JP4598695B2 - Compressor - Google Patents

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JP4598695B2
JP4598695B2 JP2006059085A JP2006059085A JP4598695B2 JP 4598695 B2 JP4598695 B2 JP 4598695B2 JP 2006059085 A JP2006059085 A JP 2006059085A JP 2006059085 A JP2006059085 A JP 2006059085A JP 4598695 B2 JP4598695 B2 JP 4598695B2
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valve
compression chamber
passage
valve passage
spring
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JP2007239474A (en
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崇史 瀬畑
文昭 佐野
照彦 西木
谷　　真男
英治 渡邊
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Mitsubishi Electric Corp
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Description

この発明は、冷凍空調装置に用いる圧縮機に関し、更に詳しくはスクロール圧縮機の圧縮対象の冷媒を外部から導入する弁構造の改良に関するものである。   The present invention relates to a compressor used in a refrigeration air conditioner, and more particularly to an improvement in a valve structure for introducing a refrigerant to be compressed by a scroll compressor from the outside.

従来のスクロール圧縮機は、密閉容器内に板状渦巻歯を有する固定スクロール及び揺動スクロールを備え、固定スクロールの板状渦巻歯と揺動スクロールの板状渦巻歯とが噛み合わされて圧縮室が形成され、固定スクロールに対して揺動スクロールを自転しないように旋回運動させて圧縮室内の冷媒を圧縮するものである。そして、固定スクロールの板状渦巻歯には吸入管に連通するように、水平方向に延びる弁通路が設けられ、その内側に弁が摺動可能に設けられ、吸入管が密閉容器を貫通して圧入されている。さらに、弁はバネによって吸入管の閉鎖方向に付勢されており、吸入管の端面で突き当たり、この端面でシールされ、冷媒が機外に逆流するのを防止している。その弁の周面には開閉方向に沿って逃がし溝が形成されている。   A conventional scroll compressor includes a fixed scroll and a swing scroll having a plate-like spiral tooth in a hermetically sealed container, and the compression chamber is formed by meshing the plate-like spiral tooth of the fixed scroll and the plate-like spiral tooth of the swing scroll. It is formed and compresses the refrigerant in the compression chamber by turning the swing scroll so as not to rotate with respect to the fixed scroll. A plate-like spiral tooth of the fixed scroll is provided with a valve passage extending in the horizontal direction so as to communicate with the suction pipe, and a valve is slidably provided therein, and the suction pipe passes through the sealed container. It is press-fitted. Further, the valve is urged by the spring in the closing direction of the suction pipe, hits the end face of the suction pipe and is sealed at the end face to prevent the refrigerant from flowing back to the outside of the machine. A relief groove is formed in the circumferential surface of the valve along the opening and closing direction.

また、弁通路の両側面には圧縮室に通じる圧縮室連通路と連通する同形状の弁通路開口部がそれぞれ設けられ、これら弁通路開口部にバネの終端面が位置している。
運転時には、冷媒が吸入管から吸入され、吸入圧力によって弁はバネ力に打ち勝って弁止まり面に突き当たり、吸入冷媒は弁通路開口部を通り、圧縮室連通路を経て圧縮室に入る。また、運転停止時は、吐出圧力と吸入圧力の差圧によって冷媒は圧縮室より圧縮室連通路、弁通路開口部及び弁通路を通って圧縮機外に逆流しようとする。バネを通過して弁背面導入された冷媒が弁を吸入管の端面に押し戻し、シールされて冷媒の逆流を防ぐ。
さらに、弁の周面に、開閉方向に沿って逃がし溝が形成されているため、大量の液冷媒や冷凍機油が弁通路に滞留している状態においても、これら滞留している液冷媒や冷凍機油が逃がし溝を通るため、弁に対する抵抗とはならず、弁が閉じ遅れることなくスムーズ閉鎖することができ、弁の閉じ遅れによる逆転音の発生を防止でき、冷凍機油の圧縮機外に持ち出されることを防止できる（例えば、特許文献１参照）。 In addition, valve passage openings of the same shape communicating with the compression chamber communication passage communicating with the compression chamber are respectively provided on both side surfaces of the valve passage, and the end face of the spring is located in these valve passage openings.
During operation, the refrigerant is sucked from the suction pipe, the valve overcomes the spring force by the suction pressure, hits the valve stop surface, and the suction refrigerant passes through the valve passage opening and enters the compression chamber through the compression chamber communication passage. When the operation is stopped, the refrigerant tends to flow backward from the compression chamber to the outside of the compressor through the compression chamber communication passage, the valve passage opening, and the valve passage due to the differential pressure between the discharge pressure and the suction pressure. The refrigerant introduced through the spring and introduced into the back of the valve pushes the valve back to the end face of the suction pipe and is sealed to prevent back flow of the refrigerant.
Furthermore, since a relief groove is formed along the opening and closing direction on the peripheral surface of the valve, even when a large amount of liquid refrigerant or refrigerating machine oil stays in the valve passage, these staying liquid refrigerant or freezer Since the machine oil passes through the escape groove, it does not become resistance to the valve, it can be closed smoothly without delay in closing, it can prevent reverse sound due to valve closing delay, and it is taken out of the compressor of the refrigerator oil (See, for example, Patent Document 1).

