Arvand HVAC 40

‫ﺑﻪ ﻧﺎﻡ ﺁﻥ ﻛﻪ ﺟﺎﻥ ﺭﺍ ﻓﻜﺮﺕ ﺁﻣﻮﺧﺖ‬

‫ﺷﻤﺎﺭﻩ ﭼﻬﻠﻢ ‪90 -‬‬

‫ﻧﺸﺮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺩﺭ ﺍﻳﻦ ﺷﻤﺎﺭﻩ ﻣﻰﺧﻮﺍﻧﻴﺪ‪:‬‬

‫ﺷﻤﺎﺭﻩ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ﺑﻴﻦﺍﻟﻤﻠﻠﻰ‪:‬‬ ‫‪1684-4270‬‬

‫ﻛﺎﺭﺧﺎﻧﻪﺍﺻﻠﻰ)ﺷﻤﺎﺭﻩ‪(1‬ﻭﻭﺍﺣﺪﻓﺮﻭﺵ‪:‬ﻛﺮﺝ‪،‬ﻧﺴﻴﻢﺷﻬﺮ‪،‬‬ ‫ﺳﻪﺭﺍﻩ ﺁﺩﺭﺍﻥ‪ ،‬ﺑﻪ ﻃﺮﻑ ﺷﻬﺮﻳﺎﺭ‪ ،‬ﺍﻧﺘﻬﺎﻯ ﺧﻴﺎﺑﺎﻥ ﺳﻌﺪﻯ‪.‬‬ ‫ﺷﻤﺎﺭﻩﻫﺎﻯ ﻭﺍﺣﺪ ﻓﺮﻭﺵ )ﻛﺪ ‪:(021‬‬ ‫‪ 88802677-8‬ﻭ ‪ 88739880-2‬ﻭ ‪88504770-4‬‬ ‫ﺷﻤﺎﺭﻩﻫﺎﻯ ﻭﺍﺣﺪ ﻓﺮﻭﺵ )ﻛﺪ ‪:(0229‬‬ ‫‪ 4586036 -4585899‬ﻭ ‪ 4584983-7‬ﻭ ‪4584996-7‬‬ ‫ﺷﻤﺎﺭﻩﻫﺎﻯ ﻓﺎﻛﺲ ﻭﺍﺣﺪ ﻓﺮﻭﺵ‪:‬‬ ‫‪ 0229-4585079‬ﻭ ‪021-88766794‬‬ ‫ﺷﻤﺎﺭﻩﻫﺎﻯ ﻛﺎﺭﺧﺎﻧﻪ )ﻛﺪ ‪:(0229‬‬ ‫‪ 4585657-8‬ﻭ ‪ 4584998‬ﻭ ‪4584717‬‬ ‫ﺷﻤﺎﺭﻩ ﻓﺎﻛﺲ ﻛﺎﺭﺧﺎﻧﻪ )ﻛﺪ ‪:(0229‬‬ ‫‪4584198‬‬ ‫ﭘﺴﺖ ﺍﻟﻜﺘﺮﻭﻧﻴﻜﻰ ﺑﺎﺯﺭﮔﺎﻧﻰ‪:‬‬ ‫‪info@arvandcorp.com‬‬

‫ﻭﺍﺣﺪ ﻓﺮﻭﺵ‪:‬‬

‫ﺗﺎﺯﻩﻫﺎﻯ ﺗﻬﻮﻳﻪ‪2 ...................................................................................................‬‬ ‫ﺁﺏ ﻣﺼﺮﻓﻰ ﺩﺭﺳﻴﺴﺘﻢﻫﺎﻯ ﺳﺮﻣﺎﻳﺶ ﺗﺒﺨﻴﺮﻯ‪4 ............................................‬‬ ‫ﺭﻭﺍﺑﻂ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‪6 ..........................................................................................‬‬ ‫ﻃﺒﻘﻪﺑﻨﺪﻯ ﺳﻴﺴـﺘﻢ ﺳـﺮﻣﺎﻳﺶ ﺟﺬﺑـﻰ ﺍﺯ ﻧﻈﺮ ﻣﻨﺒﻊ ﮔﺮﻣﺎﻳـﻰ ﻋﻤﻠﻴﺎﺕ‬ ‫ﺗﻐﻠﻴﻆ ﻭ ﺍﺣﻴﺎ‪7 .......................................................................................‬‬ ‫ﺗﻮﺯﻳﻊ ﻫﻮﺍ ﺩﺭ ﺍﺳﺘﺨﺮﻫﺎ‪15 ...................................................................................‬‬ ‫ﺍﻧﺘﺨﺎﺏ ﭼﻴﻠﺮﻫﺎﻯ ﺟﺬﺑﻰ‪19 ................................................................................‬‬ ‫ﻣﺤﺎﺳﺒﺎﺕ ﻛﻮﺭﻩ ﻫﻮﺍﻯ ﮔﺮﻡ‪27 ............................................................................‬‬

‫‪sales@arvandcorp.com‬‬

‫ﻣﻨﺎﺑﻊ ﺗﻮﻟﻴﺪ ﺁﺏﮔﺮﻡ ﻣﺼﺮﻓﻰ‪29..........................................................................‬‬

‫‪w w w. a r v a n d c o r p . c o m‬‬

‫ﻣﻼﺣﻈﺎﺕ ﺍﺟﺮﺍﻳﻰ ﺑﺮﺍﻯ ﻧﺼﺐ ﺗﺎﺳﻴﺴﺎﺕ ﺩﺭ ﺳﺎﺧﺘﻤﺎﻥ‪32 ..............................‬‬

‫ﻛﺎﺭﺧﺎﻧﻪ ﺷــﻤﺎﺭﻩ ‪ :2‬ﻛﻴﻠﻮﻣﺘﺮ ‪ 26‬ﺍﺗﻮﺑﺎﻥ ﺗﻬﺮﺍﻥ‪ ،‬ﻗﻢ ‪ -‬ﺷــﻬﺮﻙ‬ ‫ﺻﻨﻌﺘﻰ ﺷﻤﺲﺁﺑﺎﺩ ‪ -‬ﺑﻠﻮﺍﺭ ﮔﻠﺴﺘﺎﻥ ‪ -‬ﮔﻠﺸﻦ ‪ - 10‬ﻗﻄﻌﻪ ‪.10‬‬ ‫ﭘﺴﺖ ﺍﻟﻜﺘﺮﻭﻧﻴﻜﻰ‪:‬‬

‫ﻗﻮﺍﻧﻴﻦ ﻓﻦ‪36 .......................................................................................................‬‬

‫ﻧﺸﺎﻧﻰ ﺍﻳﻨﺘﺮﻧﺖ‪:‬‬

‫ﺑﺮﺭﺳﻰ ﻣﻮﺍﺭﺩ ﺍﻗﺘﺼﺎﺩﻯ ﻭ ﻫﺰﻳﻨﻪﻫﺎﻯ ﺳﻴﺴﺘﻢﻫﺎﻯ ﺳﺮﻣﺎﻳﺶ ﺗﺒﺨﻴﺮﻯ‪37....‬‬

‫‪gac@arvandcorp.com‬‬

‫ﻣﺤﺎﺳﺒﺎﺕﺳﺮﺍﻧﮕﺸﺘﻰﺭﻭﺷﻨﺎﻳﻰ‪40 ...................................................................‬‬

‫ﺗﻠﻔﻦﻫﺎﻯ ﺗﻤﺎﺱ ﻭ ﻓﺎﻛﺲ‪:‬‬ ‫‪021-56230345-9‬‬

‫ﺻﺎﺣﺐ ﺍﻣﺘﻴﺎﺯ‪ :‬ﺷﺮﻛﺖ ﺻﻨﺎﻳﻊ ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﻣﺪﻳﺮ ﻣﺴﻮﻭﻝ‪ :‬ﻣﻬﻨﺪﺱ ﻣﻨﻮﭼﻬﺮ ﺷﺠﺎﻋﻰ‬ ‫ﺳﺮﺩﺑﻴﺮ‪ :‬ﻣﻬﻨﺪﺱ ﺣﺴﻦ ﺑﻬﺮﺍﻣﻰ‬

‫ﻋﻼﻗﻪﻣﻨﺪﺍﻥ ﺟﻬﺖ ﺩﺭﻳﺎﻓﺖ ﺭﺍﻳﮕﺎﻥ ﺍﻳﻦ ﻧﺸﺮﻳﻪ ﻭ ﺍﺭﺳﺎﻝ ﺁﺛﺎﺭ ﺧﻮﺩ‬ ‫ﻣﻰﺗﻮﺍﻧﻨﺪ ﺑﺎ ﻭﺍﺣﺪ ﺭﻭﺍﺑﻂﻋﻤﻮﻣﻰ ﺷﺮﻛﺖ ﺻﻨﺎﻳﻊ ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﻳﺎ ﺍﺯ ﻃﺮﻳﻖ ﺻﻨﺪﻭﻕ ﭘﺴﺘﻰ ‪ 37685 - 113‬ﺍﻗﺪﺍﻡ ﻧﻤﺎﻳﻨﺪ‪.‬‬

‫ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﻣﻄﺎﻟﺐ ﻭ ﺗﺼﺎﻭﻳﺮ ﻧﺸﺮﻳﻪ ﺍﺭﻭﻧﺪ ﺑﺎ ﺫﻛﺮ ﻣﻨﺒﻊ ﺑﻼﻣﺎﻧﻊ ﺍﺳﺖ‪.‬‬ ‫ﻋﻼﻗﻪﻣﻨــﺪﺍﻥ ﺑﻪ ﺩﺭﺝ ﻣﻄﻠﺐ ﺩﺭ ﺍﻳﻦ ﻧﺸــﺮﻳﻪ ﻣﻰﺗﻮﺍﻧﻨﺪ ﺁﺛﺎﺭ ﺧﻮﺩ ﺭﺍ ﺑﻪ‬ ‫ﻧﺸﺎﻧﻰ ﻧﺸﺮﻳﻪ ﺍﺭﺳﺎﻝ ﻧﻤﺎﻳﻨﺪ‪.‬‬ ‫ﺍﺭﻭﻧﺪ ﺩﺭ ﺭﺩ‪ ،‬ﻗﺒﻮﻝ ﻳﺎ ﺍﺻﻼﺡ ﻭ ﻭﻳﺮﺍﻳﺶ ﻣﻘﺎﻻﺕ ﺁﺯﺍﺩ ﺍﺳﺖ‪.‬‬ ‫ﻣﻘﺎﻻﺕ ﺍﺭﺳﺎﻟﻰ ﻋﻮﺩﺕ ﺩﺍﺩﻩ ﻧﺨﻮﺍﻫﺪ ﺷﺪ‪.‬‬

‫‪ARVAND Internal Magazine‬‬ ‫‪Managing Director: M. Shojaei‬‬ ‫‪Editor in chief: H. Bahrami‬‬

‫ﺻﻔﺤﻪ ‪ / 2‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺩﺭ ﻓﻀﺎ ﺗﺸﺨﯿﺺ ﻣﯽﺩﻫﻨﺪ ﻭ ﺗﻐﯿﯿﺮﺍﺕ ﻻﺯﻡ‬

‫ﺩﺭ ﺧﺼﻮﺹ ﻭﺿﻌﯿﺖ ﺍﺗﺎﻕ ﺍﺭﺍﺋﻪ ﻣﯽﺩﻫﻨﺪ‪.‬‬

‫ﺭﺍ ﺩﺭ ﺗﻨﻈﯿﻤﺎﺕ ﺳﯿﺴﺘﻢ ﺑﻪ ﻋﻤﻞ ﻣﯽﺁﻭﺭﻧﺪ‪.‬‬

‫ﺗﺎﺯﻩﻫﺎﻯ‬ ‫ﺗﻬﻮﻳﻪ‬

‫ﻭﺍﺣﺪﻫﺎﯼ ﺗﻬﻮﯾﻪ ﻫﯿﺒﺮﯾﺪﯼ‬ ‫ﺷﺮﮐﺖ ‪ Reznor‬ﻣﺤﺼﻮﻝ ﺟﺪﯾﺪ ﺧﻮﺩ‬ ‫ﺭﺍ ﻣﻌﺮﻓﯽ ﮐﺮﺩ‪ .‬ﺳﺮﯼ ‪ Z‬ﻭﺍﺣﺪﻫﺎﯼ ﻫﯿﺒﺮﯾﺪﯼ‬ ‫ﯾﮑﭙﺎﺭﭼﻪ ﺗﻬﻮﯾﻪ‪ ،‬ﺗﺮﮐﯿﺒﯽ ﺍﺳﺖ ﺍﺯ ﯾﮏ ﭘﻤﭗ‬

‫ﻭﺍﺣﺪﻫـﺎﯼ ﻓﻦﮐﻮﯾﻞ ﺑـﺎ ﻇﺮﻓﯿﺖ‬ ‫‪ 200cfm‬ﺗﺎ ‪1200cfm‬‬

‫ﻓﻦﻫﺎﯼ ﻣﺤﻮﺭﯼ ﺷـﺮﮐﺖ ‪Ziehl-‬‬ ‫‪Abegg‬‬

‫ﺷﺮﮐﺖ ‪International Environmental‬‬

‫ﺷــﺮﮐﺖ ‪ Ziehl-Abegg‬ﺑــﻪ ﺗﺎﺯﮔﯽ‬

‫ﻣﺤﺼــﻮﻝ ﺟﺪﯾــﺪﯼ ﺑــﺮﺍﯼ ﺗﺎﺳﯿﺴــﺎﺕ‬

‫ﻓﻦﻫﺎﯾﯽ ﻣﺠﻬﺰ ﺑﻪ ﻓﻨﺎﻭﺭﯼ ‪ Ecblue‬ﺭﻭﺍﻧﻪ‬

‫ﺧﻮﺍﺑﮕﺎﻩﻫــﺎﯼ ﺩﺍﻧﺸــﺠﻮﯾﯽ ﯾﺎ ﺗﺎﺳﯿﺴــﺎﺕ‬

‫ﺑﺎﺯﺍﺭ ﮐﺮﺩﻩ ﺍﺳــﺖ ﮐــﻪ ﺑﺮﺍﯼ ﺑــﻪ ﺣﺪﺍﮐﺜﺮ‬

‫ﮐﺎﺭﺑﺮﺩﯼ ﺩﺭ ﺷــﺮﺍﯾﻂ ﺁﺏ ﻭ ﻫﻮﺍﯾﯽ ﻣﺮﻃﻮﺏ‬

‫ﺭﺳﺎﻧﺪﻥ ﻣﯿﺰﺍﻥ ﺑﺎﺯﺩﻩ ﺍﻧﺮﮊﯼ‪ ،‬ﺍﺯ ﻣﻮﺗﻮﺭﻫﺎﯼ‬

‫ﻭ ﺧﻮﺭﻧﺪﻩ ﻃﺮﺍﺣﯽ ﮐﺮﺩﻩ ﺍﺳــﺖ‪ .‬ﻭﺍﺣﺪﻫﺎﯼ‬

‫ﺭﻭﺗﻮﺭ ﺧﺎﺭﺟﯽ ﺟﺮﯾﺎﻥ ‪ -‬ﻣﺴﺘﻘﯿﻢ ﺍﺳﺘﻔﺎﺩﻩ‬

‫ﻓﻦﮐﻮﯾــﻞ ‪ Vertical Series‬ﮐــﻪ ﺍﺯ ﻓﻮﻻﺩ‬

‫ﻣﯽﮐﻨﻨﺪ‪ .‬ﺍﻟﮕــﻮﯼ ﭘﺮﻩ ﻓﻦﻫــﺎﯼ ﻣﺤﻮﺭﯼ‬

‫ﺯﻧﮓﻧﺰﻥ ﺳﺎﺧﺘﻪ ﻣﯽﺷﻮﻧﺪ‪ ،‬ﺩﺍﺭﺍﯼ ﻇﺮﻓﯿﺖ‬

‫‪ FE2owlet‬ﺍﺯ ﺑﺎﻝﻫﺎﯼ ﺟﻐﺪ ﮔﺮﻓﺘﻪ ﺷﺪﻩ‬

‫‪ 200cfm‬ﺗﺎ ‪ 1200cfm‬ﻫﺴﺘﻨﺪ‪.‬‬

‫ﺍﺳﺖ ﺗﺎ ﺍﺯ ﻣﯿﺰﺍﻥ ﺳﺮﻭﺻﺪﺍﻫﺎ ﮐﺎﺳﺘﻪ ﺷﻮﺩ‪.‬‬

‫ﻫﻮﺩﻫﺎﯼ ‪UniFlow Fume‬‬

‫ﭼﯿﻠﺮﻫﺎﯼ ﺁﺑﯽ ﺑﺎ ﭼﻬﺎﺭ ﮐﻤﭙﺮﺳـﻮﺭ‬ ‫‪Maglev‬‬

‫‪ HEMCO‬ﺍﺯ ﺭﻭﺳــﺎﺯﻩﻫﺎﯼ ﻓﺎﯾﺒــﺮﮔﻼﺱ‬

‫ﻧﯿﺰ ﺍﺭﺗﻘﺎ ﻣﯽﯾﺎﺑﺪ‪ .‬ﺍﯾﻦ ﻭﺍﺣﺪﻫﺎ ﺩﺭ ﺯﻣﺴــﺘﺎﻥ‬

‫ﭼﯿﻠــﺮ ‪ 500‬ﺗﻨــﯽ ‪ MS-500F‬ﻧــﺎﻡ‬

‫ﺳﺎﺧﺘﻪ ﺷﺪﻩﺍﻧﺪ ﮐﻪ ﺩﺭ ﺑﺮﺍﺑﺮ ﻣﻮﺍﺩ ﺷﯿﻤﯿﺎﯾﯽ‬

‫ﻭ ﺑﻪ ﻣﻨﻈﻮﺭ ﻓﺮﺍﻫﻢ ﺳﺎﺧﺘﻦ ﻫﻮﺍﯾﯽ ﺑﺎ ﺩﺭﺟﻪ‬

‫ﻣﺤﺼﻮﻝ ﺟﺪﯾﺪ ﺷــﺮﮐﺖ ‪ Multistack‬ﺑﺎ‬

‫ﺣﺮﺍﺭﺕ ‪ 21˚C‬ﺗﻠﻔﯿﻘﯽ ﺍﺳــﺖ ﺍﺯ ﺳﯿﺴــﺘﻢ‬

‫ﭼﻬﺎﺭ ﮐﻤﭙﺮﺳــﻮﺭ ﺑﺪﻭﻥ ﺭﻭﻏــﻦ ‪Maglev‬‬

‫ﺍﺯ ﻣﻘﺎﻭﻣﺖ ﺑﺎﻻﯾﯽ ﺑﺮﺧﻮﺭﺩﺍﺭﻧﺪ‪ .‬ﺍﯾﻦ ﻫﻮﺩﻫﺎ‬

‫ﭘﻤﭗ ﺣﺮﺍﺭﺗﯽ ‪ DX‬ﻭ ﭼﺮﺥ ﺍﻧﺘﺎﻟﭙﯽ‪ .‬ﻣﺤﺼﻮﻝ‬

‫ﺍﺳــﺖ‪ .‬ﻧﻈــﺎﺭﺕ ﺑــﺮ ﻋﻤﻠﮑﺮﺩ ﻫــﺮ ﯾﮏ ﺍﺯ‬

‫ﺟﺪﯾﺪ ﺷــﺮﮐﺖ ‪ Reznor‬ﺩﺭ ﺷــﺮﺍﯾﻂ ﺁﺏ ﻭ‬

‫ﺍﯾــﻦ ﮐﻤﭙﺮﺳــﻮﺭﻫﺎ ﺑــﻪ ﺻــﻮﺭﺕ ﺟﺪﺍﮔﺎﻧﻪ‬

‫ﻫﻮﺍﯾﯽ ﮔﺮﻡﺗﺮ‪ ،‬ﻫﻮﺍﯼ ﺗﺎﺯﻩﺍﯼ ﺑﺪﻭﻥ ﺭﻃﻮﺑﺖ ﺑﺎ‬

‫ﻭ ﺍﺯ ﻃﺮﯾــﻖ ﺳﯿﺴــﺘﻢ ﮐﻨﺘــﺮﻝ ‪FlexSys‬‬

‫ﺩﻣﺎﯼ ‪ 21˚C‬ﺗﻮﻟﯿﺪ ﻣﯽﮐﻨﺪ‪.‬‬

‫ﺻــﻮﺭﺕ ﻣﯽﭘﺬﯾﺮﺩ ﺑﻪ ﮔﻮﻧــﻪﺍﯼ ﮐﻪ ﺑﺎﯾﺪ ﻫﺮ‬

‫ﮔﺮﻣﺎﯾﺸــﯽ ﻭ ﯾﮏ ﭼــﺮﺥ ﺑﺎﺯﯾﺎﺑــﯽ ﺍﻧﺮﮊﯼ ﺩﺭ‬ ‫ﯾــﮏ ﻭﺍﺣﺪ ﮐﻪ ﺑﺪﯾﻦﺗﺮﺗﯿﺐ ﺑﺎﺯﺩﻩ ﺳﯿﺴــﺘﻢ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺣﺲﮔﺮﯼ ﺍﺷﺎﺭﻩ ﮐﺮﺩ ﮐﻪ ﻧﻮﺳﺎﻧﺎﺕ ﺩﻣﺎﯾﯽ ﺭﺍ‬

‫ﻃﺮﯾﻖ ﭘﯿﺶﺯﻣﯿﻨﻪ ﺭﻧﮕﯽ‪ ،‬ﺻﻔﺤﻪ ﺍﻃﻼﻋﺎﺗﯽ‬

‫ﭘﻤﭗﻫﺎﯼ ﮔﺮﻣﺎﯾﺶ ﺩﺍﺧﻠﯽ ﺑﺎ ﻗﺎﺑﻠﯿﺖ‬ ‫ﻧﺼﺐ ﺭﻭﯼ ﺩﯾﻮﺍﺭ‬ ‫ﺷــﺮﮐﺖ‬

‫‪Electric‬‬

‫‪Mitsubishi‬‬

‫ﯾﮏ ﻫﻤﺴــﻮ ﺑﺎ ﺳﺎﯾﺮ ﮐﻤﭙﺮﺳــﻮﺭﻫﺎ ﺩﺍﺭﺍﯼ‬ ‫ﺑﯿﺸــﺘﺮﯾﻦ ﻋﻤﻠﮑﺮﺩ ﺑﺎﺷــﻨﺪ ﺗﺎ ﺑﺎﺯﺩﻩ ﺍﻧﺮﮊﯼ‬ ‫ﻧﯿﺰ ﺑﻪ ﺑﺎﻻﺗﺮﯾﻦ ﺳﻄﺢ ﺧﻮﺩ ﺑﺮﺳﺪ‪.‬‬

‫ﻫﻮﺩﻫﺎﯼ ‪ UniFlow Fume‬ﺷــﺮﮐﺖ‬

‫ﺑﺎ ﺑﺮﺧــﻮﺭﺩﺍﺭﯼ ﺍﺯ ﺳﯿﺴــﺘﻢ ‪VaraFlow‬‬ ‫ﻗﺎﺩﺭﻧﺪ ﺟﺮﯾﺎﻥ ﻫﻮﺍ ﺭﺍ ﺍﺯ ﻃﺮﯾﻖ ﯾﮏ ﻣﺤﻔﻈﻪ‬ ‫ﻭ ﺑــﺎ ﮐﻤﺘﺮﯾﻦ ﻣﯿﺰﺍﻥ ﺁﺷــﻔﺘﮕﯽ ﺑﻪ ﺩﺭﯾﭽﻪ‬ ‫ﺧﺮﻭﺟﯽ ﻫﺪﺍﯾﺖ ﮐﻨﻨﺪ‪.‬‬

‫ﻃـﺮﺡ ﺟﺪﯾـﺪ ﺭﻃﻮﺑﺖﺯﻥﻫـﺎﯼ‬ ‫ﺑﺨﺎﺭ ‪XT‬‬ ‫ﺩﺭ ﻃﺮﺡ ﺟﺪﯾــﺪ ﺭﻃﻮﺑﺖﺯﻥﻫﺎﯼ ﺑﺨﺎﺭ‬ ‫‪ XT‬ﻋﻤﻠﮑــﺮﺩ ﺍﺭﺗﻘﺎ ﯾﺎﻓﺘــﻪ ﻭ ﮐﺎﺭﮐﺮﺩﻫﺎﯼ‬

‫ﭘﻤﭗﻫــﺎﯼ ﮔﺮﻣﺎﯾــﺶ ﺩﺍﺧﻠﯽ ﺑــﺎ ﻇﺮﻓﯿﺖ‬

‫ﺳﺮﯼ ‪ FMS-1650‬ﻣﺎﻧﯿﺘﻮﺭﻫﺎﯼ‬ ‫‪®BACnet‬‬

‫ﻋﺮﺿﻪ ﮐﺮﺩﻩ ﺍﺳــﺖ ﮐــﻪ ﺑﺎ ﺑﺮﺧــﻮﺭﺩﺍﺭﯼ ﺍﺯ‬

‫ﺷﺮﮐﺖ ‪ Triatek‬ﻣﺎﻧﯿﺘﻮﺭﻫﺎﯾﯽ ﺑﻪ ﺑﺎﺯﺍﺭ‬

‫ﻓﻨﺎﻭﺭﯼ ‪Hyper-Heating INVERTER‬‬

‫ﻋﺮﺿﻪ ﮐﺮﺩﻩ ﺍﺳــﺖ ﺑﺎ ﻣــﻮﺍﺭﺩ ﮐﺎﺭﺑﺮﺩﯼ ﺩﺭ‬

‫ﻗﺎﺩﺭﻧــﺪ ﺩﺭ ﺩﻣــﺎﯼ ‪ 5˚F‬ﺑﺮﺍﺑﺮ ‪ 100‬ﺩﺭﺻﺪ ﻭ‬

‫ﺑﯿﻤﺎﺭﺳﺘﺎﻥﻫﺎ‪ ،‬ﺁﺯﻣﺎﯾﺸــﮕﺎﻩﻫﺎ ﻭ ﺍﺗﺎﻕﻫﺎﯼ‬

‫ﺩﺭ ﺩﻣــﺎﯼ ˚‪ -13‬ﺑﺮﺍﺑﺮ ‪ 73‬ﺩﺭﺻﺪ ﺍﺯ ﻇﺮﻓﯿﺖ‬

‫ﺗﻤﯿﺰ ﮐﻪ ﺑﻪ ﺻﻮﺭﺕ ﻫﻤﺰﻣﺎﻥ ﻓﺸــﺎﺭ‪ ،‬ﺩﻣﺎ‪،‬‬

‫ﮔﺮﻣﺎﯾﺸــﯽ ﺧــﻮﺩ ﺭﺍ ﺍﺭﺍﺋﻪ ﺩﻫﻨــﺪ‪ .‬ﺍﺯ ﺩﯾﮕﺮ‬

‫ﺭﻃﻮﺑــﺖ ﻭ ﺗﻐﯿﯿــﺮﺍﺕ ﺁﺏ ﻭ ﻫﻮﺍﯾــﯽ ﺭﺍ ﺩﺭ‬

‫ﺣﺲﮔﺮﻫـﺎﯼ ﺟﺪﯾـﺪ ﺷـﺮﮐﺖ‬ ‫‪ILLUMRA‬‬

‫ﻗﺎﺑﻠﯿﺖﻫﺎﯼ ﺍﯾــﻦ ﻭﺍﺣﺪﻫﺎﯼ ﺟﺪﯾﺪ ﻣﯽﺗﻮﺍﻥ‬

‫ﺻﻔﺤﻪ ﻧﻤﺎﯾﺶ ﺧﻮﺩ ﻧﺸﺎﻥ ﻣﯽﺩﻫﻨﺪ‪ .‬ﺳﺮﯼ‬

‫ﺷــﺮﮐﺖ ‪ ILLUMRA‬ﺳــﺮﯼ ‪E3T‬‬

‫ﺑﻪ ﻭﺟﻮﺩ ﯾﮏ ﺳﯿﺴﺘﻢ ﺗﺼﻔﯿﻪ ﺳﻪﻣﺮﺣﻠﻪﺍﯼ ﻭ‬

‫‪ FMS-1650‬ﻣﺎﻧﯿﺘﻮﺭﻫﺎﯼ ‪ ®BACnet‬ﺍﺯ‬

‫ﺣﺲﮔﺮﻫــﺎﯼ ﺑﯽﺳــﯿﻢ ﺧﻮﺭﺷــﯿﺪﯼ ﺩﺭ‬

‫‪ 27000Btu/h‬ﻭ ﻗﺎﺑﻠﯿــﺖ ﻧﺼﺐ ﺭﻭﯼ ﺩﯾﻮﺍﺭ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺗــﺎﺯﻩﺍﯼ ﺍﺯ ﻃﺮﯾــﻖ ﮐﻨﺘﺮﻝﮐﻨﻨﺪﻩﻫــﺎﯼ‬ ‫‪ Vapor-Logic4‬ﺑــﻪ ﺁﻥ ﺍﻓــﺰﻭﺩﻩ ﺷــﺪﻩ‬ ‫ﺍﺳــﺖ‪ .‬ﻇﺮﻓﯿﺖ ﺍﯾﻦ ﺭﻃﻮﺑﺖﺯﻥﻫﺎ ﺍﺯ ‪ 2‬ﺗﺎ‬ ‫‪ 90‬ﮐﯿﻠﻮﮔﺮﻡ ﺑﺮ ﺳﺎﻋﺖ ﺍﻋﻼﻡ ﺷﺪﻩ ﺍﺳﺖ‪.‬‬

‫ﺻﻔﺤﻪ ‪ / 3‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻭ ﭘﻨﺠــﺮﻩﺍﯼ ﺧــﻮﺩ ﺭﺍ ﻭﺍﺭﺩ ﺑــﺎﺯﺍﺭ ﮐــﺮﺩ‪.‬‬

‫ﺍﯾﻦ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ﺍﻧﺠﻤﻦ ﻣﻬﻨﺪﺳﯽ ﺭﻭﺷﻨﺎﯾﯽ‬

‫ﺑﻪ ﻧﺴــﺨﻪ ‪ 2007‬ﻭ ‪ 15‬ﺍﻟﺤﺎﻗﯿﻪ ﺑﻪ ﻧﺴﺨﻪ‬

‫ﺍﯾــﻦ ﺣﺲﮔﺮﻫﺎﯼ ﺑﯽﺳــﯿﻢ ﺑــﺮﺍﯼ ﺍﻧﻮﺍﻉ‬

‫ﺁﻣﺮﯾــﮑﺎﯼ ﺷــﻤﺎﻟﯽ )‪ (IES‬ﺑــﺎ ﺍﻧﺠﻤــﻦ‬

‫‪ 2010‬ﺍﯾﻦ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ﺍﻓﺰﻭﺩﻩ ﺷﺪﻩ ﺍﺳﺖ‪.‬‬

‫ﺳﯿﺴﺘﻢﻫﺎﯼ ﻣﺤﺮﮎ ﺳﺎﺯﮔﺎﺭ ﻭ ﻣﺤﺼﻮﻻﺕ‬

‫‪ ASHRAE‬ﻣﺸــﺎﺭﮐﺖ ﺩﺍﺷﺘﻪ ﻭ ﺍﺯ ﺯﻣﺎﻥ‬

‫ﮐﻨﺘﺮﻝﮐﻨﻨــﺪﻩ ﺍﺯ ﺟﻤﻠــﻪ ﺗﺮﻣﻮﺳــﺘﺎﺕﻫﺎ‪،‬‬

‫ﺍﻧﺘﺸﺎﺭ ﺁﻥ ﺩﺭ ﺳــﺎﻝ ‪ 2007‬ﺗﺎ ﮐﻨﻮﻥ ‪109‬‬

‫ﺭﻟﻪﻫــﺎ‪ ،‬ﮐﻨﺘﺮﻝﮐﻨﻨﺪﻩﻫــﺎﯼ ﺍﺗــﺎﻕ ﻭ‬

‫ﺍﻟﺤﺎﻗﯿﻪ ﺑﻪ ﺁﻥ ﺍﻓﺰﻭﺩﻩ ﺷﺪﻩ ﺍﺳﺖ‪.‬‬

‫ﺷــﺒﮑﻪﻫﺎﯼ ‪ BACnet‬ﻭ ‪ Ethernet‬ﺑﺮﺍﯼ‬ ‫ﺗﻠﻔﯿﻖ ﺑﺎ ﺳﯿﺴــﺘﻢﻫﺎﯼ ﻣﺪﯾﺮﯾﺖ ﺍﻧﺮﮊﯼ ﺍﺯ‬ ‫ﭘﺮﻭﺗــﮑﻞ ‪ EnOcean‬ﺍﺳــﺘﻔﺎﺩﻩ ﻣﯽﮐﻨﻨﺪ‪.‬‬ ‫ﺣﺲﮔﺮ ‪ E3T‬ﺑﺎ ﺑﺮﺧﻮﺭﺩﺍﺭﯼ ﺍﺯ ﻗﺎﺑﻠﯿﺖﻫﺎﯼ‬ ‫ﻻﺯﻡ ﻋﻤﻠﮑﺮﺩ ﺳﯿﺴــﺘﻢ ﻣﺮﺑﻮﻃﻪ ﺩﺭ ﺗﺎﺭﯾﮑﯽ‬ ‫ﺭﺍ ﺑﺮﺍﯼ ﭼﻨﺪ ﺭﻭﺯ ﺍﻣﮑﺎﻥﭘﺬﯾﺮ ﻣﯽﺳﺎﺯﺩ‪.‬‬

‫ﺷـﺮﮐﺖﮐﻨﻨﺪﮔﺎﻥ ﺩﺭ ﺭﻗﺎﺑـﺖ‬ ‫ﺍﻣﮑﺎﻥﺳﻨﺠﯽ ‪CFD‬‬ ‫ﺍﻧﺠﻤــﻦ ‪ ASHRAE‬ﺑــﺮﺍﯼ ﺍﺭﺯﯾﺎﺑﯽ‬

‫ﻫﻤﮑﺎﺭﯼ ‪ ASHRAE‬ﻭ ‪ IES‬ﺩﺭ‬ ‫ﺗﻘﻮﯾﺖ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ‪90.2‬‬

‫‪ CFD‬ﺩﺭ ﺟﺴﺖﻭﺟﻮﯼ ﻣﺴﺎﺑﻘﻪﺩﻫﻨﺪﮔﺎﻧﯽ‬

‫ﺍﻧﺠﻤــﻦ ‪ ASHRAE‬ﻭ ﺍﻧﺠﻤــﻦ‬

‫ﻫﺴــﺘﻨﺪ ﺗــﺎ ﺍﺯ ﺍﯾﻦ ﻃﺮﯾــﻖ ﺿﺮﯾﺐ ﺍﺗﻼﻑ‬

‫ﻣﻬﻨﺪﺳــﯽ ﺭﻭﺷــﻨﺎﯾﯽ ﺁﻣﺮﯾﮑﺎﯼ ﺷــﻤﺎﻟﯽ‬

‫ﺷﺒﮑﻪﻫﺎﯼ ﮐﺎﻧﺎﻟﯽ ﺑﻪ ﻟﺤﺎﻅ ﻋﺪﺩﯼ ﺗﻌﯿﯿﻦ‬

‫)‪ (IES‬ﻫﻤﮑﺎﺭﯼﻫﺎﯾﯽ ﺭﺍ ﺩﺭ ﺯﻣﯿﻨﻪ ﺍﺭﺗﻘﺎﯼ‬

‫ﺷــﻮﺩ‪ .‬ﺑﺮﻧﺪﮔﺎﻥ ﺭﻗﺎﺑﺖ ‪CFD Shootout‬‬

‫ﺳــﻄﺢ ﻣﻼﺣﻈــﺎﺕ ﺍﺳــﺘﺎﻧﺪﺍﺭﺩ ‪ANSI/‬‬

‫ﺍﻣﮑﺎﻥﺳﻨﺠﯽ ﻭ ﺩﻗﺖ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﺭﻭﺵﻫﺎﯼ‬

‫ﻧﺘﺎﯾــﺞ ﺧــﻮﺩ ﺭﺍ ﺩﺭ ﻭﺭﻗﻪﻫــﺎﯼ ﻓﻨــﯽ ﮐﻪ‬

‫ﺳﯿﺴـﺘﻢﻫﺎﯼ ﺗﻬﻮﯾـﻪ ﺳـﻘﻔﯽ‬ ‫ﻣﻨﺎﺳـﺐ ﺑﺮﺍﯼ ﺟﺮﯾﺎﻥﻫﺎﯼ ﻫﻮﺍﯾﯽ‬ ‫ﮔﺮﻡ ﻭ ﺁﻟﻮﺩﻩ‬

‫ﮐﻢﺍﺭﺗﻔﺎﻉ‪ ،‬ﺑﺎ ﯾﮑﺪﯾﮕﺮ ﺁﻏﺎﺯ ﮐﺮﺩﻩﺍﻧﺪ‪ .‬ﻫﯿﺎﺕ‬

‫ﻣﻮﺗــﻮﺭ ﺳﯿﺴــﺘﻢﻫﺎﯼ ﺗﻬﻮﯾﻪ ﺳــﻘﻔﯽ‬

‫ﻣﺪﯾــﺮﻩ ‪ ASHRAE‬ﺩﺭ ﺳــﺎﻝ ‪ 2009‬ﺑﺮ‬

‫ﺷــﺮﮐﺖ ‪ Continental Fan‬ﺑــﺎ ﻇﺮﻓﯿﺖ‬

‫ﺍﺭﺗﻘﺎﯼ ‪ 30‬ﺩﺭﺻﺪﯼ ﺑﺎﺯﺩﻩ ﺍﻧﺮﮊﯼ ﻧﺴــﺒﺖ‬

‫ﺗﻬﻮﯾــﻪ ‪ 61000cfm‬ﺩﺭ ﻓﻀﺎﻫﺎﯼ ﺧﺎﺭﺟﯽ‬

‫ﺑــﻪ ﻧﺴــﺨﻪ ‪ 2004‬ﺗﺎﮐﯿﺪ ﻭﺭﺯﯾــﺪ‪ .‬ﮐﻤﯿﺘﻪ‬

‫ﻣﻄﺎﻟﻌﻪ ﮐﯿﻔﯿﺖ ﻫﻮﺍﯼ ﻓﺮﻭﺷﮕﺎﻩﻫﺎﯼ‬ ‫ﺧﺮﺩﻩﻓﺮﻭﺷﯽ‬

‫ﻗــﺮﺍﺭ ﻣﯽﮔﯿﺮﻧﺪ ﻭ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺁﻥﻫﺎ ﺑﺮﺍﯼ‬

‫ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ‪ 90.2‬ﻧﯿﺰ ﺩﺭ ﻧﻈﺮ ﺩﺍﺭﺩ ﺩﺭ ﺳﺎﻝ‬

‫ﺩﺭ ﯾــﮏ ﭘــﺮﻭﮊﻩ ﺗﺤﻘﯿﻘﺎﺗــﯽ ﺑــﺎ‬

‫ﺟﺮﯾﺎﻥﻫــﺎﯼ ﻫﻮﺍﯾﯽ ﮔﺮﻡ ﻭ ﺁﻟﻮﺩﻩ ﻣﻨﺎﺳــﺐ‬

‫ﺟﺎﺭﯼ ﺑﻪ ﺑﺮﺭﺳــﯽ ﺗﺎﺛﯿﺮﮔــﺬﺍﺭﯼ ﺗﻐﯿﯿﺮﺍﺕ‬

‫ﺳــﺮﻣﺎﯾﻪﮔﺬﺍﺭﯼ ‪ 1.5‬ﻣﯿﻠﯿــﻮﻥ ﺩﻻﺭﯼ‬

‫ﺍﺳــﺖ‪ .‬ﻭﺟﻮﺩ ﯾﮏ ﺩﻣﭙﺮ ﺗﺨﻠﯿﻪ ﭘﺮﻭﺍﻧﻪﺍﯼ ﻭ‬

‫ﭘﯿﺸﻨﻬﺎﺩﯼ ﺑﭙﺮﺩﺍﺯﺩ‪.‬‬

‫ﻣﻮﺳﺴــﻪ ﻣﻠــﯽ ﺍﺳــﺘﺎﻧﺪﺍﺭﺩﻫﺎ ﻭ ﻓﻨﺎﻭﺭﯼ‬

‫ﺍﻧﺘﺸـﺎﺭ ﻧﺴـﺨﻪﻫﺎﯼ ﺟﺪﯾـﺪ‬ ‫ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ‪ASHRAE‬‬

‫)‪ ،(NIST‬ﻣﻘﺮﺭ ﺷــﺪﻩ ﺍﺳﺖ ﺗﺎ ﺭﻭﺵﻫﺎﯼ‬

‫ﺍﺯ ﺟﻤﻠــﻪ ﻣــﻮﺍﺭﺩ ﺩﯾﮕﺮ ﻭﯾﮋﮔﯽﻫــﺎﯼ ﺍﯾﻦ‬ ‫ﻣﺤﺼﻮﻝ ﺑﻪ ﺷﻤﺎﺭ ﻣﯽﺭﻭﻧﺪ‪.‬‬

‫ﻧﺴﺨﻪ ‪ 2010‬ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ‪90.1‬‬

‫ﺑــﺎﺯﺩﻩ ﺍﻧﺮﮊﯼ ﺳــﺎﺧﺘﻤﺎﻥﻫﺎﯼ ﻣﺴــﮑﻮﻧﯽ‬

‫ﻧﺴــﺨﻪﻫﺎﯼ ‪ 2010‬ﺍﺳــﺘﺎﻧﺪﺍﺭﺩﻫﺎﯼ‬ ‫‪ ASHRAE‬ﺩﺭ ﺯﻣﯿﻨﻪ ﻣﺒﺮﺩﻫﺎ ﺑﻪ ﺻﻮﺭﺕ‬

‫ﺍﺭﺍﺋﻪ ﺧﻮﺍﻫﻨﺪ ﮐﺮﺩ ﻭ ﻣﻤﮑﻦ ﺍﺳــﺖ ﺑﺘﻮﺍﻧﻨﺪ‬ ‫ﺟﻮﺍﯾﺰ ﻧﻘﺪﯼ ﺩﺭﯾﺎﻓﺖ ﮐﻨﻨﺪ‪.‬‬

‫ﺑﻬﺒــﻮﺩ ﺷــﺮﺍﯾﻂ ﺗﻬﻮﯾﻪ ﻭ ﮐﯿﻔﯿــﺖ ﻫﻮﺍﯼ‬ ‫ﺩﺍﺧﻞ ﻓﺮﻭﺷــﮕﺎﻩﻫﺎﯼ ﺑﺰﺭﮒ ﺧﺮﺩﻩﻓﺮﻭﺷﯽ‬ ‫ﻣﻮﺭﺩ ﻣﻄﺎﻟﻌﻪ ﻗﺮﺍﺭ ﮔﯿﺮﺩ‪ .‬ﺩﺭ ﺍﯾﺎﻻﺕ ﻣﺘﺤﺪﻩ‬ ‫ﻧﺰﺩﯾﮏ ﺑﻪ ‪ 1.36‬ﻣﯿﻠﯿﻮﻥ ﻣﺘﺮ ﻣﺮﺑﻊ ﻓﻀﺎ ﺑﻪ‬

‫ﻧﺴــﺨﻪ ﺗﺎﺯﻩ ﺍﻧﺘﺸــﺎﺭﯾﺎﻓﺘﻪ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ‬

‫ﯾﮏ ﺑﺴﺘﻪ ﻣﻨﺘﺸﺮ ﺷﺪ‪ .‬ﺩﺭ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ‪ 34‬ﮐﻪ‬

