JP2018169078A - Air conditioner - Google Patents
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- JP2018169078A JP2018169078A JP2017066147A JP2017066147A JP2018169078A JP 2018169078 A JP2018169078 A JP 2018169078A JP 2017066147 A JP2017066147 A JP 2017066147A JP 2017066147 A JP2017066147 A JP 2017066147A JP 2018169078 A JP2018169078 A JP 2018169078A
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Abstract
Description
本発明は、空気調和機に関し、特に、空気調和機の室外機に関する。 The present invention relates to an air conditioner, and more particularly to an outdoor unit of an air conditioner.
特許文献１は室外機の熱交換器を開示する。熱交換器は、冷房運転時に、圧縮機から吐出された冷媒が流入する複数の分岐冷媒流通路を備える。それぞれの分岐冷媒流通路の流出口には１つの分流器が接続される。分流器は最下方に配置される分岐冷媒流通路よりも重力方向上方に配置される。圧縮機から吐出される高温高圧の冷媒は、複数の分岐冷媒流通路に分流され、熱交換器の広い範囲で熱エネルギーの交換をする。こうして効率的な熱交換は実現される。 Patent document 1 discloses the heat exchanger of an outdoor unit. The heat exchanger includes a plurality of branch refrigerant flow passages into which refrigerant discharged from the compressor flows during cooling operation. One shunt is connected to the outlet of each branch refrigerant flow passage. The flow divider is arranged above the branch refrigerant flow passage arranged at the lowermost position in the gravity direction. The high-temperature and high-pressure refrigerant discharged from the compressor is divided into a plurality of branch refrigerant flow passages, and exchanges heat energy in a wide range of the heat exchanger. Thus, efficient heat exchange is realized.
冷房運転時に冷媒の流量が低循環量となった場合には冷媒の流速が遅くなるため、ガス冷媒よりもさらに流速が遅くなる液冷媒は滞留しやすくなる。そのため最下方に配置されるの分岐冷媒流通路では、分岐冷媒流通路の最下端よりも重力方向上方に分流器が設けられている場合、最下段の分岐冷媒流通路に液冷媒が溜まりやすくなる。冷媒の循環が滞り、性能の低下が引き起こされることが懸念される。 When the flow rate of the refrigerant becomes a low circulation amount during the cooling operation, the flow rate of the refrigerant becomes slow, so that the liquid refrigerant whose flow rate becomes slower than the gas refrigerant is likely to stay. Therefore, in the branch refrigerant flow passage arranged at the lowermost position, when the flow divider is provided above the lower end of the branch refrigerant flow passage in the gravity direction, the liquid refrigerant easily collects in the lowermost branch refrigerant flow passage. . There is a concern that the circulation of the refrigerant will stagnate and the performance will be reduced.
本発明は、最下段の分岐冷媒流通路で発生する液冷媒の滞留を抑制し、熱交換器の性能向上に寄与することができる空気調和機を提供することを目的とする。 An object of this invention is to provide the air conditioner which can suppress the retention of the liquid refrigerant which generate | occur | produces in the lowermost branch refrigerant | coolant flow path, and can contribute to the performance improvement of a heat exchanger.
本発明によれば、第１冷媒管で圧縮機に接続される第１分流器と、前記第１分流器よりも低い位置に配置されて、第２冷媒管で膨張弁に接続される第２分流器と、前記第１分流器および前記第２分流器の間で並列に流路を形成して伝熱フィンに結合される分岐冷媒管を有する熱交換器と、前記分岐冷媒管のうち、前記第２分流器よりも低い位置に流路を形成する特定分岐冷媒管、および、前記特定分岐冷媒管と前記第２冷媒管を接続するバイパス管とを備える空気調和機は提供される。 According to the present invention, the first shunt connected to the compressor by the first refrigerant pipe and the second shunt disposed at a position lower than the first shunt and connected to the expansion valve by the second refrigerant pipe. Of the branch refrigerant pipe, a heat exchanger having a branch refrigerant pipe coupled to heat transfer fins by forming a flow path in parallel between the first flow divider and the second flow divider and the heat transfer fin, An air conditioner including a specific branch refrigerant pipe that forms a flow path at a position lower than the second shunt and a bypass pipe that connects the specific branch refrigerant pipe and the second refrigerant pipe is provided.
冷房運転時には、圧縮機から吐出された高温高圧の冷媒が第１分流器で分流されて分岐冷媒管に導入される。分岐冷媒管で冷媒は熱エネルギーを放出し液化する。過冷却状態となった液冷媒は自重によってバイパス管を通って第２冷媒管に流入する。液冷媒は第２分流器よりも低い位置にある分岐冷媒管内に留まらずに流通する。 During the cooling operation, the high-temperature and high-pressure refrigerant discharged from the compressor is diverted by the first diverter and introduced into the branch refrigerant pipe. In the branch refrigerant pipe, the refrigerant releases heat energy and liquefies. The supercooled liquid refrigerant flows into the second refrigerant pipe through the bypass pipe by its own weight. The liquid refrigerant flows without staying in the branch refrigerant pipe located at a position lower than that of the second flow divider.
