JP2010216551A - Reduction gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a safer reduction gear having non-complicated construction for preventing the fall-off of a rotary casing even when strong impact is applied thereto to possibly destroy internal part of a speed reducer (a connecting member). <P>SOLUTION: The reduction gear 300 includes a ring member 313 provided on the rotary casing 317, an inside member 312 inscribed on the ring member 313, first and second supporting blocks 314, 315 arranged on both axial sides of the inside member 312, and the connecting member 323 connecting the first and second supporting blocks 314, 315 to each other. The first supporting block 314 is fixed to a fixing part 308 to output rotation from the rotary casing 317. At least parts of the casing 317 and the fixing part 308 or the first supporting block 314 are opposed to each other via a clearance 350. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a reduction gear.

  Patent Document 1 discloses a reduction gear 30 as shown in FIG.

  FIG. 8 is a longitudinal sectional view of the speed reducer 30.

  The speed reducer 30 is fixed to the casing 36 with a slight difference in the number of teeth from the input shaft 32, the external gear 34 that rotates eccentrically around the input shaft 32, and the external gear 34. An internal gear 38 in which the tooth gear 34 is inscribed and meshed, and first and second support blocks 40 and 41 disposed on both sides in the axial direction of the external gear 34 are provided. In this example, the eccentric body shaft 50 penetrates the external gear 34 in the axial direction and transmits the relative rotation of the internal gear 38 and the external gear 34 to the first support block 40 and the second support block 41. ing.

  The first support block 40 is firmly connected to the carrier pin 68 by a stepped portion 68B of the carrier pin 68 and a bolt (not shown). Further, the second support block 41 is firmly connected to the carrier pin 68 by the stepped portion 68 </ b> C of the carrier pin 68 and the hooked bolt 77. For this reason, the first and second support blocks 40 and 41 are not dropped from the casing 36 during normal operation. However, if the carrier pin 68 or the hooked bolt 77 is broken, the first support block 40 may drop from the casing 36. Therefore, in this conventional example, the following measures are taken.

  A plate 70 having a protrusion 70 </ b> A is provided at an end 36 </ b> A (the left end in FIG. 1) of the casing 36. The first support block 40 is formed with a convex facing portion 40A that faces the protruding portion 70A. The outer diameter d1 of the facing portion 40A is set larger than the inner diameter D1 of the protruding portion 70A. That is, the protrusion 70A and the facing portion 40A partially overlap each other when viewed from the axial direction. Thereby, even if the carrier pin 68 or the hooked bolt 77 is broken, the first support block 40 is prevented from dropping from the casing 36 due to the engagement between the projection 70A and the facing portion 40A.

  That is, in a reduction gear of the type in which the casing is fixed and the shaft inside the casing (for example, the output shaft) rotates, even if the inside of the reduction gear is broken, the projection is integrated with the shaft. This prevents structural members from separating from the casing and prevents them from falling off the casing.

Japanese Patent Laid-Open No. 2004-138094 (Claim 1, FIG. 1)

  However, when the second support block 41 is fixed and the rotation is extracted from the casing 36, the casing 36 itself falls together with the first support block 40 when the carrier pin 68 or the hooked bolt 77 is broken. End up.

  The present invention has been made to solve such a conventional problem, and particularly in a speed reduction device that extracts rotation from a casing, even if a connecting member such as a carrier pin is broken, the rotation casing or the rotation The problem is to structurally prevent the reduction of most of the reduction gears including the casing from dropping and to enhance the safety of the reduction gears.

  The present invention includes a ring member provided in a casing, an inner member inscribed in the ring member, first and second support blocks disposed on both axial sides of the inner member, and the first and second supports. And a connecting member for connecting the blocks, wherein the first support block is fixed to the fixed portion, the rotation is taken out from the casing, the rotating casing, and the fixed portion or the first support. The above-described problem is solved by adopting a configuration in which at least a part of the block is opposed to each other with a gap.

  In the present invention, the first support block is fixed to a fixed portion and rotation is taken out from the casing, and the rotating casing and the fixed portion or the first support block face each other with a gap. .

  As a result, when the situation where the connecting member breaks occurs, the casing and the fixed portion or the first support block face each other with a gap between the casing and the speed reduction device that extracts rotation from the casing. It is possible to prevent the casing and the fixed portion or the first support block from being caught at the portion, and falling off as the entire speed reducer.

