JP2001232546A - Method and device for polishing power transmission member and oscillation inscribing and meshing planetary gear transmission mechanism using power transmission member - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce noise and angle backlash by improving surface coarseness of a bearing hole of a power transmission member. SOLUTION: A film abrasive 110 is pressed against the bearing hole of an external tooth gear W (power transmission member) by backing up by a shoe 120, the external tooth gear W is relatively rotated in the peripheral direction for the film polishing member 110 in this condition, and the external tooth gear W is vibrated in the axial direction at the same time to polish a tooth face.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a polishing method and a polishing apparatus for a power transmission member, which are suitable for an external gear or the like internally meshed with the internal gear inside the internal gear. The present invention relates to a gear transmission mechanism having a polished external gear and having a center of the internal gear inside the periphery of the external gear.

[0002]

2. Description of the Related Art Conventionally, there is provided an external gear internally meshed with the internal gear inside the internal gear, and the external gear engages with an eccentric body to oscillate and rotate. A gear mechanism in which the center of the gear is inside the periphery of the external gear (international classification F16H
A transmission mechanism corresponding to 1/32) is widely known.

[0003] This type of oscillating internally meshing planetary gear transmission mechanism includes, for example, a first shaft, an eccentric body that rotates by rotation of the first shaft, and an eccentric body that is attached to the eccentric body via a bearing to perform eccentric rotation. A plurality of enabled external gears, an internal gear in which the external gear inscribes and meshes through internal teeth formed of external pins, and a rotation component of the external gear to the external gear And a second shaft connected via an inner pin for taking out only the second shaft.

FIGS. 12 and 13 show a conventional example of this structure. In this conventional example, the first axis is used as an input axis,
The above structure is applied to a "reduction gear" by using the second shaft as an output shaft and fixing the internal gear.

The input shaft 1 has a predetermined phase difference (18 in this example).
0 °), the eccentric bodies 3a, 3b are fitted. The eccentric bodies 3a and 3b are respectively connected to the input shaft 1 (center O1).
(Center O2). Each eccentric body 3a, 3b has a plurality of bearing rollers 4a,
Two external gears 5a, 5b are mounted in a double row via 4b. That is, bearing holes 14a and 14b are formed at the centers of the external gears 5a and 5b.
Bearing rollers 4a, 4b are accommodated (inserted) in gaps between the eccentric bodies 3a, 3b and the eccentric bodies 3a, 3b. The reason why the number of the external gears is two (double row) is mainly to increase transmission capacity, maintain strength, and maintain rotational balance.

The external gears 5a, 5b have inner roller holes 6a,
6b, a plurality of inner pins 7 and inner rollers 8 are fitted, and outer teeth 9 having a trochoid tooth shape or an arc tooth shape are provided on the outer periphery of the external gears 5a and 5b. And the internal gear 20 fixed internally. Also, an inner pin 7 penetrating the external gears 5a, 5b
Is fixed or fitted to a flange near the output shaft 2.

The internal gear 20 has a pin holding ring 10 having a plurality of semicircular pin holding holes 13 formed in the inner periphery thereof along the axial direction. And an outer pin 11 that forms an arcuate tooth shape at a (semicircular) portion exposed from the pin holding hole 13.

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,
Although the external gears 5a and 5b try to oscillate around the input shaft 1, their rotation is restricted by the internal gear 20, 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 20 is N + 1, the difference N between the numbers of teeth is 1. Therefore, the external gears 5a and 5b are shifted (rotated) by one tooth with respect to the internal gear 20 fixed to the casing 12 for each rotation of the input shaft 1. This means that one rotation of the input shaft 1 has been reduced to -1 / N rotation of the external gears 5a, 5b (minus represents reverse rotation).

The rotation of the external gears 5a and 5b is absorbed by the gap between the inner roller holes 6a and 6b and the inner pin 7 (the inner roller 8), and only the rotation component is absorbed by the inner pin 7
To the output shaft 2.

As a result, a speed reduction of -1 / N between the input shaft 1 and the output shaft 2 is achieved.