‫‪ 90.1‬ﺍﻧﺠﻤــﻦ ‪ ASHRAE‬ﺩﺭ ﻗﯿــﺎﺱ‬

‫ﺗﻠﻔﯿﻘﯽ ﺍﺯ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ‪ANSI/ASHRAE‬‬

‫ﺍﯾﻦ ﻓﺮﻭﺷﮕﺎﻩﻫﺎﯼ ﺧﺮﺩﻩﻓﺮﻭﺷﯽ ﺍﺧﺘﺼﺎﺹ‬

‫ﺑﺎ ﻧﺴــﺨﻪ ‪ 2004‬ﺍﯾﻦ ﺍﺳــﺘﺎﻧﺪﺍﺭﺩ ﻣﻮﺟﺐ‬

‫‪ ،2010-34‬ﺑــﺎ ﻣﺤﻮﺭﯾﺖ ﻣﻮﺿﻮﻉ ﻧﻘﺶ ﻭ‬

‫ﯾﺎﻓﺘﻪ ﺍﺳــﺖ ﺍﻣﺎ ﺍﻃﻼﻋﺎﺕ ﺍﻧﺪﮐﯽ ﭘﯿﺮﺍﻣﻮﻥ‬

‫ﺍﻓﺰﺍﯾﺶ ‪ 20‬ﺩﺭﺻﺪﯼ ﺑﺎﺯﺩﻩ ﺍﻧﺮﮊﯼ ﺷﺪ‪ .‬ﺩﺭ‬

‫ﺍﻣﻨﯿﺖ ﻃﺒﻘﻪﺑﻨﺪﯼ ﻣﺒﺮﺩﻫﺎ ﻭ ﺍﺳــﺘﺎﻧﺪﺍﺭﺩ‬

‫ﮐﯿﻔﯿﺖ ﻭ ﺗﻬﻮﯾﻪ ﻫﻮﺍ ﺩﺭ ﺁﻥﻫﺎ ﺩﺭ ﺩﺳﺘﺮﺱ‬

‫ﻫﻤﯿﻦ ﺍﺭﺗﺒﺎﻁ ﻟﯿﻦ ﺟﯽ ﺑﻠﻨﺠﺮ )‪Lynn G‬‬

‫‪ 2010-ANSI/ASHRA 15‬ﺑﺎ ﻣﻮﺿﻮﻉ‬

‫ﺍﺳــﺖ‪ ASHRAE .‬ﻣﺴﻮﻭﻟﯿﺖ ﺍﯾﻦ ﭘﺮﻭﮊﻩ‬

‫‪ ،(Bellenger‬ﺭﯾﯿﺲ ﺍﯾﻦ ﺍﻧﺠﻤﻦ‪ ،‬ﺍﻇﻬﺎﺭ‬

‫ﺍﺳــﺘﺎﻧﺪﺍﺭﺩ ﺍﯾﻤﻨــﯽ ﺑﺮﺍﯼ ﺳﯿﺴــﺘﻢﻫﺎﯼ‬

‫ﺭﺍ ﺑــﻪ ﺩﮐﺘﺮ ﺟﻔﺮﯼ ﺳــﯿﮕﻞ ﺍﺯ ﺩﺍﻧﺸــﮕﺎﻩ‬

‫ﺩﺍﺷﺖ‪» :‬ﺍﯾﻦ ﺍﺳــﺘﺎﻧﺪﺍﺭﺩ ﻣﻮﺟﺐ ﺍﺭﺗﻘﺎﯼ‬

‫ﺗﺒﺮﯾﺪ‪ ،‬ﺍﺳﺖ‪ ،‬ﺑﻪ ﺭﻭﺵ ﻧﺎﻡﮔﺬﺍﺭﯼ ﻣﺒﺮﺩﻫﺎ‬

‫ﺗﮕﺰﺍﺱ ﻭ ﺩﮐﺘﺮ ﯾﻠﻨﺎ ﺍﺳــﺮﺑﺮﯾﮏ ﺍﺯ ﺩﺍﻧﺸﮕﺎﻩ‬

‫ﭼﺸــﻤﮕﯿﺮ ﺑﺎﺯﺩﻩ ﺍﻧﺮﮊﯼ ﺩﺭ ﺳﺎﺧﺘﻤﺎﻥﻫﺎﯼ‬

‫ﻭ ﻃﺒﻘﻪﺑﻨﺪﯼ ﺍﻃﻼﻋﺎﺕ ﻣﺮﺑﻮﻁ ﺑﻪ ﺳــﻤﻮﻡ‬

‫ﭘﻦ‪ ،‬ﺳــﭙﺮﺩﻩ ﺍﺳــﺖ‪ .‬ﺧﺒﺮﻫﺎﯼ ﻣﻨﺘﺸــﺮﻩ‬

‫ﺟﺪﯾﺪ ﻭ ﺳــﺎﺧﺘﻤﺎﻥﻫﺎﯼ ﺑﺎﺯﺳﺎﺯﯼﺷــﺪﻩ‬

‫ﻭ ﻗﺎﺑﻠﯿﺖ ﺍﺷﺘﻌﺎﻝ ﺁﻥﻫﺎ ﺍﺷﺎﺭﻩ ﺷﺪﻩ ﺍﺳﺖ‪.‬‬

‫ﺣﺎﮐﯽ ﺍﺯ ﺁﻥ ﺍﺳﺖ ﮐﻪ ﺍﺣﺘﻤﺎﻝ ﻣﯽﺭﻭﺩ ﺍﯾﻦ‬

‫ﺧﻮﺍﻫﺪ ﺷــﺪ‪ «.‬ﮔﻔﺘﻨﯽ ﺍﺳــﺖ ﺩﺭ ﺗﻮﺳﻌﻪ‬

‫ﺩﺭ ﺍﺳــﺘﺎﻧﺪﺍﺭﺩ ‪ 37 ،2010-34‬ﺍﻟﺤﺎﻗﯿــﻪ‬

‫ﭘﺮﻭﮊﻩ ﺩﺭ ﺩﺳﺎﻣﺒﺮ ‪ 2012‬ﺑﻪ ﭘﺎﯾﺎﻥ ﺭﺳﺪ‪.‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﯾﮏ ﭘﺮﺍﻭﻧﻪ ﻣﺤﻮﺭﯼ ﻣﻘﺎﻭﻡ ﺩﺭ ﺑﺮﺍﺑﺮ ﺟﺮﻗﻪ‪،‬‬

‫‪ ،ASHRAE 90.2‬ﺑــﺎ ﻣﺤﻮﺭﯾﺖ ﻃﺮﺍﺣﯽ‬

‫‪ ASHRAE‬ﺁﻥﻫﺎ ﺭﺍ ﻣﻨﺘﺸــﺮ ﻣﯽﺳــﺎﺯﺩ‬

‫ﺻﻔﺤﻪ ‪ / 4‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻋﻠﻤﻰ‬

‫ﺁﺏ ﻣﺼﺮﻓﻰ ﺩﺭﺳﻴﺴﺘﻢﻫﺎﻯ‬ ‫ﺳﺮﻣﺎﻳﺶ ﺗﺒﺨﻴﺮﻯ‬ ‫ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﺁﺏ ﺩﺭ ﺳﯿﺴﺘﻢﻫﺎﯼ ﺳﺮﻣﺎﯾﺶ‬

‫ﻣﯽﺷــﻮﺩ‪ ،‬ﺑﺮﺍﯼ ﺭﺍﻩﺍﻧﺪﺍﺯﯼ ﮐﻨﺪﺍﻧﺴــﻮﺭﻫﺎﯼ‬

‫ﺳﯿﺴﺘﻢ ﺳﺮﻣﺎﯾﺸﯽ‪ ،‬ﺑﻪ ﺷﺮﺍﯾﻂ ﺁﺏ ﻭ ﻫﻮﺍﯾﯽ‬

‫ﺗﺒﺨﯿﺮﯼ‪ ،‬ﯾﮑــﯽ ﺍﺯ ﺍﻟﺰﺍﻣﺎﺕ ﻋﻤﺪﻩ ﻣﺤﯿﻄﯽ‬

‫ﺗﺒﺨﯿﺮﯼ ﯾﺎ ﺑﺮﺝﻫﺎﯼ ﺧﻨﮏﮐﻦ ﮐﻪ ﺑﺮﺍﯼ ﺩﻓﻊ‬

‫ﻣﺤﻞ ﺑﺴﺘﮕﯽ ﺩﺍﺭﺩ‪ .‬ﻧﺮﺥ ﺑﺎﻻ ﺩﺭ ﺯﯾﺮﺁﺏﮐﺸﯽ‬

‫ﺩﺭ ﺷــﺮﺍﯾﻂ ﺁﺏﻭﻫﻮﺍﯾﯽ ﮔﺮﻡ ﻭ ﺧﺸﮏ ﺍﺳﺖ‪.‬‬

‫ﺣﺮﺍﺭﺕ ﺑﻪﮐﺎﺭ ﺑﺮﺩﻩ ﻣﯽﺷﻮﻧﺪ‪ ،‬ﺑﻪ ﺁﺏ ﺍﺣﺘﯿﺎﺝ‬

‫ﻭ ﺗﻌﻮﯾﺾ ﺗﺪﺭﯾﺠﯽ ﻣﺘﻨﺎﻭﺏ ﺁﺏ‪ ،‬ﻓﻘﻂ ﺗﺤﺖ‬

‫ﺑﻪ ﻣﻨﻈﻮﺭ ﺩﺳــﺘﯿﺎﺑﯽ ﺑﻪ ﺟﻨﺒﻪﻫﺎﯼ ﻣﺼﺮﻑ‬

‫ﺩﺍﺭﺩ‪ .‬ﺍﻟﮑﺘﺮﯾﺴﯿﺘﻪ ﻣﺼﺮﻓﯽ ﺩﺭ ﺳﯿﺴﺘﻢﻫﺎﯼ‬

‫ﺷﺮﺍﯾﻂ ﺳﺨﺖ ﮐﯿﻔﯿﺖ ﺁﺏ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﺍﺳﺖ‪.‬‬

‫ﺁﺏ‪ ،‬ﻣﯿﺰﺍﻥ ﺁﺏ ﻣﺼﺮﻓﯽ ﺩﺭ ﻣﺪﺍﺭﺱ ﺭﺍ ﺑﺮﺍﯼ‬

‫ﺳﺮﻣﺎﯾﺶ ﺗﺮﺍﮐﻤﯽ‪ ،‬ﺍﺯ ﻟﺤﺎﻅ ﺗﺎﺛﯿﺮ ﺳﺮﻣﺎﯾﺸﯽ‪،‬‬

‫ﺑﺮﺧﯽ ﺍﺯ ﻣﺼﺮﻑﮐﻨﻨﺪﮔﺎﻥ ﺑﺴﺘﺮﻫﺎﯼ ﭘﻮﺷﺎﻟﯽ‬

‫ﻣﺼﺎﺭﻑ ﺳــﺮﻭﯾﺲﻫﺎﯼ ﺑﻬﺪﺍﺷﺘﯽ‪ ،‬ﺣﻤﺎﻡ‪،‬‬

‫ﺩﺭ ﻣﻘﺎﯾﺴــﻪ ﺑــﺎ ﺳﯿﺴــﺘﻢﻫﺎﯼ ﺳــﺮﻣﺎﯾﺶ‬

‫ﺍﺭﺯﺍﻥﻗﯿﻤــﺖ‪ ،‬ﺍﺯ ﺯﯾﺮﺁﺏﮐﺸــﯽ ﻭ ﺗﻌﻮﯾــﺾ‬

‫ﺗﺒﺨﯿﺮﯼ ﺑﯿﺸــﺘﺮ ﺧﻮﺍﻫﺪ ﺑﻮﺩ‪ .‬ﻣﻘﺪﺍﺭ ﻫﺰﯾﻨﻪ‬

‫ﺗﺪﺭﯾﺠﯽ ﻣﺘﻨــﺎﻭﺏ ﺁﺏ ﺻﺮﻑﻧﻈﺮ ﮐﺮﺩﻩ ﻭ ﺩﺭ‬

‫ﺁﺏ ﺩﺭ ﺍﯾﻦ ﻓﺮﺍﯾﻨﺪﻫﺎ ﻣﻌﻤﻮﻻ ﮐﻤﺘﺮ ﺍﺯ ﻫﺰﯾﻨﻪ‬

‫ﻋﻮﺽ ﯾﮏ ﯾﺎ ﺩﻭ ﺑﺎﺭ ﺩﺭ ﻫﺮ ﻓﺼﻞ ﺑﺴــﺘﺮﻫﺎ ﺭﺍ‬

‫ﺍﻟﮑﺘﺮﯾﺴﯿﺘﻪ ﻣﺼﺮﻓﯽ ﺍﺳﺖ ﺍﻣﺎ ﺩﺭ ﻫﺮ ﺩﻭ ﻧﻮﻉ‬

‫ﺗﻌﻮﯾﺾ ﻣﯽﮐﻨﻨﺪ‪.‬‬

‫ﺳﺮﺍﯾﺪﺍﺭﯼ‪ ،‬ﺭﺳﺘﻮﺭﺍﻥ‪ ،‬ﺷﺴﺘﺸﻮ ﻭ ﺳﺮﻣﺎﯾﺶ‪،‬‬ ‫ﺩﺭ ﻧﻈﺮ ﺑﮕﯿﺮﯾﺪ‪ .‬ﺳــﺎﺯﻣﺎﻥ ﻣﻬﻨﺪﺳﯿﻦ ﺍﯾﺎﻟﺖ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﻧﯿﻮﻣﮑﺰﯾﮑﻮ ﺑﻪ ﻃﻮﺭ ﺗﺨﻤﯿﻨﯽ ﺍﻇﻬﺎﺭ ﻣﯽﮐﻨﺪ‬ ‫ﮐــﻪ ﻣﺪﺍﺭﺱ ﺑﻪ ﺍﺯﺍﯼ ﻫﺮ ﻧﻔــﺮ ﺩﺭ ﺭﻭﺯ‪ 15 ،‬ﺗﺎ‬

‫ﻓﺮﺍﯾﻨﺪ‪ ،‬ﺁﺏ ﻧﻘﺶ ﻋﻤﺪﻩﺍﯼ ﺍﯾﻔﺎ ﻣﯽﻧﻤﺎﯾﺪ‪.‬‬

‫ﺣﺎﻝ ﺑﻪ ﺍﯾﻦ ﻣﻮﺿﻮﻉ ﻣﯽﭘﺮﺩﺍﺯﯾﻢ ﮐﻪ ﺍﯾﻦ‬

‫‪ 25‬ﮔﺎﻟﻦ ﺁﺏ ﺭﺍ ﺑﺮﺍﺳﺎﺱ ﺍﻣﮑﺎﻧﺎﺗﯽ ﮐﻪ ﺩﺍﺭﻧﺪ‪،‬‬

‫ﻣﯿﺰﺍﻥ ﻣﺼــﺮﻑ ﺁﺏ ﺍﺯ ﻣﻨﺎﺑﻊ ﻣﺨﺘﻠﻒ‪،‬‬

‫ﺍﻟﮕﻮﯼ ﻣﺼﺮﻑ ﭼﮕﻮﻧﻪ ﺑﺎ ﺁﺏ ﻣﺼﺮﻑ ﺷــﺪﻩ‬

‫ﻣﺘﻔﺎﻭﺕ ﺍﺳــﺖ‪ .‬ﻋﻮﺍﻣﻠﯽ ﮐﻪ ﺑﺮ ﻣﺼﺮﻑ ﺁﺏ‬

‫ﺑــﺮﺍﯼ ﺗﻮﻟﯿﺪ ﺑﺮﻕ ﺑﻪ ﻣﻨﻈــﻮﺭ ﺭﺍﻩﺍﻧﺪﺍﺯﯼ ﯾﮏ‬

‫ﻣﻮﺭﺩ ﺍﺳــﺘﻔﺎﺩﻩ ﻗــﺮﺍﺭ ﻣﯽﺩﻫﻨــﺪ‪ .‬ﻋﻼﻭﻩ ﺑﺮ‬

‫ﺗﺎﺛﯿﺮﮔــﺬﺍﺭ ﻫﺴــﺘﻨﺪ‪ ،‬ﻋﺒﺎﺭﺗﻨﺪ ﺍﺯ‪ :‬ﺷــﺮﺍﯾﻂ‬

‫ﺧﻨﮏﮐﻨﻨﺪﻩ ﺗﺒﺨﯿﺮﯼ ﻣﻘﺎﯾﺴﻪ ﻣﯽﺷﻮﺩ؟ ﺑﻪ‬

‫ﻣﺼﺮﻑ ﺁﺏ‪ ،‬ﻓﺮﺍﯾﻨﺪ ﺗﻮﻟﯿﺪ ﺍﻟﮑﺘﺮﯾﺴﯿﺘﻪ ﺑﺮﺍﯼ‬

‫ﺟﻮﯼ‪ ،‬ﺗﺎﺛﯿﺮ ﺑﺴــﺘﺮ‪ ،‬ﺳــﺮﻋﺖ ﻫﻮﺍﯼ ﺑﺴﺘﺮ‬

‫ﺍﯾﻦ ﻣﻨﻈﻮﺭ‪ ،‬ﻣﯿﺎﻧﮕﯿﻦ ﺳــﺎﻟﯿﺎﻧﻪ ﺁﺏ ﻣﺼﺮﻓﯽ‬

‫ﻣﺼﺎﺭﻑ ﮔﻮﻧﺎﮔﻮﻥ ﺍﺯ ﺁﺏ ﺍﺳــﺘﻔﺎﺩﻩ ﻣﯽﻧﻤﺎﯾﺪ‬

‫ﺩﺭ ﺳﯿﺴــﺘﻢ ﺳــﺮﻣﺎﯾﺶ ﺗﺒﺨﯿﺮﯼ‪ ،‬ﺳﯿﺴﺘﻢ‬

‫ﺩﺭ ﺑﺮﺝﻫــﺎﯼ ﺧﻨﮏﮐﻦ ﻭ ﺳــﺎﯾﺮ ﻣﺼﺎﺭﻑ ﺩﺭ‬

‫ﮐﻪ ﻣﻬﻢﺗﺮﯾﻦ ﺁﻥ ﺩﻓﻊ ﺣﺮﺍﺭﺕ ﺗﻮﺳﻂ ﺑﺮﺝﻫﺎﯼ‬

‫ﺗﻮﺯﯾــﻊ ﺁﺏ ﻭ ﻧــﺮﺥ ﺯﯾﺮﺁﺏﮐﺸــﯽ ﻭ ﺗﻌﻮﯾﺾ‬

‫ﺍﯾﺴــﺘﮕﺎﻩ ﺗﻮﻟﯿﺪ ﺑﺮﻕ ﺍﻟﮑﺘﺮﯾﺴــﯿﺘﻪ »ﺳــﺎﻥ‬

‫ﺧﻨﮏﮐﻦ ﺗﺒﺨﯿﺮﯼ ﺍﺳﺖ‪ .‬ﺑﻨﺎﺑﺮﺍﯾﻦ ﻫﻨﮕﺎﻣﯽ‬

‫ﺗﺪﺭﯾﺠﯽ ﺁﺏ‪ .‬ﻧﺘﺎﯾﺞ ﺗﺠﺰﯾﻪ ﻭ ﺗﺤﻠﯿﻠﯽ ﮐﻪ ﺩﺭ‬

‫ﺧــﻮﺁﻥ«‪ ،‬ﻣﻌــﺎﺩﻝ ‪ 500‬ﮔﺎﻟــﻦ ﺩﺭ ﻣﮕﺎﻭﺍﺕ‬

‫ﮐﻪ ﺑﺮﺍﯼ ﭘﻤﭙــﺎﮊ ﮔﺎﺯ ﻃﺒﯿﻌﯽ ﯾﺎ ﺁﺏ ﺑﻪ ﻣﺤﻞ‬

‫ﺧﺼﻮﺹ ﻣﺼﺮﻑ ﺁﺏ ﺩﺭ ﻣﺪﺍﺭﺳﯽ ﺑﺎ ﺳﯿﺴﺘﻢ‬

‫ﺳــﺎﻋﺖ‪ ،‬ﯾﺎ ‪ 0.5‬ﮔﺎﻟﻦ ﺩﺭﮐﯿﻠﻮﻭﺍﺕ ﺳــﺎﻋﺖ‬

‫ﺳﺮﻣﺎﯾﺶ ﺗﺒﺨﯿﺮﯼ ‪ 17,000‬ﻓﻮﺕ ﻣﮑﻌﺐ ﺩﺭ‬

‫ﺩﺭ ﻧﯿﺮﻭﮔﺎﻩﻫــﺎ ﺑﺮﺁﻭﺭﺩ ﺷــﺪﻩ ﺍﺳــﺖ‪ .‬ﺩﻣﺎﯼ‬

‫ﺩﻗﯿﻘﻪ‪ ،‬ﺳــﺮﻣﺎﯾﺶ ﺗﺒﺨﯿﺮﯼ ﻣﺴﺘﻘﯿﻢ ‪ -‬ﻏﯿﺮ‬

‫ﻫﻮﺍ ﺩﺭ ﺗﺎﺑﺴــﺘﺎﻥ ﻣﯽﺗﻮﺍﻧــﺪ ﻣﻮﺟﺐ ﺍﻓﺰﺍﯾﺶ‬

‫ﻣﺴﺘﻘﯿﻢ ﻭ ﺳﯿﺴﺘﻢﻫﺎﯼ ﻣﺮﮐﺐ ﻣﺴﺘﻘﯿﻢ ‪-‬‬

‫ﻣﻘــﺪﺍﺭ ﺫﮐﺮ ﺷــﺪﻩ‪ ،‬ﺗﺎ ‪ 0.95‬ﮔﺎﻟــﻦ ﺑﻪ ﺍﺯﺍﯼ‬

‫ﺗﺮﺍﮐﻤﯽ ﺍﻧﺒﺴــﺎﻁ ﻣﺴــﺘﻘﯿﻢ ﺍﻧﺠﺎﻡ ﺷﺪﻩ ﺩﺭ‬

‫ﻫﺮ ﮐﯿﻠﻮﻭﺍﺕ ﺳــﺎﻋﺖ ﺩﺭ ﻧﯿﺮﻭﮔﺎﻩﻫﺎ ﺷــﻮﺩ‪.‬‬

‫ﺟﺪﻭﻝ )‪ (1‬ﺍﺭﺍﺋﻪ ﺷﺪﻩ ﺍﺳﺖ‪ .‬ﻫﻤﭽﻨﯿﻦ ﺍﯾﻦ‬

‫ﺍﯾــﻦ ﻣﻘﺪﺍﺭ‪ ،‬ﻣﯿــﺰﺍﻥ ﺁﺏ ﻣــﻮﺭﺩ ﻧﯿﺎﺯ ﺟﻬﺖ‬

‫ﻣﯽﮐﻨﺪ‪ .‬ﺩﯾﺪﮔﺎﻫﯽ ﺍﺟﻤﺎﻟﯽ ﺩﺭ ﺻﺮﻓﻪﺟﻮﯾﯽ‬

‫ﺟﺪﻭﻝ ﻧﺸﺎﻥ ﻣﯽﺩﻫﺪ ﮐﻪ ﻣﻘﺪﺍﺭ ﻋﻤﺪﻩﺍﯼ ﺍﺯ‬

‫ﻣﻌــﺎﺩﻥ‪ ،‬ﻓﺮﺍﯾﻨﺪﻫــﺎﯼ ﮔﻮﻧﺎﮔــﻮﻥ ﻭ ﺣﻤﻞ‬

‫ﺁﺏ ﺭﺍ ﺑﺎ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺩﺳﺘﮕﺎﻩ ﺭﺳﻮﺏﮔﯿﺮﯼ‬

‫ﺯﻏﺎﻝﺳﻨﮓ ﻻﺯﻡ ﺑﺮﺍﯼ ﺗﻮﻟﯿﺪ ﺍﻟﮑﺘﺮﯾﺴﯿﺘﻪ ﺭﺍ‬

‫ﺁﺏ‪ ،‬ﺑﺮ ﺭﻭﯼ ﻣﯿﺰﺍﻥ ﺁﺏ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﺑﺮﺍﯼ ﻧﯿﻞ‬

‫ﺗﺸﺘﮏ ﻣﺘﻨﺎﻭﺏ ﻣﯽﺗﻮﺍﻥ ﺫﺧﯿﺮﻩ ﻧﻤﻮﺩ‪ .‬ﻧﺮﺥ‬

‫ﺷﺎﻣﻞ ﻧﻤﯽﺷــﻮﺩ‪ .‬ﻋﺪﻡ ﺑﺎﺯﺩﻫﯽ ﻣﻮﺟﻮﺩ ﺩﺭ‬

‫ﺑﻪ ﺍﻫﺪﺍﻑ ﻣــﻮﺭﺩ ﻧﻈﺮ ﺗﻤﺮﮐﺰ ﻣﯽﯾﺎﺑﺪ‪ .‬ﺗﻮﺍﻧﯽ‬

‫ﺯﯾﺮﺁﺏﮐﺸــﯽ ﻭ ﺗﻌﻮﯾﺾ ﺗﺪﺭﯾﺠــﯽ ﺁﺏ ﻻﺯﻡ‬

‫ﺍﻧﺘﻘﺎﻻﺕ ﺍﻟﮑﺘﺮﯾﮑﯽ‪ ،‬ﻣﻮﺟﺐ ﻣﯽﺷﻮﺩ‪ 15 ،‬ﺗﺎ‬

‫ﮐﻪ ﺗﻮﺳــﻂ ﺍﻟﮑﺘﺮﯾﺴــﯿﺘﻪ ﺩﺭ ﻧﯿﺮﻭﮔﺎﻩ ﺗﻮﻟﯿﺪ‬

‫ﺑﺮﺍﯼ ﮐﻨﺘﺮﻝ ﺗﺠﻤﻊ ﺟﺎﻣﺪﺍﺕ ﺑﺮ ﺭﻭﯼ ﺑﺴــﺘﺮ‬

‫‪ 30٪‬ﺍﺯ ﺗﻮﺍﻥ ﺗﻮﻟﯿﺪﯼ‪ ،‬ﺩﺭ ﻓﺮﺍﯾﻨﺪﻫﺎﯼ ﺍﻧﺘﻘﺎﻝ‬

‫ﻋﻤﻠﯿﺎﺕ‪ ،‬ﺍﺯ ﺍﻟﮑﺘﺮﯾﺴﯿﺘﻪ ﺍﺳﺘﻔﺎﺩﻩ ﻣﯽﺷﻮﺩ‪،‬‬ ‫ﻣﺼﺮﻑ ﺁﺏ ﻫﻤﯿﺸﻪ ﺿﻤﻨﯽ ﺑﻮﺩﻩ ﻭ ﻫﺰﯾﻨﻪ ﺁﻥ‬ ‫ﺩﺭ ﻗﺒﺾ ﻗﯿﺪ ﻣﯽﺷﻮﺩ‪.‬‬ ‫ﻗﺒﻮﺽ ﻣﺎﻫﯿﺎﻧــﻪ ﺁﺏ‪ ،‬ﺗﻮﺟﻪ ﻣﺎ ﺭﺍ ﻓﻘﻂ‬ ‫ﺑﻪ ﻣﺼﺮﻑ ﺁﺏ ﺩﺭ ﺭﺩﻩﻫﺎﯼ ﺳﺎﺧﺘﻤﺎﻧﯽ ﺟﻠﺐ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺻﻔﺤﻪ ‪ / 5‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺟﺪﻭﻝ )‪ (1‬ﺍﻟﮕﻮﯼ ﻣﺼﺮﻑ ﺁﺏ ﺩﺭ ﺳﯿﺴﺘﻢ ﺳﺮﻣﺎﯾﺶ ﺗﺒﺨﯿﺮﯼ‬

‫ﺳﯿﺴﺘﻢ‬

‫ﮐﺮﺩ‪ .‬ﺑﺮﺍﯼ ﺭﻭﺷــﻦ ﺷــﺪﻥ ﺗﻔﺎﻭﺕ ﻣﻮﺟﻮﺩ‬

‫ﺗﺨﻤﯿﻦ ﺁﺏ ﻣﺼﺮﻓﯽ‬

‫ﺑﯿــﻦ ﻣﺼﺮﻑ ﮐﺮﺩﻥ ﻭ ﺑﻪ ﻫﺪﺭ ﺩﺍﺩﻥ‪ ،‬ﻣﺜﺎﻟﯽ‬

‫ﮔﺎﻟﻦ ﺩﺭ ﻫﺮ ﺳﺎﻝ ﺑﺎ‬ ‫ﮔﺎﻟﻦ ﺩﺭ ﻫﺮ ﺳﺎﻝ ﺍﺯ ﻃﺮﯾﻖ‬ ‫ﺯﯾﺮﺁﺏﮐﺸﯽ ﻭ ﺗﻌﻮﯾﺾ ﺗﺪﺭﯾﺠﯽ ﺁﺏ ﺭﺳﻮﺏﮔﯿﺮﯼ ﺗﺸﺘﮏ‬

‫ﻣﯽﺯﻧﯿﻢ‪ .‬ﺑﻪ ﻋﻨﻮﺍﻥ ﻣﺜﺎﻝ‪ ،‬ﯾﮏ ﻓﻼﺵﺗﺎﻧﮏ‬

‫ﺳﯿﺴﺘﻢ ﻣﺴﺘﻘﯿﻢ‬

‫‪9,667‬‬

‫‪6,284‬‬

‫ﺳﯿﺴﺘﻢ ﻣﺴﺘﻘﯿﻢ‪ +‬ﻏﯿﺮﻣﺴﺘﻘﯿﻢ‬

‫‪11,900‬‬

‫‪7,735‬‬

‫ﻣﺴﺘﻘﯿﻢ ﺍﻧﺒﺴﺎﻃﯽ‪ +‬ﻣﺴﺘﻘﯿﻢ ﺗﺒﺨﯿﺮﯼ‬

‫‪6,000‬‬

‫‪3,900‬‬

‫ﺳﺮﻭﯾﺲ ﺑﻬﺪﺍﺷﺘﯽ‪ ،‬ﺑﻪ ‪ 3‬ﮔﺎﻟﻦ ﺁﺏ ﺍﺣﺘﯿﺎﺝ‬ ‫ﺩﺍﺭﺩ‪ .‬ﺩﺭ ﺍﯾــﻦ ﺷــﯿﻮﻩ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺁﺏ‪ ،‬ﺩﺭ‬ ‫ﻭﺍﻗﻊ ﮐﺎﺭ ﻣﻔﯿﺪﯼ ﺍﻧﺠﺎﻡ ﺷــﺪﻩ ﺍﺳــﺖ‪ ،‬ﺍﻣﺎ‬ ‫ﻫﻤﯿﻦ ﻭﺳﯿﻠﻪ ﺩﺭ ﺻﻮﺭﺗﯽﮐﻪ ﺗﺤﺖ ﻧﮕﻬﺪﺍﺭﯼ‬

‫ﺍﻟﮑﺘﺮﯾﺴــﯿﺘﻪ ﺑﻪ ﻣﻘﺎﻭﻣﺖ ﺍﻟﮑﺘﺮﯾﮑﯽ ﺗﺒﺪﯾﻞ‬

‫ﺩﺭ ﺩﻗﯿﻘــﻪ ﻭﺍﺣــﺪ ﺗﺮﺍﮐﻤﯽ‪ ،‬ﺗﻮﺳــﻂ ﻭﺍﺣﺪ‬

‫ﻭ ﺍﺳــﺘﻔﺎﺩﻩ ﺻﺤﯿــﺢ ﻗﺮﺍﺭ ﻧﮕﯿــﺮﺩ‪ ،‬ﻣﻮﺟﺐ‬

‫ﺷﻮﺩ‪ .‬ﺍﻭﺝ ﻣﺼﺮﻑ ﺁﺏ ﺑﺮﺍﯼ ﺍﻟﮑﺘﺮﯾﺴﯿﺘﻪ ﻻﺯﻡ‬

‫ﺑﺰﺭﮒﺗﺮﯼ ﮐﻪ ﺩﺭﺟﺪﻭﻝ )‪ (2‬ﻧﺸﺎﻥ ﺩﺍﺩﻩ ﺷﺪﻩ‬

‫ﻫــﺪﺭ ﺭﻓﺘــﻦ ﺁﺏ ﻣﯽﺷــﻮﺩ‪ .‬ﺳــﺎﺯﻣﺎﻥ ﺁﺏ‬

‫ﺟﻬﺖ ﺭﺍﻩﺍﻧﺪﺍﺯﯼ ﯾــﮏ ﻭﺍﺣﺪ ﺗﺮﺍﮐﻤﯽ‪18.5 ،‬‬

‫ﺍﺳــﺖ )‪ 12,500‬ﻓﻮﺕ ﻣﮑﻌــﺐ ﺩﺭ ﺩﻗﯿﻘﻪ(‪،‬‬

‫ﮔﺎﻟﻦ ﺩﺭ ﺳﺎﻋﺖ ﺍﺳﺖ‪ .‬ﺍﯾﻦ ﻣﻘﺪﺍﺭ ﺗﺨﻤﯿﻨﯽ‪،‬‬

‫ﺩﻗﯿﻖﺗﺮ ﺑﺎﺯﮔﺮﺩﺍﻧﺪﻩ ﻣﯽﺷﻮﺩ‪.‬‬

‫»ﻧﯿﻮ ﺍﻧﮕﻠﻨــﺪ« ﺑﯿﺎﻥ ﮐﺮﺩﻩ ﺍﺳــﺖ ﮐﻪ ﺣﺘﺎ‬ ‫ﯾﮏ ﺳــﺮﻭﯾﺲ ﺑﻬﺪﺍﺷــﺘﯽ ﮐﻪ ﺩﺍﺭﺍﯼ ﻧﺸﺘﯽ‬ ‫ﺍﺳــﺖ‪ ،‬ﺑﻪ ﺗﻨﻬﺎﯾﯽ ﻣﯽﺗﻮﺍﻧﺪ ﺭﻭﺯﺍﻧﻪ ﺑﯿﺶ ﺍﺯ‬

‫ﻣﺮﺑﻮﻁ ﺑﻪ ﺩﺳﺘﮕﺎﻩ ﺳﺮﻣﺎﯾﺶ ﺗﺮﺍﮐﻤﯽ ﺍﺳﺖ‬

‫ﺩﺭ ﺳــﺮﻣﺎﯾﺶ ﺗﺒﺨﯿــﺮﯼ ﺁﺏ ﺑــﻪ ﻫﺪﺭ‬

‫ﮐﻪ ﺩﺭ ﺷــﺮﺍﯾﻂ ﻃﺮﺍﺣﯽ ﺑﺎ ﻧﺴــﺒﺖ ﺑﺎﺯﺩﻫﯽ‬

‫ﻧﻤــﯽﺭﻭﺩ‪ ،‬ﺑﻠﮑــﻪ ﺍﺯ ﺁﺏ ﺑﻪ ﻣﻨﻈــﻮﺭ ﻓﺮﺍﻫﻢ‬

‫ﺍﻧــﺮﮊﯼ ‪ ،10‬ﺩﺭ ﺣــﺎﻝ ﺗﺒــﺎﺩﻝ ‪ 6500‬ﻓﻮﺕ‬

‫ﮐــﺮﺩﻥ ﻣﺤﯿﻄﯽ ﺭﺍﺣــﺖ‪ ،‬ﺍﻓﺰﺍﯾــﺶ ﺭﻓﺎﻩ ﻭ‬

‫ﻣﮑﻌﺐ ﺩﺭ ﺩﻗﯿﻘﻪ ﻫﻮﺍ ﺍﺳﺖ‪ .‬ﻣﻄﺎﺑﻖ ﺟﺪﻭﻝ‬

‫ﺁﺳﺎﯾﺶ ﻭ ﺑﺎﺯﺩﻫﯽ ﺍﺳﺘﻔﺎﺩﻩ ﻣﯽﺷﻮﺩ‪ .‬ﺁﺏ ﺭﺍ‬

‫)‪ ،(2‬ﻣﯽﺗﻮﺍﻥ ﻣﻘﺪﺍﺭ ﻓــﻮﻕ ﺭﺍ ﺑﺎ ﺁﺏ ﻣﺼﺮﻑ‬

‫ﻣﯽﺗﻮﺍﻥ ﻣﺎﻧﻨﺪ ﮔﺎﺯ ﯾﺎ ﺯﻏﺎﻝﺳﻨﮓ‪ ،‬ﺑﻪ ﻋﻨﻮﺍﻥ‬

‫ﺗﺒﺨﯿــﺮ ﻭ ﺗﻌﺮﯾﻖ‪ ،‬ﻣﻮﺟﺐ ﺍﯾﺠﺎﺩ ﺳــﺮﻣﺎﯾﺶ‬

‫ﺷﺪﻩ ﺩﺭ ﺳﯿﺴﺘﻢ ﺳﺮﻣﺎﯾﺶ ﺗﺒﺨﯿﺮﯼ ﻣﻘﺎﯾﺴﻪ‬

‫ﻧﻮﻋﯽ ﺩﯾﮕﺮ ﺍﺯ ﺳــﻮﺧﺖﻫﺎﯼ ﺍﺳﺘﺨﺮﺍﺟﯽ ﺩﺭ‬

‫ﺗﺒﺨﯿﺮﯼ ﺷﺪﻩ ﻭ ﺳﺮﻣﺎﯾﺶ ﻣﻔﯿﺪﯼ ﺭﺍ ﻓﺮﺍﻫﻢ‬

‫ﻧﻤﻮﺩ‪ .‬ﺟﺮﯾﺎﻥ ﻫﻮﺍﯼ ﺍﻓﺰﺍﯾﺶﯾﺎﻓﺘﻪ ﻣﻮﺭﺩ ﻧﯿﺎﺯ‬

‫ﻧﻈﺮ ﮔﺮﻓﺖ‪ .‬ﺍﺗﻼﻑ ﺳــﻮﺧﺖ ﯾﺎ ﺁﺏ ﺑﺴﯿﺎﺭ ﭘﺮ‬

‫ﻣﯽﻧﻤﺎﯾﻨــﺪ‪ .‬ﺑﺎ ﺍﯾﻦ ﻭﺟــﻮﺩ‪ ،‬ﮔﯿﺎﻫﺎﻥ ﭘﻨﺒﻪ‪،‬‬

‫ﺳﯿﺴﺘﻢ ﺳــﺮﻣﺎﯾﺶ ﺗﺒﺨﯿﺮﯼ‪ ،‬ﺑﺮﺍﯼ ﺗﮑﻤﯿﻞ‬

‫ﻫﺰﯾﻨﻪ ﺍﺳــﺖ ﺯﯾﺮﺍ ﺩﺭ ﺁﻥ ﺻﻮﺭﺕ‪ ،‬ﺍﺯ ﻣﺼﺮﻑ‬

‫ﺭﻭﺯﺍﻧﻪ ‪ 300‬ﮔﺎﻟﻦ ﺁﺏ ﺭﺍ ﺍﺯ ﻃﺮﯾﻖ ﻓﺮﺍﯾﻨﺪ ﻓﻮﻕ‬

‫ﺳﺮﻣﺎﯾﺶ ﻗﺎﺑﻞ ﻣﻘﺎﯾﺴﻪ ﺑﺎ ‪ 6500‬ﻓﻮﺕ ﻣﮑﻌﺐ‬

‫ﺍﯾﻦ ﻣﻨﺎﺑﻊ ﻧﺘﺎﯾﺞ ﻣﻄﻠﻮﺑﯽ ﺣﺎﺻﻞ ﻧﺨﻮﺍﻫﯿﻢ‬

‫ﺑﻪ ﺗﺒﺨﯿﺮ ﻭ ﺗﻌﺮﯾﻖ ﻣﯽﺭﺳﺎﻧﻨﺪ‪.‬‬

‫‪ 200‬ﮔﺎﻟــﻦ ﺁﺏ ﺭﺍ ﻫــﺪﺭ ﺩﻫﺪ‪ .‬ﺩﺭﺧﺘﺎﻧﯽ ﮐﻪ‬ ‫ﺑﺮ ﺳــﺎﺧﺘﻤﺎﻥﻫﺎ ﺳــﺎﯾﻪ ﻣﯽﺍﻧﺪﺍﺯﻧﺪ‪ ،‬ﻧﯿﺎﺯ ﺑﻪ‬ ‫ﺳــﺮﻣﺎﯾﺶ ﺩﺭ ﺍﯾﻦ ﺍﻣﺎﮐــﻦ ﺭﺍ ﮐﺎﻫﺶ ﺩﺍﺩﻩ‬ ‫ﻭ ﻫﻤﭽﻨﯿﻦ ﺍﺯ ﻃﺮﯾﻖ ﻓﺮﺍﯾﻨﺪﯼ ﻣﻮﺳــﻮﻡ ﺑﻪ‬

‫ﺗﻦ –‬ ‫ﺳﺎﻋﺖ ‪/‬‬ ‫ﮔﺎﻟﻦ‬

‫ﻣﻌﺎﺩﻝ ﺗﻦ‬ ‫)‪(5‬‬

‫ﺁﺏﻣﺼﺮﻓﯽﮔﺎﻟﻦ‬ ‫ﺁﺏ ﻣﺼﺮﻓﯽ ﮔﺎﻟﻦ ﺯﯾﺮﺁﺏﮐﺸﯽ‬ ‫‪ /‬ﺳﺎﻋﺖ ﻭﺍﺕ‬ ‫‪ /‬ﺳﺎﻋﺖ ﻭﺍﺕ‪ /‬ﻣﺘﻨﺎﻭﺏ ﮔﺎﻟﻦ ‪/‬‬ ‫‪/‬ﺭﺳﻮﺏﮔﯿﺮﯼ‬ ‫ﮐﺸﯽ‬ ‫ﺯﯾﺮﺁﺏ‬ ‫ﺳﺎﻋﺖ )‪(4‬‬ ‫ﺗﺸﺘﮏ‬

‫ﺗﺒﺨﯿﺮﮔﺎﻟﻦ‪/‬‬ ‫ﺳﺎﻋﺖ )‪(3‬‬

‫ﻧﮑﺎﺕ‪:‬‬ ‫‪ -1‬ﺩﻣﺎﯼ ﻫﻮﺍﯼ ﺭﻓﺖ ﺧﻨﮏﮐﻨﻨﺪﻩ ﺗﺒﺨﯿﺮﯼ‬ ‫ﺩﻣﺎﯼ ﻫﻮﺍﯼ ﺧﺸﮏ ﺑﯿﺮﻭﻥ = ﺩﻣﺎﯼ ﻫﻮﺍﯼ ﺧﺸﮏ ﺩﺍﺧﻞ ‪) -‬ﺑﺎﺯﺩﻩ ﺗﺒﺨﯿﺮ× )ﺩﻣﺎﯼ ﻫﻮﺍﯼ‬ ‫ﺧﺸﮏ ﺩﺍﺧﻞ – ﺩﻣﺎﯼ ﻫﻮﺍﯼ ﻣﺮﻃﻮﺏ ﺩﺍﺧﻞ((‬ ‫‪ -2‬ﺍﻃﻼﻋﺎﺕ ﺁﺏ ﻭ ﻫﻮﺍ ﺩﺭ ﻣﺎﻩ ﺟﻮﻻﯼ ﺩﺭﺁﻟﺒﻮﮐﺮﮎ‪:‬‬ ‫ﺭﺍﻫﻨﻤﺎﯼ ﺁﺏ ﻭ ﻫﻮﺍﯼ ﻧﯿﻮﻣﮑﺰﯾﮑﻮ‪2-72-4523 NMERDI ،‬‬

‫ﺩﻣﺎﯼ ﻫﻮﺍﯼ‬ ‫ﺭﻓﺖ )‪(1‬‬

‫ﺩﺭﺻﺪ ﺑﺎﺯﺩﻩ‬

‫ﺩﻣﺎﯼ ﻫﻮﺍﯼ‬ ‫ﺩﻣﺎﯼ ﻫﻮﺍﯼ ﺳﺮﻣﺎﯾﺶﺗﺒﺨﯿﺮﯼ‬ ‫ﻣﺮﻃﻮﺏ‬ ‫ﺧﺸﮏﻣﺤﯿﻄﯽ ﻣﺴﺘﻘﯿﻢ)ﻓﻮﺕ‬ ‫ﺩﺭﺟﻪ ﻓﺎﺭﻧﻬﺎﯾﺖ ﺩﺭﺟﻪ ﻓﺎﺭﻧﻬﺎﯾﺖ )‪ (2‬ﻣﮑﻌﺐﺩﺭﺩﻗﯿﻘﻪ(‬ ‫)‪(2‬‬

‫‪ -3‬ﺑﺮ ﺍﺳﺎﺱ ﻓﺮﻣﻮﻝ ﺗﺒﺨﯿﺮ‪ :‬ﮔﺎﻟﻦ ﺩﺭ ﺳﺎﻋﺖ = )‪ × 1/2‬ﻓﻮﺕ ﻣﮑﻌﺐ ﺩﺭ ﺩﻗﯿﻘﻪ )ﺩﻣﺎﯼ ﻫﻮﺍﯼ‬ ‫ﺧﺸﮏ ‪ – E‬ﺩﻣﺎﯼ ﻫﻮﺍﯼ ﺧﺸﮏ ‪10.000/(L‬‬ ‫ﺑﺮﺍﺳﺎﺱ ﻧﺮﺥ ﺯﯾﺮﺁﺏﮐﺸﯽ ﻣﺘﻨﺎﻭﺏ ‪12‬ﺍﻭﻧﺲ ﺑﺮ ﺩﻗﯿﻘﻪ‪ ،‬ﻭﺍﺣﺪ ﮐﻮﭼﮏ ﻭ ‪ 25‬ﺍﻭﻧﺲ ﺑﺮ ﺩﻗﯿﻘﻪ‪،‬‬ ‫ﻭﺍﺣﺪ ﺑﺰﺭﮒ‪.‬‬ ‫‪ -4‬ﺑﺮﺍﺳﺎﺱ ﻣﻌﺎﺩﻟﻪ ‪(TDBout – TDBin)×AF×CFM =Q‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺟﺪﻭﻝ )‪ (2‬ﻣﻘﺎﯾﺴﻪ ﻣﯿﺰﺍﻥ ﺁﺏ ﻣﺼﺮﻓﯽ ﺩﺭﺳﯿﺴﺘﻢ ﺳﺮﻣﺎﯾﺶ ﺗﺒﺨﯿﺮﯼ‬

