JPH08208151A - Guide roller supporting means of elevator - Google Patents

Abstract

PURPOSE: To improve riding confortableness by changing an elasticity constant for elastically supporting the elevating part of an elevator for a guide rail the most suitably. CONSTITUTION: In a guide roller supporter 20, a guide roller 10 is energized toward a guide rail 2 by an electro-magnetic repulsion force generated between a pair of mutually facing electro-magnets 24, 25. By controlling the bigness of a current electrified to the electro-magnets 24, 25 by a controller 27, an energizing force, namely an elasticity constant for elastically supporting a cage frame 8 in a horizontal direction for the guide rail 2 can be set suitably. Accordingly, by changing the elasticity constant based on the elevating speed of the cage frame 8 and the bigness of bending amount at each position in the elevating direction of the guide rail 2, confortableness can be improved by the reduction of the bigness of vibration force transmitted to the cage frame 8.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a ride comfort by changing the magnitude of the urging force for urging a guide roller toward a guide rail that guides the lifting and lowering of an elevator ascending / descending portion according to the ascending / descending speed. The present invention relates to an elevator guide roller supporting device that can improve the vehicle.

[0002]

2. Description of the Related Art As shown in FIG. 8, a guide rail 2 for guiding the lifting and lowering of a lifting and lowering portion 1 of an elevator includes a vertically extending hoistway 4 by a bracket 3 arranged at a predetermined interval. It is fixed to the wall surface 5 of the. On the other hand, the car room 6 in which the person of the ascending / descending portion 1 rides is attached to the car frame 8 suspended by the rope 7 via the anti-vibration rubber 9.

At the upper and lower four corners of the car frame 8, guide roller supporting devices 11 for supporting the guide roller 10 rotating while contacting the guide rail 2 are attached. These guide roller support devices 11 swing with their base end portions pivotally supported by a frame 12 having an L-shape in side view fixed to the car frame 8 and a bracket 13 integrally provided on the frame 12. And a guide roller support arm 14 that is movable. The guide roller 10 is axially supported by the center portion of the guide roller support arm 14 in the longitudinal direction,
It is supported so as to be rotatable and relatively displaceable with respect to the car frame 8. In addition, the guide roller 10 includes the frame 12
The coil spring 16 attached to the T-shaped bracket 15 attached to the guide rail 2 urges the guide rail 2 toward the guide rail 2 so that the guide rail 2 rotates without being separated from the guide rail 2. Further, the guide roller support arm 1
4 is regulated by a stopper 17 so as not to swing more than a predetermined angle, so that the car frame 8 does not come too close to the guide rail 2.

[0004]

By the way, the guide rail 2 has an initial deflection that occurs when it is fixed to the wall surface 5,
Bending due to thermal expansion, traveling bending and the like caused by pressing the guide roller 10 when the car frame 8 moves up and down, and the like occur. The flexure of the guide rail 2 tends to be small in the portion supported by the bracket 3 and large in the intermediate portion between the brackets 3. As a result, the guide roller 10 rotating while being in contact with the guide rail 2 is forcibly displaced in the horizontal direction due to the bending of the guide rail 2, so that the car frame 8 has an exciting force proportional to the displacement amount of the guide roller 10. Acts via the coil spring 16. The exciting force has a frequency f whose main component is a value obtained by dividing the interval L between the brackets 3 by the ascending / descending speed V of the car frame 8.

As described above, the car frame 8 has the guide roller 1
It is elastically supported in the horizontal direction with respect to the guide rail 2 via 0 and the coil spring 16. The natural frequency is determined by the weights of the car room 6 and the car frame 8 and the coil spring 16
It is set to a specific value from the spring constant of. As a result, when the frequency f of the exciting force acting on the car frame 8 approaches the natural frequency of the car frame 8, the car frame 8 vibrates significantly and the riding comfort deteriorates.

