JP4321220B2 - Scroll compressor - Google Patents

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JP4321220B2
JP4321220B2 JP2003375068A JP2003375068A JP4321220B2 JP 4321220 B2 JP4321220 B2 JP 4321220B2 JP 2003375068 A JP2003375068 A JP 2003375068A JP 2003375068 A JP2003375068 A JP 2003375068A JP 4321220 B2 JP4321220 B2 JP 4321220B2
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JP2005139935A (en
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清春 池田
崇史 瀬畑
慎 関屋
文昭 佐野
照彦 西木
毅 伏木
英治 渡邊
谷  真男
聡経 新井
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三菱電機株式会社
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この発明は冷凍・空調装置などに使用される冷媒圧縮機に関わるものである。   The present invention relates to a refrigerant compressor used in a refrigeration / air conditioner or the like.
図5は従来のスクロール圧縮機の要部断面図である。図において、吸入冷媒ガスは固定スクロール1の鏡板外周から半径方向に貫通して設けた吸入通路1aより、固定スクロール1と揺動スクロール2とにより形成される圧縮室1cの外周部(圧縮室外周空間1g)に流入する。   FIG. 5 is a cross-sectional view of a main part of a conventional scroll compressor. In the figure, the suction refrigerant gas passes through the suction passage 1a provided in the radial direction from the outer periphery of the end plate of the fixed scroll 1, and the outer peripheral portion of the compression chamber 1c formed by the fixed scroll 1 and the orbiting scroll 2 (the outer periphery of the compression chamber). It flows into space 1g).
吸入冷媒ガスは電動機から駆動軸を介して与えられる回転を利用して圧縮され、高圧状態となって吐出口1fより密閉容器内に排出される。電動機部の配置される密閉容器内は高圧雰囲気で満たされ、この高圧冷媒ガスはやがて密閉容器の胴部に配置された吐出パイプより密閉容器外に排出される。   The sucked refrigerant gas is compressed using the rotation given from the electric motor through the drive shaft, becomes a high pressure state, and is discharged into the sealed container from the discharge port 1f. The inside of the sealed container in which the electric motor unit is disposed is filled with a high-pressure atmosphere, and this high-pressure refrigerant gas is eventually discharged out of the sealed container through a discharge pipe disposed in the trunk of the sealed container.
ここで、固定スクロール1に設けられた吸入通路1aは2つの径からなる同軸円筒面11、12で構成されている。小径の円筒面11には、圧縮室外周空間と連通する切り欠き11aが設けられているとともに、小径の円筒面11の内部には円筒面にガイドされて移動可能な円筒形の弁13と、この弁13を付勢するバネ14が収納されている。   Here, the suction passage 1a provided in the fixed scroll 1 is composed of coaxial cylindrical surfaces 11 and 12 having two diameters. The small-diameter cylindrical surface 11 is provided with a notch 11a communicating with the outer peripheral space of the compression chamber, and the small-diameter cylindrical surface 11 has a cylindrical valve 13 that is guided by the cylindrical surface and is movable. A spring 14 for energizing the valve 13 is accommodated.
一方大径の円筒面12には密閉容器の外側より挿入された銅などの低剛性材料からなる外側パイプ15が、小径の円筒面11との段部1bに突き当てられて取り付けられるとともに、高剛性材料からなる内側パイプ16が外側パイプ15内周に圧入して取り付けられている。この圧入により押し広げられた外側パイプ15の外周は、大径の円筒面12の内周に固着することにより、吸入通路1aと密閉容器との気密は保たれている。   On the other hand, an outer pipe 15 made of a low-rigidity material such as copper inserted from the outside of the sealed container is attached to the large-diameter cylindrical surface 12 while being abutted against the step portion 1b with the small-diameter cylindrical surface 11. An inner pipe 16 made of a rigid material is press-fitted and attached to the inner periphery of the outer pipe 15. The outer periphery of the outer pipe 15 pushed and expanded by the press-fitting is fixed to the inner periphery of the large-diameter cylindrical surface 12, so that the airtightness between the suction passage 1a and the sealed container is maintained.
圧縮機の運転が開始されると圧縮室1cが吸入冷媒ガスを取り込むため負圧となり、この負圧が小径の円筒面11に設けられた切り欠き11aを通じて弁13背面に作用するため、弁13はバネ力に打ち勝って圧縮機半径方向の中心側に移動し、内側パイプ16と弁13の端面間に形成された流路から冷媒ガスが流入して、切り欠き11aを通じて圧縮室外周空間に取り込まれて圧縮される構造となっている。   When the operation of the compressor is started, the compression chamber 1c takes in the intake refrigerant gas, so that a negative pressure is generated. This negative pressure acts on the back surface of the valve 13 through the notch 11a provided in the small-diameter cylindrical surface 11. Overcomes the spring force and moves to the center side in the radial direction of the compressor. The refrigerant gas flows in from the flow path formed between the inner pipe 16 and the end face of the valve 13, and is taken into the outer circumferential space of the compression chamber through the notch 11a. The structure is compressed.
