JP2019047593A - Electric motor with brake - Google Patents

Abstract

To provide an electric motor with a brake that suppresses a grease content of a bearing from reaching a brake disk to control lowering of a brake torque.SOLUTION: An electric motor with a brake includes: an electric motor body; a rotation shaft accommodated in the electric motor body; a bearing bracket arranged at one end of the electric motor body; a bearing that is provided at the bearing bracket to rotatably support the rotation shaft; a disk brake that is arranged in the bearing bracket and has a disk; a space formed by the bearing, the rotation shaft, and an inner wall of the bearing bracket; and a collar that is mounted so as to be located in the space that is in a periphery of the rotation shaft. The bearing includes lubrication oil. The collar is provided with an oil return unit.SELECTED DRAWING: Figure 2

Description

  Embodiments of the present invention relate to a motor with a brake.

  In an electric motor with a brake, a disc type brake is arranged on the opposite load side of the electric motor. In this electric motor, by arranging the felt packing between the bearing on the non-load side and the brake disc, it is possible to suppress that the oil component leaking from the bearing reaches the brake disc.

JP, 2009-67522, A

  However, due to the deterioration caused by the rotational wear of the felt packing, oil and fat components leak from the felt packing and reach the brake disc surface through the rotary shaft surface etc., causing a problem that the brake torque decreases when the brake is operated. .

  Therefore, it is possible to provide an electric motor with a brake in which the fat and oil content of the bearing is prevented from reaching the brake disc, and the decrease in brake torque is suppressed.

  The motor with a brake according to the embodiment is provided on an electric motor body, a rotating shaft stored in the electric motor body, a bearing bracket disposed at one end of the electric motor body, and the bearing bracket, and rotates the rotating shaft. A freely supported bearing, a disc brake disposed on the bearing bracket and including a disc, a space formed by the bearing, the rotating shaft and the inner wall of the bearing bracket, and the space around the rotating shaft And a collar mounted to be positioned, said bearing comprising lubricating oil, said collar provided with an oil return.

Longitudinal sectional view showing a schematic configuration of a motor for a hoist according to a first embodiment Partially enlarged cross-sectional view showing a schematic configuration of a hoist motor Partially enlarged cross-sectional view showing a schematic configuration of a hoist motor Partially enlarged sectional view showing a schematic configuration of a motor for a hoist according to a second embodiment Partially enlarged sectional view showing a schematic configuration of a motor for a hoist according to a third embodiment

  Hereinafter, embodiments will be described based on the drawings. In the following description, the same parts are denoted by the same reference numerals, and the description will be omitted.

First Embodiment
Hereinafter, the motor with brake 1 according to the first embodiment will be described with reference to FIGS. 1 to 3. FIG. 1 is a longitudinal sectional side view of a motor with a brake 1 according to the present embodiment. FIG. 2 is an enlarged view of a portion P of FIG. FIG. 3 is an enlarged view of a portion Q in FIG.

  The braked motor 1 is, for example, a rotating electric machine used for raising and lowering an elevator car. The braked motor 1 includes a motor body 2, a sheave 3, and a disc brake 4. The mesh wheel 3 is a load for a hoisting machine, and the disc brake 4 functions as a braking device for braking the rotation of the rotating shaft 10. In the following description, regarding the motor body 2, the direction in which the sheave 3 is positioned is taken as the load side, and the direction in which the disc brake 4 is located is taken as the non-load side.

  The motor body 2 mainly includes, for example, a permanent magnet type synchronous motor. The motor body 2 is driven, for example, by inverter control. The motor body 2 is provided with the stator 5 and the rotor 6 stored therein. The stator 5 is composed of a stator core 7 formed in a cylindrical shape by laminating a large number of steel plates, and a winding 8 wound around the inner periphery of the stator core 7.

  The rotor 6 includes a rotor core 9 formed of a large number of steel plates disposed on the inner peripheral side of the stator 5 with a gap, and a not-shown permanent magnet fixed to the inner or outer peripheral surface of the rotor core 9. The rotary shaft 10 is inserted into and fixed to the central portion of the rotor core 9. The sheave 3 is coupled to an end 10 a of the rotary shaft 10 projecting outward from the load-side bearing bracket 15. A net (not shown) for hanging the elevator car is hung around the outer periphery of the sheave 3.