[0012] This internal meshing planetary gear transmission mechanism is
At present, it is applied to various reduction gears or speed-up gears. For example, in the above structure, the first shaft is used as the input shaft, the second shaft is used as the output shaft, and the internal gear is fixed. However, the first shaft is used as the input shaft, and the internal gear is used as the output shaft. In addition, the speed reducer can be configured by fixing the second shaft. Furthermore, in these structures,
By reversing the input and output shafts, a "speed increaser" can be configured.

By the way, in order to reduce the size and increase the load capacity of this kind of internally meshing planetary gear transmission mechanism, among the components having meshing portions and sliding portions, the internal gear 20 has high force characteristics. External gears 5a, 5b, outer pins 11, inner rollers 8,
Inner pin 7, bearing rollers 4a, 4b, eccentric bodies 3a, 3b
Must be made to have high strength properties and high hardness properties. Therefore, the above-mentioned components are usually manufactured using a metal material having such characteristics.

However, metal materials having high strength characteristics and high hardness characteristics usually have a relatively high friction coefficient. Therefore, the sliding contact surfaces using these metal materials need to be lubricated with oil or grease. There is. Here, since lubrication is generally performed by forming an oil film on the contact surface, it is necessary to provide a gap for this purpose between the contact surfaces of the transmission mechanism.

On the other hand, such a gap creates play and play in the entire mechanism, and the rotation of one side immediately becomes the rotation of the other side, and does not appear. Such a response delay is hereinafter referred to as angle backlash.

When the power transmission mechanism is used as a position control mechanism involving forward and reverse rotation, such as a joint of an industrial robot, the angle backlash causes a reduction in control accuracy. Therefore, in order to eliminate the angle backlash, the gap must be reduced. However, it is not preferable to reduce the gap from the viewpoint of holding the lubricating oil. This is opposite to the improvement in lubrication performance.

It is also known that a chemical conversion coating such as a phosphate film is formed on the sliding part to reduce the friction coefficient of the sliding part. The chemical conversion coating itself has a low coefficient of friction, but has a low coefficient of friction because it holds a large amount of lubricating oil on minute irregularities.

Therefore, it is conceivable to form the above-mentioned known chemical conversion coating on the sliding contact surface (including the meshing portion) of the transmission mechanism. However, the chemical conversion coating itself is liable to wear, and the coating peels off in a short time. There is a disadvantage.

Japanese Patent Application No. 60-271649 (Japanese Patent Publication No.
In Japanese Patent No. 36825 and Japanese Patent No. 1623717), in order to reduce the gap between the contact surfaces of the transmission mechanism and maintain the lubricating oil for a long period of time, the direction of the tooth trace of the tooth profile and the direction of the tooth trace are described. Proposal of a structure and manufacturing method of a contact surface or the like in which an uneven surface is formed in a direction (tooth profile direction) intersecting with the tooth trace direction of the grinding, and a chemical conversion coating is applied with a film thickness smaller than the height of the unevenness. are doing.

[0020]

However, in each of these known methods, the friction coefficient of the contact surface of the tooth profile between the external gear and the internal gear is reduced by the presence (holding) of the lubricating oil to increase the friction coefficient. The goal was to achieve efficiency and long life, but not to have the idea of smoothing the contact surface. In particular, chemical conversion coatings do not have low friction per se, but retain lubricating oil between uneven coatings to obtain low friction. Was not necessarily good in surface roughness.

As described above, in the conventional transmission mechanism, the main purpose is to reduce the coefficient of friction by retaining the lubricating oil. Therefore, the tooth surface (contact surface) of the gear and the surface roughness of the bearing hole are reduced.
We did not actively increase it. For this reason, when the meshing portion of the external gear and the external pin of the internal gear make rolling contact with sliding, there is a problem that roughness of the contact surface generates sliding noise and rolling noise. In addition, since the slip noise increases for such a reason, it is difficult to make the gap between the external gear and the internal gear smaller than ever, which has caused the above-mentioned increase in angle backlash.

On the other hand, the present inventor has disclosed in Japanese Patent Application No. 11-0.
08021 (currently undisclosed) proposes a method for remarkably improving the tooth surface roughness, thereby sufficiently solving the above problems.

However, the present inventor has sufficiently solved the above-mentioned problem, but has learned that there is a new possibility (problem).

