JPH06241284A - Transmission series with internal meshing planetary gear structure - Google Patents

Abstract

PURPOSE:To actualize those of being lighter in weight, compact in size and high steeliness as well as to make multifarious combinations easily obtainable at the time of promoting a series of reduction gears adopted with an internal meshing planetary gear structure. CONSTITUTION:A reduction gear mechanism part is supported inboard on a casing 112 via a pair of bearings 115a and 114b, while a range of up to these paired bearings 115a, 115b is set to a reduction gear part pack F and unitized as one body. In addition, this reduction gear part pack F is housed in an internal gear 110 and, in turn, this internal gear 110 is unified with the casing 112, and further a planetary gear structural part D or E, inclusive of an output shaft cover too, are unitized. Likewise, those of input side portions A1, A2, B and C are also unitized respectively, and at the same frame number, respective ones are made so as to be optionally combined together via a joint spline 200.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a series of transmissions adopting an internally meshing planetary gear structure.

[0002]

2. Description of the Related Art Conventionally, a first shaft, an external gear mounted via an eccentric body provided on the first shaft so as to be eccentrically rotatable with respect to the first shaft, and the external gear. There is widely known an internally meshing planetary gear structure including an internally toothed gear that internally meshes with a second shaft that is connected to the externally toothed gear via a means that transmits only the rotation component of the externally toothed gear. Has been.

A conventional example of this structure is shown in FIGS. In this conventional example, the first shaft is used as an input shaft and the second shaft is used as an output shaft, and the internal gear is fixed to apply the above structure to a "speed reducer".

An eccentric body 3 is fitted to the input shaft 1 via a key 30. An external gear 5 is attached to the eccentric body 3 via a bearing 4. A plurality of inner roller holes 6 are provided in the external gear 5, and an inner pin 7 and an inner roller 8 are fitted therein.

External teeth 9 having a trochoidal tooth profile, an arc tooth profile, or the like are provided on the outer periphery of the external gear 5. The external teeth 9 are internally meshed with the internal gear 10 fixed to the casing 12. Specifically, the internal teeth of the internal gear 10 have a structure in which the outer pin 11 is loosely fitted in the outer pin hole 13 so as to be easily rotated.

The inner pin 7 penetrating the external gear 5 is fixed to the flange portion 14 of the output shaft 2.

When the input shaft 1 makes one revolution, the eccentric body 3 makes one revolution. The external gear 5 also tries to oscillate around the input shaft 1 by one rotation of the eccentric body 3, but the internal gear 10
Since the rotation of the external gear 5 is restricted by the rotation of the external gear 5, the external gear 5 almost swings while inscribed in the internal gear 10.

Now, for example, when the number of teeth of the external gear 5 is N and the number of teeth of the internal gear 10 is N + 1, the difference in the number of teeth is 1. Therefore, the external gear 5 is displaced (rotated) by one tooth with respect to the internal gear 10 fixed to the casing 12 for each rotation of the input shaft 1. This is 1 of input shaft 1
It means that the rotation is reduced to -1 / N rotation of the external gear.

The rotation of the external gear 5 absorbs its swinging component by the gap between the inner roller hole 6 and the inner pin 7, and only the rotation component is transmitted to the output shaft 2 via the inner pin 7.

Here, the inner roller hole 6 and the inner pin 7
The (inner roller 8) forms a "constant speed internal gear mechanism".

As a result, a reduction ratio of -1 / N is eventually achieved.

In this conventional example, the internal gear of the internal mesh planetary gear structure is fixed and the first shaft is the input shaft and the second shaft is the output shaft, but the second shaft is fixed and the first shaft is the output shaft. The speed reducer can also be configured by using one shaft as the input shaft and the internal gear as the output shaft. Further, it is possible to construct a speed increaser by reversing these inputs and outputs.

Further, this conventional example has a structure in which the entire speed reducer is floor-mounted, but a structure in which a mounting flange 36 is provided on this floor mounting is also known as shown in FIG. 14, for example. Note that the substantially same portions are denoted by the same reference numerals.

By the way, as described above, the function of forming a circular arc tooth profile, which is one element of the constant velocity internal gear mechanism constituted by the inner roller hole 6, in the inner pin 7, and the function of the external gear 5 are as follows. Although it has a function as a carrier body that transmits the rotational force due to rotation to the output shaft 2, in particular, in order to ensure the good function of the former, it is possible to rotate freely around the inner pin 7. The presence of the inner roller 8 was essential. Since the inner roller 8 is required to be coaxially and accurately machined on both the outer circumference and the inner circumference with a functionally hard material, there is a problem that the cost tends to increase.