  The non-load side bearing bracket 16 is fixed to one end of the motor body 2 by a bearing holding fixing bolt 20. At the non-load side end of the non-load side bearing bracket 16, a disk brake 4 for braking the rotor 6 is provided. In the disc brake 4, a disc 22 is disposed at the end on the non-load side of the rotating shaft 10. The disk 22 is axially slidably engaged with a spline (not shown) provided in the axial direction of the rotating shaft 10 and is provided. The disk 22 is thereby configured to rotate with the rotation of the rotary shaft 10 and to be movable along the axial direction of the rotary shaft 10 by the pressing of an armature 24 described later. There is a gap between the disk 22 and the rotating shaft 10, and it is possible to pass the gap and move the fat and oil component in the front and back direction of the disk 22.

  As also shown in FIG. 2, an armature 24 is provided on the load side of the disk brake 4 and on the non-load side of the disk 22. The armature 24 is configured to be reciprocally movable in the axial direction by an electromagnetic coil 25 a and a spring 25 b provided in the disk brake 4. A pad portion 26 is provided at a portion facing the disc 22 of the armature 24. A pad portion 27 is provided at a portion of the non-load side bearing bracket 16 opposed to the disk 22. The disk 22 is disposed so as to be sandwiched by the pad portions 26 and 27.

  The spring 25 b is configured to bias the armature 24 toward the disc 22. The electromagnetic coil attracts the armature 24 in the reverse load side, that is, in the direction opposite to the biasing force of the spring 25b in the energized state, so that the disc 22 does not receive the braking force. When the electromagnetic coil is disconnected, the armature 24 presses the disc 22 by the biasing force of the spring in the disc brake 4. As a result, the disk 22 moves to the load side, and the disk 22 is held in contact with the pad portions 26 and 27 so that the frictional force generates a braking force on the disk 22. Thus, the rotation of the rotary shaft 10 is braked.

  In the motor body 2, load side bearing brackets 15 and anti-load side bearing brackets 16 are disposed at both ends of the stator 5. The load side bearing bracket 15 is located on the load side of the motor body 2, and the anti-load side bearing bracket 16 is located on the anti-load side. In the non-load side bearing bracket 16, the non-load side bearings 18 configured by the bearings 18a are respectively supported. Although the bearing which is not illustrated also exists in the load side bearing bracket 15, description is abbreviate | omitted here. The non-load side bearing 18 holds lubricating oil which is an oil component such as grease. The rotating shaft 10 of the rotor 6 is rotatably supported by the non-load side bearing 18.

  As shown in FIGS. 2 and 3, the non-load bearing bracket 16 is located on the non-load side of the non-load bearing 18 and includes the rotary shaft 10 and the inner wall 16 a of the non-load bearing bracket 16 and the non-load side. There is a space 32 defined by the bearings 18. The lubricating oil moves from the non-load side bearing 18 to the space 32. The rotating shaft 10 is mounted with a collar 30 fixed by shrink fitting around the rotating shaft 10, and the rotating shaft 10 is configured to be located in the space 32. The collar 30 is a ring-shaped member made of metal. As described above, since the collar 30 is shrink-fitted and fixed to the rotating shaft 10, the collar 30 rotates as the rotating shaft 10 rotates. A gap 31 is present between the collar 30 and the non-load side bearing bracket 16 (inner wall 16a).

  The collar 30 has a substantially rectangular shape as a whole in a longitudinal cross section, and a collar-shaped oil return portion 30a extending in at least the load side in the axial direction is provided at an end opposite to the rotation shaft 10. The lubricating oil that has leaked from the non-load side bearing 18 into the space 32 and has moved to the side surface of the collar 30 is diverted as indicated by arrow A in FIG. , Directed to the axially loaded side, ie the non-loaded side bearing 18 side. The action of turning the lubricating oil is mainly generated by the action of centrifugal force generated in the collar 30 rotating with the rotating shaft 10. In this way, the lubricating oil that has been redirected in the axial load direction is directed away from the gap 31 formed between the collar 30 and the non-load bearing bracket 16, so that the lubrication is lubricated. Oil is prevented from passing through the gap 31 and reaching the disc 22.

  The collar 30 functions as a leakage suppressing member that suppresses the flow of lubricating oil flowing out of the non-load side bearing 18 in the direction of the disk 22. Here, when the lubricating oil moves in the direction of the disc 22, the lubricating oil passes through the gap 31 and further through the gap between the disc 22 and the rotary shaft 10 and the like, and the pad portions 26 and 27 of the disc 22 There is a possibility to reach between.