暖房運転時には、膨張弁を通過した冷媒は第２冷媒管に導入される。冷媒は第２分流器で分流されて分岐冷媒管に導入される。分岐冷媒管で冷媒は熱エネルギーを吸収し気化する。ガス冷媒は圧縮機に吸入される。 During the heating operation, the refrigerant that has passed through the expansion valve is introduced into the second refrigerant pipe. The refrigerant is branched by the second flow divider and introduced into the branch refrigerant pipe. In the branch refrigerant pipe, the refrigerant absorbs heat energy and vaporizes. The gas refrigerant is sucked into the compressor.
前記バイパス管には、前記第２冷媒管から前記特定分岐冷媒管に向かう冷媒の流通を阻止する逆止弁が組み込まれてもよい。冷房運転時にはバイパス管を通って第２分流器を迂回して分岐冷媒管から第２冷媒管に液冷媒は流入する。暖房運転時には、バイパス管は閉じられるので、分岐冷媒管には必ず第２分流器から二相冷媒は流入する。二相冷媒は良好に熱交換器全体に行き渡ることができる。 The bypass pipe may incorporate a check valve that prevents the refrigerant from flowing from the second refrigerant pipe to the specific branch refrigerant pipe. During the cooling operation, the liquid refrigerant flows from the branch refrigerant pipe into the second refrigerant pipe, bypassing the second flow divider through the bypass pipe. Since the bypass pipe is closed during heating operation, the two-phase refrigerant always flows into the branch refrigerant pipe from the second shunt. The two-phase refrigerant can be well distributed throughout the heat exchanger.
前記第２冷媒管は、前記特定分岐冷媒管の最下位置よりも下方で前記熱交換器内に組み込まれて前記伝熱フィンに結合されてもよく、前記バイパス管は、前記熱交換器および前記膨張弁の間で前記第２冷媒管に接続されてもよい。冷房運転時に、分岐冷媒管で液化しきれなかったガス冷媒は第２分流器を通過して第２冷媒管で更に熱エネルギーを放出する。こうして冷媒の液化はさらに促進される。 The second refrigerant pipe may be incorporated in the heat exchanger below the lowest position of the specific branch refrigerant pipe and coupled to the heat transfer fin, and the bypass pipe may include the heat exchanger and The second refrigerant pipe may be connected between the expansion valves. During the cooling operation, the gas refrigerant that has not been liquefied in the branch refrigerant pipe passes through the second shunt and further releases thermal energy through the second refrigerant pipe. In this way, liquefaction of the refrigerant is further promoted.
以上のように開示の装置によれば、最下段の分岐冷媒管で液冷媒の滞留を抑制し、熱交換器の性能向上に寄与することができる。 As described above, according to the disclosed apparatus, it is possible to suppress the stagnation of the liquid refrigerant with the lowermost branch refrigerant pipe and contribute to the improvement of the performance of the heat exchanger.
以下、添付図面を参照しつつ本発明の一実施形態を説明する。 Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.
（１）空気調和機の構成
図１は本発明の一実施形態に係る空気調和機１１の構成を概略的に示す。空気調和機１１は室内機１２および室外機１３を備える。室内機１２は例えば建物内の室内空間に設置される。その他、室内機１２は室内空間に相当する空間に設置されればよい。室内機１２には室内熱交換器１４が組み込まれる。室外機１３には圧縮機１５、室外熱交換器１６、膨張弁１７および四方弁１８が組み込まれる。室内熱交換器１４、圧縮機１５、室外熱交換器１６、膨張弁１７および四方弁１８は冷凍回路１９を形成する。
(1) Configuration of Air Conditioner FIG. 1 schematically shows a configuration of an air conditioner 11 according to an embodiment of the present invention. The air conditioner 11 includes an indoor unit 12 and an outdoor unit 13. The indoor unit 12 is installed in an indoor space in a building, for example. In addition, the indoor unit 12 may be installed in a space corresponding to the indoor space. An indoor heat exchanger 14 is incorporated in the indoor unit 12. The outdoor unit 13 includes a compressor 15, an outdoor heat exchanger 16, an expansion valve 17, and a four-way valve 18. The indoor heat exchanger 14, the compressor 15, the outdoor heat exchanger 16, the expansion valve 17 and the four-way valve 18 form a refrigeration circuit 19.
