TW201345824A - Hoisting machine, and rotating electrical machine with the same - Google Patents

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

Winch and rotating electric machine with same

Embodiments of the present invention relate to a hoist and a rotating electrical machine including the same.

Among the elevators, a hoist for lifting the elevator for moving the vehicle is provided. In the hoist for an elevator, a rotating shaft is provided to rotate a sheave in which a sling is wound, and a chuck (Spider) is stopped at a tip end portion of the rotating shaft by a key or the like; The rotor is fitted to the outer peripheral side of the chuck. Japanese Laid-Open Patent Publication No. Hei 11-165970 (hereinafter referred to as Patent Document 1).

In such elevators, with the current high-rise buildings, the demand for lifting conveyors is very strong. Therefore, the need for large capacity and high speed for hoists is gradually increasing.

On the other hand, in order to reduce the impact on the environment, the demand for low noise and low vibration of the hoist is also increasing, and it is necessary to respond to the demand for the above-mentioned large capacity and high speed. Furthermore, in order to make the installation of the elevator simple, there is also a need for a small and lightweight winch.

In order to achieve such demand, how to improve the stator (Stator) - Concentric (same core) accuracy between the rotors, which is important to reduce loss and reduce electromagnetic noise.

[Previous Technical Literature] [Patent Literature]

[Patent Document 1] Japanese Patent Laid-Open No. Hei 11-165970

However, 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 eccentricity harmonic, which is further classified into a static eccentric harmonic and a dynamic eccentric harmonic. Further, these magnetic fluxes act as a magnetic attraction force between the stator and the rotor, deforming the stator into a polygonal shape, or causing the chuck to be distorted and vibrated. If this vibration is outside the hearing range, it will become electromagnetic vibration, and if it is within the hearing range, it will become electromagnetic noise.

The fundamental wave, or the source of the vibration caused by the combination of the fundamental wave and the static eccentric harmonic, for example, there is a mechanical imbalance of the gap length due to the poor roundness of the stator and the rotor (eccentricity). The source of the vibration caused by the combination of the fundamental wave and the dynamic eccentric harmonic, for example, the magnetic flux distribution of the above-mentioned void due to the vortex of the rotor (axial bending, etc.) is unbalanced. The length of the gap before or during operation is unbalanced and is a source of vibration and noise.

Conventionally, the engagement portion of the chuck on the rotating shaft is only by the chuck. The tubular shape portion is supported. Therefore, the rotor's own weight and magnetic attraction force easily cause the occurrence of chuck bending. In order to suppress this bending, it is necessary to increase the diameter of the chuck portion that is fitted to the rotor, and as a result, the assembly of the winch is deteriorated or the source of the quality is increased, which causes disadvantages.

The present invention has been made in view of the above circumstances, and it is an object of the present invention to provide a hoist that can suppress noise and vibration during operation without causing deterioration in assemblability, and a rotary electric machine including the same.

A hoist according to an embodiment of the present invention includes a rotating shaft supported by a bearing, and a sheave is fixed around the shaft, and a chuck is engaged with the tip end portion of the rotating shaft. The tip end portion is formed with an outer peripheral portion of the tip end portion for engagement, and a convex portion for engagement that extends in the axial direction from the tip end side is formed. The chuck is formed with an engaging portion for a convex portion that engages with the outer peripheral side of the convex portion on the side of the rotating shaft, and is formed with an end-side extending portion that engages with the outer peripheral portion of the leading end portion.