‫ﺻﻔﺤﻪ ‪ / 6‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺗﺨﺼﺼﻰ‬

‫ﺭﻭﺍﺑﻂ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬ ‫ﻣﺤﺎﺳﺒﺎﺕ ﻫﺪ ﻣﮑﺸﯽ ﻣﺜﺒﺖ ﺧﺎﻟﺺ ﭘﻤﭗ )‪(NPSH‬‬

‫ﻗﻮﺍﻧﯿﻦ ﭘﻤﭗ‬ ‫‪GPM‬‬ ‫‪RPM‬‬ ‫‪ᎏ2 = ᎏ2‬‬ ‫‪GPM1 RPM1‬‬

‫‪冥 = 冤ᎏ‬‬ ‫‪RPM 冥‬‬

‫‪冤‬‬

‫‪= ᎏ‬‬ ‫‪冥 = 冤ᎏ‬‬ ‫‪RPM 冥 冤 HD 冥‬‬

‫‪冤‬‬

‫‪2‬‬

‫‪RPM2‬‬

‫‪2‬‬

‫‪1‬‬

‫‪1.5‬‬

‫‪HD2‬‬ ‫‪1‬‬

‫‪3‬‬

‫‪RPM2‬‬

‫‪3‬‬

‫‪1‬‬

‫‪HD‬‬ ‫‪GPM‬‬ ‫‪ᎏ2 = ᎏ2‬‬ ‫‪HD1‬‬ ‫‪GPM1‬‬

‫‪GPM‬‬ ‫‪BHP‬‬ ‫‪ᎏᎏ2 = ᎏ2‬‬ ‫‪GPM1‬‬ ‫‪BHP1‬‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫‪GPM × HD × SP.GR.‬‬ ‫‪BHP = ᎏᎏᎏ‬‬ ‫‪3960 × PUMPEFF.‬‬ ‫‪BHP‬‬ ‫‪MHP = ᎏ‬‬ ‫‪M/DEFF.‬‬ ‫‪V2‬‬ ‫‪VH = ᎏ‬‬ ‫‪2g‬‬

‫‪NPSHAVAIL > NPSHREQ’D‬‬ ‫‪NPSHAVAIL = HA ⫾ HS − HF − HVP‬‬ ‫ﻣﮑﺶ ﻣﺜﺒﺖ ﻣﻮﺟﻮﺩ ﺩﺭ ﭘﻤﭗ ﺑﺮ ﺣﺴﺐ ﻓﻮﺕ = ‪NPSHAVAIL‬‬ ‫ﻣﮑﺶ ﻣﺜﺒﺖ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﺩﺭ ﭘﻤﭗ ﺑﺮ ﺣﺴﺐ ﻓﻮﺕ = ‪NPSHREQ’D‬‬ ‫‪HA‬‬ ‫ﻓﺸﺎﺭ ﺩﺭ ﺳﻄﺢ ﻣﺎﯾﻊ )ﻓﻮﺕ ‪ 34 -‬ﻓﻮﺕ ﺑﺮﺍﯼ ﺁﺏ =‬ ‫ﺩﺭ ﻓﺸﺎﺭ ﺍﺗﻤﺴﻔﺮ ﯾﮏ(‬ ‫‪HS‬‬ ‫ﺍﺭﺗﻔﺎﻉ ﺳﻄﺢ ﻣﺎﯾﻊ ﺑﺎﻻ ﺯﯾﺮ)‪ (+‬ﯾﺎ ﭘﻤﭗ )‪) (−‬ﻓﻮﺕ( =‬ ‫‪HF‬‬ ‫ﺍﺗﻼﻑ ﺍﺻﻄﮑﺎﮐﯽ ﺑﯿﻦ ﭘﻤﭗ ﻣﻨﺒﻊ )ﻓﻮﺕ( =‬ ‫‪HVP‬‬ ‫ﻓﺸﺎﺭ ﻣﻄﻠﻖ ﺑﺨﺎﺭ ﺁﺏ ﺩﺭ ﺩﻣﺎﯼ ﻣﺎﯾﻊ )ﻓﻮﺕ ‪= -‬‬ ‫ﻃﺒﻖ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ﺍﻧﺠﻤﻦ ﺳﺮﻣﺎﯾﺶ‪ ،‬ﮔﺮﻣﺎﯾﺶ ﻭ‬ ‫ﺗﻬﻮﯾﻪ ﻣﻄﺒﻮﻉ ﺁﻣﺮﯾﮑﺎ(‬

‫ﺗﻬﻮﯾﻪ ﻣﻄﺒﻮﻉ ﭼﮕﺎﻟﯿﺪﻩ‬

‫‪P × 2.31‬‬ ‫‪HD = ᎏ‬‬ ‫‪SP.GR.‬‬

‫ﮔﺎﻟﻦ ﺩﺭ ﺩﻗﯿﻘﻪ‬ ‫ﺩﻭﺭ ﺩﺭ ﺩﻗﯿﻘﻪ‬ ‫ﻓﻮﺕ ﺁﺏ‬ ‫ﺗﻮﺍﻥ ﺗﺮﻣﺰﯼ ﺑﺮ ﺣﺴﺐ ﺍﺳﺐ ﺑﺨﺎﺭ‬ ‫ﺛﺎﺑﺖ‬ ‫ﺛﺎﺑﺖ‬ ‫ﻭﺯﻥ ‪q‬‬ ‫ﻣﺨﺼﻮﺹ‪ y‬ﻣﺎﯾﻊ ﻧﺴﺒﺖ ﺑﻪ ‪p‬ﺁﺏ‬ ‫‪1.0‬‬ ‫‪60–80%‬‬ ‫‪85–95%‬‬ ‫‪Motor/Drive‬‬ ‫ﻓﺸﺎﺭ ﺑﺮ ﺣﺴﺐ‬ ‫ﻫﺪ ﺳﺮﻋﺘﯽ ﺑﺮ ﺣﺴﺐ ﻓﻮﺕ‬ ‫ﺳﺮﻋﺖ ﺑﺮ ﺣﺴﺐ ﻓﻮﺕ ﺑﺮ ﺛﺎﻧﯿﻪ‬ ‫) ‪ (32.16Ft./ Sec2‬ﺷﺘﺎﺏ ﮔﺮﺍﻧﺶ‬

‫=‬ ‫=‬ ‫=‬ ‫=‬ ‫=‬ ‫=‬ ‫=‬ ‫=‬ ‫=‬ ‫=‬ ‫=‬ ‫=‬ ‫=‬ ‫=‬ ‫=‬

‫‪GPM‬‬ ‫‪RPM‬‬ ‫‪HD‬‬ ‫‪BHP‬‬ ‫ﭘﻤﭗ‬ ‫ﺍﻧﺪﺍﺯﻩ‬ ‫‪Pump‬‬ ‫‪Size‬‬ ‫ﺁﺏ‬ ‫ﭼﮕﺎﻟﯽ‬ ‫‪Water‬‬ ‫‪Density‬‬ ‫‪SP.GR.‬‬ ‫)ﺁﺏ(‬ ‫)‪SP.GR. (Water‬‬ ‫‪PUMPEFF.‬‬ ‫‪M/DEFF.‬‬ ‫‪M/D‬‬ ‫‪P‬‬ ‫‪VH‬‬ ‫‪V‬‬ ‫‪g‬‬

‫‪CFM × ΔWLB.‬‬ ‫‪GPMAC COND = ᎏᎏ‬‬ ‫‪SpV × 8.33‬‬ ‫‪CFM × ΔWGR.‬‬ ‫‪GPMAC COND = ᎏᎏ‬‬ ‫‪SpV × 8.33 × 7000‬‬ ‫ﺟﺮﯾﺎﻥ ﺗﻬﻮﯾﻪ ﻣﻄﺒﻮﻉ ﭼﮕﺎﻟﯿﺪﻩ )ﮔﺎﻟﻦ ﺩﺭ ﺩﻗﯿﻘﻪ( = ‪GPMAC COND‬‬ ‫‪CFM‬‬ ‫ﻧﺮﺥ ﺟﺮﯾﺎﻥ ﻫﻮﺍ )ﻓﻮﺕ ﻣﮑﻌﺐ ﺩﺭ ﺩﻗﯿﻘﻪ( =‬ ‫‪SpV‬‬ ‫)‪ (Cu.Ft./Lb.DA‬ﺣﺠﻢ ﻣﺨﺼﻮﺹ ﻫﻮﺍ =‬ ‫)‪ (Lb.H2O/Lb.DA‬ﺭﻃﻮﺑﺖ ﻣﺨﺼﻮﺹ =‬ ‫‪ΔWLB.‬‬ ‫‪ΔWGR.‬‬ ‫)‪ (Gr.H2O/Lb.DA‬ﺭﻃﻮﺑﺖ ﻣﺨﺼﻮﺹ =‬

‫ﺭﻃﻮﺑﺖﺯﻧﯽ‬

‫‪冣‬‬

‫‪WGR.‬‬ ‫‪− ᎏ‬‬ ‫‪SpV‬‬ ‫‪ROOM AIR‬‬

‫‪冢‬‬

‫‪冣‬‬

‫‪冢‬‬

‫‪冣‬‬

‫‪SUPPLY AIR‬‬

‫‪SUPPLY AIR‬‬

‫‪冣‬‬

‫‪WLB.‬‬ ‫‪− ᎏ‬‬ ‫‪SpV‬‬ ‫‪ROOM AIR‬‬

‫‪冢‬‬

‫‪WGR.‬‬ ‫‪GRAINSREQ’D = ᎏ‬‬ ‫‪SpV‬‬

‫‪冢‬‬

‫‪WLB.‬‬ ‫‪POUNDSREQ’D = ᎏ‬‬ ‫‪SpV‬‬

‫‪CFM × GRAINSREQ’D × 60‬‬ ‫‪LB. STM/HR = ᎏᎏᎏ‬‬ ‫‪= CFM × POUNDSREQ’D × 60‬‬ ‫‪7000‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺻﻔﺤﻪ ‪ / 7‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻣﻘﺎﻻﺕ‬

‫ﻃﺒﻘﻪﺑﻨﺪﻯ ﺳﻴﺴﺘﻢ ﺳﺮﻣﺎﻳﺶ‬ ‫ﺟﺬﺑﻰ ﺍﺯ ﻧﻈﺮ ﻣﻨﺒﻊ ﮔﺮﻣﺎﻳﻰ‬ ‫ﻋﻤﻠﻴﺎﺕ ﺗﻐﻠﻴﻆ ﻭ ﺍﺣﻴﺎ‬

‫ﻧﻮﻉ ﻣﻨﺒــﻊ ﮔﺮﻣﺎﯾﯽ ﺑــﺮﺍﯼ ﻋﻤﻠﯿﺎﺕ‬

‫ﺁﺏ ﮔــﺮﻡ ﮐﻪ ﻣﻨﻈــﻮﺭ ﺍﺯ ﺁﻥ‪ ،‬ﺁﺑﯽ ﺑﺎ‬

‫ﮐﺎﺭ ﻣﯽﮐﻨﺪ ﻗﺪﯾﻤﯽﺗــﺮ ﺍﺯ ﭼﯿﻠﺮﻫﺎﯼ ﺁﺏ‬

‫ﺗﻐﻠﯿــﻆ ﻣﺤﻠﻮﻝ ﯾﺎ ﺍﺣﯿــﺎﯼ ﻣﺎﺩﻩ ﺟﺎﺫﺏ‬

‫ﺩﻣﺎﯼ ﮐﻤﺘﺮ ﺍﺯ ‪ 100‬ﺩﺭﺟﻪ ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ‬

‫ﮔﺮﻡ ﺍﺳــﺖ‪ .‬ﻟﻤﭗ ﻭ ﺯﯾﮕﻠﺮ ﺩﺭﺳﺎﻝ ‪1996‬‬

‫ﺍﺯ ﻧﻈــﺮ ﮐﻠــﯽ ﺗﺎﺛﯿﺮﯼ ﺑــﺮ ﺗﺮﺗﯿﺐ ﭼﺮﺧﻪ‬

‫ﺩﺭ ﻓﺸﺎﺭ ﺟﻮ ﺍﺳﺖ‪ ،‬ﺗﻨﻬﺎ ﺑﺮﺍﯼ ﭼﯿﻠﺮﻫﺎﯼ‬

‫ﻣﯿﻼﺩﯼ ﺍﯾﺪﻩ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺳــﯿﺎﻝﻫﺎﯼ‬

‫ﺳــﺮﻣﺎﯾﺶ ﺩﺭ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ ﻣﺨﺘﻠﻒ‬ ‫ﻧــﺪﺍﺭﺩ ﺍﻣﺎ ﺑﻪ ﻟﺤﺎﻅ ﺳــﺎﺧﺘﺎﺭﯼ ﻣﻮﺟﺐ‬ ‫ﺑﺮﻭﺯ ﺑﺮﺧﯽ ﺗﻔﺎﻭﺕﻫﺎ ﻣﯽﺷﻮﺩ‪.‬‬ ‫ﺑﺨــﺎﺭ‪ ،‬ﺁﺏ ﺩﺍﻍ‪ ،‬ﺁﺏ ﮔــﺮﻡ‪،‬‬ ‫ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ ﻭ ﺍﻧﺮﮊﯼ ﺧﻮﺭﺷﯿﺪﯼ ﻫﺮ‬ ‫ﯾــﮏ ﻣﯽﺗﻮﺍﻧﻨﺪ ﻣﻨﺒﻊ ﻣﺴــﺘﻘﯿﻢ ﯾﺎ ﻏﯿﺮ‬

‫ﯾﮏﺍﺛﺮﻩ ﻣﻮﺭﺩ ﺍﺳﺘﻔﺎﺩﻩ ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﺩ‪ ،‬ﺩﺭ‬ ‫ﺻﻮﺭﺗﯽﮐﻪ ﺁﺏ ﺩﺍﻍ ﻭ ﺑﺨﺎﺭ ﻗﺎﺑﻠﯿﺖ ﮐﺎﺭﺑﺮﺩ‬ ‫ﺑﺮﺍﯼ ﻫﺮ ﺩﻭ ﻧﻮﻉ ﭼﯿﻠﺮ ﯾﮏﺍﺛﺮﻩ ﻭ ﺩﻭ ﺍﺛﺮﻩ‬ ‫ﺭﺍ ﺩﺍﺭﻧﺪ‪.‬‬ ‫ﺩﺭ ﺳﯿﺴﺘﻢﻫﺎﯼ ﺟﺬﺑﯽ ﺁﻣﻮﻧﯿﺎﮐﯽ ﻧﯿﺰ‬ ‫ﻓﺎﺭﻍ ﺍﺯ ﺷﻌﻠﻪﻣﺴﺘﻘﯿﻢ‪ ،‬ﺍﻣﮑﺎﻥ ﺍﺳﺘﻔﺎﺩﻩ‬

‫ﮐﻢﺩﻣﺎ ﻣﺎﻧﻨﺪ ﺁﺏ ﮔﺮﻡ ﺭﺍ ﺑﺮﺍﯼ ﭼﯿﻠﺮﻫﺎﯼ‬ ‫ﺟﺬﺑــﯽ ﺟﻤﻊﺑﻨﺪﯼ ﻭ ﺍﺭﺍﺋﻪ ﮐﺮﺩﻧﺪ‪ .‬ﺁﻥﻫﺎ‬ ‫ﻣﻘﺎﻻﺕ ﺯﯾﺎﺩﯼ ﺩﺭ ﻣﻮﺭﺩ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ‬ ‫ﯾﮏﺍﺛﺮﻩ ﺑﺎ ﺭﻭﯾﮑﺮﺩ ﺑﻬﺮﻩﮔﯿﺮﯼ ﺍﺯ ﺁﺏ ﮔﺮﻡ‬ ‫ﺭﺍ ﻣﻨﺘﺸــﺮ ﻧﻤﻮﺩﻧﺪ‪ .‬ﺗﺤﻘﯿﻘﺎﺕ ﺁﻥﻫﺎ ﺣﺘﺎ‬ ‫ﺯﻣﯿﻨﻪﻫﺎﯾﯽ ﺭﺍ ﺑــﺮﺍﯼ ﺍﯾﺠﺎﺩ ﭼﺮﺧﻪﻫﺎﯾﯽ‬ ‫ﮐﻪ ﺑﺎ ﺩﻣﺎﯼ ﺑﺴﯿﺎﺭ ﮐﻤﺘﺮ ﮐﺎﺭ ﻣﯽﮐﻨﻨﺪ ﺭﺍ‬

‫ﺑــﺎ ﺯﻭﺝﻫﺎﯼ ﻣﺒــﺮﺩ ﻭ ﺟــﺎﺫﺏ ﻣﺨﺘﻠﻒ‬

‫ﺟﺪﻭﻝ ﺯﯾﺮ ﺑﻪ ﻃﻮﺭ ﺧﻼﺻﻪ ﺩﻣﺎﯼ ﺳﯿﺎﻝ‬

‫ﺑﺎﺷــﻨﺪ‪ .‬ﺍﻣﺮﻭﺯﻩ ﺁﺏ ﺩﺍﻍ ﮐﻪ ﺗﺤﺖ ﻓﺸﺎﺭ‬

‫ﮔﺮﻡﮐﻨﻨﺪﻩ ﺩﺭ ﺳــﻪ ﻧﻮﻉ ﺳﯿﺴﺘﻢ ﺟﺬﺑﯽ‬

‫ﺑــﺎﻻ ﻭ ﺑــﺎ ﺩﻣــﺎﯼ ‪ 110‬ﺗــﺎ ‪ 130‬ﺩﺭﺟﻪ‬

‫ﻟﯿﺘﯿﻤﯽ ﺗــﮏ ﺍﺛﺮﻩ‪ ،‬ﺩﻭ ﺍﺛﺮﻩ‪ ،‬ﻭ ﺁﻣﻮﻧﯿﺎﮐﯽ‬

‫ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ ﺗﻮﻟﯿﺪ ﻣﯽﺷــﻮﺩ‪ ،‬ﺑﻪ ﺩﻟﯿﻞ‬

‫ﺭﺍ ﻧﺸﺎﻥ ﻣﯽﺩﻫﺪ‪.‬‬

‫ﺿﺮﯾﺐ ﮐﺎﺭﺍﯾﯽ ﭼﺮﺧﻪﻫﺎﯼ ﯾﮏﺍﺛﺮﻩ ﺍﺳﺖ‪.‬‬

‫ﺑﺮﺧﯽ ﻣﺸــﮑﻼﺕ‪ ،‬ﮐﺎﺭﺑــﺮﺩ ﭼﻨﺪﺍﻧﯽ ﺩﺭ‬

‫ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺁﺏ ﮔﺮﻡ ﻭ ﺁﺏ ﺩﺍﻍ‬

‫ﺗﺼﻮﯾﺮ )‪ (1‬ﻧﻤﻮﻧﻪﺍﯼ ﺍﺯ ﭼﺮﺧﻪ ﻧﯿﻢﺍﺛﺮﻩ ﺭﺍ‬

‫ﺳﯿﺴــﺘﻢﻫﺎﯼ ﮔﺮﻣﺎﯾﺸﯽ ﺳﺎﺧﺘﻤﺎﻥﻫﺎﯼ‬

‫ﭼﯿﻠﺮﻫــﺎﯼ ﺟﺬﺑــﯽ ﺁﺏ ﮔــﺮﻡ ﺍﺯ‬

‫ﻣﺴــﮑﻮﻧﯽ ﻭ ﺍﺩﺍﺭﯼ ﻧــﺪﺍﺭﺩ ﻭ ﺑــﻪ ﺗﺒــﻊ‬

‫ﻧــﻮﻉ ﯾﮏﺍﺛﺮﻩ ﻫﺴــﺘﻨﺪ ﺍﻣــﺎ ﺁﺏ ﺩﺍﻍ ﺩﺭ‬

‫ﺁﻥ ﭼﯿﻠﺮﻫﺎﯾــﯽ ﺟﺬﺑــﯽ ﮐﻪ ﺑــﺎ ﺁﺏ ﺩﺍﻍ‬

‫ﭼﯿﻠﺮﻫــﺎﯼ ﺩﻭ ﺍﺛــﺮﻩ ﻧﯿﺰ ﮐﺎﺭﺑــﺮﺩ ﺩﺍﺭﺩ‪.‬‬

‫ﮐﺎﺭ ﻣﯽﮐﻨﻨــﺪ ﻧﯿﺰ ﻣﻌﻤــﻮﻻ ﺩﺭ ﺍﯾﻦﮔﻮﻧﻪ‬ ‫ﺳــﺎﺧﺘﻤﺎﻥﻫﺎ ﻣــﻮﺭﺩ ﺍﺳــﺘﻔﺎﺩﻩ ﻗــﺮﺍﺭ‬ ‫ﻧﻤﯽﮔﯿﺮﻧﺪ‪ ،‬ﻣﮕــﺮ ﺁﻥﮐﻪ ﺩﺭ ﺑﺮﺧﯽ ﻣﻮﺍﺭﺩ‬ ‫ﺻﻨﻌﺘﯽ ﻭ ﻭﯾﮋﻩ‪ ،‬ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﺳﯿﺴﺘﻢ ﺁﺏ‬ ‫ﺩﺍﻍ ﺑﻨﺎ ﺑﻪ ﺑﺮﺧﯽ ﺩﻻﯾــﻞ ﺍﺟﺘﻨﺎﺏﻧﺎﭘﺬﯾﺮ‬ ‫ﺑﺎﺷــﺪ‪ .‬ﺍﻣﺎ ﭼﯿﻠﺮﻫﺎﯼ ﻣﺠﻬــﺰ ﺑﻪ ﮊﻧﺮﺍﺗﻮﺭ‬ ‫ﺑﺨﺎﺭ ﻣﯽﺗﻮﺍﻧﻨﺪ ﺗﺤﺖ ﺷــﺮﺍﯾﻂ ﺧﺎﺻﯽ ﺑﺎ‬ ‫ﺁﺏ ﺩﺍﻍ ﻭ ﺣﺘﺎ ﺑﺎ ﺁﺏ ﮔﺮﻡ ﻧﯿﺰ ﮐﺎﺭ ﮐﻨﻨﺪ‪.‬‬

‫ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﭼﯿﻠﺮﻫﺎﯼ ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ‬ ‫ﻭ ﭼﯿﻠﺮﻫﺎﯾــﯽ ﮐﻪ ﮊﻧﺮﺍﺗﻮﺭ ﺁﻥﻫــﺎ ﺑﺎ ﺑﺨﺎﺭ‬ ‫ﻧﻮﻉ ﺳﯿﺴﺘﻢ ﺟﺬﺑﯽ‬ ‫ﻟﯿﺘﯿﻤﯽ ﺗﮏﺍﺛﺮﻩ‬ ‫ﻟﯿﺘﯿﻤﯽ ﺩﻭﺍﺛﺮﻩ‬ ‫ﺁﻣﻮﻧﯿﺎﮐﯽ‬

‫ﮐﻪ ﺩﺭ ﻫﻤﺎﻥ ﺳﺎﻝ ﻧﻤﻮﻧﻪﻫﺎﯼ ﺗﺤﻘﯿﻘﺎﺗﯽ‬ ‫ﺁﻥ ﻣﻮﺭﺩ ﺁﺯﻣﺎﯾــﺶ ﻗﺮﺍﺭ ﮔﺮﻓﺖ‪ .‬ﺍﻟﺒﺘﻪ ﺩﺭ‬ ‫ﭼﺮﺧﻪﻫﺎﯼ ﻧﯿﻢﺍﺛﺮﻩ ﺿﺮﯾﺐ ﮐﺎﺭﺍﯾﯽ ﻧﺼﻒ‬

‫ﻧﻤﺎﯾــﺶ ﻣﯽﺩﻫﺪ‪ .‬ﺍﺧﺘــﻼﻑ ﺍﺻﻠﯽ ﺑﯿﻦ‬ ‫ﺍﯾــﻦ ﭼﺮﺧﻪ ﺑــﺎ ﭼﺮﺧﻪ ﯾﮏﺍﺛــﺮﻩ ﺍﺿﺎﻓﻪ‬ ‫ﺷﺪﻥ ﯾﮏ ﺍﺑﺰﻭﺭﺑﺮ ﻭ ﯾﮏ ﮊﻧﺮﺍﺗﻮﺭ ﺍﺳﺖ‪.‬‬ ‫ﺩﺭ ﺍﯾﻦ ﺳﯿﺴــﺘﻢ ﺑﺨﺎﺭ ﺁﺏ ﻧﺎﺷﯽ ﺍﺯ‬ ‫ﻋﻤﻠﯿﺎﺕ ﺗﻐﻠﯿﻆ ﺩﺭ ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﭘﺎﯾﯿﻦ ﺑﻪ‬

‫ﺩﻣﺎﯼ ﺑﺨﺎﺭ ﯾﺎ ﮔﺎﺯ ﺩﺍﻍ ﻓﺮﺍﯾﻨﺪﻫﺎ‬

‫ﺁﺏ ﺩﺍﻍ ﯾﺎ ﺳﯿﺎﻝ ﺩﺍﻍ ﻓﺮﺍﯾﻨﺪﻫﺎ‬

‫‪225-250‬‬

‫‪240-300‬‬

‫)‪(110-120‬‬

‫)‪(115-150‬‬

‫‪350-365‬‬

‫‪310-400‬‬

‫)‪(175-185‬‬

‫)‪(155-205‬‬

‫‪210-385‬‬

‫‪210-385‬‬

‫)‪(100-195‬‬

‫)‪(100-195‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﻣﺴﺘﻘﯿﻢ ﮔﺮﻣﺎﯾﺸــﯽ ﺑﺮﺍﯼ ﺍﻧﻮﺍﻉ ﭼﯿﻠﺮﻫﺎ‬

‫ﺍﺯ ﺁﺏ ﺩﺍﻍ ﻭ ﺑﺨــﺎﺭ ﻧﯿــﺰ ﻭﺟــﻮﺩ ﺩﺍﺭﺩ‪.‬‬

‫ﺗﺤﺖ ﻋﻨﻮﺍﻥ ﭼﺮﺧﻪ ﻧﯿﻢﺍﺛﺮﻩ ﺑﻪﻭﺟﻮﺩ ﺁﻭﺭﺩ‬

‫ﺻﻔﺤﻪ ‪ / 8‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺟﺎﯼ ﺭﻓﺘﻦ ﺑﻪ ﮐﻨﺪﺍﻧﺴﻮﺭ ﺑﺎﺭ ﺩﯾﮕﺮ ﺟﺬﺏ‬

‫ﺳﯿﺴــﺘﻢ ﻧﯿﻢﺍﺛﺮﻩ ﺁﺏ ﮔﺮﻡ ﺭﺍ ﻧﺴــﺒﺖ ﺑﻪ‬

‫ﻟﯿﺘﯿﻢ ﺑﺮﻭﻣﺎﯾﺪ ﺍﺑﺰﻭﺭﺑﺮ ﺩﻭﻡ ﻣﯽﺷﻮﺩ ﻭ ﺑﻪ‬

‫ﺳﯿﺴﺘﻢﻫﺎﯼ ﯾﮏﺍﺛﺮﻩ ﺗﺎ ﺣﺪﻭﺩﯼ ﺗﻮﺟﯿﻪ‬

‫ﺍﯾﻦ ﺗﺮﺗﯿﺐ ﺑﺨﺸﯽ ﺍﺯ ﺁﺏ ﻣﺤﻠﻮﻝ ﺍﺭﺳﺎﻟﯽ‬

‫ﻧﻤﻮﺩ‪.‬‬

‫ﺑــﺎ ﮐﺎﻫــﺶ ﺩﻣــﺎﯼ ﺁﺏ ﮔــﺮﻡ‪ ،‬ﺍﺯ‬ ‫ﻇﺮﻓﯿﺖ ﺳــﺮﻣﺎﯾﯽ ﮐﺎﺳــﺘﻪ ﻣﯽﺷﻮﺩ‪ .‬ﺩﺭ‬

‫ﺍﺯ ﺳــﻮﯼ ﺍﺑﺰﻭﺭﺑﺮ ﺍﻭﻝ ﺗﻮﺳﻂ ﺍﺑﺰﻭﺭﺑﺮ ﺩﻭﻡ‬

‫ﺑﺮﺍﯼ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺳــﯿﺎﻻﺕ ﮐﻢﺩﻣﺎ‬

‫ﺳﯿﺴــﺘﻢﻫﺎﯼ ﻣﺘﻌﺎﺭﻑ ﺟﺬﺑﯽ ﮐﻪ ﺑﺎ ﺁﺏ‬

‫ﺍﺯ ﺁﻥ ﺟﺪﺍ ﺷــﺪﻩ ﻭ ﻧﯿﺎﺯﻣﻨــﺪﯼ ﮔﺮﻣﺎﯾﯽ‬

‫ﻣﺎﻧﻨﺪ ﺁﺏ ﮔــﺮﻡ ﺩﺭ ﭼﯿﻠﺮﻫــﺎﯼ ﺟﺬﺑﯽ‪،‬‬

‫ﮔــﺮﻡ ﮐﺎﺭ ﻣﯽﮐﻨﻨﺪ ﺑــﺮﺍﯼ ﺗﻮﻟﯿﺪ ﻳﮏ ﺗﻦ‬

‫ﮊﻧﺮﺍﺗﻮﺭ ﺑــﺮﺍﯼ ﺟﺪﺍﺳــﺎﺯﯼ ﺁﺏ ﺍﺯ ﻟﯿﺘﯿﻢ‬

‫ﺍﻭﻟﯿﻦ ﺍﻗــﺪﺍﻡ ﻣﯽﺗﻮﺍﻧﺪ ﺍﻓﺰﺍﯾﺶ ﺳــﻄﺢ‬

‫ﺗﺒﺮﯾﺪ ﺳﺮﻣﺎﯾﺶ‪ ،‬ﺩﻣﺎﯼ ﺁﺏ ﮔﺮﻡ ﻭﺭﻭﺩﯼ‬

‫ﺑﺮﻭﻣﺎﯾﺪ ﮐﻤﺘﺮ ﻣﯽﺷﻮﺩ‪.‬‬

‫ﺣﺮﺍﺭﺗﯽ ﮊﻧﺮﺍﺗﻮﺭ ﻭ ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﺑﺎﺷــﺪ‪.‬‬

‫ﺑــﻪ ﮊﻧﺮﺍﺗــﻮﺭ ‪ 93.3‬ﺩﺭﺟــﻪ ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ‬

‫ﺍﯾــﻦ ﺳﯿﺴــﺘﻢ ﺍﮔﺮﭼــﻪ ﻣﯽﺗﻮﺍﻧﺪ ﺑﺎ‬

‫ﺑﻪ ﻋﻨﻮﺍﻥ ﻣﺜﺎﻝ ﺑﺎ ﺩﻭ ﺑﺮﺍﺑﺮ ﻧﻤﻮﺩﻥ ﺳﻄﺢ‬

‫)‪ 200‬ﺩﺭﺟــﻪ ﻓﺎﺭﻧﻬﺎﯾــﺖ( ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻪ‬

‫ﺩﻣﺎﻫﺎﯼ ﮐﻤﺘﺮﯼ ﮐﺎﺭ ﮐﻨــﺪ ﺍﻣﺎ ﺩﺑﯽ ﺁﺏ‬

‫ﺣﺮﺍﺭﺗﯽ ﮊﻧﺮﺍﺗﻮﺭ ﻣﯽﺗــﻮﺍﻥ ‪ 0.3‬ﺗﻦ ﺗﺒﺮﯾﺪ‬

‫ﻣﯽﺷﻮﺩ‪ ،‬ﺍﻣﺎ ﺗﻮﺭﻥ ﺑﻠﻮﻡ ﻭ ﻧﯿﻤﻮ ﺩﺭ ﺳﺎﻝ‬

‫ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ ﺩﺭ ﺁﻥﻫﺎ ﺍﻓﺰﺍﯾﺶ ﯾﺎﻓﺘﻪ‬

‫)‪ 1‬ﮐﯿﻠﻮﻭﺍﺕ( ﻇﺮﻓﯿﺖ ﺳــﺮﻣﺎﯾﯽ ﺭﺍ ﺑﺎ ﺁﺏ‬

‫‪ 1994‬ﻣﯿﻼﺩﯼ ﻧﺸﺎﻥ ﺩﺍﺩﻧﺪ ﮐﻪ ﺑﺎ ﺍﺿﺎﻓﻪ‬

‫ﮔﺮﻡ ‪ 79‬ﺩﺭﺟﻪ ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ )‪ 174‬ﺩﺭﺟﻪ‬

‫ﮐﺮﺩﻥ ﯾﮏ ﮐﻤﭙﺮﺳــﻮﺭ ﻣﺎﺑﯿﻦ ﺍﻭﺍﭘﺮﺍﺗﻮﺭ ﻭ‬

‫ﻓﺎﺭﻧﻬﺎﯾــﺖ( ﺗﺎﻣﯿــﻦ ﻧﻤﻮﺩ‪ ،‬ﺑــﺎ ﺍﻓﺰﺍﯾﺶ‬

‫ﺍﺑﺰﻭﺭﺑﺮ ﻣﯽﺗﻮﺍﻥ ﺍﺯ ﺩﻣﺎﯼ ﺁﺏ ﮔﺮﻡ ﻭﺭﻭﺩﯼ‬

‫ﺳــﻄﺢ ﺣﺮﺍﺭﺗــﯽ ﻣﺒﺪﻝ ﻧﯿﺰ ﺍﯾــﻦ ﻣﻘﺪﺍﺭ‬

‫ﮐﺎﺳــﺖ ﻭ ﺑــﻪ ﻫﻤﺎﻥ ﻇﺮﻓﯿﺖ ﺳــﺮﻣﺎﯾﯽ‬

‫ﺑﻪ ‪ 77.6‬ﺩﺭﺟﻪ ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ )‪ 172‬ﺩﺭﺟﻪ‬

‫ﺩﺳــﺖ ﯾﺎﻓــﺖ‪ .‬ﻫﻤﺎﻥﮔﻮﻧﻪ ﮐﻪ ﺍﺷــﺎﺭﻩ‬

‫ﻓﺎﺭﻧﻬﺎﯾﺖ( ﺗﻘﻠﯿﻞ ﺧﻮﺍﻫﺪ ﯾﺎﻓﺖ‪.‬‬

‫ﺷﺪ‪ ،‬ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺁﺏ ﮔﺮﻡ ﯾﮑﯽ ﺍﺯ ﻣﻮﺍﺭﺩ‬

‫ﻭ ﺩﺭ ﻣﺠﻤﻮﻉ ﺿﺮﯾﺐ ﮐﺎﺭﺍﯾﯽ ﻧﺴــﺒﺖ ﺑﻪ‬ ‫ﺳﯿﺴــﺘﻢﻫﺎﯼ ﯾﮏﺍﺛﺮﻩ ﺑﻪﺷﺪﺕ ﮐﺎﻫﺶ‬ ‫ﻣﯽﯾﺎﺑﺪ‪ .‬ﺩﺭ ﺟﺎﯾﯽ ﮐﻪ ﺑﺮﺍﯼ ﺗﺎﻣﯿﻦ ﺍﻧﺮﮊﯼ‬ ‫ﮔﺮﻣﺎﯾــﯽ ﮊﻧﺮﺍﺗﻮﺭ ﺍﺯ ﺍﺗﻼﻑ ﺣﺮﺍﺭﺕ ﺳــﺎﯾﺮ‬ ‫ﺳﯿﺴﺘﻢﻫﺎ ﯾﺎ ﻣﺎﺷﯿﻦﻫﺎ ﺍﺳﺘﻔﺎﺩﻩ ﻣﯽﺷﻮﺩ‬ ‫ﺗﻮﺟﻪ ﺯﯾــﺎﺩ ﺑﻪ ﻣﻮﺿﻮﻉ ﺿﺮﯾــﺐ ﮐﺎﺭﺍﯾﯽ‬ ‫ﭼﻨﺪﺍﻥ ﻗﺎﺑﻞ ﻗﺒﻮﻝ ﻧﯿﺴــﺖ‪ ،‬ﺯﯾﺮﺍ ﺩﺭ ﺍﯾﻦ‬ ‫ﺣﺎﻟﺖ ﻗﺼﺪ ﺍﯾﻦ ﺍﺳــﺖ ﮐﻪ ﺑﻪ ﮔﻮﻧﻪﺍﯼ ﺍﺯ‬ ‫ﺍﻧﺮﮊﯼ ﮔﺮﻣﺎﯾﯽ ﺗﻠﻒ ﺷﺪﻩ ﺍﺳﺘﻔﺎﺩﻩ ﻧﻤﻮﺩﻩ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﮔﺮﻣﺎﯾﯽ ﮊﻧﺮﺍﺗﻮﺭ ﺍﺳﺖ‪.‬‬

‫ﻭ ﺁﺑــﯽ ﺭﺍ ﺑﺎ ﺩﻣﺎﯼ ﮐﻤﺘــﺮﯼ ﮔﺮﻡ ﻧﻤﻮﺩﻩ‬ ‫ﻭ ﺁﻥ ﺭﺍ ﺑﺮﺍﯼ ﺳــﺮﻣﺎﯾﺶ ﻣﻮﺭﺩ ﺍﺳــﺘﻔﺎﺩﻩ‬

‫ﻧﻈﺮﯾﻪﭘﺮﺩﺍﺯﯼ ﺩﺭ ﻣﻮﺭﺩ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ‬

‫ﺯﻣﯿﻨﻪﺳﺎﺯ ﺑﺮﺍﯼ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺍﻧﺮﮊﯼﻫﺎﯼ‬

‫ﺁﺏ ﮔــﺮﻡ ﺑﺎ ﺩﻣﺎﯼ ﮐﻢ ﺑــﺮﺍﯼ ﭼﯿﻠﺮﻫﺎﯼ‬

‫ﺗﺠﺪﯾﺪﭘﺬﯾﺮ ﻭ ﺧﻠﻖ ﺳﯿﺴﺘﻢﻫﺎﯼ ﺗﺮﮐﯿﺒﯽ‬

‫ﯾﮏﺍﺛــﺮﻩ‪ ،‬ﻣﻘﺪﻣــﻪﺍﯼ ﺑــﺮﺍﯼ ﺑﻬﺮﻩﮔﯿﺮﯼ‬

‫ﺍﺳﺖ ﻭ ﺍﺳﺘﻔﺎﺩﻩ ﺍﯾﻦﭼﻨﯿﻦ ﺍﺯ ﮐﻤﭙﺮﺳﻮﺭ‬

‫ﺍﺯ ﺍﻧﺮﮊﯼ ﻧﺎﺷــﯽ ﺍﺯ ﺗﻠﻔﺎﺕ ﺣﺮﺍﺭﺗﯽ ﺍﻧﻮﺍﻉ‬

‫ﺩﺭ ﺳــﺎﺧﺘﺎﺭ ﺳﯿﺴــﺘﻢ ﺟﺬﺑــﯽ ﯾﮑﯽ ﺍﺯ‬

‫ﻣﺎﺷــﯿﻦﻫﺎ ﺑــﺮﺍﯼ ﮔــﺮﻡ ﻧﻤــﻮﺩﻥ ﺁﺏ ﻭ‬

‫ﻫﻤﯿﻦ ﺍﯾﺪﻩﻫﺎﺳﺖ‪.‬‬

‫ﺳﭙﺲ ﺑﻪﮐﺎﺭﮔﯿﺮﯼ ﺁﻥ ﺑﺮﺍﯼ ﺗﺎﻣﯿﻦ ﺍﻧﺮﮊﯼ‬

‫ﺗﻮﺭﻥﺑﻠــﻮﻡ ﻭ ﻧﯿﻤﻮ ﻃــﯽ ﺗﺤﻘﯿﻘﺎﺕ‬

‫ﻗﺮﺍﺭ ﺩﻫﯿﻢ‪ .‬ﺑﻨﺎﺑﺮﺍﯾﻦ ﺑﺎ ﻓﺮﺽ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ‬ ‫ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ ﮐﻪ ﺩﺭ ﺣﺎﻝ ﺑﻪ ﻫﺪﺭ ﺭﻓﺘﻦ‬

‫ﮐﻨﺪﺍﻧﺴﻮﺭ‬

‫ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﺯﯾﺎﺩ‬

‫ﻫﺴــﺘﻨﺪ‪ ،‬ﻣﯽﺗﻮﺍﻧﯿــﻢ ﺑﻪﮔﻮﻧﻪﺍﯼ ﮐﺎﻫﺶ‬ ‫ﺿﺮﯾﺐ ﮐﺎﺭﺍﯾﯽ ﻭﯾﮋﻩ ﺩﺭ ﺳﯿﺴــﺘﻢ ﻧﯿﻢﺍﺛﺮﻩ‬ ‫ﺭﺍ ﺑﺎ ﺑﻪﮐﺎﺭﮔﯿﺮﯼ ﺍﺯ ﺗﻠﻔﺎﺕ ﺣﺮﺍﺭﺗﯽ ﺟﺒﺮﺍﻥ‬ ‫ﮐﻨﯿﻢ‪ .‬ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺍﻧــﺮﮊﯼ ﺣﺮﺍﺭﺗﯽ ﯾﮏ‬

‫ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﺩﻣﺎﯼ‬ ‫ﺯﯾﺎﺩ‬

‫ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﮐﻢ‬

‫ﺩﻭﺩﮐــﺶ ﯾﺎ ﺍﻧﺮﮊﯼ ﮔﺮﻣﺎﯾﯽ ﺑﺪﻧﻪ ﻧﺎﺷــﯽ‬

‫ﺑﺨﺎﺭ ﯾﺎ ﺁﺏ‬ ‫ﮔﺮﻡ‬

‫ﺍﺑﺰﻭﺭﺑﺮ ﺩﻭﻡ‬

‫ﺍﺯ ﮐﺎﺭﮐــﺮﺩ ﯾﮏ ﻣﻮﺗــﻮﺭ ﻣﮑﺎﻧﯿﮑﯽ ﯾﺎ ﺁﺏ‬ ‫ﻭﺭﻭﺩ ﻭ ﺧﺮﻭﺝ‬ ‫ﺁﺏ ﺑﺮﺝ‬ ‫ﺁﺏ ﺑﺮﺝ ﺧﻨﮏﮐﻦ‬ ‫ﺧﻨﮏﮐﻦ‬ ‫ﺍﻭﺍﭘﺮﺍﺗﻮﺭ‬

‫ﮔﺮﻡ ﺭﺍﺩﯾﺎﺗﻮﺭ ﯾﮏ ﺍﺗﻮﻣﺒﯿﻞ ﮐﻪ ﻫﻤﮕﯽ ﺩﺭ‬ ‫ﺣﺎﻟﺖ ﻋﺎﺩﯼ ﺑــﺪﻭﻥ ﺍﻧﺠﺎﻡ ﻫﯿﭻ ﮐﺎﺭﯼ‪،‬‬

‫ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﺩﻣﺎﯼ ﮐﻢ‬

‫ﮔﺮﻣﺎﯼ ﻣﺤﯿــﻂ ﺭﺍ ﺍﻓﺰﺍﯾــﺶ ﻣﯽﺩﻫﻨﺪ‪،‬‬ ‫ﻣﯽﺗﻮﺍﻧﻨﺪ ﺗﺤﺖ ﺷــﺮﺍﯾﻄﯽ ﺧــﺎﺹ ﻭ ﺑﺎ‬

‫ﺍﺑﺰﻭﺭﺑﺮ ﺍﻭﻝ‬

‫ﺑﻪﮐﺎﺭﮔﯿﺮﯼ ﺗﺠﻬﯿﺰﺍﺕ ﻭ ﺳﯿﺴﺘﻢ ﻣﻨﺎﺳﺐ‬

‫ﺁﺏ ﺳﺮﺩﺷﺪﻩ‬

‫ﻋﺎﻣــﻞ ﻣﻨﺎﺳــﺒﯽ ﺑــﺮﺍﯼ ﺗﺎﻣﯿــﻦ ﺍﻧﺮﮊﯼ‬ ‫ﮔﺮﻣﺎﯾﯽ ﺳﯿﺴﺘﻢﻫﺎﯼ ﻧﯿﻢﺍﺛﺮﻩ ﺑﺎﺷﻨﺪ‪ .‬ﺍﺯ‬ ‫ﺍﯾﻦ ﺩﯾﺪﮔﺎﻩ ﻣﯽﺗﻮﺍﻥ ﮐﺎﻫﺶ ﻗﺎﺑﻞ ﺗﻮﺟﻪ‬

‫ﺗﺼﻮﯾﺮ )‪ (1‬ﭼﺮﺧﻪ ﺳﯿﺴﺘﻢ ﺟﺬﺑﯽ ﻧﯿﻢﺍﺛﺮﻩ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺻﻔﺤﻪ ‪ / 9‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺧــﻮﺩ ﺑﺎ ﺍﺿﺎﻓﻪ ﮐﺮﺩﻥ ﮐﻤﭙﺮﺳــﻮﺭ ﻣﻮﻓﻖ‬

‫‪Q‬‬

‫)‪(1‬‬

‫‪D‬‬

‫ ‪ U u 60 t E t L‬‬

‫ﺷــﺪﻧﺪ ﺩﻣﺎﯼ ﺁﺏ ﮔــﺮﻡ ﻭﺭﻭﺩﯼ ﺑﻪ ﭼﯿﻠﺮ‬

‫ﺑﺎﯾﺪ ﺍﯾﻦ ﺍﺳﻨﺎﺩ ﻣﻼﮎ ﺗﻌﯿﯿﻦ ﻭ ﺍﻧﺘﺨﺎﺏ‬ ‫ﻗﺮﺍﺭ ﮔﯿﺮﻧﺪ‪.‬‬

‫ﺭﺍ ﺗﺎ ‪ 79.4‬ﺩﺭﺟﻪ ﺳﺎﻧﺘﯽﮔﺮﺍﺩ )‪ 175‬ﺩﺭﺟﻪ‬

‫‪ = D‬ﺩﺑﯽ ﺁﺏ ﮔﺮﻡ )‪(gpm‬‬

‫ﻓﺎﺭﻧﻬﺎﯾﺖ( ﮐﺎﻫﺶ ﺩﻫﻨﺪ ﻭ ﺩﺭ ﻋﯿﻦ ﺣﺎﻝ‬

‫‪ = Q‬ﻇﺮﻓﯿــﺖ ﮔﺮﻣﺎﯾــﯽ ﻣــﻮﺭﺩ ﻧﯿﺎﺯ‬

‫ﺑﻪ ﻫﻤﺎﻥ ﻇﺮﻓﯿﺖ ﺩﺳــﺖ ﯾﺎﺑﻨﺪ‪ .‬ﺩﺭ ﺍﯾﻦ‬ ‫ﺗﺤﻘﯿﻖ‪ ،‬ﺿﺮﯾﺐ ﮐﺎﺭﺍﯾﯽ ﺑﺮﺍﯼ ﺳﯿﺴــﺘﻢ‬ ‫ﻣﺘﻌﺎﺭﻑ ‪ 0.77‬ﻭ ﺑﺮﺍﯼ ﺳﯿﺴﺘﻢ ﻣﺠﻬﺰ ﺑﻪ‬

‫ﮊﻧﺮﺍﺗﻮﺭ )‪(Btu/hr‬‬ ‫‪ = ρ‬ﭼﮕﺎﻟﯽ ﺁﺏ ﺩﺭ ﺩﻣﺎﯼ ﻣﻮﺭﺩ ﻧﻈﺮ‬ ‫)‪(lb/gal‬‬

‫ﮐﻤﭙﺮﺳﻮﺭ ‪ 0.79‬ﺑﻪ ﺩﺳﺖ ﺁﻣﺪ‪ .‬ﺩﺭ ﻫﻤﯿﻦ‬

‫)ﭼﮕﺎﻟــﯽ ﺁﺏ ﺑﺮﺍﯼ ﺩﻣــﺎﯼ ‪،260 F‬‬

‫ﺁﺯﻣﺎﯾﺶ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺁﺏ ﮔــﺮﻡ ﺑﺎ ﺩﻣﺎﯼ‬

‫‪ 32oF ،180oF ،200oF ،212oF‬ﺑــﻪ ﺗﺮﺗﯿﺐ‬

‫‪ 79.4‬ﺩﺭﺟــﻪ ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ )‪ 175‬ﺩﺭﺟﻪ‬

‫‪ 7.996 ،8.035 ،8.097 ،8.33‬ﻭ ‪7.823‬‬

‫ﻓﺎﺭﻧﻬﺎﯾــﺖ( ﻣﻨﺠﺮ ﺑﻪ ﮐﺎﻫــﺶ ‪ 0.23‬ﺗﻦ‬

‫ﭘﻮﻧﺪ ﺑﺮ ﮔﺎﻟﻦ ﺍﺳﺖ‪(.‬‬

‫‪o‬‬

‫ﺍﺯ ﻇﺮﻓﯿــﺖ ﮐﻞ ‪ 1.0‬ﺗﻦ ﺗﺒﺮﯾﺪ ﻭ ﮐﺎﻫﺶ‬

‫‪ = 60‬ﺑﺮﺍﯼ ﺗﺒﺪﯾﻞ ﺳﺎﻋﺖ ﺑﻪ ﺩﻗﯿﻘﻪ‬

‫ﺿﺮﯾﺐ ﮐﺎﺭﺍﯾﯽ ﺗﺎ ﺣﺪ ‪ 0.63‬ﺷﺪ ﺍﻣﺎ ﺍﺿﺎﻓﻪ‬

‫‪ = tE‬ﺩﻣﺎﯼ ﺁﺏ ﻭﺭﻭﺩﯼ )‪( F‬‬

‫ﮐﺮﺩﻥ ﮐﻤﭙﺮﺳــﻮﺭ ﺑﻪ ﺍﯾــﻦ ﭼﺮﺧﻪ ﻫﻤﺎﻥ‬

‫‪ = tL‬ﺩﻣﺎﯼ ﺁﺏ ﺧﺮﻭﺟﯽ )‪( F‬‬

‫ﻋﯿﺐ ﺑﺰﺭﮒ ﺳﯿﺴﺘﻢﻫﺎﯼ ﺗﺮﺍﮐﻤﯽ‪ ،‬ﯾﻌﻨﯽ‬

‫ﭼﻨﺎﻧﭽــﻪ ﺩﺭ ﺭﺍﺑﻄــﻪ )‪ (1‬ﻣﯿﺎﻧﮕﯿــﻦ‬

‫ﻣﺼﺮﻑ ﺍﻟﮑﺘﺮﯾﺴــﯿﺘﻪ ﺭﺍ ﺑﻪ ﻫﻤﺮﺍﻩ ﺩﺍﺭﺩ‪.‬‬

‫ﭼﮕﺎﻟــﯽ ﺁﺏ ﺭﺍ ‪ 8‬ﻓﺮﺽ ﮐﻨﯿﻢ‪ ،‬ﻣﯽﺗﻮﺍﻧﯿﻢ‬

‫ﺑﻪ ﻋﻨﻮﺍﻥ ﻣﺜﺎﻝ ﺩﺭ ﻫﻤﯿﻦ ﺁﺯﻣﺎﯾﺶ ﺑﺮﺍﯼ‬

‫ﺭﺍﺑﻄﻪ ﺭﺍ ﺑﻪ ﺷﮑﻞ ﺳﺎﺩﻩﺗﺮ ﺯﯾﺮ ﺑﻨﻮﯾﺴﯿﻢ‪:‬‬

‫‪o‬‬

‫ﺍﺳــﺐ( ﺍﻧﺮﮊﯼ ﺍﻟﮑﺘﺮﯾﮑﯽ ﻣﺼﺮﻑ ﺧﻮﺍﻫﺪ‬ ‫ﻣﯽﺗﻮﺍﻧﺪ ﺗﺒﺪﯾﻞ ﺑﻪ ﻋــﺪﺩ ﻗﺎﺑﻞ ﺗﻮﺟﻪﺍﯼ‬ ‫ﺷﻮﺩ؛ ﺍﮔﺮ ﭼﻪ ﻓﺎﺻﻠﻪ ﺁﻥ ﺑﺎ ﺳﯿﺴﺘﻢﻫﺎﯼ‬ ‫ﺗﻤﺎﻡ ﺗﺮﺍﮐﻤﯽ ﻫﻨﻮﺯ ﺑﺴــﯿﺎﺭ ﺯﯾﺎﺩ ﺍﺳــﺖ‪.‬‬ ‫ﺯﯾﺮﺍ ﺩﺭ ﺁﻥ ﺳﯿﺴﺘﻢﻫﺎ ﻣﺼﺮﻑ ﺍﻟﮑﺘﺮﯾﮑﯽ‬ ‫ﺑــﻪ ﺍﺯﺍﯼ ﻫﺮ ﺗﻦ ﺗﺒﺮﯾﺪ ﺑﯿﻦ ‪ 800‬ﺗﺎ ‪1000‬‬

‫‪D‬‬

‫‪ = ∆t‬ﺍﺧﺘﻼﻑ ﺩﻣــﺎﯼ ﺁﺏ ﻭﺭﻭﺩﯼ ﻭ‬ ‫ﺧﺮﻭﺟﯽ )‪(oF‬‬ ‫ﺍﻣﺎ ﺍﻏﻠﺐ ﺑــﻪ ﺻﻮﺭﺕ ﺳﺮﺍﻧﮕﺸــﺘﯽ‬ ‫ﭼﮕﺎﻟﯽ ﺭﺍ ﺑﺮﺍﺑﺮ ‪ 8.33‬ﻓﺮﺽ ﻧﻤﻮﺩﻩ ﻭ ﺩﺑﯽ‬ ‫ﺭﺍ ﭼﻨﯿﻦ ﺗﺨﻤﯿﻦ ﻣﯽﺯﻧﻨﺪ‪:‬‬ ‫‪Q‬‬ ‫‪500 't‬‬

‫‪D‬‬

‫ﻭﺍﺕ ﺍﺳﺖ ﻭ ﺩﺭ ﺧﻮﺵﺑﯿﻨﺎﻧﻪﺗﺮﯾﻦ ﺣﺎﻟﺖ‬ ‫ﺍﯾــﻦ ﻣﻘﺪﺍﺭ ﮐﻤﺘــﺮ ﺍﺯ ‪ 600‬ﻭﺍﺕ ﻧﺨﻮﺍﻫﺪ‬

‫ﺭﺍ ‪ 20‬ﺩﺭﺟــﻪ ﻓﺎﺭﻧﻬﺎﯾــﺖ ﺩﺭﻧﻈﺮ ﮔﯿﺮﯾﻢ‪،‬‬

‫ﺷﺪ‪.‬‬

‫ﺭﺍﺑﻄﻪ ﺗﺨﻤﯿﻨﯽ ﺯﯾﺮ ﻧﺘﯿﺠﻪ ﻣﯽﺷﻮﺩ‪:‬‬

‫ﭼﯿﻠﺮﻫــﺎﯼ ﺁﺏ ﺩﺍﻍ ﻭ ﺁﺏ ﮔــﺮﻡ ﻣﺘﻌﺎﺭﻑ‬

‫ﺑﺴــﯿﺎﺭ ﺧﻮﺑﯽ ﺑــﺮﺍﯼ ﭼﯿﻠﺮﻫــﺎﯼ ﺟﺬﺑﯽ‬ ‫ﺍﺳــﺖ‪ .‬ﺑﺨــﺎﺭ ﻭﺭﻭﺩﯼ ﺑﻪ ﮊﻧﺮﺍﺗــﻮﺭ ﭼﯿﻠﺮ‬ ‫ﺟﺬﺑﯽ ﺑﺎﯾﺪ ﺧﺸــﮏ ﻭ ﺑﺪﻭﻥ ﻗﻄﺮﺍﺕ ﺁﺏ‬ ‫ﺑﺎﺷﺪ‪ .‬ﻭﺟﻮﺩ ﻫﻮﺍ ﺑﻪ ﻫﻤﺮﺍﻩ ﺑﺨﺎﺭ ﺍﺯ ﺩﻣﺎﯼ‬ ‫ﺁﻥ ﮐﺎﺳﺘﻪ ﻭ ﻣﯽﺗﻮﺍﻧﺪ ﺍﻧﺘﻘﺎﻝ ﺣﺮﺍﺭﺕ ﺩﺭ‬ ‫ﮊﻧﺮﺍﺗــﻮﺭ ﺭﺍ ﺩﭼﺎﺭ ﺍﺧﺘﻼﻝ ﮐﻨﺪ ﻭ ﺩﺭ ﻋﯿﻦ‬ ‫ﺣــﺎﻝ ﻭﺭﻭﺩ ﺩﯼﺍﮐﺴــﯿﺪﮐﺮﺑﻦ ﺑﻪ ﻫﻤﺮﺍﻩ‬ ‫ﮐﺮﺑﻨﯿــﮏ ﻭ ﺧﻮﺭﺩﮔﯽ ﻟﻮﻟﻪﻫــﺎﯼ ﮊﻧﺮﺍﺗﻮﺭ‬ ‫ﺷــﻮﺩ‪ .‬ﺑﻨﺎﺑﺮﺍﯾﻦ ﺑﺨﺎﺭ ﺑﺎﯾﺪ ﺗﺎ ﺣﺪ ﺍﻣﮑﺎﻥ‬ ‫ﺧﺎﻟﺺ ﻭ ﺑﺪﻭﻥ ﻣﻮﺍﺩ ﺯﺍﺋﺪ ﺑﺎﺷﺪ‪.‬‬ ‫ﻓﺸــﺎﺭ ﺑﺨﺎﺭ ﺑــﺮﺍﯼ ﭼﯿﻠﺮﻫــﺎﯼ ﯾﮏ‬ ‫ﻣﺮﺣﻠﻪﺍﯼ ﺑﯿﻦ ‪ 9‬ﺗﺎ ‪ 12‬ﻭ ﺑﺮﺍﯼ ﭼﯿﻠﺮﻫﺎﯼ‬ ‫ﺩﻭ ﻣﺮﺣﻠﻪﺍﯼ ‪ 110‬ﺗــﺎ ‪ 120‬ﭘﻮﻧﺪ ﺑﺮ ﺍﯾﻨﭻ‬ ‫ﻣﺮﺑــﻊ ﻣﺘﻌــﺎﺭﻑ )ﻏﯿﺮﻣﻄﻠــﻖ( ﺩﺭ ﻧﻈﺮ‬ ‫ﮔﺮﻓﺘﻪ ﻣﯽﺷﻮﺩ‪ .‬ﺩﻣﺎﯼ ﮊﻧﺮﺍﺗﻮﺭ ﭼﯿﻠﺮﻫﺎﯼ‬ ‫ﯾﮏﺍﺛــﺮﻩ ﻧﯿﺰ ﺑﯿــﻦ ‪ 115‬ﺗــﺎ ‪ 120‬ﺩﺭﺟﻪ‬ ‫ﺳﺎﻧﺘﯽﮔﺮﺍﺩ )‪ (240oF - 248oF‬ﺑﺎﯾﺪ ﺑﺎﺷﺪ‪.‬‬ ‫ﺑــﺮﺍﯼ ﭼﯿﻠﺮﻫﺎﯼ ﺩﻭ ﺍﺛﺮﻩ ﺍﯾﻦ ﻣﻘﺪﺍﺭ ﺑﺮﺍﺑﺮ‬

‫ﻭ ﺍﮔﺮ ﺍﺧﺘﻼﻑ ﺩﻣﺎﯼ ﺭﻓﺖ ﻭ ﺑﺮﮔﺸﺖ‬

‫ﺩﻣــﺎﯼ ﺁﺏ ﻭﺭﻭﺩﯼ ﺑــﻪ ﮊﻧﺮﺍﺗــﻮﺭ‬

‫ﮔﺮﻣــﺎﯼ ﻧﻬﺎﻥ ﺑﺨــﺎﺭ ﻣﻨﺒــﻊ ﺍﻧﺮﮊﯼ‬

‫‪Q‬‬ ‫‪1000‬‬

‫ﺑــﺎ ‪ 188‬ﺩﺭﺟﻪ ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ )‪ 370‬ﺩﺭﺟﻪ‬ ‫ﻓﺎﺭﻧﻬﺎﯾﺖ( ﺍﺳﺖ‪.‬‬ ‫ﺩﺭﻣــﻮﺭﺩ ﭼﯿﻠﺮﻫــﺎﯼ ﯾﮏﺍﺛــﺮﻩ ﺑﻬﺘﺮ‬ ‫ﺍﺳﺖ ﮐﻪ ﺩﺭ ﻣﺴــﯿﺮ ﺑﺨﺎﺭ ﺍﺯ ﻓﺸﺎﺭﺷﮑﻦ‬ ‫ﺍﺳﺘﻔﺎﺩﻩ ﻧﺸﻮﺩ‪ ،‬ﺯﯾﺮﺍ ﻣﻌﻤﻮﻻ ﭘﺲ ﺍﺯ ﺍﻓﺖ‬

‫‪D‬‬

‫ﻓﺸــﺎﺭ‪ ،‬ﺩﻣﺎﯼ ﺑﺨﺎﺭ ﮐﻢﻓﺸــﺎﺭ ﺑﻪ ﻫﻤﺎﻥ‬

‫ﺑﻪ ﺗﺮﺗﯿﺐ ‪ 100‬ﺗﺎ ‪ 130‬ﺩﺭﺟﻪ ﺳﺎﻧﺘﯽﮔﺮﺍﺩ‬

‫ﺍﺯ ﺁﻧﺠــﺎ ﮐــﻪ ﺩﺭ ﻋﻤــﻞ ﭼﯿﻠﺮﻫــﺎﯼ‬

‫ﻧﺴــﺒﺖ ﮐﺎﻫﺶ ﻧﻤﯽﯾﺎﺑﺪ ﻭ ﻣﻤﮑﻦ ﺍﺳﺖ‬

‫)‪ (212OF- 266OF‬ﻭ ‪ 80‬ﺗــﺎ ‪ 95‬ﺩﺭﺟــﻪ‬

‫ﺟﺬﺑﯽ ﺑﺎ ﮊﻧﺮﺍﺗﻮﺭ ﺑﺨﺎﺭ ﺗﺤﺖ ﺷــﺮﺍﯾﻄﯽ ﺑﺎ‬

‫ﺍﺿﺎﻓﻪ ﺩﻣﺎﯼ ﺑﺨﺎﺭ ﮐﻪ ﺗﺤﺖ ﺗﺎﺛﯿﺮ ﺗﻘﻠﯿﻞ‬

‫ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ )‪ (176OF -203OF‬ﺍﺳــﺖ‪.‬‬

‫ﺁﺏ ﺩﺍﻍ ﯾــﺎ ﺁﺏ ﮔﺮﻡ ﻧﯿﺰ ﻣﻮﺭﺩ ﺍﺳــﺘﻔﺎﺩﻩ‬

‫ﻓﺸــﺎﺭ ﺑﻪ ﻭﺟــﻮﺩ ﺁﻣﺪﻩ ﺍﺳــﺖ ﺍﺯ ﻣﻘﺪﺍﺭ‬

‫ﺑﺮﺍﯼ ﺗﻌﯿﯿﻦ ﺍﻧﺪﺍﺯﻩ ﭘﻤﭗ ﻭ ﻟﻮﻟﻪﻫﺎﯼ ﺭﻓﺖ‬

‫ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﻧــﺪ‪ ،‬ﮐﺎﺭﺧﺎﻧﺠﺎﺕ ﺳــﺎﺯﻧﺪﻩ‬

‫ﻣﺠﺎﺯ ﮐﺎﺭﮐﺮﺩ ﮊﻧﺮﺍﺗﻮﺭ ﺑﯿﺸــﺘﺮ ﺑﺎﺷــﺪ‪ .‬ﺩﺭ‬

‫ﻭ ﺑﺮﮔﺸــﺖ ﺁﺏ ﺩﺍﻍ ﯾﺎ ﺁﺏ ﮔﺮﻡ ﺑﺎﯾﺪ ﺩﺑﯽ‬

‫ﺩﺭ ﮐﺎﺗﺎﻟﻮﮒﻫــﺎﯼ ﺧﻮﺩ ﭼﮕﻮﻧﮕﯽ ﺗﻌﯿﯿﻦ‬

‫ﻭﺍﻗــﻊ ﭘــﺲ ﺍﺯ ﻋﻤﻠﯿﺎﺕ ﺗﻘﻠﯿﻞ ﻓﺸــﺎﺭ‪،‬‬

‫ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﺗﻌﯿﯿﻦ ﺷــﻮﺩ‪ .‬ﺩﺑﯽ ﺭﺍ ﻣﯽﺗﻮﺍﻥ‬

‫ﻣﻘﺪﺍﺭ ﻣﻌــﺎﺩﻝ ﺁﺏ ﮔﺮﻡ ﺑــﻪ ﺟﺎﯼ ﺑﺨﺎﺭ‬

‫ﺑﺨﺎﺭ ﻓﻮﻕ ﺩﺍﻍ ﻣﯽﺷــﻮﺩ‪ .‬ﺍﯾﻦ ﻣﻮﺿﻮﻉ‬

‫ﺍﺯ ﻃﺮﯾﻖ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﻣﺤﺎﺳﺒﻪ ﻧﻤﻮﺩ‪:‬‬

‫ﺭﺍ ﺩﺭ ﻗﺎﻟــﺐ ﻧﻤﻮﺩﺍﺭﻫﺎ ﻭ ﺭﻭﺍﺑﻄﯽ ﺷــﺮﺡ‬

‫ﺍﺯ ﻧﻈﺮ ﺧﺸــﮏ ﻧﻤﻮﺩﻥ ﺑﺨﺎﺭ ﻣﻔﯿﺪ ﺍﺳﺖ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫‪1‬‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺷﺪ ﮐﻪ ﺩﺭ ﻇﺮﻓﯿﺖﻫﺎﯼ ﺑﯿﺸﺘﺮ ﺳﺮﻣﺎﯾﺸﯽ‬

‫‪Q‬‬ ‫‪480 't‬‬

‫ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺑﺎ ﮊﻧﺮﺍﺗﻮﺭ ﺑﺨﺎﺭ‬

‫ﺑﺨﺎﺭ ﻧﯿﺰ ﻣﯽﺗﻮﺍﻧﺪ ﻣﻮﺟﺐ ﺗﻮﻟﯿﺪ ﺍﺳــﯿﺪ‬

‫‪o‬‬

‫ﺗﺎﻣﯿﻦ ﯾﮏ ﺗﻦ ﺗﺒﺮﯾــﺪ‪ 117 ،‬ﻭﺍﺕ )‪0.15‬‬

‫ﻣﯽﺩﻫﻨــﺪ‪ .‬ﺑﻨﺎﺑﺮﺍﯾﻦ ﺩﺭ ﻣــﻮﺍﺭﺩ ﺍﺟﺮﺍﯾﯽ‬

‫ﺻﻔﺤﻪ ‪ / 10‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺍﻣﺎ ﺍﺯ ﻧﻈﺮ ﺩﻣﺎ ﻣﻤﮑﻦ ﺍﺳــﺖ ﻣﺨﺎﻃﺮﺍﺗﯽ‬

‫ﺧﺸﮏ ﺑﻮﺩﻥ ﺑﺨﺎﺭ ﺑﻪ ﺷﺮﻁ ﺑﺮﺧﻮﺭﺩﺍﺭﯼ‬

‫ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ ﺍﺯ ﻧﻮﻉ ﺁﻣﻮﻧﯿﺎﮐﯽ ﺑﻮﺩﻧﺪ‬

‫ﺭﺍ ﻣﺘﻮﺟﻪ ﮊﻧﺮﺍﺗﻮﺭ ﺳﺎﺯﺩ‪ .‬ﺑﻪ ﻋﻨﻮﺍﻥ ﻣﺜﺎﻝ‬

‫ﺍﺯ ﺩﻣﺎﯼ ﻣﻨﺎﺳﺐ ﻣﯽﺗﻮﺍﻧﺪ ﺑﻬﺘﺮﯾﻦ ﺣﺎﻟﺖ‬

‫ﮐــﻪ ﻣﺼﺎﺭﻑ ﮐﺜﯿﺮﯼ ﺑــﻪ ﻋﻨﻮﺍﻥ ﯾﺨﭽﺎﻝ‬

‫ﺩﻣﺎﯼ ﺑﺨﺎﺭ ﭘﺲ ﺍﺯ ﮐﺎﻫﺶ ﻓﺸــﺎﺭ ﺍﺯ ‪150‬‬

‫ﺑﺎﺷــﺪ‪ .‬ﺑﻨﺎﺑﺮﺍﯾﻦ ﻣﺨﻠﻮﻁ ﺁﺏ ﺍﺷــﺒﺎﻉ ﺑﺎ‬

‫ﺧﺎﻧﮕﯽ ﺩﺍﺷــﺘﻨﺪ‪ .‬ﺍﺯ ﺍﯾــﻦ ﻧﻈﺮ ﻣﯽﺗﻮﺍﻥ‬

‫ﺑﻪ ‪ 15‬ﭘﻮﻧﺪ ﺑﺮ ﺍﯾﻨﭻ ﻣﺮﺑﻊ ﻣﻤﮑﻦ ﺍﺳﺖ ﺑﻪ‬

‫ﺑﺨــﺎﺭ ﻣﯽﺗﻮﺍﻧﺪ ﻣﻨﺠﺮ ﺑﻪ ﮐﺎﻫﺶ ﺳــﻬﻢ‬

‫ﮔﻔﺖ ﮐﻪ ﻓﻨﺎﻭﺭﯼ ﺳــﺎﺧﺖ ﺳﯿﺴﺘﻢﻫﺎﯼ‬

‫‪ 150‬ﺩﺭﺟﻪ ﺳﺎﻧﺘﯽﮔﺮﺍﺩ ﺑﺮﺳﺪ ﻭ ﺍﯾﻦ ﻣﻘﺪﺍﺭ‬

‫ﺣﺮﺍﺭﺗﯽ ﺑﺨﺎﺭ ﻭ ﺩﺭ ﻧﺘﯿﺠﻪ ﮐﺎﻫﺶ ﮔﺮﻣﺎﯼ‬

‫ﺷﻌﻠﻪﻣﺴﺘﻘﯿﻢ ﻣﺘﻘﺪﻡﺗﺮ ﺍﺯ ﺳﯿﺴﺘﻢﻫﺎﯼ‬

‫ﺩﺭ ﺣﺎﻟﺖ ﮐﺎﻫﺶ ﻓﺸﺎﺭ ﺍﺯ ‪ 75‬ﺑﻪ ‪ 15‬ﭘﻮﻧﺪ‬

‫ﮐﻞ ﺷﻮﺩ‪.‬‬

‫ﺑﺨــﺎﺭ ﯾــﺎ ﺁﺏ ﮔﺮﻡ ﺍﺳــﺖ ﺍﻣــﺎ ﺗﻨﻬﺎ ﺩﺭ‬

‫ﺑــﺮ ﺍﯾﻨﭻ ﻣﺮﺑﻊ‪ 140 ،‬ﺩﺭﺟﻪ ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ‬

‫ﭼﯿﻠﺮﻫــﺎﯼ ﺟﺬﺑــﯽ ﯾﮏﺍﺛــﺮﻩ ﺑﺮﺍﯼ‬

‫ﺳﺎﻟﯿﺎﻥ ﺍﺧﯿﺮ )‪ 1980‬ﻣﯿﻼﺩﯼ ﺑﻪ ﺑﻌﺪ( ﺍﺯ‬

‫ﺧﻮﺍﻫــﺪ ﺑــﻮﺩ‪ .‬ﺩﺭ ﻫﺮ ﯾــﮏ ﺍﺯ ﺩﻭ ﺣﺎﻟﺖ‬

‫ﻋﻤﻠﯿــﺎﺕ ﺗﻐﻠﯿــﻆ ﺑــﻪ ‪ 18.3‬ﭘﻮﻧــﺪ ﺩﺭ‬

‫ﺍﯾﻦ ﻓﻨﺎﻭﺭﯼ ﺑﺮﺍﯼ ﺗﻮﻟﯿﺪ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ‬

‫ﻓﻮﻕ ﺩﻣﺎﯼ ﺑﺨﺎﺭ ﻭﺭﻭﺩﯼ ﺑﻪ ﮊﻧﺮﺍﺗﻮﺭ ﺑﺎﻻﺗﺮ‬

‫ﺳــﺎﻋﺖ )‪ 8.3‬ﮐﯿﻠﻮﮔــﺮﻡ ﺩﺭ ﺳــﺎﻋﺖ(‬

‫ﺑــﻪ ﻣﻨﻈﻮﺭ ﮐﺎﺭﺑﺮﺩ ﺩﺭ ﺗﺎﺳﯿﺴــﺎﺕ ﺗﻬﻮﯾﻪ‬

‫ﺍﺯ ﺣﺪ ﻣﺠﺎﺯ ﺍﻏﻠﺐ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ ﯾﮏ‬

‫ﺑﺨﺎﺭ ﺑﻪ ﺍﺯﺍﯼ ﻫﺮ ﺗــﻦ ﺗﺒﺮﯾﺪ ﻧﯿﺎﺯ ﺩﺍﺭﻧﺪ‪.‬‬

‫ﻣﻄﺒﻮﻉ ﺳــﺎﺧﺘﻤﺎﻥﻫﺎ ﺍﺳــﺘﻔﺎﺩﻩ ﺷــﺪﻩ‬

‫ﻣﺮﺣﻠﻪﺍﯼ ﺍﺳﺖ‪.‬‬

‫ﺍﯾــﻦ ﻣﻘﺪﺍﺭ ﺑﺮﺍﯼ ﭼﯿﻠﺮﻫــﺎﯼ ﺩﻭ ﺍﺛﺮﻩ ﺩﺭ‬

‫ﺍﺳــﺖ‪ .‬ﺑﻨﺎﺑﺮﺍﯾــﻦ‪ ،‬ﺍﺯ ﺍﯾﻦ ﻧﻈــﺮ ﻓﻨﺎﻭﺭﯼ‬

‫ﺍﺳﺎﺳــﺎ ﺩﺭ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ‪ ،‬ﺍﻧﺮﮊﯼ‬

‫ﺣــﺪﻭﺩ ‪ 10‬ﭘﻮﻧﺪ ﺩﺭ ﺳــﺎﻋﺖ ﺍﺳــﺖ‪ .‬ﺑﺮ‬

‫ﻣﺮﺑﻮﻁ ﺑﻪ ﺁﻥ ﻣﺘﺎﺧﺮﺗﺮ ﺍﺯ ﺳﯿﺴــﺘﻢﻫﺎﯼ‬

‫ﻧﺎﺷﯽ ﺍﺯ ﮔﺮﻣﺎﯼ ﻧﻬﺎﻥ ﺑﺨﺎﺭ ﻣﻮﺭﺩ ﺍﺳﺘﻔﺎﺩﻩ‬

‫ﺍﯾﻦ ﺍﺳــﺎﺱ ﭼﻨﺎﻧﭽﻪ ﮔﺮﻣــﺎﯼ ﮐﻞ ﺑﺨﺎﺭ‬

‫ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﺩ ﻭ ﮔﺮﻣﺎﯼ ﻣﺤﺴــﻮﺱ ﺑﺨﺎﺭ‬ ‫ﭼﻨﺪﺍﻥ ﺗﺎﺛﯿﺮﯼ ﺩﺭ ﻓﺮﺍﯾﻨﺪ ﺗﻐﻠﯿﻆ ﻧﺪﺍﺭﺩ‪.‬‬ ‫ﺍﺯ ﺍﯾﻦﺭﻭ ﻓﻮﻕﺩﺍﻍ ﺷﺪﻥ ﺑﺨﺎﺭ ﮐﻪ ﺍﻓﺰﺍﯾﺶ‬ ‫ﮔﺮﻣــﺎﯼ ﻣﺤﺴــﻮﺱ ﻭ ﺍﻓﺰﺍﯾــﺶ ﺩﻣﺎﯼ‬ ‫ﺑﺨﺎﺭ ﺭﺍ ﺑﻪ ﻫﻤــﺮﺍﻩ ﺩﺍﺭﺩ‪ ،‬ﻣﻮﺟﺐ ﮐﻨﺪﯼ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺍﻧﺘﻘﺎﻝ ﺣــﺮﺍﺭﺕ ﻭ ﺗﺎﺧﯿﺮ ﺩﺭ ﺍﺧﺬ ﮔﺮﻣﺎﯼ‬ ‫ﻧﻬﺎﻥ ﻣﯽﺷــﻮﺩ ﺯﯾﺮﺍ ﻣﺪﺗﯽ ﻃﻮﻝ ﺧﻮﺍﻫﺪ‬

‫ﺭﺍ ﺑــﻪ ﺍﺯﺍﯼ ﻫﺮ ﭘﻮﻧــﺪ‪ 1000Btu ،‬ﺩﺭﻧﻈﺮ‬ ‫ﮔﯿﺮﯾــﻢ‪ ،‬ﻣﯽﺗﻮﺍﻧﯿﻢ ﻧﯿــﺎﺯ ﮔﺮﻣﺎﯾﯽ ﮊﻧﺮﺍﺗﻮﺭ‬ ‫ﭼﯿﻠﺮﻫــﺎﯼ ﯾﮏﺍﺛــﺮﻩ ﻭ ﺩﻭ ﺍﺛــﺮﻩ ﺭﺍ ﺑــﻪ‬ ‫ﺗﺮﺗﯿــﺐ ﺩﺭ ﺣــﺪﻭﺩ ‪18300‬ﻭ ‪10000Btu‬‬

‫ﺩﺭ ﺳــﺎﻋﺖ ﺑــﻪ ﺍﺯ ﺍﯼ ﻫﺮ ﺗــﻦ ﻇﺮﻓﯿﺖ‬ ‫ﺳﺮﻣﺎﯾﺸﯽ ﺗﺨﻤﯿﻦ ﺑﺰﻧﯿﻢ‪.‬‬

‫ﺟﺬﺑــﯽ ﺑﺨــﺎﺭ ﯾــﺎ ﺁﺏ ﮔﺮﻡ ﻣﺤﺴــﻮﺏ‬ ‫ﻣﯽﺷــﻮﺩ‪ .‬ﭼﯿﻠﺮﻫــﺎﯼ ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ‬ ‫ﺍﻭﻟﯿــﻪ ﻫﻤﮕﯽ ﺍﺯ ﻧــﻮﻉ ﺁﻣﻮﻧﯿﺎﮐﯽ ﺑﻮﺩﻧﺪ‪،‬‬ ‫ﺩﺭﺻﻮﺭﺗﯽﮐﻪ ﭼﯿﻠﺮﻫــﺎﯼ ﻣﻮﺭﺩ ﺑﺤﺚ ﺩﺭ‬ ‫ﺍﯾﻦ ﻗﺴــﻤﺖ ﺍﺯ ﻧﻮﻉ ﻟﯿﺘﯿﻢ ﺑﺮﻭﻣﺎﯾﺪ ﻭ ﺁﺏ‬ ‫ﻫﺴﺘﻨﺪ‪ .‬ﺍﻟﺒﺘﻪ ﺍﻣﺮﻭﺯﻩ ﺍﻧﻮﺍﻉ ﺳﯿﺴﺘﻢﻫﺎﯼ‬ ‫ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ ﺁﻣﻮﻧﯿﺎﮐﯽ ﻧﯿﺰ ﺑﻪ ﻋﻨﻮﺍﻥ‬ ‫ﻭﺍﺣﺪﻫــﺎﯼ ﮐﻢﻇﺮﻓﯿــﺖ ﻣﺤﻠــﯽ ﻣﻮﺭﺩ‬

‫ﮐﺸــﯿﺪ ﺗﺎ ﺑﺨﺎﺭ ﺳﺮﺩ ﺷــﺪﻩ ﻭ ﺑﻪ ﺩﻣﺎﯼ‬

‫ﺳﯿﺴـﺘﻢ ﺳـﺮﻣﺎﯾﺶ ﺟﺬﺑـﯽ‬ ‫ﺷﻌﻠﻪﻣﺴﺘﻘﯿﻢ‬

‫ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ ﺩﻭ‬

‫ﺍﺯ ﮔﺮﻣﺎﯼ ﻧﻬﺎﻥ ﺑﺨﺎﺭ ﺑﺪﻭﻥ ﺭﺳــﯿﺪﻥ ﺑﻪ‬

‫ﺍﻭﻟﯿﻦ ﺳﯿﺴﺘﻢﻫﺎﯼ ﺳﺮﻣﺎﯾﺶ ﺟﺬﺑﯽ‬

‫ﺍﻣﺘﯿﺎﺯ ﺑﺰﺭﮒ ﻧﺴــﺒﺖ ﺑﻪ ﺳــﺎﯾﺮ ﭼﯿﻠﺮﻫﺎ‬

‫ﺍﺷــﺒﺎﻉ ﺑﺮﺳــﺪ ﻭ ﻣﯽﺩﺍﻧﯿﻢ ﮐﻪ ﺍﺳﺘﻔﺎﺩﻩ‬ ‫ﺩﻣﺎﯼ ﺍﺷــﺒﺎﻉ ﻭ ﺩﻣﺎﯾﯽ ﮐــﻪ ﺩﺭ ﺁﻥ ﺑﺨﺎﺭ‬ ‫ﺗﻘﻄﯿﺮ ﺷﻮﺩ‪ ،‬ﻣﯿﺴﺮ ﻧﺨﻮﺍﻫﺪ ﺑﻮﺩ‪ .‬ﭼﻨﯿﻦ‬

‫ﺟﺪﻭﻝ ﺯﯾﺮ ﺧﻼﺻﻪﺍﯼ ﺍﺯ ﻣﺸﺨﺼﺎﺕ ﺳﯿﺎﻝﻫﺎﯼ ﮔﺮﻡﮐﻨﻨﺪﻩ ﺳﻪ ﻧﻮﻉ ﺳﯿﺴﺘﻢ ﺟﺬﺑﯽ ﻟﯿﺘﯿﻤﯽ‬ ‫ﯾﮏﺍﺛﺮﻩ‪ ،‬ﺩﻭ ﺍﺛﺮﻩ ﻭ ﺁﻣﻮﻧﯿﺎﮐﯽ ﺩﻣﺎﯼ ﮐﻢ ﺭﺍ ﻧﻤﺎﯾﺶ ﻣﯽﺩﻫﺪ‪.‬‬

‫ﺣﺎﻟﺘﯽ‪ ،‬ﺍﺧﺘﻼﻻﺗﯽ ﺭﺍ ﺩﺭ ﻣﺴﯿﺮ ﭼﮕﺎﻟﯿﺪﻩ‬ ‫)ﺁﺏ ﺣﺎﺻﻞ ﺍﺯ ﺗﻘﻄﯿﺮ ﺑﺨﺎﺭ( ﻧﯿﺰ ﺑﻪ ﻭﺟﻮﺩ‬ ‫ﻣﯽﺁﻭﺭﺩ‪ .‬ﭼﻨﺎﻧﭽﻪ ﺑﻪ ﻫﺮ ﺩﻟﯿﻠﯽ ﻧﺎﮔﺰﯾﺮ ﺑﻪ‬ ‫ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﻓﺸﺎﺭﺷــﮑﻦ ﺑﻮﺩﯾﻢ‪ ،‬ﻣﯽﺑﺎﯾﺪ‬ ‫ﺩﺭ ﻣﺴــﯿﺮ ﺑﺨﺎﺭ ﭼﯿﻠﺮ ﺍﺯ ﻓــﻮﻕ ﮔﺮﻡﺯﺩﺍ‬

‫‪2‬‬

‫ﺳﯿﺴﺘﻢ ﻟﯿﺘﯿﻤﯽ‬ ‫ﺗﮏﺍﺛﺮﻩ‬ ‫ﻓﺸﺎﺭ ﺑﺨﺎﺭ ﻭﺭﻭﺩﯼ‪psig ،‬‬ ‫)‪(kPa‬‬ ‫ﺩﻣﺎﯼ ﺑﺨﺎﺭ ﻭﺭﻭﺩﯼ‪°F ،‬‬

‫ﺍﺳــﺘﻔﺎﺩﻩ ﮐﻨﯿﻢ ﺗﺎ ﺩﻣﺎﯼ ﺑﺨــﺎﺭ ﺗﻌﺪﯾﻞ‬ ‫ﺷــﻮﺩ‪ .‬ﺍﮔﺮ ﭼﻪ ﺍﯾﻦ ﺭﻭﺵ ﻣﻤﮑﻦ ﺍﺳﺖ‬

‫)‪(°C‬‬ ‫ﺩﻣﺎﯼ ﺁﺏ ﺩﺍﻍ‪°F ،‬‬ ‫)‪(°C‬‬

‫ﻫﺰﯾﻨﻪﻫــﺎﯼ ﺯﯾﺎﺩﯼ ﺭﺍ ﺑــﻪ ﭘﺮﻭﮊﻩ ﺗﺤﻤﯿﻞ‬ ‫ﮐﻨــﺪ‪ .‬ﺍﺯ ﻃﺮﻑ ﺩﯾﮕﺮ ﺑﺨــﺎﺭ ﻣﺮﻃﻮﺏ ﻧﯿﺰ‬ ‫ﮐﻪ ﺣﺎﻭﯼ ﻣﻘﺪﺍﺭﯼ ﺁﺏ ﺍﺳــﺖ‪ ،‬ﺁﻧﺘﺎﻟﭙﯽ‬ ‫ﮐﻤﺘﺮﯼ ﺍﺯ ﺑﺨﺎﺭ ﺧﺸــﮏ ﺩﺍﺭﺩ‪ ،‬ﺍﺯ ﺍﯾﻦ ﺭﻭ‬

‫ﺍﺳﺘﻘﺒﺎﻝ ﻗﺮﺍﺭ ﮔﺮﻓﺘﻪﺍﻧﺪ‪.‬‬

‫‪5-15‬‬

‫‪65-145‬‬

‫‪0-200‬‬

‫)‪(135-205‬‬

‫)‪(110-120‬‬

‫)‪(100-1480‬‬

‫‪225-250‬‬

‫‪305-365‬‬

‫‪210-385‬‬

‫)‪(110-120‬‬

‫)‪(175-185‬‬

‫)‪(100-195‬‬

‫‪240-300‬‬

‫‪310-400‬‬

‫‪210-385‬‬

‫)‪(115-150‬‬

‫)‪(155-205‬‬

‫)‪(100-195‬‬

‫‪40-100‬‬

‫‪40-80‬‬

‫‪-60 to 40‬‬

‫)‪(4-38‬‬

‫)‪(4-27‬‬

‫)‪(-51 to 4‬‬

‫‪0.6-0.7‬‬

‫‪0.9-1.2‬‬

‫‪0.1-0.8‬‬

‫ﺩﻣﺎﯼ ﺁﺏ ﺳﺮﺩ ﺧﺮﻭﺟﯽ‪°F ،‬‬ ‫)‪(°C‬‬ ‫ﺿﺮﯾﺐ ﮐﺎﺭﺍﯾﯽ‬

‫ﺳﯿﺴﺘﻢ ﻟﯿﺘﯿﻤﯽ ﺳﯿﺴﺘﻢ ﺁﻣﻮﻧﯿﺎﮐﯽ‬ ‫ﺩﻣﺎﯼ ﭘﺎﯾﯿﻦ‬ ‫ﺩﻭﺍﺛﺮﻩ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺻﻔﺤﻪ ‪ / 11‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﮔﺮﻣﺎﯾﯽ ﺟﺪﺍﮔﺎﻧﻪ ﻧﺪﺍﺷــﺘﻪ ﻭ ﺍﺯ ﺍﯾﻦ ﻧﻈﺮ‬

‫ﻣﻘــﺮﻭﻥ ﺑﻪ ﺻﺮﻓﻪ ﻭ ﻣﻨﻄﻘﯽ ﻧﯿﺴــﺖ‪ .‬ﺍﺯ‬

‫ﻭﺟﻮﺩ ﻧــﺪﺍﺭﺩ ﻭ ﺑﻪ ﺗﺒﻊ ﺁﻥ ﺍﻣﮑﺎﻥ ﺗﺎﻣﯿﻦ‬

‫ﺧﻮﺩﮐﻔﺎ ﻫﺴــﺘﻨﺪ ﻭ ﺩﻭﻡ ﺍﯾﻨﮑﻪ ﺑﻪ ﺩﻟﯿﻞ‬

‫ﺍﯾﻦﺭﻭ ﻣﺰﯾﺖ ﺩﻭ ﻓﺼﻠــﯽ ﺑﻮﺩﻥ ﺍﯾﻦﮔﻮﻧﻪ‬

‫ﮔﺮﻣﺎﯾﺶ ﺍﺯ ﻃﺮﯾــﻖ ﺍﯾﻦﮔﻮﻧﻪ ﭼﯿﻠﺮﻫﺎ ﻧﯿﺰ‬

‫ﺩﺭ ﺍﺧﺘﯿﺎﺭ ﺩﺍﺷــﺘﻦ ﺳﯿﺴــﺘﻢ ﺍﺣﺘﺮﺍﻕ‪،‬‬

‫ﭼﯿﻠﺮﻫﺎ ﻣﺤﺪﻭﺩ ﻭ ﺗﻨﻬﺎ ﺩﺭ ﺻﻮﺭﺕ ﻭﺟﻮﺩ‬

‫ﻭﺟﻮﺩ ﻧﺨﻮﺍﻫﺪ ﺩﺍﺷﺖ‪.‬‬

‫ﺍﻣﮑﺎﻥ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﺁﻥﻫﺎ ﺩﺭ ﻫﺮ ﺩﻭ ﻓﺼﻞ‬

‫ﺷﺮﺍﯾﻂ ﻣﻨﺎﺳﺐ ﻣﻘﺮﻭﻥ ﺑﻪ ﺻﺮﻓﻪ ﺍﺳﺖ‪.‬‬

‫ﺩﯾﺪﮔﺎﻫــﯽ ﻭﺟﻮﺩ ﺩﺍﺭﺩ ﮐﻪ ﻣﻌﺘﻘﺪ ﺑﻪ‬

‫ﺗﺎﺑﺴﺘﺎﻥ ﻭ ﺯﻣﺴﺘﺎﻥ ﺑﻪ ﻣﻨﻈﻮﺭ ﺳﺮﻣﺎﯾﺶ‬

‫ﺍﺯ ﺩﯾﺪﮔﺎﻫﯽ ﺩﯾﮕﺮ ﺑﺎ ﺗﻮﺟﻪ ﺑﻪ ﻗﯿﻤﺖ‬

‫ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺷﻌﻠﻪﻣﺴﺘﻘﯿﻢ‬

‫ﻭ ﮔﺮﻣﺎﯾﺶ ﻭﺟﻮﺩ ﺩﺍﺭﺩ‪ .‬ﺩﻭ ﻓﺼﻠﯽ ﺑﻮﺩﻥ‬

‫ﺍﺭﺯﺍﻥ ﺳﻮﺧﺖ ﻭ ﺗﺠﻬﯿﺰﺍﺕ ﻣﻮﻟﺪ ﺁﺏﮔﺮﻡ‬

‫ﺑــﻪ ﻫﻤﺮﺍﻩ ﺩﯾﮓﻫــﺎﯼ ﺑﺨﺎﺭ ﯾــﺎ ﺁﺏﮔﺮﻡ‬

‫ﺍﯾﻦﮔﻮﻧــﻪ ﭼﯿﻠﺮﻫﺎ ﺗﺎﺛﯿﺮ ﭼﺸــﻢﮔﯿﺮﯼ ﺩﺭ‬

‫ﻭ ﺑﺨــﺎﺭ ﻣﺎﻧﻨﺪ ﺍﻧﻮﺍﻉ ﺩﯾﮓﻫﺎ ﻭ ﻫﻤﭽﻨﯿﻦ‬

‫ﺍﺳــﺖ‪ .‬ﺑﺮ ﺍﺳــﺎﺱ ﺍﯾﻦ ﻧﻈﺮ‪ ،‬ﭼﯿﻠﺮﻫﺎﯼ‬

‫ﮐﺎﻫﺶ ﺳــﻄﺢ ﻣﻮﺗﻮﺭﺧﺎﻧــﻪ ﻭ ﻫﻤﭽﻨﯿﻦ‬

‫ﮔﺮﺍﻧﯽ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ‬

‫ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ ﺗﻨﻬﺎ ﺩﺭ ﻓﺼﻞ ﺗﺎﺑﺴــﺘﺎﻥ‬

‫ﮐﺎﻫﺶ ﻣﻘﺪﺍﺭ ﻟﻮﻟﻪﮐﺸــﯽﻫﺎﯼ ﺩﻭ ﻓﺼﻠﯽ‬

‫ﻭ ﺍﺳــﺘﻬﻼﮎ ﻧﺴــﺒﺘﺎ ﺯﯾﺎﺩ ﻭ ﻫﺰﯾﻨﻪﻫﺎﯼ‬

‫ﻣــﻮﺭﺩ ﺑﻬﺮﻩﺑــﺮﺩﺍﺭﯼ ﻗــﺮﺍﺭ ﻣﯽﮔﯿﺮﻧﺪ ﻭ‬

‫ﺑﯿﻦ ﺩﯾﮓ ﻭ ﭼﯿﻠﺮ ﻭ ﮐﻠﮑﺘﻮﺭﻫﺎﯼ ﻣﺸﺘﺮﮎ‬

‫ﻧﮕﻬــﺪﺍﺭﯼ ﻭ ﺭﺍﻫﺒﺮﯼ ﺁﻥﻫﺎ‪ ،‬ﺍﺳــﺘﻔﺎﺩﻩ‬

‫ﺩﺭ ﻭﺍﻗــﻊ ﺟــﻮﺭ ﺗﺎﻣﯿــﻦ ﺳــﺮﻣﺎ ﺭﺍ ﺧﻮﺩ‬

‫ﺩﺍﺭﺩ ﺍﻣــﺎ ﺑﺎ ﺗﻮﺟﻪ ﺑﻪ ﻣﺤــﺪﻭﺩﻩ ﺣﺪﺍﮐﺜﺮ‬

‫ﺍﺯ ﭼﻨﯿــﻦ ﺳﯿﺴــﺘﻤﯽ ﺗﻨﻬــﺎ ﺑــﻪ ﺩﻟﯿﻞ‬

‫ﮐﺸــﯿﺪﻩ ﻭ ﮔﺮﻣﺎﯼ ﻻﺯﻡ ﺭﺍ ﺑﺪﻭﻥ ﺍﺭﺗﺒﺎﻁ‬

‫ﺩﻣــﺎﯼ ﺁﺏﮔﺮﻡ ﺧﺮﻭﺟﯽ ﺍﺯ ﺁﻥﻫﺎ ﮐﻪ ﺑﯿﻦ‬

‫ﺩﻭ ﻓﺼﻠــﯽ ﺑــﻮﺩﻥ ﭼﻨــﺪﺍﻥ ﺍﻗﺘﺼﺎﺩﯼ‬

‫ﺑﺎ ﺩﯾﮓﻫﺎ‪ ،‬ﺧﻮﺩ ﺗﺎﻣﯿــﻦ ﻣﯽﮐﻨﻨﺪ ﻭ ﺩﺭ‬

‫‪ 55‬ﺗــﺎ ‪ 60‬ﺩﺭﺟﻪ ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ )‪ 131‬ﺗﺎ‬

‫ﻧﯿﺴﺖ‪ .‬ﺧﻮﺷﺒﺨﺘﺎﻧﻪ ﺩﺭ ﺳﺎﻝﻫﺎﯼ ﺍﺧﯿﺮ‬

‫ﻓﺼﻞ ﺗﺎﺑﺴــﺘﺎﻥ ﻧﯿــﺰ ﻣﺎﻧﻨــﺪ ﭼﯿﻠﺮﻫﺎﯼ‬

‫‪ 140‬ﺩﺭﺟﻪ ﻓﺎﺭﻧﻬﺎﯾﺖ( ﺍﺳﺖ‪ ،‬ﻻﺯﻡ ﻣﯽﺁﯾﺪ‬

‫ﺗﻮﻟﯿﺪﮐﻨﻨــﺪﮔﺎﻥ ﺩﺍﺧﻠﯽ ﮐﻤــﺮ ﻫﻤﺖ ﺑﻪ‬

‫ﺩﯾﮕــﺮ ﺍﺯ ﻣﺪﺍﺭ ﺍﺳــﺘﻔﺎﺩﻩ ﺧﺎﺭﺝ ﺷــﺪﻩ ﻭ‬

‫ﮐﻪ ﺑــﺮﺍﯼ ﺗﺎﻣﯿﻦ ﮔﺮﻣﺎﯾــﺶ ﮐﺎﻓﯽ ﺑﺮﺍﯼ‬

‫ﻣﯿﺎﻥ ﺑﺴــﺘﻪ ﻭ ﺍﻧــﻮﺍﻉ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ‬

‫ﺑﻪ ﺧﻮﺍﺏ ﺯﻣﺴــﺘﺎﻧﯽ ﻣﯽﺭﻭﻧــﺪ‪ .‬ﺑﻪ ﺍﯾﻦ‬

‫ﻓﻀﺎﻫﺎ‪ ،‬ﺳــﻄﺢ ﮐﻮﯾﻞ ﺗﺠﻬﯿﺰﺍﺕ ﺗﺒﺎﺩﻝ‬

‫ﺭﺍ ﺗﻮﻟﯿــﺪ ﻣﯽﮐﻨﻨﺪ ﺍﻣﺎ ﻫﻨﻮﺯ ﺍﯾﻦ ﺻﻨﻌﺖ‬

‫ﻃﺮﯾﻖ ﻟﻮﻟﻪﮐﺸــﯽﻫﺎ ﻭ ﺗﺠﻬﯿﺰﺍﺕ ﺍﻧﺘﻘﺎﻝ‬

‫ﺣﺮﺍﺭﺕ ﻣﺎﻧﻨﺪ ﻫﻮﺍﺳﺎﺯﻫﺎ ﻭ ﻓﻦﮐﻮﯾﻞﻫﺎ ﺭﺍ‬

‫ﻭﺍﺑﺴــﺘﮕﯽﻫﺎﯾﯽ ﺑﻪ ﮐﺸــﻮﺭﻫﺎﯼ ﺻﺎﺣﺐ‬

‫ﻭ ﺗﻮﺯﯾﻊ ﺳــﯿﺎﻝ ﮔﺮﻡ ﺍﻋــﻢ ﺍﺯ ﺑﺨﺎﺭ‪ ،‬ﺁﺏ‬

‫ﺑﯿﺸﺘﺮ ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺖ‪ .‬ﺑﻪﮐﺎﺭﮔﯿﺮﯼ ﭼﻨﯿﻦ‬

‫ﻓﻨــﺎﻭﺭﯼ ﺩﺍﺭﺩ‪ .‬ﺍﮔــﺮ ﺍﺯ ﻧﻈــﺮ ﻗﻄﻌﺎﺕ ﻭ‬

‫ﺩﺍﻍ ﯾــﺎ ﺁﺏ ﮔــﺮﻡ ﺣﺬﻑ ﺷــﺪﻩ ﻭ ﺑﺎ ﻓﺪﺍ‬

‫ﺗﺮﻓﻨــﺪﯼ ﺑــﺮﺍﯼ ﻣﻨﺎﺳﺐﺳــﺎﺯﯼ ﮔﺮﻣﺎ‪،‬‬

‫ﻣﺼﺎﻟﺢ‪ ،‬ﺗﻮﻟﯿﺪ ﺩﺍﺧﻠﯽ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ‬

‫ﻧﻤــﻮﺩﻥ ﺍﻣﺘﯿﺎﺯ ﺩﻭ ﻓﺼﻠﯽ ﺑــﻮﺩﻥ‪ ،‬ﺗﻨﻬﺎ‬

‫ﺿﻤﻦ ﺍﻓﺰﺍﯾﺶ ﺳــﻄﺢ ﺍﺷﻐﺎﻝ ﺗﺠﻬﯿﺰﺍﺕ‬

‫ﺭﺍ ﻧﺴﺒﺖ ﺑﻪ ﭼﯿﻠﺮﻫﺎﯼ ﺗﺮﺍﮐﻤﯽ ﺑﻪ ﻟﺤﺎﻅ‬

‫ﺑــﻪ ﺍﻣﺘﯿــﺎﺯ ﯾﮑﭙﺎﺭﭼــﻪ ﻭ ﺧﻮﺩﮐﻔﺎ ﺑﻮﺩﻥ‬

‫ﺗــﻮﺍﻡ ﺑﺎ ﺍﻓﺰﺍﯾــﺶ ﻫﺰﯾﻨﻪﻫــﺎﯼ ﺍﻭﻟﯿﻪ ﻧﯿﺰ‬

‫ﺭﺳﯿﺪﻥ ﺑﻪ ﺧﻮﺩﮐﻔﺎﯾﯽ ﺻﻨﻌﺖ ﺳﺮﻣﺎﯾﺶ‬

‫ﺍﮐﺘﻔﺎ ﻣﯽﺷــﻮﺩ‪ .‬ﻣﻤﮑﻦ ﺍﺳﺖ ﺩﺭ ﭘﺎﺭﻩﺍﯼ‬

‫ﻫﺴﺖ‪.‬‬

‫ﻭ ﺗﻬﻮﯾﻪ ﻣﻄﺒﻮﻉ ﮔﺎﻣــﯽ ﺑﻪ ﺟﻠﻮ ﺑﺪﺍﻧﯿﻢ‪،‬‬

‫ﻣﻮﺍﺭﺩ ﻭ ﺑﺮﺧــﯽ ﭘﺮﻭﮊﻩﻫﺎﯼ ﺧﺎﺹ ﭼﻨﯿﻦ‬

‫ﭼﯿﻠﺮﻫــﺎﯼ‬

‫ﻧﻤﯽﺗﻮﺍﻧﯿﻢ ﭼﻨﯿﻦ ﻧﺴــﺒﺘﯽ ﺭﺍ ﺑﯿﻦ ﺗﻮﻟﯿﺪ‬

‫ﺩﯾﺪﮔﺎﻫﯽ ﺻﺤﯿﺢ ﻭ ﻣﻨﺎﺳــﺐ ﺑﺎﺷﺪ ﺍﻣﺎ‬

‫ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ ﺑــﻪ ﻣﺮﺍﺗــﺐ ﮐﻤﺘــﺮ ﺍﺯ‬

‫ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ ﺷﻌﻠﻪﻣﺴﺘﻘﯿﻢ ﻭ ﺗﻮﻟﯿﺪ‬

‫ﺑﻪ ﺩﻟﯿﻞ ﺑﺮﻭﺯ ﭘﺎﺭﻩﺍﯼ ﻣﺸﮑﻼﺕ ﻭ ﻣﻌﺎﯾﺐ‬

‫ﻇﺮﻓﯿﺖ ﺳــﺮﻣﺎﯾﯽ ﺁﻥﻫﺎﺳــﺖ‪ ،‬ﺑﻨﺎﺑﺮﺍﯾﻦ‬

‫ﺍﻧﻮﺍﻉ ﺩﯾﮓﻫــﺎﯼ ﻓﻮﻻﺩﯼ ﻭ ﭼﺪﻧﯽ ﻗﺎﺋﻞ‬

‫ﺩﯾﮕﺮ ﺑــﻪ ﻫﯿﭻﻭﺟــﻪ ﻧﻤﯽﺗــﻮﺍﻥ ﭼﻨﯿﻦ‬

‫ﺍﺯ ﺍﯾــﻦ ﻧﻈﺮ ﻣﻨﺎﺳــﺐ ﻣﻨﺎﻃــﻖ ﻣﻌﺘﺪﻝ‬

‫ﺷﻮﯾﻢ‪ .‬ﺑﻨﺎﺑﺮﺍﯾﻦ ﺍﺯ ﺩﯾﺪﮔﺎﻩ ﮐﻼﻥ ﺍﻗﺘﺼﺎﺩ‬

‫ﺩﯾﺪﮔﺎﻫﯽ ﺭﺍ ﺩﺭ ﺍﮐﺜــﺮ ﻣﻮﺍﺭﺩ ﻗﺎﺑﻞ ﻗﺒﻮﻝ‬

‫ﯾﺎ ﺳﺮﺩﺳــﯿﺮ ﻧﯿﺴــﺘﻨﺪ‪ ،‬ﺯﯾــﺮﺍ ﺩﺭ ﻓﺼﻞ‬

‫ﻣﻠﯽ‪ ،‬ﻫﻨﻮﺯ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﺩﯾﮓﻫﺎﯼ ﺟﺪﺍﮔﺎﻧﻪ‬

‫ﺩﺍﻧﺴــﺖ‪ .‬ﭼﻨﯿﻦ ﺗﺼﻤﯿﻤﯽ ﻣﻌﺎﯾﺐ ﺯﯾﺮ ﺭﺍ‬

‫ﺯﻣﺴﺘﺎﻥ ﻧﻤﯽﺗﻮﺍﻧﻨﺪ ﭘﺎﺳﺨﮕﻮﯼ ﻧﯿﺎﺯﻫﺎﯼ‬

‫ﺑﻪ ﻫﻤــﺮﺍﻩ ﭼﯿﻠﺮﻫــﺎﯼ ﺟﺬﺑــﯽ ﻣﻘﺮﻭﻥ‬

‫ﺩﺭ ﭘﯽ ﺧﻮﺍﻫﺪ ﺩﺍﺷﺖ‪:‬‬

‫ﮔﺮﻣﺎﯾﯽ ﺑﺎﺷﻨﺪ‪ ،‬ﺑﻪ ﺧﺼﻮﺹ ﺍﮔﺮ ﺑﻪ ﻫﻤﺮﺍﻩ‬

‫ﺑﻪ ﺻﺮﻓﻪﺗﺮ ﺍﺳﺖ‪ .‬ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﺩﯾﮓﻫﺎﯼ‬

‫‪ -‬ﺍﻓﺰﺍﯾﺶ ﺳــﻄﺢ ﺍﺷﻐﺎﻝ ﻣﻮﺗﻮﺭﺧﺎﻧﻪ‬

‫ﺍﺣﺘﯿﺎﺝﻫﺎﯼ ﮔﺮﻣﺎﯾﺸــﯽ ﺳﺎﺧﺘﻤﺎﻥ‪ ،‬ﻧﯿﺎﺯ‬

‫ﺟﺪﺍﮔﺎﻧﻪ ﻧﻪﺗﻨﻬﺎ ﻣﻘﺮﻭﻥ ﺑﻪ ﺻﺮﻓﻪﺗﺮ ﺑﻠﮑﻪ‬

‫ﺑﻪ ﺩﻟﯿﻞ ﻭﺟﻮﺩ ﺩﻭ ﺳﯿﺴــﺘﻢ ﮔﺮﻣﺎﯾﺸــﯽ‬

‫ﺑﻪ ﺁﺏ ﮔﺮﻡ ﻣﺼﺮﻓﯽ ﻫﻢ ﺯﯾﺎﺩ ﺑﺎﺷﺪ‪.‬‬

‫ﺩﺭ ﺑﺴﯿﺎﺭﯼ ﻣﻮﺍﺭﺩ ﺍﺟﺮﺍﯾﯽﺗﺮ ﻫﻢ ﻫﺴﺖ‪.‬‬

‫ﮐﻪ ﻣﯽﺗﻮﺍﻧﺪ ﺑﺎ ﮐﺎﻫﺶ ﺳــﻄﺢ ﺍﺷــﻐﺎﻝ‬

‫ﺑــﻪ ﻃــﻮﺭ ﻣﻌﻤــﻮﻝ ﭼﯿﻠﺮﻫــﺎﯼ‬

‫ﺑﻪ ﻭﯾﮋﻩ ﺩﺭ ﺳﺎﺧﺘﻤﺎﻥﻫﺎ ﻭ ﻣﻮﻗﻌﯿﺖﻫﺎﯾﯽ‬

‫ﺗﺠﻬﯿــﺰﺍﺕ ﺍﻧﺘﻘﺎﻝ ﻭ ﺗﻮﺯﯾﻊ ﺳــﯿﺎﻝ ﮔﺮﻡ‬

‫ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ ﺑــﺮ ﺍﺳــﺎﺱ ﻇﺮﻓﯿــﺖ‬

‫ﮐــﻪ ﺩﯾﮓﻫﺎ ﻓــﺎﺭﻍ ﺍﺯ ﺗﺎﻣﯿــﻦ ﮔﺮﻣﺎﯾﺶ‬

‫ﺑﺮﺍﺑــﺮﯼ ﻧﻤﻮﺩﻩ ﻭ ﻣﺰﯾــﺖ ﭘﯿﺶ ﮔﻔﺘﻪ ﺩﺭ‬

‫ﺳﺮﻣﺎﯾﺸــﯽ ﺍﻧﺘﺨﺎﺏ ﻣﯽﺷــﻮﻧﺪ ﺑﻨﺎﺑﺮﺍﯾﻦ‬

‫ﻣﯽﺑﺎﯾﺪ ﻧﯿﺎﺯﻫﺎﯼ ﮔﺮﻣﺎﯾﺸﯽ ﺩﯾﮕﺮﯼ ﻣﺎﻧﻨﺪ‬

‫ﺍﯾﻦ ﺧﺼﻮﺹ ﺭﺍ ﮐﻢﺭﻧﮓ ﺳﺎﺯﺩ‪.‬‬

‫ﺍﻧﺘﺨﺎﺏ ﻇﺮﻓﯿﺖ ﺑﯿﺸــﺘﺮ ﺑــﻪ ﻧﺤﻮﯼ ﮐﻪ‬

‫ﺗﺎﻣﯿﻦ ﺑﺨﺎﺭ ﺑﺮﺍﯼ ﺗﺠﻬﯿﺰﺍﺕ ﺭﺍ ﻧﯿﺰ ﺑﺮﺁﻭﺭﺩﻩ‬

‫ﺑﺘﻮﺍﻧﺪ ﻧﯿﺎﺯﻫﺎﯼ ﮔﺮﻣﺎﯾﺸــﯽ ﺭﺍ ﺩﺭ ﻣﻨﺎﻃﻖ‬

‫ﺳــﺎﺯﻧﺪ‪ .‬ﺩﺭ ﺑﺴــﯿﺎﺭﯼ ﺍﺯ ﺳﺎﺧﺘﻤﺎﻥﻫﺎﯼ‬

‫ﻇﺮﻓﯿــﺖ‬

‫ﮔﺮﻣﺎﯾــﯽ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﺩﻭﺩﮐﺶﻫﺎﯼ ﻣﺘﻌﺪﺩ ﻭ‬‫ﺍﺷﻐﺎﻝ ﻓﻀﺎ ﺑﺮﺍﯼ ﻋﺒﻮﺭ ﺩﺍﺩﻥ ﺁﻥﻫﺎ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺩﺍﺭﻧــﺪ‪ .‬ﺍﻭﻝ ﺍﯾﻨﮑــﻪ ﻧﯿــﺎﺯﯼ ﺑــﻪ ﻣﻮﻟﺪ‬

‫ﻣﻌﺘﺪﻝ ﯾﺎ ﺳﺮﺩﺳﯿﺮ ﺑﺮﺁﻭﺭﺩﻩ ﺳﺎﺯﺩ ﭼﻨﺪﺍﻥ‬

‫ﺑﻠﻨﺪ ﻭ ﻭﺳﯿﻊ ﺍﻣﮑﺎﻥ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﺁﺏ ﮔﺮﻡ‬

‫ﺻﻔﺤﻪ ‪ / 12‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫‪ -‬ﺍﯾﺠــﺎﺩ ﺍﺧﺘــﻼﻝ ﺩﺭ ﻣﺤــﻞ ﺍﺧﺬ‬

‫ﺑﺮ ﻫﻤﯿﻦ ﺍﺳــﺎﺱ ﺑﻪ ﺧﻮﺩﯼ ﺧﻮﺩ ﺷﺎﻣﻞ‬

‫ﺳﺮﻣﺎﯾﺸﯽ ﭼﯿﻠﺮﻫﺎﯼ ﺩﻭ ﺍﺛﺮﻩ ﺍﺳﺖ‪ .‬ﺗﺼﻮﯾﺮ‬

‫ﺍﻧﺸــﻌﺎﺏ ﻟﻮﻟــﻪ ﻣﻨﺒــﻊ ﺍﻧﺒﺴــﺎﻁ ﺩﺭ‬

‫ﺗﻤﺎﻣــﯽ ﻣﺰﺍﯾــﺎ ﻭ ﻣﻌﺎﯾــﺐ ﭼﯿﻠﺮﻫﺎﯼ ﺩﻭ‬

‫)‪ (2‬ﭼﺮﺧــﻪ ﺳﺮﻣﺎﯾﺸــﯽ ﻧﻮﻋــﯽ ﭼﯿﻠــﺮ‬

‫ﺳﯿﺴﺘﻢﻫﺎﯼ ﺩﻭﻟﻮﻟﻪﺍﯼ ﯾﺎ ﺍﻓﺰﺍﯾﺶ ﺗﻌﺪﺍﺩ‬

‫ﻣﺮﺣﻠــﻪﺍﯼ ﻣﯽﺷــﻮﻧﺪ ﻭ ﺩﺭ ﻋﯿــﻦ ﺣﺎﻝ‬

‫ﺷﻌﻠﻪﻣﺴﺘﻘﯿﻢ ﺭﺍ ﻧﻤﺎﯾﺶ ﻣﯽﺩﻫﺪ‪.‬‬

‫ﺁﻥﻫﺎ‬

‫ﻣﺎﻧﻨــﺪ ﺁﻥﻫﺎ ﺩﺍﺭﺍﯼ ﺳــﻪ ﮔﻮﻧــﻪ ﺟﺮﯾﺎﻥ‬

‫ ﺗﺎﻣﯿﻦ ﻫﻮﺍﯼ ﺍﺣﺘﺮﺍﻕ ﻭ ﺗﺎﺯﻩ ﺑﯿﺸﺘﺮ‬‫ﺩﺭ ﺣﺎﻟــﺖ ﮐﺎﺭﮐﺮﺩ ﻫﻤﺰﻣﺎﻥ ﺩﯾﮓ )ﺑﺮﺍﯼ‬ ‫ﺗﺎﻣﯿﻦ ﺁﺏ ﮔــﺮﻡ ﻣﺼﺮﻓﯽ( ﻭ ﭼﯿﻠﺮ )ﺑﺮﺍﯼ‬

‫ﺷﻌﻠﻪﻣﺴﺘﻘﯿﻢ ﺩﻭ ﺍﺛﺮﻩ ﺗﺎ ‪ 1.2‬ﻧﯿﺰ ﻣﯽﺭﺳﺪ‬

‫ﺗﺎﻣﯿﻦ ﺳﺮﻣﺎﯾﺶ(‬

‫ﮐﻪ ﺍﺯ ﺍﯾﻦ ﻧﻈﺮ ﺑﺮﺗﺮﯼ ﻗﺎﺑﻞﺗﻮﺟﻬﯽ ﻧﺴﺒﺖ‬

‫ﻣﺮﺑﻮﻁ ﺑﻪ ﻟﻮﻟﻪﮐﺸﯽ ﺳﻮﺧﺖ‬ ‫ ﺍﻓﺰﺍﯾﺶ ﻗﺎﺑﻞ ﺗﻮﺟﻪ ﺳﺮﻣﺎﯾﻪﮔﺬﺍﺭﯼ‬‫ﺍﻭﻟﯿﻪ ﻭ ﻫﺰﯾﻨﻪﻫﺎﯼ ﺭﺍﻫﺒﺮﯼ‬

‫ﺩﺭ ﺗﺼﻮﯾﺮ )‪ (2‬ﺍﺯ ﻧﻮﻉ ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ ﺩﻭ‬ ‫ﺍﺛــﺮﻩ ﺑﺎ ﺟﺮﯾﺎﻥ ﻣﻌﮑﻮﺱ ﻣﻮﺍﺯﯼ ﺍﺳــﺖ‪.‬‬ ‫ﻫﻤﺎﻥﮔﻮﻧﻪ ﮐﻪ ﻣﺸــﺎﻫﺪﻩ ﻣﯽﺷــﻮﺩ‪ ،‬ﺩﺭ‬ ‫ﺍﻭﺍﭘﺮﺍﺗﻮﺭ‪ ،‬ﺁﺏ ﺗﺤﺖ ﻓﺸــﺎﺭ ‪ 6.8‬ﻣﯿﻠﯽﻣﺘﺮ‬

‫ﺑﻪ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ ﯾﮏﺍﺛﺮﻩ ﺩﺍﺭﺩ‪.‬‬

‫ﺟﯿﻮﻩ ﻣﻄﻠﻖ ﺑﺎ ﮔﺮﻓﺘﻦ ﮔﺮﻣﺎ ﺍﺯ ﺁﺏ ﺩﺍﺧﻞ‬

‫ﺩﺭ ﭼﯿﻠﺮﻫﺎﯼ ﺷﻌﻠﻪﻣﺴﺘﻘﯿﻢ‪ ،‬ﮊﻧﺮﺍﺗﻮﺭ‬

‫ﮐﻮﯾﻞ ﺳﯿﺴــﺘﻢ ﺳﺮﻣﺎﯾﺸــﯽ ﺳﺎﺧﺘﻤﺎﻥ‬

‫ﺩﻣﺎﯼ ﺑﺎﻻ ﻣﺠﻬﺰ ﺑﻪ ﻣﺸــﻌﻞ ﻭ ﺳﯿﺴﺘﻢ‬

‫ﺗﺒﺨﯿﺮ ﺷــﺪﻩ ﻭ ﺟــﺬﺏ ﻟﯿﺘﯿــﻢ ﺑﺮﻭﻣﺎﯾﺪ‬

‫ﺳﻮﺧﺖﺭﺳــﺎﻧﯽ ﺍﺳــﺖ ﻭ ﮔﺮﻣﺎﯼ ﮊﻧﺮﺍﺗﻮﺭ‬

‫ﻣﻮﺟــﻮﺩ ﺩﺭ ﺍﺑﺰﻭﺭﺑــﺮ ﻣﯽﺷــﻮﺩ‪ .‬ﻣﺤﻠﻮﻝ‬

‫ﻣﻮﺍﺭﺩﯼ ﮐﻪ ﺗﺎﮐﻨﻮﻥ ﺑﻪ ﺁﻥﻫﺎ ﺍﺷــﺎﺭﻩ‬

‫ﺩﻣﺎﯼ ﭘﺎﯾﯿﻦ ﻫﻤﭽﻮﻥ ﭼﯿﻠﺮﻫﺎﯼ ﺩﻭ ﺍﺛﺮﻩ‬

‫ﺩﺍﺷــﺘﯿﻢ ﻣﻌﺎﯾﺒﯽ ﺑــﻮﺩ ﮐــﻪ ﭼﯿﻠﺮﻫﺎﯼ‬

‫ﺍﺯ ﻃﺮﯾﻖ ﺑﺨﺎﺭ ﺁﺏ ﺟﺪﺍ ﺷــﺪﻩ ﺍﺯ ﻣﺤﻠﻮﻝ‬

‫ﺭﻗﯿﻖ ‪ 58.5‬ﺩﺭﺻﺪ ﺗﻮﺳــﻂ ﭘﻤﭗ ﮊﻧﺮﺍﺗﻮﺭ‬

‫ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ ﺩﺭ ﺳﯿﺴــﺘﻢﻫﺎ ﻭ ﺩﺭ‬

‫ﺭﻗﯿﻖ ﺗﺎﻣﯿﻦ ﻣﯽﺷﻮﺩ‪.‬‬

‫ﺩﻣــﺎﯼ ﭘﺎﯾﯿــﻦ ﺍﺯ ﻣﺒﺪﻝ ﺩﻣــﺎﯼ ﭘﺎﯾﯿﻦ‬

‫ﻣﻘﺎﯾﺴــﻪ ﺑﺎ ﺳــﺎﯾﺮ ﺗﺠﻬﯿﺰﺍﺕ ﺩﺍﺭﻧﺪ‪ .‬ﺑﺎﯾﺪ‬ ‫ﺍﺷﺎﺭﻩ ﮐﻨﯿﻢ ﮐﻪ ﺍﯾﻦﮔﻮﻧﻪ ﭼﯿﻠﺮﻫﺎ ﻣﻌﺎﯾﺐ‬ ‫ﺫﺍﺗﯽ ﻭ ﻣﻄﻠﻘــﯽ ﺭﺍ ﻧﯿﺰ ﺑﻪ ﻫﻤﺮﺍﻩ ﺩﺍﺭﻧﺪ‪.‬‬ ‫ﺩﻣــﺎﯼ ﺑﺎﻻ ﺩﺭ ﺑﺨــﺶ ﮊﻧﺮﺍﺗﻮﺭ ﺍﺻﻠﯽ ﮐﻪ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﻣﺤﻠﻮﻝ ﻫﺴﺘﻨﺪ‪.‬‬ ‫ﺿﺮﯾــﺐ ﺑﻬــﺮﻩ ﭼﯿﻠﺮﻫــﺎﯼ ﺟﺬﺑﯽ‬

‫‪ -‬ﺍﻓﺰﺍﯾــﺶ ﻣﺼــﺮﻑ ﻭ ﻫﺰﯾﻨﻪﻫــﺎﯼ‬

‫ﭼﺮﺧﻪ ﺳﺮﻣﺎﯾﺸﯽ ﻧﻤﺎﯾﺶ ﺩﺍﺩﻩ ﺷﺪﻩ‬

‫ﺍﺣﺘﻤﺎﻝ ﺧﻮﺭﺩﮔﯽ ﻭ ﻓﺮﺳﺎﯾﺶ ﺭﺍ ﺍﻓﺰﺍﯾﺶ‬

‫ﭼﯿﻠﺮﻫــﺎﯼ ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ ﺑﺎ ﺗﻮﺟﻪ‬

‫ﮔﺬﺭ ﻧﻤــﻮﺩﻩ ﻭ ﻭﺍﺭﺩ ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﭘﺎﯾﯿﻦ‬

‫ﺑــﻪ ﺩﻭ ﻓﺼﻠــﯽ ﺑــﻮﺩﻥ ﺩﺍﺭﺍﯼ ﺩﻭ ﭼﺮﺧﻪ‬

‫ﻣﯽﺷــﻮﺩ‪ .‬ﻣﺤﻠﻮﻝ ﭘــﺲ ﺍﺯ ﺗﻐﻠﯿﻆ ﺍﻭﻟﯿﻪ‬

‫ﺳﺮﻣﺎﯾﺶ ﻭ ﮔﺮﻣﺎﯾﺶ ﻫﺴﺘﻨﺪ ﮐﻪ ﭼﺮﺧﻪ‬

‫ﺍﺯ ﮊﻧﺮﺍﺗﻮﺭ ﺧﺎﺭﺝ ﻭ ﺑﻪ ﺩﻭ ﺑﺨﺶ ﺗﻘﺴــﯿﻢ‬

‫ﺳﺮﻣﺎﯾﺸــﯽ ﺁﻥﻫﺎ ﺑﺴﯿﺎﺭ ﺷﺒﯿﻪ ﺑﻪ ﭼﺮﺧﻪ‬

‫ﻣﯽﺷــﻮﺩ‪ .‬ﺑﺨﺸــﯽ ﺍﺯ ﺁﻥ ﺑــﺎﺭ ﺩﯾﮕﺮ ﺑﻪ‬

‫ﻣﯽﺩﻫﺪ‪ ،‬ﺗﻨﺶﻫﺎﯼ ﺯﯾــﺎﺩﯼ ﺭﺍ ﺑﻪﻭﺟﻮﺩ‬ ‫ﺧﺮﻭﺝ ﺁﺏ ﺑﺮﺝ‬ ‫ﺧﻨﮏﮐﻦ‬

‫ﺁﻭﺭﺩﻩ ﻭ ﺍﺣﺘﻤــﺎﻝ ﻧﺸــﺘﯽ ﺑﯿﻦ ﺳــﻄﻮﺡ‬ ‫ﺧﺎﺭﺟﯽ ﻟﻮﻟﻪﻫــﺎ ﻭ ﺻﻔﺤﻪ ﻧﮕﻬﺪﺍﺭﻧﺪﻩ ﺭﺍ‬

‫‪195‬‬

‫ﺳﯿﺴﺘﻢ ﺗﺨﻠﯿﻪ ﻫﻮﺍ‬

‫‪300‬‬

‫ﮔﺮﻡ ﮐﻦ ﺁﺏ ﻣﺼﺮﻓﯽ‬

‫‪46.2 95‬‬ ‫‪mm‬‬ ‫‪Hg abs‬‬

‫ﺑﯿﺶ ﺍﺯ ﭘﯿﺶ ﻣﯽﮐﻨﺪ‪ .‬ﺑﻨﺎﺑﺮﺍﯾﻦ ﺍﺳﺘﻔﺎﺩﻩ‬

‫ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﭘﺎﯾﯿﻦ‬ ‫‪50 mm‬‬ ‫‪Hg abs‬‬

‫ﺍﺯ ﻣﺼﺎﻟــﺢ ﺧﺎﺹ ﻭ ﺩﻗﺖ ﺑﺴــﯿﺎﺭ ﺑﺎﻻ ﺑﻪ‬

‫‪3‬‬

‫ﺗﻨﻈﯿﻢ ﺩﻣﺎ ﺩﺭ ﺩﺳﺘﻮﺭ ﮐﺎﺭ ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﺩ‪.‬‬ ‫ﺑﺮﺁﻭﺭﺩﻩ ﻧﻤﻮﺩﻥ ﭼﻨﯿــﻦ ﻧﯿﺎﺯﻫﺎﯾﯽ ﻣﻨﺠﺮ‬ ‫ﺑﻪ ﺍﻓﺰﺍﯾﺶ ﻗﯿﻤﺖ ﺁﻥﻫﺎ ﻧﺴــﺒﺖ ﺑﻪ ﺳﺎﯾﺮ‬ ‫ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ ﻣﯽﺷﻮﺩ‪.‬‬ ‫ﻋﻠﯽﺭﻏــﻢ ﻣﻌﺎﯾﺒﯽ ﮐﻪ ﺑﺮﺷــﻤﺮﺩﯾﻢ‪،‬‬ ‫ﺍﯾﻦﮔﻮﻧــﻪ ﭼﯿﻠﺮﻫــﺎ ﺩﺭ ﻣﻨﺎﻃﻘــﯽ ﮐــﻪ‬ ‫ﺯﻣﺴﺘﺎﻥﻫﺎﯼ ﺳﺨﺘﯽ ﻧﺪﺍﺭﻧﺪ‪ ،‬ﻣﯽﺗﻮﺍﻧﻨﺪ‬ ‫ﺑﻬﺘﺮﯾﻦ ﺍﻧﺘﺨﺎﺏ ﺑﺎﺷﻨﺪ‪.‬‬ ‫ﺍﻣــﺮﻭﺯﻩ ﭼﯿﻠﺮﻫﺎﯼ ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ‬ ‫ﺑﻪﺻﻮﺭﺕ ﺩﻭ ﺍﺛﺮﻩ ﺳــﺎﺧﺘﻪ ﻣﯽﺷــﻮﻧﺪ ﻭ‬

‫‪180‬‬

‫ﮐﻨﺪﺍﻧﺴﻮﺭ‬

‫ﻫﻨﮕﺎﻡ ﺳﺎﺧﺖ ﻭ ﻫﻤﭽﻨﯿﻦ ﮐﻨﺘﺮﻝ ﺩﻗﯿﻖ‬ ‫ﮐﺎﺭﮐﺮﺩ ﻣﺸــﻌﻞ ﺍﺯ ﻧﻈﺮ ﺍﻧﺪﺍﺯﻩ ﺷــﻌﻠﻪ ﻭ‬

‫ﺁﺏ ﮔﺮﻡ‬ ‫ﻣﺼﺮﻓﯽ‬

‫‪60.2%‬‬

‫ﭘﻤﭗ ﮊﻧﺮﺍﺗﻮﺭ‬ ‫ﺩﻣﺎﯼ ﺑﺎﻻ‬

‫ﺍﻭﺍﭘﺮﺍﺗﻮﺭ‬ ‫‪44‬‬

‫‪66% 390mm Hg abs‬‬

‫‪150‬‬

‫‪6.8 mm Hg abs‬‬

‫‪54‬‬

‫ﺁﺏ ﺳﺮﺩ‬

‫‪63%‬‬

‫‪91‬‬

‫‪120‬‬ ‫‪4‬‬

‫ﻣﻨﺒﻊ ‪42‬‬

‫ﺟﻤﻊﺁﻭﺭﯼ‬ ‫ﻣﺒﺮﺩ‬

‫ﭘﻤﭗ ﻣﺒﺮﺩ‬

‫‪5 mm‬‬

‫‪2‬‬

‫ﮊﻧﺮﺍﺗﻮﺭ ﺷﻌﻠﻪ‬ ‫ﻣﺴﺘﻘﯿﻢ‬

‫‪8‬‬

‫‪5‬‬

‫‪ 58.5%‬ﺍﺑﺰﻭﺭﺑﺮ‪Hg abs‬‬ ‫‪85‬‬

‫‪305‬‬

‫ﻭﺭﻭﺩ‬ ‫ﺁﺏ ﺑﺮﺝ‬ ‫ﺧﻨﮏﮐﻦ‬

‫‪1‬‬ ‫‪95‬‬

‫ﭘﻤﭗ ﻣﺤﻠﻮﻝ‬ ‫‪260 6‬‬

‫ﺍﺩﺍﮐﺘﻮﺭ‬

‫ﭘﻤﭗ ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﭘﺎﯾﯿﻦ‬

‫ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﺩﻣﺎﯼ ﺑﺎﻻ‬ ‫ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﺩﻣﺎﯼ ﭘﺎﯾﯿﻦ‬

‫ﺗﺼﻮﯾﺮ )‪ (2‬ﭼﺮﺧﻪ ﺳﺮﻣﺎﯾﺶ ﺩﺭ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺷﻌﻠﻪ ﻣﺴﺘﻘﯿﻢ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺻﻔﺤﻪ ‪ / 13‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺳﯿﺴﺘﻢ ﺗﺨﻠﯿﻪ ﻫﻮﺍ ﻭ‬ ‫ﮔﺎﺯﻫﺎﯼ ﻏﯿﺮ ﻗﺎﺑﻞ ﺗﻘﻄﯿﺮ‬

‫ﻭ ﺳــﭙﺲ ﺑﻪ ﻫﻤﺮﺍﻩ ﺑﺨﺎﺭ ﺁﺏ ﺟﺪﺍ ﺷﺪﻩ‬

‫‪165‬‬

‫ﺩﺭ ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﭘﺎﯾﯿﻦ ﻭﺍﺭﺩ ﮐﻨﺪﺍﻧﺴــﻮﺭ‬

‫ﮔﺮﻡ ﮐﻦ ﺁﺏ ﻣﺼﺮﻓﯽ‬ ‫ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﭘﺎﯾﯿﻦ‬

‫ﮐﻨﺪﺍﻧﺴﻮﺭ‬

‫‪55%‬‬

‫‪3‬‬

‫ﻣﯽﺷﻮﺩ‪ .‬ﺑﺨﺎﺭ ﻣﺒﺮﺩ ﺩﺭ ﮐﻨﺪﺍﻧﺴﻮﺭ ﺗﻘﻄﯿﺮ‬

‫ﺁﺏ ﮔﺮﻡ‬ ‫ﻣﺼﺮﻓﯽ‬

‫ﺷــﺪﻩ ﻭ ﺑﻪ ﺍﻭﺍﭘﺮﺍﺗﻮﺭ ﺑﺮﻣﯽﮔﺮﺩﺩ‪ .‬ﺍﺯ ﺳﻮﯼ‬

‫ﭘﻤﭗ ﮊﻧﺮﺍﺗﻮﺭ‬ ‫ﺩﻣﺎﯼ ﺑﺎﻻ‬

‫ﺍﻭﺍﭘﺮﺍﺗﻮﺭ‬ ‫‪140‬‬

‫ﺩﯾﮕــﺮ ﻣﺤﻠﻮﻝ ﻏﻠﯿــﻆ ﺍﯾﺠﺎﺩ ﺷــﺪﻩ ﺩﺭ‬ ‫‪255‬‬

‫‪26060.5%‬‬

‫‪7‬‬

‫‪130‬‬

‫ﮊﻧﺮﺍﺗﻮﺭ ﺷﻌﻠﻪ‬ ‫ﻣﺴﺘﻘﯿﻢ‬

‫‪205‬‬

‫ﻣﻨﺒﻊ‬ ‫ﺟﻤﻊﺁﻭﺭﯼ‬ ‫ﻣﺒﺮﺩ‬ ‫ﭘﻤﭗ ﺍﻭﺍﭘﺮﺍﺗﻮﺭ‬

‫‪5‬‬

‫ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﺑــﺎﻻ ﭘﺲ ﺍﺯ ﮔﺬﺭ ﺍﺯ ﻣﺒﺪﻝ‬ ‫ﺣﺮﺍﺭﺗــﯽ ﺩﻣﺎﯼ ﺑﺎﻻ ﺑﺎ ﻣﺤﻠﻮﻝ ﻣﺘﻮﺳــﻂ‬ ‫ﺧﺮﻭﺟﯽ ﺍﺯ ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﭘﺎﯾﯿﻦ ﻣﺨﻠﻮﻁ‬ ‫ﺷــﺪﻩ ﻭ ﺑﺎ ﮔﺬﺭ ﺍﺯ ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﺩﻣﺎﯼ‬

‫ﺍﺑﺰﻭﺭﺑﺮ‪195‬‬

‫ﭘﺎﯾﯿﻦ ﺑﻪ ﺍﺑﺰﻭﺭﺑﺮ ﺑﺎﺯﻣﯽﮔﺮﺩﺩ ﻭ ﺑﻪ ﺍﯾﻦ ﺗﺮ‬

‫‪205‬‬ ‫‪6‬‬

‫ﭘﻤﭗ ﻣﺤﻠﻮﻝ‬

‫‪230‬‬

‫ﺍﺩﺍﮐﺘﻮﺭ‬

‫ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﺩﻣﺎﯼ ﺑﺎﻻ‬ ‫ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﺩﻣﺎﯼ ﭘﺎﯾﯿﻦ‬

‫ﭘﻤﭗ ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﭘﺎﯾﯿﻦ‬

‫ﺗﯿﺐ ﭼﺮﺧﻪ ﺳــﺮﻣﺎﯾﺶ ﮐﺎﻣﻞ ﻣﯽﺷﻮﺩ‪.‬‬ ‫ﺍﯾﻦ ﭼﺮﺧﻪ ﺩﻗﯿﻘﺎ ﻣﺸﺎﺑﻪ ﭼﺮﺧﻪﺍﯼ ﺍﺳﺖ‬ ‫ﮐــﻪ ﻗﺒﻼ ﺩﺭ ﻣﻮﺭﺩ ﭼﯿﻠــﺮ ﺟﺬﺑﯽ ﺩﻭ ﺍﺛﺮﻩ‬ ‫ﺷﺮﺡ ﺩﺍﺩﻩ ﺷﺪ‪.‬‬

‫ﺗﺼﻮﯾﺮ )‪ (3‬ﭼﺮﺧﻪ ﮔﺮﻣﺎﯾﺶ ﺩﺭ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺷﻌﻠﻪ ﻣﺴﺘﻘﯿﻢ‪.‬‬

‫ﺗﺼﻮﯾــﺮ )‪ (3‬ﭼﺮﺧــﻪ ﭼﯿﻠــﺮ ﺟﺬﺑﯽ‬ ‫ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ ﺭﺍ ﺩﺭ ﺣﺎﻟــﺖ ﮔﺮﻣﺎﯾﺶ‬ ‫ﮐﻨﺪﺍﻧﺴﻮﺭ‬

‫ﻧﺸــﺎﻥ ﻣﯽﺩﻫﺪ‪ .‬ﺩﺭ ﭼﺮﺧــﻪ ﮔﺮﻣﺎﯾﺶ‪،‬‬ ‫ﺗﺒﺨﯿﺮﯼ ﺩﺭ ﺍﻭﺍﭘﺮﺍﺗــﻮﺭ ﺻﻮﺭﺕ ﻧﻤﯽﮔﯿﺮﺩ‬

‫ﮊﻧﺮﺍﺗﻮﺭ ﻣﺮﺣﻠﻪ‬ ‫ﺩﻭﻡ )ﺩﻣﺎﯼ‬ ‫ﮐﻢ(‬

‫ﺍﻭﺍﭘﺮﺍﺗﻮﺭ‬ ‫ﺮ‬ ‫ﺍﺑﺰﻭﺭﺑﺮ‬

‫ﮊﻧﺮﺍﺗﻮﺭ‬ ‫ﻣﺮﺣﻠﻪ ﺍﻭﻝ‬ ‫)ﺩﻣﺎﯼ ﺯﯾﺎﺩ(‬

‫ﺩﻣــﺎﯼ ﭘﺎﯾﯿﻦ ﻭ ﺑــﺎﻻ ﺩﺭ ﺍﺧﺘﯿﺎﺭ ﻣﺤﻔﻈﻪ‬ ‫ﺍﻭﺍﭘﺮﺍﺗﻮﺭ ‪ -‬ﺍﺑﺰﻭﺭﺑﺮ ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﺩ ﺗﺎ ﮔﺮﻣﺎﯼ‬ ‫ﺧﻮﺩ ﺭﺍ ﺑــﻪ ﺁﺏ ﺟــﺎﺭﯼ ﺩﺭ ﮐﻮﯾﻞ ﺩﻫﺪ‪.‬‬ ‫ﺑﻨﺎﺑﺮﺍﯾﻦ ﺩﺭ ﺍﯾﻦ ﭼﺮﺧﻪ ﮐﻨﺪﺍﻧﺴﻮﺭ ﻭ ﺧﻂ‬

‫ﻭﺭﻭﺩ ﺁﺏ‬ ‫ﮔﺮﻡ‬

‫ﺗﺨﻠﯿﻪ‬ ‫ﺩﻭﺩ‬

‫ﺁﺏ ﺳﺮﺩ ﺑﺮﺝ ﺧﻨﮏﮐﻦ ﮐﺎﻣﻼ ﻏﯿﺮ ﻓﻌﺎﻝ‬ ‫ﺍﺳﺖ‪.‬‬ ‫ﺩﺭ ﺑﺮﺧﯽ ﻣﺪﻝﻫﺎ ﺑﺨﺎﺭ ﺍﯾﺠﺎﺩ ﺷــﺪﻩ‬

‫ﭘﻤﭗ ﻣﺤﻠﻮﻝ‬

‫ﭘﻤﭗ‬ ‫ﻣﺒﺮﺩ‬

‫ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﻣﺤﻠﻮﻝ‬

‫ﺩﺭ ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﺑﺎﻻ ﺑﻪ ﻃﻮﺭ ﻣﺴﺘﻘﯿﻢ ﻭ‬ ‫ﺍﺯ ﻣﻌﺒﺮ ﮐﻨﺎﺭﮔﺬﺭﯼ ﻭﺍﺭﺩ ﻣﺤﻔﻈﻪ ﺍﻭﺍﭘﺮﺍﺗﻮﺭ‬ ‫‪ -‬ﺍﺑﺰﻭﺭﺑﺮ ﺷــﺪﻩ ﻭ ﭘﺲ ﺍﺯ ﮔﺮﻡ ﮐﺮﺩﻥ ﺁﺏ‬

‫ﺗﺼﻮﯾﺮ )‪ (4‬ﭼﺮﺧﻪ ﮔﺮﻣﺎﯾﺸﯽ ﺩﺭ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺷﻌﻠﻪ ﻣﺴﺘﻘﯿﻢ ﺑﺎ ﺷﯿﺮ ﺟﺪﺍﮐﻨﻨﺪﻩ ﻭ ﻣﺴﯿﺮ‬ ‫ﮐﻨﺎﺭﮔﺬﺭ‬

‫ﺩﺍﺧﻞ ﮐﻮﯾﻞ ﺍﻭﺍﭘﺮﺍﺗﻮﺭ ﺗﺒﺪﯾﻞ ﺑﻪ ﻣﺎﯾﻊ ﺷﺪﻩ‬ ‫ﻭ ﺑﻪ ﻫﻤﺮﺍﻩ ﻣﺤﻠﻮﻝ ﺍﺑﺰﻭﺭﺑﺮ ﺑﺎﺭ ﺩﯾﮕﺮ ﻭﺍﺭﺩ‬ ‫ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﺑﺎﻻ ﻣﯽﺷــﻮﺩ‪ .‬ﺩﺭ ﺍﯾﻦﮔﻮﻧﻪ‬

‫ﺍﺑﺰﻭﺭﺑﺮ ﺑﺎﺯﮔﺸــﺘﻪ ﻭ ﻗﺴﻤﺘﯽ ﺩﯾﮕﺮ ﭘﺲ ﺍﺯ‬

‫ﺷﻌﻠﻪﻣﺴﺘﻘﯿﻢ‪ ،‬ﺁﺏ ﺑﯿﺸــﺘﺮﯼ ﺍﺯ ﺩﺳﺖ‬

‫ﮔــﺬﺭ ﺍﺯ ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﺩﻣــﺎﯼ ﺑﺎﻻ ﻭﺍﺭﺩ‬

‫ﻣﯽﺩﻫــﺪ ﻭ ﻏﻠﯿﻆﺗﺮ ﻣﯽﺷــﻮﺩ‪ .‬ﺑﺨﺎﺭ ﺁﺏ‬

‫ﮊﻧﺮﺍﺗــﻮﺭ ﺩﻣــﺎﯼ ﺑﺎﻻ ﻣﯽﺷــﻮﺩ‪ .‬ﻣﺤﻠﻮﻝ‬

‫ﺟﺪﺍﺷﺪﻩ ﺍﺯ ﻣﺤﻠﻮﻝ ﺍﺯ ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﺑﺎﻻ‬

‫ﺩﺍﺷــﺖ‪ .‬ﺩﺭ ﺍﯾﻦﮔﻮﻧﻪ ﻣﺪﻝﻫﺎ ﯾﮏ ﺷــﯿﺮ‬

‫ﻭﺭﻭﺩﯼ ﺑﻪ ﮊﻧﺮﺍﺗــﻮﺭ ﺩﻣﺎﯼ ﺑﺎﻻ ﮐﻪ ﺩﺍﺭﺍﯼ‬

‫ﺭﺍﻫــﯽ ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﭘﺎﯾﯿﻦ ﻣﯽﺷــﻮﺩ ﺗﺎ‬

‫ﮐﻪ ﺩﺭ ﭼﺮﺧﻪ ﺗﺎﺑﺴــﺘﺎﻧﯽ ﺑﺴﺘﻪ ﺍﺳﺖ ﺩﺭ‬

‫ﻏﻠﻈﺖ ﻣﺘﻮﺳــﻄﯽ ﺍﺳــﺖ ﺩﺭ ﻣﺠﺎﻭﺭﺕ‬

‫ﻣﻮﺟﺐ ﺗﻐﻠﯿﻆ ﻣﺤﻠﻮﻝ ﺭﻗﯿﻖ ﺍﻭﻟﯿﻪ ﺷﻮﺩ‬

‫ﺯﻣﺴﺘﺎﻥ ﺑﺎﺯ ﺷﺪﻩ ﻭ ﺍﺭﺗﺒﺎﻁ ﻣﺴﺘﻘﯿﻤﯽ ﺭﺍ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﻣﺪﻝﻫﺎ‪ ،‬ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣــﺎﯼ ﭘﺎﯾﯿﻦ ﻫﻢ ﻫﯿﭻ‬ ‫ﻧﻘﺸــﯽ ﺩﺭ ﻓﻌﻞﻭﺍﻧﻔﻌﺎﻝ ﭼﺮﺧﻪ ﻧﺨﻮﺍﻫﺪ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺧﺮﻭﺝ‬ ‫ﺁﺏ ﮔﺮﻡ‬

‫ﺑﻠﮑﻪ ﻣﺤﻠﻮﻝ ﮔﺮﻡ ﺷﺪﻩ ﺗﻮﺳﻂ ﺩﻭ ﮊﻧﺮﺍﺗﻮﺭ‬

‫ﺻﻔﺤﻪ ‪ / 14‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﮊﻧﺮﺍﺗﻮﺭ ﻣﺮﺣﻠﻪ ﺩﻭﻡ‬ ‫)ﺩﻣﺎﯼ ﮐﻢ(‬

‫ﺑﯿــﻦ ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﺑﺎﻻ ﻭ ﺍﻭﺍﭘﺮﺍﺗﻮﺭ ﺑﺮﻗﺮﺍﺭ‬

‫ﮐﻨﺪﺍﻧﺴﻮﺭ‬

‫ﻣﯽﮐﻨــﺪ‪ .‬ﺗﺼﻮﯾﺮ )‪ (4‬ﭼﻨﯿﻦ ﭼﺮﺧﻪﺍﯼ ﺭﺍ‬

‫ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ‬ ‫ﺁﺏ ﮔﺮﻡ ﻣﺼﺮﻓﯽ‬

‫ﻧﻤﺎﯾــﺶ ﻣﯽﺩﻫﺪ‪ .‬ﺩﺭ ﺍﯾﻦ ﭼﺮﺧﻪ ﺷــﯿﺮ‬ ‫‪ VD‬ﺑﻪ ﻫﻨﮕﺎﻡ ﮔﺮﻣﺎﯾﺶ ﺑﻪﺻﻮﺭﺕ ﺩﺳﺘﯽ‬

‫ﺁﺏ ﮔﺮﻡ‬ ‫ﻣﺼﺮﻓﯽ‬

‫ﺑﺎﺯ ﺷﺪﻩ ﻭ ﺍﺭﺗﺒﺎﻁ ﻣﺴﺘﻘﯿﻢ ﻭ ﮐﻨﺎﺭﮔﺬﺭ ﺭﺍ‬ ‫ﺍﻭﺍﭘﺮﺍﺗﻮﺭ‬

‫ﺑﺮﻗﺮﺍﺭ ﻣﯽﺳﺎﺯﺩ‪.‬‬ ‫ﮔﺮﻭﻫــﯽ ﺍﺯ ﭼﯿﻠﺮﻫــﺎﯼ ﺟﺬﺑــﯽ‬

‫ﮊﻧﺮﺍﺗﻮﺭ‬ ‫ﻝ‬ ‫ﻣﺮﺣﻠﻪ ﺍﻭﻝ‬ ‫)ﺩﻣﺎﯼ ﺯﯾﺎﺩ(‬

‫ﺍﺑﺰﻭﺭﺑﺮ‬

‫ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ ﺩﺍﺭﺍﯼ ﯾــﮏ ﻣﺒــﺪﻝ ﺁﺏ‬ ‫ﮔــﺮﻡ ﻣﺼﺮﻓﯽ ﻟﺤﻈﻪﺍﯼ ﻫﻢ ﻫﺴــﺘﻨﺪ ﮐﻪ‬ ‫ﺑــﻪ ﮐﻤﮏ ﺁﻥ ﻣﯽﺗــﻮﺍﻥ ﺁﺏ ﮔﺮﻡ ﻣﺼﺮﻓﯽ‬

‫ﺗﺨﻠﯿﻪ‬ ‫ﺩﻭﺩ‬

‫ﺭﺍ ﺩﺭ ﺣــﺪ ﻣﺤﺪﻭﺩ ﺗﺎﻣﯿﻦ ﻧﻤﻮﺩ‪ .‬ﺍﻣﺎ ﺗﻮﺍﻥ‬ ‫ﭘﻤﭗ ﻣﺒﺮﺩ‬ ‫ﭘﻤﭗ ﻣﺤﻠﻮﻝ‬

‫ﮔﺮﻣﺎﯾﺸﯽ ﺍﯾﻦ ﭼﯿﻠﺮﻫﺎ ﺍﺟﺎﺯﻩ ﻧﻤﯽﺩﻫﺪ ﮐﻪ‬ ‫ﺑﻪ ﻫﻨﮕﺎﻡ ﺗﺎﻣﯿﻦ ﺳــﺮﻣﺎﯾﺶ ﺩﺭ ﻭﺿﻌﯿﺖ‬ ‫ﺗﻤــﺎﻡ ﺑﺎﺭ ﺍﺯ ﻣﺒــﺪﻝ ﺁﺏ ﮔﺮﻡ ﻣﺼﺮﻓﯽ ﻧﯿﺰ‬

‫ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﻣﺤﻠﻮﻝ‬

‫ﺍﺳﺘﻔﺎﺩﻩ ﺷﻮﺩ‪ .‬ﺑﻨﺎﺑﺮﺍﯾﻦ ﻣﺒﺪﻝ ﮔﺮﻣﺎﯾﺸﯽ‬ ‫ﺗﺼﻮﯾﺮ )‪ (5‬ﭼﺮﺧﻪ ﺗﺎﻣﯿﻦ ﮔﺮﻣﺎﯾﺶ ﺁﺏ ﮔﺮﻡ ﻣﺼﺮﻓﯽ ﺑﻪ ﻭﺳﯿﻠﻪ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺷﻌﻠﻪ ﻣﺴﺘﻘﯿﻢ‬

‫ﺗﻨﻬــﺎ ﺩﺭ ﭼﺮﺧﻪ ﮔﺮﻣﺎﯾﺸــﯽ ﯾــﺎ ﺑﻪ ﻃﻮﺭ‬ ‫ﻣﺴﺘﻘﻞ ﻗﺎﺩﺭ ﺑﻪ ﮐﺎﺭ ﺧﻮﺍﻫﺪ ﺑﻮﺩ‪ .‬ﺣﺘﺎ ﺩﺭ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﻣــﻮﺍﺭﺩﯼ ﮐﻪ ﻧﯿﺎﺯ ﺑــﻪ ﺁﺏ ﮔﺮﻡ ﻣﺼﺮﻓﯽ ﻭ‬ ‫ﺟﺪﻭﻝ ﺯﯾﺮ ﻧﺸــﺎﻧﮕﺮ ﻇﺮﻓﯿﺖ ﻭ ﺿﺮﯾﺐ ﺑﻬﺮﻩ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ ﺳــﺎﺧﺖ ﭼﻨﺪ ﺷﺮﮐﺖ‬

‫ﮔﺮﻣﺎﯾﺶ ﺳــﺎﺧﺘﻤﺎﻥ ﺯﯾﺎﺩ ﻣﻄﺮﺡ ﺑﺎﺷﺪ‪،‬‬

‫ﻣﻌﺮﻭﻑ ﺍﺳــﺖ ﮐﻪ ﺍﺯ ﻣﺘﻦ ﻣﻘﺎﻟﻪ ‪ Patti Welesko Adcock‬ﺗﺤﺖ ﻋﻨﻮﺍﻥ ‪From Fire to Ice‬‬

‫ﺍﻣﮑﺎﻥ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﺁﻥ ﺩﺭ ﭼﺮﺧﻪ ﮔﺮﻣﺎﯾﺸﯽ‬

‫ﺍﺧﺬ ﺷﺪﻩ ﺍﺳﺖ‪:‬‬

‫ﻧﯿــﺰ ﻭﺟﻮﺩ ﻧﺪﺍﺭﺩ‪ .‬ﺑﻨﺎﺑﺮﺍﯾﻦ ﺑﺮﺍﯼ ﺍﯾﻦﮔﻮﻧﻪ‬ ‫ﭼﯿﻠﺮﻫــﺎ ﭼﺮﺧﻪ ﺳــﻮﻣﯽ ﺗﺤــﺖ ﻋﻨﻮﺍﻥ‬

‫ﺳﺎﺧﺖ‬

‫ﻧﻮﻉ‬

‫ﻧﺮﺥ ﻇﺮﻓﯿﺖ‬

‫ﺷﺮﺡ‬

‫‪Carrier‬‬

‫ﯾﮏﺍﺛﺮﻩ‬

‫‪100-680 tons‬‬

‫ﻣﻨﺒﻊ ﮔﺮﻣﺎﯾﯽ‪ :‬ﺑﺨﺎﺭ ﯾﺎ ﺁﺏ ﮔﺮﻡ ﺿﺮﯾﺐ ﺑﻬﺮﻩ‪:‬‬

‫ﺩﻭ ﺍﺛﺮﻩ‬ ‫)ﮔﻮﺍﻫﯽ ﺍﺯ ﺍﺑﺎﺭﺍ(‬

‫)ﺑﺨﺎﺭ( ‪ 100-1700 tons‬ﻣﻨﺒﻊ ﮔﺮﻣﺎﯾﯽ‪ :‬ﺑﺨﺎﺭ‬ ‫‪135-1000 tons‬‬ ‫ﻣﻨﺒﻊ ﮔﺮﻣﺎﯾﯽ‪ :‬ﮔﺎﺯﻭﯾﯿﻞ ﯾﺎ ﮔﺎﺯ‬ ‫)ﮔﺎﺯﻭﯾﯿﻞ ﯾﺎ ﮔﺎﺯ(‬ ‫ﺿﺮﯾﺐ ﺑﻬﺮﻩ‪) 1.0 :‬ﺑﺮﺍﯼ ﮔﺎﺯﻭﯾﯿﻞ(‬ ‫‪) 0.97‬ﺑﺮﺍﯼ ﮔﺎﺯ(‬

‫‪ McQuay‬ﺩﻭ ﺍﺛﺮﻩ‬ ‫)ﮔﻮﺍﻫﯽ ﺍﺯ ﺳﺎﻧﯿﻮ(‬ ‫‪Trane‬‬

‫ﯾﮏﺍﺛﺮﻩ‬

‫‪0.7‬‬

‫ﺿﺮﯾﺐ ﺑﻬﺮﻩ‪1.2 :‬‬

‫ﺿﺮﯾﺐ ﺑﻬﺮﻩ‪1.2 :‬‬ ‫)ﺑﺨﺎﺭ( ‪ 100-1500 tons‬ﻣﻨﺒﻊ ﮔﺮﻣﺎﯾﯽ‪ :‬ﺑﺨﺎﺭ‬ ‫)ﮔﺎﺯ( ‪ 100-1500 tons‬ﻣﻨﺒﻊ ﮔﺮﻣﺎﯾﯽ‪ :‬ﺷﻌﻠﻪ ﻣﺴﺘﻘﯿﻢ ﺿﺮﯾﺐ ﺑﻬﺮﻩ‪0.99 :‬‬ ‫‪100-1600 tons‬‬

‫ﺩﻭ ﺍﺛﺮﻩ‬ ‫‪380-1000 tons‬‬ ‫)ﮔﻮﺍﻫﯽ ﺍﺯ ﮐﺎﻭﺍﺯﺍﮐﯽ( )ﺑﺨﺎﺭ ﯾﺎ ﺁﺏ ﮔﺮﻡ(‬ ‫‪100-1100 tons‬‬ ‫‪York‬‬

‫ﻣﻨﺒﻊ ﮔﺮﻣﺎﯾﯽ‪ :‬ﺑﺨﺎﺭ ﯾﺎ ﺁﺏ ﮔﺮﻡ‬ ‫ﺿﺮﯾﺐ ﺑﻬﺮﻩ‪066-067 :‬‬ ‫ﻣﻨﺒﻊ ﮔﺮﻣﺎﯾﯽ‪ :‬ﺑﺨﺎﺭ ﯾﺎ ﺁﺏ ﮔﺮﻡ ﺿﺮﯾﺐ ﺑﻬﺮﻩ‪1.2 :‬‬ ‫ﻣﻨﺒﻊ ﮔﺮﻣﺎﯾﯽ‪ :‬ﺷﻌﻠﻪ ﻣﺴﺘﻘﯿﻢ‬ ‫ﺿﺮﯾﺐ ﺑﻬﺮﻩ‪097-098 :‬‬ ‫)ﺩﺭ ﺻﻮﺭﺕ ﺑﺎﺯﺩﻩ ﺑﺎﻻﯼ ﺳﻮﺧﺖ ‪(1.05 -‬‬

‫‪100-1400 tons‬‬

‫ﻣﻨﺒﻊ ﮔﺮﻣﺎﯾﯽ‪ :‬ﺑﺨﺎﺭ ﯾﺎ ﺁﺏ ﮔﺮﻡ‬ ‫ﺿﺮﯾﺐ ﺑﻬﺮﻩ‪) 0.69 :‬ﺑﺨﺎﺭ( ﯾﺎ ‪) 0.67‬ﺁﺏ ﮔﺮﻡ(‬

‫‪450-1500 tons‬‬ ‫ﺩﻭ ﺍﺛﺮﻩ‬ ‫)ﮔﻮﺍﻫﯽ ﺍﺯ ﻫﯿﺘﺎﭼﯽ( ‪180-1000 tons‬‬

‫ﻣﻨﺒﻊ ﮔﺮﻣﺎﯾﯽ‪ :‬ﺑﺨﺎﺭ ﺿﺮﯾﺐ ﺑﻬﺮﻩ‪1.19 :‬‬ ‫ﻣﻨﺒﻊ ﮔﺮﻣﺎﯾﯽ‪ :‬ﺷﻌﻠﻪ ﻣﺴﺘﻘﯿﻢ ﺿﺮﯾﺐ ﺑﻬﺮﻩ‪:‬‬ ‫‪1.0‬‬

‫ﯾﮏﺍﺛﺮﻩ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﭼﺮﺧﻪ ﺗﺎﻣﯿﻦ ﺁﺏ ﮔﺮﻡ ﻣﺼﺮﻓﯽ ﻧﯿﺰ ﻭﺟﻮﺩ‬ ‫ﺩﺍﺭﺩ ﮐﻪ ﺑﻬﺮﻩﺑﺮﺩﺍﺭﯼ ﺍﺯ ﺁﻥ ﺗﻨﻬﺎ ﺩﺭ ﻓﺼﻮﻝ‬ ‫ﻣﻌﺘــﺪﻝ ﻣﺎﻧﻨﺪ ﭘﺎﯾﯿﺰ ﻭ ﺑﻬــﺎﺭ ﺍﻣﮑﺎﻥﭘﺬﯾﺮ‬ ‫ﺍﺳــﺖ‪ .‬ﺗﺼﻮﯾﺮ )‪ (5‬ﻧﻤﺎﯾﺸــﮕﺮ ﺍﯾﻦ ﭼﺮﺧﻪ‬ ‫ﺍﺳﺖ‪ .‬ﻫﻤﺎﻥﮔﻮﻧﻪ ﮐﻪ ﺩﺭ ﺗﺼﻮﯾﺮ ﻣﺸﺨﺺ‬ ‫ﺍﺳــﺖ ﺩﺭ ﭼﺮﺧﻪ ﺗﺎﻣﯿﻦ ﺁﺏ ﮔﺮﻡ ﻣﺼﺮﻓﯽ‬ ‫ﺑﻪ ﻭﺳــﯿﻠﻪ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺷﻌﻠﻪﻣﺴــﺘﻘﯿﻢ‬ ‫ﺗﻨﻬﺎ ﻣﺒــﺪﻝ ﺁﺏ ﮔﺮﻡ ﻭ ﮊﻧﺮﺍﺗﻮﺭ ﺩﻣﺎﯼ ﺑﺎﻻ‬ ‫ﺩﺭ ﻣﺪﺍﺭ ﺍﺳــﺘﻔﺎﺩﻩ ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﻧﺪ ﻭ ﺳﺎﯾﺮ‬ ‫ﻗﺴﻤﺖﻫﺎ ﻏﯿﺮﻓﻌﺎﻝ ﻫﺴﺘﻨﺪ‪.‬‬

‫ﭘﯽﻧﻮﺷﺖ‬

‫‪1- Superheat‬‬ ‫‪2- Desuperheater‬‬

‫ﺻﻔﺤﻪ ‪ / 15‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻓﻨﻰ‬

‫ﺗﻮﺯﻳﻊ ﻫﻮﺍ ﺩﺭ ﺍﺳﺘﺨﺮﻫﺎ‬

‫ﺗﻮﺯﯾﻊ ﻣﻨﺎﺳــﺐ ﺟﺮﯾﺎﻥ ﻫﻮﺍ ﺩﺭ ﺳﻄﺢ‬

‫)‪ (USOC1‬ﺗﺼﺮﯾﺢ ﺷﺪﻩ ﺍﺳﺖ ﮐﻪ ﺑﻪ ﻣﻨﻈﻮﺭ‬

‫ﺍﺯ ﺑــﺮﻭﺯ ﺍﯾﻦ ﻣﺸــﮑﻞ ﺑــﺮ ﺭﻭﯼ ﭘﻨﺠﺮﻩﻫﺎ ﻭ‬

‫ﺍﺳﺘﺨﺮ ﯾﮑﯽ ﺍﺯ ﻣﻬﻢﺗﺮﯾﻦ ﻋﻮﺍﻣﻠﯽ ﺍﺳﺖ ﮐﻪ‬

‫ﺭﻗﯿﻖﺳﺎﺯﯼ ﻏﻠﻈﺖ ﺁﻻﯾﻨﺪﻩﻫﺎﯼ ﺳﻄﺢ ﺁﺏ‬

‫ﺩﯾﻮﺍﺭﻫﺎﯼ ﺍﺳــﺘﺨﺮ‪ ،‬ﺟﺮﯾــﺎﻥ ﻫﻮﺍﯼ ﮔﺮﻡ ﻭ‬

‫ﺩﺭ ﺩﺳﺘﯿﺎﺑﯽ ﺑﻪ ﮐﯿﻔﯿﺖ ﻗﺎﺑﻞ ﻗﺒﻮﻝ ﻫﻮﺍﯼ‬

‫ﺩﺭ ﻣﺤــﻞ ﺗﻨﻔﺲ ﺷــﻨﺎﮔﺮﺍﻥ‪ ،‬ﺑﺨﺸــﯽ ﺍﺯ‬

‫ﺧﺸــﮏ ﺍﺭﺳﺎﻟﯽ ﺑﻪ ﺍﺳــﺘﺨﺮ ﺑﺎﯾﺪ ﺍﺯ ﻃﺮﯾﻖ‬

‫ﺩﺍﺧﻞ ﻧﻘــﺶ ﻣﻮﺛﺮﯼ ﺭﺍ ﺑﺮ ﺟــﺎﯼ ﺧﻮﺍﻫﺪ‬

‫ﺟﺮﯾﺎﻥ ﻫﻮﺍﯼ ﺍﺭﺳــﺎﻟﯽ ﺑﻪ ﺍﺳــﺘﺨﺮ ﺑﺎﯾﺪ ﺍﺯ‬

‫ﺩﺭﯾﭽﻪﻫــﺎﯼ ﮐﻔــﯽ ﺑــﻪ ﻣــﻮﺍﺯﺍﺕ ﺩﯾﻮﺍﺭﻫﺎ‬

‫ﮔﺬﺍﺷﺖ‪ .‬ﺗﻬﻮﯾﻪ ﻓﻀﺎﯼ ﺩﺍﺧﻞ ﺍﺳﺘﺨﺮﻫﺎﯼ‬

‫ﺳﻄﺢ ﮐﺎﺳﻪ ﺍﺳــﺘﺨﺮ ﻧﯿﺰ ﻋﺒﻮﺭ ﮐﻨﺪ‪ .‬ﺍﻟﺒﺘﻪ‬

‫ﻫﺪﺍﯾﺖ ﺷﻮﺩ‪.‬‬

‫ﺳﺮﭘﻮﺷــﯿﺪﻩ ﺑﻪ ﻭﯾﮋﻩ ﺩﺭ ﻣﻮﺍﺭﺩﯼ ﮐﻪ ﺑﺮﺍﯼ‬

‫ﺍﻧﺠﻤــﻦ ‪ ASHRAE‬ﺳــﺮﻋﺖ ﺟﺮﯾﺎﻥ ﻫﻮﺍ‬

‫ﺿﺪﻋﻔﻮﻧــﯽ ﮐــﺮﺩﻥ ﺁﺏ ﺍﺯ ﮐﻠﺮ ﺍﺳــﺘﻔﺎﺩﻩ‬

‫ﺑﺮ ﺭﻭﯼ ﺳــﻄﺢ ﺁﺏ ﺍﺳــﺘﺨﺮﻫﺎ ﺭﺍ ﺑﻪ ﺍﻧﺪﺍﺯﻩ‬

‫ﻣﯽﺷﻮﺩ‪ ،‬ﺍﻫﻤﯿﺘﯽ ﺩﻭ ﭼﻨﺪﺍﻥ ﺩﺍﺭﺩ‪ .‬ﺗﻮﺯﯾﻊ‬

‫)‪ 0.05−0.15m/s (10−30fpm‬ﻣﺤــﺪﻭﺩ‬

‫ﻫﻮﺍ ﺩﺭ ﻓﻀﺎﯼ ﺍﺳــﺘﺨﺮ ﺑﺎﯾﺪ ﻃﻮﺭﯼ ﺍﻧﺠﺎﻡ‬

‫ﮐﺮﺩﻩ ﺍﺳﺖ ﻭ ﺳﺮﻋﺖﻫﺎﯼ ﺑﺎﻻﺗﺮ ﺭﺍ ﺑﻪ ﺩﻟﯿﻞ‬

‫ﺷــﻮﺩ ﮐﻪ ﺍﺯ ﺍﯾﺠﺎﺩ ﻓﻀﺎﯼ ﻣﺮﺩﻩ ﺟﻠﻮﮔﯿﺮﯼ‬

‫ﺍﻓﺰﺍﯾﺶ ﻧﺮﺥ ﺗﺒﺨﯿﺮ ﺁﺏ ﺍﺳــﺘﺨﺮ ﻭ ﮐﺎﻫﺶ‬

‫ﺷﻮﺩ‪.‬‬

‫ﺷﺮﺍﯾﻂ ﺁﺳﺎﯾﺶ ﺷﻨﺎﮔﺮﺍﻥ ﻣﺠﺎﺯ ﻧﻤﯽﺩﺍﻧﺪ‪.‬‬

‫ﻃﺮﺍﺣﯽ ﮐﺎﻧﺎﻝ‬ ‫ﻃﺮﺍﺣــﯽ ﻭ ﺳــﺎﺧﺖ ﺷــﺒﮑﻪ ﮐﺎﻧــﺎﻝ‬ ‫ﺑﺎﯾﺪ ﺑــﺮ ﻣﺒﻨــﺎﯼ ﺁﺧﺮﯾﻦ ﺍﺳــﺘﺎﻧﺪﺍﺭﺩﻫﺎﯼ‬ ‫ﺍﻧﺠﻤﻦﻫــﺎﯼ‪ SMACNA 2‬ﻭ ‪ASHRAE‬‬

‫ﻃﺮﺍﺣﯽ ﮐﺎﻧﺎﻝ ﺳﯿﺴﺘﻢﻫﺎﯼ ﺗﻬﻮﯾﻪ ﻣﻄﺒﻮﻉ‬

‫ﯾﮑــﯽ ﺍﺯ ﻧﮑﺎﺕ ﮐﻠﯽ ﮐﻪ ﺑﻪ ﻧﻮﻋﯽ ﻧﻘﻄﻪ‬

‫ﯾﮑــﯽ ﺍﺯ ﻣﺸــﮑﻼﺕ ﻣﺘﺪﺍﻭﻟــﯽ ﮐﻪ ﺩﺭ‬

‫ﺍﺷــﺘﺮﺍﮎ ﺗﻤﺎﻣــﯽ ﺩﯾﺪﮔﺎﻩﻫــﺎﯼ ﻣﺨﺘﻠﻒ‬

‫ﺍﺳــﺘﺨﺮﻫﺎﯼ ﺳﺮﭘﻮﺷــﯿﺪﻩ ﺑــﺎ ﭘﻨﺠﺮﻩﻫﺎﯼ‬

‫ﻃﺮﺍﺣﯽ ﺑﻪ ﺷــﻤﺎﺭ ﻣﯽﺭﻭﺩ ﺁﻥ ﺍﺳﺖ ﮐﻪ ﺑﻪ‬

‫ﺑــﺰﺭﮒ ﺑﻪ ﻭﺟﻮﺩ ﻣﯽﺁﯾــﺪ‪ ،‬ﺗﻘﻄﯿﺮ ﺑﺨﺎﺭ ﺁﺏ‬

‫ﻣﻨﻈﻮﺭ ﺧﺎﺭﺝ ﮐﺮﺩﻥ ﻫﻮﺍﯼ ﮔﺮﻡ ﻭ ﻣﺮﻃﻮﺏ‬

‫ﻣﻮﺟﻮﺩ ﺩﺭ ﻫﻮﺍ ﺑﺮ ﺭﻭﯼ ﺷﯿﺸــﻪ ﺍﺳــﺖ‪ .‬ﺍﺯ‬

‫ﮐــﻪ ﻣﻌﻤﻮﻻ ﺑﺮ ﺭﻭﯼ ﺳــﻄﺢ ﺁﺏ ﺍﺳــﺘﺨﺮ‬

‫ﺁﻧﺠﺎﯾﯽ ﮐﻪ ﭘﻨﺠﺮﻩﻫﺎ ﺩﺭ ﻣﻌﺮﺽ ﺗﻘﻄﯿﺮ ﺑﺨﺎﺭ‬

‫ﺷــﺎﻣﻞ ﻭﺭﻕﻫــﺎﯼ ﮔﺎﻟﻮﺍﻧﯿﺰﻩ ﺍﺳــﺘﺎﻧﺪﺍﺭﺩ‪،‬‬

‫ﻗﺮﺍﺭ ﻣﯽﮔﯿــﺮﺩ‪ ،‬ﺟﺮﯾﺎﻥ ﻫــﻮﺍﯼ ﺭﻓﺖ ﺑﺎﯾﺪ‬

‫ﺁﺏ ﻫﺴــﺘﻨﺪ‪ ،‬ﻃﺮﺍﺣﯽ ﺳﯿﺴﺘﻢﻫﺎﯼ ﺗﻮﺯﯾﻊ‬

‫ﺁﻟﻮﻣﯿﻨﯿــﻮﻡ ﻭ ﻣﻮﺍﺩ ﭘﻠﯿﻤﺮﯼ ﻫﺴــﺘﻨﺪ‪ .‬ﺩﺭ‬

‫ﺭﻃﻮﺑﺖ ﻣﻮﺟﻮﺩ ﺩﺭ ﻓﻀﺎﯼ ﺩﺍﺧﻞ ﺍﺳــﺘﺨﺮ‬

‫ﻫــﻮﺍ ﺑﺎﯾﺪ ﺑــﺎ ﺗﻤﺮﮐﺰ ﺑﺮ ﺍﯾــﻦ ﺑﺨﺶ ﺍﻧﺠﺎﻡ‬

‫ﺍﮐﺜﺮ ﻣﻮﺍﺭﺩ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﻭﺭﻕﻫﺎﯼ ﮔﺎﻟﻮﺍﻧﯿﺰﻩ‬

‫ﺭﺍ ﺩﺭﯾﺎﻓــﺖ ﻭ ﺳــﭙﺲ ﺍﺯ ﻧﺎﺣﯿﻪ ﺳــﻘﻒ ﺑﻪ‬

‫ﮔﯿــﺮﺩ‪ .‬ﺍﻟﺒﺘﻪ ﺑﺎ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺷﯿﺸــﻪﻫﺎﯼ‬

‫ﺍﺳــﺘﺎﻧﺪﺍﺭﺩ ﺍﻣﮑﺎﻥﭘﺬﯾــﺮ ﺍﺳــﺖ‪ .‬ﺑــﺮﺍﯼ‬

‫ﺧﺎﺭﺝ ﺗﺨﻠﯿﻪ ﺷــﻮﺩ‪ .‬ﺍﻟﺒﺘﻪ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﺍﯾﻦ‬

‫ﺩﻭ ﺟﺪﺍﺭﻩ‪ ،‬ﺳــﻪ ﺟــﺪﺍﺭﻩ ﯾﺎ ﺷﯿﺸــﻪﻫﺎﯼ‬

‫ﮐﺎﻧﺎﻝﻫﺎﯾﯽ ﮐﻪ ﺩﺭ ﺯﯾﺮ ﮐﻒ ﺍﺟﺮﺍ ﻣﯽﺷــﻮﻧﺪ‬

‫ﺭﻭﺵ ﻣﺴﺘﻠﺰﻡ ﺩﻗﺖ ﺑﺴﯿﺎﺭﯼ ﺍﺳﺖ‪ .‬ﭼﺮﺍﮐﻪ‬

‫ﻣﺮﻏﻮﺑﯽ ﮐﻪ ﺿﺮﯾﺐ ﺍﻧﺘﻘﺎﻝ ﺣﺮﺍﺭﺕ ﺑﺴــﯿﺎﺭ‬

‫ﻧﯿــﺰ ﺑﻬﺘﺮ ﺍﺳــﺖ ﺍﺯ ﮐﺎﻧﺎﻝﻫــﺎﯼ ﻏﯿﺮﻓﻠﺰﯼ‬

‫ﺑﺮﺍﯼ ﺑﻪ ﺣﺪﺍﻗﻞ ﺭﺳــﺎﻧﺪﻥ ﺳــﺮﻋﺖ ﺗﺒﺨﯿﺮ‬

‫ﭘﺎﯾﯿﻨــﯽ ﺩﺍﺭﻧﺪ ﻣﯽﺗﻮﺍﻥ ﺍﯾﻦ ﻣﺸــﮑﻞ ﺭﺍ ﺑﻪ‬

‫ﯾــﺎ ﮐﺎﻧﺎﻝﻫﺎﯼ ﻓﻠــﺰﯼ ﺑﺎ ﺭﻭﮐــﺶ ﻣﺤﺎﻓﻆ‬

‫ﺁﺏ ﺍﺳــﺘﺨﺮ‪ ،‬ﺍﻟﮕﻮﯼ ﺟﺮﯾﺎﻥ ﻫﻮﺍ ﺩﺭ ﺩﺍﺧﻞ‬

‫ﻣﯿــﺰﺍﻥ ﺯﯾﺎﺩﯼ ﮐﺎﻫــﺶ ﺩﺍﺩ‪ .‬ﺭﻭﺵ ﻋﻤﻠﯽ‬

‫ﺍﺳﺘﺨﺮ ﺑﺎﯾﺪ ﺑﻪﮔﻮﻧﻪﺍﯼ ﺑﺎﺷﺪ ﮐﻪ ﺟﺮﯾﺎﻥ ﻫﻮﺍ‬

‫ﺑــﺮﺍﯼ ﺍﺯ ﺑﯿﻦ ﺑــﺮﺩﻥ ﺑﺨﺎﺭ ﺷﯿﺸــﻪﻫﺎ ﺁﻥ‬

‫ﺍﺳﺘﻔﺎﺩﻩ ﺷﻮﺩ‪.‬‬ ‫● ﺑﺮﺍﯼ ﺟﻠﻮﮔﯿﺮﯼ ﺍﺯ ﺍﻧﺘﻘﺎﻝ ﺍﺭﺗﻌﺎﺷﺎﺕ‬

‫ﺑﺮ ﺭﻭﯼ ﺳﻄﺢ ﺁﺏ ﺣﺪﺍﻗﻞ ﺑﺎﺷﺪ‪.‬‬

‫ﺍﺳــﺖ ﮐﻪ ﺩﻣﺎﯼ ﺳﻄﺢ ﺷﯿﺸــﻪ ﺍﺯ ﺩﻣﺎﯼ‬

‫ﺳﯿﺴــﺘﻢ ﺑﻪ ﺳﺎﺯﻩ ﺳــﺎﺧﺘﻤﺎﻥ‪ ،‬ﺩﺭ ﻣﺤﻞ‬

‫ﺩﺭ ﺑﺮﺧــﯽ ﺍﺯ ﺍﺳــﺘﺎﻧﺪﺍﺭﺩﻫﺎ ﻣﺎﻧﻨــﺪ‬

‫ﻧﻘﻄﻪ ﺷــﺒﻨﻢ ﻫﻮﺍﯼ ﺩﺍﺧﻞ ﺍﺳﺘﺨﺮ ﺑﯿﺸﺘﺮ‬

‫ﺍﺗﺼﺎﻝ ﺷــﺒﮑﻪ ﮐﺎﻧﺎﻝ ﺑﻪ ﺳﯿﺴــﺘﻢ ﺑﺎﯾﺪ ﺍﺯ‬

‫ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ﮐﻤﯿﺘﻪ ﺍﻟﻤﭙﯿﮏ ﺍﯾﺎﻻﺕ ﻣﺘﺤﺪﻩ‬

‫ﺑﺎﺷــﺪ‪ .‬ﺑﻪ ﻫﻤﯿﻦ ﻣﻨﻈﻮﺭ ﺟﻬﺖ ﺟﻠﻮﮔﯿﺮﯼ‬

‫ﺍﺗﺼﺎﻻﺕ ﺍﻧﻌﻄﺎﻑﭘﺬﯾﺮ ﺍﺳﺘﻔﺎﺩﻩ ﺷﻮﺩ‪.‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺍﺳﺘﺨﺮﻫﺎ ﺭﻋﺎﯾﺖ ﺷﻮﺩ ﺭﺍ ﻣﯽﺗﻮﺍﻥ ﺩﺭ ﻣﻮﺍﺭﺩ‬ ‫ﺯﯾﺮ ﺧﻼﺻﻪ ﮐﺮﺩ‪:‬‬ ‫● ﻣﻮﺍﺩ ﺗﻮﺻﯿﻪ ﺷــﺪﻩ ﺑــﺮﺍﯼ ﮐﺎﻧﺎﻝﻫﺎ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺍﻧﺠﺎﻡ ﮔﯿﺮﺩ‪ .‬ﻣﻼﺣﻈﺎﺗﯽ ﮐﻪ ﺑﺎﯾﺪ ﺩﺭ ﻫﻨﮕﺎﻡ‬

‫ﺻﻔﺤﻪ ‪ / 16‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺍﺗﺎﻕ ﺗﺠﻬﯿﺰﺍﺕ ﻣﮑﺎﻧﯿﮑﯽ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺗﺼﻮﯾﺮ )‪ (1‬ﺳﺎﺧﺘﺎﺭ ﻣﺘﺪﺍﻭﻝ ﺷﺒﮑﻪ ﮐﺎﻧﺎﻝ ﮐﻔﯽ ﺩﺭ ﺍﺳﺘﺨﺮﻫﺎ‬

‫● ﺗﻤﺎﻣﯽ ﺩﺭﯾﭽﻪﻫﺎ ﻭ ﺗﻮﺯﯾﻊﮐﻨﻨﺪﻩﻫﺎﯼ‬

‫ﻭﺟــﻮﺩ ﺩﺍﺭﺩ‪ ،‬ﻋﺎﯾﻖﮐﺎﺭﯼ ﺑﺎﯾﺪ ﺩﺭ ﻗﺴــﻤﺖ‬

‫● ﺑﺮﺍﯼ ﺑــﻪ ﺣﺪﺍﻗﻞ ﺭﺳــﺎﻧﺪﻥ ﻫﺰﯾﻨﻪ‬

‫ﻫــﻮﺍ ﺑﺎﯾﺪ ﺑــﺮ ﻣﺒﻨﺎﯼ ﻣﻌﯿــﺎﺭ ‪ ،NC3‬ﻣﻘﺪﺍﺭ‬

‫ﺧﺎﺭﺟﯽ ﮐﺎﻧﺎﻝ ﺍﻧﺠﺎﻡ ﮔﯿﺮﺩ‪.‬‬ ‫● ﻣــﻮﺍﺩ ﻭ ﺗﺠﻬﯿــﺰﺍﺕ ﺟﺎﻧﺒــﯽ ﻣﻮﺭﺩ‬

‫ﺍﻭﻟﯿﻪ ﻭ ﺍﻓﺖ ﻓﺸــﺎﺭ ﺍﯾﺠﺎﺩ ﺷــﺪﻩ ﺩﺭ ﻣﺴﯿﺮ‬ ‫ﻫــﻮﺍ‪ ،‬ﻣﺤﻞ ﻧﺼﺐ ﺳﯿﺴــﺘﻢ ﺗﻬﻮﯾﻪ ﺑﺎﯾﺪ ﺗﺎ‬

‫ﻣﻄﻠﻮﺏ ﺍﻧﺠــﺎﻡ ﮔﯿﺮﺩ‪ .‬ﮐﻠﯿﻪ ﻣــﻮﺍﺩ ﺑﻪﮐﺎﺭ‬

‫ﺍﺳــﺘﻔﺎﺩﻩ ﺩﺭ ﺷــﺒﮑﻪ ﮐﺎﻧﺎﻝ ﺑﺎﯾﺪ ﻣﻘﺎﻭﻣﺖ‬

‫ﺣﺪ ﺍﻣﮑﺎﻥ ﺑﻪ ﻓﻀﺎﯼ ﺩﺍﺧﻞ ﺍﺳﺘﺨﺮ ﻧﺰﺩﯾﮏ‬

‫ﺭﻓﺘﻪ ﺑﺮﺍﯼ ﺳﺎﺧﺖ ﺩﺭﯾﭽﻪﻫﺎ ﺑﺎﯾﺪ ﻣﻘﺎﻭﻣﺖ‬

‫ﮐﺎﻓﯽ ﺩﺭ ﺑﺮﺍﺑﺮ ﻣﻮﺍﺩ ﺷــﯿﻤﯿﺎﯾﯽ ﻣﻮﺟﻮﺩ ﺩﺭ‬

‫ﮐﺎﻓﯽ ﺩﺭ ﺑﺨﺎﺭﺍﺕ ﻣﻮﺍﺩ ﺷﯿﻤﯿﺎﯾﯽ ﻭ ﻓﻀﺎﯼ‬

‫ﻫﻮﺍﯼ ﺍﺳﺘﺨﺮ ﺭﺍ ﺩﺍﺷــﺘﻪ ﺑﺎﺷﻨﺪ‪ .‬ﺳﺎﺧﺘﺎﺭ‬

‫ﺑﺎﺷﺪ‪.‬‬ ‫● ﺩﺭﯾﭽﻪﻫﺎﯼ ﺗﻮﺯﯾﻊ ﻫﻮﺍ ﺑﺎﯾﺪ ﺍﺯ ﺟﻨﺲ‬

‫ﻣﺮﻃﻮﺏ ﺍﺳﺘﺨﺮ ﺭﺍ ﺩﺍﺷﺘﻪ ﺑﺎﺷﺪ‪.‬‬

‫ﻓﻮﻻﺩﻫﺎﯼ ﺿﺪ ﺯﻧﮓ ﺳﺮﯼ ‪ 400‬ﺑﻪ ﮔﻮﻧﻪﺍﯼ‬

‫ﺁﻟﻮﻣﯿﻨﯿﻮﻡ ﺳــﺎﺧﺘﻪ ﺷــﻮﻧﺪ‪ .‬ﺍﯾﻦ ﺩﺭﯾﭽﻪﻫﺎ‬

‫‪‬ﻣﻘـﺪﺍﺭ ﻫﻮﺍﺩﻫـﯽ ﻫـﺮ ﯾـﮏ ﺍﺯ‬

‫ﺍﺳﺖ ﮐﻪ ﺩﺭ ﻫﻮﺍﯼ ﻣﺮﻃﻮﺏ ﻭ ﺩﺭ ﻣﺠﺎﻭﺭﺕ‬

‫ﺑﺎﯾﺪ ﺑﺮ ﺍﺳــﺎﺱ ﺍﻓﺖ ﻓﺸﺎﺭ ﺍﺳﺘﺎﺗﯿﮏ ﮐﻢ ﻭ‬

‫ﺑﺨﺎﺭﺍﺕ ﮐﻠﺮ ﺑﻪ ﺳــﺮﻋﺖ ﺩﭼــﺎﺭ ﺧﻮﺭﺩﮔﯽ‬

‫ﺩﺭﯾﭽﻪﻫـﺎﯼ ﺗﻮﺯﯾـﻊ ﻫـﻮﺍ ﺗﻘﺮﯾﺒﺎ‬

‫ﻣﯽﺷﻮﻧﺪ‪ .‬ﻓﻮﻻﺩﻫﺎﯼ ﺿﺪ ﺯﻧﮓ ﺳﺮﯼ ‪316‬‬

‫ﭘﺮﺗﺎﺏ ﺑﺎﺩ ﻣﻨﺎﺳﺐ ﺍﻧﺘﺨﺎﺏ ﺷﻮﻧﺪ‪.‬‬ ‫● ﻫــﻮﺍﯼ ﺭﻓــﺖ ﺑﺎﯾــﺪ ﻣﺴــﺘﻘﯿﻤﺎ ﺑﻪ‬

‫ﺑﺎﯾـﺪ ﺑـﻪ ﺍﻧـﺪﺍﺯﻩ ‪170 m3/hr‬‬

‫ﺑﺎ ﺭﻭﮐﺶ ﮔﺎﻟﻮﺍﻧﯿﺰﻩ ﯾﺎ ﻭﺭﻕﻫﺎﯼ ﺁﻟﻮﻣﯿﻨﯿﻮﻡ‬

‫ﺳــﻤﺖ ﺳــﻄﻮﺡ ﺩﺍﺧﻠــﯽ ﺍﺳــﺘﺨﺮ ﻣﺎﻧﻨﺪ‬

‫)‪ (100cfm‬ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﺷﻮﺩ‪.‬‬

‫ﻣﻘﺎﻭﻣﺖ ﺧﻮﺑﯽ ﺩﺭ ﺑﺮﺍﺑﺮ ﺷــﺮﺍﯾﻂ ﯾﺎﺩ ﺷﺪﻩ‬

‫ﺩﺭﻫﺎ‪ ،‬ﺩﯾﻮﺍﺭﻫﺎ ﻭ ﺷﯿﺸــﻪﻫﺎ ﻫﺪﺍﯾﺖ ﺷــﻮﺩ‬

‫ﺩﺍﺭﻧﺪ ﻭ ﺑﺮﺍﯼ ﺟﺪﺍﺭﻩ ﺩﺍﺧﻠﯽ ﮐﺎﻧﺎﻝ ﻣﯽﺗﻮﺍﻥ‬

‫ﮐﻪ ﺍﺣﺘﻤﺎﻝ ﺗﻘﻄﯿﺮ ﺑﺨﺎﺭ ﺁﺏ ﺑﺮ ﺭﻭﯼ ﺁﻥﻫﺎ‬

‫● ﺑــﺮﺍﯼ ﻫﻮﺍﺑﻨﺪ ﮐﺮﺩﻥ ﻗﺴــﻤﺖﻫﺎﯼ‬

‫ﺍﺯ ﺁﻥﻫــﺎ ﺍﺳــﺘﻔﺎﺩﻩ ﮐــﺮﺩ‪ .‬ﮐﺎﻧﺎﻝﻫﺎﯼ ﺯﯾﺮ‬

‫ﺑﯿﺸــﺘﺮ ﺍﺳــﺖ‪ .‬ﺑﻪ ﻣﻨﻈﻮﺭ ﺧــﺎﺭﺝ ﮐﺮﺩﻥ‬

‫ﻣﺨﺘﻠــﻒ ﮐﺎﻧــﺎﻝ ﻧﺒﺎﯾــﺪ ﺍﺯ ﺩﺭﺯﮔﯿﺮﻫــﺎﯼ‬

‫ﺯﻣﯿﻨــﯽ ﺑﻪﺩﻟﯿﻞ ﺩﺷــﻮﺍﺭﯼ ﺗﻌﻮﯾﺾ ﮐﺎﻧﺎﻝ‬

‫ﻫﻮﺍﯼ ﺁﻟﻮﺩﻩ ﺳــﺎﮐﻦ ﮐﻪ ﺑﺮ ﺭﻭﯼ ﺳﻄﺢ ﺁﺏ‬

‫ﻓﺎﯾﺒﺮﮔﻼﺱ ﺍﺳﺘﻔﺎﺩﻩ ﺷﻮﺩ‪ .‬ﺩﺭ ﻣﻮﺍﺭﺩﯼ ﮐﻪ‬

‫ﺑﺎﯾــﺪ ﺍﺯ ﻣﻮﺍﺩ ﻓﻠﺰﯼ ﺗﻘﻮﯾﺖ ﺷــﺪﻩ ﺑﺎ ﺍﻟﯿﺎﻑ‬

‫ﺍﺳــﺘﺨﺮ ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﺩ‪ ،‬ﺑﺨﺸــﯽ ﺍﺯ ﻫﻮﺍﯼ‬

‫ﺍﺣﺘﻤﺎﻝ ﺗﻘﻄﯿــﺮ ﺑﺨﺎﺭ ﺁﺏ ﺩﺭ ﺩﺍﺧﻞ ﮐﺎﻧﺎﻝ‬

‫ﺷﯿﺸﻪ ﯾﺎ ﻣﻮﺍﺩ ﭘﻠﯿﻤﺮﯼ ﺳﺎﺧﺘﻪ ﺷﻮﻧﺪ‪.‬‬

‫ﺭﻓﺖ ﺍﺭﺳــﺎﻝ ﺷــﺪﻩ ﺑﻪ ﺩﺍﺧﻞ ﻣﺤﯿﻂ ﺑﺎﯾﺪ‬

‫ﻫﻮﺍﺩﻫﯽ ﻣــﻮﺭﺩ ﻧﯿﺎﺯ ﻭ ﺍﻟﮕﻮﯼ ﺗﻮﺯﯾﻊ ﻫﻮﺍﯼ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺻﻔﺤﻪ ‪ / 17‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺩﺭﯾﭽﻪ ﺑﺮﮔﺸﺖ ﻫﻮﺍ‬ ‫ﮐﺎﻧﺎﻝ ﺭﻓﺖ‬

‫ﮐﺎﻧﺎﻝ ﺭﻓﺖ‬

‫ﺗﺼﻮﯾﺮ )‪ (2‬ﺳﺎﺧﺘﺎﺭ ﻣﺘﺪﺍﻭﻝ ﺷﺒﮑﻪ ﮐﺎﻧﺎﻝ ﺳﻘﻔﯽ ﺩﺭ ﺍﺳﺘﺨﺮﻫﺎ‬

‫ﺑﺮﮔﺸﺖ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﻗﻄﺮ‬ ‫ﻋﻤﯿﻖ‬

‫ﺍﺳﮑﯿﻤﺮ‬ ‫ﺑﺮﮔﺸﺖ‬ ‫ﺑﺮﮔﺸﺖ‬ ‫ﺷﯿﺮ‬ ‫ﺳﻪﺭﺍﻫﻪ‬

‫ﺍﺳﮑﯿﻤﺮ‬ ‫ﺷﯿﺮ‬ ‫ﺳﻪﺭﺍﻫﻪ‬

‫ﺑﺮﮔﺸﺖ‬ ‫ﻓﯿﻠﺘﺮ‬

‫ﺑﺮﮔﺸﺖ‬

‫ﮔﺮﻣﮑﻦ‬

‫ﺗﺨﻠﯿﻪ‬

‫ﺗﺨﻠﯿﻪ‬

‫ﺗﺨﻠﯿﻪ‬

‫ﺷﯿﺮ‬ ‫ﺳﻪﺭﺍﻫﻪ‬ ‫ﭘﻤﭗ ﻭ ﻣﻮﺗﻮﺭ‬

‫ﺷﯿﺮ‬ ‫ﺳﻪﺭﺍﻫﻪ‬ ‫ﺷﯿﺮ‬ ‫ﺳﻪﺭﺍﻫﻪ‬

‫ﺗﺼﻮﯾﺮ )‪ (3‬ﻃﺮﺣﻮﺍﺭﻩ ﺳﯿﺴﺘﻢ ﻟﻮﻟﻪﮐﺸﯽ ﺍﺳﺘﺨﺮ ﻭ ﻧﺤﻮﻩ ﺍﺳﺘﻘﺮﺍﺭ ﺗﺎﺳﯿﺴﺎﺕ ﻣﮑﺎﻧﯿﮑﯽ ﺁﻥ‬

‫ﺑﺮ ﺭﻭﯼ ﺳــﻄﺢ ﺁﺏ ﺍﺳــﺘﺨﺮ ﻫﺪﺍﯾﺖ ﺷﻮﺩ‪.‬‬

‫ﺑﺮﮔﺸﺖ ﺗﺨﻠﯿﻪ ﻣﯽﺷﻮﻧﺪ‪.‬‬

‫ﻭ ﺑﺎﺯﮔﺮﺩﺍﻧــﺪﻥ ﺁﻥ ﺑﻪ ﺳﯿﺴــﺘﻢ ﺗﻬﻮﯾﻪ ﺑﻪ‬

‫ﺑﺪﯾﻦﺗﺮﺗﯿﺐ ﺁﻻﯾﻨﺪﻩﻫﺎﯼ ﻣﺘﺼﺎﻋﺪ ﺷــﺪﻩ ﺍﺯ‬

‫● ﻣﺤﻞ ﻗﺮﺍﺭﮔﯿﺮﯼ ﺩﺭﯾﭽﻪﻫﺎﯼ ﻭﺭﻭﺩﯼ‬

‫ﻣﻨﻈﻮﺭ ﺍﻧﺠﺎﻡ ﻋﻤﻞ ﭘﺎﮐﺴﺎﺯﯼ ﻭﺟﻮﺩ ﺩﺍﺷﺘﻪ‬

‫ﺁﺏ ﺍﺳﺘﺨﺮ ﺑﻪ ﻫﻤﺮﺍﻩ ﻫﻮﺍﯼ ﺭﻓﺖ ﺍﺯ ﺳﻄﺢ‬

‫ﻫﻮﺍﯼ ﺑﺮﮔﺸﺖ ﺑﺎﯾﺪ ﺑﻪﮔﻮﻧﻪﺍﯼ ﺗﻌﯿﯿﻦ ﺷﻮﺩ‬

‫ﺑﺎﺷــﺪ‪ .‬ﺁﺭﺍﯾﺶ ﺩﺭﯾﭽﻪﻫﺎﯼ ﯾﺎﺩ ﺷﺪﻩ ﺑﺎﯾﺪ‬

‫ﺍﺳــﺘﺨﺮ ﺧــﺎﺭﺝ ﻭ ﺍﺯ ﻃﺮﯾــﻖ ﺩﺭﯾﭽﻪﻫﺎﯼ‬

‫ﮐﻪ ﺍﻣﮑﺎﻥ ﺑﺎﺯﯾﺎﺑﯽ ﻫــﻮﺍﯼ ﮔﺮﻡ ﻭ ﻣﺮﻃﻮﺏ‬

‫ﺑﻪ ﻧﺤﻮﯼ ﺑﺎﺷــﺪ ﮐﻪ ﻣﺎﻧﻊ ﺍﺯ ﺍﯾﺠﺎﺩ ﻓﻀﺎﯼ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺻﻔﺤﻪ ‪ / 18‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻣــﺮﺩﻩ ﺩﺭ ﺩﺍﺧﻞ ﻓﻀﺎﯼ ﺍﺳــﺘﺨﺮ ﺷــﻮﺩ ﻭ‬

‫ﺑﻪﮔﻮﻧﻪﺍﯼ ﺧﻮﺍﻫﺪ ﺑﻮﺩ ﮐــﻪ ﺟﺮﯾﺎﻥ ﻫﻮﺍ ﺑﺮ‬

‫ﻧﺎﺣﯿﻪ ﺳــﻘﻒ ﻭ ﺩﻭﺭﺗﺎﺩﻭﺭ ﺍﺳــﺘﺨﺮ ﺍﺳﺖ‬

‫ﺑﺎﺯﭼﺮﺧﺎﻧــﯽ ﻫﻮﺍﯼ ﺁﻟﻮﺩﻩ ﻣﺤﺘﻮﯼ ﺑﺨﺎﺭﺍﺕ‬

‫ﺭﻭﯼ ﺳــﻄﺢ ﺁﺏ ﺍﺳــﺘﺨﺮ ﺣﺪﺍﻗﻞ ﺍﺳﺖ‪.‬‬

‫)ﺗﺼﻮﯾــﺮ ‪ .(39‬ﺍﺯ ﺍﯾــﻦ ﺭﻭﺵ ﻣﻌﻤــﻮﻻ ﺩﺭ‬

‫ﮐﻠﺮ ﺩﺭ ﻓﻀﺎﯼ ﺩﺍﺧﻞ ﺍﺳﺘﺨﺮ ﻧﯿﺰ ﺑﻪ ﺣﺪﺍﻗﻞ‬

‫ﺑــﺮﺍﯼ ﺗﻮﺯﯾــﻊ ﯾﮑﻨﻮﺍﺧﺖ ﺟﺮﯾــﺎﻥ ﻫﻮﺍ ﺩﺭ‬

‫ﻣﻮﺍﻗﻌﯽ ﺍﺳــﺘﻔﺎﺩﻩ ﻣﯽﺷــﻮﺩ ﮐــﻪ ﺍﻣﮑﺎﻥ‬

‫ﮐﺎﻫﺶ ﯾﺎﺑﺪ‪.‬‬ ‫● ﻃﺒﻖ ﺍﺳــﺘﺎﻧﺪﺍﺭﺩ ‪ASHRAE 52.1‬‬

‫ﺳﺮﺗﺎﺳﺮ ﺳﻄﺢ ﺩﺍﺧﻠﯽ ﭘﻨﺠﺮﻩ ﻭ ﺟﻠﻮﮔﯿﺮﯼ‬

‫ﺍﺟــﺮﺍﯼ ﮐﺎﻧــﺎﻝ ﺑــﻪ ﺻﻮﺭﺕ ﮐﻔــﯽ ﻭﺟﻮﺩ‬

‫ﺍﺯ ﺗﻘﻄﯿﺮ ﺑﺨﺎﺭ ﺁﺏ ﺩﺭ ﮔﻮﺷــﻪﻫﺎ ﻭ ﻟﺒﻪﻫﺎﯼ‬

‫ﻧﺪﺍﺷــﺘﻪ ﺑﺎﺷــﺪ‪ .‬ﻫﻤﺎﻥﻃﻮﺭ ﮐﻪ ﻣﺸﺎﻫﺪﻩ‬

‫ﺭﺍﻧﺪﻣــﺎﻥ ﻓﯿﻠﺘﺮﻫــﺎﯼ ﻣﻮﺭﺩ ﺍﺳــﺘﻔﺎﺩﻩ ﺩﺭ‬

‫ﺯﯾﺮﯾﻦ ﭘﻨﺠﺮﻩ‪ ،‬ﻧﯿﺰ ﺑﻬﺘﺮ ﺍﺳﺖ ﻧﺴﺒﺖ ﻃﻮﻝ‬

‫ﻣﯽﮐﻨﯿﺪ‪ ،‬ﺩﺭ ﻫﺮ ﺩﻭ ﺭﻭﺵ‪ ،‬ﺟﺮﯾﺎﻥ ﻫﻮﺍﯾﯽ‬

‫ﺳﯿﺴــﺘﻢﻫﺎﯼ ﺗﻬﻮﯾﻪ ﺍﺳــﺘﺨﺮﻫﺎ ﺑﺎﯾﺪ ﺑﯿﻦ‬

‫ﺑﻪ ﻋﺮﺽ ﺍﯾﻦ ﺩﺭﯾﭽﻪﻫﺎ ﺑﯿﺸﺘﺮ ﺑﺎﺷﺪ‪.‬‬

‫ﮐﻪ ﻣﺴﺘﻘﯿﻤﺎ ﺑﻪ ﺳﻄﺢ ﺁﺏ ﺍﺳﺘﺨﺮ ﺩﻣﯿﺪﻩ‬ ‫ﻣﯽﺷﻮﺩ ﺣﺪﺍﻗﻞ ﺍﺳﺖ‪.‬‬

‫ﭼﻬﻞﻭﭘﻨﺞ ﺗﺎ ﺷﺼﺖﻭﭘﻨﺞ ﺩﺭﺻﺪ ﺑﺎﺷﺪ‪.‬‬ ‫● ﻃﺮﺍﺣﯽ ﺳﯿﺴــﺘﻢﻫﺎﯼ ﻫﻮﺍﯾﯽ ﺑﺎﯾﺪ‬

‫‪‬ﺩﺭ ﺍﺳـﺘﺨﺮﻫﺎﯼ ﺳﺮﭘﻮﺷـﯿﺪﻩ‬

‫ﺑﻪﮔﻮﻧــﻪﺍﯼ ﺻﻮﺭﺕ ﭘﺬﯾﺮﺩ ﮐﻪ ﺳــﺮﻭﺻﺪﺍﯼ‬

‫ﺑـﻪ ﻣﻨﻈـﻮﺭ ﺟﻠﻮﮔﯿـﺮﯼ ﺍﺯ ﺑـﺮﻭﺯ‬

‫ﺍﯾﺠﺎﺩ ﺷﺪﻩ ﺗﻮﺳــﻂ ﺁﻥﻫﺎ ﺑﯿﻦ ‪45−50NC‬‬

‫ﻣﺸـﮑﻼﺗﯽ ﻣﺎﻧﻨﺪ ﻻﯾﻪﻻﯾﻪ ﺷﺪﻥ‬

‫ﻣﺎﻧﻨـﺪ ﭘﻨﺠﺮﻩﻫـﺎ ﻭ ﺗﻤﺎﻣـﯽ‬

‫ﺑﺎﺷــﺪ‪ .‬ﻫﺮ ﭼﻨﺪ ﮐﻪ ﺩﺭ ﺍﺭﺯﯾﺎﺑﯽ ﺍﯾﻦ ﻣﺴﺎﻟﻪ‬

‫ﻫﻮﺍ‪ ،‬ﺩﺭﯾﭽﻪ ﻫﻮﺍﯼ ﺑﺮﮔﺸـﺖ ﺑﺎﯾﺪ‬

‫ﺑﺨﺶﻫﺎﯾـﯽ ﺍﺯ ﻓﻀـﺎﯼ ﺩﺍﺧﻞ ﮐﻪ‬

‫ﺑﺎﯾﺪ ﺗﺎﺛﯿــﺮ ﺍﻧﻌﮑﺎﺱ ﻭ ﺟﺬﺏ ﺍﻣﻮﺍﺝ ﺻﻮﺗﯽ‬

‫ﺩﺭ ﺑﯿﺸﺘﺮﯾﻦ ﺍﺭﺗﻔﺎﻉ ﻣﻤﮑﻦ ﺗﻌﺒﯿﻪ‬

‫ﻣﺴﺘﻌﺪ ﺗﻘﻄﯿﺮ ﺑﺨﺎﺭ ﺁﺏ ﻫﺴﺘﻨﺪ‬

‫ﺗﻮﺳــﻂ ﺍﺟﺰﺍﯼ ﻣﺨﺘﻠﻒ ﺳﺎﺧﺘﻤﺎﻥ ﻣﺎﻧﻨﺪ‬

‫ﺷـﻮﺩ‪ .‬ﺑﻪ ﻃﻮﺭ ﺍﯾـﺪﻩﺁﻝ‪ ،‬ﺩﺭﯾﭽﻪ‬

‫ﺑﺎﯾـﺪ ﺩﺭ ﻣﻌـﺮﺽ ﺟﺮﯾـﺎﻥ ﻫﻮﺍﯼ‬

‫ﺩﯾﻮﺍﺭﻫﺎ‪ ،‬ﮐﻒ‪ ،‬ﺳــﻘﻒ ﻭ ﻏﯿﺮﻩ ﻧﯿﺰ ﺩﺭ ﻧﻈﺮ‬

‫ﻭﺭﻭﺩﯼ ﮐﺎﻧـﺎﻝ ﺑﺮﮔﺸـﺖ ﺑﺎﯾﺪ ﺑﻪ‬

‫ﺭﻓﺖ ﻗـﺮﺍﺭ ﺩﺍﺷـﺘﻪ ﺑﺎﺷـﻨﺪ‪ .‬ﺑﻪ‬

‫ﮔﺮﻓﺘﻪ ﺷﻮﺩ‪.‬‬

‫ﺍﻧـﺪﺍﺯﻩ )‪3−4.5m (10−15ft‬‬

‫ﺩﺭ ﺗﺼﻮﯾــﺮ )‪ (38‬ﯾﮑــﯽ ﺍﺯ ﺭﻭﺵﻫﺎﯼ‬

‫ﺑﺎﻻﺗﺮ ﺍﺯ ﺳﻄﺢ ﺍﺳﺘﺨﺮ ﻗﺮﺍﺭ ﮔﯿﺮﺩ‪.‬‬

‫ﻣﺘﺪﺍﻭﻝ ﻃﺮﺍﺣﯽ ﮐﺎﻧﺎﻝ ﺩﺭ ﺍﺳﺘﺨﺮﻫﺎ ﻧﺸﺎﻥ‬

‫ﻗﺮﺍﺭﮔﯿﺮﯼ ﺍﯾـﻦ ﺩﺭﯾﭽﻪ ﺩﺭ ﻓﻀﺎﯼ‬

‫ﺩﺍﺩﻩ ﺷــﺪﻩ ﺍﺳــﺖ‪ .‬ﺩﺭ ﺍﯾﻦ ﺭﻭﺵ‪ ،‬ﮐﺎﻧﺎﻝ‬

‫ﻓﻮﻗﺎﻧﯽ ﺍﺳـﺘﺨﺮ ﺗﻀﻤﯿﻦﮐﻨﻨﺪﻩﯼ‬

‫ﺭﻓﺖ ﺍﺯ ﺯﯾﺮ ﮐﻒ ﻋﺒﻮﺭ ﻣﯽﮐﻨﺪ ﺩﺭ ﺣﺎﻟﯽ ﮐﻪ‬

‫ﺁﻥ ﺧﻮﺍﻫـﺪ ﺑﻮﺩ ﮐـﻪ ﺟﺮﯾﺎﻥ ﻫﻮﺍ‬

‫ﺑﺮﮔﺸــﺖ ﻫﻮﺍ ﺍﺯ ﻧﺎﺣﯿﻪ ﻓﻮﻗﺎﻧﯽ ﻧﺰﺩﯾﮏ ﺑﻪ‬

‫ﭘﯿـﺶ ﺍﺯ ﺧﺮﻭﺝ ﺍﺯ ﻓﻀﺎﯼ ﺩﺍﺧﻞ‪،‬‬

‫ﺳــﻘﻒ ﺍﻧﺠﺎﻡ ﻣﯽﮔﯿﺮﺩ‪ .‬ﺑﺪﯾﻦﺗﺮﺗﯿﺐ ﺗﻤﺎﻡ‬

‫ﺩﺭ ﺳﺮﺗﺎﺳـﺮ ﺁﻥ ﮔـﺮﺩﺵ ﮐـﺮﺩﻩ‬

‫ﻓﻀﺎﯼ ﺩﺍﺧﻞ ﺍﺳــﺘﺨﺮ ﺗﺤﺖ ﭘﻮﺷﺶ ﻗﺮﺍﺭ‬

‫ﺑﺎﺷﺪ‪.‬‬

‫ﻣﯽﮔﯿــﺮﺩ ﻭ ﺍﺣﺘﻤﺎﻝ ﺍﯾﺠــﺎﺩ ﻓﻀﺎﯼ ﻣﺮﺩﻩ‬

‫‪‬ﺗﻤﺎﻣﯽ ﺳـﻄﻮﺡ ﻣﺮﺗﺒـﻂ ﺑﺎ ﺧﺎﺭﺝ‬

‫ﻋﻨﻮﺍﻥ ﯾﮏ ﻗﺎﻋﺪﻩ ﺳﺮﺍﻧﮕﺸـﺘﯽ‬ ‫ﻫﻮﺍﯼ ﺭﻓﺖ ﺑﻪ ﺍﺯﺍﯼ ﻫﺮ ﻣﺘﺮ ﻣﺮﺑﻊ‬ ‫ﺍﺯ ﺳـﻄﺢ ﭘﻨﺠﺮﻩ ﺑﺎﯾﺪ ‪55−73m3/‬‬

‫‪) hr‬ﺑـﻪ ﺍﺯﺍﯼ ﻫﺮ ﻓﻮﺕ ﻣﺮﺑﻊ ﺑﯿﻦ‬ ‫‪ (3−5cfm‬ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﺷﻮﺩ‪.‬‬

‫ﭘﯽﻧﻮﺷﺖ‬ ‫‪1. US Olympic Committee‬‬ ‫‪2. Sheet Metal and Air Conditioning‬‬

‫ﺑﻪ ﺣﺪﺍﻗﻞ ﻣﯽﺭﺳــﺪ‪ .‬ﺿﻤﻦ ﺁﻥﮐﻪ ﺍﻟﮕﻮﯼ‬

‫ﯾﮑــﯽ ﺩﯾﮕــﺮ ﺍﺯ ﺭﻭﺵﻫــﺎﯼ ﻣﺘﺪﺍﻭﻝ‬

‫‪Contractors National Associations‬‬

‫ﺟﺮﯾﺎﻥ ﻫﻮﺍ ﺩﺭ ﺍﯾﻦ ﺷــﯿﻮﻩ ﻃﺮﺍﺣﯽ ﮐﺎﻧﺎﻝ‬

‫ﻃﺮﺍﺣــﯽ ﮐﺎﻧﺎﻝ‪ ،‬ﺍﺟﺮﺍﯼ ﺷــﺒﮑﻪ ﮐﺎﻧﺎﻝ ﺩﺭ‬

‫‪3. Noise Criteria‬‬

‫ﻓﻦﮐﻮﯾﻞ ﺻﺒﺎ‪ ،‬ﺑﻬﺘﺮﯾﻦ ﻓﻦﮐﻮﯾﻞ ﺍﯾﺮﺍﻧﯽ ﺩﺭ ﺍﯾﺮﺍﻥ ﻭ ﺧﺎﻭﺭﻣﯿﺎﻧﻪ‬ ‫ﻭ ﺗﻨﻬﺎ ﺭﻗﯿﺐ ﺳﺮﺳﺨﺖ ﻓﻦﮐﻮﯾﻞﻫﺎﯼ ﺍﺭﻭﭘﺎﯾﯽ ﺩﺭ ﺍﯾﺮﺍﻥ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

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‫ﻛﺎﺭﺑﺮﺩﻯ‬

‫ﺍﻧﺘﺨﺎﺏ ﭼﻴﻠﺮﻫﺎﻯ ﺟﺬﺑﻰ‬ ‫ﺑــﺮﺍﯼ ﺍﻧﺘﺨﺎﺏ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﻣﯽﺑﺎﯾﺪ ﻣﻮﺍﺭﺩ ﺯﯾﺮ ﻣﻮﺭﺩ ﺗﺤﻠﯿﻞ ﻭ‬ ‫ﺑﺮﺭﺳﯽ ﻗﺮﺍﺭ ﮔﯿﺮﻧﺪ‪:‬‬

‫ﺗﻌﯿﯿﻦ ﺷــﻮﺩ‪ .‬ﺍﯾﻦ ﻣﻮﺍﺭﺩ ﺷﺎﻣﻞ ﺣﺎﻟﺖ ﺳﯿﺎﻝ ﮔﺮﻡﮐﻨﻨﺪﻩ )ﺑﺨﺎﺭ ﯾﺎ‬ ‫ﻣﺎﯾﻊ(‪ ،‬ﺩﻣﺎ‪ ،‬ﺩﺑﯽ ﻭ ﮔﺮﻣﺎﯼ ﻭﯾﮋﻩ ﻣﯽﺷــﻮﺩ‪ .‬ﻣﻤﮑﻦ ﺍﺳــﺖ ﻣﻨﺒﻊ‬

‫● ﻧﯿﺎﺯﻫﺎﯼ ﺳﺮﻣﺎﯾﺸﯽ ﻭ ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ‬

‫ﮔﺮﻣﺎﯾــﯽ ﺍﺯ ﻧــﻮﻉ ﻣﻮﻟﺪ ﺣﺮﺍﺭﺗﯽ ﺑــﺪﻭﻥ ﻓﺮﺍﯾﻨﺪ ﺑﺎﺯﯾﺎﺑــﯽ ﯾﺎ ﺍﺯ ﻧﻮﻉ‬

‫● ﻧﻮﻉ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﻣﻨﺎﺳﺐ‬

‫ﮔﺮﻣــﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ ﺑﺎﺷــﺪ‪ .‬ﺩﺭ ﻫﺮ ﺩﻭ ﺣﺎﻟــﺖ ﺗﻌﯿﯿﻦ ﻧﻮﻉ‪ ،‬ﮐﻤﯿﺖ‬

‫● ﻧــﻮﻉ ﻣﻨﺎﺑــﻊ ﮔﺮﻣﺎﯾﯽ ﻭ ﻣﺤﺎﺳــﺒﻪ ﮔﺮﻣﺎﯼ ﻗﺎﺑــﻞ ﺑﺎﺯﯾﺎﻓﺖ‬

‫ﻭ ﮐﯿﻔﯿﺖ ﺁﻥ ﺿﺮﻭﺭﯼ ﺍﺳــﺖ‪ .‬ﺩﺭ ﺑﺮﺧﯽ ﻣﻮﺍﺭﺩ ﻧﯿﺰ ﻣﻤﮑﻦ ﺍﺳــﺖ‬

‫)ﭼﻨﺎﻧﭽــﻪ ﺍﻣــﮑﺎﻥ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ ﻭﺟﻮﺩ ﺩﺍﺷــﺘﻪ‬

‫ﻣﻨﺒﻊ ﮔﺮﻣﺎﯾﯽ ﺗﺮﮐﯿﺒﯽ ﺍﺯ ﺳــﯿﺎﻝ ﮔﺮﻡ ﺗﻮﻟﯿﺪ ﺷــﺪﻩ ﺑﺪﻭﻥ ﻓﺮﺍﯾﻨﺪ‬

‫ﺑﺎﺷﺪ‪(.‬‬ ‫● ﺑﺮﺭﺳــﯽ ﺧﺮﻭﺟﯽ ﺳﺮﻣﺎﯾﺸﯽ ﻗﺎﺑﻞ ﺩﺳــﺘﯿﺎﺑﯽ ﺑﺎ ﺗﻮﺟﻪ ﺑﻪ‬ ‫ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ ﻣﻮﺟﻮﺩ ﯾﺎ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ‬ ‫● ﺗﻌﯿﯿــﻦ ﻇﺮﻓﯿﺖ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺑﺮ ﺍﺳــﺎﺱ ﻣﻘــﺪﺍﺭ ﮔﺮﻣﺎﯼ‬

‫ﺑﺎﺯﯾﺎﺑﯽ ﻭ ﺳﯿﺎﻝ ﮔﺮﻡ ﺗﻮﻟﯿﺪ ﺷﺪﻩ ﻧﺎﺷﯽ ﺍﺯ ﻓﺮﺍﯾﻨﺪ ﺑﺎﺯﯾﺎﺑﯽ ﺑﺎﺷﺪ‪.‬‬

‫ﺗﻌﯿﯿﻦ ﻧﻮﻉ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﻣﻨﺎﺳﺐ‬ ‫ﺩﺭ ﺍﻧﺘﺨﺎﺏ ﻭ ﺗﻌﯿﯿﻦ ﻧﻮﻉ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﻋﻮﺍﻣﻞ ﻣﺨﺘﻠﻔﯽ ﻫﻤﭽﻮﻥ‬

‫ﺑﺎﺯﯾﺎﻓﺘﯽ‬ ‫● ﻣﺤﺎﺳﺒﻪ ﺗﺠﻬﯿﺰﺍﺕ ﺩﻓﻊﮐﻨﻨﺪﻩ ﮔﺮﻣﺎ ﻣﺎﻧﻨﺪ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ‬

‫ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ‪ ،‬ﺷﺮﺍﯾﻂ ﺁﺏﻭﻫﻮﺍﯾﯽ‪ ،‬ﻋﻤﺮ ﻣﻔﯿﺪ‪ ،‬ﺳﻬﻮﻟﺖ ﺗﻌﻤﯿﺮ ﻭ‬

‫● ﻣﺤﺎﺳﺒﻪ ﻭ ﺗﻌﯿﯿﻦ ﺍﻧﺮﮊﯼ ﻭ ﺗﻮﺍﻥ ﺍﻟﮑﺘﺮﯾﮑﯽ ﻣﻮﺭﺩ ﻧﯿﺎﺯ‬

‫ﻧﮕﻬﺪﺍﺭﯼ‪ ،‬ﺍﻣﮑﺎﻥ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ ﺗﻠﻒ ﺷﺪﻩ‪ ،‬ﺿﺮﯾﺐ‬

‫● ﺗﻮﺟــﻪ ﺑــﻪ ﺑﺎﺭﻫﺎﯼ ﺟﺰﯾــﯽ ﻭ ﺑﺎﺭﻫﺎﯼ ﻫﻤﺰﻣــﺎﻥ ﺩﺭ ﺯﻣﺎﻥ‬

‫ﮐﺎﺭﺍﯾﯽ ﻭ ﺻﺮﻓﻪﺟﻮﯾﯽ ﺩﺭ ﻣﺼﺮﻑ ﺍﻧﺮﮊﯼ‪ ،‬ﺗﺎﺛﯿﺮﮔﺬﺍﺭ ﻫﺴﺘﻨﺪ‪.‬‬

‫ﺭﺍﻫﺒﺮﯼ‬

‫ﺩﺭ ﺍﻏﻠﺐ ﭘﺮﻭﮊﻩﻫﺎ ﺩﺳﺘﯿﺎﺑﯽ ﺑﻪ ﮔﺰﯾﻨﻪ ﺍﯾﺪﻩﺁﻝ ﮐﻪ ﺩﺭ ﺁﻥ ﺗﻤﺎﻣﯽ‬

‫● ﺑﺮﺭﺳــﯽ ﺑﺮﺧﯽ ﮔﺰﯾﻨﻪﻫــﺎﯼ ﺩﯾﮕﺮ ﻭ ﻣﻘﺎﯾﺴــﻪ ﺁﻥ ﺑﺎ ﮔﺰﯾﻨﻪ‬

‫ﻣﻮﺍﺭﺩ ﯾﺎﺩ ﺷــﺪﻩ ﺩﺭ ﺑﺎﻻﺗﺮﯾﻦ ﻭ ﺑﻬﺘﺮﯾﻦ ﺣﺪ ﺧﻮﺩ ﺑﺎﺷــﻨﺪ‪ ،‬ﺍﻣﺮﯼ‬

‫ﻣﻨﺘﺨﺐ‬

‫ﺭﻭﯾﺎﯾﯽ ﻭ ﻏﯿﺮﻭﺍﻗﻌﯽ ﺍﺳــﺖ ﺍﻣﺎ ﯾﺎﻓﺘــﻦ ﻧﻘﻄﻪﺍﯼ ﮐﻪ ﻣﺤﻞ ﺗﻘﺎﻃﻊ‬

‫ﺗﻌﯿﯿﻦ ﻧﯿﺎﺯﻫﺎﯼ ﺳﺮﻣﺎﯾﺸﯽ ﻭ ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ‬

‫ﻫﻤــﻪ ﺍﯾﻦ ﺧﻄﻮﻁ ﺑﺎﺷــﺪ‪ ،‬ﺑﻪ ﻋﻨﻮﺍﻥ ﻧﻘﻄﻪ ﺑﻬﯿﻨــﻪ ﺍﻣﮑﺎﻥﭘﺬﯾﺮ ﻭ‬

‫ﺗﻌﯿﯿﻦ ﺷــﺮﺍﯾﻂ ﮐﺎﺭ ﺳﯿﺴﺘﻢ ﺑﺮ ﺍﺳــﺎﺱ ﻧﯿﺎﺯﻫﺎﯼ ﺳﺮﻣﺎﯾﺸﯽ‬

‫ﻋﻤﻠﯽ ﺍﺳﺖ‪.‬‬ ‫ﺍﮔﺮﭼﻪ ﻣﻤﮑﻦ ﺍﺳﺖ‪ ،‬ﮔﺰﯾﻨﺸﯽ ﻣﺒﺘﻨﯽ ﺑﺮ ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻦ ﮐﻠﯿﻪ‬

‫ﻣﺒﺘﻨﯽ ﺑﺮ ﻣﺤﺎﺳﺒﺎﺕ ﺑﺎﺭ ﭘﺮﻭﮊﻩ ﺷﺎﻣﻞ ﻣﻮﺍﺭﺩ ﺯﯾﺮ ﺍﺳﺖ‪:‬‬ ‫● ﺩﻣﺎﯼ ﺁﺏ ﺳﺮﺩ ﺧﺮﻭﺟﯽ ﺍﺯ ﭼﯿﻠﺮ ﺑﺮ ﺣﺴﺐ )‪ (oF‬ﯾﺎ )‪(oC‬‬

‫ﻣﺰﺍﯾــﺎ ﻭ ﻣﻌﺎﯾﺐ ﺩﺭ ﺍﻧﻄﺒﺎﻕ ﺑﺎ ﺷــﺮﺍﯾﻂ ﺧــﺎﺹ‪ ،‬ﻣﺘﻀﻤﻦ ﺗﻤﺎﻣﯽ‬

‫● ﺗﻌﯿﯿﻦ ﺍﺧﺘﻼﻑ ﺩﻣﺎ ﺑﯿــﻦ ﺁﺏ ﻭﺭﻭﺩﯼ ﻭ ﺧﺮﻭﺟﯽ ﭼﯿﻠﺮ ﺑﺮ‬

‫ﻋﻮﺍﻣﻞ ﺩﺭ ﻋﺎﻟﯽﺗﺮﯾﻦ ﺳــﻄﺢ ﺧﻮﺩ ﻧﺒﺎﺷﺪ ﺍﻣﺎ ﺑﻪ ﻃﻮﺭ ﻗﻄﻊ ﭼﻨﯿﻦ‬ ‫ﺍﻧﺘﺨﺎﺑــﯽ ﻋﻘﻼﻧﯽ ﻭ ﻣﻨﻄﻘﯽ ﺧﻮﺍﻫــﺪ ﺑﻮﺩ‪ .‬ﻣﻄﻠﻖ ﻧﻤﻮﺩﻥ ﯾﮑﯽ ﺍﺯ‬

‫ﺣﺴﺐ )‪ (oF‬ﯾﺎ )‪(oC‬‬ ‫● ﺗﻌﯿﯿﻦ ﺩﻣــﺎﯼ ﺁﺏ ﻭﺭﻭﺩﯼ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨــﺪﻩ ﺑﻪ ﭼﯿﻠﺮ ﺑﺮ‬

‫ﻋﻮﺍﻣﻞ ﺗﺎﺛﯿﺮﮔﺬﺍﺭ ﻭ ﺑﯽﺗﻮﺟﻬﯽ ﯾﺎ ﺣﺘﺎ ﮐﻢﺗﻮﺟﻬﯽ ﺑﻪ ﺳــﺎﯾﺮ ﻋﻮﺍﻣﻞ‬ ‫ﻋﻮﺍﻗﺐ ﻧﺎﺧﻮﺷﺎﯾﻨﺪﯼ ﺩﺭ ﭘﯽ ﺧﻮﺍﻫﺪ ﺩﺍﺷﺖ‪ .‬ﺍﻟﺒﺘﻪ ﺳﻬﻢ ﻭ ﻣﻘﺪﺍﺭ‬

‫ﺣﺴﺐ )‪ (oF‬ﯾﺎ )‪(oC‬‬ ‫● ﺗﻌﯿﯿﻦ ﺩﻣﺎﯼ ﻣﺮﻃﻮﺏ ﻣﺤﯿﻂ ﺑﺮ ﺣﺴﺐ )‪ (oF‬ﯾﺎ )‪(oC‬‬

‫ﻫﺮ ﯾﮏ ﺍﺯ ﻋﻮﺍﻣﻞ ﯾﺎﺩ ﺷــﺪﻩ ﻧﺴﺒﺖ ﺑﻪ ﺷﺮﺍﯾﻂ ﻣﺘﻔﺎﻭﺕ ﻭ ﻣﺘﻨﻮﻉ‬

‫ﺩﺭ ﻣــﻮﺭﺩ ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ ﻧﯿﺰ ﺑﺎﯾﺪ‪ ،‬ﻧﻮﻉ‪ ،‬ﮐﻤﯿﺖ ﻭ ﮐﯿﻔﯿﺖ ﺁﻥ‬

‫ﺍﺳــﺖ‪ .‬ﺑﻨﺎﺑﺮﺍﯾﻦ ﺩﺭﺳــﺖ ﺍﯾﻦ ﺍﺳــﺖ ﮐﻪ ﻧﻘﻄﻪ ﺑﻬﯿﻨﻪ ﺑﺎ ﺗﻮﺟﻪ ﺑﻪ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﻣﻘﺪﺍﺭ ﺳــﺮﻣﺎﯾﻪﮔﺬﺍﺭﯼ ﺍﻭﻟﯿﻪ‪ ،‬ﻫﺰﯾﻨﻪﻫﺎﯼ ﺩﻭﺭﻩ ﺑﻬﺮﻩﺑﺮﺩﺍﺭﯼ‪ ،‬ﻧﻮﻉ‬