冷凍回路１９は第１循環経路２１を備える。第１循環経路２１は四方弁１８の第１口１８ａおよび第２口１８ｂを相互に結ぶ。第１循環経路２１には、圧縮機１５が設けられている。圧縮機１５の吸入管１５ａは四方弁１８の第１口１８ａに冷媒配管を介して接続される。第１口１８ａからガス冷媒は圧縮機１５の吸入管１５ａに供給される。圧縮機１５は低圧のガス冷媒を所定の圧力まで圧縮する。圧縮機１５の吐出管１５ｂは四方弁１８の第２口１８ｂに冷媒配管を介して接続される。圧縮機１５の吐出管１５ｂからガス冷媒は四方弁１８の第２口１８ｂに供給される。冷媒配管は例えば銅管であればよい。 The refrigeration circuit 19 includes a first circulation path 21. The first circulation path 21 connects the first port 18a and the second port 18b of the four-way valve 18 to each other. A compressor 15 is provided in the first circulation path 21. The suction pipe 15a of the compressor 15 is connected to the first port 18a of the four-way valve 18 via a refrigerant pipe. The gas refrigerant is supplied to the suction pipe 15a of the compressor 15 from the first port 18a. The compressor 15 compresses the low-pressure gas refrigerant to a predetermined pressure. The discharge pipe 15b of the compressor 15 is connected to the second port 18b of the four-way valve 18 via a refrigerant pipe. Gas refrigerant is supplied from the discharge pipe 15 b of the compressor 15 to the second port 18 b of the four-way valve 18. The refrigerant pipe may be a copper pipe, for example.
冷凍回路１９は第２循環経路２２をさらに備える。第２循環経路２２は四方弁１８の第３口１８ｃおよび第４口１８ｄを相互に結ぶ。第２循環経路２２には、第３口１８ｃ側から順番に室外熱交換器１６、膨張弁１７および室内熱交換器１４が組み込まれる。室外熱交換器１６は、通過する冷媒と周囲の空気との間で熱エネルギーを交換する。室内熱交換器１４は、通過する冷媒と周囲の空気との間で熱エネルギーを交換する。第２循環経路２２は例えば銅管などで形成されればよい。 The refrigeration circuit 19 further includes a second circulation path 22. The second circulation path 22 connects the third port 18c and the fourth port 18d of the four-way valve 18 to each other. The outdoor heat exchanger 16, the expansion valve 17, and the indoor heat exchanger 14 are incorporated into the second circulation path 22 in order from the third port 18c side. The outdoor heat exchanger 16 exchanges heat energy between the refrigerant passing therethrough and ambient air. The indoor heat exchanger 14 exchanges thermal energy between the refrigerant passing therethrough and ambient air. The second circulation path 22 may be formed of, for example, a copper pipe.
室外機１３には送風ファン２３が組み込まれる。送風ファン２３は室外熱交換器１６に通風する。送風ファン２３は例えば羽根車の回転に応じて気流を生成する。気流は室外熱交換器１６を通り抜ける。通り抜ける気流の流量は羽根車の回転数に応じて調整される。 A blower fan 23 is incorporated in the outdoor unit 13. The blower fan 23 ventilates the outdoor heat exchanger 16. The blower fan 23 generates an air flow according to the rotation of the impeller, for example. The airflow passes through the outdoor heat exchanger 16. The flow rate of the airflow passing through is adjusted according to the rotational speed of the impeller.
室内機１２には送風ファン２４が組み込まれる。送風ファン２４は室内熱交換器１４に通風する。送風ファン２４は羽根車の回転に応じて気流を生成する。送風ファン２４の働きで室内機１２には室内空気が吸い込まれる。室内空気は室内熱交換器１４を通り抜け冷媒と熱交換する。熱交換された冷気または暖気の気流は室内機１２から吹き出される。通り抜ける気流の流量は羽根車の回転数に応じて調整される。 A blower fan 24 is incorporated in the indoor unit 12. The blower fan 24 ventilates the indoor heat exchanger 14. The blower fan 24 generates an air flow according to the rotation of the impeller. Indoor air is sucked into the indoor unit 12 by the action of the blower fan 24. The indoor air passes through the indoor heat exchanger 14 and exchanges heat with the refrigerant. The heat-exchanged cold air or warm air flow is blown out from the indoor unit 12. The flow rate of the airflow passing through is adjusted according to the rotational speed of the impeller.