4‧‧‧ bearing

5‧‧‧ bearing

7‧‧‧Slot wheel

18‧‧‧ chuck

18b‧‧‧ Rear end extension

18f‧‧‧Inlays for convex parts

18k‧‧‧Iron joints

18r‧‧‧End

19‧‧‧Rotary axis

19en‧‧‧The outer part of the apex

19e‧‧‧The outer periphery of the apex

19f‧‧‧ apex

19t‧‧‧ convex

20‧‧‧Rotor core

21‧‧‧End cover

23‧‧‧ chuck

23b‧‧‧ Rear end extension

24‧‧‧ chuck

24b‧‧‧ rear end extension

25‧‧‧ chuck

25b‧‧‧ rear end extension

26‧‧‧ chuck

27‧‧‧ chuck

28‧‧‧Rotary axis

28f‧‧‧The outer part of the apex

29‧‧‧Rotary axis

29t‧‧‧ convex

30‧‧‧Rotary axis

30t‧‧‧ convex

31‧‧‧ chuck

31f‧‧‧Inlays for convex parts

32‧‧‧ chuck

32b‧‧‧ Rear end extension

33‧‧‧ chuck

33k‧‧‧Iron Engagement

34‧‧‧ chuck

34a‧‧‧Fins

34k‧‧‧core joints

34h‧‧‧ventilation holes

35‧‧‧ chuck

35a‧‧‧Fins

35k‧‧‧Iron engagement

36‧‧‧ chuck

36a‧‧‧Fins

36k‧‧‧Iron Engagement

37‧‧‧ chuck

37k‧‧‧Iron Engagement

37b‧‧‧ rear end extension

40‧‧‧ chuck

40k‧‧‧Iron Embedding

40b‧‧‧ rear end extension

42‧‧‧ chuck

42b‧‧‧ rear end extension

43‧‧‧ chuck

43b‧‧‧ Rear end extension

44‧‧‧Rotary axis

44f‧‧‧The outer periphery of the apex

44c‧‧‧ditch

44h‧‧‧ oil hole

45‧‧‧ chuck

45h‧‧‧ oil hole

104‧‧‧ Bearing

105‧‧‧ bearing

110‧‧‧Rotor core

118‧‧‧ chuck

119‧‧‧Rotary axis

119e‧‧‧The outer periphery of the apex

119f‧‧‧ apex

C‧‧‧Rotor

JC‧‧‧Rotor

KB‧‧‧Interface

KT‧‧‧Interface

M1‧‧‧Winding machine

M101‧‧‧Winding machine

Fig. 1 is a schematic cross-sectional view showing a front portion of a hoisting machine according to a first embodiment.

Fig. 2 is a perspective view of a hoist according to a first embodiment.

Fig. 3 is a partial cross-sectional development view showing a configuration of a hoist according to a first embodiment.

Fig. 4 is a cross-sectional view showing a front portion of a hoist according to a second embodiment; intention.

Fig. 5 is a schematic cross-sectional view showing a front portion of a hoist according to a third embodiment.

Fig. 6 is a schematic cross-sectional view showing a front portion of a hoisting machine according to a fourth embodiment.

Fig. 7 is a schematic cross-sectional view showing a front portion of a hoist according to a fifth embodiment.

Fig. 8 is a schematic cross-sectional view showing a front portion of a hoisting machine according to a sixth embodiment.

Fig. 9 is a schematic cross-sectional view showing a front portion of a hoist according to a seventh embodiment.

Fig. 10 is a cross-sectional view showing a front portion of a hoisting machine according to an eighth embodiment.

Fig. 11 is a cross-sectional view showing a front portion of a hoisting machine according to a ninth embodiment.

Fig. 12 is a schematic cross-sectional view showing a front portion of a hoisting machine according to a tenth embodiment.

Fig. 13 is a schematic cross-sectional view showing the front portion of the hoisting machine of the eleventh embodiment.

Fig. 14 is a schematic cross-sectional view showing a front portion of a hoist according to a twelfth embodiment.

Fig. 15 is a cross-sectional view showing the front portion of the hoisting machine of the thirteenth embodiment.

Fig. 16 is a cross-sectional view showing a front portion of a hoist according to a fourteenth embodiment schematic diagram.

Fig. 17 is a cross-sectional view showing a front portion of a hoist according to a fifteenth embodiment.

Fig. 18 is a cross-sectional view showing the front portion of the hoisting machine of the sixteenth embodiment.

Fig. 19 is a schematic cross-sectional view showing a front portion of a hoist according to a seventeenth embodiment.

Fig. 20 is a cross-sectional view showing the front portion of the hoisting machine of the eighteenth embodiment.

Fig. 21 is a schematic cross-sectional view showing a front portion of a conventional example of a hoist.

Hereinafter, a hoist according to an embodiment and a rotary electric machine including the same will be described with reference to the drawings. In the following description, components that are the same as or similar to those already described are denoted by the same or similar reference numerals, and the detailed description thereof will be omitted as appropriate. In the following description, the hoist is described by a hoist for an elevator.

[First Embodiment]

First, the first embodiment will be described. Fig. 1 is a schematic cross-sectional view showing the front portion of the hoist according to the embodiment. Fig. 2 is a perspective view of the hoist according to the embodiment. Fig. 3 is a partial cross-sectional development view showing the structure of the hoist according to the embodiment.

As shown in FIGS. 1 to 3, the hoisting machine M1 of the present embodiment has a pair of bearings 4 and 5 which are respectively provided on the bearing bases 2 and 3 which are erected on the mounting table 1, and a rotary shaft 19 which is coupled by a pair of bearings 4. And 5 supports; and the rotor C is engaged with the rotating shaft 19; and the stator S is disposed on the outer peripheral side of the rotor C. The rotating shaft 19 is fixed around the shaft by a sheave 7 for winding a hoist for an elevator. With this configuration, the drive unit of the hoisting machine is overhanged.

