WO2013102991A1 - Hoisting machine, and rotating electrical machine provided with same - Google Patents

Hoisting machine, and rotating electrical machine provided with same Download PDF

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Publication number
WO2013102991A1
WO2013102991A1 PCT/JP2012/008417 JP2012008417W WO2013102991A1 WO 2013102991 A1 WO2013102991 A1 WO 2013102991A1 JP 2012008417 W JP2012008417 W JP 2012008417W WO 2013102991 A1 WO2013102991 A1 WO 2013102991A1
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WO
WIPO (PCT)
Prior art keywords
spider
hoisting machine
fitting
outer peripheral
bearing
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Application number
PCT/JP2012/008417
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French (fr)
Japanese (ja)
Inventor
圭史 尾崎
Original Assignee
株式会社 東芝
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Publication date
Application filed by 株式会社 東芝 filed Critical 株式会社 東芝
Priority to CN201280066039.2A priority Critical patent/CN104039677B/en
Publication of WO2013102991A1 publication Critical patent/WO2013102991A1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B11/00—Main component parts of lifts in, or associated with, buildings or other structures
    • B66B11/04—Driving gear ; Details thereof, e.g. seals
    • B66B11/043—Driving gear ; Details thereof, e.g. seals actuated by rotating motor; Details, e.g. ventilation
    • B66B11/0438—Driving gear ; Details thereof, e.g. seals actuated by rotating motor; Details, e.g. ventilation with a gearless driving, e.g. integrated sheave, drum or winch in the stator or rotor of the cage motor

Definitions

  • Embodiments of the present invention relate to a hoisting machine and a rotating electric machine including the same.
  • the elevator hoist includes a rotating shaft that rotates a sheave on which a rope is wound, a spider that is locked around the tip of the rotating shaft with a key, and a rotor that is fitted to the outer periphery of the spider. It is equipped with.
  • Patent Literature 1 Japanese published patent gazettes and Japanese Patent Laid-Open No. 11-165970 (hereinafter referred to as Patent Literature 1).
  • the magnetic flux generated in the gap formed by the stator and the rotor includes a fundamental wave that generates torque and other harmonics.
  • One of the harmonics is an eccentric harmonic, and this eccentric harmonic is classified into a static eccentric harmonic and a dynamic eccentric harmonic.
  • These magnetic fluxes act as a magnetic attractive force between the stator and the rotor, causing the stator to be deformed into a polygon or bending the spider to generate vibration. If this vibration is outside the audible range, it becomes electromagnetic vibration, and if it is within the audible range, it becomes electromagnetic noise.
  • the cause of vibrations caused by the fundamental wave or a combination of the fundamental wave and static eccentric harmonics is a mechanical imbalance in the gap length due to poor roundness (center misalignment) of the stator and rotor. It is done.
  • As a cause of the vibration caused by the combination of the fundamental wave and the dynamic eccentric harmonic there is a magnetic flux distribution imbalance in the air gap due to the swing of the rotor (such as shaft bending). And the gap length imbalance before or during operation causes vibration and noise.
  • the spider is supported only on the tubular shape portion of the spider at the fitting portion of the rotating shaft. For this reason, it is easy to generate
  • the present invention has been made in view of the above circumstances, and provides a hoisting machine capable of suppressing noise and vibration during operation without causing deterioration of assemblability and a rotating electrical machine including the same. Let it be an issue.
  • a hoisting machine includes a rotating shaft in which a sheave is fixed around a shaft and supported by a bearing, and a spider that is fitted to the tip of the rotating shaft.
  • the front end portion is formed with a front end outer peripheral portion for fitting and a fitting convex portion extending in the axial direction from the front end side.
  • the spider is formed with a convex fitting portion that fits on the outer peripheral side of the convex portion on the rotating shaft side, and a rear end extending portion that fits on the outer peripheral portion of the tip portion.
  • FIG. 1 is a front partial sectional view showing the configuration of the hoist according to the present embodiment.
  • FIG. 2 is a perspective view of the hoist according to the present embodiment.
  • FIG. 3 is a partial cross-sectional development view showing the configuration of the hoist according to the present embodiment.
  • the hoisting machine M1 includes a pair of bearings 4 and 5 provided on bearing bases 2 and 3 erected on the mounting base 1, a pair of bearings 4, 5, a rotating shaft 19 supported by the rotating shaft 19, a rotor C fitted to the rotating shaft 19, and a stator S disposed on the outer peripheral side of the rotor C.
  • a sheave 7 around which an elevator rope is wound is fixed to the rotary shaft 19 around the shaft. With this configuration, the drive unit of the hoisting machine is overhanging.
  • the front end portion 19f of the rotary shaft 19 is formed with a front end portion outer peripheral portion 19e for fitting and a fitting convex portion 19t extending in the axial direction from the front end side.
  • the convex portion 19t has a disk shape with a smaller diameter than the outer diameter of the outer peripheral portion 19e of the tip portion.
  • the rotor C has a rotor core 10 and a spider 18 that fits into the rotor core 10.
  • the spider 18 extends in a cylindrical shape at the distal end side and is fitted to the inner peripheral side of the rotor core 10 and extends from the base end side of the core fitting portion 18k to the inner diameter side.
  • a convex fitting portion 18f fitted on the outer peripheral side of the convex portion 19t, and a rear end extending portion 18b extending in a cylindrical shape from the proximal end side of the iron core fitting portion 18k to the rotating shaft 19 side, Have.
  • the protrusion fitting portion 18f is formed of a ring-shaped disk portion.
  • the rear end side extending portion 18b is located on the outer peripheral side of the front end portion outer peripheral portion 19e, and when the hoisting machine M1 is assembled, the convex fitting portion 18f and the convex portion 19t are fitted.
  • the rear end side extending portion 18b is fitted to the front end portion outer peripheral portion 19e so that the axis of the rear end side extending portion 18b and the axis of the rotary shaft 19 coincide with each other.
  • the stator S includes a stator core 13 that is disposed on the outer peripheral side of the rotor core 10 and forms a gap 12 with the rotor core 10, and a stator frame 15 that supports the stator core 13 from the outer peripheral side. It is equipped with.
  • the spider 18 is formed with a plurality of bolt insertion holes through which the convex fitting portion 18f is inserted, and a fixing bolt 22 through which the bolt insertion hole is inserted is screwed to the distal end portion 19f of the rotating shaft 19.
  • a female screw portion (not shown) is formed in a fixing bolt mounting hole (not shown).
  • a ring-shaped end lid (lid) 21 is provided on the spider side (rotor side) of the bearing 4 on the axially front end side of the bearings 4 and 5.
  • the end 18r of the rear end extending portion 18b reaches the inner peripheral side of the end lid 21.
  • the spider 18 and the rotary shaft 19 are fitted, the spider 18 is moved in the axial direction of the rotary shaft 19 by guiding the rear end side extending portion 18b to the tip outer peripheral portion 19e, The convex portion 19t is brought into contact with the convex fitting portion 18f. Then, the fixing bolt 22 is inserted into the bolt insertion hole and fastened to the distal end portion 19f, whereby the convex portion 19t is inserted into the convex fitting portion 18f to form the fitting portion KT, and the outer periphery of the distal end portion A fitting part KB is formed by the part 19e and the rear end side extending part 18b.
  • the spider 18 when the spider 18 is fitted to the rotary shaft 19, it is fitted by forming a double fit (double fit) by the two fitting portions KT and KB. ing.
  • the distal end portion outer peripheral portion 19e is guided by the rear end side extending portion 18b and moves in the axial direction of the rotary shaft 19. It is fitted in the direction and prevented from being fitted in the shifted direction. Therefore, the rigidity of the spider portion fitted to the rotary shaft 19 is improved, and the effect of suppressing the deflection of the spider 18 due to the weight of the rotor C and the magnetic attraction force becomes remarkable, and the assembling property is not deteriorated.
  • the hoisting machine M1 that suppresses noise and vibration during operation can be realized.
  • the rear surface 18s of the convex fitting portion 18f can be fitted in a state where the rear surface 18s is in surface contact with the ring surface 19s formed around the convex portion 19t in the tip portion 19f. Is even more appropriate.
  • the eccentric amount of the rotor C is suppressed, the imbalance of the air gap 12 can be prevented, and vibration and noise due to electromagnetic vibration can be suppressed. Furthermore, since the space
  • the spider 18 is formed with a convex fitting portion 18f that fits on the outer peripheral side of the convex portion 19t of the rotary shaft 19, and a rear end that fits on the outer peripheral portion 19e of the distal end portion of the rotary shaft 19.
  • the side extension part 18b is formed and has a double fitting structure. Therefore, when the spider 18 is pulled out at the time of disassembling such as replacement of the bearing, the one fitting portion acts as a guide portion, so that the fitting surface is prevented from being damaged.
  • the rear surface 18s of the convex fitting portion 18f and the ring surface 19s of the front end portion 19f are brought into surface contact with each other, so that the spider 18 is tilted with respect to the rotating shaft 19 by any chance.
  • the inclination can be corrected by finally tightening the fixing bolt 22.
  • the eccentricity of the rotor core 20 can be suppressed, and the gap 12 between the rotor core 10 and the stator core 13 can be kept uniform in the circumferential direction on the outer peripheral side of the rotor core 10. .
  • the elevator provided with the hoisting machine M1 according to the present embodiment, an elevator with these effects is obtained, and the elevator can suppress noise and vibration during operation.
  • FIG. 4 is a front partial sectional view showing the configuration of the hoist according to this embodiment.
  • the outer peripheral diameter ⁇ Da on the rotor C side of the spider 23, that is, the outer peripheral diameter ⁇ Da of the portion adjacent to the rotor core 10 is changed to the outer peripheral diameter on the bearing side, that is, the spider 23.
  • the diameter is larger than the outer peripheral diameter of the rear end side extending portion 23b.
  • the deflection suppressing effect of the spider 23 be enhanced, but also the grasping force (holding force) of the fitting part KB by the rear end side extension part 23b and the front end part 19f. ) Can be increased. Moreover, since the transmission torque accompanying the grasping force can be increased, the diameter of the spider 23 and the rotating shaft 19 can be reduced as compared with the conventional case with respect to the increase in the capacity of the hoisting machine driving unit.
  • FIG. 5 is a front partial sectional view showing the configuration of the hoist according to the present embodiment.