圧縮機が運転を停止すると、弁13はバネ14の発生する力により内側パイプ16側に移動してその端面間で密着し、吐出孔1fより逆流した高圧の冷媒ガスや、駆動軸の給油穴4aを通じて圧縮室外周空間に導かれた潤滑油の吸入パイプ3側空間3aへの流出を防止している。(たとえば特許文献1参照)   When the compressor stops operating, the valve 13 is moved to the inner pipe 16 side by the force generated by the spring 14 and closely contacts between its end faces, and the high-pressure refrigerant gas flowing backward from the discharge hole 1f or the oil supply hole of the drive shaft The lubricating oil guided to the outer peripheral space of the compression chamber through 4a is prevented from flowing out into the suction pipe 3 side space 3a. (For example, see Patent Document 1)
特開平1−34312号公報JP-A-1-34312
しかしながら、内側パイプ16端面を弁13の挿入されている小径の円筒面11に対して、高精度の直角度を保ちながら圧入組立てすることは困難であり、内側パイプ16と弁13の端面間には若干の隙間が生じる恐れがあった。   However, it is difficult to press-fit and assemble the end surface of the inner pipe 16 with respect to the small-diameter cylindrical surface 11 in which the valve 13 is inserted, while maintaining a high-accuracy squareness, and between the inner pipe 16 and the end surface of the valve 13 is difficult. There was a risk that some gaps would occur.
図6は内側パイプ16が傾斜して組み立てられた場合の一例であり、圧縮機運転停止時の弁13と内側パイプ16との端面間に隙間20が生じている。圧縮機の運転停止時にはこの隙間20を通じて、圧縮機室から吸入パイプ側空間3aへの冷媒の逆流が生じて、冷媒ガスの逆流音あるいは潤滑油10aの流出が発生し、騒音や信頼性上の課題が生じる恐れがあった。   FIG. 6 is an example of the case where the inner pipe 16 is assembled at an inclination, and a gap 20 is generated between the end faces of the valve 13 and the inner pipe 16 when the compressor is stopped. When the operation of the compressor is stopped, a reverse flow of the refrigerant from the compressor chamber to the suction pipe side space 3a occurs through the gap 20, and a reverse flow sound of the refrigerant gas or the outflow of the lubricating oil 10a occurs, resulting in noise and reliability. There was a risk of problems.
また、内側パイプ16の挿入不良などにより内側パイプ16端面の直角度が充分確保できない場合には、弁13外径と小径の円筒面11内径とのクリアランスを大きく設定して弁13の姿勢に自由度を許容させ、傾斜した内側パイプ16端面にならわせることで対応可能となるが、上記クリアランスを大きく設定した場合には、図7に示すように、弁13が小径の円筒面11の内面でこじれてひっかかる恐れがある。図7は、弁13が小径の円筒面11の内面でこじれてひっかかった場合の説明図である。   In addition, when the squareness of the end face of the inner pipe 16 cannot be sufficiently secured due to poor insertion of the inner pipe 16, the clearance between the outer diameter of the valve 13 and the inner diameter of the small cylindrical surface 11 can be set large to freely adjust the posture of the valve 13. However, when the clearance is set large, as shown in FIG. 7, the valve 13 is formed on the inner surface of the small-diameter cylindrical surface 11. There is a risk that it will be twisted. FIG. 7 is an explanatory diagram in the case where the valve 13 is caught by the inner surface of the small-diameter cylindrical surface 11.
このような状態で圧縮機が運転を停止した場合には、弁13は小径の円筒面11内をスムーズに移動できず、弁13と小径の円筒面11の内面との間に生じた隙間や、小径の円筒面11に設けられた切り欠き1gを通って圧縮室側から冷媒が吸入パイプ側空間3a側に逆流して、冷媒ガスの逆流音あるいはの流出が発生し、騒音や信頼性の面で問題となっていた。以上のように、従来においては、冷媒ガスの逆流音は圧縮機運転停止時の静粛性を損ない、また潤滑油の流出は軸受への給油量が不足して軸受の焼損事故を起こし圧縮機故障の原因となっていた。   When the compressor stops operating in such a state, the valve 13 cannot smoothly move in the small diameter cylindrical surface 11, and a gap generated between the valve 13 and the inner surface of the small diameter cylindrical surface 11 Then, the refrigerant flows backward from the compression chamber side to the suction pipe side space 3a side through the notch 1g provided in the small-diameter cylindrical surface 11, and the backflow sound or outflow of the refrigerant gas is generated. It was a problem in terms. As described above, in the past, the backflow sound of the refrigerant gas impairs the quietness when the compressor is shut down, and the outflow of lubricant causes the bearing to burn out due to insufficient oil supply to the bearing, causing the compressor to fail. It was the cause.
本発明の目的は、上記問題点を解決するためのものであり、低騒音で信頼性の高い圧縮機を提供することを目的とする。また、弁端面のシール性を向上させ、または冷媒ガスの逆流音発生を防止させ、または潤滑油の流出を防止することを目的とする。   An object of the present invention is to solve the above-described problems, and an object thereof is to provide a compressor with low noise and high reliability. It is another object of the present invention to improve the sealing performance of the valve end face, prevent the backflow noise of the refrigerant gas from being generated, or prevent the lubricating oil from flowing out.