FIG. 9 shows the frequency f of the exciting force acting on the car frame 8 and the ascending / descending speed of the car frame 8 on the horizontal axis, and the magnitude of the exciting force transmitted to the car frame 8 on the vertical axis. FIG. 6 is a diagram showing a change in the magnitude of the exciting force when the spring constant of the coil spring 16 is small, and a dotted line showing a change in the magnitude of the exciting force when the spring constant of the coil spring 16 is large.
As is clear from this figure, when the spring constant of the coil spring 16 is small, when the ascending / descending speed is Va, the coil spring 1
When the spring constant of 6 is large, resonance occurs when the ascending / descending speed is Vc. Then, at the ascending / descending speed Vb, the exciting force when the spring constant of the coil spring 16 is small becomes equal to the exciting force when the spring constant is large.

Therefore, until the ascending / descending speed of the car frame 8 gradually increases to reach the speed Vb, the spring constant of the coil spring 16 is increased and the ascending / descending speed of the car frame 8 is Vb.
If the spring constant of the coil spring 16 can be reduced after exceeding the above, the exciting force transmitted to the car frame 8 can be significantly reduced over the entire range of the ascending / descending speed. However, in the conventional elevator, the spring constant of the coil spring 16 cannot be changed according to the ascending / descending speed.
Therefore, conventionally, even if the bending amount of the guide rail 2 is the same, the spring force of the coil spring 16 is focused on the riding comfort in the region where the raising / lowering speed of the car frame 8 in which the vibration force transmitted to the car frame 8 is large. The constant is set small.

On the other hand, as shown in FIG. 8, a cable 1 for supplying electric power to the electric equipment in the car room 6 is provided under the car frame 8.
8 is suspended. As a result, the weight of the cable 18 acts as an unbalanced load W that tilts the car frame 8.
Since the hanging length of the cable 18 changes depending on the position of the car frame 8 in the hoisting direction in the hoistway 1, the magnitude of the unbalanced load W also changes depending on the position of the car frame 8 in the hoisting direction, as shown in FIG.

Further, the guide rail reaction forces F acting on the individual guide rollers 10 provided at the four corners of the car frame 8 in the upper, lower, left and right corners are not uniform, and in particular, the uppermost floor where the hanging length of the cable 18 becomes the longest. At the position, the largest guide rail reaction force F1 is applied to the upper left and lower right guide rollers 10.
F2 acts.

Therefore, when the spring constant of the coil spring 16 is too small, the guide rail 10 is largely displaced by the guide rail reaction forces F1 and F2, and the guide roller support arm 14 contacts the stopper 17. Then, the exciting force is directly transmitted to the car frame 8 via the stopper 17 and the frame 12, so that the riding comfort is extremely deteriorated. Therefore, the spring constant of the coil spring 16 must be increased to some extent so that the swing of the roller support arm 14 falls within the allowable range even when the magnitude of the unbalanced load W is maximum, and the car frame 8 is There is no choice but to sacrifice the riding comfort when going up and down at high speed.

Therefore, an object of the present invention is to provide a guide roller supporting device for an elevator which can solve the problems of the prior art and improve the riding comfort of the elevator.

[0012]

In order to achieve the above object, an elevator guide roller supporting device of the present invention supports a guide roller that rotates while being in contact with a guide rail that guides the lifting and lowering of an elevator. In a guide roller supporting device attached to the portion, a support means for supporting the guide roller rotatably and relatively displaceable with respect to the elevating part, and interposed between the guide roller and the elevating part, A biasing means for biasing the guide roller toward the guide rail is provided, and the biasing means biases the guide roller by an electromagnetic force.

[0013]

In the elevator guide roller supporting apparatus of the present invention, the guide roller is biased toward the guide rail by the electromagnetic force. Therefore, the biasing force can be adjusted to an arbitrary magnitude by changing the magnitude of the electromagnetic force. can do. This makes it possible to optimally control the value of the elastic constant that elastically supports the elevator ascending / descending portion in the horizontal direction with respect to the guide rail, so that the vibration force transmitted to the elevator ascending / descending portion is reduced, and thus the elevator ride You can improve your comfort.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Each embodiment of the guide roller supporting device for an elevator according to the present invention will be described in detail below with reference to the drawings. In the following description, common parts will be denoted by the same reference numerals and the description thereof will be omitted.

