JPH084846A - Transmission to be used for series of geared motor - Google Patents

Abstract

PURPOSE:To achieve common use of planetary frames for holding a planetary gear when a geared motor to be combined with a transmission having a simple planetary gear structure is made into a series. CONSTITUTION:A plurality of holding holes 452 (1/3), 452 (1/4), 452 (1/5) for holding supporting pins for supporting respective planetary gears in relation to plural kinds of planetary gears having the potential of being selectively incorporated in order to realize a plurality of gear ratios 1/3, 1/4, 1/5 are formed on a pair of planetary frames (output shaft flange) and a carrier for holding the planetary gears.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission (a speed reducer or a speed increaser when the input / output system is reversed) used in a series of geared motors.

[0002]

2. Description of the Related Art Conventionally, a series of geared motors, which are composed of a plurality of geared motors each of which is formed by combining various motors and speed reducers and have a plurality of selectable gear ratios, have been widely provided on the market.

In this type of geared motor series, a plurality of gear ratios are prepared according to the size of several types, which are generally called "frame numbers," prepared in accordance with the counterpart machine. The user can select a geared motor having a torque (capacity), a size, or a rotation speed according to the purpose from the series of geared motors finely classified in this way.

Conventionally, a sun gear, a planetary gear externally meshed with the sun gear, and a sun gear are used as a structure of a deceleration portion (gearup portion when used as a gearbox, the same applies hereinafter) of a transmission of a geared motor of this type. A transmission that employs a so-called simple planetary gear structure including a planetary frame that holds a planetary gear and an internal gear that internally meshes with the planetary gear has been widely put into practical use.

FIG. 7 shows an example thereof.

The speed reducer incorporates first and second speed reducers A and B, each of which has a simple planetary gear structure.

Both the first and second speed reducers A and B have a sun gear 602, which has a float structure in order to realize an equal load distribution.
702, planetary gears 604, 704 that externally mesh with the sun gears 602, 702, and internal gears 606, 706 that internally mesh with the planetary gears 604, 704. The planetary gears 604 and 704 are held by planetary frames (disks or output shaft flanges) 608 and 708.

The operation of the speed reducer will be briefly described while also explaining the other structure of the speed reducer.

When the input shaft 610 rotates, the coupling 6
The sun gear 602 rotates via 11. Sun gear 60
When 2 rotates, the planetary gear 604 is inscribed in the internal gear 606 fixed to the casing 612, and the sun gear 60
Revolve around the outer circumference of 2.

The planetary gear 604 is supported by a support pin 614 via a bearing 616.
Revolution of the sun gear 602 is a disk (planetary frame) 6
08 is transmitted. When the disc 608 rotates, the sun gear 70 of the second reduction gear B connected to the disc 608 is rotated.
2 rotates. When the sun gear 702 rotates, the planetary gear 7
04 orbits the outer periphery of the sun gear 702 while inscribed in the internal gear 706 fixed to the casing 612.

The planet gear 704 has a support pin 714 and a bearing 7
16 is supported via the output shaft flange (planetary frame) 7 to revolve the support pin 714 with respect to the sun gear 702.
08 is transmitted. The output shaft flange 708 is the output shaft 62.
0 is splined to the output shaft flange 708.
The rotation of the output shaft 620 rotates.

[0012]

In the series of geared motors as described above, the respective parts of the geared motor that should be conventionally prepared in the series are shared as much as possible,
It is important to reduce the types of parts in the entire series in order to reduce management costs and processing costs.

However, there is a problem that the planetary frame for holding the planetary gear must be manufactured for each different gear ratio.

This is because it is necessary to change the number of teeth (diameter) of the planetary gear to be held in the planetary frame in order to change the gear ratio, and therefore the holding hole for the support pin of the planetary gear formed in the planetary frame. This is because the distance from the axis center of is different for each gear ratio. Therefore, there is a problem in that it is necessary to manufacture planetary frames having different positions for forming the holding holes for each gear ratio.

Further, in general, the planetary frame is often manufactured integrally with the output shaft, so that it is necessary to stock various types of planetary frames including the output shaft, which is a considerable weight of the transmission parts. Also, it was not preferable.

In order to avoid this, as shown in FIG. 7, the planetary frame (output shaft flange 708) and the output shaft 620 are arranged.
It is possible to adopt a method in which the output shaft 620 is separated from the output shaft 620 and the output shaft 620 is shared.
As for itself, it is still necessary to prepare parts different in the number of gear ratios, and the output shaft flange 708 and the output shaft 6
Since 20 is a separate part, the number of assembling steps is increased and the number of parts cannot be reduced so much.