本発明は、それぞれの渦巻歯を組合せることによって圧縮室を形成し、外側の圧縮室から内側の圧縮室へと前記圧縮室の容積を減少させながら吸入された冷媒を圧縮する固定スクロール、及び揺動スクロールと、前記固定スクロール、前記揺動スクロールとともに圧縮機構部を構成するフレームと、前記固定スクロールあるいは前記フレームに設けられ、前記外側の圧縮室に連通する切り欠き部を有する小径の円筒部および吸入された冷媒ガスを前記小径の円筒部の前記切り欠き部を介して前記外側の圧縮室に導く大径の円筒部とから構成される吸入流路と、前記小径の円筒部内部に設けられた円筒形状あるいは円板形状の弁と、前記小径の円筒部内に収納され、前記弁を大径の円筒部側に押圧するバネと、前記小径の円筒部と前記大径の円筒部との段部に設けられ、中央部に貫通穴を有し、前記小径の円筒部よりも大きく、前記大径の円筒部内径と略同等かあるいは前記大径の円筒部内径よりも小さな外径を有するリングと、前記大径の円筒部内面に設けられ、前記外側パイプよりも前記内側パイプを高剛性材料で構成し、前記外側パイプで前記リングを前記段部に押圧固定し、前記内側パイプを前記外側パイプ内に圧入して拡管して前記外側パイプを前記大径の円筒部内面に固着するようにして前記リングを前記段部に押圧固定する押圧固定手段と、を備え、運転時には、前記弁が前記バネのバネ力に打ち勝って前記吸入通路の前記小径の円筒部内を前記圧縮機の半径方向の中心側に移動することによって前記冷媒が前記切り欠き部を通じて前記外側の圧縮室に取り込まれて圧縮され、停止時には前記弁が前記リングの貫通孔を塞ぐことによって、前記冷媒の逆流を防止するようにしたものである。 The present invention forms a compression chamber by combining the respective spiral teeth, and a fixed scroll that compresses the sucked refrigerant while reducing the volume of the compression chamber from the outer compression chamber to the inner compression chamber, and A small-diameter cylindrical portion having an orbiting scroll, the fixed scroll, a frame constituting a compression mechanism unit together with the orbiting scroll, and a notch portion provided in the fixed scroll or the frame and communicating with the outer compression chamber. A suction flow path comprising a large-diameter cylindrical portion that guides the sucked refrigerant gas to the outer compression chamber through the notch portion of the small-diameter cylindrical portion, and is provided inside the small-diameter cylindrical portion. A cylindrical or disc-shaped valve, a spring that is housed in the small-diameter cylindrical portion and presses the valve toward the large-diameter cylindrical portion, the small-diameter cylindrical portion, and the large-diameter circle Provided with a through hole in the center, and is larger than the small diameter cylindrical portion, and is substantially the same as the large diameter cylindrical portion inner diameter or smaller than the large diameter cylindrical portion inner diameter. A ring having a diameter and an inner surface of the large-diameter cylindrical portion, the inner pipe is made of a highly rigid material than the outer pipe, and the inner pipe is pressed and fixed to the stepped portion by the outer pipe, Pressure fixing means for press-fitting a pipe into the outer pipe and expanding the pipe so that the outer pipe is fixed to the inner surface of the large-diameter cylindrical portion, and the ring is pressed and fixed to the stepped portion. The valve overcomes the spring force of the spring and moves inside the small diameter cylindrical portion of the suction passage toward the center in the radial direction of the compressor, whereby the refrigerant enters the outer compression chamber through the notch. Intake and pressure Is one in which the valve at the time stopped by closing the through hole of the ring, and to prevent the backflow of the refrigerant.
本発明の冷媒圧縮機は運転停止時に冷媒ガスの逆流音を防止し、また潤滑油の流出を防止することにより、静粛性および信頼性に優れた冷媒圧縮機を提供することができる。また、内側パイプの端面が小径の円筒面に対して傾斜していても、弁とリングの端面シールにより圧縮機運転停止時の冷媒逆流防止および潤滑油流出防止が行える。 The refrigerant compressor of the present invention can provide a refrigerant compressor excellent in quietness and reliability by preventing backflow noise of refrigerant gas when operation is stopped and preventing outflow of lubricating oil. Even if the end surface of the inner pipe is inclined with respect to the small-diameter cylindrical surface, the valve and ring end surface seals can prevent refrigerant backflow and lubricating oil outflow when the compressor is stopped.
実施の形態1.
本発明の実施の形態1を図1、図2に基づいて説明する。
図1は本発明の実施の形態1を表すスクロール圧縮機の縦断面図である。図2は吸入通路1a付近を拡大した要部説明図であり、圧縮機が運転を停止した状態を示している。
Embodiment 1 FIG.
A first embodiment of the present invention will be described with reference to FIGS.
1 is a longitudinal sectional view of a scroll compressor representing Embodiment 1 of the present invention. FIG. 2 is an explanatory view of a main part in which the vicinity of the suction passage 1a is enlarged, and shows a state where the compressor has stopped operating.
