JP2005132571A - Elevator apparatus - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an elevator apparatus capable of preventing vibration and noise from occurring due to resonance during stationary running. <P>SOLUTION: This elevator apparatus comprises a hoist 6 having a worm gear 6a, a car frame 3 suspended from the hoist 6 through a rope 5 by a roping method of 1:1, and a car 1 installed in the car frame 3 through vibration isolating rubbers 2. Where the vertical secondary natural frequencies are f<SB>1</SB>and f<SB>2</SB>of the vibration system of the elevator apparatus and the operating frequency of the worm gear 6a of the hoist 6 is f<SB>g</SB>, 2<SP>1/2</SP>×f1<f<SB>g</SB><0.9×f<SB>2</SB>or 1.1×f<SB>2</SB><f<SB>g</SB>. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an elevator apparatus capable of preventing vibration of a car generated due to meshing of a worm gear of a hoisting machine.

  In general, a hoisting machine of an elevator apparatus, for example, an elevator hoisting machine with a gear reducer, generates a high-frequency vibration that is an integral multiple of the vibration caused by the meshing of the worm gear (three times for a three-row worm). For this reason, this vibration propagates through the main rope of the elevator apparatus to cause vibrations and noises in the car, which makes passengers in the car uncomfortable.

  As means for preventing this, a first dead load (weight) 15 is attached to an end of the main rope 12 on the side of the car 13 as disclosed in, for example, Japanese Patent Publication No. 60-42153 shown in FIG. In addition, a method has been proposed in which a dynamic vibration absorber composed of a beam 19 and a second dead load (weight) 21 is installed so that the vibration frequency matches the vibration vibration frequency.

  In FIG. 10, an anti-vibration rubber 18 is interposed between the first dead load 15 and the upper frame 17 a of the car frame 17, and the second dead load 21 is connected to the first dead load 15 via a beam 19 and a bolt 20. Is installed. In FIG. 10, reference numeral 16 denotes a nut.

  The operation of this conventional example will be described with reference to FIGS. The elevator apparatus configured as shown in FIG. 10 can be mechanically simplified as shown in FIG. The primary and secondary natural frequencies of the car also vary depending on the rope length as shown in FIG. On the other hand, the hoisting machine worm gear meshing frequency serving as the vibration source depends on the traveling speed, that is, the rope length, as shown in FIG. If the meshing frequency of the worm gear (or an integer multiple thereof) matches the natural frequency of the car, the car vibration and the noise resulting from the car vibration increase, causing discomfort to passengers in the car. Therefore, by providing a dynamic vibration absorber having the same frequency as the natural frequency of the vibration source as shown in FIG. 10, the car vibration can be reduced as shown in FIG.

  However, in the method of attaching the dynamic vibration absorbers 19 and 20, the natural frequency of the dynamic vibration absorbers 19 and 20 gradually changes during use, and the vibration reduction effect may be reduced. Further, in order to maintain the vibration reduction effect, it is necessary to periodically adjust the dynamic vibration absorbers 19 and 20, and further attaching the dynamic vibration absorbers 19 and 20 may increase the car weight and lower the elevator operation efficiency. .

  Therefore, the present invention has been made in consideration of such points, and an object of the present invention is to provide an elevator apparatus that greatly reduces the shaking of the elevator apparatus during traveling and has a good ride comfort. .

The present invention includes a hoisting machine having a worm gear, a car frame suspended from the hoisting machine with a rope by 1: 1 roping, and a car provided on the car frame via an elastic body. When the primary and secondary natural frequencies in the vertical direction of the vibration system consisting of the body / car frame / rope are respectively f ₁ and f ₂ and the meshing frequency f _g of the worm gear of the hoist, 2 ^1/2 The elevator apparatus is characterized in that × f ₁ <f _g <0.9 × f ₂ or 1.1 × f ₂ <f _g is satisfied.

  According to the present invention, since the meshing frequency of the hoisting machine worm gear serving as the excitation source is separated from the natural frequency of the vibration system of the elevator apparatus, an increase in car vibration due to resonance can be prevented.

