JP6130690B2 - Reduction gear - Google Patents

Description

  The present invention relates to a reduction gear.

  Conventionally, a reduction gear as shown in Patent Document 1 has been used. The reduction gear device includes a reduction gear casing that houses a reduction gear mechanism, and a bearing housing that houses a bearing that supports an input shaft (protruding shaft) protruding from the reduction gear casing. The bearing housing includes a cylindrical housing body and a flange portion formed radially outward from one axial end portion of the housing body, and the flange portion is fixed to the speed reducer casing by a bolt. .

JP 2005-308070 A

  However, in the reduction gear shown in Patent Document 1, the distance from the center of the housing body to the bolt (fixing member) is increased, and as a result, the pitch of the bolt is also increased. Therefore, a sufficient coupling fixing force cannot be obtained between the reduction gear casing and the bearing housing, and the lubricant may leak from between the reduction gear casing and the bearing housing. On the other hand, if the number of bolts is increased or the number of seal members is increased in order to prevent the leakage of the lubricant, the assemblability is deteriorated.

  Accordingly, the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a speed reducer that can reduce the possibility of lubricant leakage without impairing assembly.

The present invention relates to a speed reducer comprising: a speed reducer casing that houses a speed reduction mechanism; and a bearing housing that houses a bearing that supports a projecting shaft projecting from the speed reducer casing, wherein the bearing housing is a cylindrical housing body. And a flange portion formed radially inward from one axial end portion of the housing body, the flange portion being fixed to the speed reducer casing by a fixing member, and more than the fixing member On the radially inner side, a seal member is disposed between the flange portion and the speed reducer casing. The inner diameter of the flange portion is smaller than the outer diameter of the bearing, and the protruding shaft has an axial direction of the bearing. moving recess to place the regulating member for regulating is provided and have a separable part the restricting member in the circumferential direction, the inner edge portion is brought into contact with the reduction gear casing of the flange portion , Outside portion of the inner edge by have a gap between the reduction gear casing, in which the above-mentioned problems are eliminated.

  In the present invention, since the flange portion “formed radially inward” of the housing body and the reduction gear casing are connected by the fixing member, the distance from the center of the bearing housing to the fixing member is made shorter than before. can do. Therefore, a sufficient coupling and fixing force can be obtained between the reduction gear casing and the bearing housing without increasing the number of fixing members and seal members, and lubricant leakage can be prevented.

  Further, in the present invention, the restricting member that restricts the axial movement of the bearing is configured to have a portion that can be separated in the circumferential direction, so that the assemblability is not impaired.

  According to the present invention, the possibility of lubricant leakage can be reduced without impairing assembly.

Sectional drawing of the reduction gear to which an example of embodiment which concerns on this invention was applied Schematic diagram showing the regulating member in FIG. 1 (top view (A), side view (B)) Schematic diagram showing the assembly procedure of the speed reducer of FIG. 1 (assembly of speed reduction mechanism (A), assembly of bearing housing (B)) Schematic diagram showing the assembly procedure of the reduction gear of FIG. 1 (bearing assembly (A), regulation member assembly (B)) Schematic diagram showing assembly procedure of reduction gear of FIG. 1 (bearing assembly (A), spacer assembly (B)) Schematic diagram showing assembly procedure of reduction gear of FIG. 1 (Flange cover assembly (A), seal cover assembly (B)) Schematic diagram showing the assembly procedure of the reduction gear of Fig. 1 (Assembly of oil seal and seal presser)

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

  First, an outline of the reduction gear device 100 will be described below.

  The speed reduction device 100 includes a speed reducer casing 128 that houses the speed reduction mechanism 102, and a bearing housing 130 that houses a bearing 126 that supports an output shaft (projection shaft) 122 projecting from the speed reducer casing 128. The bearing housing 130 includes a cylindrical housing main body 132 and a flange portion 134 that is formed radially inward from one axial end O of the housing main body 132. The flange portion 134 is fixed to the reduction gear casing 128 with bolts (fixing members) 154, and a seal member 148 is disposed between the flange portion 134 and the reduction gear casing 128 on the radially inner side of the bolt 154. ing. Further, the inner diameter D2 of the flange portion 134 is smaller than the outer diameter d5 of the bearing 126. The output shaft 122 is provided with a recess in which a restricting member 138 for restricting the movement of the bearing 126 in the axial direction O is provided, and the restricting member 138 has a portion that can be separated in the circumferential direction.

