JPH11280854A - Transmission system of internal planetary gear structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To shorten the axial lengths of a driven part and a reduction part and enchance the degrees of freedom in the design of the driven part by providing an output bolt used also as an internal pin (carrier pin) in the reduction part, and screwing the output bolt into tap holes formed on a rotary member of the driven part through the external gears. SOLUTION: A transmission system comprises a driving part M, a reduction part R, and a driven part S, and a geared motor is used in the M1 driving part M having a motor shaft used as a high-speed shaft 301 of the reduction part R. The high-speed shaft 301 transmits the power to three external gears 305a-305c internally engaged with an internal gear 310 through the eccentric bodies 303a-303c. An output bolt 332 is built in the through holes 306 formed on these external gears 305a-305c through an internal roller 308, and on this occasion, a plurality of tap holes 338 are formed on a connection face Sa at a rotary member S1 side of the driven part S, so that the output bolt 332 is screwed into the tap holes 338 from a driving part M side.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an internally meshing planetary gear structure suitable for being applied to a speed reducer or a speed-increasing gear, in particular, a speed reducer or a speed-increasing device which is required to have a small size and a high output. It relates to a transmission system.

[0002]

2. Description of the Related Art Conventionally, an external gear which is mounted eccentrically rotatable with respect to a high-speed shaft via an eccentric body provided on the high-speed shaft, and an external gear inscribed therein. BACKGROUND ART An internally meshing planetary gear structure including an internal gear that meshes and a low-speed shaft that is connected to the external gear via means for transmitting only the rotation component of the external gear is widely known.

FIGS. 5 and 6 show a conventional example of this structure.
In this conventional example, the above structure is applied to a "reduction gear" by fixing the internal gear to the high speed shaft as the input shaft 1 and the low speed shaft as the output shaft 2.

The input shaft 1 has a predetermined phase difference (18 in this example).
0 °), the eccentric bodies 3a and 3b are fitted. The eccentric bodies 3a and 3b are integrated. Two external gears 5a, 5b are mounted on the respective eccentric bodies 3a, 3b via bearings 4a, 4b. This external gear 5
a, 5b are provided with a plurality of inner roller holes 6;
And the inner roller 8 is fitted.

The reason why the number of external gears is two (double row) is as follows.
This is mainly to increase transmission capacity, maintain strength, and maintain rotational balance.

[0006] On the outer periphery of the external gears 5a and 5b, external teeth 9 such as a trochoid tooth shape and an arc tooth shape are provided. The external teeth 9 are internally meshed with an internal gear 10 fixed to a 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 and held so as to be easily rotated.

The inner pin 7 penetrating the external gears 5a and 5b is fixed or fitted to the flange portion 14 of the output shaft 2.

When the input shaft 1 makes one rotation, the eccentric bodies 3a, 3b
Makes one revolution. By one rotation of the eccentric bodies 3a and 3b,
The external gears 5a and 5b also try to oscillate around the input shaft 1, but their rotation is restricted by the internal gear 10, so that the external gears 5a and 5b Mostly only swinging while touching.

For example, if the number of teeth of the external gears 5a and 5b 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, each time the input shaft 1 rotates, the external gears 5 a and 5 b are connected to the internal gear 1 fixed to the casing 12.
It is shifted (rotated) by one tooth with respect to 0.
This means that one rotation of the input shaft 1 has been reduced to -1 / N rotation of the external gear.

The rotation of the external gears 5a and 5b is absorbed 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. You.

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

In this conventional example, the internal gear having the internal meshing planetary gear structure is fixed, and the high-speed shaft is used as the input shaft and the low-speed shaft is used as the output shaft. It is also possible to configure a speed machine.

By the way, as described above, the inner pin 7 has a function of forming an arc tooth shape which is one element of the constant speed internal gear mechanism constituted by the inner roller holes 6a and 6b, The rotation force of the rotation of 5a and 5b is output shaft 2
There is a function as a carrier body for transmitting to the inner pin 7, but in particular, in order to properly secure the former function, the presence of an inner roller 8 that can freely rotate around the outer periphery of the inner pin 7 is essential. there were. The inner roller 8 has a problem that the cost is likely to be high because the inner roller 8 needs to be coaxially and precisely processed with a functionally hard material on both the outer periphery and the inner periphery thereof.

