JP2015135189A - Assembling method of reduction gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress the vibration of a roller-type reduction gear.SOLUTION: An input shaft 7 is arranged coaxially with an inner gear 3 of a fixed arrangement, and an eccentric disc 9 which can rotate in the inner gear 3 is arranged. A cage 14 which can rotate between the inner gear 3 and the eccentric disc 9 is arranged at a shaft end of an output shaft 12 which is arranged coaxially with the input shaft 7, and pockets 18 smaller in number than inner teeth 4 of the inner gear 3 are formed. Rollers 19 are accommodated in the pockets 18, the rollers 19 are pressed by a rolling bearing 11 fit to the eccentric disc 9 by the rotation of the eccentric disc 9 which rotates together with the input shaft 7, and sequentially engaged with the inner teeth 4, and the rollers 19 are moved to a one-tooth divided direction of the inner teeth 4 per one rotation of the input shaft 7, and the output shaft 12 is reduced in speed and rotated. A tooth bottom circle radius of the inner gear 3, a circumscription circle radius of the rolling bearing 11 with an axial core of the input shaft 7 as a center, and outside diameters of the rollers 19 are measured in advance, and a minimum roller clearance which is formed between tooth bottoms of the rollers 19 and the inner gear 3 is managed by a selective combination of dimensions of these three components.

Description

  The present invention relates to a roller-type speed reducer that sequentially engages an inner tooth formed on an inner periphery of an internal gear with a smaller number of rollers than the inner tooth to decelerate and transmit the rotation of an input shaft to an output shaft.

  As this type of roller speed reducer, the one described in Patent Document 1 has been conventionally known. In the roller type speed reducer, the input shaft and the output shaft are arranged coaxially so that the shaft end portions face each other, and the internal gear has a plurality of curved inner teeth on the inner periphery by a housing that covers the shaft end portions of both shafts. The shaft end of the input shaft is provided with two eccentric discs that are rotatable in the internal gear at an axial interval, and the shaft end of the output shaft is eccentric with the internal gear. A cage is provided between the rolling bearings press-fitted into each outer diameter surface of the disc, and the cage has a plurality of pockets having a number smaller than that of the inner teeth at portions facing each of the two eccentric discs. Rollers that are formed at equal intervals in the circumferential direction and that roll along the outer diameter surface of the rolling bearing and sequentially mesh with the internal teeth of the internal gear are accommodated in the pockets.

  In the reduction gear configured as described above, when the input shaft rotates, the roller sequentially meshes with the internal teeth of the internal gear by the rotation of the eccentric disk, and the roller is one tooth of the internal teeth per one rotation of the input shaft. The position shifts in the circumferential direction by the amount, and the output shaft rotates at a reduced speed relative to the input shaft.

  Here, in order to obtain a smooth rotation transmission, in the reduction gear described in Patent Document 1, the tooth profile of the internal teeth is set so that the rotation angle of the output shaft is in a range corresponding to one pitch of the internal gear. The output shaft is rotated by the rotation of the eccentric disk, and at that time, all of the plurality of rollers are set to the inner teeth, with the curve outside the roller as one tooth among the curves parallel to the locus drawn by the center of the roller. I try to contact them.

JP 62-93565 A

  By the way, various parts such as an internal gear, an eccentric disk, a rolling bearing, and a roller forming a roller type reduction gear have manufacturing errors. Conventionally, various parts having these manufacturing errors are simply assembled and used as a roller. Since the speed reducer is assembled, the roller gap does not have a constant size, and a good product with a constant quality cannot be obtained.

  Here, the roller clearance refers to the roller 19 disposed on the eccentric disc displacement side of the rolling bearing 11 fitted to the outer periphery of the eccentric disc in FIG. It refers to a gap 20 formed between the roots 4a of the inner teeth 4 formed on the inner periphery of the gear 3.

  Conventionally, as described above, since the assembly does not manage the roller gap 20, the roller gap 20 of an appropriate size cannot be secured, and the roller gap 20 may be larger than necessary. . In this case, when the roller 19 once pulled out from the internal tooth 4 of the internal gear 3 enters the adjacent internal tooth 4, it collides with the tooth bottom 4 a of the internal tooth 4 and causes vibration.

