JPWO2010087180A1 - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
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- JPWO2010087180A1 JPWO2010087180A1 JP2010529964A JP2010529964A JPWO2010087180A1 JP WO2010087180 A1 JPWO2010087180 A1 JP WO2010087180A1 JP 2010529964 A JP2010529964 A JP 2010529964A JP 2010529964 A JP2010529964 A JP 2010529964A JP WO2010087180 A1 JPWO2010087180 A1 JP WO2010087180A1
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- Prior art keywords
- vane
- oil
- piston
- rotary compressor
- oil supply
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0854—Vane tracking; control therefor by fluid means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/38—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/02 and having a hinged member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/023—Lubricant distribution through a hollow driving shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
Abstract
ピストン３２の内面３２ｂから円筒形の嵌合部３２ａに連通する給油穴６０を形成されることにより、油溝４５がクランク軸３１の回転により一定区間この給油穴６０に連通し、油溝４５に存在するオイルが給油穴６０を通り、円筒型の嵌合部３２ａとベーン３３先端の挿入部３３ａで形成される揺動部に供給されることにより、揺動部の摺動状態が更に良化すると共に、揺動部のシール性も向上して揺動部の隙間を通じて高圧の圧縮室３９から低圧の吸入室へのガスの漏れをさらに抑制できる。By forming an oil supply hole 60 that communicates from the inner surface 32 b of the piston 32 to the cylindrical fitting portion 32 a, the oil groove 45 communicates with the oil supply hole 60 for a certain section by rotation of the crankshaft 31, and The existing oil passes through the oil supply hole 60 and is supplied to the swinging portion formed by the cylindrical fitting portion 32a and the insertion portion 33a at the tip of the vane 33, thereby further improving the sliding state of the swinging portion. At the same time, the sealing performance of the oscillating portion is also improved, and gas leakage from the high pressure compression chamber 39 to the low pressure suction chamber can be further suppressed through the clearance of the oscillating portion.
Description
本発明は、空調機、冷凍機、ブロワ、給湯機等に使用されることが可能な回転型圧縮機に関するものである。 The present invention relates to a rotary compressor that can be used for an air conditioner, a refrigerator, a blower, a water heater, and the like.
従来、冷凍装置や空気調和装置などにおいては、蒸発器で蒸発したガス冷媒を吸入し、凝縮するために必要な圧力まで圧縮し、冷媒回路中に高温高圧のガス冷媒を送り出す回転型圧縮機が使用されている。このような回転型圧縮機の一つとして、ローリングピストン型ロータリ圧縮機が知られている。
ローリングピストン型ロータリ圧縮機は、たとえば図１９、図２０に示すように、電動機２と圧縮機構部３をクランク軸３１で連結して密閉容器１内に収納したものである。圧縮機構部３は、シリンダ３０とこのシリンダ３０の両端面を閉塞する上軸受３４ａの端板３４と下軸受３５ａの端板３５とで形成された圧縮室３９と、この圧縮室３９内に上軸受３４ａおよび下軸受３５ａに支持されたクランク軸３１の偏心部３１ａに嵌合されたピストン１３２と、このピストン１３２の外周にの偏心回転に追従して往復運動し圧縮室３９内を低圧部と高圧部とに仕切るベーン１３３を備えている。クランク軸３１には軸線に沿って油穴４１が設けられるとともに、上軸受３４ａ、下軸受３５ａに対する壁部には、それぞれ油穴４１に連通した給油穴４２、４３が設けられている。また、クランク軸３１の偏心部３１ａに対する壁部には油穴４１に連通した給油穴４４が設けられ、外周部には油溝４５が形成されている。シリンダ３０には、圧縮室３９内の低圧部に向けてガスを吸入する吸入ポート４０が開通され、上軸受３４ａには、圧縮室３９内の低圧部から転じて形成される高圧部からガスを吐出する吐出ポート３８が開通されている。吐出ポート３８は上軸受３４ａを貫通する平面視円形の孔として形成されている。吐出ポート３８の上面には所定の大きさ以上の圧力を受けた場合に解放される吐出弁３６が設けられている。カップマフラ−３７は吐出弁３６を覆っている。低圧部側ではピストン１３２の摺接部が吸入ポート４０を通過して吸入室を徐々に拡大しながら離れていき、吸入ポート４０から吸入室内にガスを吸入する。一方、高圧部側ではピストン１３２の摺動部が吐出ポート３８へ圧縮室３９を徐々に縮小しながら近づいていき、所定圧力以上に圧縮された時点で吐出弁３６が開いて吐出ポート３８からガスを流出し、カップマフラ−３７より密閉容器１内に吐出される。
上記の構成では、ピストン１３２とベーン１３３先端の摺動部の面圧が高くオイルが保持されにくく、摺動性が厳しいため、磨耗が起こりやすい。なお、代替冷媒の移行により、非共沸混合冷媒のＲ４０７ＣやＲ４１０Ａを使用すると冷媒自身の潤滑性が悪く、磨耗がさらに発生しやすい。
この磨耗を解決する手段として、図２１に示す特許文献１が提案されている。図２１に示すように、シリンダ３０と、シリンダ３０内に設けられたクランク軸３１の偏心部３１ａに嵌合されたピストン３２と、シリンダ３０に設けられたスロット内を往復運動してピストン３２と先端部で揺動自由に接続されるベーン３３と、シリンダ３０の両端面を閉塞する二つの端板３４、３５と、少なくとも一方の端板３４、３５に吐出ポート３８とを有する揺動ピストン型圧縮機を採用することで、ピストン３２とベーン３３先端の揺動部の摺動面積が大きいので面圧が下がり摺動性が良好になり、信頼性を向上させることができる。Conventionally, in a refrigeration apparatus, an air conditioner, and the like, there is a rotary compressor that sucks gas refrigerant evaporated in an evaporator, compresses it to a pressure necessary for condensation, and sends high-temperature and high-pressure gas refrigerant into a refrigerant circuit. in use. As one of such rotary compressors, a rolling piston rotary compressor is known.
For example, as shown in FIGS. 19 and 20, the rolling piston type rotary compressor is configured such that the electric motor 2 and the compression mechanism unit 3 are connected to each other by a crankshaft 31 and accommodated in the sealed container 1. The compression mechanism unit 3 includes a compression chamber 39 formed by a cylinder 30, an end plate 34 of an upper bearing 34 a that closes both end faces of the cylinder 30, and an end plate 35 of a lower bearing 35 a, and an upper portion in the compression chamber 39. A piston 132 fitted to an eccentric portion 31a of the crankshaft 31 supported by the bearing 34a and the lower bearing 35a, and a reciprocating motion following the eccentric rotation on the outer periphery of the piston 132, and the inside of the compression chamber 39 as a low pressure portion. A vane 133 is provided to partition the high pressure part. The crankshaft 31 is provided with an oil hole 41 along the axis, and oil supply holes 42 and 43 communicating with the oil hole 41 are provided on the walls of the upper bearing 34a and the lower bearing 35a, respectively. An oil supply hole 44 communicating with the oil hole 41 is provided in the wall portion of the crankshaft 31 with respect to the eccentric portion 31a, and an oil groove 45 is formed in the outer peripheral portion. The cylinder 30 is opened with a suction port 40 for sucking gas toward the low pressure portion in the compression chamber 39, and the upper bearing 34 a receives gas from the high pressure portion formed by turning from the low pressure portion in the compression chamber 39. A discharge port 38 for discharging is opened. The discharge port 38 is formed as a circular hole passing through the upper bearing 34a in plan view. On the upper surface of the discharge port 38, there is provided a discharge valve 36 that is released when a pressure of a predetermined magnitude or more is applied. The cup muffler 37 covers the discharge valve 36. On the low pressure part side, the sliding contact portion of the piston 132 passes through the suction port 40 and gradually separates from the suction chamber, and sucks gas from the suction port 40 into the suction chamber. On the other hand, on the high pressure side, the sliding portion of the piston 132 approaches the discharge port 38 while gradually reducing the compression chamber 39, and when the pressure is compressed to a predetermined pressure or higher, the discharge valve 36 opens and the gas is discharged from the discharge port 38. Is discharged from the cup muffler 37 into the sealed container 1.
In the above configuration, the surface pressure of the sliding portion between the piston 132 and the tip of the vane 133 is high and the oil is not easily held, and the sliding property is severe. Note that when the non-azeotropic refrigerants R407C and R410A are used due to the transition of the alternative refrigerant, the lubricity of the refrigerant itself is poor and wear is more likely to occur.
As means for solving this wear, Patent Document 1 shown in FIG. 21 has been proposed. As shown in FIG. 21, the cylinder 30, the piston 32 fitted in the eccentric portion 31 a of the crankshaft 31 provided in the cylinder 30, and the piston 32 by reciprocating in the slot provided in the cylinder 30 A swing piston type having a vane 33 that is swingably connected at the tip, two end plates 34 and 35 closing both end surfaces of the cylinder 30, and a discharge port 38 in at least one of the end plates 34 and 35. By adopting the compressor, the sliding area of the oscillating portion at the tip of the piston 32 and the vane 33 is large, so that the surface pressure is lowered and the slidability is improved and the reliability can be improved.
しかしながら、特許文献１の構成ではベーン３３とピストン３２の嵌合する揺動部の潤滑は圧縮室に存在するミスト状のオイルが吸入室へ差圧により流れていくのみであり、過負荷などの厳しい運転において、揺動部の摩耗などの信頼性に課題が生じる恐れがあった。 However, in the configuration of Patent Document 1, lubrication of the oscillating portion in which the vane 33 and the piston 32 are fitted only causes the mist-like oil present in the compression chamber to flow into the suction chamber due to the differential pressure, which causes overload and the like. In severe operation, there is a risk of problems in reliability such as wear of the rocking part.
