KR970009386B1 - Elevator and cooling device using linear motor - Google Patents

Abstract

Disclosed is an elevator using a linear motor and apparatus to cool the motor. The elevator comprises an air gap regulator, a cooler and a brake(25). In the air gap regulator, an air gap and roller location(12b) are simultaneously adjusted by a ring type regulator(12a). In the cooler stator(15) of the linear motor is formed as a hollow pipe for cooling. The brake(25) is automatically operated by electro-magnetic force, or manually operated by handle manipulation. Thereby, the sudden braking is prevented so that safe drive is performed.

Description

Elevator and Motor Cooling System Using Linear Motor

1 to 10 are views of a conventional elevator,

1 is a perspective view of a conventional elevator.

2 is a perspective view showing another embodiment of a conventional elevator.

3 is a configuration diagram of a rail brake.

(A) (b) of FIG. 4 is a block diagram of an air gap adjusting apparatus.

(A) and (b) of FIG. 5 are side and front views of the stator upper support structure.

6 is a side view and a front view of the lower support structure.

7 is a configuration diagram of a cooling device.

8 is a stator configuration diagram.

9 is a configuration diagram of an air gap detection device.

10 is a configuration diagram of the vibration isolator.

11 to 19 are views related to the present invention.

11 is a perspective view of an elevator according to the present invention.

(A) (b) of FIG. 12 is a front view and a partial plan view of an air gap adjusting device.

13 is a partial front view showing the stator upper support structure.

Figure 14 (a) is a partial cross-sectional view showing the stator lower support structure.

(b) is a partial plan view.

15 is a cross-sectional view of the cooling device.

16 is a cross-sectional view showing a modification of the stator.

(A) (b) (c) of FIG. 17 shows the detailed configuration of the stator.

(a) is a top view, (b) is a front view, (c) is a partial sectional drawing.

18 is an exploded cross-sectional view of the vibration isolator.

(b) is a cross-sectional view of the coupling state.

19 is a front view and a side view of the brake device.

* Explanation of symbols for main parts of the drawings

11: mover 11a: cylindrical body

11b: Through Hole 11e: Through Hole

12: air gap adjusting roller 12a: ring-shaped adjustment member of the tapered cross section

12b: Roller 12f: Spring pressure adjusting bolt

15: stator 15g: groove

19a: suction port 19b: discharge

19c: pipe 20: fan

24: car 25: brake

25e: Brake 29: Air guide plate

29a: Information Guide 29b: Information Guide

29b: air through

The present invention relates to an elevator using a linear motor.

In a conventional elevator, the hoisting system is spreading and spreading. In this method, a hoist is installed by installing a machine room on an elevator, and one end of a car is suspended by a rope, and one end of the car is suspended by a count weight. Therefore, the size of the hoist is relatively large and a brake device other than a brake device is installed in the machine room. Therefore, the space is inevitably required in the room, and the occupied area of the housing by the machine room becomes a problem, and the cost is high in terms of rigidity of the machine room structure with respect to heavy weight. In recent years, while solving the above-mentioned problem, an elevator using a linear induction motor as a driving source has been in the spotlight. Since the linear induction motor is directly driven by the motor itself, it is possible to simply reduce the weight of the whole machine without the need for a rotary machine such as a hoist and other reducers and pulleys. While it is unnecessary and has the advantage of miniaturizing the elevator system, there are many problems such as the maintenance of the brake during the emergency braking, the difficulty of manual winding up, the difficulty of adjusting the air gap.

An embodiment of a conventional linear motor elevator is shown in FIGS. 1 to 10.

Referring first to the parts used in FIG. 1, 41 is the upper frame, 42 is the hanger frame, 43 is the count weight guide rail, 44 is the car guide rail, 45 is the count weight frame, 46 is the pulley, 47 is the rope, 48 is The count weight guide roller, 49 is the car guide roller, 50 is the count weight, 51 is the mover, 52 is the air gap adjusting roller, 53 is the actuator dustproof device, 54 is the cooling device, 55 is Stator, 56 shows the stator upper support structure, 57 shows the air gap fluctuation detection device, 58 shows the stator lower support structure.

Hereinafter, referring to the configuration of an elevator using a conventional linear motor, as shown in FIG. 1, the stator 55 is supported by the upper and lower support structures 56 and 58 on the upper frame 41. .

