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JP4814907B2 - Refrigeration cycle equipment - Google Patents
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JP4814907B2 - Refrigeration cycle equipment - Google Patents

Refrigeration cycle equipment Download PDF

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JP4814907B2
JP4814907B2 JP2008141009A JP2008141009A JP4814907B2 JP 4814907 B2 JP4814907 B2 JP 4814907B2 JP 2008141009 A JP2008141009 A JP 2008141009A JP 2008141009 A JP2008141009 A JP 2008141009A JP 4814907 B2 JP4814907 B2 JP 4814907B2
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flow path
refrigerant
channel
outlet
refrigerant flow
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JP2009287837A (en
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広 米田
禎夫 関谷
義典 飯塚
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Hitachi Global Life Solutions Inc
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Hitachi Appliances Inc
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Priority to JP2008141009A priority Critical patent/JP4814907B2/en
Priority to CN2009102031164A priority patent/CN101592411B/en
Priority to KR1020090046710A priority patent/KR101120223B1/en
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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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/043—Condensers made by assembling plate-like or laminated elements
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/045—Condensers made by assembling a tube on a plate-like element or between plate-like elements

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Other Air-Conditioning Systems (AREA)

Description

本発明は、冷凍サイクル装置に係り、特に凝縮器を備えた蒸気圧縮式の冷凍サイクル装置に好適なものである。   The present invention relates to a refrigeration cycle apparatus, and is particularly suitable for a vapor compression refrigeration cycle apparatus equipped with a condenser.

蒸気圧縮式の冷凍サイクル装置は、冷媒を圧縮機により圧縮し、圧縮された冷媒の熱を凝縮器により、例えば大気またはその他の媒体中に放熱させて冷媒を凝縮させ、凝縮された冷媒を減圧装置により減圧し、減圧された冷媒を蒸発器で蒸発させることにより、例えば空気や水、不凍液などの媒体を冷却するものである。前記凝縮器では、冷媒は、ガス状態で流入され、凝縮器内で凝縮され、液状態で流出される。そのため、凝縮器の入口と出口とでは、内部の冷媒の密度が大きく異なる。   A vapor compression type refrigeration cycle apparatus compresses refrigerant by a compressor, dissipates heat of the compressed refrigerant into, for example, the atmosphere or other medium by a condenser, condenses the refrigerant, and decompresses the condensed refrigerant. A medium such as air, water, or antifreeze is cooled by reducing the pressure by the apparatus and evaporating the pressure-reduced refrigerant by an evaporator. In the condenser, the refrigerant flows in in a gas state, condenses in the condenser, and flows out in a liquid state. Therefore, the density of the internal refrigerant differs greatly between the inlet and the outlet of the condenser.

このような冷凍サイクル装置として、図７に示すような室外熱交換器３を凝縮器に用いる冷凍サイクル装置がある（従来技術１）。この室外熱交換器３は、複数の冷媒流路３ａ〜３ｆで構成されている。第１冷媒流路３ａは入口部３ａ１から出口部３ａ２に至る流路で構成され、第２冷媒流路３ｂは入口部３ｂ１から出口部３ｂ２に至る流路で構成され、第３冷媒流路３ｃは入口部３ｃ１から出口部３ｃ２に至る流路で構成され、第４冷媒流路３ｄは入口部３ｄ１から出口部３ｄ２に至る流路で構成され、第５冷媒流路３ｅは入口部３ｅ１から出口部３ｅ２に至る流路で構成され、第６冷媒流路３ｆは入口部３ｆ１から出口部３ｆ２に至る流路で構成されている。 As such a refrigeration cycle apparatus, there is a refrigeration cycle apparatus using an outdoor heat exchanger 3 as shown in FIG. 7 as a condenser (prior art 1). The outdoor heat exchanger 3 includes a plurality of refrigerant channels 3a to 3f. The first refrigerant flow path 3a is composed of a flow path from the inlet part 3a1 to the outlet part 3a2, and the second refrigerant flow path 3b is composed of a flow path from the inlet part 3b1 to the outlet part 3b2, and the third refrigerant flow path 3c. consists of a flow path to the inlet portion 3c 1 or et outlet 3c2, fourth refrigerant passage 3d is composed of a channel from the inlet portion 3d1 to the outlet portion 3d2, a fifth coolant flow path 3e is inlet 3e1 The sixth refrigerant flow path 3f is composed of a flow path from the inlet section 3f1 to the outlet section 3f2.

室外熱交換器３の冷媒配管１１から流入するガス状冷媒は、分流器１２ａ〜１２ｃを経て４分配され、第１〜第４冷媒流路３ａ〜３ｄに流入され、外部に熱を放出し凝縮が行われる。第１〜第４冷媒流路３ａ〜３ｄの出口部３ａ２〜３ｄ２においては、冷媒は凝縮が終了し、液状冷媒になっている。そして、第１冷媒流路３ａと第２冷媒流路３ｂから流出された液冷媒は、分流器１３にて合流され、第５冷媒流路３ｅに流れ込み、更に外部に放熱する。また、第３冷媒流路３ｃと第４冷媒流路３ｄから流出された液冷媒は、分流器１４にて合流され、第６冷媒流路３ｆに流れ込み、更に外部に放熱する。そして、第５冷媒流路３ｅ、第６冷媒流路３ｆの出口部３ｅ２、３ｆ２から流出された液冷媒は、分流器１５にて合流され、冷媒配管１１に流出される。   The gaseous refrigerant flowing from the refrigerant pipe 11 of the outdoor heat exchanger 3 is divided into four through the flow dividers 12a to 12c, flows into the first to fourth refrigerant flow paths 3a to 3d, and releases heat to condense. Is done. In the outlet portions 3a2 to 3d2 of the first to fourth refrigerant flow paths 3a to 3d, the refrigerant has finished condensing and is a liquid refrigerant. Then, the liquid refrigerant flowing out from the first refrigerant flow path 3a and the second refrigerant flow path 3b is merged by the flow divider 13, flows into the fifth refrigerant flow path 3e, and further radiates heat to the outside. The liquid refrigerant that has flowed out of the third refrigerant channel 3c and the fourth refrigerant channel 3d is merged by the flow divider 14, flows into the sixth refrigerant channel 3f, and further radiates heat to the outside. Then, the liquid refrigerant that has flowed out from the outlet portions 3e2 and 3f2 of the fifth refrigerant flow path 3e and the sixth refrigerant flow path 3f is merged by the flow divider 15 and flows out to the refrigerant pipe 11.

一方、空気調和機用熱交換器として、特開平１０−２６７４６９号公報（特許文献１）に示されたものがある（従来技術２）。この従来技術２では、蒸発器として用いられる熱交換器を複数の並列の冷媒流路で構成し、各冷媒流路に設けられた細管部の長さを変えることで、各冷媒流路の圧力損失を調整し、冷媒の偏流を防止するようにしている。   On the other hand, as a heat exchanger for an air conditioner, there is one disclosed in Japanese Patent Laid-Open No. 10-267469 (Patent Document 1) (Prior Art 2). In this prior art 2, the heat exchanger used as an evaporator is constituted by a plurality of parallel refrigerant flow paths, and the lengths of the narrow tubes provided in the respective refrigerant flow paths are changed, whereby the pressure of each refrigerant flow path is changed. The loss is adjusted to prevent refrigerant drift.

特開平１０−２６７４６９号公報（第７頁、図５）JP-A-10-267469 (page 7, FIG. 5)

従来技術１の室外熱交換器３では、内部の冷媒密度が大きい出口部３ａ２〜３ｄ２の空間的高さが第１〜第４冷媒流路３ａ〜３ｄで違うため、各出口部３ａ２〜３ｄ２では、高さの差と内部の冷媒の密度、及び重力に起因する圧力の差、すなわちヘッド差による圧力の差が生ずる。そのため、各出口部３ａ２〜３ｄ２の内部の冷媒の圧力は、高さの最も高い出口部３ａ２が最も低く、高さの最も低い出口部３ｄ２が最も高い。   In the outdoor heat exchanger 3 of the prior art 1, the spatial heights of the outlet portions 3a2 to 3d2 having a large internal refrigerant density are different in the first to fourth refrigerant flow paths 3a to 3d. The difference in height and the density of the refrigerant inside, and the pressure difference due to gravity, that is, the pressure difference due to the head difference occurs. Therefore, the pressure of the refrigerant inside each of the outlet portions 3a2 to 3d2 is the lowest at the highest outlet portion 3a2 and the highest at the lowest outlet portion 3d2.

