KR101683622B1 - Series of Reducer Device - Google Patents

Abstract

In both of the reduction gear device having the main bearing and the reduction gear device having no main bearing, axial movement of the external gear is regulated at a low cost.
Gears 124 and 224 and internal gears 126 and 226 to which the external gears engage with each other and casings 144 and 244 provided with internal gears and carriers 132 and 232 relatively rotating with the casing A first reduction gear unit (100) in which a main bearing (150x, 150y) is disposed between a casing and a carrier and a second reduction gear unit (200) in which a main bearing is not disposed, The carrier of the apparatus and the carrier of the second reduction gear are shared. In the first reduction gear device, the axial movement of the external gear is regulated by the inner ring of the main bearing disposed in the main bearing arrangements 132Bx and 132By of the carrier In the second reduction gear unit, the movement of the external gear in the axial direction is restricted by the movement regulating members 280x and 280y disposed in the main bearing arrangement portion of the carrier.

Description

Series of Reducer Device}

This application claims priority based on patent application No. 2014-249404, filed December 9, 2014. The entire contents of which are incorporated herein by reference.

The present invention relates to a series of reduction devices.

Patent Document 1 discloses a structure in which a reduction gear having an internal gear to which the external gear is meshed and meshed with the internal gear, a casing provided with the internal gear, and a carrier relatively rotating with the internal gear, Lt; / RTI >

In this decelerating device, the carrier is supported on the casing by a bearing having a large capacity called a main bearing. In addition, axial movement of the external gear is regulated by the inner ring of the main bearing.

Prior art literature

(Patent Literature)

Patent Document 1: JP-A-2010-286098 (Fig. 1)

Although the decelerating device is used by being mounted on various industrial machines and the like, depending on the application of the industrial machine or the like, a very large moment may be input to the main bearing of the decelerator from the side of the industrial machine for some reason.

With respect to such a large moment, there is a limit in coping with measures to increase the capacity of the main bearing, and the cost is also high. As a result, it has been proposed that such a moment is borne by a larger bearing mechanism provided on the side of an industrial machine or the like. According to this configuration, as described later in detail, the arrangement of the main bearings can be omitted on the decelerating device side as a result.

On the other hand, however, in the case of a reduction gear device having no main bearing, how to regulate the movement of the external gear in the axial direction becomes a problem.

SUMMARY OF THE INVENTION The present invention has been made in order to solve such a problem, and it is an object of the present invention to provide a reduction gear device having a main bearing and a reduction gear device having no main bearing, have.

The present invention relates to a series of reduction gears including a shout gear, an internal gear engaged with the shout gear, a casing provided with the internal gear, and a carrier rotating relative to the casing, the space between the casing and the carrier And a second reduction device in which a main bearing is not disposed between the casing and the carrier, wherein the carrier of the first reduction device and the carrier of the second reduction device In the first reduction gear device, the axial movement of the external gear is restricted by the inner ring of the main bearing disposed in the main bearing arrangement portion of the carrier, and in the second reduction gear device, The axial movement of the external gear is regulated by the movement regulating member disposed in the main bearing arrangement portion of the internal gear, Will.

In the present invention, in the first reduction gear device having the main bearing, the inner ring of the main bearing restricts the axial movement of the external gear. In the second reduction gear unit having no main bearing, a space in which the main bearing is disposed in the first reduction gear unit is used. Namely, a movement regulating member is disposed in the main bearing arrangement portion, and the movement regulating member regulates the axial movement of the external gear.

Thus, in the first reduction gear unit having the main bearing and the second reduction gear unit having no main bearing, even in the case of the second reduction gear unit having the common carrier cost and having no main bearing, can do.

According to the present invention, in both of the reduction gear device having the main bearing and the reduction gear device having no main bearing, axial movement of the external gear can be regulated at a low cost.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view showing a first reduction gear unit (a) and a second reduction gear unit (b) in a series of reduction gears according to an embodiment of the present invention.
2 is an enlarged cross-sectional view of a main portion of the first reduction gear device in the series.
3 is an enlarged sectional view of a main part of the second reduction gear device in the series.
4 is a sectional view showing a configuration example in which the second reduction gear is mounted on the other machine.
Fig. 5 is an enlarged cross-sectional view of a main portion corresponding to Fig. 3 showing a modified example of the second decelerator.