The present invention has been made in view of such a conventional problem, and provides a planetary frame that can be commonly used for geared motors having different gear ratios, thereby significantly reducing the number of parts. An object of the present invention is to provide a transmission used in a series of geared motors in which the planetary frame and the output shaft can be integrated without causing any problems.

[0018]

SUMMARY OF THE INVENTION The present invention comprises a plurality of geared motors which are a combination of various motors and transmissions, and makes it possible to select a plurality of gear ratios under the condition that the mating dimensions for the counterpart machine are the same. The transmission used in a series of geared motors, comprising a sun gear, a planetary gear externally meshed with the sun gear, a planetary frame holding the planetary gear, and an internal gear internally meshed with the planetary gear. A transmission used in a series of geared motors, which includes a simple planetary gear transmission unit, corresponding to a plurality of types of planetary gears that may be selectively incorporated in the planetary frame to achieve the plurality of gear ratios. Then, by forming a plurality of holding holes for holding the support pins that support the respective planetary gears, the above problem is solved.

[0019]

In the present invention, the planetary frame for holding the planetary gear is not formed with the holding hole (for the support pin) for holding the planetary gear corresponding to only one gear ratio as in the conventional case. Corresponding to a plurality of types of planetary gears that may be selectively incorporated to achieve a plurality of gear ratios, a plurality of holding holes for holding the support pins supporting each planetary gear are formed. .

As a result, the planetary gears having different speed ratios can be commonly attached to the same planetary frame (only by selecting the corresponding support pin holding hole).

Since the number of parts of the planetary frame itself can be reduced,
It is now possible to produce this and the output shaft in one piece without any problems, and it is possible to further reduce the number of parts.

In view of the fact that the planetary frame can be shared, the present invention arranges a pair of planetary frames on both sides in the axial direction of the planetary gear, and holds the supporting pins of the planetary gear on both sides, as in an embodiment described later. It is possible to realize a structure in which the pair of planetary frames are independently supported and rotatably supported by the casing without increasing the number of parts.

Since this structure holds the planetary gears together with the planetary frame directly supported by the casing,
Since the planetary gear can be assembled with extremely high precision, as described in the embodiment, excellent durability is ensured, and the bearing between the support pin and the planetary gear, which was conventionally required, is omitted. The additional effect of being able to do this is also obtained.

When a pair of planetary frames is provided as described above, it is desirable that the pair of planetary frames are fixed and connected to each other so that the support pins of the planetary gears are not relatively rotatable so that no force is applied in the tangential direction. , In this case, it is very easy to connect the two by using the holding pin which is not used in the gear ratio among the plurality of supporting pin holding holes provided and penetrating the carrier pin there. Can be connected.

That is, a part of the plurality of support pin holding holes opened can be used as a through hole for connecting the pair of planetary frames.

[0026]

Embodiments of the present invention will now be described in detail with reference to the drawings.

FIG. 1 is a partially cutaway front view of a speed reducer to which the present invention is applied, and FIG. 2 is a sectional view taken along the line II--II of FIG.

The speed reducer is used as a speed reducer for a so-called geared motor by being connected to a motor.

This speed reducer has a simple planetary gear structure including a sun gear 402, a planetary gear 404 externally meshed with the sun gear 402, and an internal gear 406 internally meshed with the planetary gear 404. It is used as the structure of part C.

The sun gear 402 is spline-coupled to the input shaft 410, and does not particularly adopt a float structure for realizing equal load distribution. The input shaft 410 is
It is connected to the motor shaft 430 via a coupling 411.

The planetary gear 404 is externally meshed with the sun gear 402 and internally meshed with the internal gear 406.

The planetary gear 404 is slidably supported by a support pin 414. Support pin 414
Is supported by a pair of planetary frames so as to be slidably rotatable. Specifically, in this embodiment, the carrier 408A arranged on the input shaft side (right side in FIG. 1) and the output shaft flange 408B integrally formed with the output shaft 420 form a pair of planetary frames. Support pin holding holes 450, 452 are formed in the carrier 408A and the output shaft flange 408B, and the support pin 414 has the support pin holding hole 450,
Both ends are supported by 452 so as to freely slide and rotate.

Both planetary frames, that is, the carrier 408A and the output shaft flange 408B are independently provided to the casing 412 via bearings 416A and 416B (the sun gear 4).
It is rotatably supported (coaxial with 02).

