JP2013040033A - Hoisting machine for elevator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve the following problems of an elevator hoisting machine: a large gap is formed between a disk and a brake lining in consideration of displacement of the disk due to bending of a fixed main shaft between a no-load state and a maximum movable load state, thereby enlarging the disk brake device in the axial direction, accordingly, and increasing axial length of the hoisting machine.SOLUTION: The disk brake is disposed in an area where the position of the rotating surface of the disk inclined in the maximum movable load state and the position of the rotating surface of the disk in the no-load state are hardly changed, thereby minimizing the clearance which has been needed between the disk and the brake lining to prevent the axial length of the hoisting machine from being increased.

Description

  The present invention relates to an elevator hoisting machine for raising and lowering a car of an elevator system up and down, and more particularly to a thin elevator hoisting machine in which the axial length of the hoisting machine is shortened.

  In recent elevator systems, in order to reduce the height of the building, a machine room for storing machinery such as a hoisting machine is not provided in the upper part of the hoistway, and so-called machine room-less machines are provided in the hoistway. Elevator systems are widespread.

  In the case of this machine room-less elevator system, all devices including the hoisting machine conventionally installed in the machine room are installed in the hoistway.

There are various configurations for installing the hoisting machine in the hoistway, but in order to install the hoisting machine in a relatively narrow gap between the carriage and the hoistway wall, it is installed so as to face the hoistway wall. A hoisting machine is required.
And, in many cases, a counterweight is arranged on the side hoistway of such a thin hoisting machine, and the hoisting machine is surrounded by the hoistway wall, the carriage and the counterweight in all directions. Will be installed.

  Therefore, if the hoisting machine can be reduced in size, the cross section of the hoistway can be reduced, and the degree of freedom of layout of equipment installed in the hoistway can be increased.

  For this reason, downsizing of the hoisting machine used in the machine room-less elevator system, particularly reduction of the axial length of the entire hoisting machine, that is, reduction in thickness, is an important technical issue.

  As a conventional thin hoisting machine, for example, as described in Patent Document 1 to Patent Document 3, a stator is formed integrally with the housing on the outer peripheral portion of the fixed main shaft fixedly supported by the housing, In addition, it is known that a rotor is integrally formed on an outer peripheral portion of a sheave rotatably attached to one end of a fixed main shaft via a bearing, and an electric motor portion is configured by the rotor and the stator that are arranged to face each other. It has been.

  When operating the elevator system, when the sheave is driven to rotate by the motor section, the car is moved up and down through the main rope wound around the sheave. In addition, it is known that a disc provided integrally with a sheave by a disc brake device is sandwiched from both sides by a brake lining for braking.

JP 2004-137037 A JP 2004-299824 A WO / 2006-129338

In a conventional thin elevator hoisting machine, a suspension load is applied to a sheave and a fixed main shaft that rotatably supports the sheave via a main rope via a main rope, and the suspension load acts as a result of the suspension load. A bending displacement occurs in the fixed main shaft through the vehicle.
In other words, the fixed main shaft of the hoisting machine is fixedly supported by the casing, so that it has a cantilever structure with the fixed main shaft as a beam starting from this shaft supporting portion.

Therefore, when the suspension load is applied to the sheave, the fixed main shaft is displaced by bending in the direction in which the suspension load is applied. When bending occurs in the fixed main shaft, the displacement of the bending is transmitted to the sheave that is rotatably supported by the fixed main shaft, and as a result, is also transmitted to the disk provided in the sheave. Here, the displacement of the disk increases in the radial direction around the axis of the sheave (= the axis of the fixed main shaft).
Note that the suspension load applied to the sheave of the hoisting machine is (1) no load before installing the hoisting machine, and (2) the user is on the car after installing the hoisting machine. Since it fluctuates between the case of a light load that is not present and (3) the case of a heavy load that the user is riding on until the maximum load load is reached, the bending displacement of the fixed main spindle also occurs accordingly. That is, a displacement occurs between a state where there is no displacement due to bending or a slight displacement and a state where the maximum load is applied.

  In the hoist described in Patent Document 1 and Patent Document 2, the disc brake device is provided at the top of the sheave in the direction where the suspension load is applied (near the outermost periphery in the direction of bending of the fixed main shaft). The disc displacement caused by the bending of the fixed main shaft is greatly amplified.