  Next, the overall configuration of the reduction gear 100 will be described below.

  The reduction gear 100 includes a reduction gear casing 128 that houses a reduction gear mechanism 102 that is a parallel shaft type two-stage reduction gear using a helical gear. The reduction gear casing 128 is filled with a lubricant (lubricating oil) that lubricates the speed reduction mechanism 102. The reduction gear 100 is used by being connected to a motor (not shown). In addition to the input shaft 104 that receives power from the motor via a key, the speed reduction mechanism 102 includes gear shafts of an intermediate shaft 114 and an output shaft (projecting shaft) 122.

  The input shaft 104 is supported by a pair of bearings 106 and 108, and a first helical pinion 110 is attached to the input shaft 104. The intermediate shaft 114 is supported by bearings 116 and 117, and a helical gear 118 and a second helical pinion 120 that mesh with the first helical pinion 110 are mounted on the intermediate shaft 114. The helical pinions 110 and 120 and the helical gear 118 are integrated with each gear shaft (104 and 114) by a key or directly. In addition, you may integrate with a spline etc.

  One end of the output shaft 122 protruding from the opening 128C of the speed reducer casing 128 is supported by the bearing 125 at the opposite housing end 122A. An output gear 124 that meshes with the second helical pinion 120 on the intermediate shaft 114 is key-mounted on a mechanism central portion 122B adjacent to the non-housing side end portion 122A of the output shaft 122. The outer diameter d2 of the mechanism central portion 122B is larger than the outer diameter d1 of the non-housing side end portion 122A (d2> d1) and larger than the outer diameter d3 of the housing side continuous portion 122C adjacent to the mechanism central portion 122B. It is made small (d2 <d3). Therefore, the output gear 124 can be inserted from the opposite end 122A of the output shaft 122 and attached to the mechanism central portion 122B of the output shaft 122.

  The bearing 106 is a tapered roller type bearing, and the bearings 108, 116, 117, and 125 are thrust self-aligning type bearings, and each gear shaft (104, 114) is caused by rotation of a helical pinion or a helical gear. , 122) can be received. The bearings 108, 116, 117, and 125 have spherical holes on the outer ring raceways, so that an alignment error and shaft deflection can be allowed by performing a centering motion in the outer ring. The bearings 106, 108, 116, 117, and 125 are accommodated in the speed reducer casing 128.

On the other hand, the reduction gear 100 includes a bearing housing 130 that houses a bearing 126 that supports the other end of the output shaft 122. The bearing housing 130 includes a housing main body 132 and a flange portion 134. The housing body 132 is cylindrical. And the flange part 134 is integrally formed toward the radial inner side from the reduction gear casing 128 side end part (axial direction O one end part) of the housing main body 132. As shown in FIG. The flange part 134 is provided with an opening part 134C having an inner diameter D2 through which the output shaft 122 passes. A peripheral portion close to the opening portion 134C is an inner edge portion 134A, and a portion outside the inner edge portion 134A is an outer edge portion 134B. Abutting portions 128A and non-contacting portions 128B are provided in the peripheral portion near the opening portion 128C of the reduction gear casing 128 so as to face and correspond to the inner edge portion 134A and the outer edge portion 134B. The inner diameter D1 of the opening 128C is larger than the inner diameter D2 of the opening 134C of the flange portion 134 (D1> D2). The abutting portion 128A abuts on the inner edge portion 134A and constitutes an abutting region. In contrast, the non-contact portion 128B faces the outer edge portion 134B with a gap G therebetween. That is, the inner edge portion 134A of the flange portion 134 abuts on the reduction gear casing 128, and the outer edge portion 134B that is an outer portion of the inner edge portion 134A has a gap G between the non-contact portion 128B of the reduction gear casing 128. It is configured.

  A convex portion 134AA is provided on the inner edge portion 134A. Correspondingly, the contact portion 128A is provided with a recess 128AA. That is, the inner edge portion 134A and the abutting portion 128A constitute a wax, and the positioning for connecting the speed reducer casing 128 and the bearing housing 130 is easy. A seal member 148 is disposed on the radially outer side of the convex portion 134AA. The seal member 148 employs an O-ring in this embodiment. However, for example, liquid packing may be used. In the present embodiment, the seal member 148 is disposed on the flange portion 134 side, but may be disposed on the reduction gear casing 128 side. Further outside the seal member 148 in the radial direction, the flange portion 134 is connected and fixed to the reduction gear casing 128 by a bolt (fixing member) 154. That is, the seal member 148 is disposed between the flange portion 134 and the reduction gear casing 128 on the radially inner side of the bolt 154. It should be noted that both the seal member 148 and the bolt 154 are located inside the inner edge portion 134A. A plurality of bolts 154 are provided at equal intervals in the circumferential direction.

  The bearing 126 is disposed inside the housing main body 132 and supports the first support portion 122E of the output shaft 122. As shown in FIG. 1, the first support portion 122E is adjacent to the casing side connection portion 122D following the housing side connection portion 122C of the output shaft 122, and has the maximum outer diameter d4 at the output shaft 122. That is, in the output shaft 122, the portion where the bearing 126 is disposed has the maximum diameter d4. The output shaft 122 is integrally formed by cutting after heat-treating (hardening) the base material. That is, the first support portion 122E of the output shaft 122 uses a surface layer portion that has a small machining allowance from the base material and has a high heat treatment effect.

The outer diameter d5 of the bearing 126 is rot larger than the inner diameter D2 of the opening 134C of the flange portion 134 (d5> D2), bearing 126 is configured to assemble the counter-flange side in the axial direction O to the bearing housing 130 ing. The bearing 126 is also a thrust self-aligning type bearing, and can receive a thrust load applied to the output shaft 122 due to rotation of the output gear 124 that is a helical gear. The bearing 126 also has a spherical hole in the outer ring raceway, like the bearings 108, 116, 117, and 125, and therefore allows for mounting errors and shaft deflection by performing a centering motion in the outer ring. Can do. Unlike the bearings 108, 116, 117, and 125, the bearing 126 is a single row and has a large size. Therefore, it is possible to receive a larger unidirectional thrust load than the bearings 108, 116, 117 and 125.

  The restricting member 138 is also disposed inside the housing body 132. The restricting member 138 is assembled to the restricting position portion 122F adjacent to the first support portion 122E of the output shaft 122. The outer diameter d6 of the restriction position portion 122F is smaller than the outer diameter d4 of the first support portion 122E and the outer diameter d7 of the positioning portion 122G adjacent to the restriction position portion 122F (d6 <d7 <d4). That is, by providing the restricting position portion 122F, the output shaft 122 is provided with a recess in which the restricting member 138 for restricting the axial movement of the bearing 126 is disposed. As shown in FIGS. 2A and 2B, the restricting member 138 has a ring shape and is divided into semicircular first and second divided bodies 138A and 138B. That is, the restricting member 138 is configured to have two portions that can be separated in the circumferential direction. The first and second divided bodies 138A and 138B are provided with four bolt holes 138AA and 138BA, respectively. For this reason, the regulating member 138 is not limited to its inner diameter, and can be disposed at the regulating position portion 122F by separating the regulating member 138, and can be connected to each other with a bolt. That is, the restricting member 138 is composed of two divided bodies (first and second divided bodies 138A and 138B), and the divided bodies 138A and 138B are connected and fixed to each other in a state where the divided bodies 138A and 138B are arranged in the recesses of the output shaft 122. It becomes the composition which is done.

  The bearing 140 is assembled to the second support portion 122H adjacent to the positioning portion 122G of the output shaft 122. As the bearing 140, an inexpensive ball bearing can be used because the thrust load applied to the output shaft 122 is received by the bearings 125 and 126. Positioning of the bearing 140 in the axial direction O is performed by a positioning portion 122G having an outer diameter d7 (d8 <d7) larger than the outer diameter d8 of the second support portion 122H and the spacer 142. The spacer 142 is configured such that a coil spring is provided on the outer periphery. The outer position of the spacer 142 in the axial direction O is determined by an inner protrusion 136A provided on the inner side of the flange cover 136. The flange cover 136 is fixed to the housing main body 132 by bolts 156.

  The oil seal 152 is assembled to the non-casing side end portion 122I located at the outermost end portion of the output shaft 122 and adjacent to the second support portion 122H of the output shaft 122. The outer periphery of the oil seal 152 is supported by a seal cover 144 disposed on the outer side in the radial direction, and an axial end portion thereof is pressed by a seal presser 146. The seal cover 144 is fixed to the inner convex portion 136 </ b> A of the flange cover 136 with bolts 158, and the seal presser 146 is fixed to the seal cover 144 with bolts 160. Reference numerals 112 and 150 are also oil seals, and the airtightness inside and outside the reduction gear 100 is maintained by these.

