JP2005188294A - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
JP2005188294A
JP2005188294A JP2003426823A JP2003426823A JP2005188294A JP 2005188294 A JP2005188294 A JP 2005188294A JP 2003426823 A JP2003426823 A JP 2003426823A JP 2003426823 A JP2003426823 A JP 2003426823A JP 2005188294 A JP2005188294 A JP 2005188294A
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Prior art keywords
orbiting scroll
oil supply
scroll
wrap
component
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JP2003426823A
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JP4329530B2 (en
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Taisei Kobayakawa
大成 小早川
Akinori Fukuda
昭徳 福田
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Panasonic Holdings Corp
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Matsushita Electric Industrial Co Ltd
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Priority to JP2003426823A priority Critical patent/JP4329530B2/en
Priority to CNB2004101048733A priority patent/CN100400887C/en
Publication of JP2005188294A publication Critical patent/JP2005188294A/en
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Abstract

<P>PROBLEM TO BE SOLVED: To improve sealing of a compression space, to secure lubricity and cooling of a sliding part and to improve high performance and high reliability in simple constitution. <P>SOLUTION: This scroll compressor is constituted by providing a plurality of oil feeding fine pores 120a, b communicating with an oil reservoir in a high pressure space on a lap head end surface without providing a chip seal groove on the lap head end surface of a revolving scroll part 103. Consequently, it is possible to improve the sealing of the compression spaces and to promote lubricity and cooling of the sliding part by pressure-differentially feeding oil to the compression spaces 105a, b in the middle of compression by the plurality of oil feeding fine pores 120a, b. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、空調機、冷凍機等に使用されるスクロール圧縮機に関するものである。   The present invention relates to a scroll compressor used for an air conditioner, a refrigerator, and the like.

以下に従来のスクロール圧縮機の圧縮機構部への給油方式（例えば、特許文献１参照）について図面を参照にしながら説明する。   Hereinafter, an oil supply method (for example, see Patent Document 1) to a compression mechanism portion of a conventional scroll compressor will be described with reference to the drawings.

図１４は特許文献１に記載された従来のスクロール圧縮機の縦断面図を示すものである。   FIG. 14 is a longitudinal sectional view of a conventional scroll compressor described in Patent Document 1.

図１４に示すように、旋回軸受１８を潤滑した後の潤滑油は旋回スクロール２の背部５に満たされる。一方、旋回スクロール２のスクロールラップ２ｂの先端にはチップシール溝２ｃが設けられており、これにチップシール２２が装着されている。また、固定スクロール１のスクロールラップ１ｂの先端にもチップシールが装着されている。旋回スクロール２には、このチップシール溝２ｃと旋回スクロール背部５とを連通させる連通孔２ｄが形成されている。この旋回スクロール背部５の圧力は連通孔２ｄの断面積で絞られ概ね一定に保たれているため、潤滑油量を常に好ましい状態に保つことができる。旋回スクロール２の背部５に満たされた潤滑油８は連通孔２ｄよりチップシール溝２ｃに供給され、チップシール２２の背面部２ｆはもちろんのことスクロールラップ２ｂ先端部の隙間まで全面が潤滑油８で覆われる。チップシール２２の周囲から溢れた潤滑油８はさらに、固定スクロール１に配設されたチップシール２１の周囲を覆うようになる。   As shown in FIG. 14, the lubricating oil after lubricating the orbiting bearing 18 is filled in the back portion 5 of the orbiting scroll 2. On the other hand, a tip seal groove 2c is provided at the tip of the scroll wrap 2b of the orbiting scroll 2, and a tip seal 22 is attached thereto. A tip seal is also attached to the tip of the scroll wrap 1 b of the fixed scroll 1. The orbiting scroll 2 is formed with a communication hole 2d that allows the tip seal groove 2c and the orbiting scroll back portion 5 to communicate with each other. Since the pressure of the orbiting scroll back portion 5 is reduced by the cross-sectional area of the communication hole 2d and is kept substantially constant, the amount of lubricating oil can always be kept in a preferable state. Lubricating oil 8 filled in the back portion 5 of the orbiting scroll 2 is supplied to the tip seal groove 2c through the communication hole 2d, and the entire surface of the tip seal 22 extends to the clearance at the tip of the scroll wrap 2b as well as the rear portion 2f. Covered with. The lubricating oil 8 overflowing from the periphery of the tip seal 22 further covers the periphery of the tip seal 21 provided in the fixed scroll 1.

