JP3542144B2 - Scroll type fluid machine and its processing method - Google Patents

Description

【００１２】
また、一方のスクロール部材に対応する代数螺線の指数ｋをｋ＜１．０とした代数螺線であり、他方のスクロール部材の代数螺線が一方の代数螺線を１８０°前後回転したたものであってもよい。
【００１３】
上記第２の目的を達成するために、本発明のスクロ−ル形流体機械は、端板とこれに直立している渦巻体とで形成された２つのスクロ−ル部材が渦巻体を内側に向けた状態で互いにかみ合っており、一方のスクロ−ル部材が他方のスクロ−ル部材に対して見かけ上自転しないように所定の旋回半径で公転運動するスクロ−ル形流体機械において、前記渦巻体の外側の渦曲線を外側曲線、前記渦巻体の内側の渦曲線を内側曲線としたときに、前記２つの渦巻体の渦曲線が、極座標形式で動径ｒ、偏角θ、代数螺線の係数ａ、代数螺線の指数ｋとしたとき、前記式(１)で表される代数螺線を旋回させて得られる包絡線からなり、その代数螺線の指数ｋが偏角θに対応して変化することを特徴とするものである。
【００１４】
前記代数螺線は、指数ｋをｋ＞１．０で、かつ係数ａが定数に設定されたものであり、前記代数螺線の指数ｋを偏角θの関数として変化させたものであってもよい。
【００１５】
上記第３の目的を達成するために、本発明のスクロ−ル形流体機械は、前記一方のスクロ−ル部材の代数螺線がその原点を中心として角度α回転されたものであって、他方のスクロ−ル部材の代数螺線が前記原点を中心として角度（１８０°−α）回転されたものである。
【００１６】
また、前記一方のスクロ−ル部材が旋回スクロ−ル部材であって、旋回スクロ−ル部材の渦巻体の厚さが他方のスクロ−ル部材の渦巻体の厚さより厚くしてもよい。
【００１７】
上記第４の目的を達成するために、本発明のスクロ−ル部材の加工方法は、スクロ−ル部材の渦巻体の外側曲線および内側曲線が代数螺線を旋回運動させたときの包絡線からなり、両スクロール部材のうちの一方のスクロール部材に設けられた渦巻体の外側曲線および内側曲線上に沿ってカッタの中心を移動させることにより他方のスクロール部材の渦巻体の加工を行うことを特徴とするものである。
【００１８】
【作用】
両スクロ−ルの渦巻体の形状を決めるための基本渦曲線を、極座標形式で動径ｒ、偏角θ、代数螺線の係数ａ、代数螺線の指数ｋとした数式（１）で表した代数螺線を用いているため、代数螺線の指数ｋの値を変えるだけで簡単に渦巻のピッチを変えることができる。指数ｋがｋ＞１．０の場合は、渦巻の巻き角（偏角θ）が大きくなるにしたがって渦巻のピッチは大きくなり、反対にｋ＜１．０の場合は、渦巻の巻き角（偏角θ）が大きくなるにしたがって渦巻のピッチは小さくなる。
【００１９】
また、それぞれに渦巻体を有する静止しているスクロ−ル部材と旋回するスクロ−ル部材を備えたものにおいて、両渦巻体の最内領域の当接点間に形成されるすきま容積が両渦巻体の相対的公転運動に伴い実質的に零になるように構成するとともに、それぞれの渦巻体は、代数螺線を基本渦曲線として渦巻壁の厚さが渦巻きの巻き角に応じて次第に変化する形状を有しているので、トップクリアランス小さくでき、再膨張損失を小さくでき、効率を向上させることができる。
【００２０】
また、代数螺線の指数ｋをｋ＜１．０にするか、係数ａまたは指数ｋが偏角θの関数となる代数螺線を渦巻体の基本渦曲線にすることにより渦巻壁の厚みを適宜変化させることができる。
【００２１】
前記一方のスクロ−ル部材の代数螺線がその原点を中心として角度α回転されたものであって、他方のスクロ−ル部材の代数螺線が前記原点を中心として角度（１８０°−α）回転されたものでは、角度α回転しているので、この角度αにより２つの渦巻壁の厚みを変えて形成することができ、両渦巻体の材質が異なる場合でも渦巻体の強度を確保することができる。
【００２２】
また、半径ｅ１、ｅ２が前記旋回半径ｅとｅ＝ｅ１＋ｅ２の関係を有するものであって、両スクロ−ルのそれぞれの渦巻体が、外側曲線が両スクロ−ルの代数螺線をそれぞれ半径ｅ１、ｅ２で旋回運動させたときの内側包絡線で形成され、内側曲線が両スクロ−ルの代数螺線をそれぞれ半径ｅ１、ｅ２で旋回運動させたときの外側包絡線で形成されているので、半径ｅ１、ｅ２の大小関係、値を変えることにより２つの渦巻壁の厚みを変えて形成することができ、両渦巻体の材質が異なる場合でも渦巻体の強度を確保できる。また、インボリュ−ト曲線よりも渦巻体寸法を小型化でき、流体の内部漏れを低減して性能向上が図れるスクロ−ル形流体機械を提供することができる。
【００２３】
スクロ−ル部材の渦巻体の外側曲線および内側曲線が代数螺線を旋回運動させたときの包絡線で形成されるものであって、両スクロール部材のうちの一方のスクロール部材に設けられた渦巻体の外側曲線および内側曲線に沿ってカッタの中心を移動させることにより他方のスクロール部材の渦巻体の加工を行うので、連続的に加工することができ、歯側面など寸法精度良く効率的に加工できる。
【００２４】
【実施例】
以下、本発明の第１の実施例を図１から図１０により説明する。図１は本実施例のスクロ−ル形圧縮機を適用した冷凍サイクル構成を示す図、図２は本実施例に係るスクロ−ル形流体機械のスクロ−ル形状を示す旋回スクロ−ルの平面図、図３は図２の縦断面図、図４は作動原理を示す図、図５から図８は渦巻体の形成方法の説明図、図９は渦巻体の巻き始め部形成法の説明図、図１０はカッタの軌跡を説明する図である。
【００２５】
図１に示すように、冷凍サイクルは、主としてスクロ−ル形圧縮機３０、凝縮器３１、膨張弁３２、蒸発器３３から構成されている。スクロ−ル形圧縮機３０は、それぞれ同一形状の渦巻体を有し、渦巻体の厚みが渦巻きの巻き角に応じて連続的に変化する渦巻体によって形成された旋回スクロ−ル１と固定スクロ−ル４、旋回スクロ−ル１を回転するクランク軸１３、クランク軸１３を軸支するフレ−ム１４、旋回スクロ−ル１の公転運動は許容し自転運動を防止するオルダムリング１５、クランク軸１３を駆動するモ−タ１６、吸入パイプ１７と吐出パイプ１８から構成されている。
【００２６】
このように構成されたスクロ−ル形圧縮機においては、モ−タ１６に通電することによりクランク軸１３が回転すると、旋回スクロ−ル１はオルダムリング１５により自転することなく公転運動し、作動原理として示した図４に示されるように、両スクロ−ル１、４間で冷媒の圧縮作用が行われる。圧縮された高温・高圧の冷媒は矢印のごとく吐出パイプ１８から凝縮器３１に流入し、熱交換を行って液化し、膨張弁３２で絞られて断熱膨張して低温・低圧となり、蒸発器３３により熱交換してガス化された後、吸入パイプ１７を経てスクロ−ル形圧縮機３０に吸入される。
【００２７】
図２および図３に示すように、旋回スクロ−ル１は、旋回側渦巻体２と端板３とにより形成される。旋回側渦巻体２は旋回外側曲線２ａと旋回内側曲線２ｂとによりなり、旋回スクロ−ル１の中心Ｏは、旋回外側曲線２ａと旋回内側曲線２ｂの原点である。ここで、旋回側渦巻体は、旋回外側曲線２ａを式（１）で代表される代数螺線を基本渦曲線とし、代数螺線の指数ｋをｋ＜１．０にしている。
【００２８】
【数１】

【００２９】
又、固定スクロ−ル４の渦巻体５も旋回スクロ−ル１の渦巻体２と同様に形成されている。固定側渦巻体５は固定外側曲線５ａと固定内側曲線５ｂからなり、固定スクロ−ル４の中心Ｏ´は、固定外側曲線５ａ、固定内側曲線５ｂの原点であり、固定外側曲線５ａを式（１）で表される代数螺線を原点Ｏ´を中心に１８０°回転させて基本渦曲線とし、代数螺線の係数ａ、代数螺線の指数ｋは旋回外側曲線２ａと同じ値にしている。
【００３０】
圧縮作用は以下のように行われる。固定側渦巻体５を静止し、旋回側渦巻体２を固定スクロ−ル中心Ｏ´の周りに自転することなしに旋回半径ｅ（＝ＯＯ´）で公転運動させることにより、図４に示すように旋回側渦巻体２と固定側渦巻体５の間に形成された複数の三日月状の密閉した作動室６、６が形成される。作動室６、６の容積は、図４に示すように固定スクロ−ル４の外周側に設けられた吸入ポ−トから流体の吸込みが終了した状態(１)から、９０゜、１８０゜、２７０゜と公転が進むにしたがって、(２)、(３)、(４)とその容積を縮小し、流体の圧縮作用が行われる。そして、圧縮された流体は最後に吐出ポ−ト７から吐き出される。
【００３１】
旋回側渦巻体２、固定側渦巻体５を後述のように構成することにより、渦巻体の渦巻壁の厚さｔは渦巻き始めから巻終わりにかけて連続的に変化させることができ、内部の流体の圧力が最も高圧になる渦巻体の中央部が厚く、低圧になる巻終わり部では薄く形成でき、渦巻体の渦巻壁の各部が作用する圧力に見合って一様な強度となる。渦巻壁の厚さが一定なインボリュ−ト曲線等に比べ渦巻体の容積を減らすことができ、材料費の低減、軽量化が可能となる。また、渦巻の巻き始めから一巻きほどの範囲は渦巻壁の厚さは比較的厚く構成され、流体の内部漏れを低減することができる。
【００３２】
次に、本実施例における旋回側渦巻体２と固定側渦巻体５の構成法を図５、図６、図７、図８を用いて説明する。ここでは、渦巻体の外側曲線を基本渦曲線にとった場合を例に挙げて説明する。
【００３３】
図５、図６はそれぞれ旋回側と固定側の基本渦曲線と、この基本渦曲線を旋回半径ｅで円運動させたときに描く円軌跡の包絡線を示し、図７、図８はそれぞれ旋回側と固定側の渦曲線の構成を示す。実線１０は旋回側の基本渦曲線で、式（１）で表される代数螺線である。破線１１と１２は基本渦曲線１０の包絡線で、１１が外側包絡線、１２が内側包絡線である。また、実線２０で示す固定側の基本渦曲線２０は、旋回側の基本渦曲線１０を原点Ｏの周りに１８０゜回転させたものである。破線２１と２２は基本渦曲線２０の包絡線で、２１が外側包絡線、２２が内側包絡線である。
【００３４】
ここで、渦巻体の外側曲線を基本渦曲線とするため、旋回外側曲線２ａは実線１０が選ばれ、固定外側曲線５ａは実線２０が選ばれる。渦巻体の内側曲線は、複数の密封容積を作るための両渦巻間の接触が幾何学的に保証されるように、次のように決められる。旋回内側曲線２ｂは固定外側曲線５ａと接触するため固定側の基本渦曲線２０の外側包絡線２１が選ばれ、固定内側曲線５ｂは旋回外側曲線２ａと接触するため旋回側の基本渦曲線１０の外側包絡線１１が選ばれる。
【００３５】
以上、渦巻壁の厚さが渦巻の巻き角に応じて連続的に変化する渦巻体の基本的な渦曲線構成法を説明したが、このままでは、渦巻体の巻き始めで内側曲線と外側曲線が一致してしない。巻き始め部の構成は、旋回側渦巻体２を固定側渦巻体５の周りに旋回半径ｅで公転運動させたときに両渦巻体が干渉しないという条件を満足する必要がある。そこで、この巻き始め部の構成の一例を図９により説明する。
【００３６】
図９において、点Ａは旋回外側曲線２ａの開始位置、点Ｂは旋回内側曲線２ｂの開始位置を表す。ここで点Ａの位置は、旋回側渦巻体２を固定側渦巻体５の周りに旋回半径ｅで公転運動させたときに両渦巻体が干渉しないという条件から、旋回外側曲線２ａ上で原点Ｏから旋回半径ｅの半分の距離に決められる。この点Ａが、図５から図８において、固定側の基本渦曲線２０の外側包絡線２１にあたる旋回内側曲線２ｂ上では点Ｂに相当しており、点Ａを通る旋回半径ｅを半径とする円弧は点Ｂで旋回内側曲線２ｂとなめらかに接続することになる。なお、固定側渦巻対の巻き始め部形状も前記旋回側と同様に形成される。
【００３７】
次に、このような渦巻体の製造方法を説明する。図１０は、旋回側渦巻体を形成するときのカッタ−の軌跡を示す。例えば旋回半径ｅを半径とするカッタ−（エンドミル等）を用い、固定側渦巻体５の外側曲線５ａ及び内側曲線５ｂ上をカッタ−の中心座標を移動させることにより、連続的に旋回側渦巻体２が加工されるようになり、渦巻体の寸法精度を向上して効率的に加工することができる。固定側渦巻体５を加工する場合は、反対に、旋回側渦巻体２の渦曲線である外側曲線２ａ及び内側曲線２ｂ上をカッタ−中心を移動させることにより同様に加工される。
【００３８】
以上、渦巻体の外側曲線を基本渦曲線としたときの渦巻体の形成法を説明したが、次に、渦巻体の内側曲線を基本渦曲線としたときの渦巻体の形成法について説明する。図１１、図１２はそれぞれ旋回側と固定側の渦曲線を示す。この場合は、渦巻体の内側曲線が基本渦曲線のため、旋回内側曲線２ｂは図５における実線１０が選ばれ、固定内側曲線５ｂは図６における実線２０が選ばれる。渦巻体の外側曲線は次のように決められる。旋回外側曲線２ａは固定内側曲線５ｂと接触するため図６における固定側の基本渦曲線２０の内側包絡線２２を選び、固定外側曲線５ａは旋回内側曲線２ｂと接触するため図５における旋回側の基本渦曲線１０の内側包絡線１２を選ぶことにより、複数の密封容積を作るための両渦巻間の接触が幾何学的に保証されることになる。
