KR20110025136A - Series of simple planetary gear reducer - Google Patents

Abstract

PURPOSE: A series of simple planetary gear reducer is provided to improve the output torque by sharing the inner gears. CONSTITUTION: An internal gear(122) contacts and fits to the planetary gear. The oil fin(120) supports the planetary gear to rotate. A carrier body(124) supports the oil fin. Bearings(134, 138) support the carrier body on the outside of the holding position of the oil fin. The inner ring of the bearing is formed as one body with the carrier body(124).

Description

Series of simple planetary gear reducer

This invention claims priority based on Japanese Patent Application No. 2009-203783 for which it applied on September 3, 2009. The entire contents of that application are incorporated by reference in this specification.

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

A sun gear, a planetary gear meshing with the sun gear, an internal gear meshed by the planetary gear, an planetary pin that rotationally supports the planetary gear, and an orbital component of the planetary gear supporting the planetary pin The series of simple planetary gear reducers with different reduction ratios, including a carrier body synchronous with the above, is, for example, in the patent literature, the internal gear is a common part in the series.

Japanese Unexamined Patent Publication No. 2007-64365

However, when the internal gear formed integrally with the casing is used as a common part, the reduction gear ratio determined by the number of teeth of the sun gear and the internal gear becomes small (low reduction ratio), so that the sun gear becomes larger and the planetary gear becomes smaller. The support position of the pin is away from the center of rotation of the carrier body. That is, in the reduction ratio, since the radius of the circle connecting the center of the planetary pin in the circumferential direction of the carrier body (hereinafter referred to as a "pitch circle") becomes large, the support position of the planetary pin approaches the internal gear.

When the main bearing which supports a carrier body is arrange | positioned on the outer side of a planetary pin as shown in patent document 1, since the thickness of the part of the carrier body between a planetary pin and a main bearing needs to be ensured to some extent, The diameter of the planetary pin is limited by the inner diameter of the bearing. By limiting 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 the components such as internal gears are to be commonized between reducers having different reduction ratios, the magnitude of the output torque is limited. In addition, when the planetary pin diameter is increased to secure the output torque, the reduction gear itself becomes large.

Accordingly, the present invention has been made to solve the above problems, and provides a series of simple planetary gear reducers capable of improving output torque without increasing the speed reducer itself constituting the series while making common parts such as internal gears. Let's make it a task.

The present invention relates to a sun gear, a planetary gear meshed with the sun gear, an internal gear meshed with the planetary gear, an planetary pin that rotatably supports the planetary gear, and a planetary pin that supports the planetary gear so as to rotate. In a series of simple planetary gear reducers having different reduction ratios, the main bearing supporting the carrier body outside the support position of the planetary pin in the radial direction of the carrier body, having a carrier body synchronized with the idle component of the gear. The inner ring of the main bearing is integrally formed with the carrier body, and the casing on which the internal gear is formed is common, and the sun gear, the planetary gear, and the planetary pin in the carrier body. This problem is solved by having the 1st sub-series whose support position changes with the said reduction ratio.

In the series of the simple planetary gear reducer of the present invention, the 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. As a result, the main bearing can be made as large as possible, and even in the case of the reduction ratio, the diameter of the planetary pin can be made thick while securing the thickness of the portion of the carrier body between the planetary pin and the main bearing. As a result, the planetary bearing disposed between the planetary gear and the planetary pin can be enlarged as a result. Therefore, the output torque can be improved without increasing 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 common as the first sub-series, the total number of parts in the series, the total amount of inventory and the cost of parts are reduced.

According to the present invention, it is possible to improve the output torque without increasing the speed reducer itself while making components such as internal gears common.

1 is a schematic cross-sectional view of a simple planetary gear reducer of the first sub-series according to the first embodiment of the present invention.
2 is a schematic cross-sectional view of another simple planetary gear reducer of the first sub-series as well.
3 is a schematic cross-sectional view of a simple planetary gear reducer of a second sub-series according to a second embodiment of the present invention.
4 is a schematic cross-sectional view of a simple planetary gear reducer of the first sub-series according to the third embodiment of the present invention.
5 is a schematic cross-sectional view of another simple planetary gear reducer of the first sub-series as well.

EMBODIMENT OF THE INVENTION Hereinafter, an example of embodiment of this invention is described in detail, referring drawings.