The tip end portion 19f of the rotating shaft 19 is formed with a tip end portion outer peripheral portion 19e for engagement, and a convex portion 19t for engaging in the axial direction from the tip end side is formed. In the present embodiment, the convex portion 19t is formed in a disk shape having a diameter smaller than the outer diameter of the outer peripheral portion 19e of the tip end portion.

The rotor C has a rotor core 10 and a chuck 18 that is engaged with the rotor core 10. The chuck 18 has a core engaging portion 18k, the tip end side is extended in a tubular shape and is flanked on the inner peripheral side of the rotor core 10, and the convex portion engaging portion 18f is provided from the base end side of the core engaging portion 18k. The inner peripheral side is extended to engage with the outer peripheral side of the convex portion 19t, and the rear end side extending portion 18b extends from the proximal end side of the core engaging portion 18k toward the rotating shaft 19 side in a tubular shape. In the present embodiment, the convex portion fitting portion 18f is formed by an annular disk portion. Further, the rear end side extending portion 18b is located on the outer peripheral side of the tip end portion outer peripheral portion 19e, and when the hoisting machine M1 is assembled, the convex portion engaging portion 18f is engaged with the convex portion 19t, and the rear end side extending portion 18b is flanked by the apex The outer peripheral portion 19e has the axial center of the rear end extending portion 18b aligned with the axial center of the rotating shaft 19.

The stator S includes a stator core 13 disposed on the outer peripheral side of the rotor core 10, and a gap 12 formed between the stator core 10 and the stator frame; 15. The stator core 13 is supported from the outer peripheral side.

In the chuck 18, the insertion convex portion 18f is formed. The insertion hole of the plurality of bolts; at the tip end portion 19f of the rotary shaft 19, a female screw portion (not shown) that is screwed into the fastening bolt 22 inserted into the bolt insertion hole is formed in the mounting hole for the fastening bolt ( Not shown).

Further, among the bearings 4 and 5, the shaft on the tip end side in the axial direction An end cap 21 of the ring is provided on the chuck side (rotor side) of the bearing 4. In the present embodiment, the end portion 18r of the rear end side extension portion 18b reaches the inner peripheral side of the end cover 21.

In this embodiment, the chuck 18 and the rotating shaft 19 are embedded. When the rear end side extension portion 18b is guided to the tip end portion outer peripheral portion 19e, the chuck 18 is moved in the axial direction of the rotation shaft 19, and the convex portion 19t and the convex portion engagement portion 18f are brought into contact with each other. Pick up. Then, the fastening bolt 22 is inserted into the bolt insertion hole and fastened to the distal end portion 19f, whereby the convex portion 19t is pushed into the convex portion engagement portion 18f to form the engagement portion KT, and the outer peripheral portion of the distal end portion is formed. The engagement portion KB is formed between the 19e and the rear end side extension portion 18b.

As described above, in the present embodiment, when the chuck 18 is embedded When the rotary shaft 19 is connected to the rotary shaft 19, the two engagement portions KT and KB are double-engaged (double-fitted) to engage. Further, when the chuck 18 is flanked by the rotating shaft 19, the leading end outer peripheral portion 19e is guided to the rear end side extending portion 18b to move in the axial direction of the rotating shaft 19, so that the fitting is appropriate The direction is engaged to prevent engagement in the direction of the offset. Therefore, the chuck portion that is engaged with the rotating shaft 19 has a higher rigidity, and has a significant suppression effect on the bending of the chuck 18 accompanying the weight of the rotor C and the magnetic attraction force. It is possible to realize the hoisting machine M1 that does not cause deterioration in assemblability and suppresses noise and vibration during operation.

Moreover, the rear surface 18s of the engaging portion 18f for the convex portion, and the tip end portion The toroidal surface 19s formed around the convex portion 19t in 19f can be engaged in a state of surface contact, so that the fitting state is more appropriate.

In addition, since the eccentric amount of the rotor C is suppressed, it is possible to prevent The imbalance of the gap 12 can suppress vibration and noise caused by electromagnetic vibration. Moreover, since the interval of the gap 12 can be maintained with high precision during the operation of the hoisting machine M1, the characteristics of the hoisting machine M1 can be improved, the size and weight can be reduced.

Further, on the chuck 18, a shaft 19 is formed The convex portion 19f on the outer peripheral side of the convex portion 19t is formed with a distal end side extension portion 18b that is flanked by the distal end portion outer peripheral portion 19e of the rotary shaft 19, and has a double engagement structure. Therefore, when the chuck is removed in order to replace the bearing or the like, when the chuck 18 is removed, one of the engaging portions functions as a guiding portion, so that the engaging surface is prevented from being damaged.