この結果、チップシール２１、２２の全面が潤滑油８によって覆われるため、シール性能が向上し、さらにはチップシール先端面の摺動特性も向上する。また、潤滑油８は常に供給されるためチップシール先端部に摩擦熱がこもらず常に比較的低い温度が保たれ、摺動特性を向上させることができる。また、チップシール２２は図に示すように、潤滑油８の圧力によって固定スクロール１の歯底面に所定の力で押し付けられるため、スクロールラップの先端部における径方向の洩れを低減できる。
特開平６−２８８３６１号公報 As a result, since the entire surfaces of the chip seals 21 and 22 are covered with the lubricating oil 8, the sealing performance is improved, and the sliding characteristics of the tip seal tip surface are also improved. Further, since the lubricating oil 8 is always supplied, frictional heat does not accumulate at the tip seal tip, and a relatively low temperature is always maintained, so that sliding characteristics can be improved. Further, as shown in the figure, the tip seal 22 is pressed against the tooth bottom surface of the fixed scroll 1 by a pressure of the lubricating oil 8 with a predetermined force, so that leakage in the radial direction at the tip end portion of the scroll wrap can be reduced.
JP-A-6-288361

しかしながら、上記従来の構成では、吐出圧力空間に連通する給油孔２ｄが吸入空間に連通するチップシール溝２ｃに開口しているため、その圧力差に応じた給油量が連続的に給油孔２ｄ経由で吸入室内に供給されることになり、その結果吸入ガスは高温高圧オイルからの受熱損失により、体積効率が低下するという課題を有していた。   However, in the above conventional configuration, the oil supply hole 2d communicating with the discharge pressure space is opened in the tip seal groove 2c communicating with the suction space, so that the oil supply amount corresponding to the pressure difference continuously passes through the oil supply hole 2d. As a result, the suction gas has a problem that the volumetric efficiency is lowered due to heat loss from the high-temperature and high-pressure oil.

これを改善する方策としては、給油孔２ｄの孔径を小さくするかチップシール溝２ｃを浅くして流路抵抗により給油量を減らす、もしくはチップシール溝２ｃ長さを短くして端部を吸入室から離して、受熱損失を減らせばよいが、前者の方策ではチップシール溝２ｃとチップシール２２の間に生じる隙間を十分にシールできないという性能面の課題が生じ、後者の場合は吸入空間のシールと潤滑が不足するという信頼性面の課題が生じる。   As measures to improve this, the diameter of the oil supply hole 2d is reduced or the tip seal groove 2c is shallowed to reduce the amount of oil supplied by the flow resistance, or the tip seal groove 2c is shortened to connect the end to the suction chamber. It is sufficient to reduce the heat receiving loss, but the former method has a performance problem that the gap formed between the tip seal groove 2c and the tip seal 22 cannot be sufficiently sealed. In the latter case, the suction space is sealed. This leads to a reliability problem of insufficient lubrication.

本発明は、このような従来の課題を解決するものであり、高性能かつ高信頼性を確保するスクロール圧縮機を提供することを目的とする。   The present invention solves such a conventional problem, and an object of the present invention is to provide a scroll compressor that ensures high performance and high reliability.

前記従来の課題を解決するために、本発明は旋回スクロール部品のラップ先端面にチップシール溝を設けずにかつラップ先端面に高圧空間のオイル溜まりに連通する複数の給油細孔を設けるものである。   In order to solve the above-mentioned conventional problems, the present invention provides a plurality of oil supply pores communicating with an oil sump in a high-pressure space without providing a tip seal groove on the wrap tip surface of the orbiting scroll part. is there.

