supported by a single carrier so that all the planetary gears are arranged equally around the axis of the sun gear. A planetary transmission comprising restraining means arranged at intervals and selectively restraining the rotation of each rotatable ring gear. (2) The planetary transmission according to claim 1, wherein each sun gear is integrally formed and has the same number of teeth. (3) The planetary transmission according to claim 1, characterized in that the number of planetary gear mechanisms is three.