The series of simple planetary gear reducers according to the present invention is constituted by 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 the first sub-series of the series of the simple planetary gear reducer will be described with reference to FIGS. 1 and 2. In the simple planetary gear reducer 100 (200) of the first sub-series, the carrier body 124 (outside the support position of the planetary pins 120 (220) in the radial direction of the carrier body 124 (224). 224) bearings (main bearings) 134, 138 (234, 238), and the inner ring of the bearings 134, 138 (234, 238) and its carrier body 124 (224). The internal gear 122 (222) is integrally formed on the casing 142 (242) (the internal gear may be formed separately from the casing as a modification of the present embodiment). ). In the first sub-series, the casing 142 becomes common with the casing 242 and further includes the sun gear 114 (214), the planetary gear 116 (216), and the carrier body 124 (224). It is characterized in that the supporting position of the planetary pins 120 (220) in accordance with the reduction ratio.

Here, the simple planetary gear reducers 100 and 200 illustrated in FIGS. 1 and 2 have only a reduction ratio of about 1/4 and about 1/10, respectively, so that the simple planetary gear reducer 100 of FIG. ) Will be described in detail.

The simple planetary gear reducer 100 includes a sun gear 114, a planetary gear 116 meshing with the sun gear 114, an internal gear 122 meshed with the planetary gear 116, and A planetary pin 120 for rotatably supporting the planetary gear 116 and a carrier body 124 for supporting the planetary pin 120 and synchronous with an idle component of the planetary gear 116 are provided. However, the casing 142 rotatably supports the carrier body 124 via the bearings 134 and 138.

The sun gear 114 is pressed 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 is coupled to the motor shaft. The sun gear 114 is provided with, for example, a helical gear (may be a flat gear), and meshes with the planetary gear 116.

The planetary gear 116 is disposed on the outer periphery of the sun gear 114, the plurality of planetary gears rotating around the sun gear (114). The planetary gear 116 is supported by the planetary pin 120 via the planetary bearing 118. The planetary bearing 118 divides the needle into two in the axial direction O, and arrange | positions it in the gun roller state. As a result, partial contact of the needle can be reduced when the sun gear 114 and the planetary gear 116 are engaged with each other. Moreover, since the needle is used in the state of the total roller without the supporter, the large torque can be transmitted to the planetary pin 120.

The internal gear 122 is integrally formed on the casing 142 including a tooth portion engaged with the planetary gear 116.

The planetary pin 120 is supported by the carrier body 124. The planetary pins 120 are formed separately from the carrier body 124. As a result, since the planetary pin 120 can be processed with high surface precision (shape or roughness), the life of the planetary bearing 118 can be extended, and the torque loss in the planetary gear 116 can be reduced. .

The carrier body 124 is configured to connect the carrier body main body 126 and the carrier body plate 128. The carrier body main body 126 is fastened and fixed to the carrier body plate 128 by the bolt 130. Thereby, the carrier body 124 extracts and rotates the idle component to the planetary pin 120 in synchronization with the idle component of the planetary gear 116. The carrier body 124 is formed with press-fitting holes 126B and 128B through which the planetary pin 120 is press-fitted. The formation positions of these press-in holes 126B and 128B change with a reduction ratio. On the side opposite to the planetary gear of the carrier body main body 126, a flange-shaped output shaft 132 is integrally provided. A plurality of bolt holes are provided in the end face thereof, and the driven shaft of the partner machine is connected by connecting bolts (not shown) to the bolt holes of the output shaft 132.

The bearings 134 and 138 are disposed as a main bearing on the radially outer side of the carrier body 124, and rotatably support the carrier body 124. The bearings 134 and 138 are angular ball bearings, each having balls 135 and 139 and outer rings 136 and 140, and their inner rings are formed integrally with the carrier body 124. As a result, compared with the case where the inner ring is provided separately from the carrier body, the portion 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. The diameter of the planetary pin 120 can be thickened while ensuring the thickness of 126A and 128A.

The bearings 134 and 138 are arranged in the axial direction O with the internal gear 122 interposed therebetween. And the bearings 134 and 138 are arrange | positioned at the back surface combination. As a result, it is possible to support high radial loads and axial loads. The outer races 136 and 140 of the bearings 134 and 138 have a structure separate from the casing 142. Thus, the casing 142 can be used in common as it is in the first sub-series even if the bearings 134 and 138 are different. The inner raceway surfaces of the bearings 134 and 138 are formed on the outer circumferential surfaces 127 and 129 of the carrier body 124.