Here, when the size of the roller gap 20 and [delta] _1, the [delta] ₁ can be expressed by the following equation (1).
δ ₁ = (A−B) −C Formula (1)
In the above formula (1),
A: tooth root circle radius of internal gear 3 B: circumscribed radius of rolling bearing 11 centering on the axis of the input shaft C: outer diameter of roller 19

  The inventors of the present case have verified the influence of the roller gap 20 formed between the roller 19 and the tooth bottom 4a of the internal gear 3 on the speed reducer, and have derived the following items.

Efficiency: Unevenness of rotation occurs due to excessive or small variation in roller clearance. Moreover, since the loss at the excessively small gap becomes excessive, the efficiency is lowered.
Life: When the roller passes through the excessively small gap, excessive surface pressure is generated at the contact portion between the roller and the inner diameter of the internal gear or between the roller and the outer ring of the rolling bearing, and early peeling occurs.
Vibration: The roller behavior becomes unstable at an excessive gap, and vibration is generated.

  Further, when the characteristic evaluation was performed with the roller gap 20 as an input characteristic value, the result shown in FIG. 6 was obtained. For this reason, optimization of the roller gap 20 is important.

  An object of the present invention is to suppress the vibration of the speed reducer and stabilize the quality by setting the roller gap to an optimum range.

  In order to solve the above-described problems, in the present invention, a fixedly arranged internal gear and an eccentric disk that can rotate within the internal gear are provided at the shaft end, and a rolling bearing is provided on the outer diameter surface of the eccentric disk. Between the internal gear and the rolling bearing at the shaft end portion of the output shaft facing the input shaft. A pocket having a smaller number than the internal teeth formed on the inner periphery of the internal gear is provided at equal intervals in the circumferential direction at a portion of the cage that is opposed to the rolling bearing in the radial direction in the radial direction. Each of them accommodates a roller that meshes with the inner tooth, and the eccentric disk rotates in sequence with the inner tooth by the eccentric rotation of the eccentric disk, and moves in the circumferential direction by one tooth of the inner tooth per one rotation of the input shaft. To reduce the rotational speed of the output shaft. A roller formed between the roller and the bottom of the internal gear by measuring in advance the root radius of the internal gear, the circumscribed circle radius of the rolling bearing centered on the axis of the input shaft and the outer diameter of the roller. A configuration in which the gap is managed in a range of 0 to 20 μm is adopted.

  Here, the roller gap refers to the gap 20 shown in FIG. 5. If the size of the roller gap is in the range of 0 to 20 μm, as is apparent from the test results of various characteristics shown in FIG. It is possible to obtain a speed reducer that has little variation and high quality and long life.

  In the speed reducer according to the present invention, two eccentric discs are fitted with rolling bearings, and the two eccentric discs are positioned so that the center of the cylindrical outer diameter surface thereof is shifted by 180 ° in the circumferential direction. In the state where the rolling bearings are fitted to the two eccentric disks, the rotational circle diameters of the outer ring outer diameter surfaces of the respective rolling bearings are simultaneously measured, thereby efficiently performing the measurement operation. It can be carried out.

  By using a laser displacement meter or a capacitance displacement meter for measuring the root circle radius of the internal gear, it is possible to perform highly accurate measurement.

  In the reduction gear according to the present invention, as described above, the root circle radius of the internal gear, the circumscribed circle radius of the rolling bearing centering on the axis of the input shaft and the outer diameter of the roller are measured in advance, and these three parts are measured. By controlling the roller gap formed between the roller and the bottom of the internal gear in the range of 0 to 20 μm by selecting and combining the dimensions of the gears, the vibration of the reduction gear can be suppressed and the quality can be stabilized. .