For this reason, in the general thin hoisting machines described in Patent Document 1 and Patent Document 2, a displacement due to bending between a no-load (or light load) state and a state in which the maximum load load acts is taken into consideration. The brake stroke is increased so that there is sufficient clearance between the disc and brake lining when the brake is released.
Therefore, the disk disc brake device is enlarged in the axial direction of the hoisting machine at least by the brake stroke, and as a result, the axial length dimension of the hoisting machine is increased.

Further, in Patent Document 3, in order to suppress the displacement of the fixed main shaft and the disk due to the suspension load, both ends of the fixed main shaft in the axial direction are supported by the casings, and the sheave can be rotated at the intermediate portion of the fixed main shaft between the two support portions. A supported configuration is shown.
However, even if the displacement of the fixed main shaft and the disk due to the suspension load can be suppressed by this configuration, both ends of the fixed main shaft are supported by the support portions, so that the axial dimension of the fixed main shaft increases only by this support portion. There are challenges.

  An object of the present invention is to provide a thin elevator hoisting machine having a disc brake device that can suppress the axial length of the hoisting machine as much as possible.

  A feature of the present invention is that a fixed main shaft having one end as a free end is provided in a housing main body that houses a stator and a stator winding, and a sheave is rotatably attached to the free end side of the fixed main shaft and is attached to the sheave. In an elevator hoisting machine equipped with a disc brake device that forms a disc and sandwiches the disc from both sides to apply braking, outside the main rope wound around the sheave and under the maximum load Elevator equipped with a disc brake device that brakes the disc in a region where the distance between the position of the rotating surface of the disc tilted at the position of the disc and the position of the rotating surface of the disc under no load or light load is within a predetermined range For hoisting machines.

  By adopting such a configuration, the position of the rotating surface of the disc tilted in a state where the maximum load is applied is almost the same as the position of the rotating surface of the disc in a no-load (or light load) state. Since the disc brake device is arranged in an area that is acceptable even if it changes, the length of the gap required between the brake lining and the disc can be reduced, and the shaft of the disc brake device can be reduced accordingly. The length can be suppressed.

It is sectional drawing which shows the general structure of a machine room less elevator system. It is sectional drawing at the time of arrange | positioning a passenger car, a counterweight, and the elevator hoist to a hoistway. It is sectional drawing which shows the structure of the thin hoisting machine which this invention makes object. It is the front view which looked at the winding machine shown in FIG. 2 from the other side of the passenger car. The disc brake device is omitted. It is a side view of the hoisting machine of a no load state in order to explain the influence by bending. It is a side view of a hoisting machine when a maximum load load acts and bending displacement arises in order to explain the influence by bending. It is a front view of the winding machine which is one Example of this invention. It is sectional drawing of the disc brake apparatus shown in FIG.

Hereinafter, an elevator hoist according to an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a cross-sectional view for explaining a general configuration of a machine room-less elevator. Reference numeral 10 is a hoistway provided in a building, in which the elevator is accommodated.

  The elevator has a car 11, a counterweight 12 and a hoisting machine 13 as main components. A pulley 14 is attached to the lower part of the car 11, and a pulley 15 is attached to the counterweight 12. A sheave 16 is attached to 13 rotation shafts (= rotation shaft of an electric motor).

  Here, although the hoisting machine 13 is mounted on the floor surface at the bottom of the hoistway 10, the hoisting machine 13 may be attached to a beam fixed near the top of the hoistway 10.

  A beam 17 is fixed to the upper part of the hoistway 10, and intermediate pulleys 18A and 18B are attached to the beam 17, so that the winding direction of the main rope 19 is changed. One end of the main rope 19 is attached to the upper wall surface of the hoistway 10, and starting from this end, the pulley 15 of the counterweight 12, the first intermediate pulley 18A, the sheave 16 of the hoisting machine 13, and the second intermediate The other end is attached to the upper wall surface of the hoistway 19 through the pulley 18B and the pulley 14 of the car 11. This roping is called 2-to-1 roping, and the hoisting force of the hoisting machine 13 is reduced using the principle of a moving pulley.