  • the outer diameter ⁇ Db1 on the bearing 4 side of the rear end side extension 24b of the spider 24 is made larger than the inner diameter ⁇ Db2 of the bearing 4 as compared with the first embodiment.
  • the rigidity of the spider 24 and the rigidity of the rotary shaft 19 can be increased, and the deflection suppression and the grasping force (holding force) of the fitting portion KT are increased. be able to.
  • the transmission torque accompanying the grasping force can be increased, the diameter of the spider 24 and the rotary shaft 19 can be reduced as compared with the conventional case with respect to the increase in the capacity of the hoisting machine driving unit. it can.
  • FIG. 6 is a front partial sectional view showing the configuration of the hoist according to this embodiment.
  • the outer diameter ⁇ Db1 on the bearing 4 side of the rear end side extending portion 25b of the spider 25 is made larger than the inner diameter ⁇ Db2 of the bearing 4 as in the third embodiment.
  • the axial position of the bearing 4 is fixed at the end portion 25r of the rear end side extending portion 25b on the bearing 4 side.
  • the end surface 4f of the bearing 4 can be used as a reference surface, so that a more accurate assembly accuracy can be obtained and the axial movement of the bearing 4 can be prevented. Can also be done.
  • FIG. 7 is a front partial sectional view showing the configuration of the hoist according to this embodiment.
  • a rib-like convex portion RP is provided between the bearing 4 and the end lid 21 on the outer peripheral portion of the spider 26 on the bearing 4 side.
  • the lubricating oil on the side can be stirred.
  • FIG. 8 is a partial front sectional view showing the configuration of the hoist according to the present embodiment.
  • the fitting portion KB between the spider 27 and the outer peripheral portion 28f of the tip end portion of the rotating shaft 28 is tapered as compared with the first embodiment.
  • FIG. 9 is a partial front sectional view showing the configuration of the hoist according to this embodiment.
  • the relationship between the length LT of the fitting portion KT and the length LB of the fitting portion KB is configured as LT> LB in the rotating shaft 29 as compared with the first embodiment. That is, the length LT of the convex portion 29t extending in the axial direction from the distal end side of the rotating shaft 29 is significantly longer than that of the first embodiment.
  • the convex part 29t becomes an insertion guide, and the eccentricity at the time of assembly can be suppressed.
  • the assembly accuracy can be improved and the gap 12 can be made more uniform in the circumferential direction.
  • FIG. 10 is a front partial cross-sectional view showing the configuration of the hoist according to the present embodiment.
  • the relationship between the length LT of the fitting portion KT and the length KB of the fitting portion KB is LT> LB, and the distal end side of the rotating shaft 30
  • the outer peripheral surface of the convex part 30t that extends in the axial direction and constitutes the fitting part KT is tapered.
  • the inner peripheral surface of the convex fitting portion 31f formed on the spider 31 is also tapered.
  • FIG. 11 is a front partial sectional view showing the configuration of the hoist according to the present embodiment.
  • the present embodiment has a structure in which a screw engagement portion N is formed in the fitting portion KB formed by the rear end side extension portion 32b of the spider 32 and the tip end outer peripheral portion 19en of the rotary shaft 19. ing.
  • the pressure input necessary to form the fitting portion KB is reduced, so that it is possible to prevent shaft bending due to press-fitting and the like, and the eccentricity with respect to the rotor C. It can be prevented.
  • the detachability is improved, and the maintainability of the hoisting machine is improved.
  • FIG. 12 is a front partial sectional view showing the configuration of the hoist according to this embodiment.
  • fins 33a are provided on the inner peripheral side of the core fitting portion 33k of the spider 33.
  • the rigidity of the spider 33 is improved by the fins 33a, the deflection suppressing effect is enhanced, and the cooling air is generated by the operation.
  • air can be blown toward the rotor S and the stator S. Accordingly, it is possible to achieve a reduction in size and weight of the hoisting machine driving unit accompanying an improvement in the cooling performance of the rotor C.
  • the fins 33a are illustrated as being provided, but from the viewpoint of the air flow rate, a plurality of fins having a cross shape or the like may actually be arranged in the axial direction. Many.
  • FIG. 13 is a front partial sectional view showing the configuration of the hoist according to this embodiment.
  • fins 34a are provided on the inner peripheral side of the core fitting portion 34k of the spider 34. Further, a ventilation hole 34h communicating with the space on the inner peripheral side of the fitting portion 34k for the iron core and the space on the bearing 4 side of the rotor core 10 is formed in the spider 34, and the cooling air generated by the fins 34a is used as a bearing. 4 and the structure which ventilates to the stator S side.
  • the cooling performance can be increased while improving the rigidity of the spider 34 with the fins 34a, and the further reduction in size and weight of the hoisting machine drive unit can be realized. be able to.
  • FIG. 14 is a front partial sectional view showing the configuration of the hoist according to the present embodiment.
  • the axial length of the fins 35a disposed on the inner peripheral side of the core fitting portion 35k of the spider 35 is set to be more axial than the axial end of the rotor core 10.
  • the configuration is extended to the outside.
  • the amount of air blown to the outer peripheral side of the stator S can be increased, and the cooling performance can be further improved.
  • FIG. 15 is a partial front sectional view showing the configuration of the hoist according to the present embodiment.
  • the axial length of the fins 36a arranged on the inner peripheral side of the core fitting portion 36k of the spider 36 is more axial than the axial end of the rotor core 10.
  • the configuration is extended to the outside.
  • the amount of air blown to the outer peripheral side of the stator S can be increased, and the cooling performance can be further improved.
  • FIG. 16 is a front partial sectional view showing the configuration of the hoist according to this embodiment.
  • the outer diameter of the core fitting portion 37k of the spider 37 is increased.
  • a fixed plate 38 that contacts the bearing 4 is disposed on the rotor C side of the bearing 4.
  • the spider 37 is formed with a plurality of bolt insertion holes through which the inner and rear end extending portions 37b of the core insertion portion 37k are inserted.
  • a female screw is formed in at least a part of the bolt insertion hole.
  • the axial position of the bearing 4 can be fixed, and the occurrence of bearing inner ring creep can be prevented.
  • FIG. 17 is a partial front sectional view showing the configuration of the hoist according to this embodiment.
  • the outer diameter ⁇ De of the core fitting portion 40k of the spider 40 is increased.
  • the spider 40 is formed with a plurality of bolt insertion holes through which the rear end side extending portion 40b of the spider 40 is inserted from the inside of the core fitting portion 40k. With this configuration, the bearing 4 is pressed by the push bolt 41 inserted through the bolt insertion hole.
  • the axial position of the bearing 4 can be fixed, and the occurrence of bearing inner ring creep can be prevented.
  • FIG. 18 is a front partial sectional view showing the configuration of the hoist according to the present embodiment.
  • the bearing 4 is arranged at the end of the spider 42 on the bearing 4 side as compared with the first embodiment. That is, the bearing 4 is in contact with the outer periphery of the end portion of the rear end side extending portion 42b of the spider 42.
  • the fitting portion KB by the rear end side extending portion 42b and the front end portion outer peripheral portion 19f of the rotating shaft 19 can be set long. Accordingly, the deflection suppressing effect can be greatly enhanced, and the length from the rotor core 10 to the end lid 21 can be shortened, which is more effective in suppressing deflection and further downsizing the hoisting machine. It becomes possible. Further, when the bearing 4 is replaced, the entire spider 42 can be taken out and disassembled.
  • FIG. 19 is a partial front sectional view showing the configuration of the hoist according to this embodiment.
  • the end portion on the bearing 4 side of the rear end extension portion 43b of the spider 43 is positioned on the rotor C side with respect to the end lid 21, and the rear end side extension
  • the axial direction length of the protruding portion 43b is shortened.
  • the deflection suppressing effect is reduced as compared with the first embodiment, but the outer diameter restriction condition of the rear end side extending portion 43b is eliminated, so that the outer diameter of the rear end side extending portion 43b is increased.
  • the same effect as that of the first embodiment can be obtained.
  • FIG. 20 is a front partial sectional view showing the configuration of the hoist according to the present embodiment.
  • a circumferential groove 44c is provided in the outer peripheral portion 44f of the tip end portion of the rotating shaft 44, and an oil injection hole 44h leading to the groove is provided.
  • the spider 45 when the spider 45 is disassembled, by applying hydraulic pressure to the oil injection hole 44h, the fitting by the core fitting portion 45k and the tip outer peripheral portion 44f of the spider 45 is performed.
  • the fitting force (holding force) of the wearing part KB can be reduced, and the disassembly can be facilitated.
  • a mechanical detent can be formed. Further, using the reamer type mounting hole, assembling can be improved by providing a guide stud during assembly / disassembly.
  • the present embodiment is an example of a hoisting machine other than the elevator hoisting machine as compared with the first to nineteenth embodiments.
  • a similar operation and effect can be obtained in a rotating electrical machine provided with a pulley or the like instead of the sheave 7.
  • FIG. 21 is a front partial sectional view showing a configuration of an example of a conventional hoisting machine.
  • a conventional hoisting machine M101 shown in FIG. 21 includes a pair of bearings 104 and 105 provided on bearing bases 102 and 103 standing on a mounting base 101, and a rotating shaft 119 supported by the pair of bearings 104 and 105, respectively.
  • a distal end outer peripheral portion 119e for fitting is formed at the distal end portion 119f of the rotating shaft 119.
  • the rotor JC has a rotor core 110 and a spider 118 that fits into the rotor core 110.
  • the stator JS includes a stator core 113, and a gap 112 is formed between the rotor core 110 and the stator core 113.
  • the spider 118 has a tubular shape portion 111m that is fitted to the outer peripheral portion 119e of the distal end portion.
  • the key 129 is arrange
  • the conventional hoisting machine M101 has the following problems (1) to (5).
  • the spider is formed with a convex fitting portion that fits to the outer peripheral side of the convex portion of the rotating shaft, and a rear end side extending portion that fits to the outer peripheral portion of the tip end portion of the rotating shaft. It has been double fitted. Therefore, when pulling out the spider, one of the fitting portions acts as a guide portion, so that damage to the fitting surface is avoided.
  • the present invention is used in an elevator or the like using a rotating electric machine.