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

The first reduction gear unit (first reduction gear unit) shown in FIG. 1A and the second reduction gear unit (second reduction gear unit) shown in FIG. 1B are included in the series of reduction gears . The deceleration devices belonging to the series all include external gears, internal gears to which the external gears engage and engage, a casing provided with the internal gear, and a carrier rotating relative to the casing. However, in the first reduction device, a large-capacity bearing called a main bearing is disposed between the first casing and the first carrier, but the second reduction device is provided between the second casing and the second carrier, .

Referring to Fig. 1, the schematic configuration of the first reduction device 100 and the second reduction device 200 will be described. 2 and 3 are enlarged cross-sectional views of main parts of Figs. 1 (a) and 1 (b), respectively.

In the following description, the constituent members of the first reduction gear train 100 are denoted by 100 symbols, the constituent members of the second decelerator 200 are denoted by 200 symbols, and for the sake of convenience, A description will be given of the apparatus 100 and a configuration specific to the first reduction device 100 and the second reduction device 200 will be described. The two components having the same two digits are components common to the first reduction device 100 and the second reduction device 200 (joint: shape and size are the same).

The first reduction gear unit 100 and the second reduction gear unit 200 are disposed on the boundary surface in the axial center of the two external gears 124x and 124y (224x and 224y in the second reduction gear unit 200) The axial load side and the opposite side of the load have a similar configuration to the first reduction gear F100 (F200 in the second reduction gear unit 200). For this reason, it is assumed that the member having the axial suffix x is attached to the member on the axial load side and the member having the suffix y is attached to the member on the side opposite to the load in the drawing, and a common explanation is given by using the suffix- The relationship on the opposite side of the load will be described.

The configuration of the first reduction device 100 will be described.

The first reduction gear apparatus 100 is provided with an input pinion (not shown in Fig. 1, for example, an input pinion 214 provided at the front end of the spline shaft 212 in Fig. 4). The input pinion is simultaneously engaged with three split gears (only one shown) 116 disposed at three positions in the circumferential direction. The split gear 116 is fixed to three eccentric body shafts (only one shown) 118 via a spline 119, respectively.

Three eccentric body shafts 118 are provided at equal intervals in the circumferential direction at positions offset from the axis C126 of the internal gear 126. [ Two eccentric bodies 120 (120x and 120y) are integrally formed on the respective eccentric body shafts 118. The eccentric body 120 is eccentric with respect to the axis C118 of the eccentric body shaft 118 by 隆 E (DELTA Ex, DELTA Ey) in a phase of 180 degrees. Two eccentric gears 124 (124x and 124y) are fitted to the respective eccentric bodies 120 through needle bearings 122 (122x and 122y). The external gear 124 is in contact with and meshes with the internal gear 126.

The internal gear 126 includes an internal gear main body 126A integrated with the casing 144 and an outer pin 126B which is rotatably supported by the internal gear main body 126A and constitutes an internal tooth of the internal gear 126, ). The number of internal teeth of the internal gear 126 (the number of external pins 126B) is slightly larger than the external teeth of the external gear 124 (one in this example).

A pair of carriers 132 (132x and 132y) are disposed on both axial sides of the external gear 124. The carrier 132y on the opposite side of the load is integrated with the carrier 132x on the load side through the bolt 138 and the carrier pin 136 integrally projected from the carrier 132x on the load side.

The carrier 132 is provided with three eccentric body sole holes 132Px (132Py) (132Px, 132Py) (only one is shown in Fig. 1). The eccentric body shaft 118 is inserted into the eccentric body shaft hole 132P through a pair of conical roller bearings 140 (140x, 140y) and is rotatably supported by the carrier 132. [

A pair of main bearings 150 (150x and 150y) is disposed between the casing 144 of the first reduction gear unit 100 and the carrier 132. [ That is, the carrier 132 is supported by the casing 144 through the main bearing 150. [

The main bearing 150 is constituted by a conical roller bearing in this example and each of the outer ring 151 (151x and 151y), the conical roller 152 (152x and 152y) (153 (153x, 153y)).

