JP6600223B2 - Electromagnetic brake - Google Patents

Description

  The present invention relates to an electromagnetic brake suitable for use in an electric shutter switch.

  Conventionally, an electric shutter opening / closing machine has a hoisting motor as a power source for lifting the shutter, and a non-excitation operation type electromagnetic brake that restricts the shutter from closing due to its own weight when power supply to the motor is stopped. And. An example of this type of electromagnetic brake is described in Patent Document 1.

The electromagnetic brake disclosed in Patent Document 1 brakes a brake wheel that rotates in synchronization with a hoisting motor, and includes a brake disk that is pressed against the brake wheel by the spring force of the brake spring.
The brake disk is pressed against the brake wheel by the spring force of the spring member when the power supply to the hoisting motor is cut off and the hoisting motor stops. When the hoisting motor stops, the weight of the shutter acts on the brake disc from the hoisting motor via the brake wheel, and a rotational force is applied to the brake disc in the direction in which the shutter is lowered. The electromagnetic brake shown in Patent Document 1 includes a ratchet mechanism in order to restrict reverse rotation of the brake disk due to this rotational force.

The ratchet mechanism has a recess formed in the outer peripheral portion of the brake disc and a ratchet that meshes with the recess when the brake disc rotates reversely.
In the conventional electric shutter opening / closing device, the rotation direction of the hoisting motor at the time of winding the shutter is a direction corresponding to the mounting position of the hoisting motor and the configuration of the speed reducer. The electromagnetic brake incorporated in the electric shutter switch needs to have a ratchet mechanism specification (the rotation direction of the brake disc regulated by the ratchet mechanism) adapted to this rotation direction. For this reason, conventionally, two types of electromagnetic brakes having different rotation directions of the brake disc regulated by the ratchet mechanism have been manufactured. Among these electromagnetic brakes, an electromagnetic brake that meets the specifications of the ratchet mechanism is incorporated in the electric shutter switch.

Japanese Patent No. 3482750

  In order to manufacture two types of electromagnetic brakes having different ratchet mechanism specifications, it is necessary to manufacture two types of ratchets, two members that support the ratchet, etc., or to perform processing according to the rotation direction. For this reason, there has been a problem that productivity of the electromagnetic brake is lowered.

  The present invention has been made to solve such a problem, and an object of the present invention is to provide an electromagnetic brake that increases the productivity by adopting a configuration capable of regulating the rotation without depending on the rotation direction.

  In order to achieve this object, an electromagnetic brake according to the present invention is formed in an annular shape, a field core whose rotation about an axis is restricted, an electromagnetic coil provided in the field core, and the field core A brake shaft penetrating through the shaft center portion, and rotatably supported by the brake shaft and positioned at a position facing the field core, and when the electromagnetic coil is energized, the field core is attracted by magnetism. A brake wheel which is disposed at a position facing an end face of the armature opposite to the field core, and rotates integrally with a rotating shaft of a braked device in a state where a friction member is located between the armature and the armature. , Provided in the field core, for biasing the armature toward the brake wheel. And a lock mechanism that restricts rotation of the armature relative to the field core, and the lock mechanism is formed in a cylindrical shape, and is positioned on the same axis as the brake shaft, and the inner periphery of the field core An outer ring fixed to the inner ring, and an inner ring portion of the outer ring, which is disposed in a state of rotating integrally with the armature and being rotatable with respect to the brake shaft, and is orthogonal to the axis of the brake shaft An inner ring having a plurality of cam portions projecting in the direction spaced apart from each other in a rotational direction, a carrier rotatably supported on the brake shaft, and an axis parallel to the axis of the brake shaft on the carrier. A plurality of planetary rollers that are rotatably supported as a center and are inserted between cam portions of the inner ring in contact with the inner peripheral portion of the outer ring, The portion is formed in a mountain shape that faces the inner peripheral portion of the outer ring when viewed from the axial direction of the brake shaft, and is unidirectional with a roller type in cooperation with the inner peripheral portion of the outer ring and the planetary roller. It constitutes a clutch.

  According to the present invention, in the electromagnetic brake, the brake shaft is configured to be rotatable with respect to the field core, and includes a rotating body that rotates integrally with the brake shaft, and the rotating body includes the cam portion. And a plurality of pressing pieces disposed between the planetary roller and the planetary roller, the pressing piece being sandwiched by the cam portion and the inner peripheral portion of the outer ring, the one-way clutch. May be movable in the rotational direction of the brake shaft between the cam portion and the planetary roller.

  According to the present invention, in the electromagnetic brake, an inner peripheral portion of the outer ring is formed in a state in which a large number of concave portions and convex portions are alternately arranged over the entire area in the circumferential direction, and the planetary roller is provided with a concave portion and a convex portion of the outer ring. The inclined portion that contacts the planetary roller in the cam portion of the inner ring has a concave portion of the planetary roller and a convex portion and a concave portion that mesh with the convex portion. It may be formed.

  According to the present invention, the armature is pressed against the brake wheel via the friction member by the spring force of the spring member when the electromagnetic coil is in a non-excited state. In this state, when rotational torque is applied to the armature from the brake wheel side and the armature rotates, the inner ring rotates relative to the outer ring integrally with the armature, and the cam portion of the inner ring approaches the planetary roller. Further, when the inner ring rotates with respect to the outer ring, the planetary roller is sandwiched in the wedge-shaped space formed between the cam part and the inner peripheral part of the outer ring, and the roller type one-way clutch is in a connected state. Therefore, the rotation of the inner ring is restricted.

The cam portion of the inner ring is formed in a mountain shape when viewed from the axial direction. For this reason, it does not depend on the rotation direction of the inner ring, and the connected state is established when the inner ring rotates with respect to the outer ring. Thus, when the roller type one-way clutch is in the connected state, the rotation of the armature is restricted, and the brake wheel is braked by friction.
Therefore, since the rotation of the brake wheel can be regulated without depending on the rotation direction, it is not necessary to manufacture two types of electromagnetic brakes having different specifications. As a result, according to the present invention, an electromagnetic brake with high productivity can be provided.

It is sectional drawing of the electromagnetic brake which concerns on this invention. It is a front view of an electromagnetic brake. It is sectional drawing which expands and shows a locking mechanism. FIG. 4 is a cross-sectional view taken along line IV-IV of the locking mechanism in FIG. 3. It is sectional drawing which expands and shows the one-way clutch part of a locking mechanism. It is the VI-VI sectional view taken on the line of the locking mechanism in FIG. It is the VII-VII sectional view taken on the line of the locking mechanism in FIG. It is a disassembled perspective view of the principal part. It is the perspective view which looked at a part of carrier from diagonally front upper. It is a disassembled perspective view of a part of lock mechanism. It is sectional drawing which shows the connection state of a one way clutch. It is sectional drawing which shows the connection state of a one way clutch. It is sectional drawing which shows the state at the time of manual winding. It is sectional drawing which shows the state at the time of manual winding.

Hereinafter, an embodiment of an electromagnetic brake according to the present invention will be described in detail with reference to FIGS.
An electromagnetic brake 1 shown in FIG. 1 is provided in an electric shutter opening / closing device 2. The electric shutter opening / closing machine 2 drives a shutter using a hoisting motor (not shown) as a power source, and includes a rotating shaft 3 that is braked by an electromagnetic brake 1. The rotary shaft 3 rotates in synchronization with the hoisting motor when the shutter is wound up and when the shutter is lowered. In this embodiment, the electric shutter opening / closing device 2 corresponds to the “braking device” in the present invention.

  A brake wheel 4 constituting a part of the electromagnetic brake 1 is attached to the distal end portion of the rotating shaft 3 so as to rotate integrally with a fixing bolt 5 and a key 6. The brake wheel 4 has a disk portion 4 a having a diameter larger than that of the rotating shaft 3. The friction member 7 is fixed to one end portion (the right end portion in FIG. 1) of the outer peripheral portion of the disc portion 4a in the direction in which the tip of the rotating shaft 3 is directed in the axial direction. In the following description, one end side in the axial direction (right side in FIG. 1) is simply referred to as “front side”, and the other end side is referred to as “rear side”.