  In addition, since the casing and the fixing portion or the first support block have a gap that causes a labyrinth effect, inflow of chips and coolant can be prevented.

  According to the present invention, even if a strong impact is applied and a part (connection member) in the speed reducer is broken without complicating the structure, the rotary casing or most of the speed reducer including the rotary casing is dropped. This can be structurally prevented and the safety of the reduction gear can be increased.

The longitudinal cross-sectional view of the reduction gear concerning Embodiment 1 of this invention The B section enlarged view of the reduction gear concerning Embodiment 1. FIG. A longitudinal sectional view of a reduction gear according to a second embodiment of the present invention. Comparison diagram of dropout prevention mechanism shown in FIG. 2 and other dropout prevention mechanisms Overall schematic perspective view of an automatic tool changer incorporating a drive device FIG. 5 is a vertical sectional view of the automatic tool changer drive device of FIG. Front view of the tool magazine of FIG. Longitudinal sectional view of a conventional speed reducer with a protrusion inside the speed reducer

  For the sake of convenience, the automatic tool changer 1 will be described first for the sake of clarity.

  5 to 7 show an overall schematic perspective view of the automatic tool changer, a longitudinal sectional view of a driving device of the automatic tool changer, and a front view of the tool magazine, respectively.

  An automatic tool changer 1 such as a machining center automatically takes out a necessary tool 4 from a tool magazine 3 provided with many tools 4 on the outer periphery and replaces it with the tool 4 attached to the head unit 5.

  The automatic tool changer 1 includes a tool magazine 3 having a plurality of tools 4 in a casing 2. The tool magazine 3 has a disk shape, and different types of tools 4 are arranged radially. The tool magazine 3 can be rotated by a motor 10 attached to the tool magazine 3.

  On the other hand, the automatic tool changer 1 includes a head portion 5 for transmitting power to the tool 4. Further, the head portion 5 can be advanced and retracted in the vertical direction (vertical direction in FIG. 5), and is configured to be able to deliver the tool 4 from the tool magazine 3.

  With the above-described configuration, the head unit 5 selects an appropriate tool 4 according to a processing object (not shown) and processing content, and performs processing (for example, drilling or cutting).

  The reduction gear 310 and the fixed portion 308 are fixed by connecting the first support block 314 and the fixed portion 308 with a bolt 328. The tool magazine 3 is connected and fixed to the anti-fixed body side of the speed reducer 310 in such a manner as to further cover the cover 320 of the speed reducer 310. The tool magazine 3 is connected and fixed to the casing 317 by a bolt 380 provided in the casing 317 of the speed reducer 310.

  The speed reducer 310 is a so-called swinging intermeshing planetary gear speed reducer, and outputs power from the casing 317. As a result, the tool magazine main body 171 integrated by the casing 317 and the bolt 380 rotates.

  In the automatic tool changer as described above, chips and coolant (cutting oil) are scattered with processing, and these chips and coolant may enter the speed reduction device 300.

  Next, the structure of the reduction gear apparatus 300 concerning an example of embodiment of this invention is demonstrated.

  FIG. 1 shows a longitudinal sectional view of a reduction gear device 300 according to Embodiment 1 of the present invention. FIG. 2 is an enlarged view of the surfaces of the disc 319 and the first support block 314 that are provided to prevent the reduction gear from falling off in the axial direction.

  First, a schematic configuration of the reduction gear 300 will be described.

  The reduction gear device 300 mainly includes a reduction gear 310 and a fixed portion 308 to which a drive source (not shown) of the reduction gear 310 is attached.

  Reference numeral 302 in the figure indicates a recess into which a motor shaft (both not shown) of a motor (drive source) is inserted.

  A motor shaft, which is an output shaft of the motor, is connected to a joint shaft 303 installed on the fixed portion 308. A pinion 304 formed by cutting directly at the tip of the joint shaft 303 meshes with a bevel gear (bevel gear) 307. The bevel gear 307 is connected and fixed to one end of the input shaft 311 of the speed reducer 310 by a bolt 305. Further, the shaft center O2 of the pinion 304 and the shaft center O1 of the bevel gear 307 are configured to form a predetermined angle A.

  The configuration of the speed reducer 310 is as follows.

