JP3406211B2 - Inner roller and outer roller of internal meshing planetary gear structure and method of manufacturing the same - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an inner roller or an outer roller having an internally meshing planetary gear structure, and a manufacturing method thereof.

[0002]

2. Description of the Related Art Conventionally, a first shaft, an eccentric body that rotates by rotation of the first shaft, and an external gear that is eccentrically rotatable with respect to the first shaft via the eccentric body. An internal meshing planetary having an internal gear with which the external gear internally meshes, and a second shaft connected to the external gear via means for transmitting only the rotation component of the external gear. Gear structures are widely known.

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".

A predetermined phase difference (18 in this example) is applied to the input shaft 1.
The eccentric bodies 3a and 3b are fitted at 0 °. The eccentric bodies 3a and 3b are integrated. Two external gears 5a and 5b are attached to the eccentric bodies 3a and 3b via bearings 4a and 4b. This external gear 5
a, 5b are provided with a plurality of inner roller holes 6, and the inner pin 7
And the inner roller 8 is inserted.

The inner pin 7 is covered with the inner roller 8 in order to disperse the slip during operation (the inner pin 7 and the external gear 5).
This is because the slips of a and 5b are dispersed into the slip of the inner pin 7 and the inner roller 8 and the slip of the inner roller 8 and the external gears 5a and 5b.

The inner pin 7 and the inner roller 8 penetrating the external gears 5a, 5b are fixed or fitted to the flange portion of the output shaft 2.

Two external gears (double row) are used.
This is mainly for the purpose of increasing transmission capacity, maintaining strength, and maintaining rotational balance.

External teeth 9 having a trochoidal tooth profile, an arc tooth profile, or the like are provided on the outer circumferences of the external gears 5a and 5b. The external teeth 9 are internally meshed with the internal gear 10 fixed to the casing 12.

The internal teeth of the internal gear 10 are specifically the external pin 1
It is composed of 1. The outer pin 11 has an outer pin hole 13
It is loosely fitted in and is held for easy rotation. Note that, as shown in FIG. 8 , for example, the outer pin 11 is sometimes covered with the outer roller 14. As a result, the slip during operation is dispersed (as compared with the case where the outer pin 11 and the outer pin hole 13 are slid in FIG. 6, the outer pin 11A and the outer roller 1 are slid as shown in FIG. 8) .
4 and the outer pin 11A and the outer pin hole 13 can be dispersed).

The operation of this speed reducer will be briefly described. When the input shaft 1 makes one revolution, the eccentric bodies 3a and 3b make one revolution. When the eccentric bodies 3a and 3b rotate once, the external gears 5a and 5b also try to swing and rotate around the input shaft 1. However, since the rotation of the internal gear 10 is restricted by the internal gear 10, the external gears 5 a and 5 b almost swing only while inscribed in the internal gear 10.

If, for example, 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, the external gears 5 a and 5 b are fixed to the casing 12 every time the input shaft 1 rotates once.
It is shifted (rotated) by one tooth with respect to 0.
This means that the rotation of the input shaft 1 is reduced to -1 / N of the external gear. The minus sign means reverse rotation.

In the rotation of the external gears 5a and 5b, the swing component is absorbed by the gap between the inner roller hole 6 and the inner roller 8, and only the rotation component is output through the inner pin 7 in the inner roller 8 to the output shaft. It is transmitted to 2. As a result, the reduction ratio-N
Slowdown is achieved.

Therefore, by combining the speed reducer of the intermeshing planetary gear structure with, for example, a motor, it is possible to obtain a geared motor having a large reduction ratio with only one speed reduction mechanism.

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, in this prior art example, the eccentric body was directly incorporated in the outer periphery of the first shaft, but the first shaft is connected to the "3" through the spur gear.
There is also known a type in which an eccentric body is incorporated into each of the first shafts of a book, and an eccentric body is incorporated in each of the dispersed first shafts, and an external gear is oscillated and rotated through the eccentric body. The present invention can be applied without any problem even to such a type of internally meshing planetary gear structure.

[0016]

By the way, as exaggeratedly shown in FIG. 9 , a gap δ1 is provided between the outer circumference of the inner pin 7 and the inner circumference of the inner roller 8. Further, as exaggeratedly shown in FIG. 10 , a gap δ2 is provided between the outer circumference of the outer pin 11A and the inner circumference of the outer roller 14. This gap δ1,
δ2 is for ensuring a lubricating oil film between the two members and for allowing the members in contact with each other to smoothly slide.