More specifically, the outer periphery of the carrier 132 is composed of a large-diameter portion 132A (132Ax, 132Ay) provided on the opposite side to the axial direction external gear and a main bearing arrangement portion (more specifically, (132B (132Bx, 132By)). The outer diameter d132B of the main bearing arrangement portion 132B is smaller than the outer diameter d132A of the large diameter portion 132A while the inner bearing abutment surface 132C (132Cx, 132Cy)). The inner ring contact surface 132C is formed in a plane perpendicular to the axis.

The inner ring 153 of the main bearing 150 is disposed on the main bearing arrangement portion 132B of the carrier 132 and abuts on the inner ring abutment surface 132C of the carrier 132. [ In this embodiment, the inner ring 153x on the load side directly abuts on the inner ring abutment surface 132Cx, but the inner ring 153y on the opposite side of the load has a shim 171 ).

This padding 171 is for adjusting the preload of the main bearing 150y on the opposite side of the load and the main bearing 150x on the load side. The inner ring 153 of the main bearing 150 and the inner ring abutment surface 132C of the carrier 132 may be in direct contact with each other or indirectly in contact with each other through the padding 171 or a spacer.

However, the large-diameter portion 132Ax of the carrier 132x on the load side constitutes the seal surface of the oil seal 170. [

The inner ring 153 of the main bearing 150 extends beyond the main bearing arrangement portion 132B of the carrier 132 toward the axial direction external gear and the end face 153A (153Ax, 153Ay) on the axial external gear side (124E (124Ex, 124Ey)) of the external gear (124). In other words, the axial length L153 of the inner ring 153 of the main bearing 150 is smaller than the axial length L153 between the inner ring contact surface 132C of the carrier 132 and the axial end surface 124E of the external gear 124 (When the shim 171 is inserted, it is slightly shortened corresponding to the axial length).

With this configuration, the inner ring 153 of the main bearing 150 can regulate the movement of the external gears 124 in the axial direction. More specifically, the movement restriction of the external gears 124x by the inner ring 153x of the main bearing 150x on the load side is restricted to the axial load side and the external restriction by the inner ring 153y of the main bearing 150y on the opposite side of the load It is possible to restrict the movement of the gear 124y on the opposite side to the axial load.

The outer ring 151 of the main bearing 150 is described below. In this embodiment, the casing 144 includes an outer pin arrangement portion 144A provided at the center of the inner periphery in the axial direction, 144B (144Bx, 144By) provided on both sides of the main bearing arrangements (more specifically, the outer ring arranging portions) 144Bx, 144B. The axial length L144A of the outer pin disposition portion 144A is equal to the axial length L126B of the outer pin 126B. The inner diameter D144A of the outer pin arrangement portion 144A (the inner diameter of the portion where the grooves for arranging the outer pins 126B are not formed) is smaller than the inner diameter D144B of the main bearing arrangement portion 144B, 144F (144Fx, 144Fy) are provided between the main bearing arrangement portion 144A and the main bearing arrangement portion 144B. The outer ring contact face 144F is formed as a plane perpendicular to the axis.

The outer ring 151 of the main bearing 150 is disposed in the main bearing arrangement portion 144B of the casing 144 and abuts the outer ring abutment surface 144F of the casing 144. [ According to the present embodiment, the axial movement of the outer pin 126B is restricted by the outer ring 151 of the main bearing 150 with this configuration. Specifically, the movement of the outer pin 126B relative to the axial load side is restricted by the outer ring 151x of the main bearing 150x on the load side, and the outer ring 151x of the outer ring 151x of the main bearing 150y, (126B) is restrained from moving on the opposite side to the axial load.