  A reduction gear 310 according to the present embodiment includes an internal gear (ring member) 313 provided in a rotary casing (casing) 317, an external gear (inner member) 312 inscribed in the internal gear 313, and an external gear. First and second support blocks 314 and 315 arranged on both sides in the axial direction of 312 and inner pins (connecting members) 323 that connect the first and second support blocks 314 and 315 are provided.

  The “rotating casing 317” in the present invention is defined to include not only the rotating casing 317 but also a member that is integrally fixed to the rotating casing 317, such as the disk 319 in the embodiment.

  The external gear 312 is in mesh with the internal gear 313 while swinging, the rotation of the external gear 312 is restricted, and the output is taken out from the rotary casing 317 provided with the internal gear 313. It is configured (described later).

  Three eccentric bodies 326 (326A, 326B, 326C) are integrally formed on the input shaft 311. The external gear 312 is incorporated on the outer periphery of the eccentric body 326 via rollers 334 (334A, 334B, 334C).

  The eccentric phase of each eccentric body 326 is shifted by 120 degrees, and the eccentric phase difference of the external gear 312 is 120 degrees.

  The external gear 312 has a slightly smaller number of teeth than the internal gear 313. The external gear 312 includes an internal pin hole 325 that passes through the external gear 312. The inner pin 323 is loosely fitted with the inner pin hole 325.

  On the other hand, the internal gear 313 includes an outer pin (roller) 340 that is rotatably mounted on the inner periphery of the rotary casing 317.

  First and second support blocks 314 and 315 are disposed on the axially fixed portion 308 side (drive source side) and the non-fixed portion side (counter drive source side) of the external gear 312, respectively. In the present embodiment, the first support block 314 on the drive source (motor) side, that is, the fixed portion 308 side is fixed to the fixed portion 308 via a bolt 328. Inner pins 323 are integrally formed on the first support block 314 (there are a plurality in the circumferential direction, but only one is shown). The inner pin 323 is connected and fixed to the disk-shaped second support block 315 by a bolt 316. That is, the inner pin 323 functions as a connecting member that constrains the rotation of the external gear 312 and connects the first and second support blocks 314 and 315.

  An inner roller 324 is attached to the outer periphery of the inner pin 323 as a sliding acceleration member.

  Next, a mechanism for preventing the reduction gear 310 from falling off and an inflow prevention mechanism for chips and the like will be described.

  In the present embodiment, the rotary casing 317 (more specifically, a disc 319 fastened to the rotary casing 317 via a bolt 318) and the first support block 314 are opposed to each other with a gap 350 therebetween. Has been.

  First, a configuration in which the disc 319 and the first support block 314 face each other will be described.

  The rotating casing 317 is provided with a disk 319 via a bolt 318 at the end of the rotating casing 317 on the axial direction fixing portion 308 side. The disc 319 has a protruding portion 319J that protrudes inward in the radial direction from the rotating casing 317. Further, a cover 320 attached to the side opposite to the fixed portion of the speed reducer 300 is fixed to the rotary casing 317 by a bolt 321. The breaking stress of the bolt 318 that fixes the disk 319 fixed to the rotating casing 317 is set to be larger than the breaking stress of the bolt 321 that holds the cover 320 on the side opposite to the fixed portion of the reduction gear 300. Yes. This is because the weight of the rotating casing 317 and the second support block that the bolt 318 supports when the inner pin 323 breaks is larger than the weight of the second support block 315 that the bolt 321 supports. It is because it is large.

  A stepped portion 314B is formed at the end of the fixed portion 308 on the first support block 314 side, and an inner peripheral portion 319C of the disc 319 faces the stepped portion 314B. The disc 319 has a first surface 319 </ b> A directed to the counter drive source side on a surface P <b> 1 intersecting the axis O <b> 1 of the rotary casing 317.

  On the other hand, the first support block 314 has a second surface 314A that faces the drive source side near the outer periphery of the end on the axial drive source side and faces the first surface 319A in a non-contact manner.

  Since the outer diameter d1 of the first support block 314 having the second surface 314A is larger than the inner diameter D1 of the disc 319 having the first surface 319A, the first surface 319A and the second surface 314A are viewed from the axial direction. It overlaps with.

  Further, the disc 319 integrated with the rotating casing 317, the fixing portion 308, and the first support block 314 have a gap 350. In this embodiment, the gap 350 is formed in a U-shaped cross section so as to surround the outer periphery of the end of the disk 319 (so that a labyrinth effect can be obtained). The width X of the gap 350 is determined by the inner diameter and axial thickness of the disk 319 in consideration of the type of coolant and the size of the chips.