In addition, the rear 18s of the engaging portion 18f for the convex portion is first The annular faces 19s of the end portions 19f are in surface contact with each other, whereby even when the chuck 18 is assembled with respect to the rotating shaft 19 in a state where the tilting is performed, the tilting can be corrected by locking the fastening bolts 22 at the end. 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 circumferential side of the rotor core 10.

Further, the lifting and lowering machine M1 of the present embodiment is provided with the lifting and lowering The machine will become an elevator that achieves these effects, and can make an elevator that suppresses noise and vibration during operation.

[Second Embodiment]

Next, a second embodiment will be described. Fig. 4 is a cross-sectional view showing the front portion of the hoist according to the embodiment.

In the present embodiment, the outer circumference of the rotor C side of the chuck 23 is compared with the first embodiment. Da, that is, the outer circumference of the portion adjacent to the rotor core 10 Da is enlarged, and is larger than the outer peripheral diameter of the bearing side, that is, the outer peripheral diameter of the rear end side extension portion 23b of the chuck 23.

In addition to the effects of the first embodiment, the bending suppression effect of the chuck 23 can be enhanced, and the gripping force of the engaging portion KB formed by the rear end extending portion 23b and the leading end portion 19f can be increased ( Retentivity). Further, since the transmission torque accompanying the gripping force can be increased, the diameter of the hoisting drive unit can be reduced, and the diameter of the chuck 23 and the rotating shaft 19 can be reduced as compared with the conventional one.

[Third embodiment]

Next, a third embodiment will be described. Fig. 5 is a cross-sectional view showing the front portion of the hoist according to the embodiment.

In the present embodiment, the outer diameter of the bearing 4 side of the rear end side extension portion 24b of the chuck 24 is compared with that of the first embodiment. Db1 is enlarged, than the inner diameter of the bearing 4 Db2 is still big.

In this way, in addition to the effects of the first embodiment, It is also possible to enhance the rigidity of the chuck 24 and the rigidity of the rotary shaft 19, and to increase the bending suppression and the gripping force (holding force) of the engaging portion KT. Further, as in the second embodiment, since the transmission torque accompanying the gripping force can be increased, the diameter of the hoisting drive unit can be reduced, and the diameter of the chuck 24 and the rotary shaft 19 can be reduced as compared with the conventional one. .

[Fourth embodiment]

Next, a fourth embodiment will be described. Fig. 6 is a schematic cross-sectional view showing the front portion of the hoist according to the embodiment.

In the third embodiment, the outer diameter of the bearing 4 side of the rear end side extension portion 25b of the chuck 25 is obtained. Db1 is enlarged, than the inner diameter of the bearing 4 Db2 is still big. In addition, in the third embodiment, the axial direction position of the bearing 4 is fixed by the end portion 25r on the bearing 4 side of the rear end side extension portion 25b.

In this way, in addition to the effect of the third embodiment, the end surface 4f of the bearing 4 can be used as a reference surface, and assembly accuracy with higher precision can be obtained, and the bearing 4 can be prevented from moving in the axial direction.

[Fifth Embodiment]

Next, a fifth embodiment will be described. Fig. 7 is a cross-sectional view showing the front portion of the hoist according to the embodiment.

In the present embodiment, the outer peripheral portion of the chuck 4 on the side of the bearing 4 is configured to be provided with a rib-like convex portion RP between the bearing 4 and the end cover 21, and is configured to be capable of agitating the bearing. 4 chuck 26 side of the lubricant.

In this way, in addition to the effects of the first embodiment, deterioration due to curing of the lubricating oil or the like can be prevented, and the life of the bearing 4 can be increased.

[Sixth embodiment]

Next, a sixth embodiment will be described. Fig. 8 is a cross-sectional view showing the front portion of the hoist according to the embodiment.

In the present embodiment, the engagement portion KB between the chuck 27 and the outer peripheral portion 28f of the tip end portion of the rotary shaft 28 is pushed and pulled in comparison with the first embodiment.

In addition to the effects of the first embodiment, the mutual contact area between the engagement portion KB between the chuck 28 and the outer peripheral portion 28f of the tip end portion can be increased, so that the rigidity of the engagement portion KB can be improved. It prevents eccentricity during the engagement and improves the ease of loading and unloading.

[Seventh embodiment]

Next, a seventh embodiment will be described. Fig. 9 is a cross-sectional view showing the front portion of the hoist according to the embodiment.

