JPH11139716A - Roller guide device for elevator - Google Patents

Abstract

(57) [Summary] [Problem] To provide an elevator with good ride comfort by suppressing the lateral swing of a car with a simple configuration. A guide rail provided on a hoistway, a roller of an elevator for guiding a vertical movement of a car along the rail, a supporter movably supported by the roller frame on a shaft support, and Provided between the support and the car frame,
An elastic member for urging the roller to press the guide rail via the support is provided, and the elastic member has a non-linear characteristic.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an elevator roller guide device for damping an elevator car,
In particular, the present invention relates to an elevator roller guide device suitable for reducing lateral vibration of a car.

[0002]

2. Description of the Related Art A conventional roller guide device is disclosed in JP-A-7-144.
The structure and characteristics are shown in FIG.

In FIG. 6, a roller guide device 4 is disposed at each of the upper end and the lower end of a car frame 1 of an elevator, and guides a car 3 along a guide rail 2. More specifically, referring to FIG. 5, the roller guide device 4 is provided with rollers 7 on three levers 6 each of which is pivotally supported at one end by a pin on a base 5 fixed to the car frame 1. The rollers 7 are adapted to roll on the front and both sides of the guide rail 2 (shown in FIG. 6).

[0006] A coil spring 9 is provided between the base 5 and the lever 6, and the roller 7 is urged toward the guide rail 2 by the coil spring 9.

[0005]

However, the prior art has the following problems.

Namely, the offset load in the car, the car frame 1 is inclined, the roller guide device deflection increases of 4 of the coil spring 9, the lever stopper 11 becomes a gap [delta] ₁ of upper or A section zero lever 6 Hit.

[0007] The stopper 11 prevents displacement of the lever, and is usually made of a material such as hard rubber. Therefore, vibrations caused by seams of the rails 2 and installation errors and the like pass from the rolling rollers 7 through the stoppers 11 to the levers 6, the bases 5,
Vibration is transmitted to the car via the car frame 1 as vibration. Thus, there is a problem that vibrations in the car increase and passengers feel a deterioration in riding comfort.

FIG. 7 shows the spring 9 and the stopper 11
And the roller guide pressing force. When the stopper 11 hits (δ> δ ₁ ), the support rigidity of the roller suddenly increases,
This indicates that the vibration is easily transmitted. Usually (δ <
δ ₁ ), the rigidity of the spring 9 is about 50 kg / mm, and the stopper 11
Has a rigidity of about 200 kg / mm.

An object of the present invention is to provide a roller guide device for an elevator which prevents a deterioration in riding comfort by adopting a structure in which the lever 6 does not contact the stopper 11 even when an eccentric load of the car occurs. .

[0010]

In order to achieve the above object, in the present invention, the characteristics of the coil spring 9 are made non-linear, and the spring force increases as the deflection increases. Or make the characteristic linear, arrange a plurality of them in parallel,
As the springs flexed, the levers 6 were successively applied to the plurality of springs.

That is, the coil spring 9 is set so that the rigidity increases as the deflection increases.

That is, although the deflection increases as the force acting on the coil spring increases due to the eccentric load of the car, the rigidity increases as the deflection increases, so that the force applied to the spring before the lever 6 hits the stopper 11 and the spring reaction force are increased. They meet.

The spring rigidity at the time of balancing is set lower than the rigidity of the stopper 11.

As described above, even if an eccentric load occurs, the rail 2
Vibration from the vehicle is not transmitted to the car and a good ride comfort can be secured.

[0015]

1 to 3 show an embodiment, and FIG. 4 shows the rigidity of springs 91 to 94. FIG.

FIG. 1 is a modification of the conventional example (FIG. 5) in which the portion B is changed.

In FIG. 5, the wire diameter and coil diameter of the coil spring 9 are uniform, and the spring rigidity is constant, that is, a linear spring. On the other hand, in FIG. 1, a coil spring 91 is used instead of the coil spring 9. The coil spring 91 has a uniform wire diameter but a gradually increasing coil diameter. That is, it has a non-linear spring stiffness.

This characteristic is shown by a solid line in FIG. That is,
As the deflection increases, the spring stiffness also increases. Conventionally, it had hit the deflection [delta] ₁ becomes the stopper 11 with the roller reaction force F _1, deflection even F ₁ by using the coil spring 91 does not hit the stopper at [delta] ₁ below. Further, the spring stiffness (curve inclination) at F ₁ is determined by the rigidity of the stopper 11 (δ>
smaller than the curve slope of) at [delta] _1, the riding comfort is also improved.

The deflection becomes δ ₁ for the first time at F ₂ and the lever 6 hits the stopper 11. However, by setting the load of F _{2 to} be larger than the roller reaction force generated by the normal eccentric load, the lever 11 Do not hit 6.

For example, if the spring stiffness at δ <δ ₁ ′ is 50 kg
/ Mm-70kg / mm, spring rigidity at δ = δ ₁ ′ is 100k
g / mm, spring rigidity at δ = δ ₁ is 150 kg / mm, δ
> 200 kg / mm spring rigidity at δ ₁ (rigidity of stopper)
Choose

FIG. 2 shows an example of a non-linear spring having the same coil diameter but a different wire diameter. The effects and operations are the same as described above.

FIG. 3 shows a configuration in which two linear springs are used in parallel, and a gap Gap is set between the outer spring 94 and the lever 6. Referring to FIG. 4, only the inner coil spring 93 receives the roller reaction force up to the deflection δ _{0 of the} position A corresponding to the gap, but if the deflection exceeds δ ₀ , the outer coil spring 94
Also comes into contact with the lever 6, the composite spring rigidity increases. Further flexing, strikes the stopper 11 at [delta] _1.

As an example of setting the spring stiffness, δ <δ ₀ and 50
kg / mm, 130 kg / mm at δ ₀ <δ <δ ₁ , 20 at δ ₁ <δ
0 kg / mm (the rigidity of the stopper 11) is considered.

As described above, since the roller springs 93 and 94 receive the roller reaction force due to the unbalanced load without hitting the stopper 11, it is possible to prevent a decrease in riding comfort.

[0025]

As described above, even if the roller reaction force increases due to the car bias load, the reaction force is generated by the coil springs 91 to 94, so that the lever 6 does not hit the stopper 11. Therefore, it is possible to maintain good riding comfort under an uneven load.

[Brief description of the drawings]

FIG. 1 is a configuration diagram showing a first embodiment of a roller guide device of the present invention.

FIG. 2 is a configuration diagram showing a second embodiment of the roller guide device of the present invention.

FIG. 3 is a configuration diagram showing a third embodiment of the roller guide device of the present invention.

FIG. 4 is a characteristic diagram showing a roller support spring rigidity of the roller guide device of the present invention.

FIG. 5 is a configuration diagram showing an example of a conventional roller guide device.

FIG. 6 is a configuration diagram showing a car mounting state of a conventional roller guide device and a relationship with a rail.

FIG. 7 is a characteristic diagram showing a roller support spring rigidity of a conventional roller guide device.

[Explanation of symbols]

 91, 92: Non-linear spring, 93, 94: Linear spring.

Claims (2)

[Claims] 1. A guide rail provided in a hoistway, a roller of an elevator for guiding a vertical movement of a car along the rail, and a supporter movably supported by the shaft frame to support the roller. And an elastic member provided between the support and the car frame, the elastic member urging the roller to press the guide rail through the support, the elastic member having a non-linear characteristic A roller guide device for an elevator. 2. The roller guide device according to claim 1, wherein the number of elastic members is n (n ≧ 2), and 1
A roller guide device for an elevator, wherein at least n-1 elastic members urge the roller.