JP5198342B2 - Rotating electric machine - Google Patents

Description

  The present invention relates to a rotating electrical machine including a bearing portion that performs oil lubrication.

  For example, an outer rotor type rotating electrical machine used for a hoist is supported by a pivot, a stator made of a permanent magnet fixed to the pivot, and rotatably supported by the pivot via a bearing. And a provided rotor. The rotor has a cylindrical rotor frame positioned coaxially with the pivot, and end plates that close both ends of the rotor frame. On the other hand, a bearing box is formed at the center of the end plate, and an outer ring of the bearing is fitted into the bearing box. The inner ring of the bearing is fitted on the pivot. Further, a cantilever pivot is fixed to the other end plate, and this pivot is rotatably supported by a bearing base disposed outside the rotor (for example, Patent Document 1).

  A bearing is fitted on the cantilever pivot, and the bearing and the bearing are fitted and rotatably supported by housing the outer ring of the bearing in a bearing stand. A machine inner lid and a machine outer lid are provided at positions corresponding to both ends of the bearing, and each constitutes a bearing box of a bearing stand. A seal 7 is disposed in the pivot through part of the inner lid to prevent oil and grease from flowing out of the bearing. The seal is generally made of an oil seal or felt.

  The rotor frame functions as a sheave around which a rope (rope) is wound, and a brake disk is attached to an end plate on the bearing side of the sheave. The brake that holds the brake disc is attached to a seat provided on the bearing base.

  A rotating body constituted by a sheave, a brake disk, and a pivot is supported by a bearing and is rotatable. The rotating body can be braked (stopped) by sandwiching the brake disc between pads provided in the brake. The area sandwiched by the pads is called the braking surface of the brake disc.

  In the hoist with the above-described configuration, there are two points where the lubricating oil is used: a rope (rope) to be applied to the sheave and a bearing. Oils and fats generated from the sheaves of the sheave and oils and fats generated from the bearings may reach the braking surface of the brake disk through various paths. In order to prevent the oil and fat from reaching the brake disk braking surface, it is conceivable to provide a groove, a convex portion, or a weir in which the oil and fat accumulate in the outflow path. If it is about a slight sag or oil drop, the possibility of oil and fat flowing out to the disc braking surface by a weir or the like is low.

JP 2001-19322 A

  However, when an extremely abnormal amount of oil is generated, such as abnormal use represented by supercharging to the bearing, or accumulation of oil and fat over time due to no inspection, the oil and fat may ride on the weir, convex portion, and the like. The oil that has ridden is collected on the inner circumference of the disc, and when the disc is stopped or rotated at an extremely low speed with the location accumulated by the disc rotating at the top, the disc brake surface on the side of the anti-shelter side There is a possibility of leakage.

  As a measure for suppressing the oil and grease outflow from the bearing portion to the braking surface of the brake disk, for example, a case where a felt and an oil seal are used in combination in the seal portion of the bearing chamber is assumed. However, in the case of this configuration, the size of the seal portion increases, and as a result, the entire bearing box becomes large.

  When oil or grease adheres to the disc braking surface, the friction coefficient with the brake pad decreases, and as a result, the braking force of the brake decreases. If the friction coefficient is set low in consideration of such a decrease in the friction coefficient, it is necessary to set a large pressing force or braking radius in order to obtain a necessary brake torque. When the pressing force is set to a large value, the capacity of the brake increases, and it is necessary to increase the size accordingly. If the braking radius is set to be large, the outer diameter of the disk is increased, and the entire hoisting machine is increased in size.

  In order to prevent oil and fat from adhering to the disc braking surface, maintenance management is important in the operation of the device. If there are few oil prevention measures between the oil generation site and the braking surface, the time for the oil to reach the braking surface is shortened, and the maintenance management interval must be shortened.

  By extending felt seals and installing oil seals and labyrinths in the bearing box seals, it is possible to extend the path of the oil spill path. However, in any of these measures, dimensional aspects, cost problems, etc. May cause adverse effects.

  The present invention has been made in view of the above points, and its purpose is to stably prevent the oil and fat flowing out from the bearing portion and the like from adhering to the brake braking surface, and to suppress a decrease in brake performance. An object of the present invention is to provide a rotating electrical machine capable of improving safety as a device.

A rotating electrical machine according to an aspect of the present invention is fixed to a pivot shaft at least one end portion of which is rotatably supported by a bearing portion, a rotating body attached to the pivot shaft, and an end portion of the rotating body on the bearing portion side. An annular brake disc positioned coaxially with the pivot,
The brake disk has an outer diameter larger than an outer diameter of the rotating body and an inner diameter smaller than an inner diameter of the rotating body, and an outer peripheral portion of the brake disk is positioned on an outer peripheral side of the rotating body and has a braking surface. Configured, the inner peripheral portion of the brake disk constitutes a weir protruding inward from the inner periphery of the rotating body,
The brake disc is an annular oil reservoir groove formed on a side surface of the dam on the rotating body side and extending in the circumferential direction, and an annular oil groove provided on the joint side with the rotating body at a position having a larger diameter than the rotating body. And an inner peripheral surface of the brake disk forms a tapered surface having a larger diameter toward the rotating body.

  According to the above configuration, it is possible to stably prevent the oil and fat flowing out from the bearing portion and the like from adhering to the brake braking surface, and it is possible to suppress the deterioration of the brake performance and improve the safety as a device. Can provide a rotating electric machine.