In the present embodiment, the relationship between the length LT of the engagement portion KT and the length LB of the side portion KB is LT>LB in the rotation axis 29 as compared with the first embodiment. In other words, the length LT of the convex portion 29t extending from the distal end side of the rotating shaft 29 in the axial direction is much larger than that of the first embodiment.

Since the outer diameter of the convex portion 29t is smaller than the distal end portion 29f of the rotating shaft 29, the pressing force required to form the engaging portion KT is smaller than the pressing force required to form the engaging portion KB. Therefore, the convex portion 29t becomes an insertion guide, and eccentricity at the time of assembly can be suppressed.

In this way, in addition to the effects of the first embodiment, the assembly accuracy can be 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 cross-sectional view showing the front portion of the hoist according to the embodiment.

In the present embodiment, the relationship between the length LT of the engagement portion KT and the length KB of the engagement portion KB in the rotation shaft 30 is LT>LB, and the outer circumference of the convex portion 30t is formed. The surface is formed in a push-out shape, and the convex portion 30t constitutes an engaging portion KT that extends from the tip end side of the rotating shaft 30 in the axial direction. In response to this, the inner peripheral surface of the convex portion fitting portion 31f formed in the chuck 31 is also pushed and pulled.

In this way, in addition to the effects of the seventh embodiment, the eccentricity during the engagement and the ease of lifting and unloading can be prevented.

[Ninth Embodiment]

Next, a ninth embodiment will be described. Fig. 11 is a cross-sectional view showing the front portion of the hoist according to the embodiment.

In the present embodiment, the rear end side extension portion 32b of the chuck 32 and the outer peripheral portion of the tip end portion of the rotary shaft 19 are compared with the first embodiment. The engagement portion KB formed by the 19en is formed into a structure of the screw engagement portion N.

In this way, in addition to the effects of the first embodiment, the press-fitting force required to form the engaging portion KB is reduced, so that the shaft bending due to the press-fitting can be prevented, and the eccentricity with respect to the rotor C can be prevented. In addition, by reducing the required pressing force, the detachability can be improved, and the operability of the hoist can be improved.

[Tenth embodiment]

Next, a tenth embodiment will be described. Fig. 12 is a cross-sectional view showing the front portion of the hoist according to the embodiment.

In the present embodiment, the fins 33a are provided on the inner peripheral side of the core engaging portion 33k of the chuck 33 as compared with the first embodiment. In this way, in addition to the effects of the first embodiment, the rigidity of the chuck 33 can be increased by the fins 33a, the bending suppression effect can be enhanced, and the cooling air can be generated by the operation to circulate the cooling air to the wind tunnel wall. A wind tunnel formed by W and the rotor C, whereby air can be blown toward the rotor S or the stator S. Therefore, the cooling performance of the rotor C is improved, and accordingly, the drive unit of the hoist can be made compact and lightweight.

In addition, although only one fin 33a is provided in FIG. 12, from the viewpoint of the amount of blown air, a plurality of fins having a cross shape or the like when viewed from the axial direction are often disposed.

[Eleventh Embodiment]

Next, an eleventh embodiment will be described. Figure 13 is the embodiment A schematic cross-sectional view of the front portion of the hoist.

In the present embodiment, the fins 34a are provided on the inner peripheral side of the core engaging portion 34k of the chuck 34 as compared with the tenth embodiment. Further, the chuck 34 is formed with a vent hole 34h that communicates the inner peripheral side space of the core engaging portion 34k with the bearing 4 side space of the rotor core 10, and is configured to cool the wind generated by the fin 34a. Ventilation towards the bearing 4 or stator S side.

As a result, in addition to the effect of the tenth embodiment, the rigidity of the chuck 34 can be increased by the fins 34a, and the cooling performance can be increased, so that the hoisting drive unit can be further reduced in size and weight.

[12th embodiment]

Next, a twelfth embodiment will be described. Fig. 14 is a cross-sectional view showing the front portion of the hoist according to the embodiment.

In the present embodiment, the axial length of the fin 35a disposed on the inner circumferential side of the core side connecting portion 35k of the chuck 35 is formed to be longer than the axial end of the rotor core 10 as compared with the tenth embodiment. The part also extends outward in the axial direction.

In this way, in addition to the effects of the tenth embodiment, the amount of air blown toward the outer peripheral side of the stator S can be increased, and the cooling performance can be further improved.

[Thirteenth embodiment]

Next, a twelfth embodiment will be described. Figure 15 is the embodiment A schematic cross-sectional view of the front portion of the hoist.

In the present embodiment, the axial length of the fin 36a disposed on the inner circumferential side of the core engaging portion 36k of the chuck 36 is formed to be longer than the axial end of the rotor core 10 as compared with the eleventh embodiment. The part also extends outward in the axial direction.