As is apparent from FIG. 5, a pair of bearings 1 for supporting the output shaft 2 is provided with a load variation generated in the speed reduction mechanism and an external radial load acting on the output shaft 2 from a partner machine.
Since the support is provided by 5a and 15b, in order to increase the stability of the support, it is generally necessary to make the Y section in FIG. 5 longer and the X section as short as possible.

However, since it is difficult to shorten the X section, the Y section must be necessarily lengthened, and as a result, there is a problem in that the axial length of the speed reducer increases.

In view of such a problem, Japanese Patent Laid-Open Publication No.
In Japanese Patent No. 44792, the applicant has proposed a configuration as shown in FIGS.

The structure shown in FIGS.

In view of such a problem, Japanese Patent Laid-Open No.
In Japanese Patent No. 44792, the applicant has proposed a configuration as shown in FIGS.

The structure shown in FIGS.

In the following description, those shown in FIGS. 3 and 4 are given the same numbers in the last two digits for parts that are the same as or similar to those in FIGS. 5 and 6, and detailed descriptions are omitted. Only the place will be described. The output shaft (low speed shaft)
102 is divided into a flange portion (first low-speed shaft) 114A and a support ring (second low-speed shaft) 114B.

That is, the carrier pin 116 is penetrated through the flange portion (first low-speed shaft) 114A of the output shaft 102, a retaining ring 124 is disposed at one end of the carrier pin 116, and a screw portion is provided at the other end. 127, and the flange 1
The first and second low-speed shafts are divided by strongly sandwiching the retaining ring 14A, the spacer 125, and the support ring (second low-speed shaft) 114B between the retaining ring 124 and a nut 128 screwed into the screw portion 127. Flange part 11
4A and the support ring 114B are integrated.

Flange 114A, carrier pin 11
6, and the support ring 114B include a pair of bearings 115a,
Both ends are supported by the casing 112 by 115b.

In the structure shown in FIGS. 3 and 5, power is transmitted by connecting the output shafts 2 and 102 to a (member) rotating member of a mating machine (second mating member).

In FIG. 7, M is a motor (first mating member), R is a reduction portion of an internally meshing planetary gear structure,
S indicates a driven part (a second partner member).

In the example shown in FIG. 7A, the motor M
Motor shaft (rotating member) M1, high-speed shaft R1 of the reduction unit R
For example, as shown in FIG. 3, a geared motor is combined from the beginning as a so-called geared motor, and a low-speed shaft R2 of a reduction unit R and an input shaft (rotating member) S1 of a driven unit S are connected by a general coupling C. Connected. Although this connection structure corresponds to the most common connection structure, the total axial length L of the driven portion S and the deceleration portion R is long, and the connection structure lacks compactness.

Therefore, as a method of shortening the connecting portion as much as possible, a method as shown in FIG. In this method, both the low-speed axis R2 of the reduction section R and the input axis S1 of the driven section S are formed in a plane, and the flange R3 of the low-speed axis R2 is formed.
Are connected to each other. As a result, the axial length L1 can be shortened by the amount of omitting the coupling C.

However, this connection method is effective when the diameter D1 of the rotating member S1 of the driven portion S is larger than the diameter D2 of the low-speed shaft R2 of the reduction portion R, but cannot be adopted when it is small. For this reason, conventionally, as shown in FIG. 7C, a bolt S2 (or S2 ') penetrating a part or all of the driven portion S is connected to the low-speed shaft R2 of the reduction portion R from the driven portion S side. The two are connected by screwing into the tapped hole T formed in the above.

[0028]

However, this method cannot be used when there is another member in the hatched portion H1 in FIG. 7C, and it cannot be used as shown in the lower part of FIG. 7C. When the thin flange S3 cannot be formed on the driven portion S side, various problems occur.