  Between the rotating casing 317 and the disk 319, a washer 327 having a clearance in the circumferential direction is engaged with and disposed on the bolt 318.

  A bearing 322 A is provided between the first support block 314 and the input shaft 311, a bearing 322 C is provided between the second support block 315 and the input shaft 311, and the first support block 314 and the rotary casing 317 are provided. A bearing 322B is disposed between the second support block 315 and the rotary casing 317.

  In the present embodiment, the first support block 314 on the drive source side is fixed to the fixing unit 308. Further, since the second support block 315 is connected and fixed to the first support block 314 via the integrally formed inner pin 323, the inner pin 323 and the second support block 315 are also connected to the fixing portion 308. It is fixed.

  Next, the operation of the speed reducer 300 will be described.

  When a rotation instruction is input to a motor (drive source) (not shown), the motor shaft rotates by the specified amount (angle). The rotation of the motor shaft is transmitted to the pinion 304 through the joint shaft 303, and further transmitted to the bevel gear 307 that meshes with the pinion 304. Since the bevel gear 307 is connected and fixed to the input shaft 311 of the speed reducer 310, the input shaft 311 rotates.

  When the input shaft 311 rotates, the eccentric body 326 formed on the input shaft 311 rotates. As a result, the external gear 312 mounted on the outer periphery of the eccentric body 326 via the rollers 334 rotates and rotates. In this embodiment, since the internal pin 323 passes through the external gear 312 and this internal pin 323 is fixed to the fixing portion 308 via the first support block 314, the rotation of the external gear 312 is achieved. Is restrained. For this reason, the internal gear 313 meshed with the external gear 312 is externalized at a reduction ratio corresponding to (the number of teeth difference between the internal gear 313 and the external gear 312) / (the number of teeth of the internal gear 313). Displaces relative to the tooth gear 312 (rotates). The rotation of the internal gear 313 is taken out from the rotating casing 317 in which the internal gear 313 is integrally formed.

  The disk 319 is provided in a state where it does not come into contact with either the first support block 314 or the fixed portion 308 integrated with the first support block 314, so that the speed reducer 310 rotates during normal operation. Has no effect on. On the other hand, the second support block 315 is firmly connected to the inner pin 323. Accordingly, during normal operation, the second support block 315 and the rotating casing 317 do not fall off from the fixed portion 308 side including the first support block 314.

  However, when some accident such as a collision occurs, the internal pin 323 or the bolt 316 that looks strong in the speed reducer 310 having such a structure may break.

  Therefore, in a structure without any consideration for the breakage, if the inner pin 323 or the bolt 316 breaks, the second support block 315 and the rotating casing 317 lose their support base, and the rotating casing 317 There is a risk of falling off.

  However, in the present embodiment, the first surface 319A on the side opposite to the axial direction of the disc 319 and the second surface 314A on the end surface on the side of the fixed portion 308 of the first support block 314 overlap when viewed from the axial direction. Therefore, even if a strong impact is applied and the inner pin 323 or the bolt 316 in the speed reducer 310 is broken, the first surface 319A is caught by the second surface 314A, and the rotary casing 317 falls off structurally. Therefore, the safety of the speed reduction device 300 can be improved. Furthermore, since the cover 320 is provided so as to cover the second support block 315, the occurrence of secondary damage due to the fall of the second support block 315 can be prevented.

  In addition, since the second surface 314A is formed at the end of the first support block 314 that is originally separated from the fixed portion 308, it is not necessary to have a convex and convex engagement. Even though the shapes of the two surfaces 319A and 314A are overlapped in the radial direction, there is no problem that the flexibility and ease of assembly of the reduction gear 300 are reduced.

  Further, the disk 319 fastened by the rotating casing 317 and the bolt 318 and the fixed portion 308 or the first support block 314 are opposed to each other with a gap 350 having a width X in consideration of the size of chips and the like. It is supposed to be configured. As a result, a flow path in which the disk 319 and the fixing portion 308 or the first support block 314 are intricate is formed, and the pressure loss of the fluid that flows into the flow path increases, the flow rate decreases, and it serves as a seal. Can (labyrinth effect). As a result, it is possible to prevent chips and coolant from flowing into the workpiece around the reduction gear 300. Thereby, damage of the oil seal 341 inside the reduction gear 310 from the disc 319 is prevented.