FIG. 1A is a side view showing a hoisting machine according to the first embodiment of the present invention, partially broken away, and FIG. 1B is a view from the direction of line AA in FIG. FIG. FIG. 2 is a cross-sectional view showing a joint between a rotor frame and a brake disc and a brake disc of the hoist according to the first embodiment. FIG. 3 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the second embodiment. FIG. 4 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the third embodiment. FIG. 5 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the fourth embodiment. FIG. 6 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the fifth embodiment. FIG. 7 is a cross-sectional view corresponding to FIG. 2 illustrating a main part of the hoist according to the sixth embodiment. FIG. 8 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the seventh embodiment. FIG. 9 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the eighth embodiment. FIG. 10 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the ninth embodiment. FIG. 11 is a cross-sectional view corresponding to FIG. 2 illustrating a main part of the hoist according to the tenth embodiment. FIG. 12 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the eleventh embodiment. FIG. 13 is a cross-sectional view corresponding to FIG. 2 showing a main part of a hoist according to a twelfth embodiment. FIG. 14 is a cross-sectional view corresponding to FIG. 2 showing a main part of a hoist according to a thirteenth embodiment. FIG. 15 is a cross-sectional view corresponding to FIG. 2 showing a main part of a hoist according to a fourteenth embodiment. FIG. 16 is a cross-sectional view corresponding to FIG. 2 showing a main part of a hoist according to the fifteenth embodiment. FIG. 17 is a cross-sectional view corresponding to FIG. 2 illustrating a main part of the hoist according to the sixteenth embodiment. FIG. 18 is a cross-sectional view corresponding to FIG. 2 showing a main part of a hoist according to the seventeenth embodiment. FIG. 19 is a cross-sectional view corresponding to FIG. 2 showing a main part of a hoist according to an eighteenth embodiment. FIG. 20 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the nineteenth embodiment. FIG. 21 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the twentieth embodiment. FIG. 22 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the twenty-first embodiment. FIG. 23 is a cross-sectional view corresponding to FIG. 2 showing a main part of a hoist according to a twenty-second embodiment. FIG. 24 is a cross-sectional view corresponding to FIG. 2 showing a main part of a hoisting machine according to a twenty-third embodiment. FIG. 25 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the twenty-fourth embodiment. FIG. 26 is a cross-sectional view corresponding to FIG. FIG. 27 is a cross-sectional view corresponding to FIG. 2 showing a main part of a hoist according to a twenty-sixth embodiment. FIG. 28 is a cross-sectional view corresponding to FIG. 2 showing a main part of a hoist according to a twenty-seventh embodiment. FIG. 29 is a cross-sectional view corresponding to FIG. 2 and showing a relevant part of the hoist according to the twenty-eighth embodiment. FIG. 30 is a cross-sectional view corresponding to FIG. 2 and showing a relevant part of a hoisting machine according to a twenty-ninth embodiment. FIG. 31A is a cross-sectional view corresponding to FIG. 2 illustrating a main part of the hoist according to the thirtieth embodiment, and FIG. 31B is a side view illustrating a part of the brake disk. FIG. 32A is a cross-sectional view corresponding to FIG. 2 illustrating a main part of the hoist according to the thirty-first embodiment, and FIG. 32B is a side view illustrating a part of the brake disk. FIG. 33 is a cross-sectional view corresponding to FIG. 2 showing a main part of a hoist according to a thirty-second embodiment. FIG. 34 is a cross-sectional view corresponding to FIG. FIG. 35 is a cross-sectional view corresponding to FIG. 2 and showing a relevant part of a hoist according to a thirty-fourth embodiment. FIG. 36 is a cross-sectional view corresponding to FIG. 2 and showing a relevant part of a hoist according to a 35th embodiment. FIG. 37 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the thirty-sixth embodiment. FIG. 38 is a cross-sectional view corresponding to FIG. 2 showing a main part of a hoist according to a thirty-seventh embodiment. FIG. 39 is a cross-sectional view corresponding to FIG. 2 showing a main part of the hoist according to the thirty-eighth embodiment.

Hereinafter, a rotating electrical machine according to an embodiment of the present invention will be described in detail with reference to the drawings.
(First embodiment)
FIG. 1A is a side view showing the elevator hoisting machine according to the first embodiment in a partially broken view, and FIG. 1B is a brake disc viewed from the direction A in FIG. FIG. 3 is an enlarged sectional view of a part of the brake disc.

  As shown in FIG. 1, the hoisting machine 30 is configured as, for example, an outer rotor type rotating electrical machine. The hoisting machine 30 includes a sheave 31 that forms a rotating body. The sheave 31 has a cylindrical rotor frame 32 and first and second end walls 34 and 36 that are fixed to both ends of the rotor frame and that are substantially disk-shaped and close both ends of the rotor frame. ing. On the outer peripheral surface of the rotor frame 32, a plurality of engagement grooves 33 for winding a rope are formed concentrically.

  The hoisting machine 30 has a cantilevered first pivot 38 and a cantilevered second pivot 40. The outer end portion of the first pivot 38 is fixed to a support base 42 erected on the base 41, whereby the first pivot 38 is supported substantially horizontally. The first pivot 38 passes through the first end wall 34 and extends coaxially into the rotor frame 32. The first end wall 34 of the sheave 31 is rotatably supported on the first pivot 38 by a bearing 44.

  The second pivot 40 is fixed to the center of the second end wall 36 or formed integrally with the second end wall 36 and protrudes outward from the second end wall. The second pivot 40 extends coaxially with the first pivot 38 and the rotor frame 32. A bearing 46 is fitted on the second pivot 40, and the outer ring of this bearing is housed in a bearing stand 48. The bearing stand 48 is erected on the base 41. As a result, the second pivot 40 is rotatably supported by the bearing base 48 via the bearing 46.

An annular inner lid 47a and a disk-like outer lid 47b are provided at positions corresponding to both ends of the bearing 46, and constitute a bearing box of the bearing stand 48. For example, a lubricant such as grease is held in the bearing 46. A seal 53 is attached to a penetrating portion of the second pivot 40 in the in-machine lid 47a to prevent oil and grease from flowing out of the bearing 46. The seal 53 is generally made of an oil seal or felt.
Thus, the sheave 31 and the second pivot 40 that function as a rotating body are rotatably supported by the bearings 44 and 46, the support base 42, and the bearing base 48, and are held substantially horizontally.

  A stator 50 is attached to the first pivot 38 within the rotor frame 32. The stator 50 includes a cylindrical stator core 51 fixed to the outer periphery of the first pivot 38 and a stator coil 52 wound around the stator core. The stator core 51 is configured by laminating a plurality of annular metal plates made of a magnetic material, for example, a silicon steel plate. A plurality of slots extending in the axial direction are formed on the outer peripheral portion of the stator core 51, and the stator coil 52 is embedded in these slots. The coil ends of the stator coil 52 protrude in the axial direction from both end faces of the stator core 51.

  An annular permanent magnet 54 is fixed to the inner peripheral surface of the rotor frame 32, and faces the outside of the stator core 51 with a predetermined gap. By energizing the stator coil 52 of the stator 50, the permanent magnet 54 is induced, and the sheave 31 as a rotor and the permanent magnet 54 are rotated around the first and second pivots 38 and 40.

  An annular brake disc 60 is attached to the end of the sheave 31 on the bearing 46 side or the second end wall 36. The brake disk 60 is fixed to one end of the rotor frame 32 by screwing, for example. The brake disc 60 is positioned coaxially with the sheave 31 and rotates integrally with the sheave 31. The brake disk 60 is formed to have an outer diameter larger than the outer diameter of the rotor frame 32 and an inner diameter smaller than the outer diameter of the rotor frame 32. The outer peripheral portion of the brake disk 60 protrudes radially outward from the rotor frame 32, and both surfaces of the outer peripheral portion constitute a braking surface 60a.