Therefore, the function of forming a circular arc tooth profile which is one element of the constant velocity internal gear mechanism of the inner pin 7,
A function that separates the function as a carrier body that transmits the rotational force due to the rotation of the external gear 5 to the output shaft 2 so that even if the inner roller 8 is eliminated, the same performance can be obtained with the inner roller 8. Has been proposed (Actual exploitation number 59-12795)
1).

This structure is shown in FIGS. Here again, the substantially same parts are designated by the same reference numerals.

In this structure, as means for transmitting the rotation component of the external gear, internal pin holes (corresponding to internal roller holes) 19a, 19b provided in the external gears 5a, 5b are arranged at a constant speed internal gear mechanism. And an annular support ring 17 that receives a rotation corresponding to the rotation component of the externally toothed gear of the inner pin 7.
And projected from the flange portion 14 formed on the output shaft 2,
Carrier body 16 connected and fixed to the support ring 17
Have and.

Two external gears (double row) are used.
This is mainly for the purpose of increasing transmission capacity, maintaining strength, and maintaining rotational balance. The eccentric directions of the external gears 5a and 5b are 180 ° out of phase with each other.

The inner pin 7 is rotatably fitted in the flange portion 14 and the support ring 17 via bushes 18a and 18b, respectively. That is, since the inner pin 7 does not need to be firmly connected to the output shaft 2 due to the existence of the carrier body 16, it can be configured to rotate itself, and as a result, the conventional inner roller 8 can be omitted. There is something. The annular support ring 17 is incorporated in the tip portion of the carrier body 16.

Since the carrier body 16 only has to have a function of transmitting the rotational force of the support ring 17 to the output shaft, the carrier pin 16 does not oscillate at the corresponding portions of the external gears 5a and 5b. A large through hole 20a that does not interfere with
20b is provided.

In FIG. 15, reference numerals 15a and 15b are used.
Is a bearing of the output shaft 2, 21 is an inner pin retainer plate for axially positioning the inner pin 7, 22 is a steel plate race ring, and 23 is an inner pin retainer bolt.

By the way, in the planetary gear structure of the internal meshing type as described above, the reduction ratio can be freely changed only by changing the external gears 5a, 5b, the internal gear 10, the outer pin 11, and the eccentric bodies 3a, 3b. Can be changed.

Therefore, the sub-series (this sub-series) is divided into several sizes from small to large in accordance with the market demand for the size of the mating machine, which is determined by the dimensions of the output shaft 2 and the casing 12. A series is hereinafter referred to as a “frame number”) is prepared in advance, and several types of gear ratios are pre-serialized and prepared in the same frame number, so that various users can be supported.

Specifically, in the publicly known one, the reduction ratio is 1/6 to 1/119, and the combination of motors is 0.1 kw to 13
2kw and output torque of 0.35kgm-6000kgm are prepared by multiple frame numbers.

[0025]

However, as is apparent from FIGS. 12, 14, and 15, in such a conventional speed reducer, load fluctuations occurring in the speed reduction mechanism portion and the output shaft 2 are reduced.
Since the external radial load acting on the external machine is supported by the pair of bearings 15a and 15b supporting the output shaft 2, in order to increase the stability of the support, generally, the Y section of each figure is long and It was necessary to make the X section as short as possible.

However, since it is difficult to shorten the X section, the Y section must be necessarily lengthened, resulting in a problem that the axial length of the speed reducer becomes long.

In the structure shown in FIGS. 15 and 16, the carrier body 16 is formed integrally with the output shaft 2, so that the manufacturing is extremely difficult and the cost is high, and the inner roller 8 is used.
There is also a problem that the cost reduction effect due to the omission of is omitted.

On the other hand, in the structure of FIG. 14 in which the speed reducer of FIG. 12 and FIG. 13 is flange-mounted, the above problem still exists and the casing 12 needs to have a long section Y, so that the other machine can be used. Installation flange 36
Since the distance Z between the internal gear and the flange 37 for mounting the internal gear is long, it has a double flange structure, which makes the mold complicated and difficult to manufacture when it is manufactured by, for example, aluminum die casting or aluminum casting, resulting in high cost. There was also a problem.

In each of the structures shown in FIGS. 12 and 13, an eccentric body 3, a bearing 4, an external gear 5, and an internal gear 10 are stacked on a motor including a casing 12 and an input shaft 1. Since it is a method of fixing with a bolt, the whole part must be disassembled in order to separate the motor part and the gear reducer part and replace the motor, resulting in the following problems.
That is, in recent years, in a field in which such a geared motor is used (for example, in the field of physical distribution systems), various performances are required for a motor to be adopted according to its application. For example, even if they have the same horsepower, a general mere induction motor, a motor with a brake, a motor that has an inverter control circuit and can control the rotation speed with a constant torque, and is completely waterproofed to improve safety. A wide variety of motors, including attached control circuits, have come to be used.