冷凍回路１９で冷房運転が実施される場合には、四方弁１８は第２口１８ｂおよび第３口１８ｃを相互に接続し第１口１８ａおよび第４口１８ｄを相互に接続する。したがって、圧縮機１５の吐出管１５ｂから高温高圧の冷媒が室外熱交換器１６に供給される。冷媒は室外熱交換器１６、膨張弁１７および室内熱交換器１４を順番に流通する。室外熱交換器１６では冷媒から外気に放熱する。膨張弁１７で冷媒は低圧まで減圧される。減圧された冷媒は室内熱交換器１４で周囲の空気から吸熱する。冷気が生成される。冷気は送風ファン２４の働きで室内空間に吹き出される。 When the cooling operation is performed in the refrigeration circuit 19, the four-way valve 18 connects the second port 18b and the third port 18c to each other and connects the first port 18a and the fourth port 18d to each other. Therefore, high-temperature and high-pressure refrigerant is supplied to the outdoor heat exchanger 16 from the discharge pipe 15 b of the compressor 15. The refrigerant flows through the outdoor heat exchanger 16, the expansion valve 17, and the indoor heat exchanger 14 in order. The outdoor heat exchanger 16 radiates heat from the refrigerant to the outside air. The refrigerant is decompressed to a low pressure by the expansion valve 17. The decompressed refrigerant absorbs heat from the surrounding air in the indoor heat exchanger 14. Cold air is generated. The cold air is blown out into the indoor space by the function of the blower fan 24.
冷凍回路１９で暖房運転が実施される場合には、四方弁１８は第２口１８ｂおよび第４口１８ｄを相互に接続し第１口１８ａおよび第３口１８ｃを相互に接続する。圧縮機１５から高温高圧の冷媒が室内熱交換器１４に供給される。冷媒は室内熱交換器１４、膨張弁１７および室外熱交換器１６を順番に流通する。室内熱交換器１４では冷媒から周囲の空気に放熱する。暖気が生成される。暖気は送風ファン２４の働きで室内空間に吹き出される。膨張弁１７で冷媒は低圧まで減圧される。減圧された冷媒は室外熱交換器１６で周囲の空気から吸熱する。その後、冷媒は圧縮機１５に戻る。 When the heating operation is performed in the refrigeration circuit 19, the four-way valve 18 connects the second port 18b and the fourth port 18d to each other and connects the first port 18a and the third port 18c to each other. A high-temperature and high-pressure refrigerant is supplied from the compressor 15 to the indoor heat exchanger 14. The refrigerant flows through the indoor heat exchanger 14, the expansion valve 17, and the outdoor heat exchanger 16 in order. The indoor heat exchanger 14 radiates heat from the refrigerant to the surrounding air. Warm air is generated. Warm air is blown into the indoor space by the function of the blower fan 24. The refrigerant is decompressed to a low pressure by the expansion valve 17. The decompressed refrigerant absorbs heat from the surrounding air in the outdoor heat exchanger 16. Thereafter, the refrigerant returns to the compressor 15.
（２）室外機の構成
図２に示されるように、室外熱交換器１６は、室外機１３の底板２６に組み付けられて、底板２６から垂直方向に立ち上がる。室外熱交換器１６は、地面ＧＤに直交する垂直面に広がって、相互に平行に配列される複数の伝熱フィン２７と、伝熱フィン２７を貫通しながら水平方向に延びる銅管からなる伝熱管２８とを備える。伝熱フィン２７と伝熱管２８とは結合される。室外熱交換器１６は、風の流通方向に対して前後に重ねられる風下側の伝熱ユニット２９ａと、風上側の伝熱ユニット２９ｂで構成される。個々の伝熱ユニット２９ａ、２９ｂごとに垂直方向に１列の伝熱管２８が配列される。伝熱フィン２７および冷媒管２８は銅やアルミニウムその他の伝熱素材から形成される。ここで伝熱ユニット２９ａ、２９ｂは、１枚のフィンに伝熱管２８を挿通する挿通穴を２列有するもので一体的に作られていても良い。
(2) Configuration of Outdoor Unit As shown in FIG. 2, the outdoor heat exchanger 16 is assembled to the bottom plate 26 of the outdoor unit 13 and rises from the bottom plate 26 in the vertical direction. The outdoor heat exchanger 16 extends in a vertical plane perpendicular to the ground GD, and is composed of a plurality of heat transfer fins 27 arranged in parallel to each other and a copper pipe extending in the horizontal direction while penetrating the heat transfer fins 27. And a heat pipe 28. The heat transfer fins 27 and the heat transfer tubes 28 are coupled. The outdoor heat exchanger 16 includes a leeward heat transfer unit 29a and a windward heat transfer unit 29b that are stacked in the front-rear direction with respect to the wind flow direction. One row of heat transfer tubes 28 is arranged in the vertical direction for each of the heat transfer units 29a and 29b. The heat transfer fins 27 and the refrigerant tubes 28 are formed of copper, aluminum or other heat transfer material. Here, the heat transfer units 29a and 29b may be integrally formed with two rows of insertion holes through which the heat transfer tubes 28 are inserted into one fin.
室外熱交換器１６に囲まれて送風ファン２３は配置される。送風ファン２３は、水平軸線３１回りに回転自在に支持されるハブ２３ａと、ハブ２３ａから径方向外方に広がる複数の羽根２３ｂとを備える。羽根２３ｂは室外機１３の底板２６に平行な水平軸線３１に平行に気流を生成する。室外熱交換器１６は、室外機１３の背面と背面に連続する一方の側面とに沿って広がる。 The blower fan 23 is disposed surrounded by the outdoor heat exchanger 16. The blower fan 23 includes a hub 23a that is rotatably supported around the horizontal axis 31 and a plurality of blades 23b that extend radially outward from the hub 23a. The blades 23 b generate an air flow parallel to a horizontal axis 31 parallel to the bottom plate 26 of the outdoor unit 13. The outdoor heat exchanger 16 extends along the back surface of the outdoor unit 13 and one side surface continuous to the back surface.
室外熱交換器１６の一端では伝熱ユニット２９ａ、２９ｂごとに上下１対ずつの伝熱管２８からなる複数のヘアピン管３２が伝熱フィン２７に挿通される。図３に示されるように、室外熱交換器１６の他端ではヘアピン管を連結するＵ字管３３の接続に基づき上下方向に４つの流路を構成する分岐冷媒管３４ａ、３４ｂ、３４ｃ、３４ｄおよび、それらが合流して１つの流路となる共通冷媒管３５が形成される。個々の分岐冷媒管３４ａ〜３４ｄは、底板２６に平行な水平方向に延びる伝熱管２８からなる複数のヘアピン管３２とヘアピン管を連結するＵ字管３３とで構成される。分岐冷媒管３４ａ〜３４ｄの流入口３６ａ、３６ｂ、３６ｃ、３６ｄには分岐冷媒管３４ａ〜３４ｄごとに個別に連結管３７を介して第１分流器３８が接続される。分岐冷媒管３４ａ〜３４ｄの流出口３９ａ、３９ｂ、３９ｃ、３９ｄには分岐冷媒管３４ａ〜３４ｄごとに個別に連結管４１を介して第２分流器４２が接続される。こうして第１分流器３８および第２分流器４２の間には４本の流路が並列に設けられる。分岐冷媒管３４ａ〜３４ｄは並列に流路を形成する。第２分流器４２は第１分流器３８よりも重力方向に低い位置に配置される。ここでは、「流入口」および「流出口」は、冷房運転時の冷媒の流れに基づき便宜的に名付けられたものであって、暖房運転時には「流入口」から室外熱交換器１６の冷媒は流出し、「流出口」から室外熱交換器１６に冷媒は流入する。 At one end of the outdoor heat exchanger 16, a plurality of hairpin tubes 32 including a pair of upper and lower heat transfer tubes 28 are inserted into the heat transfer fins 27 for each of the heat transfer units 29 a and 29 b. As shown in FIG. 3, at the other end of the outdoor heat exchanger 16, branch refrigerant pipes 34a, 34b, 34c, 34d that constitute four flow paths in the vertical direction based on the connection of the U-shaped pipe 33 that connects the hairpin pipes. And the common refrigerant | coolant pipe | tube 35 in which they merge and become one flow path is formed. Each of the branch refrigerant tubes 34 a to 34 d is composed of a plurality of hairpin tubes 32 including heat transfer tubes 28 extending in the horizontal direction parallel to the bottom plate 26 and a U-shaped tube 33 connecting the hairpin tubes. The first flow divider 38 is connected to the inlets 36a, 36b, 36c, and 36d of the branch refrigerant pipes 34a to 34d via the connecting pipe 37 for each of the branch refrigerant pipes 34a to 34d. The second flow divider 42 is connected to the outlets 39a, 39b, 39c, and 39d of the branch refrigerant pipes 34a to 34d via the connecting pipe 41 individually for each of the branch refrigerant pipes 34a to 34d. Thus, four flow paths are provided in parallel between the first flow divider 38 and the second flow divider 42. The branch refrigerant pipes 34a to 34d form flow paths in parallel. The second flow divider 42 is disposed at a position lower than the first flow divider 38 in the direction of gravity. Here, the “inlet” and “outlet” are named for convenience based on the refrigerant flow during the cooling operation, and the refrigerant of the outdoor heat exchanger 16 is transferred from the “inlet” during the heating operation. The refrigerant flows out and flows into the outdoor heat exchanger 16 from the “outlet”.
第１分流器３８は１つの第１冷媒管４３で圧縮機１５に接続される。第２分流器４２は１つの第２冷媒管４４で膨張弁１７に接続される。第２冷媒管４４は一部に共通冷媒管３５を含む。したがって、第２冷媒管４４は、分岐冷媒管３４ａ〜３４ｄのうち最下方に配置される分岐冷媒管３４ｄ（特定分岐冷媒管）の最下位置よりも下方で室外熱交換器１６内に組み込まれて伝熱フィン２７に結合される。 The first flow divider 38 is connected to the compressor 15 by one first refrigerant pipe 43. The second flow divider 42 is connected to the expansion valve 17 by one second refrigerant pipe 44. The second refrigerant pipe 44 includes a common refrigerant pipe 35 in part. Therefore, the second refrigerant pipe 44 is incorporated into the outdoor heat exchanger 16 below the lowermost position of the branch refrigerant pipe 34d (specific branch refrigerant pipe) disposed at the lowermost position among the branch refrigerant pipes 34a to 34d. To the heat transfer fin 27.
図４に示されるように、上から１番目の分岐冷媒管３４ａは、流入口３６ａから前側の伝熱ユニット２９ａ内で水平方向に往復しながら上方に向かい、後側の伝熱ユニット２９ｂ内で水平方向に往復しながら流出口３９ａまで下降する。分岐冷媒管３４ａの連結管４１は流出口３９ａからさらに下降して第２分流器４２に結合される。 As shown in FIG. 4, the first branch refrigerant pipe 34a from the top is directed upward while reciprocating in the horizontal direction in the front heat transfer unit 29a from the inlet 36a, and in the rear heat transfer unit 29b. It descends to the outlet 39a while reciprocating in the horizontal direction. The connecting pipe 41 of the branch refrigerant pipe 34a is further lowered from the outlet 39a and coupled to the second flow divider 42.
上から２番目の分岐冷媒管３４ｂは、流入口３６ａよりも低い位置に配置される流入口３６ｂから前側の伝熱ユニット２９ａ内で水平方向に往復しながら下降し、後側の伝熱ユニット２９ｂ内で水平方向に往復しながら流出口３９ｂまで上昇する。流出口３９ｂは流出口３９ａよりも低い位置に位置する。分岐冷媒管３４ｂの連結管４１は流出口３９ｂから下降して第２分流器４２に結合される。 The second branch refrigerant pipe 34b from the top descends while reciprocating in the horizontal direction in the front heat transfer unit 29a from the inlet 36b disposed at a position lower than the inlet 36a, and the rear heat transfer unit 29b. Ascending to the outlet 39b while reciprocating in the horizontal direction. The outflow port 39b is located at a position lower than the outflow port 39a. The connecting pipe 41 of the branch refrigerant pipe 34b descends from the outlet 39b and is coupled to the second flow divider 42.
上から３番目の分岐冷媒管３４ｃは、流入口３６ｂよりも低い位置に配置される流入口３６ｃから前側の伝熱ユニット２９ａ内で水平方向に往復しながら上方に向かい、後側の伝熱ユニット２９ｂ内で水平方向に往復しながら流出口３９ｃまで下降する。流出口３９ｃは流出口３９ｂよりも低い位置に位置する。分岐冷媒管３４ｃの連結管４１は流出口３９ｃからさらに下降して第２分流器４２に結合される。 The third branch refrigerant pipe 34c from the top is directed upward while reciprocating in the horizontal direction in the heat transfer unit 29a on the front side from the flow inlet 36c disposed at a position lower than the flow inlet 36b, and is located on the rear heat transfer unit. It descends to the outlet 39c while reciprocating in the horizontal direction in 29b. The outlet 39c is located at a position lower than the outlet 39b. The connecting pipe 41 of the branch refrigerant pipe 34c is further lowered from the outlet 39c and coupled to the second flow divider 42.
最下位置の分岐冷媒管３４ｄは、流入口３６ｃよりも低い位置に配置される流入口３６ｄから前側の伝熱ユニット２９ａ内で水平方向に往復しながら第２分流器４２よりも低い位置まで下降し、後側の伝熱ユニット２９ｂ内で水平方向に往復しながら流出口３９ｄまで上昇する。すなわち、分岐冷媒管３４ｄは第２分流器４２よりも低い位置に流路を形成する。流出口３９ｄは流出口３９ｃよりも低い位置に位置する。分岐冷媒管３４ｄの連結管４１は流出口３９ｄから下降して第２分流器４２に結合される。 The lowermost branch refrigerant pipe 34d descends from the inlet 36d disposed at a position lower than the inlet 36c to a position lower than the second flow divider 42 while reciprocating horizontally in the front heat transfer unit 29a. Then, it moves up to the outlet 39d while reciprocating in the horizontal direction in the rear heat transfer unit 29b. That is, the branch refrigerant pipe 34 d forms a flow path at a position lower than the second flow divider 42. The outflow port 39d is located at a position lower than the outflow port 39c. The connecting pipe 41 of the branch refrigerant pipe 34d descends from the outlet 39d and is coupled to the second flow divider 42.
室外機１３は、分岐冷媒管３４ｄから延びて第２冷媒管４４に接続されるバイパス管４５を備える。バイパス管４５は共通冷媒管３５の流出口４６と膨張弁１７との間で第２冷媒管４４に合流する。バイパス管４５は流出口４６から第２冷媒管４４に向かって下降する。バイパス管４５には逆止弁４７が組み込まれる。逆止弁４７は、分岐冷媒管３４ｄから第２冷媒管４４に向かう冷媒の流通を許容するとともに、第２冷媒管４４から分岐冷媒管３４ｄに向かう冷媒の流通を阻止する。 The outdoor unit 13 includes a bypass pipe 45 extending from the branch refrigerant pipe 34 d and connected to the second refrigerant pipe 44. The bypass pipe 45 joins the second refrigerant pipe 44 between the outlet 46 of the common refrigerant pipe 35 and the expansion valve 17. The bypass pipe 45 descends from the outlet 46 toward the second refrigerant pipe 44. A check valve 47 is incorporated in the bypass pipe 45. The check valve 47 allows the refrigerant to flow from the branch refrigerant pipe 34d to the second refrigerant pipe 44, and prevents the refrigerant from flowing from the second refrigerant pipe 44 to the branch refrigerant pipe 34d.
（３）室外機の動作
次に室外機１３の動作を説明する。冷房運転時には、圧縮機１５から吐出された冷媒が第１分流器３８で分流されて分岐冷媒管３４ａ〜３４ｄに導入される。分岐冷媒管３４ａ〜３４ｄで冷媒は熱エネルギーを放出し液化する。液冷媒は自重によって分岐冷媒管３４ｄからバイパス管４５を通って第２冷媒管４４に流入する。液冷媒は第２分流器４２よりも低い位置にある分岐冷媒管３４ｄ内に留まらずに流通する。ガス冷媒は分岐冷媒管３４ｄの流出口３９ｄから第２分流器４２へ流れる。効率的なエネルギー交換は実現される。分岐冷媒管３４ａ〜３４ｄで液化しきれなかったガス冷媒は第２分流器４２を通過して第２冷媒管４４（共通冷媒管３５）で更に熱エネルギーを放出する。こうして冷媒の液化はさらに促進される。
(3) Operation of outdoor unit Next, the operation of the outdoor unit 13 will be described. During the cooling operation, the refrigerant discharged from the compressor 15 is diverted by the first diverter 38 and introduced into the branch refrigerant tubes 34a to 34d. In the branch refrigerant tubes 34a to 34d, the refrigerant releases heat energy and liquefies. The liquid refrigerant flows from the branch refrigerant pipe 34d through the bypass pipe 45 into the second refrigerant pipe 44 by its own weight. The liquid refrigerant flows without staying in the branch refrigerant pipe 34d located at a position lower than the second flow divider 42. The gas refrigerant flows from the outlet 39d of the branch refrigerant pipe 34d to the second flow divider 42. Efficient energy exchange is realized. The gas refrigerant that has not been liquefied in the branch refrigerant pipes 34a to 34d passes through the second flow divider 42 and further releases thermal energy through the second refrigerant pipe 44 (common refrigerant pipe 35). In this way, liquefaction of the refrigerant is further promoted.
暖房運転時には、膨張弁１７を通過した冷媒が第２冷媒管４４に導入される。冷媒は第２分流器４２で分流されて分岐冷媒管３４ａ〜３４ｄに導入される。分岐冷媒管３４ａ〜３４ｄで冷媒は熱エネルギーを吸収し気化する。ガス冷媒は圧縮機１５に吸い込まれる。 During the heating operation, the refrigerant that has passed through the expansion valve 17 is introduced into the second refrigerant pipe 44. The refrigerant is divided by the second flow divider 42 and introduced into the branch refrigerant pipes 34a to 34d. In the branch refrigerant pipes 34a to 34d, the refrigerant absorbs heat energy and vaporizes. The gas refrigerant is sucked into the compressor 15.
前述のように、バイパス管４５には逆止弁４７が組み込まれるので、冷房運転時にはバイパス管４５を通って第２分流器４２を迂回して分岐冷媒管３４ｄから第２冷媒管４４に液冷媒は流入する。その一方で、暖房運転時には、バイパス管４５は閉じられるので、分岐冷媒管３４ｄには必ず第２分流器４２から二相冷媒は流入する。 As described above, since the check valve 47 is incorporated in the bypass pipe 45, during cooling operation, the liquid refrigerant passes from the branch refrigerant pipe 34d to the second refrigerant pipe 44 through the bypass pipe 45 and bypasses the second flow divider 42. Flows in. On the other hand, since the bypass pipe 45 is closed during heating operation, the two-phase refrigerant always flows from the second flow divider 42 into the branch refrigerant pipe 34d.
本願の他の実施例として、図５に示されるように、最下方の分岐冷媒管３４ｄは、室外熱交換器１６に区画される流入口５１から水平方向に往復しながら重力方向下方に下降する第１下降部５２と、室外熱交換器１６内で第１下降部５２の下端よりも重力方向上方に位置する導入口５３から水平方向に往復しながら重力方向下方に下降する第２下降部５４と、第１下降部５２の流出口５５に第２下降部５４の導入口５３を接続する接続管５６とを備えてもよい。第２下降部５４の流出口５７は第２分流器４２よりも低い位置に位置するものの、液冷媒は第２分流器４２よりも低い位置にある第２下降部５４内に留まらずに流通するため、分岐冷媒管３４ｄを流通するガス冷媒はスムースに第２分流器４２に流れ込むことができる。 As another embodiment of the present application, as shown in FIG. 5, the lowermost branch refrigerant pipe 34 d descends downward in the gravity direction while reciprocating in the horizontal direction from the inlet 51 defined in the outdoor heat exchanger 16. The first descending portion 52 and the second descending portion 54 that descends downward in the gravitational direction while reciprocating in the horizontal direction from the inlet 53 located above the lower end of the first descending portion 52 in the outdoor heat exchanger 16 in the gravitational direction. And a connecting pipe 56 that connects the inlet 53 of the second descending portion 54 to the outlet 55 of the first descending portion 52. Although the outlet 57 of the second descending portion 54 is located at a position lower than the second flow divider 42, the liquid refrigerant flows without staying in the second descending portion 54 located at a position lower than the second flow divider 42. Therefore, the gas refrigerant flowing through the branch refrigerant pipe 34d can smoothly flow into the second flow divider 42.
１１…空気調和機、１５…圧縮機、１６…熱交換器（室外熱交換器）、１７…膨張弁、２７…伝熱フィン、３４ａ…分岐冷媒管、３４ｂ…分岐冷媒管、３４ｃ…分岐冷媒管、３４ｄ…特定分岐冷媒管（分岐冷媒管）、３８…第１分流管、４２…第２分流器、４３…第１冷媒管、４４…第２冷媒管、４５…バイパス管、４７…逆止弁、５１…流入口、５２…第２下降部、５３…導入口、５４…第２下降部。 DESCRIPTION OF SYMBOLS 11 ... Air conditioner, 15 ... Compressor, 16 ... Heat exchanger (outdoor heat exchanger), 17 ... Expansion valve, 27 ... Heat transfer fin, 34a ... Branch refrigerant pipe, 34b ... Branch refrigerant pipe, 34c ... Branch refrigerant Pipe, 34d ... specific branch refrigerant pipe (branch refrigerant pipe), 38 ... first shunt pipe, 42 ... second shunt pipe, 43 ... first refrigerant pipe, 44 ... second refrigerant pipe, 45 ... bypass pipe, 47 ... reverse Stop valve, 51 ... inlet, 52 ... second descending portion, 53 ... inlet port, 54 ... second descending portion.
Claims (3)
前記第１分流器よりも低い位置に配置されて、第２冷媒管で膨張弁に接続される第２分流器と、
前記第１分流器および前記第２分流器の間で並列に流路を形成して伝熱フィンに結合される分岐冷媒管を有する熱交換器と、
前記分岐冷媒管のうち、前記第２分流器よりも低い位置に流路を形成する特定分岐冷媒管、および、前記第２冷媒管を接続するバイパス管と
を備えることを特徴とする空気調和機。 A first shunt connected to the compressor by a first refrigerant pipe;
A second shunt disposed at a position lower than the first shunt and connected to the expansion valve by a second refrigerant pipe;
A heat exchanger having a branch refrigerant pipe coupled in parallel to the heat transfer fin by forming a flow path in parallel between the first flow divider and the second flow divider;
An air conditioner comprising: a specific branch refrigerant pipe that forms a flow path at a position lower than the second shunt of the branch refrigerant pipe; and a bypass pipe that connects the second refrigerant pipe. .
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| WO2022163800A1 (en) * | 2021-01-29 | 2022-08-04 | ダイキン工業株式会社 | Refrigeration cycle device |
| JP2022117023A (en) * | 2021-01-29 | 2022-08-10 | ダイキン工業株式会社 | Refrigeration cycle device |
| JP7125632B2 (en) | 2021-01-29 | 2022-08-25 | ダイキン工業株式会社 | refrigeration cycle equipment |
| CN116829885A (en) * | 2021-01-29 | 2023-09-29 | 大金工业株式会社 | Refrigeration cycle device |
| EP4286768A4 (en) * | 2021-01-29 | 2024-04-03 | Daikin Industries, Ltd. | Refrigeration cycle device |
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