特開２００２−１４７３６０号公報JP 2002-147360 A

最近は圧縮機の大きさは同一のまま上限容量を大きくする傾向にあり、冷媒流量が以前の上限より大きくなっている。
特許文献１に記載の従来のスクロール圧縮機の弁構造では、冷媒流量が大きくなりすぎると、運転停止直後に逆流する冷媒量も大きくなるので、バネの側面より付加する力も大きくなる。また、冷媒の作動圧力が高くなり、かつ運転範囲も拡大する傾向にあるので、運転中の高低圧差が大きくなり、これによっても停止直後高差圧によりバネの側面から付加する力も大きくなる。
このように、バネの側面より付加する力が大きくなると、弁通路開口部が両側面とも同形状であるため、弁を押し戻す間にバネ端面部は冷媒によって圧縮室連通路と反対側の弁通路開口部方向に押され、弁通路開口部からはみ出し、最悪の場合はバネが弁通路開口部を通って飛び出す可能性があるという問題があった。 Recently, the upper limit capacity tends to be increased while the size of the compressor remains the same, and the refrigerant flow rate is larger than the previous upper limit.
In the valve structure of the conventional scroll compressor described in Patent Document 1, if the refrigerant flow rate becomes too large, the amount of refrigerant that flows backward immediately after the operation stops increases, so that the force applied from the side surface of the spring also increases. Further, since the operating pressure of the refrigerant tends to increase and the operating range tends to expand, the high / low pressure difference during operation increases, and this also increases the force applied from the side of the spring due to the high differential pressure immediately after stopping.
In this way, when the force applied from the side surface of the spring increases, the valve passage opening has the same shape on both side surfaces, so that the spring end surface portion is opposite to the compression chamber communication passage by the refrigerant while pushing back the valve. There is a problem in that the spring is pushed in the direction of the opening and protrudes from the valve passage opening, and in the worst case, the spring may jump out through the valve passage opening.

この発明は、上記のような課題を解決するためになされたもので、バネの弁通路開口部へのはみ出しを防止し、弁の開閉動作が妨げられることによる逆転音の発生や冷凍機油の機外への持ち出されて軸受が給油不足なり、軸受信頼性が低下することを防止する圧縮機を得ることを目的とするものである。   The present invention has been made to solve the above-described problems, and prevents the spring from protruding to the valve passage opening, and the reverse opening of the valve due to the hindering of the valve opening / closing operation. It is an object of the present invention to obtain a compressor that prevents the bearing reliability from being lowered due to being taken out and the bearing being insufficiently lubricated.

この発明に係る圧縮機は、密閉容器内に導入された冷媒を圧縮室で圧縮する圧縮機構部と、前記圧縮機構部を駆動する電動機要素とを備え、前記密閉容器を貫通して設けられた吸入管と前記圧縮室に通じる圧縮室連通路とに連通する弁通路を前記圧縮機構部に設け、前記弁通路内に摺動自在な弁と、該弁を前記吸入管の弁座面に付勢するバネと、該バネを保持し、且つ前記吸入管より冷媒が吸入された時に該冷媒の吸入圧力によりバネのバネ力に打ち勝って押し付けられる前記弁を止める弁止まり面とを設け、前記弁通路の両側面に前記圧縮室連通路と連通する弁通路開口部をそれぞれ設け、前記圧縮室連通路と反対側の弁通路開口部を前記圧縮室連通路側の弁通路開口部より小さく形成し、前記弁通路の側面で前記小さくした弁通路開口部と前記弁止まり面との間の位置にバネはみ出し防止用壁を設けるようにしたものである。   The compressor according to the present invention includes a compression mechanism that compresses the refrigerant introduced into the sealed container in a compression chamber, and an electric motor element that drives the compression mechanism, and is provided through the sealed container. A valve passage communicating with the suction pipe and the compression chamber communication passage communicating with the compression chamber is provided in the compression mechanism portion, a valve slidable in the valve passage, and the valve is attached to a valve seat surface of the suction pipe. A spring that holds the spring and a valve stop surface that stops the valve that is pressed against the spring force of the spring by the suction pressure of the refrigerant when the refrigerant is sucked from the suction pipe; Valve passage openings that communicate with the compression chamber communication passage are respectively provided on both side surfaces of the passage, and a valve passage opening opposite to the compression chamber communication passage is formed smaller than a valve passage opening on the compression chamber communication passage side. , The reduced valve passage opening on the side of the valve passage Is obtained so as to provide a spring extrusion preventing wall at a position between said valve stop surface.