First Embodiment First, an elevator guide roller supporting device according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 4. As shown in FIG. 1, the guide roller supporting device 20 of the elevator according to the first embodiment is attached to the four corners of the car frame 8 in the vertical and horizontal directions. As shown in an enlarged view in FIG. 2, the guide roller support device 20 includes a frame 21 fixed to the car frame 8 and having a substantially U-shape in a side view, and a bracket 22 formed integrally with the frame 21. A guide roller support arm 23 whose base end extends axially and extends linearly.
And a first electromagnet 24 attached to the tip of the guide roller support arm 23, and the first electromagnet 24.
A second electromagnet attached to the tip of the frame 21 so as to face the electromagnets 24 and 25.
And a controller 27 that controls the magnitude of the current that is passed through the wiring 26.

An electromagnetic repulsive force is generated between the first and second electromagnets 24 and 25 according to the magnitude of the electric current to be applied, and urges the guide roller 10 toward the guide rail 2.
On the other hand, when the guide rail 10 moves up and down and passes through the bent portion of the guide rail 2, the guide roller 10 is forcibly displaced in the horizontal direction. When the guide roller support arm 23 swings and the gap between the electromagnets 24 and 25 is narrowed, the electromagnetic repulsive force between the electromagnets 24 and 25 increases, and the guide roller 10 is pushed back toward the guide rail 2.

By the way, in the conventional guide roller supporting device 11 using the coil spring 16, the magnitude of the urging force for urging the guide roller 10 toward the guide rail 2 is as shown in FIG. Arm 14
Linearly inversely proportional to the amount of displacement of the tip of. Accordingly, when the conventional guide roller supporting device 11 is used, the elastic constant of elastically supporting the car frame 8 in the horizontal direction with respect to the guide rail 2 is determined by the spring constant of the coil spring 16.

On the other hand, when the magnitude of the current passing through the electromagnets 24 and 25 is constant, the electromagnets 24 and 2
The magnitude of the electromagnetic repulsive force generated between the five
It is inversely proportional to the square of the gap dimension. Thus, in the guide roller supporting device 20 of the first embodiment, as shown in FIG. 4, the magnitude of the urging force that urges the guide roller 10 toward the guide rail 2 is determined by the tip of the guide roller supporting arm 23. It is inversely proportional to the square of the displacement of. That is, the inclination of the graph showing the relationship between the displacement amount of the tip end of the guide roller support arm 23 and the guide roller biasing force, that is, the elastic constant for elastically supporting the car frame 8 horizontally with respect to the guide rail 2 is the guide roller support. It changes depending on the amount of displacement of the tip of the arm 23.

Therefore, in the guide roller supporting device 20 of the first embodiment, the electromagnets 24 and 25 are provided with the elastic constants for elastically supporting the car frame 8 in the horizontal direction with respect to the guide rails 2 in order to maintain a constant value. It is necessary to change the magnitude of the energized current according to the amount of displacement of the tip of the guide roller support arm 23.

Therefore, in the guide roller supporting device 20 of the first embodiment, the sensor 28 for detecting the inclination of the roller supporting arm 23 is attached to the base end side of the guide roller supporting arm 23. Then, the controller 26 calculates the amount of tip displacement of the guide roller support arm 23 from the output signal of the sensor 28 obtained via the wiring 29, and controls the magnitude of the current flowing to the electromagnets 24 and 25 based on the result.

When the elastic constant for elastically supporting the car frame 8 in the horizontal direction with respect to the guide rail 2 is used in a state of "large", the tip displacement of the guide roller support arm 23 and the guide roller biasing force are used. The relationship may be a straight line L1 having a large inclination shown in FIG. That is, the straight line L1
At the points a and d above, the magnitude of the current supplied to the electromagnets 24 and 25 in order to generate the corresponding biasing force is "small". Further, at the points b and c, the magnitude of the current supplied to the electromagnets 24 and 25 to generate the corresponding biasing force is set to "medium". Then, at the midpoint between the points b and c on the straight line L1, the magnitude of the current flowing through the electromagnets 24 and 25 is made larger than “medium”.

Similarly, when the elastic constant is used in a "small" state, at the points e and h on the straight line L2 having a small inclination shown in FIG. 4, the magnitude of the current flowing through the electromagnets 24 and 25 is large. Is set to be “small”, the magnitude of the current is set to “medium” at the points f and g, and the magnitude of the current is set to be larger than “medium” at the intermediate point between the points f and g.

As is clear from the above description, the guide roller supporting device 20 of the first embodiment is provided with the controller 27.
The value of the elastic constant for elastically supporting the car frame 8 in the horizontal direction with respect to the guide rail 2 can be set to an arbitrary value by controlling the magnitude of the current flowing to the electromagnets 24 and 25 using. Not only that, but the elastic constant can be changed instantaneously. Therefore, by controlling the elastic constant to an optimum value according to the ascending / descending state of the car frame 8, for example, by changing the elastic constant according to the ascending / descending speed of the car frame 8, the vibration force transmitted to the car frame 8 is reduced. It is possible to improve the riding comfort.

Next, an example of how to select the optimum elastic constant will be described. Elevators have travel patterns such as stop, acceleration, ascent and descent at constant speed, deceleration, and stop. Therefore, the elastic constant is set to "large" until the car frame 8 starts accelerating from the stopped state and its ascending / descending speed gradually increases to the speed Vb shown in FIG. When the ascending / descending speed of the car frame 8 further increases to reach the speed Vb,
The elastic constant is switched to "small" and this state is maintained until a steady speed is reached. The elastic constant is "small" until the ascending / descending speed of the car frame 8 gradually decreases from the steady speed and reaches Vb.
Leave as it is. Then, when the ascending / descending speed reaches Vb, the elastic constant is switched to "large", and the state is maintained until the car frame 8 stops thereafter.

As a result, as shown in FIG. 9, the car frame 8
The excitation force transmitted to the point changes from the point a to the point b in FIG. 9 along the graph indicated by the dotted line, and between the points b and c changes along the graph indicated by the solid line. Therefore, the exciting force transmitted to the car frame 8 can be significantly reduced and the riding comfort can be improved.

That is, in the guide roller supporting device 20 of the first embodiment, the urging force for urging the guide roller 10 toward the guide rail 2 is generated by the electromagnetic repulsive force generated between the electromagnets 24 and 25. , Electromagnet 2
By controlling the value of the electric current flowing through 4/25 using the controller 27, the magnitude of the urging force, that is, the car frame 8
The value of the elastic constant that elastically supports the guide rail 2 in the horizontal direction can be optimized. Therefore, according to the guide roller supporting device 20 of the first embodiment, the car frame 8
The exciting force transmitted to the vehicle can be reduced, and the riding comfort can be significantly improved.

Second Embodiment Next, with reference to FIGS. 5 and 6, an elevator guide roller support device 30 according to a second embodiment of the present invention will be described. As described above, when the eccentric load W acts on the car frame 8 of the elevator, the guide rail reaction force F generated by the eccentric load W acts on the guide roller 10. Therefore, in order to prevent the guide roller 10 from being largely displaced by the guide rail reaction force F, the guide rail reaction force F
The guide roller 10 must be biased with a biasing force C that balances with. In this case, in the guide roller supporting device 20 of the first embodiment described above, the electromagnetic repulsive force generated between the electromagnets 24 and 25 must be strengthened when the eccentric load W becomes large, and the car frame 8 faces the guide rails 2. There is a possibility that the elastic constant for elastically supporting in the horizontal direction cannot be set to an optimum value.

In order to solve the above problem, in the guide roller supporting device 30 of the second embodiment, the guide roller supporting device 20 of the first embodiment is provided with the third and fourth electromagnets 31 and 32, and the third and fourth electromagnets 31 and 32. A controller 33 for individually controlling the magnitudes of the currents that flow to the first and second electromagnets 24 and 25 and the third and fourth electromagnets 31 and 32 is newly added. And the third and fourth electromagnets 3
1 and 32 are configured to generate only the biasing force C that balances the guide rail reaction force F generated by the unbalanced load W. On the other hand, the first and second electromagnets 24 and 25 are
A biasing force D for elastically supporting the car frame 8 horizontally with respect to the guide rail 2 is generated.

It has been found that the magnitude of the unbalanced load W changes as shown in FIG. 10 depending on the raising / lowering position of the car frame 8 in the hoistway 1. Therefore, in the second embodiment, the magnitude of the guide rail reaction force F generated by the eccentric load W is stored in the storage means built in the controller 33 in a state corresponding to the ascending / descending position of the car frame 8. ing. The controller 33 reads out the magnitude of the guide rail reaction force F from the storage means on the basis of a signal obtained from a means (not shown) for detecting the ascending / descending position of the car frame 8, and an electromagnetic wave balanced with the guide rail reaction force F. The magnitude of the current flowing through the third and fourth electromagnets 31 and 32 is controlled so as to generate repulsive force.

However, the third and fourth electromagnets 31
The electromagnetic repulsive force generated between the third and third electromagnets 31
・ Changes in inverse proportion to the square of the gap between 32. Therefore, the controller 33 controls the guide roller support arm 23
From the signal obtained from the sensor 28 provided in
And the size of the gap between the fourth electromagnets 31 and 32 is calculated,
Based on the calculation result, the third and fourth electromagnets 31 and 32
Controls the magnitude of the current that is applied to the. As a result, FIG.
As shown in, the electromagnetic repulsive force is generated by the third and fourth electromagnets 31.
It can be controlled so that it does not change depending on the size of the gap between the 32. Therefore, the urging force C for urging the guide roller 10 by the third and fourth electromagnets 31 and 32 is not affected by the displacement amount of the guide roller 10. Instead, it can be balanced with the guide rail reaction force F.

According to the guide roller supporting device 30 of the second embodiment, the guide roller 10 includes the third and fourth electromagnets 31.
The urging force C generated by 32 is urged toward the guide rail 2 so as to balance with the guide rail reaction force F. As a result, the guide roller 10 is not forcibly displaced by the guide rail reaction force F. Since the guide rail reaction force F and the urging force C are balanced, the guide roller 10 can be freely displaced in the horizontal direction.
As a result, the guide roller 10 causes the guide rail 2 to move by the biasing force D generated by the first and second electromagnets 24 and 25.
The car frame 8 is elastically supported in the horizontal direction with respect to the guide rails 2. Then, as described in the first embodiment, by controlling the magnitude of the electromagnetic repulsive force D that urges the guide roller 10, the elastic constant for elastically supporting the car frame 8 in the horizontal direction with respect to the guide rail 2 is optimized. It can be set to any value.

Therefore, according to the guide roller supporting device 30 of the second embodiment, the car frame 8 is elastically supported in the horizontal direction with respect to the guide rail 2 regardless of the size of the eccentric load W acting on the car frame 8. Since the elastic constant to be set can be set to an optimum value, the exciting force transmitted to the car frame 8 can be reduced and the riding comfort can be significantly improved.

Embodiment 3 By the way, the deflection of the guide rail 2 is not constant from top to bottom, and there are portions where the deflection is large and portions where it is small. Then, when the car frame 8 passes through a place where the guide rail 2 is largely bent, the car frame 8 receives a large vibration force. Therefore, the deflection amount of the guide rail 2 is measured in advance, and the urging force C for urging the guide roller 10 toward the guide rail 2 is weakened only at the moment when the guide roller 10 passes through a portion having a large deflection amount. By doing so, the vibration force received by the car frame 8 can be reduced.

Therefore, in the third embodiment, the bending amount of the guide rail 2 at each position in the ascending / descending direction is stored in the storage means incorporated in the controller 33 of the guide roller supporting device 30 of the second embodiment shown in FIG. It is stored as a map. Then, the controller 33 is input with data indicating the ascending / descending position and the ascending / descending speed of the car frame 8 measured by a sensor (not shown). The controller 33 has a cage frame 8
The car frame 8 is obtained by checking the information indicating the ascending / descending position of the car and the bending amount of the guide rail 2 stored in the storage means.
It can be known in advance that is passing through a portion of the guide rail 2 where the bending is large. Then, the controller 33
Before the car frame 8 passes through the portion of the guide rail 2 where the bending is large, the value of the current flowing through the electromagnets 24 and 25 is controlled, and the biasing force that biases the guide roller 10 toward the guide rail 2 is reduced. At this time, the amount of reducing the urging force is determined in consideration of the ascending / descending speed of the car frame 8.

That is, according to the guide roller supporting device of the third embodiment, the elastic constant for elastically supporting the car frame 8 in the horizontal direction with respect to the guide rail 2 is determined by the bending amount of the guide rail 2 and the car frame 8. Since it can be controlled according to the ascending / descending position and the ascending / descending speed, the exciting force transmitted to the car frame 8 can be minimized and the riding comfort can be improved.

Embodiment 4 As shown in FIG. 7, the guide roller supporting device 40 of the embodiment 4 according to the present invention is similar to the guide roller supporting device 11 of the prior art shown in FIG. This is a combination of the third and fourth electromagnets 31 and 32 and the controller 33 included in the device 30.

The third and fourth electromagnets 31 and 32 and the controller 33 are the guide roller supporting device 30 of the second embodiment.
Performs the same action as in. That is, the guide roller 10 is biased by the biasing force C generated by the third and fourth electromagnets 31 and 32. At this time, since the urging force C balances with the guide rail reaction force F generated by the unbalanced load W, the guide roller 10 is not forcibly displaced so as to compress the coil spring 16 with the guide rail reaction force F.

Therefore, regardless of the magnitude of the guide rail reaction force F, a coil spring 16 having a low spring constant can be used. As a result, according to the guide roller supporting device 40 of the fourth embodiment, the resonance frequency can be sufficiently separated from the vibration force received by the car frame 8 when the car frame 8 moves up and down at a high speed. The driving force transmitted to the frame 8 can be reduced to improve the riding comfort.

Although the guide roller supporting device for an elevator according to the present invention has been described above with reference to the first to fourth embodiments, the present invention is not limited to the above-described embodiments, and various modifications are possible based on the gist of the present invention. Needless to say, it is possible to change. For example, in the embodiment described above, a pair of electromagnets facing each other is provided as a means for urging the guide roller, and the guide roller is urged by the electromagnetic repulsive force generated between the electromagnets. However, it is not necessary to be restricted to this, for example, one of the electromagnets can be changed to a permanent magnet. Further, the guide roller may be biased by using an electromagnetic attraction force. Furthermore, it is easy for experts in this field to use a drive means such as a linear motor instead of the electromagnet.

[0040]

As is apparent from the above description, the guide roller supporting device for an elevator according to the present invention urges the guide roller toward the guide rail by the electromagnetic force, so that the strength of the electromagnetic force can be adjusted. With this, it is possible to change the value of the elastic constant that elastically supports the lifting portion of the elevator with respect to the guide rail. Therefore, the elastic constants corresponding to the changes in the elevator ascending / descending speed, the magnitude of the bending of the guide rail at each position in the ascending / descending direction, or the magnitude of the eccentric load acting to incline the elevator ascending / descending portion, etc. By controlling to the optimum value,
By rotating the guide rollers in contact with the guide rails, it is possible to reduce the magnitude of the exciting force applied to the elevator ascending / descending portion, and it is possible to significantly improve the riding comfort of the elevator. Further, since the guide roller supporting device of the present invention does not detect the vibration of the ascending / descending portion to perform active control of the elastic constant, the structure is simple and the manufacturing cost can be reduced.

[Brief description of drawings]

FIG. 1 is a side view schematically showing the structure of an elevator including a guide roller supporting device according to a first embodiment of the present invention.

2 is an enlarged side view of the guide roller supporting device shown in FIG.

FIG. 3 is a graph showing the relationship between the amount of gap between electromagnets and electromagnetic repulsive force.

FIG. 4 is a graph showing the relationship between the displacement of the guide roller and the reaction force of the coil spring.

FIG. 5 is an enlarged side view of the guide roller support device according to the second embodiment.

FIG. 6 is a graph showing the relationship between the amount of gap between electromagnets and electromagnetic repulsive force.

FIG. 7 is an enlarged side view showing a guide roller supporting device according to a third embodiment.

FIG. 8 is a side view schematically showing the structure of an elevator including a conventional guide roller supporting device.

FIG. 9 is a graph showing the relationship between the ascending / descending speed of the car frame and the vibration force received by the car frame.

FIG. 10 is a graph showing changes in the magnitude of an eccentric load that acts on the car frame.

[Explanation of symbols]

 1 Elevator Lifting Part 2 Guide Rail 3 Bracket 4 Hoistway 5 Wall Surface 6 Car Room 7 Hanging Rope 8 Car Frame 9 Anti-vibration Rubber 10 Guide Roller 11 Guide Roller Support Device 14 Guide Roller Support Arm 16 Coil Spring 17 Stopper 20 Example 1 Guide roller supporting device 24 first electromagnet 25 second electromagnet 26 wiring 27 controller 28 sensor 29 wiring 30 guide roller supporting device 31 of the second embodiment 31 third electromagnet 32 fourth electromagnet 33 controller 34 wiring 40 embodiment 4 Guide roller support device W Unbalanced load F, F1, F2 Guide rail reaction force C Energizing force balanced with guide rail reaction force D Guide roller energizing force

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor's view An Hiroshi Anzai No. 1 Toshiba-cho, Fuchu-shi, Tokyo Inside Toshiba Fuchu factory (72) Inventor Hideya Obara No. 1 Toshiba-cho, Fuchu-shi, Tokyo Toshiba Corporation Fuchu Factory

Claims (5)

[Claims] 1. A guide roller supporting device attached to an elevating part of an elevator, which supports a guide roller rotating while contacting a guide rail for guiding the elevating and lowering of an elevator, wherein the guide roller is rotatable and can be moved relative to the elevating part. And a biasing unit that is interposed between the guide roller and the elevating portion and biases the guide roller toward the guide rail. A guide roller supporting device for an elevator, characterized in that means is adapted to urge the guide roller by an electromagnetic force. 2. A second urging means for urging the guide roller toward the guide rail by an electromagnetic force is provided, and the second urging means acts to incline the elevating portion. 2. The guide roller supporting device for an elevator according to claim 1, wherein an urging force generated by an unbalanced load and balanced with a reaction force acting on the guide roller is generated. 3. A control means for controlling the magnitude of the electromagnetic force, and an ascending / descending speed detecting means for detecting an ascending / descending speed of the ascending / descending portion, wherein the control means obtains information obtained from the ascending / descending speed detecting means. The guide roller supporting device for an elevator according to claim 1, wherein the magnitude of the electromagnetic force is controlled based on the above. 4. A storage means for storing the magnitude of deflection at each position of the guide rail in the ascending / descending direction, and an ascending / descending position detecting means for detecting an ascending / descending position of the ascending / descending portion, and the control means comprises: 4. The magnitude of the electromagnetic force is controlled by comparing the deflection data stored in the storage means with the ascending / descending position information obtained from the ascending / descending position detecting means. Elevator guide roller support device. 5. A guide roller supporting device attached to an elevating part of an elevator, which supports a guide roller rotating while being in contact with a guide rail for guiding the elevating and lowering of an elevator, wherein the guide roller is rotatable and can be moved relative to the elevating part. And a first supporting means for supporting the guide roller toward the guide rail by an elastic reaction force of an elastic member which is interposed between the guide roller and the elevating part. Urging means, and second urging means for urging the guide roller by an electromagnetic force so as to balance with a reaction force generated by an unbalanced load acting to incline the elevating portion and acting on the guide roller. An elevator guide roller support device comprising: