JPS6364386B2

JPS6364386B2 -

Info

Publication number: JPS6364386B2
Application number: JP55144669A
Authority: JP
Priority date: 1980-10-16
Filing date: 1980-10-16
Publication date: 1988-12-12
Also published as: JPS5767489A

Description

[Detailed description of the invention]

この発明は建物のエレベータ昇降路上端等の機
械室に設置されるエレベータ巻上装置に関する。従来のエレベータ巻上装置を第１図により述べ
ると、図中１は建物の機械室床、１ａは床１上に
設置された建築支持体、２は支持体１ａ上に架設
された型鋼等の鋼材製梁、３は梁２上に配設され
た防振ゴム等からなる防振体、４は下部に巻上機
台４ａを有する巻上機で、上記防振体３上に支持
されている。５は巻上機４に巻装されてエレベー
タ乗りかごとつり合いおもり（図示せず）とを吊
持する主索である。こうした構成のものでは、巻上機４に生じる振
動が防振体３によつて吸振されて、建物に伝わる
振動が減少するようになるが、しかし例えばサイ
リスタ制御方式で制御される電動機を備えた巻上
機４を用いている場合は、その巻上機４に生じる
主な振動周波数に対し梁２の機械インピーダンス
が小さく、制振作用の不足で建物の居室にエレベ
ータの振動騒音が発生して不快な状態となること
があつた。これに対して、最近では特開昭53−124843号公
報に見られるようなものが考えられて来た。これ
は第２図に示す如く梁２と防振体３の間にさらに
防振体６と制振塊体７を介在させた構成で、上記
第１図のものより吸振性の向上が図れるようにな
るが、その公報中に記述してある如く制振塊体７
の重量を、巻上機４の重量（約800Kg）の約1/2の
400Kg程度とする必要がある。この為に巻上装置
全体としては重量が巻上機４の1.5倍（1200Kg）
以上にもなつてしまう問題があつた。この発明は上記事情に鑑みなされ、巻上機に発
生する振動の建物への伝播を非常に軽量な制振塊
体で防止できて、装置全体の軽量化が図れるエレ
ベータ巻上装置を提供することを目的とする。つまり、本発明のエレベータ巻上装置は、前記
目的を達成する為に、エレベータの機械室床上に
一対の梁を並設し、この両方の梁の各々の上面両
端寄り部にそれぞれ第１防振体を配設し、これら
各第１防振体上に個々に分離独立した制振塊体を
それぞれ設けると共に、それら各制振塊体に側方
に延出するばねとおもりとからなる動的吸振器を
それぞれ設け、更にそれら制振塊体上にそれぞれ
第２防振体を配設し、これら第２防振体上に巻上
機台を介してエレベータ巻上機を支持させた構成
で、その巻上機から発生した振動が各第２防振体
→制振塊体→第１防振体→梁を介して建物側に伝
播する際に、その途中の制振塊体のところで、動
的吸振器であるばねとおもりとの働きによる共振
周波数の応答倍率の変化から該振動を著しく吸振
できて、制振塊体を従来のものより大幅に軽量な
ものとしても建物への振動伝播を確実に防止でき
るようになる。以下、本発明の一実施例を第３図により説明す
る。なお図中前記第１図及び第２図に示したもの
と重複する構成のものには同一符号を付して説明
の簡略化を図ることにする。先ずエレベータ機械室床１上の左右一対の支持
体１ａ上にそれらと直交する状態で互いに並列し
て一対の鋼材製梁２が架設され、これら両方の梁
２の各々の上面両端寄り部にそれぞれ第１防振体
６が配設され、これら各第１防振体６上に個々に
分離独立した制振塊体７Ａがそれぞれ設けられ、
更にそれら各制振塊体７Ａ上にそれぞれ第２防振
体３が配設され、これら第２防振体３上に巻上機
台４ａを介してエレベータ巻上機４が支持させて
いる。ここで、前記各第１、第２防振体６，３相
互間に介在された各々の制振塊体７Ａは、第２図
に示した従来の制振塊体７が400Kg（巻上機４の
重量800Kgの1/2）もあるのに対し、個々に12Kg程
度と言つた非常に軽量な板材より構成されて、各
制振塊体７Ａの総重量でも48Kg程度である。また
この各制振塊体７Ａにはこの側方に延出するばね
８とおもり９とからなる動的吸振器がそれぞれ設
けられている。即ち、制振塊体７Ａは第１、第２
防振体３，６相互間より両外側方へ適当長さ延出
されていて、この両側延出部が適度な曲げ剛性を
有することでばね８とされている。つまり制振塊
体７Ａにこれと一体のばね８が設けられている。
このばね８の端部におもり９が取付けられてい
る。このおもり９は12Kg程度で上記制振塊体７Ａ
と同等である。つまり本発明装置では、第２図に
示す従来装置の制振塊体７が巻上機４の約1/2、
つまり400Kg程度であるに対し、制振塊体７Ａ及
びおもり９がそれぞれ12Kg程度と云つた非常に軽
いものとされ、装置全体として非常に軽量なもの
となつている。次に、本発明の装置の制振作用について第２図
の従来装置と比較しながら説明すると、上記第３
図の本発明装置は力学モデルで示すと第４図の様
に表わせる。なお、このモデルでは説明の簡略化
のために縦方向のみの自由度について考え、さら
に減衰項については省略したものとしている。ま
た、第２図の従来装置は第５図に示す力学モデル
として表わせ、第４図の本発明装置のモデル中の
ばね８とおもり９に相当するものが無い構成であ
る。たゞしこの第５図のモデルでは第４図と同様
軽量な制振塊体７Ａを用いているものとして説明
する。ここで、図中M₃は巻上機４の質量 M₂は軽量な制振塊体７Ａの質量 M₁は梁２の質量 K₃は第２防振体のばね定数 K₂は第１防振体のばね定数 K₁は梁２の等価ばね定数 K₄はばね８のばね定数 M₄はおもり９の質量である。しかして上記第４図及び第５図の両モデルは簡
単なバネーマス系モデルであることで、汎用の振
動解折プログラムにより周波数応答を計算するこ
とができ、その各々の計算結果は第６図に示す様
になる。つまり第６図中実線は第４図の本発明装
置モデルの周波数応答で、点線は第５図の従来装
置モデルの周波数応答であり、これから明らかと
なるように実線で示す本発明装置ではばね８のば
ね定数K₄とおもりの質量M₄できまる共振周波数
The present invention relates to an elevator hoisting device installed in a machine room such as at the end of an elevator hoistway in a building. A conventional elevator hoisting device is described with reference to Fig. 1. In the figure, 1 is the floor of a machine room of a building, 1a is an architectural support installed on the floor 1, and 2 is a structure such as a shaped steel installed on the support 1a. A steel beam, 3 a vibration isolator made of anti-vibration rubber etc. arranged on the beam 2, 4 a hoisting machine having a hoisting machine stand 4a at the bottom, supported on the vibration isolator 3. There is. A main rope 5 is wound around the hoist 4 and suspends the elevator car and a counterweight (not shown). With such a configuration, the vibration generated in the hoisting machine 4 is absorbed by the vibration isolator 3, and the vibration transmitted to the building is reduced. When the hoisting machine 4 is used, the mechanical impedance of the beam 2 is small relative to the main vibration frequency generated in the hoisting machine 4, and vibration noise of the elevator is generated in the rooms of the building due to insufficient vibration damping. There were times when I was in an uncomfortable situation. In contrast, recently, a method such as that shown in Japanese Patent Application Laid-Open No. 124843/1983 has been considered. As shown in Fig. 2, this has a structure in which a vibration isolator 6 and a damping block 7 are further interposed between the beam 2 and the vibration isolator 3, and it is possible to improve the vibration absorption performance compared to the structure shown in Fig. 1 above. However, as described in the publication, the damping mass 7
The weight of hoist 4 is approximately 1/2 of the weight of hoist 4 (approximately 800Kg).
It needs to be around 400Kg. Therefore, the weight of the entire hoisting device is 1.5 times that of hoisting machine 4 (1200Kg)
There were more problems than I mentioned above. The present invention was made in view of the above circumstances, and an object of the present invention is to provide an elevator hoisting device that can prevent the vibrations generated in the hoisting machine from propagating to a building using a very lightweight vibration damping mass, and can reduce the weight of the entire device. With the goal. In other words, in order to achieve the above object, the elevator hoisting device of the present invention has a pair of beams arranged side by side on the floor of the machine room of the elevator, and a first vibration isolator is installed at the upper surface of each beam near both ends. A vibration damping block is provided on each of the first vibration isolators, and separate and independent vibration damping blocks are provided on each of the first vibration isolators. A structure in which a vibration absorber is provided respectively, a second vibration isolator is disposed on each of the vibration damping masses, and an elevator hoisting machine is supported on these second vibration isolators via a hoisting machine stand. When the vibration generated from the hoisting machine propagates to the building side via each second vibration isolator → damping mass → first vibration isolator → beam, at the vibration damping mass on the way, The vibration can be significantly absorbed due to the change in the response magnification of the resonance frequency due to the action of the spring and weight, which are dynamic vibration absorbers, and even if the damping mass is made significantly lighter than conventional ones, the vibration propagation to the building can be prevented. can be reliably prevented. An embodiment of the present invention will be described below with reference to FIG. Components in the figure that are the same as those shown in FIGS. 1 and 2 are given the same reference numerals to simplify the explanation. First, a pair of steel beams 2 are installed in parallel to each other on a pair of left and right supports 1a on the elevator machine room floor 1 in a state perpendicular to them. A first vibration isolator 6 is provided, and separate and independent vibration damping masses 7A are provided on each of the first vibration isolators 6,
Further, second vibration isolators 3 are disposed on each of the vibration damping masses 7A, and the elevator hoist 4 is supported on these second vibration isolators 3 via a hoist stand 4a. Here, each vibration damping mass 7A interposed between the first and second vibration isolators 6 and 3 is different from the conventional vibration damping mass 7 shown in FIG. The weight of each damping mass 7A is 1/2 of the 800Kg of the damping mass 7A), whereas the total weight of each vibration damping block 7A is about 48Kg. Further, each vibration damping block 7A is provided with a dynamic vibration absorber consisting of a spring 8 and a weight 9 extending laterally. That is, the damping mass 7A has the first and second
The vibration isolators 3 and 6 extend outwardly by an appropriate length from each other, and these extending portions on both sides have appropriate bending rigidity to form a spring 8. In other words, the damping mass 7A is provided with a spring 8 integral therewith.
A weight 9 is attached to the end of this spring 8. This weight 9 is about 12 kg and is the vibration damping mass 7A.
is equivalent to In other words, in the device of the present invention, the damping mass 7 of the conventional device shown in FIG.
In other words, the vibration damping mass 7A and the weight 9 are each about 12 kg, which is very light, whereas the vibration damping mass 7A and the weight 9 are each about 12 kg, making the device as a whole extremely lightweight. Next, the vibration damping effect of the device of the present invention will be explained by comparing it with the conventional device shown in Fig. 2.
The device of the present invention shown in the figure can be expressed as a dynamic model as shown in FIG. 4. In this model, in order to simplify the explanation, only the degree of freedom in the vertical direction is considered, and the attenuation term is omitted. Further, the conventional device shown in FIG. 2 is represented as a dynamic model shown in FIG. 5, and has a configuration in which there is no spring 8 and weight 9 in the model of the device of the present invention shown in FIG. However, in the model shown in FIG. 5, the description will be made on the assumption that a lightweight damping mass 7A is used as in FIG. 4. Here, in the figure, M ₃ is the mass of the hoisting machine 4, M ₂ is the mass of the lightweight damping mass 7A, M ₁ is the mass of the beam 2, K ₃ is the spring constant of the second vibration isolator, and K ₂ is the first damping mass. The spring constant K ₁ of the vibrating body is the equivalent spring constant K ₄ of the beam 2 , and the spring constant M ₄ is the mass of the weight 9 . However, since both the models shown in Figures 4 and 5 above are simple spring-mass models, their frequency responses can be calculated using a general-purpose vibration analysis program, and the results of each calculation are shown in Figure 6. It becomes as shown. In other words, the solid line in FIG. 6 is the frequency response of the device model of the present invention in FIG. 4, and the dotted line is the frequency response of the conventional device model in FIG. The resonance frequency determined by the spring constant K ₄ and the weight M ₄

【式】の付近で著しく応答特性が変化て、応答倍率が変わる。このことは一般にい
われる動的吸振器としてばね８及びおもり９が働
いているのであり、この応答倍率の変化から巻上
機４の振動を吸振することが可能となる。特にサ
イリスタ制御される電動機を有する巻上機４の振
動は電源周波数の整数倍を中心として著しく卓越
した周波数をもつが、この周波数に合わせて上記
ばね８とおもり９による共振周波数を設定すれ
ば、その巻上機４の振動を著しく吸振できるよう
になるのである。一方上記第５図の従来装置のモ
デル（ただし本発明装置同様軽量な制振塊体７Ａ
を使用した場合）では第６図点線で示す如く応答
特性の変化が見られず、これでは巻上機４の振動
の吸振は不可能であり、この従来装置のような構
成では前述した第２図に示す如き非常に重い制振
塊体７を使用することが必要となるのである。なお、従来一般に考えられている様な巻上機自
身にばね及びおもりを取付けると云つた動的吸振
器（図示せず）では、そのおもりの重量が巻上機
の重量の最低1/5（160Kg）以上必要となるが、本
発明の装置の如く軽い制振塊体７Ａに動的吸振器
としてばね８とおもり９を取付ける構成であれ
ば、そのおもり９は制振塊体７Ａの重量とほゞ等
しくすればよく、制振塊体７Ａ及びばね８および
９共に非常に軽量なもので十分である。また、上記おもり９はばね８に対する取付位置
を図示しないが長孔とスライド可能な締付けボル
ト等により調整可能としておくことで、吸振周波
数を各種巻上機の振動周波数に応じて簡単に調整
することができる。なお、本発明装置では、上記実施例の如くばね
８とおもり９を別体物とせずに、両者一枚の平板
（図示せず）で一体物として構成するようにして
もよく、この場合平板の質量を分布質量として考
える。この発明は以上詳した如くなしたから、軽い制
振塊体とこれに設けた軽い動的吸振器つまりばね
とおもりとにより、エレベータ巻上機の振動を確
実に吸振することができて、振動が建物へ伝わる
ことを防止し、静かな居住環境が得られるエレベ
ータ巻上装置となる。The response characteristics change significantly near [Equation], and the response magnification changes. This means that the spring 8 and the weight 9 are working as a generally known dynamic vibration absorber, and it is possible to absorb vibrations of the hoisting machine 4 from this change in response magnification. In particular, the vibration of the hoisting machine 4 having a thyristor-controlled electric motor has an extremely prominent frequency centered on an integral multiple of the power supply frequency, but if the resonance frequency of the spring 8 and weight 9 is set in accordance with this frequency, The vibration of the hoisting machine 4 can be significantly absorbed. On the other hand, the model of the conventional device shown in FIG.
), no change in response characteristics is observed as shown by the dotted line in Figure 6, and in this case it is impossible to absorb the vibrations of the hoisting machine 4. It is therefore necessary to use a very heavy damping mass 7 as shown in the figure. In addition, in a conventional dynamic vibration absorber (not shown) in which a spring and a weight are attached to the hoisting machine itself, the weight of the weight is at least 1/5 of the weight of the hoisting machine ( However, if the spring 8 and the weight 9 are attached as a dynamic vibration absorber to the light damping mass 7A as in the device of the present invention, the weight 9 will be equal to the weight of the vibration damping mass 7A. It is sufficient that the damping mass 7A and the springs 8 and 9 are both very lightweight. Further, although the mounting position of the weight 9 with respect to the spring 8 is not shown, the vibration absorption frequency can be easily adjusted according to the vibration frequency of various hoisting machines by making it adjustable using a long hole and a slideable tightening bolt. I can do it. In addition, in the device of the present invention, the spring 8 and the weight 9 may not be separate bodies as in the above embodiment, but may be constructed as an integrated body by a single flat plate (not shown); in this case, the flat plate Consider the mass of as a distributed mass. Since this invention has been made as detailed above, the vibration of the elevator hoist can be reliably absorbed by the light vibration damping block and the light dynamic vibration absorber provided therein, that is, the spring and the weight. This is an elevator hoisting device that prevents noise from being transmitted to the building and provides a quiet living environment.

[Brief explanation of drawings]

第１図はエレベータ巻上装置の従来例を示す正
面図、第２図はエレベータ巻上装置の他の異なつ
た従来例を示す正面図、第３図はこの発明の一実
施例を示す正面図、第４図は本発明装置の力学モ
デル図、第５図は第２図に示す従来装置の力学モ
デル図、第６図は第４図と第５図との両モデルの
周波数応答比較説明図である。１……機械室床、１ａ……建築支持体、２……
鋼材製の梁、３……第１防振体、４……巻上機、
４ａ……巻上機台、５……主索、６……第２防振
体、７，７Ａ……制振塊体、８……ばね、９……
おもり。 Fig. 1 is a front view showing a conventional example of an elevator hoisting device, Fig. 2 is a front view showing another different conventional example of an elevator hoisting device, and Fig. 3 is a front view showing an embodiment of the present invention. , FIG. 4 is a dynamic model diagram of the device of the present invention, FIG. 5 is a dynamic model diagram of the conventional device shown in FIG. 2, and FIG. 6 is a frequency response comparison diagram of both models in FIGS. It is. 1...Machine room floor, 1a...Architectural support, 2...
Steel beam, 3... first vibration isolator, 4... hoisting machine,
4a...Hoisting machine base, 5...Main rope, 6...Second vibration isolator, 7,7A...Vibration damping mass, 8...Spring, 9...
Weight.

Claims

[Scope of Claims] 1. A pair of beams are arranged side by side on the floor of a machine room of an elevator, and first vibration isolators are respectively arranged near both ends of the upper surface of both beams, and each of these first vibration isolators Separate and independent vibration damping masses are provided on the body, and each vibration damping mass is provided with a dynamic vibration absorber consisting of a spring and a weight extending laterally,
Furthermore, a second vibration isolator is disposed on each of the vibration damping masses, and an elevator hoisting machine is supported on the second vibration isolators via a hoisting machine stand. Hoisting device. 2. The elevator hoisting device according to claim 1, wherein the spring and weight of the dynamic vibration absorber are constituted by a single flat plate integrally extending laterally from the vibration damping mass.