JP5955563B2 - Hoisting machine and rotating electric machine equipped with the same - Google Patents

Description

  Embodiments described herein relate generally to a hoisting machine and a rotating electrical machine including the hoisting machine.

  In the elevator, an elevator hoist for moving the car up and down is installed. The elevator hoist includes a rotating shaft that rotates a sheave around which a rope is wound, a spider that is locked at the tip of the rotating shaft with a key, and a rotor that is fitted to the outer periphery of the spider, (For example, refer to Patent Document 1).

  In such elevators, with the recent increase in the number of buildings, there is a strong demand for improving the transportation capacity of elevators, and thus there is an increasing need for large capacity and high speed for hoisting machines.

  On the other hand, in order to improve environmental resistance, there is an increasing demand for lowering noise and vibration of the hoisting machine, and it is necessary to meet the demands contradicting the above-mentioned large capacity and high speed. Furthermore, in order to facilitate the installation work of the elevator, there is a demand for a smaller and lighter hoisting machine.

  In order to realize such requirements, it is important to reduce loss and electromagnetic noise by improving the accuracy of the concentricity between the stator and the rotor.

JP-A-11-165970

  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.

  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.

  Conventionally, the spider is supported only by the tubular shape portion of the spider on 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. .

  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 according to an embodiment of the present invention includes a rotary shaft in which a sheave is fixed around an axis and supported by a bearing, and a spider that is fitted to a tip portion of the rotary 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.

It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 1st Embodiment. It is a perspective view of the winding machine which concerns on 1st Embodiment. It is a partial section expanded view showing composition of a winding machine concerning a 1st embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 2nd Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 3rd Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 4th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 5th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 6th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 7th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 8th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 9th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 10th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 11th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 12th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 13th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 14th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 15th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 16th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 17th Embodiment. It is a front fragmentary sectional view which shows the structure of the winding machine which concerns on 18th Embodiment. It is a front fragmentary sectional view which shows the structure of an example of the conventional winding machine.

  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.

[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.

  As shown in FIGS. 1 to 3, the hoisting machine M <b> 1 according to the present embodiment includes a pair of bearings 4 and 5 provided on the bearing bases 2 and 3 erected on the mounting base 1, and a pair of bearings 4 and 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.

  A front end portion 19f of the rotating 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 is formed. 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.

  The rotor C includes a rotor core 10 and a spider 18 that is fitted to 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.

  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).

  Further, a ring-shaped end lid 21 is provided on the spider side (rotor side) of the bearing 4 on the axial 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.

  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.

  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.

  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.

  Further, since the amount of eccentricity of the rotor C is suppressed, it is possible to prevent the air gap 12 from being unbalanced and to suppress vibration and noise due to electromagnetic vibration. 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.

  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.

  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. .

  Moreover, in the elevator provided with the hoisting machine M1 which concerns on this embodiment, it becomes an elevator from which these effects were acquired, and it can be set as the elevator which suppressed the noise and vibration during driving | operation.

[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.

  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.

  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.

[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.

  In the present embodiment, the outer diameter φDb1 on the bearing 4 side of the rear end extension 24b of the spider 24 is made larger than the inner diameter φDb2 of the bearing 4 as compared with the first embodiment.

  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.

[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.

  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.

  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.

[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.

  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.

  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.

[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.

  In the present embodiment, the fitting portion KB between the spider 27 and the tip outer peripheral portion 28f of the rotating shaft 28 is tapered as compared with the first embodiment.

  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.

[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.

  In the present embodiment, as compared with the first 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. 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.

  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.

  Thereby, in addition to the effects exhibited in the first embodiment, the assembly accuracy is improved, and the gap 12 can be made more uniform in the circumferential direction.

[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.

  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.

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.

  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.

  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.

[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.

  In this embodiment, the fin 33a is provided in the inner peripheral side of the fitting part 33k for iron cores of the spider 33 compared with 1st Embodiment. 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 realize a reduction in size and weight of the hoisting machine driving unit accompanying improvement in the cooling performance of the rotor C.

  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.

[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.

  In this embodiment, the fin 34a is provided in the inner peripheral side of the fitting part 34k for iron cores of the spider 34 compared with 10th Embodiment. 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.