本発明は、従来技術の有するこのような問題点に鑑みてなされたものであり、ベーンとピストンの嵌合揺動部に積極的にオイルを供給することができ、回転型圧縮機の信頼性をさらに向上させることを目的とする。 The present invention has been made in view of the above-described problems of the prior art, and can actively supply oil to the fitting swinging portion of the vane and the piston, thereby improving the reliability of the rotary compressor. It aims at improving further.
上記目的を達成するために、本発明の回転型圧縮機は、シリンダ内を旋回運動するピストンと、前記シリンダ内を吸入室と吐出口が開口する圧縮室に仕切り前記シリンダのベーン溝に挿入されるベーンと、前記ベーン先端の挿入部と前記挿入部が挿入される前記ピストンの嵌合部とで形成される揺動部で前記ピストンと前記ベーンとが揺動自在に接続される回転型圧縮機であって、高圧のオイル溜りから前記揺動部へのオイル供給経路を形成したものである。
これにより、ベーンとピストンの嵌合揺動部に積極的にオイルを供給することができ、回転型圧縮機の信頼性をさらに向上させることができる。In order to achieve the above object, a rotary compressor according to the present invention is inserted into a vane groove of a cylinder, which is divided into a piston that rotates in a cylinder, and a compression chamber in which a suction chamber and a discharge port are opened. Rotation type compression in which the piston and the vane are swingably connected by a swinging portion formed by a vane having a vane, an insertion portion at the tip of the vane, and a fitting portion of the piston into which the insertion portion is inserted An oil supply path from a high pressure oil reservoir to the swinging part is formed.
Thereby, oil can be positively supplied to the fitting rocking | fluctuation part of a vane and a piston, and the reliability of a rotary compressor can further be improved.
本発明の回転型圧縮機は、ベーンとピストンの嵌合揺動部に高圧のオイルを供給する経路を形成することで、積極的にオイルを供給することができ、回転型圧縮機の信頼性を向上することができる。 The rotary compressor according to the present invention can supply oil actively by forming a passage for supplying high-pressure oil to the fitting swinging portion of the vane and the piston, and the reliability of the rotary compressor Can be improved.
１ 密閉容器
２ 電動機
３ 圧縮機構部
５ 上シェル
６ オイル溜り
７ バネ
２２ 固定子
２４ 回転子
３０ シリンダ
３０ａ シリンダ内壁
３０ｂ スロット
３１ クランク軸
３１ａ 偏芯部
３２ ピストン
３２ａ 嵌合部
３２ｂ ピストン内面
３２ｃ 窪み
３３ ベーン
３３ａ 挿入部
３３ｂ ベーン背面
３３ｃ ベーン下端面
３３ｄ 窪み
３４ 端板
３４ａ 上軸受
３５ 端板
３５ａ 下軸受
３６ 吐出弁
３７ カップマフラ−
３８ 吐出ポート
３９ 圧縮室
４０ 吸入ポート
４１ 油穴
４２ 給油穴
４３ 給油穴
４４ 給油穴
４５ 油溝
４８ 経路
５１ 冷媒吐出管
５２ 吐出空間
６０ 給油穴
６１ 給油穴
６２ 給油穴
６３ 給油穴DESCRIPTION OF SYMBOLS 1 Airtight container 2 Electric motor 3 Compression mechanism part 5 Upper shell 6 Oil reservoir 7 Spring 22 Stator 24 Rotor 30 Cylinder 30a Cylinder inner wall 30b Slot 31 Crankshaft 31a Eccentric part 32 Piston 32a Fitting part 32b Piston inner surface 32c Depression 33 Vane 33a Insertion portion 33b Back surface of vane 33c Lower end surface of vane 33d Depression 34 End plate 34a Upper bearing 35 End plate 35a Lower bearing 36 Discharge valve 37 Cup muffler
38 Discharge port 39 Compression chamber 40 Suction port 41 Oil hole 42 Oil supply hole
43 Oil supply hole 44 Oil supply hole 45 Oil groove 48 Path 51 Refrigerant discharge pipe 52 Discharge space 60 Oil supply hole 61 Oil supply hole 62 Oil supply hole 63 Oil supply hole
第１の発明は、シリンダ内を旋回運動するピストンと、前記シリンダ内を吸入室と吐出口が開口する圧縮室に仕切り前記シリンダのベーン溝に挿入されるベーンと、前記ベーン先端の挿入部と挿入部が挿入される前記ピストンの嵌合部とで形成される揺動部で前記ピストンと前記ベーンとが揺動自在に接続される回転型圧縮機であって、高圧のオイル溜りから前記揺動部へのオイル供給経路を形成したことにより、ベーンとピストンの嵌合揺動部に積極的にオイルを供給することができ、回転型圧縮機の信頼性をさらに向上させることができる。
第２の発明は、特に第１の発明のオイル供給経路が、ピストンの内面から前記ピストンの嵌合部に連通する給油穴により構成されたことにより、高圧オイル溜りから容易に揺動部に供給する経路を構成することができる。
第３の発明は、特に、第１の発明のオイル供給経路が、ベーンの背面から前記ベーンの挿入部先端に連通する穴により構成されることにより、高圧オイル溜りから容易に揺動部に供給する経路を構成することができる。
第４の発明は、特に第１の発明のオイル供給経路が、シリンダの端面に配された下軸受を貫通する穴と、この穴にベーンの往復運動により間欠開口するように、前記ベーン先端の挿入部の端面から前記ベーンの挿入部先端に連通する穴により構成されることにより、揺動部にオイルの量を調節して供給することが可能となり、揺動部の信頼性を向上するとともに効率も向上することができる。
第５の発明は、特に第１から第４の発明のベーンの挿入部先端に窪みを構成したことにより、揺動部へ確実にオイルを供給することができる。
第６の発明は、特に第１から第４の発明のピストンの嵌合部に窪みを構成したことにより、揺動部へ確実にオイルを供給することができる。
以下、本発明の実施の形態について、図面を参照しながら説明する。なお、この実施の形態によって本発明が限定されるものではない。A first invention is a piston that pivots in a cylinder, a vane that is partitioned into a compression chamber in which a suction chamber and a discharge port are opened in the cylinder, and is inserted into a vane groove of the cylinder, and an insertion portion at the tip of the vane, A rotary compressor in which the piston and the vane are swingably connected to each other by a swinging portion formed by a fitting portion of the piston into which the insertion portion is inserted. By forming the oil supply path to the moving part, oil can be actively supplied to the fitting swinging part of the vane and the piston, and the reliability of the rotary compressor can be further improved.
In the second aspect of the invention, in particular, the oil supply path of the first aspect of the invention is configured by an oil supply hole communicating from the inner surface of the piston to the fitting portion of the piston, so that the high pressure oil reservoir can be easily supplied to the swinging portion. A route can be configured.
In the third aspect of the invention, in particular, the oil supply path of the first aspect of the invention is configured by a hole communicating from the back surface of the vane to the tip of the insertion portion of the vane, so that the high pressure oil reservoir can be easily supplied to the swinging portion. A route can be configured.
According to a fourth aspect of the present invention, in particular, the oil supply path of the first aspect of the present invention is configured so that the hole passing through the lower bearing disposed on the end surface of the cylinder and the vane tip is opened intermittently by reciprocating movement of the vane. By comprising a hole that communicates from the end surface of the insertion portion to the tip of the insertion portion of the vane, it becomes possible to adjust and supply the amount of oil to the swinging portion, and improve the reliability of the swinging portion. Efficiency can also be improved.
According to the fifth aspect of the present invention, in particular, since the recess is formed at the tip of the insertion portion of the vane according to the first to fourth aspects of the invention, oil can be reliably supplied to the swinging portion.
In the sixth aspect of the invention, in particular, since the recess is formed in the fitting portion of the piston of the first to fourth aspects of the invention, oil can be reliably supplied to the swinging portion.
Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.
（実施の形態１）
図１は本発明の第１の実施の形態における回転型圧縮機の縦断面図、図２は同回転型圧縮機の圧縮機構部の拡大断面図である。図３は同回転型圧縮機の圧縮動作を示す模式図、図４は同回転型圧縮機の要部を示す拡大分解斜視図、図５は同回転型圧縮機の要部を示す拡大斜視図である。(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a rotary compressor according to a first embodiment of the present invention, and FIG. 2 is an enlarged sectional view of a compression mechanism portion of the rotary compressor. FIG. 3 is a schematic view showing a compression operation of the rotary compressor, FIG. 4 is an enlarged exploded perspective view showing a main part of the rotary compressor, and FIG. 5 is an enlarged perspective view showing a main part of the rotary compressor. It is.