  The electromagnetic brake 1 is accommodated in one housing 11. The housing 11 projects from the main body 12 to the outer side in the radial direction (lower side in FIG. 1). The main body 12 has a bottomed cylindrical shape that opens toward the brake mounting portion 2a of the electric shutter opening / closing device 2. And a convex portion 13. The main body portion 12 is fixed to the brake mounting portion 2a. A brake shaft 14 penetrates through the axial center of the main body 12 having a bottomed cylindrical shape. The brake shaft 14 is disposed at a position spaced forward from the rotating shaft 3. The axis C1 of the brake shaft 14 is located on an extension line of the axis C2 of the rotary shaft 3.

Further, the brake shaft 14 is supported so as to be rotatable and movable in the axial direction at two locations, a rear end portion and an intermediate portion penetrating the housing 11. A rear end portion of the brake shaft 14 is supported by the brake wheel 4 by a ball bearing 15, and an intermediate portion of the brake shaft 14 is supported by the housing 11 by a slide bearing 16.
A circlip 17 and an armature 18 are provided at the rear end of the brake shaft 14 and in the vicinity of the front of the ball bearing 15. The circlip 17 regulates the backward movement of the armature 18 with respect to the brake shaft 14.

  The armature 18 is formed in a disk shape from a magnetic material. The brake shaft 14 passes through the axial center portion of the armature 18. The armature 18 is supported by the brake shaft 14 so as to be movable in the axial direction and rotatable with respect to the brake shaft 14. The outer peripheral portion of the armature 18 extends radially outward from the friction member 7 described above, and faces the friction member 7 from the front.

  A chain wheel 22 of a manual hoisting mechanism 21 is provided at the front end portion of the brake shaft 14. The manual winding mechanism 21 is for manually winding the shutter during a power failure or emergency. An operation chain (not shown) is wound around the chain wheel 22, and the operator rotates by pulling the chain. The brake shaft 14 rotates integrally with the chain wheel 22.

A brake release lever 23 is arranged between the chain wheel 22 and the main body 12 of the housing 11. As shown in FIG. 2, the brake release lever 23 is formed in a shape extending in a direction orthogonal to the axial direction of the brake shaft 14. The brake release lever 23 has a brake shaft 14 passing through one end thereof, and is supported by the brake shaft 14 so as to be swingable in the front-rear direction. Further, as shown in FIG. 1, the brake release lever 23 is held in a state of being sandwiched between a contact member 24 fixed to the brake shaft 14 and a protruding piece 25 of the housing 11. A protrusion 26 is provided on a portion of the brake release lever 23 that faces the contact member 24.
An operation wire 27 is attached to the other end of the brake release lever 23. The brake release lever 23 is pulled by the operator by swinging in a direction in which the wire 27 is pulled by the operator and the other end portion moves forward as indicated by a two-dot chain line in FIG. Push 14 forward.

A field core 31 is fixed to the inner bottom portion of the main body 12 of the housing 11 by fixing bolts 32.
The field core 31 is formed in an annular shape and is positioned on the same axis as the brake shaft 14. Further, the field core 31 is fixed to the housing 11, so that the rotation around the axis and the movement in the axial direction are restricted.
The outer diameter of the field core 31 is smaller than the outer diameter of the armature 18. The armature 18 is disposed near the rear of the field core 31. The brake wheel 4 described above is disposed at a position facing the end face (rear face) on the opposite side to the field core 31 in the armature 18. A gap serving as a predetermined air gap G is formed between the rear end portion of the field core 31 and the armature 18 in contact with the friction member 7.

An annular groove 33 that opens rearward is formed on the outer periphery of the field core 31. An electromagnetic coil 34 is provided in the annular groove 33. The electromagnetic coil 34 generates a magnetic flux (not shown) when energized. The electromagnetic coil 34 is energized when the hoisting motor operates.
The armature 18 is attracted to the field core 31 by magnetism when the electromagnetic coil 34 is energized. At this time, the armature 18 and the brake shaft 14 integrally move backward, or the armature 18 moves backward with respect to the brake shaft 14.

A spring member 35 and a thrust bearing 36 and a frame receiver 42 of a lock mechanism 41 to be described later are provided on the inner periphery of the field core 31.
The spring member 35 is for urging the armature 18 toward the brake wheel 4, and is accommodated in a non-through hole 39 opened on the rear surface of the field core 31. The thrust bearing 36 is provided between the spring member 35 and the armature 18 and is pressed against the armature 18 by the spring force of the spring member 35. For this reason, the spring force of the spring member 35 is transmitted to the armature 18 through the thrust bearing 36.

