JP3987697B2 - Gas compressor - Google Patents

Gas compressor Download PDF

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Publication number
JP3987697B2
JP3987697B2 JP2001267792A JP2001267792A JP3987697B2 JP 3987697 B2 JP3987697 B2 JP 3987697B2 JP 2001267792 A JP2001267792 A JP 2001267792A JP 2001267792 A JP2001267792 A JP 2001267792A JP 3987697 B2 JP3987697 B2 JP 3987697B2
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discharge
oil
cylinder
gas
gas passage
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JP2002250289A (en
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洋明 関口
誠 井尻
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カルソニックコンプレッサー株式会社
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Priority to JP2001267792A priority Critical patent/JP3987697B2/en
Priority to US10/033,853 priority patent/US20020094294A1/en
Priority to EP01310845A priority patent/EP1217215B1/en
Priority to MYPI20015848A priority patent/MY129076A/en
Priority to DE60109121T priority patent/DE60109121T2/en
Priority to CNB011381841A priority patent/CN1309960C/en
Publication of JP2002250289A publication Critical patent/JP2002250289A/en
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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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C18/344—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 inner member
    • F04C18/3446—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 inner member the inner and outer member being in contact along more than one line or surface
    • 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
    • F04C29/026—Lubricant separation
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、カーエアコンシステムの一部として車両に搭載される、または空調システムの一部として室外機に搭載される気体圧縮機に関し、特に、油含有高圧冷媒ガスの圧力損失を低減し、コンプレッサ性能の向上を図ったものである。
【０００２】
【従来の技術】
従来、この種の気体圧縮機は、たとえば図３に示したように内周略楕円状のシリンダ１を有し、そのシリンダ１の両端面にはサイドブロック２、３がそれぞれ取り付けられている。また、このようなフロントおよびリア側のサイドブロック２、３間に介挿されたシリンダ１の内側にはロータ４が配設されており、このロータ４は、その軸心に一体に設けたロータ軸５と、これを支持するサイドブロック２、３の軸受６、７とを介して回転可能に横架されている。
【０００３】
図４に示したように、ロータ４にはその径方向にスリット状にベーン溝８が５つ切り込み形成され、その各ベーン溝８にはベーン９がそれぞれ１つずつ装着されており、これらのベーン９はそれぞれロータ４の外周面からシリンダ１の内壁に向かって出没自在に設けられている。
【０００４】
シリンダ１の内側は、シリンダ１内壁、サイドブロック２、３内面、ロータ４外周面およびベーン９先端側両側面によって複数の小室に仕切られ、この仕切り形成された各小室が圧縮室１０であり、この圧縮室１０はロータ４が図中矢印イの方向に回転することにより容積の大小変化を繰り返す。
