JP2009132471A - Hoist system for elevator, and elevator device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hoist system for an elevator and an elevator device, preventing abnormal increased speed of a car and shortening traveling time of the car. <P>SOLUTION: In the hoist system 3 for the elevator, a rotor 13 is rotated by driving force of a motor 30. A traction sheave 15 around which a main rope 6 for suspending the car and a counterpoise is wound can be rotated independently from the rotor 13. The rotor 13 is provided with an electromagnetic clutch device 39, and the traction sheave 15 is provided with a centrifugal clutch device 40. The electromagnetic clutch device 39 has an electromagnetic actuator 42 including an electromagnet, and can transmit rotational force between the rotor 13 and the traction sheave 15 by controlling power feeding to the electromagnet. The centrifugal clutch device 40 has a centrifugal actuator 44 including a centrifugal weight, and can transmit rotational force between the rotor 13 and the traction sheave 15 by displacing the centrifugal weight by centrifugal force of the traction sheave. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an elevator hoist apparatus for raising and lowering a car and a counterweight, and an elevator apparatus.

  2. Description of the Related Art Conventionally, a drive device such as an elevator in which a continuously variable transmission is provided between a drive motor and a drum speed reducer has been proposed. An electromagnetic clutch device is provided between the reduction gear and the continuously variable transmission. Power transmission between the speed reducer and the electromagnetic clutch device is performed via a transmission chain or the like (see, for example, Patent Document 1).

Japanese Utility Model Publication No. 49-47357

  However, in an elevator to which the conventional driving device as described above is applied, when the weight difference between the car side and the counterweight side is large, the power transmission from the driving motor is interrupted by the operation of the electromagnetic clutch device. In some cases, the speed of the car may become abnormally high.

  The present invention has been made to solve the above-mentioned problems, and can prevent the speed of the car from becoming abnormally high and shorten the time for moving the car. It is an object of the present invention to obtain an elevator hoist apparatus and an elevator apparatus that can perform the above.

  The elevator hoist apparatus device according to the present invention has a motor, a rotating body rotated by a driving force of the motor, a car and a main rope for suspending a counterweight, and is wound independently of the rotating body. An electromagnetic clutch device capable of transmitting a rotational force between a rotating body and a driving sheave by controlling a power feeding to the electromagnetic magnet, and a rotation of the driving sheave. Centrifugal clutch device having a centrifugal operation device including a centrifugal weight displaced with respect to a driving sheave according to a centrifugal force, and capable of transmitting the rotational force between the rotating body and the driving sheave by displacement of the centrifugal weight due to the centrifugal force It has.

  In the elevator hoist apparatus according to the present invention, the rotational force can be transmitted between the rotating body and the driving sheave by controlling the power supply to the electromagnetic magnet, and the rotating body is displaced by the displacement of the centrifugal weight due to the centrifugal force of the driving sheave. Since the rotational force can be transmitted between the driving sheave and the drive sheave, the speed of the car can be made higher than the normal driving speed by opening the electromagnetic clutch device, depending on the load in the car and the moving distance of the car. can do. Accordingly, it is possible to shorten the time required for the car to move to the destination floor and to improve the operation efficiency of the elevator. In addition, when the car speed approaches an abnormally high speed, the centrifugal clutch device is operated by the centrifugal force of the driving sheave, so that the rotation of the driving sheave is limited by the rotating body, and the set range is reduced. The rotational speed of the driving sheave can be suppressed so as not to exceed. Thereby, it can prevent that the speed of a cage | basket | car becomes high abnormally.

Preferred embodiments of the present invention will be described below with reference to the drawings.
Embodiment 1 FIG.
1 is a block diagram showing an elevator apparatus according to Embodiment 1 of the present invention. In the figure, a hoisting machine device 3 for raising and lowering a car 1 and a counterweight 2 is provided in the hoistway. In the car 1, for example, heavy objects (loads) such as passengers and luggage can be loaded. The weight of the counterweight 2 is set so that the car 1 side and the counterweight 2 side are balanced when the load in the car 1 is ½ of the maximum load weight of the car 1.

  A pair of car suspension cars 4 is provided at the lower part of the car 1, and a counterweight suspension car 5 is provided at the upper part of the counterweight 2. The car 1 and the counterweight 2 are suspended in a hoistway by a plurality of main ropes 6 that are continuously wound in the order of each car suspension car 4, the hoisting machine device 3, and the counterweight suspension car 5. ing. One end portion and the other end portion of each main rope 6 are connected to a first rope stopping device 7 and a second rope stopping device 8 provided at the upper part in the hoistway, respectively.

  The car 1 is provided with a scale device (car load detecting device) 9 for detecting the load in the car 1. Information from the scale device 9 is sent to a control device 10 that controls the operation of the elevator. The car 1 is lifted and lowered in the hoistway by the control of the hoisting machine device 3 by the control device 10, and can be stopped at a plurality of floors provided in the building.

  FIG. 2 is a longitudinal sectional view showing the hoisting machine device 3 of FIG. FIG. 3 is a cross-sectional view taken along line III-III in FIG. FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. In the figure, a horizontally arranged main shaft 12 is fixed to a housing 11 fixed in a hoistway. The housing 11 includes a disk-shaped housing main body 11a disposed perpendicular to the axis of the main shaft 12, a cylindrical outer peripheral wall 11b that is fixed to the outer peripheral portion of the housing main body 11a, and that is centered on the axis of the main shaft 12. have. The height of the outer peripheral wall 11b and the length of the main shaft 12 are substantially the same.

  A rotating body 13 is supported on the main shaft 12 via a main shaft side bearing 14. A driving sheave 15 is supported on the rotating body 13 via a sheave-side bearing 16. The rotating body 13 and the drive sheave 15 are arranged coaxially with the main shaft 12. The rotating body 13 and the drive sheave 15 are rotatable independently of each other about the axis of the main shaft 12.

  The driving sheave 15 includes a sheave shaft 17 disposed on the axis of the main shaft 12, a disc-shaped sheave plate 18 that is fixed to the sheave shaft 17 and perpendicular to the axial direction of the sheave shaft 17, and the sheave It has an annular (cylindrical) sheave annular portion 19 that is fixed to the outer periphery of the plate 18 and that is centered on the axis of the sheave shaft 17. The sheave side bearing 16 is fitted on the sheave shaft 17.

  A plurality of main rope grooves 20 are provided on the outer peripheral surface of the sheave annular portion 19 along the rotation direction of the drive sheave 15. The main rope grooves 20 are arranged at intervals from each other in the width direction of the sheave annular portion 19 (that is, the axial direction of the sheave shaft 17). Each main rope 6 is wound around the sheave annular portion 19 along the main rope groove 20. The car 1 and the counterweight 2 are raised and lowered in the hoistway when the driving sheave 15 rotates. The dimension of the sheave annular portion 19 in the width direction is substantially the same as the length of the sheave shaft 17.