Here, the outer periphery 142A of the casing 142 is fitted with a connecting casing (not shown) of the counterpart machine and functions as a seal portion E serving as a reference upon mounting. In the casing 142, the intermediate end cover 144 and the front end cover 146 are connected to the bolt 148 in the axial direction O. An oil seal 152 is provided between the intermediate end cover 144 and the input shaft 110. Moreover, the bearing 112 is arrange | positioned inside the intermediate | middle end cover 144, and the intermediate | middle end cover 144 supports the input shaft 110 rotatably via the bearing 112. As shown in FIG. The bearing 112 is fitted and fixed in the axial direction O by the intermediate end cover 144 and the front end cover 146. Here, reference numeral 150 in FIG. 1 denotes an oil seal disposed between the casing 142 and the output shaft 132 in order to seal the inside and the 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 via 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 rotates and revolves around the sun gear 114. At this time, since the internal gear 122 engaged with the planetary gear 116 is in a fixed state, the idle 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 mounted on the output shaft 132.

Here, the simple planetary gear reducer 200 shown in FIG. 2 also operates similarly to the simple planetary gear reducer 100 shown in FIG. However, while the reduction ratio of the simple planetary gear reducer 100 is about 1/4, 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. Compared with 114, the sun gear 214 is smaller, and the planetary gear 216 is larger than the planetary gear 116. In the first sub-series, the casings 142 and 242 are common, so that the radiuses R1 and R2 of the circles (pitch circles) connecting the center positions of the planetary pins 120 and 220 are not the same ( R1> R2 and the carrier body 124 are also different from the carrier body 224. Specifically, the formation positions (pitch diameters of the indentation holes) of the indentation holes 126B (128B) and 226B (228B) of the planetary pins 120 and 220 are different. That is, depending on 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 respectively. The sun gear 214, the planetary gear 216, and the carrier body 224 are changed. However, in the present embodiment, the planetary pins 120 and 220 are also common, but the planetary pins may not be common as a modification of the present embodiment.

In this embodiment, the bearings 134, 138 (234, 238) are provided outside the support position of the planetary pins 120 (220) in the radial direction of the carrier body 124 (224). The inner ring of 134, 138, 234, 238 is formed integrally with the carrier bodies 124, 224. As a result, the bearings 134 and 138 (234 and 238) can be made to be as large as possible. For example, even when the simple planetary gear reducer 100 has a reduction ratio of about 1/4, the carrier for supporting the planetary pins 120 can be obtained. The diameter of the planetary pin 120 can be thickened, ensuring the thickness of the portions 126A and 128A of the sieve 124. As a result, the planetary bearing 118 disposed between the planetary gear 116 and the planetary pin 120 can be enlarged as a result. Therefore, the output torque can be improved without increasing the speed reducer itself. In particular, in the present embodiment, since the planetary pins 120 (220) are made separate from the carrier body 124 (224), the life of the planetary bearings 118 can be extended. At the same time, since the inner rings of the bearings 134 and 138 (234 and 238) are not provided as 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 as the first sub-series is used in common, the total number of parts in the series, the total amount of inventory, and the cost of parts are reduced. Reduction can be achieved.

In the present embodiment, two bearings 134 and 138 (234 and 238) are used in the axial direction O with the internal gear 122 (222) interposed therebetween, and the bearings 134 and 138 (234, 238) is a rear combination. As a result, it is possible to support high radial loads and axial loads.

In the present embodiment, since the casing 142 (242) is common, the part connected to the counterpart machine, that is, the outer circumference 142A of the casing 142 has the same shape, so that the counterpart machine requires it. It is easy to replace the series of simple planetary gear reducers according to the output torque and rotational speed, and the outer circumference 142A of the casing 142 functions as the in-long part E at the time of replacement, so that the center of gravity can be easily adjusted. .

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

Next, in 2nd Embodiment of this invention, an example of the 2nd sub series in the series of a simple planetary gear reducer is demonstrated using FIG. 1, FIG.

In the present embodiment, the simple planetary gear reducer 100 constitutes the simple planetary gear reducer 300 and the second sub series. That is, in the second sub-series, the simple planetary gear reducer 100 (300) is located outside the support position of the planetary pins 120 (320) in the radial direction of the carrier body 124 (324). Bearings 134 and 138 (334 and 338) for supporting the sieve 124 (324), and the inner ring of the bearings 134 and 138 (334 and 338) and the carrier body 124 (324). The internal gear 122 (322) is integrally formed in the casing 142 (342) (the internal gear may be formed separately from the casing as a modification of the present embodiment). ). In the second sub-series, the casing 142 342 is changed in accordance with the reduction ratio, and the support positions of the planetary pins 120 and 320 are made common so that the carrier body 124 and the carrier body 324 are used. Is characterized by being common.