【００３９】
また、この時渦巻体の巻き始め部は、前述した渦巻体の外側曲線を基本渦曲線とした場合（図９）と異なり図１３のように形成される。図１３において、点Ａは旋回側渦巻体２を形成する旋回外側曲線２ａの開始位置、点Ｂは旋回内側曲線２ｂの開始位置を表す。点Ａと点Ｂの位置は、原点Ｏを中心に旋回半径ｅの半分を半径とする円を描き、この円周上の一点Ｃをとおり旋回外側曲線２ａと旋回内側線２ｂとをなめらかに結ぶ直線で接続することによって決められる。このとき、点Ｃは点Ａと点Ｂを結ぶ直線の中間点となる。以上述べたことは、旋回側渦巻体の巻き始め部の形状を説明したが、固定側渦巻体も旋回側と同様に形成される。
【００４０】
以上、渦巻壁の厚さが渦巻の巻き角に応じて連続的に変化する渦巻体の形成法を説明したが、さらに、本実施例の渦巻体では、トップクリアランス容積が零になり、トップクリアランス内流体の再膨張に伴う損失がないという従来のインボリュ−ト曲線にはない優れた特徴を有している。図１４は、図４で示した本実施例のスクロ−ル形圧縮機の作動原理図において、渦巻体中央部のかみ合い状態を説明する要部拡大図である。図に１４に示すように、旋回側渦巻体２と固定側渦巻体５の最も内側の接触点８、８´で形成される最内室６ａは、図から明らかなように、本実施例では旋回側渦巻体２が固定側渦巻体５の周りに旋回半径ｅ（＝ＯＯ´）で、相対的に公転運動を行うと、図１４の（１）、（２）、（３）、（４）の順に接触点８、８´で形成される最内室６ａの容積が減少し、従来存在していたトップクリアランス容積は零になる。このため、圧縮された流体は無駄な再膨張を起こすことなく吐出ポ−ト（図示せず）からすべて外部に吐き出されることになる。なお、図１４では省略したが、実際には最内室６ａと通じる位置に吐出ポ−トを形成する必要があるため、この吐出ポ−ト部の容積はトップクリアランス容積になるが、従来のものに比べてこの量は非常に小さく実質的に零とみなすことができる。ここでは、渦巻体の巻き始め部形成が図９で示したものについて説明したが、図１３で示した巻き始め部形成のものも、説明は省略するが同様にトップクリアランス容積は零になる。
【００４１】
このように形成されたスクロ−ル圧縮機を冷凍サイクルあるいは冷房専用のサイクルに適用しているので、渦巻体間の流体の内部漏れが低減でき、トップクリアランス容積も零になるため圧縮機の効率が大幅に向上する。これより、エネルギ効率に優れ、信頼性の高い冷凍・空調システムが得られる。
【００４２】
次に本発明の第２の実施例を図１５から図１８により説明する。第１の実施例では、渦巻体の基本渦曲線を式（１）で表される代数螺線とし、代数螺線の指数ｋをｋ＜１．０にし、代数螺線の係数ａも任意の定数とした場合を示したが、さらに、式（１）で表される代数螺線の係数ａあるいは代数螺線の指数ｋが、偏角θの関数となるような基本渦曲線にすることにより渦巻壁の厚みを適宜変化させることができ、渦巻体の強度を確保しながら、インボリュ−ト曲線よりも渦巻体を小型化できる。この場合、代数螺線の指数ｋはｋ＜１．０の範囲に限定されなくなる。この実施例を図１５、図１６を参照しながら説明する。
【００４３】
図１５および図１６は、渦巻体の基本渦曲線を式（１）で表される代数螺線とし、代数螺線の指数ｋをｋ＞１．０の定数にし、代数螺線の係数ａも定数とした場合のスクロ−ル形状を示し、図１５は旋回スクロ−ル、図１６は圧縮機として用いた場合の吸い込み終了（圧縮開始）時の渦巻体の構成を示す。図１７および図１８は、図１５および図１６と同様、代数螺線の指数ｋをｋ＞１．０にし、代数螺線の係数ａも図１４および図１５と同じ定数値だが、指数ｋが偏角θの関数で表される代数螺線を基本渦曲線にした場合のスクロ−ル形状を示している。具体的には指数ｋは偏角θの一次関数で、巻き始めから巻き終わりにかけて直線的にｋの値が減少するようになっている。図１６および図１８を比較して見ると明らかなように、代数螺線の指数ｋをｋ＞１．０の定数とした図１５および図１６では、渦巻壁の厚さは渦巻の中央部（巻き始め）にいくほど薄くなり強度上問題になりやすいが圧力差が小さい場合に適用できる。反対に渦巻の外周に至るほど渦巻壁の厚さは厚くなるため外形を一定にした場合最外周の作動室６、６の容積（行程容積）は小さくなる。これに対し、代数螺線の指数ｋを渦巻の巻き角によって変化させた図１７および図１８では、指数ｋはｋ＞１．０だが、巻き始め部の渦巻壁の厚さは強度が問題にならない程度に確保され、渦巻の外周では代数螺線の指数ｋがｋ＜１．０の場合と同様に巻き終わり部にいくほど渦巻壁の厚さは薄くなって行程容積は増加している。詳しい数値解析を行った結果、外形（渦巻の径と高さ）を一定とすると、図１７および図１８に示す渦巻体は図１５および図１６に示す渦巻体に比べ行程容積が約３割増加し、内部容積比も前者の２．７１から後者の２．８０と大きくなっていることがわかった。従って、行程容積と内部容積比を一定にした場合には、図１７および図１８に示す渦巻体の方が、渦巻体を小型化できることになる。ここでは、指数ｋが偏角θの一次関数で変化する場合を示したが、偏角θの二次、三次関数あるいは対数関数で与えてもよい。あるいは、指数ｋを常数とし、代数螺線の係数ａを偏角θの関数で変化するようにしても同様に渦巻壁の厚みを適宜変化させることができ、渦巻体の強度を確保しながら、インボリュ−ト曲線よりも渦巻体を小型化でき、流体の内部漏れを低減して性能向上となるスクロ−ル形圧縮機を得ることができる。
【００４４】
本発明の第３の実施例を図１９から図３０により説明する。図１９はスクロ−ルを組み合わせた状態を示す平面図、図２０は作動原理を説明する図、図２１から図２４はスクロ−ル形状の形成方法を説明する図、図２５は旋回スクロ−ルの巻き始め部の構成を示す平面図、図２６は固定スクロ−ルの巻き始め部の構成を示す平面図、図２７から図２９は角度αを設けた場合のスクロ−ルの形状変化を示す平面図、図３０は渦巻体中央部のかみ合い状態を示す平面図、図３１は渦巻体中央部のかみ合い状態を示す平面図である。
【００４５】
本実施例のスクロ−ル形状は第１の実施例に示すスクロ−ル形状と同様に形成されるが、本実施例では、旋回スクロ−ルと固定スクロ−ルとは材質が異なるように形成されており、例えば、旋回スクロ−ルはアルミ合金等の軽量・低強度材料、固定スクロ−ルは、旋回スクロ−ルよりも強度の高い通常の鉄系材料で構成されている。本実施例のように、低強度材料からなる旋回側渦巻体２は、より強度の高い固定側渦巻体５に比べて全体的に渦巻壁の厚さが厚く構成され、両者ほぼ等しい強度となるように設定されるが、旋回スクロ−ルおよび固定スクロ−ルの渦巻体の外側曲線と内側曲線、渦巻曲線の原点Ｏ、Ｏ´および代数螺線の指数ｋは第１の実施例と同様に設定されている。
【００４６】
しかし、旋回側渦巻体２の構成は、旋回外側曲線２ａを式（１）で表される代数螺線を渦巻壁の厚さをより厚くするために、後述するように原点Ｏを中心に角度αだけ回転させて基本渦曲線としている。これより、旋回側渦巻体２及び固定側渦巻体５の渦巻壁の厚みはともに渦巻の巻き始めから巻き終わりにかけて連続的に変化しており、内部の流体の圧力が最も高圧になる渦巻体の中央部が厚く、低圧になる巻き終わり部では薄くなっており、渦巻壁の厚さが一定なインボリュ−ト曲線等に比べ渦巻体の容積を減らすことができ、材料費の低減、軽量化が可能となるとともに、渦巻の巻き始めから一巻きほどの範囲は渦巻壁の厚さは比較的厚く構成され、流体の内部漏れを低減することができる。また、低強度材料からなる旋回側渦巻体２は、より強度の高い固定側渦巻体５に比べて全体的に渦巻壁の厚さが厚く構成され、両者ほぼ等しい強度となる。
【００４７】
作動原理は、第１の実施例と同様図２０に示すように、固定側渦巻体５を静止し、旋回側渦巻体２を固定スクロ−ル中心Ｏ´の周りに自転することなしに旋回半径ｅ（＝ＯＯ´）で公転運動させることにより、２つの渦巻体２、５間に複数の三日月状の密閉した空間、作動室６、６が形成され、作動室６、６の容積が、流体の吸込みが終了した状態(１)から、９０゜、１８０゜、２７０゜と公転が進むにしたがって、(２)、(３)、(４)とその容積を縮小し、流体の圧縮作用が行われる。
【００４８】
次に、本実施例における旋回側渦巻体２と固定側渦巻体５の形成法を渦巻体の外側曲線を基本渦曲線にとった場合を例に挙げて詳述する。図２１、図２２はそれぞれ旋回側と固定側の基本渦曲線と、この基本渦曲線を旋回半径ｅで円運動させたときに描く円軌跡の包絡線を示し、図２３、図２４はそれぞれ旋回側と固定側の渦曲線の構成を示す。実線１０は旋回側の基本渦曲線で、式（１）で表される代数螺線を原点Ｏを中心として角度αだけ回転したものである。破線１１と１２は基本渦曲線１０の包絡線で、１１が外側包絡線、１２が内側包絡線である。
【００４９】
また、実線２０は固定側の基本渦曲線で、この曲線は旋回側の基本渦曲線１０を原点Ｏの周りに（１８０゜−α）回転させたものである。破線２１と２２は基本渦曲線２０の包絡線で、２１が外側包絡線、２２が内側包絡線である。第１の実施例と同様に、渦巻体の外側曲線が基本渦曲線のため、旋回外側曲線２ａは実線１０が選ばれ、固定外側曲線５ａは実線２０が選ばれ、渦巻体の内側曲線は、複数の密封容積を作るための両渦巻間の接触が幾何学的に保証されるように、次のように決められる。又、旋回内側曲線２ｂは固定外側曲線５ａと接触するため固定側の基本渦曲線２０の外側包絡線２１が選ばれ、固定内側曲線５ｂは旋回外側曲線２ａと接触するため固定側の基本渦曲線１０の外側包絡線１１が選ばれる。
【００５０】
ここで、一点鎖線で示した旋回外側曲線２ａ′及び固定内側曲線５ｂ′は角度αが０°の場合であり、第１の実施例に相当する場合であるが、本実施例の場合は、旋回側の基本渦曲線１０と固定側の基本渦曲線２０とは同一形状で位相が（１８０°−α）ずれているため、位相差がちょうど１８０°となる第１の実施例に示したスクロ−ル形状と異なり、固定側と旋回側で渦巻壁の厚みを変化することができる。又、渦巻体の巻き始めで内側曲線と外側曲線が一致してしないため、この巻き始め部は第１の実施例と同様に、一例として図２５、図２６に示したように決められる。図２５は、旋回側渦巻体２において基本渦曲線である旋回外側曲線２ａを回転（角度α）させたときの巻き始め部の構成を示し、図２６は、この旋回側渦巻体２にかみ合う固定側渦巻体５の巻き始め部の構成を示す。図中の渦曲線において、実線が回転しない場合（α＝０°）、破線は実線の旋回外側曲線２ａを原点Ｏを中心として時計方向（以下、正方向とする）に角度α回転した場合で、一点鎖線は反時計方向（以下、負方向とする）に角度−α回転した場合である。このように、式（１）で表される代数螺線からなる旋回外側曲線２ａ（実線）を角度α回転させることにより旋回側渦巻体２の渦巻壁の厚さは厚くなり、固定側渦巻体５の渦巻壁の厚さは薄くなる。又、逆に角度−α回転した場合には旋回側渦巻体２の渦巻壁の厚さは薄くなり、固定側渦巻体５の渦巻壁の厚さは厚くなる。
【００５１】
巻き始め部の構成は、旋回側渦巻体２を固定側渦巻体５の周りに旋回半径ｅで公転運動させたときに両渦巻体が干渉しないという条件を満足する必要があるが、本実施例では、単一の円弧により内側曲線と外側曲線とを接続する方法を説明する。図２５に示す旋回側渦巻体２では、旋回外側曲線２ａ上で原点Ｏから旋回半径ｅの半分の距離にある点Ａを通る旋回半径ｅを半径とする円弧により、旋回内側曲線２ｂと旋回外側曲線２ａはなめらかに接続される。図２６に示す固定側渦巻体５では、固定外側曲線５ａ上で原点Ｏ′から旋回半径ｅの半分の距離にある点Ｂを通る旋回半径ｅを半径とする円弧により固定内側曲線５ｂと固定外側曲線５ａはなめらかに接続される。なお、このときの円弧の中心位置は回転の角度αによって変化し、この座標は図２２における点Ａ、Ａ′、Ａ″にそれぞれ相当している。
【００５２】
回転角度αの変化によるスクロ−ル形状の変化を示す図２７から図２９に示したことから分かるように、角度αの値により旋回側渦巻体２と固定側渦巻体５の渦巻壁の厚みが変化し、図２８、図２９から、角度αが同一数値で方向（回転方向に相当）が異なる場合は、旋回側渦巻体２と固定側渦巻体５の形状がちょうど入れ替わっていることがわかる。また、行程容積は、吸入終了時の作動室６の面積を比較してもわかるように、図２７に示したα＝０°の回転しない場合と同じ面積であり、使用材質に応じて固定側と旋回側で渦巻壁の厚さを適宜変化させることができるとともに、第１の実施例と同様にインボリュ−ト曲線よりも渦巻体を小型化できる効果がある。なお、ここでは旋回側渦巻体２の外側曲線を回転させた例を挙げたが固定側渦巻体５の方を回転させても同様の構成が実現できる。
【００５３】
なお、本実施例における渦巻体の創成法も第１の実施例で述べたものと同様である。また、渦巻体中央部のかみあい状態を拡大して示した図３０に示すように、本実施例の渦巻体においても第１の実施例と同様にトップクリアランス容積が零になり、トップクリアランス内流体の再膨張に伴う損失がないという優れた特長を有している。すなわち、図３０において、旋回側渦巻体２と固定側渦巻体５の最も内側の接触点８、８´で形成される最内室６ａは、図３０から明らかなように、旋回側渦巻体２が固定側渦巻体５の周りに旋回半径ｅ（＝ＯＯ´）で、相対的に公転運動を行うと、図３０に示す（１）、（２）、（３）、（４）の順に、接触点８、８´で形成される最内室６ａの容積が減少し、トップクリアランス容積は零になる。このため、圧縮された流体は無駄な再膨張を引き起こすことなく吐出ポ−ト（図示せず）からすべて外部に吐き出されることになる。なお、図２４では省略したが、実際には最内室６ａと通じる位置に吐出ポ−トを形成する必要があるので、この吐出ポ−ト部の容積はトップクリアランス容積になるが、この容積は行程容積に比べて小さく実質的に零とみなすことができる。
【００５４】
以上のように、本実施例では、渦巻体の巻き始め部構成が図２５、図２６で示したものについてのみ説明したが、後述するこれ以外の巻き始め部構成でも、同様にトップクリアランス容積を零とすることが可能である。
【００５５】
以上は、渦巻体の外側曲線を基本渦曲線としたときの渦巻壁厚さの異なる渦巻体の構成法を説明したが、渦巻体の内側曲線を基本渦曲線としたときも、基本渦曲線である旋回側渦巻体２の旋回内側曲線２ｂと固定側渦巻体５の固定内側曲線５ｂを位相差が１８０°前後になるように旋回内側曲線２ｂあるいは固定内側曲線５ｂを適宜角度αを変化させることにより同様に構成される。一例として図２６に式（１）で表される代数螺線を原点Ｏを中心にα＝−３０°回転させて旋回内側曲線２ｂ（旋回側渦巻体２の基本渦曲線）とし、固定内側曲線５ｂ（固定側渦巻体の基本渦曲線）は旋回内側曲線２ｂと位相差が（１８０°−α）のときのスクロ−ル形状を示す。内側曲線が基本渦曲線の場合は、図３１に示した外側曲線が基本渦曲線の場合と回転（角度α）の影響が逆に表われ、α＝−３０°で、図２８のα＝３０°の場合と同様に旋回側渦巻体２の渦巻壁厚さは厚く、固定側渦巻体５の渦巻壁厚さは薄く構成される。このように構成することにより、渦巻体の材質が異なった場合でも、渦巻体の各部を作用する圧力に対して同様な強度にでき、小型化により軸受荷重が低減されるため圧縮機の信頼性が大幅に向上する。
【００５６】
本発明の第４の実施例を図３２から図３５により説明する。第３の実施例で述べた構成は、旋回側渦巻体２と固定側渦巻体５の各々の基本渦曲線は回転はしているものの基本的には同一の数式で表され、式（１）で表される代数螺線を基本とし、代数螺線の指数ｋをｋ＜１．０にし、代数螺線の係数ａも任意の定数に設定した場合を示したが、本発明はこれに限定されるものではなく、以下、本実施例で示すように、例えば、式（１）で表される代数螺線の係数ａあるいは代数螺線の指数ｋが、偏角θの関数となるようにしても渦巻壁の厚みを適宜変化させることができ、渦巻体の強度を確保しながら、インボリュ−ト曲線よりも渦巻体を小型化できる。この場合、代数螺線の指数ｋはｋ＜１．０の範囲に限定されなくなる。さらに、旋回側渦巻体２と固定側渦巻体５の各々の基本渦曲線を異なる曲線で構成してもよい。
【００５７】
図３２に示すように、渦巻体の外側曲線を基本渦曲線とし、旋回側渦巻体２の外側曲線２ａと固定側渦巻体５の外側曲線５ａは、式（１）で表される代数螺線で代数螺線の指数ｋ、代数螺線の係数ａを両者各々異なる数値で構成している。この場合は、渦曲線を回転させる必要はなく、異なる２つの基本渦曲線を適宜選定することにより図１９で示した渦巻体と同様の効果を奏する渦巻体を構成することができる。図２５、図２６では、渦巻体の外側曲線を基本渦曲線に採ったときの、単一の円弧を接続曲線とする巻き始め部構成を説明したが、本発明の巻き始め部構成はこれに限定されるものではなくこれ以外にも種々の構成が考えられる。図３３、図３４、図３５によりこのように構成された渦巻体の巻き始め部の他の構成を説明する。図３３、図３４は、渦巻体の外側曲線を基本渦曲線に採った場合、図３５は、図３１に示したように渦巻体の内側曲線を基本渦曲線に採った場合を示している。図３３から図３５の各図では、旋回側渦巻体２と固定側渦巻体５を、ともに同一のｘ−ｙ座標軸で表している。図３３は、巻き始め部の接続曲線を２つの円弧で構成した場合で、破線が図２５、図２６に示した単一円弧の場合である。旋回側渦巻体２は、ｒ１とｒ２の２つの円弧により外側曲線２ａと内側曲線２ｂが接続され、固定側渦巻体５は、ｒ３とｒ４の２つの円弧により外側曲線５ａと内側曲線５ｂが接続されている。円弧同士の接続点Ａ、Ｂは原点Ｏ（あるいはＯ´）より旋回半径ｅの半分を半径とする円に接しており、円弧ｒ１とｒ４、円弧ｒ２とｒ３の中心座標は同じである。
【００５８】
図３４は、図３３と異なり、円弧と直線によって巻き始め部を構成している。円弧半径ｒは旋回側と固定側が同じ（すなわちｒ＝ｅ）で、円弧に接続する直線は、図３３と同様に、原点Ｏ（あるいはＯ´）より旋回半径ｅの半分を半径とする円に点Ａ、Ｂで接するようになっている。図３５は、図３１に示した渦巻体の内側曲線を基本渦曲線に採った場合の巻き始め部構成で、内側曲線２ｂ、５ｂと外側曲線２ａ、５ａは各々直線で接続されている。この場合、直線は旋回半径ｅの半分を半径とする円に点Ａ、Ｂで接するが、この円の中心Ｃは、原点Ｏ（あるいはＯ´）上にない。
【００５９】
以上述べたことから分かるように、渦巻体の巻き始め部を構成する内側曲線と外側曲線とを結ぶ接続線の必要条件は次の通りである。少なくとも内側曲線に内接し、旋回側渦巻体２と固定側渦巻体５を同一座標軸で表したときに、旋回半径ｅの半分を半径とする円がこれらの接続線間に内接するような任意の曲線（直線、円弧も含む）からなる。このような巻き始め部構成により、説明は省略するが図２５と同様にトップクリアランス容積は零になる。
【００６０】
本発明の第５の実施例を図３６から図４３により説明する。図３６は、本実施例の渦巻体構成法を説明する平面図であり、巻き始め部において渦巻体の内側曲線と外側曲線がほぼ接続するため、前記したような接続曲線がほとんど不要となり、構成が簡便化されるものである。図３６、図３７はそれぞれ旋回側と固定側の基本渦曲線と、この基本渦曲線を旋回半径ｅの半分の半径で円運動させたときに描く円軌跡の包絡線を示し、図３８、図３９はそれぞれ旋回側と固定側の渦曲線の構成を示す。実線１０は旋回側の基本渦曲線で、式（１）で表される代数螺線を原点Ｏを中心として角度αだけ回転したものである。破線１３と１４は基本渦曲線１０の包絡線で、１３が外側包絡線、１４が内側包絡線である。また、実線２０は固定側の基本渦曲線で、この曲線は旋回側の基本渦曲線１０を原点Ｏの周りに（１８０°−α）回転させたものである。破線２３と２４はこの基本渦曲線２０の包絡線で、２３が外側包絡線、２４が内側包絡線である。ここで、渦巻体は複数の密封容積を作るための両渦巻間の接触が幾何学的に保証されるように、以下のように構成される。旋回外側曲線２ａは旋回側の基本渦曲線１０の内側包絡線１４が選ばれ、固定外側曲線５ａは固定側の基本渦曲線２０の内側包絡線２４が選ばれる。渦巻体の内側曲線は、旋回内側曲線２ｂは固定外側曲線５ａと接触するため、固定側の基本渦曲線２０の外側包絡線２３が選ばれ、固定内側曲線５ｂは旋回外側曲線２ａと接触するため旋回側の基本渦曲線１０の外側包絡線１３が選ばれる。このように、旋回側の基本渦曲線１０と固定側の基本渦曲線２０とは同一形状で位相を（１８０°−α）ずらして構成しているため、旋回側と固定側で渦巻壁の厚みを変化することができるとともに、各渦巻体を構成する内側曲線と外側曲線が巻き始め部でほぼ接続するため、両者間の接続曲線はほとんど不要となり、構成を簡便化できる。以上のように構成することで、基本渦曲線としては、前記した図２５に示した場合と同様に種々の曲線を適用することができる。なお、、角度αが０°の場合は旋回側と固定側の渦巻体は同一形状になる。
【００６１】
図４０から図４３は、図３６から図３９で示した渦曲線構成法における、基本渦曲線の回転（角度α）によるスクロ−ル形状変化図と渦巻体中央部のかみあい状態を示す図（α＝３０°の場合）である。この図から分かるように、図２７から図３０で示したのと同様に、角度αの値により、旋回側渦巻体２と固定側渦巻体５の渦巻壁の厚みを変化することができるとともに、各渦巻体の巻き始め部がなめらかな曲線で構成され、トップクリアランス容積も零にできる。
【００６２】
本発明の第６の実施例を図４４から図４７により説明する。図４４から図４７は、渦巻体構成法を説明する平面図で、図３６から図３９に示す実施例と同様に巻き始め部において渦巻体の内側曲線と外側曲線がなめらかに接続し、構成が簡便化できるものである。本実施例では、スクロ−ル圧縮機の旋回半径をｅとしたとき、ｅ＝ｅ１＋ｅ２を満足する２つの半径ｅ１とｅ２を決め、これらの値を適宜選定することにより旋回側渦巻体２と固定側渦巻体５の渦巻壁の厚みを変化することができるものである。図４４、図４５は旋回側と固定側の基本渦曲線と、この基本渦曲線を半径ｅ１と半径ｅ２で円運動させたときに描く円軌跡の包絡線を示し、図４６、図４７はそれぞれ旋回側と固定側の渦曲線の構成を示す。実線１０は旋回側の基本渦曲線で、式（１）で表される代数螺線である。破線３４は基本渦曲線１０を半径ｅ１で円運動させたときの外側包絡線、破線３５は基本渦曲線１０を半径ｅ２で円運動させたときの内側包絡線である。また、実線２０は固定側の基本渦曲線で、この曲線は旋回側の基本渦曲線１０を原点Ｏの周りに１８０°回転させたものである。破線３６はこの基本渦曲線２０を半径ｅ２で円運動させたときの外側包絡線、破線３７は基本渦曲線２０を半径ｅ１で円運動させたときの内側包絡線である。ここで、渦巻体は複数の密封容積を作るための両渦巻間の接触が幾何学的に保証されるように、以下のように構成される。旋回外側曲線２ａは旋回側の基本渦曲線１０の内側包絡線３５が選ばれ、固定外側曲線５ａは固定側の基本渦曲線２０の内側包絡線３７が選ばれる。渦巻体の内側曲線は、旋回内側曲線２ｂは固定外側曲線５ａ（３７）と接触するため、内側包絡線３７と旋回半径ｅの距離だけ隔たった固定側の基本渦曲線２０の外側包絡線３６が選ばれ、同様に、固定内側曲線５ｂは旋回外側曲線２ａ（３５）と接触するため、内側包絡線３５と旋回半径ｅの距離だけ隔たった旋回側の基本渦曲線１０の外側包絡線３４が選ばれる。このように、基本渦曲線１０と基本渦曲線２０で各々ｅ１、ｅ２の２つの異なる半径の包絡線を考え、ｅ１＞ｅ２とすることにより、渦巻きの巻き角によって渦巻壁の厚さが次第に変化するとともに、旋回側渦巻体２は固定側渦巻体５に比べて全体的に渦巻壁の厚さを厚く構成することができる。ｅ１＜ｅ２の場合は、反対に固定側渦巻体５の方が旋回側渦巻体２よりも渦巻壁の厚さを厚く構成することができる。
【００６３】
以上スクロ−ル形流体機械として圧縮機を例に挙げて、渦巻壁の厚さが渦巻の巻き角に応じて連続的に変化し、かつ、固定側と旋回側で渦巻壁の厚みが異なる渦巻体のもう一つの基本的な渦曲線構成法を述べたが、本発明はこれ以外に膨張機、ポンプにも適用することができる。また、本発明ではスクロ−ルの運動形態として、一方のスクロ−ルが固定しもう一方のスクロ−ルが任意の旋回半径で自転せずに公転運動を行う形式としたが、相対的に上記の運動と等価な運動形態となる両回転式のスクロ−ル形流体機械にも適用することができる。また、渦巻体の基本渦曲線として式（１）で表される代数螺線を用いたが、本発明はこれに限定されるものではなく、本発明で明らかにした渦巻体の構成法は、渦巻きの曲率が連続的に変化するなめらかな任意の渦曲線に適用することができる。
【００６４】
【発明の効果】
以上説明したように、本発明によれば、代数螺線を基本渦曲線に用いることにより、渦巻体の巻始め部の強度を確保しながら渦巻体を小型化できるため、軸受荷重も小さくなり、信頼性の高いスクロ−ル流体機械を提供できる。また、渦巻壁の厚みを次第に変化させることができるため、渦巻体間の流体の内部漏れが低減され、トップクリアランス容積も小さく、あるいは零にできるためスクロ−ル流体機械の効率を向上することができる。また、このスクロ−ル流体機械を搭載することにより、エネルギ効率に優れ、信頼性の高い空調設備を提供できる。
【００６５】
また、渦巻体の材質が旋回側と固定側で異なる場合でも、各々強度的に必要な渦巻壁の厚さを保ちながら、渦巻きの巻き角に応じて渦巻壁の厚さが連続的に変化する渦巻体の構成法を明らかにするとともに、代数螺線を基本渦曲線に用いることにより、渦巻体の巻き始め部の強度を確保しながら、インボリュ−ト曲線よりも渦巻体を小型化することができる。
【００６６】
【図面の簡単な説明】
【図１】本発明の第１の実施例を示すスクロ−ル圧縮機を搭載した空調設備の構成図である。
【図２】本実施例の旋回スクロ−ルの構成図である。
【図３】図１の横断面図である。
【図４】本実施例のスクロ−ル圧縮機の作動原理を示す平面図である。
【図５】本実施例のスクロ−ル形状の形成法を説明する図である。
【図６】本実施例のスクロ−ル形状の形成法を説明する図である。
【図７】本実施例のスクロ−ル形状の形成法を説明する図である。
【図８】本実施例のスクロ−ル形状の形成法を説明する図である。
【図９】本実施例のスクロ−ルの巻始め部の形成を説明する図である。
【図１０】本実施例のスクロ−ル形状を加工するカッタの軌跡を示す図である。
【図１１】本実施例のスクロ−ル形状の形成法を説明する図である。
【図１２】本実施例のスクロ−ル形状の形成法を説明する図である。
【図１３】本実施例のスクロ−ルの巻始め部の形成を説明する図である。
【図１４】本実施例の渦巻体中央部のかみ合い状態を示す要部拡大図である。
【図１５】本発明の第２の実施例を示すスクロ−ル形状の平面図である。
【図１６】本実施例を示すスクロ−ル形状の平面図である。
【図１７】本実施例を示すスクロ−ル形状の平面図である。
【図１８】本実施例を示すスクロ−ル形状の平面図である。
【図１９】本発明の第３の実施例を示すスクロ−ル形状の平面図である。
【図２０】スクロ−ル圧縮機の作動原理を説明する図である。
【図２１】本実施例のスクロ−ル形状の形成法を説明する図である。
【図２２】本実施例のスクロ−ル形状の形成法を説明する図である。
【図２３】本実施例のスクロ−ル形状の形成法を説明する図である。
【図２４】本実施例のスクロ−ル形状の形成法を説明する図である。
【図２５】本実施例の旋回スクロ−ルの巻き始め部の構成を示す平面図である。
【図２６】本実施例の固定スクロ−ルの巻き始め部の構成を示す平面図である。
【図２７】角度αを設けた場合のスクロ−ル形状変化を示す平面図である。
【図２８】角度αを設けた場合のスクロ−ル形状変化を示す平面図である。
【図２９】角度αを設けた場合のスクロ−ル形状変化を示す平面図である。
【図３０】渦巻体中央部のかみ合い状態を示す平面図である。
【図３１】渦巻体中央部のかみ合い状態を示す平面図である。
【図３２】本発明の第４の実施例を示すスクロ−ル形状の平面図である。
【図３３】本実施例の巻き始め部の構成を示す平面図である。
【図３４】本実施例の巻き始め部の構成を示す平面図である。
【図３５】本実施例の巻き始め部の構成を示す平面図である。
【図３６】本発明の第５の実施例を示すスクロ−ル形状の形成法を説明する図である。
【図３７】本実施例を示すスクロ−ル形状の形成法を説明する図である。
【図３８】本実施例を示すスクロ−ル形状の形成法を説明する図である。
【図３９】本実施例を示すスクロ−ル形状の形成法を説明する図である。
【図４０】本実施例の角度αの変化によるスクロ−ル形状変化を示す平面図である。
【図４１】本実施例の角度αの変化によるスクロ−ル形状変化を示す平面図である。
【図４２】本実施例の角度αの変化によるスクロ−ル形状変化を示す平面図である。
【図４３】本実施例における渦巻体中央部のかみ合い状態を示す平面図である。
【図４４】本発明の第５の実施例を示すスクロ−ル形状の形成法を説明する図である。
【図４５】本実施例を示すスクロ−ル形状の形成法を説明する図である。
【図４６】本実施例を示すスクロ−ル形状の形成法を説明する図である。
【図４７】本実施例を示すスクロ−ル形状の形成法を説明する図である。
【符号の説明】
１…旋回スクロ−ル、２…旋回側渦巻体、２ａ…旋回外側曲線、２ｂ…旋回内側曲線、３…端板、４…固定スクロ−ル、５…固定側渦巻体、５ａ…固定外側曲線、５ｂ…固定内側曲線、６…作動室、６ａ…最内室、７…吐出ポ−ト、８、８´…接触点、９…クランク軸、１０…旋回側基本渦曲線、１１、１３、３４…旋回側基本渦曲線の外側包絡線、１２、１４、３５…旋回側基本渦曲線の内側包絡線、１５…フレ−ム、１６…オルダムリング、１７…モ−タ、１８…吸入パイプ、１９…吐出パイプ、２０…固定側基本渦曲線、２１、２３、３６…固定側基本渦曲線の外側包絡線、２２、２４、３７…固定側基本渦曲線の内側包絡線、３０…スクロ−ル圧縮機、３１…凝縮器、３２…膨張弁、３３…蒸発器、Ｏ…旋回スクロ−ル中心、Ｏ´…固定スクロ−ル中心、ｅ…旋回半径、α…渦曲線の回転の角度、ｅ１、ｅ２…円運動（公転運動）の半径。[0001]
[Industrial applications]
The present invention relates to a scroll type fluid machine, which is a kind of positive displacement type fluid machine, and more particularly, to a scroll fluid machine in which a curve of a spiral body is formed by an algebraic spiral, a scroll member, and a method for processing the scroll member.
[0002]
[Prior art]
A conventional scroll-type fluid machine is composed of a fixed scroll and a swirling scroll having spiral bodies of the same shape combined eccentrically with each other. The spiral shape generally has a spiral pitch and a spiral wall thickness. A constant involute curve is used. The advantage of using the involute curve as the vortex curve is that the normal pitch of the vortex is constant, so that the inner and outer vortex curves can be processed simultaneously with a single cutter. On the other hand, since the thickness of the spiral wall is constant, the stress at the center of the spiral body, which is at the highest pressure, becomes high, which tends to cause a problem in strength. That is, the thickness is determined from the constraints on strength, the number of turns of the spiral is determined from the operating pressure ratio, which is a design condition, the height and the spiral pitch, etc. of the spiral are determined from the stroke volume, and other constraints on the external dimensions are imposed. The dimensions are determined. In this manner, when one of the shapes of the spiral body, for example, the turning scroll, is determined, the shape of the fixed scroll to be engaged with the shape is determined by selecting the inner envelope of the turning inner curve as the fixed inner curve. In addition, the central part of the spiral has a large internal pressure difference, and thus has the disadvantage that the performance tends to deteriorate due to internal leakage of the fluid. Further, in the involute curve, since the spiral pitch is constant, the rate of volume change is also constant, and is the ratio of the sealed volume at the outermost circumference (stroke volume) to the sealed volume at the innermost circumference within a predetermined dimension. When trying to increase the internal volume ratio, increasing the number of turns of the spiral causes a decrease in the spiral pitch, and a constant spiral wall thickness causes a problem in that the turning radius is reduced and the stroke volume is also reduced.
[0003]
To solve the above problem, US Pat. No. 3,802,809 discloses a known technique for increasing the thickness of the spiral wall near the center of the spiral body to withstand high pressure. Known techniques for changing the internal volume ratio by changing the spiral pitch can be found in U.S. Pat. No. 2,324,168 and JP-A-3-11102.
[0004]
[Problems to be solved by the invention]
The structure disclosed in U.S. Pat. No. 3,802,809 solves the problem of strength by increasing the thickness of the spiral wall at the beginning of winding of the spiral body, but the range in which the thickness of the spiral wall is large is limited. Since it is limited to a part at the beginning of winding, the effect of reducing internal leakage of fluid through the end face of the spiral is small. Further, since the thickness of the spiral wall is constant at portions other than the winding start portion, it is impossible to increase both the stroke volume and the internal volume ratio within a predetermined size as in the involute curve.