In this way, in addition to the effects of the eleventh embodiment, the amount of air blown toward 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. Figure 16 is a cross-sectional view showing the front portion of the hoist according to the embodiment.

In the present embodiment, the outer diameter of the core engaging portion 37k of the chuck 37 is enlarged as compared with the first embodiment. Further, on the rotor C side of the bearing 4, a fixing plate 38 that abuts against the bearing 4 is disposed. Further, an insertion hole for inserting a plurality of bolts inserted into the inner side of the core engaging portion 37k and the rear end side extending portion 37b is formed in the chuck 37. In the present embodiment, the female thread is formed in at least a part of the bolt insertion hole. With this configuration, the fixing plate 38 is pressed by the fixing bolts 39 inserted into the bolt insertion holes.

In this way, in addition to the effects of the first embodiment, the axial position of the bearing 4 can be fixed, and the occurrence of creep of the inner ring of the bearing can be prevented.

[Fifteenth embodiment]

Next, a fifteenth embodiment will be described. Figure 17 is a cross-sectional view showing the front portion of the hoist according to the embodiment.

In the present embodiment, the outer diameter of the core engaging portion 40k of the chuck 40 is compared with that of the first embodiment. De expanded. Further, in the chuck 40, an insertion hole for inserting a plurality of bolts inserted into the rear end side extension portion 40b of the chuck 40 from the inside of the core engaging portion 40k is formed. With this configuration, the bearing 4 is pressed by the fixing bolt 41 inserted into the bolt insertion hole.

In this way, in addition to the effects of the first embodiment, the axial position of the bearing 4 can be fixed, and the occurrence of the creeping of the inner ring of the bearing can be prevented.

[Sixth embodiment]

Next, a sixteenth embodiment will be described. Fig. 18 is a cross-sectional view showing the front portion of the hoist according to the embodiment.

In the present embodiment, the bearing 4 is disposed at the end portion of the chuck 42 on the bearing 4 side as compared with the first embodiment. That is, the bearing 4 abuts against the outer periphery of the end portion of the rear end side extension portion 42b of the chuck 42.

In this way, in addition to the effects of the first embodiment, the engagement portion KB formed by the rear end side extension portion 42b and the distal end portion outer peripheral portion 19f of the rotary shaft 19 can be set long. Therefore, the bending suppression effect can be greatly enhanced, and the length from the rotor core 10 to the end cover 21 can be shortened, and the bending suppression can be more effective, and the hoist can be downsized. Further, when the bearing 4 is replaced, the entire chuck 42 can be taken out and disassembled.

[17th embodiment]

Next, a seventeenth embodiment will be described. Fig. 19 is a cross-sectional view showing the front portion of the hoist according to the embodiment.

In the first embodiment, the end portion of the rear end side extension portion 43b of the chuck 43 on the side of the bearing 4 is located closer to the rotor C than the end cover 21, thereby shortening the rear end side extension. The length of the portion 43b in the axial direction.

In the present embodiment, the bending suppression effect is reduced as compared with the first embodiment. However, since the restriction condition of the outer diameter of the rear end side extension portion 43b is no longer present, the rear end side extension portion 43b is increased. The outer diameter is equivalent to the effect of the first embodiment.

[18th embodiment]

Next, an eighteenth embodiment will be described. Fig. 20 is a cross-sectional view showing the front portion of the hoist according to the embodiment.

In the first embodiment, a circumferential groove 44c is provided in the outer peripheral portion 44f of the tip end portion of the rotary shaft 44, and an oil hole 44h communicating with the groove is provided.

In this way, in addition to the effect of the first embodiment, when the chuck 45 is disassembled, the core engagement portion 45k and the tip end outer peripheral portion 44f of the chuck 45 can be reduced by applying hydraulic pressure to the oil hole 44h. The side contact force (grip force) of the formed engaging portion KB can be easily decomposed.

[19th embodiment]

Next, a nineteenth embodiment will be described. Although not shown in the drawings, the relationship between the fastening bolts 22, 39, and 41 and the attachment holes formed at the tip end portions of the rotary shaft is made smaller than that of the first to eighteenth embodiments. (reamer) style.

In this way, in addition to the effects of the first to eighteenth embodiments, a mechanical stopper can be formed. Further, by using the above-mentioned mounting hole which is formed in a winch type, it is possible to improve the assemblability by providing a guide stud during assembly and disassembly.

[Twentyth embodiment]

Next, a twentieth embodiment will be described. In the present embodiment, the hoisting machine other than the hoist for the elevator is used as compared with the first to ninth embodiments. For example, in a rotary electric machine in which a pulley or the like is provided instead of the sheave 7, the same action and effect can be obtained.