The present invention relates to a hoisting machine having a worm gear, a car sheave frame suspended from the hoisting machine by a rope 2: 1, a car frame provided on the car sheave frame, and an elastic body on the car frame. The primary and secondary natural frequencies of the vibration system comprising a car / elastic body / car frame / car sheave frame / rope are respectively set as f ₁ and f ₂ , and the meshing frequency of the worm gear of the hoisting machine when a ^{_{f g, 2 1/2 × f 1}} <f g <0.9 × f 2 or a elevator apparatus characterized by 1.1 × _f 2 _{<f g} is so established.

The present invention relates to a hoisting machine having a worm gear, a car sheave frame suspended from the hoisting machine by a rope 2: 1, a car frame provided on the car sheave frame via an elastic body, and a car frame. F ₁ , f ₂ , and the meshing frequency f of the worm gear of the hoisting machine, respectively. when the ^{_{g, 2 1/2 × f 1 <}} f g <0.9 × f 2 or a elevator apparatus characterized by 1.1 × _f 2 _{<f g} is so established.

  The present invention is an elevator apparatus in which an additional elastic body is provided between the car and the car frame.

  The present invention is an elevator apparatus in which a dynamic vibration absorber is provided in a car sheave frame or a car frame.

  According to the present invention, car vibration can be further reduced.

  According to the present invention, since the car vibration can be reduced even when the vibration frequency of the vibration source temporarily matches the natural frequency of the car during acceleration / deceleration traveling, an elevator apparatus with good riding comfort can be provided.

  According to the present invention, since the primary and secondary natural frequencies of the vibration system and the vibration source are separated from each other, it is possible to prevent an increase in car vibration and in-car noise due to resonance during steady running. Therefore, according to the present invention, it is possible to provide an elevator apparatus with good riding comfort.

  According to the present invention, since the primary and secondary natural frequencies of the vibration system of the elevator apparatus are separated from the vibration frequency of the excitation source, it is possible to prevent an increase in car vibration and noise due to resonance during steady running. . Therefore, according to the present invention, it is possible to provide an elevator apparatus with good riding comfort.

First Embodiment A first embodiment of the present invention will be described with reference to FIGS.

  FIG. 1 is a block diagram showing a first embodiment of a 1: 1 roping elevator apparatus according to the present invention, FIG. 2 is an explanatory view showing a vibration model of the elevator apparatus in FIG. 1, and FIGS. 3 and 4 are hoisting machines. FIG. 5 is an explanatory view showing the effect of the elevator apparatus, and FIG. 5 is an explanatory view showing the relationship between the meshing frequency of the worm gear and the natural frequency of the car.

  As shown in FIG. 1, the elevator apparatus includes a hoisting machine 6 having a worm gear 6 a, a car frame 3 suspended from the hoisting machine 6 by a main rope 5 by 1: 1 roping, and a vibration isolating rubber on the car frame 3. (Elastic body) 2 provided with a car 1. A spring 4 is interposed between the main rope 5 and the car frame 3.

  The vibration system of the elevator apparatus shown in FIG. 1 can be simplified as shown in FIG.

In FIG. 2, the primary and secondary natural frequencies in the vertical direction of the vibration system composed of such a car / anti-vibration rubber / car frame / car sheave frame / rope are respectively expressed as f ₁ , f ₂ , and hoisting machine 6. the meshing frequency of the worm gear 6a is taken as f _g, the following equation is established.

Specifically, the spring constant and the number of the anti-vibration rubbers 2 are determined so that the following equation is established, or the weight of the car 1 or the car frame 3 is adjusted.

Here, in the case of 1: 1 roping, if the influence of damping is ignored, the primary and secondary natural frequencies of the vibration system of the elevator apparatus can be approximately expressed by the following equations.

  Next, the operation of the present embodiment having such a configuration will be described.

If it is configured so that the formula (1) is established, as shown in FIG. 3, the vibration frequency of the vibration source and the natural frequency of the vibration system of the elevator apparatus do not coincide with each other during steady running, and resonance does not occur. Further, as shown in FIG. 4, the frequency of the excitation source is set to A (2 ^1/2 × f ₁ <f _g <0.9 × f ₂ ) or B (1.1 × f ₂ <f _g ). This is limited to a region where the acceleration response magnification of the vibration system is small.

Incidentally, the frequency f _g of the vibration source can the response magnification 1 below by a 2 ^1/2 times or more the natural frequency f ₁ of the first vibration system, 2-order natural frequency of the vibration system it is possible to lower the response magnification by releasing from f ₂ 10% or more.

  According to the present embodiment, as shown in FIG. 3, it does not resonate with the vibration of the vibration source of the vibration system of the elevator apparatus (meshing of the worm gear 6a of the hoisting machine 6) during steady running, and FIG. As shown in FIG. 5, the response acceleration of the vibration system can be reduced.

  4 is a diagram showing frequency response characteristics of the vibration system, and FIGS. 5A and 5B are diagrams showing acceleration waveforms of the vibration system.

  Therefore, in the elevator apparatus according to the present embodiment, the car vibration is greatly reduced as compared with the case where the dynamic vibration absorber is used. Therefore, it is possible to provide an elevator apparatus that is comfortable to ride.

  Although the car vibration during steady running can be greatly reduced by the above configuration, if a dynamic vibration absorber is installed in the car frame (not shown), the car vibration can be generated even when passing through the resonance point during acceleration / deceleration. It can be prevented from increasing.

Second Embodiment Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 6 is a block diagram showing a second embodiment of a 2: 1 roping elevator apparatus according to the present invention. In the embodiment shown in FIG. 6, the same parts as those in the first embodiment shown in FIG. 1 to FIG.

  In FIG. 6, the car 1 is fixed to the car frame 3 via a vibration isolating rubber (elastic body) 2, and the car sheave frame 8 is fixed to the car frame 3. Further, the car sheave frame 8 is suspended from the hoisting machine 6 by the main rope 5 having the spring 4 being wound around the car sheave 7 attached to the car sheave frame 8.

The vibration system of the elevator apparatus configured as described above can be mechanically simplified as shown in FIG. 2 as in the first embodiment. The primary and secondary natural frequencies in the vertical direction of the vibration system composed of such a car / anti-vibration rubber / car frame / car sheave frame / rope are respectively f ₁ and f ₂ , and the worm gear 6a of the hoisting machine 6 is meshed. The following equation is established when f _g is a high frequency.

Here, in the case of 2: 1 roping, if the influence of damping is ignored, the primary and secondary natural frequencies of the car can be approximately calculated by the following equations.

  Next, the operation of the present embodiment having such a configuration will be described.

When configured so that the above equation holds, the frequency of the excitation source and the natural frequency of the vibration system do not coincide with each other and do not resonate during steady running as shown in FIG. Moreover, as shown in FIG. 4, the frequency of the excitation source is set to A (2 ^1/2 × f ₁ <f _g <0.9 × f ₂ ) or B (1.1 × f ₂ <f _g ). It is limited to a region where the acceleration response magnification of the vibration system is small.

  As described above, according to the present embodiment, as shown in FIG. 3, the vibration system does not resonate with the vibration of the excitation source (hoisting machine worm gear meshing) during steady running, and FIGS. As shown, the response acceleration of the vibration system can be reduced.

  Therefore, in the elevator apparatus according to the present embodiment, the car vibration is greatly reduced as compared with the case where the dynamic vibration absorber is used. Therefore, it is possible to provide an elevator apparatus that is comfortable to ride.

Third Embodiment Next, a third embodiment of the present invention will be described with reference to FIGS. FIG. 7 is a block diagram showing a third embodiment of a 2: 1 roping elevator apparatus according to the present invention. In the embodiment shown in FIG. 7, the same parts as those in the first embodiment shown in FIGS.

  In FIG. 7, the car 1 is fixed to the car frame 3, and the car sheave frame 8 is attached to the car frame 3 via the vibration isolating rubber 2. The car sheave frame 8 is suspended from the hoisting machine 6 by the main rope 5 having the spring 4 being wound around the car sheave 7 attached to the car sheave frame 8.

The vibration system of the elevator apparatus configured as described above can be mechanically simplified as shown in FIG. The first and second natural frequencies in the vertical direction of such a car / car frame / anti-vibration rubber / car sheave frame / rope are f ₁ and f ₂ , respectively, and the worm gear 6a of the hoisting machine 6 is meshed. The following equation is established when f _g is a high frequency.

Here, in the case of 2: 1 roping, if the influence of damping is ignored, the primary and secondary natural frequencies of the car can be approximately calculated by the following equations.

  Next, the operation of the present embodiment having such a configuration will be described.

When configured so that the above equation holds, the frequency of the excitation source and the natural frequency of the vibration system do not coincide with each other and do not resonate during steady running as shown in FIG. Moreover, as shown in FIG. 4, the frequency of the excitation source is set to A (2 ^1/2 × f ₁ <f _g <0.9 × f ₂ ) or B (1.1 × f ₂ <f _g ). It is limited to a region where the acceleration response magnification of the vibration system is small.

  As described above, according to the present embodiment, as shown in FIG. 3, the vibration system does not resonate with the vibration of the excitation source (hoisting machine worm gear meshing) during steady running, and FIGS. As shown, the response acceleration of the vibration system can be reduced.

  Therefore, in the elevator apparatus according to the present embodiment, the car vibration is greatly reduced as compared with the case where the dynamic vibration absorber is used. Therefore, it is possible to provide an elevator apparatus that is comfortable to ride.

In FIG. 7, even when there is only one sheave, the same effect can be expected by setting the range within the formula (1) based on the natural frequency obtained by the inter-sheave distance L ₀ = 0 in the above formula. it can.

  Further, in FIG. 7, the car sheave 8 is arranged on the car 1, but the same effect can be expected even if it is arranged below the car as shown in FIG.

It is a lineblock diagram showing a 1st embodiment of an elevator apparatus by the present invention. It is explanatory drawing which shows the vibration system of the elevator apparatus by this invention. The figure which shows the natural frequency of a vibration system and a winding machine. The figure which shows the acceleration response magnification of a vibration system. The figure which shows the acceleration waveform of a vibration system. It is a block diagram which shows 2nd Embodiment of the elevator apparatus by this invention. It is a block diagram which shows 3rd Embodiment of the elevator apparatus by this invention. It is explanatory drawing which shows the vibration system of the elevator apparatus by this invention. It is a block diagram which shows the other Example of 3rd Embodiment of the elevator apparatus by this invention. It is a block diagram which shows the conventional elevator apparatus. Explanatory drawing which shows the vibration system of an elevator apparatus. The figure which shows the natural frequency of a vibration system and a winding machine. The figure which shows the acceleration response magnification of a vibration system.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Car 2 Anti-vibration rubber 3 Car frame 4 Spring 5 Main rope 6 Hoisting machine 6a Worm gear 7 Car sheave 8 Car sheave frame 12 Main rope 13 Car

Claims (5)

A hoisting machine having a worm gear;
A car frame suspended by a rope to the hoisting machine with 1: 1 roping,
Provided with a basket provided on the car frame via an elastic body,
2 ^1/2 when the primary and secondary natural frequencies of the vibration system including the car / elastic body / car frame / rope are f ₁ and f ₂ and the meshing frequency f _g of the worm gear of the hoisting machine, respectively. An elevator apparatus characterized in that × f ₁ <f _g <0.9 × f ₂ or 1.1 × f ₂ <f _g is established. A hoisting machine having a worm gear;
A car sheave frame suspended 2: 1 by a rope on a hoisting machine;
A car frame provided on the car sheave frame;
Provided with a basket provided on the car frame via an elastic body,
When the primary and secondary natural frequencies of the vibration system including the car / elastic body / car frame / carsief frame / rope are f ₁ and f ₂ , respectively, and the meshing frequency f _g of the worm gear of the hoist is 2 An elevator apparatus characterized in that ^1/2 × f ₁ <f _g <0.9 × f ₂ or 1.1 × f ₂ <f _g is established. A hoisting machine having a worm gear;
A car sheave frame suspended 2: 1 by a rope on a hoisting machine;
A car frame provided on the car sheave frame via an elastic body;
It has a car provided in the car frame,
When the primary and secondary natural frequencies of a vibration system including a car, a car frame, an elastic body, a car sheave frame, and a rope are f ₁ and f ₂ , and the meshing frequency f _g of the worm gear of the hoisting machine is 2 An elevator apparatus characterized in that ^1/2 × f ₁ <f _g <0.9 × f ₂ or 1.1 × f ₂ <f _g is established.   4. The elevator apparatus according to claim 3, wherein an additional elastic body is provided between the car and the car frame.   5. The elevator apparatus according to claim 1, wherein a dynamic vibration absorber is provided on the car sheave frame or the car frame.

Images