[0005]
In the case of a scroll type fluid machine disclosed in U.S. Pat. No. 2,324,168 and Japanese Patent Laid-Open No. 3-11102, a structure in which a spiral pitch is changed to change an internal volume ratio is shown. When the spiral pitch is reduced from the outer periphery to the center of the spiral in order to increase the ratio, the thickness of the spiral wall becomes thinner toward the central portion (start of winding) of the spiral, and no consideration is given to strength. Conversely, the thickness of the spiral wall increases toward the outer periphery of the spiral, so that the stroke volume decreases. As described above, the swirl volume and the internal volume ratio can be both increased, and the vortex curve which can reduce the size of the spiral body more than the involute curve at the same stroke volume and the same internal volume ratio was unknown. Further, the geometric theory of the spiral body in which the spiral pitch and the thickness of the spiral wall change, that is, the method of forming the spiral curve and the spiral body, etc., has not been clarified.
[0006]
A first object of the present invention is to provide a scroll fluid machine having a spiral body in which the thickness of the spiral body changes gradually according to the winding angle of the spiral.
[0007]
A second object of the present invention is to provide a scroll fluid machine that can reduce the size of a spiral body compared to an involute curve while maintaining the strength of the spiral body, reduce internal leakage of fluid, and improve performance. Is to do.
[0008]
A third object of the present invention is to provide a scroll fluid machine that can secure the same strength even when the materials of the fixed scroll and the revolving scroll are different.
[0009]
A fourth object of the present invention is to provide a method of processing a scroll member having a spiral body in which the thickness of the spiral body changes gradually according to the winding angle of the spiral.
[0010]
[Means for Solving the Problems]
In order to achieve the first object, a scroll-type fluid machine according to the present invention comprises two scroll members formed by an end plate and a spiral body standing upright on the end plate. In a scroll-type fluid machine which is engaged with each other in a turned state and revolves with a turning radius e so that one scroll member does not apparently rotate with respect to the other scroll member, When the outer vortex curve is an outer curve and the inner vortex curve is an inner curve, the vortex curves of the two vortices are represented by a radial coordinate r, a declination θ, and a coefficient of an algebraic spiral in a polar coordinate format. a, where an index k of an algebraic spiral is an envelope obtained by turning an algebraic spiral represented by the following equation, and the thickness of the wall of the spiral body decreases from the inner circumference to the outer circumference. It is characterized by the following.
[0011]
(Equation 1)

[0012]
In addition, the algebraic screw corresponding to one scroll member has an index k of k <1.0, and the algebraic screw of the other scroll member has rotated the one algebraic screw by about 180 °. It may be something.
[0013]
In order to achieve the second object, a scroll-type fluid machine according to the present invention comprises two scroll members formed by an end plate and a spiral body standing upright on the end plate. A scroll-type fluid machine which engages with each other in a directed state and revolves around a predetermined turning radius so that one scroll member does not apparently rotate with respect to the other scroll member. , The vortex curve of the two spirals is represented by a radial radius r, a deflection angle θ, and an algebraic spiral in a polar coordinate format. Assuming that the coefficient a and the exponent k of the algebraic spiral are k, the envelope consists of an envelope obtained by turning the algebraic spiral represented by the formula (1), and the exponent k of the algebraic spiral corresponds to the argument θ. It is characterized by changing.
[0014]
The algebraic spiral has an index k of k> 1.0 and a coefficient a is set to a constant, and is obtained by changing the index k of the algebraic spiral as a function of the argument θ. Is also good.
[0015]
In order to achieve the third object, a scroll-type fluid machine according to the present invention is configured such that the algebraic spiral of the one scroll member is rotated by an angle α about its origin, and The algebraic spiral of the scroll member is rotated by an angle (180 ° -α) about the origin.
[0016]
Further, the one scroll member may be a revolving scroll member, and a spiral body of the revolving scroll member may be thicker than a spiral body of the other scroll member.
[0017]
In order to achieve the fourth object, a method for processing a scroll member according to the present invention is characterized in that the outer curve and the inner curve of the scroll body of the scroll member are obtained from the envelope when the algebraic spiral is swirled. BecomeOf the scroll provided on one of the scroll members.Outer and inner curvesAlong the lineBy moving the center of the cutterOf the other scroll memberIt is characterized in that the spiral body is processed.
[0018]
[Action]
Of the scroll of both scrollsTo determine the shapeBasic vortex curveToIn a polar coordinate format, a radius r, an angle θ, a coefficient a of an algebraic spiral, and an index k of an algebraic spiral are defined.Expression (1)Since the algebraic spiral is used, the pitch of the spiral can be easily changed only by changing the value of the index k of the algebraic spiral. When the index k is k> 1.0, the pitch of the spiral increases as the spiral angle (deviation θ) increases. Conversely, when k <1.0, the spiral angle (deviation) increases. As the angle θ) increases, the pitch of the spiral decreases.
[0019]
Further, in the apparatus provided with a stationary scroll member and a revolving scroll member each having a spiral body, the clearance volume formed between the contact points in the innermost regions of both the spiral bodies is such that Each spiral body has an algebraic spiral as a basic vortex curve and the thickness of the spiral wall changes gradually according to the spiral angle of the spiral. , The top clearance can be reduced, the re-expansion loss can be reduced, and the efficiency can be improved.
[0020]
In addition, the thickness of the spiral wall is reduced by setting the index k of the algebraic spiral to k <1.0 or by making the algebraic spiral in which the coefficient a or the index k is a function of the argument θ the basic spiral curve of the spiral body. It can be changed as appropriate.
[0021]
The algebraic spiral of the one scroll member is rotated by an angle α about its origin, and the algebraic spiral of the other scroll member is angled (180 ° -α) about the origin. In the rotated one, since the angle α is rotated, it is possible to change the thickness of the two spiral walls by this angle α, and to secure the strength of the spiral even when the materials of both spirals are different. Can be.
[0022]
Further, the radii e1 and e2 have a relationship of the turning radius e and e = e1 + e2, and the respective spiral bodies of both scrolls have outer curves each having an algebraic spiral of both scrolls having a radius e1. , E2, and the inner curve is formed by the outer envelope when the algebraic spirals of both scrolls are turned by the radii e1 and e2, respectively. By changing the magnitude relation and value of the radii e1 and e2, the two spiral walls can be formed with different thicknesses, and the strength of the spiral bodies can be ensured even when the materials of the two spiral bodies are different. Further, it is possible to provide a scroll type fluid machine in which the size of the spiral body can be made smaller than that of the involute curve, the internal leakage of the fluid can be reduced, and the performance can be improved.
[0023]
Outer and inner curves of scroll member scrollIsIt is formed by an envelope when several spirals are swirled,Of the scroll provided on one of the scroll members.By moving the center of the cutter along the outer and inner curvesOf the other scroll memberSince the spiral body is machined, it can be machined continuously, and can be efficiently machined with high dimensional accuracy, such as the tooth side surface.
[0024]
【Example】
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a diagram showing the configuration of a refrigeration cycle to which the scroll type compressor according to the present embodiment is applied, and FIG. 2 is a plan view of a swirling scroll showing the scroll shape of the scroll type fluid machine according to the present embodiment. FIG. 3, FIG. 3 is a longitudinal sectional view of FIG. 2, FIG. 4 is a view showing the principle of operation, FIGS. 5 to 8 are explanatory views of a method for forming a spiral body, and FIG. FIG. 10 is a diagram for explaining the locus of the cutter.
[0025]
As shown in FIG. 1, the refrigeration cycle mainly includes a scroll compressor 30, a condenser 31, an expansion valve 32, and an evaporator 33. The scroll type compressor 30 has a spiral body having the same shape, and a swirl scroll 1 and a fixed scroll formed by a spiral body in which the thickness of the spiral body changes continuously according to the winding angle of the spiral. 1, a crankshaft 13 for rotating the rotating scroll 1, a frame 14 for supporting the crankshaft 13, an Oldham ring 15 for allowing the orbiting scroll 1 to revolve and prevent a rotating motion, and a crankshaft. A motor 16 for driving the motor 13, a suction pipe 17 and a discharge pipe 18 are provided.
[0026]
In the scroll type compressor constructed as described above, when the motor 16 is energized and the crankshaft 13 rotates, the orbiting scroll 1 revolves without rotating by the Oldham ring 15 and operates. As shown in FIG. 4 showing the principle, the refrigerant is compressed between the scrolls 1 and 4. The compressed high-temperature and high-pressure refrigerant flows into the condenser 31 from the discharge pipe 18 as indicated by an arrow, performs heat exchange, liquefies, is throttled by the expansion valve 32 and adiabatically expands to a low-temperature and low-pressure. After being gasified by heat exchange, it is sucked into the scroll compressor 30 through the suction pipe 17.
[0027]
As shown in FIGS. 2 and 3, the turning scroll 1 is formed by a turning-side spiral body 2 and an end plate 3. The turning-side spiral body 2 is composed of a turning outer curve 2a and a turning inner curve 2b, and the center O of the turning scroll 1 is the origin of the turning outer curve 2a and the turning inner curve 2b. Here, the turning-side spiral body has a turning outer curve 2a.Equation (1)The algebraic spiral represented by is defined as a basic vortex curve, and the index k of the algebraic spiral is set to k <1.0.
[0028]
(Equation 1)

[0029]
Further, the spiral body 5 of the fixed scroll 4 is formed similarly to the spiral body 2 of the revolving scroll 1. The fixed spiral member 5 is composed of a fixed outer curve 5a and a fixed inner curve 5b. The center O 'of the fixed scroll 4 is the origin of the fixed outer curve 5a and the fixed inner curve 5b.Equation (1)The algebraic spiral represented by is rotated by 180 ° about the origin O 'to be a basic vortex curve, and the coefficient a of the algebraic spiral and the index k of the algebraic spiral have the same values as the outer curve 2a.
[0030]
The compression action is performed as follows. As shown in FIG. 4, the stationary spiral body 5 is stationary and the revolving spiral body 2 is revolved around the fixed scroll center O 'without revolving around the rotating radius e (= OO'). A plurality of crescent-shaped closed working chambers 6, 6 formed between the swirling-side spiral body 2 and the fixed-side spiral body 5 are formed. As shown in FIG. 4, the volumes of the working chambers 6, 90 are 90 °, 180 °, from the state (1) in which the suction of the fluid from the suction port provided on the outer peripheral side of the fixed scroll 4 is completed. As the revolution progresses to 270 °, (2), (3), and (4) and the volume thereof are reduced, and the fluid is compressed. Then, the compressed fluid is finally discharged from the discharge port 7.
[0031]
By configuring the swirling-side spiral body 2 and the fixed-side spiral body 5 as described later, the thickness t of the spiral wall of the spiral body can be continuously changed from the start to the end of the spiral, and the fluid inside the spiral can be changed. The center of the spiral where the pressure is the highest is thicker and the end of the spiral where the pressure is the lower is thinner, and the strength becomes uniform in proportion to the pressure applied to each part of the spiral wall of the spiral. The volume of the spiral body can be reduced as compared with an involute curve or the like in which the spiral wall has a constant thickness, and the material cost and weight can be reduced. Further, in the range of about one turn from the start of the spiral, the thickness of the spiral wall is configured to be relatively thick, and internal leakage of the fluid can be reduced.
[0032]
Next, a configuration method of the swirling-side spiral body 2 and the fixed-side spiral body 5 in the present embodiment will be described with reference to FIGS. 5, 6, 7, and 8. FIG. Here, a case where the outer curve of the spiral body is taken as a basic vortex curve will be described as an example.
[0033]
FIGS. 5 and 6 show the basic vortex curves on the turning side and the fixed side, respectively, and the envelope of the circular locus drawn when the basic vortex curve is circularly moved with the turning radius e. FIGS. The vortex curves on the fixed and fixed sides are shown. Solid line 10 is the basic vortex curve on the turning side,Equation (1)Is an algebraic spiral represented by Dashed lines 11 and 12 are the envelopes of the basic vortex curve 10, 11 is the outer envelope, and 12 is the inner envelope. The fixed-side basic vortex curve 20 shown by the solid line 20 is obtained by rotating the turning-side basic vortex curve 10 around the origin O by 180 °. Dashed lines 21 and 22 are the envelopes of the basic vortex curve 20, 21 is the outer envelope, and 22 is the inner envelope.
[0034]
Here, the solid curve 10 is selected as the turning outer curve 2a, and the solid line 20 is selected as the fixed outer curve 5a, in order to set the outer curve of the spiral body as the basic vortex curve. The inner curve of the spiral is determined as follows so that the contact between the spirals to create a plurality of sealed volumes is geometrically ensured. Since the turning inner curve 2b is in contact with the fixed outer curve 5a, the outer envelope 21 of the fixed-side basic vortex curve 20 is selected, and the fixed inner curve 5b is in contact with the turning outer curve 2a, so that the turning-side basic vortex curve 10 The outer envelope 11 is selected.
[0035]
As described above, the basic spiral curve construction method of the spiral body in which the thickness of the spiral wall continuously changes according to the spiral angle of the spiral has been described. Do not match. The configuration of the winding start portion must satisfy the condition that the two spirals do not interfere with each other when the orbiting spiral 2 is revolved around the fixed spiral 5 with a turning radius e. Therefore, an example of the configuration of the winding start portion will be described with reference to FIG.
[0036]
In FIG. 9, point A represents the start position of the outside turning curve 2a, and point B represents the start position of the inside turning curve 2b. Here, the position of the point A is set to the origin O on the outer turning curve 2a from the condition that the two spirals do not interfere with each other when the orbiting-side spiral 2 revolves around the fixed-side spiral 5 with the turning radius e. Is determined to be a half of the turning radius e. This point A corresponds to point B on the turning inner curve 2b corresponding to the outer envelope 21 of the fixed-side basic vortex curve 20 in FIGS. 5 to 8, and the turning radius e passing through the point A is defined as the radius. The arc will smoothly connect to the turning inner curve 2b at the point B. In addition, the shape of the winding start portion of the fixed-side spiral pair is also formed in the same manner as in the turning side.
[0037]
Next, a method for manufacturing such a spiral body will be described. FIG. 10 shows the locus of the cutter when forming the swirl-side spiral body. For example, by using a cutter (end mill or the like) having a turning radius e as a radius, the center coordinates of the cutter are moved on the outer curve 5a and the inner curve 5b of the fixed-side spiral body 5, thereby continuously turning the spiral body. 2 can be processed, and the dimensional accuracy of the spiral body can be improved and the spiral body can be processed efficiently. On the other hand, when processing the fixed spiral 5, the same processing is performed by moving the center of the cutter on the outer curve 2 a and the inner curve 2 b, which are the spiral curves of the swirling spiral 2.
[0038]
The method of forming a spiral body when the outer curve of the spiral body is a basic spiral curve has been described above. Next, a method of forming a spiral body when the inner curve of the spiral body is a basic spiral curve will be described. 11 and 12 show vortex curves on the turning side and the fixed side, respectively. In this case, since the inner curve of the spiral body is the basic vortex curve, the solid line 10 in FIG. 5 is selected as the turning inner curve 2b, and the solid line 20 in FIG. 6 is selected as the fixed inner curve 5b. The outer curve of the spiral is determined as follows. Since the turning outer curve 2a contacts the fixed inner curve 5b, the inner envelope 22 of the fixed-side basic vortex curve 20 in FIG. 6 is selected, and the fixed outer curve 5a contacts the turning inner curve 2b in FIG. By choosing the inner envelope 12 of the basic vortex curve 10, the contact between the two spirals to create a plurality of sealed volumes is geometrically ensured.
[0039]
Further, at this time, the winding start portion of the spiral body is formed as shown in FIG. 13 unlike the case where the outer curve of the spiral body is used as the basic spiral curve (FIG. 9). In FIG. 13, point A represents the start position of the outer turning curve 2a forming the turning-side spiral body 2, and point B represents the start position of the inner turning curve 2b. The positions of points A and B draw a circle centered on the origin O and have a radius equal to half of the turning radius e, and smoothly connect the turning outside curve 2a and the turning inside line 2b through one point C on the circumference. It is determined by connecting with a straight line. At this time, the point C is an intermediate point of a straight line connecting the points A and B. What has been described above has described the shape of the winding start portion of the turning-side spiral body. However, the fixed-side spiral body is also formed in the same manner as the turning-side spiral body.
[0040]
As described above, the method for forming the spiral body in which the thickness of the spiral wall continuously changes according to the spiral angle of the spiral is described. Further, in the spiral body of the present embodiment, the top clearance volume becomes zero and the top clearance volume becomes zero. An excellent feature not found in the conventional involute curve that there is no loss due to re-expansion of the internal fluidSignhave. FIG. 14 is an enlarged view of a main part of the scroll type compressor according to the present embodiment shown in FIG. As shown in FIG. 14, the innermost chamber 6 a formed by the innermost contact points 8 and 8 ′ of the swirling-side spiral body 2 and the fixed-side spiral body 5, as is apparent from the figure, in this embodiment, When the revolving spiral body 2 relatively revolves around the fixed spiral body 5 with a revolving radius e (= OO '), (1), (2), (3), and (4) in FIG. 2), the volume of the innermost chamber 6a formed by the contact points 8 and 8 'decreases, and the top clearance volume conventionally existing becomes zero. For this reason, all the compressed fluid is discharged to the outside from a discharge port (not shown) without causing unnecessary re-expansion. Although not shown in FIG. 14, since the discharge port must be formed at a position communicating with the innermost chamber 6a, the volume of this discharge port is the top clearance volume. This quantity is very small compared to that and can be considered as substantially zero. Here, the case where the winding start portion of the spiral body is formed as shown in FIG. 9 has been described. However, the description of the winding start portion formed as shown in FIG. 13 is omitted, but the top clearance volume becomes zero similarly.
[0041]
Since the scroll compressor thus formed is applied to a refrigeration cycle or a cycle dedicated to cooling, internal leakage of fluid between the spiral bodies can be reduced, and the top clearance volume becomes zero, so that the efficiency of the compressor is reduced. Is greatly improved. Thus, a highly reliable refrigeration / air-conditioning system having excellent energy efficiency can be obtained.
[0042]
Next, a second embodiment of the present invention will be described with reference to FIGS. In the first embodiment, the basic vortex curve of the spiral body isEquation (1)The case where the algebraic spiral represented by the following formula is used, the index k of the algebraic spiral is set to k <1.0, and the coefficient a of the algebraic spiral is also set to an arbitrary constant is shown.Equation (1)The coefficient of the algebraic spiral represented by or the index k of the algebraic spiral is a basic vortex curve that becomes a function of the argument θ, so that the thickness of the spiral wall can be appropriately changed. The spiral body can be made smaller than the involute curve while ensuring strength. In this case, the index k of the algebraic spiral is not limited to the range of k <1.0. This embodiment will be described with reference to FIGS.
[0043]
15 and 16 show the basic vortex curve of the spiral body.Equation (1)The scroll shape when the algebraic spiral exponent k is a constant of k> 1.0 and the algebraic spiral coefficient a is also a constant is shown in FIG. FIG. 16 shows the structure of the spiral body at the end of suction (compression start) when used as a compressor. 17 and 18, as in FIGS. 15 and 16, the index k of the algebraic spiral is set to k> 1.0, and the coefficient a of the algebraic spiral is the same constant value as in FIGS. 14 and 15, but the index k is This shows a scroll shape when an algebraic spiral represented by a function of the argument θ is used as a basic vortex curve. Specifically, the index k is a linear function of the argument θ, and the value of k decreases linearly from the beginning to the end of winding. As is apparent from a comparison of FIGS. 16 and 18, in FIGS. 15 and 16 in which the index k of the algebraic spiral is a constant of k> 1.0, the thickness of the spiral wall is equal to the center of the spiral ( The lower the pressure difference, the lower the pressure difference. Conversely, the thickness of the spiral wall increases toward the outer periphery of the spiral, so that the volume (stroke volume) of the outermost working chambers 6, 6 decreases when the outer shape is kept constant. On the other hand, in FIGS. 17 and 18 in which the index k of the algebraic spiral is changed according to the winding angle of the spiral, the index k is k> 1.0, but the thickness of the spiral wall at the beginning of winding has a problem in strength. In the outer periphery of the spiral, the thickness of the spiral wall becomes thinner toward the end of the spiral and the stroke volume increases, as in the case where the index k of the algebraic spiral is k <1.0. As a result of detailed numerical analysis, assuming that the outer shape (diameter and height of the spiral) is constant, the swirl body shown in FIGS. 17 and 18 has a stroke volume increased by about 30% as compared with the spiral body shown in FIGS. However, it was found that the internal volume ratio increased from 2.71 of the former to 2.80 of the latter. Therefore, when the stroke volume and the internal volume ratio are kept constant, the spiral body shown in FIGS. 17 and 18 can reduce the size of the spiral body. Here, the case where the index k changes with a linear function of the argument θ is shown, but the index k may be given by a quadratic, cubic function or logarithmic function of the argument θ. Alternatively, even if the index k is a constant and the coefficient a of the algebraic spiral is changed as a function of the argument θ, the thickness of the spiral wall can be appropriately changed in the same manner, and while maintaining the strength of the spiral body, It is possible to obtain a scroll type compressor in which the size of the spiral body can be reduced more than the involute curve, the internal leakage of the fluid can be reduced, and the performance can be improved.
[0044]
A third embodiment of the present invention will be described with reference to FIGS. 19 is a plan view showing a state in which the scrolls are combined, FIG. 20 is a view for explaining the principle of operation, FIGS. 21 to 24 are views for explaining a method of forming the scroll shape, and FIG. 25 is a swivel scroll. 26 is a plan view showing the configuration of the winding start portion of the fixed scroll, and FIGS. 27 to 29 show the change in the shape of the scroll when the angle α is provided. FIG. 30 is a plan view showing a meshing state of the center of the spiral body, and FIG. 31 is a plan view showing a meshing state of the central part of the spiral body.
[0045]
The scroll shape of this embodiment is formed in the same manner as the scroll shape shown in the first embodiment, but in this embodiment, the turning scroll and the fixed scroll are formed so that the materials are different. For example, the turning scroll is made of a lightweight and low-strength material such as an aluminum alloy, and the fixed scroll is made of an ordinary iron-based material having higher strength than the turning scroll. As in the present embodiment, the swirling-side spiral body 2 made of a low-strength material has a generally thicker spiral wall than the fixed-side spiral body 5 having higher strength, and both have almost the same strength. The outer and inner curves of the spiral scroll and the fixed scroll, the origins O and O 'of the spiral curve, and the index k of the algebraic spiral are the same as in the first embodiment. Is set.
[0046]
However, the configuration of the turning-side spiral body 2 is such that the turning outer curve 2a isEquation (1)In order to further increase the thickness of the spiral wall, the algebraic spiral represented by is rotated by an angle α about the origin O as a basic vortex curve as described later. Accordingly, the thicknesses of the spiral walls of the swirl-side spiral body 2 and the fixed-side spiral body 5 continuously change from the start to the end of the spiral, and the pressure of the internal fluid becomes the highest. The central part is thicker and the end part where the winding pressure becomes low is thinner, so that the volume of the spiral body can be reduced compared to an involute curve with a constant spiral wall thickness, reducing material costs and reducing weight. As much as possible, the spiral wall has a relatively large thickness in the range of about one turn from the start of the spiral, so that the internal leakage of the fluid can be reduced. In addition, the swirling-side spiral body 2 made of a low-strength material has a generally thicker spiral wall than the stationary-side spiral body 5 having higher strength, and both have almost the same strength.
[0047]
The principle of operation is the same as in the first embodiment, as shown in FIG. 20, in which the fixed-side spiral body 5 is stationary and the swivel-side spiral body 2 does not rotate around the fixed scroll center O 'without turning. By making the revolving motion of e (= OO ′), a plurality of crescent-shaped closed spaces, working chambers 6, 6 are formed between the two spiral bodies 2, 5, and the working chambers 6, 6 have a fluid capacity. As the revolution progresses from 90 °, 180 ° and 270 ° from the state (1) where the suction of the fluid has been completed, the volume is reduced to (2), (3) and (4) and the compression action of the fluid is performed. Is
[0048]
Next, a method of forming the swirl-side spiral body 2 and the fixed-side spiral body 5 in the present embodiment will be described in detail by taking as an example a case where the outer curve of the spiral body is taken as a basic spiral curve. 21 and 22 show the basic vortex curves on the turning side and the fixed side, respectively, and the envelope of the circular locus drawn when the basic vortex curve is circularly moved with the turning radius e. FIGS. The vortex curves on the fixed and fixed sides are shown. Solid line 10 is the basic vortex curve on the turning side,Equation (1)Is obtained by rotating the algebraic spiral represented by the following expression around the origin O by the angle α. Dashed lines 11 and 12 are the envelopes of the basic vortex curve 10, 11 is the outer envelope, and 12 is the inner envelope.