That is, since the driven portion S needs to be formed with a portion through which the bolt S2 penetrates, the degree of freedom in designing the driven portion S is significantly restricted. Bolt S of length appropriate for depth
2 and S2 'must be selected. Particularly, when the depth is long as shown in the lower side of the figure, the length of the bolt S2' is correspondingly long, and the fixing becomes unstable accordingly. There was a defect. In addition, when the special bolt S2 'is used, not only is the cost increased, but also, for example, when the bolt S2' is replaced, it takes time to order.

Further, when there is another member in the portion of H2 in addition to the hatched portion H1, there is another problem that the connection itself becomes impossible in the first place.

The present invention has been made in view of such a problem, and greatly improves the degree of freedom in designing a driven part, further reduces the number of parts and reduces cost, and reduces the number of parts. It is an object of the present invention to provide a transmission system having an internally meshing planetary gear structure capable of shortening the total axial length of the first and second mating members.

[0032]

According to a first aspect of the present invention, there is provided a high-speed shaft connected to a rotating member of a first mating member;
An external gear mounted eccentrically rotatable with respect to the high-speed shaft through an eccentric body provided on the high-speed shaft, an internal gear in which the external gear meshes internally, and the external gear, It is connected via means for transmitting only the rotation component of the external gear, and is connected to the rotating member of a second mating member disposed on the opposite side of the first mating member across the external gear. And a means for transmitting only the rotation component, wherein an inner pin connected to the low-speed shaft is loosely fitted into an inner pin hole formed in the external gear. In the transmission system of the meshing planetary gear structure, a structure in which the connection surfaces formed in a plane are closely attached to each other as a connection structure between the second mating member and the low-speed shaft,
A tap hole is formed in the connection surface on the second mating member side, and a bolt that can also function as the inner pin is inserted through the inner pin hole from the side where the first mating member exists, and the tap is formed. The above problem can be solved by connecting the low speed shaft and the second counterpart member by screwing into the hole.

According to a second aspect of the present invention, a high-speed shaft connected to the rotating member of the first mating member and an eccentric member provided on the high-speed shaft are provided so as to be capable of eccentric rotation with respect to the high-speed shaft. The attached external gear, an internal gear in which the external gear meshes internally, and the external gear are connected to the external gear via means for transmitting only the rotation component of the external gear, and A low-speed shaft connected to a rotating member of a second mating member disposed on the opposite side of the external gear with respect to the first mating member, and the low-speed shaft sandwiches the external gear. First,
An internally meshing planetary gear structure in which the divided first and second low-speed shafts are divided by a second low-speed shaft and connected by a carrier pin disposed through the external gear. In the speed change system, as a connection structure between the second mating member and the low-speed shaft, a structure in which connection surfaces formed in a plane are in close contact with each other is adopted, and a tapped hole is formed in the connection surface on the second mating member side. And by screwing a bolt that can also serve as the carrier pin from the side where the first counterpart member exists through the external gear and into the tap hole, the low-speed shaft and the second The above-mentioned problem is similarly solved by performing connection with the other member.

[0034]

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

FIG. 1 is a sectional view showing a transmission system according to the present invention. FIG. 2 is a side view as viewed from the left side in FIG.

First, a transmission system having an internally meshing planetary gear structure according to this embodiment will be described with reference to FIG.

The transmission system according to the present embodiment is composed of three parts: a driving section (first counterpart member) M, a speed reduction section R, and a driven section (second counterpart member) S. The high-speed shaft (rotating member) 301 of the reduction unit R and the motor shaft (rotating member) M1 of the driving unit M are designed as a so-called geared motor, for example, as shown in FIG.

Accordingly, here, the description will be made from the speed reduction unit R.

The high-speed shaft 301 integrally connected to the motor shaft M1 is provided with an eccentric body 303a, 3
Three external gears 305 eccentrically attached to the high-speed shaft 301 via the gears 03b and 303c.
a, 305b, 305c. The external gears 305a, 305b, and 305c (hereinafter collectively referred to simply as the external gear 305) are in internal mesh with the internal gear 310, respectively. The internal teeth of the internal gear 310 are constituted by external pins 311. Further, in order to transmit only the rotation component of the external gear 305 to the external gear 305 and to allow the output bolt 332 to penetrate, a conventional internal roller hole (an internal pin hole if there is no internal roller) is provided. A corresponding through hole 306 is provided. The inner roller 308 is incorporated in the through hole 306.