図において、密閉容器10内には鏡板の一方に板状渦巻歯を有する固定スクロール1と、同形状の板状渦巻歯および揺動軸受け2aを有する揺動スクロール2、コンプライアントフレーム3等から構成される圧縮機機構部100とステータとロータよろ構成される電動機7とが配置されており、この圧縮機機構部100と電動機7は電動機7の発生する回転力を圧縮機機構部100に伝達する駆動軸4によって連結されている。   In the figure, an airtight container 10 is composed of a fixed scroll 1 having a plate-like spiral tooth on one of its end plates, a rocking scroll 2 having the same shape of a plate-like spiral tooth and a rocking bearing 2a, a compliant frame 3 and the like. The compressor mechanism unit 100 and the motor 7 constituted by the stator and the rotor are arranged. The compressor mechanism unit 100 and the motor 7 transmit the rotational force generated by the motor 7 to the compressor mechanism unit 100. They are connected by a drive shaft 4.
冷媒ガスは、密閉容器10の胴部に設けられた吸入パイプ3より密閉容器10内に吸入され、固定スクロール1の鏡板外周から半径方向に貫通して設けた吸入通路1aより、前記固定スクロール1と揺動スクロール2とにより形成される圧縮室1cの外周部(圧縮室外周空間1g)に流入する。その後、吸入された冷媒ガスは、電動機7によって駆動軸4を介して与えられる回転力を利用して圧縮され、高圧状態となって固定スクロール1の吐出口1fより密閉容器10内に排出される。本実施の形態では、電動機部7の配置される密閉容器10内は高圧雰囲気で満たされ、この高圧冷媒ガスは、密閉容器10の胴部に設けられた吐出パイプ5より密閉容器10外に排出される。   Refrigerant gas is sucked into the sealed container 10 from the suction pipe 3 provided in the body portion of the sealed container 10, and the fixed scroll 1 is introduced from the suction passage 1 a provided in the radial direction from the outer periphery of the end plate of the fixed scroll 1. And the orbiting scroll 2 flows into the outer periphery of the compression chamber 1c (compression chamber outer space 1g). Thereafter, the sucked refrigerant gas is compressed by using the rotational force applied through the drive shaft 4 by the electric motor 7, becomes a high pressure state, and is discharged into the sealed container 10 from the discharge port 1 f of the fixed scroll 1. . In the present embodiment, the inside of the sealed container 10 in which the electric motor unit 7 is disposed is filled with a high-pressure atmosphere, and this high-pressure refrigerant gas is discharged out of the sealed container 10 from the discharge pipe 5 provided in the body part of the sealed container 10. Is done.
密閉容器10底部には潤滑油10aが貯留されており、この潤滑油10a内に駆動軸4下端が侵漬されている。駆動軸4中心には給油穴4aが設けられており、密閉容器10底部はこの給油穴4aおよび揺動軸受け2aおよび主軸受6aを介して圧縮室外周空間1gと連通している。運転中は密閉容器10内が高圧雰囲気で満たされるので、吸入冷媒ガスの低圧雰囲気との差圧により、潤滑油10aは給油穴4a内を上昇して揺動スクロール2に設けられた揺動軸受け2a、コンプライアントフレーム6に設けられた主軸受け6aを潤滑した後に圧縮室外周空間1gに導かれる。   Lubricating oil 10a is stored at the bottom of the sealed container 10, and the lower end of the drive shaft 4 is immersed in the lubricating oil 10a. An oil supply hole 4a is provided at the center of the drive shaft 4, and the bottom of the hermetic container 10 communicates with the compression chamber outer peripheral space 1g through the oil supply hole 4a, the swinging bearing 2a, and the main bearing 6a. Since the inside of the sealed container 10 is filled with a high pressure atmosphere during operation, the lubricating oil 10a rises in the oil supply hole 4a due to the differential pressure of the suction refrigerant gas from the low pressure atmosphere, and the swing bearing provided in the swing scroll 2 2a, after the main bearing 6a provided on the compliant frame 6 is lubricated, it is guided to the outer circumferential space 1g of the compression chamber.
ここで、図2を用いて吸入通路1a付近について説明する。固定スクロール1に設けられた吸入通路1aは2つの径からなる同軸円筒面で構成されており、小径の円筒面11には外周側圧縮室1gに連通する切り欠き11aが設けられているとともに、その内部には円筒面にガイドされて移動可能な円筒形の弁13と、この弁を付勢するバネ14が収納されている。   Here, the vicinity of the suction passage 1a will be described with reference to FIG. The suction passage 1a provided in the fixed scroll 1 is formed of a coaxial cylindrical surface having two diameters, and a small diameter cylindrical surface 11 is provided with a notch 11a communicating with the outer peripheral compression chamber 1g. A cylindrical valve 13 that is movable while being guided by a cylindrical surface and a spring 14 that urges the valve are accommodated therein.
一方大径の円筒面12には輪形状のリング17が小径の円筒面11との間に形成された段部1bに設置され、銅材料で構成される外側パイプ15を大径の円筒面12内径に挿入し、外側パイプ15先端と段部1bとの間にリング17を挟み込んで押圧固定すると同時に、高剛性材料で構成される内側パイプ16を外側パイプ15内周に圧入して取り付け、押し広げられた外側パイプ15外周が大径の円筒面12の内周と固着する構成となっている。したがって、外側パイプ15は内側パイプ16によって大径の円筒面12内周に押圧固定される。   On the other hand, on the large-diameter cylindrical surface 12, a ring-shaped ring 17 is installed on the step portion 1b formed between the small-diameter cylindrical surface 11 and the outer pipe 15 made of a copper material is connected to the large-diameter cylindrical surface 12. The inner pipe 16 is inserted into the inner diameter, the ring 17 is sandwiched between the tip of the outer pipe 15 and the stepped portion 1b and pressed and fixed. The outer periphery of the expanded outer pipe 15 is fixed to the inner periphery of the large-diameter cylindrical surface 12. Therefore, the outer pipe 15 is pressed and fixed to the inner periphery of the large-diameter cylindrical surface 12 by the inner pipe 16.