  A brake pad 63 that faces the braking surface 60a of the brake disc 60 and a pressing mechanism 65 that presses these brake pads are provided. The brake pad 63 and the pressing mechanism 65 are supported by, for example, the bearing stand 48 by a support bracket 67. By sandwiching the brake disc 60 from both sides with the brake pad 63, the rotating body can be braked (stopped).

  As shown in FIGS. 1 and 2, at the end of the rotor frame 32 on the brake disk 60 side, there is an oil catching groove 62 between the engagement groove 33 and the brake disk 60 where the rope is wound. Is formed and extends over the entire circumference. An annular convex portion 64 is formed between the groove 62 and the brake disc 60 over the entire circumference. A plurality of convex portions 66 are provided on the inner peripheral surface of the end portion of the rotor frame 32 along the circumferential direction.

  On the other hand, on the side surface of the brake disc 60 on the side joined to the rotor frame 32, an annular convex portion 68 is provided at a position larger in diameter than the outer periphery of the rotor frame 32 so as to be coaxial with the brake disc. Yes. The inner diameter of the brake disk 60 is formed smaller than the inner peripheral dimension of the rotor frame 32, and the inner peripheral edge of the brake disk 60 protrudes from the inner peripheral edge of the rotor frame 32 toward the center, thereby forming an annular weir 70. doing. The inner peripheral surface of the brake disc 60, that is, the ceiling surface of the weir 70 forms a tapered surface 71 having a large diameter toward the rotor frame 32 side. Further, in the weir 70, an annular oil sump groove 74 is formed on the side surface of the disk on the joint side with the rotor frame 32 and extends coaxially with the brake disk 60 over the entire circumference.

  According to the hoisting machine 30 configured as described above, during operation, the permanent magnet 54 is induced by energizing the stator coil 52 of the stator 50, and the sheave 31 is moved to the first and second pivots 38. , Rotate around 40. As the sheave 31 rotates, a rope (not shown) wound around the sheave 31 is wound up.

  During operation of the hoisting machine 30, the temperature in the bearing box rises due to heat generation. Therefore, when the temperature of the lubricant rises, the oil component flows out from the lubricant, travels into the bearing, and the bearing inner roller is lubricated. The oil that has flowed out flows to the outer peripheral side along the inner surface of the second end wall 36 and the rotor frame 32 by the centrifugal force of the rotating body. A part of the oil and fat generated from the rope of the sheave 31 flows to the brake disc 60 side.

Such adhesion of oil and fat to the brake disc braking surface 60a is prevented as follows.
Oil and fat generated from the rope of the sheave 31 and flowing to the brake disc 60 side is prevented from passing by the groove 62 and the convex portion 64. Should the amount of oil increase abnormally and flow out beyond the groove 62 and the convex portion 64, the oil and fat flows to the side surface of the brake disc via the joint between the rotor frame 32 and the brake disc 60.

On the other hand, the oil generated from the lubricating oil of the bearing 46 and passing through the seal 53 and transmitted through the inner surface of the second pivot 40, the second end wall 36, and the rotor frame 32 is removed from the rotor frame 32 and the brake disc 60. May flow to the side surface of the brake disc 60 through the joint surface.
Oils and fats flowing out from these two paths are prevented from flowing out to the braking surface 60a by the convex portions 68 formed on the side surfaces of the brake disc 15.

Oil and fat adhesion to the braking surface 60a of the brake disk 60 on the side opposite to the sheave can be prevented as follows.
Oil generated from the lubricating oil of the bearing 46, penetrating the seal 53, and transmitted along the inner surface of the second pivot 40, the second end wall 36, and the rotor frame 32 is oil sump grooves in the weir 70 of the brake disk 60. 74 is accumulated and is blocked by the weir 70. Due to the centrifugal force generated by the rotation of the rotating body, the oil and fat on the inner periphery of the sheave 31 tends to gather between the convex portions 66. The convex portion 66 also serves as a guide for guiding oil and fat to the oil sump groove 74. When the rotating body rotates at a low speed or stops, oil and fat can be guided to the oil sump groove 74 of the brake disc 60 by the convex 66, and as a result, the oil collecting effect of the oil sump groove 74 can be enhanced.

  In the unlikely event that the oil or fat gets over the weir 70 and the oil sump groove 74 due to a further abnormal increase in the oil amount, the oil or fat is recovered to the sheave 31 side by the tapered surface 71 on the inner periphery of the brake disk 60 and braked. The drooping to the surface 60a is prevented.

  According to the hoisting machine 30 configured as described above, it is possible to prevent a reduction in braking force of the brake due to oil and fat by reinforcing measures for preventing oil and fat from adhering to the brake disk braking surface. This means that the friction coefficient of the pad 63 can be sufficiently exerted, and the pressing force of the pad 63 or the braking radius of the brake disk 60 can be set to a minimum required value. Improve performance and stabilize characteristics and quality. As a result, it is possible to reduce the brake capacity, reduce the size of the brake, and reduce the size and weight of the hoisting machine.

  Since multiple oil-proofing measures are taken between the oil generation site and the disc braking surface, not only does the oil adhere to the braking surface, but the oil also reaches the braking surface in the event of an abnormality. The maintenance time becomes extremely long, and the maintenance interval can be extended. The structure of the seal 53 associated with the oil / fat prevention measures of the bearing can be simplified, and the bearing box can be downsized. This can reduce the lead time for manufacturing parts and reduce machining accuracy, and can also improve productivity and reduce manufacturing costs.

  When the oil seal is not required to be used due to the simplification of the seal 53, the maintainability of the hoisting machine can be greatly improved, which is beneficial for extending the life of the hoisting machine. Since the friction loss of the seal portion is also reduced, it is possible to reduce the size and weight by suppressing the temperature rise of the sliding portion and the peripheral portion and reducing the capacity of the drive portion. Therefore, not only the performance and characteristics are improved, but also the safety is enhanced, and the possibility of releasing oil and fat is low, and the environment can be improved.

  As described above, oil and grease can be prevented from flowing out to the disc braking surface with a simple structure, contamination of peripheral equipment and surrounding environment can be suppressed, and manufacturing cost, production lead time can be reduced, and reliability can be improved. A rotating electrical machine is obtained. In addition, since the structure can be simplified, it is possible to reduce the size of the rotating electrical machine, save space, and reduce maintenance costs such as maintenance and inspection. A long-life rotating electric machine that is less susceptible to the influence of the surrounding environment such as dust can be provided.