Therefore, it is very important to be able to assemble a geared motor with a motor in a short time at the time of assembly, and to replace a motor that is actually used in a physical distribution system in a short time. As described above, the fact that the whole must be disassembled when replacing the motor, as described above, is not enough to meet the demands of this era.

The present invention has been made in view of the above conventional problems. The inscribed intermeshing planetary gear structure portion is first unitized by a reduction gear pack, and further, the inscribed intermeshing planetary gear structure portion and the motor. It is an object of the present invention to solve the above problems by preparing a unit or a double shaft type input shaft unit for disassembly, assembly, and motor replacement.

[0032]

According to the present invention, there is provided a first shaft and an externally toothed gear which is eccentrically rotatable with respect to the first shaft via an eccentric body provided on the first shaft. A second internal gear to which the external gear internally meshes, and a second gear connected to the external gear via means for transmitting only the rotation component of the external gear
And an inner pin that can constitute a constant velocity internal gear mechanism with respect to an inner roller hole provided in the external gear, and an external gear rotation of the internal pin as a means for transmitting the rotation component. An intermeshing planetary gear structure having an annular support ring that receives rotation corresponding to the components and a carrier body that projects from a flange portion formed on the second shaft and is connected and fixed to the support ring is adopted. In the transmission series,
The annular support ring and the flange portion of the second shaft are arranged so as to sandwich the external gear, and both the support ring and the flange portion can be supported by the casing via a pair of bearings. A unit sandwiched between bearings is formed as a transmission unit pack, the transmission unit pack is housed in the internal gear, and the planetary gear structure unit is formed as a unit by integrating the internal gear with a casing,
Further, the above-mentioned problem is solved by unitizing the input side parts such as the motor part and the input shaft case part, and connecting them to the planetary gear structure part by a splice or the like.

Further, in the same frame number, the above-mentioned problem is solved by making the fitting dimensions of the planetary gear structure portion and the input side portion the same.

[0034]

In the present invention, basically, an intermeshing planetary gear structure is adopted instead of a so-called parallel shaft gear structure, on which a carrier body is arranged so as to pass through the external gear, and the external gear is The annular support ring and the flange portion of the second shaft are sandwiched, and both the support ring and the flange portion are supported by the casing via a pair of bearings. As a result, in addition to being small in size, it is possible to easily obtain a high gear ratio (generally used as a speed reducer).
The rigidity of the speed change mechanism, particularly the rigidity and stability in the radial direction can be significantly improved.

Further, since the planetary gear structure and the input side portion for the planetary gear structure such as the motor and the input shaft case are unitized and can be connected by a spline, the motor can be disassembled, assembled, Easy to replace.

Therefore, in the field where the geared motor is used (for example, in the field of physical distribution system), the degree of freedom in adopting various types of motors depending on the application is increased,
Further, it becomes possible to easily replace the motor of the geared motor currently used in the physical distribution system or the like.

[0037]

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

FIG. 1 is an overall block diagram of a series of speed reducers adopting an internal meshing planetary gear structure according to the present invention. FIGS. 2 to 8 are enlarged views of respective components, and FIG. 9 is FIG. IX
It is a IX line sectional view.

In the following description, the same or similar parts as those of the conventional example will be designated by the same last two digits.

In FIGS. 6 and 9, one end of a carrier pin (carrier body) 116, which is a member separate from the flange portion 114, is fitted (press-fitted) into the flange portion 114 of the output shaft 102. A support ring 117 is fitted (press-fitted) into the other end of the carrier pin 116, and the support ring 117 and the carrier pin 116 form a carrier.

The flange portion 114, the carrier pin 116,
The support ring 117 includes a pair of bearings 115a, 115a.
Both ends are supported by the casing 112 by b.

A pipe-shaped spacer 125 is fitted (press-fitted) into the carrier pin 116 at substantially the center thereof.
Therefore, even if there is some variation in the fitting depth of the carrier pin 116 into the support ring 117 or the flange portion 114, the distance between the support ring 117 and the flange portion 114 is always kept constant by the function of the spacer 125. Moreover, the same distance can be easily ensured in all the four carrier pins 116.

Carrier pin holes (through holes) 120 through which the carrier pins 116 pass are formed in the external gears 105a and 105b.
Are formed. The carrier pin hole 120 has a size such that the carrier pin 116 and the external gears 105a and 105b do not contact each other even if the external gears 105a and 105b swing.