図3は内側パイプ16が傾斜して取り付けられた場合の説明図である。リング17は段部1bと外側パイプ15先端に挟み込んで押圧固定されているので、内側パイプ16の傾斜に関係なく、圧縮機運転停止時における圧縮室外側空間1gと吸入パイプ側空間3aの遮断(漏れ防止)は、弁13とリング17の端面により行われる。段部1bは小径の円筒面11に対して良好な直角度をもって加工が施されているので、リング17は段部1bに密着するように外側パイプ15によって押圧されるため弁13端面との平行度も良好に確保され、弁13とリング17の端面間でのシール性は良好な特性を示す。リング17は外側パイプ15先端にバックアップされて段部1bに押し付けられているので、リング17が吸入パイプ3側に後退して弁13端面との平行度が悪化したり、シール性が損なわれたりすることはない。これにより圧縮機運転停止時における冷媒逆流音の発生や潤滑油10aの流出は防止される。   FIG. 3 is an explanatory diagram when the inner pipe 16 is attached with an inclination. Since the ring 17 is sandwiched between the step portion 1b and the outer pipe 15 and fixed by pressing, the compression chamber outer space 1g and the suction pipe side space 3a are shut off when the compressor is stopped regardless of the inclination of the inner pipe 16. Leakage prevention) is performed by the end faces of the valve 13 and the ring 17. Since the step portion 1b is processed with a good squareness with respect to the small-diameter cylindrical surface 11, the ring 17 is pressed by the outer pipe 15 so as to be in close contact with the step portion 1b, and thus parallel to the end face of the valve 13. The degree of sealing is also good, and the sealing property between the end faces of the valve 13 and the ring 17 shows good characteristics. Since the ring 17 is backed up at the tip of the outer pipe 15 and pressed against the step portion 1b, the ring 17 moves backward toward the suction pipe 3 and the parallelism with the end face of the valve 13 is deteriorated or the sealing performance is impaired. Never do. Thereby, generation | occurrence | production of the refrigerant | coolant backflow sound at the time of compressor operation stop and the outflow of the lubricating oil 10a are prevented.
図4は本発明の実施の形態1を表すリング17近傍の拡大図である。リング17の外径は大径の円筒面12の内径にほぼ等しいか若干小さい程度の直径(シール性が損なわれない程度の軽微な力での圧入される程度の直径であってもよい)に加工され、またリング内径は小径の円筒面11の内径よりも小さい直径に加工されており、輪形状となっている。段部1bに面するリング17の端面は良好な平面度と面粗度に加工や成形によって製造されており、弁13との端面のシール性が向上する構成としている。リング17の外周エッジ部には段部1b外径側のR部に乗り上げることのない寸法の面取り加工が施されており、リング組立て後にリング端面と小径の円筒面11の直角度が確保される形状となっている。   FIG. 4 is an enlarged view of the vicinity of the ring 17 representing Embodiment 1 of the present invention. The outer diameter of the ring 17 is approximately equal to or slightly smaller than the inner diameter of the large cylindrical surface 12 (may be a diameter that can be press-fitted with a slight force that does not impair the sealing performance). The inner diameter of the ring is processed to be smaller than the inner diameter of the cylindrical surface 11 having a small diameter, and has a ring shape. The end face of the ring 17 facing the stepped portion 1b is manufactured by processing or molding with good flatness and surface roughness, and the sealing performance of the end face with the valve 13 is improved. The outer peripheral edge portion of the ring 17 is chamfered so as not to run over the R portion on the outer diameter side of the stepped portion 1b, and a perpendicularity between the ring end surface and the small-diameter cylindrical surface 11 is secured after the ring is assembled. It has a shape.
リング17を挟み込む(押圧する)外側パイプ15の先端は、リング17外径に近い場所を全周にわたり押圧した方がよい。外側パイプ15先端がリング17に対して傾斜してセットされると、リング17と外側パイプ15先端はある位相でのみ接触し、これを支点としてリングがばたつく可能性があるが、本実施の形態では外側パイプ15がリング17に対して傾斜してセットされた場合においても、外側パイプ15を低剛性材料である銅パイプやアルミパイプなどで構成しているので、内側パイプ16を圧入した際に外側パイプ15は半径方向に圧延されると同時に、円筒面軸方向にも圧延され、圧延された外側パイプ15の先端は、リング17外径に近い場所を全周にわたり接触して押圧力を発生することができる。したがってリング17が段部1bと外側パイプ15先端の間でばたつくことがなく、シール性も良好なため、低騒音で信頼性の高い圧縮機が得られる。   The tip of the outer pipe 15 that sandwiches (presses) the ring 17 is preferably pressed over the entire circumference at a location close to the outer diameter of the ring 17. If the tip of the outer pipe 15 is set to be inclined with respect to the ring 17, the ring 17 and the tip of the outer pipe 15 come into contact with each other only at a certain phase, and the ring may flutter using this as a fulcrum. Then, even when the outer pipe 15 is set to be inclined with respect to the ring 17, the outer pipe 15 is composed of a low-rigidity material such as a copper pipe or an aluminum pipe, so when the inner pipe 16 is press-fitted. The outer pipe 15 is rolled in the radial direction and at the same time in the axial direction of the cylindrical surface, and the tip of the rolled outer pipe 15 is brought into contact with the entire area around the outer diameter of the ring 17 to generate a pressing force. can do. Therefore, the ring 17 does not flutter between the step portion 1b and the tip of the outer pipe 15, and the sealing performance is good, so that a compressor with low noise and high reliability can be obtained.