【０００５】
圧縮室１０の容積変化が生じると、その容積増加時に、吸入室１１内の油含有低圧冷媒ガスが、シリンダ１の吸入通路１２やサイドブロック２、３の吸入口１３を介して圧縮室１０へ吸入される。そして、圧縮室１０の容積が減少し始めると、その容積減少効果により圧縮室１０の冷媒ガスが圧縮され始め、その後、圧縮室１０の容積が最小付近に近づくと、圧縮された油含有高圧冷媒ガスの圧力により、シリンダ１楕円短径部付近に開設されているシリンダ吐出穴１４の吐出弁１５が開く。これにより、シリンダ吐出穴１４から圧縮室１０内の油含有高圧冷媒ガスが吐出する。
【０００６】
シリンダ吐出穴１４から吐出した油含有高圧冷媒ガスは、シリンダ１外周の吐出チャンバ１６と吐出ガス通路２４を通って、該サイドブロック３後部に取り付けられている油分離器１８の油分離フィルタ１８−１へ導かれる。
【０００７】
油分離フィルタ１８−１に導かれた油含有高圧冷媒ガスは、油分離フィルタ１８−１を構成している金網との衝突等により油成分とガス成分に分離され、そのガス成分は吐出室１９に流入し、かつ該吐出室１９からコンプレッサケースの吐出ポート（図示省略）を経てエアコンシステムのコンデンサ側に供給される。一方、分離後の油成分は、吐出室１９底部のオイル溜まり２０に滴下し貯留されるとともに、サイドブロック２、３やシリンダ１の油穴２１を通って該油を必要とする部位に供給される。油を必要とする部位としては、たとえば軸受６、７クリアランスや、サイドブロック２、３のシリンダ対向面側に形成されたサライ溝２２と、これに連通するベーン９底部のベーン背圧空間２３である。
【０００８】
しかしながら、上記のような従来の気体圧縮機にあっては、図５に示したように、油分離性能を高めるために油分離器１８の吐出ガス通路２４を２度直角に曲げ、これにより当該ガス通路２４の内壁に油含有高圧冷媒ガスが２回衝突する構成を採用していたが、このような衝突構造によると、油分離性能の向上効果は殆どなく、それよりむしろ油含有高圧冷媒ガスの圧力損失が大となる効果の方が大きく現れ、この圧力損失の増大がコンプレッサ性能を悪化させる要因となっている。
【０００９】
【発明が解決しようとする課題】
本発明は上記問題点を解決するためになされたもので、その目的とするところは、油含有高圧冷媒ガスの圧力損失を低減し、コンプレッサ性能の向上を図れる気体圧縮機を提供することにある。
【００１０】
【課題を解決するための手段】
上記目的を達成するために、この出願の請求項１に記載の発明は、一対のサイドブロック間に介挿されたシリンダと、上記シリンダ内に回転可能に横架されたロータと、上記ロータの外周面から上記シリンダの内壁に向かって出没自在に設けられたベーンと、上記シリンダ、サイドブロック、ロータおよびベーンによって仕切り形成される圧縮室と、上記圧縮室からの冷媒ガスを吐出するシリンダ吐出穴と、上記シリンダ吐出穴から吐出された冷媒ガスを一時貯留する吐出チャンバと、上記吐出チャンバから該吐出チャンバの下流側の油分離フィルタに向かって冷媒ガスを導く直線状の吐出ガス通路と、上記油分離フィルタを装着し、該油分離フィルタにより冷媒ガスと油とを分離する油分離器と、上記油分離器により分離された冷媒ガスと油とを一時貯留する吐出室と、を備え、上記シリンダ吐出孔、吐出チャンバ、吐出ガス通路、油分離器の油分離フィルタは、それぞれ２つずつ設けられ、上記２つの吐出ガス通路は、互いに左右対称となるように内向きに傾斜していることを特徴とする。
【００１１】
そして、請求項１に記載の発明によれば、吐出ガス通路の直線化により、該吐出ガス通路を通過する油含有高圧冷媒ガスの流れがスムーズになり、油含有高圧冷媒ガスの圧力損失が減少する。
【００１２】
更に、この出願の請求項２に記載の発明は、上記吐出ガス通路における油分離器側の出口部開口が上記吐出ガス通路の入口部開口の高さ位置と同一高さに設定されることにより、吐出ガス通路が水平状に延びていることを特徴とする。
【００１３】
そして、請求項２に記載の発明によれば、吐出チャンバと連通する吐出ガス通路は、入口部開口の高さ位置に対して、油分離器側の開口が同一高さ位置に設定されていることにより、吐出ガス通路は水平状に延びるとともに、最短経路をとることができ、油含有高圧冷媒ガスの圧力損失をより一層低減できる。
【００１６】
【発明の実施の形態】
以下、本発明に係る気体圧縮機の実施形態について添付図面を基に詳細に説明する。
【００１７】
なお、本実施形態の気体圧縮機の基本的な構成、たとえば、図３および図４を用いて説明すると、一対のサイドブロック２、３間にシリンダ１が介挿設置され、このシリンダ１内側にロータ４が回転可能に横架され、また、ロータ４にはその外周面からシリンダ１の内壁に向かってベーン９が出没自在に設けられていること、上記シリンダ１の内側にはベーン９等で仕切り形成された圧縮室１０が設けられており、この圧縮室１０はロータ４の回転により容積の大小変化を繰り返すとともに、その容積変化により吸入室内の油含有低圧冷媒ガスを吸気し圧縮すること、および、この圧縮された油含有高圧冷媒ガスはシリンダ吐出穴１４から吐出されること等は従来と同様なため、それと同一部材には同一符号を付し、その詳細説明は省略する。
【００１８】