However, the oil seal arranging portion 144D in which the oil seal 170 is disposed further extends on the axial load side of the main bearing arrangement portion 144Bx on the load side. However, the oil seal arranging portion is not particularly provided on the opposite side to the axial load of the main bearing arrangement portion 144By on the opposite side of the load. This is because a separate casing (not shown) is connected to the opposite side to the axial load of the main bearing arrangement portion 144By on the opposite side of the load, and the space in the separate casing is continuous.

A stop ring groove 144J (144Jx, 144Jy) is formed in the main bearing arrangement portion 144B (144Bx, 144By) of the casing 144. [ In the first reduction gear device 100, the stop ring groove 144J is not particularly used. The stop ring groove 144J is a structure for making the casing 144 of the first reduction gear unit 100 common with the casing 244 of the second reduction gear unit 200. [ This will be described later.

Here, the operation of the first reduction device 100 will be briefly described.

However, the basic deceleration action as the decelerating device is basically the same for the first decelerator 100 and the second decelerator 200 as well.

When the input pinion (not shown) (for example, the input pinion 114 (214) provided at the tip of the joint shaft 112 (212) as shown in Fig. 4) rotates, 116 are simultaneously rotated, and the three eccentric body shafts 118 synchronously rotate in the same direction. This causes the external gear 124 mounted on the outer periphery of the eccentric body 120 to swing while being in contact with and engaging with the internal gear 126 (outer pin 126B). As a result, each time the eccentric body shaft 118 rotates once, the external gear 124 is rotated by the amount corresponding to the dimension difference (1 in this embodiment) of the external gear 124 and the internal gear 126, And rotates relative to the internal gear 126. Due to this relative rotation, the eccentric body axis 118 passing through the external gear 124 revolves around the axis C126 of the internal gear 126. As a result, the carrier 132 supporting the eccentric body shaft 118 and the casing 144 integrated with the internal gear main body 126A of the internal gear 126 rotate relative to each other, for example, (Not shown) connected to the main body.

Next, the characteristic configuration of the second reduction gear unit 200 will be mainly described with reference to FIG. 3, which is an enlarged view of FIG. 1 (b) and its main parts.

The configuration of the first reduction gear unit 100 that has been described so far is the same as that of the second reduction gear unit 200 except for the configuration of the periphery of the main bearing 150. [ In other words, the other overall constituent members of the deceleration mechanism including the carrier 232 are arranged in the first and second decelerating devices 100 and 200, including the diameters and positions of the holes formed in the constituent members, .

A major feature of the configuration of the second reduction gear unit 200 is that the main bearing is not disposed between the casing 244 and the carrier 232. [ The second reduction gear unit 200 is not provided with the main bearing because the second reduction gear unit 200 is designed on the assumption that the second reduction gear unit 200 is mounted on a specific counterpart machine.

4 shows a configuration example in which the second reduction gear unit 200 is mounted on a machine tool (mating machine) This machine tool (not shown in all) 300 includes a first member 301 and a second member 302. The second reduction gear 200 is used for relatively rotating the first member 301 and the second member 302. [

The casing 244 of the second reduction gear apparatus 200 is connected to the first member 301 via the bolts 304 in the flange portion 244G and the carrier 232x on the load side is connected to the bolts 306 To the second member (302). The first member 301 and the second member 302 are relatively rotatably connected by a pair of machine tool side bearings 308 and 309 of a large capacity. As a result, the casing 244 of the second reduction gear unit 200 and the carrier 232x on the load side can rotate relative to each other smoothly without a main bearing. The carrier 232y on the opposite side of the load integrated with the carrier 232x on the load side can also rotate relative to the casing 244 smoothly without a main bearing.

The second reduction gear unit 200 is not provided with the main bearing so that the inner diameter of the outer ring gear 124 is reduced by the inner ring 153 of the main bearing 150 like the first reduction gear unit 100, The movement in the direction can not be regulated.

As a result, in the second reduction gear apparatus 200 according to the present embodiment, the movement regulating member 280 (280x, 280y) is disposed in the main bearing arrangement portion 232B of the carrier 232, The axial movement of the external gear 224 of the second reduction gear unit 200 is regulated by the second gear unit 280.