That is, although an inner pin is conventionally inserted into the inner roller hole (inner pin hole), in the present embodiment, the output bolt 332 is inserted into a space in which the inner pin has been inserted conventionally. Things. Therefore, this output bolt 3
Since 32 serves as an inner pin, the present embodiment does not particularly provide an inner pin as in the related art.

The low-speed shaft is, similarly to the type shown in FIG. 3, an output flange (first low-speed shaft) 314A and a support ring (second low-speed shaft).
(Low speed shaft) 314B, and are connected by a carrier bolt 316.

A pipe-shaped spacer 325 is fitted (press-fitted) almost at the center of the carrier bolt 316. The flange 314A and the support ring 314B are
It is in contact with the end of the spacer 325. In this way, the distance between the flange portion 314A and the support ring 314B is always kept constant by the function of the spacer 325 by employing a structure in which the speed reduction mechanism is supported by the pair of bearings 315a and 315b. The same distance is easily secured at all three carrier bolts 316.

The holes (or screw holes) 332a and 332b for the output bolt 332 are
Holes (or screw holes) 316a and 316b. By doing so, the number of processing steps can be reduced, and at the same time, the thickness of the output bolt 332 and the carrier bolt 316 can be made the same, so that there is an advantage that parts management becomes easy.

Here, in this embodiment, the connection surface Ra of the flange portion 314A of the reduction portion R on the driven portion S side and the connection surface Sa of the rotating member S1 of the driven portion S on the reduction portion R side are: A structure in which the two are formed in a plane and are closely connected to each other is adopted. Note that reference numeral 350 in the figure denotes an inlay portion.

The connecting surface Sa of the driven part S on the side of the rotating member S1
Are formed with a plurality of (in the illustrated example, nine: corresponding to the positions of the output bolts 332) tapped holes 338. 308 (inner pin hole) is penetrated and screwed. By this screwing, the rotating member S1 of the driven portion S and the flange portion 314A of the reduction portion R are connected.

Next, the operation of the present embodiment will be described.

The rotation of the high-speed shaft 301 connected to the motor shaft M 1 causes the external gear 305 to swing and rotate together with the eccentric body 303. The rotation of the high-speed shaft 301 is converted into the oscillating rotation of the external gear 305 through the engagement between the external pin 311 corresponding to the internal teeth of the internal gear 310 and the external gear 305, and the rotation of the oscillating rotation rotates. The component (decelerated rotation) is transmitted from the external gear 305 to the flange portion 314A via the output bolt 332 serving also as an internal pin. Also, output bolt 33
The power transmitted to the support ring 314B through the support ring 2 is also transmitted to the flange portion 314A through the carrier bolt 316. The power transmitted to the flange 314A is
The power is transmitted to the rotating member S1 of the driven portion S via the same output bolt 332 and the threaded portion of the tapped hole 338.

By doing so, it is no longer necessary to form a through hole for the bolt S2 in the driven portion S, which is conventionally required, and the design flexibility of the driven portion S can be greatly increased. it can.

The flange 314A and the rotating member S1
Is transmitted between the flange 314A and the rotating member S1.
Is expressed by (clamping force) x (friction coefficient) on both sides of
The diameter and the number of the output bolts 332 may be designed in consideration of the capacity to be transmitted.

In this embodiment, the output bolt 332
Is screwed into the tapped hole 338 of the rotating member S1. Instead, a tapped hole is formed in the rotating member S1 so that the carrier bolt 316 can be screwed as it is, and the carrier bolt 316 is inserted into the tapped hole. May be screwed together. In this case, the carrier bolt 316 also functions as a carrier pin (claim 2).

When the carrier bolt 316 is used for connection,
Since the carrier bolt 316 does not need to receive power from the external gear 305 (having no function of the inner pin), there is an advantage that the parallelism with the high-speed shaft 301 is not required as much as the inner pin. can get. That is, when the connection with the tapped hole of the driven portion S is performed, the parallelism with the high-speed shaft 301 may sometimes be slightly out of order. In some cases, the degree of adverse effects may be smaller than the connection.