[0049]
Further, a solid line 20 is a basic vortex curve on the fixed side.(180 ° -α)It is rotated. Dashed lines 21 and 22 are the envelopes of the basic vortex curve 20, 21 is the outer envelope, and 22 is the inner envelope. As in the first embodiment, since the outer curve of the spiral body is a basic vortex curve, a solid line 10 is selected as the turning outer curve 2a, a solid line 20 is selected as the fixed outer curve 5a, and the inner curve of the spiral body is The following is determined so that the contact between the spirals to create a plurality of sealed volumes is geometrically guaranteed. Further, since the turning inner curve 2b is in contact with the fixed outer curve 5a, the outer envelope 21 of the fixed-side basic vortex curve 20 is selected, and the fixed inner curve 5b is in contact with the turning outer curve 2a and thus is the fixed-side basic vortex curve. Ten outer envelopes 11 are selected.
[0050]
Here, the turning outer curve 2a 'and the fixed inner curve 5b' shown by the one-dot chain line correspond to the case where the angle α is 0 ° and correspond to the first embodiment, but in the case of the present embodiment, The basic vortex curve 10 on the turning side and the basic vortex curve 20 on the fixed side have the same shape and phase.(180 ° -α)Unlike the scroll shape shown in the first embodiment in which the phase difference is just 180 ° because of the shift, the thickness of the spiral wall can be changed between the fixed side and the turning side. Further, since the inner curve and the outer curve do not match at the beginning of winding of the spiral body, this winding start portion is determined as shown in FIGS. 25 and 26 as an example, as in the first embodiment. FIG. 25 shows the configuration of the winding start portion when the turning outer curve 2a, which is the basic vortex curve, is rotated (angle α) in the turning-side spiral 2, and FIG. The structure of the winding start part of the side spiral body 5 is shown. In the vortex curve shown in the figure, when the solid line does not rotate (α = 0 °), the broken line indicates the solid turning outer curve 2a in a clockwise direction (hereinafter referred to as a positive direction) around the origin O.Angle α timesIn this case, the dash-dot line is turned in the counterclockwise directionAngle-α timesIt is a case where it turned. in this way,Equation (1)The turning outer curve 2a (solid line) consisting of an algebraic spiral represented byAngle α timesBy turning, the thickness of the spiral wall of the swirling-side spiral body 2 increases, and the thickness of the spiral wall of the fixed-side spiral body 5 decreases. And converselyAngle-α timesIn the case of turning, the thickness of the spiral wall of the swirling-side spiral 2 becomes thin, and the thickness of the spiral wall of the fixed-side spiral 5 becomes thick.
[0051]
The configuration of the winding start portion is required to satisfy the condition that both the spirals do not interfere when the orbiting spiral 2 is revolved around the fixed spiral 5 with a radius of rotation e. Now, a method of connecting the inner curve and the outer curve with a single arc will be described. In the turning-side spiral body 2 shown in FIG. 25, the turning inside curve 2b and the turning outside curve 2a are formed by an arc having a turning radius e passing through a point A located at a half distance of the turning radius e from the origin O on the turning outside curve 2a. The curve 2a is connected smoothly. In the fixed-side spiral body 5 shown in FIG. 26, the fixed inner curve 5b and the fixed outer curve 5a are formed by an arc having a turning radius e passing through a point B which is a half of the turning radius e from the origin O 'on the fixed outer curve 5a. The curve 5a is smoothly connected. Note that the center position of the arc at this time changes depending on the rotation angle α, and the coordinates correspond to points A, A ′, and A ″ in FIG. 22, respectively.
[0052]
As can be seen from FIGS. 27 to 29 showing the change in the scroll shape due to the change in the rotation angle α, the thickness of the spiral wall of the swirling-side spiral body 2 and the fixed-side spiral body 5 depends on the value of the angle α. 28 and FIG. 29, when the angle α is the same numerical value and the direction (corresponding to the rotation direction) is different, it can be seen that the shapes of the swirling-side spiral 2 and the fixed-side spiral 5 are just interchanged. Further, as can be seen by comparing the area of the working chamber 6 at the end of the suction, the stroke volume is the same as that of the case where the rotation is not performed at α = 0 ° shown in FIG. In addition, the thickness of the spiral wall can be appropriately changed on the turning side and the spiral body can be made smaller than the involute curve as in the first embodiment. Here, an example in which the outer curve of the swirl-side spiral body 2 is rotated has been described, but the same configuration can be realized by rotating the fixed-side spiral body 5.
[0053]
The method for creating a spiral body in the present embodiment is the same as that described in the first embodiment. Further, as shown in FIG. 30 in which the meshing state of the center portion of the spiral body is enlarged, also in the spiral body of the present embodiment, the top clearance volume becomes zero similarly to the first embodiment, and the fluid in the top clearance is reduced. It has an excellent feature that there is no loss due to re-expansion. That is, in FIG. 30, the innermost chamber 6 a formed by the innermost contact points 8 and 8 ′ of the swirling-side spiral 2 and the fixed-side spiral 5 is, as is clear from FIG. Performs relatively revolving motion around the fixed-side spiral body 5 with a turning radius e (= OO ′), the order of (1), (2), (3), and (4) shown in FIG. The volume of the innermost chamber 6a formed by the contact points 8, 8 'decreases, and the top clearance volume becomes zero. For this reason, all the compressed fluid is discharged to the outside from a discharge port (not shown) without causing useless re-expansion. Although not shown in FIG. 24, since the discharge port must be formed at a position communicating with the innermost chamber 6a, the volume of the discharge port is the top clearance volume. Is smaller than the stroke volume and can be regarded as substantially zero.
[0054]
As described above, in the present embodiment, only the configuration of the winding start part of the spiral body shown in FIGS. 25 and 26 has been described. It can be zero.
[0055]
The above describes the method of constructing a spiral body with a different spiral wall thickness when the outer curve of the spiral body is used as the basic vortex curve.However, when the inner curve of the spiral body is used as the basic vortex curve, The angle α of the turning inside curve 2b or the fixed inside curve 5b is appropriately changed so that the phase difference between the turning inside curve 2b of a certain turning side spiral 2 and the fixed inside curve 5b of the fixed side spiral 5 becomes about 180 °. Is similarly configured. FIG. 26 shows an example.Equation (1)Is rotated by α = −30 ° around the origin O to form a turning inner curve 2b (basic vortex curve of the turning-side spiral body 2), and a fixed inner curve 5b (basic vortex of the fixed-side spiral body). Curve) has a phase difference with the turning inside curve 2b.(180 ° -α)The scroll shape at the time of is shown. When the inner curve is the basic vortex curve, the effect of the rotation (angle α) is opposite to that when the outer curve shown in FIG. 31 is the basic vortex curve, and α = −30 ° and α = 30 in FIG. As in the case of °, the spiral wall thickness of the swirling-side spiral body 2 is thick and the spiral wall thickness of the fixed-side spiral body 5 is thin. With this configuration, even if the material of the spiral body is different, the same strength can be obtained for the pressure acting on each part of the spiral body, and the bearing load is reduced by downsizing, so the reliability of the compressor is reduced. Is greatly improved.
[0056]
A fourth embodiment of the present invention will be described with reference to FIGS. In the configuration described in the third embodiment, although the basic vortex curves of the swirl-side spiral 2 and the fixed-side spiral 5 rotate, they are basically expressed by the same mathematical formula,Equation (1)Although the algebraic spiral represented by 基本 is basically used, the index k of the algebraic spiral is set to k <1.0, and the coefficient a of the algebraic spiral is set to an arbitrary constant. However, the present invention is not limited to this. In the following, as shown in the present embodiment, for example,Equation (1)Even if the coefficient a of the algebraic spiral or the index k of the algebraic spiral represented by is a function of the argument θ, the thickness of the spiral wall can be appropriately changed, and the strength of the spiral body is secured. The spiral body can be made smaller than the involute curve. In this case, the index k of the algebraic spiral is not limited to the range of k <1.0. Furthermore, the basic vortex curves of the swirl-side spiral body 2 and the fixed-side spiral body 5 may be configured by different curves.
[0057]
As shown in FIG. 32, the outer curve of the spiral is a basic spiral curve, and the outer curve 2a of the swirl-side spiral 2 and the outer curve 5a of the fixed-side spiral 5 are:Equation (1)The exponent k of the algebraic spiral and the coefficient a of the algebraic spiral are represented by different numerical values. In this case, it is not necessary to rotate the vortex curve, and a spiral body having the same effect as the spiral body shown in FIG. 19 can be formed by appropriately selecting two different basic vortex curves. In FIGS. 25 and 26, the winding start portion configuration in which a single arc is used as the connection curve when the outer curve of the spiral body is used as the basic vortex curve has been described. The present invention is not limited thereto, and various other configurations can be considered. 33, 34, and 35, another configuration of the winding start portion of the spiral body configured as described above will be described. 33 and 34 show the case where the outer curve of the spiral is taken as the basic spiral curve, and FIG. 35 shows the case where the inner curve of the spiral is taken as the basic spiral curve as shown in FIG. In each of FIGS. 33 to 35, the turning-side spiral body 2 and the fixed-side spiral body 5 are both represented by the same xy coordinate axis. FIG. 33 shows a case where the connection curve at the winding start portion is composed of two arcs, and a broken line shows the case of a single arc shown in FIGS. 25 and 26. The outer-side curve 2a and the inner-side curve 2b are connected by two arcs r1 and r2 in the revolving-side spiral body 2, and the outer-side curve 5a and the inner curve 5b are connected by the two side arcs r3 and r4 in the fixed-side spiral body 5. Have been. The connection points A and B between the arcs are in contact with a circle whose radius is half the turning radius e from the origin O (or O '), and the center coordinates of the arcs r1 and r4 and the arcs r2 and r3 are the same.
[0058]
FIG. 34 differs from FIG. 33 in that the winding start portion is constituted by an arc and a straight line. The arc radius r is the same on the turning side and the fixed side (ie, r = e), and the straight line connected to the arc is a circle having a radius equal to half of the turning radius e from the origin O (or O ′) as in FIG. The points A and B are in contact with each other. FIG. 35 shows a winding start configuration in which the inner curve of the spiral body shown in FIG. 31 is used as a basic vortex curve. The inner curves 2b and 5b and the outer curves 2a and 5a are connected by straight lines. In this case, the straight line touches a circle having a radius equal to half of the turning radius e at points A and B, but the center C of this circle is not on the origin O (or O ').
[0059]
As can be understood from the above description, the necessary conditions of the connecting line connecting the inner curve and the outer curve constituting the winding start portion of the spiral body are as follows. When the swirl-side spiral body 2 and the fixed-side spiral body 5 are inscribed at least in the inner curve and are represented by the same coordinate axis, a circle having a radius of half of the swirl radius e is inscribed between these connection lines. It consists of curves (including straight lines and arcs). With such a winding start configuration, the top clearance volume becomes zero as in FIG.
[0060]
A fifth embodiment of the present invention will be described with reference to FIGS. FIG. 36 is a plan view for explaining the spiral body forming method of this embodiment. Since the inner curve and the outer curve of the spiral body are almost connected at the start of winding, the connection curve as described above is almost unnecessary, and Is simplified. 36 and 37 show the basic vortex curves on the turning side and the fixed side, respectively, and the envelope of the circular locus drawn when the basic vortex curve is circularly moved with a radius of half the turning radius e. Reference numeral 39 indicates the configuration of the swirl side and the fixed side vortex curves, respectively. Solid line 10 is the basic vortex curve on the turning side,Equation (1)Is obtained by rotating the algebraic spiral represented by the following expression around the origin O by the angle α. Dashed lines 13 and 14 are the envelopes of the basic vortex curve 10, 13 is the outer envelope, and 14 is the inner envelope. Further, a solid line 20 is a basic vortex curve on the fixed side.(180 ° -α)It is rotated. Dashed lines 23 and 24 are the envelopes of the basic vortex curve 20, 23 is the outer envelope, and 24 is the inner envelope. Here, the spiral body is configured as follows so that the contact between the spirals for creating a plurality of sealed volumes is geometrically ensured. As the turning outer curve 2a, the inner envelope 14 of the turning-side basic vortex curve 10 is selected, and as the fixed outer curve 5a, the inner envelope 24 of the fixing-side basic vortex curve 20 is selected. As the inner curve of the spiral body, since the turning inner curve 2b contacts the fixed outer curve 5a, the outer envelope 23 of the fixed-side basic vortex curve 20 is selected, and the fixed inner curve 5b contacts the turning outer curve 2a. The outer envelope 13 of the turning-side basic vortex curve 10 is selected. Thus, the basic vortex curve 10 on the turning side and the basic vortex curve 20 on the fixed side have the same shape and phase.(180 ° -α)Because the structure is shifted, the thickness of the spiral wall can be changed between the swivel side and the fixed side, and the inner curve and the outer curve that constitute each spiral body are almost connected at the winding start part, Almost no connection curve is required, and the configuration can be simplified. With the configuration described above, various curves can be applied as the basic vortex curve as in the case shown in FIG. 25 described above. When the angle α is 0 °, the spiral bodies on the turning side and the fixed side have the same shape.