この発明の圧縮機においては、密閉容器を貫通して設けられた吸入管と密閉容器内に導入された冷媒を圧縮する圧縮室に通じる圧縮室連通路とに連通する弁通路を圧縮機構部に設け、その弁通路の両側面に圧縮室連通路に連通する弁通路開口部をそれぞれ設け、圧縮室連通路と反対側の弁通路開口部を圧縮室連通路側の弁通路開口部より小さく形成し、弁通路の側面で小さくなった弁通路開口部と弁止まり面との間の位置にバネはみ出し防止用壁を設けたので、圧縮機の運転停止時に逆流する冷媒量が多くなったり、高低圧差が大きくなったりして弁を押し戻す間にバネのバネ端面部は冷媒によって圧縮室連通路と反対側の弁通路開口部方向に押され、弁通路開口部からはみ出そうとするが、そのバネ端面部のはみ出しはバネはみ出し防止用壁によって阻止されるため、バネ端面部の弁通路開口部からのはみ出しが防止され、弁の開閉を正常に維持することにより、弁が閉じ遅れることなくスムーズに移動し、弁が閉じ遅れることによる逆転音の発生を防止でき、かつ冷凍機油が圧縮機外に持ち出されることを防止できるため、給油不足による軸受信頼性の低下を防止できるという効果がある。   In the compressor according to the present invention, the compression mechanism portion includes a valve passage communicating with the suction pipe provided through the sealed container and the compression chamber communication path leading to the compression chamber for compressing the refrigerant introduced into the sealed container. Provided on both sides of the valve passage are valve passage openings that communicate with the compression chamber communication passage, and the valve passage opening opposite to the compression chamber communication passage is made smaller than the valve passage opening on the compression chamber communication passage side. In addition, since a spring protrusion prevention wall is provided at a position between the valve passage opening and the valve stop surface that have become smaller on the side surface of the valve passage, the amount of refrigerant that flows backward when the compressor is stopped increases, While the pressure difference increases or the valve is pushed back, the spring end face is pushed by the refrigerant toward the valve passage opening on the side opposite to the compression chamber communication passage, and tries to protrude from the valve passage opening. The protrusion of the end face is for preventing the spring from protruding Therefore, the spring end face is prevented from protruding from the valve passage opening, and by maintaining the valve normally open and closed, the valve moves smoothly without delay in closing, and reverse rotation due to delay in closing the valve. Since the generation of noise can be prevented and the refrigerating machine oil can be prevented from being taken out of the compressor, it is possible to prevent a decrease in bearing reliability due to insufficient lubrication.

実施の形態１．
図１はこの発明の実施の形態１のスクロール圧縮機の縦断面図、図２は同スクロール圧縮機の弁通路開口部で、（ａ）は停止時の形状を示す説明図、（ｂ）は運転時の形状を示す説明図である。
図１において、１は固定スクロールであり、外周部はガイドフレーム１５にボルト（図示せず）によって締結されている。台板部１ａの一方の面（図１において下側）には板状渦巻歯１ｂが形成されると同時に、外周部にはオルダム案内溝１ｃがほぼ一直線上に２ヶ形成されている。このオルダム案内溝１ｃにはオルダムリング９の爪９ｂが往復摺動自在に係合されている。
さらに、固定スクロール１には、図２に示すように圧縮室１ｄと連通する圧縮室連通路１ｋが設けられ、その圧縮室連通路１ｋと密閉容器１０を貫通して圧入された吸入管１０ａとに連通する水平方向に延びる弁通路１７ｄが圧縮室連通路１ｋに対して直角方向に設けられている。その弁通路１７ｄの両側面に圧縮室連通路１ｋに連通する弁通路開口部１ｊがそれぞれ設けられている。また、その弁通路１７ｄの内側に弁１７が摺動するように設けられている。 Embodiment 1 FIG.
1 is a longitudinal sectional view of a scroll compressor according to Embodiment 1 of the present invention, FIG. 2 is a valve passage opening of the scroll compressor, (a) is an explanatory view showing a shape when stopped, (b) is It is explanatory drawing which shows the shape at the time of a driving | operation.
In FIG. 1, 1 is a fixed scroll, and the outer peripheral part is fastened to the guide frame 15 by a bolt (not shown). A plate-like spiral tooth 1b is formed on one surface (lower side in FIG. 1) of the base plate portion 1a, and at the same time, two Oldham guide grooves 1c are formed on a substantially straight line. A claw 9b of the Oldham ring 9 is engaged with the Oldham guide groove 1c so as to be slidable back and forth.
Furthermore, the fixed scroll 1 is provided with a compression chamber communication passage 1k communicating with the compression chamber 1d as shown in FIG. 2, and a suction pipe 10a press-fitted through the compression chamber communication passage 1k and the sealed container 10; A valve passage 17d that extends in the horizontal direction is provided in a direction perpendicular to the compression chamber communication passage 1k. Valve passage openings 1j communicating with the compression chamber communication passage 1k are provided on both side surfaces of the valve passage 17d. Further, the valve 17 is provided to slide inside the valve passage 17d.

また、弁１７はバネ１８により吸入管１０ａの方向に閉じるように付勢されており、吸入管１０ａの弁座面となる端面で止まり、シールされ、冷媒の逆流を防ぐ構造となっている。バネ端面部１８ａが弁通路１７ｄの終端座面である弁止まり面１ｇに収まりやすいように側面はテーパ形状になっている。
また、その弁止まり面１ｇに、運転停止直後の逆流した冷媒を、弁１７ｄの背面側端面に導くための逃がし溝である高圧冷媒導入溝１ｈが設けられている。 Further, the valve 17 is biased by a spring 18 so as to be closed in the direction of the suction pipe 10a. The valve 17 stops at the end surface serving as a valve seat surface of the suction pipe 10a and is sealed to prevent the refrigerant from flowing backward. The side surface has a tapered shape so that the spring end surface portion 18a can easily fit in the valve stop surface 1g which is the terminal seat surface of the valve passage 17d.
The valve stop surface 1g is provided with a high-pressure refrigerant introduction groove 1h, which is an escape groove for guiding the refrigerant that has flowed back immediately after the stop of operation to the rear end surface of the valve 17d.

さらに、弁通路１７ｄの両側面にそれぞれ設けられた弁通路開口部１ｊについては、図２に示すように、圧縮室連通路１ｋと反対側の弁通路開口部１ｊを圧縮室連通路１ｋ側の弁通路開口部１ｊより小さく形成しており、弁通路１７ｄの側面で小さくなった弁通路開口部１ｊとバネ端面部１８ａが当接する弁止まり面１ｇとの間の位置にバネはみ出し防止用壁１ｌが設けられている。
また、運転時に、圧縮室連通路１ｋと反対側の小さくした弁通路開口部１ｊの終端部が、弁止まり面１ｇに弁１７が着座した時に弁１７の側面の間にくるように設定している。
さらに、運転時に冷媒が吸入管１０ａから弁通路１７ｄへとスムーズに流入するように、弁通路１７ｄの両側面に設けられた２つの弁通路開口部１ｊの面積は、吸入管１０ａの内径面積より大きく形成されている。 Further, with respect to the valve passage openings 1j provided on both side surfaces of the valve passage 17d, as shown in FIG. 2, the valve passage opening 1j opposite to the compression chamber communication passage 1k is connected to the compression chamber communication passage 1k side. The spring protruding prevention wall 11 is formed at a position between the valve passage opening 1j, which is formed smaller than the valve passage opening 1j, and becomes smaller on the side surface of the valve passage 17d, and the valve stop surface 1g with which the spring end face 18a abuts. Is provided.
Further, during operation, the end portion of the reduced valve passage opening 1j on the side opposite to the compression chamber communication passage 1k is set to be between the side surfaces of the valve 17 when the valve 17 is seated on the valve stop surface 1g. Yes.
Further, the area of the two valve passage openings 1j provided on both side surfaces of the valve passage 17d is larger than the inner diameter area of the suction pipe 10a so that the refrigerant smoothly flows from the suction pipe 10a to the valve passage 17d during operation. Largely formed.

２は揺動スクロールであり、台板部２ａの上面には固定スクロール１の板状渦巻歯１ｂと実質的に同一形状の板状渦巻歯２ｂが設けられており、前記固定スクロール１の板状渦巻歯１ａと揺動スクロール２の板状渦巻歯２ｂとは幾何学的に圧縮室１ｄを形成している。台板２ａの板状渦巻歯２ｂと反対側の面の中心部には中空円筒のボス部２ｆが形成されており、主軸４上端の揺動軸部４ｂと回転自在に係合されている。
また、台板２ａの板状渦巻歯２ｂと反対側の面にはコンプライアントフレーム３のスラスト軸受け３ａと圧接摺動可能なスラスト面２ｄが形成されている。揺動スクロール２の台板２ａの外周部には、前記固定スクロール１のオルダム案内溝１ｃと９０度の位相差をもつオルダム案内溝２ｅがほぼ一直線上に２ヶ形成されており、このオルダム案内溝２ｅにはオルダムリング９の爪９ａが往復摺動自在に係合されている。また台板部２ａには前記圧縮室１ｄとスラスト面２ｄを貫通する揺動スクロール抽出孔２ｊが設けられ、圧縮途中の冷媒ガスを抽出してスラスト面２ｄに導く構造となっている。 Reference numeral 2 denotes an orbiting scroll, and a plate-like spiral tooth 2b having substantially the same shape as the plate-like spiral tooth 1b of the fixed scroll 1 is provided on the upper surface of the base plate portion 2a. The spiral tooth 1a and the plate-like spiral tooth 2b of the orbiting scroll 2 geometrically form a compression chamber 1d. A hollow cylindrical boss 2f is formed at the center of the surface of the base plate 2a opposite to the plate-like spiral teeth 2b, and is rotatably engaged with the swing shaft 4b at the upper end of the main shaft 4.
Further, a thrust surface 2d that can slide in contact with the thrust bearing 3a of the compliant frame 3 is formed on the surface of the base plate 2a opposite to the plate-like spiral teeth 2b. Two Oldham guide grooves 2e having a phase difference of 90 degrees with the Oldham guide groove 1c of the fixed scroll 1 are formed on the outer periphery of the base plate 2a of the orbiting scroll 2 in a substantially straight line. A claw 9a of the Oldham ring 9 is engaged with the groove 2e so as to be slidable back and forth. The base plate 2a is provided with an orbiting scroll extraction hole 2j that penetrates the compression chamber 1d and the thrust surface 2d, and has a structure for extracting refrigerant gas during compression and guiding it to the thrust surface 2d.

コンプライアントフレーム３はその外周部に設けられた上下２つの円筒面３ｄ、３ｅを、ガイドフレーム１５の内周部に設けた円筒面１５ａ、１５ｂによって半径方向に支持されており、その中心部には電動機固定子７により回転駆動される主軸４を半径方向に支持する主軸受け３ｃおよび副主軸受け３ｈが形成されている。またスラスト軸受け３ａ面内から軸方向に貫通する連絡通路３ｓが設けてあり、そのスラスト軸受け側開口部２ｋは揺動スクロール抽出孔２ｊに対面して配置されている。   The compliant frame 3 has two upper and lower cylindrical surfaces 3d and 3e provided on the outer peripheral portion thereof supported in a radial direction by cylindrical surfaces 15a and 15b provided on the inner peripheral portion of the guide frame 15, and has a central portion. Are formed with a main bearing 3c and a sub main bearing 3h that support the main shaft 4 that is rotationally driven by the electric motor stator 7 in the radial direction. Further, a communication passage 3s penetrating in the axial direction from the surface of the thrust bearing 3a is provided, and the thrust bearing side opening 2k is arranged to face the swing scroll extraction hole 2j.

ガイドフレーム１５の外周面１５ｇは焼きばめ、もしくは溶接などによって密閉容器１０に固着されているものの、その外周部に設けた切り欠き部１５ｃにより、固定スクロール１の吐出ポート１ｅから吐出される高圧の冷媒ガスを圧縮機構部（１，２，３，１５）と電動機要素（７，８）の間に設けられた吐出管１０ｂに導く流路は確保されている。
また、切り欠き部１５ｃは吐出管１０ｂとは反対の位置に設けられている。また、ガイドフレーム１５の内周面には、コンプライアントフレーム３の外周面に形成された上下円筒面３ｄ、３ｅと係合する円筒面１５ａ、１５ｂ、およびシール材を収納するシール溝が２カ所設けられており、それぞれ上側及び下側シール材１６ａ、１６ｂが設置されている。 これら２つのシール材１６ａ、１６ｂを用いて密封されたガイドフレーム１５の内周面とコンプライアントフレーム３の外周面からなるフレーム空間１５ｆは、コンプライアントフレーム３の連絡通路３ｓとのみ連通しており、揺動スクロール抽出孔２ｊより供給される圧縮途中の冷媒ガスを封入する構造となっている。 Although the outer peripheral surface 15g of the guide frame 15 is fixed to the sealed container 10 by shrink fitting or welding, the high pressure discharged from the discharge port 1e of the fixed scroll 1 by the notch 15c provided on the outer peripheral portion. A flow path for guiding the refrigerant gas to the discharge pipe 10b provided between the compression mechanism (1, 2, 3, 15) and the electric motor element (7, 8) is secured.
The notch 15c is provided at a position opposite to the discharge pipe 10b. The guide frame 15 has two cylindrical grooves 15a and 15b that engage with the upper and lower cylindrical surfaces 3d and 3e formed on the outer peripheral surface of the compliant frame 3, and two seal grooves that store the sealing material. There are provided upper and lower sealing materials 16a and 16b, respectively. The frame space 15f formed by the inner peripheral surface of the guide frame 15 and the outer peripheral surface of the compliant frame 3 sealed with the two sealing materials 16a and 16b communicates only with the communication passage 3s of the compliant frame 3. The refrigerant gas in the middle of compression supplied from the swing scroll extraction hole 2j is sealed.

４は主軸であり、その上端部は揺動スクロール２の揺動軸受け２ｃと回転自在に係合する揺動軸４ｂが形成されており、その下側には主軸バランサ４ｅが焼きばめられている。 さらに、その下にはコンプライアントフレーム３の主軸受け３ｃおよび副主軸受け３ｈと回転自在に係合する主軸部４ｃが形成されている。
また、主軸４の下側はサブフレーム６の副軸受け６ａと回転自在に係合する副軸部４ｄが形成され、この副軸部４ｄと前述した主軸部４ｃ間には電動機回転子８が焼きばめられている。電動機回転子８の上端面には上バランサ８ａが、下端面には下バランサ８ｂが固定されており、前述した主軸バランサ４ｅとあわせて合計３ヶのバランサにより、静バランスおよび動バランスがとられている。
さらに、主軸４の下端にはオイルパイプ４ｆが圧入されており、密閉容器１０底部の油だめ１０ｇにたまった冷凍機油１０ｅを吸い上げる構造となっている。また、密封容器１０の側面にはガラス端子１０ｆが設置されており、電動機固定子７からのリード線が接合されている。 Reference numeral 4 denotes a main shaft. An upper end portion of the main shaft 4 is formed with a rocking shaft 4b that is rotatably engaged with a rocking bearing 2c of the rocking scroll 2, and a main shaft balancer 4e is fitted on the lower side thereof. Yes. Further, a main shaft portion 4c that is rotatably engaged with the main bearing 3c and the sub main bearing 3h of the compliant frame 3 is formed below the main shaft portion 4c.
Further, a lower shaft 4d is formed on the lower side of the main shaft 4 so as to be rotatably engaged with the sub-bearing 6a of the sub-frame 6. Between the sub-shaft portion 4d and the main shaft 4c, the motor rotor 8 is baked. It is fitted. An upper balancer 8a is fixed to the upper end surface of the motor rotor 8, and a lower balancer 8b is fixed to the lower end surface, and static balance and dynamic balance are achieved by a total of three balancers together with the main spindle balancer 4e. ing.
Further, an oil pipe 4f is press-fitted into the lower end of the main shaft 4 so that the refrigerating machine oil 10e accumulated in the oil sump 10g at the bottom of the sealed container 10 is sucked up. Further, a glass terminal 10 f is installed on the side surface of the sealed container 10, and a lead wire from the motor stator 7 is joined.

次に高圧シェルタイプのフレームコンプライアントスクロール圧縮機の基本動作について説明する。
圧縮機の運転時には、吸入冷媒が吸入管１０ａより吸入され、吸入圧力により弁１７はバネ力に打ち勝って弁止まり面１ｇ付近まで押し下げられ、吸入冷媒は固定スクロール１の板状渦巻歯１ｂ及び揺動スクロール２の板状渦巻歯２ｂで形成される圧縮室１ｄに入る。
電動機固定子７により駆動される揺動スクロール２は偏心旋回運動に伴って圧縮室１ｄの容積を減少させる。
この圧縮行程により吸入冷媒は高圧となり、固定スクロール１の吐出ポート１ｅより密閉容器１０内に吐き出される。なお、上記圧縮行程において圧縮途中の中間圧力の冷媒ガスは揺動スクロール２の揺動スクロール抽出孔２ｊよりコンプライアントフレーム３の連絡通路３ｓを経て、フレーム空間１５ｆに導かれ、このフレーム空間１５ｆの中間圧力雰囲気を維持する。高圧となった吐出ガスは密閉容器１０内を高圧雰囲気で満たし、吐出管１０ｂから圧縮機外に放出される。 Next, the basic operation of the high pressure shell type frame compliant scroll compressor will be described.
During the operation of the compressor, the suction refrigerant is sucked from the suction pipe 10a, and the valve 17 overcomes the spring force by the suction pressure and is pushed down to the vicinity of the valve stop surface 1g. It enters the compression chamber 1d formed by the plate-like spiral teeth 2b of the dynamic scroll 2.
The orbiting scroll 2 driven by the electric motor stator 7 reduces the volume of the compression chamber 1d with the eccentric turning motion.
Due to this compression stroke, the suction refrigerant becomes high pressure and is discharged into the sealed container 10 from the discharge port 1 e of the fixed scroll 1. In the compression stroke, the intermediate-pressure refrigerant gas in the middle of compression is guided to the frame space 15f through the communication passage 3s of the compliant frame 3 from the swing scroll extraction hole 2j of the swing scroll 2, and the frame space 15f Maintain an intermediate pressure atmosphere. The high-pressure discharge gas fills the sealed container 10 with a high-pressure atmosphere and is discharged from the discharge pipe 10b to the outside of the compressor.

密閉容器１０底部の油だめ１０ｇにためられた冷凍機油１０ｅは、差圧により主軸４を軸方向に貫通する給油穴４ｇを通り揺動軸受け空間４ｂに導かれる。
揺動軸受け２ｃの絞り作用によって中間圧力となった冷凍機油１０ｅは、揺動スクロール２とコンプライアントフレーム３によって囲まれたボス部空間２ｈを満たし、このボス部空間２ｈと低圧雰囲気空間を連絡する圧力調整弁（記載せず）を経由して低圧空間に導かれ、低圧の冷媒ガスとともに圧縮室１ｄに吸入される。
圧縮行程により冷凍機油１０ｅは高圧の冷媒ガスとともに吐出ポート１ｅから密閉容器１０内に吐出される。 The refrigerating machine oil 10e accumulated in the oil sump 10g at the bottom of the hermetic container 10 is guided to the swing bearing space 4b through the oil supply hole 4g penetrating the main shaft 4 in the axial direction due to the differential pressure.
The refrigerating machine oil 10e having an intermediate pressure due to the throttle action of the rocking bearing 2c fills the boss part space 2h surrounded by the rocking scroll 2 and the compliant frame 3, and connects the boss part space 2h and the low-pressure atmosphere space. It is led to a low pressure space via a pressure regulating valve (not shown) and sucked into the compression chamber 1d together with a low pressure refrigerant gas.
The refrigerating machine oil 10e is discharged into the sealed container 10 from the discharge port 1e together with the high-pressure refrigerant gas by the compression stroke.

圧縮機の運転停止時には、図２（ａ）に示すように、弁通路１７ｄの両側面に弁通路開口部１ｊがそれぞれ設けられ、圧縮室連通路１ｋと反対側の弁通路開口部１ｊを圧縮室連通路１ｋ側の弁通路開口部１ｊより小さく形成しており、弁通路１７ｄの側面で小さくなった弁通路開口部１ｊと弁止まり面１ｇとの間の位置にバネはみ出し防止用壁１ｌが設けられていることにより、逆流する冷媒量が多くなったり、高低圧差が大きくなったりして弁１７を押し戻す間にバネ１８のバネ端面部１８ａは冷媒によって圧縮室連通路１ｋと反対側の弁通路開口部１ｊ方向に押され、弁通路開口部１ｊからはみ出そうとするが、そのバネ端面部１８ａのはみ出しはバネはみ出し防止用壁１１によって阻止されるため、バネ端面部１８ａの弁通路開口部１ｊからのはみ出しが防止されることとなる。
従って、弁１７が閉じ遅れることなくスムーズに移動し、弁１７が閉じ遅れることによる逆転音の発生を防止でき、かつ冷凍機油が圧縮機外に持ち出されることを防止できるので給油不足による軸受信頼性の低下を防止できる。 When the operation of the compressor is stopped, as shown in FIG. 2A, valve passage openings 1j are respectively provided on both side surfaces of the valve passage 17d, and the valve passage opening 1j on the opposite side to the compression chamber communication passage 1k is compressed. A spring protruding prevention wall 11 is formed at a position between the valve passage opening 1j and the valve stop surface 1g which is formed smaller than the valve passage opening 1j on the side of the chamber communication passage 1k and becomes smaller on the side surface of the valve passage 17d. The spring end surface portion 18a of the spring 18 is a valve on the side opposite to the compression chamber communication path 1k by the refrigerant while the amount of the refrigerant flowing backward increases or the difference between high and low pressure increases and the valve 17 is pushed back. The spring end face 18a is pushed in the direction of the passage opening 1j and tries to protrude from the valve passage opening 1j, but the spring end face portion 18a is prevented from protruding by the spring protrusion preventing wall 11, so that the valve passage opening portion of the spring end face portion 18a is prevented. 1 Protruding from the fact that is prevented.
Accordingly, the valve 17 can move smoothly without delay in closing, the reverse sound due to the delay in closing the valve 17 can be prevented, and the refrigerating machine oil can be prevented from being taken out of the compressor. Can be prevented.

また、圧縮機の運転時に、圧縮室連通路１ｋと反対側の小さくした弁通路開口部１ｊの終端部が、弁止まり面１ｇに弁１７が着座した時に弁１７の側面の間にくるように設定しているので、運転時の弁通路開口部面積は従来の弁通路開口部の時と同じであり、バネ端面部１８ａのはみ出しを防止しつつ、吸入圧損が従来と同等の圧縮機が成立する。   Further, during operation of the compressor, the terminal portion of the reduced valve passage opening 1j opposite to the compression chamber communication passage 1k is located between the side surfaces of the valve 17 when the valve 17 is seated on the valve stop surface 1g. Therefore, the area of the valve passage opening during operation is the same as that of the conventional valve passage opening, and a compressor with a suction pressure loss equivalent to that of the conventional one is formed while preventing the spring end surface portion 18a from protruding. To do.

上述した実施の形態１の圧縮機は、高圧シェルタイプのフレームコンプライアントスクロール圧縮機であるが、吸入側に上述した実施の形態１と同様の逆転防止のために弁機構を設けたものであれば、スクロール圧縮機やロータリー圧縮機、その他の圧縮機でも同様の効果を得ることができる。   The compressor according to the first embodiment described above is a high-pressure shell type frame compliant scroll compressor, but may be provided with a valve mechanism on the suction side to prevent reverse rotation as in the first embodiment described above. For example, the same effect can be obtained with a scroll compressor, a rotary compressor, and other compressors.

この発明の実施の形態１のスクロール圧縮機の縦断面図。1 is a longitudinal sectional view of a scroll compressor according to Embodiment 1 of the present invention. 同スクロール圧縮機の弁通路開口部で、（ａ）は停止時の形状を示す説明図、（ｂ）は運転時の形状を示す説明図。The valve passage opening part of the scroll compressor, (a) is explanatory drawing which shows the shape at the time of a stop, (b) is explanatory drawing which shows the shape at the time of driving | operation.

符号の説明Explanation of symbols

１ 固定スクロール、１ａ 台板部、１ｂ 板状渦巻歯、１ｄ 圧縮室、１ｅ 吐出ポート、１ｆ 弁通路、２ 揺動スクロール、２ａ 台板部、２ｂ 板状渦巻歯、２ｃ 揺動軸受け、３ コンプライアントフレーム、３ａ スラスト軸受け、３ｓ 連絡通路、４ 主軸、４ｂ 揺動軸受け空間、４ｃ 主軸部、４ｄ 副軸部、４ｆ オイルパイプ、４ｇ 給油穴、６ サブフレーム、７ 電動機固定子、８ 電動機回転子、９ オルダムリング、１０ 密閉容器、１０ａ 吸入管、１０ｂ 吐出管、１０ｅ 冷凍機油、１０ｇ 油だめ、１５ ガイドフレーム、１７ 弁、１８ バネ、１８ａ バネ端面部。
DESCRIPTION OF SYMBOLS 1 Fixed scroll, 1a Base plate part, 1b Plate-shaped spiral tooth, 1d Compression chamber, 1e Discharge port, 1f Valve passage, 2 Swing scroll, 2a Base plate part, 2b Plate-shaped spiral tooth, 2c Swing bearing, 3 Comp Client frame, 3a thrust bearing, 3s communication passage, 4 main shaft, 4b swing bearing space, 4c main shaft portion, 4d subshaft portion, 4f oil pipe, 4g oiling hole, 6 subframe, 7 motor stator, 8 motor rotor , 9 Oldham ring, 10 sealed container, 10a suction pipe, 10b discharge pipe, 10e refrigerating machine oil, 10g sump, 15 guide frame, 17 valve, 18 spring, 18a spring end face.

Claims (3)

密閉容器内に導入された冷媒を圧縮室で圧縮する圧縮機構部と、前記圧縮機構部を駆動する電動機要素とを備え、前記密閉容器を貫通して設けられた吸入管と前記圧縮室に通じる圧縮室連通路とに連通する弁通路を前記圧縮機構部に設け、
前記弁通路内に摺動自在な弁と、該弁を前記吸入管の弁座面に付勢するバネと、該バネを保持し、且つ前記吸入管より冷媒が吸入された時に該冷媒の吸入圧力によりバネのバネ力に打ち勝って押し付けられる前記弁を止める弁止まり面とを設け、
前記弁通路の両側面に前記圧縮室連通路と連通する弁通路開口部をそれぞれ設け、
前記圧縮室連通路と反対側の弁通路開口部を前記圧縮室連通路側の弁通路開口部より小さく形成し、前記弁通路の側面で前記小さくした弁通路開口部と前記弁止まり面との間の位置にバネはみ出し防止用壁を設けたことを特徴とする圧縮機。 A compression mechanism that compresses the refrigerant introduced into the sealed container in a compression chamber, and an electric motor element that drives the compression mechanism, and communicates with a suction pipe provided through the sealed container and the compression chamber. A valve passage communicating with the compression chamber communication passage is provided in the compression mechanism section;
A valve that is slidable in the valve passage, a spring that urges the valve against a valve seat surface of the suction pipe, and a suction of the refrigerant when the refrigerant is sucked from the suction pipe while holding the spring A valve stop surface for stopping the valve pressed against the spring force of the spring by pressure,
Provided on both side surfaces of the valve passage with valve passage openings communicating with the compression chamber communication passage,
A valve passage opening opposite to the compression chamber communication passage is formed to be smaller than a valve passage opening on the compression chamber communication passage side, and the reduced valve passage opening and the valve stop surface on a side surface of the valve passage. A compressor characterized in that a spring protruding prevention wall is provided at a position between them. 前記小さくした弁通路開口部の終端部が、前記弁止まり面に前記弁が着座した時に当該弁の側面の間にくるように設定したことを特徴とする請求項１に記載の圧縮機。   2. The compressor according to claim 1, wherein an end portion of the reduced valve passage opening is set to be between the side surfaces of the valve when the valve is seated on the valve stop surface. 前記弁通路の両側面に設けられた２つの弁通路開口部の面積は、前記吸入管の内径面積より大きく形成されていることを特徴とする請求項１又は２記載の圧縮機。
The compressor according to claim 1 or 2, wherein the area of the two valve passage openings provided on both side surfaces of the valve passage is formed larger than the inner diameter area of the suction pipe.
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Publication number Priority date Publication date Assignee Title
JPS62186086A (en) * 1986-02-10 1987-08-14 Matsushita Refrig Co Scroll type compressor
JP2005256655A (en) * 2004-03-10 2005-09-22 Mitsubishi Electric Corp Compressor

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62186086A (en) * 1986-02-10 1987-08-14 Matsushita Refrig Co Scroll type compressor
JP2005256655A (en) * 2004-03-10 2005-09-22 Mitsubishi Electric Corp Compressor

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