The axial length L280 of the movement limiting member 280 is set equal to the axial length L153 of the inner ring 153 of the main bearing 150 of the first reduction gear device 100. [ The first reduction gear unit 100 is formed with the same structure as that in which the axial movement of the external gear 124 is restricted by the inner ring 153 of the main bearing 150, 200, the movement restricting member 280 can restrict movement of the external gear 224 in the axial direction.

The movement restricting member 280 is formed of a material having a hardness lower than that of the external gear 224 and has a cross section (a cross section cut by a plane including the axis C226 of the internal gear 226) (280S (280Sx, 280Sy)) having a substantially rectangular ring shape. The movement restricting member 280 is provided with an abutting portion 280C (280Cx, 280Cy) which abuts against the external gear 224 with the stepped portion 280S as a boundary and an abutting portion 280Cx And a body portion 280B (280Bx, 280By) located on the opposite side. The thickness H280C of the abutting portion 280C in the radial direction (only H280Cy in the H280Cx and H280Cy in Fig. 3) is constant and the thickness H280B in the radial direction of the body portion 280B H280By only on the opposite side of the load). The thickness H280C in the radial direction of the abutment portion 280C is smaller than the thickness H280B in the radial direction of the body portion 280B.

However, in the present embodiment, the chamfered portion 280F (280Fy only on the side opposite to the load) is formed on the tooth profile side end face side 280D (280Dx, 280Dy) of the abutting portion 280C of the movement regulating member 280 . However, in this specification, the presence of the chamfered portion 280F is not taken into account in specifying the thicknesses of the abutting portion 280C and the main body portion 280B. In other words, the constitution of " the radial thickness of the abutting portion is smaller than the radial thickness of the main body portion " here means that a difference in thickness is generated between the abutment portion and the main body portion by a method other than chamfering Which means that the design is done.

However, in this embodiment, a step portion 280S is formed between the abutting portion 280C having a constant thickness H280C in the radial direction and the main portion 280B having a constant thickness H280B in the radial direction, The thickness H280C of the abutting portion 280C in the radial direction is made smaller than the thickness H280B of the main portion 280B in the radial direction by the presence of the step portion 280S. However, the specific configuration of " the radial thickness of the abutment portion is smaller than the radial thickness of the body portion " is not limited to this configuration. For example, the outer periphery of the abutment portion is formed in a non-parallel relationship with the shaft, and the configuration in which the thickness in the radial direction of the abutment portion becomes gradually smaller as the abutment portion is approached to the external gear (configuration in which the abutment portion and the body portion have no stepped portion) You can.

Returning to the description of the second reduction gear unit 200, the second reduction gear unit 200 in the present embodiment is provided with a fall-off prevention member 284 in addition to the movement restriction member 280. The fall preventing member 284 is axially fixed with respect to the casing 244 so that the entire deceleration mechanism including the shout gear 224 relative to the casing 244 falls off in the axial direction, The outer pin 226B is prevented from falling off in the axial direction and the outer pin 226B from falling off in the radial direction with respect to the casing 244. [

Specifically, the fall-off prevention member 284 is entirely constituted by a ring-shaped member. The fall-off prevention member 284 has a casing abutment surface 284A abutting against a cross section (an end surface corresponding to the outer abutment abutment surface 144F) 244F of the casing 244, a casing abutting surface 284A, And has an outer pin facing surface 284B that faces the axial end surface 226B1 of the outer pin 226B. The protruding portion 284C capable of supporting the radially inner side of the axial end portion of the outer pin 226B from the radially inward end of the outer pin opposing face 284B is parallel to the shaft And extends toward the shout gear 224 side. The end face 284D of the protruding portion 284C faces the axial end face 224E of the external gear 224.

The fall-off preventing member 284 has a stop ring 285 engaging with the stop ring groove 244J formed in the casing 244 and an end face 244F of the casing 244 (corresponding to the outer ring contact face 144F) And is fixed to the casing 244 by the stop ring 285. As shown in Fig.

The front end surface 284D of the protruding portion 284C of the fall-off prevention member 284 is located at a position corresponding to the front end surface 284D of the yoke gear 224 when viewed from the axial direction. And is overlapped with the axial end surface 224E. The projecting portion 284C of the fall-off prevention member 284 overlaps with the axial end portion of the outer pin 226B when the fall-off preventing member 284 and the outer pin 226B are viewed from the radial direction. The outer pin opposing surface 284B of the fall-off preventing member 284 overlaps the axial end surface 226B1 of the outer pin 226B when the fall-off preventing member 284 and the outer pin 226B are viewed from the axial direction .

However, in this embodiment, the fall-off preventing member 284 has a recessed portion (a thickness H280C in the radial direction of the abutting portion 280C) radially outward of the abutting portion 280C of the movement regulating member 280, Is formed to be smaller than the thickness H280B in the radial direction of the main body portion 280B, thereby entering the concave portion formed in the radially outer side of the abutting portion 280C). That is, the main body portion 280B of the movement regulating member 280 and the fall-off preventing member 284 are overlapped when viewed from the axial direction.

However, the fall-off preventing member 284, the external gear 224, and the external pin 226B do not always have to be always in contact with each other. Rather, the declutching member and the shaking gear or the outer pin are opposed to each other with a slight clearance at the time of normal operation, and when the axial position of the casing and the shout gear is to deviate greatly for some reason, As shown in Fig.

As described above, the stop ring groove 244J is used only in the second speed reduction device 200. In the present embodiment, the stop ring groove 244J does not require the stop ring groove 144J The stop ring groove 144J is formed in the casing 144 of the first reduction gear unit 100 as well as the casing 244 of the second reduction gear unit 200. [

Next, the operation of the series of reduction devices will be described.

In this series, in the first reduction gear train 100, the inner ring 153 of the main bearing 150 is restricted by the inner ring abutment surface 132C of the carrier 132 from regulating the movement on the opposite side to the axial gear teeth The axial end face 124E of the shake gear 124 is abutted. Thus, axial movement of the external gear 124 can be restricted by the inner ring 153 of the main bearing 150. [

On the other hand, in the second reduction gear apparatus 200, the main bearing arrangement portion 232B of the carrier 232 (where the main bearing 150 is disposed in the first reduction gear train 100) And the movement restricting member 280 restricts the movement of the external gear 224 in the axial direction.

As a result, the following merits are obtained.

Generally, as a method of regulating the axial movement of the external gear, in addition to a method of regulating the external gear by the inner ring of the main bearing, a protrusion is formed on the end face of the carrier on the external gear side, Is widely known. However, in the case of the present embodiment, forming protrusions for regulating the external gear only on the carriers of the second reduction gear means that the commonality (compatibility) between the carriers in the first reduction gear and the second reduction gear is lost. Since the carrier is one of the very expensive base members among the reduction gears, preparing the carrier separately for each of the first reduction gear and the second reduction gear is a factor that greatly increases the cost.

On the other hand, for example, a method of making the carriers common can be conceived by forming protrusions on the carriers of both the first reduction device and the second reduction device. However, depending on the circumstances, a first reducing device for normal use having a main bearing has priority, and a manufacturing pattern in which the first reducing device is utilized as a second reducing device without a main bearing for a specific use is overwhelmingly large. In this case, design changes to form protrusions on the carriers are very large-scale design changes. This is because, unlike, for example, a design change in which a groove or a hole is formed, a design change in forming the protrusion largely changes the design or manufacturing process of the carrier itself.

Further, for example, when the first and second reduction gears have a simple structure in which protrusions are provided on the carrier to restrict the axial movement of the external gear, in the first reduction gear, The axial movement of the external gear is regulated by the protruding portion of the carrier, thereby increasing the sliding resistance. However, in order to avoid this, when it is intended to prevent axial movement of the external gear relative to the inner ring of the main bearing, the design of the peripheral member as well as the carrier is required to be changed. .