The internal gear 110 is integrated with a casing 112, and the casing 112 further includes an output shaft cover 112.
integrated with a.

The speed reduction mechanism unit is unitized as a speed reduction unit pack F as will be described later, and is housed in the internal gear 110.

The inner pin 107 corresponds to the support ring 11
7 and the flange portion 114 are press-fitted. Therefore,
Free rotation is no longer possible. However, since the shape of the inner pin is a simple cylinder, it is possible to easily perform mirror finishing with a hard material (at low cost), and the pair of bearings 115a and 115b sandwiches the reduction gear mechanism to support both ends. Since such a structure is adopted, the rigidity of the whole can be greatly increased, the inner pin 107 can be supported in an extremely stable state, and further, since the inner pin 107 and the carrier pin 116 are separated, the output shaft, etc. Since the radial load that flows in from the carrier pin 116 is taken up by the carrier pin 116 and the inner pin 107 is not likely to receive a strong radial load, it can be supported in a more stable state. But there is no particular problem. However, the inner pin 107 may be loosely fitted instead of being press-fitted.

FIG. 1 shows a series structure in which each member of a direct motor type, a double shaft type, and a two-stage type is combined with a leg mounting type and a flange type planetary gear structure part within the same frame number. It shows that it has been systematized. As described above, FIGS. 2 to 8 show enlarged views of each part.

Here, the motor direct-coupling types A1 and A2 are for forming a so-called geared motor, and are for integrally connecting the motor and the planetary gear structure.

The double shaft type B is for connecting a drive source (motor or the like) to the input shaft 101 by a coupling or the like. This double shaft type is also called a reducer.

The two-stage type C is for combining a planetary gear structure in two stages to obtain a large reduction in speed.

These input side portions are connected to the input shaft 101 of the planetary gear structure via a splice 200. For this reason, in the same frame number, the fitting dimensions of the input side portion and the planetary gear structure portion are the same in this product group.

As the planetary gear structure, a leg mounting type D and a flange type E are prepared. The leg mounting type D is used when the leg flange portion 150 is mounted on the mating machine when it is mounted on the mating machine, and the details thereof have already been described. The flange shape E is used when the flange portion 152 formed in the direction perpendicular to the shaft is installed on the mating machine.

All the constituent parts A to E are unitized, and oil seal measures are taken so that they can be individually stocked and transported without trouble, and the joint dimensions with the joint spline 200 are made common. Has been done.

The speed reduction unit pack F is a unit in which only the speed reduction mechanism unit of the planetary gear structure is taken out, and is commonly used for the leg mounting type D and the flange type E. Since this portion is unitized, it is possible to extremely easily change the reduction ratio within the same frame number.

The example shown in FIG. 1 (FIGS. 2 to 8) shows one embodiment, and although not shown, for example, the motor direct connection types A1 and A2 may have the same horsepower. Including a general mere induction motor, a motor with a brake, a motor with an inverter control circuit that can control the rotation speed with a constant torque, a motor that is completely waterproof to improve safety, etc. Various motors are available. Similarly, other components B to E
There are also some variations available. For the reduction gear pack F, several variations having different reduction ratios are prepared.

As an example of the combination, leg mounting type D,
FIG. 10 shows a combination of the splice 200 and the motor direct connection type A1. Further, as an example of another combination, FIG. 11 shows a combination of a leg mounting type D, a two-stage type C, a joint spline 200, and a motor direct connection type A2.

Next, the operation of this embodiment will be described.

Referring again to FIGS. 6 and 9, the external gear 10
5 oscillates with the rotation of the input shaft 101, and the internal gear 1
The rotation of the input shaft 101 due to the meshing of the outer pin 111 corresponding to the inner teeth of 10 and the outer gear 105 is the decelerated rotation (rotation) of the outer gear 105, which is exactly the same as the conventional known example. is there.

In the rotation of the external gear 105, the swing component is absorbed by the gap between the inner pin hole (corresponding to the inner roller hole) 119 and the inner pin 107, and only the rotation component passes through the inner pin 107. It is transmitted to the flange 114 of the output shaft 102 and the support ring 117. The rotational force transmitted to the support ring 117 is transmitted to the output shaft 1 via the carrier pin 116.
02.

The external radial load acting on the output shaft 102 is supported by the bearing 115a and the bearing 115a via the carrier pin 116 and the support ring 117 by both ends, so that the external radial load does not affect the inner pin 107. .