以上のように、本実施の形態では、それぞれの渦巻歯を組合せることによって圧縮室1cを形成し、外側の圧縮室から内側の圧縮室へと前記圧縮室の容積を減少させながら吸入された冷媒を圧縮する固定スクロール1、及び揺動スクロール2と、前記固定スクロール1、前記揺動スクロール2とともに圧縮機構部100を構成するフレーム50と、固定スクロール1あるいはフレーム50に設けられ、外側の圧縮室あるいは圧縮室外周空間1gに連通する切り欠き部11aを有する小径の円筒部11および吸入された冷媒ガスを小径の円筒部11を介して外側の圧縮室1gに導く大径の円筒部12とから構成される吸入流路と、小径の円筒部11内部に設けられた円筒形状あるいは円板形状の弁13と、小径の円筒部11内に収納され、弁13を大径の円筒部12側に押圧するバネ14と、小径の円筒部11と大径の円筒部12との段部1bに設けられ、中央部に貫通穴を有し、小径の円筒部11内径よりも大きく、大径の円筒部12内径と略同等かあるいは大径の円筒部12内径よりも小さな外径を有するリング17と、大径の円筒部12内に設けられ、リング17を段部1bに押圧固定する押圧固定手段15、16と、を備え、弁13がリング17の貫通孔を塞ぐことによって、冷媒ガスの逆流を防止するようにしたので、内側パイプ16の端面が小径の円筒面11に対して傾斜していても、弁13とリング17の端面シールにより圧縮機運転停止時の冷媒逆流防止および潤滑油流出防止が行える。   As described above, in the present embodiment, the compression chamber 1c is formed by combining the respective spiral teeth, and suction is performed while reducing the volume of the compression chamber from the outer compression chamber to the inner compression chamber. The fixed scroll 1 and the orbiting scroll 2 for compressing the refrigerant, the frame 50 constituting the compression mechanism unit 100 together with the fixed scroll 1 and the orbiting scroll 2, and the fixed scroll 1 or the frame 50 are provided on the outer compression. A small-diameter cylindrical portion 11 having a notch portion 11a communicating with the outer space 1g of the chamber or the compression chamber, and a large-diameter cylindrical portion 12 for guiding the sucked refrigerant gas to the outer compression chamber 1g via the small-diameter cylindrical portion 11; A suction flow path constituted by: a cylindrical or disk-shaped valve 13 provided inside the small-diameter cylindrical portion 11; Is provided on the step portion 1b of the small-diameter cylindrical portion 11 and the large-diameter cylindrical portion 12, and has a through hole in the central portion. A ring 17 having an outer diameter larger than the inner diameter and substantially equal to the inner diameter of the large-diameter cylindrical portion 12 or smaller than the inner diameter of the large-diameter cylindrical portion 12, and a ring 17 provided in the large-diameter cylindrical portion 12 Pressure fixing means 15, 16 for pressing and fixing to the portion 1 b, and the valve 13 blocks the through hole of the ring 17 so as to prevent the reverse flow of the refrigerant gas, so that the end surface of the inner pipe 16 has a small diameter. Even if it is inclined with respect to the cylindrical surface 11, the end face seals of the valve 13 and the ring 17 can prevent the backflow of refrigerant and the outflow of lubricating oil when the compressor is stopped.
また、円筒面の段部平面を円筒面に良好な直角度をもって設定すれば、リング17は段部平面に密着して弁13端面との平行度が容易に確保される。また、リング17は外側パイプ15先端にバックアップされて円筒面段部1bに押し付けられるので、リング17が吸入パイプ3側に後退して弁13端面との平行度が悪化してシール性が損なわれることはない。   Further, if the stepped plane of the cylindrical surface is set with a good perpendicularity to the cylindrical surface, the ring 17 is in close contact with the stepped plane and the parallelism with the end face of the valve 13 is easily ensured. Also, since the ring 17 is backed up at the tip of the outer pipe 15 and pressed against the cylindrical surface step 1b, the ring 17 moves backward to the suction pipe 3 side, the degree of parallelism with the end face of the valve 13 deteriorates, and the sealing performance is impaired. There is nothing.
また、リング17の段部1bへの押圧固定手段15、16は、外側パイプ15と内側パイプ16で構成され、外側パイプ15よりも内側パイプ16を高剛性材料で構成し、外側パイプ15でリング17を段部1bに押圧固定し、内側パイプ16を外側パイプ15内に圧入して拡管して外側パイプ15を大径の円筒部12内面に固着するようにしたので、簡単な構成で組立が容易でありながらシール性が向上するので、信頼性が高く低コストで組立が容易な圧縮機が得られる。   Further, the pressing and fixing means 15, 16 to the step portion 1 b of the ring 17 are constituted by the outer pipe 15 and the inner pipe 16, the inner pipe 16 is made of a highly rigid material than the outer pipe 15, and the outer pipe 15 is used as a ring. 17 is pressed and fixed to the stepped portion 1b, and the inner pipe 16 is press-fitted into the outer pipe 15 and expanded to fix the outer pipe 15 to the inner surface of the large-diameter cylindrical portion 12. Since the sealing performance is improved while being easy, it is possible to obtain a compressor that is highly reliable, easy to assemble at low cost.
また、リング17の外径部に面取りを設けたので、リング17の大径の円筒部への挿入や圧入が容易となり、リング17の変形が生じにくく、シール性が向上する。また、内側パイプ16を鉄系材料とし、外側パイプ15を銅系材料あるいはアルミ系材料としたので、外側パイプ15の内面に内側パイプ16を圧入した場合に内側パイプ16によって外側パイプ15が拡管されやすく、外側パイプ15が大径の円筒面12の内面に密着しやすくなり、外側パイプ15と大径の円筒面12とのシール性が向上し、信頼性の高い圧縮機が得られる。   Further, since the outer diameter portion of the ring 17 is chamfered, it is easy to insert and press-fit the ring 17 into the large-diameter cylindrical portion, the deformation of the ring 17 hardly occurs, and the sealing performance is improved. Further, since the inner pipe 16 is made of an iron-based material and the outer pipe 15 is made of a copper-based material or an aluminum-based material, the outer pipe 15 is expanded by the inner pipe 16 when the inner pipe 16 is press-fitted into the inner surface of the outer pipe 15. Thus, the outer pipe 15 is easily adhered to the inner surface of the large-diameter cylindrical surface 12, the sealing performance between the outer pipe 15 and the large-diameter cylindrical surface 12 is improved, and a highly reliable compressor is obtained.
本発明の実施の形態1を表す圧縮機の縦断面図である。It is a longitudinal cross-sectional view of the compressor showing Embodiment 1 of this invention. 本発明の実施の形態1を表す圧縮機の吸入通路1a付近を拡大した要部説明図である。It is principal part explanatory drawing which expanded the suction passage 1a vicinity of the compressor showing Embodiment 1 of this invention. 本発明の実施の形態1を表す圧縮機の内側パイプ16が傾斜して取り付けられた場合の説明図である。It is explanatory drawing when the inner pipe 16 of the compressor showing Embodiment 1 of this invention is attached inclining. 本発明の実施の形態1を表すリング17近傍の拡大図である。It is an enlarged view of the ring 17 vicinity showing Embodiment 1 of this invention. 従来のスクロール圧縮機の要部断面図である。It is principal part sectional drawing of the conventional scroll compressor. 内側パイプ16が傾斜して組み立てられた場合の説明図である。It is explanatory drawing when the inner side pipe 16 is inclined and assembled. 弁13が小径の円筒面11の内面でこじれてひっかかった場合の説明図である。It is explanatory drawing when the valve 13 is twisted and caught on the inner surface of the small-diameter cylindrical surface 11.
符号の説明Explanation of symbols
1 固定スクロール、1a 吸入通路、1b 段部、1c 圧縮室、1f 吐出口、1g 圧縮室外周空間、2 揺動スクロール、 2a 揺動軸受け、3 吸入パイプ、 3a 吸入パイプ側空間、4 駆動軸、 4a 給油穴、5 吐出パイプ、 6 フレーム、 6a 主軸受、 7 電動機、10 密閉容器、 10a 潤滑油、11 小径の円筒面、 11a 切り欠き、 12 大径の円筒面、13 弁、 14 バネ、 15 外側パイプ、 16 内側パイプ、 17 リング、 20 隙間、100圧縮機機構部。 DESCRIPTION OF SYMBOLS 1 Fixed scroll, 1a Suction passage, 1b Step part, 1c Compression chamber, 1f Discharge port, 1g Compression chamber outer peripheral space, 2 Swing scroll, 2a Swing bearing, 3 Suction pipe, 3a Suction pipe side space, 4 Drive shaft, 4a Oil supply hole, 5 Discharge pipe, 6 Frame, 6a Main bearing, 7 Electric motor, 10 Airtight container, 10a Lubricating oil, 11 Small diameter cylindrical surface, 11a Notch, 12 Large diameter cylindrical surface, 13 Valve, 14 Spring, 15 Outer pipe, 16 inner pipe, 17 ring, 20 gap, 100 compressor mechanism.

Claims (3)

  1. それぞれの渦巻歯を組合せることによって圧縮室を形成し、外側の圧縮室から内側の圧縮室へと前記圧縮室の容積を減少させながら吸入された冷媒を圧縮する固定スクロール、及び揺動スクロールと、前記固定スクロール、前記揺動スクロールとともに圧縮機構部を構成するフレームと、前記固定スクロールあるいは前記フレームに設けられ、前記外側の圧縮室に連通する切り欠き部を有する小径の円筒部および吸入された冷媒ガスを前記小径の円筒部の前記切り欠き部を介して前記外側の圧縮室に導く大径の円筒部とから構成される吸入流路と、前記小径の円筒部内部に設けられた円筒形状あるいは円板形状の弁と、前記小径の円筒部内に収納され、前記弁を大径の円筒部側に押圧するバネと、前記小径の円筒部と前記大径の円筒部との段部に設けられ、中央部に貫通穴を有し、前記小径の円筒部よりも大きく、前記大径の円筒部内径と略同等かあるいは前記大径の円筒部内径よりも小さな外径を有するリングと、前記大径の円筒部内面に設けられ、外側パイプと内側パイプで構成され、前記外側パイプよりも前記内側パイプを高剛性材料で構成し、前記外側パイプで前記リングを前記段部に押圧固定し、前記内側パイプを前記外側パイプ内に圧入して拡管して前記外側パイプを前記大径の円筒部内面に固着するようにして前記リングを前記段部に押圧固定する押圧固定手段と、を備え、運転時には、前記弁が前記バネのバネ力に打ち勝って前記吸入通路の前記小径の円筒部内を前記圧縮機の半径方向の中心側に移動することによって前記冷媒が前記切り欠き部を通じて前記外側の圧縮室に取り込まれて圧縮され、停止時には前記弁が前記リングの貫通孔を塞ぐことによって、前記冷媒の逆流を防止するようにしたことを特徴とするスクロール圧縮機。 A fixed scroll that forms a compression chamber by combining the respective spiral teeth, and compresses the sucked refrigerant while reducing the volume of the compression chamber from the outer compression chamber to the inner compression chamber; A frame that forms a compression mechanism together with the fixed scroll and the orbiting scroll, a small-diameter cylindrical portion that is provided in the fixed scroll or the frame and has a notch communicating with the outer compression chamber, and a suction unit A suction flow path composed of a large-diameter cylindrical portion that guides the refrigerant gas to the outer compression chamber through the notch portion of the small-diameter cylindrical portion, and a cylindrical shape provided inside the small-diameter cylindrical portion Alternatively, a disk-shaped valve, a spring housed in the small-diameter cylindrical portion and pressing the valve toward the large-diameter cylindrical portion, and a step of the small-diameter cylindrical portion and the large-diameter cylindrical portion A ring having a through hole in a central portion and having an outer diameter that is larger than the small-diameter cylindrical portion and substantially equal to the large-diameter cylindrical portion inner diameter or smaller than the large-diameter cylindrical portion inner diameter. the provided in the cylindrical inner surface of the large diameter, is constituted by the outer pipe and inner pipe, than the outer pipe constitutes the inner pipe at high rigid material, pressed and fixed to the ring on the step portion in the outer pipe And pressing and fixing means for pressing and fixing the ring to the stepped portion so that the inner pipe is press-fitted into the outer pipe and expanded to fix the outer pipe to the inner surface of the large-diameter cylindrical portion , In operation, the valve overcomes the spring force of the spring and moves inside the small-diameter cylindrical portion of the suction passage toward the center in the radial direction of the compressor, whereby the refrigerant passes through the notch to the outside. It is compressed is taken into the compression chamber by the valve at the time of stop blocks the through hole of the ring, the scroll compressor being characterized in that so as to prevent backflow of the refrigerant.
  2. 前記リングの外径部に面取りを設けたことを特徴とする請求項1に記載のスクロール圧縮機。 The scroll compressor according to claim 1, wherein a chamfer is provided at an outer diameter portion of the ring.
  3. 前記内側パイプを鉄系材料とし、前記外側パイプを銅系材料あるいはアルミ系材料としたことを特徴とする請求項または請求項に記載のスクロール圧縮機。 The scroll compressor according to claim 1 or 2 , wherein the inner pipe is made of an iron-based material, and the outer pipe is made of a copper-based material or an aluminum-based material.
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JP3034661B2 (en) * 1991-10-03 2000-04-17 株式会社日立製作所 Hermetic electric compressor
JP3448469B2 (en) * 1997-09-26 2003-09-22 三洋電機株式会社 Scroll compressor
JP2000097179A (en) * 1998-09-24 2000-04-04 Mitsubishi Electric Corp Rotary compressor
CN2431467Y (en) * 2000-05-19 2001-05-23 江明榆 Stainless steel stamp-welded type plastic composite pipe fitting
CN2483583Y (en) * 2001-02-27 2002-03-27 江明榆 Stainless steel and plastic composite pipe connecting device
JP3988435B2 (en) * 2001-10-29 2007-10-10 三菱電機株式会社 Scroll compressor
JP4032281B2 (en) * 2001-11-08 2008-01-16 三菱電機株式会社 Scroll compressor

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2434159A2 (en) 2010-09-28 2012-03-28 Mitsubishi Electric Corporation Scroll compressor with a check valve
JP2012072680A (en) * 2010-09-28 2012-04-12 Mitsubishi Electric Corp Scroll compressor

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CN100359177C (en) 2008-01-02
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