  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.

[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.

  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.

  Thereby, in addition to the effect show | played by 10th Embodiment, the ventilation volume to the outer peripheral side of the stator S can be increased, and the improvement of cooling performance can be aimed at more.

[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.

  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.

  Thereby, in addition to the effect produced 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.

[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.

  In this embodiment, compared with 1st Embodiment, the outer diameter of the fitting part 37k for iron cores of the spider 37 is enlarged. 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.

  Thereby, in addition to the effect 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.

[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.

  In the present embodiment, the outer diameter φDe of the core fitting portion 40k of the spider 40 is increased compared to the first embodiment. 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.

  Thereby, in addition to the effect 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.

[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.

  In this embodiment, the bearing 4 is arrange | positioned in the edge part by the side of the bearing 4 of the spider 42 compared with 1st 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.

  Thereby, in addition to the effect show | played by 1st Embodiment, the fitting part KB by the rear-end side extension part 42b and the front-end | tip part outer peripheral part 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.

[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.

  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.

  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.

[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.

  In the present embodiment, compared to the first embodiment, a circumferential groove 44c is provided on 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.

  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.

[Nineteenth Embodiment]
Next, a nineteenth embodiment will be described. In the present 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 method as compared with the first to eighteenth embodiments.

  Thereby, in addition to the effect show | played by 1st-18th embodiment, a mechanical rotation stop can be formed. Further, using the reamer type mounting hole, assembling can be improved by providing a guide stud during assembly / disassembly.

[20th embodiment]
Next, a twentieth embodiment will be described. The present embodiment is an example of a hoisting machine other than an 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.

(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 the 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.

  The rotor JC includes a rotor core 110 and a spider 118 that is fitted to 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.

  The conventional hoisting machine M101 has the following problems (1) to (5).

(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) (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) (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.

  When the diameters of the stator JS and the rotor JC are 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) (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.

  As an example of the vibration, there is a worsening of good balance as shown in the following formula.

Correction surface eccentricity ε = mr / M where m: unbalance amount
r: Unbalance radius
M: Rotor self-weight Good balance G = εω / 1000 Here, ω: Angular velocity As shown in the above formula, when the amount of unbalance increases, the value of good balance increases, resulting in an increase in vibration.

  The relationship between the forces in the creep and fretting phenomenon, which is one factor of the short life of the bearings 104 and 105, is that the rotational force, that is, the 'rotational load', and the force that the bearing part tries to be stationary, that is, the 'static load' is rotated. Occurs when 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) (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 at the time of pulling out, and there is a possibility that the fitting surface and the key 129 may be damaged (galling). high. 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.

  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.

  Moreover, adjustment of the space | gap of a rotor and a stator is unnecessary. 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.

  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.

  Although some 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.

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 peripheral portion 44c Groove 44h Lubricating hole 45 Spider 45h Lubrication hole 104 Bearing 105 Bearing 110 Rotor core 118 Spider 119 Rotating shaft 119e Tip peripheral portion 119f Tip C Rotor JC Rotor KB Fitting portion KT Fitting portion M1 hoisting machine M101 hoisting machine

Claims (9)

A rotary shaft with a sheave fixed around the shaft and supported by bearings;
A spider that fits from the outer peripheral side to the tip of the rotating shaft and fits to the inner peripheral side of the rotor core ;
With
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 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.   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.   The hoisting machine according to claim 2, wherein an end portion on the bearing side of the spider is configured to define an axial position of the bearing. 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. The spider has a tubular core fitting portion that fits on the inner peripheral side of the rotor core;
Fins provided on the inner peripheral side of the core fitting portion;
The hoist according to any one of claims 1 to 4, further comprising:   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. In the tip portion, a groove formed in the outer peripheral portion of the tip portion along the outer peripheral direction,
An oil supply hole that opens in a surface of the tip portion intersecting in the axial direction and communicates with the groove ;
The hoist according to claim 5 or 6, wherein: is formed.   The rotary electric machine which has a winding machine of any one of Claims 1-7. The rotating electrical machine according to claim 8, wherein the hoisting machine is an elevator hoisting machine.

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