Longitudinal front view showing an embodiment of a reduction gear according to the present invention Sectional view along the line II-II in FIG. Sectional drawing which shows the measurement state of the circumscribed radius of a rolling bearing centering on the shaft center of an input shaft Graph showing the measurement results of the circumscribed circle radius of rolling bearings Sectional view showing the root circle radius of the internal gear, the circumscribed circle radius of the rolling bearing around the axis of the input shaft, and the outer diameter of the roller Graph showing verification results of roller clearance and various characteristics

  Embodiments of the present invention will be described below with reference to the drawings. As shown in FIG. 1, the housing 1 has a cylindrical shape. The housing 1 is divided into two in the axial direction, and a first divided housing 1a and a second divided housing 1b are provided.

  The first divided housing 1a and the second divided housing 1b are coupled and integrated by tightening bolts (not shown), and the inner surface of the abutting side end spans the first divided housing 1a and the second divided housing 1b. A large-diameter recess 2 is formed.

  As shown in FIGS. 1 and 2, an internal gear 3 is press-fitted into the large-diameter recess 2, and a plurality of internal teeth 4 are provided on the inner periphery of the internal gear 3.

  As shown in FIG. 1, an end plate 5 is provided at the open end of the first divided housing 1 a, and an input shaft 7 is inserted into a shaft insertion hole 6 formed in the center of the end plate 5. The input shaft 7 is rotatably supported by a bearing 8 incorporated in the shaft insertion hole 6, is arranged coaxially with the internal gear 3, and has an internal gear 3 at the end of the shaft located in the housing 1. Two eccentric discs 9 which can be rotated inside are provided at intervals in the axial direction.

The two eccentric discs 9 are mounted so that the center of the cylindrical outer diameter surface is shifted by 180 ° in the circumferential direction, and a rolling bearing 11 is press-fitted into the outer diameter surface 10. A ball bearing is adopted as the rolling bearing 11. Here, [delta] ₀ shown in FIG. 2 shows the amount of eccentricity of the center O ₁ of the cylindrical radially outer surface of the center O ₀ with eccentric disc 9 of the input shaft 7.

  As shown in FIG. 1, the output shaft 12 is inserted inside the second divided housing 1b. The output shaft 12 is rotatably supported by a bearing 13 incorporated in the opening end portion of the second divided housing 1b, and is arranged coaxially with the input shaft 7.

  A cage 14 is provided at the end of the output shaft 12 facing the input shaft 7, and the cage 14 is rotatable between the rolling bearing 11 on the eccentric disc 9 and the facing portion of the internal gear 3. The cage 14 has a closed end on the output shaft 12 side, and a bearing 17 that receives the shaft end of the input shaft 7 is incorporated in a small-diameter hole 16 formed in the center of the closed end surface 15.

As shown in FIG. 1 and FIG. 2, the cage 14 is formed with a plurality of pockets 18 arranged in the circumferential direction at equal intervals in a double row, and the pockets 18 in each row are formed on each of the two eccentric disks 9. A plurality of pockets 18 in one row and a plurality of pockets 18 in the other row are offset from each other by a half pitch in the circumferential direction.

  The plurality of pockets 18 in each row is smaller than the number of teeth of the inner teeth 4 formed on the inner periphery of the internal gear 3, and one roller 19 is accommodated in each pocket 18 so as to be movable in the radial direction. .

  The roller 19 is capable of meshing with the internal teeth 4 of the internal gear 3, and the internal teeth 4 with which the rollers 19 mesh are curved tooth shapes that allow the plurality of rollers 19 arranged in the circumferential direction to simultaneously contact each other. It is said that. In order to allow all the rollers 19 to be in contact with each other, as described in the above-mentioned Patent Document 1, the eccentric disk 9 has a rotational angle of the output shaft 12 within a range corresponding to one pitch of the internal teeth 4 of the internal gear 3. The rotation of the output shaft 12 rotates, and at this time, of the curves parallel to the trajectory drawn by the center of the roller 19, the tooth profile is defined as one tooth corresponding to the curve outside the roller 19.

The speed reducer shown in the embodiment has the above-described configuration. When the speed reducer is assembled, the outer ring 11a of the rolling bearing 11 centering on the root circle radius A of the internal gear 3 and the axis of the input shaft shown in FIG. Of the roller 19 and the outer diameter C of the roller 19 are respectively measured, and the size δ _{1 of the} roller gap 20 formed between the roller 19 and the tooth bottom of the internal gear 3 by matching by selecting and combining the dimensions of these three parts. However, the size δ ₁ of the roller gap 20 is managed so that it becomes 0 to 20 μm.