  Next, the operation of the reduction gear 100 will be described.

  When the motor shaft of a motor (not shown) rotates, the input shaft 104 connected to the motor shaft via a key rotates. When the input shaft 104 rotates, the intermediate shaft 114 rotates through meshing of the first helical pinion 110 and the helical gear 118, and further, the output shaft 122 rotates through meshing of the second helical pinion 120 and the output gear 124. At this time, since all the gears are helical gears or helical pinions, the tooth contact of each gear is dispersed, and the reduction gear 100 can be made to have a small operating sound. At the same time, torque fluctuations can be reduced. In the output shaft 122 as well, since the bearings 125 and 126 are bearings that can receive a thrust load, the thrust load applied to the output shaft 122 can be reliably received.

  Next, an assembling procedure of the reduction gear 100 will be described with reference to FIGS.

  First, as shown in FIG. 3A, the speed reduction mechanism 102 is assembled to the speed reducer casing 128. That is, the input shaft 104, the intermediate shaft 114, and the output shaft 122 are incorporated in the speed reducer casing 128, and at that time, the helical pinions 110 and 120, the helical gear 118, and the output gear 124 are attached to the bearings 106, 108, 116, 117, and 125. Also incorporate. At this stage, since the bearing housing 130 is not connected and fixed to the reduction gear casing 128, the bearings 126 and 140 are not assembled to the output shaft 122. That is, the output shaft 122 is in a state of protruding in the axial direction O from the opening portion 128 </ b> C of the speed reducer casing 128 so that the casing side connection portion 122 </ b> D of the output shaft 122 is exposed.

  Next, as shown in FIG. 3B, the bearing housing 130 is assembled. Specifically, the opening part 134 </ b> C of the flange part 134 is inserted from the outside in the axial direction O into the casing side connection part 122 </ b> D of the output shaft 122. Then, the concave portion 128AA of the abutting portion 128A and the convex portion 134AA of the inner edge portion 134A are fitted and aligned to bring the abutting portion 128A into contact with the inner edge portion 134A. Then, the bolt 154 is rotated by the L-shaped tool TL, and the contact portion 128A and the inner edge portion 134A are connected and fixed by screwing the bolt 154. Thus, the outer edge portion 134B is configured to face the non-contact portion 128B via the gap G.

  Next, as shown in FIG. 4A, the bearing 126 is assembled to the bearing housing 130 and the output shaft 122 from the side opposite to the flange in the axial direction O. Specifically, the bearing 126 is moved from the outside in the axial direction O, is loosely fitted to the output shaft 122, and is inserted into the housing main body 132 of the bearing housing 130. And the outer ring | wheel of the bearing 126 is contact | abutted to the flange part 134, and the inner ring | wheel of the bearing 126 is arrange | positioned on the outer periphery of the 1st support part 122E of the output shaft 122. FIG.

  Next, as shown in FIG. 4B, the regulating member 138 is assembled to the output shaft 122 from the side opposite to the flange in the axial direction O. Specifically, the restricting member 138 is moved to the restricting position portion 122F of the output shaft 122 from the radial direction while being separated into the first and second divided bodies 138A and 138B. That is, the first and second divided bodies 138A and 138B are fitted into the recesses of the output shaft 122 formed by the first support part 122E, the restriction position part 122F, and the positioning part 122G. Then, the bolts are engaged with the bolt holes 138AA and 138BA shown in FIGS. 2A and 2B to connect the first and second divided bodies 138A and 138B. Thereby, the movement of the bearing 126 in the axial direction O is restricted.

  Next, as shown in FIG. 5A, the bearing 140 is assembled to the output shaft 122 from the side opposite to the flange in the axial direction O. Specifically, the bearing 140 is moved from the outside in the axial direction O and is loosely fitted to the output shaft 122, and is moved to a position where the inner ring of the bearing 140 contacts the side surface of the positioning portion 122G of the output shaft 122. It arrange | positions on the outer periphery of 122H.

  Next, as shown in FIG. 5B, the spacer 142 is assembled from the side opposite to the flange in the axial direction O. Specifically, the spacer 142 is moved from the outside in the axial direction O, is loosely fitted to the output shaft 122, and is moved to a position where it abuts against the outer ring of the bearing 140.