この複数の給油細孔により、圧縮途中の圧縮室に差圧給油し、圧縮室のシールを高めるとともに、摺動部の潤滑と冷却を促進するものである。   The plurality of oil supply pores provide differential pressure oil supply to the compression chamber in the middle of compression, enhances the seal of the compression chamber, and promotes lubrication and cooling of the sliding portion.

本発明のスクロール圧縮機は、旋回スクロール部品のラップ先端に設けた複数の給油細孔からの給油によりチップシールを使用することなく、高性能かつ高信頼性を実現することができる。   The scroll compressor of the present invention can achieve high performance and high reliability without using a tip seal by supplying oil from a plurality of oil supply pores provided at the lap ends of the orbiting scroll component.

第１の発明は旋回スクロール部品のラップ先端面にチップシール溝を設けずにかつラップ先端面に高圧空間のオイル溜まりに連通する複数の給油細孔を設けることによって、圧縮途中の圧縮室に差圧給油し、圧縮室のシールを高めることによって高性能化を実現するとともに、摺動部の潤滑と冷却を促進することによって高信頼性も実現することができる。   According to the first aspect of the present invention, a tip seal groove is not provided on the wrap front end surface of the orbiting scroll component, and a plurality of oil supply pores communicating with the oil reservoir in the high pressure space are provided on the wrap front end surface. High performance can be achieved by pressure-lubricating and enhancing the seal of the compression chamber, and high reliability can be achieved by promoting lubrication and cooling of the sliding portion.

第２の発明は、第１の発明における複数の給油細孔を、旋回スクロール鏡板内の１つの給油孔に集約して連通させることによって、第１の発明と同様な効果をより少ない加工工数で実現することができる。   In the second invention, the same effect as in the first invention can be achieved with a smaller number of processing steps by consolidating the plurality of oil supply pores in the first invention into one oil supply hole in the orbiting scroll end plate. Can be realized.

第３の発明は、第１の発明における複数の給油細孔の孔径を異ならせることによって、隣接する圧縮室への、細かい給油配分の制御をすることができ、更なる高性能化と高信頼性化を図ることができる。   In the third aspect of the invention, by making the diameters of the plurality of oil supply pores in the first aspect different, fine distribution of oil supply to the adjacent compression chambers can be controlled, and further improvement in performance and high reliability can be achieved. Can be improved.

第４の発明は、第３の発明における複数の給油細孔の孔径を、細孔の両端の差圧が大きくなるラップ巻終わり側ほど小さくすることによって、吸入空間への過剰給油を抑え、冷媒ガスの過熱による体積効率の低下を回避することができ、更なる高性能化を図ることができる。   According to a fourth aspect of the invention, excessive oil supply to the suction space is suppressed by reducing the diameter of the plurality of oil supply pores in the third invention toward the end of the wrap winding where the differential pressure across the pores increases. A decrease in volumetric efficiency due to gas overheating can be avoided, and further performance enhancement can be achieved.

第５の発明は、第１の発明における複数の給油細孔の長さを、細孔の周辺温度が高くなるラップ巻始め側ほど短くすることによって、熱膨張による旋回スクロール部品のラップ先端と固定スクロール部品の底面空間の接近による給油細孔開口端近傍の流路抵抗の増大を回避することができ、更なる高信頼性化を図ることができる。   According to a fifth aspect of the present invention, the length of the plurality of oil supply pores in the first invention is shortened toward the wrap winding start side where the peripheral temperature of the pores is higher, thereby fixing the wrap tips of the orbiting scroll parts by thermal expansion. An increase in flow path resistance in the vicinity of the oil supply pore opening end due to the approach of the bottom surface space of the scroll component can be avoided, and higher reliability can be achieved.

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。   Embodiments of the present invention will be described below with reference to the drawings.

（実施の形態１）
図１は、本発明の実施の形態１におけるスクロール圧縮機の縦断面図、図２は旋回スクロール部品の拡大断面図、図３は旋回スクロール部品をラップ側から見た図である。 (Embodiment 1)
1 is a longitudinal cross-sectional view of a scroll compressor according to Embodiment 1 of the present invention, FIG. 2 is an enlarged cross-sectional view of an orbiting scroll component, and FIG. 3 is a view of the orbiting scroll component as viewed from the lap side.