  Next, in the hoisting machines according to the second to thirty-eighth embodiments according to the present invention, the configuration around the brake disk will be mainly described. In the second to thirty-eighth embodiments, only portions different from the first embodiment described above will be described in detail. Other configurations are the same as those of the first embodiment, and a detailed description thereof is omitted.

(Second Embodiment)
FIG. 3 is an enlarged cross-sectional view showing a main part of the hoist according to the second embodiment.
A felt 76 is provided in an oil sump groove 74 provided in the brake disk 60.

According to this configuration, oil and fat can be absorbed by the felt 76 in the case of an abnormal amount of oil while obtaining the same actions and effects as those of the first embodiment, so that further oil resistance can be achieved. Further, by replacing the felt 76, it is possible to stabilize the quality over time and to improve maintainability.

(Third embodiment)
FIG. 4 is an enlarged cross-sectional view showing a main part of the hoist according to the third embodiment.
Similar to the first embodiment, an oil sump groove 74 is formed in the weir 70 of the brake disk 60. In the present embodiment, the position of the oil sump groove 74 overlaps the inner peripheral surface of the rotor frame 32.
According to this configuration, it is possible to reinforce the oil and fat securing in the oil sump groove 74 while obtaining the same operation and effect as the first embodiment. Also, the inner diameter of the brake disc 60 can be increased, and the weight of the brake disc can be reduced and the space of the inner periphery can be increased. By expanding the space, the degree of freedom of the shape of the bearing stand is increased, and the hoisting machine can be further downsized.

(Fourth embodiment)
FIG. 5 is an enlarged cross-sectional view showing a main part of the hoist according to the fourth embodiment.
According to this embodiment, the felt 76 is provided in the oil sump groove 74 of the hoisting machine of the third embodiment described above.

  According to this configuration, the same functions and effects as those of the first and third embodiments can be obtained, and in the case of an abnormal amount of oil, the fat and oil can be absorbed by the felt 76, and further oil resistance can be achieved. In addition, by replacing the felt 76, it is possible to improve the stability and maintainability over time.

(Fifth embodiment)
FIG. 6 is an enlarged cross-sectional view showing a main part of the hoist according to the fifth embodiment.
Similar to the first embodiment, an oil sump groove 74 is formed in the weir 70 of the brake disk 60. In the present embodiment, the oil sump groove 74 is configured to increase in width from the opening side toward the bottom side. According to this configuration, the same actions and effects as in the first embodiment can be obtained, while securing the oil and fat in the oil sump groove 74 can be further strengthened, and a further oilproof effect can be obtained.

(Sixth embodiment)
FIG. 7 is an enlarged cross-sectional view showing a main part of the hoist according to the sixth embodiment.
According to the present embodiment, the felt 76 is provided in the oil sump groove 74 of the hoisting machine of the fifth embodiment described above. According to this configuration, the same functions and effects as those of the first and fifth embodiments can be obtained, and in the case of an abnormal amount of oil, the fats and oils can be absorbed by the felt 76, and further oil resistance can be achieved. In addition, by replacing the felt 76, it is possible to improve the stability and maintainability over time.

(Seventh embodiment)
FIG. 8 is an enlarged cross-sectional view showing a main part of the hoist according to the seventh embodiment.
Similar to the first embodiment, an oil sump groove 74 is formed in the weir 70 of the brake disk 60. In the present embodiment, the inner peripheral side end surface 60 c of the brake disc 60 is configured such that the outer peripheral portion protrudes toward the rotor frame 32 than the oil sump groove 74. According to this configuration, the same actions and effects as in the first embodiment can be obtained, while securing the oil and fat in the oil sump groove 74 can be further strengthened, and a further oilproof effect can be obtained.

(Eighth embodiment)
FIG. 9 is an enlarged cross-sectional view showing a main part of the hoist according to the eighth embodiment.
According to the present embodiment, the felt 76 is provided in the oil sump groove 74 of the hoisting machine of the seventh embodiment described above. According to this configuration, the same functions and effects as those of the first and seventh embodiments can be obtained, and in the case of an abnormal amount of oil, the fat and oil can be absorbed by the felt 76, and further oilproofness can be achieved. In addition, by replacing the felt 76, it is possible to improve the stability and maintainability over time.

(Ninth embodiment)
FIG. 10 is an enlarged cross-sectional view showing a main part of the hoist according to the ninth embodiment.
An oil sump groove 74 is formed in the weir 70 of the brake disc 60. In the present embodiment, the inner peripheral side end surface 60 c of the brake disc 60 is configured such that the outer peripheral portion protrudes toward the rotor frame 32 than the oil sump groove 74. The inner circumference of the opening of the oil sump groove 74 is formed larger than the inner circumference of the other part of the oil sump groove. Thereby, the opening of the oil sump groove 74 forms a convex shape that protrudes radially outward. According to this configuration, the same actions and effects as in the first embodiment can be obtained, while securing the oil and fat in the oil sump groove 74 can be further strengthened, and a further oilproof effect can be obtained.

(Tenth embodiment)
FIG. 11 is an enlarged cross-sectional view illustrating a main part of the hoist according to the tenth embodiment.
According to the present embodiment, the felt 76 is provided in the oil sump groove 74 of the hoisting machine of the ninth embodiment described above. According to this configuration, the same functions and effects as those of the first and ninth embodiments can be obtained, and in the case of an abnormal amount of oil, the fat and oil can be absorbed by the felt 76, and further oilproofness can be achieved. In addition, by replacing the felt 76, it is possible to improve the stability and maintainability over time.

(Eleventh embodiment)
FIG. 12 is an enlarged cross-sectional view showing a main part of the hoist according to the eleventh embodiment.
An oil sump groove 74 is formed in the weir 70 of the brake disc 60. A groove 80 is formed on the inner peripheral surface of the brake disc 60 over the entire circumference. Further, a plurality of oil recovery grooves 81 each having one end communicating with the groove 80 and the other end opening on the inner surface of the brake disk 60 on the rotor frame 32 side are formed in the inner peripheral portion of the brake disk 60, and the circumferential direction Are spaced apart from each other.

  According to this configuration, the same action and effect as in the first embodiment can be obtained, and in the case of an abnormal oil amount, the oil that has advanced to the inner periphery of the brake disk 60 can be blocked by the groove 80. The oil and fat blocked by the groove 80 can be returned to the rotor frame 32 side by the oil recovery groove 81, and an oil-proofing measure for the braking surface 60a on the anti-shelter side can be strengthened.