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  • Engineering & Computer Science (AREA)
  • Civil Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Structural Engineering (AREA)
  • Cage And Drive Apparatuses For Elevators (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)

Abstract

This hoisting machine (M1) is provided with: a rotation shaft (19) to which a sheave (7) is fixed with axial rotation and which is supported by bearings (4, 5); and a spider (18) that fits the distal end section (19f) of the rotation shaft (19). The distal end section (19f) has formed thereon a distal end section outer peripheral part (19e) for fitting, and a convex part (19t) for fitting, the convex part extending from the distal end side in the axial direction. The spider (18) has formed thereon a convex-part-fitting part (18f) that fits the outer peripheral side of the convex part (19t) on the rotation shaft side, and a rear-end-side extending part (18b) that fits the distal end section outer peripheral part (19e).

Description

巻上機およびそれを備えた回転電機Hoisting machine and rotating electric machine equipped with the same
　本発明の実施形態は、巻上機およびそれを備えた回転電機に関する。 Embodiments of the present invention relate to a hoisting machine and a rotating electric machine including the same.
　エレベータでは、乗りかごを昇降動させるエレベータ用巻上機が設置されている。このエレベータ用巻上機には、ロープが巻かれる綱車を回転させる回転軸と、回転軸の先端部にキーなどで廻り止めされたスパイダーと、スパイダーの外周側に嵌合された回転子と、を備えている。例えば、日本国の公開特許公報、特開平１１－１６５９７０号公報(以下、特許文献１という）がある。 In the elevator, an elevator hoisting machine that moves the car up and down is installed. The elevator hoist includes a rotating shaft that rotates a sheave on which a rope is wound, a spider that is locked around the tip of the rotating shaft with a key, and a rotor that is fitted to the outer periphery of the spider. It is equipped with. For example, there are Japanese published patent gazettes and Japanese Patent Laid-Open No. 11-165970 (hereinafter referred to as Patent Literature 1).
　このようなエレベータでは、昨今のビルの高層化に伴い、エレベータの輸送能力を向上させる要求が強く、このため、巻上機に対し、大容量・高速化の必要性が高くなっている。 Such elevators have a strong demand for improving the transportation capacity of elevators with the recent increase in the number of buildings. Therefore, the need for large capacity and high speed for the hoisting machines is increasing.
　一方、対環境性を向上させるべく、巻上機の低騒音・低振動化の要求が高まっており、前述の大容量・高速化とは相反する要求に応える必要がある。更には、エレベータの据付工事を容易にするため、巻上機の小形・軽量化の要求もある。 On the other hand, in order to improve environmental resistance, there is an increasing demand for low noise and low vibration of the hoisting machine, and it is necessary to meet the requirements contrary to the large capacity and high speed described above. Furthermore, in order to facilitate the installation work of the elevator, there is a demand for a smaller and lighter hoisting machine.
　このような要求事項を実現させるためには、固定子－回転子間の同心(同芯)度精度を向上させることにより、損失低減・電磁騒音の低減を図ることが重要になる。 In order to realize such requirements, it is important to reduce loss and electromagnetic noise by improving the accuracy of concentricity (concentricity) between the stator and the rotor.
特開平１１－１６５９７０号公報Japanese Patent Laid-Open No. 11-165970
　ところで、固定子と回転子とによって形成される空隙に生じる磁束には、トルクを発生させる基本波と、その他に高調波とがある。高調波の１つには偏心高調波があり、この偏心高調波は静的偏心高調波と動的偏心高調波とに分類される。そして、これらの磁束が固定子と回転子との間に磁気吸引力として作用し、固定子を多角形に変形させたり、スパイダーに曲げ変形を生じさせたりして振動を発生させる。この振動が聴感範囲外であれば電磁振動となり、聴感範囲内であれば電磁騒音となる。 Incidentally, the magnetic flux generated in the gap formed by the stator and the rotor includes a fundamental wave that generates torque and other harmonics. One of the harmonics is an eccentric harmonic, and this eccentric harmonic is classified into a static eccentric harmonic and a dynamic eccentric harmonic. These magnetic fluxes act as a magnetic attractive force between the stator and the rotor, causing the stator to be deformed into a polygon or bending the spider to generate vibration. If this vibration is outside the audible range, it becomes electromagnetic vibration, and if it is within the audible range, it becomes electromagnetic noise.
　基本波、または、基本波と静的偏心高調波とを組合せたものによる振動の要因としては、固定子と回転子の真円度不良（芯ずれ）などによる空隙長の機械的不平衡が挙げられる。基本波と動的偏心高調波とを組合せたものによる振動の要因としては、回転子の振れ回り（軸曲がりなど）による上記空隙の磁束分布不平衡が挙げられる。そして、運転前または運転中の空隙長の不平衡は振動・騒音の要因となる。 The cause of vibrations caused by the fundamental wave or a combination of the fundamental wave and static eccentric harmonics is a mechanical imbalance in the gap length due to poor roundness (center misalignment) of the stator and rotor. It is done. As a cause of the vibration caused by the combination of the fundamental wave and the dynamic eccentric harmonic, there is a magnetic flux distribution imbalance in the air gap due to the swing of the rotor (such as shaft bending). And the gap length imbalance before or during operation causes vibration and noise.
　従来、スパイダーは、回転軸の嵌着部にスパイダーの管状形状部でのみで支持されている。このため、回転子の自重および磁気吸引力に伴うスパイダーのたわみが発生しやすい。そして、このたわみを抑制するには、回転子に嵌着しているスパイダー部分を大径化する必要があり、結果として巻上機の組立性の悪化や質量増の要因という弊害を招いている。 Conventionally, the spider is supported only on the tubular shape portion of the spider at the fitting portion of the rotating shaft. For this reason, it is easy to generate | occur | produce the bending of the spider accompanying the dead weight of a rotor and magnetic attraction. In order to suppress this deflection, it is necessary to increase the diameter of the spider part that is fitted to the rotor, resulting in adverse effects such as deterioration of the assembly property of the hoist and mass increase. .
　本発明は上記事情に鑑みてなされたものであり、組立性の悪化を生じさせずに、運転中の騒音、振動を抑えることができる巻上機およびそれを備えた回転電機を提供することを課題とする。 The present invention has been made in view of the above circumstances, and provides a hoisting machine capable of suppressing noise and vibration during operation without causing deterioration of assemblability and a rotating electrical machine including the same. Let it be an issue.
　本発明の実施形態に係る巻上機は、綱車が軸回りに固定されて軸受に支持された回転軸と、回転軸の先端部に嵌着するスパイダーと、を備える。先端部には、嵌着用の先端部外周部が形成されているとともに、先端側から軸方向に延び出す嵌着用の凸部が形成されている。スパイダーには、回転軸側で凸部の外周側と嵌着する凸部用嵌着部が形成されているとともに、先端部外周部に嵌着する後端側延出し部が形成されている。 A hoisting machine according to an embodiment of the present invention includes a rotating shaft in which a sheave is fixed around a shaft and supported by a bearing, and a spider that is fitted to the tip of the rotating shaft. The front end portion is formed with a front end outer peripheral portion for fitting and a fitting convex portion extending in the axial direction from the front end side. The spider is formed with a convex fitting portion that fits on the outer peripheral side of the convex portion on the rotating shaft side, and a rear end extending portion that fits on the outer peripheral portion of the tip portion.
第１実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 1st Embodiment. 第１実施形態に係る巻上機の斜視図である。It is a perspective view of the winding machine which concerns on 1st Embodiment. 第１実施形態に係る巻上機の構成を示す部分断面展開図である。It is a partial section expanded view showing composition of a winding machine concerning a 1st embodiment. 第２実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 2nd Embodiment. 第３実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 3rd Embodiment. 第４実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 4th Embodiment. 第５実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 5th Embodiment. 第６実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 6th Embodiment. 第７実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 7th Embodiment. 第８実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 8th Embodiment. 第９実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 9th Embodiment. 第１０実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 10th Embodiment. 第１１実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 11th Embodiment. 第１２実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 12th Embodiment. 第１３実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 13th Embodiment. 第１４実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 14th Embodiment. 第１５実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 15th Embodiment. 第１６実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 16th Embodiment. 第１７実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 17th Embodiment. 第１８実施形態に係る巻上機の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 18th Embodiment. 従来の巻上機の一例の構成を示す正面部分断面図である。It is a front fragmentary sectional view which shows the structure of an example of the conventional winding machine.
　以下、添付図面を参照しながら、実施形態に係る巻上機およびそれを備えた回転電機ついて説明する。なお、以下の説明では、すでに説明したものと同一または類似の構成要素には同一または類似の符号を付し、その詳細な説明を適宜省略している。また、以下の説明では、巻上機としてエレベータ用の巻上機で説明する。 Hereinafter, a hoist according to an embodiment and a rotating electrical machine including the same will be described with reference to the accompanying drawings. In the following description, the same or similar components as those already described are denoted by the same or similar reference numerals, and detailed description thereof is omitted as appropriate. In the following description, an elevator hoisting machine will be described as the hoisting machine.
　［第１実施形態］
　まず、第１実施形態について説明する。図１は、本実施形態に係る巻上機の構成を示す正面部分断面図である。図２は、本実施形態に係る巻上機の斜視図である。図３は、本実施形態に係る巻上機の構成を示す部分断面展開図である。 [First Embodiment]
First, the first embodiment will be described. FIG. 1 is a front partial sectional view showing the configuration of the hoist according to the present embodiment. FIG. 2 is a perspective view of the hoist according to the present embodiment. FIG. 3 is a partial cross-sectional development view showing the configuration of the hoist according to the present embodiment.
　図１～３に示すように、本実施形態に係る巻上機Ｍ１は、取付台１に立設する軸受台２、３にそれぞれ設けられた一対の軸受４、５と、一対の軸受４、５に支持された回転軸１９と、回転軸１９に嵌着する回転子Ｃと、回転子Ｃの外周側に配置されている固定子Ｓと、を有する。回転軸１９にはエレベータ用のロープが巻き付けられる綱車７が軸回りに固定されている。この構成により、巻上機の駆動部をオーバーハングする構成になっている。 As shown in FIGS. 1 to 3, the hoisting machine M1 according to the present embodiment includes a pair of bearings 4 and 5 provided on bearing bases 2 and 3 erected on the mounting base 1, a pair of bearings 4, 5, a rotating shaft 19 supported by the rotating shaft 19, a rotor C fitted to the rotating shaft 19, and a stator S disposed on the outer peripheral side of the rotor C. A sheave 7 around which an elevator rope is wound is fixed to the rotary shaft 19 around the shaft. With this configuration, the drive unit of the hoisting machine is overhanging.
　回転軸１９の先端部１９ｆには、嵌着用の先端部外周部１９ｅが形成されているともに、先端側から軸方向に延び出す嵌着用の凸部１９ｔが形成されている。本実施形態では、凸部１９ｔは、先端部外周部１９ｅの外径に比べて小径の円板状とされている。 The front end portion 19f of the rotary shaft 19 is formed with a front end portion outer peripheral portion 19e for fitting and a fitting convex portion 19t extending in the axial direction from the front end side. In the present embodiment, the convex portion 19t has a disk shape with a smaller diameter than the outer diameter of the outer peripheral portion 19e of the tip portion.
　回転子Ｃは、回転子鉄心１０と、回転子鉄心１０に嵌着するスパイダー１８と、を有する。スパイダー１８は、先端側に筒状に延び出して回転子鉄心１０の内周側に嵌着する鉄心用嵌着部１８ｋと、鉄心用嵌着部１８ｋの基端側から内径側に延び出して凸部１９ｔの外周側に嵌着する凸部用嵌着部１８ｆと、鉄心用嵌着部１８ｋの基端側から回転軸１９側に筒状に延び出す後端側延出し部１８ｂと、を有する。本実施形態では、凸部用嵌着部１８ｆはリング状の円板部で構成されている。また、後端側延出し部１８ｂは、先端部外周部１９ｅの外周側に位置しており、巻上機Ｍ１を組み立てる際、凸部用嵌着部１８ｆと凸部１９ｔとが嵌着するとともに、後端側延出し部１８ｂが先端部外周部１９ｅに嵌着して後端側延出し部１８ｂの軸心と回転軸１９の軸心とが一致するようになっている。 The rotor C has a rotor core 10 and a spider 18 that fits into the rotor core 10. The spider 18 extends in a cylindrical shape at the distal end side and is fitted to the inner peripheral side of the rotor core 10 and extends from the base end side of the core fitting portion 18k to the inner diameter side. A convex fitting portion 18f fitted on the outer peripheral side of the convex portion 19t, and a rear end extending portion 18b extending in a cylindrical shape from the proximal end side of the iron core fitting portion 18k to the rotating shaft 19 side, Have. In the present embodiment, the protrusion fitting portion 18f is formed of a ring-shaped disk portion. The rear end side extending portion 18b is located on the outer peripheral side of the front end portion outer peripheral portion 19e, and when the hoisting machine M1 is assembled, the convex fitting portion 18f and the convex portion 19t are fitted. The rear end side extending portion 18b is fitted to the front end portion outer peripheral portion 19e so that the axis of the rear end side extending portion 18b and the axis of the rotary shaft 19 coincide with each other.
　固定子Ｓには、回転子鉄心１０の外周側に配置されて回転子鉄心１０との間に空隙１２を形成する固定子鉄心１３と、固定子鉄心１３を外周側から支える固定子枠１５と、を備えている。 The stator S includes a stator core 13 that is disposed on the outer peripheral side of the rotor core 10 and forms a gap 12 with the rotor core 10, and a stator frame 15 that supports the stator core 13 from the outer peripheral side. It is equipped with.
　スパイダー１８には、凸部用嵌着部１８ｆを挿通する複数本のボルト挿通孔が形成されており、回転軸１９の先端部１９ｆには、ボルト挿通孔を挿通した固定ボルト２２がネジ結合する雌ネジ部（図示せず）が、固定ボルト用の取付穴（図示せず）に形成されている。 The spider 18 is formed with a plurality of bolt insertion holes through which the convex fitting portion 18f is inserted, and a fixing bolt 22 through which the bolt insertion hole is inserted is screwed to the distal end portion 19f of the rotating shaft 19. A female screw portion (not shown) is formed in a fixing bolt mounting hole (not shown).
　また、軸受４、５のうち軸方向先端側の軸受４のスパイダー側（回転子側）にはリング状の端ふた(蓋)２１が設けられている。本実施形態では、後端側延出し部１８ｂの端部１８ｒが端ふた２１の内周側にまで到達している。 Further, a ring-shaped end lid (lid) 21 is provided on the spider side (rotor side) of the bearing 4 on the axially front end side of the bearings 4 and 5. In the present embodiment, the end 18r of the rear end extending portion 18b reaches the inner peripheral side of the end lid 21.
　本実施形態では、スパイダー１８と回転軸１９とを嵌着させる際、先端部外周部１９ｅに後端側延出し部１８ｂを案内させることによってスパイダー１８を回転軸１９の軸心方向に移動させ、凸部用嵌着部１８ｆに凸部１９ｔを当接させる。そして、ボルト挿通孔に固定ボルト２２を挿通させて先端部１９ｆに締結することにより、凸部１９ｔが凸部用嵌着部１８ｆに入れられて嵌着部ＫＴが形成されるとともに、先端部外周部１９ｅと後端側延出し部１８ｂとによる嵌着部ＫＢが形成される。 In the present embodiment, when the spider 18 and the rotary shaft 19 are fitted, the spider 18 is moved in the axial direction of the rotary shaft 19 by guiding the rear end side extending portion 18b to the tip outer peripheral portion 19e, The convex portion 19t is brought into contact with the convex fitting portion 18f. Then, the fixing bolt 22 is inserted into the bolt insertion hole and fastened to the distal end portion 19f, whereby the convex portion 19t is inserted into the convex fitting portion 18f to form the fitting portion KT, and the outer periphery of the distal end portion A fitting part KB is formed by the part 19e and the rear end side extending part 18b.
　以上説明したように、本実施形態では、スパイダー１８が回転軸１９に嵌着する際、２箇所の嵌着部ＫＴ、ＫＢによる二重嵌着（二重嵌合）を形成して嵌着している。しかも、スパイダー１８が回転軸１９に嵌着する際、先端部外周部１９ｅが後端側延出し部１８ｂに案内されて回転軸１９の軸心方向に移動するので、嵌着させる際に適切な方向に嵌着され、ずれた方向に嵌着されることが防止されている。従って、回転軸１９と嵌着しているスパイダー部分の剛性が向上して、回転子Ｃの自重および磁気吸引力に伴うスパイダー１８のたわみ抑制効果が顕著となり、組立性の悪化を生じさせずに運転中の騒音、振動を抑えた巻上機Ｍ１を実現させることができる。 As described above, in the present embodiment, when the spider 18 is fitted to the rotary shaft 19, it is fitted by forming a double fit (double fit) by the two fitting portions KT and KB. ing. In addition, when the spider 18 is fitted to the rotary shaft 19, the distal end portion outer peripheral portion 19e is guided by the rear end side extending portion 18b and moves in the axial direction of the rotary shaft 19. It is fitted in the direction and prevented from being fitted in the shifted direction. Therefore, the rigidity of the spider portion fitted to the rotary shaft 19 is improved, and the effect of suppressing the deflection of the spider 18 due to the weight of the rotor C and the magnetic attraction force becomes remarkable, and the assembling property is not deteriorated. The hoisting machine M1 that suppresses noise and vibration during operation can be realized.
　そして、凸部用嵌着部１８ｆの後面１８ｓが、先端部１９ｆのうち凸部１９ｔの周囲に形成されているリング面１９ｓに面接触した状態で嵌着することが可能であり、嵌着状態が更に適切となっている。 Then, the rear surface 18s of the convex fitting portion 18f can be fitted in a state where the rear surface 18s is in surface contact with the ring surface 19s formed around the convex portion 19t in the tip portion 19f. Is even more appropriate.
　また、回転子Ｃの偏心量が抑制されるので、空隙１２の不平衡を防止することができ、電磁振動による振動、騒音を抑制することができる。更に、巻上機Ｍ１の運転時に空隙１２の間隔を精度良く維持することができるので、巻上機Ｍ１の特性向上、小型化、軽量化を実現させることができる。 Further, since the eccentric amount of the rotor C is suppressed, the imbalance of the air gap 12 can be prevented, and vibration and noise due to electromagnetic vibration can be suppressed. Furthermore, since the space | interval of the space | gap 12 can be maintained with sufficient precision at the time of driving | operation of the winding machine M1, the characteristic improvement, size reduction, and weight reduction of the winding machine M1 can be implement | achieved.
　また、スパイダー１８には、回転軸１９の凸部１９ｔの外周側と嵌着する凸部用嵌着部１８ｆが形成されているとともに、回転軸１９の先端部外周部１９ｅに嵌着する後端側延出し部１８ｂが形成されており、二重嵌着構造となっている。従って、軸受の交換時などの分解時にスパイダー１８を引抜く際、一方の嵌着部が案内部として作用するので、嵌着面に損傷が生じることが回避される。 Further, the spider 18 is formed with a convex fitting portion 18f that fits on the outer peripheral side of the convex portion 19t of the rotary shaft 19, and a rear end that fits on the outer peripheral portion 19e of the distal end portion of the rotary shaft 19. The side extension part 18b is formed and has a double fitting structure. Therefore, when the spider 18 is pulled out at the time of disassembling such as replacement of the bearing, the one fitting portion acts as a guide portion, so that the fitting surface is prevented from being damaged.
　また、凸部用嵌着部１８ｆの後面１８ｓと先端部１９ｆのリング面１９ｓとを面接触をさせることにより、万一、回転軸１９に対するスパイダー１８の傾きが発生した状態で組立てた場合であっても、最終的に固定ボルト２２を締め付けることにより、その傾きを是正することができる。この結果、回転子鉄心２０の偏心を抑制することができ、回転子鉄心１０と固定子鉄心１３との空隙１２を回転子鉄心１０の外周側で円周方向に均一に保つことが可能となる。 Further, the rear surface 18s of the convex fitting portion 18f and the ring surface 19s of the front end portion 19f are brought into surface contact with each other, so that the spider 18 is tilted with respect to the rotating shaft 19 by any chance. However, the inclination can be corrected by finally tightening the fixing bolt 22. As a result, the eccentricity of the rotor core 20 can be suppressed, and the gap 12 between the rotor core 10 and the stator core 13 can be kept uniform in the circumferential direction on the outer peripheral side of the rotor core 10. .
　また、本実施形態に係る巻上機Ｍ１を備えたエレベータでは、これらの効果が得られたエレベータとなり、運転中の騒音、振動を抑えたエレベータとすることができる。 Moreover, in the elevator provided with the hoisting machine M1 according to the present embodiment, an elevator with these effects is obtained, and the elevator can suppress noise and vibration during operation.
　［第２実施形態］
　次に、第２実施形態について説明する。図４は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Second Embodiment]
Next, a second embodiment will be described. FIG. 4 is a front partial sectional view showing the configuration of the hoist according to this embodiment.
　本実施形態では、第１実施形態に比べ、スパイダー２３の回転子Ｃ側の外周径φＤａ、すなわち、回転子鉄心１０に隣接する部位の外周径φＤａを、軸受側の外周径、すなわち、スパイダー２３の後端側延出し部２３ｂの外周径よりも大径化する。 In this embodiment, compared to the first embodiment, the outer peripheral diameter φDa on the rotor C side of the spider 23, that is, the outer peripheral diameter φDa of the portion adjacent to the rotor core 10 is changed to the outer peripheral diameter on the bearing side, that is, the spider 23. The diameter is larger than the outer peripheral diameter of the rear end side extending portion 23b.
　これにより、第１実施形態で奏される効果に加え、スパイダー２３のたわみ抑制効果を増強できるだけでなく、後端側延出し部２３ｂと先端部１９ｆとによる嵌着部ＫＢの把握力（保持力）を増加させることができる。また、把握力に伴う伝達トルクを大きくできることから、巻上機駆動部の大容量化に対し、従来に比べてスパイダー２３と回転軸１９との小径化を図ることができる。 Thereby, in addition to the effect exerted by the first embodiment, not only can the deflection suppressing effect of the spider 23 be enhanced, but also the grasping force (holding force) of the fitting part KB by the rear end side extension part 23b and the front end part 19f. ) Can be increased. Moreover, since the transmission torque accompanying the grasping force can be increased, the diameter of the spider 23 and the rotating shaft 19 can be reduced as compared with the conventional case with respect to the increase in the capacity of the hoisting machine driving unit.
　［第３実施形態］
　次に、第３実施形態について説明する。図５は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Third Embodiment]
Next, a third embodiment will be described. FIG. 5 is a front partial sectional view showing the configuration of the hoist according to the present embodiment.
　本実施形態では、第１実施形態に比べ、スパイダー２４の後端側延出し部２４ｂの軸受４側の外径φＤｂ１を軸受４の内径φＤｂ２よりも大径化する。 In this embodiment, the outer diameter φDb1 on the bearing 4 side of the rear end side extension 24b of the spider 24 is made larger than the inner diameter φDb2 of the bearing 4 as compared with the first embodiment.
　これにより、第１実施形態で奏される効果に加え、スパイダー２４の剛性と回転軸１９の剛性を増強することができ、たわみ抑制と嵌着部ＫＴの把握力（保持力）とを増加させることができる。また、第２実施形態と同様、把握力に伴う伝達トルクを大きくできることから、巻上機駆動部の大容量化に対し、従来に比べてスパイダー２４と回転軸１９との小径化を図ることができる。 Thereby, in addition to the effect produced in the first embodiment, the rigidity of the spider 24 and the rigidity of the rotary shaft 19 can be increased, and the deflection suppression and the grasping force (holding force) of the fitting portion KT are increased. be able to. Further, as in the second embodiment, since the transmission torque accompanying the grasping force can be increased, the diameter of the spider 24 and the rotary shaft 19 can be reduced as compared with the conventional case with respect to the increase in the capacity of the hoisting machine driving unit. it can.
　［第４実施形態］
　次に、第４実施形態について説明する。図６は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Fourth Embodiment]
Next, a fourth embodiment will be described. FIG. 6 is a front partial sectional view showing the configuration of the hoist according to this embodiment.
　本実施形態では、第３実施形態と同様に、スパイダー２５の後端側延出し部２５ｂの軸受４側の外径φＤｂ１を軸受４の内径φＤｂ２より大径化する。そして、第３実施形態に比べ、後端側延出し部２５ｂの軸受４側の端部２５ｒで軸受４の軸方向位置の固定を行っている。 In the present embodiment, the outer diameter φDb1 on the bearing 4 side of the rear end side extending portion 25b of the spider 25 is made larger than the inner diameter φDb2 of the bearing 4 as in the third embodiment. Compared with the third embodiment, the axial position of the bearing 4 is fixed at the end portion 25r of the rear end side extending portion 25b on the bearing 4 side.
　これにより、第３実施形態で奏される効果に加え、軸受４の端面４ｆを基準面とすることが可能となり、より精度の良い組立精度が得られ、また、軸受４の軸方向の移動防止を行うこともできる。 As a result, in addition to the effects achieved in the third embodiment, the end surface 4f of the bearing 4 can be used as a reference surface, so that a more accurate assembly accuracy can be obtained and the axial movement of the bearing 4 can be prevented. Can also be done.
　［第５実施形態］
　次に、第５実施形態について説明する。図７は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Fifth Embodiment]
Next, a fifth embodiment will be described. FIG. 7 is a front partial sectional view showing the configuration of the hoist according to this embodiment.
　本実施形態では、第１実施形態に比べ、スパイダー２６の軸受４側の外周部において、軸受４と端ふた２１との間にリブ状凸部ＲＰを設けた構成としており、軸受４のスパイダー２６側の潤滑油を攪拌することができる構成になっている。 In the present embodiment, compared to the first embodiment, a rib-like convex portion RP is provided between the bearing 4 and the end lid 21 on the outer peripheral portion of the spider 26 on the bearing 4 side. The lubricating oil on the side can be stirred.