図１と図２に示す本発明の回転型圧縮機は、電動機２と圧縮機構部３をクランク軸３１で連結して密閉容器１内に収納したものである。圧縮機構部３は、シリンダ３０とこのシリンダ３０の両端面を閉塞する上軸受３４ａの端板３４と下軸受３５ａの端板３５とで形成された圧縮室３９と、この圧縮室３９内に上軸受３４ａおよび下軸受３５ａに支持されたクランク軸３１の偏心部３１ａに嵌合されたピストン３２と、圧縮室３９内を低圧部と高圧部とに仕切りピストン３２と先端部で揺動自由に接続されるベーン３３とを備えている。図４の分解斜視図に示すように、ベーン３３の先端部である円筒形の挿入部３３ａと、ピストン３２に形成されベーン３３の挿入部３３ａが挿入される円筒形の嵌合部３２ａとが揺動自在に嵌合接続する構成となっており、ベーン３３先端の挿入部３３ａとピストン３２の嵌合部３２ａの間には揺動の為の隙間が設けられている。クランク軸３１には軸線部に油穴４１が設けられるとともに、上軸受３４ａ、下軸受３５ａに対する壁部には、それぞれ油穴４１に連通した給油穴４２、４３が設けられている。また、クランク軸３１の偏心部３１ａに対する壁部には油穴４１に連通した給油穴４４が設けられ、外周部には油溝４５が形成されている。オイル溜り６に貯留されている高圧のオイルはクランク軸３１の回転による遠心力で油穴４１を上り、油穴４２、４３、４４、および油溝４５に供給され、軸受部の潤滑を行っている。シリンダ３０には、圧縮室３９内の低圧部に向けてガスを吸入する吸入ポート４０が開通され、上軸受３４ａには、圧縮室３９内の低圧部から転じて形成される高圧部からガスを吐出する吐出ポート３８が開通されている。吐出ポート３８は上軸受３４ａの端板３４を貫通する平面視円形の孔として形成されている。吐出ポート３８の上面には所定の大きさ以上の圧力を受けた場合に解放される吐出弁３６が設けられている。カップマフラ−３７は吐出弁３６を覆っている。 The rotary compressor of the present invention shown in FIGS. 1 and 2 is one in which an electric motor 2 and a compression mechanism 3 are connected by a crankshaft 31 and stored in a sealed container 1. The compression mechanism unit 3 includes a compression chamber 39 formed by a cylinder 30, an end plate 34 of an upper bearing 34 a that closes both end faces of the cylinder 30, and an end plate 35 of a lower bearing 35 a, and an upper portion in the compression chamber 39. The piston 32 fitted to the eccentric part 31a of the crankshaft 31 supported by the bearing 34a and the lower bearing 35a, and the compression chamber 39 is partitioned into a low pressure part and a high pressure part, and the piston 32 and the tip part are connected to freely swing. The vane 33 is provided. As shown in the exploded perspective view of FIG. 4, a cylindrical insertion portion 33a that is a tip portion of the vane 33 and a cylindrical fitting portion 32a that is formed on the piston 32 and into which the insertion portion 33a of the vane 33 is inserted. It is configured to be swingably fitted and connected, and a gap for swinging is provided between the insertion portion 33a at the tip of the vane 33 and the fitting portion 32a of the piston 32. The crankshaft 31 is provided with an oil hole 41 in the axial line portion, and oil supply holes 42 and 43 communicating with the oil hole 41 are provided on the wall portions of the upper bearing 34a and the lower bearing 35a, respectively. An oil supply hole 44 communicating with the oil hole 41 is provided in the wall portion of the crankshaft 31 with respect to the eccentric portion 31a, and an oil groove 45 is formed in the outer peripheral portion. The high-pressure oil stored in the oil reservoir 6 climbs the oil hole 41 by centrifugal force generated by the rotation of the crankshaft 31, and is supplied to the oil holes 42, 43, 44 and the oil groove 45 to lubricate the bearing portion. Yes. The cylinder 30 is opened with a suction port 40 for sucking gas toward the low pressure portion in the compression chamber 39, and the upper bearing 34 a receives gas from the high pressure portion formed by turning from the low pressure portion in the compression chamber 39. A discharge port 38 for discharging is opened. The discharge port 38 is formed as a circular hole that passes through the end plate 34 of the upper bearing 34a in plan view. On the upper surface of the discharge port 38, there is provided a discharge valve 36 that is released when a pressure of a predetermined magnitude or more is applied. The cup muffler 37 covers the discharge valve 36.
次に、図３を用いて、本実施の形態の圧縮動作を説明する。図３に示すように、ピストン３２を９０度ずつ回転させた時のピストン３２とベーン３３との位置関係を図３（Ａ），（Ｂ），（Ｃ），（Ｄ）の順に示している。図３に示すようにクランク軸３１が一回転する間に低圧部側ではピストン３２の摺接部が吸入ポート４０を通過して吸入室を徐々に拡大しながら離れていき、吸入ポート４０から吸入室内にガスを吸入する。一方、高圧部側ではピストン３２の摺動部が吐出ポート３８へ圧縮室３９を徐々に縮小しながら近づいていき、所定圧力以上に圧縮された時点で吐出弁３６が開いて吐出ポート３８からガスを流出し、カップマフラ−３７より密閉容器１内に吐出される。 Next, the compression operation of this embodiment will be described with reference to FIG. As shown in FIG. 3, the positional relationship between the piston 32 and the vane 33 when the piston 32 is rotated by 90 degrees is shown in the order of FIGS. 3 (A), (B), (C), and (D). . As shown in FIG. 3, while the crankshaft 31 makes one rotation, the sliding contact portion of the piston 32 passes through the suction port 40 on the low-pressure portion side and moves away while gradually expanding the suction chamber. Inhale gas into the room. On the other hand, on the high pressure side, the sliding portion of the piston 32 approaches the discharge port 38 while gradually reducing the compression chamber 39, and when the pressure is compressed to a predetermined pressure or higher, the discharge valve 36 opens and the gas is discharged from the discharge port 38. Is discharged from the cup muffler 37 into the sealed container 1.
以上のように構成された回転型圧縮機において、図２と図５に示すように、ピストン３２の内面３２ｂから円筒形の嵌合部３２ａに連通する給油穴６０が形成されている。この給油穴６０が形成されることにより、油溝４５がクランク軸３１の回転により一定区間この給油穴６０に連通し、油溝４５に存在するオイルが給油穴６０を通り、円筒型の嵌合部３２ａとベーン３３先端の挿入部３３ａで形成される揺動部に供給される。この供給されたオイルにより揺動部の摺動状態が更に良化すると共に、揺動部のシール性も向上して揺動部の隙間を通じて高圧の圧縮室３９から低圧の吸入室へのガスの漏れをさらに抑制できる。また給油穴６０に油溝４５が連通している間、オイルが供給されるので、供給量をコントロールすることができる。図１９、２０で示す一般的なローリングピストン型ロータリ圧縮機では、ベーン１３３先端ではオイルが保持されにくく、摺動性が厳しく油膜が形成されにくいのに対し、本実施の形態の回転型圧縮機では揺動部に給油穴６０によって供給されたオイルが保持されるため、摺動状態が良化し、信頼性が向上する。従って、本実施の形態では、揺動部に対して、高圧のオイル溜りから揺動部へのオイル供給経路を形成したことにより、積極的にオイルを供給することができ、回転型圧縮機の信頼性を向上することができる。 In the rotary compressor configured as described above, as shown in FIGS. 2 and 5, an oil supply hole 60 that communicates from the inner surface 32b of the piston 32 to the cylindrical fitting portion 32a is formed. By forming the oil supply hole 60, the oil groove 45 communicates with the oil supply hole 60 for a certain period by the rotation of the crankshaft 31, and the oil existing in the oil groove 45 passes through the oil supply hole 60 and is fitted in a cylindrical shape. It is supplied to a swinging portion formed by the insertion portion 33a at the tip of the portion 32a and the vane 33. This supplied oil further improves the sliding state of the oscillating part and also improves the sealing performance of the oscillating part so that the gas from the high-pressure compression chamber 39 to the low-pressure suction chamber passes through the gap of the oscillating part. Leakage can be further suppressed. Further, since the oil is supplied while the oil groove 45 is in communication with the oil supply hole 60, the supply amount can be controlled. In the general rolling piston type rotary compressor shown in FIGS. 19 and 20, oil is not easily held at the tip of the vane 133, and the sliding property is severe and the oil film is difficult to be formed. Then, since the oil supplied by the oil supply hole 60 is held in the swinging portion, the sliding state is improved and the reliability is improved. Therefore, in the present embodiment, the oil supply path from the high-pressure oil reservoir to the oscillating portion is formed with respect to the oscillating portion, so that oil can be actively supplied. Reliability can be improved.
（実施の形態２）
次に、ベーン３３先端の挿入部３３ａとピストン３２の嵌合部３２ａとで形成される揺動部にオイルを供給する他の実施の形態を説明する。
図６は本発明の第２の実施の形態における回転型圧縮機の圧縮機構部の拡大断面図であり、図７は同回転型圧縮機の要部を示す拡大斜視図である。なお、前述の実施の形態１と同一構成要素には同一符号を付与して説明を省略する。(Embodiment 2)
Next, another embodiment in which oil is supplied to a swinging portion formed by the insertion portion 33a at the tip of the vane 33 and the fitting portion 32a of the piston 32 will be described.
FIG. 6 is an enlarged cross-sectional view of the compression mechanism portion of the rotary compressor according to the second embodiment of the present invention, and FIG. 7 is an enlarged perspective view showing the main part of the rotary compressor. In addition, the same code | symbol is provided to the same component as above-mentioned Embodiment 1, and description is abbreviate | omitted.