なお、第１〜第４冷媒流路３ａ〜３ｄの入口部３ａ１〜３ｄ１においても、空間的高さの違いに伴う内部の冷媒の圧力に差異があるが、入口部では、冷媒の状態がガス状態であり、液体に比べ密度が小さいため、出口部に比べてその圧力の差異は小さい。   In addition, in the inlet portions 3a1 to 3d1 of the first to fourth refrigerant flow paths 3a to 3d, there is a difference in the pressure of the internal refrigerant due to the difference in spatial height, but in the inlet portion, the state of the refrigerant is gas. Since the density is smaller than that of the liquid, the pressure difference is smaller than that of the outlet portion.

そのため、空間的に上方に存在する冷媒流路は、冷媒流路の入口と出口の圧力差が大きくなる。流路の内部の冷媒は、流路の入口と出口との圧力差を駆動力として流動するため、上方に存在する冷媒流路に流れる冷媒の流量が大きくなりやすい。   Therefore, the refrigerant flow path that exists spatially upward has a large pressure difference between the inlet and the outlet of the refrigerant flow path. Since the refrigerant inside the flow channel flows using the pressure difference between the inlet and the outlet of the flow channel as a driving force, the flow rate of the refrigerant flowing through the refrigerant flow channel existing above tends to increase.

このように冷媒の偏流が起こると、各冷媒流路３ａ〜３ｄでの交換熱量にばらつきが発生するため、有効に利用できる熱交換器の伝熱面積が減少する。有効伝熱面積の減少は、冷媒の凝縮圧力を増大させ、冷媒の圧縮動力を増加させるので、冷凍サイクルの運転時のエネルギー消費を増大させてしまう。従って、従来技術１では、省エネルギー性が低下してしまう、という問題を有していた。   When the refrigerant drifts as described above, the amount of heat exchanged in the refrigerant flow paths 3a to 3d varies, and the heat transfer area of the heat exchanger that can be used effectively is reduced. The reduction in the effective heat transfer area increases the condensation pressure of the refrigerant and increases the compression power of the refrigerant, thereby increasing the energy consumption during the operation of the refrigeration cycle. Therefore, the prior art 1 has a problem that the energy saving performance is lowered.

一方、従来技術２では、冷媒流路に圧力損失を付加するため、圧縮機の仕事が増大し、省エネルギー性が低下してしまう、という問題を有していた。   On the other hand, in the prior art 2, since pressure loss is added to the refrigerant flow path, there is a problem that the work of the compressor is increased and energy saving performance is reduced.

本発明の目的は、並列する複数の冷媒流路での冷媒の偏流を抑制し、省エネルギー性に優れた冷凍サイクル装置を提供することを目的とする。   An object of the present invention is to provide a refrigeration cycle apparatus that suppresses refrigerant drift in a plurality of refrigerant flow paths arranged in parallel and is excellent in energy saving.

前述の目的を達成するための本発明の態様では、圧縮機、凝縮器、減圧装置及び蒸発器を順次冷媒配管で接続してサイクル流路を構成し、前記凝縮器は、複数の冷媒流路を形成する第１冷媒流路、第２冷媒流路、第３冷媒流路及び第４冷媒流路が並列に接続されると共に、上下に位置して設けられている冷凍サイクル装置において、前記凝縮器の入口側が最も上に位置する前記第１冷媒流路における運転時に内部の冷媒が液状態となる第１流路出口部を、当該凝縮器の入口側が前記第１冷媒流路の入口側よりもそれぞれ下に位置する前記第２冷媒流路、前記第３冷媒流路及び前記第４冷媒流路における運転時に内部の冷媒が液状態となる第２流路出口部、第３流路出口部及び第４流路出口部よりも下側に位置させると共に、前記凝縮器の入口側が２番目に高い前記第２冷媒流路の前記第２流路出口部を前記第３流路出口部及び前記第４流路出口部よりも下側に位置させ、前記凝縮器の入口側が上に位置する前記冷媒流路の流路出口側を前記凝縮器の入口側が下に位置する前記冷媒流路の流路出口側よりも上側に位置させた場合における流路出口側の高さの差よりも、前記凝縮器の複数の冷媒流路における運転時の内部の冷媒が液状態となる流路出口側の高さの差が小さくなるように当該複数の冷媒流路が構成され、前記凝縮器は伝熱管及びフィンからなるクロスフィンチューブ型熱交換器で構成され、前記凝縮器の複数の冷媒流路のうちの空間的に最も高い位置の入口側伝熱管を含む前記第１冷媒流路は、第１中間パイプを介して、第１上流流路と第１下流流路とに空間的に分離されて配置されており、前記第１上流流路は前記第２冷媒流路、前記第３冷媒流路及び前記第４冷媒流路より高い位置に配置されており、前記第１下流流路は前記上流流路、前記第３冷媒流路及び前記第４冷媒流路よりも低い位置に配置されており、前記第１上流流路と前記第１下流流路とを接続する前記第１中間パイプ内の冷媒状態が気液二相で前記第１流路出口部が液状態となるように運転されると共に、前記第２冷媒流路は、第２中間パイプを介して、第２上流流路と第２下流流路とに空間的に分離されて配置されており、前記第２上流流路は前記第３冷媒流路及び前記第４冷媒流路より高い位置に配置されており、前記第２下流流路は前記第２上流流路、前記第３冷媒流路及び前記第４冷媒流路よりも低い位置に配置されており、前記圧縮機から吐出される冷媒の流れ方向及び当該圧縮機へ吸入される冷媒の流れ方向を切り替える切替弁を備え、前記凝縮器が室外熱交換器で構成され前記蒸発器が室内熱交換器で構成され、前記第１冷媒流路、前記第２冷媒流路、前記第３冷媒流路及び前記第４冷媒流路はそれぞれ前記第１流路出口部、前記第２流路出口部、前記第３流路出口部及び前記第４流路出口部までは何れの冷媒流路とも合流せずにそれぞれ１本の流路で構成され、前記第１流路出口部、前記第２流路出口部、前記第３流路出口部及び前記第４流路出口部の下流側で前記第１冷媒流路、前記第２冷媒流路、前記第３冷媒流路及び前記第４冷媒流路が合流するように構成したことにある。 In an aspect of the present invention for achieving the above-described object, a compressor, a condenser, a decompression device, and an evaporator are sequentially connected by a refrigerant pipe to form a cycle flow path, and the condenser includes a plurality of refrigerant flow paths. In the refrigeration cycle apparatus in which the first refrigerant flow path, the second refrigerant flow path, the third refrigerant flow path, and the fourth refrigerant flow path are formed in parallel and connected to each other in the vertical direction. vessels inside the refrigerant during operation in said first refrigerant flow path inlet side is located on the most of the first flow path outlet portion serving as a liquid state, the inlet side of the condenser inlet side of the first coolant channel the second refrigerant flow also located under each of the second flow path outlet portion inside of the refrigerant becomes a liquid state during operation in the third refrigerant flow path and the fourth refrigerant flow path, a third flow passage outlet and fourth channel outlet is located below the portion Rutotomoni, the inlet of the condenser There is positioned lower than the said second flow path outlet portion of the second highest second refrigerant passage third channel outlet and the fourth flow path outlet portion, the condenser inlet side upper The height difference on the channel outlet side when the channel outlet side of the refrigerant channel located at the upper side is positioned above the channel outlet side of the refrigerant channel located below the condenser inlet side Rather, the plurality of refrigerant flow paths are configured so that the difference in height on the flow path outlet side where the refrigerant inside the plurality of refrigerant flow paths of the condenser is in a liquid state becomes smaller. The first refrigerant flow path includes a heat transfer tube and a cross fin tube type heat exchanger composed of fins, and includes an inlet-side heat transfer pipe at a spatially highest position among the plurality of refrigerant flow paths of the condenser. via a first intermediate pipe, it is spatially separated into a first upstream passage and the first downstream flow path Are arranged Te, the first upstream passage and the second refrigerant flow path, the third is arranged in a position higher than the coolant flow path and the fourth refrigerant flow path, the first downstream flow path wherein In the first intermediate pipe, which is disposed at a position lower than the upstream flow path , the third refrigerant flow path, and the fourth refrigerant flow path, and connects the first upstream flow path and the first downstream flow path. refrigerant state is operated such that the first flow path outlet portion in the gas-liquid two-phase becomes a liquid state of Rutotomoni, the second refrigerant flow path through the second intermediate pipe, and a second upstream channel The second upstream flow path is disposed so as to be spatially separated from the second downstream flow path, and the second upstream flow path is disposed at a position higher than the third refrigerant flow path and the fourth refrigerant flow path. The downstream flow path is disposed at a position lower than the second upstream flow path, the third refrigerant flow path, and the fourth refrigerant flow path. A switching valve that switches a flow direction of refrigerant discharged from the compressor and a flow direction of refrigerant sucked into the compressor, the condenser is configured by an outdoor heat exchanger, and the evaporator is configured by an indoor heat exchanger The first refrigerant channel , the second refrigerant channel , the third refrigerant channel, and the fourth refrigerant channel are respectively the first channel outlet , the second channel outlet , and the third until the passage outlet portion and the fourth flow path outlet portion are each composed of one channel without merging with any of the coolant channel, the first flow path outlet portion, the second flow path outlet portion The first refrigerant flow path , the second refrigerant flow path , the third refrigerant flow path, and the fourth refrigerant flow path merge downstream of the third flow path outlet and the fourth flow path outlet. It is in the configuration.