  The lock mechanism 41 has two functions which will be described later. As shown in FIGS. 3 and 4, the lock mechanism 41 has an annular frame receiver 42 fixed to the inner peripheral portion of the field core 31, and the frame receiver 42. It is comprised with the some components provided in the radial inside. The first function of the lock mechanism 41 is a function that regulates the rotation of the armature 18 relative to the field core 31. The second function is a function of transmitting the rotational force of the brake shaft 14 to the armature 18 when a shutter (not shown) is manually wound up.

The frame receiver 42 is positioned on the same axis as the brake shaft 14 and is fixed to the inner peripheral portion of the field core 31 by press-fitting. In this embodiment, the frame receiver 42 constitutes an “outer ring” in the present invention.
As shown in FIG. 5, a large number of concave portions 42a and convex portions 42b are formed in the inner peripheral portion of the frame receiver 42 so as to be alternately arranged over the entire area in the circumferential direction. The recess 42 a is configured by a recess groove extending in the axial direction of the brake shaft 14. The opening shape of the recess 42a is semicircular. The convex portion 42 b is configured by a semi-circular ridge that extends in the axial direction of the brake shaft 14.

  As shown in FIG. 4, a plurality of planetary rollers 43 are meshed with the inner peripheral portion of the frame receiver 42 having these concave portions 42a and convex portions 42b. As shown in FIG. 5, the planetary roller 43 is formed in a gear shape having a convex portion 43 a that meshes with the concave portion 42 a of the top receiver 42 and a concave portion 43 b that meshes with the convex portion 42 b of the top receiver 42. As shown in FIG. 3, a shaft portion 44 having an axis parallel to the axis of the brake shaft 14 is provided at the front end of the planetary roller 43. The shaft portion 44 is supported on an outer peripheral portion of a carrier 45 described later so as to be rotatable about an axis parallel to the axis of the brake shaft 14.

  As shown in FIGS. 6 and 8, the carrier 45 includes an annular plate portion 46 through which the brake shaft 14 penetrates, and a plurality of support pieces 47 projecting radially outward from the outer peripheral portion of the annular plate portion 46. Has been. The support pieces 47 are arranged at regular intervals in the circumferential direction of the annular plate portion 46. The shaft portion 44 of the planetary roller 43 is fitted into the through hole 47a of the support piece 47 from behind and is rotatably supported by the support piece 47. As shown in FIG. 9, a counterbore 47b is formed at the front of the support piece 47 according to this embodiment. As shown in FIG. 3, an O-ring 48 is attached to the counterbore portion 47b. A shaft portion 44 is fitted in the hollow portion of the O-ring 48. The outer peripheral portion of the O-ring 48 is pressed against the inner peripheral portion of the frame receiver 42. For this reason, the planetary roller 43 is given resistance in the rotational direction by friction between the shaft portion 44 and the O-ring 48.

As shown in FIG. 6, the annular plate portion 46 of the carrier 45 has a through hole 46 a into which the brake shaft 14 is fitted, and is supported by the brake shaft 14 so as to be rotatable and movable in the axial direction. For this reason, when the carrier 45 rotates around the axis C1 of the brake shaft 14, the planetary roller 43 rolls along the frame receiver 42 and rotates around the shaft portion 44, and the axis C1 of the brake shaft 14 is rotated. Revolves as a center.
Further, as shown in FIG. 3, the annular plate portion 46 of the carrier 45 is located in the central portion of the lock mechanism 41 in the axial direction of the brake shaft 14. A star piece 51 described later is disposed behind the annular plate portion 46, and an annular plate portion 53 of a winding piece 52 described later is disposed forward.