本実施の形態では、ベーン３３の背面３３ｂからベーン３３先端の挿入部３３ａに連通する給油穴６１を形成している。ベーン３３の背面３３ｂにはオイルが存在するので給油穴６１を通して、ベーン３３先端とピストン３２の嵌合部３２ａとで形成される揺動部の隙間を通して高圧部と吸入室の差圧により揺動部にオイルが供給された後、吸入室へ供給されることで摺動状態が良化し、信頼性が向上する。 In the present embodiment, an oil supply hole 61 that communicates from the back surface 33b of the vane 33 to the insertion portion 33a at the tip of the vane 33 is formed. Since oil is present on the back surface 33b of the vane 33, it swings due to the pressure difference between the high pressure portion and the suction chamber through the oil supply hole 61 and through the clearance of the swinging portion formed by the tip of the vane 33 and the fitting portion 32a of the piston 32. After the oil is supplied to the part, it is supplied to the suction chamber, so that the sliding state is improved and the reliability is improved.
（実施の形態３）
次に、ベーン３３先端の挿入部３３ａとピストン３２の嵌合部３２ａとで形成される揺動部にオイルを供給する更に他の実施の形態を説明する。
図８は本発明の第３の実施の形態における回転型圧縮機の圧縮機構部の拡大断面図であり、図９と図１０は本発明の第３の実施の形態における回転型圧縮機の要部を示す拡大斜視図である。なお、前述の実施の形態１と２と同一構成要素には同一符号を付与して説明を省略する。(Embodiment 3)
Next, still another embodiment for supplying oil to a swinging portion formed by the insertion portion 33a at the tip of the vane 33 and the fitting portion 32a of the piston 32 will be described.
FIG. 8 is an enlarged cross-sectional view of the compression mechanism portion of the rotary compressor according to the third embodiment of the present invention, and FIGS. 9 and 10 show the essential parts of the rotary compressor according to the third embodiment of the present invention. It is an expansion perspective view which shows a part. Note that the same components as those in the first and second embodiments are given the same reference numerals and description thereof is omitted.
本実施の形態では、下軸受３５ａの端板３５からオイル溜り６に開口する給油穴６２を設けると共に、ベーン３３の下端面３３ｃからベーン３３先端の挿入部３３ａに連通する給油穴６３を設けている。給油穴６３の下端面３３ｃ側はベーン３３の往復運動により給油穴６２と間欠的に連通する位置に配設している。この構成によりオイル溜り６のオイルは給油穴６２と給油穴６３を経由してベーン３３先端とピストン３２の揺動部を潤滑した後、吸入室へ供給される。この結果、揺動部の摺動状態が良化し、信頼性が向上する。また給油穴６３は給油穴６２と間欠的に連通するので連通している割合を変更することで供給するオイル量を調節できる。 In the present embodiment, an oil supply hole 62 that opens from the end plate 35 of the lower bearing 35a to the oil reservoir 6 is provided, and an oil supply hole 63 that communicates from the lower end surface 33c of the vane 33 to the insertion portion 33a at the tip of the vane 33 is provided. Yes. The lower end surface 33 c side of the oil supply hole 63 is disposed at a position where the oil supply hole 62 intermittently communicates with the reciprocating motion of the vane 33. With this configuration, the oil in the oil reservoir 6 is supplied to the suction chamber after lubricating the tip of the vane 33 and the swinging portion of the piston 32 via the oil supply hole 62 and the oil supply hole 63. As a result, the sliding state of the swinging portion is improved and the reliability is improved. Further, since the oil supply hole 63 is intermittently communicated with the oil supply hole 62, the amount of oil to be supplied can be adjusted by changing the communication ratio.
（実施の形態４）
次に、ベーン３３先端の挿入部３３ａとピストン３２の嵌合部３２ａとで形成される揺動部にオイルを供給するために適用されるベーン３３先端の挿入部３３ａの実施の形態を説明する。
図１１と図１３と図１５は本発明の第４の実施の形態における回転型圧縮機の圧縮機構部の拡大断面図であり、図１２と図１４と図１６は同回転型圧縮機の要部を示す拡大斜視図である。なお、前述の実施の形態１から３と同一構成要素には同一符号を付与して説明を省略する。(Embodiment 4)
Next, an embodiment of the insertion portion 33a at the tip of the vane 33 applied to supply oil to the swinging portion formed by the insertion portion 33a at the tip of the vane 33 and the fitting portion 32a of the piston 32 will be described. .
11, 13, and 15 are enlarged sectional views of the compression mechanism portion of the rotary compressor according to the fourth embodiment of the present invention. FIGS. 12, 14, and 16 are the main parts of the rotary compressor. It is an expansion perspective view which shows a part. The same components as those in the first to third embodiments are given the same reference numerals and the description thereof is omitted.
本実施の形態では、ベーン３３先端の挿入部３３ａにＤカット等の窪み３３ｄを設けたものである。なお、この窪み３３ｄは、オイルを供給する給油穴が形成されているときには、ベーン３３先端とピストン３２の揺動部にオイルを供給する給油穴に臨む部位に設けたものである。このＤカット等の窪み３３ｄにより給油穴から供給されるオイルを貯留できると共に揺動部が潤滑しやすくなる。 In the present embodiment, the insertion portion 33a at the tip of the vane 33 is provided with a recess 33d such as a D-cut. The recess 33d is provided in a portion facing the oil supply hole for supplying oil to the tip of the vane 33 and the swinging portion of the piston 32 when the oil supply hole for supplying oil is formed. The oil supplied from the oil supply hole can be stored by the depression 33d such as the D cut, and the swinging portion can be easily lubricated.
（実施の形態５）
次に、ベーン３３先端の挿入部３３ａとピストン３２の嵌合部３２ａとで形成される揺動部にオイルを供給する更に他の実施の形態を説明する。
図１７は本発明の第５の実施の形態における回転型圧縮機の圧縮機構部の拡大断面図であり、図１８は同回転型圧縮機の要部を示す拡大斜視図である。なお、前述の実施の形態１から４と同一構成要素には同一符号を付与して説明を省略する。(Embodiment 5)
Next, still another embodiment for supplying oil to a swinging portion formed by the insertion portion 33a at the tip of the vane 33 and the fitting portion 32a of the piston 32 will be described.
FIG. 17 is an enlarged cross-sectional view of a compression mechanism of a rotary compressor according to a fifth embodiment of the present invention, and FIG. 18 is an enlarged perspective view showing a main part of the rotary compressor. The same components as those in the first to fourth embodiments are given the same reference numerals, and the description thereof is omitted.
本実施の形態では、ベーン３３先端とピストン３２の揺動部にオイルを供給する給油穴６０に臨むピストン３２に形成された円筒形の嵌合部３２ａに窪み３２ｃを設けたものである。この窪み３２ｃにより給油穴６０から供給されるオイルを貯留できると共に揺動部が潤滑しやすくなる。なおこの窪み３２ｃはベーン３３もしくはピストン３２の一方、又は両方に構成してもよい。 In the present embodiment, a hollow 32c is provided in a cylindrical fitting portion 32a formed in the piston 32 facing the oil supply hole 60 for supplying oil to the tip of the vane 33 and the swinging portion of the piston 32. The recess 32c can store the oil supplied from the oil supply hole 60 and can easily lubricate the swinging portion. The recess 32c may be formed in one or both of the vane 33 and the piston 32.
なお、前述の各実施の形態において、ベーン３３先端とピストン３２の揺動部にオイルを供給する給油穴の端部にＣ面取りを設けてもよい。このＣ面取りにより給油穴から供給されるオイルを貯留できると共に揺動部が潤滑しやすくなる。 In each of the above-described embodiments, C chamfering may be provided at the end of the oil supply hole that supplies oil to the tip of the vane 33 and the swinging portion of the piston 32. By this C chamfering, the oil supplied from the oil supply hole can be stored and the swinging portion can be easily lubricated.
以上のように、本発明の回転型圧縮機は、ベーン先端の磨耗や焼き付きなどの信頼性面の低下を抑制するとともに、漏れ損失と摺動損失を同時に低減し、圧縮機の高効率化を図ることが可能となる。これにより、ＨＦＣ系冷媒やＨＣＦＣ系冷媒を用いたエアーコンディショナー用圧縮機のほかに、自然冷媒ＣＯ２や可燃性冷媒を用いたエアーコンディショナーやヒートポンプ式給湯機などにも適用できる。 As described above, the rotary compressor of the present invention suppresses deterioration of reliability such as vane tip wear and seizure, and simultaneously reduces leakage loss and sliding loss, thereby improving the efficiency of the compressor. It becomes possible to plan. Thereby, in addition to the compressor for an air conditioner using an HFC refrigerant or an HCFC refrigerant, the present invention can be applied to an air conditioner using a natural refrigerant CO2 or a flammable refrigerant, a heat pump type hot water heater, or the like.
本発明は、空調機、冷凍機、ブロワ、給湯機等に使用されることが可能な回転型圧縮機に関するものである。 The present invention relates to a rotary compressor that can be used for an air conditioner, a refrigerator, a blower, a water heater, and the like.
従来、冷凍装置や空気調和装置などにおいては、蒸発器で蒸発したガス冷媒を吸入し、凝縮するために必要な圧力まで圧縮し、冷媒回路中に高温高圧のガス冷媒を送り出す回転型圧縮機が使用されている。このような回転型圧縮機の一つとして、ローリングピストン型ロータリ圧縮機が知られている。
ローリングピストン型ロータリ圧縮機は、たとえば図１９、図２０に示すように、電動機２と圧縮機構部３をクランク軸３１で連結して密閉容器１内に収納したものである。圧縮機構部３は、シリンダ３０とこのシリンダ３０の両端面を閉塞する上軸受３４ａの端板３４と下軸受３５ａの端板３５とで形成された圧縮室３９と、この圧縮室３９内に上軸受３４ａおよび下軸受３５ａに支持されたクランク軸３１の偏心部３１ａに嵌合されたピストン１３２と、このピストン１３２の外周に偏心回転に追従して往復運動し圧縮室３９内を低圧部と高圧部とに仕切るベーン１３３を備えている。クランク軸３１には軸線に沿って油穴４１が設けられるとともに、上軸受３４ａ、下軸受３５ａに対する壁部には、それぞれ油穴４１に連通した給油穴４２、４３が設けられている。また、クランク軸３１の偏心部３１ａに対する壁部には油穴４１に連通した給油穴４４が設けられ、外周部には油溝４５が形成されている。シリンダ３０には、圧縮室３９内の低圧部に向けてガスを吸入する吸入ポート４０が開通され、上軸受３４ａには、圧縮室３９内の低圧部から転じて形成される高圧部からガスを吐出する吐出ポート３８が開通されている。吐出ポート３８は上軸受３４ａを貫通する平面視円形の孔として形成されている。吐出ポート３８の上面には所定の大きさ以上の圧力を受けた場合に解放される吐出弁３６が設けられている。カップマフラ−３７は吐出弁３６を覆っている。低圧部側ではピストン１３２の摺接部が吸入ポート４０を通過して吸入室を徐々に拡大しながら離れていき、吸入ポート４０から吸入室内にガスを吸入する。一方、高圧部側ではピストン１３２の摺動部が吐出ポート３８へ圧縮室３９を徐々に縮小しながら近づいていき、所定圧力以上に圧縮された時点で吐出弁３６が開いて吐出ポート３８からガスを流出し、カップマフラ−３７より密閉容器１内に吐出される。
上記の構成では、ピストン１３２とベーン１３３先端の摺動部の面圧が高くオイルが保持されにくく、摺動性が厳しいため、磨耗が起こりやすい。なお、代替冷媒の移行により、非共沸混合冷媒のＲ４０７ＣやＲ４１０Ａを使用すると冷媒自身の潤滑性が悪く、磨耗がさらに発生しやすい。
この磨耗を解決する手段として、図２１に示す特許文献１が提案されている。図２１に示すように、シリンダ３０と、シリンダ３０内に設けられたクランク軸３１の偏心部３１ａに嵌合されたピストン３２と、シリンダ３０に設けられたスロット内を往復運動してピストン３２と先端部で揺動自由に接続されるベーン３３と、シリンダ３０の両端面を閉塞する二つの端板３４、３５と、少なくとも一方の端板３４、３５に吐出ポート３８とを有する揺動ピストン型圧縮機を採用することで、ピストン３２とベーン３３先端の揺動部の摺動面積が大きいので面圧が下がり摺動性が良好になり、信頼性を向上させることができる。
Conventionally, in a refrigeration apparatus, an air conditioner, and the like, there is a rotary compressor that sucks gas refrigerant evaporated in an evaporator, compresses it to a pressure necessary for condensation, and sends high-temperature and high-pressure gas refrigerant into a refrigerant circuit. in use. As one of such rotary compressors, a rolling piston rotary compressor is known.
For example, as shown in FIGS. 19 and 20, the rolling piston type rotary compressor is configured such that the electric motor 2 and the compression mechanism unit 3 are connected to each other by a crankshaft 31 and accommodated in the sealed container 1. The compression mechanism unit 3 includes a compression chamber 39 formed by a cylinder 30, an end plate 34 of an upper bearing 34 a that closes both end faces of the cylinder 30, and an end plate 35 of a lower bearing 35 a, and an upper portion in the compression chamber 39. The piston 132 fitted to the eccentric portion 31a of the crankshaft 31 supported by the bearing 34a and the lower bearing 35a, and the outer periphery of the piston 132 reciprocates following the eccentric rotation so that the inside of the compression chamber 39 and the high pressure portion A vane 133 is provided for partitioning. The crankshaft 31 is provided with an oil hole 41 along the axis, and oil supply holes 42 and 43 communicating with the oil hole 41 are provided on the walls of the upper bearing 34a and the lower bearing 35a, respectively. An oil supply hole 44 communicating with the oil hole 41 is provided in the wall portion of the crankshaft 31 with respect to the eccentric portion 31a, and an oil groove 45 is formed in the outer peripheral portion. The cylinder 30 is opened with a suction port 40 for sucking gas toward the low pressure portion in the compression chamber 39, and the upper bearing 34 a receives gas from the high pressure portion formed by turning from the low pressure portion in the compression chamber 39. A discharge port 38 for discharging is opened. The discharge port 38 is formed as a circular hole passing through the upper bearing 34a in plan view. On the upper surface of the discharge port 38, there is provided a discharge valve 36 that is released when a pressure of a predetermined magnitude or more is applied. The cup muffler 37 covers the discharge valve 36. On the low pressure part side, the sliding contact portion of the piston 132 passes through the suction port 40 and gradually separates from the suction chamber, and sucks gas from the suction port 40 into the suction chamber. On the other hand, on the high pressure side, the sliding portion of the piston 132 approaches the discharge port 38 while gradually reducing the compression chamber 39, and when the pressure is compressed to a predetermined pressure or higher, the discharge valve 36 opens and the gas is discharged from the discharge port 38. Is discharged from the cup muffler 37 into the sealed container 1.
In the above configuration, the surface pressure of the sliding portion between the piston 132 and the tip of the vane 133 is high and the oil is not easily held, and the sliding property is severe. Note that when the non-azeotropic refrigerants R407C and R410A are used due to the transition of the alternative refrigerant, the lubricity of the refrigerant itself is poor and wear is more likely to occur.
As means for solving this wear, Patent Document 1 shown in FIG. 21 has been proposed. As shown in FIG. 21, the cylinder 30, the piston 32 fitted in the eccentric portion 31 a of the crankshaft 31 provided in the cylinder 30, and the piston 32 by reciprocating in the slot provided in the cylinder 30 A swing piston type having a vane 33 that is swingably connected at the tip, two end plates 34 and 35 closing both end surfaces of the cylinder 30, and a discharge port 38 in at least one of the end plates 34 and 35. By adopting the compressor, the sliding area of the oscillating portion at the tip of the piston 32 and the vane 33 is large, so that the surface pressure is lowered and the slidability is improved and the reliability can be improved.
しかしながら、特許文献１の構成ではベーン３３とピストン３２の嵌合する揺動部の潤滑は圧縮室に存在するミスト状のオイルが吸入室へ差圧により流れていくのみであり、過負荷などの厳しい運転において、揺動部の摩耗などの信頼性に課題が生じる恐れがあった。 However, in the configuration of Patent Document 1, lubrication of the oscillating portion in which the vane 33 and the piston 32 are fitted only causes the mist-like oil present in the compression chamber to flow into the suction chamber due to the differential pressure, which causes overload and the like. In severe operation, there is a risk of problems in reliability such as wear of the rocking part.
本発明は、従来技術の有するこのような問題点に鑑みてなされたものであり、ベーンとピストンの嵌合揺動部に積極的にオイルを供給することができ、回転型圧縮機の信頼性をさらに向上させることを目的とする。 The present invention has been made in view of the above-described problems of the prior art, and can actively supply oil to the fitting swinging portion of the vane and the piston, thereby improving the reliability of the rotary compressor. It aims at improving further.
上記目的を達成するために、本発明の回転型圧縮機は、シリンダ内を旋回運動するピストンと、前記シリンダ内を吸入室と吐出口が開口する圧縮室に仕切り前記シリンダのベーン溝に挿入されるベーンと、前記ベーン先端の挿入部と前記挿入部が挿入される前記ピストンの嵌合部とで形成される揺動部で前記ピストンと前記ベーンとが揺動自在に接続される回転型圧縮機であって、高圧のオイル溜りから前記揺動部へのオイル供給経路を形成したものである。
これにより、ベーンとピストンの嵌合揺動部に積極的にオイルを供給することができ、回転型圧縮機の信頼性をさらに向上させることができる。
In order to achieve the above object, a rotary compressor according to the present invention is inserted into a vane groove of a cylinder, which is divided into a piston that rotates in a cylinder, and a compression chamber in which a suction chamber and a discharge port are opened. Rotation type compression in which the piston and the vane are swingably connected by a swinging portion formed by a vane having a vane, an insertion portion at the tip of the vane, and a fitting portion of the piston into which the insertion portion is inserted An oil supply path from a high pressure oil reservoir to the swinging part is formed.
Thereby, oil can be positively supplied to the fitting rocking | fluctuation part of a vane and a piston, and the reliability of a rotary compressor can further be improved.
本発明の回転型圧縮機は、ベーンとピストンの嵌合揺動部に高圧のオイルを供給する経路を形成することで、積極的にオイルを供給することができ、回転型圧縮機の信頼性を向上することができる。 The rotary compressor according to the present invention can supply oil actively by forming a passage for supplying high-pressure oil to the fitting swinging portion of the vane and the piston, and the reliability of the rotary compressor Can be improved.
第１の発明は、シリンダ内を旋回運動するピストンと、前記シリンダ内を吸入室と吐出口が開口する圧縮室に仕切り前記シリンダのベーン溝に挿入されるベーンと、前記ベーン先端の挿入部と挿入部が挿入される前記ピストンの嵌合部とで形成される揺動部で前記ピストンと前記ベーンとが揺動自在に接続される回転型圧縮機であって、高圧のオイル溜りから前記揺動部へのオイル供給経路を形成したことにより、ベーンとピストンの嵌合揺動部に積極的にオイルを供給することができ、回転型圧縮機の信頼性をさらに向上させることができる。
第２の発明は、特に第１の発明のオイル供給経路が、ピストンの内面から前記ピストンの嵌合部に連通する給油穴により構成されたことにより、高圧オイル溜りから容易に揺動部に供給する経路を構成することができる。
第３の発明は、特に、第１の発明のオイル供給経路が、ベーンの背面から前記ベーンの挿入部先端に連通する穴により構成されることにより、高圧オイル溜りから容易に揺動部に供給する経路を構成することができる。
第４の発明は、特に第１の発明のオイル供給経路が、シリンダの端面に配された下軸受を貫通する穴と、この穴にベーンの往復運動により間欠開口するように、前記ベーン先端の挿入部の端面から前記ベーンの挿入部先端に連通する穴により構成されることにより、揺動部にオイルの量を調節して供給することが可能となり、揺動部の信頼性を向上するとともに効率も向上することができる。
第５の発明は、特に第１から第４の発明のベーンの挿入部先端に窪みを構成したことにより、揺動部へ確実にオイルを供給することができる。
第６の発明は、特に第１から第４の発明のピストンの嵌合部に窪みを構成したことにより、揺動部へ確実にオイルを供給することができる。
以下、本発明の実施の形態について、図面を参照しながら説明する。なお、この実施の形態によって本発明が限定されるものではない。
A first invention is a piston that pivots in a cylinder, a vane that is partitioned into a compression chamber in which a suction chamber and a discharge port are opened in the cylinder, and is inserted into a vane groove of the cylinder, and an insertion portion at the tip of the vane, A rotary compressor in which the piston and the vane are swingably connected to each other by a swinging portion formed by a fitting portion of the piston into which the insertion portion is inserted. By forming the oil supply path to the moving part, oil can be actively supplied to the fitting swinging part of the vane and the piston, and the reliability of the rotary compressor can be further improved.
In the second aspect of the invention, in particular, the oil supply path of the first aspect of the invention is configured by an oil supply hole communicating from the inner surface of the piston to the fitting portion of the piston, so that the high pressure oil reservoir can be easily supplied to the swinging portion. A route can be configured.
In the third aspect of the invention, in particular, the oil supply path of the first aspect of the invention is configured by a hole communicating from the back surface of the vane to the tip of the insertion portion of the vane, so that the high pressure oil reservoir can be easily supplied to the swinging portion. A route can be configured.
According to a fourth aspect of the present invention, in particular, the oil supply path of the first aspect of the present invention is configured so that the hole passing through the lower bearing disposed on the end surface of the cylinder and the vane tip is opened intermittently by reciprocating movement of the vane. By comprising a hole that communicates from the end surface of the insertion portion to the tip of the insertion portion of the vane, it becomes possible to adjust and supply the amount of oil to the swinging portion, and improve the reliability of the swinging portion. Efficiency can also be improved.
According to the fifth aspect of the present invention, in particular, since the recess is formed at the tip of the insertion portion of the vane according to the first to fourth aspects of the invention, oil can be reliably supplied to the swinging portion.
In the sixth aspect of the invention, in particular, since the recess is formed in the fitting portion of the piston of the first to fourth aspects of the invention, oil can be reliably supplied to the swinging portion.
Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.
（実施の形態１）
図１は本発明の第１の実施の形態における回転型圧縮機の縦断面図、図２は同回転型圧縮機の圧縮機構部の拡大断面図である。図３は同回転型圧縮機の圧縮動作を示す模式図、図４は同回転型圧縮機の要部を示す拡大分解斜視図、図５は同回転型圧縮機の要部を示す拡大斜視図である。
(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a rotary compressor according to a first embodiment of the present invention, and FIG. 2 is an enlarged sectional view of a compression mechanism portion of the rotary compressor. FIG. 3 is a schematic view showing a compression operation of the rotary compressor, FIG. 4 is an enlarged exploded perspective view showing a main part of the rotary compressor, and FIG. 5 is an enlarged perspective view showing a main part of the rotary compressor. It is.
図１と図２に示す本発明の回転型圧縮機は、電動機２と圧縮機構部３をクランク軸３１で連結して密閉容器１内に収納したものである。圧縮機構部３は、シリンダ３０とこのシリンダ３０の両端面を閉塞する上軸受３４ａの端板３４と下軸受３５ａの端板３５とで形成された圧縮室３９と、この圧縮室３９内に上軸受３４ａおよび下軸受３５ａに支持されたクランク軸３１の偏心部３１ａに嵌合されたピストン３２と、圧縮室３９内を低圧部と高圧部とに仕切りピストン３２と先端部で揺動自由に接続されるベーン３３とを備えている。図４の分解斜視図に示すように、ベーン３３の先端部である円筒形の挿入部３３ａと、ピストン３２に形成されベーン３３の挿入部３３ａが挿入される円筒形の嵌合部３２ａとが揺動自在に嵌合接続する構成となっており、ベーン３３先端の挿入部３３ａとピストン３２の嵌合部３２ａの間には揺動の為の隙間が設けられている。クランク軸３１には軸線部に油穴４１が設けられるとともに、上軸受３４ａ、下軸受３５ａに対する壁部には、それぞれ油穴４１に連通した給油穴４２、４３が設けられている。また、クランク軸３１の偏心部３１ａに対する壁部には油穴４１に連通した給油穴４４が設けられ、外周部には油溝４５が形成されている。オイル溜り６に貯留されている高圧のオイルはクランク軸３１の回転による遠心力で油穴４１を上り、油穴４２、４３、４４、および油溝４５に供給され、軸受部の潤滑を行っている。シリンダ３０には、圧縮室３９内の低圧部に向けてガスを吸入する吸入ポート４０が開通され、上軸受３４ａには、圧縮室３９内の低圧部から転じて形成される高圧部からガスを吐出する吐出ポート３８が開通されている。吐出ポート３８は上軸受３４ａの端板３４を貫通する平面視円形の孔として形成されている。吐出ポート３８の上面には所定の大きさ以上の圧力を受けた場合に解放される吐出弁３６が設けられている。カップマフラ−３７は吐出弁３６を覆っている。 The rotary compressor of the present invention shown in FIGS. 1 and 2 is one in which an electric motor 2 and a compression mechanism 3 are connected by a crankshaft 31 and stored in a sealed container 1. The compression mechanism unit 3 includes a compression chamber 39 formed by a cylinder 30, an end plate 34 of an upper bearing 34 a that closes both end faces of the cylinder 30, and an end plate 35 of a lower bearing 35 a, and an upper portion in the compression chamber 39. The piston 32 fitted to the eccentric part 31a of the crankshaft 31 supported by the bearing 34a and the lower bearing 35a, and the compression chamber 39 is partitioned into a low pressure part and a high pressure part, and the piston 32 and the tip part are connected to freely swing. The vane 33 is provided. As shown in the exploded perspective view of FIG. 4, a cylindrical insertion portion 33a that is a tip portion of the vane 33 and a cylindrical fitting portion 32a that is formed on the piston 32 and into which the insertion portion 33a of the vane 33 is inserted. It is configured to be swingably fitted and connected, and a gap for swinging is provided between the insertion portion 33a at the tip of the vane 33 and the fitting portion 32a of the piston 32. The crankshaft 31 is provided with an oil hole 41 in the axial line portion, and oil supply holes 42 and 43 communicating with the oil hole 41 are provided on the wall portions of the upper bearing 34a and the lower bearing 35a, respectively. An oil supply hole 44 communicating with the oil hole 41 is provided in the wall portion of the crankshaft 31 with respect to the eccentric portion 31a, and an oil groove 45 is formed in the outer peripheral portion. The high-pressure oil stored in the oil reservoir 6 climbs the oil hole 41 by centrifugal force generated by the rotation of the crankshaft 31, and is supplied to the oil holes 42, 43, 44 and the oil groove 45 to lubricate the bearing portion. Yes. The cylinder 30 is opened with a suction port 40 for sucking gas toward the low pressure portion in the compression chamber 39, and the upper bearing 34 a receives gas from the high pressure portion formed by turning from the low pressure portion in the compression chamber 39. A discharge port 38 for discharging is opened. The discharge port 38 is formed as a circular hole that passes through the end plate 34 of the upper bearing 34a in plan view. On the upper surface of the discharge port 38, there is provided a discharge valve 36 that is released when a pressure of a predetermined magnitude or more is applied. The cup muffler 37 covers the discharge valve 36.
次に、図３を用いて、本実施の形態の圧縮動作を説明する。図３に示すように、ピストン３２を９０度ずつ回転させた時のピストン３２とベーン３３との位置関係を図３（Ａ），（Ｂ），（Ｃ），（Ｄ）の順に示している。図３に示すようにクランク軸３１が一回転する間に低圧部側ではピストン３２の摺接部が吸入ポート４０を通過して吸入室を徐々に拡大しながら離れていき、吸入ポート４０から吸入室内にガスを吸入する。一方、高圧部側ではピストン３２の摺動部が吐出ポート３８へ圧縮室３９を徐々に縮小しながら近づいていき、所定圧力以上に圧縮された時点で吐出弁３６が開いて吐出ポート３８からガスを流出し、カップマフラ−３７より密閉容器１内に吐出される。 Next, the compression operation of this embodiment will be described with reference to FIG. As shown in FIG. 3, the positional relationship between the piston 32 and the vane 33 when the piston 32 is rotated by 90 degrees is shown in the order of FIGS. 3 (A), (B), (C), and (D). . As shown in FIG. 3, while the crankshaft 31 makes one rotation, the sliding contact portion of the piston 32 passes through the suction port 40 on the low-pressure portion side and moves away while gradually expanding the suction chamber. Inhale gas into the room. On the other hand, on the high pressure side, the sliding portion of the piston 32 approaches the discharge port 38 while gradually reducing the compression chamber 39, and when the pressure is compressed to a predetermined pressure or higher, the discharge valve 36 opens and the gas is discharged from the discharge port 38. Is discharged from the cup muffler 37 into the sealed container 1.
以上のように構成された回転型圧縮機において、図２と図５に示すように、ピストン３２の内面３２ｂから円筒形の嵌合部３２ａに連通する給油穴６０が形成されている。この給油穴６０が形成されることにより、油溝４５がクランク軸３１の回転により一定区間この給油穴６０に連通し、油溝４５に存在するオイルが給油穴６０を通り、円筒型の嵌合部３２ａとベーン３３先端の挿入部３３ａで形成される揺動部に供給される。この供給されたオイルにより揺動部の摺動状態が更に良化すると共に、揺動部のシール性も向上して揺動部の隙間を通じて高圧の圧縮室３９から低圧の吸入室へのガスの漏れをさらに抑制できる。また給油穴６０に油溝４５が連通している間、オイルが供給されるので、供給量をコントロールすることができる。図１９、２０で示す一般的なローリングピストン型ロータリ圧縮機では、ベーン１３３先端ではオイルが保持されにくく、摺動性が厳しく油膜が形成されにくいのに対し、本実施の形態の回転型圧縮機では揺動部に給油穴６０によって供給されたオイルが保持されるため、摺動状態が良化し、信頼性が向上する。従って、本実施の形態では、揺動部に対して、高圧のオイル溜りから揺動部へのオイル供給経路を形成したことにより、積極的にオイルを供給することができ、回転型圧縮機の信頼性を向上することができる。 In the rotary compressor configured as described above, as shown in FIGS. 2 and 5, an oil supply hole 60 that communicates from the inner surface 32b of the piston 32 to the cylindrical fitting portion 32a is formed. By forming the oil supply hole 60, the oil groove 45 communicates with the oil supply hole 60 for a certain period by the rotation of the crankshaft 31, and the oil existing in the oil groove 45 passes through the oil supply hole 60 and is fitted in a cylindrical shape. It is supplied to a swinging portion formed by the insertion portion 33a at the tip of the portion 32a and the vane 33. This supplied oil further improves the sliding state of the oscillating part and also improves the sealing performance of the oscillating part so that the gas from the high-pressure compression chamber 39 to the low-pressure suction chamber passes through the gap of the oscillating part. Leakage can be further suppressed. Further, since the oil is supplied while the oil groove 45 is in communication with the oil supply hole 60, the supply amount can be controlled. In the general rolling piston type rotary compressor shown in FIGS. 19 and 20, oil is not easily held at the tip of the vane 133, and the sliding property is severe and the oil film is difficult to be formed. Then, since the oil supplied by the oil supply hole 60 is held in the swinging portion, the sliding state is improved and the reliability is improved. Therefore, in the present embodiment, the oil supply path from the high-pressure oil reservoir to the oscillating portion is formed with respect to the oscillating portion, so that oil can be actively supplied. Reliability can be improved.
（実施の形態２）
次に、ベーン３３先端の挿入部３３ａとピストン３２の嵌合部３２ａとで形成される揺動部にオイルを供給する他の実施の形態を説明する。
図６は本発明の第２の実施の形態における回転型圧縮機の圧縮機構部の拡大断面図であり、図７は同回転型圧縮機の要部を示す拡大斜視図である。なお、前述の実施の形態１と同一構成要素には同一符号を付与して説明を省略する。
(Embodiment 2)
Next, another embodiment in which oil is supplied to a swinging portion formed by the insertion portion 33a at the tip of the vane 33 and the fitting portion 32a of the piston 32 will be described.
FIG. 6 is an enlarged cross-sectional view of the compression mechanism portion of the rotary compressor according to the second embodiment of the present invention, and FIG. 7 is an enlarged perspective view showing the main part of the rotary compressor. In addition, the same code | symbol is provided to the same component as above-mentioned Embodiment 1, and description is abbreviate | omitted.
本実施の形態では、ベーン３３の背面３３ｂからベーン３３先端の挿入部３３ａに連通する給油穴６１を形成している。ベーン３３の背面３３ｂにはオイルが存在するので給油穴６１を通して、ベーン３３先端とピストン３２の嵌合部３２ａとで形成される揺動部の隙間を通して高圧部と吸入室の差圧により揺動部にオイルが供給された後、吸入室へ供給されることで摺動状態が良化し、信頼性が向上する。 In the present embodiment, an oil supply hole 61 that communicates from the back surface 33b of the vane 33 to the insertion portion 33a at the tip of the vane 33 is formed. Since oil is present on the back surface 33b of the vane 33, it swings due to the pressure difference between the high pressure portion and the suction chamber through the oil supply hole 61 and through the clearance of the swinging portion formed by the tip of the vane 33 and the fitting portion 32a of the piston 32. After the oil is supplied to the part, it is supplied to the suction chamber, so that the sliding state is improved and the reliability is improved.
（実施の形態３）
次に、ベーン３３先端の挿入部３３ａとピストン３２の嵌合部３２ａとで形成される揺動部にオイルを供給する更に他の実施の形態を説明する。
図８は本発明の第３の実施の形態における回転型圧縮機の圧縮機構部の拡大断面図であり、図９と図１０は本発明の第３の実施の形態における回転型圧縮機の要部を示す拡大斜視図である。なお、前述の実施の形態１と２と同一構成要素には同一符号を付与して説明を省略する。
(Embodiment 3)
Next, still another embodiment for supplying oil to a swinging portion formed by the insertion portion 33a at the tip of the vane 33 and the fitting portion 32a of the piston 32 will be described.
FIG. 8 is an enlarged cross-sectional view of the compression mechanism portion of the rotary compressor according to the third embodiment of the present invention, and FIGS. 9 and 10 show the essential parts of the rotary compressor according to the third embodiment of the present invention. It is an expansion perspective view which shows a part. Note that the same components as those in the first and second embodiments are given the same reference numerals and description thereof is omitted.
本実施の形態では、下軸受３５ａの端板３５からオイル溜り６に開口する給油穴６２を設けると共に、ベーン３３の下端面３３ｃからベーン３３先端の挿入部３３ａに連通する給油穴６３を設けている。給油穴６３の下端面３３ｃ側はベーン３３の往復運動により給油穴６２と間欠的に連通する位置に配設している。この構成によりオイル溜り６のオイルは給油穴６２と給油穴６３を経由してベーン３３先端とピストン３２の揺動部を潤滑した後、吸入室へ供給される。この結果、揺動部の摺動状態が良化し、信頼性が向上する。また給油穴６３は給油穴６２と間欠的に連通するので連通している割合を変更することで供給するオイル量を調節できる。 In the present embodiment, an oil supply hole 62 that opens from the end plate 35 of the lower bearing 35a to the oil reservoir 6 is provided, and an oil supply hole 63 that communicates from the lower end surface 33c of the vane 33 to the insertion portion 33a at the tip of the vane 33 is provided. Yes. The lower end surface 33 c side of the oil supply hole 63 is disposed at a position where the oil supply hole 62 intermittently communicates with the reciprocating motion of the vane 33. With this configuration, the oil in the oil reservoir 6 is supplied to the suction chamber after lubricating the tip of the vane 33 and the swinging portion of the piston 32 via the oil supply hole 62 and the oil supply hole 63. As a result, the sliding state of the swinging portion is improved and the reliability is improved. Further, since the oil supply hole 63 is intermittently communicated with the oil supply hole 62, the amount of oil to be supplied can be adjusted by changing the communication ratio.
（実施の形態４）
次に、ベーン３３先端の挿入部３３ａとピストン３２の嵌合部３２ａとで形成される揺動部にオイルを供給するために適用されるベーン３３先端の挿入部３３ａの実施の形態を説明する。
図１１と図１３と図１５は本発明の第４の実施の形態における回転型圧縮機の圧縮機構部の拡大断面図であり、図１２と図１４と図１６は同回転型圧縮機の要部を示す拡大斜視図である。なお、前述の実施の形態１から３と同一構成要素には同一符号を付与して説明を省略する。
(Embodiment 4)
Next, an embodiment of the insertion portion 33a at the tip of the vane 33 applied to supply oil to the swinging portion formed by the insertion portion 33a at the tip of the vane 33 and the fitting portion 32a of the piston 32 will be described. .
11, 13, and 15 are enlarged sectional views of the compression mechanism portion of the rotary compressor according to the fourth embodiment of the present invention. FIGS. 12, 14, and 16 are the main parts of the rotary compressor. It is an expansion perspective view which shows a part. The same components as those in the first to third embodiments are given the same reference numerals and the description thereof is omitted.
本実施の形態では、ベーン３３先端の挿入部３３ａにＤカット等の窪み３３ｄを設けたものである。なお、この窪み３３ｄは、オイルを供給する給油穴が形成されているときには、ベーン３３先端とピストン３２の揺動部にオイルを供給する給油穴に臨む部位に設けたものである。このＤカット等の窪み３３ｄにより給油穴から供給されるオイルを貯留できると共に揺動部が潤滑しやすくなる。 In the present embodiment, the insertion portion 33a at the tip of the vane 33 is provided with a recess 33d such as a D-cut. The recess 33d is provided in a portion facing the oil supply hole for supplying oil to the tip of the vane 33 and the swinging portion of the piston 32 when the oil supply hole for supplying oil is formed. The oil supplied from the oil supply hole can be stored by the depression 33d such as the D cut, and the swinging portion can be easily lubricated.
（実施の形態５）
次に、ベーン３３先端の挿入部３３ａとピストン３２の嵌合部３２ａとで形成される揺動部にオイルを供給する更に他の実施の形態を説明する。
図１７は本発明の第５の実施の形態における回転型圧縮機の圧縮機構部の拡大断面図であり、図１８は同回転型圧縮機の要部を示す拡大斜視図である。なお、前述の実施の形態１から４と同一構成要素には同一符号を付与して説明を省略する。
(Embodiment 5)
Next, still another embodiment for supplying oil to a swinging portion formed by the insertion portion 33a at the tip of the vane 33 and the fitting portion 32a of the piston 32 will be described.
FIG. 17 is an enlarged cross-sectional view of a compression mechanism of a rotary compressor according to a fifth embodiment of the present invention, and FIG. 18 is an enlarged perspective view showing a main part of the rotary compressor. The same components as those in the first to fourth embodiments are given the same reference numerals, and the description thereof is omitted.
本実施の形態では、ベーン３３先端とピストン３２の揺動部にオイルを供給する給油穴６０に臨むピストン３２に形成された円筒形の嵌合部３２ａに窪み３２ｃを設けたものである。この窪み３２ｃにより給油穴６０から供給されるオイルを貯留できると共に揺動部が潤滑しやすくなる。なおこの窪み３２ｃはベーン３３もしくはピストン３２の一方、又は両方に構成してもよい。 In the present embodiment, a hollow 32c is provided in a cylindrical fitting portion 32a formed in the piston 32 facing the oil supply hole 60 for supplying oil to the tip of the vane 33 and the swinging portion of the piston 32. The recess 32c can store the oil supplied from the oil supply hole 60 and can easily lubricate the swinging portion. The recess 32c may be formed in one or both of the vane 33 and the piston 32.
なお、前述の各実施の形態において、ベーン３３先端とピストン３２の揺動部にオイルを供給する給油穴の端部にＣ面取りを設けてもよい。このＣ面取りにより給油穴から供給されるオイルを貯留できると共に揺動部が潤滑しやすくなる。 In each of the above-described embodiments, C chamfering may be provided at the end of the oil supply hole that supplies oil to the tip of the vane 33 and the swinging portion of the piston 32. By this C chamfering, the oil supplied from the oil supply hole can be stored and the swinging portion can be easily lubricated.
以上のように、本発明の回転型圧縮機は、ベーン先端の磨耗や焼き付きなどの信頼性面の低下を抑制するとともに、漏れ損失と摺動損失を同時に低減し、圧縮機の高効率化を図ることが可能となる。これにより、ＨＦＣ系冷媒やＨＣＦＣ系冷媒を用いたエアーコンディショナー用圧縮機のほかに、自然冷媒ＣＯ２や可燃性冷媒を用いたエアーコンディショナーやヒートポンプ式給湯機などにも適用できる。 As described above, the rotary compressor of the present invention suppresses deterioration of reliability such as vane tip wear and seizure, and simultaneously reduces leakage loss and sliding loss, thereby improving the efficiency of the compressor. It becomes possible to plan. Thereby, in addition to the compressor for an air conditioner using an HFC refrigerant or an HCFC refrigerant, the present invention can be applied to an air conditioner using a natural refrigerant CO2 or a flammable refrigerant, a heat pump type hot water heater, or the like.
１ 密閉容器
２ 電動機
３ 圧縮機構部
５ 上シェル
６ オイル溜り
７ バネ
２２ 固定子
２４ 回転子
３０ シリンダ
３０ａ シリンダ内壁
３０ｂ スロット
３１ クランク軸
３１ａ 偏芯部
３２ ピストン
３２ａ 嵌合部
３２ｂ ピストン内面
３２ｃ 窪み
３３ ベーン
３３ａ 挿入部
３３ｂ ベーン背面
３３ｃ ベーン下端面
３３ｄ 窪み
３４ 端板
３４ａ 上軸受
３５ 端板
３５ａ 下軸受
３６ 吐出弁
３７ カップマフラ−
３８ 吐出ポート
３９ 圧縮室
４０ 吸入ポート
４１ 油穴
４２ 給油穴
４３ 給油穴
４４ 給油穴
４５ 油溝
４８ 経路
５１ 冷媒吐出管
５２ 吐出空間
６０ 給油穴
６１ 給油穴
６２ 給油穴
６３ 給油穴
DESCRIPTION OF SYMBOLS 1 Airtight container 2 Electric motor 3 Compression mechanism part 5 Upper shell 6 Oil reservoir 7 Spring 22 Stator 24 Rotor 30 Cylinder 30a Cylinder inner wall 30b Slot 31 Crankshaft 31a Eccentric part 32 Piston 32a Fitting part 32b Piston inner surface 32c Depression 33 Vane 33a Insertion portion 33b Back surface of vane 33c Lower end surface of vane 33d Depression 34 End plate 34a Upper bearing 35 End plate 35a Lower bearing 36 Discharge valve 37 Cup muffler
38 discharge port 39 compression chamber 40 suction port 41 oil hole 42 oil supply hole 43 oil supply hole 44 oil supply hole 45 oil groove 48 path 51 refrigerant discharge pipe 52 discharge space 60 oil supply hole 61 oil supply hole 62 oil supply hole 63 oil supply hole
Claims (6)
前記シリンダ内を吸入室と吐出口が開口する圧縮室に仕切り前記シリンダのベーン溝に挿入されるベーンと、
前記ベーン先端の挿入部と前記挿入部が挿入される前記ピストンの嵌合部とで形成される揺動部と、
を備え、
前記揺動部で前記ピストンと前記ベーンとが揺動自在に接続される回転型圧縮機であって、
高圧のオイル溜りから前記揺動部へのオイル供給経路を形成したことを特徴とする回転型圧縮機。A piston that swivels in the cylinder;
A vane that is partitioned into a compression chamber in which a suction chamber and a discharge port are opened in the cylinder and is inserted into a vane groove of the cylinder;
A swinging portion formed by an insertion portion of the vane tip and a fitting portion of the piston into which the insertion portion is inserted;
With
A rotary compressor in which the piston and the vane are swingably connected at the swing portion;
A rotary compressor characterized in that an oil supply path from a high-pressure oil reservoir to the swinging portion is formed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010529964A JP5542675B2 (en) | 2009-01-29 | 2010-01-28 | Rotary compressor |
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009017572 | 2009-01-29 | ||
| JP2009017572 | 2009-01-29 | ||
| JP2010529964A JP5542675B2 (en) | 2009-01-29 | 2010-01-28 | Rotary compressor |
| PCT/JP2010/000503 WO2010087180A1 (en) | 2009-01-29 | 2010-01-28 | Rotary compressor |
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| JPWO2010087180A1 true JPWO2010087180A1 (en) | 2012-08-02 |
| JP5542675B2 JP5542675B2 (en) | 2014-07-09 |
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| JP2010529964A Active JP5542675B2 (en) | 2009-01-29 | 2010-01-28 | Rotary compressor |
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| Country | Link |
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| JP (1) | JP5542675B2 (en) |
| CN (1) | CN102016320A (en) |
| WO (1) | WO2010087180A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5948209B2 (en) * | 2012-10-11 | 2016-07-06 | 東芝キヤリア株式会社 | Hermetic compressor and refrigeration cycle apparatus |
| KR102351791B1 (en) | 2014-09-19 | 2022-01-17 | 엘지전자 주식회사 | Compressor |
| CN110836184B (en) | 2018-08-17 | 2022-03-04 | Lg电子株式会社 | Rotary compressor |
| KR102254378B1 (en) * | 2019-05-31 | 2021-05-21 | 엘지전자 주식회사 | Rotary compressor |
| KR102250823B1 (en) * | 2019-07-17 | 2021-05-11 | 엘지전자 주식회사 | Rotary compressor |
| CN117287390A (en) * | 2023-07-18 | 2023-12-26 | 广州市德善数控科技有限公司 | Oscillating rotor type compressor |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57184291U (en) * | 1981-05-19 | 1982-11-22 | ||
| JPS6397895A (en) * | 1986-10-09 | 1988-04-28 | Daikin Ind Ltd | Helium compressor |
| JPH04228894A (en) * | 1990-12-27 | 1992-08-18 | Matsushita Refrig Co Ltd | Rotary compressor |
| JPH04255591A (en) * | 1991-02-05 | 1992-09-10 | Matsushita Refrig Co Ltd | Rotary compressor |
| JPH06257579A (en) * | 1993-03-04 | 1994-09-13 | Matsushita Electric Ind Co Ltd | Rotary compressor |
| JPH08151988A (en) * | 1994-11-28 | 1996-06-11 | Matsushita Electric Ind Co Ltd | Rotary compressor |
| JPH10148193A (en) * | 1996-11-19 | 1998-06-02 | Matsushita Electric Ind Co Ltd | Rotary compressor |
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- 2010-01-28 WO PCT/JP2010/000503 patent/WO2010087180A1/en active Application Filing
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| Publication number | Publication date |
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| JP5542675B2 (en) | 2014-07-09 |
| CN102016320A (en) | 2011-04-13 |
| WO2010087180A1 (en) | 2010-08-05 |
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