The bearings 416A and 416B also function as stoppers for preventing the support pin 414 from coming off in the axial direction.

The internal gear 406 is fixed to the casing 412, and the input shaft 410 is the pair of planetary frames, that is, the carrier 408A and the output shaft flange 408B.
Are supported via ball bearings 436A and 436B.

The carrier 408A and the output shaft flange 408B (a pair of planetary frames) are firmly fixed and connected by a carrier pin 440 (a member different from the support pin 414). Specifically, a snap ring 442 is fitted on one end side of the carrier pin 440.
A female screw 440A is formed on the other end of the carrier pin 440. Further, carrier pin holes 441A and 441B are formed in the carrier 408A and the output shaft flange 408B. The carrier pin 440 is the spacer 44.
4 with the carrier pin holes 441A, 4
41B is penetrated. Then, the carrier 408A and the output shaft flange 408B are connected by screwing and tightening the nut 446 to the female screw of the carrier pin 440.

Carrier 4 by this carrier pin 440
Although the connection of 08A and the output shaft flange 408B is not always essential, the presence of the carrier pin 440 causes both planetary frames to rotate integrally at the same speed without fail, so that the support pin 414 is biased in the orbit tangential direction. The load can be effectively prevented from occurring, and the support pin 414
Will always be able to support you well.

Here, the reduction ratios 1/3 and 1 / are shown in FIGS.
Planetary gears 404 (1/3), 404 (1/4), 404 required to realize three or four gear ratios of 4 and 1/5
(1/5) support pin holding holes 452 (1/3), 452
(1/4), 452 (1/5), sun gear 402 (1 /
3), 402 (1/4), 402 (1/5), and the positional relationship (on the output shaft flange 408B side) of the carrier pin 440 are shown.

Further, FIG. 3 shows these support pin holding holes 45.
2 shows a state in which 2 is formed without interference. As is clear from FIG. 3, each support pin holding hole 452 has a corresponding planetary gear 4 when the planetary gear 404 corresponding to each hole is assembled.
04 and the carrier pin hole 441B of the carrier pin 440 are formed at positions where they do not interfere with each other.

A completely similar support pin holding hole 452 is also formed on the carrier 408A side.

Next, the operation of this speed reducer will be described.

When the motor shaft 430 rotates, the input shaft 410 rotates via the coupling 411, and the sun gear 402, which is splined with the input shaft 410, rotates at the same speed. When the sun gear 402 rotates, the planetary gear 404 revolves along the outer circumference of the sun gear 402 while inscribed in the internal gear 406 fixed to the casing 412.

This revolution is carried out by a pair of planetary frames, that is, the carrier 408A and the output shaft flange 4 via the support pin 414.
It is transmitted to 08B. The revolution power transmitted to the output shaft flange 420 side is direct, and the revolution power transmitted to the carrier 408A side is the carrier pin 440 and the output shaft flange 4
It is transmitted to the output shaft 420 via 08B.

At this time, since both the carrier 408A and the output shaft flange 408B are independently supported by the casing via the ball bearings 416A and 416B, the assembling and rotation accuracy of the support pin 414 should be kept extremely high. You can Further, it is possible to secure a high rigidity of the reduction gear as a whole even against a load in the radial direction from the output shaft 420 side, so that the input shaft 410 and other members can be accurately supported. Therefore, it is not necessary to float the sun gear 402, and noise can be reduced accordingly.

Further, since the carrier 408A and the output shaft flange 408B are firmly fixed and connected through the carrier pin 440, they both rotate at the same speed without fail, and the support pin 414 is rotated correspondingly in the tangential direction of the revolution orbit. Unbalanced load is prevented.

Further, the support pin 414 is slidably rotatable with respect to the planetary gear 404, and is also slidably rotatable (not fixed) with respect to the carrier 408A and the output shaft flange 408B. The relative sliding speed between the pin 414 and the planetary gear 404 is reduced. Therefore,
Coupled with the high mounting accuracy of the support pin 414 itself (without the bearing), the planetary gear 404 can be smoothly rotatably supported for a long period of time. Therefore, the bearing noise is eliminated and the noise can be further reduced, and the number of parts can be reduced accordingly.

Here, for example, when the present reduction gear is assembled as a reduction gear having a reduction ratio of 1/3, a smaller planetary gear 404 (1/3) is held by a support pin as shown in FIGS. 3 and 4. It can be realized by assembling using the hole 452 (1/3). When manufacturing a reduction gear with a reduction ratio of 1/4, as shown in FIGS. 3 and 5, the planetary gear 404 (1/3) slightly larger than the planetary gear 404 (1/3) described above.
/ 4) is assembled using the support pin holding hole 452 (1/4). Further, in order to obtain a speed reducer having a reduction ratio of 1/5, a larger planetary gear 404 (1/5) is assembled using the support pin holding hole 452 (1/5).