(Comparative review example)

Fig. 21 is a schematic cross-sectional view showing a front portion of an example of a conventional hoist. As shown in FIG. 21, the conventional hoist M101 has a pair of bearings 104 and 105 which are respectively disposed on bearing stages 102 and 103 which are erected on the mounting table 101, and a rotating shaft 119 which is supported by a pair of bearings 104 and 105; The rotor JC is engaged with the rotating shaft 119, and the stator JS is disposed on the outer peripheral side of the rotor JC. A tip end portion outer peripheral portion 119e for engagement is formed in the tip end portion 119f of the rotary shaft 119.

The rotor JC has a rotor core 110 and is embedded in the rotor iron The chuck 110 of the heart 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 chuck 118 has a tubular shape portion 111m that is engaged with the outer peripheral portion 119e of the tip end portion. Further, a key 129 is disposed as a stopper for the chuck 118 with respect to the tubular shape portion 111m.

The conventional hoist M101 has the following disadvantages (1) to (5).

(1) (The gap length is unbalanced due to the increase in the bending curvature of the rotor, resulting in electromagnetic noise, vibration, and increased diameter)

Since the chuck 118 is supported only by the tubular shape portion 111m on the rotating shaft 119, the chuck 118 is likely to be bent due to the weight and magnetic attraction of the rotor JC. The following countermeasures must be taken as a bending suppression method. That is, the outer diameter of the chuck portion of the engaging portion JT of the chuck 118 and the rotating shaft 119 must be The diameter of D1 is increased, and the shaft diameter of the rotating shaft 119 also needs to be increased. This may result in deterioration of the assembly property of the hoisting machine M101 or an increase in quality.

(2) (The manufacturing efficiency involved in the adjustment of the gap length is reduced)

In addition to the above-described bending, since the engaging end portion of the chuck 118 has an open shape, it cannot be corrected even when it is flanked only in a slight tilt state during assembly. Therefore, it becomes an unbalance factor of the void 112, and in order to correct it, it is necessary to adjust the void 112, etc., and the characteristic deterioration or the assembly time which is expensive is caused.

(3) (Electrical characteristics deteriorate, diameter increases)

When the gap 112 is enlarged to cope with the countermeasures (1) and (2) described above, the exciting current is increased, and as a result, deterioration in characteristics such as deterioration of power factor and increase in power consumption are caused. Further, in order to obtain the necessary capacity for the operation machine, it is necessary to increase the diameter of the stator core 110 and the rotor core 113, resulting in an increase in the diameter of the hoist.

If the diameters of the stator JS and the rotor JC are increased, the cantilever load due to their respective weights is large, and the vortex vibration is increased. As a result, deterioration in characteristics such as deterioration in riding comfort or deterioration in life of components due to vibration may result in shortening of life. In addition, in order to increase the rigidity of the assembly system in order to suppress the vibration, the entire device is increased in size, or a plurality of anti-vibration rubbers of the anti-vibration system are required, which leads to an increase in the number of parts and a complicated structure.

(4) (Vibration caused by inconsistent shaft center and shortened bearing life)

When the bending of the rotor JC is increased to cause an imbalance in the gap, the entire rotor will be vortexed. When this vortex phenomenon occurs, the centrifugal force and the axial runout are caused by the rotation and rotation imbalance of the magnetic attraction force due to the edge runout of the rotor JC, and a rotational force or the like is generated. As a result, the vibration is increased and the life of the bearing and the hoist M101 is shortened.

An example of the vibration is, for example, a deterioration in the balance shown by the following formula.

Corrected surface eccentricity ε=mr/M where m: unbalanced amount

r: unbalanced radius

M: rotor weight

Balance degree G=εω/1000 where ω: angular velocity

As in the above equation, as the amount of unbalance increases, the value of the balance increases, and as a result, the vibration increases.

In addition, a factor in which the life of the bearings 104, 105 is shortened, that is, a creeping wear phenomenon (Creep Fretting Phenomenon) occurs when the force is such that the rotational force (ie, "rotational load") and the bearing portion are to be restored to rest. When the force (ie, "stationary load") becomes "rotational load > stationary load". Therefore, when the axes are inconsistent, the life of the bearings 104, 105 is shortened, and the life of the hoist M101 is shortened.

(5) (damage during decomposition)

When the bearing 104 is replaced, the chuck 118 must be removed, but since the engaging end portion has an open shape, there is no guide at the time of removal, and the engaging surface or the key 129 is likely to be damaged. As a result, the chuck 118 or the rotating shaft 119 may not be used any more, and it becomes a factor of shortening the life of the hoisting machine M101.