  Next, as shown in FIG. 6A, the flange cover 136 is assembled from the side opposite to the flange in the axial direction O. Specifically, the flange cover 136 is moved from the outside in the axial direction O and is loosely fitted to the output shaft 122. Then, the outer ring of the bearing 140 and the spacer 142 are fitted inside the flange cover 136. Then, the axial O end surface of the flange cover 136 and the axial O end surface of the bearing housing 130 are brought into contact with each other. Then, the flange cover 136 and the bearing housing 130 are connected and fixed with bolts 156. At this time, the spacer 142 is pressed against the bearing 140 by the inner convex portion 136A of the flange cover 136. That is, the bearing 140 is positioned in the axial direction O by the positioning portion 122G of the output shaft 122 and the flange cover 136 via the spacer 142.

  Next, as shown in FIG. 6B, the seal cover 144 is assembled to the flange cover 136 from the side opposite to the flange in the axial direction O. Specifically, the seal cover 144 is moved from the outside in the axial direction O and is fitted inside the flange cover 136. Then, the seal cover 144 is fixed to the inner convex portion 136 </ b> A of the flange cover 136 with a bolt 158.

  Next, as shown in FIG. 7, the oil seal 152 is assembled to the output shaft 122 from the side opposite to the flange in the axial direction O. Specifically, the oil seal 152 is moved from the outside in the axial direction O, and is inserted and disposed between the seal cover 144 and the opposite end 122 </ b> I of the output shaft 122. Then, the seal presser 146 is moved from the outside in the axial direction O and disposed at the position of the oil seal 152, and the seal presser 146 is fixed to the seal cover 144 with the bolt 160.

In the present embodiment, the flange portion 134 “formed radially inward” of the housing main body 132 and the reduction gear casing 128 are connected by a bolt 154. For this reason, the distance from the axial center O (the center of the bearing housing 130) of the output shaft 122 to the bolt 154 can be made shorter than before. That is, if the same number of bolts 154 as in the prior art are used, the pitch interval of the bolts 154 is shortened. In addition, the contact area (the contact part 128A and the inner edge part 134A) where the reduction gear casing 128 and the bearing housing 130 contact each other is the radially inner side of the housing main body 132, and the contact area is made smaller than before. Can do. That is, it is possible to increase the connection fixing force exerted on the contact area as compared with the conventional case. Therefore, it is possible to apply a larger pressure than the conventional pressure to the seal member 148 located on the inner side in the radial direction of the bolt 154, and to improve the airtightness of the seal member 148. In other words, (without reducing the assembling property) without increasing the number of bolts 154 and the sealing member 148, it is possible to obtain a sufficient consolidated fixing force between the reduction gear casing 128 and the bearing housing 130, a lubricant Can prevent leakage.

  At this time, in the present embodiment, the flange portion 134 and the reduction gear casing 128 are connected and fixed by the bolt 156, so that the inner diameter D2 of the flange portion 134 is smaller than the outer diameter d5 of the bearing 126 (D2 < d5). For this reason, the bearing 126 is assembled to the output shaft 122 only from the side opposite to the flange in the axial direction O. However, the restricting member 138 has a configuration having separable portions at two locations in the circumferential direction (first and second). Divided bodies 138A and 138B). That is, as described above, after the bearing 126 is assembled to the output shaft 122 from the side opposite the flange in the axial direction O, the restriction member 138 can be easily assembled to the output shaft 122 from the side opposite the flange in the axial direction O. Is possible, and assembly is good.

  Further, in the present embodiment, the regulating member 138 is configured by two divided bodies (first and second divided bodies 138A, 138B), and the respective divided bodies 138A, 138B are arranged in the recesses of the output shaft 122. And are connected and fixed to each other. That is, the restricting member 138 can be easily disposed in the recess of the output shaft 122 and securely fixed. In addition, the size (the thickness in the radial direction and the width in the axial direction O) and the material of the regulating member 138 can be optimized so that the thrust load applied to the output shaft 122 can be sufficiently received. However, the present invention is not limited thereto, and may be a retaining ring type structure having a portion (slit) that can be separated at one place in the circumferential direction of the regulating member. In this case, since the material is a spring material, the inner diameter can be enlarged, and the restricting member can be disposed in the concave portion of the output shaft, and the corresponding strength can be provided.