　これにより、第１実施形態で得られる効果に加え、潤滑油の固化などによる劣化を防止することができ、軸受４の長寿命化ができる。 Thereby, in addition to the effects obtained in the first embodiment, deterioration due to solidification of the lubricating oil can be prevented, and the life of the bearing 4 can be extended.
　［第６実施形態］
　次に、第６実施形態について説明する。図８は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Sixth Embodiment]
Next, a sixth embodiment will be described. FIG. 8 is a partial front sectional view showing the configuration of the hoist according to the present embodiment.
　本実施形態では、第１実施形態に比べ、スパイダー２７と回転軸２８の先端部外周部２８ｆとの嵌着部ＫＢをテーパ状にしている。 In the present embodiment, the fitting portion KB between the spider 27 and the outer peripheral portion 28f of the tip end portion of the rotating shaft 28 is tapered as compared with the first embodiment.
　これにより、第１実施形態で奏される効果に加え、スパイダー２８と先端部外周部２８ｆとの嵌着部ＫＢにおける互いの接触面積を増加させることができるので、嵌着部ＫＢの剛性を向上させることができ、更に、嵌着時の偏心の防止・着脱の容易さも向上させることができる。 Thereby, in addition to the effect show | played by 1st Embodiment, since the mutual contact area in the fitting part KB of the spider 28 and the front-end | tip part outer peripheral part 28f can be increased, the rigidity of the fitting part KB is improved. Furthermore, the prevention of eccentricity during fitting and the ease of attachment / detachment can be improved.
　［第７実施形態］
　次に、第７実施形態について説明する。図９は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Seventh Embodiment]
Next, a seventh embodiment will be described. FIG. 9 is a partial front sectional view showing the configuration of the hoist according to this embodiment.
　本実施形態では、第１実施形態に比べ、回転軸２９において、嵌着部ＫＴの長さＬＴと嵌着部ＫＢの長さＬＢとの関係をＬＴ＞ＬＢとして構成する。すなわち、回転軸２９の先端側から軸心方向に延び出す凸部２９ｔの長さＬＴが第１実施形態よりも大幅に長い。 In the present embodiment, the relationship between the length LT of the fitting portion KT and the length LB of the fitting portion KB is configured as LT> LB in the rotating shaft 29 as compared with the first embodiment. That is, the length LT of the convex portion 29t extending in the axial direction from the distal end side of the rotating shaft 29 is significantly longer than that of the first embodiment.
　回転軸２９の先端部２９ｆよりも凸部２９ｔのほうが外径が小さいので、嵌着部ＫＴを形成する際に必要な圧入力は、嵌着部ＫＢを形成する際に必要な圧入力よりも小さい。従って、凸部２９ｔが挿入ガイドとなり、組立時の偏心抑制をすることができる。 Since the outer diameter of the convex portion 29t is smaller than that of the tip portion 29f of the rotating shaft 29, the pressure input necessary for forming the fitting portion KT is larger than the pressure input necessary for forming the fitting portion KB. small. Therefore, the convex part 29t becomes an insertion guide, and the eccentricity at the time of assembly can be suppressed.
　これにより、第１実施形態で奏される効果に加え、組立精度が向上し、空隙１２を円周方向に更に均一にすることができる。 Thereby, in addition to the effects achieved in the first embodiment, the assembly accuracy can be improved and the gap 12 can be made more uniform in the circumferential direction.
　［第８実施形態］
　次に、第８実施形態について説明する。図１０は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Eighth Embodiment]
Next, an eighth embodiment will be described. FIG. 10 is a front partial cross-sectional view showing the configuration of the hoist according to the present embodiment.
　本実施形態では、第７実施形態に比べ、回転軸３０において、嵌着部ＫＴの長さＬＴと嵌着部ＫＢの長さＫＢの関係をＬＴ＞ＬＢとし、かつ、回転軸３０の先端側から軸心方向に延び出して嵌着部ＫＴを構成している凸部３０ｔの外周面をテーパ状に構成している。これに対応させ、スパイダー３１に形成された凸部用嵌着部３１ｆの内周面もテーパ状にされている。 In this embodiment, compared to the seventh embodiment, in the rotating shaft 30, the relationship between the length LT of the fitting portion KT and the length KB of the fitting portion KB is LT> LB, and the distal end side of the rotating shaft 30 The outer peripheral surface of the convex part 30t that extends in the axial direction and constitutes the fitting part KT is tapered. Corresponding to this, the inner peripheral surface of the convex fitting portion 31f formed on the spider 31 is also tapered.
　これにより、第７実施形態で奏される効果に加え、嵌着時の偏心の防止・着脱の容易さも向上させることができる
　［第９実施形態］
　次に、第９実施形態について説明する。図１１は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 Thereby, in addition to the effect show | played by 7th Embodiment, the prevention of eccentricity at the time of insertion and the ease of attachment / detachment can also be improved [9th Embodiment].
Next, a ninth embodiment will be described. FIG. 11 is a front partial sectional view showing the configuration of the hoist according to the present embodiment.
　本実施形態では、第１実施形態に比べ、スパイダー３２の後端側延出し部３２ｂと回転軸１９の先端部外周部１９ｅｎとによる嵌着部ＫＢにねじ係合部Ｎを形成した構造になっている。 Compared with the first embodiment, the present embodiment has a structure in which a screw engagement portion N is formed in the fitting portion KB formed by the rear end side extension portion 32b of the spider 32 and the tip end outer peripheral portion 19en of the rotary shaft 19. ing.
　これにより、第１実施形態で奏される効果に加え、嵌着部ＫＢを形成するのに必要な圧入力が軽減されるので、圧入による軸曲がりなどを防止でき、回転子Ｃに対して偏心防止ができる。また、必要な圧入力の軽減により、着脱性が向上し、巻上機の保守性の向上にも繋がる。 As a result, in addition to the effects achieved in the first embodiment, the pressure input necessary to form the fitting portion KB is reduced, so that it is possible to prevent shaft bending due to press-fitting and the like, and the eccentricity with respect to the rotor C. It can be prevented. In addition, by reducing the necessary pressure input, the detachability is improved, and the maintainability of the hoisting machine is improved.
　［第１０実施形態］
　次に、第１０実施形態について説明する。図１２は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Tenth embodiment]
Next, a tenth embodiment will be described. FIG. 12 is a front partial sectional view showing the configuration of the hoist according to this embodiment.
　本実施形態では、第１実施形態に比べ、スパイダー３３の鉄心用嵌着部３３ｋの内周側にフィン３３ａを設ける。これにより、第１実施形態で奏される効果に加え、フィン３３ａでスパイダー３３の剛性向上を行い、たわみ抑制効果を増強すると共に、運転による冷却風を発生させ、この冷却風が風洞壁Ｗと回転子Ｃで形成される風洞を流れることによって、回転子Ｓや固定子Ｓに向けて送風することができる。従って、回転子Ｃの冷却性能向上に伴う巻上機駆動部の小形・軽量化を実現することができる。 In this embodiment, compared to the first embodiment, fins 33a are provided on the inner peripheral side of the core fitting portion 33k of the spider 33. Thereby, in addition to the effect produced in the first embodiment, the rigidity of the spider 33 is improved by the fins 33a, the deflection suppressing effect is enhanced, and the cooling air is generated by the operation. By flowing through the wind tunnel formed by the rotor C, air can be blown toward the rotor S and the stator S. Accordingly, it is possible to achieve a reduction in size and weight of the hoisting machine driving unit accompanying an improvement in the cooling performance of the rotor C.
　なお、図１２では１枚のフィン３３ａが設けられているように描かれているが、送風量の観点で、実際には軸方向から見て十文字状などの複数のフィンが配置されることが多い。 In FIG. 12, the fins 33a are illustrated as being provided, but from the viewpoint of the air flow rate, a plurality of fins having a cross shape or the like may actually be arranged in the axial direction. Many.
　［第１１実施形態］
　次に、第１１実施形態について説明する。図１３は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Eleventh embodiment]
Next, an eleventh embodiment will be described. FIG. 13 is a front partial sectional view showing the configuration of the hoist according to this embodiment.
　本実施形態では、第１０実施形態に比べ、スパイダー３４の鉄心用嵌着部３４ｋの内周側にフィン３４ａを設ける。更に、鉄心用嵌着部３４ｋの内周側の空間と回転子鉄心１０の軸受４側の空間とに連通する通風孔３４ｈをスパイダー３４に形成し、上述のフィン３４ａで発生した冷却風を軸受４や固定子Ｓ側へ通風する構成とする。 In this embodiment, as compared with the tenth embodiment, fins 34a are provided on the inner peripheral side of the core fitting portion 34k of the spider 34. Further, a ventilation hole 34h communicating with the space on the inner peripheral side of the fitting portion 34k for the iron core and the space on the bearing 4 side of the rotor core 10 is formed in the spider 34, and the cooling air generated by the fins 34a is used as a bearing. 4 and the structure which ventilates to the stator S side.
　これにより、第１０実施形態で奏される効果に加え、フィン３４ａでスパイダー３４の剛性を向上させつつ冷却性能を増加することができ、巻上機駆動部の更なる小形・軽量化を実現することができる。 As a result, in addition to the effects achieved in the tenth embodiment, the cooling performance can be increased while improving the rigidity of the spider 34 with the fins 34a, and the further reduction in size and weight of the hoisting machine drive unit can be realized. be able to.
　［第１２実施形態］
　次に、第１２実施形態について説明する。図１４は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Twelfth embodiment]
Next, a twelfth embodiment will be described. FIG. 14 is a front partial sectional view showing the configuration of the hoist according to the present embodiment.
　本実施形態では、第１０実施形態に比べ、スパイダー３５の鉄心用嵌着部３５ｋの内周側に配置したフィン３５ａの軸方向長さを、回転子鉄心１０の軸方向端部よりも軸方向外側にまで延長させた構成にしている。 In the present embodiment, compared to the tenth embodiment, the axial length of the fins 35a disposed on the inner peripheral side of the core fitting portion 35k of the spider 35 is set to be more axial than the axial end of the rotor core 10. The configuration is extended to the outside.
　これにより、第１０実施形態で奏される効果に加え、固定子Ｓの外周側への送風量を増加させることができ、より冷却性能の向上を図ることができる。 Thereby, in addition to the effects achieved in the tenth embodiment, the amount of air blown to the outer peripheral side of the stator S can be increased, and the cooling performance can be further improved.
　［第１３実施形態］
　次に、第１２実施形態について説明する。図１５は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Thirteenth embodiment]
Next, a twelfth embodiment will be described. FIG. 15 is a partial front sectional view showing the configuration of the hoist according to the present embodiment.
　本実施形態では、第１１実施形態に比べ、スパイダー３６の鉄心用嵌着部３６ｋの内周側に配置したフィン３６ａの軸方向長さを、回転子鉄心１０の軸方向端部よりも軸方向外側にまで延長させた構成にしている。 In the present embodiment, compared to the eleventh embodiment, the axial length of the fins 36a arranged on the inner peripheral side of the core fitting portion 36k of the spider 36 is more axial than the axial end of the rotor core 10. The configuration is extended to the outside.
　これにより、第１１実施形態で奏される効果に加え、固定子Ｓの外周側への送風量を増加させることができ、冷却性能の更なる向上を図ることができる。 Thereby, in addition to the effects exhibited in the eleventh embodiment, the amount of air blown to the outer peripheral side of the stator S can be increased, and the cooling performance can be further improved.
　［第１４実施形態］
　次に、第１４実施形態について説明する。図１６は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Fourteenth embodiment]
Next, a fourteenth embodiment will be described. FIG. 16 is a front partial sectional view showing the configuration of the hoist according to this embodiment.
　本実施形態では、第１実施形態に比べ、スパイダー３７の鉄心用嵌着部３７ｋの外径を大径化する。また、軸受４の回転子Ｃ側に、軸受４に当接する固定板３８を配置する。そして、スパイダー３７には、鉄心用嵌着部３７ｋの内側および後端側延出し部３７ｂを挿通する複数本のボルト挿通孔が形成されている。本実施形態では、ボルト挿通孔の少なくとも一部に雌ネジが形成されている。この構成により、固定板３８には、ボルト挿通孔を挿通した押しボルト３９で押圧されるようになっている。 In this embodiment, compared to the first embodiment, the outer diameter of the core fitting portion 37k of the spider 37 is increased. A fixed plate 38 that contacts the bearing 4 is disposed on the rotor C side of the bearing 4. The spider 37 is formed with a plurality of bolt insertion holes through which the inner and rear end extending portions 37b of the core insertion portion 37k are inserted. In this embodiment, a female screw is formed in at least a part of the bolt insertion hole. With this configuration, the fixing plate 38 is pressed by the push bolt 39 inserted through the bolt insertion hole.
　これにより、第１実施形態で奏される効果に加え、軸受４の軸方向位置の固定を可能とし、軸受内輪クリープの発生を防止することが可能となる。 Thereby, in addition to the effects exhibited in the first embodiment, the axial position of the bearing 4 can be fixed, and the occurrence of bearing inner ring creep can be prevented.
　［第１５実施形態］
　次に、第１５実施形態について説明する。図１７は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Fifteenth embodiment]
Next, a fifteenth embodiment is described. FIG. 17 is a partial front sectional view showing the configuration of the hoist according to this embodiment.