Specifically, the above-mentioned Japanese Patent Application No. Hei 11-00802 is disclosed.
According to the technology for improving the surface roughness of the "tooth surface" proposed by No. 1, it has become clear that the transmission mechanism has dramatically lower noise and lower backlash than before. No consideration was given to the surface roughness of the bearing hole. This is because before the above technology was proposed, the surface roughness of the bearing hole was generally sufficiently good compared to the tooth surface, so it is only necessary to take measures mainly by focusing on the lubrication state of the tooth surface. It was thought that.

However, as a result of the above-mentioned proposal, the surface roughness of the tooth surface was remarkably improved. As a result, the influence of the surface roughness of the bearing hole became more apparent than expected. In other words, it was expected that noise and backlash reduction effects could be obtained at a higher level by improving the bearing holes (which had not received much attention in the past).

In consideration of the above circumstances, the present invention can contribute to the reduction of noise generated due to the meshing and rotation of the teeth of the external gear, and the angular backlash during rotation can be reduced. Polishing method for a power transmission member capable of increasing a substantial load capacity of an external gear in a compact state by increasing a substantial allowable load of a hole portion, and a transmission mechanism having an external gear manufactured by the grinding method. And an object of the present invention is to provide a polishing apparatus used for carrying out the polishing method.

[0027]

According to the present invention, there is provided a method for polishing a power transmission member having a bearing hole formed in the inside thereof in an axial direction, wherein the pressing member backs up the inner peripheral surface of the bearing hole. By pressing the film abrasive by doing so, by sliding the inner peripheral surface and the film abrasive relative to each other in the circumferential direction in that state, the inner peripheral surface is polished to solve the above problem. It is.

According to the present invention, the undulation and roughness of the bearing hole of the power transmission member are reduced, the smoothness of the inner peripheral surface is increased, and the roundness and cylindricity can be improved. Accordingly, for example, when the bearing roller is inserted directly into the bearing hole and the roller makes rolling contact, it is possible to suppress the occurrence of slip noise and rolling noise. This characteristic has a very large meaning as a characteristic required when, for example, the power transmission member is an external gear and the external gear is used in the swinging internal meshing structure (the details will be described later).

In addition, by reducing the surface roughness,
Fluid lubrication between the contact surfaces becomes possible. For this reason, there is little risk of seizure of the bearing hole portion, the gap between the bearing roller and the bearing hole can be reduced, and rattling noise is reduced. This, for example, when the power transmission member is a gear, leads to an increase in clearance accuracy between the power transmission member and a mating gear that meshes with the power transmission member, and can reduce angle backlash at a higher level.

After the inner peripheral surface of the bearing hole is polished with a forming whetstone or cut with a CBN tool, the inner peripheral surface is subjected to pressure polishing using the film abrasive. Is also good. By doing so, it is possible to perform more efficient combined processing by cutting and polishing.

Further, when the circumferential pressing grinding is performed using the film abrasive, the bearing hole of the power transmission member is further vibrated in the axial direction relative to the film abrasive. You may. Then, the surface roughness can be further improved.

For the reasons described above, the power transmission member according to the present invention is preferably an external gear, and in that case, a pressing member for the tooth surface is further provided on the tooth surface of the external gear. By backing up, the tooth surface film abrasive is pressed, and in this state, the teeth of the external gear and the tooth surface film abrasive are relatively slid in the tooth profile direction, whereby the tooth surface and the inner peripheral surface are slid. May be simultaneously pressed and polished.

In this way, the tooth surface and the bearing hole can be simultaneously polished in one operation, so that the manufacturing process and time are shortened, and the cost is reduced.

When the above-mentioned polishing method is adopted, the teeth of the external gear are polished in the direction of the tooth trace with a forming grindstone, and then the tooth surface and the inner peripheral surface are pressed with the film abrasive. Polishing is preferably performed, and more efficient tooth surface processing is achieved.

As the film abrasive, it is preferable to use a polyester film coated with a fine abrasive such as aluminum oxide, silicon carbide or diamond.

On the other hand, in the power transmission member polishing apparatus of the present invention, a film abrasive for polishing an inner peripheral surface of a bearing hole of the power transmission member and a biasable member against the inner peripheral surface are provided. A pressing mechanism that has a pressing member and presses the film abrasive on the inner peripheral surface with a predetermined pressure via the pressing member; and relatively slides the inner peripheral surface and the film abrasive in the circumferential direction. By providing a polishing drive mechanism, the above problem has been solved.