  A shock absorber 191 is provided at the lower portion of the counterweight 12 to buffer the impact caused by the collision of the counterweight 12. It is what has been.

  In such an elevator, an operation command is given to an electric motor, a braking mechanism, and the like of the hoisting machine 16 by a controller (not shown), and the car 11 moves up and down toward a predetermined level of the building by the operation command. It is.

  FIG. 2 is a sectional view of the hoistway 10 in which an elevator using a thin elevator hoisting machine targeted by the present invention is arranged.

  In the hoistway 10, a car 11 and a counterweight 12 connected by a main rope 19 (not shown) are arranged so as to be able to be raised and lowered.

  A thin hoisting machine 13 is installed in a gap between the hoistway 10 and the car 11, and the thin hoisting machine 13 includes a housing assembly 20 that houses a stator that constitutes an electric motor unit, A rotor arranged opposite to the stator and constituting an electric motor part, and a sheave assembly 21 integrally formed with the rotor and a sheave 16 around which the main rope 19 is wound. The sheave 6 is rotated together with the rotor, and the car 11 is moved up and down via the main rope 19.

  Since the inspection work of the thin hoisting machine 13 is normally performed from the car 11 side, the casing assembly 20 of the hoisting machine 13 is arranged toward the car 11 side.

  Next, a specific configuration of the thin hoisting machine 13 will be described with reference to FIG. The housing body 22 of the housing assembly 20 has a boss portion 23 formed at the center thereof, and one end of a fixed main shaft 24 is inserted into the boss portion 23 and fixed. Further, the sheave assembly 21 is rotatably supported on the free end side of the fixed main shaft 24 to constitute a motor having a cantilever support structure.

  In addition, in the annular storage recess 25 located on the outer peripheral side of the boss portion 23 of the housing body 22, electrical parts such as a stator 26 and a stator winding 27 constituting the electric motor portion are stored.

  Further, a sheave housing 29 is rotatably supported on the free end side of the fixed main shaft 11 via a bearing 28. The sheave housing 29 is supported by a sheave 30 (corresponding to the sheave 16 in FIG. 1) and an electric motor unit. Are integrally formed with an electric part such as the rotor 31 or the like.

  Here, the casing main body 22 is manufactured by casting a cast iron or the like to form an approximate shape and then machining a portion requiring dimensional accuracy.

  As described above, the housing main body 22 is integrally formed with the hollow boss portion 23 at the center thereof, and the stator 26, the stator winding 27, and the like can be accommodated inside the outer periphery thereof. It is cast and manufactured so as to form a bottomed annular storage recess 25 that can be formed.

  A rotor 31 is disposed opposite to the stator 27 with a predetermined gap using the storage recess 25, and a plurality of permanent magnets 32 are fixed to the inner peripheral surface of the rotor 31. . Therefore, the rotor of a surface magnet type motor is constituted by this. In this case, the rotor 31 needs to be a magnetic body, and is integrally formed of the magnetic body together with the sheave housing 29 and the sheave 30.

  Here, a disk 33 is integrally formed on the outer periphery of the rotor 31, and the brake disk 33 is formed as an annular disk projecting radially on the outer peripheral side of the rotor 31.

  The sheave housing 29, the sheave 30 and the rotor 31 are not integrally formed, but are manufactured by separate parts that can be divided separately, and then fixed by fitting such as bolts or shrink fitting. Is also good.

  As described above, the permanent magnet 32 arranged inside the rotor 31 has N poles and S poles alternately arranged in the circumferential direction, and the number of N poles and S poles is the same and the number is the number of poles. It is half.

  Such a rotor 31 is disposed so as to face the outer side of the stator 27 disposed in the housing recess 25 integrally formed with the housing main body 22 in the radial direction with a minute air gap interposed therebetween. An outer rotor type electric motor is configured.

  And the rotational force which generate | occur | produced in this electric motor part is transmitted to the sheave 30 via the rotor 31, and drives the main rope 19 wound around the sheave 30, and raises / lowers the passenger car 11 up and down. It will be. Although details of the disc brake device are not shown in FIG. 3, when the car is moved up and down, the brake lining is released from the disc by a signal from a control device (not shown) to release the braking operation. Is stopped and the position is maintained, the brake lining is pressed against the disc by a signal from the control device to apply a braking force to the disc to perform a braking operation.

  4 to 6 are diagrams for explaining the phenomenon of bending displacement of the fixed main shaft 24 due to the suspension load, and FIG. 4 is a front view of the hoisting machine 13 in FIG. 2 viewed from the opposite side of the car 11. 5 is a side view of the hoisting machine 13 when the suspension load is not applied to the sheave 30, and FIG. 6 is a side view of the hoisting machine 13 when the suspension load is applied to the sheave 30. In this case, the disc brake device is omitted.

  As described with reference to FIG. 3, when the sheave assembly 21 is rotatably attached to the housing assembly 20, one end of the fixed main shaft 24 that supports the sheave 30 is connected to the boss portion 23 of the housing body 22. It is fixed and has a cantilever structure that rotatably supports the sheave 30 at the other axial end (= free end).

  As described above, the suspension load applied to the sheave of the hoisting machine is determined by the user in (1) no load before installing the hoisting machine and (2) the car after installing the hoisting machine. Since it fluctuates between the case where it is not boarded and (3) the case where the user is on board until the maximum loading load is reached, the bending displacement of the fixed main spindle also occurs accordingly.

  FIG. 5 shows the case of no load (or light load) before installing the hoisting machine. In this case, no suspended load is applied, or even if it is applied, the fixed main shaft 24 is light. No bending displacement occurs, and naturally the sheave 30, the rotor 31, and the disk 33 are not affected by the bending of the fixed main shaft 24.

  On the other hand, when the user is on board until the maximum load is reached after installing the hoist, when an upward suspension load is applied to the sheave 30 via the main rope 19 as shown in FIG. The sheave 30 is applied with a force that rotates counterclockwise as indicated by an arrow P in FIG.

  For this reason, bending occurs on the free end side of the fixed main shaft 24. As a result, the sheave 30, the rotor 31 and the disc 33 supported on the free end side of the fixed main shaft 24 are aligned along the center line 34 shown in FIG. Will tilt. As a result, the rotating surface of the disk 33 also tilts from the rotating surface 35 under no load as shown in FIG. 6 under the influence of bending.

  Therefore, in the hoist described in Patent Document 1 and Patent Document 2, the disc brake device is provided at the top of the sheave in the direction where the suspension load is applied (near the outermost periphery in the direction of bending of the fixed main shaft 24). Therefore, the displacement of the disk 33 due to the bending of the fixed main shaft 24 is greatly amplified.

  In the case where the gap length between the disk 33 and the brake lining is adjusted when there is no load, the disk 33 and the brake lining come into contact with each other due to the inclination of the disk 33 caused by the bending that occurs on the free end side of the fixed main shaft 24 and slide. If this continues for a long time, the brake lining may be worn out and a normal braking operation may not be obtained.

  Conventionally, as a countermeasure, the length of the gap between the disc 33 and the brake lining is increased so that the brake lining does not contact the disc 33 even if the disc 33 is inclined.

  Therefore, the disc brake device is enlarged in the axial direction of the hoisting machine by at least the gap between the long disc 33 and the brake lining, and as a result, the axial length dimension of the hoisting machine is increased. .

  In addition, if the gap between the disc 33 and the brake lining becomes long, there is a concern that a loud noise may be generated when the brake lining collides with the disc 33 during a braking operation.

In order to solve such a problem, the present invention makes the following proposal.
That is, in the cantilever structure hoisting machine, the displacement state of the disk 33 in the case of no load (or light load) (in this case, no displacement or minute displacement) and the maximum loading load are applied, and the fixed main shaft 24 is inclined. Even in a displacement state in which the inclination of the disk 33 is greatly increased, the displacement of the disk 33 is not changed as shown by reference numeral 36 in FIG. There are no areas.

  That is, as can be seen in FIG. 6, the position of the rotating surface 35 of the disc 33 tilted in the state where the maximum load is applied and the position of the rotating surface 35 in the state of no load (or light load) are hardly changed. If the disc brake device is arranged in the region 36, the disc 33 tilts in a state where the maximum loading load is applied even if the gap length between the disc 33 and the brake lining is set for no load (or light load). However, contact between the disc 33 and the brake lining can be avoided.