However, when such gaps δ1 and δ2 are provided, the inner pin 7 and the inner roller 8 or the outer pin 11A is formed.
There is a problem that rattling occurs between the outer roller 14 and the outer roller 14, and eventually rattling occurs in the entire gear transmission mechanism. Therefore, there is a drawback that the rotation on the driving side does not immediately appear as the rotation on the driven side when the rotation on one side shifts to the rotation on the other side. Hereinafter, such a delay in response will be referred to as “angle backlash”.

This angular backlash reduces the degree of control when the intermeshing planetary gear structure is used as a control mechanism such as a servomotor. There are various possible causes for the occurrence of angular backlash in the internally meshing planetary gear structure. As a device for eliminating such angular backlash, conventionally, for example, an external gear, an internal gear and the like are used for forward rotation and reverse rotation. Various structures are known such as division, or division of roles for forward rotation and reverse rotation (JP-A-59-106744, JP-A-59-113340, etc. ).

Further, the applicant of the present invention has proposed a method for minimizing the gap between the outer pin and the outer pin hole (in an internally meshing planetary gear structure of a type having no outer roller), as disclosed in Japanese Patent Application No. 60-86571. He also proposes Japanese Patent Publication No. 5-86506).

However, in any of the above-mentioned known examples, what has hitherto been focused on the gap δ1 between the inner pin and the inner roller and the gap δ2 between the outer pin and the outer roller in order to reduce the angular backlash. The actual situation is that no measures have been taken for the angle backlash that occurs here.

The reason for this is that it is necessary to always secure a predetermined lubricating oil between the inner pin and the inner roller, or between the outer pin and the outer roller; even if there is a processing error, an assembly error, or each member during power transmission. Even if a state occurs in which the axial center of the inner pin and the inner roller or the outer pin and the outer roller deviates due to the deformation of the two members, it is necessary to smoothly slide the two members; therefore, the clearances δ1, δ2 This is because it was considered that the configuration cannot be eliminated (essential configuration).

As a method of ensuring good sliding between the two sliding members without providing a gap, it is conceivable to use a material having a low friction and good compatibility such as white metal or fluororesin. However, the inner roller and the outer roller of the intermeshing planetary gear structure generally have a large torque that is amplified from several times to 100 times or more the torque of the input shaft, and therefore have high hardness and high strength from the viewpoint of durability. Material (eg high carbon chrome bearing steel steel (JIS G4
805 SUJ2 or equivalent)
Alloy steel for machine structure (JIS G4103, JIS G4
104, JISG4105) is carburized and quenched,
A material having a surface hardness of about HRC58-64 must be used, and this method cannot be adopted in many cases.

A structure may be considered in which a circumferential groove is provided on the inner circumference of the inner roller (or the outer circumference of the inner pin) and oil is secured in this circumferential groove, but this method only leads to an increase in the processing cost of the inner roller. In addition, since a sharp notch that causes stress concentration in the high hardness and high strength material is provided, the strength is remarkably reduced, which is not preferable as the configuration of the inner roller and the outer roller of this type of intermeshing planetary gear structure.

Further, in connection with this, since it is necessary to process a material having high hardness and high strength with high precision, the inner and outer diameters of the inner roller and the outer roller must be machined by "grinding", and particularly, When the inner diameter is processed by grinding, there is a limit (economically 2-3 μ) in the finish roughness (since grinding is the processing of shearing the crystal grains of the material), and the oil film is maintained at this roughness. In order to have a certain size gap δ
There was also a circumstance that the existence of 1 and δ2 was essential.

For this reason, however, the gap δ1 between the inner pin and the inner roller or the gap δ2 between the outer pin and the outer roller is considered to be indispensable, and therefore the occurrence of angular backlash due to this is unavoidable. It was thought that it was.

The present invention has been made in view of the above-mentioned problems of the prior art, and it is conventionally (naturally) necessary to perform processing as close to a true cylinder as possible. We have reviewed the shape of the roller by changing the way of thinking, and provide an inner roller or an outer roller with an intermeshing planetary gear structure that can reduce angular backlash to a greater extent than before without causing any new inconvenience. To aim.

