JP4233843B2 - Refrigeration cycle equipment - Google Patents

Refrigeration cycle equipment Download PDF

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Publication number
JP4233843B2
JP4233843B2 JP2002318130A JP2002318130A JP4233843B2 JP 4233843 B2 JP4233843 B2 JP 4233843B2 JP 2002318130 A JP2002318130 A JP 2002318130A JP 2002318130 A JP2002318130 A JP 2002318130A JP 4233843 B2 JP4233843 B2 JP 4233843B2
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Japan
Prior art keywords
oil
compressor
refrigerant
expander
pipe
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Expired - Fee Related
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JP2002318130A
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Japanese (ja)
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JP2004150749A (en
Inventor
和生 中谷
義和 川邉
典穂 岡座
晃 鶸田
雄二 井上
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Panasonic Corp
Panasonic Holdings Corp
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Panasonic Corp
Matsushita Electric Industrial Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Description

【０００１】
【発明の属する技術分野】
本発明は、冷媒として二酸化炭素を用い、圧縮機と室外側熱交換器と膨張機と室内側熱交換器とを備えた冷凍サイクル装置に関する。
【０００２】
【従来の技術】
圧縮機と室外側熱交換器と膨張機と室内側熱交換器とを備えた冷凍サイクル装置において、圧縮機と膨張機との潤滑オイルを確保するために、圧縮機の出口側の配管にオイル分離器を設け、このオイル分離器で分離したオイルを、圧縮機の吸入側と、膨張機の入口側に供給する構成が提案されている（例えば特許文献１参照）。
【０００３】
【特許文献１】
特開２００１−１４１３１５号公報
【０００４】
【発明が解決しようとする課題】
しかしながら、オイル分離器で分離したオイルを、圧縮機の吸入側と、膨張機の入口側に供給するためには、分割供給するために、オイル戻し管にそれぞれ弁か必要となり、分流制御も困難である。
【０００５】
そこで本発明は、従来のように分流制御を行うことなく、圧縮機と膨張機との潤滑を円滑に行うことを目的とする。
【０００６】
【課題を解決するための手段】
請求項１記載の本発明の冷凍サイクル装置は、冷媒として二酸化炭素を用い、圧縮機と第１の熱交換器と膨張機と第２の熱交換器とを備えた冷凍サイクル装置であって、前記膨張機の冷媒流出側配管に第１オイル分離器を設け、前記第１オイル分離器で分離したオイルを前記圧縮機の吸入側配管に戻すとともに、前記圧縮機の吐出側配管に第２オイル分離器を設け、前記第２オイル分離器で分離したオイルを前記膨張機の冷媒流入側配管に戻すことを特徴とする。
請求項２記載の本発明の冷凍サイクル装置は、冷媒として二酸化炭素を用い、圧縮機と第１の熱交換器と膨張機と第２の熱交換器と補助圧縮機とを備え、前記補助圧縮機を前記圧縮機の吸入側配管に接続し、前記膨張機で回収した動力によって前記補助圧縮機を駆動する冷凍サイクル装置であって、前記膨張機の冷媒流出側配管に第１オイル分離器を設け、前記第１オイル分離器で分離したオイルを前記補助圧縮機の吸入側配管に戻すとともに、前記圧縮機の吐出側配管に第２オイル分離器を設け、前記第２オイル分離器で分離したオイルを前記膨張機の冷媒流入側配管に戻すことを特徴とする。
請求項３記載の本発明の冷凍サイクル装置は、冷媒として二酸化炭素を用い、圧縮機と第１の熱交換器と膨張機と第２の熱交換器と補助圧縮機とを備え、前記補助圧縮機を前記圧縮機の吐出側配管に接続し、前記膨張機で回収した動力によって前記補助圧縮機を駆動する冷凍サイクル装置であって、前記膨張機の冷媒流出側配管に第１オイル分離器を設け、前記第１オイル分離器で分離したオイルを前記圧縮機の吸入側配管に戻すとともに、前記補助圧縮機の吐出側配管に第２オイル分離器を設け、前記第２オイル分離器で分離したオイルを前記膨張機の冷媒流入側配管に戻すことを特徴とする。
請求項４記載の本発明は、請求項１から請求項３のいずれかに記載の冷凍サイクル装置において、前記第１オイル分離器の第１オイル戻し管に絞り装置を設けたことを特徴とする。
請求項５記載の本発明は、請求項１から請求項３のいずれかに記載の冷凍サイクル装置において、前記第２オイル分離器の第２オイル戻し管に絞り装置を設けたことを特徴とする。
請求項６記載の本発明は、請求項１に記載の冷凍サイクル装置において、前記圧縮機の吐出側配管と吸入側配管とが接続される第１四方弁と、前記膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁４とを備え、前記第１オイル分離器を前記膨張機の冷媒流出口から前記第２四方弁までの間の配管に設け、前記第１オイル分離器の第１オイル戻し管を、前記第１四方弁から前記圧縮機の吸入口までの間の配管に設けたことを特徴とする。
請求項７記載の本発明は、請求項２に記載の冷凍サイクル装置において、前記圧縮機の吐出側配管と前記補助圧縮機の吸入側配管とが接続される第１四方弁と、前記膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁４とを備え、前記第１オイル分離器を前記膨張機の冷媒流出口から前記第２四方弁までの間の配管に設け、前記第１オイル分離器の第１オイル戻し管を、前記第１四方弁から前記補助圧縮機の吸入口までの間の配管に設けたことを特徴とする。
請求項８記載の本発明は、請求項３に記載の冷凍サイクル装置において、前記補助圧縮機の吐出側配管と前記圧縮機の吸入側配管とが接続される第１四方弁と、前記膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁４とを備え、前記第１オイル分離器を前記膨張機の冷媒流出口から前記第２四方弁までの間の配管に設け、前記第１オイル分離器の第１オイル戻し管を、前記第１四方弁から前記圧縮機の吸入口までの間の配管に設けたことを特徴とする。
請求項９記載の本発明は、請求項１に記載の冷凍サイクル装置において、前記圧縮機の吐出側配管と吸入側配管とが接続される第１四方弁と、前記膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁とを備え、前記第２オイル分離器を前記圧縮機の吐出口から前記第１四方弁までの間の配管に設け、前記第２オイル分離器の第２オイル戻し管を、前記第２四方弁から前記膨張機の冷媒流入口までの間の配管に設けたことを特徴とする。
請求項１０記載の本発明は、請求項２に記載の冷凍サイクル装置において、前記圧縮機の吐出側配管と前記補助圧縮機の吸入側配管とが接続される第１四方弁と、前記膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁とを備え、前記第２オイル分離器を前記圧縮機の吐出口から前記第１四方弁までの間の配管に設け、前記第２オイル分離器の第２オイル戻し管を、前記第２四方弁から前記膨張機の冷媒流入口までの間の配管に設けたことを特徴とする。
請求項１１記載の本発明は、請求項３に記載の冷凍サイクル装置において、前記補助圧縮機の吐出側配管と前記圧縮機の吸入側配管とが接続される第１四方弁と、前記膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁とを備え、前記第２オイル分離器を前記補助圧縮機の吐出口から前記第１四方弁までの間の配管に設け、前記第２オイル分離器の第２オイル戻し管を、前記第２四方弁から前記膨張機の冷媒流入口までの間の配管に設けたことを特徴とする。
請求項１２記載の本発明は、請求項１から請求項３のいずれかに記載の冷凍サイクル装置において、オイルとして、ＰＡＧ、ＡＢ、ナフテン系鉱油などの前記冷媒と溶解性の低いオイルを用いたことを特徴とする。
【０００７】
【発明の実施の形態】
本発明による第１の実施の形態は、膨張機の冷媒流出側配管に第１オイル分離器を設け、第１オイル分離器で分離したオイルを圧縮機の吸入側配管に戻すとともに、圧縮機の吐出側配管に第２オイル分離器を設け、第２オイル分離器で分離したオイルを膨張機の冷媒流入側配管に戻すものである。
本実施の形態によれば、圧縮機の吐出冷媒中のオイルで膨張機の摺動部を潤滑することで、膨張機にオイル溜めを設けることなく膨張部と軸との潤滑を行うことができ、圧縮機と膨張機との一体化が容易となる。また、蒸発器にオイルが流入しないので蒸発器でのオイル溜まりがなく、蒸発器の熱伝達の低下を防止でき、ＣＯＰを向上させることができる。また、放熱器にオイルが流入しないので放熱器でのオイル溜まりがなく、放熱器の熱伝達の低下を防止でき、ＣＯＰを向上させることができる。
本発明による第２の実施の形態は、膨張機の冷媒流出側配管に第１オイル分離器を設け、第１オイル分離器で分離したオイルを補助圧縮機の吸入側配管に戻すとともに、圧縮機の吐出側配管に第２オイル分離器を設け、第２オイル分離器で分離したオイルを膨張機の冷媒流入側配管に戻すものである。
本実施の形態によれば、圧縮機の吐出冷媒中のオイルで膨張機の摺動部を潤滑することで、膨張機にオイル溜めを設けることなく膨張部と軸との潤滑を行うことができ、膨張機と補助圧縮機との一体化が容易となる。また、蒸発器にオイルが流入しないので蒸発器でのオイル溜まりがなく、蒸発器の熱伝達の低下を防止でき、ＣＯＰを向上させることができる。また、放熱器にオイルが流入しないので放熱器でのオイル溜まりがなく、放熱器の熱伝達の低下を防止でき、ＣＯＰを向上させることができる。
本発明による第３の実施の形態は、膨張機の冷媒流出側配管に第１オイル分離器を設け、第１オイル分離器で分離したオイルを圧縮機の吸入側配管に戻すとともに、補助圧縮機の吐出側配管に第２オイル分離器を設け、第２オイル分離器で分離したオイルを膨張機の冷媒流入側配管に戻すものである。
本実施の形態によれば、圧縮機の吐出冷媒中のオイルで膨張機の摺動部を潤滑することで、膨張機にオイル溜めを設けることなく膨張部と軸との潤滑を行うことができ、膨張機と補助圧縮機との一体化が容易となる。また、蒸発器にオイルが流入しないので蒸発器でのオイル溜まりがなく、蒸発器の熱伝達の低下を防止でき、ＣＯＰを向上させることができる。また、本実施の形態によれば、放熱器にオイルが流入しないので放熱器でのオイル溜まりがなく、放熱器の熱伝達の低下を防止でき、ＣＯＰを向上させることができる。
本発明による第４の実施の形態は、第１から第３の実施の形態において、第１オイル分離器の第１オイル戻し管に絞り装置を設けたものである。
本実施の形態によれば、この絞り装置により適切なオイル戻し量を確保することができる。
本発明による第５の実施の形態は、第１から第３の実施の形態において、第２オイル分離器の第２オイル戻し管に絞り装置を設けたものである。
本実施の形態によれば、この絞り装置により適切なオイル戻し量を確保することができる。
本発明による第６の実施の形態は、第１の実施の形態において、圧縮機の吐出側配管と吸入側配管とが接続される第１四方弁と、膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁とを備え、第１オイル分離器を膨張機の冷媒流出口から第２四方弁までの間の配管に設け、第１オイル分離器の第１オイル戻し管を、第１四方弁から圧縮機の吸入口までの間の配管に設けたものである。
本実施の形態によれば、第１四方弁の切り替えによって冷房運転モードと暖房運転モードとを利用することができる冷凍サイクルにおいて、圧縮機の吐出冷媒中のオイルで膨張機の摺動部を潤滑することができる。また、蒸発器にオイルが流入しないので蒸発器でのオイル溜まりがなく、蒸発器の熱伝達の低下を防止でき、ＣＯＰを向上させることができる。
本発明による第７の実施の形態は、第２の実施の形態において、圧縮機の吐出側配管と補助圧縮機の吸入側配管とが接続される第１四方弁と、膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁とを備え、第１オイル分離器を膨張機の冷媒流出口から第２四方弁までの間の配管に設け、第１オイル分離器の第１オイル戻し管を、第１四方弁から補助圧縮機の吸入口までの間の配管に設けたものである。