  This area 36 can be determined after calculation or actual measurement. However, the area 36 cannot be determined uniformly by various factors such as the size and thickness of the disk 33, the size of the rotor, the deformation of the housing body 22, and the like. Absent.

  Therefore, when applying the present invention, in accordance with the concept of the present invention, the position of the rotating surface 35 of the disc 33 tilted with the maximum load applied and the rotating surface in a no-load (or light load) state. It is only necessary to determine the area 36 where the position 35 is almost unchanged and to arrange the disc brake device in that area.

Next, an embodiment of a thin hoisting machine based on such a concept will be described with reference to FIG.
FIG. 7 is a front view of the hoisting machine 13 as viewed from the opposite side of the car. The main rope 19 is wound around the sheave 30 in a U-shape with both end portions extended upward.

  A rotor 31 integrally formed with the sheave 30 and a disk 33 formed integrally with the rotor 31 are arranged on the outer periphery of the sheave 30.

Therefore, the disk 33 is configured to be rotated integrally with the sheave 30 and the rotor 31 and to be rotatable without contacting the housing assembly 20 located behind. A disc brake device 37 is fixed to the housing assembly 20. As shown in FIG. 7, the fixed position is located on the side of the sheave 6 just outside the main rope 7 wound around the sheave 30 and extended upward. avoid than the transverse center line C _H sheaves 6 are arranged in a region 36 located in the upper part.

The disc brake device 37 is configured as shown in FIG.
In FIG. 8, the disc brake device 37 includes an electromagnet portion including a fixed iron core 39 and an electromagnetic coil 40 built in a brake housing 38, a movable iron core 41 attracted to the fixed iron core 39 of the electromagnet portion, and the movable iron core 41. A brake lining 42 fixed to the surface and a spring 43 that urges the movable iron core 41 toward the disk 33 are configured. The brake housing 38 has an opening 44 for receiving the disk 33 therein, and the disk 33 is guided into the brake housing 38 from the opening 44.

  In a state where braking is not applied, a direct current is supplied to the electromagnetic coil 40 from a drive circuit (not shown). This direct current is obtained by rectifying an AC power source using a full-wave rectifier bridge composed of four diodes. The electromagnetic coil 40 is energized because braking is not applied in a normal operation state.

  In this state, since the magnetic force is generated in the fixed iron core 39, the movable iron core 41 is attracted to the fixed iron core 39 against the repulsive force of the spring 43, and the brake lining 42 is separated from the disk 33 and applied to the disk 33 as a braking force. Does not occur.

  When applying braking, the energization of the electromagnetic coil 40 from a drive circuit (not shown) is interrupted, and the magnetic force generated in the fixed iron core 39 disappears, so that the movable iron core 41 is pressed toward the disk 33 by the urging force of the spring 43. The brake lining 42 sandwiches the disc 33 from both sides. As a result, a braking force is generated in the disk 33.

  The disc brake device 37 may be anything other than the structure shown in FIG.

As shown in FIG. 7, the disc brake device 37 having such a configuration is located outside the main rope 7 that is folded back in a U shape at a position overlapping the disc 33, and the sheave 6 or the fixed main shaft. approximate distance L2 shifted from the longitudinal centerline C _V extending in the direction of take suspended load 24, is disposed above the area approximate distance L1 than the transverse center line C _H orthogonal to the longitudinal center line C _V . Further, the disc brake device 37 is disposed in a pair symmetrically (line symmetric) with respect to the longitudinal center line _CV .

For this embodiment, it is adapted to be positioned from approximately 20 ° from the transverse center line C _H about the axis of the sheave 30 in the angular range of 40 °.

  Here, the position where the disc brake device 37 is disposed is the position of the rotating surface 35 of the disc 33 tilted in a state where the maximum loading load is applied as described above, and the rotating surface in a state of no load (or light load). The region 36 is selected so that the position 35 hardly changes.

  Further, this region 36 is based on an invariant point where the position of the rotating surface 35 of the disc 33 tilted in the state where the maximum load is applied and the position of the rotating surface 35 in the state of no load (or light load) do not change. The predetermined range is set, specifically, the range in which the displacement of about 1/10 of the stroke of the movable iron core 41 of the disc brake device 37 is generated.

  Thus, since the disc brake device 37 is disposed outside the main rope 19 folded back in a U-shape, the disc brake device 37 can brake the disc 33 without contacting the main rope 19, so that the hoisting machine 13 can be made thin.

  That is, when the main rope 19 and the disc brake device 37 are arranged in series, the axial length is obtained by adding both dimensions, but the disc brake device 37 is arranged outside the main rope 19 so It becomes the form arranged in parallel, and the shaft length can be shortened.

  Further, the disc brake device 37 is placed in a region 36 where the position of the rotating surface 35 of the disc 33 tilted in a state where the maximum load is applied and the position of the rotating surface 35 in a state of no load (or light load) hardly change. Therefore, the length of the gap until the brake lining 42 brakes the disc 33 can be reduced, and the axial length of the disc brake device 37 can be reduced accordingly. Furthermore, a reduction in collision noise can be expected.

  In this way, the disc brake device 37 is arranged outside the main rope 19, the position of the disc 33 is inclined with the maximum load applied, and the position of the rotating surface 35 of the disc 33 tilted and no load (or light load). ), The axial length of the hoisting machine can be reduced as much as possible.

  In the embodiment shown in FIG. 7, the case where the hoisting machine 13 is provided at the bottom of the hoistway 10 has been described. Alternatively, the hoisting machine 13 is attached to a beam near the uppermost part of the hoistway 10. The present invention can also be applied to the case where it is provided. In this case, since the main rope 19 extends downward, the suspension load also acts downward. Therefore, the configuration of the embodiment shown in FIG. 7 is rotated 180 degrees.

  As a matter of course, this configuration can provide the same operations and effects as those described above.

DESCRIPTION OF SYMBOLS 10 ... Hoistway, 11 ... Ride car, 12 ... Counterweight, 13 ... Thin hoisting machine, 19 ... Main rope,
DESCRIPTION OF SYMBOLS 20 ... Housing assembly, 21 ... Sheave assembly, 22 ... Housing main body, 23 ... Boss part, 24 ... Fixed spindle,
25 ... Storage recess, 26 ... Stator, 27 ... Stator winding, 30 ... Sheave, 31 ... Rotor,
33 ... Disc, 37 ... Disc brake device, 39 ... Stator, 40 ... Electromagnetic coil,
41 ... movable iron core, 42 ... brake lining, 43 ... spring.

Claims (5)

A housing main body containing a stator and a stator winding, a fixed main shaft fixed on one side to the main body and the other as a free end, and rotatable on a free end side of the fixed main shaft via a bearing A sheave attached to which a main rope is wound, a rotor that is formed integrally with the sheave and forms a motor part in cooperation with the stator, and a disk that rotates integrally with the sheave In the elevator hoisting machine provided,
Outside the main rope wound around the sheave and above the center line orthogonal to the center line of the sheave extending in the direction of the suspension load applied to the sheave, the maximum load was applied. A disc brake device that brakes the disc in a region where the position of the rotating surface of the disc tilted in a state and the position of the disc rotating surface in a no-load or light-load state are not substantially changed. Elevator hoisting machine. 2. The elevator hoist according to claim 1, wherein the disc brake device is provided in a pair at positions symmetrical with respect to a center line of the sheave extending in a direction of a suspension load applied to the sheave. An elevator hoisting machine characterized by having The elevator hoist according to claim 2, wherein the disc brake device is fixed to the housing body. A housing main body containing a stator and a stator winding, a fixed main shaft fixed on one side to the main body and the other as a free end, and rotatable on a free end side of the fixed main shaft via a bearing A sheave attached to which a main rope is wound, a rotor that is formed integrally with the sheave and forms a motor part in cooperation with the stator, and a disk that rotates integrally with the sheave In the elevator hoisting machine provided,
Outside the main rope wound around the sheave and above the center line orthogonal to the center line of the sheave extending in the direction of the suspension load applied to the sheave, the maximum load was applied. A disc brake device that brakes the disc in a region where the distance between the position of the rotating surface of the disc tilted in a state and the position of the rotating surface of the disc in a no-load or light-load state is within a predetermined range A hoisting machine for an elevator characterized by the arrangement of 5. The elevator hoist according to claim 4, wherein the predetermined range is 1/10 or less of a stroke of an operating iron core built in the disc brake device.

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