The star piece 51 constitutes an “inner ring” in the present invention. As shown in FIGS. 4, 8 and 10, the star piece 51 according to this embodiment includes an annular portion 54 through which the brake shaft 14 passes, a plurality of drive pins 55 provided in the annular portion 54, and an annular shape. A plurality of cam portions 56 projecting from the portion 54 in a direction perpendicular to the axial direction of the brake shaft 14 (outside in the radial direction).
The annular portion 54 has a first through hole 54a into which the brake shaft 14 is fitted, and is supported on the brake shaft 14 so as to be rotatable and movable in the axial direction.
The drive pin 55 is fixed to the annular portion 54 so as to protrude rearward from the annular portion 54. The drive pins 55 according to this embodiment are press-fitted into the second through holes 54b of the annular portion 54, respectively. These drive pins 55 are arranged at regular intervals in the circumferential direction of the annular portion 54. In this embodiment, five drive pins 55 are provided on the annular portion 54.

  As shown in FIG. 3, these drive pins 55 are fitted in notches 57 formed in the axial center portion of the armature 18. As shown in FIG. 8, the notch 57 is formed in a shape extending radially outward from a hole 58 formed to pass the brake shaft 14 through the axial center portion of the armature 18. Further, the same number of notches 57 as the number of drive pins 55 are provided. That is, five cutouts arranged radially at a certain interval in the circumferential direction of the armature 18 are radially formed in the axial center portion of the armature 18. For this reason, the star piece 51 is disposed in the inner peripheral portion of the piece receiver 42 in a state of rotating integrally with the armature 18 and being rotatable with respect to the brake shaft 14.

  As shown in FIG. 4, the plurality of cam portions 56 of the star piece 51 are each formed in a mountain shape that faces the inner peripheral portion of the piece receiver 42 when viewed from the axial direction of the brake shaft 14. Each cam portion 56 according to this embodiment has a first inclined portion 59 located on one side in the circumferential direction of the annular portion 54 of the star piece 51 and a second inclined portion 60 located on the other side. ing. A wedge-shaped space S is formed between the first and second inclined portions 59 and 60 and the inner peripheral portion of the frame receiver 42. The wedge-shaped space S is formed in a shape that becomes the narrowest in the vicinity of the tip portion of the cam portion 56.

The plurality of cam portions 56 are arranged at regular intervals in the circumferential direction (rotation direction) of the annular portion 54 of the star piece 51. The cam portion 56 according to this embodiment is disposed at the same position as the drive pin 55 in the circumferential direction of the annular portion 54. The planetary roller 43 described above is inserted between two cam portions 56 adjacent to each other while being in contact with the inner peripheral portion of the frame receiver 42.
As shown in FIGS. 11 and 12, the cam portion 56 contacts the planetary roller 43 as the star piece 51 rotates about the brake shaft 14. FIG. 11 shows a state in which the star piece 51 is rotated counterclockwise with respect to the piece receiver 42 in FIG. 11, and FIG. Is shown. As the star piece 51 rotates with respect to the piece receiver 42, the planetary roller 43 enters the wedge-shaped space S described above. The planetary roller 43 is sandwiched between the first inclined portion 59 or the second inclined portion 60 of the cam portion 56 and the inner peripheral portion of the frame receiver 42 and is pushed into the narrowest portion of the wedge-shaped space S. Thus, the movement with respect to the frame receiver 42 is restricted. In this state, further rotation of the star piece 51 (armature 18) is restricted.

That is, the cam portion 56 according to this embodiment constitutes a roller type one-way clutch 61 in cooperation with the inner peripheral portion of the frame receiver 42 and the planetary roller 43. The one-way clutch 61 is configured on both sides of a mountain-shaped cam portion 56, respectively. For this reason, as shown in FIGS. 11 and 12, when the star piece 51 rotates with respect to the piece receiver 42, the one-way clutch 61 is engaged without depending on the rotation direction.
As shown in FIG. 5, the first inclined portion 59 and the second inclined portion 60 according to this embodiment include convex portions 59 a and 60 a that mesh with the concave portion 43 b of the planetary roller 43, and the convex portion 43 a of the planetary roller 43. Recesses 59b and 60b that mesh with each other are formed.

  As shown in FIGS. 7 and 8, the hoisting piece 52 has an annular plate portion 62 through which the brake shaft 14 passes, and a plurality of pressing pieces 63 protruding rearward from the outer peripheral portion of the annular plate portion 62. Yes. In this embodiment, the winding piece 52 constitutes a “rotating body” as referred to in the invention of claim 2. The winding piece 52 according to this embodiment is urged rearward by a conical spring 64 provided between the sliding piece 16 and the sliding bearing 16, as shown in FIG. The spring force of the conical spring 64 is transmitted from the annular plate portion 62 of the winding piece 52 to the armature 18 via the annular plate portion 46 of the carrier 45 and the annular portion 54 of the star piece 51. That is, these members are supported by the brake shaft 14 while being sandwiched between the circlip 17 and the conical spring 64.

  A circular hole 62a through which the brake shaft 14 passes and two notches 62b extending from the circular hole 62a to one and the other in the radial direction are formed in the axial center portion of the annular plate portion 62 of the hoisting piece 52. Yes. The circular hole 62a is formed in a shape in which the brake shaft 14 is fitted so as to be rotatable and movable in the axial direction. The notch 62b is formed in a shape into which a connecting pin 65 provided on the brake shaft 14 can be inserted. The opening width of the notch 62b according to this embodiment (the circumferential width of the annular plate portion 62) is wider than the outer diameter of the connecting pin 65. For this reason, the winding piece 52 can be rotated with respect to the brake shaft 14 by an angle at which the connecting pin 65 can move within the notch 62b. The winding top 52 rotates with respect to the field core 31 when the brake shaft 14 rotates with respect to the field core 31 and the connecting pin 65 pushes the side wall of the notch 62b.

  As shown in FIG. 3, the pressing piece 63 extends rearward from the annular plate portion 62 to a position overlapping with the planetary roller 43 when viewed from a direction orthogonal to the axis of the brake shaft 14. Further, as shown in FIG. 4, the pressing piece 63 is disposed between the tip portion of the cam portion 56 and the planetary roller 43 when viewed from the axial direction of the brake shaft 14. More specifically, a total of five sets of pressing pieces 63 are provided for each cam portion 56, with the first pressing piece 63 a and the second pressing piece 63 b positioned on both sides of the cam portion 56 as one set. The first pressing piece 63 a is provided at a position facing the first inclined portion 59 of the cam portion 56, and the second pressing piece 63 b is provided at a position facing the second inclined portion 60 of the cam portion 56. It has been.

Further, the first pressing piece 63a and the second pressing piece 63b are braked between the cam portion 56 and the planetary roller 43 in the state where the one-way clutch 61 is connected (see FIGS. 11 and 12). It is formed in a shape that can move in the rotation direction of the shaft 14. More specifically, as shown in FIG. 11, in a state where the planetary roller 43 contacts the first inclined portion 59 of the cam portion 56 and the one-way clutch 61 is connected, the first pressing piece 63 a is connected to the planetary roller 43. Never touch.
Further, as shown in FIG. 12, in a state where the planetary roller 43 contacts the second inclined portion 60 of the cam portion 56 and the one-way clutch 61 is connected, the second pressing piece 63 b is connected to the planetary roller 43. There is no contact. For this reason, the first and second pressing pieces 63a and 63b do not block the above-described one-way clutch 61 from being connected.

  As shown in FIGS. 13 and 14, the first pressing piece 63 a and the second pressing piece 63 b are formed between the two cam portions 56 adjacent to each other when the winding piece 52 rotates with respect to the piece receiver 42. While pushing the planetary roller 43 toward the intermediate part, the cam part 56 is pushed in the same direction. FIG. 13 shows a state in which the winding frame 52 rotates counterclockwise with respect to the frame receiver 42 in FIG. The first pressing piece 63 a shown in FIG. 13 presses the planetary roller 43, and the second pressing piece 63 b presses the cam portion 56. FIG. 14 shows a state where the winding frame 52 rotates in the clockwise direction in FIG. The first pressing piece 63a shown in FIG. 14 pushes the cam portion 56, and the second pressing piece 63b pushes the planetary roller 43.

Next, the operation of the electromagnetic brake 1 according to this embodiment will be described.
In this electromagnetic brake 1, when the winding motor operates and the shutter moves up and down, the electromagnetic coil 34 is energized, and the armature 18 is attracted to the field core 31 by magnetism against the spring force of the spring member 35. For this reason, braking of the brake wheel 4 is released, and the rotating shaft 3 of the shutter opening / closing machine 2 rotates.
When the winding motor is stopped and the energization of the electromagnetic coil 34 is interrupted, the armature 18 is pressed against the friction member 7 of the brake wheel 4 by the spring force of the spring member 35, and the armature 18 and the brake wheel 4 are frictionally applied. It becomes a combined state. In this state, when the shutter is lowered by its own weight and the rotary shaft 3 rotates, this rotation is transmitted to the star piece 51 of the lock mechanism 41 via the brake wheel 4 and the armature 18, and the star piece 51 is transferred to the frame receiver 42. Rotate.

  When the star piece 51 rotates in this manner, the planetary roller 43 is sandwiched between the wedge-shaped spaces S as shown in FIGS. 11 and 12, and the one-way clutch 61 described above is in a connected state. That is, the planetary roller 43 is sandwiched and stopped between the inner peripheral portion of the frame receiver 42 and the cam portion 56 of the star frame 51, and further rotation of the star frame 51 is restricted. As a result, the rotary shaft 3 stops together with the armature 18 and the brake wheel 4. Thus, when the rotating shaft 3 stops, it does not depend on the rotation direction of the rotating shaft 3.

  When the shutter is manually wound during a power failure or emergency, the operator operates the manual winding mechanism 21 connected to the front end of the brake shaft 14. In this case, the brake shaft 14 is rotated together with the chain wheel 22 in the direction in which the shutter is wound up. When the brake shaft 14 rotates with respect to the field core 31, the rotational force is transmitted from the connecting pin 65 to the hoisting piece 52, and the planetary roller is moved in the direction in which the one-way clutch 61 is released as shown in FIGS. 43 and the cam portion 56 are pressed by the first pressing piece 63a or the second pressing piece 63b. The one-way clutch 61 can be released without depending on the rotation direction when the brake shaft 14 rotates. When the cam portion 56 is pressed by the first pressing piece 63a or the second pressing piece 63b, the star piece 51 rotates with respect to the field core 31 together with the armature 18 and the brake wheel 4, and the rotating shaft 3 rotates. As a result, the shutter can be rolled up manually.

  When the rolled shutter is manually lowered, an operator wire 27 connected to the brake release lever 23 is pulled by the operator. When the wire 27 is pulled, as shown by a two-dot chain line in FIG. 1, the brake release lever 23 swings and the brake shaft 14 moves forward with respect to the housing 11. As a result, the frictional force generated when the armature 18 is pressed against the friction member 7 decreases, and the weight of the shutter cannot be supported, and the rotary shaft 3 rotates with the brake wheel 4 to lower the shutter.

According to the electromagnetic brake 1 configured as described above, the roller-type one-way clutch 61 is connected in a state where the electromagnetic coil 34 is not energized, whereby the rotation of the armature 18 is restricted, and the brake wheel 4 is Damped by friction. The one-way clutch 61 is connected both when the armature 18 rotates in one direction and when it rotates in the other direction. Therefore, the rotation of the brake wheel 4 can be regulated without depending on the rotation direction. There is no need to produce two different types of electromagnetic brakes. As a result, according to the present invention, an electromagnetic brake with high productivity can be provided.

  In the electromagnetic brake 1 according to this embodiment, when the brake shaft 14 is rotated with respect to the field core 31, the cam portion 56 of the star piece 51 (inner ring) is moved to the first pressing piece 63a or the second pressing piece. The one-way clutch 61 is pushed in the direction to be released by 63b. Further, the first pressing piece 63 a or the second pressing piece 63 b presses the planetary roller 43 in the same direction as the cam portion 56. For this reason, the brake shaft 14, the star piece 51, and the armature 18 rotate integrally, and the brake wheel 4 connected to the armature 18 via the friction member 7 rotates in the same direction. Therefore, in the electric shutter opening / closing machine 2 provided with the electromagnetic brake 1, it is possible to manually wind up the shutter even when the electromagnetic coil 34 is in a non-energized state.

