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³í¹®¸í Simulink¸¦ Ȱ¿ëÇÑ ³»ºÎ ¿­±³È¯±â Àû¿ë ÃÊÀÓ°è CO2 ³Ãµ¿½Ã½ºÅÛ ¿­-°æÁ¦¼º ¼º´ÉÆò°¡ / Thermo-Economic Performance Evaluation of a Supercritical CO2 Refrigeration System with an Internal Heat Exchanger Using Simulink
ÀúÀÚ¸í ¾çÁ¤ÈÆ(Jung Hoon Yang) ; Á¶Áø±Õ(Jin Kyun Cho)½Äº°ÀúÀÚ ; ¹®ÁÖÇö(Joo Hyun Moon)
¹ßÇà»ç ´ëÇѼ³ºñ°øÇÐȸ
¼ö·Ï»çÇ× ¼³ºñ°øÇÐ³í¹®Áý, Vol.37 No.11 (2025-11)
ÆäÀÌÁö ½ÃÀÛÆäÀÌÁö(521) ÃÑÆäÀÌÁö(15)
ISSN 1229-6422
ÁÖÁ¦ºÐ·ù ȯ°æ¹×¼³ºñ
ÁÖÁ¦¾î CO2 ³Ã¸Å ½Ã½ºÅÛ; ³»ºÎ ¿­±³È¯±â; ½É½ºÄÉÀÌÇÁ; ½Ã¹Ä¸µÅ©; °ú¿­µµ; ÃÊÀÓ°è ; CO2 refrigeration system; Internal heat exchanger; Simscape; Simulink; Superheat; Transcritical
¿ä¾à1 º» ¿¬±¸´Â °¡½ºÄð·¯ÀÇ ÇÉ ¸éÀû°ú °ü°æ, ±×¸®°í ¿Ü±â¿Âµµ(20-40¡É) º¯È­°¡ ÃÊÀÓ°è CO2 ³Ãµ¿½Ã½ºÅÛÀÇ ¿­¿ªÇÐÀû ¼º´É°ú °æÁ¦¼º¿¡ ¹ÌÄ¡´Â ¿µÇâÀ» ºÐ¼®ÇÏ¿´´Ù. ÇÉ ¸éÀûÀÇ °æ¿ì, 0.06 m©÷¿¡¼­ 0.20 m©÷ ±îÁö È®´ëÇÔ¿¡ µû¶ó ½Ã½ºÅÛ ¼º´ÉÀÌ Å©°Ô Çâ»óµÇ¾ú´Ù. 40¡É °í¿Â Á¶°Ç¿¡¼­ COP´Â 1.22¿¡¼­ 2.2·Î ¾à 80% »ó½ÂÇÏ¿´À¸¸ç, ¾ÐÃà±â ¼ÒºñÀü·ÂÀº 148.1 W¿¡¼­ 90.4 W·Î ¾à 39% °¨¼ÒÇÏ¿© ¿¡³ÊÁö Àý°¨ È¿°ú°¡ ¸íÈ®È÷ ¹ß»ýÇÏ¿´´Ù. ¶ÇÇÑ, ÃѺñ¿ë(Total Cost) ºÐ¼® °á°ú 40¡ÉÀÇ °í¿Â Á¶°Ç¿¡¼­´Â ÇÉ ¸éÀûÀ» Áõ°¡½Ãų¼ö·Ï ¼º´É ¹× °æÁ¦¼ºÀÌ ¸ðµÎ °³¼±µÇ¾î, ÃÖ´ë ¸éÀû(0.2 m©÷)¿¡¼­ ÃÖÀû È¿À²ÀÌ ³ªÅ¸³µ´Ù. ±×·¯³ª 20~40¡ÉÀÇ Àü ¿Âµµ ±¸°£À» Á¾ÇÕÀûÀ¸·Î °í·ÁÇÒ °æ¿ì, ÇÉ ¸éÀû Áõ°¡¿¡ µû¸¥ ¼º´É Çâ»ó·üÀº 0.14-0.16 m©÷ ÀÌÈĺÎÅÍ Á¡Â÷ µÐÈ­µÇ°í, Ãß°¡ÀûÀÎ Á¦ÀÛºñ¿ëÀÌ ¹ß»ýÇϹǷΠÀÌ ¹üÀ§°¡ ½ÇÁúÀûÀÎ ÃÖÀû ¼³°è±¸°£À¸·Î ÆÇ´ÜµÈ´Ù. ¹Ý¸é, ÆÄÀÌÇÁ °ü°æÀº 0.004 m¿¡¼­ 0.011 m·Î È®´ëÇÒ¼ö·Ï, 40¡É ±âÁØ COP°¡ 2.05¿¡¼­ 1.616À¸·Î Ç϶ôÇϰí ÃѺñ¿ëÀº 68,114 KRW¿¡¼­ 97,847 KRW·Î Áö¼ÓÀûÀ¸·Î »ó½ÂÇÏ¿© ¼º´É°ú °æÁ¦¼º ¸ðµÎ ¾ÇÈ­µÇ¾ú´Ù. µû¶ó¼­ ÆÄÀÌÇÁ Á÷°æÀº Å×½ºÆ® ¹üÀ§ ³» ÃÖ¼ÒÄ¡ÀÎ 0.004 m·Î ¼³°èÇÏ´Â °ÍÀÌ °¡Àå ¹Ù¶÷Á÷ÇÏ´Ù. °á·ÐÀûÀ¸·Î, ¿Ü±â¿Âµµ º¯µ¿¼ºÀÌ Å« ȯ°æ¿¡¼­ °íÈ¿À² ¿î¿µÀ» ´Þ¼ºÇϱâ À§Çؼ­´Â ÆÄÀÌÇÁ Á÷°æ ´Ü¼ø ÃÖ¼ÒÈ­º¸´Ù ÇÉ ¸éÀû °æÁ¦Àû ÃÖÀûÈ­°¡ ½Ã½ºÅÛ ¼º´É°ú °æÁ¦¼ºÀ» °áÁ¤ÇÏ´Â ´õ ÇÙ½ÉÀûÀÎ ¼³°è º¯¼öÀÓÀ» È®ÀÎÇÏ¿´´Ù. º» ¿¬±¸¿¡¼­ Á¦¾ÈÇÑ ÃÊÀÓ°è CO2 ³Ãµ¿ »çÀÌŬÀÇ ¼º´É ºÐ¼® °á°ú´Â, °í¿Â ¿Ü±â Á¶°Ç¿¡¼­ ¿îÀüµÇ´Â »ó¾÷¿ë ³ÃÀå ¼îÄÉÀ̽º, Àú¿Â ¿î¼Û Â÷·®(³Ãµ¿ Æ®·°), ¼Ò±Ô¸ð ³Ãµ¿Ã¢°í ½Ã½ºÅÛ µîÀÇ ¼³°è ÃÖÀûÈ­¿¡ ÀÀ¿ëµÉ ¼ö ÀÖ´Ù. ƯÈ÷ ÇÉ ¸éÀû È®´ë¸¦ ÅëÇÑ COP Çâ»ó°ú ¼ÒºñÀü·Â Àý°¨ È¿°ú´Â, ¿­±³È¯±â Á¦Á¶ ¹× ½Ã½ºÅÛ ¼³°è ´Ü°è¿¡¼­ ¿¡³ÊÁö È¿À²¼º°ú ºñ¿ë È¿À²¼ºÀ» µ¿½Ã¿¡ °í·ÁÇÑ ¼³°è ±âÁØÀ¸·Î Ȱ¿ë °¡´ÉÇÏ´Ù.
¿ä¾à2 Global warming increases refrigeration demand, impacting electricity consumption as higher ambient temperatures degrade system performance (higher power, lower COP). We simulated a transcritical CO2 system, varying gas cooler tube diameter (0.004-0.011 m) and fin area (0.06-0.20 m©÷) from 20-40¡É. Enlarging tube diameter (0.004 to 0.011 m) proved detrimental: at 40¡É, COP decreased 21.2% (from 2.05 to 1.62) and total cost increased, indicating the optimal diameter is 0.004 m. Conversely, expanding fin area (0.06 to 0.20 m©÷) markedly improved heat rejection. At 40¡É, COP increased 80% (from 1.22 to 2.19) and compressor power dropped 39% (from 148.1 to 90.4 W). While performance improved up to 0.20 m©÷, total cost analysis identified an economic optimum in the 0.14-0.16 m©÷ range. Comparative results demonstrate that fin area adjustments produce more significant performance changes than tube diameter modifications, particularly under high ambient temperature conditions. Therefore, in practical system design, it is more effective to address fin area configuration before tube diameter adjustments, as this approach can maintain higher energy efficiency over different seasons while also reducing operational costs.
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DOI https://doi.org/10.6110/KJACR.2025.37.11.521