Another object of the present invention is to provide an optimum method for actually manufacturing the inner roller or the outer roller.

[0028]

According to a first aspect of the present invention, there is provided a first shaft, an eccentric body which rotates by rotation of the first shaft, and an eccentric rotation with respect to the first shaft via the eccentric body. An external gear incorporated in a possible state, an internal gear with which the external gear meshes internally, and a first gear connected to the external gear via means for transmitting only the rotation component of the external gear. A cylindrical inner roller used with a cylindrical inner pin to form a means for transmitting only the rotation component of an internally meshing planetary gear structure including two shafts, the first shaft and the An eccentric body that rotates by the rotation of one shaft, an external gear that is eccentrically rotatable with respect to the first shaft via the eccentric body, and an internal gear that the internal gear meshes with. A second shaft connected to the external gear via a means for transmitting only the rotation component of the external gear. In a cylindrical inner roller used together with a cylindrical inner pin to form means for transmitting only the rotation component of the internally meshing planetary gear structure, a longitudinal section of the inner peripheral wall of the cylinder is The above-mentioned problem is solved by forming the inner diameter of the central portion in the axial direction of the barrel into a barrel shape having a larger diameter than the inner diameters of both end portions.

According to a second aspect of the present invention, the first shaft, the eccentric body that rotates by the rotation of the first shaft, and the eccentric body are incorporated into the eccentric body so as to be eccentrically rotatable with respect to the first shaft. An external gear, an internal gear with which the external gear meshes internally, and a second shaft connected to the external gear via means for transmitting only the rotation component of the external gear. In a method for manufacturing a cylindrical inner roller used with a cylindrical inner pin to form a means for transmitting only the rotation component of the internally meshing planetary gear structure, a first shaft and a first shaft An eccentric body that rotates by rotation, an externally toothed gear that is eccentrically rotatable with respect to the first shaft via the eccentric body, an internal gear that internally meshes with the externally toothed gear, and the external A second gear connected to the gear via a means for transmitting only the rotation component of the external gear
An inner mesh planetary gear structure having a shaft, and a method of manufacturing a cylindrical inner roller used together with a cylindrical inner pin to form a means for transmitting only the rotation component,
A procedure for forming a cylindrical inner roller material by hollowing and cutting the central portion of the cylindrical inner roller material in the axial direction, a procedure for burnishing the inner peripheral wall of the cylindrical inner roller material, and the burnishing processing. A barrel-shaped forming procedure for deforming the entire inner roller material into a barrel shape in which the central portion in the axial direction is swollen by heat-treating the inner roller material, and grinding the outer peripheral wall of the barrel-shaped inner roller material. However, the above problem is solved by including a procedure of forming only the outer peripheral wall into a perfect cylindrical shape.

According to a third aspect of the present invention, in the second aspect, the processing strain is more positively applied during the burnishing process so that the residual strain before the heat treatment due to the working and the residual strain due to the heat treatment causes the cylindrical shape The above problem is solved by forming the vertical cross-sectional shape of the peripheral wall into a clearer barrel shape.

Claims 1, 2 and 3 are focused on the inner roller of the intermeshing planetary gear structure, and exactly the same construction is applied to the outer roller as claimed in claims 4, 5 and 6.

[0032]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to the drawings.

The present invention is characterized by the shape of the inner roller or the outer roller of the intermeshing planetary gear structure, particularly the inner peripheral vertical cross section. There is no change. Therefore, the structure of the intermeshing planetary gear structure itself has already been described in detail, and the description thereof will be omitted.

The longitudinal section of the inner roller or the outer roller according to the present invention is not such that the inner peripheral wall is straight as in the conventional case, and the inner diameter of the inner peripheral wall in the axial center is larger than the inner diameter of both ends. When the inner pin or the outer pin is inserted, the lubricating oil such as oil or grease can be retained therein.

FIG. 1 is a vertical sectional view of the inner roller 30 according to the present invention. Here, the barrel shape is exaggeratedly drawn.

FIG. 2 is an actual measurement graph in which the shape and roughness of the inner peripheral wall of the inner roller 30 according to the embodiment of the present invention are measured by a roughness meter. Here, the scales in the radial direction Y and the axial direction X are not the same for the purpose of measurement, and the magnification in the radial direction Y is set to 200 times the axial direction X.