本発明によれば、並列する複数の冷媒流路での冷媒の偏流を抑制し、省エネルギー性に優れた冷凍サイクル装置を提供することができる。   ADVANTAGE OF THE INVENTION According to this invention, the drift of the refrigerant | coolant in the some refrigerant | coolant flow path in parallel can be suppressed, and the refrigeration cycle apparatus excellent in energy saving property can be provided.

以下、本発明の複数の実施形態について図１から図６を用いて説明する。各実施形態及び従来例の図における同一符号は同一物または相当物を示す。   Hereinafter, a plurality of embodiments of the present invention will be described with reference to FIGS. The same reference numerals in the drawings of each embodiment and the conventional example indicate the same or equivalent.

（第１実施形態）
本発明の第１実施形態の冷凍サイクル装置１０を備えた空気調和機２０を図１から図５を用いて説明する。 (First embodiment)
An air conditioner 20 including a refrigeration cycle apparatus 10 according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 5.

まず、本実施形態の空気調和機２０の全体に関して図１を参照しながら説明する。図１は本発明の第１実施形態の冷凍サイクル装置１０を備えた空気調和機２０の構成図である。   First, the entire air conditioner 20 of the present embodiment will be described with reference to FIG. FIG. 1 is a configuration diagram of an air conditioner 20 including a refrigeration cycle apparatus 10 according to a first embodiment of the present invention.

空気調和機２０は、室外機８と室内機９とからなる分離型の空気調和機であり、冷凍サイクル装置１０、室外ファン装置６及び室内ファン装置７等を備えて構成されている。   The air conditioner 20 is a separation-type air conditioner composed of an outdoor unit 8 and an indoor unit 9, and includes a refrigeration cycle device 10, an outdoor fan device 6, an indoor fan device 7, and the like.

冷凍サイクル装置１０は、圧縮機１、四方切替弁２、室外熱交換器３、減圧装置４、室内熱交換器５を冷媒配管１１で順次接続してサイクル流路を構成している。冷凍サイクル装置１０の内部には冷媒が封入されており、本実施形態では冷媒Ｒ４１０Ａが封入されているが、その他の冷媒、例えばアンモニアや炭化水素、二酸化炭素等の冷媒を用いても構わない。   In the refrigeration cycle apparatus 10, a compressor 1, a four-way switching valve 2, an outdoor heat exchanger 3, a pressure reducing apparatus 4, and an indoor heat exchanger 5 are sequentially connected by a refrigerant pipe 11 to constitute a cycle flow path. A refrigerant is sealed inside the refrigeration cycle apparatus 10, and in the present embodiment, the refrigerant R410A is sealed. However, other refrigerants such as ammonia, hydrocarbons, carbon dioxide, and the like may be used.

室外機８には、圧縮機１、四方切替弁２、室外熱交換器３、減圧装置４、室外ファン装置６、圧縮機駆動装置、温度センサ、各要素を接続する配管や電気配線などが搭載されている。   The outdoor unit 8 is equipped with a compressor 1, a four-way switching valve 2, an outdoor heat exchanger 3, a pressure reducing device 4, an outdoor fan device 6, a compressor driving device, a temperature sensor, piping for connecting each element, electric wiring, and the like. Has been.

室内機９には、室内熱交換器５、室内ファン装置７、温度センサ、各要素を接続する配管や電気配線などが搭載されている。   The indoor unit 9 is equipped with an indoor heat exchanger 5, an indoor fan device 7, a temperature sensor, piping for connecting each element, electrical wiring, and the like.

冷房運転時に四方切替弁２が実線に示すように切り替えられることにより、室外熱交換器３を凝縮器として機能させると共に、室内熱交換器５を蒸発器として機能させる冷房サイクルの冷凍サイクル装置１０が構成される。また、暖房運転時に四方切替弁２が破線に示すように切り替えられることにより、室内熱交換器５を凝縮器として機能させると共に、室外熱交換器３を蒸発器として機能させる暖房サイクルの冷凍サイクル装置１０が構成される。   By switching the four-way switching valve 2 as indicated by a solid line during the cooling operation, the refrigeration cycle apparatus 10 for the cooling cycle that causes the outdoor heat exchanger 3 to function as a condenser and the indoor heat exchanger 5 to function as an evaporator is provided. Composed. In addition, when the four-way switching valve 2 is switched as indicated by the broken line during heating operation, the indoor heat exchanger 5 functions as a condenser and the outdoor heat exchanger 3 functions as an evaporator. 10 is configured.

室外ファン装置６は、室外ファン６ａと、これを駆動するモータ６ｂとからなっている。室外熱交換器３では、室外ファン６ａの回転により通風される室外空気と、内部を流れる冷媒とが熱交換される。また、室内ファン装置７は、室内ファン７ａと、これを駆動するモータ７ｂとからなっている。室内熱交換器５では、室内ファン７ａの回転により通風される室内空気と、内部を流れる冷媒とが熱交換される。 Chamber outside the fan unit 6 is composed of an outdoor fan 6 a, a motor 6b for driving the same. In the outdoor heat exchanger 3, and the outside air which is ventilated by rotation of the outdoor fan 6 a, the refrigerant flowing through the inside is heat-exchanged. The indoor fan device 7 is composed of the indoor fan 7 a, a motor 7b for driving the same. In the indoor heat exchanger 5, the indoor air is ventilated by rotation of the indoor fan 7 a and the refrigerant flowing through the inside is heat-exchanged.

係る構成にて、圧縮機１、室外ファン装置６、室内ファン装置７が駆動されると、冷凍サイクル装置１０の内部の冷媒がサイクル内を循環し、冷凍サイクルとして機能する。すなわち、冷房運転時において、冷媒は、圧縮機１にて圧縮されて高温高圧のガス状冷媒となり、四方切替弁２を通して室外熱交換器３に流入される。室外熱交換器３では、内部の冷媒が室外空気によって冷却され、徐々にガスから液へと状態を変え、室外熱交換器３の出口では冷媒が全て液状になる。この場合、室外熱交換器３は凝縮器として機能している。室外熱交換器３を出た高圧の液状冷媒は、減圧装置４で減圧され、ガスと液の混ざった、いわゆる気液二相状態となる。減圧装置４にて気液二相となった冷媒は、さらに室内熱交換器５に流入され、室内空気から熱を奪い、冷媒自身は気液二相状態からガス状態へと変化する。この場合、室内熱交換器５は蒸発器として機能している。室内熱交換器５を出たガス状冷媒は圧縮機１に戻り、冷房サイクルが形成される。 In this configuration, when the compressor 1, the outdoor fan device 6, and the indoor fan device 7 are driven, the refrigerant inside the refrigeration cycle device 10 circulates in the cycle and functions as a refrigeration cycle. That is, during the cooling operation, the refrigerant is compressed by the compressor 1 to become a high-temperature and high-pressure gaseous refrigerant, and flows into the outdoor heat exchanger 3 through the four-way switching valve 2. In the outdoor heat exchanger 3, the internal refrigerant is cooled by the outdoor air, and gradually changes its state from gas to liquid, and all the refrigerant becomes liquid at the outlet of the outdoor heat exchanger 3. In this case, the outdoor heat exchanger 3 functions as a condenser. The high-pressure liquid refrigerant exiting the outdoor heat exchanger 3 is depressurized by the decompression device 4 and becomes a so-called gas-liquid two-phase state in which gas and liquid are mixed. The refrigerant that has become a gas-liquid two-phase in the decompression device 4 further flows into the indoor heat exchanger 5, takes heat from the indoor air, and the refrigerant itself changes from the gas-liquid two-phase state to the gas state. In this case, the indoor heat exchanger 5 functions as an evaporator. The gaseous refrigerant that has exited the indoor heat exchanger 5 returns to the compressor 1 to form a cooling cycle.

尚、四方切替弁２を破線のように切り替えることにより、冷媒の流れ方向が変更され、室内熱交換器５が凝縮器として機能し、また、室外熱交換器３が蒸発器として機能することで、暖房サイクルが形成される。   By switching the four-way switching valve 2 as indicated by the broken line, the refrigerant flow direction is changed, the indoor heat exchanger 5 functions as a condenser, and the outdoor heat exchanger 3 functions as an evaporator. A heating cycle is formed.

次に、図２から図５を参照しながら、冷房サイクル時の凝縮器、すなわち室外熱交換器３に本発明を適用する場合について詳しく説明する。   Next, the case where the present invention is applied to the condenser during the cooling cycle, that is, the outdoor heat exchanger 3, will be described in detail with reference to FIGS.

図２は図１の空気調和機２０の室外熱交換器３の基本構成要素を分解して示す図である。室外熱交換器３は、複数枚並置されたアルミニウム製のフィン３１と、このフィン３１を貫通して蛇行状に延びる銅製の伝熱管３２と、からなるクロスフィンチューブ型熱交換器で構成されている。図２では、室外熱交換器３の基本構成要素を部分的に示している。   FIG. 2 is an exploded view showing basic components of the outdoor heat exchanger 3 of the air conditioner 20 of FIG. The outdoor heat exchanger 3 is configured by a cross fin tube heat exchanger including a plurality of aluminum fins 31 juxtaposed and a copper heat transfer pipe 32 extending through the fins 31 in a meandering manner. Yes. In FIG. 2, the basic components of the outdoor heat exchanger 3 are partially shown.

伝熱管３２は、複数枚のフィン３１を貫通する複数のＵ字型の伝熱管３２ａと、この伝熱管３２ａの端部３２ａ１に溶接されて伝熱管３２ａと共に蛇行状の冷媒流路を形成する配管部品であるリターンパイプ３２ｂとから構成されている。蛇行状に延びる伝熱管３２は上下に多段の冷媒流路を形成している。そして、室外熱交換器３は、図２に示す熱交換器要素を空気の流れ方向に２つ重ねて配置する、いわゆる２列の熱交換器になっている。   The heat transfer tube 32 includes a plurality of U-shaped heat transfer tubes 32a penetrating the plurality of fins 31, and a pipe welded to the end portion 32a1 of the heat transfer tube 32a to form a meandering refrigerant flow path together with the heat transfer tubes 32a. It consists of a return pipe 32b which is a part. The heat transfer tube 32 extending in a meandering manner forms a multistage refrigerant flow path vertically. The outdoor heat exchanger 3 is a so-called two-row heat exchanger in which two heat exchanger elements shown in FIG. 2 are stacked in the air flow direction.

このような室外熱交換器３では、伝熱管３２ｂの外側を流れる空気は、伝熱管３２ａの管軸に交差する方向、すなわち、フィン３１間の隙間に沿って流れる。   In such an outdoor heat exchanger 3, the air flowing outside the heat transfer tube 32 b flows along the direction intersecting the tube axis of the heat transfer tube 32 a, that is, along the gap between the fins 31.

図３は図１の空気調和機１０の室外機８の透視図である。室外熱交換器３は、略Ｌ字状に曲げられて形成され、室外ファン６ａの吸込み側に配置されている。なお、図２では、簡略のために、室外熱交換器３の伝熱管３２を１つの冷媒流路として表わしてあるが、実際には図４に示すような複数の冷媒流路からなっている。   FIG. 3 is a perspective view of the outdoor unit 8 of the air conditioner 10 of FIG. The outdoor heat exchanger 3 is bent and formed in a substantially L shape, and is disposed on the suction side of the outdoor fan 6a. In FIG. 2, for the sake of simplicity, the heat transfer tube 32 of the outdoor heat exchanger 3 is shown as one refrigerant flow path, but actually includes a plurality of refrigerant flow paths as shown in FIG. 4. .

図４は図１の空気調和機１０の室外熱交換器３における配管部品が取り付けられたる側から見た側面図、図５は図４の室外熱交換器の冷媒流路を模式的に表わす図である。室外熱交換器３は、複数の冷媒流路である第１〜第６冷媒流路３ａ〜３ｆを備えて構成されている。   4 is a side view of the outdoor heat exchanger 3 of the air conditioner 10 shown in FIG. 1 as viewed from the side where piping components are attached, and FIG. 5 is a diagram schematically showing the refrigerant flow path of the outdoor heat exchanger of FIG. It is. The outdoor heat exchanger 3 includes first to sixth refrigerant channels 3a to 3f that are a plurality of refrigerant channels.

第１冷媒流路３ａは入口部３ａ１から出口部３ａ２に至る流路で構成され、第２冷媒流路３ｂは入口部３ｂ１から出口部３ｂ２に至る流路で構成され、第３冷媒流路３ｃは入口部３ｃ１から出口部３ｃ２に至る流路で構成され、第４冷媒流路３ｄは入口部３ｄ１から出口部３ｄ２に至る流路で構成され、第５冷媒流路３ｅは入口部３ｅ１から出口部３ｅ２に至る流路で構成され、第６冷媒流路３ｆは入口部３ｆ１から出口部３ｆ２に至る流路で構成されている。   The first refrigerant flow path 3a is composed of a flow path from the inlet part 3a1 to the outlet part 3a2, and the second refrigerant flow path 3b is composed of a flow path from the inlet part 3b1 to the outlet part 3b2, and the third refrigerant flow path 3c. Is composed of a channel from the inlet 3c1 to the outlet 3c2, the fourth refrigerant channel 3d is composed of a channel from the inlet 3d1 to the outlet 3d2, and the fifth refrigerant channel 3e is from the inlet 3e1 to the outlet. The sixth refrigerant channel 3f is configured by a channel from the inlet 3f1 to the outlet 3f2.

第１〜第４冷媒流路３ａ〜３ｄの入口部３ａ１〜３ｄ１は、室外熱交換器３の第１列側にこの順の高さ位置に設けられると共に、分流器１２を介して冷媒配管１１に接続されている。つまり、冷媒配管１１による冷媒流路は、分流器１２を介して、第１〜第４冷媒流路３ａ〜３ｄへ分岐されている。分流器１２は、室外熱交換器３の高さ方向に沿って延び、冷媒配管１１及び第１〜第４冷媒流路３ａ〜３ｄより大きな流路断面積を有している。 The inlet portions 3 a 1 to 3 d 1 of the first to fourth refrigerant flow paths 3 a to 3 d are provided at the height positions in this order on the first row side of the outdoor heat exchanger 3, and the refrigerant pipe 11 via the flow divider 12. It is connected to the. That is, the refrigerant flow path by the refrigerant pipe 11 via the flow divider 1 2, is branched into the first to fourth refrigerant flow path 3 a to 3 d. The flow divider 12 extends along the height direction of the outdoor heat exchanger 3, and has a larger flow path cross-sectional area than the refrigerant pipe 11 and the first to fourth refrigerant flow paths 3a to 3d.

第１〜第２冷媒流路３ａ〜３ｂは、並列に接続されると共に、上下に多段に設けられている。第３〜第４冷媒流路３ｃ〜３ｄは、並列に接続されると共に、上下に多段に設けられている。従って、第１〜第４冷媒流路３ａ〜３ｄは並列流路を構成している。   The first to second refrigerant flow paths 3a to 3b are connected in parallel and provided in multiple stages in the vertical direction. The third to fourth refrigerant flow paths 3c to 3d are connected in parallel and provided in multiple stages in the vertical direction. Therefore, the 1st-4th refrigerant flow paths 3a-3d comprise the parallel flow path.