According to the series of decelerating apparatuses of the present embodiment, there is no need to manufacture separate carriers in the first and second decelerating apparatuses 100 and 200, and merely in the second decelerating apparatus 200, It is solved only by disposing the movement regulating member 280, so that the cost can be greatly reduced.

Particularly, in the series of decelerating apparatuses according to the present embodiment, the stop ring groove 144J equivalent to the stop ring groove 244J for engaging the stop ring 285 used only in the second reduction gear unit 200, But also in the casing 144 of the speed reducing device 100.

This makes it possible for the casing 144 of the first reduction gear unit 100 and the casing 244 of the second reduction gear unit 200 to include the stop ring grooves 144J and 244J in complete common use. That is, the largest and the most costly casings can be used in common, facilitating the inventory management and lowering the cost.

However, it is not always necessary to completely standardize the casing, and for example, a stop ring groove may be formed when the second reduction gear unit 200 is configured as required.

According to the series of reduction gears according to the present embodiment, in the second reduction gear unit 200, the outer pin 226B constituting the internal gear 226 is fixed to the casing 244 in the axial direction, Preventing member 284 and the external gear 224 are overlapped with each other when viewed from the axial direction.

With this, the fall-off prevention member 284 can regulate the movement of the shout gear 224 in the axial direction not only with respect to the carrier 232 but also with respect to the casing 244. That is, since the deceleration mechanism including the shout gear 224 and the carrier 232 is shifted in the axial direction with respect to the casing 244 (when the casing 244 is too deep, It is possible to prevent the occurrence of the problem of dropping out.

Now, if there is no dropout prevention member 284, for example, the second reduction gear 200 before being attached to the partner machine is to be placed on a workbench (not shown) or the like I think about the situation. In this case, since the casing 244 of the second reduction gear unit 200 itself is heavy, even when any one of the load side and the load side is downward, the casing 244 is supported by its own weight So that the oil seal 270 may be broken or shifted. Further, for example, there may be a case where the entire reduction mechanism is removed from the casing 244 while the carrier 232 is being maintained during transportation.

However, in the series of decelerating apparatuses according to the present embodiment, the deceleration preventing member 284 restricts the movement of the shout gear 224 not only with respect to the carrier 232 but also with respect to the casing 244 in the axial direction can do. As a result, the occurrence of the problem can be effectively prevented.

However, in the series of decelerating apparatuses according to the present embodiment, the disengagement preventing member 284 of the second decelerator 200 is overlapped with the outer pin 226B when viewed from the axial direction and viewed from the radial direction have. In other words, the fall-off preventing member 284 can prevent both the axial movement (dropout) and the radial movement (dropout) of the outer pin 226B. Particularly, in the radial detachment of the outer pin 226B, since it is practically difficult to obtain the same configuration at the outer ring 151 of the main bearing 150 of the first reduction gear device 100, It can be understood as an effect obtained additionally.

In the series of reduction gears according to the present embodiment, the movement regulating member 280 of the second reduction gear unit 200 is formed of a material having hardness lower than that of the external gear 224. As in the present embodiment, if it is only necessary to regulate the movement of the external gear 224 in the axial direction, it is considered that a material with low hardness is sufficient in many cases. A material having a low hardness can be generally manufactured at a low cost, and a movement regulating member can be obtained at a lower cost.

In the series of reduction gears according to the present embodiment, the movement regulating member 280 of the second reduction gear unit 200 includes the abutting portion 280C abutting against the external gear 224 and the abutting portion And the thickness H280C in the radial direction of the abutting portion 280C is smaller than the thickness H280B in the radial direction of the body portion 280B . This makes it possible to keep the abutment area with the external gear 224 small while maintaining the rigidity of the entire movement regulating member 280 as high as possible, thereby reducing the sliding resistance accordingly.

However, in the movement regulating member 280 of the second reduction gear device 200, the "thickness in the radial direction of the portion abutted against the external gear is smaller than the thickness in the radial direction other than the portion abutting the external gear" The configuration is not necessarily an essential configuration. The movement regulating member 290 may be, for example, a simple ring shape as shown in Fig.