As a result, the load on the inner pin 107 becomes extremely small, and the shape of the inner pin 107 can be made extremely simple, so that high-precision machining can be easily realized with a hard material, and even without an inner roller. A good "constant speed internal gear mechanism" can be constructed. Further, due to the presence of the carrier pin 116, this inner pin 107 can also be incorporated so that it can be loosely fitted, that is, it can rotate itself. In this case, a smoother "constant speed internal gear mechanism" can be obtained. realizable.

The planetary gear structure parts D and E and the input side parts A to C of the motor or the like can be easily assembled, disassembled and replaced by combining the respective units.

[0063]

As described above, according to the present invention, since the reduction gear mechanism portion is supported by the pair of bearings on both sides, the total length of the reduction gear portion can be shortened, and the reduction gear portion can be highly accurate and highly precise. Rigid assembly is possible.

Further, since the planetary gear structure and the input side of the motor and the like are unitized, it is possible to easily select the combination of the motors according to the application and the assembly time can be shortened. In addition, the work is simplified when the motor is replaced during use as a geared motor.

Further, since the speed reduction unit pack is unitized, it is easy to change the speed reduction ratio within the frame number.

[Brief description of drawings]

FIG. 1 is an overall configuration diagram of a speed reducer series that employs an internally meshing planetary gear structure according to an embodiment of the present invention.

FIG. 2 is a cross-sectional view showing an enlarged motor direct connection type A1 in the series configuration.

FIG. 3 is a sectional view showing a double shaft type B in an enlarged manner in the series configuration.

FIG. 4 is an enlarged cross-sectional view of the two-stage C in the series configuration.

FIG. 5 is an enlarged cross-sectional view of the motor direct connection type A2 in the series configuration.

FIG. 6 is an enlarged sectional view of a leg mounting type D in the series configuration.

FIG. 7 is a sectional view showing an enlarged flange type E in the series configuration.

FIG. 8 is an enlarged cross-sectional view of the reduction gear pack E in the series configuration.

9 is a sectional view taken along line IX-IX in FIG.

FIG. 10 is a sectional view showing an example of combination of series.

FIG. 11 is a sectional view showing another example of series combination.

FIG. 12 is a partially cutaway front view showing an example of a speed reducer (with a motor) adopting a conventional internally meshing planetary gear structure.

13 is a sectional view taken along line XII-XII in FIG.

FIG. 14 is a partially cutaway front view showing another example of a reduction gear (with a motor) that employs a conventional internally meshing planetary gear structure.

FIG. 15 is a cross-sectional view showing still another example in which a conventional internally meshing planetary gear structure is adopted.

16 is a sectional view taken along line XVI-XVI in FIG.

[Explanation of symbols]

 101 ... Input shaft 102 ... Output shaft 103a, 103b ... Eccentric body 105a, 105b ... External gear 107 ... Internal pin 110 ... Internal gear 112 ... Casing 114 ... Flange part 115a, 115b ... Bearing 116 ... Carrier pin 117 ... Support ring 200 ... Joint splines A1, A2 ... Motor direct connection type B ... Double shaft type C ... Two-stage type D ... Leg mounting type E ... Flange type F ... Reduction gear pack

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hideka Tanaka 6-1, Asahi-cho, Obu-shi, Aichi Sumitomo Heavy Industries, Ltd. Nagoya Works

Claims (2)

[Claims] 1. A first shaft, an external gear mounted eccentrically with respect to the first shaft via an eccentric body provided on the first shaft, and an internal gear internally contacting the external gear. An internal gear that meshes,
A second shaft connected to the external gear via a means for transmitting only the rotation component of the external gear, and the internal shaft provided on the external gear as means for transmitting the rotation component An inner pin that can form a constant-velocity internal gear mechanism with respect to the roller hole, an annular support ring that receives rotation corresponding to the rotation component of the external gear of the inner pin, and a flange that is formed on the second shaft. A series of transmissions employing an internally meshing planetary gear structure having a carrier body connected and fixed to the support ring, wherein the annular support ring and the flange portion of the second shaft are connected to the external gear. The support ring and the flange portion can both be supported by the casing through a pair of bearings, and the portion sandwiched between the pair of bearings is unitized as a transmission unit pack and The pack is housed in the internal gear, and the internal gear is integrated with the casing to unitize the planetary gear structure unit, and further, the input unit such as the motor unit and the input shaft case unit is unitized, A series of transmissions adopting an inscribed planetary gear structure, characterized in that it can be connected to the planetary gear structure section by a splice or the like. 2. The same frame number in claim 1,
A series of transmissions adopting an internally meshing planetary gear structure in which the engagement dimensions of the planetary gear structure portion and the input side portion are the same.