　本実施形態では、第１実施形態に比べ、スパイダー４０の鉄心用嵌着部４０ｋの外径φＤｅを大径化する。そして、スパイダー４０には、鉄心用嵌着部４０ｋの内側から、スパイダー４０の後端側延出し部４０ｂを挿通する複数本のボルト挿通孔が形成されている。この構成により、ボルト挿通孔を挿通した押しボルト４１で軸受４が押圧されるようになっている。 In this embodiment, as compared with the first embodiment, the outer diameter φDe of the core fitting portion 40k of the spider 40 is increased. The spider 40 is formed with a plurality of bolt insertion holes through which the rear end side extending portion 40b of the spider 40 is inserted from the inside of the core fitting portion 40k. With this configuration, the bearing 4 is pressed by the push bolt 41 inserted through the bolt insertion hole.
　これにより、第１実施形態で奏される効果に加え、軸受４の軸方向位置の固定を可能とし、軸受内輪クリープの発生を防止することが可能となる。 Thereby, in addition to the effects exhibited in the first embodiment, the axial position of the bearing 4 can be fixed, and the occurrence of bearing inner ring creep can be prevented.
　［第１６実施形態］
　次に、第１６実施形態について説明する。図１８は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Sixteenth Embodiment]
Next, a sixteenth embodiment will be described. FIG. 18 is a front partial sectional view showing the configuration of the hoist according to the present embodiment.
　本実施形態では、第１実施形態に比べ、スパイダー４２の軸受４側の端部に、軸受４を配置する。すなわち、スパイダー４２の後端側延出し部４２ｂの端部外周に軸受４が当接している。 In this embodiment, the bearing 4 is arranged at the end of the spider 42 on the bearing 4 side as compared with the first embodiment. That is, the bearing 4 is in contact with the outer periphery of the end portion of the rear end side extending portion 42b of the spider 42.
　これにより、第１実施形態で奏される効果に加え、後端側延出し部４２ｂと回転軸１９の先端部外周部１９ｆとによる嵌着部ＫＢを長く設定することができる。従って、たわみ抑制効果を大幅に増強することができ、また、回転子鉄心１０から端ふた２１までの長さの短縮も可能となり、たわみ抑制に更に効果がある上、巻上機の小形化が可能となる。また、軸受４の交換時、スパイダー４２ごと取り出して分解することが可能となる。 Thereby, in addition to the effect exhibited in the first embodiment, the fitting portion KB by the rear end side extending portion 42b and the front end portion outer peripheral portion 19f of the rotating shaft 19 can be set long. Accordingly, the deflection suppressing effect can be greatly enhanced, and the length from the rotor core 10 to the end lid 21 can be shortened, which is more effective in suppressing deflection and further downsizing the hoisting machine. It becomes possible. Further, when the bearing 4 is replaced, the entire spider 42 can be taken out and disassembled.
　［第１７実施形態］
　次に、第１７実施形態について説明する。図１９は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Seventeenth embodiment]
Next, a seventeenth embodiment will be described. FIG. 19 is a partial front sectional view showing the configuration of the hoist according to this embodiment.
　本実施形態では、第１実施形態に比べ、スパイダー４３の後端側延出し部４３ｂの軸受４側の端部を、端ふた２１よりも回転子Ｃ側に位置させており、後端側延出し部４３ｂの軸心方向長さを短くしている。 In the present embodiment, compared to the first embodiment, the end portion on the bearing 4 side of the rear end extension portion 43b of the spider 43 is positioned on the rotor C side with respect to the end lid 21, and the rear end side extension The axial direction length of the protruding portion 43b is shortened.
　本実施形態では、第１実施形態に比べ、たわみ抑制効果は低減するが、後端側延出し部４３ｂの外径の制約条件が無くなるので、後端側延出し部４３ｂの外径を増大させることで第１実施形態と同等の効果が得られる。 In this embodiment, the deflection suppressing effect is reduced as compared with the first embodiment, but the outer diameter restriction condition of the rear end side extending portion 43b is eliminated, so that the outer diameter of the rear end side extending portion 43b is increased. Thus, the same effect as that of the first embodiment can be obtained.
　［第１８実施形態］
　次に、第１８実施形態について説明する。図２０は、本実施形態に係る巻上機の構成を示す正面部分断面図である。 [Eighteenth embodiment]
Next, an eighteenth embodiment will be described. FIG. 20 is a front partial sectional view showing the configuration of the hoist according to the present embodiment.
　本実施形態では、第１実施形態に比べ、回転軸４４の先端部外周部４４ｆに円周状の溝４４ｃを設け、同溝に通じる注油孔４４ｈを設ける。 In this embodiment, compared to the first embodiment, a circumferential groove 44c is provided in the outer peripheral portion 44f of the tip end portion of the rotating shaft 44, and an oil injection hole 44h leading to the groove is provided.
　これにより、第１実施形態で奏される効果に加え、スパイダー４５の分解時に、同注油孔４４ｈに油圧をかけることにより、スパイダー４５の鉄心用嵌着部４５ｋと先端部外周部４４ｆとによる嵌着部ＫＢの嵌着力（把握力）を低減させることができ、分解を容易にすることができる。 As a result, in addition to the effects achieved in the first embodiment, when the spider 45 is disassembled, by applying hydraulic pressure to the oil injection hole 44h, the fitting by the core fitting portion 45k and the tip outer peripheral portion 44f of the spider 45 is performed. The fitting force (holding force) of the wearing part KB can be reduced, and the disassembly can be facilitated.
　［第１９実施形態］
　次に、第１９実施形態について説明する。本実施形態では、図示しないが、第１～第１８実施形態に比べ、固定ボルト２２、３９、４１と回転軸の先端部に形成されている取付穴との関係をリーマ方式にしている。 [Nineteenth Embodiment]
Next, a nineteenth embodiment will be described. In this embodiment, although not shown, the relationship between the fixing bolts 22, 39, 41 and the mounting hole formed in the tip end portion of the rotating shaft is a reamer system as compared to the first to eighteenth embodiments.
　これにより、第１～第１８実施形態で奏される効果に加え、機械的な廻り止めを形成することができる。また、リーマ方式とした上記取付孔を利用して、組立・分解時にガイドスタッドを設けることにより組立性を向上させることができる。 Thus, in addition to the effects exhibited in the first to eighteenth embodiments, a mechanical detent can be formed. Further, using the reamer type mounting hole, assembling can be improved by providing a guide stud during assembly / disassembly.
　［第２０実施形態］
　次に、第２０実施形態について説明する。本実施形態では、第１～第１９実施形態に比べ、エレベータ用巻上機以外の巻上機の例である。例えば、綱車７の代わりにプーリなどを設けた回転電機においても、同様の作用、効果が得られる。 [20th embodiment]
Next, a twentieth embodiment will be described. The present embodiment is an example of a hoisting machine other than the elevator hoisting machine as compared with the first to nineteenth embodiments. For example, a similar operation and effect can be obtained in a rotating electrical machine provided with a pulley or the like instead of the sheave 7.
　（比較検討例）
　図２１は、従来の巻上機の一例の構成を示す正面部分断面図である。図２１に示す従来の巻上機Ｍ１０１は、取付台１０１に立設する軸受台１０２、１０３にそれぞれ設けられた一対の軸受１０４、１０５と、一対の軸受１０４、１０５に支持された回転軸１１９と、回転軸１１９に嵌着する回転子ＪＣと、回転子ＪＣの外周側に配置されている固定子ＪＳと、を有する。回転軸１１９の先端部１１９ｆには、嵌着用の先端部外周部１１９ｅが形成されている。 (Comparative study example)
FIG. 21 is a front partial sectional view showing a configuration of an example of a conventional hoisting machine. A conventional hoisting machine M101 shown in FIG. 21 includes a pair of bearings 104 and 105 provided on bearing bases 102 and 103 standing on a mounting base 101, and a rotating shaft 119 supported by the pair of bearings 104 and 105, respectively. And a rotor JC fitted to the rotary shaft 119 and a stator JS disposed on the outer peripheral side of the rotor JC. A distal end outer peripheral portion 119e for fitting is formed at the distal end portion 119f of the rotating shaft 119.
　回転子ＪＣは、回転子鉄心１１０と、回転子鉄心１１０に嵌着するスパイダー１１８と、を有する。固定子ＪＳは固定子鉄心１１３を備えており、回転子鉄心１１０と固定子鉄心１１３との間には空隙１１２が形成されている。スパイダー１１８は、先端部外周部１１９ｅに嵌着する管状形状部１１１ｍを有する。そして、管状形状部１１１ｍに対するスパイダー１１８の廻り止めとしてキー１２９が配置されている。 The rotor JC has a rotor core 110 and a spider 118 that fits into the rotor core 110. The stator JS includes a stator core 113, and a gap 112 is formed between the rotor core 110 and the stator core 113. The spider 118 has a tubular shape portion 111m that is fitted to the outer peripheral portion 119e of the distal end portion. And the key 129 is arrange | positioned as a rotation stop of the spider 118 with respect to the tubular shape part 111m.
　従来の巻上機Ｍ１０１では、以下の（１）～（５）の難点があった。 The conventional hoisting machine M101 has the following problems (1) to (5).
（１）　（回転子のたわみ増に伴う空隙長の不平衡による電磁騒音、振動、大径化）
　スパイダー１１８は回転軸１１９に管状形状部１１１ｍのみで支持されているため、回転子ＪＣの自重および磁気吸引力によってスパイダー１１８のたわみが発生しやすい。そして、たわみ抑制方法としては、以下の方策が必要であった。すなわち、スパイダー１１８と回転軸１１９との嵌着部ＪＴにおけるスパイダー部分の外径φＤ１を大径化し、かつ、回転軸１１９の軸径も大径化する必要があった。このことは、巻上機Ｍ１０１の組立性の悪化や質量増の要因となっていた。 (1) (Electromagnetic noise, vibration, and diameter increase due to unbalanced gap length due to increased rotor deflection)
Since the spider 118 is supported on the rotating shaft 119 only by the tubular portion 111m, the spider 118 is likely to bend due to the weight of the rotor JC and the magnetic attractive force. And the following measures were needed as a deflection | deviation control method. That is, it is necessary to increase the outer diameter φD1 of the spider portion in the fitting portion JT between the spider 118 and the rotating shaft 119 and to increase the diameter of the rotating shaft 119. This has been a factor of deterioration in assembling and mass of the hoisting machine M101.
（２）　（空隙長の調整に関する製造効率の低下）
　前述のたわみと共に、スパイダーの１１８嵌着端部が開口形状となっているため、組立時に、若干の傾き状態で嵌着されても補正することが不可能であった。このため、空隙１１２の不平衡の要因となり、その補正を行うため、空隙１１２の調整などが必要であり、特性悪化や多大な組立時間が必要であった。 (2) (Decrease in production efficiency related to adjustment of gap length)
Along with the above-described deflection, since the 118 fitting end of the spider has an opening shape, it is impossible to correct even if it is fitted in a slightly inclined state during assembly. For this reason, the gap 112 becomes an unbalanced factor, and in order to correct the gap 112, adjustment of the gap 112 and the like are required, and characteristic deterioration and a lot of assembly time are required.
（３）　（電気特性悪化・大径化）
　前述の（１）および（２）に伴う対策として、空隙１１２の拡大を行うと、励磁電流が増加し、結果として力率が悪化するなど特性悪化・消費電力増大を招く。また、適用機器に必要な容量を得るために、固定子鉄心１１０および回転子鉄心１１３を大径化する必要があり、巻上機の大径化の要因となっていた。 (3) (Deterioration of electrical characteristics and increase in diameter)
If the gap 112 is enlarged as a countermeasure associated with the above (1) and (2), the excitation current increases, resulting in deterioration of characteristics and increase of power consumption such as deterioration of power factor. Moreover, in order to obtain the capacity required for the applied equipment, it is necessary to increase the diameter of the stator core 110 and the rotor core 113, which has been a factor in increasing the diameter of the hoisting machine.
　固定子ＪＳおよび回転子ＪＣが大径化されると各々の自重による片持ち荷重が大きく、振れ回り振動が増大する。その結果、乗り心地悪化など特性悪化や振動による部品寿命悪化・短命化の要因となっていた。また、振動抑制のため、据付系の剛性向上に伴う装置全体の大型化や防振系統の防振ゴムの複数化など部品点数増加・構成の複雑化をまねく要因となっていた。 ¡When the diameter of the stator JS and the rotor JC is increased, the cantilever load due to their own weight increases, and the whirling vibration increases. As a result, it has been a cause of deterioration of characteristics such as deterioration of ride comfort and deterioration of component life and shortening of life due to vibration. In addition, in order to suppress vibrations, it has become a factor that increases the number of parts and complicates the configuration, such as an increase in the size of the entire device due to improved rigidity of the installation system and the use of multiple anti-vibration rubber in the anti-vibration system.
（４）　（軸心不一致による振動・軸受の短寿命）
　回転子ＪＣのたわみ増大による空隙の不平衡が発生する場合、回転子全体の振れ回り現象が発生する。同振れ回り現象が発生すると、回転子ＪＣの外周振れによる磁気吸引力の回転・回転アンバランスによる遠心力・軸振れに伴う回転力などが発生する。その結果、振動の増大と軸受ならびに巻上機Ｍ１０１の短寿命を招いていた。 (4) (Vibration due to shaft center mismatch, short life of bearing)
When the air gap is unbalanced due to an increase in the deflection of the rotor JC, a swinging phenomenon of the entire rotor occurs. When the whirling phenomenon occurs, rotation of magnetic attraction force due to the outer periphery shake of the rotor JC, centrifugal force due to rotational unbalance, rotational force due to shaft vibration, and the like are generated. As a result, an increase in vibration and a short life of the bearing and the hoisting machine M101 are incurred.
　振動の一例としては、下式に示す通りつりあい良さの悪化があげられる。 As an example of vibration, as shown in the following formula, the balance is deteriorated.
　　　修正面偏心　　ε＝ｍｒ／Ｍ　　　　ここで、ｍ：アンバランス量　
　　　　　　　　　　　　　　　　　　　　　　　　ｒ：アンバランス半径
　　　　　　　　　　　　　　　　　　　　　　　　Ｍ：回転子自重
　　　つりあい良さ　Ｇ＝εω／１０００　　　ここで、ω：角速度