本実施形態の気体圧縮機においても、上記のようにシリンダ吐出穴１４から吐出した油含有高圧冷媒ガスは、吐出チャンバ１６および吐出ガス通路２４を通って、油分離器１８に装着されている油分離フィルタ１８−１側へ導かれるが、本実施形態の気体圧縮機では、図１に示したように、そのような吐出ガス通路２４を直線状に形成し、吐出ガス通路２４の直線化を図っている。
【００１９】
すなわち、吐出ガス通路２４は、その一端２４ａ側が吐出チャンバ１６側に開口し、かつ他端２４ｂ側は油分離器１８の油分離フィルタ１８−１側に開口するように構成されており、このような吐出ガス通路２４の一端（入口部開口）２４ａから他端（出口部開口）２４ｂまでの間が途中で１度も曲がることなく完全に直線で結ばれるように形成されている。
【００２０】
また、吐出ガス通路２４は、吐出チャンバ１６からリア側のサイドブロック３を貫通して油分離器１８側へ入ってくるように穿孔形成されているが、本実施形態では、そのような油分離器１８側への吐出ガス通路２４の入り角も変わっていない。
図１から明らかなように、吐出ガス通路２４は、シリンダ１、サイドブロック２、３およびロータ４の軸線方向に対して斜めに直線状になっている。
【００２１】
つまり、従来の気体圧縮機における吐出ガス通路２４は、図５に示したようにリア側のサイドブロック３を貫通して油分離器１８側へ入った直後に、略直角に曲がっているが、本実施形態の気体圧縮機における吐出ガス通路２４は、図１に示したようにリア側のサイドブロック３を貫通して油分離器１８側へ入った直後も曲がることなく、直線状に形成されている。
【００２２】
本実施形態の気体圧縮機の場合、図４を用いて説明すると、シリンダ吐出穴１４、吐出チャンバ１６、吐出ガス通路２４、油分離器１８の油分離フィルタ１８−１は、それぞれ２つずつ設けられているが、これは、シリンダ１の内周略楕円形状とベーン９を５枚備える構造との関係から、ロータ４が１回転するとシリンダ１内の２箇所で吸気動作と圧縮動作が行なわれ、その２箇所で圧縮された油含有高圧冷媒ガスをそれぞれ別々に油分離器１８側へ導くようにしているためである。
【００２３】
上記２つの吐出ガス通路２４、２４は双方ともに前述の通り直線状に設けられているが、これらの両吐出ガス通路２４、２４は、互いに平行でなく、油分離器１８の中央に並設されている２つの油分離フィルタ１８−１、１８−１に向かってハの字状に斜めに配置されている。
【００２４】
本実施形態の気体圧縮機においても、シリンダ吐出穴１４から吐出した油含有高圧冷媒ガスは、吐出チャンバ１６と吐出ガス通路２４を通って油分離器１８の油分離フィルタ１８−１へ導かれるが、本実施形態のように吐出ガス通路２４の直線化を図ると、シリンダ吐出穴１４から油分離フィルタ１８−１側へと油含有高圧冷媒ガスをスムーズに移行させることができ、これにより、油含有高圧冷媒ガスの圧力損失が低減され、コンプレッサ性能が向上する。
【００２５】
ところで、油含有高圧冷媒ガスの圧力損失は吐出ガス通路２４の通路断面積にも関係があり、吐出ガス通路２４の通路断面積が大きいほど油含有高圧冷媒ガスの圧力損失は小さくなる。従って、吐出ガス通路２４の通路断面積はなるべく大きく設けることが好ましい。
【００２６】
次いで、図２は、本発明に係る気体圧縮機の別実施形態の構成を示すもので、図２（ａ）は油分離器をリア側からみた正面図、（ｂ）は油分離器をリアサイドブロック当接面側からみた正面図、（ｃ）は（ｂ）中Ｂ−Ｂ線断面図である。
【００２７】
すなわち、この実施形態においては、油含有高圧冷媒ガスの圧力損失をより低減するために、吐出ガス通路２４の一端２４ａ、すなわち、吐出ガス通路２４の入口部となる吐出チャンバ１６側の入口部開口の高さ位置に対して、吐出ガス通路２４の他端２４ｂ、すなわち、油分離器１８側の出口部開口の高さ位置を同一高さ位置に設定することにより、入口部並びに出口部の両開口２４ａ、２４ｂを結ぶ吐出ガス通路２４は、水平状をなす最短経路をとることになる。
図２から明らかなように、吐出ガス通路２４は、シリンダ１、サイドブロック２、３およびロータ４の軸線方向に対して斜めに直線状になっている。
【００２８】
従って、シリンダ吐出穴１４から吐出した油含有高圧冷媒ガスは、吐出チャンバ１６から吐出ガス通路２４を通じて油分離器１８の油分離フィルタ１８−１へ導かれるが、この実施形態のように、吐出ガス通路２４が最短経路を構成し、通路長さが短いため、油含有高圧冷媒ガスの圧力損失を低く抑えることができる。
【００２９】
更に、吐出ガス通路２４が水平状に延びているため、高圧冷媒ガス通過時の抵抗を少なくでき、このことも圧力損失を低減できる一要因となり、コンプレッサ機能をより向上させることができる。
【００３０】
【発明の効果】
本発明に係る気体圧縮機にあっては、上記の如く、吐出ガス通路を直線状に形成したため、この吐出ガス通路を介してシリンダ吐出穴側から油分離器の油分離フィルタ側へと油含有高圧冷媒ガスがスムーズに流れるようになるから、この種油含有高圧冷媒ガスの圧力損失が小さくなり、コンプレッサ性能の向上を図ることができるという効果を有する。
【００３１】