  Here, when measuring the circumscribed radius B of the outer ring 11a of the rolling bearing 11 around the axis of the input shaft 7, a gauge outer ring (not shown) having the same diameter as the rolling bearing 11 is prepared in advance. The contact 31 of the dial gauge 30 is pressed against the perfect circular outer diameter surface formed on the outer periphery of the gauge outer ring, the pointer is shaken, and the deflection amount of the pointer is stored.

  Thereafter, as shown in FIG. 3, with the first divided housing 1a and the internal gear 3 removed, the contact 31 of the dial gauge 30 is inserted into the pocket 18, and the contact 31 is inserted into the outer ring 11a of the rolling bearing 11. The input shaft 7 is rotated once in a state in which the input shaft 7 is pressed against the outer diameter surface of the needle and the shake amount of the pointer is made to coincide with the stored shake amount.

  As a result of the measurement, as indicated by the graph of FIG. 4, the dial gauge 30 is detected as a sine curve by adding a value (2δ) that is twice the eccentric amount δ of the eccentric disk 9. By adding the amplitude W to the radius of the cage outer ring, the circumscribed radius B of the outer ring 11a in the rolling bearing 11 can be known.

  In this way, by directly measuring the outer diameter surface of the outer ring 11a of the rolling bearing 11 with the rolling bearing 11 fitted to the outer diameter surface of the eccentric disc 9, the outer diameter and rolling of the eccentric disc 9 are measured. It is not necessary to measure the inner ring inner diameter and the coaxiality of the bearing 11, and the measurement work is easy, and the measurement can be performed with high accuracy. In addition, since it can be measured in the assembly line of the speed reducer, no significant line change is required.

  Here, when measuring the root circle radius of the internal gear, it is measured using a laser displacement meter or a capacitance displacement meter.

  FIG. 1 shows a reduction gear assembled by matching with a selected combination of dimensions of three parts. When the input shaft 7 in the speed reduction device is rotated, the roller 19 is sequentially meshed with the internal teeth 4 of the internal gear 3 by the rotation of the eccentric disk 9, and the roller 19 is one of the internal teeth 4 per one rotation of the input shaft 7. It moves in the circumferential direction by the amount of teeth, and the output shaft 12 rotates at a reduced speed.

At this time, the magnitude [delta] ₁ of the roller gap 20 formed between the tooth bottom of the internal gear 3 and the roller 19, so as to be 0～20Myuemu, since the roller gap 20 is managed, the roller 19 is an internal gear There is no collision with 3 and no vibration is generated.

  It is possible to suppress the occurrence of rotation unevenness due to excessive or small variations in the roller gap 20 or excessive loss in the excessive gap portion, and there is no inconvenience that the efficiency is lowered.

When the roller 19 passes through the undergap portion, an excessive surface pressure is generated at the contact portion between the roller 19 and the inner diameter of the internal gear or between the roller 19 and the outer ring 11a of the rolling bearing 11 to cause early peeling. By causing the size δ ₁ to be in the range of 0 to 20 μm, such inconvenience does not occur.

DESCRIPTION OF SYMBOLS 1 Housing 3 Internal gear 4 Internal tooth 7 Input shaft 9 Eccentric disk 12 Output shaft 14 Cage 18 Pocket 19 Roller 20 Roller clearance

The present invention is an assembly of a roller type speed reducer in which inner teeth formed on the inner periphery of an internal gear are successively meshed with a smaller number of rollers than the inner teeth, and the rotation of the input shaft is decelerated and transmitted to the output shaft. Regarding the method .