(Twelfth embodiment)
FIG. 13: is sectional drawing which expands and shows the principal part of the winding machine which concerns on 12th Embodiment.
According to the present embodiment, the felt 76 is provided in the groove 80 of the hoisting machine of the eleventh embodiment described above. According to this configuration, the same function and effect as those of the first and eleventh embodiments can be obtained, and in the case of an abnormal amount of oil, the fat and oil can be absorbed by the felt 76, and further oilproofness can be achieved. In addition, by replacing the felt 76, it is possible to improve the stability and maintainability over time.

(13th Embodiment)
FIG. 14 is an enlarged cross-sectional view showing a main part of the hoist according to the thirteenth embodiment.
An oil sump groove 74 is formed in the weir 70 of the brake disc 60. On the inner peripheral surface of the brake disk 60, a convex portion 82 is formed on the opposite side surface side of the rotor frame 32 over the entire circumference. According to this configuration, the same action and effect as in the first embodiment can be obtained, and in the case of an abnormal amount of oil, the oil that has advanced to the inner periphery of the brake disk 60 can be dammed by the convex portion 82.

(Fourteenth embodiment)
FIG. 15 is an enlarged cross-sectional view showing a main part of the hoist according to the fourteenth embodiment.
There is no oil sump groove in the weir 70 of the brake disc 60, and a cylinder 84 is fitted to the inner peripheral surface of the brake disc 60 instead. The cylinder 84 is fitted to the brake disc 60 by, for example, cold fitting or press fitting. One end of the cylinder 84 protrudes from the inner periphery of the brake disc 60 toward the rotor frame 32, and an annular shielding plate 85 is integrally formed with the other end. The shielding plate 85 protrudes radially inward and outward from the cylinder 84.

  According to this configuration, even when the oil reservoir groove on the side surface of the disk of the first embodiment is not provided, the same operation and effect as those of the first embodiment can be obtained by attaching the cylinder 84, and the oilproofing Measures can be strengthened. In addition, it is possible to reinforce oil-proof measures and standardize the brake disc 60 after the hoisting machine is installed.

(Fifteenth embodiment)
FIG. 16 is an enlarged cross-sectional view showing a main part of the hoist according to the fifteenth embodiment.
There is no oil sump groove in the weir 70 of the brake disc 60, and a cylinder 84 is fitted to the inner peripheral surface of the brake disc 60 instead. The cylinder 84 is fitted to the brake disc 60 by, for example, cold fitting or press fitting. One end of the cylinder 84 protrudes from the inner peripheral edge of the brake disc 60 toward the rotor frame 32 and is further bent toward the outer peripheral side to form a fixed portion 84a. An annular shielding plate 85 is integrally formed at the other end of the cylinder 84. The shielding plate 85 protrudes radially inward and outward from the cylinder 84. A felt 76 is fixed between the fixed portion 84 a of the cylinder 84 and the inner peripheral edge of the brake disk 60.

  According to this configuration, the same actions and effects as those of the first and fourteenth embodiments can be obtained, and the oil-proof measures can be enhanced. In addition, it is possible to reinforce oil-proof measures and standardize the brake disc 60 after the hoisting machine is installed. Further, when the amount of oil is abnormal, the oil and fat can be absorbed by the felt 76, so that further oilproofness can be achieved. By exchanging the felt 76, not only can the quality of the aged be stabilized and the maintainability can be improved, but also the fixing force of the felt 76 can be strengthened.

(Sixteenth embodiment)
FIG. 17 is an enlarged cross-sectional view illustrating a main part of the hoist according to the sixteenth embodiment.
There is no oil sump groove in the weir 70 of the brake disc 60, and a cylinder 84 is fitted to the inner peripheral surface of the brake disc 60 instead. The cylinder 84 is fitted to the brake disc 60 by, for example, cold fitting or press fitting. One end of the cylinder 84 protrudes from the inner periphery of the brake disc 60 toward the rotor frame 32, and an annular shielding plate 85 is integrally formed with the other end. The shielding plate 85 protrudes radially inward and outward from the cylinder 84. After the cylinder 84 is fitted to the brake disc 60, the cylinder 84 is fixed to the brake disc by bending a plurality of fixing portions 84a provided at one end of the cylinder 84 to the brake disc 60 side.

  According to this configuration, even when the oil reservoir groove on the side surface of the disk of the first embodiment is not provided, the same operation and effect as those of the first embodiment can be obtained by attaching the cylinder 84, and the oilproofing Measures can be strengthened. In addition, it is possible to reinforce oil-proof measures and standardize the brake disc 60 after the hoisting machine is installed.

(Seventeenth embodiment)
FIG. 18 is an enlarged cross-sectional view showing a main part of the hoist according to the seventeenth embodiment.
According to the seventeenth embodiment, in the sixteenth embodiment, the felt 76 is arranged in a space formed by chamfering the inner peripheral edge of the brake disk 60. According to this configuration, the same actions and effects as those of the sixteenth embodiment can be obtained, and furthermore, oilproofing measures for the contact portion between the brake disc 60 and the cylinder 84 can be strengthened. Further, the cylinder 84 can be removed and the felt 76 can be easily replaced.

(Eighteenth embodiment)
FIG. 19 is an enlarged cross-sectional view showing a main part of the hoist according to the eighteenth embodiment.
There is no oil sump groove in the weir 70 of the brake disc 60, and instead, an annular shielding plate 85 is provided on the inner periphery of the brake disc 60 on the side opposite to the sheave. The shielding plate 85 protrudes radially inward from the inner peripheral surface of the brake disc 60. An annular groove 86 is formed on the joint surface of the brake disk 60 with the shielding plate 85.

  According to this configuration, even when the oil reservoir groove on the side surface of the disk of the first embodiment is not provided, the same operation and effect as the first embodiment can be obtained by mounting the shielding plate 85, and Oil measures can be strengthened. By providing the groove 86, an oil sump effect can be added between the brake disk 60 and the shielding plate 85, and an oil prevention measure can be enhanced.

(Nineteenth embodiment)
FIG. 20 is an enlarged cross-sectional view illustrating a main part of the hoist according to the nineteenth embodiment.
According to the nineteenth embodiment, the felt 76 is disposed in the groove 86 in the eighteenth embodiment. According to this configuration, the same actions and effects as those of the first and nineteenth embodiments can be obtained, and the oil and fat can be absorbed by the felt 76, so that further oilproofness can be achieved. Further, the shielding plate 85 can be removed and the felt 76 can be easily replaced.