According to the brake-equipped motor 1 of the first embodiment, the following effects can be obtained.
The non-load bearing bracket 16 has a space 32 located on the anti-load side of the non-load bearing 18 and formed by the rotary shaft 10, the inner wall 16a of the non-load bearing bracket 16, and the non-load bearing 18. Existing. A collar 30, which is shrink-fitted and fixed to the rotation shaft 10, is disposed in the space 32. The collar 30 is provided at its end on the opposite side of the rotary shaft 10 in the longitudinal cross section with an oil return portion 30 a that protrudes in the axial direction in a bowl shape. A gap 31 is present between the collar 30 and the non-load side bearing bracket 16 (inner wall 16a).

  According to this configuration, the lubricating oil that has leaked from the non-load side bearing 18 into the space 32 and has moved on the surface of the collar 30 by the oil return portion 30a provided in the collar 30 is the axial load side, that is, the reverse load. It is directed to the side bearing 18 side. In this way, the axially diverted lubricating oil is directed away from the gap 31 formed between the collar 30 and the non-load bearing bracket 16. That is, the lubricating oil is directed by the collar 30 away from the path to the disc 22. Therefore, the lubricating oil is prevented from passing through the gap 31 and reaching the disc 22. Thereby, the electric motor 1 with a brake in which the fall of the brake torque was suppressed can be provided.

  In addition, since the collar 30 is made of metal, it does not deteriorate. As a result, the deterioration of the collar 30 does not cause the lubricant to leak. Accordingly, it is possible to provide the braked motor 1 with excellent maintenance performance, with a decrease in brake torque being suppressed.

Second Embodiment
Next, a second embodiment will be described with reference to FIG. FIG. 4 is a view corresponding to FIG. 3 in the first embodiment. As shown in FIG. 4, the non-load bearing bracket 16 is located on the non-load side of the non-load bearing 18, and includes the rotary shaft 10, the inner wall 16 a of the non-load bearing bracket 16, and the non-load bearing 18. There is a space 32 configured by the above, and a collar 34 that is shrink-fitted and fixed to the rotation shaft 10 is disposed so as to be located in the space 32. The collar 34 is made of metal. A gap 31 is present between the collar 34 and the non-load side bearing bracket 16 (inner wall 16a).

  The collar 34 has a substantially rectangular shape in the vertical cross section, and is open at the upper end so as to be continuous with the wall surface of the collar 34 in the axial direction and on the load side at the end opposite to the rotating shaft 10. The oil return part 34a in which the character face was formed is provided. The oil return portion 34 a is formed at the end of the collar 34 so as to be curled and extended in the axial load side direction. The lubricating oil that has leaked from the non-load side bearing 18 into the space 32 and has moved to the side surface of the collar 30 is diverted as indicated by the arrow B in FIG. , Oriented in the direction of the axis of rotation 10 or upward in the figure.

  The action of turning the lubricating oil is mainly due to the action of centrifugal force generated on the collar 34 rotating with the rotating shaft 10. In this manner, the lubricant oil which is turned in the axial load direction is moved away from the gap 31 formed between the collar 34 and the non-load bearing bracket 16, that is, the path to the disc 22. The lubricating oil is prevented from passing through the gap 31 and reaching the disc 22.

  According to the motor with brake 1 in the second embodiment, the same effect as that of the motor with brake 1 in the first embodiment can be obtained. The lubricating oil that has been turned by the oil return portion 34 a is turned in the direction away from the path leading to the disk 22, so the lubricating oil is further suppressed from passing through the gap 31 and reaching the disk 22.

Third Embodiment
Next, a third embodiment will be described with reference to FIG. FIG. 5 is a view corresponding to FIG. 3 and FIG. 4 in the first and second embodiments. As shown in FIG. 5, the non-load side bearing bracket 16 is located on the non-load side of the non-load side bearing 18 and includes the rotary shaft 10, the inner wall 16 a of the non-load side bearing bracket 16 and the non-load side bearing 18. There is a space 32 formed by the above, and a collar 36 shrink-fitted and fixed to the rotation shaft 10 is disposed so as to be located in the space 32. The collar 36 is made of metal. A gap 31 exists between the collar 36 and the non-load side bearing bracket 16 (inner wall 16a).

  The collar 36 is provided with a first oil return portion 36 a extending in the axial direction to the load side at an end of the longitudinal cross section opposite to the rotation shaft 10. Furthermore, the second oil return portion 36b is provided connected to a second oil return portion 36b configured to extend the first oil return portion 36a away from the rotation shaft 10 along the shape of the inner wall 16a. ing. The second oil return portion 36b is provided along the surface shape of the inner wall 16a of the non-load side bearing bracket 16, and in the present embodiment, has a U-shape opened on the load side. At this time, the shape of the inner wall 16a has a U-shape open on the load side in the vertical cross section.