The line 32L in FIG. 2 corresponds to the inner peripheral wall 32 on the substance side of the lower half of FIG. That is, with the line 32L as a boundary, the lower part is the substance side and the upper part is the hollow hole side.

As shown in FIGS. 1 and 2, in the inner roller 30 according to this embodiment, the longitudinal section of the inner peripheral wall 32 of the cylinder is not straight, and the inner diameter d1 of the central portion in the axial direction is the inner diameter of both ends. The diameter is larger than d2 (d1> d2), and the central portion P1 of the through hole 31 has a convex (concave when viewed from the entity side) barrel shape. The size of the inner roller 30 according to this embodiment is such that the axial length L1 is 25 mm and the inner diameter d2 at both end portions P2 is 1.
2 mm, the thickness t at both ends P2 is 2.5 mm,
In this case, the difference in inner diameter between the central portion P1 and both end portions P2 (d
1-d2) is about 5 to 6 μ on one side.

The convex portion (recessed portion when viewed from the body side) 32R1 at the central portion P1 and the recessed portion (convex portion when viewed from the body side) 32R2 at both end portions P2 are smoothly continuous, and further this recessed portion 32R.
2 and both end surfaces 32R3 are also smoothly continuous.

FIG. 3 shows an inner roller 30 according to this embodiment.
It is a conceptual diagram which shows the state which was attached to the inner pin 7. Note that in FIG. 3 as well, since the visibility is prioritized, the radial direction Y and the axial direction X
The scales of are not the same.

As is apparent from FIG. 3, the outer periphery of the inner pin 7 is formed straight in the axial direction as usual. The outer periphery 7A of the inner pin 7 is the convex portion 3 (on the substance side) of the inner peripheral wall 32 of the inner roller 30.
2R2 and 32R2 are lightly contacted, and the gap H between the central portion P1 of the inner peripheral wall 32 and the (substance side) recess 32R1 (ie (d1-d2) / 2) is as described above (due to the barrel shape). It becomes about 5 to 6 μ. It should be noted that this gap H is not significantly affected by the size of the inner roller 30 and has an absolute value of 2-1.
The allowable range is about 0 μ.

When the gap H is too small, the original function of the gap is not exhibited, and when it is too large, a radial (large) force acts between the inner roller 30 and the inner pin 7. However, the arc at the two convex portions 32R2, 32R2 (as viewed from the entity side) becomes smaller, and this 2
This is because the torque is transmitted only at points, and the inner pin 7 comes into contact with the inner roller 30 only at this portion (at any time), which is not preferable in terms of wear resistance.

By forming the inner peripheral wall 32 of the inner roller 30 into such a shape, the gap H in FIG. 3 functions as a space for securing the lubricating oil. Further, since the inner pin 7 is in contact with the inner roller 30 at the two convex portions 32R2, 32R2 of the inner peripheral wall 32 of the inner roller 30, the axial center O1 of the inner roller 30 and the inner pin 7 has a particularly large force. There is no deviation unless it is applied, and basically there is no rattling. Therefore, unlike the related art, the angular backlash caused by the gap δ1 does not occur.

Further, even if there is a processing error or an assembly error, or if each member elastically deforms during power transmission, an unexpectedly large external load is applied and the inner pin 7 bends. Even if it becomes necessary, since the lubricating oil is secured in the gap H, smooth sliding can be maintained.

Therefore, by adopting the inner roller (or outer roller) having such a structure, the inner roller (outer roller) and the inner pin can be secured while securing a large amount of lubricating oil, that is, without lowering the durability. Angular backlash can be reduced by reliably maintaining the coaxiality of the (outer pin). Further, even if a processing error, elastic deformation during operation, elastic deformation due to an external load, or the like occurs, good slip characteristics can be ensured, so that power loss can be significantly reduced.

When the inner roller 30 according to this embodiment is manufactured by the manufacturing method described later, the inner peripheral wall 3
Coupled with the fact that the surface of No. 2 is mirror-finished by the burnishing process, even if the lubricating oil film becomes thin, it is difficult to cause seizure. According to the experiment in the actual machine, its power transmission capacity is improved about three times. It has been confirmed that noise during operation is also reduced.

Next, a method for manufacturing the inner roller (or outer roller) having such a shape will be specifically described.

For the inner roller having the barrel-shaped inner peripheral wall as described above, a method is conceivable in which the inner peripheral wall is cut by, for example, an ultra-high-precision NC (Nunerical Control) machine tool in the same manufacturing process as the conventional one. To be However, an NC machine tool capable of cutting a material of high hardness and high strength with high accuracy has a very high cost, and the processing time for each inner roller becomes long. However, practically, it cannot be realized in terms of cost.

Therefore, the inventors have devised a manufacturing method in which so-called burnishing processing and heat treatment are combined and the processing strain and thermal strain are positively utilized.

FIGS. 4A to 4D show the manufacturing method thereof. Since each part in FIG. 4 is prioritized for easy viewing, the deformation is exaggerated and drawn, and the scales in the radial direction Y and the axial direction X are not the same. The following will be described in order.

FIG. 4 (A) First, in the state before the heat treatment (the material is soft), the central portion of the cylindrical inner roller material is hollowed and cut in the axial direction X,
A cylindrical inner roller material 30A is formed, and the outer diameter and inner diameter of the inner roller material 30A are intermediately finished.

Here, the outer diameter is generally processed by grinding by a centerless grinder or turning by a precision lathe, and the inner diameter is processed by turning by a precision lathe. Note that this processing is processing by shearing the material structure.

FIG. 4 (B) Next, the entire length of the outer peripheral wall 33 in the axial direction is chucked by the chucking device 50.
And the inner peripheral wall 32 is burnished by the roller burnishing tool 52 to obtain the inner roller material 30B. The burnishing process here is a known process per se, and is a process of rolling (in a crushed manner) the inner peripheral wall 32 processed by shearing the tissue in FIG. 4 (A). Therefore, a finer roughness (mirror surface) than that of turning or grinding can be obtained.

FIG. 4C. After the inner peripheral wall 32 is burnished in this way,
FIG. 4C is an exaggerated drawing of the degree of slight bending after heat treatment.

When the inner roller material 30C is made of high carbon chrome bearing steel material (SUJ2 of JIS G4805 or its equivalent), the heat treatment here is preferably a step of hardening the whole by known quenching and tempering. .

Further, the material of the inner roller material 30C is alloy steel for machine structure (JIS G4103, JIS G4104,
When a so-called carburized steel such as JIS G4105) is used, it is preferable that the surface is hardened by so-called carburizing and quenching.

In any case, at the time of quenching, both ends in the axial direction have a large heat dissipation area, so that they are cooled quickly, so that they shrink more than the central part and harden in that state. A curved shape as shown is obtained. In FIG. 4 (C), lo is the curved length on the outer circumference, δo is the relative shrinkage of the outer diameter, and li and δi are the curved length and the shrinkage on the inner diameter side, respectively.

That is, as is clear from the figure, the inner roller material 30C has .delta.o at both ends l0 on the outer peripheral side.
The diameter is small, and the inner peripheral side has a so-called barrel shape in which both ends of the axial direction li are smaller than the central part by δi at both ends.

As described above, in this embodiment, the deformation (thermal strain) caused by the heat treatment is positively utilized,
A major feature of this is that the inner wall has a barrel shape.

4D. Finally, the outer peripheral wall of the inner roller material 30C deformed into a barrel shape on both the inner peripheral wall 32 and the outer peripheral wall 33 is finished by grinding. As a result, it is possible to obtain the intended inner roller 30 which is straight for the outer peripheral wall 33 and barrel-shaped for the inner peripheral wall. As shown in FIG. 4 (D), this inner roller 30 has a diameter at both axial end portions li of the inner peripheral wall that is smaller than the central portion by .delta.i.

Next, with reference to FIG. 5, a method for forming this barrel shape more positively (larger) will be described.

In this method, when performing the burnishing process, the chucking was performed over the entire length in the axial direction in the previous embodiment, but here, the chucking is intentionally removed at both ends. It is a thing. As a result, when the roller burnishing tool 52 applies a processing pressure from the inner peripheral side during the burnishing process, the inner roller material 30E
As a result, a phenomenon occurs in which both ends of the inner peripheral wall expand to the outer peripheral side as shown by the broken line in the figure, the processing (rolling) here becomes light, and it is possible to create a state in which only the inner peripheral wall 32 is not expanded. As a result, when the chucking device 50 'is released, as shown in FIG. 5B, a barrel shape in which both end portions 1B have a diameter smaller by δB is already obtained at the stage where the heat treatment is not yet performed. Will be able to. Therefore, by performing the heat treatment process described above, the barrel shape can be further clarified as compared with the previous embodiment.

In practice, the chucking is performed so that the gap H (FIG. 3) actually formed is 2 to 10 μ (preferably 5 to 6 μ) in consideration of the size of each inner roller and the applied torque. The method of heat treatment should be determined.

In order to further increase the degree of barrel shape, in addition to the above-described embodiment, only the central portion is radiated slowly at the stage of heat radiation (both ends are intentionally radiated quickly). A heat radiation environment such as that described above, for example, an environment in which cold air is blown only near both ends during heat radiation may be formed.

[0065] By these methods, for example, when the inner diameter d2 of the inner roller is in the range of 6mm~60mm is 1.7 times the outer diameter (d2 + 2 t) from the approximately 1.3-fold (i.e. t
If / d is in the range of 1/3 to 1/6), a barrel shape of the intended degree in the required axial length L1 (about 1.5 to 4 times the inner diameter d2 is required) It has been confirmed by the inventors' tests that the shape can be sufficiently formed.
However, ideally, the outer diameter d2 + 2 t is the inside diameter d2 1.5
If it is about double (1.4 to 1.6 times), a good gap H can be secured (without particularly performing further heat treatment).

In any case, the outer peripheral wall is finally ground straight as described above.

In the inner roller thus manufactured, a gap H is formed between the inner roller and the inner pin at the axial center portion of the inner peripheral wall, and this serves as a lubricating oil holding portion. Further, since the inner peripheral wall is markedly mirror-finished by the burnishing process as compared with the conventional grinding process, seizure hardly occurs, and both ends are in contact with each other almost at all times (the gap between the inner pin and the inner roller is almost zero). ), The cause of angular backlash can be eliminated. In addition to the mirror surface of the inner peripheral wall, the oil film that is constantly formed can maintain high power transmission efficiency, and the power transmission capacity can be improved to about three times.

In the above embodiment, the inner roller is taken as an example to describe the structure and the manufacturing method, but it goes without saying that the present invention can be applied to the outer roller in the same manner.

[0069]

As described above, the inner roller (outer roller) according to the present invention or the inner roller (outer roller) manufactured by the method according to the present invention has a barrel-shaped gap in its inner peripheral wall. Sufficient lubricating oil can be secured, and therefore, the inner pin (outer pin) can be held coaxially with the inner roller (outer roller) with almost no rattling. Therefore, it is possible to secure lubricating oil (maintain durability), improve power transmission efficiency and transmission capacity, reduce noise, and reduce angular backlash.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view of an inner roller applied to an internally meshing planetary gear structure according to the present invention.

FIG. 2 is a graph in which the shape of the inner peripheral wall in the lower half of the inner roller in FIG. 1 is measured.

FIG. 3 is a vertical cross-sectional view showing a state in which an inner pin is assembled to the inner roller of FIG.

FIG. 4 is a process diagram illustrating a method for manufacturing the inner roller according to FIG.

FIG. 5 is a partial process diagram showing a modified example of the manufacturing process according to FIG.

FIG. 6 is a partially cutaway front view for explaining the configuration of a conventional internally meshing planetary gear structure.

7 is a sectional view taken along line VII-VII of FIG.

FIG. 8 is a partially enlarged cross-sectional view for explaining the configuration of an internally meshing planetary gear structure having an outer roller.

FIG. 9 is a transverse sectional view for explaining the relationship between a conventional inner roller and an inner pin.

FIG. 10 is a transverse cross-sectional view for explaining the relationship between a conventional outer roller and an outer pin.

[Explanation of symbols]

1 ... Input shaft 3a, 3b ... eccentric body 5a, 5b ... External gear 6a, 6b ... Inner roller hole 7 ... Inner pin 8, 30 ... Inner roller 10 ... Internal gear 11 ... Outer pin 13 ... Outer pin hole 14 ... Outer roller 32 ... Inner wall 52 ... Roller burnishing tool

─────────────────────────────────────────────────── --Continued from the front page (56) Reference JP-A-3-172650 (JP, A) JP-A-5-79510 (JP, A) JP-A-5-223149 (JP, A) JP-A-9- 329202 (JP, A) Actual Kaihei 7-22123 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) F16H 1/32 B23P 13/02 B23P 15/14

Claims (6)