更に、本発明に係る気体圧縮機にあっては、吐出ガス通路を直線状に形成するとともに、吐出チャンバと連通する入口部開口の高さ位置と油分離器側の出口部開口の高さ位置を同一高さ位置に設定することにより、吐出ガス通路を水平状に延びる最短経路にでき、吐出ガス通路を通過する油含有高圧冷媒ガスの圧力損失をより低減させることでコンプレッサ性能をより向上させることができるという効果を有する。
【図面の簡単な説明】
【図１】図１は本発明に係る気体圧縮機の要部の説明図であって、（ａ）は当該気体圧縮機に内蔵されている油分離器の正面図、（ｂ）はその背面図、（ｃ）は（ｂ）のＢ−Ｂ線断面図である。
【図２】図２は本発明に係る気体圧縮機における別実施形態の要部の説明図であって、（ａ）は当該気体圧縮機に内蔵されている油分離器の正面図、（ｂ）はその背面図、（ｃ）は（ｂ）のＢ−Ｂ線断面図である。
【図３】従来の気体圧縮機の断面図。
【図４】図３のＡ−Ａ線断面図。
【図５】図５は図３に示した従来の気体圧縮機に搭載されている油分離器の説明図であって、（ａ）は当該油分離器の正面図、（ｂ）はその背面図、（ｃ）は（ｂ）のＢ−Ｂ線断面図である。
【符号の説明】
１ シリンダ
２ フロント側のサイドブロック
３ リア側のサイドブロック
４ ロータ
５ ロータ軸
６、７ 軸受
８ ベーン溝
９ ベーン
１０ 圧縮室
１１ 吸入室
１２ 吸入通路
１３ 吸入口
１４ シリンダ吐出穴
１５ 吐出弁
１６ 吐出チャンバ
１８ 油分離器
１８−１ 油分離フィルタ
１９ 吐出室
２０ オイル溜まり
２１ 油穴
２２ サライ溝
２３ ベーン背圧空間
２４ 吐出ガス通路[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a gas compressor that is mounted on a vehicle as a part of a car air-conditioning system or is mounted on an outdoor unit as a part of an air-conditioning system, and more particularly, a compressor that reduces pressure loss of oil-containing high-pressure refrigerant gas. This is intended to improve performance.
[0002]
[Prior art]
Conventionally, this type of gas compressor has, for example, a substantially elliptic cylinder 1 as shown in FIG. 3, and side blocks 2 and 3 are attached to both end faces of the cylinder 1. Further, a rotor 4 is disposed inside the cylinder 1 inserted between the front and rear side blocks 2 and 3, and the rotor 4 is a rotor provided integrally with the shaft center. The shaft 5 and the bearings 6 and 7 of the side blocks 2 and 3 that support the shaft 5 are rotatably mounted horizontally.
[0003]
As shown in FIG. 4, the rotor 4 is formed with five vane grooves 8 formed in a slit shape in the radial direction, and one vane 9 is mounted in each vane groove 8. The vanes 9 are provided so as to be able to protrude and retract from the outer peripheral surface of the rotor 4 toward the inner wall of the cylinder 1.
[0004]
The inner side of the cylinder 1 is partitioned into a plurality of small chambers by the inner wall of the cylinder 1, the side blocks 2, 3 inner surfaces, the outer peripheral surface of the rotor 4 and both side surfaces on the tip end side of the vane 9, and each of the formed compartments is a compression chamber 10, The compression chamber 10 repeats a change in volume as the rotor 4 rotates in the direction of arrow A in the figure.
[0005]
When the volume change of the compression chamber 10 occurs, when the volume increases, the oil-containing low-pressure refrigerant gas in the suction chamber 11 enters the compression chamber 10 via the suction passage 12 of the cylinder 1 and the suction ports 13 of the side blocks 2 and 3. Inhaled. When the volume of the compression chamber 10 starts to decrease, the refrigerant gas in the compression chamber 10 starts to be compressed due to the volume reduction effect. After that, when the volume of the compression chamber 10 approaches the minimum, the compressed oil-containing high-pressure refrigerant The discharge valve 15 of the cylinder discharge hole 14 opened in the vicinity of the cylinder 1 elliptical short diameter portion is opened by the pressure of the gas. Thereby, the oil-containing high-pressure refrigerant gas in the compression chamber 10 is discharged from the cylinder discharge hole 14.
[0006]
The oil-containing high-pressure refrigerant gas discharged from the cylinder discharge hole 14 passes through the discharge chamber 16 and the discharge gas passage 24 on the outer periphery of the cylinder 1 and passes through the oil separation filter 18-of the oil separator 18 attached to the rear part of the side block 3. Led to 1.
[0007]
The oil-containing high-pressure refrigerant gas guided to the oil separation filter 18-1 is separated into an oil component and a gas component by collision with a wire mesh constituting the oil separation filter 18-1, and the gas component is discharged into the discharge chamber 19. And is supplied from the discharge chamber 19 to the condenser side of the air conditioner system through the discharge port (not shown) of the compressor case. On the other hand, the separated oil component is dripped and stored in the oil reservoir 20 at the bottom of the discharge chamber 19 and is supplied to a portion requiring the oil through the oil holes 21 of the side blocks 2 and 3 and the cylinder 1. The The parts that require oil include, for example, the bearings 6 and 7, the Sarai groove 22 formed on the cylinder facing surface side of the side blocks 2 and 3, and the vane back pressure space 23 at the bottom of the vane 9 communicating therewith. is there.
[0008]
However, in the conventional gas compressor as described above, as shown in FIG. 5, in order to improve the oil separation performance, the discharge gas passage 24 of the oil separator 18 is bent at a right angle of 2 degrees, thereby The configuration in which the oil-containing high-pressure refrigerant gas collides twice with the inner wall of the gas passage 24 has been adopted. However, according to such a collision structure, there is almost no effect of improving the oil separation performance, but rather the oil-containing high-pressure refrigerant gas. The effect of increasing the pressure loss appears more greatly, and this increase in pressure loss is a factor that deteriorates the compressor performance.
[0009]
[Problems to be solved by the invention]
The present invention has been made to solve the above problems, and an object of the present invention is to provide a gas compressor capable of reducing the pressure loss of oil-containing high-pressure refrigerant gas and improving the compressor performance. .
[0010]
[Means for Solving the Problems]
In order to achieve the above object, an invention according to claim 1 of the present application includes a cylinder interposed between a pair of side blocks, a rotor rotatably mounted in the cylinder, A vane provided so as to freely protrude from the outer peripheral surface toward the inner wall of the cylinder, a compression chamber partitioned by the cylinder, side block, rotor and vane, and a cylinder discharge hole for discharging refrigerant gas from the compression chamber A discharge chamber that temporarily stores the refrigerant gas discharged from the cylinder discharge hole, a linear discharge gas passage that guides the refrigerant gas from the discharge chamber toward an oil separation filter on the downstream side of the discharge chamber, An oil separator that is equipped with an oil separation filter and separates refrigerant gas and oil by the oil separation filter; and a refrigerant gas separated by the oil separator; And a discharge chamber for storing temporarily bets, the cylinder discharge hole, the discharge chamber, the discharge gas passage, an oil separation filter of the oil separator is provided two each, the two discharge gas passage, right and left with each other It is inclined inward so as to be symmetric .
[0011]
According to the first aspect of the present invention, the flow of the oil-containing high-pressure refrigerant gas passing through the discharge gas passage becomes smooth due to the straightening of the discharge gas passage, and the pressure loss of the oil-containing high-pressure refrigerant gas is reduced. To do.
[0012]
Further, the invention according to claim 2 of this application is such that the outlet opening on the oil separator side in the discharge gas passage is set to the same height as the height of the inlet opening of the discharge gas passage. The discharge gas passage extends horizontally.
[0013]
According to the second aspect of the invention, the discharge gas passage communicating with the discharge chamber is set such that the opening on the oil separator side is at the same height position with respect to the height position of the inlet opening. Thus, the discharge gas passage extends horizontally and can take the shortest path, and the pressure loss of the oil-containing high-pressure refrigerant gas can be further reduced.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of a gas compressor according to the present invention will be described in detail with reference to the accompanying drawings.
[0017]
In addition, if it demonstrates using the basic composition of the gas compressor of this embodiment, for example, FIG.3 and FIG.4, the cylinder 1 will be inserted and installed between a pair of side blocks 2,3, The rotor 4 is rotatably mounted horizontally, and the rotor 4 is provided with a vane 9 that can be projected and retracted from its outer peripheral surface toward the inner wall of the cylinder 1. A compression chamber 10 formed in a partition is provided, and the compression chamber 10 repeatedly changes in volume due to the rotation of the rotor 4, and inhales and compresses the oil-containing low-pressure refrigerant gas in the suction chamber by the volume change. Further, since the compressed oil-containing high-pressure refrigerant gas is discharged from the cylinder discharge hole 14 and the like, the same members are denoted by the same reference numerals, and detailed description thereof is omitted.
[0018]
Also in the gas compressor of the present embodiment, the oil-containing high-pressure refrigerant gas discharged from the cylinder discharge hole 14 as described above passes through the discharge chamber 16 and the discharge gas passage 24 and is installed in the oil separator 18. Although guided to the separation filter 18-1 side, in the gas compressor of the present embodiment, as shown in FIG. 1, such a discharge gas passage 24 is formed linearly, and the discharge gas passage 24 is linearized. I am trying.
[0019]
That is, the discharge gas passage 24 is configured such that one end 24a side opens to the discharge chamber 16 side and the other end 24b side opens to the oil separation filter 18-1 side of the oil separator 18. The discharge gas passage 24 is formed so that the portion from one end (opening portion opening) 24a to the other end (exit opening portion) 24b is completely connected with a straight line without being bent once.
[0020]
The discharge gas passage 24 is perforated so as to pass through the rear side block 3 from the discharge chamber 16 and enter the oil separator 18 side. In this embodiment, such oil separation is performed. The angle of entry of the discharge gas passage 24 toward the container 18 has not changed.
As is apparent from FIG. 1, the discharge gas passage 24 is linearly inclined with respect to the axial direction of the cylinder 1, the side blocks 2, 3 and the rotor 4.
[0021]
That is, the discharge gas passage 24 in the conventional gas compressor is bent at a substantially right angle immediately after entering the oil separator 18 side through the rear side block 3 as shown in FIG. The discharge gas passage 24 in the gas compressor of the present embodiment is formed in a straight line without bending even immediately after passing through the rear side block 3 and entering the oil separator 18 side as shown in FIG. ing.
[0022]
In the case of the gas compressor according to the present embodiment, two cylinder discharge holes 14, two discharge chambers 16, two discharge gas passages 24, and two oil separation filters 18-1 of the oil separator 18 are provided. However, because of the relationship between the substantially elliptical shape of the inner circumference of the cylinder 1 and the structure having five vanes 9, the intake operation and the compression operation are performed at two locations in the cylinder 1 when the rotor 4 makes one rotation. This is because the oil-containing high-pressure refrigerant gas compressed at the two locations is separately led to the oil separator 18 side.
[0023]
The two discharge gas passages 24 and 24 are both provided in a straight line as described above. However, the two discharge gas passages 24 and 24 are not parallel to each other but are provided in parallel at the center of the oil separator 18. The two oil separation filters 18-1 and 18-1 are diagonally arranged in a letter C shape.
[0024]
Also in the gas compressor of this embodiment, the oil-containing high-pressure refrigerant gas discharged from the cylinder discharge hole 14 is guided to the oil separation filter 18-1 of the oil separator 18 through the discharge chamber 16 and the discharge gas passage 24. When the discharge gas passage 24 is straightened as in the present embodiment, the oil-containing high-pressure refrigerant gas can be smoothly transferred from the cylinder discharge hole 14 to the oil separation filter 18-1 side. The pressure loss of the contained high-pressure refrigerant gas is reduced, and the compressor performance is improved.
[0025]
By the way, the pressure loss of the oil-containing high-pressure refrigerant gas is also related to the passage cross-sectional area of the discharge gas passage 24, and the pressure loss of the oil-containing high-pressure refrigerant gas decreases as the passage cross-sectional area of the discharge gas passage 24 increases. Therefore, it is preferable that the passage cross-sectional area of the discharge gas passage 24 be as large as possible.
[0026]
Next, FIG. 2 shows a configuration of another embodiment of the gas compressor according to the present invention. FIG. 2 (a) is a front view of the oil separator as viewed from the rear side, and FIG. 2 (b) is a rear side view of the oil separator. The front view seen from the block contact surface side, (c) is a BB line sectional view in (b).
[0027]
That is, in this embodiment, in order to further reduce the pressure loss of the oil-containing high-pressure refrigerant gas, one end 24a of the discharge gas passage 24, that is, the inlet portion opening on the discharge chamber 16 side serving as the inlet portion of the discharge gas passage 24 is provided. The other end 24b of the discharge gas passage 24, that is, the height position of the outlet opening on the oil separator 18 side is set to the same height position, so that both the inlet portion and the outlet portion are set. The discharge gas passage 24 connecting the openings 24a and 24b takes a shortest horizontal path.
As is apparent from FIG. 2, the discharge gas passage 24 is linearly inclined with respect to the axial direction of the cylinder 1, the side blocks 2, 3 and the rotor 4.
[0028]
Accordingly, the oil-containing high-pressure refrigerant gas discharged from the cylinder discharge hole 14 is guided from the discharge chamber 16 to the oil separation filter 18-1 of the oil separator 18 through the discharge gas passage 24. As in this embodiment, the discharge gas Since the passage 24 constitutes the shortest path and the passage length is short, the pressure loss of the oil-containing high-pressure refrigerant gas can be kept low.
[0029]
Furthermore, since the discharge gas passage 24 extends horizontally, the resistance during passage of the high-pressure refrigerant gas can be reduced, which is one factor that can reduce the pressure loss, and the compressor function can be further improved.
[0030]
【The invention's effect】
In the gas compressor according to the present invention, since the discharge gas passage is formed linearly as described above, oil is contained from the cylinder discharge hole side to the oil separation filter side of the oil separator through the discharge gas passage. Since the high-pressure refrigerant gas flows smoothly, the pressure loss of the seed oil-containing high-pressure refrigerant gas is reduced, and the compressor performance can be improved.
[0031]
Further, in the gas compressor according to the present invention, the discharge gas passage is formed in a straight line, and the height position of the inlet opening that communicates with the discharge chamber and the height position of the outlet opening on the oil separator side Are set at the same height position, the discharge gas passage can be made the shortest route extending horizontally, and the compressor performance is further improved by further reducing the pressure loss of the oil-containing high-pressure refrigerant gas passing through the discharge gas passage. It has the effect of being able to.
[Brief description of the drawings]
FIG. 1 is an explanatory view of a main part of a gas compressor according to the present invention, wherein (a) is a front view of an oil separator built in the gas compressor, and (b) is a rear surface thereof. FIG. 4C is a sectional view taken along line BB in FIG.
FIG. 2 is an explanatory view of a main part of another embodiment of the gas compressor according to the present invention, in which (a) is a front view of an oil separator built in the gas compressor; ) Is a rear view thereof, and (c) is a sectional view taken along line BB of (b).
FIG. 3 is a cross-sectional view of a conventional gas compressor.
4 is a cross-sectional view taken along line AA in FIG.
5 is an explanatory view of an oil separator mounted on the conventional gas compressor shown in FIG. 3, wherein (a) is a front view of the oil separator, and (b) is a rear surface thereof. FIG. 4C is a sectional view taken along line BB in FIG.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Cylinder 2 Front side block 3 Rear side block 4 Rotor 5 Rotor shaft 6, 7 Bearing 8 Vane groove 9 Vane 10 Compression chamber 11 Suction chamber 12 Suction passage 13 Suction port 14 Cylinder discharge hole 15 Discharge valve 16 Discharge chamber DESCRIPTION OF SYMBOLS 18 Oil separator 18-1 Oil separation filter 19 Discharge chamber 20 Oil reservoir 21 Oil hole 22 Sarai groove 23 Vane back pressure space 24 Discharge gas passage

Claims (2)

一対のサイドブロック間に介挿されたシリンダと、
上記シリンダ内に回転可能に横架されたロータと、
上記ロータの外周面から上記シリンダの内壁に向かって出没自在に設けられたベーンと、
上記シリンダ、サイドブロック、ロータおよびベーンによって仕切り形成される圧縮室と、
上記圧縮室からの冷媒ガスを吐出するシリンダ吐出穴と、
上記シリンダ吐出穴から吐出された冷媒ガスを一時貯留する吐出チャンバと、
上記吐出チャンバから該吐出チャンバの下流側の油分離フィルタに向かって冷媒ガスを導く直線状の吐出ガス通路と、
上記油分離フィルタを装着し、該油分離フィルタにより冷媒ガスと油とを分離する油分離器と、
上記油分離器により分離された冷媒ガスと油とを一時貯留する吐出室と、
を備え、
上記シリンダ吐出孔、吐出チャンバ、吐出ガス通路、油分離器の油分離フィルタは、それぞれ２つずつ設けられ、
上記２つの吐出ガス通路は、互いに左右対称となるように内向きに傾斜している
ことを特徴とする気体圧縮機。A cylinder interposed between a pair of side blocks;
A rotor horizontally mounted rotatably in the cylinder;
A vane provided so as to be movable in and out from the outer peripheral surface of the rotor toward the inner wall of the cylinder;
A compression chamber partitioned by the cylinder, side block, rotor and vane;
A cylinder discharge hole for discharging refrigerant gas from the compression chamber;
A discharge chamber for temporarily storing refrigerant gas discharged from the cylinder discharge hole;
A straight discharge gas passage for guiding the refrigerant gas from the discharge chamber toward the oil separation filter on the downstream side of the discharge chamber;
An oil separator that is equipped with the oil separation filter and separates the refrigerant gas and the oil by the oil separation filter;
A discharge chamber for temporarily storing refrigerant gas and oil separated by the oil separator;
Equipped with a,
The cylinder discharge hole, the discharge chamber, the discharge gas passage, and the oil separation filter of the oil separator are each provided in two,
The gas compressor according to claim 2, wherein the two discharge gas passages are inclined inward so as to be symmetrical with each other . 上記吐出ガス通路における油分離器側の出口部開口が上記吐出ガス通路の入口部開口の高さ位置と同一高さに設定されることにより、吐出ガス通路が水平状に延びていることを特徴とする請求項１に記載の気体圧縮機。  The outlet opening on the oil separator side in the discharge gas passage is set at the same height as the height of the inlet opening of the discharge gas passage, so that the discharge gas passage extends horizontally. The gas compressor according to claim 1.
JP2001267792A 2000-12-22 2001-09-04 Gas compressor Expired - Fee Related JP3987697B2 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP2001267792A JP3987697B2 (en) 2000-12-22 2001-09-04 Gas compressor
US10/033,853 US20020094294A1 (en) 2000-12-22 2001-12-20 Gas compressor
EP01310845A EP1217215B1 (en) 2000-12-22 2001-12-21 Gas compressor
MYPI20015848A MY129076A (en) 2000-12-22 2001-12-21 Gas compressor
DE60109121T DE60109121T2 (en) 2000-12-22 2001-12-21 gas compressor
CNB011381841A CN1309960C (en) 2000-12-22 2001-12-22 Gas compressor

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2000-391184 2000-12-22
JP2000391184 2000-12-22
JP2001267792A JP3987697B2 (en) 2000-12-22 2001-09-04 Gas compressor

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US7520210B2 (en) 2006-09-27 2009-04-21 Visteon Global Technologies, Inc. Oil separator for a fluid displacement apparatus
JP5216470B2 (en) * 2008-08-08 2013-06-19 カヤバ工業株式会社 Variable displacement vane pump
EP3051136B1 (en) * 2015-01-29 2020-04-01 Pfeiffer Vacuum Gmbh Vacuum pump
KR102141871B1 (en) * 2015-05-26 2020-08-07 한온시스템 주식회사 Compressor with an oil return means

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Publication number Priority date Publication date Assignee Title
JPS572704Y2 (en) * 1978-07-29 1982-01-18
JPS6016794Y2 (en) * 1978-08-19 1985-05-24 株式会社ボッシュオートモーティブ システム vane compressor
JPS57148097A (en) * 1981-03-09 1982-09-13 Mitsubishi Heavy Ind Ltd Rotary compressor
US4810177A (en) * 1982-06-18 1989-03-07 Diesel Kiki Co., Ltd. Vane compressor with vane back pressure adjustment
JP2585380Y2 (en) * 1992-11-20 1998-11-18 カルソニック株式会社 Rotary compressor
JPH0712072A (en) * 1993-06-23 1995-01-17 Toyota Autom Loom Works Ltd Vane compressor
JPH07151083A (en) * 1993-11-29 1995-06-13 Nippondenso Co Ltd Vane type compressor
JP2913155B2 (en) * 1995-09-01 1999-06-28 セイコー精機株式会社 Gas compressor
JPH0979156A (en) * 1995-09-08 1997-03-25 Seiko Seiki Co Ltd Gas compressor
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JP2002250289A (en) 2002-09-06
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EP1217215A2 (en) 2002-06-26
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DE60109121T2 (en) 2005-07-21
US20020094294A1 (en) 2002-07-18
CN1309960C (en) 2007-04-11
EP1217215B1 (en) 2005-03-02
DE60109121D1 (en) 2005-04-07

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