  The rotator 13 is disposed between the housing body 11a and the sheave plate 18 and the rotator body 21. The rotator 13 is fixed to the rotator body 21 and disposed on the inner side of the sheave annular portion 19. It has the insertion part 22, and the housing side insertion part 23 fixed to the sheave side insertion part 22 and arrange | positioned inside the outer peripheral wall 11b.

  The rotor body 21 is provided with a main shaft side bearing hole 24 into which the main shaft side bearing 14 is fitted, and a sheave side bearing hole 25 that is arranged coaxially with the main shaft side bearing hole 24 and into which the sheave side bearing 16 is fitted. It has been. The main shaft side bearing hole 24 and the sheave side bearing hole 25 communicate with each other. That is, the rotating body body 21 is provided with a through hole including a main shaft side bearing hole 24 and a sheave side bearing hole 25.

  The sheave side insertion portion 22 includes an annular (cylindrical) first rotating body annular portion 26 that opposes the sheave annular portion 19 in the radial direction of the rotating body 13, a first rotating body annular portion 26, and a rotating body barrel. The first rotating body side wall 27 connecting the portion 21 is provided.

  The housing-side insertion portion 23 includes an annular (cylindrical) second rotating body annular portion 28 that faces the outer peripheral wall 11b in the radial direction of the rotating body 13, and a second rotating body annular portion 28 and a first rotating body annular portion. 26, and a second rotating body side wall portion 29 that connects to H.26. In this example, the outer diameter of the second rotating body annular portion 28 is larger than the outer diameter of the first rotating body annular portion 26.

  A motor 30 is provided between the outer peripheral wall 11b and the second rotating body annular portion 28 to rotate the rotating body 13 by receiving power. The motor 30 includes a stator 31 provided on the inner peripheral surface of the outer peripheral wall 11b and including the winding 31a, and a permanent magnet 32 provided on the outer peripheral surface of the second rotating body annular portion 28 and facing the stator 31. is doing. The permanent magnet 32 receives a rotating magnetic field by supplying power to the winding 31a. Thereby, the rotating body 13 is rotated together with the permanent magnet 32.

  A brake device 33 that brakes the rotation of the rotating body 13 is provided inside the second rotating body annular portion 28. The brake device 33 is supported by the housing 11.

  As shown in FIG. 3, the brake device 33 is provided on each movable member 34 and a pair of movable members 34 that can be displaced with respect to the rotating body 13. A pair of brake shoes 35 that can be brought into and out of contact with the inner peripheral surface, a common brake spring 36 that urges the movable member 34 in a direction in which each brake shoe 35 contacts the second rotating body annular portion 28, Each brake shoe 35 has a common brake electromagnetic magnet 37 that displaces the movable member 34 in a direction away from the second rotating body annular portion 28 against the urging force.

  The movable member 34 is displaced with respect to the rotating body 13 by being rotated around a pin 38 provided in the housing 11. In addition, the brake electromagnetic magnet 37 generates an electromagnetic force against the urging force of the brake spring 36 by receiving power.

  As shown in FIG. 2, the rotating body 13 is provided with an electromagnetic clutch device 39 for transmitting a rotational force between the rotating body 13 and the drive sheave 15. Further, as shown in FIG. 2, the driving sheave 15 is provided with a centrifugal clutch device 40 for transmitting a rotational force between the rotating body 13 and the driving sheave 15.

  The electromagnetic clutch device 39 includes a plate-shaped rotating body side contact body 41 disposed between the sheave plate 18 and the first rotating body side wall portion 27, and a plurality of (this rotating body side contact body 41 is displaced by power supply control. In the example, three electromagnetic actuators 42 are provided. As shown in FIG. 4, the electromagnetic actuators 42 are arranged at equal intervals in the circumferential direction of the rotating body side contact body 41.

  The centrifugal clutch device 40 includes a plate-shaped sheave-side contact body 43 disposed between the sheave plate 18 and the first rotating body side wall 27, and sheave-side contact according to the rotational speed of the drive sheave 15. And a plurality of (three in this example) centrifugal actuators 44 for displacing the body 43. As shown in FIG. 4, the centrifugal actuators 44 are arranged at equal intervals in the circumferential direction of the sheave side contact body 43.

  The rotating body side contact body 41 and the sheave side contact body 43 are opposed to each other in the axial direction of the main shaft 12, as shown in FIG. Moreover, the rotary body side contact body 41 and the sheave side contact body 43 are displaceable in the direction in which they contact and separate from each other. That is, the rotating body side contact body 41 is displaced by the electromagnetic actuator 42 in a direction in which the rotor side contact body 41 contacts and separates from the sheave side contact body 43. Further, the sheave side contact body 43 is displaced by the centrifugal actuator 44 in a direction in which the sheave side contact body 43 comes in contact with and separates from the rotary body side contact body 41. The transmission of the rotational force between the rotating body 13 and the driving sheave 15 is executed when the rotating body side contact body 41 and the sheave side contact body 43 come into contact with each other, and the rotating body side contact body 41 and the sheave side contact body 43 are contacted. Are released by separating from each other.

  A planetary gear device 45 is provided between the sheave annular portion 19 and the first rotating body annular portion 26. The planetary gear unit 45 includes a sheave side rack gear 46 provided on the inner peripheral surface of the sheave annular portion 19, a rotary body side rack gear 47 provided on the outer peripheral surface of the first rotary body annular portion 26, and a sheave side rack gear. 46 and the rotating body side rack gear 47, and a plurality of planetary gears 48 that mesh with the sheave side rack gear 46 and the rotating body side rack gear 47, respectively.

  Each planetary gear 48 rotates while meshing with each of the sheave-side rack gear 46 and the rotor-side rack gear 47 by the relative rotation of the rotating body 13 and the drive sheave 15. This prevents the rotational speed difference between the rotating body 13 and the drive sheave 15 from becoming extremely large.

  The main shaft 12 is provided with a main shaft through hole 49 along the axis of the main shaft 12. The cross-sectional shape of the opening of the main shaft through hole 49 on the sheave shaft 17 side is a quadrangle. The sheave shaft 17 is provided with a sheave shaft through hole 50 along the axis of the sheave shaft 17.

  Here, FIG. 5 is a partially broken perspective view showing the sheave shaft 17 of FIG. The sheave shaft 17 is provided with a sheave encoder (speed detection device) 51 that generates a signal corresponding to the rotation of the drive sheave 15. The sheave encoder 51 includes a cylindrical rotating portion 51a that rotates integrally with the driving sheave 15, and a main body 51b that is disposed inside the rotating portion 51a and detects the rotation of the rotating portion 51a. .

  A square pipe 52 having a square cross section that is passed through a sheave shaft through hole 50 is connected to the main body 51 b of the sheave encoder 51. The end of the square pipe 52 is fitted into the opening of the main shaft through hole 49. Thereby, the rotation of the square pipe 52 is prevented. A signal line 53 connected to the sheave encoder 51 is passed through the square pipe 52 and the main shaft through hole 49. Information from the sheave encoder 51 is sent to the control device 10 through the signal line 53.

  The rotating body barrel 21 is provided with a rotating body encoder 74 that generates a signal corresponding to the rotation of the rotating body 13. Information from the rotating body encoder 74 is also sent to the control device 10 via a signal line (not shown).

  FIG. 6 is an enlarged view showing a VI portion of FIG. 7 is a partially broken perspective view showing the electromagnetic clutch device 39, the centrifugal clutch device 40, and the planetary gear device 45 of FIG. In the figure, a pair of guide plates 54 for guiding the planetary gear 48 so as to rotate while meshing with the sheave side rack gear 46 and the rotating body side rack gear 47 are attached to the gear shaft of each planetary gear 48.

  As shown in FIG. 6, a step portion 55 that restricts the displacement of the guide plate 54 is provided on each side of the inner peripheral surface of the sheave annular portion 19 and the outer peripheral surface of the first rotating body annular portion 26. Yes. As a result, the planetary gear 48 is prevented from being largely displaced with respect to the sheave side rack gear 46 and the rotating body side rack gear 47.

  The rotating body side contact body 41 has a clutch disk 56 and a plurality of clutch shoes 57 attached to the surface of the clutch disk 56 on the sheave side contact body 43 side. The contact of the rotating body side contact body 41 with the sheave side contact body 43 is performed by the clutch shoe 57 coming into contact with the sheave side contact body 43. As shown in FIG. 4, the clutch shoes 57 are arranged at equal intervals in the rotational direction of the drive sheave 15. The sheave side contact body 43 is a clutch disk having the same shape as the clutch disk 56 of the rotating body side contact body 41.

  Each electromagnetic actuator 42 is disposed inside the first rotating body annular portion 26. Further, each electromagnetic actuator 42 is attached to an attachment metal 58 fixed to the inner peripheral surface of the first rotating body annular portion 26 with a bolt. Further, each electromagnetic actuator 42 is configured to bias the electromagnetic rod 59 in a direction in which the rotating body side contact body 41 contacts the sheave side contact body 43 and the electromagnetic rod 59 displaced integrally with the rotating body side contact body 41. A biasing spring 60 and a clutch electromagnetic magnet 61 that displaces the electromagnetic rod 59 in a direction in which the rotating body side contact body 41 moves away from the sheave side contact body 43 against the biasing force of the biasing spring 60 are provided.

  The electromagnetic rod 59 penetrates the first rotating body side wall portion 27 so as to be displaceable. The electromagnetic rod 59 is displaced in a direction in which the urging force of the urging spring 60 is applied when power supply to the electromagnetic coil included in the clutch electromagnetic magnet 61 is stopped. Thereby, the rotating body side contact body 41 is displaced in a direction in which the rotor side contact body 41 contacts the sheave side contact body 43. In addition, the electromagnetic rod 59 is displaced in a direction against the urging force of the urging spring 60 by performing power supply to the electromagnetic magnet 61 for clutch. Thereby, the rotating body side contact body 41 is displaced in a direction away from the sheave side contact body 43.

  Each of the rotating body 13 and the main shaft 12 is provided with a sliding current collector (not shown) in contact with each other. One sliding current collector slides with respect to the other sliding current collector by the rotation of the rotating body 13. Power is supplied to the electromagnetic magnet 61 for clutch through each sliding current collector.

  On the surface of the sheave plate 18 opposite to the first rotating body side wall 27 side (outer surface of the sheave plate 18), a recess 62 is provided along the rotational direction of the drive sheave 15. Each centrifugal actuator 44 is provided in the recess 62. A centrifugal clutch cover 63 that covers the recess 62 is attached to the drive sheave 15 with screws.

  FIG. 8 is a partially cutaway front view showing the centrifugal clutch device 40 of FIG. The centrifugal actuator 44 is a centrifugal weight 64 that is displaced radially outward in response to the centrifugal force generated by the rotation of the drive sheave 15, and a rotation that is rotated with respect to the drive sheave 15 in accordance with the displacement of the centrifugal weight 64. The movable arm 65, the arm biasing spring (arm biasing body) 66 that biases the rotating arm 65 in a direction against the centrifugal force received by the centrifugal weight 64, and the sheave-side contact body 43 are integrally displaced. A rod 67 and a conversion device (conversion means) 68 that converts the rotation of the rotation arm 65 into the displacement of the centrifugal rod 67 are provided.

  The pivot arm 65 is pivotable about a shaft pin 69 provided on the sheave plate 18. The shaft pin 69 is attached to an intermediate portion of the rotating arm 65. The centrifugal weight 64 is attached to one end of the rotating arm 65. The other end of the rotating arm 65 is displaced inward in the radial direction of the drive sheave 15 by the displacement of the centrifugal weight 64 due to the centrifugal force of the drive sheave 15.

  The arm biasing spring 66 is connected in an extended state between the connection pin 70 attached to the sheave plate 18 and the rotating arm 65. Thereby, the arm biasing spring 66 generates an elastic restoring force, and biases the rotating arm 65 in a direction against the centrifugal force received by the centrifugal weight 64 by the generated elastic restoring force. Displacement of the centrifugal weight 64 due to the biasing force of the arm biasing spring 66 is restricted by the centrifugal weight 64 hitting the stopper 71 provided on the sheave plate 18.

  The centrifugal rod 67 penetrates the sheave plate 18 so as to be displaceable. The centrifugal rod 67 is connected to the sheave side contact body 43.

  As shown in FIG. 6, the conversion device 68 includes a taper member 72 fixed to the centrifugal rod 67 and a return spring that biases the taper member 72 in a direction in which the sheave side contact body 43 moves away from the rotary body side contact body 41. Return urging body) 73.

  The taper member 72 is provided with an inclined surface 72a that is inclined with respect to a plane (a plane perpendicular to the shaft pin 69) including a path along which the rotation arm 65 is rotated. In this example, the shape of the taper member 72 is conical. The other end of the rotating arm 65 is in contact with the inclined surface 72a. Thereby, the rotating arm 65 receives the taper member 72 biased by the return spring 73.

  When the rotating arm 65 is rotated while being in contact with the inclined surface 72a in the direction in which the centrifugal weight 64 is displaced radially outward (that is, the direction in which the centrifugal weight 64 is separated from the stopper 71), the taper member 72 is returned. The spring 73 is pushed in a direction against the urging force of the spring 73. Thereby, the centrifugal rod 67 is displaced, and the sheave side contact body 43 is displaced in the direction in which the centrifugal body 67 contacts the rotating body side contact body 41. That is, the centrifugal rod 67 is brought into contact with the rotating body side contact body 41 when the taper member 72 is pushed against the urging force of the return spring 73 by the rotating arm 65 rotated while being in contact with the inclined surface 72a. The sheave sheave contact body 43 is displaced.

  When the centrifugal weight 64 is displaced in a direction approaching the stopper 71, the taper member 72 is displaced while pushing the rotating arm 65 by the urging force of the return spring 72. Thereby, the sheave side contact body 43 is displaced in the direction away from the rotating body side contact body 41.

  The return spring 73 is provided in a contracted state between the sheave plate 18 and the taper member 72. The taper member 72 is biased by the elastic restoring force of the return spring 73.

  A car passage detection sensor (car landing position detection device) that can detect whether or not the car 1 has passed at a position that is a predetermined distance away from each floor in a vertical direction (that is, a predetermined position with respect to each floor). (Not shown) are arranged. Information from each car passage detection sensor. It is sent to the control device 10.

  Next, control of the hoisting machine device 3 by the control device 10 will be described. The control device 10 controls the hoisting machine device 3 based on information from each of the scale device 9, the sheave encoder 51, the rotating body encoder 74, and the car passage detection sensor. A predetermined reference range determined based on the load in the car 1 when the car 1 side and the counterweight 2 side are balanced is set in the control device 10 in advance. In this example, the predetermined reference range is determined based on a load that is ½ of the maximum load weight of the car 1.

  The control device 10 performs control on the electromagnetic clutch device 39 according to the moving direction of the car 1 based on information from the scale device 9. That is, the control device 10 determines the direction of the force applied to the car 1 due to the weight difference between the car 1 side and the counterweight 2 side when the load in the car 1 detected by the scale device 9 deviates from a predetermined reference range. Only when the moving direction of the car 1 is the same, the electromagnetic clutch device 39 is controlled to release the transmission of the rotational force between the rotating body 13 and the driving sheave 15 (control of the opening operation). . The control of the opening operation for the electromagnetic clutch device 39 is control for supplying power to the electromagnetic magnet 61 for the clutch and displacing the rotating body side contact body 41 in a direction away from the sheave side contact body 43.

  Further, the control device 10 determines that the direction of the force applied to the car 1 due to the weight difference between the car 1 side and the counterweight 2 side is the moving direction of the car 1 when the load in the car 1 deviates from a predetermined reference range. When it is in the reverse direction and when the load in the car 1 is within a predetermined range, the control (control of connection operation) that executes the transmission of the rotational force between the rotating body 13 and the driving sheave 15 is electromagnetic. This is performed for the clutch device 39. Control of the connection operation with respect to the electromagnetic clutch device 39 is control for stopping the power supply to the electromagnetic magnet 61 for the clutch and displacing the rotating body side contact body 41 in the direction in which the sheave side contact body 43 is contacted.

  Specifically, when the car 1 descends when the load in the car 1 is large outside the predetermined reference range, and when the load within the car 1 is small outside the predetermined reference range. When the car 1 is raised, the electromagnetic clutch device 39 performs an opening operation under the control of the control device 10.

  Further, when the load in the car 1 is within a predetermined reference range, when the car 1 is lowered when the load in the car 1 is smaller than the predetermined reference range, and when the load in the car 1 is When the car 1 rises when it is larger than the predetermined reference range, the electromagnetic clutch device 39 performs a connection operation under the control of the control device 10.

  Further, the control device 10 controls the motor 30 to move the car 1 at a preset normal operation speed based on information from the rotary body encoder 74. That is, the control device 10 controls the motor 30 so that the speed of the car 1 becomes the normal operation speed regardless of the control for the electromagnetic clutch device 39.

  Furthermore, when the car 1 is to be landed on each floor, the control device 10 controls the motor 30 based on information from the sheave encoder 51 and the car passage detection sensor. That is, the control device 10 obtains the relationship between the position of the car 1 and the moving speed based on the information from each of the sheave encoder 51 and the car passage detection sensor, and based on the obtained relationship between the position and the moving speed. Thus, the landing position of the car 1 is adjusted by controlling the current to the motor 30.

  Next, the operation will be described. FIG. 9 is a configuration diagram showing a state in which the load in the car 1 of FIG. 1 is larger than a predetermined reference range. FIG. 10 is a configuration diagram showing a state where the load in the car 1 of FIG. 1 is smaller than a predetermined reference range. The control device 10 determines whether or not the load in the car 1 is out of a predetermined reference range based on information from the scale device 9.

  When a large number of passengers get in the car 1 and the load in the car 1 is larger than the predetermined reference range (FIG. 9), the control is performed when the descending operation of the car 1 is started. The electromagnetic clutch device 39 is released by the control of the device 10. Accordingly, the car 1 naturally moves downward due to the weight difference between the car 1 side and the counterweight 2 side.

  When the load in the car 1 is reduced outside the predetermined reference range due to the small number of passengers in the car 1 (FIG. 10), when the ascending operation of the car 1 is started, the control device 10 The release operation of the electromagnetic clutch device 39 is performed under the control of. As a result, the car 1 naturally moves upward due to the weight difference between the car 1 side and the counterweight 2 side.

  When the speed of the car 1 is increased after the movement of the car 1 downward or upward is started, the centrifugal weight 64 is displaced according to the centrifugal force generated by the rotation of the driving sheave 15 and the sheave contact body 43 rotates. It is displaced toward the body side contact body 41. If the speed of the car 1 is within the range of the normal operation speed, the electromagnetic clutch device 39 continues the disengagement operation, so that the sheave side contact body 43 does not contact the rotating body side contact body 41.

  When the speed of the car 1 further exceeds the maximum value of the normal operation speed and reaches the first abnormal speed, the operation of the centrifugal clutch device 40 is performed even when the electromagnetic clutch device 39 continues the opening operation. Thus, the sheave side contact body 43 comes into contact with the rotating body side contact body 41. Thereby, the rotational force is transmitted between the rotating body 13 and the driving sheave 15, and the rotational speed of the driving sheave 15 is limited by the rotating body 13. In this way, the speed of the car 1 is prevented from becoming higher than the first abnormal speed. In this example, the value of the first abnormal speed is set to 1.5 times the maximum value of the normal operation speed.

  Thereafter, when the destination floor of the car 1 approaches, the connection operation of the electromagnetic clutch device 39 is performed under the control of the control device 10. Thereafter, the car 30 is landed on the destination floor by controlling the motor 30 based on information from the car passage sensor and the sheave encoder 51.

  When the speed of the car 1 further increases beyond the first abnormal speed for some reason and reaches the second abnormal speed, an emergency stop device (not shown) mounted on the car 1 operates the governor. The braking force is applied directly to the car 1. In this example, the value of the second abnormal speed is set to 1.3 times the value of the first abnormal speed.

  On the other hand, when the load in the car 1 is within the predetermined reference range, when the car 1 is lowered when the load in the car 1 is smaller than the predetermined reference range, and when the load in the car 1 is When the car 1 rises when it is larger than the predetermined reference range, the connection operation of the electromagnetic clutch device 39 is continued under the control of the control device 10. Thereby, the driving sheave 15 is rotated according to the rotation of the rotating body 13. Accordingly, the car 1 is moved at the normal operation speed.

  In such an elevator hoist apparatus, the rotating body 13 is provided with an electromagnetic clutch device 39 capable of transmitting a rotational force between the rotating body 13 and the drive sheave 15 by controlling the power supply to the electromagnetic magnet 61 for the clutch. Since the centrifugal clutch device 40 capable of transmitting the rotational force between the rotating body 13 and the driving sheave 15 by the displacement of the centrifugal weight 64 due to the centrifugal force of the driving sheave 15 is provided in the driving sheave 15, the electromagnetic clutch device 39. By performing the opening operation, the speed of the car 1 can be made higher than the normal operation speed depending on the load in the car 1 and the moving distance of the car 1. Accordingly, it is possible to shorten the time required for the car 1 to move to the destination floor, and to improve the operation efficiency of the elevator. Further, when the speed of the car 1 approaches an abnormally high speed, the centrifugal clutch device 40 is operated by the centrifugal force of the drive sheave 15, so that the rotation of the drive sheave 15 is limited by the rotating body 13, The rotational speed of the drive sheave 15 can be suppressed so as not to exceed the set range. As a result, the speed of the car 1 can be prevented from becoming abnormally high.

  Moreover, the rotary body side contact body 41 is provided in the rotary body 13, the sheave side contact body 43 is provided in the drive sheave 15, and the rotary body side contact body 41 and the sheave side contact body 43 are brought into contact with each other. Since the rotational force is transmitted between the rotating body 13 and the driving sheave 15, the transmission position of the rotational force due to the operation of the electromagnetic clutch device 39 and the transmission position of the rotational force due to the operation of the centrifugal clutch device 40. Can be matched. Further, the clutch shoe that generates the contact friction force can be made common, and the clutch shoe has only to be provided in either the rotating body side contact body 41 or the sheave side contact body 43, so that the number of parts can be reduced. be able to.

  Further, since the planetary gear device 45 is provided between the sheave annular portion 19 of the driving sheave 15 and the sheave-side insertion portion 22 of the rotating body 13, between the rotating body 13 and the driving sheave 15. It is possible to prevent the difference in rotational speed from becoming extremely large.

  The electromagnetic actuator 42 also includes an electromagnetic rod 59 that is displaced integrally with the rotating body side contact body 41, and an urging force that biases the electromagnetic rod 59 in a direction in which the rotating body side contact body 41 contacts the sheave side contact body 43. A spring 60 and a clutch electromagnetic magnet 61 that displaces the electromagnetic rod 59 in a direction in which the rotating body side contact body 41 moves away from the sheave side contact body 43 against the urging force of the urging spring 60 by performing power feeding. Therefore, the rotating body side contact body 41 can be displaced with a simple configuration.

  Further, the centrifugal actuator 44 has a rotating arm 65 that is displaced with respect to the drive sheave 15 in accordance with the displacement of the centrifugal weight 64 due to the centrifugal force of the drive sheave 15 and a direction that opposes the centrifugal force of the drive sheave 15. An arm biasing spring 66 for biasing the pivoting arm 65, a centrifugal rod 67 displaced integrally with the sheave-side contact body 43, and a conversion for converting the pivoting of the pivoting arm 65 into a displacement of the centrifugal rod 67. Since the device 68 is included, it is possible to execute and block the transmission of the rotational force between the rotating body 13 and the drive sheave 15 according to the rotational speed of the drive sheave 15 without performing electrical control. it can.

  The conversion device 68 has a taper member 72 provided with an inclined surface 72a, and the rotating rod 65 is rotated while being in contact with the inclined surface 72a, whereby the centrifugal rod 67 is displaced. Therefore, the rotation of the rotation arm 65 can be converted into the displacement of the centrifugal rod 67 with a simple configuration.

  Further, in such an elevator apparatus, the direction of the force applied to the car 1 by the control device 10 when the load in the car 1 deviates from a predetermined reference range and the weight difference between the car 1 side and the counterweight 2 side. Only when the moving direction of the car 1 is the same, the electromagnetic clutch device 39 is controlled to cancel the transmission of the rotational force between the rotating body 13 and the driving sheave 15. When the opening operation is performed, the car 1 can be accelerated more reliably. Further, depending on the load in the car 1 and the moving distance of the car 1, the speed of the car 1 can be made higher than the normal operation speed. Accordingly, it is possible to shorten the time required for the car 1 to move to the destination floor, and to improve the operation efficiency of the elevator.

  Moreover, since the control apparatus 10 controls the hoisting machine apparatus 3 based on the information from the sheave encoder 51, when the connection operation of the electromagnetic clutch apparatus 39 is continued, the speed of the car 1 is normally operated. Control to follow the speed can be performed more reliably.

  A car passage detection sensor capable of detecting whether or not the car 1 has passed is disposed at a predetermined position with respect to each floor in the hoistway, and the control device 10 includes a sheave encoder 51 and a car passage detection sensor. Since the landing position of the car 1 is adjusted based on the information from the car 1, the landing of the car 1 is performed even when the opening operation of the electromagnetic clutch device 39 is performed and the speed of the car 1 is high. The position can be detected more accurately, and the impact on the car 1 at the time of landing can be suppressed.

  In the above example, the clutch shoe 57 is provided on the rotating body side contact body 41. However, the rotating body side contact body 41 may be the clutch disk 56 only, and the sheave side contact body 43 may be provided with a clutch shoe.

  In the above example, the electromagnetic clutch device 39 and the centrifugal clutch device 40 are disposed at the same position in the radial direction of the hoisting machine device 3. The position of the device 40 in the radial direction may be different from each other. For example, the position of the electromagnetic clutch device 39 may be radially outside the position of the centrifugal clutch device 40. In this case, the rotating body side contact body 41 can come into contact with the sheave plate 18, and the sheave side contact body 43 can come into contact with the first rotating body side wall portion 27.

Embodiment 2. FIG.
FIG. 11 is a longitudinal sectional view showing an elevator hoist apparatus 3 according to Embodiment 2 of the present invention. FIG. 12 is an enlarged view showing the XII portion of FIG. Further, FIG. 13 is a partially broken perspective view showing the electromagnetic clutch device, centrifugal clutch device and roller of FIG. In the drawing, a plurality of metal rollers (for example, iron or the like) 81 are disposed between the inner peripheral surface of the sheave annular portion 19 and the outer peripheral surface of the first rotating body annular portion 26. Each roller 81 is in contact with the inner peripheral surface of the sheave annular portion 19 and the outer peripheral surface of the first rotary body annular portion 26 by the relative rotation of the rotating body 13 and the drive sheave 15. It can roll in the circumferential direction between the sheave annular portion 19 and the first rotating body annular portion 26. Each roller 81 has a cylindrical shape. Other configurations are the same as those in the first embodiment.

  Even in such an elevator hoist apparatus, similarly to the planetary gear apparatus 45 of the first embodiment, the difference in rotational speed between the rotating body 13 and the drive sheave 15 is prevented from becoming extremely large. be able to. In addition, since the configuration can be simplified, the cost can be reduced.

Embodiment 3 FIG.
FIG. 14 is a longitudinal sectional view showing an elevator hoist apparatus 3 according to Embodiment 3 of the present invention. FIG. 15 is an enlarged view showing the XV-XV portion of FIG. Further, FIG. 16 is a partially broken perspective view showing the electromagnetic clutch device and the centrifugal clutch device of FIG. In the figure, a space exists between the inner peripheral surface of the sheave annular portion 19 and the outer peripheral surface of the first rotating body annular portion 26. That is, contact between the sheave ring portion 19 and the first rotating body ring portion 26 is avoided. Other configurations are the same as those in the first embodiment.

  Even in such an elevator hoist apparatus, the operation efficiency of the elevator can be improved by the control of the electromagnetic clutch device 39. Further, the operation of the centrifugal clutch device 40 can prevent the speed of the car 1 from becoming abnormally high. Furthermore, since the member interposed between the sheave annular portion 19 and the first rotating body annular portion 26 can be eliminated, the number of parts can be reduced. Moreover, since the resistance between the rotating body 13 and the driving sheave 15 can be reduced, the car 1 can be easily moved to the nearest floor even when an elevator failure occurs.

Embodiment 4 FIG.
FIG. 17 is a perspective view showing an elevator hoist apparatus according to Embodiment 4 of the present invention. In the figure, the hoisting machine device 3 is mounted on a pair of machine tables 85 provided at the upper part of the hoistway via a plurality of vibration control devices 86. Each vibration damping device 86 has a vibration proof rubber.

  The drive sheave 15 and the rotating body 13 are rotated around a common main shaft 12. The axis of the main shaft 12 is orthogonal to the vertical plane including the axis of the output shaft of the motor 30. A speed reducer 87 is provided between the motor 30 and the rotating body 13 to reduce the output from the motor 30 and transmit it to the rotating body 13. A brake device 33 that brakes the rotation of the output shaft of the motor 30 is provided between the speed reducer 87 and the motor 30. The rotating body 13, the drive sheave 15, the motor 30, the brake device 33, and the speed reducer 87 are mounted on a support base 88 fixed on each vibration damping device 86.

  The brake device 33 is provided with a brake drum 89 that is rotated integrally with the output shaft of the motor 30 and a brake shoe (not shown). The arm 90 and a brake actuating device 91 that displaces the brake arm 90 in a direction in which the brake shoe is brought into contact with and separated from each other are provided.

  The brake arm 90 is displaced in a direction in which the brake shoe contacts and separates from the brake drum 89 by rotating with respect to the support base 88. The brake actuator 91 includes a brake spring (not shown) that biases the brake arm 90 in a direction in which the brake shoe contacts the brake drum 89, and the brake shoe moves away from the brake drum 89 against the biasing force of the brake spring. It has an electromagnetic magnet (not shown) that displaces the brake arm 90 in the direction. The rotation of the output shaft of the motor 30 is braked when the brake shoe contacts the brake drum 89.

  FIG. 18 is a longitudinal sectional view showing the hoisting machine device 3 of FIG. Moreover, FIG. 19 is a principal part enlarged view which shows the winding machine apparatus 3 of FIG. Furthermore, FIG. 20 is a partially broken perspective view showing the hoisting machine apparatus 3 of FIG. In the figure, the speed reducer 87 is disposed in the gear case 92, the gear case 92, the worm shaft 93 that is rotated coaxially with the output shaft of the motor 30, the gear case 92, and the worm shaft 93. And a meshing worm wheel 94. The worm shaft 93 is rotated together with the output shaft of the motor 30. The worm wheel 94 is rotatable about the main shaft 12. The worm wheel 94 is rotated at a lower speed than the rotation of the worm shaft 93 by the rotation of the worm shaft 93. Lubricating oil is stored in the gear case 92. That is, the speed reducer 87 is a worm gear type speed reducer.

  The main shaft 12 is fixed horizontally to the support base 88. The rotating body 13 is rotatably attached to the main shaft 12 via a bearing 95. The worm wheel 94 is fixed to the rotating body 13 with bolts 96. Thereby, the rotating body 13 is rotated integrally with the worm wheel 94. A gap is interposed between the worm wheel 94 and the main shaft 12.

  The rotator 13 includes a rotator body 97 fitted with a bearing 95, an annular (tubular) rotator annular part 98 centered on the axis of the main shaft 12, and the rotator annular part 98 and the rotator body 97. It has the 1st rotary body side wall part 99 and the 2nd rotary body side wall part 100 which connect between each. The rotating body trunk portion 97, the rotating body annular portion 98, and the first rotating body side wall portion 99 are manufactured by integral molding. The second rotating body side wall portion 100 is a separate member from the rotating body body portion 97, the rotating body annular portion 98, and the first rotating body side wall portion 99, and is attached to and detached from the rotating body body portion 97 and the rotating body annular portion 98. It is possible. The first rotator side wall 99 and the second rotator side wall 100 are arranged at an interval in the axial direction of the main shaft 12.

  The rotating body 13 is disposed inside the drive sheave 15. A planetary gear device 45 is provided between the rotating body 13 and the drive sheave 15. The drive sheave 15 is supported by the rotating body 13 via the planetary gear unit 45.

  As shown in FIG. 19, the driving sheave 15 is fixed to an annular (tubular) sheave annular portion 101 that surrounds the rotating body 13 via a planetary gear device 45 and one side of the sheave annular portion 101. A sheave plate 102 facing the planetary gear device 45 and the rotating body 13, and a sheave cover 103 fixed to the other side of the sheave annular portion 101 and facing the planetary gear device 45. .

  The sheave annular portion 101, the sheave plate 102, and the sheave cover 103 are separate members. The sheave plate 102 and the sheave cover 103 are fixed to the sheave annular portion 101 by bolts 104. Each main rope 6 is wound around the sheave annular portion 101.

  Between the main shaft 12 and the sheave plate 102, a sheave encoder 51 that generates a signal corresponding to the rotation of the drive sheave 15 is provided.

  Here, FIG. 21 is a partially broken front view showing the hoisting machine device 3 when viewed along the axis of the main shaft 12 of FIG. The shape of the sheave encoder 51 is an annular body that surrounds the main shaft 12 along the circumferential direction of the main shaft 12. The sheave encoder 51 includes an annular rotating portion 51 a fixed to the sheave plate 102, and an annular main body 51 b that is disposed inside the rotating portion 51 a and attached to the main shaft 12 via an attachment metal 105. Have. The rotating part 51a is rotated with respect to the main body part 51b by the rotation of the driving sheave 15.

  The electromagnetic clutch device 39 is provided on the second rotating body side wall 100, and the centrifugal clutch device 40 is provided on the sheave plate 102 (FIG. 19). The rotating body side contact body 41 and the sheave side contact body 43 are disposed between the second rotating body side wall portion 100 and the sheave plate 102. The electromagnetic actuator 42 is disposed between the first rotating body side wall 99 and the second rotating body side wall 100.

  The sheave plate 102 is provided with a recess 106 formed by bending the sheave plate 102. The recess 106 is provided in a portion of the sheave plate 102 opposite to the rotating body 13 side. The centrifugal actuator 44 is disposed in the recess 106. The recess 106 is covered with a centrifugal clutch cover 63.

  The planetary gear unit 45 includes a sheave side rack gear 46 provided on the inner peripheral surface of the sheave annular portion 101, a rotary body side rack gear 47 provided on the outer peripheral surface of the rotary body annular portion 98, a sheave side rack gear 46, and A plurality of planetary gears 48 are disposed between the rotating body side rack gears 47 and mesh with the sheave side rack gears 46 and the rotating body side rack gears 47, respectively.

  The sheave-side rack gear 46 is provided with a sheave-side guide groove 107 that extends along the circumferential direction of the sheave annular portion 101. The depth of the sheave side guide groove 107 is larger than the tooth depth of the sheave side rack gear 46. The sheave side guide groove 107 is provided at the center of the sheave side rack gear 46 in the axial direction of the main shaft 12.

  The rotating body side rack gear 47 is provided with a rotating body side guide groove 108 extending along the circumferential direction of the rotating body annular portion 98. The depth of the rotating body side guide groove 108 is greater than the depth of the teeth of the rotating body side rack gear 47. In this example, the rotating body side guide groove 108 is provided at the center of the rotating body side rack gear 47 in the axial direction of the main shaft 12.

  Each planetary gear 48 is sandwiched between the sheave plate 102 and the sheave cover 103 in the axial direction of the main shaft 12. In addition, on the outer peripheral portion of each planetary gear 48, a protruding portion 109 that is inserted into each of the sheave side guide groove 107 and the rotating body side guide groove 108 is provided. The protrusion 109 surrounds the planetary gear 48 and is provided on the entire circumference of the planetary gear 48. Each planetary gear 48 rotates in a state where the protrusion 109 is inserted into each of the sheave side guide groove 107 and the rotary body side guide groove 108 by the relative rotation of the rotating body 13 and the driving sheave 15. It rotates while meshing with each of the vehicle side rack gear 46 and the rotating body side rack gear 47. Other configurations are the same as those in the first embodiment.

  In such an elevator hoist apparatus, since the output from the motor 30 is decelerated by the speed reducer 87 and transmitted to the rotating body 13, the size of the motor 30 can be prevented from being increased.

  Further, the sheave side rack gear 46 and the rotating body side rack gear 47 are provided with a sheave side guide groove 107 and a rotating body side guide groove 108, and the protrusions 109 inserted into the sheave side guide groove 107 and the rotating body side guide groove 108 are provided respectively. Since it is provided on the outer periphery of the planetary gear 48, it is possible to prevent the planetary gear 48 from being disengaged from each of the sheave side rack gear 46 and the rotating body side rack gear 47.

Embodiment 5 FIG.
FIG. 22 is a perspective view showing an elevator hoist apparatus according to Embodiment 5 of the present invention. FIG. 23 is a longitudinal sectional view of a main part showing the hoist apparatus of FIG. In the figure, a speed reducer 111 that decelerates the output from the motor 30 and transmits it to the rotating body 13 is provided between the motor 30 and the rotating body 13. A brake device 33 that brakes the rotation of the output shaft of the motor 30 is provided between the speed reducer 111 and the motor 30.

  The speed reducer 111 includes a gear case 112 in which the main shaft 12 is rotatably provided, and a plurality of spur gears that are disposed in the gear case 112 and transmit the rotation of the output shaft of the motor 30 to the main shaft 12 at a reduced speed. ing. That is, the speed reducer 111 is a spur gear type speed reducer.

  The main shaft 12 is provided on the gear case 112 via a bearing 113. The axis of the main shaft 12 is parallel to the axis of the output shaft of the motor 30.

  The spur gears of the speed reducer 111 mesh with each other. Of each spur gear, the spur gear 114 at the final stage is fixed to the main shaft 12. The rotating body 13 is also fixed to the main shaft 12. Therefore, the main shaft 12, the rotating body 13, and the spur gear 114 at the final stage are rotated together. The rotational force of the output shaft of the motor 30 is sequentially transmitted through the spur gears and the main shaft 12 and reaches the rotating body 13. Thereby, the rotating body 13 is rotated.

  A through hole 115 is provided in the main shaft 12 along the axis of the main shaft 12. A square pipe 52 is passed through the through hole 115. One end of the square pipe 52 is fixed to the gear case 112.

  Between the square pipe 52 and the sheave plate 102, there is provided a sheave encoder 51 that generates a signal corresponding to the rotation of the drive sheave 15.

  24 is a partially broken perspective view showing the sheave encoder 51 of FIG. FIG. 25 is a partially broken front view showing the hoisting machine device 3 when viewed along the axis of the main shaft 12 of FIG. In the figure, the shape of the sheave encoder 51 is an annular body surrounding the main shaft 12 along the circumferential direction of the main shaft 12. The sheave encoder 51 includes an annular rotating portion 51 a fixed to the sheave plate 102, and an annular main body 51 b that is disposed inside the rotating portion 51 a and attached to the main shaft 12 via an attachment metal 105. Have. The rotating part 51a is rotated with respect to the main body part 51b by the rotation of the driving sheave 15. The signal line 53 from the sheave encoder 51 is passed through the square pipe 52. Other configurations are the same as those of the fourth embodiment.

  Even in such an elevator hoist apparatus, since the output from the motor 30 is decelerated by the speed reducer 111 and transmitted to the rotating body 13, it is possible to prevent the motor 30 from becoming large.

BRIEF DESCRIPTION OF THE DRAWINGS It is a block diagram which shows the elevator apparatus by Embodiment 1 of this invention. It is a longitudinal cross-sectional view which shows the winding machine apparatus of FIG. FIG. 3 is a cross-sectional view taken along line III-III in FIG. 2. FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. 2. It is a partially broken perspective view which shows the sheave shaft of FIG. It is an enlarged view which shows the VI section of FIG. It is a partially broken perspective view which shows the electromagnetic clutch apparatus, centrifugal clutch apparatus, and planetary gear apparatus of FIG. It is a partially broken front view which shows the centrifugal clutch apparatus of FIG. It is a block diagram which shows the state in which the load in the cage | basket | car of FIG. 1 has become large out of the predetermined reference | standard range. It is a block diagram which shows the state in which the load in the cage | basket | car of FIG. 1 has become small out of the predetermined reference range. It is a longitudinal cross-sectional view which shows the elevator hoist apparatus by Embodiment 2 of this invention. It is an enlarged view which shows the XII part of FIG. It is a partially broken perspective view which shows the electromagnetic clutch apparatus of FIG. 12, a centrifugal clutch apparatus, and a roller. It is a longitudinal cross-sectional view which shows the elevator hoist apparatus by Embodiment 3 of this invention. It is an enlarged view which shows the XV-XV part of FIG. It is a partially broken perspective view which shows the electromagnetic clutch apparatus and centrifugal clutch apparatus of FIG. It is a perspective view which shows the elevator hoist apparatus by Embodiment 4 of this invention. It is a longitudinal cross-sectional view which shows the winding machine apparatus of FIG. It is a principal part enlarged view which shows the winding machine apparatus of FIG. It is a partially broken perspective view which shows the winding machine apparatus of FIG. It is a partially broken front view which shows the winding machine apparatus when it sees along the axis line of the main axis | shaft of FIG. It is a perspective view which shows the elevator hoist apparatus by Embodiment 5 of this invention. It is a principal part longitudinal cross-sectional view which shows the winding machine apparatus of FIG. It is a partially broken perspective view which shows the encoder for sheaves of FIG. It is a partially broken front view which shows the winding machine apparatus when it sees along the axis line of the main axis | shaft of FIG.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Car, 2 Counterweight, 3 Hoisting machine device, 6 Main rope, 9 Weighing device (Cage load detection device), 10 Control device, 13 Rotating body, 15 Drive sheave, 19 Sheave annular part, 22 Sheave Side insertion part (insertion part), 39 Electromagnetic clutch device, 40 Centrifugal clutch device, 41 Rotating body side contact body, 42 Electromagnetic operation device, 43 Sheave side contact body, 44 Centrifugal operation device, 45 Planetary gear device, 46 Sheave side Rack gear, 47 rotating body side rack gear, 48 planetary gear, 51 sheave encoder (speed detector), 59 electromagnetic rod, 60 biasing spring (biasing body), 61 clutch electromagnetic magnet (electromagnetic magnet), 64 centrifugal weight, 65 Rotating arm, 66 Arm urging spring (arm urging body), 67 Centrifugal rod, 68 Conversion device (conversion means), 72 Taper member, 72a Inclined surface, 87 111 speed reducer.

Claims (12)

motor,
A rotating body rotated by the driving force of the motor;
A main rope for suspending a car and a counterweight is wound, and a driving sheave that can rotate independently of the rotating body,
An electromagnetic clutch device having an electromagnetic actuator including an electromagnetic magnet and capable of transmitting a rotational force between the rotating body and the driving sheave by controlling power feeding to the electromagnetic magnet, and a centrifugal force due to the rotation of the driving sheave A centrifugal operation device including a centrifugal weight that is displaced with respect to the drive sheave according to the displacement, and the rotational force can be transmitted between the rotating body and the drive sheave by the displacement of the centrifugal weight due to the centrifugal force. An elevator hoist apparatus comprising a centrifugal clutch device. The electromagnetic clutch device further includes a rotating body side contact body provided on the rotating body,
The centrifugal clutch device further includes a sheave side contact body provided on the drive sheave,
The rotating body side contact body is displaced in a direction in contact with the sheave side contact body by controlling power feeding to the electromagnetic magnet, and the sheave side contact body is displaced by the centrifugal weight due to the centrifugal force, It is designed to be displaced in the direction of contact with the rotating body side contact body,
The elevator hoisting machine according to claim 1, wherein a rotational force is transmitted between the rotating body and the driving sheave when the rotating body side contact body and the sheave side contact body come into contact with each other. apparatus.   The elevator hoist apparatus according to claim 1 or 2, further comprising a speed reducer that decelerates an output from the motor and transmits the output to the rotating body. The drive sheave has a sheave annular portion,
The rotating body has an insertion portion arranged inside the sheave annular portion and coaxial with the sheave annular portion,
The sheave-side rack gear provided on the inner peripheral surface of the sheave annular portion, the rotor-side rack gear provided on the outer peripheral surface of the insertion portion, and disposed between the sheave-side rack gear and the rotor-side rack gear, The elevator hoisting device according to any one of claims 1 to 3, further comprising: a planetary gear device having a sheave-side rack gear and a plurality of planetary gears that mesh with each of the sheave-side rack gear. Machine equipment. Each of the sheave side rack gear and the rotating body side rack gear is provided with a guide groove extending along the circumferential direction of the sheave annular portion and the insertion portion,
The outer periphery of the planetary gear is provided with a protrusion that is inserted into the guide groove provided in each of the sheave side rack gear and the rotating body side rack gear. Elevator hoisting machine equipment. The drive sheave has a sheave annular portion,
The rotating body has an insertion portion arranged inside the sheave annular portion and coaxial with the sheave annular portion,
A roller that can roll between the sheave annular portion and the insertion portion while being in contact with the inner peripheral surface of the sheave annular portion and the outer peripheral surface of the insertion portion is further provided. The elevator hoist apparatus according to any one of claims 1 to 3. The electromagnetic actuator includes an electromagnetic rod that is displaced integrally with the rotating body side contact body, and an urging body that biases the electromagnetic rod in a direction in which the rotating body side contact body contacts the sheave side contact body. In addition,
The electromagnetic rod is displaced in a direction in which the rotating body side contact body is separated from the sheave side contact body against the biasing force of the biasing body by performing power feeding to the electromagnetic magnet. The elevator hoist apparatus according to any one of claims 2 to 6. The centrifugal actuator is
A rotating arm that is rotated with respect to the driving sheave according to the displacement of the centrifugal weight due to the centrifugal force of the driving sheave;
An arm biasing body that biases the rotating arm in a direction against the centrifugal force of the driving sheave;
A centrifugal rod displaced integrally with the sheave side contact body,
The elevator hoist apparatus according to any one of claims 2 to 6, further comprising conversion means for converting rotation of the rotation arm into displacement of the centrifugal rod. The converting means is provided with an inclined surface with which the rotating arm comes into contact, and has a taper member provided on the centrifugal rod,
The centrifugal rod is displaced in a direction in which the sheave-side contact body comes into contact with the rotating body-side contact body when the taper member is pushed by the turning arm that is rotated while being in contact with the inclined surface. The elevator hoist apparatus according to claim 8. The rotating body includes a motor, a rotating body that is rotated by the driving force of the motor, a driving sheave that can rotate independently of the rotating body, and an electromagnetic magnet. The rotating body is controlled by controlling power feeding to the electromagnetic magnet. And an electromagnetic clutch device capable of transmitting rotational force between the driving sheaves, and a centrifugal weight that is displaced with respect to the driving sheave according to the centrifugal force caused by the rotation of the driving sheave, A hoisting device having a centrifugal clutch device capable of transmitting a rotational force between the rotating body and the driving sheave by displacement of
A car and a counterweight suspended by a main rope wound around the driving sheave,
A car load detecting device for detecting a load in the car, and a control device for controlling the electromagnetic clutch device according to the moving direction of the car based on information from the car load detecting device;
In the control device, the load in the car is out of a predetermined reference range, and the direction of the force applied to the car due to the weight difference between the car side and the counterweight side is the same as the moving direction of the car. The elevator apparatus according to claim 1, wherein control for canceling transmission of rotational force between the rotating body and the driving sheave is performed on the electromagnetic clutch device only when the electromagnetic clutch apparatus is engaged. A speed detecting device for generating a signal corresponding to the rotation of the driving sheave;
The elevator apparatus according to claim 10, wherein the control apparatus controls the hoisting machine apparatus based on information from the speed detection apparatus. A car floor position detecting device that is arranged at a predetermined position with respect to a plurality of floors where the car can be stopped, and can detect whether or not the car has passed;
The control device adjusts the landing position of the car by controlling a current to the motor based on information from each of the speed detection device and the car landing position detection device. The elevator apparatus according to claim 11.

Images