本実施の形態によれば、第１四方弁の切り替えによって冷房運転モードと暖房運転モードとを利用することができる冷凍サイクルにおいて、圧縮機の吐出冷媒中のオイルで膨張機の摺動部を潤滑することができる。また、蒸発器にオイルが流入しないので蒸発器でのオイル溜まりがなく、蒸発器の熱伝達の低下を防止でき、ＣＯＰを向上させることができる。
本発明による第８の実施の形態は、第３の実施の形態において、補助圧縮機の吐出側配管と圧縮機の吸入側配管とが接続される第１四方弁と、膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁とを備え、第１オイル分離器を膨張機の冷媒流出口から第２四方弁までの間の配管に設け、第１オイル分離器の第１オイル戻し管を、第１四方弁から圧縮機の吸入口までの間の配管に設けたものである。
本実施の形態によれば、第１四方弁の切り替えによって冷房運転モードと暖房運転モードとを利用することができる冷凍サイクルにおいて、圧縮機の吐出冷媒中のオイルで膨張機の摺動部を潤滑することができる。また、蒸発器にオイルが流入しないので蒸発器でのオイル溜まりがなく、蒸発器の熱伝達の低下を防止でき、ＣＯＰを向上させることができる。
本発明による第９の実施の形態は、第１の実施の形態において、圧縮機の吐出側配管と吸入側配管とが接続される第１四方弁と、膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁とを備え、第２オイル分離器を圧縮機の吐出口から第１四方弁までの間の配管に設け、第２オイル分離器の第２オイル戻し管を、第２四方弁から膨張機の冷媒流入口までの間の配管に設けたものである。
本実施の形態によれば、第１四方弁の切り替えによって冷房運転モードと暖房運転モードとを利用することができる冷凍サイクルにおいて、放熱器にオイルが流入しないので放熱器でのオイル溜まりがなく、放熱器の熱伝達の低下を防止でき、ＣＯＰを向上させることができる。
本発明による第１０の実施の形態は、第２の実施の形態において、圧縮機の吐出側配管と補助圧縮機の吸入側配管とが接続される第１四方弁と、膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁とを備え、第２オイル分離器を圧縮機の吐出口から第１四方弁までの間の配管に設け、第２オイル分離器の第２オイル戻し管を、第２四方弁から膨張機の冷媒流入口までの間の配管に設けたものである。
本実施の形態によれば、第１四方弁の切り替えによって冷房運転モードと暖房運転モードとを利用することができる冷凍サイクルにおいて、放熱器にオイルが流入しないので放熱器でのオイル溜まりがなく、放熱器の熱伝達の低下を防止でき、ＣＯＰを向上させることができる。
本発明による第１１の実施の形態は、第３の実施の形態において、補助圧縮機の吐出側配管と圧縮機の吸入側配管とが接続される第１四方弁と、膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁とを備え、第２オイル分離器を補助圧縮機の吐出口から第１四方弁までの間の配管に設け、第２オイル分離器の第２オイル戻し管を、第２四方弁から膨張機の冷媒流入口までの間の配管に設けたものである。
本実施の形態によれば、第１四方弁の切り替えによって冷房運転モードと暖房運転モードとを利用することができる冷凍サイクルにおいて、放熱器にオイルが流入しないので放熱器でのオイル溜まりがなく、放熱器の熱伝達の低下を防止でき、ＣＯＰを向上させることができる。
本発明による第１２の実施の形態は、第１から第３の実施の形態において、オイルとして、ＰＡＧ、ＡＢ、ナフテン系鉱油などの冷媒と溶解性の低いオイルを用いたものである。
本実施の形態によれば、冷媒と溶解性の低いオイルを用いることで、オイル分離器でのオイル分離を確実にし、蒸発器や放熱器での熱伝達の効率低下を防止することができ、ＣＯＰの向上を図ることができる。
【０００８】
【実施例】
以下、本発明の一実施例による冷凍サイクル装置を、ヒートポンプ式冷暖房型空気調和装置について、図面を参照して説明する。
図１は、本実施例によるヒートポンプ式冷暖房型空気調和装置の構成図である。
図に示すように、本実施例によるヒートポンプ式冷暖房型空気調和装置は、冷媒としてＣＯ2冷媒を使用し、モータ１１を有する圧縮機１と、室外側熱交換器３と、膨張機６と、室内側熱交換器８とを配管で接続した冷媒回路から構成される。圧縮機１等の摺動部潤滑用のオイルとしては、ＰＡＧ、ＡＢ、ナフテン系鉱油などの冷媒と溶解性の低いオイルを用いる。
また膨張機６の流入側には予膨張弁５が設けられている。
また予膨張弁５及び膨張機６と並列に、予膨張弁５及び膨張機６をバイパスするバイパス回路が設けられ、このバイパス回路に制御弁７が設けられている。
また、膨張機６の駆動軸と圧縮機１の駆動軸とは連結されており、圧縮機１は膨張機６で回収した動力を駆動に利用している。
そしてこの冷媒回路には、圧縮機１の吐出側配管と吸入側配管とが接続される第１四方弁２と、予膨張弁５の冷媒流入側配管と膨張機６の冷媒流出側配管とが接続されるとともにバイパス回路が接続される第２四方弁４とを備えている。
第１オイル分離器５４は、膨張機６の冷媒流出側の配管であって、バイパス回路との合流部から第２四方弁４までの間の配管に設けられている。そして、この第１オイル分離器５４で分離したオイルは、第１オイル戻し管５５によって第１四方弁２から圧縮機１の吸入口までの間の配管に戻される。また、第１オイル戻し管５５には絞り装置５６を設けている。
第２オイル分離器５１は、圧縮機１の吐出口から第１四方弁２までの間の配管に設けられている。そして、この第２オイル分離器５１で分離したオイルは、第２オイル戻し管５２によって第２四方弁２から膨張機６の流入口までの間の配管に戻される。なお、この第２オイル戻し管５２はバイパス回路との分岐部よりも下流側配管に設けることが好ましい。また、第２オイル戻し管５２には絞り装置５３を設けている。
【０００９】
本実施例によるヒートポンプ式冷暖房型空気調和装置の動作について以下に説明する。
まず、室外側熱交換器３を放熱器、室内側熱交換器８を蒸発器として用いる冷房運転モードについて説明する。この冷房運転モードでの冷媒流れを、図中実線矢印で示す。
冷房運転モード時の冷媒は、モータ１１で駆動される圧縮機１により高温高圧に圧縮されて吐出され、第１四方弁２を経て、室外側熱交換器３に導入される。室外側熱交換器３では、ＣＯ2冷媒は、超臨界状態であるので、気液二相状態とはならずに、空気や水などの外部流体に放熱する。その後ＣＯ2冷媒は、第２四方弁４を経て予膨張弁５及び膨張機６に導入され、予膨張弁５及び膨張機６で減圧される。この減圧時に膨張機６で回収した動力は圧縮機１の駆動に用いられる。このとき、例えば室外側熱交換器３の出口側で検出した高圧冷媒圧力に応じて制御弁７の開度を調整してバイパス回路に流す冷媒量を制御する。また、検出した高圧冷媒圧力に応じて予膨張弁５の開度を調整して膨張弁６に流れる冷媒量を制御する。
予膨張弁５及び膨張機６にて減圧されたＣＯ2冷媒は、第２四方弁４を経由して室内側熱交換器８に導かれ、室内側熱交換器８にて蒸発して吸熱する。この吸熱によって室内の冷房が行われる。蒸発を終えた冷媒は圧縮機１に吸入される。
【００１０】
次に、室外側熱交換器３を蒸発器、室内側熱交換器８を放熱器として用いる暖房運転モードについて説明する。この暖房運転モードでの冷媒流れを、図中波線矢印で示す。
暖房運転モード時の冷媒は、モータ１１で駆動される圧縮機１により高温高圧に圧縮されて吐出され、第１四方弁２を経て、室内側熱交換器８に導入される。室内側熱交換器８では、ＣＯ2冷媒は、超臨界状態であるので、気液二相状態とはならずに、空気や水などの外部流体に放熱し、この放熱を利用して例えば室内暖房が行われる。その後ＣＯ2冷媒は、予膨張弁５及び膨張機６に導入され、予膨張弁５及び膨張機６で減圧される。この減圧時に膨張機６で回収した動力は圧縮機１の駆動に用いられる。このとき、例えば室内側熱交換器８の出口側で検出した高圧冷媒圧力に応じて制御弁７の開度を調整してバイパス回路に流す冷媒量を制御する。また、検出した高圧冷媒圧力に応じて予膨張弁５の開度を調整して膨張弁６に流れる冷媒量を制御する。
予膨張弁５及び膨張機６にて減圧されたＣＯ2冷媒は、第２四方弁４を経由して室外側熱交換器３に導かれ、室外側熱交換器３にて蒸発して吸熱し、蒸発を終えた冷媒は第１四方弁２を経由して圧縮機１に吸入される。
【００１１】
次に、上記冷暖房運転時におけるオイルの流れについて説明する。
圧縮機１の内部にはオイル溜めを備え、所定量のオイルが蓄えられている。このオイルによって圧縮機１内の潤滑が行われている。このオイルの一部は、冷媒とともに吐出される。吐出されたオイルは、第２オイル分離器５１にて冷媒と分離され、分離されたオイルは、第２オイル戻し管５２によって膨張機６の冷媒流入側の配管に戻される。従って、膨張機６はこのオイルによって潤滑される。また、第２オイル分離器５１で分離したオイルは、第２オイル戻し管５２によって放熱器（冷房運転モードにおける室外側熱交換器３、暖房運転モードにおける室内側熱交換器８）をバイパスするので、放熱器にオイルが流入しないので放熱器でのオイル溜まりがなく、放熱器の熱伝達の効率低下を防止でき、ＣＯＰを向上させることができる。
一方、膨張機６で潤滑に使われたオイルは、冷媒とともに流出する。流出したオイルは、第１オイル分離器５４にて冷媒と分離され、分離されたオイルは、第１オイル戻し管５５によって圧縮機１の吸入側配管に戻される。従って、第１オイル分離器５４で分離したオイルは、第１オイル戻し管５５によって蒸発器（冷房運転モードにおける室内側熱交換器８、暖房運転モードにおける室外側熱交換器３）をバイパスするので、蒸発器にオイルが流入しないので蒸発器でのオイル溜まりがなく、蒸発器の熱伝達の効率低下を防止でき、ＣＯＰを向上させることができる。また、圧縮機１の吐出冷媒中のオイルで膨張機６の摺動部を潤滑することで、膨張機６にオイル溜めを設けることなく潤滑を行うことができ、圧縮機１と膨張機６との一体化が容易となる。
また、ＰＡＧ、ＡＢ、ナフテン系鉱油などの冷媒と溶解性の低いオイルを用いることで、オイル分離器５１、５４でのオイル分離を確実にし、蒸発器や放熱器での熱伝達の効率低下を防止することができ、ＣＯＰの向上を図ることができる。
【００１２】
以下、本発明の他の実施例による冷凍サイクル装置を、ヒートポンプ式冷暖房型空気調和装置について、図面を参照して説明する。
図２は、本実施例によるヒートポンプ式冷暖房型空気調和装置の構成図である。
図に示すように、本実施例によるヒートポンプ式冷暖房型空気調和装置は、冷媒としてＣＯ2冷媒を使用し、モータ１１を有する圧縮機１と、室外側熱交換器３と、膨張機６と、室内側熱交換器８と、補助圧縮機１０とを配管で接続した冷媒回路から構成される。圧縮機１等の摺動部潤滑用のオイルとしては、ＰＡＧ、ＡＢ、ナフテン系鉱油などの冷媒と溶解性の低いオイルを用いる。
また膨張機６の流入側配管には予膨張弁５が設けられている。
また予膨張弁５及び膨張機６と並列に、予膨張弁５及び膨張機６をバイパスするバイパス回路が設けられ、このバイパス回路に制御弁７が設けられている。
また、膨張機６の駆動軸と補助圧縮機１０の駆動軸とは連結されており、補助圧縮機１０は膨張機６で回収した動力によって駆動される。
そしてこの冷媒回路には、圧縮機１の吐出側配管と補助圧縮機１０の吸入側配管とが接続される第１四方弁２と、予膨張弁５の冷媒流入側配管と膨張機６の冷媒流出側配管とが接続されるとともにバイパス回路が接続される第２四方弁４とを備えている。
第１オイル分離器５４は、膨張機６の冷媒流出側の配管であって、バイパス回路との合流部から第２四方弁４までの間の配管に設けられている。そして、この第１オイル分離器５４で分離したオイルは、第１オイル戻し管５５によって第１四方弁２から圧縮機１の吸入口までの間の配管に戻される。また、第１オイル戻し管５５には絞り装置５６を設けている。
第２オイル分離器５１は、圧縮機１の吐出口から第１四方弁２までの間の配管に設けられている。そして、この第２オイル分離器５１で分離したオイルは、第２オイル戻し管５２によって第２四方弁２から膨張機６の流入口までの間の配管に戻される。なお、この第２オイル戻し管５２はバイパス回路との分岐部よりも下流側配管に設けることが好ましい。また、第２オイル戻し管５２には絞り装置５３を設けている。
【００１３】
本実施例によるヒートポンプ式冷暖房型空気調和装置の動作について以下に説明する。
まず、室外側熱交換器３を放熱器、室内側熱交換器８を蒸発器として用いる冷房運転モードについて説明する。この冷房運転モードでの冷媒流れを、図中実線矢印で示す。
冷房運転モード時の冷媒は、モータ１１で駆動される圧縮機１により高温高圧に圧縮されて吐出され、第１四方弁２を経て、室外側熱交換器３に導入される。室外側熱交換器３では、ＣＯ2冷媒は、超臨界状態であるので、気液二相状態とはならずに、空気や水などの外部流体に放熱する。その後ＣＯ2冷媒は、予膨張弁５及び膨張機６に導入され、予膨張弁５及び膨張機６で減圧される。この減圧時に膨張機６で回収した動力は補助圧縮機１０の駆動に用いられる。このとき、例えば室外側熱交換器３の出口側で検出した高圧冷媒圧力に応じて制御弁７の開度を調整してバイパス回路に流す冷媒量を制御する。また、検出した高圧冷媒圧力に応じて予膨張弁５の開度を調整して膨張弁６に流れる冷媒量を制御する。
予膨張弁５及び膨張機６にて減圧されたＣＯ2冷媒は、第２四方弁４を経由して室内側熱交換器８に導かれ、室内側熱交換器８にて蒸発して吸熱する。この吸熱によって室内の冷房が行われる。蒸発を終えた冷媒は、第１四方弁２を経て補助圧縮機１０に導かれ、補助圧縮機１０によって過給（チャージャ）され圧縮機１に吸入される。