第１冷媒流路３ａは、中間パイプ３ａ４を介して、上流流路３ａ３と下流流路３ａ５とに空間的に分離されて配置されている。また、第２冷媒流路３ｂは、中間パイプ３ｂ４を介して、上流流路３ｂ３と下流流路３ｂ５とに空間的に分離されて配置されている。第１冷媒流路３ａの上流流路３ａ３は、１列目が４段、２列目が４段の合計８段で形成され、２列目の２段で形成された下流流路３ａ５よりも長く形成されている。第２冷媒流路３ｂの上流流路３ｂ３は、１列目が６段、２列目が２段の合計８段で形成され、２列目の２段で形成された下流流路３ａ５よりも長く形成されている。   The first refrigerant flow path 3a is spatially separated into an upstream flow path 3a3 and a downstream flow path 3a5 via an intermediate pipe 3a4. The second refrigerant flow path 3b is spatially separated into the upstream flow path 3b3 and the downstream flow path 3b5 via the intermediate pipe 3b4. The upstream flow path 3a3 of the first refrigerant flow path 3a is formed by a total of 8 stages in which the first row has four stages and the second row has four stages, and the downstream flow path 3a5 formed by the second stage in the second row. It is formed long. The upstream flow path 3b3 of the second refrigerant flow path 3b is formed by a total of 8 stages, the first row being 6 stages, the second row being 2 stages, and the downstream flow path 3a5 being formed by 2 stages of the second row. It is formed long.

第３冷媒流路３ｃは、１列目が４段、２列目が６段の合計１０段で形成されている。第４冷媒流路３ｄは、１列目が６段、２列目が４段の合計１０段で形成されている。   The third refrigerant flow path 3c is formed with a total of 10 stages in which the first row has four stages and the second row has six stages. The fourth refrigerant flow path 3d is formed with a total of 10 stages in which the first row has six stages and the second row has four stages.

第５冷媒流路３ｅは、第１〜第２冷媒流路３ａ〜３ｂの並列流路と直列に接続されている。第６冷媒流路３ｆは、第３〜第４冷媒流路３ｃ〜３ｄの並列流路と直列に接続されている。従って、第５〜第６冷媒流路３ｅ〜３ｆは並列流路を構成し、第１〜第６冷媒流路３〜３ｆは直並列流路を構成している。第５冷媒流路３ｅは１列目に形成された２段で構成され、第６冷媒流路３ｄは２列目に形成された２段で構成されている。   The fifth refrigerant channel 3e is connected in series with the parallel channel of the first to second refrigerant channels 3a to 3b. The sixth refrigerant flow path 3f is connected in series with the parallel flow paths of the third to fourth refrigerant flow paths 3c to 3d. Accordingly, the fifth to sixth refrigerant flow paths 3e to 3f constitute a parallel flow path, and the first to sixth refrigerant flow paths 3 to 3f constitute a series-parallel flow path. The fifth refrigerant flow path 3e is constituted by two stages formed in the first row, and the sixth refrigerant flow path 3d is constituted by two stages formed in the second row.

第１冷媒流路３ａの上流流路３ａ３、第２冷媒流路３ｂの上流流路３ｂ３、第３冷媒流路３ｃ及び第４冷媒流路３ｄは、上からこの順に設けられている。すなわち、第１冷媒流路３ａの上流流路３ａ３は室外熱交換器３の最上部の位置に設けられ、第２冷媒流路３ｂの上流流路３ｂ３は第１冷媒流路３ａの上流流路３ａ３の下側で且つ室外熱交換器３の２番目の高さ位置に設けられ、第３冷媒流路３ｃは第２冷媒流路３ｂの上流流路の下側で且つ室外熱交換器３の３番目の高さ位置に設けられ、第４冷媒流路３ｄは第３冷媒流路３ｃの下側で且つ室外熱交換器３の４番目の高さ位置に設けられている。   The upstream flow path 3a3 of the first refrigerant flow path 3a, the upstream flow path 3b3 of the second refrigerant flow path 3b, the third refrigerant flow path 3c, and the fourth refrigerant flow path 3d are provided in this order from the top. That is, the upstream flow path 3a3 of the first refrigerant flow path 3a is provided at the uppermost position of the outdoor heat exchanger 3, and the upstream flow path 3b3 of the second refrigerant flow path 3b is the upstream flow path of the first refrigerant flow path 3a. 3 a 3 is provided at the second height position of the outdoor heat exchanger 3, and the third refrigerant channel 3 c is below the upstream channel of the second refrigerant channel 3 b and of the outdoor heat exchanger 3. The fourth refrigerant flow path 3d is provided at the third height position, and is provided below the third refrigerant flow path 3c and at the fourth height position of the outdoor heat exchanger 3.

また、第１冷媒流路３ａの下流流路３ａ５は、第２冷媒流路３ｂの下流流路３ｂ５より下側に位置されている。これらの第１冷媒流路３ａの下流流路３ａ５、第２冷媒流路３ｂの下流流路３ｂ５は、第４冷媒流路３ｄの１列目の冷媒流路の空気上流側の２列目に位置して設けられている。さらに、第１冷媒流路３ａの下流流路３ａ５、第２冷媒流路３ｂの下流流路３ｂ５は、第３冷媒流路３ｃの出口部３ｃ２、第４冷媒流路３ｄの出口部３ｄ２よりも下方に位置されていると共に、第５冷媒流路３ｅ、第６冷媒流路３ｆよりも上側に位置されている。 Further, the downstream flow path 3a5 of the first refrigerant flow path 3a is positioned below the downstream flow path 3b5 of the second refrigerant flow path 3b. Downstream passage 3a5 of the first refrigerant passage 3a, the downstream channel 3b5 of the second refrigerant flow path 3b is the second column of the fourth refrigerant flow path 3 1 row air upstream side of the coolant channel of the d It is provided in the position. Furthermore, the downstream flow path 3a5 of the first refrigerant flow path 3a and the downstream flow path 3b5 of the second refrigerant flow path 3b are more than the outlet part 3c2 of the third refrigerant flow path 3c and the outlet part 3d2 of the fourth refrigerant flow path 3d. It is located below and is located above the fifth refrigerant channel 3e and the sixth refrigerant channel 3f.

以上のような室外熱交換器３を用い、中間パイプ３ａ４、３ｂ４内の冷媒が気液二相状態となり、第１〜第４冷媒流路３ａ〜３ｄの出口部３ａ２〜３ｄ２が液状態となるように、冷媒封入量、圧縮機１の回転速度、室外ファン６ａの回転速度、室内ファン７ａの回転速度、及び減圧装置４を調整して冷房運転をすると、室外熱交換器３内の冷媒の流れは次のようになる。   Using the outdoor heat exchanger 3 as described above, the refrigerant in the intermediate pipes 3a4 and 3b4 is in a gas-liquid two-phase state, and the outlet portions 3a2 to 3d2 of the first to fourth refrigerant flow paths 3a to 3d are in a liquid state. As described above, when the cooling operation is performed by adjusting the refrigerant filling amount, the rotation speed of the compressor 1, the rotation speed of the outdoor fan 6a, the rotation speed of the indoor fan 7a, and the decompression device 4, the refrigerant in the outdoor heat exchanger 3 is adjusted. The flow is as follows.

圧縮機１で圧縮室されたガス状冷媒は、冷媒配管１１から分流器１２を経て４分配されて第１〜第４冷媒流路３ａ〜３ｄに流入され、外部（室外空気）に熱を放出し凝縮され、これらの冷媒流路３ａ〜３ｄの出口部３ａ２〜３ｄ２においては凝縮が終了し、液状冷媒となる。そして、第１冷媒流路３ａと第２冷媒流路３ｂから流出された液冷媒は、分流器１３にて合流され、第５冷媒流路３ｅに流れ込み、更に外部（室外空気）に放熱する。また、第３冷媒流路３ｃと第４冷媒流路３ｄから流出された液冷媒は、分流器１４にて合流され、第６冷媒流路３ｆに流れ込み、更に外部（室外空気）に放熱する。そして、第５冷媒流路３ｅ、第６冷媒流路３ｆの出口部３ｅ２、３ｆ２から流出された液冷媒は、分流器１５にて合流され、冷媒配管１１に流出される。   The gaseous refrigerant compressed in the compressor 1 is divided into four from the refrigerant pipe 11 via the flow divider 12, flows into the first to fourth refrigerant flow paths 3a to 3d, and releases heat to the outside (outdoor air). Then, the condensation is completed at the outlet portions 3a2 to 3d2 of the refrigerant flow paths 3a to 3d, and the liquid refrigerant is obtained. Then, the liquid refrigerant flowing out from the first refrigerant flow path 3a and the second refrigerant flow path 3b is merged by the flow divider 13, flows into the fifth refrigerant flow path 3e, and further radiates heat to the outside (outdoor air). The liquid refrigerant that has flowed out of the third refrigerant channel 3c and the fourth refrigerant channel 3d is merged by the flow divider 14, flows into the sixth refrigerant channel 3f, and further radiates heat to the outside (outdoor air). Then, the liquid refrigerant that has flowed out from the outlet portions 3e2 and 3f2 of the fifth refrigerant flow path 3e and the sixth refrigerant flow path 3f is merged by the flow divider 15 and flows out to the refrigerant pipe 11.