  As this type of roller speed reducer, the one described in Patent Document 1 has been conventionally known. In the roller type speed reducer, the input shaft and the output shaft are arranged coaxially so that the shaft end portions face each other, and the internal gear has a plurality of curved inner teeth on the inner periphery by a housing that covers the shaft end portions of both shafts. The shaft end of the input shaft is provided with two eccentric discs that are rotatable in the internal gear at an axial interval, and the shaft end of the output shaft is eccentric with the internal gear. A cage is provided between the rolling bearings press-fitted into each outer diameter surface of the disc, and the cage has a plurality of pockets having a number smaller than that of the inner teeth at portions facing each of the two eccentric discs. Rollers that are formed at equal intervals in the circumferential direction and that roll along the outer diameter surface of the rolling bearing and sequentially mesh with the internal teeth of the internal gear are accommodated in the pockets.

  In the reduction gear configured as described above, when the input shaft rotates, the roller sequentially meshes with the internal teeth of the internal gear by the rotation of the eccentric disk, and the roller is one tooth of the internal teeth per one rotation of the input shaft. The position shifts in the circumferential direction by the amount, and the output shaft rotates at a reduced speed relative to the input shaft.

  Here, in order to obtain a smooth rotation transmission, in the reduction gear described in Patent Document 1, the tooth profile of the internal teeth is set so that the rotation angle of the output shaft is in a range corresponding to one pitch of the internal gear. The output shaft is rotated by the rotation of the eccentric disk, and at that time, all of the plurality of rollers are set to the inner teeth, with the curve outside the roller as one tooth among the curves parallel to the locus drawn by the center of the roller. I try to contact them.

JP 62-93565 A

  By the way, various parts such as an internal gear, an eccentric disk, a rolling bearing, and a roller forming a roller type reduction gear have manufacturing errors. Conventionally, various parts having these manufacturing errors are simply assembled and used as a roller. Since the speed reducer is assembled, the roller gap does not have a constant size, and a good product with a constant quality cannot be obtained.

  Here, the roller clearance refers to the roller 19 disposed on the eccentric disc displacement side of the rolling bearing 11 fitted to the outer periphery of the eccentric disc in FIG. It refers to a gap 20 formed between the roots 4a of the inner teeth 4 formed on the inner periphery of the gear 3.

  Conventionally, as described above, since the assembly does not manage the roller gap 20, the roller gap 20 of an appropriate size cannot be secured, and the roller gap 20 may be larger than necessary. . In this case, when the roller 19 once pulled out from the internal tooth 4 of the internal gear 3 enters the adjacent internal tooth 4, it collides with the tooth bottom 4 a of the internal tooth 4 and causes vibration.

Here, when the size of the roller gap 20 and [delta] _1, the [delta] ₁ can be expressed by the following equation (1).
δ ₁ = (A−B) −C Formula (1)
In the above formula (1),
A: tooth root circle radius of internal gear 3 B: circumscribed radius of rolling bearing 11 centering on the axis of the input shaft C: outer diameter of roller 19

  The inventors of the present case have verified the influence of the roller gap 20 formed between the roller 19 and the tooth bottom 4a of the internal gear 3 on the speed reducer, and have derived the following items.

Efficiency: Unevenness of rotation occurs due to excessive or small variation in roller clearance. Moreover, since the loss at the excessively small gap becomes excessive, the efficiency is lowered.
Life: When the roller passes through the excessively small gap, excessive surface pressure is generated at the contact portion between the roller and the inner diameter of the internal gear or between the roller and the outer ring of the rolling bearing, and early peeling occurs.
Vibration: The roller behavior becomes unstable at an excessive gap, and vibration is generated.

  Further, when the characteristic evaluation was performed with the roller gap 20 as an input characteristic value, the result shown in FIG. 6 was obtained. For this reason, optimization of the roller gap 20 is important.

  An object of the present invention is to suppress the vibration of the speed reducer and stabilize the quality by setting the roller gap to an optimum range.