In contrast, the hoist of the first to twentieth embodiments eliminates such disadvantages. In other words, it is possible to suppress noise and vibration during operation without causing deterioration in assemblability or quality.

Furthermore, it is no longer necessary to adjust the gap between the rotor and the stator. Therefore, it is not necessary to increase the diameter of the rotor or the stator, and the characteristics are deteriorated, the assembly time is increased, the structure is complicated, the vibration caused by the inconsistent shaft center is generated, and the bearing life is shortened.

In addition, the engaging portion for the convex portion that is in contact with the outer peripheral side of the convex portion of the rotating shaft is formed on the chuck, and the end portion extending portion that is engaged with the outer peripheral portion of the tip end portion of the rotating shaft is formed to be double Inlay construction. Therefore, when the chuck is removed, one of the engaging portions functions as a guiding portion, so that damage to the engaging surface is avoided.

The embodiments have been described above, but these embodiments are presented by way of example only and are not intended to limit the scope of the invention. The embodiments can be implemented in various other forms, and various omissions, substitutions, and changes can be made without departing from the scope of the invention. The invention and its modifications are intended to be included within the scope of the invention and the scope of the invention.

[Industry Utilization]

The present invention is applied to an elevator or the like to which a rotating electrical machine is applied.

1‧‧‧Installation table

2‧‧‧ bearing table

3‧‧‧ bearing table

4‧‧‧ bearing

5‧‧‧ bearing

7‧‧‧Slot wheel

10‧‧‧Rotor core

12‧‧‧ gap

13‧‧‧ Stator core

15‧‧‧stator frame

18‧‧‧ chuck

18b‧‧‧ Rear end extension

18f‧‧‧Inlays for convex parts

18k‧‧‧Iron joints

18r‧‧‧End

18s‧‧‧The back of the fitting

19‧‧‧Rotary axis

19e‧‧‧The outer periphery of the apex

19f‧‧‧ apex

19s‧‧‧Torus

19t‧‧‧ convex

21‧‧‧End cover

22‧‧‧ fastening bolts

C‧‧‧Rotor

S‧‧‧ Stator

KB‧‧‧Interface

KT‧‧‧Interface

M1‧‧‧Winding machine

Claims (17)

A hoisting machine comprising: a rotating shaft supported by a bearing, wherein a sheave is fixed around the shaft; and a chuck engaged at a front end portion of the rotating shaft; and the front end portion of the rotating shaft is formed The outer peripheral portion of the tip end portion for engagement is formed with a convex portion for engaging in the axial direction from the distal end side, and the chuck is formed with a convex portion on the side of the rotating shaft and the outer peripheral side of the convex portion. The portion engaging portion is formed with an end side extending portion that is engaged with the outer peripheral portion of the tip end portion. The hoist according to claim 1, wherein the outer diameter of the bearing side of the chuck is made larger than the inner diameter of the bearing. The hoist according to the second aspect of the invention is characterized in that the position of the bearing in the axial direction is defined by the end portion of the bearing side of the chuck. The hoist according to the first aspect of the invention, wherein the outer peripheral portion of the tip end portion is formed as a push-out surface whose diameter is tapered toward the tip end side, and a concave surface that overlaps the push surface is formed in the chuck. The hoist according to any one of claims 1 to 4, wherein the chuck has a tubular core engaging portion that engages with an inner peripheral side of the rotor core, and a fin that is provided at the core The inner peripheral side of the engaging portion is used. The hoist according to the fifth aspect of the invention, wherein the chuck has a vent hole that communicates with a space on an inner circumferential side of the core engaging portion and a space on a bearing side of the rotor core. The hoist according to claim 5, wherein the tip end portion is formed with a groove along an outer peripheral portion of the tip end portion and an oil hole that communicates with the groove. The hoist according to claim 6, wherein the tip end portion is formed with a groove along an outer peripheral portion of the tip end portion and an oil hole that communicates with the groove. A rotary electric machine characterized by having the hoist according to any one of claims 1 to 4. A rotary electric machine characterized by having a winch according to item 5 of the patent application. A rotating electrical machine characterized by having a hoist according to item 6 of the patent application. A rotating electrical machine characterized by having a hoist according to item 7 of the patent application. The rotary electric machine according to claim 9, wherein the hoisting machine is a hoist for an elevator. The rotary electric machine according to claim 9, wherein the hoisting machine is a hoist for an elevator. For example, in the rotary electric machine of claim 10, wherein the foregoing The winch is a winch for the lift. The rotary electric machine according to claim 11, wherein the hoisting machine is a hoist for an elevator. The rotary electric machine according to claim 12, wherein the hoisting machine is a hoist for an elevator.