【００１４】
次に、室外側熱交換器３を蒸発器、室内側熱交換器８を放熱器として用いる暖房運転モードについて説明する。この暖房運転モードでの冷媒流れを、図中波線矢印で示す。
暖房運転モード時の冷媒は、モータ１１で駆動される圧縮機１により高温高圧に圧縮されて吐出され、第１四方弁２を経て、室内側熱交換器８に導入される。室内側熱交換器８では、ＣＯ2冷媒は、超臨界状態であるので、気液二相状態とはならずに、空気や水などの外部流体に放熱し、この放熱を利用して例えば室内暖房が行われる。その後ＣＯ2冷媒は、予膨張弁５及び膨張機６に導入され、予膨張弁５及び膨張機６で減圧される。この減圧時に膨張機６で回収した動力は補助圧縮機１０の駆動に用いられる。このとき、例えば室内側熱交換器８の出口側で検出した高圧冷媒圧力に応じて制御弁７の開度を調整してバイパス回路に流す冷媒量を制御する。また、検出した高圧冷媒圧力に応じて予膨張弁５の開度を調整して膨張弁６に流れる冷媒量を制御する。
予膨張弁５及び膨張機６にて減圧されたＣＯ2冷媒は、第２四方弁４を経由して室外側熱交換器３に導かれ、室外側熱交換器３にて蒸発して吸熱し、蒸発を終えた冷媒は第１四方弁２を経由して補助圧縮機１０に導かれ、補助圧縮機１０によって過給（チャージャ）され圧縮機１に吸入される。
【００１５】
次に、上記冷暖房運転時におけるオイルの流れについて説明する。
圧縮機１の内部にはオイル溜めを備え、所定量のオイルが蓄えられている。このオイルによって圧縮機１内の潤滑が行われている。このオイルの一部は、冷媒とともに吐出される。吐出されたオイルは、第２オイル分離器５１にて冷媒と分離され、分離されたオイルは、第２オイル戻し管５２によって膨張機６の冷媒流入側の配管に戻される。従って、膨張機６はこのオイルによって潤滑される。また、第２オイル分離器５１で分離したオイルは、第２オイル戻し管５２によって放熱器（冷房運転モードにおける室外側熱交換器３、暖房運転モードにおける室内側熱交換器８）をバイパスするので、放熱器にオイルが流入しないので放熱器でのオイル溜まりがなく、放熱器の熱伝達の効率低下を防止でき、ＣＯＰを向上させることができる。
一方、膨張機６で潤滑に使われたオイルは、冷媒とともに流出する。流出したオイルは、第１オイル分離器５４にて冷媒と分離され、分離されたオイルは、第１オイル戻し管５５によって補助圧縮機１０の吸入側配管に戻される。従って、補助圧縮機１０はこのオイルによって潤滑され、補助圧縮機１０から吐出される冷媒は再び圧縮機１内に戻る。また、第１オイル分離器５４で分離したオイルは、第１オイル戻し管５５によって蒸発器（冷房運転モードにおける室内側熱交換器８、暖房運転モードにおける室外側熱交換器３）をバイパスするので、蒸発器にオイルが流入しないので蒸発器でのオイル溜まりがなく、蒸発器の熱伝達の効率低下を防止でき、ＣＯＰを向上させることができる。また、圧縮機１の吐出冷媒中のオイルで膨張機６や補助圧縮機１０の摺動部を潤滑することで、膨張機６や補助圧縮機１０にオイル溜めを設けることなく潤滑を行うことができ、補助圧縮機１０と膨張機６との一体化が容易となる。
また、ＰＡＧ、ＡＢ、ナフテン系鉱油などの冷媒と溶解性の低いオイルを用いることで、オイル分離器５１、５４でのオイル分離を確実にし、蒸発器や放熱器での熱伝達の効率低下を防止することができ、ＣＯＰの向上を図ることができる。
【００１６】
以下、本発明の他の実施例による冷凍サイクル装置を、ヒートポンプ式冷暖房型空気調和装置について、図面を参照して説明する。
図３は、本実施例によるヒートポンプ式冷暖房型空気調和装置の構成図である。
図に示すように、本実施例によるヒートポンプ式冷暖房型空気調和装置は、冷媒としてＣＯ2冷媒を使用し、モータ１１を有する圧縮機１と、補助圧縮機１０と、室外側熱交換器３と、膨張機６と、室内側熱交換器８とを配管で接続した冷媒回路から構成される。圧縮機１等の摺動部潤滑用のオイルとしては、ＰＡＧ、ＡＢ、ナフテン系鉱油などの冷媒と溶解性の低いオイルを用いる。
また膨張機６の流入側配管には予膨張弁５が設けられている。
また予膨張弁５及び膨張機６と並列に、予膨張弁５及び膨張機６をバイパスするバイパス回路が設けられ、このバイパス回路に制御弁７が設けられている。
また、膨張機６の駆動軸と補助圧縮機１０の駆動軸とは連結されており、補助圧縮機１０は膨張機６で回収した動力によって駆動される。
そしてこの冷媒回路には、圧縮機１の吸入側配管と補助圧縮機１０の吐出側配管とが接続される第１四方弁２と、予膨張弁５の吸入側配管と膨張機６の吐出側配管とが接続されるとともにバイパス回路が接続される第２四方弁４とを備えている。
第１オイル分離器５４は、膨張機６の冷媒流出側の配管であって、バイパス回路との合流部から第２四方弁４までの間の配管に設けられている。そして、この第１オイル分離器５４で分離したオイルは、第１オイル戻し管５５によって第１四方弁２から圧縮機１の吸入口までの間の配管に戻される。また、第１オイル戻し管５５には絞り装置５６を設けている。
第２オイル分離器５１は、圧縮機１の吐出口から第１四方弁２までの間の配管に設けられている。そして、この第２オイル分離器５１で分離したオイルは、第２オイル戻し管５２によって第２四方弁２から膨張機６の流入口までの間の配管に戻される。なお、この第２オイル戻し管５２はバイパス回路との分岐部よりも下流側配管に設けることが好ましい。また、第２オイル戻し管５２には絞り装置５３を設けている。
【００１７】
本実施例によるヒートポンプ式冷暖房型空気調和装置の動作について以下に説明する。
まず、室外側熱交換器３を放熱器、室内側熱交換器８を蒸発器として用いる冷房運転モードについて説明する。この冷房運転モードでの冷媒流れを、図中実線矢印で示す。
冷房運転モード時の冷媒は、モータ１１で駆動される圧縮機１により高温高圧に圧縮されて吐出され、補助圧縮機１０に導かれ、補助圧縮機１０によって更に過圧（エクスプレッサ）された後に、第１四方弁２を経て、室外側熱交換器３に導入される。室外側熱交換器３では、ＣＯ2冷媒は、超臨界状態であるので、気液二相状態とはならずに、空気や水などの外部流体に放熱する。その後ＣＯ2冷媒は、予膨張弁５及び膨張機６に導入され、予膨張弁５及び膨張機６で減圧される。この減圧時に膨張機６で回収した動力は補助圧縮機１０の駆動に用いられる。このとき、例えば室外側熱交換器３の出口側で検出した高圧冷媒圧力に応じて制御弁７の開度を調整してバイパス回路に流す冷媒量を制御する。また、検出した高圧冷媒圧力に応じて予膨張弁５の開度を調整して膨張弁６に流れる冷媒量を制御する。
予膨張弁５及び膨張機６にて減圧されたＣＯ2冷媒は、第２四方弁４を経由して室内側熱交換器８に導かれ、室内側熱交換器８にて蒸発して吸熱する。この吸熱によって室内の冷房が行われる。蒸発を終えた冷媒は、第１四方弁２を経て圧縮機１に吸入される。
【００１８】
次に、室外側熱交換器３を蒸発器、室内側熱交換器８を放熱器として用いる暖房運転モードについて説明する。この暖房運転モードでの冷媒流れを、図中波線矢印で示す。
暖房運転モード時の冷媒は、モータ１１で駆動される圧縮機１により高温高圧に圧縮されて吐出され、補助圧縮機１０に導かれ、補助圧縮機１０によって更に過圧（エクスプレッサ）された後に、第１四方弁２を経て、室内側熱交換器８に導入される。室内側熱交換器８では、ＣＯ2冷媒は、超臨界状態であるので、気液二相状態とはならずに、空気や水などの外部流体に放熱し、この放熱を利用して例えば室内暖房が行われる。その後ＣＯ2冷媒は、予膨張弁５及び膨張機６に導入され、予膨張弁５及び膨張機６で減圧される。この減圧時に膨張機６で回収した動力は補助圧縮機１０の駆動に用いられる。このとき、例えば室内側熱交換器８の出口側で検出した高圧冷媒圧力に応じて制御弁７の開度を調整してバイパス回路に流す冷媒量を制御する。また、検出した高圧冷媒圧力に応じて予膨張弁５の開度を調整して膨張弁６に流れる冷媒量を制御する。
予膨張弁５及び膨張機６にて減圧されたＣＯ2冷媒は、第２四方弁４を経由して室外側熱交換器３に導かれ、室外側熱交換器３にて蒸発して吸熱し、蒸発を終えた冷媒は第１四方弁２を経由して圧縮機１に吸入される。
【００１９】
次に、上記冷暖房運転時におけるオイルの流れについて説明する。
圧縮機１の内部にはオイル溜めを備え、所定量のオイルが蓄えられている。このオイルによって圧縮機１内の潤滑が行われている。このオイルの一部は、冷媒とともに吐出される。吐出されたオイルは、冷媒とともに補助圧縮機１０に導入されて補助圧縮機１０内の潤滑を行う。そして補助圧縮機１０から吐出されたオイルは、第２オイル分離器５１にて冷媒と分離され、分離されたオイルは、第２オイル戻し管５２によって膨張機６の冷媒流入側の配管に戻される。従って、膨張機６はこのオイルによって潤滑される。また、第２オイル分離器５１で分離したオイルは、第２オイル戻し管５２によって放熱器（冷房運転モードにおける室外側熱交換器３、暖房運転モードにおける室内側熱交換器８）をバイパスするので、放熱器にオイルが流入しないので放熱器でのオイル溜まりがなく、放熱器の熱伝達の効率低下を防止でき、ＣＯＰを向上させることができる。
一方、膨張機６で潤滑に使われたオイルは、冷媒とともに流出する。流出したオイルは、第１オイル分離器５４にて冷媒と分離され、分離されたオイルは、第１オイル戻し管５５によって圧縮機１の吸入側配管に戻され、再び圧縮機１内に戻る。第１オイル分離器５４で分離したオイルは、第１オイル戻し管５５によって蒸発器（冷房運転モードにおける室内側熱交換器８、暖房運転モードにおける室外側熱交換器３）をバイパスするので、蒸発器にオイルが流入しないので蒸発器でのオイル溜まりがなく、蒸発器の熱伝達の効率低下を防止でき、ＣＯＰを向上させることができる。また、圧縮機１の吐出冷媒中のオイルで膨張機６や補助圧縮機１０の摺動部を潤滑することで、膨張機６や補助圧縮機１０にオイル溜めを設けることなく潤滑を行うことができ、補助圧縮機１０と膨張機６との一体化が容易となる。
また、ＰＡＧ、ＡＢ、ナフテン系鉱油などの冷媒と溶解性の低いオイルを用いることで、オイル分離器５１、５４でのオイル分離を確実にし、蒸発器や放熱器での熱伝達の効率低下を防止することができ、ＣＯＰの向上を図ることができる。
【００２０】
上記それぞれの実施例では、ヒートポンプ式冷暖房型空気調和装置を用いて説明したが、室外側熱交換器３を第１の熱交換器、室内側熱交換器８を第２の熱交換器とし、これら第１の熱交換器や第２の熱交換器を、温冷水器や蓄冷熱器などに利用したその他の冷凍サイクル装置であってもよい。
また、上記それぞれの実施例では、膨張機６の駆動軸を、圧縮機１又は補助圧縮機１０の駆動軸と連結し、膨張機６で回収した動力を圧縮機１又は補助圧縮機１０の駆動に利用する場合を説明したが、膨張機６の駆動軸に発電機を設けて電力に変換して利用してもよい。
また、それぞれの実施例において、高圧冷媒圧力の検出には圧力センサーを用いることができる。
【００２１】
【発明の効果】
以上のように、本発明によれば、圧縮機の吐出冷媒中のオイルで膨張機の摺動部を潤滑することで、膨張機にオイル溜めを設けることなく膨張部と軸との潤滑を行うことができ、圧縮機と膨張機との一体化が容易となる。
また本発明によれば、放熱器や蒸発器にオイルが流入しないので放熱器や蒸発器でのオイル溜まりがなく、放熱器や蒸発器の熱伝達の効率低下を防止でき、ＣＯＰを向上させることができる。
また本発明によれば、冷媒と溶解性の低いオイルを用いることで、オイル分離器でのオイル分離を確実にし、蒸発器や放熱器での熱伝達の効率低下を防止することができ、ＣＯＰの向上を図ることができる。
【図面の簡単な説明】
【図１】 本発明の一実施例によるヒートポンプ式冷暖房型空気調和装置の構成図
【図２】 本発明の他の実施例によるヒートポンプ式冷暖房型空気調和装置の構成図
【図３】 本発明の他の実施例によるヒートポンプ式冷暖房型空気調和装置の構成図
【符号の説明】
１ 圧縮機
２ 第１四方弁
３ 室外側熱交換器
４ 第２四方弁
５ 予膨張弁
６ 膨張機
７ 制御弁
８ 室内側熱交換器
１０ 補助圧縮機
１１ モータ
５１ 第２オイル分離器
５２ 第２オイル戻し管
５３ 絞り装置
５４ 第２オイル分離器
５５ 第２オイル戻し管
５６ 絞り装置[0001]
BACKGROUND OF THE INVENTION
  The present invention relates to a refrigeration cycle apparatus using carbon dioxide as a refrigerant and including a compressor, an outdoor heat exchanger, an expander, and an indoor heat exchanger.
[0002]
[Prior art]
  In a refrigeration cycle apparatus including a compressor, an outdoor heat exchanger, an expander, and an indoor heat exchanger, oil is supplied to piping on the outlet side of the compressor in order to secure lubricating oil between the compressor and the expander. There has been proposed a configuration in which a separator is provided and oil separated by the oil separator is supplied to the suction side of the compressor and the inlet side of the expander (see, for example, Patent Document 1).