[0061]
FIGS. 40 to 43 are diagrams showing the change in the scroll shape due to the rotation (angle α) of the basic vortex curve and the meshing state at the center of the spiral body in the vortex curve construction method shown in FIGS. 36 to 39 (α). = 30 °). As can be seen from this figure, the thicknesses of the spiral walls of the swirl-side spiral body 2 and the fixed-side spiral body 5 can be changed according to the value of the angle α, as shown in FIGS. 27 to 30. The winding start part of each spiral body is constituted by a smooth curve, and the top clearance volume can be made zero.
[0062]
A sixth embodiment of the present invention will be described with reference to FIGS. FIGS. 44 to 47 are plan views for explaining a method of forming a spiral body. As in the embodiment shown in FIGS. 36 to 39, the inner curve and the outer curve of the spiral body are smoothly connected at the winding start portion, and the structure is changed. It can be simplified. In this embodiment, assuming that the turning radius of the scroll compressor is e, two radii e1 and e2 satisfying e = e1 + e2 are determined, and these values are appropriately selected to fix the scroll side spiral body 2 to the swirling side spiral body 2. The thickness of the spiral wall of the side spiral body 5 can be changed. 44 and 45 show the basic vortex curves on the turning side and the fixed side, and the envelopes of circular trajectories drawn when the basic vortex curves are circularly moved with the radius e1 and the radius e2. FIGS. 46 and 47 show, respectively. The configuration of the swirl side and fixed side vortex curves is shown. Solid line 10 is the basic vortex curve on the turning side,Equation (1)Is an algebraic spiral represented by A broken line 34 is an outer envelope when the basic vortex curve 10 is circularly moved at the radius e1, and a broken line 35 is an inner envelope when the basic vortex curve 10 is circularly moved at the radius e2. A solid line 20 is a fixed-side basic vortex curve, which is obtained by rotating the turning-side basic vortex curve 10 by 180 ° around the origin O. A broken line 36 is an outer envelope when the basic vortex curve 20 is circularly moved at the radius e2, and a broken line 37 is an inner envelope when the basic vortex curve 20 is circularly moved at the radius e1. Here, the spiral body is configured as follows so that the contact between the spirals for creating a plurality of sealed volumes is geometrically ensured. As the turning outer curve 2a, the inner envelope 35 of the turning-side basic vortex curve 10 is selected, and as the fixed outer curve 5a, the inner envelope 37 of the fixing-side basic vortex curve 20 is selected. As for the inner curve of the spiral body, since the turning inner curve 2b is in contact with the fixed outer curve 5a (37), the outer envelope 36 of the fixed-side basic vortex curve 20 separated from the inner envelope 37 by the distance of the turning radius e is formed. Similarly, the fixed inner curve 5b comes into contact with the turning outer curve 2a (35), so the outer envelope 34 of the turning-side basic vortex curve 10 separated by the distance of the turning radius e from the inner envelope 35 is selected. It is. As described above, the envelopes of two different radii e1 and e2 are considered in the basic vortex curve 10 and the basic vortex curve 20, respectively, and by setting e1> e2, the thickness of the spiral wall gradually changes depending on the spiral angle of the spiral. At the same time, the swirling-side spiral body 2 can be configured so that the thickness of the spiral wall as a whole is larger than that of the fixed-side spiral body 5. In the case of e1 <e2, conversely, the fixed-side spiral body 5 can be configured to have a larger spiral wall thickness than the swirl-side spiral body 2.
[0063]
Taking a compressor as an example of a scroll type fluid machine, the thickness of the spiral wall changes continuously according to the winding angle of the spiral, and the thickness of the spiral wall differs between the fixed side and the swirling side. Although another basic vortex curve construction method of the body has been described, the present invention can be applied to expanders and pumps. Further, in the present invention, as a form of movement of the scroll, one scroll is fixed and the other scroll performs a revolving motion without rotating at an arbitrary turning radius. The present invention can also be applied to a scroll type fluid machine of both rotation type having a motion form equivalent to the motion of the above. Also, as the basic vortex curve of the spiral bodyEquation (1)Although an algebraic spiral represented by is used, the present invention is not limited to this, and the method of constructing the spiral body disclosed in the present invention is a smooth arbitrary one in which the curvature of the spiral changes continuously. Can be applied to vortex curves.
[0064]
【The invention's effect】
As described above, according to the present invention, by using an algebraic spiral for the basic vortex curve, the spiral body can be downsized while securing the strength of the winding start portion of the spiral body, so that the bearing load is also reduced, A highly reliable scroll fluid machine can be provided. Further, since the thickness of the spiral wall can be gradually changed, the internal leakage of the fluid between the spiral bodies is reduced, and the top clearance volume can be reduced or reduced to zero, thereby improving the efficiency of the scroll fluid machine. it can. Further, by installing the scroll fluid machine, it is possible to provide a highly reliable air-conditioning system with excellent energy efficiency.
[0065]
Further, even when the material of the spiral body is different between the turning side and the fixed side, the thickness of the spiral wall continuously changes according to the winding angle of the spiral, while maintaining the required strength of the spiral wall. In addition to clarifying the structure of the spiral, the use of algebraic spirals for the basic vortex curve allows the spiral body to be smaller than the involute curve while ensuring the strength of the winding start of the spiral. it can.
[0066]
[Brief description of the drawings]
FIG. 1 is a configuration diagram of an air conditioner equipped with a scroll compressor according to a first embodiment of the present invention.
FIG. 2 is a configuration diagram of a revolving scroll of the present embodiment.
FIG. 3 is a cross-sectional view of FIG.
FIG. 4 is a plan view showing the operation principle of the scroll compressor of the embodiment.
FIG. 5 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 6 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 7 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 8 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 9 is a diagram for explaining the formation of the winding start portion of the scroll according to the present embodiment.
FIG. 10 is a diagram showing a locus of a cutter for processing a scroll shape according to the present embodiment.
FIG. 11 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 12 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 13 is a view for explaining the formation of the winding start portion of the scroll according to the present embodiment.
FIG. 14 is an enlarged view of a main part showing a meshing state of a center portion of a spiral body according to the embodiment.
FIG. 15 is a scroll-shaped plan view showing a second embodiment of the present invention.
FIG. 16 is a plan view of a scroll shape showing the embodiment.
FIG. 17 is a plan view of a scroll shape showing the embodiment.
FIG. 18 is a plan view of a scroll shape showing the embodiment.
FIG. 19 is a plan view of a scroll shape showing a third embodiment of the present invention.
FIG. 20 is a diagram for explaining the operation principle of the scroll compressor.
FIG. 21 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 22 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 23 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 24 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 25 is a plan view showing a configuration of a winding start portion of the revolving scroll according to the present embodiment.
FIG. 26 is a plan view showing a configuration of a winding start portion of the fixed scroll according to the present embodiment.
FIG. 27 is a plan view showing a change in scroll shape when an angle α is provided.
FIG. 28 is a plan view showing a change in scroll shape when an angle α is provided.
FIG. 29 is a plan view showing a change in scroll shape when an angle α is provided.
FIG. 30 is a plan view showing the meshing state of the center of the spiral.
FIG. 31 is a plan view showing a meshing state of a central part of a spiral body.
FIG. 32 is a scroll-shaped plan view showing a fourth embodiment of the present invention.
FIG. 33 is a plan view illustrating a configuration of a winding start portion according to the present embodiment.
FIG. 34 is a plan view showing a configuration of a winding start portion of the present embodiment.
FIG. 35 is a plan view showing a configuration of a winding start portion of the present embodiment.
FIG. 36 is a view illustrating a method of forming a scroll shape according to a fifth embodiment of the present invention.
FIG. 37 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 38 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 39 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 40 is a plan view showing a scroll shape change due to a change in the angle α in the present embodiment.
FIG. 41 is a plan view showing a scroll shape change due to a change in the angle α in this embodiment.
FIG. 42 is a plan view showing a scroll shape change due to a change in the angle α in this embodiment.
FIG. 43 is a plan view showing an engaged state of the center of the spiral body in the present embodiment.
FIG. 44 is a diagram illustrating a method of forming a scroll shape according to a fifth embodiment of the present invention.
FIG. 45 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 46 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
FIG. 47 is a diagram illustrating a method of forming a scroll shape according to the present embodiment.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... turning scroll, 2 ... turning side spiral body, 2a ... turning outside curve, 2b ... turning inside curve, 3 ... end plate, 4 ... fixed scroll, 5 ... fixed side spiral body, 5a ... fixed outside curve 5b: fixed inner curve, 6: working chamber, 6a: innermost chamber, 7: discharge port, 8, 8 '... contact point, 9: crankshaft, 10: turning-side basic vortex curve, 11, 13, 34: outer envelope of the turning-side basic vortex curve, 12, 14, 35 ... inner envelope of the turning-side basic vortex curve, 15: frame, 16: Oldham ring, 17: motor, 18: suction pipe, 19: discharge pipe, 20: fixed-side basic vortex curve, 21, 23, 36 ... fixed-side basic vortex curve outer envelope, 22, 24, 37 ... fixed-side basic vortex curve inner envelope, 30 ... scroll Compressor, 31: condenser, 32: expansion valve, 33: evaporator, O: center of rotating scroll, O ': solid Constant scroll center, e: turning radius, α: angle of rotation of vortex curve, e1, e2: radius of circular motion (revolving motion).

Claims (9)

Two scroll members formed by an end plate and a spiral body standing upright are engaged with each other with the spiral body facing inward, and one scroll member is the other scroll member. In a scroll-type fluid machine that revolves around the turning radius e so that it does not seem to rotate, the vortex curve outside the spiral is an outer curve, and the vortex curve inside the spiral is an inner curve. When the vortex curves of the two spiral bodies are a radial radius r, a deflection angle θ, a coefficient a of an algebraic spiral, and an index k of an algebraic spiral in a polar coordinate format, an algebraic spiral represented by the following equation: A scroll type fluid machine comprising an envelope obtained by swirling the spiral, wherein the thickness of the wall of the spiral body decreases from the inner circumference to the outer circumference.

2. The scroll-type fluid machine according to claim 1, wherein the index k of the algebraic spiral changes in accordance with the argument θ. The outer curves of the scrolls of the scroll members are formed by the inner envelopes of the algebraic spirals of the respective scroll members, and the inner curves of the scrolls of the scroll members are formed by the algebraic spirals of the other scroll members. 2. The scroll-type fluid machine according to claim 1, comprising an outer envelope of the scroll. Radius e1, e2 has a relation of the turning radius e and e = e1 + e2, the two scroll - each of the spiral of the seal member, the outer curve radius algebraic spiral of the respective scroll members respectively e1, 2. The inner curve when the swirling motion is performed at e2, and the inner curve includes the outer envelope when swirling the algebraic spirals of the other scroll members at the radii e1 and e2, respectively. Scroll type fluid machinery. The algebraic spiral of the one scroll member has an index k of k <1.0, and the algebraic spiral of the other scroll member is obtained by rotating the one algebraic spiral by about 180 °. 2. A scroll fluid machine according to claim 1. The algebraic spiral of the one scroll member has an index k of k> 1.0 and the coefficient a is set to a constant, and changes the index k of the algebraic spiral as a function of the argument θ. The scroll type fluid machine according to claim 1, wherein The algebraic spiral of the one scroll member is rotated about the origin by an angle α , and the algebraic spiral of the other scroll member is an angle (180 ° -α ) about the origin. The scroll type fluid machine according to claim 1, wherein the scroll type fluid machine is rotated. 2. The scroll according to claim 1, wherein said one scroll member is a revolving scroll member, and a spiral body of the revolving scroll member is thicker than a spiral body of the other scroll member. Type fluid machinery. Two scroll members formed by an end plate and a spiral body standing upright are engaged with each other with the spiral body facing inward, and one scroll member is the other scroll member. In a method for processing a scroll member of a scroll-type fluid machine that revolves with a turning radius e so that it does not seem to rotate, a spiral curve outside the spiral body is defined as an outer curve, and a spiral curve inside the spiral body is defined as an outer curve. Assuming that the vortex curves of the two spiral bodies are an inner curve, a radial coordinate r, a deflection angle θ, a coefficient a of an algebraic spiral, and an index k of an algebraic spiral are expressed by the following formulas in a polar coordinate format. A scroll member comprising an envelope when the algebraic spiral to be turned is turned, wherein the thickness of the wall of the spiral body is reduced from the inner circumference to the outer circumference, and one of the scroll members is a scroll member. The outer curve and the inner curve of the spiral body provided at Move the center of the cutter along the top, the scroll type fluid machine of the scroll for machining of the spiral of the other scroll member - Le member machining method.

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