図１から図３において、吸入管１０１より吸い込まれた冷媒ガスは、固定スクロール部品１０３の吸入通路１０２を経て、旋回スクロール部品１０４とかみ合わさってできる圧縮室１０５ａ、ｂに閉じ込められ、中心に向かって容積を減少させながら圧縮され、吐出ポート１０６より吐出される。潤滑油はトロコイドポンプ１０７によって吸い上げられ、クランクシャフト１０８の内部の貫通孔１０９を通り旋回スクロール部品１０４の偏心軸受け内部空間１１０へと導かれる。   In FIG. 1 to FIG. 3, the refrigerant gas sucked from the suction pipe 101 passes through the suction passage 102 of the fixed scroll part 103 and is confined in the compression chambers 105 a and b formed by meshing with the orbiting scroll part 104, toward the center. As the volume is reduced, the compressed air is discharged from the discharge port 106. Lubricating oil is sucked up by the trochoid pump 107 and guided to the eccentric bearing inner space 110 of the orbiting scroll component 104 through the through hole 109 in the crankshaft 108.

ここから、オイル流路は二手に分岐し、一方は旋回スクロール部品１０４の鏡板内に設けられ反ラップ側に開口する絞り部１１１を経由して固定スクロール部品１０３と旋回スクロール部品１０４と主軸受部品１１２に囲まれて形成される背圧室１１３へと導かれる。この背圧室１１３は吐出圧力と吸入圧力の中間圧力となっており、背圧調整機構１１４によりこの中間圧力を一定圧となるよう制御する。背圧調整機構１１４は、背圧室１１３と固定スクロール部品１０３の吸入孔近傍１１５と連通する通路１１６との間に、バルブ１１７を設けたもので、背圧室１１３の圧力が設定圧力より高くなるとバルブ１１７が開き、背圧室１１３のオイルが吸入空間１１８へ供給され、背圧室内をほぼ一定の中間圧力に維持している。また吸入空間１１８へ供給されたオイルは旋回スクロール部品１０４の旋回運動とともに圧縮室１０５ａへと移動し、圧縮室間の漏れ防止に役立っている。   From here, the oil flow path is bifurcated, and one of them is provided in the end plate of the orbiting scroll component 104 and passes through a throttle 111 that opens to the opposite side of the wrap, and the fixed scroll component 103, the orbiting scroll component 104, and the main bearing component 112 is led to a back pressure chamber 113 surrounded by 112. The back pressure chamber 113 is an intermediate pressure between the discharge pressure and the suction pressure, and the intermediate pressure is controlled by the back pressure adjusting mechanism 114 so as to be a constant pressure. The back pressure adjusting mechanism 114 is provided with a valve 117 between the back pressure chamber 113 and the passage 116 communicating with the vicinity of the suction hole 115 of the fixed scroll part 103, and the pressure in the back pressure chamber 113 is higher than the set pressure. Then, the valve 117 is opened, and the oil in the back pressure chamber 113 is supplied to the suction space 118, and the back pressure chamber is maintained at a substantially constant intermediate pressure. The oil supplied to the suction space 118 moves to the compression chamber 105a along with the orbiting motion of the orbiting scroll component 104, and serves to prevent leakage between the compression chambers.

もう一方のオイル流路は旋回スクロール部品１０４の鏡板内に形成された第１の給油経路１１９ａからラップ内の高さ方向に設けられた第１の給油細孔１２０ａへ導かれ、圧縮室１０５ａに給油される。同様に、旋回スクロール部品１０４の鏡板内に形成された第２の給油経路１１９ｂからラップ内の高さ方向に設けられた第２の給油細孔１２０ｂへ導かれ、別の圧縮室１０５ｂに給油される。固定スクロール部品１０３のラップ高さと旋回スクロール部品１０４のラップ高さを適量に設定することによって、チップシールを使用しなくても第１の給油細孔１２０ａおよび第２の給油細孔１２０ｂからの給油によって、圧縮室間のシールを確保でき圧縮モレを回避することができる。また、この給油により、ラップ間等の摺動部の潤滑と冷却もおこなうことができ、摩耗や焼付きを回避することができる。   The other oil flow path is led from the first oil supply path 119a formed in the end plate of the orbiting scroll component 104 to the first oil supply hole 120a provided in the height direction in the wrap, and enters the compression chamber 105a. Refueled. Similarly, the second oil supply path 119b formed in the end plate of the orbiting scroll component 104 is guided to the second oil supply hole 120b provided in the height direction in the lap, and supplied to another compression chamber 105b. The By setting the wrap height of the fixed scroll part 103 and the wrap height of the orbiting scroll part 104 to appropriate amounts, the oil supply from the first oil supply hole 120a and the second oil supply hole 120b can be performed without using the tip seal. As a result, a seal between the compression chambers can be secured and compression leakage can be avoided. In addition, lubrication and cooling of sliding parts such as between laps can be performed by this lubrication, and wear and seizure can be avoided.

なお、第１の給油細孔１２０ａと第２の給油細孔１２０ｂは冷媒吸入から吐出までの間の給油が必要な任意の位置にそれぞれ設けることによって、給油配分することができる。本実施例では給油孔が２つの場合で説明したが、必要に応じてその数を増やせばよい。   The first oil supply pore 120a and the second oil supply pore 120b can be distributed by providing them at any position where the oil supply from the refrigerant suction to the discharge is necessary. In the present embodiment, the case of two oil supply holes has been described, but the number may be increased as necessary.

（実施の形態２）
図４は、本発明実施の形態２における旋回スクロール部品１０４ｂの拡大断面図、図５は旋回スクロール部品１０４ｂをラップ側から見た図である。図４及び図５に示すように、ラップ内の高さ方向に設ける第２の給油細孔１２０ｄを第１の給油細孔１２０ｃが連通する給油経路１１９ｃに連通させる構成にしたものである。このような構成にすることによって、実施の形態１と同様な効果を安価かつ合理的に実現することができる。 (Embodiment 2)
4 is an enlarged cross-sectional view of the orbiting scroll component 104b according to Embodiment 2 of the present invention, and FIG. 5 is a view of the orbiting scroll component 104b as viewed from the lap side. As shown in FIGS. 4 and 5, the second oil supply pore 120d provided in the height direction in the lap is configured to communicate with the oil supply passage 119c through which the first oil supply pore 120c communicates. By adopting such a configuration, the same effect as in the first embodiment can be realized inexpensively and reasonably.

（実施の形態３）
図６は、本発明の実施の形態３における旋回スクロール部品１０４ｃの拡大断面図、図７は旋回スクロール部品１０４ｃをラップ側から見た図である。図６及び図７に示すように、第２の給油細孔１２０ｆの径寸法を第１の給油孔１２０ｅの径寸法と異ならせる構成にしたものである。このような構成にすることによって、より多くの給油量が必要な場所に開口する給油細孔径を選択的に大きくする等の細かい給油配分の制御をすることが可能になり、更なる高性能化と高信頼性化を図ることができる。 (Embodiment 3)
6 is an enlarged cross-sectional view of the orbiting scroll component 104c according to Embodiment 3 of the present invention, and FIG. 7 is a view of the orbiting scroll component 104c as viewed from the lap side. As shown in FIGS. 6 and 7, the diameter of the second oil supply hole 120f is different from the diameter of the first oil supply hole 120e. By adopting such a configuration, it becomes possible to control the fine oil distribution such as selectively increasing the diameter of the oil supply pores that open to places where a larger amount of oil is needed, thereby further improving performance. High reliability can be achieved.

（実施の形態４）
図８は、本発明の実施の形態４における旋回スクロール部品１０４ｄの拡大断面図、図９は旋回スクロール部品１０４ｄをラップ側から見た図である。図８及び図９に示すように、ラップの巻終り側に設ける第２の給油細孔１２０ｈの径寸法を巻始め側に設ける第１の給油孔１２０ｇの径寸法より小さくする構成にしたものである。このような構成にすることによって、給油細孔の両開口端の差圧が大きくなる巻終り側の第２の給油細孔１２０ｈ経由の給油量を抵抗をつけることによって抑え、吸入ガスの過熱による体積効率の低下を回避することが可能になり、更なる高性能化を図ることができる。 (Embodiment 4)
FIG. 8 is an enlarged cross-sectional view of the orbiting scroll part 104d according to Embodiment 4 of the present invention, and FIG. 9 is a view of the orbiting scroll part 104d as viewed from the lap side. As shown in FIGS. 8 and 9, the diameter of the second oil supply hole 120 h provided on the winding end side of the wrap is made smaller than the diameter of the first oil supply hole 120 g provided on the winding start side. is there. By adopting such a configuration, the oil supply amount via the second oil supply pore 120h on the winding end side where the differential pressure between the two opening ends of the oil supply pore becomes large is suppressed by adding resistance, and due to overheating of the intake gas It becomes possible to avoid a decrease in volumetric efficiency, and a further increase in performance can be achieved.

（実施の形態５）
図１０は、本発明実施の形態５における旋回スクロール部品１０４ｅの拡大断面図、図１１は旋回スクロール部品１０４ｅをラップ側から見た図である。図１０及び図１１に示すように、ラップの巻始め側に設ける第１の給油細孔１２０ｉの長さを巻終り側に設ける第２の給油細孔１２０ｊの長さより短くする構成にしたものである。このような構成にすることによって、給油細孔の周辺温度が高くなり熱膨張による旋回スクロール部品１０４ｅのラップ先端と固定スクロール部品１０３の底面空間がより接近する第１の給油細孔１２０ｉの開口端近傍における流路抵抗の増大を回避することができ、圧縮室への給油安定化により、更なる高信頼性化を図ることができる。 (Embodiment 5)
FIG. 10 is an enlarged cross-sectional view of the orbiting scroll component 104e according to Embodiment 5 of the present invention, and FIG. 11 is a view of the orbiting scroll component 104e as viewed from the lap side. As shown in FIGS. 10 and 11, the length of the first oil supply pore 120i provided on the winding start side of the wrap is made shorter than the length of the second oil supply pore 120j provided on the winding end side. is there. With such a configuration, the peripheral temperature of the oil supply pores becomes high, and the opening end of the first oil supply pore 120i in which the wrap tip of the orbiting scroll component 104e and the bottom space of the fixed scroll component 103 are closer due to thermal expansion. An increase in flow path resistance in the vicinity can be avoided, and further improvement in reliability can be achieved by stabilizing the oil supply to the compression chamber.

なお、本実施例は旋回スクロール部品がアルミ合金製、固定スクロール部品が鋳鉄製の場合等、旋回スクロール部品が固定スクロール部品よりも熱膨張係数が小さい材料でつくられている場合は特に効果的である。   This embodiment is particularly effective when the orbiting scroll part is made of a material having a smaller thermal expansion coefficient than the fixed scroll part, such as when the orbiting scroll part is made of an aluminum alloy and the fixed scroll part is made of cast iron. is there.

（実施の形態６）
さらに、図１２、１３に示すように、ラップ巻始め側の給油細孔の長さを巻終り側の給油細孔の長さより短くする手段として給油細孔の開口端周辺部を窪ませることによって、流路抵抗の増加を回避しても、実施の形態５の場合と同様な効果を得ることができる。 (Embodiment 6)
Furthermore, as shown in FIGS. 12 and 13, by depressing the periphery of the opening end of the oil supply pore as a means for making the length of the oil supply pore on the wrap winding start side shorter than the length of the oil supply pore on the winding end side. Even if the increase in the channel resistance is avoided, the same effect as in the fifth embodiment can be obtained.

以上のように、本発明のスクロール圧縮機は、チップシールを使用することなく、高性能かつ高信頼性を実現することができるので、空調機、冷凍機等に適用できる。   As described above, the scroll compressor of the present invention can realize high performance and high reliability without using a tip seal, and thus can be applied to an air conditioner, a refrigerator, and the like.

本発明実施の形態１における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. 同旋回スクロール部品の拡大断面図Expanded sectional view of the orbiting scroll component 同旋回スクロール部品をラップ側より見た図A view of the orbiting scroll component viewed from the lap side 本発明実施の形態２における旋回スクロール部品の拡大断面図The expanded sectional view of the turning scroll components in Embodiment 2 of this invention 同旋回スクロール部品をラップ側より見た図A view of the orbiting scroll component viewed from the lap side 本発明実施の形態３における旋回スクロール部品の拡大断面図The expanded sectional view of the turning scroll components in Embodiment 3 of this invention 同旋回スクロール部品をラップ側より見た図A view of the orbiting scroll component viewed from the lap side 本発明実施の形態４における旋回スクロール部品の拡大断面図The expanded sectional view of the turning scroll components in Embodiment 4 of this invention 同旋回スクロール部品をラップ側より見た図A view of the orbiting scroll component viewed from the lap side 本発明実施の形態５における旋回スクロール部品の拡大断面図The expanded sectional view of the turning scroll components in Embodiment 5 of this invention 同旋回スクロール部品をラップ側より見た図A view of the orbiting scroll component viewed from the lap side 本発明実施の形態６における旋回スクロール部品の拡大断面図The expanded sectional view of the turning scroll components in Embodiment 6 of this invention 同旋回スクロール部品をラップ側より見た図A view of the orbiting scroll component viewed from the lap side 従来のスクロール圧縮機の断面図Sectional view of a conventional scroll compressor

符号の説明Explanation of symbols

１０１ 吸入管
１０２ 吸入通路
１０３ 固定スクロール部品
１０４ 旋回スクロール部品
１０５ａ 圧縮室
１０５ｂ 圧縮室
１０６ 吐出ポート
１０７ トロコイドポンプ
１０８ クランクシャフト
１０９ 貫通孔
１１０ 偏心軸受け内部空間
１１１ 絞り部
１１２ 軸受
１１３ 背圧室
１１４ 背圧調整機構
１１６ 斜め通路
１１７ バルブ
１１９ 給油通路
１２０ 給油細孔 DESCRIPTION OF SYMBOLS 101 Suction pipe 102 Suction passage 103 Fixed scroll part 104 Orbiting scroll part 105a Compression chamber 105b Compression chamber 106 Discharge port 107 Trochoid pump 108 Crankshaft 109 Through-hole 110 Eccentric bearing internal space 111 Restriction part 112 Bearing 113 Back pressure chamber 114 Back pressure adjustment Mechanism 116 Diagonal passage 117 Valve 119 Oil supply passage 120 Oil supply pore

Claims (5)

鏡板上に渦巻きラップを形成した固定スクロール部品と旋回スクロール部品のラップどうしをかみ合わせて複数の圧縮室を形成し、前記旋回スクロール部品の反ラップ側鏡板面に一定圧を印加することで両スクロール部品の鏡板部とラップ先端部とを互いに接触させ、前記旋回スクロール部品の反ラップ側鏡板面に配置された自転拘束部品により旋回スクロール部品の自転を防ぎつつ旋回運動をさせることにより、前記圧縮室を外周側から中心に向かって容積を減少させながら移動させて圧縮を行うスクロール圧縮機であって、前記旋回スクロール部品のラップ先端面に高圧空間のオイル溜まりに連通する複数の給油細孔を設けてなるスクロール圧縮機。 A plurality of compression chambers are formed by engaging the wraps of the fixed scroll part and the orbiting scroll part formed with a spiral wrap on the end plate, and both scroll parts are applied by applying a constant pressure to the end plate side of the orbiting scroll part opposite to the end. The end plate portion and the tip end portion of the orbiting scroll are brought into contact with each other, and the compression chamber is rotated by preventing the rotation of the orbiting scroll component by the rotation restricting component disposed on the anti-wrap side end plate surface of the orbiting scroll component. A scroll compressor that performs compression while reducing the volume from the outer peripheral side toward the center, wherein a plurality of oil supply pores that communicate with an oil sump in a high-pressure space are provided on a lap front end surface of the orbiting scroll component. Scroll compressor that becomes. 旋回スクロール部品のラップ先端面に設けられる複数の給油細孔は、旋回スクロール部品の鏡板内に設けられた１つの給油経路に集約されて連通することを特徴とする請求項１記載のスクロール圧縮機。 2. The scroll compressor according to claim 1, wherein a plurality of oil supply pores provided in a lap front end surface of the orbiting scroll part are aggregated and communicated with one oil supply path provided in an end plate of the orbiting scroll part. . 旋回スクロール部品のラップ先端面に設けられる複数の給油細孔の孔径が異なることを特徴とする請求項１記載のスクロール圧縮機。 The scroll compressor according to claim 1, wherein the hole diameters of the plurality of oil supply pores provided on the wrap front end surface of the orbiting scroll component are different. 旋回スクロール部品のラップ先端面に設けられる複数の給油細孔の孔径を、ラップ巻終わり側ほど小さくした請求項３記載のスクロール圧縮機。 The scroll compressor according to claim 3, wherein a hole diameter of a plurality of oil supply pores provided on a wrap front end surface of the orbiting scroll component is reduced toward a wrap winding end side. 旋回スクロール部品のラップ先端面に設けられる複数の給油細孔の長さを、ラップ巻始め側ほど短くした請求項１記載のスクロール圧縮機。 The scroll compressor according to claim 1, wherein the length of the plurality of oil supply pores provided on the wrap front end surface of the orbiting scroll component is shortened toward the wrap winding start side.
JP2003426823A 2003-12-24 2003-12-24 Scroll compressor Expired - Fee Related JP4329530B2 (en)