Here, the simple planetary gear reducers 100 and 300 shown in FIGS. 1 and 3 differ only in the reduction ratios of about 1/4 and about 1/3, respectively. For this reason, description of the component and operation | movement with respect to 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, which is a reduction ratio more than the reduction ratio of the simple planetary gear reducer 100. Here, when the casing 342 is made common with the casing 142, the radius R3 of a pitch circle becomes larger than the radius R1 of a pitch circle, and is a part of the carrier body between a planetary pin and a main bearing. There is a fear that the thickness and the thickness of the planetary pin can not be secured sufficiently. Therefore, in order to ensure the thickness of the portion of the carrier body between the planetary pin and the main bearing and the thickness of the planetary pin, the simple planetary gear reducer 300 equally has the radius of the simple planetary gear reducer 100 and the pitch circle. (R1 = R3). For this reason, the support position of the planetary pins 120 and 320 becomes common, and the carrier body 324 can be made common with the carrier body 124. Here, in the second sub-series, the planetary pins 120 and 320 are common.

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

At the same time, although the casing 142 (342) is not common, the radius of the pitch circle is set to be common (R1 = R 3), so that the outer shape of the casing 342 can be made the same as the outer shape of the casing 142. That is, since the part where the casing 342 is connected to the mating machine, that is, the outer periphery 342A of the casing 342 has the same shape as the outer periphery 142A, the second sub series is exceeded depending on the reduction ratio required by the mating machine. It is easy to replace the simple planetary gear reducer in the lifting series, and at the time of replacement, the outer circumference 342A of the casing 342 functions as the in-long part E, so that the center of gravity can be easily adjusted. That is, for the same counterpart machine, the second sub-series has connection compatibility with the first sub-series.

Moreover, the casing 342 corresponding to each part 142B, 142C of the casing 142 which makes the bearing 134, 138 and bearing 334, 338 the same, and supports the bearing 134, 138 is also equivalent. Each part 342B, 342C of can be made into the equal thickness. Thus, even if the casings 142 and 342 are not common, the output torque equivalent to the simple planetary gear reducer in the series crossing the second sub-series can be ensured.

By constructing a series of simple planetary gear reducers with the first and second sub-series, a wider reduction ratio can be covered than with the first sub-series alone, and the first relative to the same counterpart machine according to the reduction ratio. The second sub-series can be seamlessly matched.

Next, in 3rd Embodiment of this invention, another example of the 1st sub series in the series of a simple planetary gear reducer is demonstrated using FIG. 4, FIG.

This embodiment changes the angular ball bearing of each bearing 134, 138 (234, 238) of the simple planetary gear reducer 100 (200) of 1st Embodiment to the angular roller bearing. Therefore, the rollers of the bearings 434 and 438 (534 and 538), the inner ring corresponding to the outer ring 436 and 440 (536 and 540) and the bearings 434 and 438 (534 and 538) are integrally formed ( Since it is the same as that of 1st Embodiment except the carrier body 424 (524) in which the inner ring raceway surface was formed, the same code | symbol is attached | subjected to the following 2 digits, and description is abbreviate | omitted.

In this embodiment, since a roller is used for a main bearing instead of a ball, the internal load of a main bearing can be enlarged. Therefore, the load resistance of the simple planetary gear reducers 400 and 500 can be made larger than that of the first sub-series of the first embodiment having excellent low torque loss characteristics, and durability can be improved. Here, the outer ring 436, 440 (536, 540) of the bearings 434, 438 (534, 538) is separate from the casing 442 (542), so the casing 442 (542) is common. By doing so, the type of bearing can be easily changed. That is, in the first sub-series of the simple planetary gear reducer, angular ball bearings and angular roller bearings can be employed as the main bearings. At that time, since the outer ring of the main bearing has a structure separate from the casing, the main ring and the inner ring corresponding to the type of the main bearing are not changed, except for changing the carrier body, which is formed integrally with the main bearing. It is possible to provide a simple planetary gear reducer. However, even if the present embodiment is applied to the second sub-series, if the kinds of the main bearings are the same, the carrier bodies can be made common, and corresponding effects can be obtained.

Although the said embodiment was mentioned and demonstrated about this invention, this invention is not limited to the said embodiment. That is, it goes without saying that the improvement and the design change in the range which do not deviate from the summary of this invention are possible.