In any case, the same output shaft flange 408B can be used, and in any case, the planet gear 404 and the carrier pin 440 do not interfere with each other.
Note that exactly the same action can be obtained on the side of the carrier 408A.

By the way, in this embodiment, the carrier pin hole for penetrating the carrier pin for connecting the pair of planetary frames is formed separately from the support pin holding hole. Since a large number of support pin holding holes are formed for a plurality of gear ratios, a part of the support pin holding holes that are not used at the gear ratio is inserted through the carrier pin when the pair of planetary frames are coupled. It can also be used as a carrier pin hole. In the example of FIG. 3, for example, when using the support pin holding hole 452 (1/3) to obtain the reduction ratio 1/3,
The support pin holding hole 452 (1/4) can be used as a carrier pin hole without any trouble.

In this case, the problem of interference with the planetary gears can be solved more easily than when a dedicated (fixed) carrier pin hole is provided, so that a support pin holding hole corresponding to a larger gear ratio can be provided. It can also be formed. When (a large number) support pin holding holes corresponding to many kinds of gear ratios are formed, there are many holding holes that do not interfere with the support pin holding holes for the planetary gears corresponding to the gear ratio. If this support pin holding hole that does not interfere is used as a hole for a plurality of carrier pins, there is no particular problem in terms of strength.

[0051]

As described above, according to the present invention,
The planetary frame, which was conventionally required to be manufactured for each gear ratio, can now be used in common for multiple gear ratios, resulting in excellent effects such as a reduction in the number of parts and management costs. Will be obtained.

[Brief description of drawings]

FIG. 1 is a partially cutaway front view of a transmission portion of a geared motor to which the present invention is applied.

FIG. 2 is a sectional view taken along the line II-II in FIG.

FIG. 3 is a front view showing the positional relationship of support pin holding holes and carrier pin holes formed in the output shaft flange.

FIG. 4 is a front view showing a meshing state of each element when a reduction ratio of 1/3 is realized.

FIG. 5 is a front view showing a meshing state of each element when a reduction ratio of 1/4 is realized.

FIG. 6 is a front view showing a meshing state of each element when a reduction ratio of 1/5 is realized.

FIG. 7 is a front view corresponding to FIG. 1 of a transmission used for a geared motor that employs a conventional simple planetary gear structure.

[Explanation of symbols]

 C ... Reduction gear 402 ... Sun gear 404 ... Planetary gear 406 ... Internal gear 408A ... Carrier (planetary frame) 408B ... Output shaft flange (planetary frame) 410 ... Input shaft 411 ... Coupling 412 ... Casing 414 ... Support pin 420 ... Output shaft 430 ... Motor shaft 416A, 416B, 436A, 436B ... Ball bearing 440 ... Carrier pin 441 ... Carrier pin hole 444 ... Spacer 450, 452 ... Support pin holding hole

Claims (4)

[Claims] 1. A gear shift motor comprising a plurality of geared motors, each of which is formed by combining various motors and a transmission, wherein a plurality of gear ratios can be selected under the condition that the fitting dimensions for the counterpart machine are the same. A planetary gear for externally meshing with the sun gear, a planetary frame for holding the planetary gear, and a simple planetary gear shifting unit having an internal gear for internally meshing with the planetary gear. In a transmission used in a series of geared motors, the planetary frame is provided with respective planetary gears corresponding to a plurality of types of planetary gears that may be selectively incorporated to achieve the plurality of gear ratios. A transmission used in a series of geared motors, characterized in that a plurality of holding holes for holding supporting pins to be supported are formed. 2. The pair of planetary frames according to claim 1, wherein the planetary frames are arranged in pairs on both sides in the axial direction of the planetary gear,
A transmission used in a series of geared motors, in which the support pins of the planetary gears are supported on both sides and the pair of planetary frames are independently rotatably supported in a casing. 3. The transmission used in a series of geared motors according to claim 2, wherein the pair of planetary frames are fixed and connected to each other by a member different from the support pin. 4. The holding hole according to claim 3, wherein a plurality of means for fixing and connecting the pair of planetary frames to each other are provided in each planetary frame.
A transmission used in a series of geared motors in which a carrier pin is passed through a holding hole that is not used at the gear ratio.