In the inner peripheral portion of the frame receiver 42 according to this embodiment, a large number of concave portions 42a and convex portions 42b are formed in an alternating manner over the entire circumferential direction. The planetary roller 43 is formed in a gear shape having a convex portion 43 a and a concave portion 43 b that mesh with the concave portion 42 a and the convex portion 42 b of the top receiver 42. The first and second inclined portions 59 and 60 in contact with the planetary roller 43 in the cam portion 56 of the star piece 51 have convex portions 59a and 60a and concave portions 59b and 60b that mesh with the concave portion 43b and the convex portion 43a of the planetary roller 43. And are formed.
For this reason, when the planetary roller 43 is sandwiched in the wedge-shaped space S formed between the cam portion 56 of the star piece 51 and the inner peripheral portion of the piece receiver 42, the concave portion and the convex portion are engaged, and the planetary roller 43 stops reliably. Therefore, by adopting this embodiment, the reliability of the operation during braking is increased.

  DESCRIPTION OF SYMBOLS 1 ... Electromagnetic brake, 3 ... Rotating shaft, 4 ... Brake wheel, 7 ... Friction member, 14 ... Brake shaft, 31 ... Field core, 34 ... Electromagnetic coil, 35 ... Spring member, 41 ... Locking mechanism, 42 ... Top receiving ( Outer ring), 42a, 43b, 59b, 60b ... concave portion, 42b, 43a, 59a, 60a ... convex portion, 43 ... planetary roller, 45 ... carrier, 51 ... star piece (inner ring), 52 ... winding piece (rotary body), 56 ... cam portion, 59 ... first inclined portion, 60 ... second inclined portion, 61 ... one-way clutch, 63 ... pressing piece, 63a ... first pressing piece, 63b ... second pressing piece.

Claims (3)

A field core which is formed in an annular shape and whose rotation about the axis is restricted;
An electromagnetic coil provided in the field core;
A brake shaft passing through the axial center of the field core;
An armature that is rotatably supported by the brake shaft, is positioned at a position facing the field core, and is magnetically attracted to the field core when the electromagnetic coil is energized;
A brake wheel that is disposed at a position facing an end surface of the armature opposite to the field core, and rotates integrally with a rotating shaft of a braked device in a state in which a friction member is positioned between the armature and the armature;
A spring member provided on the field core and biasing the armature toward the brake wheel;
A locking mechanism that regulates rotation of the armature relative to the field core;
The locking mechanism is
An outer ring formed in a cylindrical shape and fixed to the inner periphery of the field core in a state of being located on the same axis as the brake shaft;
A plurality of cams disposed in an inner peripheral portion of the outer ring so as to rotate integrally with the armature and to be rotatable with respect to the brake shaft, and project in a direction perpendicular to the axis of the brake shaft An inner ring provided with a constant interval in the direction of rotation;
A carrier rotatably supported by the brake shaft;
A plurality of planetary rollers supported by the carrier so as to be rotatable about an axis parallel to the axis of the brake shaft, and inserted between the cam portions of the inner ring in contact with the inner peripheral portion of the outer ring. Prepared,
The cam portion is formed in a mountain shape facing the inner peripheral portion of the outer ring when viewed from the axial direction of the brake shaft, and is a roller type in cooperation with the inner peripheral portion of the outer ring and the planetary roller. An electromagnetic brake comprising a one-way clutch. The electromagnetic brake according to claim 1,
The brake shaft is configured to be rotatable with respect to the field core, and includes a rotating body that rotates integrally with the brake shaft,
The rotating body has a plurality of pressing pieces arranged between a tip portion of the cam portion and the planetary roller,
In the state where the planetary roller is sandwiched between the cam portion and the inner peripheral portion of the outer ring and the one-way clutch is connected, the pressing piece is connected to the brake shaft between the cam portion and the planetary roller. An electromagnetic brake characterized by being movable in the rotational direction. In the electromagnetic brake according to claim 1 or 2, the inner peripheral portion of the outer ring is formed in a state in which a large number of concave portions and convex portions are alternately arranged over the entire region in the circumferential direction.
The planetary roller is formed in a gear shape having a convex portion and a concave portion that mesh with the concave portion and the convex portion of the outer ring,
An electromagnetic brake, wherein a convex portion and a concave portion that mesh with a concave portion and a convex portion of the planetary roller are formed in an inclined portion that contacts the planetary roller in the cam portion of the inner ring.

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