  In addition, a washer 327 is engaged with and disposed on the bolt 318 between the rotating casing 317 and the disk 319 to ensure a circumferential clearance. Thereby, even if the coolant enters the speed reducer 310 through the step portion 314B, the coolant moves vertically in the speed reducer 310 due to gravity, and the circumferential direction secured by the washer 327 is obtained. It is discharged from the gap to the outside of the speed reducer 310.

  This circumferential clearance is adjusted by the thickness T of the washer 327. The width of the gap is determined in consideration of the viscosity of the coolant and the size of the chips in order to make the width that allows the coolant to easily come out though no chips enter.

  From the above, even if a strong impact is applied and a part of the reduction gear 310 is destroyed without complicating the structure, the rotary casing 317 or most of the reduction gear 310 including the rotary casing 317 is dropped. In addition, it is possible to improve the safety of the speed reduction device 300 by preventing the powder and liquid from flowing into the interior while structurally preventing this.

  That is, with one structure, two functions of preventing the rotation of the rotating casing 317 and the like and preventing the inflow of coolant and the like can be realized.

  In the above embodiment, the step portion 314B is provided as a space where the disk 319 faces in order to confront the first surface 319A and the second surface 314A (FIG. 2), but the outer periphery of the fixed portion 308 is circular. It may be designed to be smaller than the inner circumference D1a of the plate, and the first surface 319a1 and the second surface 314a2 may be merely opposed to each other without providing a step portion (FIG. 4 (a)). That is, a step is provided only on the first support block 314 side or only on the fixed portion 308 side (in the illustrated example, a step is formed only on the fixed portion 308b side), and a second surface 308b2 is provided here, and the first surface 319b1 and You may make it oppose (FIG.4 (b)).

  Further, a concave portion on the rotating casing 317c or 317d side and a convex portion that enters the concave portion are formed on the first support block 314c or fixed portion 308d side, and the first surface 317c1, 317d1, and the second surface 314c2 are made to face each other. , 308d2 may be formed (FIGS. 4C and 4D). Further, the first surface 319e1, 319f1, and the second surfaces 314e2, 308f2 may be formed by making the convex portions of the first support block 314e or the fixed portion 308f face the rotating casings 317e, 317f (FIG. 4E). (F)). Furthermore, a concave portion is provided only on the first support block 314g side or the fixed portion 308h side, and a convex portion that engages with the concave portion is provided on the rotary casing 317, whereby the first surface 319g1, 319h1, the second surface 314g2, 308h2 are provided. You may form (FIG.4 (g), (h)). Thus, the method of forming the first surface and the second surface is not limited to the above example. In particular, when the first surface and the second surface are formed by a combination of a step portion, a convex portion, and a concave portion, the convex portion and the concave portion do not necessarily have to be continuous over the entire circumference. The structure by which a 1st surface or a 2nd surface is formed by the convex part formed toward the radial inside from four directions may be sufficient.

  In the above case, in order to prevent the oil seal 341 from being damaged by chips, the oil seal 341 is opposed to the fixed portion 308 side (counter drive source side). More preferably, they are opposed to each other with a gap 350 having a width X that provides a labyrinth effect.

  Further, the washer 327 is used as a member that secures a clearance in the circumferential direction in order to allow the coolant that has entered the gap portion 314B to move smoothly (a part of it enters and exits), but the washer 327 is used. Instead, a specially designed member may be used. In the first place, it is not necessary to arrange a member for securing a gap such as the washer 327.

  Furthermore, if the entire reduction gear 310 can be supported when the inner pin 323 breaks, the breaking stresses of both bolts 318 and 321 may be the same. However, from the functional relationship described above, when the breaking stress of the bolt 321 is larger than the bolt 318, that is, it is not preferable that the magnitude relationship with the breaking stress of the bolts 318 and 321 in this embodiment is opposite.

  The present invention can also be applied to a speed reducer 400 as shown in FIG. 3, for example.

  In this reduction device 400, the power of a motor (drive source) (not shown) is transmitted to the input shaft 411 by meshing with a pinion 404 and a bevel gear (bevel gear) 407 that are formed by cutting directly at the tip of the joint shaft 403. . A transmission pinion 430 is formed on the input shaft 411. Further, the transmission pinion 430 meshes simultaneously with three distribution gears 431 (only one is shown in FIG. 3). The distribution gear 431 is integrated with three eccentric body shafts 432 (only one is shown in FIG. 3).