(57) [Claims] 1. A first shaft, an eccentric body that rotates by the rotation of the first shaft, an externally toothed gear incorporated in a state of being eccentrically rotatable with respect to the first shaft via the eccentric body, An internal gear to which the external gear internally meshes; and a second shaft connected to the external gear via means for transmitting only the rotation component of the external gear.
In an inner mesh planetary gear structure comprising, in a cylindrical inner roller used together with a cylindrical inner pin to form a means for transmitting only the rotation component, a longitudinal section of the inner peripheral wall of the cylinder, An inner roller of an internally meshing planetary gear structure, wherein an inner diameter of an axially central portion of the inner peripheral wall is formed in a barrel shape having a larger diameter than inner diameters of both end portions. 2. A first shaft, an eccentric body that rotates by the rotation of the first shaft, an external gear that is incorporated in a state of being eccentrically rotatable with respect to the first shaft via the eccentric body, An internal gear to which the external gear internally meshes; and a second shaft connected to the external gear via means for transmitting only the rotation component of the external gear.
In a method of manufacturing a cylindrical inner roller used together with a cylindrical inner pin to form a means for transmitting only the rotation component of an intermeshing planetary gear structure having: A step of hollowing and cutting the part in the axial direction to form a cylindrical inner roller material, a step of burnishing the inner peripheral wall of the cylindrical inner roller material, and a heat treatment of the burnished inner roller material. The barrel-shaped forming procedure for deforming the entire inner roller material into a barrel shape in which the central portion in the axial direction is swollen, and the outer peripheral wall of the inner roller material deformed into the barrel shape is ground, and only the outer peripheral wall is completed A method for manufacturing an inner roller having an intermeshing planetary gear structure, comprising: 3. The method for manufacturing an inner roller of an internally meshing planetary gear structure according to claim 2, wherein the burnishing in the burnishing procedure is performed by forming the outer periphery of the cylindrical inner roller blank by The chucking is performed so that a predetermined pressing force is generated on the radial circumferential side at the axial center position, and the heat treatment in the barrel forming procedure is performed with the chucking released. A method for manufacturing an inner roller having an intermeshing planetary gear structure, comprising: 4. A first shaft, an eccentric body that rotates by the rotation of the first shaft, an externally toothed gear incorporated in a state of being eccentrically rotatable with respect to the first shaft via the eccentric body, An internal gear to which the external gear internally meshes; and a second shaft connected to the external gear via means for transmitting only the rotation component of the external gear.
In a cylindrical outer roller used for constituting the internal teeth of the internal gear, of an internally meshing planetary gear structure comprising: a longitudinal section of an inner peripheral wall of the cylinder, and an axial center portion of the inner peripheral wall. An inner roller having an intermeshing planetary gear structure, wherein the inner diameter of the outer roller is formed into a barrel shape having a larger diameter than the inner diameters of both ends. 5. A first shaft, an eccentric body that rotates by the rotation of the first shaft, an externally toothed gear incorporated in a state of being eccentrically rotatable with respect to the first shaft via the eccentric body, An internal gear to which the external gear internally meshes; and a second shaft connected to the external gear via means for transmitting only the rotation component of the external gear.
In a method of manufacturing a cylindrical outer roller used to form the internal teeth of the internal gear of an internally meshing planetary gear structure including: a central portion of a cylindrical outer roller material, which is hollowed out in the axial direction. Then, the procedure of forming a cylindrical outer roller material, the procedure of burnishing the inner peripheral wall of the cylindrical outer roller material, and the heat treatment of the burnished outer roller material A barrel-shaped forming procedure of deforming the barrel into a barrel shape in which the central portion in the axial direction is swelled, and a procedure of grinding the outer peripheral wall of the outer roller material deformed into the barrel shape to form only the outer peripheral wall into a complete columnar shape. A method for manufacturing an outer roller having an intermeshing planetary gear structure, comprising: 6. The method of manufacturing an outer roller having an internally meshing planetary gear structure according to claim 5, wherein the burnishing process in the burnishing procedure is performed by forming an outer periphery of the cylindrical inner roller blank by the burnishing process. The chucking is performed so that a predetermined pressing force is generated on the radial circumferential side at the axial center position, and the heat treatment in the barrel forming procedure is performed with the chucking released. A method for manufacturing an outer roller having an intermeshing planetary gear structure, which is characterized by: