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翻訳をお願いします・・・翻訳ソフトだと読めません・・・

翻訳をお願いします・・・翻訳ソフトだと読めません・・・ By changing the mean diameter, the wire diameter, and the number of coils, any number of springs may be obtained to support a given load with a given deflection. However, there are certain limitations imposed by the use to which the spring is to be put. The usual procedure is to assume a mean diameter and a safe working stress, after which the wire diameter is found by substitution in the proper stress equation. The number of effective coils is the found from the deflection equation. Several trials are usually required before a suitable combination is obtained. The stress factor K depends on the spring index that must be assumed in the first trial solution for the wire diameter. For general industrial uses the spring index should be 8 to 10; for valve and clutch springs 5 is common; and 3 is a minimum value to be used only in extreme cases. Because of slight variations in the modulus of elasticity, variations in wire diameter, and other manufacturing tolerances, the deflection equations do not give extremely accurate values, and if extreme accuracy is required, the manufacturer should be consulted. Compression springs should not be compressed solid when subjected to the maximum load. A clearance between the effective coils should be provided so as to prevent wear, or to prevent a foreign substance lodging between the coils and causing a fatigue crack failure. The free length is the solid length, plus the clearance, plus the maximum deflection. The solid length depends upon the number of effective coils and the type of the end provided. Different types of ends are illustrated in Fig.3.3. Note that the effective number of coils n may be less than the actual number in the spring. A helical compression spring that is too long compared to its mean diameter may buckle at comparatively low axial loads since such a spring is a very flexible column.

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  • miraizin
  • ベストアンサー率42% (6/14)
回答No.1

平均径、ワイヤ直径、およびコイルの数を変えることによって、特定の偏向がある特定の負荷を支持するためにいろいろなスプリングを入手するかもしれません。 しかしながら、スプリングが置かれることになっている使用で設けられたある制限があります。 通例の方法は、平均径と安全な許容応力を仮定することです。(その時、ワイヤ直径は適切な応力方程式における代替で見つけられます)。 有効なコイルの数は偏向方程式から見つけることでした。 適当な組み合わせを得る前に、通常、いくつかのトライアルを必要とします。 ストレス度Kはワイヤ直径の第一審対策で想定しなければならないバネ指数によります。 一般的な工業用のために、バネ指数は、8?10であるべきです。 バルブとクラッチ・スプリングに、5は一般的です。 そして、3は、極端な場合だけに使用されるべき最小値です。 侮辱のため、ヤング率の変化、ワイヤ直径の変化、および他の製作公差、偏向方程式は非常に正確な値を与えません、そして、極限精度が必要であるなら、メーカーに相談されるべきです。 最大積載量にかけられる場合、圧縮バネは圧縮された固体であるべきではありません。 摩耗を防ぐために有効なコイルの間のクリアランスを提供するべきですか、またはコイルと引き起こすことの間で異物が宿泊するのを防ぐために、疲労は失敗を解きます。 フリー・レングスは、しっかりした長さと、クリアランスと、最大の偏向です。 しっかりした長さは有効なコイルの数と提供された終わりのタイプに頼っています。 異なったタイプの終わりは図3.3で例証されます。 コイルnの有効な数が春に実数より少ないかもしれないことに注意してください。 そのようなスプリングが非常にフレキシブルなコラムであるので、平均径と比べて、長過ぎる圧縮コイルバネは比較的低いアキシアル荷重で曲がるかもしれません    まったく意味がわかりません  一応ですが翻訳使いました

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