For example, in the said embodiment, although the output shaft was flange shape, this invention is not limited to this, It is easy to change the shape of an output shaft based on the shape of the driven shaft of a counterpart machine. For example, a cylindrical output shaft may be provided in the carrier body and connected to the driven shaft of the counterpart machine via the key groove. In addition, such a change of the output shaft to the so-called solid type (all of the above embodiments are referred to as "flange type") adds components (carrier body, output shaft, or output shaft) constituting the output shaft without impairing the effect of the present invention. This can be done easily by simply changing). That is, since the commonization other than the components constituting the output shaft can be achieved, the cost reduction of the simple planetary gear reducer having the flange type or the solid type output shaft can be reduced, and the variation of the output shaft in the series can be improved.

In addition, in the said embodiment, although two bearings were used by back 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 arrange | positioned and used, and the outer ring may be comprised as a structure separate from a casing. Even then, axial loads in both directions can be applied in the axial direction (O) of the driven shaft of the counterpart machine, and the same effect as in the case of using two bearings can be obtained, and furthermore, the axial direction (O of the simple planetary gear reducer) is obtained. Can be shortened.

Moreover, even when two bearings are used, a tapered roller bearing may be used, and the combination is not limited to a back surface, but may be a front combination or a parallel combination.

Moreover, in the said embodiment, although the planetary pin was made into the thing separate from a carrier body, this invention is not limited to this. For example, the planetary pin may be integrally formed on the carrier body. In the first sub-series in this case, carrier bodies having different formation positions of the planetary pins are prepared according to the reduction ratio. In the second sub-series, the carrier body in which the planetary pins are integrally formed can be used as it is.

In addition, in the said embodiment, although what demonstrated the gear ratios being about 1/3, about 1/4, about 1/10, this invention is not limited only to these reduction ratios.

Moreover, in the said embodiment, although the casing was fixed and the output shaft was provided in the carrier body, this invention is not necessarily limited to this, What is called a frame rotation type | mold which a carrier body is fixed and a casing rotates and an output is obtained.

In the first sub-series, different parts of the carrier body may be generated not only in the support position of the planetary pin but also in other parts depending on the reduction ratio.

The invention can be used in the manufacturing industry of reduction gears, in particular reduction gear series consisting of simple planetary gears.

100, 200, 300, 400, 500: 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: bearing
114, 214, 314, 414, 514: sun gear
116, 216, 316, 416, 516: planetary gears
118, 218, 318, 418, 518: planetary bearing
120, 220, 320, 420, 520: planetary pins
122, 222, 322, 422, 522
124, 224, 324, 424, 524: carrier body
126, 226, 326, 426, 526: carrier body
128, 228, 328, 428, 528: carrier body plate
130, 148, 230, 248, 330, 348, 430, 448, 530, 548: Bolt
132, 232, 332, 432, 532: output shaft
136, 140, 236, 240, 336, 340, 436, 440, 536, 540: paddle
142, 242, 342, 442, 542 casing
144, 244, 344, 444, 544: middle cover
146, 246, 346, 546: shear cover

Claims (5)

Solar gear, planetary gear meshing with the sun gear, internal gear meshed with the planetary gear, internal planetary gears, planetary pins rotatably supporting the planetary gears, and revolving components of the planetary gears supporting the planetary pins In a series of simple planetary gear reducers having different reduction ratios having a carrier body synchronous with
A main bearing supporting the carrier body on an outer side of the support position of the planetary pin in the radial direction of the carrier body,
The inner ring of the main bearing is integrally formed with the carrier body,
The casing on which the internal gear is formed is common, and,
The support position of the sun gear, the planetary gear, and the planetary pin in the carrier body is changed in accordance with the reduction ratio.
A series of simple planetary gear reducers having a first sub series. The method according to claim 1,
The main bearing supporting the carrier body on an outer side of the support position of the planetary pin in the radial direction of the carrier body,
The inner ring of the main bearing is integrally formed with the carrier body,
The casing is changed according to the reduction ratio,
The carrier body becomes common by making the support positions of the planetary pins in common.
A series of simple planetary gear reducers having a second sub-series. The method according to claim 2,
The series of simple planetary gear reducers of the first sub-series and the second sub-series, wherein the casing has the same shape in the portion connected to the mating machine. The method according to any one of claims 1 to 3,
A plurality of kinds can be employed as the main bearing, and 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 structure separate from the casing. A series of simple planetary gear reducers, characterized in that the casing is common regardless of the type of bearing. The method according to any one of claims 1 to 4,
A series of simple planetary gear reducers, characterized in that the main bearing is used in plurality in the axial direction with the internal gear interposed therebetween, and the main bearing is a rear combination.

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