(20th embodiment)
FIG. 21 is an enlarged cross-sectional view illustrating a main part of the hoist according to the twentieth embodiment.
According to the twentieth embodiment, in the nineteenth embodiment, the brake disc 60 is provided with an oil recovery hole 88 that communicates with the groove 86 and the side surface of the brake disc 60 on the rotor side. According to this configuration, the same actions and effects as those of the nineteenth embodiment can be obtained, and oil-proof measures can be strengthened.

(21st Embodiment)
FIG. 22 is an enlarged cross-sectional view showing a main part of the hoist according to the twenty-first embodiment.
The inner diameter of the brake disc 60 is formed substantially equal to the inner diameter of the rotor frame 32, and a cylinder 84 is fitted on the inner peripheral surface of the brake disc 60. The cylinder 84 is fitted to the brake disc 60 by, for example, cold fitting or press fitting. The end of the cylinder 84 on the rotor frame 32 side is bent inward in the radial direction and then further bent toward the rotor frame to form a substantially crank-shaped convex portion 89.

  According to this configuration, even when the weir of the brake disk 60 is omitted, the same operation and effect as in the first embodiment can be obtained by providing the cylinder 84 having the convex portion 89. In addition, even with a hoisting machine that does not have an oil sump groove, it is possible to reinforce oil-proofing measures by attaching the cylinder 84 later. Is possible.

(Twenty-second embodiment)
FIG. 23 is an enlarged cross-sectional view illustrating a main part of the hoist according to the twenty-first embodiment.
According to the twenty-second embodiment, in the twenty-first embodiment, the felt 76 is disposed between the convex portion 89 of the cylinder 84 and the inner peripheral surface of the rotor frame 32. According to this configuration, the same actions and effects as those of the first and twenty-second embodiments can be obtained, and the oil and fats can be absorbed by the felt 76, so that further oilproofness can be achieved. Moreover, by replacing the felt 76, not only can the quality of the aged be stabilized and the maintainability can be improved, but also the fixing force of the felt 76 can be strengthened.

(23rd embodiment)
FIG. 24 is an enlarged cross-sectional view illustrating a main part of the hoist according to the twenty-third embodiment.
The inner diameter of the brake disc 60 is formed substantially equal to the inner diameter of the rotor frame 32, and a cylinder 84 is fitted on the inner peripheral surface of the brake disc 60. The cylinder 84 is fitted to the brake disc 60 by, for example, cold fitting or press fitting. The end portion of the cylinder 84 constitutes a convex portion 90 that protrudes in the axial direction beyond the braking surface 60a on the side opposite to the sheave.

  According to this configuration, even when the weir of the brake disc 60 is omitted, not only operations and effects similar to those of the first embodiment can be obtained, but also the oil and fat scattered from the inner circumferential direction of the brake disc 60 can be removed from the cylinder 84. It is possible to prevent clogging by the convex portion 90 and adhere to the braking surface. In addition, even with a hoisting machine that does not have an oil sump groove, it is possible to reinforce oil-proofing measures by attaching the cylinder 84 later. Is possible.

(24th Embodiment)
FIG. 25 is an enlarged cross-sectional view of a main part of the hoist according to the twenty-fourth embodiment.
The inner diameter of the brake disc 60 is formed substantially equal to the inner diameter of the rotor frame 32, and a cylinder 84 is fitted on the inner peripheral surface of the brake disc 60. The cylinder 84 is fitted to the brake disc 60 by, for example, cold fitting or press fitting. The end portion of the cylinder 84 constitutes a convex portion 90 that protrudes in the axial direction beyond the braking surface 60a on the side opposite to the sheave. An annular groove is formed on the inner peripheral surface of the brake disk 60, here, the joint surface with the cylinder 84, and the felt 76 is disposed in this groove.

  According to this configuration, the same actions and effects as those of the first and twenty-third embodiments can be obtained, and the oil and fats can be absorbed by the felt 76, so that further oilproofness can be achieved. Replacing the felt 76 can not only improve the stability and maintainability over time, but also enhance the fixing force of the felt.

(25th Embodiment)
FIG. 26 is an enlarged cross-sectional view illustrating a main part of the hoist according to the twenty-fifth embodiment.
The inner diameter of the brake disk 60 is formed to be substantially equal to the inner diameter of the rotor frame 32, and an annular shielding plate 92 is provided on the joint surface between the rotor frame 32 and the brake disk 60. An end portion on the inner peripheral side of the shielding plate 92 protrudes from the inner periphery of the rotor frame 32 and the brake disk 60 toward the center, and is further bent toward the rotor frame to constitute a convex portion 92a.

  According to this configuration, even when the weir of the brake disk 60 is omitted, not only the same actions and effects as in the first embodiment can be obtained, but the addition of the shielding plate 92 can enhance the oil-proof measures. . Even with a hoisting machine that does not have an oil sump groove, it is possible to reinforce oil-proofing measures by attaching the shielding plate 92 later, and to enhance oil-proofing measures after installation and standardize the brake disc 60. It becomes possible.

(26th Embodiment)
FIG. 27 is an enlarged cross-sectional view illustrating a main part of the hoist according to the twenty-sixth embodiment.
According to the twenty-sixth embodiment, in the twenty-fifth embodiment, the felt 76 is disposed between the convex portion 92 a of the shielding plate 92 and the inner peripheral surface of the rotor frame 32. According to this configuration, the same functions and effects as those of the first and 25th embodiments can be obtained, and the oil and fat can be absorbed by the felt 76, so that further oilproofness can be achieved. Moreover, by replacing the felt 76, not only can the quality of the aged be stabilized and the maintainability can be improved, but also the fixing force of the felt 76 can be strengthened.

(Twenty-seventh embodiment)
FIG. 28 is an enlarged cross-sectional view showing a main part of the hoist according to the twenty-seventh embodiment.
According to the present embodiment, the oil sump groove 74 is formed in the weir 70 of the brake disk 60 as in the first embodiment. An annular groove 93 is formed in the joint surface between the rotor frame 32 and the brake disk 60, and a felt 76 is disposed in this groove.

  According to this configuration, the same action and effect as in the first embodiment are obtained, and the oil prevention measures at the joint between the brake disk 60 and the rotor frame 32 are strengthened, and the disk braking surface 60a on the rotor frame side. Oil and oil spillage can be prevented more reliably.