[0003]
[Patent Document 1]
          JP 2001-141315 A
[0004]
[Problems to be solved by the invention]
  However, in order to supply the oil separated by the oil separator to the suction side of the compressor and the inlet side of the expander, a separate valve is required for the oil return pipe, so that the flow control is difficult. It is.
[0005]
  Therefore, an object of the present invention is to smoothly perform lubrication between the compressor and the expander without performing diversion control as in the prior art.
[0006]
[Means for Solving the Problems]
  The refrigeration cycle apparatus of the present invention according to claim 1 uses carbon dioxide as a refrigerant,First heat exchangerAnd the expanderSecond heat exchangerA first oil separator is provided in the refrigerant outflow side piping of the expander, and the oil separated by the first oil separator is returned to the suction side piping of the compressor.In addition, a second oil separator is provided in the discharge side pipe of the compressor, and the oil separated by the second oil separator is returned to the refrigerant inflow side pipe of the expander.It is characterized by that.
  The refrigeration cycle apparatus of the present invention according to claim 2 uses carbon dioxide as a refrigerant,First heat exchangerAnd the expanderSecond heat exchangerAnd an auxiliary compressor, wherein the auxiliary compressor is connected to a suction side pipe of the compressor, and the auxiliary compressor is driven by the power recovered by the expander. A first oil separator is provided in the refrigerant outflow side pipe, and the oil separated by the first oil separator is returned to the suction side pipe of the auxiliary compressor.In addition, a second oil separator is provided in the discharge side pipe of the compressor, and the oil separated by the second oil separator is returned to the refrigerant inflow side pipe of the expander.It is characterized by that.
  The refrigeration cycle apparatus of the present invention described in claim 3 uses carbon dioxide as a refrigerant,First heat exchangerAnd the expanderSecond heat exchangerAnd an auxiliary compressor, wherein the auxiliary compressor is connected to a discharge side pipe of the compressor, and the auxiliary compressor is driven by the power recovered by the expander. A first oil separator is provided in the refrigerant outflow side pipe, and the oil separated by the first oil separator is returned to the suction side pipe of the compressor.In addition, a second oil separator is provided in the discharge side piping of the auxiliary compressor, and the oil separated by the second oil separator is returned to the refrigerant inflow side piping of the expander.It is characterized by that.
  According to a fourth aspect of the present invention, in the refrigeration cycle apparatus according to any one of the first to third aspects, a throttling device is provided in the first oil return pipe of the first oil separator. .
  Claim 5The invention described isClaim 1FromClaim 3In the refrigeration cycle apparatus according to any one of the above, a throttling device is provided in the second oil return pipe of the second oil separator.
  Claim 6In the refrigeration cycle apparatus according to claim 1, the present invention described is a first four-way valve to which a discharge side pipe and a suction side pipe of the compressor are connected, a refrigerant inflow side pipe and a refrigerant outflow of the expander. A second four-way valve 4 connected to a side pipe, wherein the first oil separator is provided in a pipe between the refrigerant outlet of the expander and the second four-way valve, and the first oil separator The first oil return pipe is provided in a pipe from the first four-way valve to the suction port of the compressor.
  Claim 7In the refrigeration cycle apparatus according to claim 2, the present invention described is a first four-way valve to which a discharge side pipe of the compressor and a suction side pipe of the auxiliary compressor are connected, and a refrigerant inflow of the expander A second four-way valve 4 to which a side pipe and a refrigerant outflow side pipe are connected, and the first oil separator is provided in a pipe between the refrigerant outlet of the expander and the second four-way valve, The first oil return pipe of the first oil separator is provided in a pipe from the first four-way valve to the suction port of the auxiliary compressor.
  Claim 8In the refrigeration cycle apparatus according to claim 3, the present invention described is a first four-way valve to which a discharge side pipe of the auxiliary compressor and a suction side pipe of the compressor are connected, and a refrigerant inflow of the expander A second four-way valve 4 to which a side pipe and a refrigerant outflow side pipe are connected, and the first oil separator is provided in a pipe between the refrigerant outlet of the expander and the second four-way valve, The first oil return pipe of the first oil separator is provided in a pipe from the first four-way valve to the suction port of the compressor.
  Claim 9The invention described isClaim 1In the refrigeration cycle apparatus according to claim 2, a first four-way valve to which a discharge side pipe and a suction side pipe of the compressor are connected, and a refrigerant inflow side pipe and a refrigerant outflow side pipe of the expander are connected to each other. A second oil separator is provided in a pipe from a discharge port of the compressor to the first four-way valve, and a second oil return pipe of the second oil separator is provided to the second oil separator. It is provided in piping between the four-way valve and the refrigerant inlet of the expander.
  Claim 10The invention described isClaim 2In the refrigeration cycle apparatus according to claim 1, a first four-way valve to which a discharge side pipe of the compressor and a suction side pipe of the auxiliary compressor are connected, a refrigerant inflow side pipe and a refrigerant outflow side pipe of the expander A second oil separator connected to the second oil separator, the second oil separator being provided in a pipe from the discharge port of the compressor to the first four-way valve, and a second oil return pipe of the second oil separator. Is provided in a pipe from the second four-way valve to the refrigerant inlet of the expander.
  Claim 11The invention described isClaim 3In the refrigeration cycle apparatus according to claim 1, a first four-way valve to which a discharge side pipe of the auxiliary compressor and a suction side pipe of the compressor are connected, a refrigerant inflow side pipe and a refrigerant outflow side pipe of the expander A second four-way valve to be connected, the second oil separator is provided in a pipe from the discharge port of the auxiliary compressor to the first four-way valve, and a second oil return of the second oil separator A pipe is provided in a pipe between the second four-way valve and the refrigerant inlet of the expander.
  Claim 12In the refrigeration cycle apparatus according to any one of claims 1 to 3, the present invention described is characterized in that the oil such as PAG, AB, naphthenic mineral oil or the like and an oil having low solubility are used as the oil. And
[0007]
DETAILED DESCRIPTION OF THE INVENTION
  In the first embodiment of the present invention, a first oil separator is provided in the refrigerant outflow side piping of the expander, and the oil separated by the first oil separator is returned to the suction side piping of the compressor.At the same time, a second oil separator is provided in the discharge side piping of the compressor, and the oil separated by the second oil separator is returned to the refrigerant inflow side piping of the expander.
  According to the present embodiment, by lubricating the sliding portion of the expander with oil in the refrigerant discharged from the compressor, the expansion portion and the shaft can be lubricated without providing an oil reservoir in the expander. The compressor and the expander can be easily integrated. Further, since oil does not flow into the evaporator, there is no oil accumulation in the evaporator, and heat transfer of the evaporator can be prevented from being lowered, and COP can be improved.In addition, since oil does not flow into the radiator, there is no oil accumulation in the radiator, a decrease in heat transfer of the radiator can be prevented, and COP can be improved.
  In the second embodiment of the present invention, a first oil separator is provided in the refrigerant outflow side piping of the expander, and the oil separated by the first oil separator is returned to the suction side piping of the auxiliary compressor.In addition, a second oil separator is provided in the discharge side piping of the compressor, and the oil separated by the second oil separator is returned to the refrigerant inflow side piping of the expander.Is.
  According to the present embodiment, by lubricating the sliding portion of the expander with oil in the refrigerant discharged from the compressor, the expansion portion and the shaft can be lubricated without providing an oil reservoir in the expander. The expansion device and the auxiliary compressor can be easily integrated. Further, since oil does not flow into the evaporator, there is no oil accumulation in the evaporator, and heat transfer of the evaporator can be prevented from being lowered, and COP can be improved.In addition, since oil does not flow into the radiator, there is no oil accumulation in the radiator, a decrease in heat transfer of the radiator can be prevented, and COP can be improved.
  In the third embodiment of the present invention, a first oil separator is provided in the refrigerant outflow side piping of the expander, and the oil separated by the first oil separator is returned to the suction side piping of the compressor.In addition, a second oil separator is provided in the discharge side piping of the auxiliary compressor, and the oil separated by the second oil separator is returned to the refrigerant inflow side piping of the expander.Is.
  According to the present embodiment, by lubricating the sliding portion of the expander with oil in the refrigerant discharged from the compressor, the expansion portion and the shaft can be lubricated without providing an oil reservoir in the expander. The expansion device and the auxiliary compressor can be easily integrated. Further, since oil does not flow into the evaporator, there is no oil accumulation in the evaporator, and heat transfer of the evaporator can be prevented from being lowered, and COP can be improved.Moreover, according to this Embodiment, since oil does not flow into a radiator, there is no oil accumulation in a radiator, the fall of the heat transfer of a radiator can be prevented, and COP can be improved.
  In the fourth embodiment according to the present invention, a throttling device is provided in the first oil return pipe of the first oil separator in the first to third embodiments.
  According to the present embodiment, an appropriate oil return amount can be ensured by this throttling device.
  According to the invention5thThe embodiment of1st to 3rdIn this embodiment, the second oil return pipe of the second oil separator is provided with a throttle device.
  According to the present embodiment, an appropriate oil return amount can be ensured by this throttling device.
  According to the invention6thIn the first embodiment, the first four-way valve to which the discharge side piping and the suction side piping of the compressor are connected, and the refrigerant inflow side piping and the refrigerant outflow side piping of the expander are connected in the first embodiment. The first oil separator is provided in a pipe from the refrigerant outlet of the expander to the second four-way valve, and the first oil return pipe of the first oil separator is connected to the first oil separator. It is provided in the pipe from the four-way valve to the compressor inlet.
  According to the present embodiment, in the refrigeration cycle in which the cooling operation mode and the heating operation mode can be used by switching the first four-way valve, the sliding portion of the expander is lubricated with the oil in the refrigerant discharged from the compressor. can do. Further, since oil does not flow into the evaporator, there is no oil accumulation in the evaporator, and heat transfer of the evaporator can be prevented from being lowered, and COP can be improved.
  According to the invention7thIn the second embodiment, in the second embodiment, the first four-way valve to which the discharge side piping of the compressor and the suction side piping of the auxiliary compressor are connected, the refrigerant inflow side piping and the refrigerant outflow side of the expander A first oil separator is provided in a pipe between the refrigerant outlet of the expander and the second four-way valve, and a first oil return pipe of the first oil separator is provided. Is provided in the pipe from the first four-way valve to the suction port of the auxiliary compressor.
  According to the present embodiment, in the refrigeration cycle in which the cooling operation mode and the heating operation mode can be used by switching the first four-way valve, the sliding portion of the expander is lubricated with the oil in the refrigerant discharged from the compressor. can do. Further, since oil does not flow into the evaporator, there is no oil accumulation in the evaporator, and heat transfer of the evaporator can be prevented from being lowered, and COP can be improved.
  According to the invention8thIn the third embodiment, in the third embodiment, the first four-way valve to which the discharge side piping of the auxiliary compressor and the suction side piping of the compressor are connected, the refrigerant inflow side piping and the refrigerant outflow side of the expander A first oil separator is provided in a pipe between the refrigerant outlet of the expander and the second four-way valve, and a first oil return pipe of the first oil separator is provided. Is provided in a pipe from the first four-way valve to the suction port of the compressor.
  According to the present embodiment, in the refrigeration cycle in which the cooling operation mode and the heating operation mode can be used by switching the first four-way valve, the sliding portion of the expander is lubricated with the oil in the refrigerant discharged from the compressor. can do. Further, since oil does not flow into the evaporator, there is no oil accumulation in the evaporator, and heat transfer of the evaporator can be prevented from being lowered, and COP can be improved.
  According to the invention9thThe embodiment ofFirstIn the embodiment, the first four-way valve to which the discharge side pipe and the suction side pipe of the compressor are connected, and the second four-way valve to which the refrigerant inflow side pipe and the refrigerant outflow side pipe of the expander are connected. A second oil separator is provided in a pipe between the discharge port of the compressor and the first four-way valve, and a second oil return pipe of the second oil separator is provided from the second four-way valve to the refrigerant inlet of the expander. It is provided in the pipe between.
  According to the present embodiment, in the refrigeration cycle in which the cooling operation mode and the heating operation mode can be used by switching the first four-way valve, oil does not flow into the radiator, so there is no oil accumulation in the radiator. A decrease in heat transfer of the radiator can be prevented, and COP can be improved.
  According to the invention10thThe embodiment ofSecondIn the embodiment, the first four-way valve to which the discharge side piping of the compressor and the suction side piping of the auxiliary compressor are connected, and the refrigerant inflow side piping and the refrigerant outflow side piping of the expander are connected to the second. A second oil separator is provided in the pipe from the discharge port of the compressor to the first four-way valve, and the second oil return pipe of the second oil separator is connected to the expander from the second four-way valve. It is provided in the pipe between the refrigerant inlet.
  According to the present embodiment, in the refrigeration cycle in which the cooling operation mode and the heating operation mode can be used by switching the first four-way valve, oil does not flow into the radiator, so there is no oil accumulation in the radiator. A decrease in heat transfer of the radiator can be prevented, and COP can be improved.
  According to the inventionEleventhThe embodiment isThirdIn the embodiment, the first four-way valve to which the discharge side piping of the auxiliary compressor and the suction side piping of the compressor are connected, and the refrigerant inflow side piping and the refrigerant outflow side piping of the expander are connected to the second. A second oil separator is provided in the pipe from the discharge port of the auxiliary compressor to the first four-way valve, and the second oil return pipe of the second oil separator is expanded from the second four-way valve. It is provided in the pipe between the refrigerant inlet of the machine.
  According to the present embodiment, in the refrigeration cycle in which the cooling operation mode and the heating operation mode can be used by switching the first four-way valve, oil does not flow into the radiator, so there is no oil accumulation in the radiator. A decrease in heat transfer of the radiator can be prevented, and COP can be improved.
  According to the invention12thIn the first to third embodiments, the embodiment uses a refrigerant such as PAG, AB, and naphthenic mineral oil and an oil having low solubility as the oil.
  According to the present embodiment, by using a low-solubility oil with a refrigerant, it is possible to ensure oil separation in the oil separator, and prevent a decrease in efficiency of heat transfer in the evaporator and radiator, The COP can be improved.
[0008]
【Example】
  Hereinafter, a refrigeration cycle apparatus according to an embodiment of the present invention will be described with reference to the drawings for a heat pump type air conditioning apparatus.
  FIG. 1 is a configuration diagram of a heat pump air-conditioning type air conditioner according to the present embodiment.
  As shown in the figure, the heat pump air-conditioning type air conditioner according to the present embodiment uses CO as a refrigerant.2It is composed of a refrigerant circuit using a refrigerant and having a compressor 1 having a motor 11, an outdoor heat exchanger 3, an expander 6, and an indoor heat exchanger 8 connected by piping. As the oil for lubricating the sliding portion of the compressor 1 or the like, a refrigerant such as PAG, AB or naphthenic mineral oil and an oil having low solubility are used.
  A pre-expansion valve 5 is provided on the inflow side of the expander 6.
  A bypass circuit that bypasses the pre-expansion valve 5 and the expander 6 is provided in parallel with the pre-expansion valve 5 and the expander 6, and a control valve 7 is provided in the bypass circuit.
  Moreover, the drive shaft of the expander 6 and the drive shaft of the compressor 1 are connected, and the compressor 1 uses the power recovered by the expander 6 for driving.
  The refrigerant circuit includes a first four-way valve 2 to which a discharge side pipe and a suction side pipe of the compressor 1 are connected, a refrigerant inflow side pipe of the pre-expansion valve 5 and a refrigerant outflow side pipe of the expander 6. And a second four-way valve 4 to which a bypass circuit is connected.
  The first oil separator 54 is a pipe on the refrigerant outflow side of the expander 6, and is provided in a pipe between the junction with the bypass circuit and the second four-way valve 4. The oil separated by the first oil separator 54 is returned to the pipe between the first four-way valve 2 and the suction port of the compressor 1 by the first oil return pipe 55. The first oil return pipe 55 is provided with a throttle device 56.
  The second oil separator 51 is provided in a pipe between the discharge port of the compressor 1 and the first four-way valve 2. The oil separated by the second oil separator 51 is returned to the pipe between the second four-way valve 2 and the inlet of the expander 6 by the second oil return pipe 52. The second oil return pipe 52 is preferably provided on the downstream side of the branch with the bypass circuit. The second oil return pipe 52 is provided with a throttle device 53.
[0009]
  The operation of the heat pump type air conditioning apparatus according to this embodiment will be described below.
  First, the cooling operation mode using the outdoor heat exchanger 3 as a radiator and the indoor heat exchanger 8 as an evaporator will be described. The refrigerant flow in the cooling operation mode is indicated by solid line arrows in the figure.
  The refrigerant in the cooling operation mode is compressed and discharged at high temperature and high pressure by the compressor 1 driven by the motor 11, and is introduced into the outdoor heat exchanger 3 through the first four-way valve 2. In the outdoor heat exchanger 3, the CO2Since the refrigerant is in a supercritical state, it does not enter a gas-liquid two-phase state but radiates heat to an external fluid such as air or water. Then CO2The refrigerant is introduced into the pre-expansion valve 5 and the expander 6 through the second four-way valve 4 and is decompressed by the pre-expansion valve 5 and the expander 6. The power recovered by the expander 6 during this decompression is used to drive the compressor 1. At this time, for example, the opening of the control valve 7 is adjusted in accordance with the high-pressure refrigerant pressure detected on the outlet side of the outdoor heat exchanger 3, and the amount of refrigerant flowing through the bypass circuit is controlled. Further, the amount of refrigerant flowing through the expansion valve 6 is controlled by adjusting the opening of the pre-expansion valve 5 according to the detected high-pressure refrigerant pressure.
  CO depressurized by the pre-expansion valve 5 and the expander 62The refrigerant is guided to the indoor heat exchanger 8 via the second four-way valve 4, and evaporates and absorbs heat in the indoor heat exchanger 8. Indoor cooling is performed by this heat absorption. The refrigerant that has been evaporated is sucked into the compressor 1.
[0010]
  Next, the heating operation mode using the outdoor heat exchanger 3 as an evaporator and the indoor heat exchanger 8 as a radiator will be described. The refrigerant flow in the heating operation mode is indicated by a wavy arrow in the figure.
  The refrigerant in the heating operation mode is compressed and discharged at high temperature and high pressure by the compressor 1 driven by the motor 11, and is introduced into the indoor heat exchanger 8 through the first four-way valve 2. In the indoor heat exchanger 8, the CO2Since the refrigerant is in a supercritical state, it does not enter a gas-liquid two-phase state, but dissipates heat to an external fluid such as air or water, and for example, room heating is performed using this heat dissipation. Then CO2The refrigerant is introduced into the pre-expansion valve 5 and the expander 6 and decompressed by the pre-expansion valve 5 and the expander 6. The power recovered by the expander 6 during this decompression is used to drive the compressor 1. At this time, for example, the opening amount of the control valve 7 is adjusted according to the high-pressure refrigerant pressure detected on the outlet side of the indoor heat exchanger 8 to control the amount of refrigerant flowing through the bypass circuit. Further, the amount of refrigerant flowing through the expansion valve 6 is controlled by adjusting the opening of the pre-expansion valve 5 according to the detected high-pressure refrigerant pressure.
  CO depressurized by the pre-expansion valve 5 and the expander 62The refrigerant is guided to the outdoor heat exchanger 3 via the second four-way valve 4, evaporates and absorbs heat in the outdoor heat exchanger 3, and the refrigerant that has finished evaporation passes through the first four-way valve 2. And sucked into the compressor 1.
[0011]
  Next, the flow of oil during the air conditioning operation will be described.
  An oil reservoir is provided inside the compressor 1 to store a predetermined amount of oil. The oil in the compressor 1 is lubricated. A part of this oil is discharged together with the refrigerant. The discharged oil is separated from the refrigerant in the second oil separator 51, and the separated oil is returned to the refrigerant inflow side pipe of the expander 6 by the second oil return pipe 52. Therefore, the expander 6 is lubricated by this oil. Further, the oil separated by the second oil separator 51 bypasses the radiator (the outdoor heat exchanger 3 in the cooling operation mode and the indoor heat exchanger 8 in the heating operation mode) by the second oil return pipe 52. Since the oil does not flow into the radiator, there is no oil accumulation in the radiator, the heat transfer efficiency of the radiator can be prevented from being lowered, and the COP can be improved.
  On the other hand, the oil used for lubrication in the expander 6 flows out together with the refrigerant. The oil that has flowed out is separated from the refrigerant by the first oil separator 54, and the separated oil is returned to the suction side pipe of the compressor 1 by the first oil return pipe 55. Therefore, the oil separated by the first oil separator 54 bypasses the evaporator (the indoor heat exchanger 8 in the cooling operation mode and the outdoor heat exchanger 3 in the heating operation mode) by the first oil return pipe 55. Since the oil does not flow into the evaporator, there is no oil accumulation in the evaporator, the efficiency of heat transfer of the evaporator can be prevented from decreasing, and the COP can be improved. Further, by lubricating the sliding portion of the expander 6 with the oil in the refrigerant discharged from the compressor 1, lubrication can be performed without providing an oil reservoir in the expander 6, and the compressor 1, the expander 6, Can be easily integrated.
  In addition, by using refrigerants such as PAG, AB, naphthenic mineral oil and oils with low solubility, oil separation in the oil separators 51 and 54 is ensured, and the efficiency of heat transfer in the evaporator and radiator is reduced. Can be prevented, and COP can be improved.
[0012]
  Hereinafter, a refrigeration cycle apparatus according to another embodiment of the present invention will be described with reference to the drawings for a heat pump type air conditioning apparatus.
  FIG. 2 is a configuration diagram of the heat pump type air conditioning apparatus according to the present embodiment.
  As shown in the figure, the heat pump air-conditioning type air conditioner according to the present embodiment uses CO as a refrigerant.2It is composed of a refrigerant circuit that uses a refrigerant and includes a compressor 1 having a motor 11, an outdoor heat exchanger 3, an expander 6, an indoor heat exchanger 8, and an auxiliary compressor 10 connected by piping. The As the oil for lubricating the sliding portion of the compressor 1 or the like, a refrigerant such as PAG, AB or naphthenic mineral oil and an oil having low solubility are used.
  A pre-expansion valve 5 is provided on the inflow side piping of the expander 6.
  A bypass circuit that bypasses the pre-expansion valve 5 and the expander 6 is provided in parallel with the pre-expansion valve 5 and the expander 6, and a control valve 7 is provided in the bypass circuit.
  Further, the drive shaft of the expander 6 and the drive shaft of the auxiliary compressor 10 are connected, and the auxiliary compressor 10 is driven by the power recovered by the expander 6.
  In this refrigerant circuit, the first four-way valve 2 to which the discharge side pipe of the compressor 1 and the suction side pipe of the auxiliary compressor 10 are connected, the refrigerant inflow side pipe of the pre-expansion valve 5 and the refrigerant of the expander 6 are connected. A second four-way valve 4 connected to the outflow side pipe and connected to the bypass circuit is provided.
  The first oil separator 54 is a pipe on the refrigerant outflow side of the expander 6, and is provided in a pipe between the junction with the bypass circuit and the second four-way valve 4. The oil separated by the first oil separator 54 is returned to the pipe between the first four-way valve 2 and the suction port of the compressor 1 by the first oil return pipe 55. The first oil return pipe 55 is provided with a throttle device 56.
  The second oil separator 51 is provided in a pipe between the discharge port of the compressor 1 and the first four-way valve 2. The oil separated by the second oil separator 51 is returned to the pipe between the second four-way valve 2 and the inlet of the expander 6 by the second oil return pipe 52. The second oil return pipe 52 is preferably provided on the downstream side of the branch with the bypass circuit. The second oil return pipe 52 is provided with a throttle device 53.
[0013]
  The operation of the heat pump type air conditioning apparatus according to this embodiment will be described below.
  First, the cooling operation mode using the outdoor heat exchanger 3 as a radiator and the indoor heat exchanger 8 as an evaporator will be described. The refrigerant flow in the cooling operation mode is indicated by solid line arrows in the figure.
  The refrigerant in the cooling operation mode is compressed and discharged at high temperature and high pressure by the compressor 1 driven by the motor 11, and is introduced into the outdoor heat exchanger 3 through the first four-way valve 2. In the outdoor heat exchanger 3, the CO2Since the refrigerant is in a supercritical state, it does not enter a gas-liquid two-phase state but radiates heat to an external fluid such as air or water. Then CO2The refrigerant is introduced into the pre-expansion valve 5 and the expander 6 and decompressed by the pre-expansion valve 5 and the expander 6. The power recovered by the expander 6 during this decompression is used to drive the auxiliary compressor 10. At this time, for example, the opening of the control valve 7 is adjusted in accordance with the high-pressure refrigerant pressure detected on the outlet side of the outdoor heat exchanger 3, and the amount of refrigerant flowing through the bypass circuit is controlled. Further, the amount of refrigerant flowing through the expansion valve 6 is controlled by adjusting the opening of the pre-expansion valve 5 according to the detected high-pressure refrigerant pressure.
  CO depressurized by the pre-expansion valve 5 and the expander 62The refrigerant is guided to the indoor heat exchanger 8 via the second four-way valve 4, and evaporates and absorbs heat in the indoor heat exchanger 8. Indoor cooling is performed by this heat absorption. The evaporated refrigerant is led to the auxiliary compressor 10 through the first four-way valve 2, supercharged (charged) by the auxiliary compressor 10, and sucked into the compressor 1.
[0014]
  Next, the heating operation mode using the outdoor heat exchanger 3 as an evaporator and the indoor heat exchanger 8 as a radiator will be described. The refrigerant flow in the heating operation mode is indicated by a wavy arrow in the figure.
  The refrigerant in the heating operation mode is compressed and discharged at high temperature and high pressure by the compressor 1 driven by the motor 11, and is introduced into the indoor heat exchanger 8 through the first four-way valve 2. In the indoor heat exchanger 8, the CO2Since the refrigerant is in a supercritical state, it does not enter a gas-liquid two-phase state, but dissipates heat to an external fluid such as air or water, and for example, room heating is performed using this heat dissipation. Then CO2The refrigerant is introduced into the pre-expansion valve 5 and the expander 6 and decompressed by the pre-expansion valve 5 and the expander 6. The power recovered by the expander 6 during this decompression is used to drive the auxiliary compressor 10. At this time, for example, the opening amount of the control valve 7 is adjusted according to the high-pressure refrigerant pressure detected on the outlet side of the indoor heat exchanger 8 to control the amount of refrigerant flowing through the bypass circuit. Further, the amount of refrigerant flowing through the expansion valve 6 is controlled by adjusting the opening of the pre-expansion valve 5 according to the detected high-pressure refrigerant pressure.
  CO depressurized by the pre-expansion valve 5 and the expander 62The refrigerant is guided to the outdoor heat exchanger 3 via the second four-way valve 4, evaporates and absorbs heat in the outdoor heat exchanger 3, and the refrigerant that has finished evaporation passes through the first four-way valve 2. Then, it is guided to the auxiliary compressor 10, supercharged (charged) by the auxiliary compressor 10, and sucked into the compressor 1.
[0015]
  Next, the flow of oil during the air conditioning operation will be described.
  An oil reservoir is provided inside the compressor 1 to store a predetermined amount of oil. The oil in the compressor 1 is lubricated. A part of this oil is discharged together with the refrigerant. The discharged oil is separated from the refrigerant in the second oil separator 51, and the separated oil is returned to the refrigerant inflow side pipe of the expander 6 by the second oil return pipe 52. Therefore, the expander 6 is lubricated by this oil. Further, the oil separated by the second oil separator 51 bypasses the radiator (the outdoor heat exchanger 3 in the cooling operation mode and the indoor heat exchanger 8 in the heating operation mode) by the second oil return pipe 52. Since the oil does not flow into the radiator, there is no oil accumulation in the radiator, the heat transfer efficiency of the radiator can be prevented from being lowered, and the COP can be improved.
  On the other hand, the oil used for lubrication in the expander 6 flows out together with the refrigerant. The oil that has flowed out is separated from the refrigerant by the first oil separator 54, and the separated oil is returned to the suction side pipe of the auxiliary compressor 10 by the first oil return pipe 55. Accordingly, the auxiliary compressor 10 is lubricated by the oil, and the refrigerant discharged from the auxiliary compressor 10 returns to the compressor 1 again. Further, the oil separated by the first oil separator 54 bypasses the evaporator (the indoor heat exchanger 8 in the cooling operation mode and the outdoor heat exchanger 3 in the heating operation mode) by the first oil return pipe 55. Since the oil does not flow into the evaporator, there is no oil accumulation in the evaporator, the efficiency of heat transfer of the evaporator can be prevented from decreasing, and the COP can be improved. Moreover, lubrication can be performed without providing an oil reservoir in the expander 6 or the auxiliary compressor 10 by lubricating the sliding portions of the expander 6 or the auxiliary compressor 10 with oil in the refrigerant discharged from the compressor 1. The auxiliary compressor 10 and the expander 6 can be easily integrated.
  In addition, by using refrigerants such as PAG, AB, naphthenic mineral oil and oils with low solubility, oil separation in the oil separators 51 and 54 is ensured, and the efficiency of heat transfer in the evaporator and radiator is reduced. Can be prevented, and COP can be improved.
[0016]
  Hereinafter, a refrigeration cycle apparatus according to another embodiment of the present invention will be described with reference to the drawings for a heat pump type air conditioning apparatus.
  FIG. 3 is a configuration diagram of the heat pump air-conditioning type air conditioner according to the present embodiment.
  As shown in the figure, the heat pump air-conditioning type air conditioner according to the present embodiment uses CO as a refrigerant.2It is composed of a refrigerant circuit using a refrigerant and having a compressor 1 having a motor 11, an auxiliary compressor 10, an outdoor heat exchanger 3, an expander 6, and an indoor heat exchanger 8 connected by piping. The As the oil for lubricating the sliding portion of the compressor 1 or the like, a refrigerant such as PAG, AB or naphthenic mineral oil and an oil having low solubility are used.
  A pre-expansion valve 5 is provided on the inflow side piping of the expander 6.
  A bypass circuit that bypasses the pre-expansion valve 5 and the expander 6 is provided in parallel with the pre-expansion valve 5 and the expander 6, and a control valve 7 is provided in the bypass circuit.
  Further, the drive shaft of the expander 6 and the drive shaft of the auxiliary compressor 10 are connected, and the auxiliary compressor 10 is driven by the power recovered by the expander 6.
  The refrigerant circuit includes a first four-way valve 2 to which a suction side pipe of the compressor 1 and a discharge side pipe of the auxiliary compressor 10 are connected, a suction side pipe of the pre-expansion valve 5 and a discharge side of the expander 6. And a second four-way valve 4 to which a bypass circuit is connected.
  The first oil separator 54 is a pipe on the refrigerant outflow side of the expander 6, and is provided in a pipe between the junction with the bypass circuit and the second four-way valve 4. The oil separated by the first oil separator 54 is returned to the pipe between the first four-way valve 2 and the suction port of the compressor 1 by the first oil return pipe 55. The first oil return pipe 55 is provided with a throttle device 56.
  The second oil separator 51 is provided in a pipe between the discharge port of the compressor 1 and the first four-way valve 2. The oil separated by the second oil separator 51 is returned to the pipe between the second four-way valve 2 and the inlet of the expander 6 by the second oil return pipe 52. The second oil return pipe 52 is preferably provided on the downstream side of the branch with the bypass circuit. The second oil return pipe 52 is provided with a throttle device 53.
[0017]
  The operation of the heat pump type air conditioning apparatus according to this embodiment will be described below.
  First, the cooling operation mode using the outdoor heat exchanger 3 as a radiator and the indoor heat exchanger 8 as an evaporator will be described. The refrigerant flow in the cooling operation mode is indicated by solid line arrows in the figure.
  The refrigerant in the cooling operation mode is compressed and discharged at a high temperature and a high pressure by the compressor 1 driven by the motor 11, guided to the auxiliary compressor 10, and further overpressure (expressor) by the auxiliary compressor 10. Then, it is introduced into the outdoor heat exchanger 3 through the first four-way valve 2. In the outdoor heat exchanger 3, the CO2Since the refrigerant is in a supercritical state, it does not enter a gas-liquid two-phase state but radiates heat to an external fluid such as air or water. Then CO2The refrigerant is introduced into the pre-expansion valve 5 and the expander 6 and decompressed by the pre-expansion valve 5 and the expander 6. The power recovered by the expander 6 during this decompression is used to drive the auxiliary compressor 10. At this time, for example, the opening of the control valve 7 is adjusted in accordance with the high-pressure refrigerant pressure detected on the outlet side of the outdoor heat exchanger 3, and the amount of refrigerant flowing through the bypass circuit is controlled. Further, the amount of refrigerant flowing through the expansion valve 6 is controlled by adjusting the opening of the pre-expansion valve 5 according to the detected high-pressure refrigerant pressure.
  CO depressurized by the pre-expansion valve 5 and the expander 62The refrigerant is guided to the indoor heat exchanger 8 via the second four-way valve 4, and evaporates and absorbs heat in the indoor heat exchanger 8. Indoor cooling is performed by this heat absorption. The evaporated refrigerant is sucked into the compressor 1 through the first four-way valve 2.
[0018]
  Next, the heating operation mode using the outdoor heat exchanger 3 as an evaporator and the indoor heat exchanger 8 as a radiator will be described. The refrigerant flow in the heating operation mode is indicated by a wavy arrow in the figure.
  The refrigerant in the heating operation mode is compressed and discharged at a high temperature and high pressure by the compressor 1 driven by the motor 11, is guided to the auxiliary compressor 10, and is further overpressured (expressor) by the auxiliary compressor 10. Then, it is introduced into the indoor heat exchanger 8 through the first four-way valve 2. In the indoor heat exchanger 8, the CO2Since the refrigerant is in a supercritical state, it does not enter a gas-liquid two-phase state, but dissipates heat to an external fluid such as air or water, and for example, room heating is performed using this heat dissipation. Then CO2The refrigerant is introduced into the pre-expansion valve 5 and the expander 6 and decompressed by the pre-expansion valve 5 and the expander 6. The power recovered by the expander 6 during this decompression is used to drive the auxiliary compressor 10. At this time, for example, the opening amount of the control valve 7 is adjusted according to the high-pressure refrigerant pressure detected on the outlet side of the indoor heat exchanger 8 to control the amount of refrigerant flowing through the bypass circuit. Further, the amount of refrigerant flowing through the expansion valve 6 is controlled by adjusting the opening of the pre-expansion valve 5 according to the detected high-pressure refrigerant pressure.
  CO depressurized by the pre-expansion valve 5 and the expander 62The refrigerant is guided to the outdoor heat exchanger 3 via the second four-way valve 4, evaporates and absorbs heat in the outdoor heat exchanger 3, and the refrigerant that has finished evaporation passes through the first four-way valve 2. And sucked into the compressor 1.
[0019]
  Next, the flow of oil during the air conditioning operation will be described.
  An oil reservoir is provided inside the compressor 1 to store a predetermined amount of oil. The oil in the compressor 1 is lubricated. A part of this oil is discharged together with the refrigerant. The discharged oil is introduced into the auxiliary compressor 10 together with the refrigerant to lubricate the auxiliary compressor 10. The oil discharged from the auxiliary compressor 10 is separated from the refrigerant in the second oil separator 51, and the separated oil is returned to the refrigerant inflow side pipe of the expander 6 by the second oil return pipe 52. . Therefore, the expander 6 is lubricated by this oil. Further, the oil separated by the second oil separator 51 bypasses the radiator (the outdoor heat exchanger 3 in the cooling operation mode and the indoor heat exchanger 8 in the heating operation mode) by the second oil return pipe 52. Since the oil does not flow into the radiator, there is no oil accumulation in the radiator, the heat transfer efficiency of the radiator can be prevented from being lowered, and the COP can be improved.
  On the other hand, the oil used for lubrication in the expander 6 flows out together with the refrigerant. The oil that has flowed out is separated from the refrigerant in the first oil separator 54, and the separated oil is returned to the suction-side piping of the compressor 1 by the first oil return pipe 55 and returns to the compressor 1 again. Since the oil separated by the first oil separator 54 bypasses the evaporator (the indoor heat exchanger 8 in the cooling operation mode and the outdoor heat exchanger 3 in the heating operation mode) by the first oil return pipe 55, it evaporates. Since oil does not flow into the evaporator, there is no oil accumulation in the evaporator, and it is possible to prevent a reduction in the efficiency of heat transfer of the evaporator and improve COP. Moreover, lubrication can be performed without providing an oil reservoir in the expander 6 or the auxiliary compressor 10 by lubricating the sliding portions of the expander 6 or the auxiliary compressor 10 with oil in the refrigerant discharged from the compressor 1. The auxiliary compressor 10 and the expander 6 can be easily integrated.
  In addition, by using refrigerants such as PAG, AB, naphthenic mineral oil and oils with low solubility, oil separation in the oil separators 51 and 54 is ensured, and the efficiency of heat transfer in the evaporator and radiator is reduced. Can be prevented, and COP can be improved.
[0020]
  In each of the above embodiments, the heat pump air-conditioning type air conditioner has been described. However, the outdoor heat exchanger 3 is a first heat exchanger, and the indoor heat exchanger 8 is a second heat exchanger. Other refrigeration cycle apparatuses using the first heat exchanger and the second heat exchanger for a hot water cooler, a regenerator, and the like may be used.
  In each of the above embodiments, the drive shaft of the expander 6 is connected to the drive shaft of the compressor 1 or the auxiliary compressor 10, and the power recovered by the expander 6 is used to drive the compressor 1 or the auxiliary compressor 10. However, the generator may be provided on the drive shaft of the expander 6 and converted into electric power for use.
  In each embodiment, a pressure sensor can be used to detect the high-pressure refrigerant pressure.
[0021]
【The invention's effect】
  As described above, according to the present invention, the sliding portion of the expander is lubricated with the oil in the refrigerant discharged from the compressor, so that the expansion portion and the shaft are lubricated without providing an oil reservoir in the expander. Therefore, the compressor and the expander can be easily integrated.
  In addition, according to the present invention, since oil does not flow into the radiator or the evaporator, there is no oil accumulation in the radiator or the evaporator, the heat transfer efficiency of the radiator or the evaporator can be prevented from being lowered, and the COP can be improved. Can do.
  In addition, according to the present invention, by using a refrigerant and low-solubility oil, oil separation in the oil separator can be ensured, and a decrease in efficiency of heat transfer in the evaporator or radiator can be prevented. Can be improved.
[Brief description of the drawings]
FIG. 1 is a block diagram of a heat pump type air conditioning apparatus according to an embodiment of the present invention.
FIG. 2 is a block diagram of a heat pump type air conditioning apparatus according to another embodiment of the present invention.
FIG. 3 is a block diagram of a heat pump type air conditioning apparatus according to another embodiment of the present invention.
[Explanation of symbols]
    1 Compressor
    2 First four-way valve
    3 outdoor heat exchanger
    4 Second four-way valve
    5 Pre-expansion valve
    6 Expander
    7 Control valve
    8 Indoor heat exchanger
  10 Auxiliary compressor
  11 Motor
  51 Second oil separator
  52 Second oil return pipe
  53 Aperture device
  54 Second oil separator
  55 Second oil return pipe
  56 Aperture device

Claims (12)

冷媒として二酸化炭素を用い、圧縮機と第１の熱交換器と膨張機と第２の熱交換器とを備えた冷凍サイクル装置であって、前記膨張機の冷媒流出側配管に第１オイル分離器を設け、前記第１オイル分離器で分離したオイルを前記圧縮機の吸入側配管に戻すとともに、前記圧縮機の吐出側配管に第２オイル分離器を設け、前記第２オイル分離器で分離したオイルを前記膨張機の冷媒流入側配管に戻すことを特徴とする冷凍サイクル装置。A refrigeration cycle apparatus using carbon dioxide as a refrigerant and including a compressor, a first heat exchanger, an expander, and a second heat exchanger , wherein a first oil separation is provided in a refrigerant outflow side pipe of the expander And the oil separated by the first oil separator is returned to the suction side piping of the compressor, and the second oil separator is provided to the discharge side piping of the compressor, and separated by the second oil separator. The refrigeration cycle apparatus is characterized in that the recovered oil is returned to the refrigerant inflow side piping of the expander . 冷媒として二酸化炭素を用い、圧縮機と第１の熱交換器と膨張機と第２の熱交換器と補助圧縮機とを備え、前記補助圧縮機を前記圧縮機の吸入側配管に接続し、前記膨張機で回収した動力によって前記補助圧縮機を駆動する冷凍サイクル装置であって、前記膨張機の冷媒流出側配管に第１オイル分離器を設け、前記第１オイル分離器で分離したオイルを前記補助圧縮機の吸入側配管に戻すとともに、前記圧縮機の吐出側配管に第２オイル分離器を設け、前記第２オイル分離器で分離したオイルを前記膨張機の冷媒流入側配管に戻すことを特徴とする冷凍サイクル装置。Using carbon dioxide as a refrigerant, comprising a compressor, a first heat exchanger, an expander, a second heat exchanger, and an auxiliary compressor, and connecting the auxiliary compressor to a suction side pipe of the compressor; A refrigeration cycle apparatus for driving the auxiliary compressor by power recovered by the expander, wherein a first oil separator is provided in a refrigerant outflow side pipe of the expander, and the oil separated by the first oil separator is removed. In addition to returning to the suction side piping of the auxiliary compressor, a second oil separator is provided in the discharge side piping of the compressor, and the oil separated by the second oil separator is returned to the refrigerant inflow side piping of the expander. A refrigeration cycle apparatus characterized by. 冷媒として二酸化炭素を用い、圧縮機と第１の熱交換器と膨張機と第２の熱交換器と補助圧縮機とを備え、前記補助圧縮機を前記圧縮機の吐出側配管に接続し、前記膨張機で回収した動力によって前記補助圧縮機を駆動する冷凍サイクル装置であって、前記膨張機の冷媒流出側配管に第１オイル分離器を設け、前記第１オイル分離器で分離したオイルを前記圧縮機の吸入側配管に戻すとともに、前記補助圧縮機の吐出側配管に第２オイル分離器を設け、前記第２オイル分離器で分離したオイルを前記膨張機の冷媒流入側配管に戻すことを特徴とする冷凍サイクル装置。Using carbon dioxide as a refrigerant, comprising a compressor, a first heat exchanger, an expander, a second heat exchanger, and an auxiliary compressor, and connecting the auxiliary compressor to a discharge side pipe of the compressor; A refrigeration cycle apparatus for driving the auxiliary compressor by power recovered by the expander, wherein a first oil separator is provided in a refrigerant outflow side pipe of the expander, and the oil separated by the first oil separator is removed. In addition to returning to the suction side piping of the compressor, a second oil separator is provided in the discharge side piping of the auxiliary compressor, and the oil separated by the second oil separator is returned to the refrigerant inflow side piping of the expander. A refrigeration cycle apparatus characterized by. 前記第１オイル分離器の第１オイル戻し管に絞り装置を設けたことを特徴とする請求項１から請求項３のいずれかに記載の冷凍サイクル装置。  The refrigeration cycle apparatus according to any one of claims 1 to 3, wherein a throttling device is provided in the first oil return pipe of the first oil separator. 前記第２オイル分離器の第２オイル戻し管に絞り装置を設けたことを特徴とする請求項１から請求項３のいずれかに記載の冷凍サイクル装置。Refrigeration cycle apparatus according to any one of claims 1 to 3, characterized in that a throttle device to the second oil return pipe of the second oil separator. 前記圧縮機の吐出側配管と吸入側配管とが接続される第１四方弁と、前記膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁４とを備え、前記第１オイル分離器を前記膨張機の冷媒流出口から前記第２四方弁までの間の配管に設け、前記第１オイル分離器の第１オイル戻し管を、前記第１四方弁から前記圧縮機の吸入口までの間の配管に設けたことを特徴とする請求項１に記載の冷凍サイクル装置。  A first four-way valve to which a discharge side pipe and a suction side pipe of the compressor are connected; and a second four-way valve 4 to which a refrigerant inflow side pipe and a refrigerant outflow side pipe of the expander are connected, A first oil separator is provided in a pipe between the refrigerant outlet of the expander and the second four-way valve, and a first oil return pipe of the first oil separator is connected from the first four-way valve to the compressor. The refrigeration cycle apparatus according to claim 1, wherein the refrigeration cycle apparatus is provided in a pipe extending to a suction port. 前記圧縮機の吐出側配管と前記補助圧縮機の吸入側配管とが接続される第１四方弁と、前記膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁４とを備え、前記第１オイル分離器を前記膨張機の冷媒流出口から前記第２四方弁までの間の配管に設け、前記第１オイル分離器の第１オイル戻し管を、前記第１四方弁から前記補助圧縮機の吸入口までの間の配管に設けたことを特徴とする請求項２に記載の冷凍サイクル装置。  A first four-way valve to which a discharge side pipe of the compressor and a suction side pipe of the auxiliary compressor are connected, and a second four-way valve 4 to which a refrigerant inflow side pipe and a refrigerant outflow side pipe of the expander are connected. The first oil separator is provided in a pipe from the refrigerant outlet of the expander to the second four-way valve, and the first oil return pipe of the first oil separator is provided in the first four-way The refrigeration cycle apparatus according to claim 2, wherein the refrigeration cycle apparatus is provided in a pipe from a valve to a suction port of the auxiliary compressor. 前記補助圧縮機の吐出側配管と前記圧縮機の吸入側配管とが接続される第１四方弁と、前記膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁４とを備え、前記第１オイル分離器を前記膨張機の冷媒流出口から前記第２四方弁までの間の配管に設け、前記第１オイル分離器の第１オイル戻し管を、前記第１四方弁から前記圧縮機の吸入口までの間の配管に設けたことを特徴とする請求項３に記載の冷凍サイクル装置。  A first four-way valve to which the discharge side piping of the auxiliary compressor and the suction side piping of the compressor are connected, and a second four-way valve 4 to which the refrigerant inflow side piping and the refrigerant outflow side piping of the expander are connected. The first oil separator is provided in a pipe from the refrigerant outlet of the expander to the second four-way valve, and the first oil return pipe of the first oil separator is provided in the first four-way The refrigeration cycle apparatus according to claim 3, wherein the refrigeration cycle apparatus is provided in a pipe from a valve to an inlet of the compressor. 前記圧縮機の吐出側配管と吸入側配管とが接続される第１四方弁と、前記膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁とを備え、前記第２オイル分離器を前記圧縮機の吐出口から前記第１四方弁までの間の配管に設け、前記第２オイル分離器の第２オイル戻し管を、前記第２四方弁から前記膨張機の冷媒流入口までの間の配管に設けたことを特徴とする請求項１に記載の冷凍サイクル装置。A first four-way valve to which a discharge side pipe and a suction side pipe of the compressor are connected; and a second four-way valve to which a refrigerant inflow side pipe and a refrigerant outflow side pipe of the expander are connected. A second oil separator is provided in a pipe between the discharge port of the compressor and the first four-way valve, and a second oil return pipe of the second oil separator is connected to the refrigerant of the expander from the second four-way valve. The refrigeration cycle apparatus according to claim 1 , wherein the refrigeration cycle apparatus is provided in a pipe between the inlet and the inlet. 前記圧縮機の吐出側配管と前記補助圧縮機の吸入側配管とが接続される第１四方弁と、前記膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁とを備え、前記第２オイル分離器を前記圧縮機の吐出口から前記第１四方弁までの間の配管に設け、前記第２オイル分離器の第２オイル戻し管を、前記第２四方弁から前記膨張機の冷媒流入口までの間の配管に設けたことを特徴とする請求項２に記載の冷凍サイクル装置。A first four-way valve to which a discharge side pipe of the compressor and a suction side pipe of the auxiliary compressor are connected; a second four-way valve to which a refrigerant inflow side pipe and a refrigerant outflow side pipe of the expander are connected; The second oil separator is provided in a pipe between the discharge port of the compressor and the first four-way valve, and the second oil return pipe of the second oil separator is connected to the second four-way valve. The refrigeration cycle apparatus according to claim 2 , wherein the refrigeration cycle apparatus is provided in a pipe extending to a refrigerant inlet of the expander. 前記補助圧縮機の吐出側配管と前記圧縮機の吸入側配管とが接続される第１四方弁と、前記膨張機の冷媒流入側配管と冷媒流出側配管とが接続される第２四方弁とを備え、前記第２オイル分離器を前記補助圧縮機の吐出口から前記第１四方弁までの間の配管に設け、前記第２オイル分離器の第２オイル戻し管を、前記第２四方弁から前記膨張機の冷媒流入口までの間の配管に設けたことを特徴とする請求項３に記載の冷凍サイクル装置。A first four-way valve to which a discharge side pipe of the auxiliary compressor and a suction side pipe of the compressor are connected; a second four-way valve to which a refrigerant inflow side pipe and a refrigerant outflow side pipe of the expander are connected; The second oil separator is provided in a pipe from the discharge port of the auxiliary compressor to the first four-way valve, and the second oil return pipe of the second oil separator is provided in the second four-way valve. The refrigeration cycle apparatus according to claim 3 , wherein the refrigeration cycle apparatus is provided in a pipe from a refrigerant inlet to a refrigerant inlet of the expander. オイルとして、ＰＡＧ、ＡＢ、ナフテン系鉱油などの前記冷媒と溶解性の低いオイルを用いたことを特徴とする請求項１から請求項３のいずれかに記載の冷凍サイクル装置。  The refrigeration cycle apparatus according to any one of claims 1 to 3, wherein the refrigerant is an oil having low solubility with the refrigerant such as PAG, AB, or naphthenic mineral oil.
JP2002318130A 2002-10-31 2002-10-31 Refrigeration cycle equipment Expired - Fee Related JP4233843B2 (en)

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JP2006132818A (en) * 2004-11-04 2006-05-25 Matsushita Electric Ind Co Ltd Control method for refrigerating cycle device, and refrigerating cycle device using the same
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