  In the present embodiment, the inner edge portion 134A of the flange portion 134 is in contact with the contact portion 128A of the reduction gear casing 128, and the outer edge portion 134B outside the inner edge portion 134A is the non-contact portion 128B of the reduction gear casing 128. There is a gap G between them. That is, by setting the contact area as a part of the area where the reduction gear casing 128 and the flange portion 134 face each other, a large coupling fixing force can be exerted on the narrow contact area. At the same time, it is possible to finish only the contact portion 128A and the inner edge portion 134A having a small area. For this reason, it is easy to make processing cost low and to make contact part 128A and inner edge part 134A high processing accuracy. However, the present invention is not limited to this, and there is no outer edge portion, and the entire flange portion 134 may be brought into contact with the speed reducer casing 128.

  In the present embodiment, the output shaft 122 has the maximum diameter d4 at the first support portion 122E where the bearing 126 is disposed. For this reason, the surface layer part which can reduce the machining allowance in the 1st support part 122E from a base material, and has a high effect of heat processing can be used for the 1st support part 122E. However, the present invention is not limited to this, and it is sufficient that the bearing supported by the bearing housing from the side opposite to the casing in the axial direction O can be assembled to at least the first support portion of the output shaft. It does not have to be.

  Therefore, in the present embodiment, the possibility of lubricant leakage from the contact area between the reduction gear casing 128 of the reduction gear 100 and the bearing housing 130 can be reduced without impairing the assembly of the reduction gear 100. .

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

  In the above-described embodiment, the projecting shaft that projects from the speed reducer casing 128 is the output shaft 122. However, the present invention is not limited to this, and any shaft that projects from the speed reducer casing may be used. The projecting shaft projecting from the input shaft may be an input shaft or an intermediate shaft (as in the conventional example).

  Moreover, in the said embodiment, although the reduction mechanism 102 was the reduction device 100 which is a two-stage parallel axis | shaft type | mold which has a helical gear set, the kind of reduction mechanism is not limited. For example, the number of deceleration stages may be one, or three or more. Alternatively, an orthogonal axis type reduction mechanism may be used. Furthermore, it may not be a helical gear set.

  Further, the bearing that supports the protruding shaft protruding from the reduction gear casing may not be a thrust bearing when it is not necessary to receive the thrust load.

  In the above embodiment, the bolt 154 is used as a fixing member for fixing the bearing housing 130 to the reduction gear casing 128. However, the fixing means is not limited to the bolt, and the flange portion 134 of the bearing housing 130 is connected to the reduction gear. Any material that can be fixed to the casing 128 may be used.

  The present invention is widely applicable to a speed reducer including a speed reducer casing that houses a speed reduction mechanism and a bearing housing that houses a bearing that supports a projecting shaft that projects from the speed reducer casing.

DESCRIPTION OF SYMBOLS 100 ... Deceleration apparatus 102 ... Deceleration mechanism 104 ... Input shaft 106,108,116,117,125,126,140 ... Bearing 110,120 ... Helical pinion 112,150,152 ... Oil seal 114 ... Intermediate shaft 118,124 ... Helical gear , Output gear 122 ... output shaft 128 ... reduction gear casing 128A ... contact portion 128B ... non-contact portion 130 ... bearing housing 132 ... housing main body 134 ... flange portion 134A ... inner edge portion 134B ... outer edge portion 136 ... flange cover 138 ... regulation Member 142 ... Spacer 144 ... Seal cover 146 ... Seal presser 148 ... Seal member 154, 156, 158, 160 ... Bolt

Claims (3)

In a speed reducer comprising: a speed reducer casing that houses a speed reduction mechanism; and a bearing housing that houses a bearing that supports a projecting shaft projecting from the speed reducer casing;
The bearing housing has a cylindrical housing body, and a flange portion formed radially inward from one axial end portion of the housing body,
The flange portion is fixed to the speed reducer casing by a fixing member, and a seal member is disposed between the flange portion and the speed reducer casing at a radially inner side than the fixing member,
The inner diameter of the flange portion is smaller than the outer diameter of the bearing,
The protruding shaft is provided with a recess for disposing a regulating member that regulates the axial movement of the bearing.
The regulating member has a circumferentially separable part,
The speed reducing device, wherein an inner edge portion of the flange portion is in contact with the speed reducer casing, and a portion outside the inner edge portion has a gap with the speed reducer casing. In claim 1,
The restriction member is configured by two or more divided bodies, and each divided body is connected and fixed to each other in a state where the divided bodies are disposed in the concave portion of the protruding shaft. In claim 1 or 2 ,
The projecting shaft has a maximum diameter at a portion where the bearing is disposed.

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