Incidentally, both the output bolt 332 and the carrier bolt 316 may be screwed into a tap hole formed in the rotating member S1. In this case, the output bolt 332
Means the function of the inner pin, and the carrier bolt 316 also has the function of the carrier pin.
2).

Further, in this embodiment, the carrier bolt 3
Although the speed reducing portion R having a structure supported at both ends by the support member 16 is employed, the present invention is not particularly limited to this structure. For example, even a speed reducing portion having a cantilever structure as shown in FIG. It is sufficiently applicable if an output bolt serving also as the inner pin 7 is made to penetrate from the outside (the right side in FIG. 5) of the pin 12.

[0054]

As described above, according to the present invention,
By connecting using bolts that also function as inner pins (or carrier pins), the degree of freedom in designing the second mating member is greatly improved, and the number of parts is reduced and the cost is reduced. An excellent effect is obtained that the total of the axial lengths of the speed reduction portion and the second mating member can be shortened.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a transmission system having an internally meshing planetary gear structure according to the present invention.

FIG. 2 is a side view as viewed from the left side in FIG. 1;

FIG. 3 is a cross-sectional view according to a conventional embodiment.

FIG. 4 is a sectional view taken along the line IV-IV in FIG. 3;

FIG. 5 is a sectional view according to a conventional embodiment.

FIG. 6 is a sectional view taken along the line VI-VI of FIG. 5;

FIG. 7 is a schematic configuration diagram showing a conventional transmission system having an internally meshing planetary gear structure.

[Explanation of symbols]

 301 ... high-speed shaft 303 ... eccentric body 305 (305a, 305b, 305c) ... external gear 310 ... internal gear 311 ... external pin 314A ... flange portion 314B ... support ring 316 ... carrier bolt 317 ... support ring 338 ... tapped hole R … Deceleration part S… Driven part M… Drive part

Claims (2)

[Claims] A high-speed shaft connected to a rotating member of a first mating member; and an external gear mounted eccentrically rotatable with respect to the high-speed shaft via an eccentric body provided on the high-speed shaft. An internal gear in which the external gear is internally meshed; and a means connected to the external gear via means for transmitting only a rotation component of the external gear, and an external gear with respect to the first mating member. An internal pin formed on the external gear as means for transmitting only the rotation component, and a low-speed shaft connected to a rotating member of a second mating member disposed on the opposite side with the tooth gear interposed therebetween. In a transmission system having an internally meshing planetary gear structure adopting a configuration in which an inner pin connected to the low-speed shaft is loosely fitted in the hole, as a connection structure between the second mating member and the low-speed shaft,
Adopting a structure in which the connecting surfaces formed in a plane are in close contact with each other, a tap hole is formed in the connecting surface on the second mating member side, and the bolt capable of also functioning as the inner pin is used as the first pin. The internal meshing planetary gear structure, wherein the low-speed shaft and the second mating member are connected by penetrating the inner pin hole from the side where the mating member is present and screwing into the tap hole. Transmission system. 2. A high-speed shaft connected to a rotating member of a first mating member, and an external gear mounted eccentrically rotatable with respect to the high-speed shaft via an eccentric body provided on the high-speed shaft. An internal gear in which the external gear is internally meshed; and a means connected to the external gear via means for transmitting only a rotation component of the external gear, and an external gear with respect to the first mating member. A low-speed shaft connected to a rotating member of a second mating member disposed on the opposite side of the external gear between the first and second low-speed gears. The axis is divided and arranged, and the divided first,
In a transmission system having an internally meshing planetary gear structure in which a second low-speed shaft is connected by a carrier pin disposed so as to penetrate an external gear, as a connection structure between the second mating member and the low-speed shaft,
Adopting a structure in which the connecting surfaces formed in a plane are in close contact with each other, forming a tapped hole in the connecting surface on the second mating member side, The internal meshing planetary gear structure, wherein the low-speed shaft and the second mating member are connected by penetrating the external gear from the side where the mating member is present and screwing into the tap hole. Transmission system.