JP5283591B2 - Series of simple planetary gear reducers - Google Patents

Description

  The present invention relates to a series of simple planetary gear reducers.

  A sun gear, a planet gear that meshes with the sun gear, an internal gear that meshes with the planet gear, a planet pin that rotatably supports the planet gear, and a planet pin that supports the planet pin and supports the planet gear. In a series of simple planetary gear speed reducers having different reduction ratios and having a carrier body synchronized with a revolution component, for example, in Patent Document 1, an internal gear is used as a common part in the series.

JP 2007-64365 A

  However, when the internal gear integrally formed in the casing is used as a common part, if the reduction gear ratio determined by the number of teeth of the sun gear and the internal gear becomes small (reduction speed ratio), the sun gear becomes large and the planetary gear. Therefore, the support position of the planetary pin in the carrier body becomes far from the center of rotation of the carrier body. That is, at the reduction speed ratio, the radius of a circle (hereinafter referred to as a pitch circle) connecting the centers of the planet pins in the circumferential direction of the carrier body is increased, so that the planet pin support position approaches the internal gear. Become.

  When the main bearing for supporting the carrier body is arranged outside the planetary pin as shown in Patent Document 1, it is necessary to ensure a certain thickness of the portion of the carrier body between the planetary pin and the main bearing. The planetary pin diameter is limited by the inner ring inner diameter of the main bearing. Due to the limitation on the size of the planetary pin diameter, the size of the planetary bearing disposed between the planetary pin and the planetary gear is also limited. Therefore, in the series of simple planetary gear reducers, when trying to share parts such as internal gears between reducers with different reduction ratios, the magnitude of the output torque is limited. Further, if the planetary pin diameter is increased in order to ensure the output torque, the speed reducer itself is increased in size.

  Therefore, the present invention has been made to solve the above-mentioned problems, and can improve output torque without increasing the size of the reduction gear itself that constitutes the series while sharing parts such as internal gears. It is an object to provide a series of possible simple planetary gear reducers.

The present invention provides a sun gear, a planet gear that meshes with the sun gear, an internal gear that meshes with the planet gear, a planet pin that rotatably supports the planet gear, and a planet pin that supports the planet pin. A series of simple planetary gear reducers having different reduction ratios, the carrier body being synchronized with the revolution component of the planetary gear, and supporting the carrier body outside the support position of the planetary pin in the radial direction of the carrier body. The inner ring of the main bearing is formed integrally with the carrier body, the casing in which the internal gear is formed is common, and the sun gear, the planetary gear, and the carrier body the supporting position of the planetary pins have a first subseries to be changed in accordance with the reduction ratio, further, the carrier body in the radial direction of the carrier body outside the supporting position of the planetary pins The main bearing is supported, the inner ring of the main bearing is formed integrally with the carrier body, the casing is changed according to the reduction ratio, and the supporting position of the planetary pin is made common. by have a second subseries of the carrier body is common, it is obtained by solving the above problems.
Alternatively, the present invention provides a sun gear, a planet gear that meshes with the sun gear, an internal gear that meshes with the planet gear, a planet pin that rotatably supports the planet gear, and the planet pin. And a carrier body synchronized with the revolution component of the planetary gear, and a series of simple planetary gear reducers with different reduction ratios, wherein the carrier body is positioned outside the planet pin support position in the radial direction of the carrier body. A casing in which the inner ring is formed integrally with the carrier body, the inner gear is formed, and the sun gear, the planetary gear, and the carrier. An inner ring corresponding to a type of the main bearing having a first sub-series in which a support position of the planetary pin in the body is changed according to the reduction ratio, and a plurality of types of the main bearings being employable The integrally formed carrier body is used, and the outer ring of the main bearing has a separate structure from the casing, so that the casing is common regardless of the type of the main bearing. It has been solved.

  The series of simple planetary gear speed reducers of the present invention is such that a main bearing is provided outside the support position of the planetary pin in the radial direction of the carrier body, and the inner ring of the main bearing is formed integrally with the carrier body. For this reason, the main bearing can be maximized, and even in the case of a reduced speed ratio, the planetary pin diameter can be increased while ensuring the thickness of the carrier body portion between the planetary pin and the main bearing. it can. For this reason, the planetary bearing arrange | positioned between a planetary gear and a planetary pin as a result can also be enlarged. Therefore, the output torque can be improved without increasing the size of the speed reducer itself. At the same time, since the inner ring of the main bearing is not a separate member, the number of parts can be reduced. Moreover, since the casing in which the internal gear is formed is used as the first subseries, the total number of parts, the total inventory amount, and the part cost can be reduced in the series.

  According to the present invention, it is possible to improve the output torque without increasing the size of the speed reducer while sharing parts such as an internal gear.

1 is a schematic cross-sectional view of a first subseries simple planetary gear reducer according to a first embodiment of the present invention. Similarly, a schematic sectional view of another simple planetary gear reducer in the first subseries. Schematic sectional view of a second subseries simple planetary gear reducer according to a second embodiment of the present invention. Schematic sectional view of a first subseries simple planetary gear reducer according to a third embodiment of the present invention. Similarly, a schematic sectional view of another simple planetary gear reducer in the first subseries.

  Hereinafter, an example of an embodiment of the present invention will be described in detail with reference to the drawings.

  The series of simple planetary gear reducers according to the present invention is composed of simple planetary gear reducers having different reduction ratios as shown in the background art.

  In the first embodiment of the present invention, an example of a first subseries in a series of simple planetary gear reducers will be described with reference to FIGS. 1 and 2. In the first sub-series simple planetary gear reducer 100 (200), a bearing that supports the carrier body 124 (224) outside the support position of the planetary pin 120 (220) in the radial direction of the carrier body 124 (224) ( Main bearings) 134, 138 (234, 238), and inner rings of the bearings 134, 138 (234, 238) are formed integrally with the carrier body 124 (224), and an internal gear is formed in the casing 142 (242). 122 (222) is formed integrally (as a modification of the present embodiment, an internal gear may be formed separately in the casing). In the first subseries, the casing 142 is shared with the casing 242, and the planetary pin 120 (220) is supported by the sun gear 114 (214), the planetary gear 116 (216), and the carrier body 124 (224). The position is changed according to the reduction ratio.

  Here, the simple planetary gear speed reducers 100 and 200 shown in FIGS. 1 and 2 are functionally different only in reduction ratios of about 1/4 and about 1/10, respectively. The gear reducer 100 will be described in detail.

  The simple planetary gear reducer 100 supports a sun gear 114, a planetary gear 116 that meshes with the sun gear 114, an internal gear 122 that meshes with the planetary gear 116, and the planetary gear 116 rotatably. A planetary pin 120 and a carrier body 124 that supports the planetary pin 120 and synchronizes with the revolution component of the planetary gear 116 are provided. The casing 142 rotatably supports the carrier body 124 via bearings 134 and 138.

  The sun gear 114 is press-fitted into the input shaft 110. The input shaft 110 has an insertion hole 110A into which a motor shaft (not shown) is inserted. The motor shaft is inserted into the insertion hole 110A, and the input shaft 110 and the motor shaft are coupled. The sun gear 114 is provided with, for example, a helical gear (may be a spur tooth) and meshes with the planetary gear 116.

  A plurality of the planetary gears 116 are arranged on the outer periphery of the sun gear 114 and revolve while rotating around the sun gear 114. The planetary gear 116 is supported on the planetary pin 120 via the planetary bearing 118. In the planetary bearing 118, the needle is divided into two in the axial direction O and arranged in a full roller state. For this reason, when the sun gear 114 and the planetary gear 116 mesh with each other, it is possible to reduce the needle contact per side. In addition, since the needle is used in a full roller state without a cage, a large torque can be transmitted to the planetary pin 120.

  The internal gear 122 is integrally formed with the casing 142 including a tooth profile that meshes with the planetary gear 116.

  The planetary pin 120 is supported by the carrier body 124. The planetary pin 120 is formed separately from the carrier body 124. For this reason, since the planetary pin 120 can be processed with high surface accuracy (shape, roughness, etc.), the life of the planetary bearing 118 can be extended, and the torque cross in the planetary gear 116 can be reduced.

  The carrier body 124 is configured by connecting a carrier body main body 126 and a carrier body plate 128. The carrier body main body 126 is fastened and fixed to the carrier body plate 128 by bolts 130. For this reason, the carrier body 124 rotates by taking out the revolution component by the planetary pin 120 in synchronization with the revolution component of the planetary gear 116. The carrier body 124 is formed with press-fitting holes 126B and 128B into which the planetary pin 120 is press-fitted. The positions where the press-fitting holes 126B and 128B are formed are changed according to the reduction ratio. A flange-shaped output shaft 132 is integrally provided on the side of the carrier body 126 opposite to the planetary gear. The end face is provided with a plurality of bolt holes, and a driven shaft of the counterpart machine is connected by connecting a bolt (not shown) to the bolt hole of the output shaft 132.

  The bearings 134 and 138 are arranged as main bearings on the outer side in the radial direction of the carrier body 124 to support the carrier body 124 in a rotatable manner. The bearings 134 and 138 are angular ball bearings, and include balls 135 and 139 and outer rings 136 and 140, respectively, and these inner rings are formed integrally with the carrier body 124. For this reason, compared with the case where the inner ring is provided separately from the carrier body, the portions 126A and 128A of the carrier body 124 between the planetary pin 120 and the bearings 134 and 138 without increasing the outer shape of the casing 142. It is possible to increase the diameter of the planetary pin 120 while ensuring the thickness.

  The bearings 134 and 138 are disposed in the axial direction O with the internal gear 122 interposed therebetween. And the bearings 134 and 138 are arrange | positioned by the back surface combination. For this reason, a high radial load and an axial load can be supported. The outer rings 136 and 140 of the bearings 134 and 138 have a separate structure from the casing 142. For this reason, the casing 142 can be used in common in the first subseries even if the bearings 134 and 138 are different. Inner ring raceway surfaces of the bearings 134 and 138 are formed on the outer peripheral surfaces 127 and 129 of the carrier body 124.

  The outer periphery 142 </ b> A of the casing 142 functions as a stamping portion E that is a reference for mounting by fitting with a connection casing (not shown) of the counterpart machine. An intermediate cover 144 and a front cover 146 are connected to the casing 142 with bolts 148 in the axial direction O. An oil seal 152 is provided between the middle cover 144 and the input shaft 110. A bearing 112 is disposed inside the middle cover 144, and the middle cover 144 rotatably supports the input shaft 110 via the bearing 112. The bearing 112 is sandwiched and fixed between the middle cover 144 and the front cover 146 in the axial direction O. 1 is an oil seal disposed between the casing 142 and the output shaft 132 in order to seal the inside and outside of the simple planetary gear reducer 100.

  Next, the operation of the simple planetary gear reducer 100 will be described.

  For example, the sun gear 114 rotates through the input shaft 110 by the rotation of a motor (not shown). Then, the sun gear 114 and the planetary gear 116 mesh with each other, and the planetary gear 116 revolves around the sun gear 114 while rotating. At this time, since the internal gear 122 that is in mesh with the planetary gear 116 is in a fixed state, the revolution component of the planetary gear 116 is taken out from the carrier body 124. The carrier body 124 rotates the driven shaft of the counterpart machine attached to the output shaft 132.

  Here, the simple planetary gear reducer 200 shown in FIG. 2 also operates in the same manner as the simple planetary gear reducer 100 of FIG. However, the reduction ratio of the simple planetary gear reducer 100 is about 1/4, whereas the reduction ratio of the simple planetary gear reducer 200 is about 1/10. For this reason, the number of teeth of the sun gear 214 is smaller than the number of teeth of the sun gear 114, and the number of teeth of the planetary gear 216 is larger than the number of teeth of the planetary gear 116 (in terms of the magnitude relationship, the sun gear 114 has The sun gear 214 is smaller than the planetary gear and the planetary gear 216 is larger than the planetary gear. In the first subseries, since the casings 142 and 242 are common, the radii R1 and R2 of the respective circles (pitch circles) connecting the center positions of the planetary pins 120 and 220 are not equal (R1> R2), The body 124 is also different from the carrier body 224. Specifically, the formation positions (pitch diameters of the press-fit holes) of the press-fit holes 126B (128B) and 226B (228B) of the planetary pins 120 and 220 are different. That is, according to the reduction ratio, for example, when the reduction ratio is changed from about 1/4 to about 1/10, the sun gear 114, the planetary gear 116, and the carrier body 124 of the simple planetary gear reducer 100 are The gear 214, the planetary gear 216, and the carrier body 224 are changed. In the present embodiment, the planetary pins 120 and 220 are also common. However, as a modification of the present embodiment, the planetary pins may not be common.

  In this embodiment, bearings 134 and 138 (234 and 238) are provided outside the support position of the planetary pin 120 (2220) in the radial direction of the carrier body 124 (224), and inner rings of the bearings 134, 138, 234, and 238 are provided. Are integrally formed with the carrier bodies 124 and 224. Therefore, the bearings 134 and 138 (234 and 238) can be maximized. For example, even when the simple planetary gear reducer 100 has a reduction speed ratio of about 1/4, the carrier body that supports the planetary pin 120. The diameter of the planetary pin 120 can be increased while ensuring the thickness of the portions 126A and 128A of 124. Therefore, as a result, the planetary bearing 118 disposed between the planetary gear 116 and the planetary pin 120 can be enlarged. Therefore, the output torque can be improved without increasing the size of the speed reducer itself. In particular, in this embodiment, the planetary pin 120 (220) is separated from the carrier body 124 (224), so that the life of the planetary bearing 118 can be extended. At the same time, since the inner rings of the bearings 134 and 138 (234 and 238) are not separate members, the number of parts can be reduced. In addition, since the casing 142 (242) in which the internal gear 122 (222) is integrally formed is used as the first subseries, the total number of parts in the series, the total inventory amount, and the parts cost are reduced. Reduction can be achieved.

  In this embodiment, two bearings 134, 138 (234, 238) are used in the axial direction O with the internal gear 122 (222) interposed therebetween, and the bearings 134, 138 (234, 238) are combined on the back side. ing. For this reason, a high radial load and an axial load can be supported.

  Further, in this embodiment, since the casing 142 (242) is common, the portion connected to the counterpart machine, that is, the outer periphery 142A of the casing 142 has the same shape. Replacement within the series of simple planetary gear speed reducers is easy according to the rotational speed, and the outer periphery 142A of the casing 142 functions as the stamping part E at the time of replacement.

  Therefore, according to the present embodiment, it is possible to improve the output torque without increasing the size of the speed reducer while using the internal gears 122 and 222 in common.

  Next, in the second embodiment of the present invention, an example of the second subseries in the series of simple planetary gear reducers will be described with reference to FIGS. 1 and 3.

  In this embodiment, the simple planetary gear reducer 100 constitutes the second subseries with the simple planetary gear reducer 300. That is, in the second subseries, the simple planetary gear reducer 100 (300) places the carrier body 124 (324) outside the support position of the planetary pin 120 (320) in the radial direction of the carrier body 124 (324). The bearings 134 and 138 (334 and 338) to be supported are provided, the inner rings of the bearings 134 and 138 (334 and 338) are integrally formed with the carrier body 124 (324), and the internal gears are formed in the casing 142 (342). 122 (322) is integrally formed (as a modification of the present embodiment, an internal gear may be formed separately in the casing). In the second subseries, the carrier body 124 and the carrier body 324 are shared by changing the casing 142 (342) according to the reduction ratio and by making the supporting positions of the planetary pins 120 and 320 common. It is characterized by being.

  Here, the simple planetary gear speed reducers 100 and 300 shown in FIGS. 1 and 3 are functionally different only in reduction ratios of about 1/4 and about 1/3, respectively. For this reason, description of the component and the effect | action about the simple planetary gear reducers 100 and 300 is abbreviate | omitted.

  The simple planetary gear reducer 300 has a reduction ratio of about 1/3, and is a reduction speed ratio that is further lower than the reduction ratio of the simple planetary gear reducer 100. Here, when the casing 342 is shared with the casing 142, the radius R3 of the pitch circle is larger than the radius R1 of the pitch circle, and the thickness of the portion of the carrier body between the planetary pin and the main bearing is increased. There is a risk that the thickness and the thickness of the planetary pin cannot be secured sufficiently. Therefore, the simple planetary gear speed reducer 300 has the same pitch circle radius as that of the simple planetary gear speed reducer 100 in order to sufficiently secure the thickness of the carrier body portion between the planetary pin and the main bearing and the thickness of the planetary pin. (R1 = R3). Thereby, the support positions of the planetary pins 120 and 320 are made common, and the carrier body 324 can be made common with the carrier body 124. In the second subseries, the planetary pins 120 and 320 are common.

  That is, in the second subseries, the simple planetary gear speed reducer 100 (300) having the feature that the output torque can be increased as in the first subseries, the carrier body 124 and the carrier body, not the internal gear 122 (322). By using 324 in common, the number of parts can be reduced and cost reduction can be realized.

  At the same time, although the casing 142 (342) is not common, the radius of the pitch circle is common (R1 = R3), so that the outer shape of the casing 342 can be the same as the outer shape of the casing 142. That is, the portion where the casing 342 is connected to the counterpart machine, that is, the outer circumference 342A of the casing 342 has the same shape as the outer circumference 142A, and therefore, within the series exceeding the second subseries according to the reduction ratio required by the counterpart machine. It is easy to replace the simple planetary gear reducer at, and the outer periphery 342A of the casing 342 functions as the stamping part E at the time of replacement. That is, the second subseries has connection compatibility with the first subseries for the same counterpart machine.

  Further, the bearings 134 and 138 are the same as the bearings 334 and 338, and the portions 142B and 142C of the casing 142 that support the bearings 134 and 138 are equivalent to the portions 342B and 342C of the corresponding casing 342. It can be a thickness. For this reason, even if the casing 142 (342) is not common, an equivalent output torque can be ensured for the simple planetary gear reducer in the series beyond the second subseries.

  And, by constructing a series of simple planetary gear reducers with the first and second subseries, it is possible to cover a wider range of reduction ratios than with only the first subseries, and for the same counterpart machine Thus, the first and second subseries can be made to correspond seamlessly according to the reduction ratio.

  Next, in the third embodiment of the present invention, another example of the first subseries in the series of simple planetary gear reducers will be described with reference to FIGS. 4 and 5.

  In this embodiment, the angular ball bearings of the bearings 134 and 138 (234 and 238) of the simple planetary gear reducer 100 (200) of the first embodiment are changed to angular roller bearings. Accordingly, the rollers of the bearings 434, 438 (534, 538) and the inner rings corresponding to the outer rings 436, 440 (536, 540) and the bearings 434, 438 (534, 538) are integrally formed (the inner ring raceway surface is formed. Since the carrier body 424 (524) is the same as in the first embodiment except that the carrier body 424 (524) is different, the same reference numerals are given to the last two digits, and the description is omitted.

  In this embodiment, since the main bearing uses rollers instead of balls, the load resistance of the main bearing can be increased. For this reason, compared with the 1st subseries of 1st Embodiment excellent in the low torque loss characteristic, the load resistance of the simple planetary gear speed reducers 400 and 500 can be further increased, and the durability can be increased. Here, since the outer rings 436, 440 (536, 540) of the bearings 434, 438 (534, 538) are separated from the casing 442 (542), the casing 442 (542) can be easily used in common. The type of bearing can be changed. That is, in the first subseries of simple planetary gear speed reducers, an angular ball bearing and an angular roller bearing can be adopted as the main bearing. At that time, the outer ring of the main bearing has a separate structure from the casing, so that it is possible to change the output torque or the output torque without changing anything other than the carrier body that integrally forms the inner ring corresponding to the type of the main bearing and the main bearing. It becomes possible to provide a simple planetary gear reducer according to the demand for durability. Even if this embodiment is applied to the second sub-series, if the main bearings are the same, the carrier body can be made common, and corresponding effects can be obtained.

  Although the present invention has been described with reference to the above embodiment, the present invention is not limited to the above embodiment. That is, it goes without saying that improvements and design changes can be made without departing from the scope of the present invention.

  For example, in the above embodiment, the output shaft has a flange shape, but the present invention is not limited to this, and the shape of the output shaft can be easily changed based on the shape of the driven shaft of the counterpart machine. It is. For example, a cylindrical output shaft may be provided on the carrier body and connected to the driven shaft of the counterpart machine via a keyway. In addition, the change of the output shaft to such a so-called solid type (the above embodiments are all referred to as a flange type) is a component (the carrier body and the output shaft, or the components constituting the output shaft without impairing the effects of the present invention). This can be easily done only by changing the output shaft). In other words, since components other than those constituting the output shaft can be shared, it is possible to reduce the cost of a simple planetary gear reducer having a flange type or solid type output shaft and to expand the variation of the output shaft in the series. .

  Moreover, in the said embodiment, although two bearings were used by the back surface combination, this invention is not necessarily limited to this, The case where one bearing is used may be sufficient. For example, only one cross roller bearing may be arranged and used, and the outer ring may be configured as a separate structure from the casing. Also in this case, it is possible to handle the axial load in both directions in the axial direction O of the driven shaft of the counterpart machine, obtain the same effect as when two bearings are used, and a simple planetary gear reducer. Can be shortened to the axial direction O.

  Moreover, even if it is a case where two bearings are used, a taper roller bearing may be used and the combination is not limited to a back surface, A front combination and a parallel combination may be sufficient.

  In the above embodiment, the planetary pin is separated from the carrier body, but the present invention is not limited to this. For example, the planetary pin may be formed integrally with the carrier body. In the first subseries in this case, carrier bodies having different planet pin formation positions are prepared according to the reduction ratio. In the second subseries, the carrier body integrally formed with the planetary pin can be used as it is.

  In the above embodiment, the reduction ratios of about 1/3, about 1/4, and about 1/10 have been described. However, the present invention is not limited to these reduction ratios.

  In the above embodiment, the casing is fixed and the carrier body is provided with the output shaft, but the present invention is not necessarily limited thereto, and the carrier body is fixed and the casing rotates to obtain an output. A so-called frame rotation type may be used.

  In the first subseries, different portions in the carrier body according to the reduction ratio may occur not only in the planet pin support position but also in other portions.

100, 200, 300, 400, 500 ... simple planetary gear reducer 110, 210, 310, 410, 510 ... input shaft 112, 134, 138, 212, 234, 238, 312, 334, 338, 412, 434, 438 512, 534, 538 ... bearings 114, 214, 314, 414, 514 ... sun gears 116, 216, 316, 416, 516 ... planetary gears 118, 218, 318, 418, 518 ... planetary bearings 120, 220, 320, 420, 520 ... Planetary pins 122, 222, 322, 422, 522 ... Internal gears 124, 224, 324, 424, 524 ... Carrier bodies 126, 226, 326, 426, 526 ... Carrier body bodies 128, 228, 328, 428, 528 ... Carrier body plate 130, 148, 230, 24 , 330, 348, 430, 448, 530, 548 ... bolt 132, 232, 332, 432, 532 ... output shaft 136, 140, 236, 240, 336, 340, 436, 440, 536, 540 ... outer ring 142, 242 , 342, 442, 542 ... casing 144, 244, 344, 444, 544 ... middle cover 146, 246, 346, 546 ... front cover

Claims (5)

A sun gear, a planet gear that meshes with the sun gear, an internal gear that meshes with the planet gear, a planet pin that rotatably supports the planet gear, and a planet pin that supports the planet pin and supports the planet gear. In a series of simple planetary gear reducers with different reduction ratios, with a carrier body synchronized with the revolution component,
A main bearing for supporting the carrier body outside the support position of the planetary pin in the radial direction of the carrier body;
An inner ring of the main bearing is formed integrally with the carrier body;
The casing in which the internal gear is formed is common, and
The support position of the planetary pin in the sun gear, the planetary gear, and the carrier body is changed according to the reduction ratio.
A first subseries , and
The main bearing for supporting the carrier body outside the support position of the planetary pin in the radial direction of the carrier body;
An inner ring of the main bearing is formed integrally with the carrier body;
The casing is changed according to the reduction ratio, and
A series of simple planetary gear reducers, characterized by having a second sub-series in which the carrier body is made common by making the supporting position of the planetary pin common. In claim 1 ,
In the first subseries and the second subseries, the casing has the same shape in a portion connected to a counterpart machine. A series of simple planetary gear reducers, wherein:   In claim 1 or 2,
  A plurality of types can be adopted as the main bearing, a carrier body in which an inner ring corresponding to the type of the main bearing is integrally formed is used, and the outer ring of the main bearing has a separate structure from the casing. Therefore, the casing is common regardless of the type of the main bearing.
  A series of simple planetary gear speed reducers. A sun gear, a planet gear that meshes with the sun gear, an internal gear that meshes with the planet gear, a planet pin that rotatably supports the planet gear, and a planet pin that supports the planet pin and supports the planet gear. In a series of simple planetary gear reducers with different reduction ratios, with a carrier body synchronized with the revolution component,
A main bearing for supporting the carrier body outside the support position of the planetary pin in the radial direction of the carrier body;
An inner ring of the main bearing is formed integrally with the carrier body;
The casing in which the internal gear is formed is common, and
The support position of the planetary pin in the sun gear, the planetary gear, and the carrier body is changed according to the reduction ratio.
Having a first subseries,
A plurality of types can be adopted as the main bearing, a carrier body in which an inner ring corresponding to the type of the main bearing is integrally formed is used, and the outer ring of the main bearing has a separate structure from the casing. Thus, the series of simple planetary gear reducers is characterized in that the casing is common regardless of the type of the main bearing. In any one of Claims 1 thru | or 4,
A series of simple planetary gear reducers, wherein a plurality of the main bearings are used in the axial direction with the internal gear interposed therebetween, and the main bearings are combined in the back.

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