The mover 51 is provided in the count weight frame 45, and the count weight guide roller 48 is provided in the both sides of the count weight frame 45, and is in contact with the count weight guide rail 43. As shown in FIG. The count weight frame 45 is suspended by the rope 47 and connected to the car 60 via the pulley 46 in the upper part of the hoistway. Car guide rollers 49 are provided on both sides of the car 60, and the car guide roller 9 is provided in contact with the car guide rail 44. As shown in FIG. 4, the air gap adjusting roller 52 is provided in contact with the stator 55 above and below the movable element 51, and as shown in FIG. 7, the movable element vibration isolator 53 is provided.

As shown in Fig. 7, a cooling device 54 is provided on the outer circumferential surface of the movable element 51, and as shown in Fig. 9, an air gap variation detecting device 57 is provided between the movable element 51 and the stator 55. . The rail brake 61 is installed below the car 60 as shown in FIG. 1, or is installed below the count frame 45 as shown in FIG. 2, or the third brake drum 62 is additionally provided. It is provided integrally with the pulley 46 at the upper part of the hoistway.

Hereinafter, an elevator using a conventional linear motor will be described in more detail.

When a current is applied to the mover 51, the mover 51 moves along the induction between the mover 51 and the stator 55. In this case, in order to prevent an emergency condition due to the hard and vibration generated when the linear induction motor is driven, a constant gap must be maintained between the mover 51 and the stator 55 at all times. The rollers 52 are fixed at three to four places around the stator 55. In addition, the outer peripheral surface of the movable element 51 is provided with a fin, which is a cooling device 54, as shown in FIG. 7 to cool the heat generated between the movable element 51 and the stator 55. In order to generate the cooling effect by the friction wind, and to reduce the vibration generated when driving the movable element 51, as shown in FIG. The upper and lower parts are installed in the upper part and the upper part of the stator 55 is coupled to a ball joint 56a as shown in FIGS. 5 and 6 to absorb vibrations against earthquakes and external light loads. (55) The lower part is provided with stator upper and lower support structures 56 and 58 which are coupled to the sol joint 58a, the coil spring 58b and the turn buckle 58c. Moreover, the air gap fluctuation detection device 57 of FIG. 9 is provided so that emergency braking can be detected by detecting the air gap fluctuation between the movable element 51 and the stator 55. FIG.

The elevator using the linear motor is based on the count weight frame 45 and the pulley 46 coupled thereto when the movable element 51 is driven in response to the thrust between the movable element 51 and the stator 55. The rope 47 hanging on the car 60 is moved to drive the elevator.

In this case, as illustrated in FIGS. 1 and 2, the rail brake 61 installed in the lower portion of the count weight frame 45 or the lower portion of the car 60 cuts or applies current according to the floor calling in the elevator and the hall. As a result, the magnet is turned on and off to serve as a brake. In addition, a drum brake 62 as shown in FIG. 3 is further provided on the pulley 46 as an emergency braking means in order to prevent overrun of the elevator.

The brake 62 is composed of a brake drum 63, a brake arm 64, a brake shoe 65 and a magnet 62a for operating the brake arm 64 as shown in FIG.

Conventional elevators as described above, as shown in Figs. 1 and 2, the space in the upper part of the hoistway is miniaturized and simplified, so that the space utilization of the building is not required because the machine room is unnecessary. However, when the floor stops, the rail brake 60 device incorporated in the count weight frame 45 brakes and the car 60 is stopped on the service flower. Is large, wear is also large, the malfunction is easily caused, when the malfunction is locked in the layer except the lowermost layer (lock) there was a bad maintenance and dangerous.

The structure of FIG. 1 in the embodiment of FIG. 1 is provided with a rail brake 61 on the side of the car 60 to enable inspection and repair from the inside of the car 60. However, this also excludes the lowermost floor. In addition to the dangerous workability, the number of rail brakes 61 corresponding to the braking force to withstand an unbalanced load is usually 2 to 4, so it is more difficult to open and close at the same time, the workability is very bad. The rope 47 is connected only to the relay of the pulley 46 to install and operate a drum brake 62 integrally formed on the puller 46 in the upper part of the hoistway to prevent overrun due to inertia. Because of this, the maintenance of the emergency lock state (lock) is also extremely bad, even more so when operating in combination with the rail brake (61).

As shown in FIG. 4, the adjusting device for the prevention of air gap fluctuation is arranged by radially arranging the air gap adjusting rollers 52 on the circumference of the mover 51 so that magnetic force acts between the mover 51 and the stator 55. In addition, the air gap fluctuation was reduced even when not in use, and the vibration and noise caused by the elevating driving were reduced by using an elastic material such as synthetic resin as the material of the air gap adjusting roller 52.

However, even if the correct air gap between the mover 51 and the stator 55 is adjusted, the air gap adjusting roller 5 applied to the stator 55 due to the wear of the respective air gap adjusting roller 52 due to driving is removed. When it is necessary to adjust the fluctuation of the spring wall, it is cumbersome to replace each air gap adjusting roller 52 or to adjust the position of the air gap adjusting roller 52 according to the amount of displacement to readjust the wear displacement. .

This is because, in particular, in the event of sudden braking due to air gap fluctuations, adjustment due to breakage of the air gap adjusting roller 52 due to brake malfunction, earthquake and light load, or reduction of the gap caused by uneven wear of the air gap adjusting roller 52 is required. It was a very difficult problem.

In the stator support structure as shown in FIG. 5 and FIG. 6, the stator upper support structure 56 as in FIG. 5 is fixed to the upper frame 41 on the building side by the ball joint 56a. 6, the stator lower support structure 58 as shown in FIG. 6 enables rotation to some extent by the ball joint 58a and connects the coil spring 58b to the turn buckle 58c. Is fixed to the lower elevation support B to add tension to the stator 55 and to absorb vibrations acting on the stator 55 by the coil spring 58b. In FIG. 5, 58e shows an eye bolt.

However, in the conventional stator support structure, the hoistway through the ball joint 58a, the turn buckle 58c, and the coil spring 58b in which the upper part of the stator 55 is fixed to the upper frame 41 on the building side and the lower part is a supporting member. Since the tension is added to the lower portion of the support part B, the air gap is assembled to the mover 51 which is connected to the stator 55 at all times when the stator 55 does not exactly match the gravity line. As a different load is applied to the roller 52, there is a problem that causes uneven wear of the air gap adjusting roller 52 and acts as a cause of fluctuation of the air gap.

Then, as shown in FIG. 7, as a cooling device for cooling overheating caused by the resistance of the stator 55 due to the movement of the mover 51, the mover 41 uses the flow of air generated while driving as a cooling medium. The cooling device for transferring the heat generated by the mover 51 to the cooling medium by employing the cooling fins 54a on the outer surface is adopted. Although it is possible to cool by the running wind, the temperature on the closed passage is increased, thereby reducing the cooling effect and increasing the temperature inside the car 60, thereby causing discomfort to the passengers during unloading.

As shown in FIG. 8, the configuration of the stator 55 is covered with aluminum 55b on the hollow member 55a made of pure iron, but this is a hollow as a primary conductor and a secondary conductor of the mover 51 and the stator 55. As a result of increasing the air gap amount, which is a gap with the member 55a, by the thickness of the coated aluminum, the efficiency of the linear induction motor is reduced.

As shown in FIG. 9, the air gap fluctuation detecting device 57 is a gap sensor that detects an abnormality of the air gap, which is a gap between the stator 55 and the mover 51, and the one end of the contact conductor 57a has a hollow casing ( 57b), the fixing bolt 57c is fixed and the other end is bent to form a contact point for the stator 55, and between the stator 55 and the mover 51 by using a fastening bolt 57g for adjustment. Allowable air gap is set. The fixing bolt 57c and the stator 55 are in contact with the DC power supply by the cables 57e and 57f, respectively.

The air gap fluctuation detecting device 57 is provided with contact conductors provided on the upper and lower portions of the linear induction motor when the air gap fluctuation roller 52 has a change in allowable air gap or more between the stator 55 and the mover 51 due to abrasion of the air gap adjusting roller 52. Contact with the surface of the guide 51 causes the warning lamp to sound and stops starting.

However, the air gap fluctuation detecting device 57 as described above has an air gap fluctuation detecting device 57 connected close thereto because the stator 55 and the mover 51 have respective volume expansions due to high heat generation during operation. ), The contact conductor 57a also has a volume expansion and a length expansion, so that contact between the contact conductor 57a and the stator 55 may occur even with less variation than the air gap of the actual phenomenon.

In addition, as shown in FIG. 10, the mover vibration isolator 53 is a vibration isolator that prevents the occurrence of rapid acceleration fluctuations at the start or stop of the primary conductor and is a vibration isolator that purifies the vibration of the car 60. An anti-vibration rubber 53a is provided on the upper and lower ends of the ruler 51, and the plate 536 is attached to the upper and lower ends thereof, and the vibration is caused by the acceleration change when starting and stopping by fastening the support member and the bolt 53c. To reduce the

However, since the gravity of the mover 51 always acts at the time of stop, the compressive force acts only on the lower dustproof rubber 53a of the mover 51, and the elastic recovery force of the lower dustproof rubber 53a with the passage of time is increased. The upper anti-vibration rubber 53a is rather reduced, resulting in a tensile force acting on the support member and the mover 51 to be substantially separated and coupled.

This is because the compression force is not applied to the upper dustproof rubber 53a when assembling the support member and the mover 51 in the initial state.

Because of this, the mover 51 does not absorb the soft vibration during acceleration and deceleration, and thus forms a form to cope with the fluctuation of the force suddenly, resulting in a large repulsive force resulting in the generation of vibration.

The present invention was conceived in view of the elevator using the conventional linear induction motor as described above.

The present invention solves the difficulty of repairability of the brake and the inconvenience of adjustment work according to the air gap variation of the air gap adjusting device, and the difficulty of the installation of the stator support structure on the gravity line, and the operation of the mover and the stator. Increasing the temperature on the hoistway caused by overheating reduces the cooling effect in the ball and reduces the thrust due to the increase in the amount of air gap between the stator and the mover according to the aluminum thickness, and the contact conductor of the air gap fluctuation detector is thermally expanded. This provides an elevator using a new linear induction motor that solves the case where contact can occur even when there is little variation, and the fact that the upper part of the upper dustproof rubber of the dustproof structure is unreasonable.

The present invention is to solve the problem of the problem of the maintenance of the brake lock of the prior art, to easily release the lock state of the brake at the bottom, and to configure the braking system with a structure that can be manually wound up, and the wear of the elevator Easily adjustable fluctuations and at the same time mover-attached air gap adjusting rollers provide a device capable of moving the stator circumference in a uniform amount, and it is possible to readjust the fluctuating spring force acting on the rollers. In order to facilitate the installation on the gravitational line, the lower supporting structure is provided with a device that can move freely on the gravitational line by the gravity of the stator itself, and the increase of the temperature on the hoistway due to the overheating caused by driving reduces the effect of air cooling. To improve air flow to the outer circumference of the mover In addition, it provides a structure that effectively extracts the overheated air of the hoistway into the hollow shaft of the stator, and improves the reduction of thrust as a result of the increase in air gap due to the aluminum coating. As a type, the reduction of the air gap amount corresponding to the aluminum coating amount was achieved, and the thrust was improved, and even if the actual variation was small due to the length and volume expansion of the contact conductor of the air gap fluctuation detection device, the elevator suddenly braked. In addition to improving the unreasonable point, the upper anti-rubber of the anti-vibration structure has less prevention effect over time, and the soft vibration is not absorbed during acceleration and deceleration. It can have a soft dustproof effect even during acceleration / deceleration and constant speed. It was made.

Hereinafter, the present invention will be described in detail with reference to Examples 11 to 19 of the accompanying drawings.

Referring first to the components shown in the drawings, 1 is an upper frame, 2 is a hanger frame, 3 is a count weight guide rail, 4 is a car guide rail, 5 is a count weight frame, 6 is a pulley, 7 is a rope, 8 is Count weight roller, 9 is car guide roller, 10 is count weight, 11 is mover, 12 is air gap adjuster, 13 is mover dustproof device, 14 is air gap fluctuation detector, 15 is stator, 16 is stator top The support structure 18 shows the stator lower support structure, respectively.

Hereinafter, referring to the configuration of the elevator using the linear motor according to the present invention with reference to Figure 11, the mover 11 is connected to the count weight frame 5, the upper and lower parts of the mover 11, The gap adjusting device 12, the air gap fluctuation detecting device 14, and the mover dustproof device 13 are provided, and the stator 15 penetrating the mover 11 is attached to the upper frame 1 in FIG. The stator upper support structure 16 and the cooling device 19 of FIG. 16 are relayed, and the lower part of the stator 15 of the stator lower support structure 18 of FIG. 14 and the cooling device 19 of FIG. The suction port 19a is provided in the lower support portion B by the relay.

Count weight guide rollers 8 are provided at upper and lower ends of the count weight frame 5, count weights 10 are mounted at both sides of the count weight frame 5, and count weight buffers 22 are provided at the lower support part B. ) Is installed. The upper end of the count weight frame 5 is coupled with a rope 7 by a symbol rod 27, which is connected to a lower pit via a pulley 6 provided in the upper hanger frame 2. After passing through the inside of the count weight frame (5) through a sheave (26) driven integrally with the brake (25) installed in the), the pulley (6) is wound again to pulley ( 6) is relayed and connected to the thimble rod 28 in the upper part of the car 24.

Moreover, the car guide roller 9 is provided in the upper and lower sides of the car 24, and the car buffer 23 is provided in the lower support part B. As shown in FIG.

An encoder 25b is provided at the shaft end of the sieve 26 of the count weight frame 5.

Hereinafter, an elevator using the linear motor according to the present invention will be described in more detail.

In the elevator using the linear motor according to the present invention, as shown in FIG. 11, the mover 11 is formed in a cylindrical shape, and the cylindrical mover 11 is configured as a primary side. The count weight 10 is disposed on both sides of the ruler 11 and attached to the count weight frame 5, and is composed of count weights 10, 5, and 11 with respect to the car 24 as a whole.

The car 24 and the count weights 10, 5, and 11 are ropes 7 along the sheaves 26 which are combined with the pulley 6 installed at the top and the brake 25 installed at the bottom. Connected by

In addition, the stator 15 configured as the secondary side has a predetermined air gap with the mover 11 and faces each other to generate a secondary side conductor which generates an induction magnetic field by supplying power to the primary conductor connected to the driving power source. In this configuration, the movable vehicle 11 is an elevator device for traveling along the travel axis of the stator 15.

In addition, in FIG. 11, the lower brake device is disposed while eliminating the machine room above the hoistway and minimizing the hoistway area of the linear induction motor elevator in which the car 24 and the count weights 10, 5, and 11 are disposed. The rope 7 connected from the car 24 is passed through the pulley 6 on the upper side of the car 24 and the count weights 10, 5, and 11 on the upper side pulley 6, and then the count weight frame 5. Through the sieve 26 integrally coupled to the brake 25 installed in the lower part through the through and fixed to the count weight frame 5, the pulley 6 on the count weight 10, 5, and 11 side is fixed again. In this structure, the number of pulleys 6 to be installed on the upper part in order to use the lower brake 25 can be reduced, and the structure to reduce the width of the hoistway by the outer diameter of the pulley 6 is provided. Have the same width as the same way as the existing linear induction motor type elevator. In addition, the use of the lower brake 25 eliminates the load, wear, and malfunction of the brake when braking the existing rail brake, and in particular, the water retention function in the case of malfunction due to the locking of the floor except for the lowest floor is easily solved. . Further, as shown in FIG. 19, the brake device simultaneously fastens the sieve 26 and the brake drum 25c to the shaft 25a, and the sieve 26 and the drum 25c may be integrally configured. An encoder 25b is provided at one side of the shaft 25a, and has a structure in which a key can be assembled at the other side. As the brake 25 is installed downward, the wrap angle of the rope 7 wound on the sieve 26 becomes 180 degrees, and thus the rope 7 is pushed by the inertial force generated during braking. In addition to minimizing the overrun due to the above, there is an advantage that it can be easily maintained and repaired in the lower layer when locked due to the emergency stop. It is also possible to use a device for manual reeling that was not available with conventional linear induction motors. That is, when manual winding is required by using the key installed on the other side of the shaft 25a, it is possible to easily wind it up manually using the reducer 25d.

The reducer 25d may be constituted by a worm 25f rotated by the handle 25e and a worm gear 25g engaged with the worm 25f. In addition, the reducer 25d may be configured using a helical gear, a bevel gear, a spur gear, or the like. You may.

The stator 15 penetrates the center of the mover 11 as shown in FIG. 12, and has a constant air gap between the mover iron core 11c, which is the primary conductor of the mover 11, and the stator 15. As shown in FIG. It is formed on the circumference.

The air gap adjusting device shown in FIG. 12 causes several (3 to 4) air gap adjusting rollers 12b to be combined with the fixing member 12d by the pins 12j on the mover 11. The lower part of the fixing member 12d was combined-driven by the support plate 121 pin 12g fixed to the upper part of the mover 11. Further, the rollers were configured differently in the axial direction from each other by combining the pin 12h with the roller 12c perpendicular to the pin 12j, which is the axis of the air gap adjusting roller 12b, on the front surface of the fixing member 12d.

The air gap adjusting roller 12b of the fixing member is in contact with the ring-shaped adjusting member 12a of the tapered cross section of the air gap adjusting taper which is combined with the mover 11 and the screw, and the ring-shaped adjusting member 12a is adjusted (locked or The front roller 12c, which is in contact with the ring-shaped adjustment member 12a, is rotated and the tapered surface of the ring-shaped adjustment member 12a moves so that the front roller 12c is simultaneously lowered by the same amount. Or it is structured to be upward.

In addition, the roller 12b, which is in contact with the outer circumferential surface of the stator 15, has a structure that is always subjected to a compressive force by the spring 12e, and the spring pressure adjusting bolt 12f when the spring pressure is changed due to the wear of the roller 12b. Can be adjusted by

In addition, in order to prevent loosening after adjustment of the ring-shaped adjustment member 12a of the tapered cross section, a bracket 12i is installed on the movable member 11 and fixed to the fixed hole 12k which is processed on the outer circumferential surface of the ring-shaped adjustment member 12a. It is structured to fix by inserting the bolt 12j.

The air gap adjusting device has the advantage of being easy to assemble, install and repair by adjusting the ring-shaped adjusting member 12a and simultaneously adjusting the circumferential roller 12b by the displacement amount and adjusting the fluctuation of the spring pressure. have.

In addition, the air gap variation detecting device couples the micro switch 30 to detect the displacement of the lower protrusion 12m of each fixing member 12d to the support plate 121, respectively, and the micro switch when there is a predetermined air gap variation. 30 is configured to operate to emergency stop the car 24.

Referring to FIG. 13, the stator upper support structure 16 of the stator 15 is rotatable by coupling the ring 15c to the plate 15a on the top of the stator 15 by the pin 15b, The upper frame 1 was fastened to the ring 15d fastened by the nut 15f. In addition, both ends of the ring 15d are fastened with guides 15e in order to prevent the vibration and the detachment due to the light.

Referring to FIG. 14, the stator lower support structure 18 is rotatably coupled with the spring rod 18c by the pin 18b to the fixing plate 18a, and the spring assembled to the spring rod 18c ( 18f) was subjected to a tensile force against compression in the case 18d. In addition, the lower part of the case 18d is screwed to engage with the ball link 18g, and rotates the nut machined in the ball link 18g to adjust the compression force of the spring 18f to reduce the tension applied to the stator 15. Adjustment was made. The ball link 18g has a structure capable of rotating from side to side.

One end of the ball link 18g is engaged with the link 18h, and the lower end of the link 18h is engaged with the bearing (or roller) 18j by the pin 18i. This roller 18j drives along the guide rail 18k 'of the long hole processed in the upper surface inside the box 18k. Further, a thrust bearing 118 is assembled to the lower part of the box 18k, and an upper part of the thrust bearing 181 is assembled by a shaft 18m, and the shaft 18m is fixed to the lower floor 18o. The structure is fastened by the bolt 18n.

Conventionally, it is difficult to install the support of the stator 15 to be accurately positioned on the gravitational line, and there is a problem of fluctuation of the air gap due to uneven wear of the air gap adjusting roller caused by this, but the support structure according to the present invention solves this problem. It can be basically solved.

It is attached to the mover 11 which moves with the stator 15 as a traveling axis according to the vertical error of the mover 11 and the stator 15 in which the vertical and horizontal errors of the count weight guide rail 3 are determined. The air gap adjusting roller 12b thus obtained is always subjected to the uneven load by the displacement of the error.

In the present invention, the stator 15 is movable in the direction of releasing the load in any of the front, rear, left and right directions in response to such an error, thereby minimizing the unloading load on the air gap adjusting roller 12b and compressing the spring 18f. By virtue of being able to sufficiently absorb vibration and light, the error in the rotational direction of the stator 15 is such that the cylindrical box 18k is rotatable by the thrust bearing 181, and the error on the vertical line is applied to the roller 18j. Is compensated for while moving along the long guide rail 18k 'of the inner top surface of the box 18k.

Referring to FIG. 16 (a), the conventional stator 15 includes an iron core 11c, which is the primary conductor of the movable element 11, and an aluminum (Al) or copper (Cu) material covering portion of the stator 15 ( Although it has a mechanical air gap that is a void to the iron (Fe) inner cylinder 15 excluding 15 '), the structure is inefficient in a cylindrical linear induction motor in which direct thrust according to the amount of air gap is absent. As shown in Fig. 16 (b), by processing a predetermined groove 15g in the stator 15 and coating aluminum or copper thereon, the mechanical voids up to the iron core 11c and the steel stator 15, which are primary conductors, are processed. As a result of lowering the amount by the coating amount of aluminum or copper as the secondary conductor, the thrust of the linear induction motor was further increased to maximize the efficiency of the linear induction motor.

In particular, the cooling apparatus according to the present invention has a structure in which the inner surface of the hollow member of the stator 15 is used as an air passage as shown in FIG. 15, and has an inlet 19a for absorbing air in the lower part of the stator 15. The upper part is provided with a discharge port 19b for discharging it, and the pipe 19c is relayed to the structure by which the fan 20 installed in the upper part of the building (roof) is forcibly discharged.

In addition, in the cooling apparatus according to the present invention, as shown in FIG. 17, air is introduced from the outer circumferential surface of the mover 11 to cool the inside of the mover 11 and the stator 15 simultaneously. As a structure, a plurality of long cylindrical holes 11b are formed in the cylindrical body 11a of the movable element 11, and the air guide plate 29 is attached to the outside to allow air to flow from the outside to the inside.

The mover 11 has a structure in which the iron core 11c and the coil 11d are coupled to the inside of the cylindrical body 11a, and the air guide plate 29 has a plurality of guide pieces 29a therein. 29b) is formed by cutting and bending the air guide plate 29 itself, and the guide piece 29a of the upper part is opened toward the upper side with respect to the middle part of the movable element 11, and the guide piece of the lower part ( 29a) is configured to open downward, so that the amount of heat generated in the primary conductor and the coil is increased smoothly when the mover 11 moves up and down.

The cooling device of the present invention allows the air to flow smoothly from the outside to the inside by the air guide plate 29 formed on the mover 11 rather than the external cooling effect of the mover 11 by the conventional cooling fins. By discharging the heat generation from the stator 15, which is a heat generating unit, to the outside by a forced air flow, the temperature rise inside the hoistway is prevented, thereby increasing the cooling effect by the air friction during operation. In addition, the shape of the ring-shaped adjusting member 12a of the tapered cross section of the air gap adjusting device is a funnel shape, in which contact air is accumulated during driving of the movable element 11 and flows between elevators to further improve the cooling effect.

As shown in FIG. 11, only a plurality of through holes 11e may be processed in the cylindrical body 11a of the movable element 11 so as to release heat generated from the primary conductor and the coil. The heat radiation effect by the structure of 17 degrees is better.

Existing anti-vibration structure was installed up and down in the mover 11 to seek the absorption of vibration during acceleration and deceleration, but the compressive force acts only on the anti-vibration rubber in the downward direction by the weight of the mover 11 The anti-vibration rubber of the rubber is subjected to tension, and the acceleration and deceleration (upward deceleration) is not good because the absorption of the vibration is not achieved and the result is to cope with the sudden change of the force, but it is rather bad, the operator dustproof according to the present invention The apparatus 13 changes the shape of the anti-vibration rubber 13d into a hollow hollow shape, and the bolt 13b is welded to the upper plate of the upper and lower iron plates 13a, as shown in FIG. 18, to provide the anti-vibration rubber 13d. And the lower plate has a structure in which the bolt 13b can penetrate, and is joined to the anti-vibration rubber 13d so that when the nut 13c is fastened to the bolt 13b, the anti-vibration rubber 13d is up and down, and the iron plate ( Compressed by 13a) to form dust-proof rubber 13d. Is the original height than ll, is a form of the intermediate it becomes a convex has a structure to be combined with the mover (11).

Then, when the nut 13c is loosened after being assembled to the mover fastening beam 5a of the count weight frame 5, the upper and lower two car fastening beams 5a have a lower side of the mover 11. The self-weight also receives the repulsion force that the upper anti-vibration rubber 13d pushes against the compression, and the upper part is the repulsive force against the compression generated by the compressed anti-vibration rubber 13d separating the nut 13c. 11) is a structure that can absorb the vibration by the anti-vibration rubber (13d) on both the upper and lower sides, it is possible not only to absorb the soft vibration during acceleration and deceleration, but also to obtain a certain dustproof effect in the constant speed section.

As described above, in order to solve the difficulty of maintenance of brake lock, the present invention is easy to release the lock state of the brake from the lower part, and the brake system has a structure that enables manual winding up. In addition, the passenger can be easily rescued in an emergency, thereby improving reliability.

In addition, the air gap fluctuation due to the wear of the roller can be easily adjusted, and at the same time, the air gap adjusting roller attached to the mover can move the stator circumference in a uniform amount, so that the air gap is precisely adjusted. There is an advantage that the spring force acting on the roller can be easily readjusted.

In addition, in the stator support structure, the lower support structure is provided with a device capable of moving freely on the gravity line by the gravity of the stator itself, thereby providing an easy installation on the accurate gravity line.

In particular, the temperature rise on the hoistway caused by the overheating caused by the operation reduces the effect of air cooling, allowing the air to flow smoothly to the outer circumference of the mover and effectively extracting the superheated air of the hoistway into the hollow shaft of the stator. Because of this structure, the cooling effect of the linear motor is very excellent.

In addition, there is an advantage in that the thrust is improved by improving the point that the air gap amount is increased due to the aluminum coating amount, thereby reducing the thrust, thereby obtaining a reduction in the air gap amount corresponding to the aluminum coating amount by using the stator as a ring type. .

In addition, there is an advantage that the safe operation can be achieved by improving the unreasonable occurrence of the sudden braking of the elevator even when the actual variation is small due to the length and volume expansion of the contact conductor of the air gap variation detection device.

In addition, the upper anti-rubber of the anti-vibration structure has less prevention effect over time, and smooth vibration absorption is not achieved during acceleration and deceleration. There is an advantage that can have a smooth dustproof effect even during.

Claims (11)

The air gap between the stator 15 and the mover 11 can be adjusted by the amount of displacement of the circumferential roller 12b at the same time by adjusting the ring-shaped adjustment member 12a of the tapered cross section, and the variation of the spring pressure is controlled by the spring pressure. The air gap adjusting means adapted to be adjusted by the adjustment bolt 12f, and the stator 15 of the linear motor providing the conveying force of the car 24 are formed in the form of a hollow tube, and the outlet 19b and the inlet ( 19a), a cooling means adapted to cool by the fan 20 in a forced air cooling method, and a car braking brake which is automatically operated by the electromagnetic force and manually operated by the operation of the handle 25e and installed at the lower part of the pit. Elevator using a linear motor, characterized in that it comprises a (25). 2. The mechanical voids of the iron core 11c and the steel stator 15, which are the primary conductors, are formed by processing a predetermined groove 15g in the steel stator 15, and coating aluminum or copper thereon. An elevator using a linear motor, characterized in that the secondary conductor is configured to be reduced by the coating amount of aluminum or copper. An inner surface of the hollow member of the stator 15 of the elevator using a linear motor as an air passage, forming an inlet 19a for sucking air in the lower part of the stator 15, and an outlet for discharging it in the upper part ( 19b), the motor cooling apparatus, characterized in that configured to be forcibly discharged by the fan (20) installed in the upper part of the building by relaying the pipe (19c). And a plurality of air inducing elements formed on the cylindrical body (11a) of the mover (11) of the elevator using the linear motor such that air is flowed in and out. 5. The motor according to claim 4, wherein the air induction element is formed by forming a plurality of long through holes 11b in the cylindrical body 11a of the mover 11 and attaching the air guide plate 29 to the outside. Chiller. 6. The motor cooling apparatus according to claim 5, wherein a plurality of guide pieces (29a) and air passages (29b) are formed on the air guide plate (29). 7. The motor according to claim 6, wherein the guide piece 29a of the upper part is opened toward the upper side and the guide piece 29a of the lower part is opened toward the lower side with respect to the middle part of the movable element 11. Chiller. The motor cooling apparatus according to claim 6, wherein the guide piece (29a) of the air guide plate (29) is formed by cutting and bending the air guide plate (29) itself. The ring-shaped adjustment member 12a of the tapered cross section of the air gap adjusting device coupled to the upper part of the movable element 11 is formed in a funnel shape, and the movable element 11 according to any one of claims 3 to 8. Motor cooling apparatus, characterized in that the contact air is configured to flow between the air gap when driving. 5. The motor cooling device according to claim 4, wherein the air inducing element is a plurality of through holes (11e) formed in the cylindrical body (11a) of the mover (11). Using the inner surface of the hollow member of the stator 15 of the elevator using a linear motor as an air passage and forming an inlet (19a) for sucking air in the lower part of the stator 15, and at the upper outlet ( 19b) is installed, and the pipe 19c is relayed to be forcibly discharged by the fan 20 installed in the upper part of the building, and a plurality of air are allowed to flow in and out of the cylindrical body 11a of the mover 11. Motor cooling apparatus characterized in that formed by forming an induction element.