(Twenty-eighth embodiment)
FIG. 29 is an enlarged cross-sectional view illustrating a main part of the hoist according to the twenty-eighth embodiment.
According to the present embodiment, the oil sump groove 74 is formed in the weir 70 of the brake disk 60 as in the first embodiment. An annular groove 93 is formed in the joint surface between the rotor frame 32 and the brake disk 60, and an O-ring 94 is disposed in this groove.

  According to this configuration, the same action and effect as in the first embodiment are obtained, and the oil prevention measures at the joint between the brake disk 60 and the rotor frame 32 are strengthened, and the disk braking surface 60a on the rotor frame side. Oil and oil spillage can be prevented more reliably.

(Twenty-ninth embodiment)
FIG. 30 is an enlarged cross-sectional view illustrating a main part of the hoist according to the twenty-ninth embodiment.
According to the present embodiment, the oil sump groove 74 is formed in the weir 70 of the brake disk 60 as in the first embodiment. At the joint between the outer periphery of the rotor frame 32 and the brake disc 60, grooves 95a and 95b are formed in the rotor frame and the brake disc, respectively, and a felt 76 is disposed in the space.

According to this configuration, the same action and effect as in the first embodiment are obtained, and the oil prevention measures at the joint between the brake disk 60 and the rotor frame 32 are strengthened, and the disk braking surface 60a on the rotor frame side. Oil and oil spillage can be prevented more reliably. By exchanging the felt 76, it is possible to stabilize the quality over time and improve the maintainability (30th embodiment).
FIG. 31 is an enlarged cross-sectional view showing a main part of the hoist according to the thirtieth embodiment.
According to the present embodiment, a plurality of bottomed holes 96 are formed on the side surface of the brake disk 60 on the rotor frame side of the weir 70 instead of the oil sump groove. These bottomed holes 96 are provided on the inner circumferential side slightly from the convex portions 66 at the same angular positions as the plurality of convex portions 66 formed on the inner circumferential surface of the rotor frame 32. A felt 76 is disposed in each bottomed hole 96.

  When the sheave 31 is rotated by the operation of the hoisting machine 30, the oil and fat that has flowed out from the bearing 46 is transmitted to the inner surface of the second end wall of the rotating body and the inner surface of the rotor frame 32, and then gathers on the convex portion 66. Further, it is absorbed by the felt 76. According to this configuration, even when the oil sump groove is not formed in the brake disc 60, the same operation and effect as in the first embodiment can be obtained.

(Thirty-first embodiment)
FIG. 32 is an enlarged cross-sectional view showing a main part of the hoist according to the thirty-first embodiment.
According to the present embodiment, a plurality of through holes 97 are formed in the weir 70 of the brake disc 60 in place of the oil sump groove. These through holes 97 are provided on the inner peripheral side slightly from the convex portions 66 at the same angular positions as the plurality of convex portions 66 formed on the inner peripheral surface of the rotor frame 32. Further, a threaded portion is formed at the end of each through hole 97 opposite to the rotor frame 32. A felt 76 is disposed in the opening of each through hole 97 on the rotor frame 32 side, and a screw 98 is screwed into a screw portion on the other end side of the through hole and closed.
According to this configuration, the same operations and effects as those of the thirtieth embodiment can be obtained, the felt 76 can be easily exchanged from the outside, and the maintainability can be improved.

(Thirty-second embodiment)
FIG. 33 is an enlarged cross-sectional view showing a main part of the hoist according to the thirty-second embodiment.
According to the present embodiment, the oil sump groove 74 is formed on the side surface of the weir 70 of the brake disc 60 on the side opposite to the sheave. The side surface of the weir 70 on the side opposite to the sheave is formed such that the inner peripheral portion of the weir 70 is recessed relative to the other portions. A plurality of oil recovery holes 99 are formed through the weir 70 so as to communicate with the oil sump groove 74 and the inner periphery of the sheave 31.
According to this configuration, oil that has been transferred to the anti sheave side of the brake disk 60 beyond the weir 70 and hangs down by the oil sump groove 74 can be recovered through the oil recovery hole 99 to the inner periphery of the sheave 31. it can.

(Thirty-third embodiment)
FIG. 34 is an enlarged cross-sectional view showing a main part of the hoist according to the thirty-third embodiment.
According to the thirty-third embodiment, the felt 76 is arranged in the oil sump groove 74 in the thirty-second embodiment described above. According to this configuration, the same actions and effects as those of the thirty-third embodiment can be obtained, and further, the oil and fat can be absorbed by the felt 76, so that further oilproofness can be achieved. Further, by replacing the felt 76, not only can the quality of the aged be stabilized and the maintainability can be improved, but also the fixing force of the felt can be strengthened.

(Thirty-fourth embodiment)
FIG. 35 is an enlarged cross-sectional view illustrating a main part of the hoist according to the thirty-fourth embodiment.
According to the present embodiment, the annular convex portion 100 is provided on the side surface of the weir 70 of the brake disc 60 on the side opposite to the sheave, and the oil reservoir groove 74 is formed by the convex portion. A plurality of oil recovery holes 99 are formed through the weir 70 so as to communicate with the oil sump groove 74 and the inner periphery of the sheave 31.
According to this configuration, oil that has been transferred to the anti sheave side of the brake disk 60 beyond the weir 70 and hangs down by the oil sump groove 74 can be recovered through the oil recovery hole 99 to the inner periphery of the sheave 31. it can.

(Thirty-fifth embodiment)
FIG. 36 is an enlarged cross-sectional view showing a main part of the hoist according to the thirty-fifth embodiment.
According to the thirty-fifth embodiment, the felt 76 is arranged in the oil sump groove 74 in the thirty-fourth embodiment described above. According to this configuration, the same operation and effect as in the thirty-fourth embodiment can be obtained, and further, the oil and fat can be absorbed by the felt 76, so that further oilproofness can be achieved. Further, by replacing the felt 76, not only can the quality of the aged be stabilized and the maintainability can be improved, but also the fixing force of the felt can be strengthened.

(Thirty-sixth embodiment)
FIG. 37 is an enlarged cross-sectional view showing a main part of the hoist according to the thirty-sixth embodiment.
According to this embodiment, the felt 76 is provided on the inner peripheral side of the convex portion 68 provided on the side surface of the brake disc 60 on the rotor frame 32 side. According to this configuration, the same actions and effects as those of the first embodiment can be obtained, and the oil and fat can be absorbed by the felt 76, so that further oilproofness can be achieved. Further, by replacing the felt 76, it is possible to stabilize the quality over time and improve the maintainability.