ここで、内部の冷媒が液状になっている第１〜第４冷媒流路３ａ〜３ｄの出口部３ａ２〜３ｄ２の高さの差に注目すると、一番高い位置に存在する第３冷媒流路３ｃの出口部３ｃ２と一番低い位置に存在する第１冷媒流路３ａの出口部３ａ２との差は、熱交換器の段数では８段になっている。一方、図７に示した従来の室外熱交換器３の第１〜第４冷媒流路３ａ〜３ｄの出口部３ａ２〜３ｄ２の高さの差に注目すると、一番高い位置に存在する第１冷媒流路３ａの出口部３ａ２と、一番低い位置に存在する第４冷媒流路３ｄの出口部３ｄ２との差は、熱交換器の段数では１４段になっている。すなわち、本実施形態の室外熱交換器３の第１〜第４冷媒流路３ａ〜３ｄの出口部３ａ２〜３ｄ２の高さの差は、図７に示す従来の室外熱交換器３の第１〜第４冷媒流路３ａ〜３ｄの出口部３ａ２〜３ｄ２の高さの差よりも小さくなっている。これによって、本実施形態の室外熱交換器３の第１〜第４冷媒流路３ａ〜３ｄの出口部における内部の冷媒の圧力の差が従来例よりも小さくなる。その結果、各冷媒流路の出入り口の圧力差を均一化することができる。すなわち、各冷媒流路の冷媒の流量を均一化することができ、冷媒の偏流が低減されるので、冷凍サイクルの省エネルギー性を高めることができる。   Here, when attention is paid to the difference in height between the outlet portions 3a2 to 3d2 of the first to fourth refrigerant flow paths 3a to 3d in which the internal refrigerant is liquid, the third refrigerant flow path existing at the highest position. The difference between the outlet portion 3c2 of 3c and the outlet portion 3a2 of the first refrigerant flow path 3a existing at the lowest position is eight in the number of stages of the heat exchanger. On the other hand, when attention is paid to the difference in height between the outlet portions 3a2 to 3d2 of the first to fourth refrigerant flow paths 3a to 3d of the conventional outdoor heat exchanger 3 shown in FIG. The difference between the outlet part 3a2 of the refrigerant flow path 3a and the outlet part 3d2 of the fourth refrigerant flow path 3d present at the lowest position is 14 stages in the number of stages of the heat exchanger. That is, the difference in height between the outlet portions 3a2 to 3d2 of the first to fourth refrigerant flow paths 3a to 3d of the outdoor heat exchanger 3 of the present embodiment is the first difference of the conventional outdoor heat exchanger 3 shown in FIG. -It is smaller than the difference in height between the outlet portions 3a2 to 3d2 of the fourth refrigerant flow paths 3a to 3d. Thereby, the difference of the pressure of the internal refrigerant | coolant in the exit part of the 1st-4th refrigerant flow paths 3a-3d of the outdoor heat exchanger 3 of this embodiment becomes smaller than a prior art example. As a result, the pressure difference at the entrance and exit of each refrigerant channel can be made uniform. That is, the flow rate of the refrigerant in each refrigerant channel can be made uniform, and the drift of the refrigerant is reduced, so that the energy saving performance of the refrigeration cycle can be improved.

また、第１冷媒流路３ａ及び第２冷媒流路３ｂの入口側及び出口側の高さに注目すると、入口側が上段である第１冷媒流路３ａにおける運転時に内部の冷媒が液状態となる流路出口部３ａ２側を、入口側が下段である第２冷媒流路３ｂにおける運転時に内部の冷媒が液状態となる流路出口部３ｂ２側よりも下側に位置させている。これによって、第１冷媒流路３ａと第２冷媒流路３ｂとの圧力差が小さくなり、冷媒の偏流が低減されるので、冷凍サイクルの省エネルギー性を高めることができる。   When attention is paid to the heights of the inlet side and the outlet side of the first refrigerant flow path 3a and the second refrigerant flow path 3b, the internal refrigerant is in a liquid state during operation in the first refrigerant flow path 3a whose upper side is the inlet side. The channel outlet portion 3a2 side is positioned below the channel outlet portion 3b2 side where the internal refrigerant is in a liquid state during operation in the second refrigerant channel 3b whose inlet side is the lower stage. Thereby, the pressure difference between the first refrigerant flow path 3a and the second refrigerant flow path 3b is reduced, and the drift of the refrigerant is reduced, so that the energy saving property of the refrigeration cycle can be improved.

（第２実施形態）
次に、本発明の第２実施形態について図６を用いて説明する。図６は本発明の第２実施形態の空気調和機１０の室外熱交換器３の側面図である。この第２実施形態は、次に述べる点で第１実施形態と相違するものであり、その他の点については第１実施形態と基本的には同一であるので、重複する説明を省略する。なお、図６は図４に対応するものである。 (Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 6 is a side view of the outdoor heat exchanger 3 of the air conditioner 10 according to the second embodiment of the present invention. The second embodiment is different from the first embodiment in the points described below, and the other points are basically the same as those in the first embodiment, and thus redundant description is omitted. FIG. 6 corresponds to FIG.

この第２実施形態では、室外熱交換器３の並列流路を構成する第１〜第４冷媒流路３ａ〜３ｄのうち、空間的に最も低い位置の伝熱管を含む冷媒流路である第４冷媒流路３ｄは、中間パイプ３ｄ４により上流流路３ｄ３と下流流路３ｄ５とに空間的に分離されて配置されており、かつ、下流流路３ｄ５は上流流路３ｄ３に対して高い位置に配置されている。また、第３冷媒流路３ｃについても、中間パイプ３ｃ４により上流流路３ｃ３と下流流路３ｃ５とに空間的に分離されて配置されており、かつ、下流流路３ｃ５は上流流路３ｃ３に対して高い位置に配置されている。   In the second embodiment, among the first to fourth refrigerant flow paths 3a to 3d constituting the parallel flow path of the outdoor heat exchanger 3, the refrigerant flow path includes a heat transfer tube at the spatially lowest position. 4 The refrigerant flow path 3d is spatially separated by an intermediate pipe 3d4 into an upstream flow path 3d3 and a downstream flow path 3d5, and the downstream flow path 3d5 is positioned higher than the upstream flow path 3d3. Has been placed. Further, the third refrigerant flow path 3c is also spatially separated by the intermediate pipe 3c4 into the upstream flow path 3c3 and the downstream flow path 3c5, and the downstream flow path 3c5 is separated from the upstream flow path 3c3. It is placed at a high position.

以上のような室外熱交換器３を用い、中間パイプ３ｃ４、３ｄ４内の冷媒が気液二相状態となるように冷媒封入量、圧縮機１の回転速度、室外ファン６ａの回転速度、室内ファン７ａの回転速度、及び減圧装置４を調整して運転すると、室外熱交換器３内の冷媒の流れは次のようになる。   Using the outdoor heat exchanger 3 as described above, the refrigerant filling amount, the rotational speed of the compressor 1, the rotational speed of the outdoor fan 6a, the indoor fan so that the refrigerant in the intermediate pipes 3c4 and 3d4 is in a gas-liquid two-phase state. When the rotational speed of 7a and the decompression device 4 are adjusted and operated, the refrigerant flow in the outdoor heat exchanger 3 is as follows.