　上式の通り、アンバランス量が増加すると、つりあい良さの値が増加し、その結果、振動の増加となっていた。 Correction surface eccentricity ε = mr / M where m: unbalance amount
r: Unbalance radius M: Rotor self-weight Good balance G = εω / 1000 where ω: Angular velocity

As shown in the above equation, when the amount of unbalance increases, the value of good balance increases, resulting in an increase in vibration.
　また　軸受１０４、１０５の短寿命の一要因であるクリープ・フレティング現象(Creep Fretting Phenomenon)における力の関係は、回転力、即ち‘回転荷重’と軸受部が静止しようとする力、即ち‘静止荷重’が‘回転荷重＞静止荷重’となった場合、発生する。従って、軸心不一致が発生すると軸受１０４、１０５の短寿命化に伴い、巻上機Ｍ１０１の短寿命化の要因となっていた。 In addition, the relationship between the forces in the creep / fretting phenomenon (Creep Fretting Phenomenon), which is one factor of the short life of the bearings 104 and 105, is the rotational force, that is, the 'rotational load' and the force at which the bearing part tries to be stationary, that is, 'stationary Occurs when 'load' becomes 'rotational load> static load'. Therefore, when the shaft center mismatch occurs, the life of the hoisting machine M101 is shortened as the bearings 104 and 105 are shortened.
（５）　（分解時の損傷）
　軸受１０４の交換時に、スパイダー１１８を引き抜く必要があるが、嵌着端部が開口形状のため、引く抜き時のガイドが無く、嵌着面やキー１２９の損傷を発生させる可能性が高い。その結果、スパイダー１１８または回転軸１１９の再利用が不可能となる場合があり、巻上機Ｍ１０１の短寿命化の要因となっていた。 (5) (Damage during disassembly)
When replacing the bearing 104, it is necessary to pull out the spider 118. However, since the fitting end portion has an opening shape, there is no guide when pulling out, and there is a high possibility that the fitting surface and the key 129 will be damaged. As a result, the spider 118 or the rotating shaft 119 may not be reused, which is a factor in shortening the life of the hoisting machine M101.
　一方、第１～第２０実施形態に係る巻上機では、このような難点が解消されている。すなわち、組立性の悪化や質量増を生じさせずに、運転中の騒音、振動を抑えることができる。 On the other hand, in the hoisting machines according to the first to twentieth embodiments, such difficulties are eliminated. That is, noise and vibration during operation can be suppressed without causing deterioration in assemblability and mass increase.
　また、回転子と固定子との空隙の調整が不要である。従って、回転子や固定子を大径化させる必要がなく、特性悪化、組立時間の増大、構成の複雑化、軸心不一致による振動発生・軸受の短寿命化、は生じない。 Also, there is no need to adjust the gap between the rotor and stator. Therefore, there is no need to increase the diameter of the rotor and the stator, and there is no deterioration in characteristics, an increase in assembly time, a complicated configuration, generation of vibrations due to mismatched shaft centers, and a shortened bearing life.
　また、スパイダーには、回転軸の凸部の外周側と嵌着する凸部用嵌着部が形成されているとともに、回転軸の先端部外周部に嵌着する後端側延出し部が形成された二重嵌着となっている。従って、スパイダーを引抜く際、一方の嵌着部が案内部として作用するので、嵌着面に損傷が生じることが回避される。 Further, the spider is formed with a convex fitting portion that fits to the outer peripheral side of the convex portion of the rotating shaft, and a rear end side extending portion that fits to the outer peripheral portion of the tip end portion of the rotating shaft. It has been double fitted. Therefore, when pulling out the spider, one of the fitting portions acts as a guide portion, so that damage to the fitting surface is avoided.
　以上、いくつかの実施形態を説明したが、これらの実施形態は、例として提示したものであり、発明の範囲はそれらに限定することは意図していない。これらの実施形態は、その他の様々な形態で実施されることが可能であり、発明の要旨を逸脱しない範囲で、種々の省略、置き換え、変更を行うことができる。これらの実施形態やその変形は、発明の範囲や要旨に含まれると同様に、特許請求の範囲に記載された発明とその均等の範囲に含まれるものである。 Although several embodiments have been described above, these embodiments are presented as examples, and the scope of the invention is not intended to be limited to them. These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the invention described in the claims and equivalents thereof as well as included in the scope and gist of the invention.
産業上の利用分野Industrial application fields
　本発明は、回転電機を応用するエレベータ等において利用される。 The present invention is used in an elevator or the like using a rotating electric machine.
４　軸受
５　軸受
７　綱車
１８　スパイダー
１８ｂ　後端側延出し部
１８ｆ　凸部用嵌着部
１８ｋ　鉄心用嵌着部
１８ｒ　端部
１９　回転軸
１９ｅｎ　先端部外周部
１９ｅ　先端部外周部
１９ｆ　先端部
１９ｔ　凸部
２０　回転子鉄心
２１　端ふた
２３　スパイダー
２３ｂ　後端側延出し部
２４　スパイダー
２４ｂ　後端側延出し部
２５　スパイダー
２５ｂ　後端側延出し部
２６　スパイダー
２７　スパイダー
２８　回転軸
２８ｆ　先端部外周部
２９　回転軸
２９ｔ　凸部
３０　回転軸
３０ｔ　凸部
３１　スパイダー
３１ｆ　凸部用嵌着部
３２　スパイダー
３２ｂ　後端側延出し部
３３　スパイダー
３３ｋ　鉄心用嵌着部
３４　スパイダー
３４ａ　フィン
３４ｋ　鉄心用嵌着部
３４ｈ　通風孔
３５　スパイダー
３５ａ　フィン
３５ｋ　鉄心用嵌着部
３６　スパイダー
３６ａ　フィン
３６ｋ　鉄心用嵌着部
３７　スパイダー
３７ｋ　鉄心用嵌着部
３７ｂ　後端側延出し部
４０　スパイダー
４０ｋ　鉄心用嵌着部
４０ｂ　後端側延出し部
４２　スパイダー
４２ｂ　後端側延出し部
４３　スパイダー
４３ｂ　後端側延出し部
４４　回転軸
４４ｆ　先端部外周部
４４ｃ　溝
４４ｈ　注油孔
４５　スパイダー
４５ｈ　注油孔
１０４　軸受
１０５　軸受
１１０　回転子鉄心
１１８　スパイダー
１１９　回転軸
１１９ｅ　先端部外周部
１１９ｆ　先端部
Ｃ　回転子
ＪＣ　回転子
ＫＢ　嵌着部
ＫＴ　嵌着部
Ｍ１　巻上機
Ｍ１０１　巻上機 4 Bearing 5 Bearing 7 Sheave 18 Spider 18b Rear end extending portion 18f Convex fitting portion 18k Iron core fitting portion 18r End portion 19 Rotating shaft 19en Tip portion outer peripheral portion 19e Tip portion outer peripheral portion 19f Tip portion 19t Convex portion Part 20 rotor core 21 end lid 23 spider 23b rear end side extension part 24 spider 24b rear end side extension part 25 spider 25b rear end side extension part 26 spider 27 spider 28 rotary shaft 28f front end outer peripheral part 29 rotary shaft 29t Convex 30 Rotating shaft 30t Convex 31 Spider 31f Convex fitting 32 Spider 32b Rear end extension 33 Spider 33k Core fitting 34 Spider 34a Fin 34k Core fitting 34h Ventilation hole 35 Spider 35a Fin 35k Iron core fitting part 36 Spider 36a Fin 36k Iron core fitting part 37 Spider 37k Iron core fitting portion 37b Rear end side extending portion 40 Spider 40k Iron core fitting portion 40b Rear end side extending portion 42 Spider 42b Rear end side extending portion 43 Spider 43b Rear end side extending portion 44 Rotating shaft 44f Tip portion outer peripheral portion 44c Groove 44h Oiling hole 45 Spider 45h Oiling hole 104 Bearing 105 Bearing 110 Rotor core 118 Spider 119 Rotating shaft 119e Tip portion outer periphery 119f Tip portion C Rotor JC Rotor KB fitting portion KT fitting portion M1 hoisting machine M101 hoisting machine

Claims (17)

  1. 　綱車が軸回りに固定されて軸受に支持された回転軸と、
    　前記回転軸の先端部に嵌着するスパイダーと、
    　を備え、
    　前記回転軸の前記先端部には、嵌着用の先端部外周部が形成されているとともに、先端側から軸方向に延び出す嵌着用の凸部が形成され、
    　前記スパイダーには、回転軸側で前記凸部の外周側と嵌着する凸部用嵌着部が形成されているとともに、前記先端部外周部に嵌着する後端側延出し部が形成されている巻上機。
    A rotary shaft with a sheave fixed around the shaft and supported by bearings;
    A spider to be fitted to the tip of the rotating shaft;
    With
    The front end portion of the rotating shaft is formed with a front end portion outer peripheral portion for fitting and a fitting convex portion extending in the axial direction from the front end side,
    The spider is formed with a convex fitting portion that is fitted to the outer peripheral side of the convex portion on the rotating shaft side, and a rear end side extending portion that is fitted to the outer peripheral portion of the tip end portion. Hoisting machine.
  2. 　前記スパイダーの軸受側の外径を前記軸受の内径より大径化した請求項１記載の巻上機。
    The hoist according to claim 1, wherein the outer diameter of the spider on the bearing side is larger than the inner diameter of the bearing.
  3. 　前記スパイダーの軸受側の端部で前記軸受の軸方向位置を規定する構造にされている請求項２記載の巻上機。
    The hoisting machine according to claim 2, wherein an end of the spider on the bearing side defines an axial position of the bearing.
  4. 　前記先端部外周部には、先端側にかけて徐々に径が細くなるテーパ面が形成され、
    　前記スパイダーには、前記テーパ面と重なり合う凹状面が形成されている請求項１記載の巻上機。
    In the outer peripheral portion of the distal end portion, a tapered surface whose diameter gradually decreases toward the distal end side is formed,
    The hoist according to claim 1, wherein the spider has a concave surface that overlaps the tapered surface.
  5. 　前記スパイダーは、
    　回転子鉄心の内周側に嵌着する筒状の鉄心用嵌着部と、
    　前記鉄心用嵌着部の内周側に設けられたフィンと、
    を有する請求項１～４にいずれか１項記載の巻上機。
    The spider
    A tubular core fitting portion that fits on the inner peripheral side of the rotor core; and
    Fins provided on the inner peripheral side of the core fitting portion;
    The hoist according to any one of claims 1 to 4, wherein:
  6. 　前記スパイダーには、前記鉄心用嵌着部の内周側の空間と前記回転子鉄心の軸受側の空間とに連通する通風孔が形成されている請求項５記載の巻上機。
    The hoisting machine according to claim 5, wherein the spider is formed with a ventilation hole communicating with a space on the inner peripheral side of the fitting portion for the iron core and a space on the bearing side of the rotor core.
  7. 　前記先端部には、前記先端部外周部に沿った溝と、
    　前記溝に連通する注油孔と、
    　が形成されている請求項５記載の巻上機。
    The tip has a groove along the outer periphery of the tip,
    An oiling hole communicating with the groove;
    The hoist according to claim 5, wherein
  8. 　前記先端部には、前記先端部外周部に沿った溝と、
    　前記溝に連通する注油孔と、
    　が形成されている請求項６記載の巻上機。
    The tip has a groove along the outer periphery of the tip,
    An oiling hole communicating with the groove;
    The hoist according to claim 6, wherein
  9. 　請求項１～４のいずれか１項に記載の巻上機を有する回転電機。
    A rotary electric machine comprising the hoist according to any one of claims 1 to 4.
  10. 　請求項５に記載の巻上機を有する回転電機。
    A rotating electrical machine having the hoist according to claim 5.
  11. 　請求項6に記載の巻上機を有する回転電機。
    A rotating electric machine having the hoist according to claim 6.
  12. 　請求項7に記載の巻上機を有する回転電機。
    A rotating electrical machine having the hoist according to claim 7.
  13. 　前記巻上機がエレベータ用の巻上機である請求項９記載の回転電機。
    The rotating electrical machine according to claim 9, wherein the hoisting machine is an elevator hoisting machine.
  14. 　前記巻上機がエレベータ用の巻上機である請求項９記載の回転電機。
    The rotating electrical machine according to claim 9, wherein the hoisting machine is an elevator hoisting machine.
  15. 　前記巻上機がエレベータ用の巻上機である請求項１０記載の回転電機。
    The rotating electrical machine according to claim 10, wherein the hoisting machine is an elevator hoisting machine.
  16. 　前記巻上機がエレベータ用の巻上機である請求項１１記載の回転電機。
    The rotating electrical machine according to claim 11, wherein the hoisting machine is an elevator hoisting machine.
  17. 　前記巻上機がエレベータ用の巻上機である請求項１２記載の回転電機。 The rotary electric machine according to claim 12, wherein the hoisting machine is an elevator hoisting machine.
PCT/JP2012/008417 2012-01-05 2012-12-28 Hoisting machine, and rotating electrical machine provided with same WO2013102991A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201280066039.2A CN104039677B (en) 2012-01-05 2012-12-28 Hoist engine and the electric rotating machine that possesses this hoist engine

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JP2012000653A JP5955563B2 (en) 2012-01-05 2012-01-05 Hoisting machine and rotating electric machine equipped with the same
JP2012-000653 2012-01-05

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Publication Number Publication Date
WO2013102991A1 true WO2013102991A1 (en) 2013-07-11

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PCT/JP2012/008417 WO2013102991A1 (en) 2012-01-05 2012-12-28 Hoisting machine, and rotating electrical machine provided with same

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WO2015107643A1 (en) * 2014-01-16 2015-07-23 三菱電機株式会社 Hoist for elevator
JP6134952B1 (en) * 2015-12-03 2017-05-31 株式会社明電舎 Hoisting machine

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JPH0562176U (en) * 1992-01-22 1993-08-13 東洋電機製造株式会社 Fully closed induction motor for vehicle
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WO2002048016A1 (en) * 2000-12-11 2002-06-20 Mitsubishi Denki Kabushiki Kaisha Hoist for elevator
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Publication number Priority date Publication date Assignee Title
JPH04226290A (en) * 1990-07-26 1992-08-14 Inventio Ag Driving machine without gear for elevator
JPH0562176U (en) * 1992-01-22 1993-08-13 東洋電機製造株式会社 Fully closed induction motor for vehicle
JPH1034408A (en) * 1996-07-17 1998-02-10 Toyota Motor Corp Tool holder device and tool mounting/demounting method
JP2000128462A (en) * 1998-10-27 2000-05-09 Hitachi Ltd Hoist machine
JP2002029208A (en) * 2000-07-17 2002-01-29 Koyo Seiko Co Ltd Bearing device for vehicle

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CN104039677A (en) 2014-09-10
JP5955563B2 (en) 2016-07-20
TWI527751B (en) 2016-04-01
JP2013139325A (en) 2013-07-18
CN104039677B (en) 2016-05-18
TW201345824A (en) 2013-11-16

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