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JP2007192189A (en) * 2006-01-23 2007-08-02 Matsushita Electric Ind Co Ltd Scroll compressor
JP2008101559A (en) * 2006-10-20 2008-05-01 Hitachi Appliances Inc Scroll compressor and refrigeration cycle using the same
JP2008291658A (en) * 2007-05-22 2008-12-04 Panasonic Corp Scroll compressor
JP2010084687A (en) * 2008-10-01 2010-04-15 Sanden Corp Fluid machine
JP2010270694A (en) * 2009-05-22 2010-12-02 Panasonic Corp Scroll compressor

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CN102330681A (en) * 2011-09-30 2012-01-25 安徽美芝压缩机有限公司 Vortex compressor
CN103807166B (en) * 2012-11-14 2017-12-26 艾默生环境优化技术(苏州)有限公司 Scroll compressor having a plurality of scroll members
CN104047849B (en) * 2014-07-03 2017-01-18 湖南联力精密机械有限公司 Vortex air compressor with built-in lubricating oil path
CN109538471A (en) * 2018-12-03 2019-03-29 珠海格力节能环保制冷技术研究中心有限公司 Screw compressor and refrigeration equipment
WO2021258585A1 (en) * 2020-06-23 2021-12-30 艾默生环境优化技术(苏州)有限公司 Scroll compression mechanism and scroll compressor

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JPH06288361A (en) * 1993-04-07 1994-10-11 Hitachi Ltd Scroll compressor
CN1111725A (en) * 1993-11-19 1995-11-15 倪诗茂 High compression ratio volumetric fluid displacement device
JP4104047B2 (en) * 2001-05-18 2008-06-18 松下電器産業株式会社 Scroll compressor
JP3956726B2 (en) * 2002-03-06 2007-08-08 松下電器産業株式会社 Hermetic scroll compressor and its application equipment
JP2003328966A (en) * 2002-05-15 2003-11-19 Matsushita Electric Ind Co Ltd Scroll compressor

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007192189A (en) * 2006-01-23 2007-08-02 Matsushita Electric Ind Co Ltd Scroll compressor
JP2008101559A (en) * 2006-10-20 2008-05-01 Hitachi Appliances Inc Scroll compressor and refrigeration cycle using the same
JP2008291658A (en) * 2007-05-22 2008-12-04 Panasonic Corp Scroll compressor
JP2010084687A (en) * 2008-10-01 2010-04-15 Sanden Corp Fluid machine
JP2010270694A (en) * 2009-05-22 2010-12-02 Panasonic Corp Scroll compressor

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