(Thirty-seventh embodiment)
FIG. 38 is an enlarged cross-sectional view illustrating a main part of the hoist according to the thirty-seventh embodiment.
According to the present embodiment, on the side surface of the brake disc 60 opposite to the rotor frame 32, the annular convex portion 102 is provided at a position on the inner peripheral side of the braking surface 60a. According to this configuration, the same operations and effects as those of the first embodiment can be obtained, and further, oil resistance can be further improved with respect to the braking surface 60a on the anti sheave side.

(Thirty-eighth embodiment)
FIG. 39 is an enlarged cross-sectional view showing a main part of the hoist according to the thirty-eighth embodiment.
According to the present embodiment, the brake disk 60 and the weir 70 are configured separately. With this configuration, the same operations and effects as those of the first embodiment can be obtained, and standardization by sharing the brake disk 60 can be performed.

  In addition, this invention is not limited to embodiment mentioned above, In the implementation stage, it can change variously in the range which does not deviate from the summary. In addition, the above embodiments include inventions at various stages, and various inventions can be extracted by appropriately combining a plurality of disclosed constituent elements. For example, even if some constituent elements are deleted from all the constituent elements shown in the embodiment, the problem described in the column of the problem to be solved by the invention can be solved, and is described in the column of the effect of the invention. When an effect is obtained, a configuration in which this configuration requirement is deleted can be extracted as an invention.

  In the above-described fourteenth to twenty-fourth embodiments, the cylinder and the shielding plate may be configured as a plurality of divided types such as, for example, two parts, and may be fixed to the brake disk with bolts or the like, for example. As a result, the cylinder and the shielding plate for oil-proofing can be attached in the assembled state of the hoisting machine. Moreover, you may comprise the shielding board in 25th and 26th embodiment mentioned above as several division types, such as dividing into two, for example. In this case, an oil-proof shielding plate can be attached by disassembling only the disk in the assembled state of the hoisting machine.

In the above-described embodiment, the sheave of the hoisting machine and the brake disk may be integrally formed. In this case, the rigidity can be improved. The brake disk is not limited to the rotor frame, and may be attached to other components of the winding machine. The rotating electrical machine is not limited to the outer rotor type, and may be an inner rotor type.
The application of the rotating electrical machine according to the various embodiments described above is not limited to a hoisting machine, but can be applied to a vehicle-mounted rotating electrical machine represented by a vehicle motor and other general industrial motors.

30 ... Hoisting machine, 31 ... Sheave, 32 ... Rotor frame, 34 ... First end wall, 36 ... Second end wall,
38 ... 1st pivot, 40 ... 2nd pivot, 44, 46 ... Bearing, 48 ... Bearing stand,
50 ... Stator, 60 ... Brake disc, 60a ... Braking surface, 64 ... Projection,
68 ... convex portion, 70 ... weir, 71 ... tapered surface, 74 ... oil sump groove, 76 ... felt,
84 ... Cylinder, 85 ... Shielding plate

Claims (10)

A pivot shaft having at least one end portion rotatably supported by a bearing portion;
A rotating body attached to the pivot;
An annular brake disc fixed to the end of the rotating body on the bearing portion side and positioned coaxially with the pivot,
The brake disk has an outer diameter larger than an outer diameter of the rotating body and an inner diameter smaller than an inner diameter of the rotating body, and an outer peripheral portion of the brake disk is positioned on an outer peripheral side of the rotating body and has a braking surface. Configured, the inner peripheral portion of the brake disk constitutes a weir protruding inward from the inner periphery of the rotating body,
The brake disc is an annular oil reservoir groove formed on a side surface of the dam on the rotating body side and extending in the circumferential direction, and an annular oil groove provided on the joint side with the rotating body at a position having a larger diameter than the rotating body. A rotary electric machine having a convex portion, and an inner peripheral surface of the brake disk forming a tapered surface having a larger diameter toward the rotating body side.   2. The rotating electrical machine according to claim 1, wherein the rotating body has a plurality of convex portions formed on an inner peripheral surface thereof and extending to the brake disc, and the convex portions are separated from each other along a circumferential direction.   The rotating electrical machine according to claim 1, wherein the oil sump groove is provided at a position overlapping with an inner peripheral surface of the rotating body.   The rotating electrical machine according to claim 1, comprising an annular groove formed in an inner peripheral surface of the brake disk.   The rotating electrical machine according to any one of claims 1 to 4, wherein a felt is provided in the oil sump groove. A pivot shaft having at least one end portion rotatably supported by a bearing portion;
A rotating body attached to the pivot;
An annular brake disc fixed to the end of the rotating body on the bearing portion side and positioned coaxially with the pivot,
The brake disk has an outer diameter larger than an outer diameter of the rotating body and an inner diameter smaller than an inner diameter of the rotating body, and an outer peripheral portion of the brake disk is positioned on an outer peripheral side of the rotating body and has a braking surface. And an inner peripheral portion of the brake disk forms a weir that protrudes inward from an inner periphery of the rotating body, and the brake disk is connected to the rotating body at a position having a larger diameter than the rotating body. An annular projection provided on the
A rotating electrical machine in which a cylinder is fitted to an inner peripheral surface of the brake disk, and an end of the cylinder on the rotating body side protrudes from an inner periphery of the brake disk to the rotating body side.   The rotating electrical machine according to claim 6, further comprising an annular shielding plate that is fixed to an end of the cylinder opposite to the rotating body and protrudes toward an inner peripheral side of the brake disk. A pivot shaft having at least one end portion rotatably supported by a bearing portion;
A rotating body attached to the pivot;
An annular brake disc fixed to the end of the rotating body on the bearing portion side and positioned coaxially with the pivot,
The brake disk has an outer diameter larger than an outer diameter of the rotating body and an inner diameter smaller than an inner diameter of the rotating body, and an outer peripheral portion of the brake disk is positioned on an outer peripheral side of the rotating body and has a braking surface. Configured, the inner peripheral portion of the brake disk constitutes a weir protruding inward from the inner periphery of the rotating body,
The brake disk is provided on the side of the weir that is formed on the side opposite to the rotating body side and extending in the circumferential direction on the joint side with the rotating body at a position larger in diameter than the rotating body. A rotating electric machine, wherein an inner peripheral surface of the brake disk forms a tapered surface having a larger diameter toward the rotating body.   The rotating electrical machine according to claim 8, wherein the brake disk has an oil recovery hole extending from the oil sump groove to a side surface of the weir on the rotating body side.   The rotating electrical machine according to claim 8 or 9, wherein a felt is provided in the oil sump groove.

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