In order to solve the above-described problems, in the present invention, a fixedly arranged internal gear and an eccentric disk that can rotate within the internal gear are provided at the shaft end, and a rolling bearing is provided on the outer diameter surface of the eccentric disk. Between the internal gear and the rolling bearing at the shaft end portion of the output shaft facing the input shaft. A pocket having a smaller number than the internal teeth formed on the inner periphery of the internal gear is provided at equal intervals in the circumferential direction at a portion of the cage that is opposed to the rolling bearing in the radial direction in the radial direction. Each of them accommodates a roller that meshes with the inner tooth, and the eccentric disk rotates in sequence with the inner tooth by the eccentric rotation of the eccentric disk, and moves in the circumferential direction by one tooth of the inner tooth per one rotation of the input shaft. deceleration device which is adapted to decelerate rotation of the output shaft by In standing method, root radius of the internal gear, the input shaft of the axial center previously measured outer diameter of the circumscribed circle radius and rollers of the rolling bearing around the circumscribed circle radius of the rolling bearing, the eccentric Based on the revolution radius of the rolling bearing in a state in which the rolling bearing is fitted to the outer diameter surface of the disc, the internal gear, the rolling bearing and the roller are selected and combined based on the measurement result. Thus, an assembly in which a roller gap is formed between the teeth of the roller and the internal gear is adopted.

  Here, the roller gap refers to the gap 20 shown in FIG. 5. If the size of the roller gap is in the range of 0 to 20 μm, as is apparent from the test results of various characteristics shown in FIG. It is possible to obtain a speed reducer that has little variation and high quality and long life.

In the assembling method of the speed reducer according to the present invention, there are two eccentric discs into which the rolling bearings are fitted, and the two eccentric discs are positioned at 180 ° in the circumferential direction at the center of the cylindrical outer diameter surface. The measurement operation is performed by measuring the revolution circle diameter of the outer ring outer diameter surface of each rolling bearing at the same time with the rolling bearing fitted to the two eccentric discs. Can be performed efficiently.

  By using a laser displacement meter or a capacitance displacement meter for measuring the root circle radius of the internal gear, it is possible to perform highly accurate measurement.

In the method of assembling the speed reducer according to the present invention, as described above, the root circle radius of the internal gear, the circumscribed circle radius of the rolling bearing around the axis of the input shaft and the outer diameter of the roller are measured in advance. The circumscribed radius of the rolling bearing is based on the revolution radius of the rolling bearing in a state in which the rolling bearing is fitted to the outer diameter surface of the eccentric disc, so that the outer diameter and rolling of the eccentric disc are reduced. There is no need to measure the inner ring inner diameter and the coaxiality of the bearing, the measurement work is easy, and the measurement can be performed with high accuracy. For this reason, it is possible to make an assembly in which a roller gap of a predetermined size is formed between the bottom of the roller and the internal gear by selecting and combining the dimensions of these three parts, suppressing the vibration of the reduction gear, and stabilizing the quality Can be achieved.

Longitudinal front view showing an embodiment of a reduction gear according to the present invention Sectional view along the line II-II in FIG. Sectional drawing which shows the measurement state of the circumscribed radius of a rolling bearing centering on the shaft center of an input shaft Graph showing the measurement results of the circumscribed circle radius of rolling bearings Sectional view showing the root circle radius of the internal gear, the circumscribed circle radius of the rolling bearing around the axis of the input shaft, and the outer diameter of the roller Graph showing verification results of roller clearance and various characteristics

  Embodiments of the present invention will be described below with reference to the drawings. As shown in FIG. 1, the housing 1 has a cylindrical shape. The housing 1 is divided into two in the axial direction, and a first divided housing 1a and a second divided housing 1b are provided.

  The first divided housing 1a and the second divided housing 1b are coupled and integrated by tightening bolts (not shown), and the inner surface of the abutting side end spans the first divided housing 1a and the second divided housing 1b. A large-diameter recess 2 is formed.

  As shown in FIGS. 1 and 2, an internal gear 3 is press-fitted into the large-diameter recess 2, and a plurality of internal teeth 4 are provided on the inner periphery of the internal gear 3.

  As shown in FIG. 1, an end plate 5 is provided at the open end of the first divided housing 1 a, and an input shaft 7 is inserted into a shaft insertion hole 6 formed in the center of the end plate 5. The input shaft 7 is rotatably supported by a bearing 8 incorporated in the shaft insertion hole 6, is arranged coaxially with the internal gear 3, and has an internal gear 3 at the end of the shaft located in the housing 1. Two eccentric discs 9 which can be rotated inside are provided at intervals in the axial direction.