  The surface of the second oil return portion 36b opposite to the non-load bearing bracket 16 is formed along the inner wall 16a, and the gap 31 is also formed here. The gap 31 forms a path F of the lubricating oil. Compared with the first and second embodiments, the gap 31 in the third embodiment is extended and formed due to the presence of the second oil return portion 36b, and the path F is extended.

  The lubricating oil that has leaked from the non-load side bearing 18 into the space 32 and has moved to the side of the rotary shaft 10 and the side of the collar 30 by the first oil return portion 36a provided on the collar 30 is indicated by arrow C in FIG. In the direction of the load side, that is, in the direction of the non-load bearing 18, in other words, in the figure to the right. The action of turning the lubricating oil is mainly due to the action of centrifugal force generated in the collar 36 rotating with the rotating shaft 10.

  Thus, first, the lubricating oil is turned in the axial load side direction by the first oil return portion 36a. Furthermore, as indicated by the arrow D, the lubricating oil is also turned in the load side direction by the second oil return portion 36b. The lubricating oil is thereby directed away from the gap 31.

  According to the motor with brake 1 in the third embodiment, the same effect as that of the motor with brake 1 in the first embodiment can be obtained. Furthermore, the lubricating oil reaches the disc 22 because the lubricating oil is directed away from the path leading to the gap 31 or the disc 22 by the two oil return parts of the first oil return part 36a and the second oil return part 36b. Is further suppressed. Further, due to the presence of the second oil return portion 36b, the path F (i.e., the length of the gap 31) for moving the lubricating oil in the direction of the disc 22 is extended so as to be long. Thereby, the lubricating oil can be further suppressed from passing through the path F and reaching the disc 22 side.

  As mentioned above, although some embodiments of the present invention were described, these embodiments are shown as an example and it is not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, substitutions, and modifications can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and the gist of the invention, and are included in the invention described in the claims and the equivalent scope thereof.

  For example, although the motor with a brake 1 which concerns on the said embodiment was demonstrated supposing the case where it was used for an elevator, it does not intend that it limits to this. For example, it can be applied to a hoist for various devices such as a crane. Moreover, although the said embodiment illustrated and demonstrated the disk brake 4 provided with the disk 22 of 1 sheet, it is not limited to this.

  The number of disks 22 may be any number according to the application of the motor with brake 1. In addition, by providing a so-called labyrinth structure in the movement path of the lubricating oil of the non-load side bearing bracket 16, the lubricating oil may be further suppressed from reaching the disc 22 side.

DESCRIPTION OF SYMBOLS 1 ... motor with brake, 4 ... disk brake, 10 ... rotating shaft, 10a, 10b ... end part, 15 ... load side bearing bracket, 16 ... anti-load side bearing bracket, 16a ... inner wall, 18 ... anti-load side bearing, 18a ... bearing, 22 ... disk, 24 ... armature, 30, 34, 36 ... collar, 30a, 34a ... oil return part, 31 ... gap, 32 ... space, 36a ... first oil return part, 36b ... second oil return part

Claims (6)

The motor body,
A rotary shaft stored in the motor body;
A bearing bracket disposed at one end of the motor body;
A bearing provided on the bearing bracket and rotatably supporting the rotating shaft;
A disc brake disposed on the bearing bracket and comprising a disc;
A space formed by the bearing, the rotating shaft and the inner wall of the bearing bracket;
A collar mounted so as to be located in the space around the axis of rotation;
Equipped with
The motor with a brake, wherein the bearing has a lubricating oil, and the collar is provided with an oil return portion.   The motor with a brake according to claim 1, wherein the oil return portion is provided on the opposite side of the rotation axis of the collar and has an axially projecting cross-sectionally wedge shape.   The electric motor with a brake according to claim 1, wherein the oil return portion has a U-shaped cross section provided on the opposite side of the surface of the rotary shaft of the collar.   The motor with a brake according to claim 2 or 3, wherein the oil return section directs the lubricating oil leaked from the bearing in a direction away from the disk.   When the oil return part is a first oil return part, the first oil return part is further provided with a second oil return part formed along the internal shape of the space so as to extend the first oil return part. A motor with a brake as described in. The electric motor with a brake according to claim 5, wherein the second oil return portion lengthens a path along which the lubricating oil leaked from the bearing moves in the disc direction.

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