  The three eccentric body shafts 432 have two sets of six eccentric bodies 426 (only two of them 426A and 426B are shown in the illustrated example) that are eccentric in the same phase from the shaft center at the same position in the axial direction. Prepare. An external gear 412 (412A, 412B) is fitted to the eccentric body 426 via rollers 434 (only 434A, 434B are shown).

  First and second support blocks 414 and 415 are disposed on both axial sides of the external gear 412 (the drive source side and the counter drive source side), and the rotary casing 417 is relatively rotatable via bearings 422B and 422D. I support it. The second support block 415 is connected to and fixed to the first support block 414 by a bolt 416 via a carrier body (connection member) 423. With these configurations, the external gear 412 meshes with the internal gear 413 formed integrally with the rotary casing 417 while being in a state where rotation is restrained.

  Also in this embodiment, since a collision or the like occurs and the carrier body 423 is broken, the same configuration as that of the previous embodiment can be adopted, and similarly, the rotary casing 417 and the second support block 415 are used. Can be prevented from falling off. Since this configuration itself is the same as that of the previous embodiment, members having the same or similar functions are given the same reference numerals in the last two digits as in the previous embodiment, and redundant description is omitted.

  In addition, the kind of speed reducer which can apply this invention is not limited. In addition to the oscillating internal meshing reduction gear, for example, a sun gear, a planetary gear (inner member) that is externally meshed with the sun gear, and an internal gear (ring member) that is internally meshed with the planetary gear, The present invention can also be applied to a casing rotation type simple planetary gear type reduction gear having a connecting member for rotatably holding a planetary roller.

  In addition to the simple planetary gear reduction device, the ring roller (ring member) integrated with the casing, the planetary roller (inner member) inscribed in the ring roller, and the outer peripheral surface of the retainer member (planetary) roller are substantially the same. The present invention can be similarly applied to a casing rotation type friction reduction device having a cross section of a concave arcuate portion of curvature and a connecting member that rotatably holds the planetary roller from the outer peripheral side, and the same operational effects can be obtained. .

  Further, in the above-described embodiment, in order to realize both the effect of preventing the fall and the prevention of the inflow, it is opposed to the gap having a labyrinth effect, but if only the effect of preventing the fall is realized, the gap The size of is not a problem.

DESCRIPTION OF SYMBOLS 300 ... Reduction gear 308 ... Fixed part 310 ... Reduction gear 312 ... External gear (inner member)
313: Internal gear (ring member)
314: first support block 315: second support block 317: rotating casing (casing)
319 ... Disc 323 ... Inner pin (connecting member)
327 ... Washer 350 ... Gap

Claims (7)

A ring member provided in the casing, an inner member inscribed in the ring member, first and second support blocks disposed on both sides in the axial direction of the inner member, and the first and second support blocks are coupled to each other. A speed reducer having a connecting member,
The first support block is fixed to a fixed portion and rotation is taken out from the casing, and at least a part of the rotating casing and the fixed portion or the first support block face each other with a gap therebetween. A casing rotation type speed reducer characterized by comprising: In claim 1,
The casing has a first surface formed toward the counter-drive source side on a surface intersecting the axis of the casing;
The first support block has a second surface facing the first surface in a non-contact manner. In claim 1,
A stepped portion is formed at an end of the fixed portion on the first support block side. In claims 1 to 3,
A disk having a protruding portion protruding radially inward from the casing is fixed to an end of the casing on the axial drive source side, and the protruding portion of the disk and the fixed portion or the first A casing rotation type speed reducing device, wherein the support block faces the support block with a gap. In claim 4,
A member capable of securing a gap is disposed between the casing and the disc. In claim 5,
The disc is fixed to the casing with a bolt, and a washer that also functions as a member that can secure the gap is provided on the bolt between the casing and the disc. A casing rotation type speed reducer characterized by the above. In any one of Claims 4-6,
The disc is fixed to the casing by a bolt, the cover on the counter drive source side of the reduction gear is fixed to the casing by a bolt, and the rupture stress of the bolt fixing the disc is The casing rotating type reduction gear is characterized in that it is set to be larger than the breaking stress of the bolt holding the cover on the side opposite to the driving source of the reduction gear.

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