冷媒配管１１から流入したガス状冷媒は、分流器１２を経て４分配され、第１〜第４冷媒流路３ａ〜３ｄに流入され、外部に熱を放出し凝縮が行われる。第１〜第４冷媒流路３ａ〜３ｄの出口部３ａ２〜３ｄ２においては、冷媒は凝縮が終了し、液状冷媒となる。そして、第１冷媒流路３ａと第２冷媒流路３ｂから流出した液冷媒は、分流器１３にて合流し、第５冷媒流路３ｅに流れ込み、更に外部に放熱する。また、第３冷媒流路３ｃと第４冷媒流路３ｄから流出した液冷媒は、分流器１４にて合流し、第５冷媒流路３ｆに流れ込み、更に外部に放熱する。そして、第５冷媒流路３ｅ、第６冷媒流路３ｆの出口部３ｅ２、３ｆ２から流出した液冷媒は、分流器１５にて合流し、冷媒配管１１に至る。   The gaseous refrigerant that has flowed in from the refrigerant pipe 11 is divided into four through the flow divider 12, flows into the first to fourth refrigerant flow paths 3a to 3d, releases heat to the outside, and is condensed. In the outlet portions 3a2 to 3d2 of the first to fourth refrigerant flow paths 3a to 3d, the refrigerant has finished condensing and becomes a liquid refrigerant. And the liquid refrigerant which flowed out from the 1st refrigerant flow path 3a and the 2nd refrigerant flow path 3b merges in the flow divider 13, flows into the 5th refrigerant flow path 3e, and also radiates heat outside. The liquid refrigerant that has flowed out of the third refrigerant flow path 3c and the fourth refrigerant flow path 3d merges in the flow divider 14, flows into the fifth refrigerant flow path 3f, and further radiates heat to the outside. Then, the liquid refrigerant flowing out from the outlet portions 3e2 and 3f2 of the fifth refrigerant channel 3e and the sixth refrigerant channel 3f merges at the flow divider 15 and reaches the refrigerant pipe 11.

第１冷媒流路３ａは、１列目が６段、２列目が４段の合計１０段で形成されている。第２冷媒流路３ｂは、１列目が６段、２列目が４段の合計１０段で形成されている。   The first refrigerant flow path 3a is formed with a total of 10 stages in which the first row has six stages and the second row has four stages. The second refrigerant flow path 3b is formed with a total of 10 stages, the first row being 6 stages and the second row being 4 stages.

第３冷媒流路３ｃは、中間パイプ３ｃ４を介して、上流流路３ｃ３と下流流路３ｃ５とに空間的に分離されて配置されている。また、第４冷媒流路３ｄは、中間パイプ３ｄ４を介して、上流流路３ｄ３と下流流路３ｄ５とに空間的に分離されて配置されている。第３冷媒流路３ｃの上流流路３ｃ３は、１列目が４段、２列目が４段の合計８段で形成され、２列目の２段で形成された下流流路３ｃ５よりも長く形成されている。第４冷媒流路３ｄの上流流路３ｄ３は、１列目が４段、２列目が４段の合計８段で形成され、２列目の２段で形成された下流流路３ａ５よりも長く形成されている。 The third refrigerant flow path 3c is spatially separated into an upstream flow path 3c3 and a downstream flow path 3c5 via an intermediate pipe 3c4. The fourth refrigerant passage 3d, via the intermediate pipe 3 d4, are arranged spatially separated into an upstream passage 3d3 and the downstream passage 3d5. The upstream flow path 3c3 of the third refrigerant flow path 3c is formed with a total of 8 stages in which the first row has four stages and the second row has four stages, and is more downstream than the downstream flow path 3c5 formed in the second stage of the second row. It is formed long. The upstream flow path 3d3 of the fourth refrigerant flow path 3d is formed by a total of 8 stages, 4 stages in the first row and 4 stages in the second row, and more than the downstream flow path 3a5 formed in the second stage in the second row. It is formed long.

ここで、内部の冷媒が液状になっている第１〜第４冷媒流路３ａ〜３ｄの出口部３ａ２〜３ｄ２の高さの差に注目すると、一番高い位置に存在する第４冷媒流路３ｄの出口部３ｄ２と一番低い位置に存在する第２冷媒流路３ｂの出口部３ｂ２との差は、熱交換器の段数では１０段になっている。この１０段の差は、図７に示した従来の室外熱交換器３の一番高い位置に存在する第１冷媒流路３ａの出口部３ａ２と一番低い位置に存在する第４冷媒流路３ｄの出口部３ｄ２との差の１４段より小さくなっている。つまり、この第２実施形態の第１〜第４冷媒流路３ａ〜３ｄの出口部における、内部の冷媒の圧力の差が小さくなっており、冷媒の偏流が低減されている。すなわち、冷凍サイクルの省エネルギー性が高められている。   Here, when attention is paid to the difference in height between the outlet portions 3a2 to 3d2 of the first to fourth refrigerant channels 3a to 3d in which the internal refrigerant is liquid, the fourth refrigerant channel existing at the highest position. The difference between the outlet portion 3d2 of 3d and the outlet portion 3b2 of the second refrigerant channel 3b present at the lowest position is 10 in the number of stages of the heat exchanger. The difference between the 10 stages is that the outlet portion 3a2 of the first refrigerant flow path 3a present at the highest position of the conventional outdoor heat exchanger 3 shown in FIG. 7 and the fourth refrigerant flow path present at the lowest position. The difference from the 3d outlet 3d2 is smaller than 14 stages. That is, the difference in the internal refrigerant pressure at the outlets of the first to fourth refrigerant flow paths 3a to 3d of the second embodiment is reduced, and the refrigerant drift is reduced. That is, the energy saving property of the refrigeration cycle is improved.

（その他の実施形態）
上述した実施形態では、冷凍サイクル装置の一例として、分離型の空気調和機を例に取り上げて説明したが、クロスフィンチューブ型で、複数の冷媒流路が略鉛直方向に上下多段で構成され、並列の冷媒流路を備えている凝縮器を備えた冷凍サイクル装置であれば、例えば冷凍機や冷水供給装置、給湯装置等にも本発明を適用し、省エネルギー性を高めることができる。 (Other embodiments)
In the above-described embodiment, as an example of a refrigeration cycle apparatus, a separation type air conditioner has been described as an example.However, in the cross fin tube type, a plurality of refrigerant flow paths are configured in multiple vertical stages in a substantially vertical direction, If it is a refrigerating cycle apparatus provided with the condenser provided with the parallel refrigerant flow path, this invention can be applied, for example to a refrigerator, a cold water supply apparatus, a hot water supply apparatus, etc., and energy saving property can be improved.

本発明の第１実施形態の冷凍サイクル装置を備えた空気調和機の構成図である。It is a lineblock diagram of the air harmony machine provided with the refrigerating cycle device of a 1st embodiment of the present invention. 図１の空気調和機の室外熱交換器の基本構成要素を分解して示す図である。It is a figure which decomposes | disassembles and shows the basic component of the outdoor heat exchanger of the air conditioner of FIG. 図１の空気調和機の室外機の透視図である。It is a perspective view of the outdoor unit of the air conditioner of FIG. 図１の空気調和機の室外熱交換器における配管部品が取り付けられた側から見た側面図である。It is the side view seen from the side in which the piping components in the outdoor heat exchanger of the air conditioner of FIG. 1 were attached. 図４の室外熱交換器の冷媒流路を模式的に表わす図である。It is a figure which represents typically the refrigerant | coolant flow path of the outdoor heat exchanger of FIG. 本発明の第２実施形態の空気調和機の室外熱交換器の側面図である。It is a side view of the outdoor heat exchanger of the air conditioner of 2nd Embodiment of this invention. 従来の空気調和機の室外熱交換器の側面図である。It is a side view of the outdoor heat exchanger of the conventional air conditioner.

符号の説明Explanation of symbols

１…圧縮機、２…四方切替弁、３…室外熱交換器、３ａ…第１冷媒流路、３ａ１…入口部、３ａ２…出口部、３ａ３…上流流路、３ａ４…中間パイプ、３ａ５…下流流路、３ｂ…第２冷媒流路、３ｂ１…入口部、３ｂ２…出口部、３ｂ３…上流流路、３ｂ４…中間パイプ、３ｂ５…下流流路、３ｃ…第３冷媒流路、３ｃ１…入口部、３ｃ２…出口部、３ｄ…第４冷媒流路、３ｄ１…入口部、３ｄ２…出口部、３ｅ…第５冷媒流路、３ｅ１…入口部、３ｅ２…出口部、３ｆ…第６冷媒流路、３ｆ１…入口部、３ｆ２…出口、４…減圧装置、５…室内熱交換器、６…室外ファン装置、６ａ…室外ファン、６ｂ…モータ、７…室内ファン装置、７ａ…室内ファン、７ｂ…モータ、８…室外機、９…室内機、１０…冷凍サイクル装置、１１…冷媒配管、１２…分流器、２０…空気調和機、３１…フィン、３２…伝熱管、３２ａ…Ｕ字型の伝熱管、３２ｂ…リターンパイプ。 DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... Four-way switching valve, 3 ... Outdoor heat exchanger, 3a ... 1st refrigerant flow path, 3a1 ... Inlet part, 3a2 ... Outlet part, 3a3 ... Upstream flow path, 3a4 ... Intermediate pipe, 3a5 ... Downstream Flow path, 3b ... second refrigerant flow path, 3b1 ... inlet part, 3b2 ... outlet part, 3b3 ... upstream flow path, 3b4 ... intermediate pipe, 3b5 ... downstream flow path, 3c ... third refrigerant flow path, 3c1 ... inlet part 3c2 ... exit part, 3d ... fourth refrigerant channel, 3d1 ... inlet part, 3d2 ... exit part, 3e ... fifth refrigerant channel, 3e1 ... inlet part, 3e2 ... exit part, 3f ... sixth refrigerant channel, 3f1 ... inlet, 3f2 ... outlet, 4 ... decompressor, 5 ... indoor heat exchanger, 6 ... outdoor fan device, 6 a ... outdoor fan, 6 b ... motor, 7 ... indoor fan device 7 a ... indoor fan, 7 b ... motor, 8 ... outdoor unit, 9 ... indoor unit, 10 ... refrigerating cycle apparatus, 11 ... cold Pipe, 12 ... shunt, 20 ... air conditioner, 31 ... fin, 32 ... heat transfer tubes, 32a ... U-shaped heat exchanger tubes, 32 b ... return pipe.

Claims (1)

圧縮機、凝縮器、減圧装置及び蒸発器を順次冷媒配管で接続してサイクル流路を構成し、
前記凝縮器は、複数の冷媒流路を形成する第１冷媒流路、第２冷媒流路、第３冷媒流路及び第４冷媒流路が並列に接続されると共に、上下に位置して設けられている冷凍サイクル装置において、
前記凝縮器の入口側が最も上に位置する前記第１冷媒流路における運転時に内部の冷媒が液状態となる第１流路出口部を、当該凝縮器の入口側が前記第１冷媒流路の入口側よりもそれぞれ下に位置する前記第２冷媒流路、前記第３冷媒流路及び前記第４冷媒流路における運転時に内部の冷媒が液状態となる第２流路出口部、第３流路出口部及び第４流路出口部よりも下側に位置させると共に、前記凝縮器の入口側が２番目に高い前記第２冷媒流路の前記第２流路出口部を前記第３流路出口部及び前記第４流路出口部よりも下側に位置させ、
前記凝縮器の入口側が上に位置する前記冷媒流路の流路出口側を前記凝縮器の入口側が下に位置する前記冷媒流路の流路出口側よりも上側に位置させた場合における流路出口側の高さの差よりも、前記凝縮器の複数の冷媒流路における運転時の内部の冷媒が液状態となる流路出口側の高さの差が小さくなるように当該複数の冷媒流路が構成され、
前記凝縮器は伝熱管及びフィンからなるクロスフィンチューブ型熱交換器で構成され、
前記凝縮器の複数の冷媒流路のうちの空間的に最も高い位置の入口側伝熱管を含む前記第１冷媒流路は、第１中間パイプを介して、第１上流流路と第１下流流路とに空間的に分離されて配置されており、前記第１上流流路は前記第２冷媒流路、前記第３冷媒流路及び前記第４冷媒流路より高い位置に配置されており、前記第１下流流路は前記上流流路、前記第３冷媒流路及び前記第４冷媒流路よりも低い位置に配置されており、前記第１上流流路と前記第１下流流路とを接続する前記第１中間パイプ内の冷媒状態が気液二相で前記第１流路出口部が液状態となるように運転されると共に、前記第２冷媒流路は、第２中間パイプを介して、第２上流流路と第２下流流路とに空間的に分離されて配置されており、前記第２上流流路は前記第３冷媒流路及び前記第４冷媒流路より高い位置に配置されており、前記第２下流流路は前記第２上流流路、前記第３冷媒流路及び前記第４冷媒流路よりも低い位置に配置されており、
前記圧縮機から吐出される冷媒の流れ方向及び当該圧縮機へ吸入される冷媒の流れ方向を切り替える切替弁を備え、前記凝縮器が室外熱交換器で構成され前記蒸発器が室内熱交換器で構成され、
前記第１冷媒流路、前記第２冷媒流路、前記第３冷媒流路及び前記第４冷媒流路はそれぞれ前記第１流路出口部、前記第２流路出口部、前記第３流路出口部及び前記第４流路出口部までは何れの冷媒流路とも合流せずにそれぞれ１本の流路で構成され、前記第１流路出口部、前記第２流路出口部、前記第３流路出口部及び前記第４流路出口部の下流側で前記第１冷媒流路、前記第２冷媒流路、前記第３冷媒流路及び前記第４冷媒流路が合流する
ことを特徴とする冷凍サイクル装置。 A compressor, a condenser, a decompression device and an evaporator are sequentially connected by a refrigerant pipe to form a cycle flow path,
The condenser is provided with a first refrigerant channel, a second refrigerant channel, a third refrigerant channel, and a fourth refrigerant channel that form a plurality of refrigerant channels connected in parallel and positioned above and below. In the refrigeration cycle apparatus,
Wherein the first flow path outlet portion inside of the refrigerant becomes a liquid state during the operation in the first refrigerant passage, the condenser inlet side inlet of the first refrigerant flow path inlet side of the condenser is located on the most the second refrigerant passage located below each of the side, the second flow path outlet portion inside of the refrigerant becomes a liquid state during operation in the third refrigerant flow path and the fourth refrigerant flow path, a third flow path outlet and the fourth flow path outlet is located below the Rutotomoni, the condenser inlet side the said second flow path outlet portion of the second highest second refrigerant passage third channel outlet Part and lower side than the fourth channel outlet part ,
A flow path in a case where the flow path outlet side of the refrigerant flow path where the inlet side of the condenser is positioned is positioned above the flow path outlet side of the refrigerant flow path where the inlet side of the condenser is positioned below The plurality of refrigerant flows are less than the height difference on the outlet side, so that the difference in height on the outlet side of the flow path where the refrigerant in the plurality of refrigerant flow paths of the condenser is in a liquid state becomes smaller. The road is composed,
The condenser is composed of a cross fin tube type heat exchanger composed of heat transfer tubes and fins,
The first refrigerant flow path including the inlet-side heat transfer tube at the spatially highest position among the plurality of refrigerant flow paths of the condenser includes a first upstream flow path and a first downstream flow path via a first intermediate pipe. The first upstream flow path is disposed at a position higher than the second refrigerant flow path, the third refrigerant flow path, and the fourth refrigerant flow path. the first downstream flow path wherein the upstream flow path, the third is disposed at a position lower than the coolant flow path and the fourth refrigerant flow path, the first upstream passage and the first downstream flow path the refrigerant state in the first intermediate pipe connecting is operated such that the first flow path outlet portion in the gas-liquid two-phase becomes a liquid state Rutotomoni, the second coolant channel, the second intermediate pipe Through the second upstream flow path and the second downstream flow path, and the second upstream flow path is disposed in the third refrigerant. The second downstream flow path is disposed at a position lower than the second upstream flow path, the third refrigerant flow path, and the fourth refrigerant flow path. Has been
A switching valve that switches a flow direction of the refrigerant discharged from the compressor and a flow direction of the refrigerant sucked into the compressor, wherein the condenser is an outdoor heat exchanger, and the evaporator is an indoor heat exchanger. Configured,
The first refrigerant channel , the second refrigerant channel , the third refrigerant channel, and the fourth refrigerant channel are respectively the first channel outlet , the second channel outlet , and the third channel. outlet and to said fourth flow path outlet portion are each composed of one channel without merging with any of the coolant channel, the first flow path outlet portion, the second flow path outlet portion, said The first refrigerant flow path , the second refrigerant flow path , the third refrigerant flow path, and the fourth refrigerant flow path merge on the downstream side of the third flow path outlet section and the fourth flow path outlet section. A characteristic refrigeration cycle apparatus.
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