The two eccentric discs 9 are mounted so that the center of the cylindrical outer diameter surface is shifted by 180 ° in the circumferential direction, and a rolling bearing 11 is press-fitted into the outer diameter surface 10. A ball bearing is adopted as the rolling bearing 11. Here, [delta] ₀ shown in FIG. 2 shows the amount of eccentricity of the center O ₁ of the cylindrical radially outer surface of the center O ₀ with eccentric disc 9 of the input shaft 7.

  As shown in FIG. 1, the output shaft 12 is inserted inside the second divided housing 1b. The output shaft 12 is rotatably supported by a bearing 13 incorporated in the opening end portion of the second divided housing 1b, and is arranged coaxially with the input shaft 7.

  A cage 14 is provided at the end of the output shaft 12 facing the input shaft 7, and the cage 14 is rotatable between the rolling bearing 11 on the eccentric disc 9 and the facing portion of the internal gear 3. The cage 14 has a closed end on the output shaft 12 side, and a bearing 17 that receives the shaft end of the input shaft 7 is incorporated in a small-diameter hole 16 formed in the center of the closed end surface 15.

  As shown in FIG. 1 and FIG. 2, the cage 14 is formed with a plurality of pockets 18 arranged in the circumferential direction at equal intervals in a double row, and the pockets 18 in each row are formed on each of the two eccentric disks 9. A plurality of pockets 18 in one row and a plurality of pockets 18 in the other row are offset from each other by a half pitch in the circumferential direction.

  The plurality of pockets 18 in each row is smaller than the number of teeth of the inner teeth 4 formed on the inner periphery of the internal gear 3, and one roller 19 is accommodated in each pocket 18 so as to be movable in the radial direction. .

  The roller 19 is capable of meshing with the internal teeth 4 of the internal gear 3, and the internal teeth 4 with which the rollers 19 mesh are curved tooth shapes that allow the plurality of rollers 19 arranged in the circumferential direction to simultaneously contact each other. It is said that. In order to allow all the rollers 19 to be in contact with each other, as described in the above-mentioned Patent Document 1, the eccentric disk 9 has a rotational angle of the output shaft 12 within a range corresponding to one pitch of the internal teeth 4 of the internal gear 3. The rotation of the output shaft 12 rotates, and at this time, of the curves parallel to the trajectory drawn by the center of the roller 19, the tooth profile is defined as one tooth corresponding to the curve outside the roller 19.

The speed reducer shown in the embodiment has the above-described configuration. When the speed reducer is assembled, the outer ring 11a of the rolling bearing 11 centering on the root circle radius A of the internal gear 3 and the axis of the input shaft shown in FIG. Of the roller 19 and the outer diameter C of the roller 19 are respectively measured, and the size δ _{1 of the} roller gap 20 formed between the roller 19 and the tooth bottom of the internal gear 3 by matching by selecting and combining the dimensions of these three parts. However, the size δ ₁ of the roller gap 20 is managed so that it becomes 0 to 20 μm.

  Here, when measuring the circumscribed radius B of the outer ring 11a of the rolling bearing 11 around the axis of the input shaft 7, a gauge outer ring (not shown) having the same diameter as the rolling bearing 11 is prepared in advance. The contact 31 of the dial gauge 30 is pressed against the perfect circular outer diameter surface formed on the outer periphery of the gauge outer ring, the pointer is shaken, and the deflection amount of the pointer is stored.

  Thereafter, as shown in FIG. 3, with the first divided housing 1a and the internal gear 3 removed, the contact 31 of the dial gauge 30 is inserted into the pocket 18, and the contact 31 is inserted into the outer ring 11a of the rolling bearing 11. The input shaft 7 is rotated once in a state in which the input shaft 7 is pressed against the outer diameter surface of the needle and the shake amount of the pointer is made to coincide with the stored shake amount.