5, the thickness of the movement regulating member 290 (290x, 290y) of the second reduction gear unit 200 is H290 in the radial direction at any position in the axial direction, It is constant except that there is a chamfer (290F, 290Fy). Thereby, the manufacturing cost of the movement regulating member 290 can be further reduced as long as it does not have the stepped portion. Further, as the sliding area with the external gear 224 becomes larger, there is a possibility that the movement regulating member 290 can be manufactured with a material having a lower hardness (lower cost). However, as described above, the presence of the chamfered portion does not affect the concept of " the thickness is constant ".

Other configurations are the same as those of the second reduction gear unit 200 in the previous embodiment, and therefore, the same reference numerals are assigned to the same members in FIG. 5 and redundant description is omitted.

In this embodiment, a conical roller bearing is employed as the main bearing. However, the main bearing is not necessarily made up of a conical roller bearing, and even if it is constituted by, for example, an angular roller bearing or a simple ball bearing do.

In addition, a decelerating device of the eccentric oscillation type provided with a plurality of eccentric body shafts for oscillating the external gears at positions offset from the central axis of the internal gears is exemplified. However, in the series of decelerating devices according to the present invention, The device is not limited to the decelerating device having such a configuration, and is equally applicable to a decelerating device of the eccentric oscillation type in which, for example, only one eccentric body shaft is provided at the axial center of the internal gear. It is also applicable to, for example, a reduction device of a simple planetary gear structure. That is, the present invention can be similarly applied to an internal gear in which the external gear is meshed with the external gear, a casing in which the internal gear is provided, and a carrier that rotates relative to the casing. .

100, 200 ... The first and second reduction gears
124, 224 ... Shout gear
126, 226 ... Internal gear
132, 232 ... carrier
132B, 232B ... Main bearing arrangement section
144, 244 ... Casing
150 ... Main bearing
280 ... The movement regulating member

Claims (6)

1. A series of reduction gears having internal gears which are engaged with external gears, internal gears which are engaged with the external gears, a casing provided with the internal gear, and a carrier rotating relative to the casing,
A first reduction gear device in which a main bearing is disposed between the casing and the carrier and a second reduction device in which a main bearing is not disposed between the casing and the carrier,
Wherein the carrier of the first reduction gear and the carrier of the second reduction gear are shared,
In the first reduction gear device, the axial movement of the external gear is restricted by the inner ring of the main bearing disposed in the main bearing arrangement portion of the carrier, and the axial movement of the external pin constituting the internal gear Is regulated by the outer ring of the main bearing,
In the second reduction gear device, the axial movement of the external gear is restricted by the movement limiting member disposed in the main bearing arrangement portion of the carrier, and the axial movement of the external pin constituting the internal gear is regulated And the outer pin regulating member is a member separate from the movement regulating member. The method according to claim 1,
In the second reduction gear device, the outer pin regulating member also functions as a slip-off preventing member for regulating the removal of the outer pin in the radial direction, and is fixed in the axial direction with respect to the casing so that the outer pin regulating member, , And is overlapped when viewed from the axial direction. 3. The method according to claim 1 or 2,
Wherein the movement limiting member of the second reduction gear is formed of a material having a hardness lower than that of the gear. The method of claim 3,
Wherein the movement regulating member of the second reduction gear unit has a constant thickness in the radial direction in the axial direction. 3. The method according to claim 1 or 2,
Wherein the movement restricting member of the second reduction gear has a contact portion abutting against the external gear and a body portion located on the opposite side of the axial external gear of the abutment portion, Is smaller than the thickness in the radial direction of the portion, and the outer pin regulating member overlaps with the main body portion when viewed from the axial direction. 3. The method according to claim 1 or 2,
In the second reduction gear device, the outer pin regulating member has a stop ring, a stop ring groove of the stop ring is formed in the casing,
Wherein the casing of the first reduction gear unit is formed with a stop ring groove common to the stop ring groove of the second reduction gear unit and the casing of the first reduction gear unit and the casing of the second reduction gear unit are common Lt; RTI ID = 0.0 > 1, < / RTI >

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