KR20030055143A - Shock absorber for a elevator - Google Patents

Abstract

The present invention provides a shock absorber for an elevator, in which load-displacement characteristics can be stably obtained, which can be inexpensive and miniaturized.

An elevator shock absorber (7), which is provided under a pit (6) or a cage (2) at the bottom of a hoistway (1) of an elevator and absorbs collision energy of the cage (2) or the counterweight (4). Has a plurality of flanges 7A, and a thin cylindrical portion 7B is provided between the flanges 7A, and when operating as a shock absorber 7, the thin cylindrical portion 7B is provided. A shock absorber for elevators in which a corrugation box-shaped buckling (7C or 7D) is generated in the axisymmetric mode.

Description

Shock Absorber for Elevators {SHOCK ABSORBER FOR A ELEVATOR}

The present invention relates to an elevator shock absorber installed under the pit or cage at the bottom of the hoistway of the elevator and absorbing the collision energy of the cage or counterweight.

In general, an elevator shock absorber (hereinafter referred to simply as a shock absorber) is a safety device of an elevator, and when the cage or the balance weight enters the pit without stopping at the lowest floor, it is a cushioning performance that can ensure the safety of the passenger. The performance of stopping below FIG. 1G is required. In addition, it is required that the acceleration of 2.5 G or more does not last more than 0.04 seconds. In other words, it is necessary that the shock absorber is always stable and has excellent shock absorbing performance in which large acceleration does not occur.

As a structure of a conventional shock absorber, a spring-type shock absorber is generally used in a low speed region (typically 45 to 60 m / min or less) and a hydraulic shock absorber is used in a lifting device that exceeds this low speed region, depending on the magnitude of the rated operating speed of the elevator. .

The spring shock absorber is a shock absorber that absorbs the collision energy by the elasticity of the coil spring, and the hydraulic shock absorber controls the braking force by controlling the braking force by controlling the resistance force of the oil enclosed in the cylinder by the piston entering the cylinder during the shock absorbing. It is a device that produces performance.

However, the spring-type shock absorber has a drawback in that the length of the free type is large from the problem of strength, and the hydraulic type from the structure thereof. In particular, hydraulic shock absorbers are inevitably expensive in construction.

In addition, the demand for miniaturization of the pit is increasing in recent years, and it is required to reduce the size of the shock absorber, especially the free height. Therefore, the inventors, for example, have a different application field, but use a shock absorber that buckles in the shape of a corrugation box in the axial direction as proposed in Japanese Patent Application Laid-Open No. 50-61581, which is better than conventional springs and hydraulic shock absorbers. I thought it could provide a compact and inexpensive buffer.

However, a shock absorber for an elevator is one of the important safety devices, it is important that the necessary cushioning characteristics are always obtained stably. That is, in the shock absorber using buckling, it is necessary to stably obtain the load-displacement characteristics when the load is applied in the axial direction. In particular, in order to obtain a somewhat large deformation stroke, it is necessary to obtain a regular corrugated box buckling deformation continuously.

However, in the above example, for example, Fig. 7 which is an explanatory diagram illustrating the buckling deformation when an axial load is applied to a 2 mm thick cylinder 10 without flange, and is an explanatory diagram illustrating the relationship between load and displacement. As shown in Fig. 8, when the buckling deformation proceeds, the buckling deformation irregularity caused by the initial irregularity of the cylinder 10 overlaps, and the load-displacement characteristic is disturbed. In particular, if the deformation stroke is to be lengthened, this tendency is remarkable, and the elongated cylinder 10 becomes an elongated cylinder 10. Thus, an oiler buckling occurs in which the cylinder 10 is bent in a "ku" shape, and the load decreases rapidly. There is a problem. This is caused by the stiffness in the cross section being weakened in one direction by suddenly flattening the cylindrical cross section.

Moreover, in the shock absorber for an elevator, it is important that the stroke of a shock absorber is clear. For example, if the stroke of the counterweight shock absorber is larger than the planned value, the cage connected via the rope will approach the hoist ceiling more than expected, and if not, there is a risk of collision. Usually, although some clearance value is provided in the stroke dimension of a hoistway, it is preferable that the reduction of a hoistway is increasing recently, and it does not exceed a planned value so that a buffer stroke may become. After buckling deformation occurs continuously, if there is no buckling area, suddenly a large load is applied, but the position of this inflection point varies greatly due to the irregularity of deformation due to the initial failure of the cylinder in the structure of the proposed example. It is difficult to determine clearly. In addition, a large load value is generated initially, which is undesirable because it gives an excessive acceleration to the cage during cushioning.

There is a problem that it is difficult to use the proposed proposal as it is in the shock absorber for the elevator.

An object of the present invention is to provide a shock absorber for an elevator which can obtain stable load-displacement characteristics and can be inexpensive and miniaturized.

1 is an overall configuration diagram of an elevator in which a shock absorber for an elevator, which is the object of the present invention, is used;

2 is a front view showing a shock absorber for an elevator according to an embodiment of the present invention;

3 is a table showing the dimensional relationship of the shock absorber of FIG.

4 is an explanatory diagram illustrating a relationship between a load and a displacement when the shock absorber of FIG. 2 is operated;

Fig. 5 is an explanatory diagram of a deformation shape in the case where a corrugation box-shaped buckling of two-wave axisymmetric mode is generated in a thin cylindrical portion;

Fig. 6 is an explanatory diagram of a deformation shape in the case where a corrugation box shape buckling of one wave axisymmetric mode is generated in a thin cylindrical portion;

Fig. 7 is an explanatory diagram for explaining the buckling deformation when a axial load is applied to a 2 mm thick cylinder without a flange proposed in the related art.

FIG. 8 is an explanatory diagram illustrating a relationship between a load and a displacement of the shock absorber shown in FIG. 7. FIG.

※ Explanation of sign of castle in main part of drawing

1: hoistway 2: cage

3: cage 4: rope

5: sheave 6: feet

7: shock absorber 7A: flange

7B: Thin cylindrical part 7C: Buckle shape of 2 waves

7D: 1 wave corrugation box buckling h: Thin cylindrical section height

t: thickness of thin cylindrical part

In order to achieve the above object, in the present invention, the elevator shock absorber is provided under the pit or cage at the bottom of the hoistway of the elevator, and absorbs the collision energy of the cage or the counterweight. A thin cylindrical portion is provided between the flanges and, when operated as a shock absorber, the pleated box-shaped buckling in the axisymmetric mode is generated in the thin cylindrical portion.

In this manner, the flange portion cylindrical body can be used as a shock absorber, so that a shock absorber that is cheaper and smaller than a conventional spring-type or hydraulic shock absorber can be provided, and the pit of the hoistway can be made shallow. Moreover, since it becomes very small and light compared with the past, it can be installed also under a cage or a counterweight, and the apparatus in a pit decreases and water retention improves.

EMBODIMENT OF THE INVENTION Hereinafter, the shock absorber for elevators of this invention is demonstrated based on drawing of embodiment.

Brief Description of Drawings Fig. 1 is an overall configuration diagram of an elevator in which an elevator shock absorber which is the object of the present invention is used, Fig. 2 is a front view showing an elevator shock absorber according to an embodiment of the present invention, and Fig. 3 is a dimensional relationship of the shock absorber of Fig. 2. 4 is an explanatory diagram illustrating a relationship between a load and a displacement when the shock absorber of FIG. 2 is operated. FIG. 5 is a corrugated box-shaped buckling of two-wave axisymmetric mode in a thin cylindrical portion. Fig. 6 is an explanatory diagram of deformation in the case where a corrugation box buckling of one wave axisymmetric mode is generated in a thin cylindrical portion.

In FIG. 1, 1 is a hoistway, and the cage 2 and the counterweight 3 are installed in the hoistway 1 by the rope 4, and the hoist 5 raises and lowers. 6 is a pit formed in the lower part of the hoistway 1, and the shock absorber 7 is provided in this pit 6. As shown in FIG.

FIG. 2 shows a specific configuration of the shock absorber 7, and the shock absorber 7 is composed of a plurality of flanges 7A provided at predetermined intervals, and a thin cylindrical portion 7B formed between the flanges 7A. . The total size L of the shock absorber 7, the inner diameter phi d, the thickness t of the thin cylindrical portion 7B, and the height h between the flanges 7A are as shown in FIG.

The material of the shock absorber 7 is an aluminum material, JIS A1050 annealing material, 6 steps of buckling sections are provided, and the thickness is gradually changing. In this embodiment, the thickness is made thick one by one from the upper end of the flange to the lower end. This is aimed at deforming the cylindrical portion 7B which is thin in order. The load characteristic can also be adjusted by changing the thickness. In addition, h / t at this time is set to the value of 7.2-9.0.

As is apparent from Fig. 4 showing the results of testing with the shock absorber of Fig. 2, in the shock absorber 7 of the present invention, no initial overload occurs, and a continuous stable buckling occurs, resulting in a stable load characteristic. I can see that there is. Moreover, it turns out that average load rises gradually with the change of thickness, and load characteristic can be adjusted. Thereby, the shock absorber 7 provided with the free buffer performance can be designed. In addition, it can be seen that the load-displacement characteristic increases the load rapidly as the deformation proceeds. This is because all of the thin cylindrical portions 7B are buckled, and the deformation portion disappears. This is the same state as the turn short in the spring shock absorber, and can be defined as the stroke of the shock absorber 7 with the point A in FIG. As a result, a clear stroke can be determined, and the lifting cage can be stopped within the planned value.

Fig. 5 shows a deformation in the case where the corrugation box-shaped buckling 7C in the two-axis axisymmetric mode is generated in the thin cylindrical portion 7B, and Fig. 6 shows one deformation of the thin cylindrical portion 7B. The deformation shape in the case of generating the wrinkle box shape buckling 7D in the axisymmetric mode is shown.

In addition, the relationship between the height (h) and the thickness (t) of the thin cylindrical portion when generating one wave or two waves of pleat box buckling in the thin cylindrical portion is the shape of the wrinkled box in the axisymmetric mode of one wave. 7.0 <h / t <9.8 for generating the buckling 7D, and 14.0 <h / t <22 for generating the corrugation box-shaped buckling 7C in the axis-symmetric mode of two waves. In the case of two waves, there is an advantage that the stroke δ1 for the entire length can be larger than δ2 in the case of one wave. On the other hand, in the case of one wave, as shown in Fig. 6, the expansion amount with respect to the inner diameter (Φd) is small, for example, there is an advantage that can pass the guide cylinder 8 in the center for the restraint of the shock absorber. In Fig. 6, the pleat box-shaped buckling occurs only almost outside of the thin cylindrical portion.

According to the said embodiment, since a flange part cylindrical body can be used as a shock absorber, a cheaper and smaller shock absorber can be provided compared with the conventional spring-type and hydraulic shock absorbers, and the pit of a hoistway can also be made shallow. Moreover, since it is much smaller and lighter than the conventional one, it can be installed even under a cage or a counterweight, and the water retention property is improved, such that the equipment in a pit is reduced and it is easy to secure a copper wire.

Advantageous Effects of Invention According to the present invention, it is possible to provide a shock absorber which is cheaper and smaller than a conventional spring-type and hydraulic shock absorber, and the pit of the hoistway can be made shallow. Moreover, since it becomes very small and light compared with the past, it can be installed under a cage or a counterweight, and the remarkable effect that the apparatus in a pit can be reduced and water retention can also be improved can be achieved.

Claims (6)

In the elevator shock absorber which is installed at the bottom of the elevator pit or cage of the elevator, and absorbs the collision energy of the cage or counterweight, The elevator shock absorber has a plurality of flanges, and a thin cylindrical portion is provided between the flanges, and when operating as a shock absorber, a wrinkle box-shaped buckling is generated in the thin cylindrical portion. Shock absorbers for elevators. The method of claim 1, In the case where the corrugated box-shaped buckling of one wave is generated in the thin cylindrical portion, the ratio of the thickness t of the thin cylindrical portion to the height h of the thin cylindrical portion is 7.0 <h / t <9.8 The shock absorber for the lift, characterized in that the. The method of claim 1, In the case of generating two waves of corrugation box-shaped buckling in the thin cylindrical portion, the ratio of the thickness t of the thin cylindrical portion to the height of the thin cylindrical portion h is 14 <h / t <22 The shock absorber for the lift, characterized in that the. The method according to any one of claims 1 to 3, The shock absorber for a lift, characterized in that the corrugated box-shaped buckling is in the axisymmetric mode. The method of claim 1, An elevator shock absorber characterized in that the thickness (t) is gradually thickened as the flange goes from the upper end to the lower end. The method of claim 1, And said pleat box-shaped buckling occurs only on the outer side of said thin cylindrical portion.