  As a result of the measurement, as indicated by the graph of FIG. 4, the dial gauge 30 is detected as a sine curve by adding a value (2δ) that is twice the eccentric amount δ of the eccentric disk 9. By adding the amplitude W to the radius of the cage outer ring, the circumscribed radius B of the outer ring 11a in the rolling bearing 11 can be known.

  In this way, by directly measuring the outer diameter surface of the outer ring 11a of the rolling bearing 11 with the rolling bearing 11 fitted to the outer diameter surface of the eccentric disc 9, the outer diameter and rolling of the eccentric disc 9 are measured. It is not necessary to measure the inner ring inner diameter and the coaxiality of the bearing 11, and the measurement work is easy, and the measurement can be performed with high accuracy. In addition, since it can be measured in the assembly line of the speed reducer, no significant line change is required.

  Here, when measuring the root circle radius of the internal gear, it is measured using a laser displacement meter or a capacitance displacement meter.

  FIG. 1 shows a reduction gear assembled by matching with a selected combination of dimensions of three parts. When the input shaft 7 in the speed reduction device is rotated, the roller 19 is sequentially meshed with the internal teeth 4 of the internal gear 3 by the rotation of the eccentric disk 9, and the roller 19 is one of the internal teeth 4 per one rotation of the input shaft 7. It moves in the circumferential direction by the amount of teeth, and the output shaft 12 rotates at a reduced speed.

At this time, the magnitude [delta] ₁ of the roller gap 20 formed between the tooth bottom of the internal gear 3 and the roller 19, so as to be 0～20Myuemu, since the roller gap 20 is managed, the roller 19 is an internal gear There is no collision with 3 and no vibration is generated.

  It is possible to suppress the occurrence of rotation unevenness due to excessive or small variations in the roller gap 20 or excessive loss in the excessive gap portion, and there is no inconvenience that the efficiency is lowered.

When the roller 19 passes through the undergap portion, an excessive surface pressure is generated at the contact portion between the roller 19 and the inner diameter of the internal gear or between the roller 19 and the outer ring 11a of the rolling bearing 11 to cause early peeling. By causing the size δ ₁ to be in the range of 0 to 20 μm, such inconvenience does not occur.

DESCRIPTION OF SYMBOLS 1 Housing 3 Internal gear 4 Internal tooth 7 Input shaft 9 Eccentric disk 12 Output shaft 14 Cage 18 Pocket 19 Roller 20 Roller clearance

Claims (4)

An input shaft having a fixedly arranged internal gear, an eccentric disc rotatable in the internal gear at the shaft end, a rolling bearing fitted to the outer diameter surface of the eccentric disc, and the input shaft An output shaft arranged on the same axis, and a cage rotatable between the internal gear and the rolling bearing is provided at a shaft end portion of the output shaft facing the input shaft, and the rolling of the cage Pockets that are smaller in number than the inner teeth formed on the inner periphery of the internal gear are provided at equal intervals in the circumferential direction at locations that face the bearing in the radial direction, and rollers that mesh with the inner teeth are accommodated inside the pockets. The decelerator rotates the output shaft at a reduced speed by sequentially engaging the rollers with the inner teeth by the eccentric rotation of the eccentric disk and moving the rollers in the circumferential direction by one inner tooth per rotation of the input shaft. In the device
Preliminarily measure the root radius of the inner gear, the circumscribed circle radius of the rolling bearing centered on the axis of the input shaft, and the outer diameter of the roller, and a roller gap formed between the bottom of the roller and the inner gear. The speed reducer is controlled in the range of 0 to 20 μm.   Two eccentric discs to which the rolling bearings are fitted are provided, and the two eccentric discs are provided in the axial direction so that the center of the cylindrical outer diameter surface is displaced by 180 ° in the circumferential direction, The reduction gear according to claim 1, wherein the revolution circle diameter of the outer ring outer diameter surface of each rolling bearing is simultaneously measured in a state in which the rolling bearing is fitted to the two eccentric disks.   The reduction gear according to claim 1 or 2, wherein the measurement of the root circle radius of the internal gear is performed by a laser displacement meter.   The speed reducer according to claim 1 or 2, wherein the measurement of the root circle radius of the internal gear is performed by a capacitance displacement meter.

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