As means for pressing the film abrasive against the inner peripheral surface of the bearing hole at a predetermined pressure, for example, a pneumatic cylinder mechanism can be used.

Examples of the polishing drive mechanism include a film feeder for feeding (pulling) and moving a long film abrasive in the longitudinal direction, and a work rotating device for supporting and rotating a power transmission member as a work. Can be used. When the work side is driven, the reciprocating rotation can be easily performed finely in both the circumferential direction and the axial direction of the bearing hole, so that the polishing effect by the reciprocal sliding can be further enhanced.

The provision of an oscillation mechanism for oscillating the power transmission member relative to the film abrasive in the axial direction can further enhance the polishing effect.

Further, when the power transmitting member is an external gear and the tooth surfaces of the external teeth are polished at the same time, a tooth surface film abrasive for polishing the tooth surfaces of the external gear is provided; A tooth surface having a pressing member for the tooth surface which is movable in the radial direction with respect to the axis of the external gear, and pressing the film abrasive against the tooth surface with a predetermined pressure via the pressing member; Pressing mechanism, and the polishing drive mechanism that slides the inner peripheral surface and the film abrasive material simultaneously moves the tooth surface of the external gear and the film abrasive material for the tooth surface in the tooth profile direction. It is preferable to make the sliding.

In this way, when polishing the tooth surface and the bearing hole at the same time, the polishing drive mechanism and the oscillation mechanism can be shared, and an efficient apparatus with a simple configuration can be obtained.

A typical example of an application of the power transmission member (external gear) manufactured (polished) as described above is an oscillating internal meshing planetary gear transmission mechanism. Specifically, it has an internal gear, and an external gear inscribed in the internal gear, and the external gear engages with the eccentric body to oscillate and rotate. In the oscillating internally meshing planetary gear transmission mechanism in which the center of the internal gear is located, the external gear is polished by the above-described polishing method, and the bearing hole of the external gear is loosened to the eccentric body. What is necessary is just to comprise so that it may fit, and the some roller for bearings may be directly inserted in the clearance gap between this bearing hole and this eccentric body.

With this arrangement, noise and backlash when the bearing rollers are rolled are reduced, and as a result, the backlash between the external gear and the internal gear is significantly reduced. In addition, since the noise is low, the number of bearing rollers can be increased, so that a large load can be sufficiently endured and the life of the bearing portion can be extended.

The power transmission member according to the present invention includes, in addition to the external gear, each friction roller of the friction transmission device, a power transmission shaft, and the like. (Roller) A hole in which a member, a cylindrical member, a spherical member, or the like is directly rolled, slid and rotated.

[0045]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.

FIG. 1 shows a schematic configuration of a polishing apparatus used to carry out the polishing method of the present invention, and FIG. 2 shows an enlarged view of the relationship between the main parts.

Here, the work to be polished is shown in FIG.
2, an external gear W similar to the external gears 5a and 5b of the internally meshing planetary external gear mechanism shown in FIG.

The external gear W has a trochoidal tooth profile on the outer periphery.
And is supported by a horizontal drive shaft 101. The drive shaft 101 is reciprocatingly driven in the tooth profile direction (circumferential direction of the external gear W and its bearing hole 14: see FIG. 2) while supporting the external gear W, and in the tooth trace direction (outer direction). Axial direction of the tooth gear W and its bearing hole 14: FIG.
(See Reference) for micro-vibration (oscillation). In FIG. 1, reference numeral 102 denotes a rotation driving device (polishing driving mechanism) for driving the driving shaft 101 to rotate.
Reference numeral 03 denotes an oscillation device for causing minute vibration.

A film abrasive 110 for polishing the tooth surface of the external gear W is pressed against the inner peripheral surface of the bearing hole 14 of the external gear W supported by the drive shaft 101 from the inside. Specifically, the film abrasive 110 passes through the bearing hole 14 of the external gear W from one side to the other (in a pressed state), returns at the passage destination, and returns to the bearing hole 14 (in a non-pressed state). ) I'm passing again.

As shown in FIG. 3, the film abrasive 110 is formed by polishing particles of aluminum oxide, silicon carbide, diamond or the like on the surface of a polyester film 110a by using thermosetting adhesives 110b and 110c. (A fine particle abrasive) 110d, and the side where a part of the abrasive particles 110d is exposed is the polishing side.

Returning to FIG. 1, a shoe 120 (as a pressing member in a pressing mechanism) for pressing the film abrasive 110 against the inner peripheral surface of the bearing hole 14 is provided inside the external gear W bearing hole 14. Are arranged. This shoe 120
Is a constant pressure pressing device 13 having a built-in pneumatic cylinder mechanism and the like.
The arm 131 is supported by the arm 131 and serves as a backup member for pressing the film abrasive 110 against the inner peripheral surface at a constant pressure P.

The pressing surface of the shoe 120 is formed as a convex curved surface having a curvature smaller than (or equivalent to) the concave curved surface (inner peripheral surface) of the bearing hole 14.
By pressing 0 against the inner peripheral surface, polishing can be surely and efficiently performed.

Other devices include a rotary drive device 10
A polishing control device for controlling the oscillator 2 and the oscillation device 103, a film feeding device for feeding (pulling) and moving the film abrasive 110, a control device for the constant-pressure pressing device 130 (all not shown), etc. are provided. Have been.

When polishing the bearing holes of the external gear having no inner roller hole 6 or the like or the cylindrical friction roller, the outer peripheral surfaces thereof may be clamped by the chuck 104. Alternatively, the work may be clamped (pinched) in the axial direction, or the work may be housed at the position of the sun member of the planetary structure, and the work may be clamped and rotated by the planetary member.

Next, a method of finishing the bearing hole 14 of the external gear W will be described.

In the step of finishing the teeth, the first step is a grinding step using a grindstone, and the second step is a polishing step using the above-described polishing apparatus. Note that, instead of the grinding in the first step, cutting with a CBN (cubic boron nitride) chip may be performed, or these may be combined.

In the first step, as shown in FIG. 4, a grindstone 201 formed into a cylindrical shape smaller in diameter than the bearing hole 14 is formed.
The teeth are ground by rotating the external gear W in accordance with the inner peripheral surface of the bearing hole 14 and simultaneously rotating the external gear W. This step is a base of processing, and the degree of coaxiality with the pitch circle of the external gear W, the perpendicularity of the axis of the bearing hole 14 to the side surface of the gear, and the like are ensured to some extent in this step. At this time, “roughness (small displacement)” and “swelling (overall displacement when small displacements are ignored)” remain in the axial direction of the inner peripheral surface, as shown in FIG.

Then, the polishing in the second step is performed next.

In this step, first, as shown in FIG.
The film abrasive 110 is placed in the bearing hole 14 of the external gear W, and the constant pressure pressing device 130 is operated to move the shoe 120
With this, the film abrasive 110 is pressed against the inner peripheral surface at a constant pressure P.

Next, in this state, the external gear W is intermittently or continuously rotated clockwise and counterclockwise (relatively slid). Thereby, the film abrasive 11
With 0, the inner peripheral surface is polished in the circumferential direction. At this time, the external gear W is slightly vibrated (oscillated) in the axial direction, thereby enhancing the polishing effect on the tooth surface.

FIG. 6 shows the data after the second step. By the second step, the waviness and roughness in the axial direction in the first step are largely removed.

The film abrasive 110 is polished for a predetermined time, or the bearing hole 14 is formed at a predetermined angle (predetermined rotation).
At the stage of polishing, it is fed (pulled) by a predetermined amount so that it can be polished on a new surface.

The external gear W and the film abrasive 11
In the case of the external gear W, the film abrasive 110 (shoe 120) is moved along the inner peripheral surface while the external gear W is vibrating only in the axial direction. It may be configured to rotate in the circumferential direction.
Further, the feeding direction of the film abrasive 110 is not limited to the axial direction, and may be sent in a circumferential direction or an oblique direction (helical direction).

In this way, the circumferential and axial roughness and waviness of the bearing hole of the external gear W are removed, and the surface roughness is improved. Therefore, the bearing roller 4a which comes into rolling contact while moving in the circumferential direction. , 4b. As a result, an appropriate oil film can be easily secured, so that the bearing holes 14a, 14b, the bearing rollers 4a, 4b
Also, even if the gaps between the eccentric bodies 3a and 3b are reduced, seizure hardly occurs, and rattling in the radial direction can be reduced.

Further, since the surface roughness is improved, the noise caused by the rolling of the bearing rollers 4a and 4b is reduced. As a result, the conventional roller 4 is used to prevent noise.
Although the number of the rollers a and b was reduced as much as possible, according to the present invention, even if the number of the bearing rollers 4a and 4b was increased, the noise did not increase, so that the load sharing of each roller was reduced. Higher load and longer life are achieved.

Next, a second embodiment of the present invention will be described with reference to the drawings.

FIG. 7 shows a schematic configuration of a polishing apparatus according to a second embodiment used to carry out the polishing method of the present invention.
FIG. 8 shows the relationship between the main parts in an enlarged manner.

The work to be polished is shown in FIG.
2, an external gear W similar to the external gears 5a and 5b of the internally meshing planetary external gear mechanism shown in FIG. Further, this polishing apparatus is for simultaneously polishing the bearing hole 14 and the tooth surface of the external gear W. Since the polishing of the bearing hole 14 is almost the same as that shown in the first embodiment, the same portion is used. , The same symbols are assigned to the last two digits, and description and illustration are omitted.

The external gear W has a trochoidal tooth profile on the outer periphery, and is supported by a horizontal drive shaft 201. As already described in the first embodiment, the drive shaft 201 is reciprocatingly driven in the tooth profile direction (circumferential direction of the external gear W: see the figure) while supporting the external gear W, and Micro vibration (oscillation) is provided in the tooth trace direction (the axial direction of the external gear W: see the figure).
In FIG. 7, reference numeral 202 denotes a rotation driving device (polishing driving mechanism) for rotational driving, and reference numeral 203 denotes an oscillation device for minute vibration, and the rotation driving device 102 and the oscillation device 103 in FIG. Have been.

On the outer periphery of the external gear W supported by the drive shaft 201, a film abrasive 210 (similar to that used for polishing the bearing hole 14) for polishing the tooth surface of the external gear W is provided. The outer gear W is covered and covers almost half the circumference.

Returning to FIG. 7, a shoe 250 (as a pressing member of a pressing mechanism) for a tooth surface for pressing the film abrasive 210 against the tooth surface of the external gear W is provided above and below the external gear W. Is arranged. These shoes 250
It is supported by an arm 261 of a constant pressure pressing device 260 having a built-in pneumatic cylinder mechanism and the like, and serves as a backup member for pressing the film abrasive 210 against the tooth surface of the external gear W with a constant pressure P.

The pressing surface of each shoe 250 is formed as a convex surface having a smaller curvature than the concave surface of the trochoid tooth profile (a surface having a curvature R that follows the tooth surface with the rotation of the external gear W). By pressing the film abrasive 210 against the tooth surface with the convex surface, the valley of the tooth profile can be surely and efficiently polished.

Other devices include a rotary drive device 20
1, a polishing control device for controlling the oscillation device 203 (equivalent device to FIG. 1), a film feeding device for feeding (pulling) and moving the film abrasive 210, and a control device for a constant-pressure pressing device (all shown in FIG. 1). (Not shown).

Next, a method of finishing the teeth of the external gear W and the bearing hole 14 will be described.

In the finishing step, the teeth and the bearing holes 14 are ground by a grindstone in the first step, and the polishing step using the above-mentioned polishing apparatus is performed in the second step. Note that the processing of the bearing hole 14 is the same as in the first embodiment, and a description thereof will be omitted.

In the first step (with respect to the tooth surface), as shown in FIG. 9, the grinding wheel 280 formed into a tooth shape is rotated in accordance with the tooth shape of the external gear W, and the external gear W is moved in the tooth trace direction. Grind the teeth by moving them (in the direction perpendicular to the drawing). This step is the basis of processing, and the pitch accuracy and the tooth profile accuracy of the teeth are ensured in this step. At this time, roughness and undulation remain in the tooth profile direction of the tooth surface as shown in FIG.

Then, the polishing in the second step is performed next.

In this step, first, as shown in FIG.
The film abrasive 210 is arranged so as to surround the external shape of the external gear W, and the constant-pressure pressing device 230 is operated, so that the shoe 25
0, the film abrasive 210 is pressed against the tooth surface of the external gear W with a constant pressure P. At this time, the film abrasive 210 is pressed against the inner peripheral surface of the bearing hole 14 using the shoe 250.

Next, in this state, the external gear W is intermittently or continuously rotated clockwise and counterclockwise (relatively slid). Thereby, the film abrasive 21
0 means that the tooth surface is in the tooth profile direction (circumferential direction) and the bearing hole 1
4 are simultaneously polished in the circumferential direction. At this time, the external gear W
By micro-oscillating (oscillation) in the direction of the tooth muscle,
Increases the polishing effect on the tooth surface and inner peripheral surface.

FIG. 11 shows data of the tooth surface after the second step. The undulation and roughness in the tooth profile direction in the first step are removed by the second step.

The film abrasive 210 is fed (pulled) by a predetermined amount at the stage of polishing for a predetermined time or at the stage of polishing the external gear W by a predetermined angle or by a predetermined number of teeth, so that it can be polished on a new surface. .

The external gear W and the film abrasive 21
In the case of 0, since it is only necessary to relatively slide in polishing, the film abrasive 210 is fed (pulled) while the external gear W is vibrating only in the tooth trace direction, for example. Good.

In this way, the roughness and undulation of the tooth surface and the inner peripheral surface are removed at the same time, and the surface roughness is improved, so that the outer pin 11 (internal tooth) which comes into rolling contact with sliding while moving in the tooth profile direction. It corresponds to the teeth of the external gear, and FIG.
13 (see FIG. 13). As a result, an appropriate oil film can be easily secured, so that seizure does not easily occur even if the gap between the teeth is reduced, and angle backlash can be reduced. Further, as already described in the first embodiment, the play in the radial direction in the bearing hole 14 is also improved. Therefore, the synergistic effect with the bearing hole 14 (especially the external gear W that swings and rotates). Case)
Angle backlash when switching between forward rotation and reverse rotation is greatly reduced.

Further, since the surface roughness in the tooth profile direction is improved, noise mainly due to slipping and rolling is reduced, and the dynamic load of the external pin 11 and the external gears 5a and 5b (external gear W) is reduced. By decreasing, the actual meshing rate increases,
Further noise reduction can be achieved.

[0085]

As described above, according to the present invention,
Since the surface roughness of the bearing hole of the power transmission member such as the external gear can be improved, noise generation due to rotation of the bearing roller and meshing of the teeth of the external gear can be reduced, and fluid lubrication of each contact surface can be achieved. Thus, the oil film can be secured. Therefore, the gap between the teeth or the backlash in the bearing hole can be reduced while suppressing the seizure of the tooth surface and the bearing, and from that point, it is possible to contribute to the reduction of noise and the reduction of the angle backlash. Further, since a large number of bearing rollers having a small diameter can be inserted into the bearing holes, it is possible to realize a compact power transmission member (for example, an external gear) and a high load resistance.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of a polishing apparatus according to a first embodiment of the present invention.

FIG. 2 is an enlarged view of a main part of FIG. 1;

FIG. 3 is an enlarged sectional view of a film abrasive used in the polishing apparatus.

FIG. 4 is an explanatory diagram of a grinding process performed in a step before the polishing method according to the first embodiment is performed.

FIG. 5 is a characteristic diagram showing roughness data of an inner peripheral surface before performing the polishing method.

FIG. 6 is a characteristic diagram showing roughness data of an inner peripheral surface after performing the polishing method.

FIG. 7 is a schematic configuration diagram of a polishing apparatus according to a second embodiment of the present invention.

FIG. 8 is an enlarged view of a main part of FIG. 7;

FIG. 9 is an explanatory diagram of a grinding process performed in a step before the polishing method according to the second embodiment is performed.

FIG. 10 is a characteristic diagram showing tooth surface roughness data before performing the polishing method.

FIG. 11 is a characteristic diagram showing tooth surface roughness data after performing the polishing method.

FIG. 12 is a cross-sectional view of an internally meshing planetary external gear mechanism including a workpiece to be polished.

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

[Explanation of symbols]

 W: Workpiece 110: Film abrasive 120: Shoe (pressing member) 130: Constant pressure pressing device 110a: Polyester film 110d: Fine particle abrasive

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Kazuhiro Miyamae 6-1, Asahi-machi, Obu-shi, Aichi Pref. Within the Nagoya Works of Sumitomo Heavy Industries, Ltd. (72) Inventor Takashi Toida 6-1-1 Asahi-cho, Obu-shi, Aichi Address Sumitomo Heavy Industries Machinery Co., Ltd., Nagoya Works (72) Inventor Takashi Matsumoto 6-1, Asahimachi, Obu City, Aichi Prefecture Sumitomo Heavy Industries Machinery Co., Ltd., Nagoya Works F-term (reference) 3C058 AA05 AA12 AB06 CB01 CB05 3J027 FA12 FC12 GB03 GC03 GC24 GC26 GC29 GD03 GD07 GD12 GE14 GE25

Claims (10)

[Claims] 1. A method for polishing a power transmission member having a bearing hole formed in the interior thereof in an axial direction, wherein the film abrasive is pressed against the inner peripheral surface of the bearing hole by backing up the pressing member. In this state, the inner peripheral surface is polished by relatively sliding the inner peripheral surface and the film abrasive in the circumferential direction, whereby the power transmission member is polished. 2. The pressure-polishing method according to claim 1, wherein the inner peripheral surface of the bearing hole is polished by a forming whetstone or cut by a CBN blade, and then the inner peripheral surface is pressed and polished using the film abrasive. A method for polishing a power transmission member, which is performed. 3. The method according to claim 1, wherein, when the circumferential pressing and polishing is performed using the film abrasive, the bearing hole of the power transmission member is further axially moved with respect to the film abrasive. A method for polishing a power transmission member, characterized by relatively vibrating. 4. The method for polishing a power transmission member according to claim 1, wherein the power transmission member is an external gear. 5. The tooth gear of claim 4, wherein the film abrasive for the tooth surface is pressed against the tooth surface of the external gear by backing up the tooth surface with a pressing member for the tooth surface. A method for polishing a power transmission member, characterized in that the tooth surface and the inner peripheral surface of the bearing hole are simultaneously pressed and polished by relatively sliding a surface film abrasive in a tooth profile direction. 6. The power transmission member according to claim 5, wherein after the teeth of the external gear are polished in the tooth trace direction with a forming grindstone, the tooth surface and the inner peripheral surface are pressed and polished. Polishing method. 7. A polishing apparatus for a power transmission member having a bearing hole formed in the interior thereof in an axial direction, comprising: a film abrasive for polishing an inner peripheral surface of the bearing hole; Having a pressing member that can be biased by
A pressing mechanism that presses the film abrasive onto the inner peripheral surface with a predetermined pressure via the pressing member, a polishing drive mechanism that relatively slides the inner peripheral surface and the film abrasive in the circumferential direction, A polishing apparatus for a power transmission member, comprising: 8. The power transmission member according to claim 7, further comprising an oscillation mechanism for causing said bearing hole of said power transmission member to vibrate axially relative to a film abrasive. Polishing equipment. 9. The external gear according to claim 7, wherein the power transmission member is an external gear, further comprising: a tooth surface film abrasive for polishing a tooth surface of the external gear; A tooth-surface pressing mechanism having a tooth-surface pressing member capable of moving forward and backward in the radial direction with respect to the axis, and pressing the film abrasive against the tooth surface with a predetermined pressure via the pressing member; The polishing drive mechanism for polishing the inner peripheral surface is configured to simultaneously slide the tooth surface of the external gear and the film abrasive for the tooth surface relatively in the tooth profile direction. A polishing apparatus for a power transmission member, characterized in that: 10. An external gear having an internal gear and an external gear inscribed in the internal gear, wherein the external gear engages with an eccentric body to oscillate and rotate, and an internal gear around the external gear. In the swinging internal meshing planetary gear transmission mechanism in which the center of the internal gear is located, the external gear is polished by the polishing method according to any one of claims 1 to 6, and the external gear is A swinging internally meshing planetary gear transmission mechanism, wherein the bearing hole is loosely fitted to the eccentric body, and a plurality of bearing rollers are directly inserted into a gap between the bearing hole and the eccentric body.