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‫ﮐﻤﯽ ﻭ ﮐﯿﻔﯽ ﻫﺮ‬ ‫ﺩﺧﺎﻟــﺖ ﺩﺍﺩﻥ ﺗﻤﺎﻣﯽ ﻋﻮﺍﻣﻞ ﻭ ﻧﻈﺮ ﺑﻪ ﺳــﻬﻢ ّ‬

‫ﺩﻗﯿﻖ ﺍﺯ ﻣﻨﻈﺮ ﺻﺮﻓﻪ ﺍﻗﺘﺼﺎﺩﯼ ﺍﺳــﺖ‪ .‬ﮔﺎﻫﯽ ﺗﻮﺟﻪ ﮐﻮﺗﻪﺑﯿﻨﺎﻧﻪ‬

‫ﯾﮏ ﺍﺯ ﺁﻥﻫﺎ ﻣﺘﻨﺎﺳﺐ ﺑﺎ ﺷــﺮﺍﯾﻂ ﻣﻮﺟﻮﺩ ﻭ ﻗﺎﺑﻞ ﺣﺼﻮﻝ ﺗﻌﯿﯿﻦ‬

‫ﺑــﻪ ﻣﻮﺿﻮﻋﯽ ﻫﻤﭽﻮﻥ ﺻﺮﻓﻪﺟﻮﯾﯽ ﺩﺭ ﻣﺼــﺮﻑ ﺍﻧﺮﮊﯼ ﻧﻪﺗﻨﻬﺎ ﺑﻪ‬

‫ﺷﻮﺩ‪.‬‬

‫ﺻﺮﻓﻪﺟﻮﯾــﯽ ﻧﻤﯽﺍﻧﺠﺎﻣﺪ‪ ،‬ﺑﻠﮑﻪ ﺑﺎ ﺗﺤﻤﯿﻞ ﺷــﺮﺍﯾﻂ ﻧﺎﻣﻨﺎﺳــﺐ‬

‫ﺩﺭ ﺳﯿﺴــﺘﻢﻫﺎﯼ ﮔﺮﻣﺎﯾﺶ ﻭ ﺳــﺮﻣﺎﯾﺶ ﻣﺮﮐــﺰﯼ‪ ،‬ﻣﻮﺿﻮﻉ‬ ‫ﺗﺎﻣﯿــﻦ ﺳــﺮﻣﺎﯾﺶ ﻭ ﺗﺠﻬﯿﺰﺍﺕ ﻣﺮﺑﻮﻁ ﺑﻪ ﺁﻥ ﺳــﻬﻢ ﻋﻤﺪﻩﺍﯼ ﺭﺍ‬ ‫ﺑﻪ ﺧــﻮﺩ ﺍﺧﺘﺼﺎﺹ ﻣﯽﺩﻫﺪ‪ .‬ﺑﻪ ﻭﯾﮋﻩ ﺩﺭ ﺍﯾــﺮﺍﻥ ﮐﻪ ﺍﻏﻠﺐ ﻧﻘﺎﻁ‬ ‫ﺁﻥ ﻣﻌﺘﺪﻝ ﯾﺎ ﮔﺮﻣﺴﯿﺮﯼ ﻫﺴــﺘﻨﺪ؛ ﻫﺰﯾﻨﻪﻫﺎﯼ ﻣﺮﺑﻮﻁ ﺑﻪ ﺗﺎﻣﯿﻦ‬ ‫ﺳــﺮﻣﺎﯾﺶ ﺑﻪ ﻃﻮﺭ ﻣﻌﻤﻮﻝ ﺑﯿﺸﺘﺮ ﺍﺯ ﻫﺰﯾﻨﻪﻫﺎﯼ ﻣﺮﺑﻮﻁ ﺑﻪ ﺗﺎﻣﯿﻦ‬ ‫ﮔﺮﻣﺎﯾﺶ ﺍﺳــﺖ‪ .‬ﺍﺯ ﻫﻤﯿﻦ ﺭﻭ ﺗﻌﯿﯿﻦ ﻧﻮﻉ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺑﻪ ﻋﻨﻮﺍﻥ‬ ‫ﯾﮑﯽ ﺍﺯ ﺗﺠﻬﯿﺰﺍﺕ ﺗﺎﻣﯿﻦ ﺳﺮﻣﺎﯾﺶ ﻣﺮﮐﺰﯼ ﺍﻫﻤﯿﺖ ﻗﺎﺑﻞ ﺗﻮﺟﻬﯽ‬ ‫ﻣﯽﯾﺎﺑﺪ‪ .‬ﺑﺮ ﻫﻤﯿﻦ ﺍﺳﺎﺱ ﺩﺭ ﺍﻧﺘﺨﺎﺏ ﻭ ﺗﻌﯿﯿﻦ ﻧﻮﻉ ﭼﯿﻠﺮ ﺟﺬﺑﯽ‪،‬‬ ‫ﻣﯽﺗﻮﺍﻥ ﺍﺯ ﺩﻭ ﻧﮕﺮﺵ ﮐﺎﻣﻼ ﻣﺘﻔﺎﻭﺕ ﯾﺎﺩ ﮐﺮﺩ‪.‬‬ ‫ﯾﮏ ﺩﯾﺪﮔﺎﻩ ﻣﺒﺘﻨﯽ ﺑﺮ ﺍﺭﺟﺤﯿﺖ ﻧﻮﻉ ﭼﯿﻠﺮ ﺑﻪ ﺷــﺮﺍﯾﻂ ﺍﺳﺖ‬ ‫ﻭ ﺩﯾﺪﮔﺎﻩ ﺩﻭﻡ ﺑﺮ ﺍﺭﺟﺤﯿﺖ ﺷــﺮﺍﯾﻂ ﻧﺴــﺒﺖ ﺑﻪ ﻧﻮﻉ ﭼﯿﻠﺮ ﺗﺎﮐﯿﺪ‬ ‫ﺩﺍﺭﺩ‪ .‬ﺭﻭﯾﮑﺮﺩ ﺍﻭﻝ ﺑﻪ ﺩﻧﺒﺎﻝ ﺁﻥ ﺍﺳــﺖ ﮐﻪ ﺑﺮ ﺍﺳــﺎﺱ ﺗﻌﯿﯿﻦ ﻧﻮﻉ‬ ‫ﭼﯿﻠﺮ ﺟﺬﺑﯽ‪ ،‬ﺷــﺮﺍﯾﻂ ﺧﺎﺻــﯽ ﺭﺍ ﺑﻪﻭﺟﻮﺩ ﺁﻭﺭﺩ ﻭ ﺭﻭﯾﮑﺮﺩ ﺩﻭﻡ ﺑﺮ‬ ‫ﺍﯾﻦ ﺍﻋﺘﻘﺎﺩ ﺍﺳﺖ ﮐﻪ ﻧﻮﻉ ﭼﯿﻠﺮ ﻣﯽﺑﺎﯾﺪ ﻣﺒﺘﻨﯽ ﺑﺮ ﺷﺮﺍﯾﻂ ﻣﻮﺟﻮﺩ‬ ‫ﺑﺎﺷــﺪ‪ .‬ﺍﮔﺮ ﺑﻪ ﺭﻭﯾﮑﺮﺩ ﺩﻭﻡ‪ ،‬ﺍﯾﺠﺎﺩ ﺷﺮﺍﯾﻂ ﻗﺎﺑﻞ ﺣﺼﻮﻝ ﺭﺍ ﺍﺿﺎﻓﻪ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﮐﻨﯿﻢ‪ .‬ﻣﯽﺗﻮﺍﻧﯿﻢ ﻧﮕﺎﻩ ﺗﻠﻔﯿﻘﯽ ﺩﺭﺳﺘﯽ ﻧﺴﺒﺖ ﺑﻪ ﺗﻌﯿﯿﻦ ﺷﺮﺍﯾﻂ ﻭ‬ ‫ﻧﻮﻉ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺩﺍﺷﺘﻪ ﺑﺎﺷﯿﻢ‪.‬‬

‫ﻣﻮﺟﺐ ﺯﯾﺎﻥ ﻧﯿﺰ ﻣﯽﮔﺮﺩﺩ‪.‬‬

‫ﺗﻌﯿﯿﻦ ﻧﻮﻉ ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ ﻭ ﻣﺤﺎﺳـﺒﻪ ﮔﺮﻣﺎﯼ ﻗﺎﺑﻞ‬ ‫ﺑﺎﺯﯾﺎﻓﺖ‬ ‫ﯾﮑﯽ ﺍﺯ ﻋﻮﺍﻣﻞ ﺗﻌﯿﯿﻦﮐﻨﻨــﺪﻩ ﺩﺭ ﺍﻧﺘﺨﺎﺏ ﭼﯿﻠﺮ ﺟﺬﺑﯽ‪ ،‬ﻧﻮﻉ‬ ‫ﻣﻨﺎﺑــﻊ ﮔﺮﻣﺎﯾﯽ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﺍﺳــﺖ ﻭ ﺩﺭ ﺍﯾﻦ ﻣﯿﺎﻥ ﺗﻮﺟﻪ ﺑﻪ ﺍﻣﮑﺎﻥ‬ ‫ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺗﻠﻔﺎﺕ ﮔﺮﻣﺎﯾﯽ ﺗﺠﻬﯿﺰﺍﺕ ﻭ ﺳﯿﺴﺘﻢﻫﺎﯼ ﺩﯾﮕﺮ ﻧﯿﺰ ﺑﻪ‬ ‫ﻟﺤﺎﻅ ﺻﺮﻓﻪﺟﻮﯾﯽ ﺩﺭ ﻣﺼﺮﻑ ﺍﻧــﺮﮊﯼ ﺟﺎﯾﮕﺎﻩ ﻭﯾﮋﻩﺍﯼ ﺭﺍ ﺑﻪ ﺧﻮﺩ‬ ‫ﺍﺧﺘﺼﺎﺹ ﻣﯽﺩﻫﺪ‪.‬‬ ‫ﻫﻤﺎﻥﮔﻮﻧﻪ ﮐﻪ ﭘﯿﺶ ﺍﺯ ﺍﯾﻦ ﻧﯿﺰ ﺍﺷﺎﺭﻩ ﺷﺪ‪ ،‬ﺗﻌﯿﯿﻦ ﻧﻮﻉ ﻣﻨﺎﺑﻊ‬ ‫ﮔﺮﻣﺎﯾﯽ ﺑﺪﻭﻥ ﺗﻮﺟﻪ ﺑﻪ ﺳــﺎﯾﺮ ﻧﯿﺎﺯﻫﺎﯼ ﭘﺮﻭﮊﻩ ﻭ ﺗﻨﻬﺎ ﺑﺮﺍﺳﺎﺱ ﻧﻮﻉ‬ ‫ﭼﯿﻠــﺮ ﺟﺬﺑﯽ‪ ،‬ﭘﯿﺎﻣﺪﻫﺎﯼ ﭼﻨﺪﺍﻥ ﺧﻮﺷــﺎﯾﻨﺪﯼ ﺑﻪ ﻫﻤﺮﺍﻩ ﻧﺪﺍﺭﺩ‪.‬‬ ‫ﺑﻨﺎﺑﺮﺍﯾﻦ ﺿﺮﻭﺭﯼ ﺍﺳــﺖ ﮐﻪ ﺑﯿــﻦ ﻧﯿﺎﺯﻫﺎﯼ ﺧﺎﺹ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﻭ‬ ‫ﺳــﺎﯾﺮ ﺍﺣﺘﯿﺎﺝﻫﺎﯼ ﯾﮏ ﭘﺮﻭﮊﻩ ﺗﻌﺎﺩﻟﯽ ﻣﻨﻄﻘﯽ ﻭ ﻣﻘﺮﻭﻥ ﺑﻪ ﺻﺮﻓﻪ‬ ‫ﺑﺮﻗﺮﺍﺭ ﺷﻮﺩ‪.‬‬ ‫ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ ﻫﻤﭽﻮﻥ ﺩﯾﮓﻫﺎﯼ ﺑﺨﺎﺭ ﮐﻢﻓﺸﺎﺭ ﻭ ﭘﺮ ﻓﺸﺎﺭ ﯾﺎ‬ ‫ﺁﺏ ﺩﺍﻍ ﻭ ﺁﺏ ﮔﺮﻡ ﮐﻪ ﻗﺮﺍﺭ ﺍﺳﺖ ﺑﺮﺍﯼ ﺗﺎﻣﯿﻦ ﻧﯿﺎﺯﻫﺎﯼ ﮔﺮﻣﺎﯾﺸﯽ‬

‫ﺑﻪ ﻋﻨﻮﺍﻥ ﻣﺜﺎﻝ ﺑﻨﺎ ﺑﻪ ﺩﯾﺪﮔﺎﻩ ﺍﻭﻝ‪ ،‬ﻣﻤﮑﻦ ﺍﺳﺖ ﺩﺭ ﭘﺮﻭﮊﻩﺍﯼ‬

‫ﯾﮏ ﭘﺮﻭﮊﻩ ﯾــﺎ ﻣﺼﺎﺭﻑ ﺻﻨﻌﺘﯽ ﺑﻪ ﮐﺎﺭ ﮔﺮﻓﺘﻪ ﺷــﻮﻧﺪ‪ ،‬ﻣﯽﺗﻮﺍﻧﻨﺪ‬

‫ﺗﻨﻬــﺎ ﺑﻪ ﺩﻟﯿﻞ ﺗﻮﺟﻪ ﺑﻪ ﺿﺮﯾﺐ ﮐﺎﺭﺁﯾﯽ ﺑﯿﺸــﺘﺮ‪ ،‬ﭼﯿﻠﺮ ﺩﻭ ﺍﺛﺮﻩ ﺑﻪ‬

‫ﻣﺒﻨﺎﯼ ﻣﻨﺎﺳــﺒﯽ ﺑﺮﺍﯼ ﺍﻧﺘﺨﺎﺏ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺑﺎﺷــﻨﺪ ﻭ ﺑﻪ ﻣﺴﯿﺮ‬

‫ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﯾﮏﺍﺛﺮﻩ ﺗﺮﺟﯿﺢ ﺩﺍﺩﻩ ﺷﻮﺩ‪ .‬ﺑﺎ ﻣﺤﻮﺭ ﻗﺮﺍﺭ ﮔﺮﻓﺘﻦ ﺍﯾﻦ‬

‫ﮔﺰﯾﻨﺶ ﺟﻬﺖ ﺩﻫﻨﺪ‪ .‬ﺩﺭ ﺍﯾﻦ ﺻﻮﺭﺕ ﻣﯽﺑﺎﯾﺪ ﺑﺎﺭ ﮔﺮﻣﺎﯾﺸﯽ ﻣﻮﺭﺩ‬

‫ﮔﺰﯾﻨﻪ ﻭ ﺑﺪﻭﻥ ﺗﻮﺟﻪ ﺑﻪ ﺳــﺎﯾﺮ ﺷــﺮﺍﯾﻂ ﺣﺎﮐﻢ‪ ،‬ﻧﺎﮔﺰﯾﺮ ﺑﻪ ﺩﺭ ﻧﻈﺮ‬

‫ﻧﯿﺎﺯ ﭼﯿﻠﺮ ﺩﺭ ﺗﻌﯿﯿﻦ ﻇﺮﻓﯿﺖ ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ ﺗﺎﺛﯿﺮ ﺩﺍﺩﻩ ﺷــﻮﺩ‪ .‬ﺩﺭ‬

‫ﮔﺮﻓﺘﻦ ﺗﻤﻬﯿﺪﺍﺕ ﻭ ﺷﺮﺍﯾﻂ ﻭﯾﮋﻩﺍﯼ ﺧﻮﺍﻫﯿﻢ ﺷﺪ‪ .‬ﺑﺎ ﺍﯾﻦ ﺍﻧﺘﺨﺎﺏ‪،‬‬

‫ﺍﯾﻦﮔﻮﻧﻪ ﭘﺮﻭﮊﻩﻫﺎ‪ ،‬ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ ﻧﻪ ﺑﺮ ﺍﺳــﺎﺱ ﻧﻮﻉ ﭼﯿﻠﺮ ﺟﺬﺑﯽ‪،‬‬

‫ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺩﯾﮓ ﺑﺨﺎﺭ ﭘﺮﻓﺸــﺎﺭ ﺑﻪ ﻫﻤﺮﺍﻩ ﺳﺎﯾﺮ ﺗﺠﻬﯿﺰﺍﺕ ﻣﻮﺭﺩ‬

‫ﺑﻠﮑﻪ ﺑﺮ ﺍﺳﺎﺱ ﺿﺮﻭﺭﺕﻫﺎﯼ ﺩﯾﮕﺮﯼ ﻫﻤﭽﻮﻥ ﻧﯿﺎﺯﻫﺎﯼ ﮔﺮﻣﺎﯾﺸﯽ‬

‫ﻧﯿﺎﺯ ﺑﻪ ﺧﻮﺩﯼ ﺧﻮﺩ ﺍﺟﺒﺎﺭﯼ ﻣﯽﺷــﻮﺩ ﻭ ﺣﺎﻝ ﺁﻧﮑﻪ ﻣﻤﮑﻦ ﺍﺳﺖ‬

‫ﯾﺎ ﺻﻨﻌﺘﯽ ﺗﻌﯿﯿﻦ ﻣﯽﺷــﻮﻧﺪ‪ .‬ﺑﺎ ﺍﯾﻦ ﺷــﺮﺍﯾﻂ ﮐﺎﻓﯽ ﺍﺳﺖ ﭘﺲ ﺍﺯ‬

‫ﺩﺭ ﭘــﺮﻭﮊﻩ ﻣﻔﺮﻭﺽ ﻫﯿﭻ ﯾﮏ ﺍﺯ ﻗﺴــﻤﺖﻫﺎ ﻭ ﺗﺠﻬﯿﺰﺍﺕ ﻧﯿﺎﺯﻣﻨﺪ‬

‫ﺍﻧﺘﺨﺎﺏ ﻧﻮﻉ ﭼﯿﻠﺮ ﻣﻨﺎﺳﺐ ﻭ ﻣﻨﻄﺒﻖ ﺑﺎ ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ‪ ،‬ﻣﻘﺪﺍﺭ ﺑﺎﺭ‬

‫ﺑﺨﺎﺭ ﭘﺮﻓﺸــﺎﺭ ﻧﺒﺎﺷﻨﺪ‪ .‬ﺗﺤﺖ ﺍﯾﻦ ﺷــﺮﺍﯾﻂ‪ ،‬ﺍﮔﺮﭼﻪ ﭼﯿﻠﺮ ﺟﺬﺑﯽ‬

‫ﮔﺮﻣﺎﯾﺸﯽ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﺭﺍ ﺍﺯ ﮐﺎﺗﻮﻟﻮﮒ ﮐﺎﺭﺧﺎﻧﺠﺎﺕ ﺳﺎﺯﻧﺪﻩ ﺍﺳﺘﺨﺮﺍﺝ‬

‫ﺩﻭ ﺍﺛــﺮﻩ ﺩﺭ ﻣﻘﺎﯾﺴــﻪ ﺑﺎ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﯾﮏﺍﺛــﺮﻩ ﺑﺎ ﺗﻮﺟﻪ ﺑﻪ ﺿﺮﯾﺐ‬

‫ﻧﻤــﻮﺩﻩ ﻭ ﺩﺭ ﺻﻮﺭﺕ ﻟﺰﻭﻡ ﻇﺮﻓﯿﺖ ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ ﺭﺍ ﻣﺘﻨﺎﺳــﺐ ﺑﺎ‬

‫ﮐﺎﺭﺍﯾﯽ ﺑﯿﺸﺘﺮ ﻣﯽﺗﻮﺍﻧﺪ ﺍﻣﺘﯿﺎﺯ ﺻﺮﻓﻪﺟﻮﯾﯽ ﺩﺭ ﻣﺼﺮﻑ ﺍﻧﺮﮊﯼ ﺭﺍ ﺑﻪ‬

‫ﻇﺮﻓﯿﺖ ﺳﺮﻣﺎﯾﺸﯽ ﭼﯿﻠﺮ ﺍﺭﺗﻘﺎ ﺩﻫﯿﻢ‪.‬‬

‫ﻫﻤﺮﺍﻩ ﺩﺍﺷﺘﻪ ﺑﺎﺷــﺪ؛ ﺍﻣﺎ ﺩﺭ ﻋﯿﻦ ﺣﺎﻝ ﭼﻨﯿﻦ ﺍﻧﺘﺨﺎﺑﯽ ﻣﻌﺎﯾﺒﯽ‬

‫ﺍﻣــﺎ ﺩﺭ ﭘﺮﻭﮊﻩﻫﺎﯾﯽ ﮐﻪ ﺍﻣﮑﺎﻥ ﺑﺎﺯﯾﺎﻓﺖ ﮔﺮﻣﺎ ﺍﺯ ﻣﻨﺎﺑﻊ ﻣﺨﺘﻠﻒ‬

‫ﻫﻤﭽﻮﻥ‪ ،‬ﺍﻓﺰﺍﯾﺶ ﺳﺮﻣﺎﯾﻪﮔﺬﺍﺭﯼ ﺍﻭﻟﯿﻪ‪ ،‬ﺍﻓﺰﺍﯾﺶ ﻫﺰﯾﻨﻪﻫﺎﯼ ﺩﻭﺭﻩ‬

‫ﻭﺟﻮﺩ ﺩﺍﺭﺩ ﻣﯽﺑﺎﯾﺪ ﻣﻘﺪﺍﺭ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ ﺭﺍ ﻣﺤﺎﺳﺒﻪ ﻭ ﭼﮕﻮﻧﮕﯽ‬

‫ﺭﺍﻫﺒﺮﯼ‪ ،‬ﺍﻓﺰﺍﯾﺶ ﻣﺸــﮑﻼﺕ ﺗﻌﻤﯿﺮ ﻭ ﻧﮕﻬــﺪﺍﺭﯼ ﻭ ﮐﺎﻫﺶ ﻋﻤﺮ‬

‫ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺁﻥ ﺭﺍ ﺑﻪ ﻃﻮﺭ ﻣﺴﺘﻘﯿﻢ ﯾﺎ ﻏﯿﺮﻣﺴﺘﻘﯿﻢ )ﺗﻮﻟﯿﺪ ﺳﯿﺎﻝ‬

‫ﻣﻔﯿﺪ ﺳﯿﺴــﺘﻢ ﺭﺍ ﺑﻪ ﻫﻤﺮﺍﻩ ﺧﻮﺍﻫﺪ ﺩﺍﺷﺖ‪ .‬ﻣﻘﺎﯾﺴﻪ ﺑﯿﻦ ﻣﺰﯾﺖ‬

‫ﮔﺮﻡ ﻭﺍﺳﻄﻪ( ﺭﺍ ﺗﻌﯿﯿﻦ ﮐﻨﯿﻢ‪.‬‬

‫ﺿﺮﯾﺐ ﮐﺎﺭﺍﯾﯽ ﺑﻬﺘﺮ ﻭ ﻫﺮ ﯾﮏ ﺍﺯ ﻣﻌﺎﯾﺐ ﯾﺎﺩ ﺷﺪﻩ ﻣﺴﺘﻠﺰﻡ ﺑﺮﺭﺳﯽ‬

‫ﻣﻘــﺪﺍﺭ ﮔﺮﻣﺎﯼ ﻗﺎﺑــﻞ ﺑﺎﺯﯾﺎﻓﺖ ﺍﺯ ﻣﻨﺎﺑــﻊ ﮔﺮﻣﺎﯾﯽ ﻣﺨﺘﻠﻒ ﺑﻪ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺻﻔﺤﻪ ‪ / 21‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺷــﮑﻞ ﮔﺎﺯﻫﺎﯼ ﺩﺍﻍ ﺧﺮﻭﺟــﯽ ﺍﺯ ﻣﻮﺗﻮﺭﻫﺎﯼ ﺍﺣﺘﺮﺍﻗــﯽ ﯾﺎ ﺍﻧﻮﺍﻉ‬

‫ﻫﺮ ﮐﯿﻠﻮﻭﺍﺕ )‪ (KW‬ﺗﻮﻟﯿﺪ ﺍﻟﮑﺘﺮﯾﺴﯿﺘﻪ ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺖ‪.‬‬

‫ﮐﻮﺭﻩﻫــﺎﯼ ﺫﻭﺏ ﯾﺎ ﺑﺨﺎﺭ ﺧﺮﻭﺟــﯽ ﺍﺯ ﺗﻮﺭﺑﯿﻦﻫﺎ ﻭ ﯾﺎ ﮔﺮﻣﺎﯼ ﻗﺎﺑﻞ‬

‫ﺑﺮﺍﯼ ﮊﻧﺮﺍﺗﻮﺭﻫﺎﯼ ﺍﺣﺘﺮﺍﻗﯽ ﺳﯿﻠﻨﺪﺭ ﭘﯿﺴﺘﻮﻧﯽ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ‬

‫ﺑﺎﺯﯾﺎﻓﺖ ﻧﺎﺷــﯽ ﺍﺯ ﺣــﺮﺍﺭﺕ ﺑﺪﻧﻪ ﺗﺠﻬﯿــﺰﺍﺕ ﻣﺨﺘﻠﻒ ﺭﺍ ﻣﯽﺗﻮﺍﻥ‬

‫ﻧﺎﺷــﯽ ﺍﺯ ﮔﺎﺯﻫﺎﯼ ﺧﺮﻭﺟﯽ ﺩﻭﺩﮐﺶ ﺗﻘﺮﯾﺒﺎ ﺑﯿﻦ ‪ 1.3‬ﺗﺎ ‪1.4 lb/h‬‬

‫ﺍﺯ ﻃﺮﯾﻖ ﺭﻭﺍﺑﻂ ﻣﺤﺎﺳــﺒﺎﺗﯽ ﮐﻪ ﺩﺭ ﺍﺩﺍﻣــﻪ ﻣﯽﺁﯾﺪ‪ ،‬ﺗﻌﯿﯿﻦ ﻧﻤﻮﺩ‬

‫ﺑﺨــﺎﺭ )‪ (0.59-0.64 kg/hr‬ﺑــﻪ ﺍﺯﺍﯼ ﺗﻮﻟﯿﺪ ﯾــﮏ ﮐﯿﻠﻮﻭﺍﺕ )‪(kw‬‬

‫ﻭ ﺑﺮﺍﺳــﺎﺱ ﺁﻥ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﻣﻨﺎﺳــﺐ ﺟﻬﺖ ﺑﻬﺮﻩﺑﺮﺩﺍﺭﯼ ﺍﺯ ﺍﯾﻦ‬

‫ﺍﻟﮑﺘﺮﯾﺴﯿﺘﻪ ﻣﻨﻈﻮﺭ ﻣﯽﺷﻮﺩ‪.‬‬ ‫ﺩﻣــﺎﯼ ﮔﺎﺯﻫﺎﯼ ﺩﺍﻍ ﺧﺮﻭﺟﯽ ﺍﺯ ﻣﺒــﺪﻝ ﻭ ﺑﺮﺍﯼ ﺟﻠﻮﮔﯿﺮﯼ ﺍﺯ‬

‫ﺗﻠﻔﺎﺕ ﮔﺮﻣﺎﯾﯽ ﺭﺍ ﺍﻧﺘﺨﺎﺏ ﮐﺮﺩ‪.‬‬ ‫ﺩﺭ ﺑﺮﺧﯽ ﻣﻮﺍﺭﺩ ﻣﻤﮑﻦ ﺍﺳــﺖ ﺑﯿﻦ ﻣﻨﺎﺑﻊ ﮔﺮﻣﺎﯾﯽ ﻣﺴﺘﻘﻞ ﻭ‬ ‫ﮔﺮﻣﺎﯼ ﺭﺍ ﺑﺎﺯﯾﺎﻓﺘﯽ ﺗﺮﮐﯿﺒﯽ ﻣﺘﺠﺎﻧﺲ ﻭ ﮐﺎﺭﺁﻣﺪ ﺑﻪ ﻭﺟﻮﺩ ﺁﻭﺭﺩ ﮐﻪ‬ ‫ﺑﺮﺭﺳﯽ ﭼﻨﯿﻦ ﻣﻮﺍﺭﺩﯼ ﮐﺎﻣﻼ ﻭﯾﮋﻩ ﺑﻮﺩﻩ ﻭ ﻧﯿﺎﺯﻣﻨﺪ ﺑﺮﺭﺳﯽ ﺷﺮﺍﯾﻂ‬ ‫ﺧﺎﺹ ﺍﺳﺖ‪.‬‬

‫ﺗﻘﻄﯿــﺮ ﺑﺨﺎﺭ ﺁﺏ ﻣﻮﺟــﻮﺩ ﺩﺭ ﺁﻥ ﺑﺎﯾﺪ ﺑﯿــﺶ ﺍﺯ ‪(149oC) 300oF‬‬

‫ﺑﺎﺷﺪ‪ .‬ﭼﻨﺎﻧﭽﻪ ﺍﺯ ﺭﺍﺑﻄﻪ )‪ (1‬ﺑﺮﺍﯼ ﺗﻌﯿﯿﻦ ﻣﻘﺪﺍﺭ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ‬ ‫ﺍﺳــﺘﻔﺎﺩﻩ ﮐﻨﯿﻢ‪ ،‬ﻣﯽﺗﻮﺍﻧﯿﻢ ﺑﺮﺍﯼ ﺑﻪ ﺩﺳﺖ ﺁﻭﺭﺩﻥ ﮔﺎﺯ ﺧﺮﻭﺟﯽ ﺍﺯ‬ ‫ﻣﺒﺪﻝ ﻭ ﺑﺮﺍﯼ ﺗﻌﯿﯿﻦ ﮐﻢ ﯾﺎ ﺯﯾﺎﺩ ﺑﻮﺩﻥ ﺁﻥ ﻧﺴﺒﺖ ﺑﻪ ﻣﻘﺪﺍﺭ ﺗﻌﯿﯿﻦ‬ ‫ﺷﺪﻩ ﺍﺯ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﺍﺳﺘﻔﺎﺩﻩ ﮐﻨﯿﻢ‪:‬‬

‫ﻣﺤﺎﺳﺒﻪ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ ﮔﺎﺯﻫﺎﯼ ﺧﺮﻭﺟﯽ ﺩﺍﻍ‬ ‫ﮔﺎﺯﻫــﺎﯼ ﺩﺍﻍ ﺧﺮﻭﺟــﯽ ﺍﺯ ﺗﺠﻬﯿــﺰﺍﺕ ﻭ ﮐﻮﺭﻩﻫــﺎ ﻣﯽﺗﻮﺍﻧﻨﺪ‬

‫)‪( 2‬‬

‫‪ =Tg,l‬ﺩﻣــﺎﯼ ﮔﺎﺯ ﺩﺍﻍ ﻣﻨﺒــﻊ ﮔﺮﻣﺎﯾﯽ ﮐــﻪ ﺍﺯ ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ‬

‫ﺑﻪ ﺻﻮﺭﺕ ﻣﺴــﺘﻘﯿﻢ ﻭ ﻏﯿﺮﻣﺴــﺘﻘﯿﻢ ﻣﻮﺭﺩ ﺍﺳــﺘﻔﺎﺩﻩ ﭼﯿﻠﺮﻫﺎﯼ‬ ‫ﺟﺬﺑــﯽ ﻗﺮﺍﺭ ﮔﯿﺮﻧﺪ ﺍﻣﺎ ﺍﺯ ﺁﻧﺠﺎ ﮐﻪ ﮔﺎﺯﻫﺎﯼ ﺩﺍﻍ ﺧﺮﻭﺟﯽ ﺷــﺎﻣﻞ‬

‫ﺧﺎﺭﺝ ﻣﯽﺷﻮﺩ‪F ( C) ،‬‬ ‫‪o‬‬

‫‪ =Tg,e‬ﺩﻣﺎﯼ ﮔﺎﺯ ﺩﺍﻍ ﻣﻨﺒﻊ ﮔﺮﻣﺎﯾﯽ ﮐﻪ ﺑﻪ ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﻭﺍﺭﺩ‬

‫ﺗﺮﮐﯿﺒﺎﺕ ﺷﯿﻤﯿﺎﯾﯽ ﻣﺨﺘﻠﻔﯽ ﻫﺴــﺘﻨﺪ ﺍﺯ ﮔﺮﻣﺎﯼ ﺁﻥﻫﺎ ﺑﻪﺻﻮﺭﺕ‬ ‫ﻏﯿﺮﻣﺴﺘﻘﯿﻢ ﺍﺳــﺘﻔﺎﺩﻩ ﻣﯽﺷــﻮﺩ‪ .‬ﺩﺭ ﺍﯾﻦ ﺣﺎﻟﺖ ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ‬

‫‪o‬‬

‫ﻣﯽﺷﻮﺩ‪F ( C) ،‬‬ ‫‪o‬‬

‫‪o‬‬

‫‪ =qr‬ﻣﻘﺪﺍﺭ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ‪(KWT) Btu/h ،‬‬

‫ﻣﯽﺗﻮﺍﻧﺪ ﺑﺎ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﮔﺮﻣﺎﯼ ﺧﺮﻭﺟــﯽ‪ ،‬ﺁﺏ ﮔﺮﻡ ﯾﺎ ﺣﺘﺎ ﺑﺨﺎﺭ‬

‫‪ =Cp,g‬ﮔﺮﻣﺎﯼ ﻭﯾﮋﻩ ﮔﺎﺯ ﺩﺍﻍ ﺩﺭ ﺩﺍﻣﻨﻪ ‪0.242 - 0.254 Btu/h.‬‬

‫ﺗﻮﻟﯿﺪ ﮐﻨﺪ‪ .‬ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﻣﻘﺪﺍﺭ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ ﺭﺍ ﺗﻌﯿﯿﻦ ﻣﯽﮐﻨﺪ‪:‬‬

‫)‪F (1.01- 1.06 kw,s/kg.oC‬‬

‫‪o‬‬

‫= ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺖ ﺷﺪﻩ‪(KWT) Btu/h ،‬‬

‫‪ =ηeff‬ﺿﺮﯾــﺐ ﺗﺼﺤﯿﺢ ﺑﺮﺍﯼ ﺩﻣﺎﯼ ﺁﺏ ﻭ ﺗﺎﺛﯿﺮ ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ‬ ‫ﺑﺮﺍﺳﺎﺱ ﺩﻣﺎﯼ ﮔﺎﺯ ﺧﺮﻭﺟﯽ ﻣﻄﺎﺑﻖ ﺟﺪﻭﻝ )‪(1‬‬ ‫‪ =Cp,g‬ﮔﺮﻣــﺎﯼ ﻭﯾــﮋﻩ ﮔﺎﺯ ﺩﺍﻍ ﺧﺮﻭﺟﯽ ﺩﺭ ﺩﺍﻣﻨــﻪ ‪ 0.242‬ﺗﺎ‬ ‫‪ 0.254Btu/LboF‬ﯾﺎ )‪(1.01-1.06KJT/kg.oC‬‬

‫ﭼﻨﺎﻧﭽﻪ ﺩﻣﺎﯼ ﮔﺎﺯ ﺧﺮﻭﺟﯽ ﺍﺯ ﻣﺒﺪﻝ ﮐﻤﺘﺮ ﺍﺯ ‪(149oC) 300oF‬‬

‫ﺑﺎﺷﺪ‪ ،‬ﺑﺎﯾﺪ ﻣﺤﺎﺳﺒﺎﺕ ﺑﺮ ﺍﺳﺎﺱ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﺗﮑﺮﺍﺭ ﺷﻮﺩ‪:‬‬

‫ ‪ Tg,e Tg,l Cp,g mg‬‬

‫)‪( 3‬‬

‫‪qr‬‬

‫ﻣﺤﺎﺳﺒﻪ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ ﻣﺎﯾﻊ ﺩﺍﻍ‬

‫‪ =mg‬ﺩﺑﯽ ﺟﺮﻣﯽ ﮔﺎﺯ ﺩﺍﻍ ﺧﺮﻭﺟﯽ‪(kg/s) lb/h ،‬‬

‫ﭼﻨﺎﻧﭽﻪ ﻋﻤﻠﮑﺮﺩ ﺩﺳﺘﮕﺎﻫﯽ ﻣﻨﺠﺮ ﺑﻪ ﺗﻮﻟﯿﺪ ﻣﺎﯾﻊ ﺩﺍﻍ ﺷﻮﺩ‪،‬‬

‫‪ =Tin,g‬ﺩﻣﺎﯼ ﮔﺎﺯ ﺩﺍﻍ ﻭﺭﻭﺩﯼ ﺑﻪ ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ‪F (oC) ،‬‬

‫‪o‬‬

‫ﻣﯽﺗﻮﺍﻥ ﺍﺯ ﮔﺮﻣﺎﯼ ﺁﻥ ﻧﯿﺰ ﻫﻤﭽﻮﻥ ﮔﺎﺯﻫﺎﯼ ﺩﺍﻍ ﺍﺳــﺘﻔﺎﺩﻩ ﻧﻤﻮﺩ‪.‬‬

‫‪ =Tm,W‬ﺩﻣــﺎﯼ ﻣﯿﺎﻧﮕﯿــﻦ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘــﯽ )ﺁﺏ( ﺩﺭ ﻣﺒﺪﻝ‬ ‫ﺣﺮﺍﺭﺗﯽ )ﯾﺎ ﺩﻣﺎﯼ ﺑﺨﺎﺭ ﺍﺷﺒﺎﻉ ﺷﺪﻩ ﺩﺭ ﻣﺒﺪﻝ(‪F (oC) ،‬‬

‫‪o‬‬

‫ﭼﻨﺎﻧﭽﻪ ﺑﺮﺍﯼ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﮔﺎﺯ ﺩﺍﻍ ﺧﺮﻭﺟﯽ ﻭ ﺑﺎﺯﯾﺎﻓﺖ ﮔﺮﻣﺎﯼ‬ ‫ﺁﻥ ﺍﺯ ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﺍﺳﺘﻔﺎﺩﻩ ﻧﺸﻮﺩ‪ ،‬ﺿﺮﯾﺐ ‪ ηeff‬ﺑﺮﺍﺑﺮ ‪ 1.0‬ﻭ ‪Tm,W‬‬

‫ﻧﯿﺰ ﺑﺮﺍﺑﺮ ﺩﻣﺎﯼ ﮔﺎﺯ ﺧﺮﻭﺟﯽ ﺩﺭﻧﻈﺮ ﮔﺮﻓﺘﻪ ﻣﯽﺷﻮﺩ‪.‬‬ ‫ﺑﺮﺍﯼ ﺗﻌﯿﯿﻦ ‪ Tm,W‬ﺩﺭ ﺻﻮﺭﺗﯽ ﮐﻪ ﺳــﯿﺎﻝ ﺗﻮﻟﯿﺪ ﺷــﺪﻩ ﺑﺨﺎﺭ‬ ‫ﺑﺎﺷــﺪ‪ ،‬ﻣﯽﺗﻮﺍﻥ ﺍﺯ ﺟﺪﻭﻝ )‪ (2‬ﺑﺮﺍﯼ ﺑﻪ ﺩﺳﺖ ﺁﻭﺭﺩﻥ ﻓﺸﺎﺭ ﺑﺨﺎﺭ‬ ‫ﻣﻌﺎﺩﻝ ﺍﺳﺘﻔﺎﺩﻩ ﻧﻤﻮﺩ‪.‬‬ ‫ﺑــﻪ ﺻﻮﺭﺕ ﺗﺨﻤﯿﻨﯽ ﺑﺮﺍﯼ ﺗﻮﺭﺑﯿﻦﻫــﺎﯼ ﮔﺎﺯ ﻣﯽﺗﻮﺍﻥ ﮔﺮﻣﺎﯼ‬

‫ﺟﺪﻭﻝ )‪ (1‬ﺿﺮﯾﺐ ﺗﺼﺤﯿﺢ ﺁﺏ ﺑﺮﺍﯼ ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ ﮔﺎﺯﻫﺎﯼ ﺩﺍﻍ‬ ‫ﺧﺮﻭﺟﯽ‬ ‫ﻣﯿﺎﻧﮕﯿﻦ‬ ‫‪ηeff‬‬

‫ﺣﺪﺍﮐﺜﺮ ﺟﺮﯾﺎﻥ ﮔﺎﺯ‬ ‫‪lb/lh‬‬ ‫)‪(kg/s‬‬

‫ﺣﺪﺍﻗﻞ ﺟﺮﯾﺎﻥ ﮔﺎﺯ‬ ‫‪lb/h‬‬

‫‪0.84‬‬

‫‪20,000‬‬

‫‪5000‬‬

‫)‪(2.52‬‬

‫)‪(063.‬‬

‫‪90,000‬‬

‫‪15,000‬‬

‫)‪(11.34‬‬

‫)‪(1.89‬‬

‫‪0.93‬‬

‫ﺑﺎﺯﯾﺎﻓﺘﯽ ﺭﺍ ﺑﺮﺍﺳــﺎﺱ ‪ 11‬ﺗﺎ ‪ 13 lb/h‬ﺑﺨﺎﺭ )‪ (5-5.9kg/hr‬ﺑﻪ ﺍﺯﺍﯼ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫)‪(kg/s‬‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫)‪(1‬‬

‫‪ηeff‬‬

‫‪ =mg‬ﺩﺑﯽ ﺟﺮﻣﯽ ﮔﺎﺯ ﺩﺍﻍ‪(kg/s) lb/h ،‬‬

‫ﺻﻔﺤﻪ ‪ / 22‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺟﺪﻭﻝ )‪ (2‬ﻓﺸﺎﺭ ﺑﺨﺎﺭ ﻣﻌﺎﺩﻝ ﺑﺮﺍﯼ ﺁﺏﮔﺮﻡ‬ ‫ﺩﻣﺎﯼ ﺧﺮﻭﺟﯽ )‪F (oC‬‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫‪o‬‬

‫‪340‬‬

‫‪330‬‬

‫‪320‬‬

‫‪310‬‬

‫‪300‬‬

‫‪290‬‬

‫‪240‬‬

‫‪230‬‬

‫‪220‬‬

‫‪210‬‬

‫ﺩﻣﺎﯼ‬ ‫ﻭﺭﻭﺩﯼ‬

‫)‪(171‬‬

‫)‪(166‬‬

‫)‪(160‬‬

‫)‪(154‬‬

‫)‪(149‬‬

‫)‪(143‬‬

‫)‪(116‬‬

‫)‪(110‬‬

‫)‪(104‬‬

‫)‪(99‬‬

‫)‪F (oC‬‬

‫‪9.0‬‬

‫‪6.4‬‬

‫‪4.1‬‬

‫‪240‬‬

‫)‪(163‬‬

‫)‪(146‬‬

‫)‪(130‬‬

‫)‪(116‬‬

‫‪13.0‬‬

‫‪10.2‬‬

‫‪7.9‬‬

‫‪5.4‬‬

‫‪250‬‬

‫)‪(194‬‬

‫)‪(172‬‬

‫)‪(156‬‬

‫)‪(139‬‬

‫)‪(121‬‬

‫‪14.0‬‬

‫‪10.5‬‬

‫‪8.3‬‬

‫‪5.9‬‬

‫‪260‬‬

‫)‪(200‬‬

‫)‪(174‬‬

‫)‪(159‬‬

‫)‪(142‬‬

‫)‪(127‬‬

‫‪14.0‬‬

‫‪10.7‬‬

‫‪8.5‬‬

‫‪6.4‬‬

‫‪270‬‬

‫)‪(200‬‬

‫)‪(175‬‬

‫)‪(160‬‬

‫)‪(146‬‬

‫)‪(132‬‬

‫‪o‬‬

‫ﭼﯿﻠﺮ ﯾﮏﺍﺛﺮﻩ‬

‫‪43‬‬

‫‪310‬‬

‫)‪(398‬‬

‫)‪(154‬‬

‫‪55‬‬

‫‪46‬‬

‫‪320‬‬

‫)‪(481‬‬

‫)‪(419‬‬

‫)‪(160‬‬

‫‪65‬‬

‫‪57‬‬

‫‪50‬‬

‫‪330‬‬

‫)‪(550‬‬

‫)‪(494‬‬

‫)‪(446‬‬

‫)‪(166‬‬

‫)‪182OC (360OF‬‬

‫‪75‬‬

‫‪68‬‬

‫‪59‬‬

‫‪52‬‬

‫‪340‬‬

‫)‪160OC (320OF‬‬

‫)‪(618‬‬

‫)‪(570‬‬

‫)‪(508‬‬

‫)‪(460‬‬

‫)‪(171‬‬

‫‪88‬‬

‫‪78‬‬

‫‪70‬‬

‫‪60‬‬

‫‪54‬‬

‫‪350‬‬

‫)‪(708‬‬

‫)‪(639‬‬

‫)‪(584‬‬

‫)‪(515‬‬

‫)‪(474‬‬

‫)‪(177‬‬

‫‪93‬‬ ‫)‪(743‬‬

‫‪80‬‬ ‫)‪(653‬‬

‫‪72‬‬

‫‪62‬‬

‫‪56‬‬

‫‪360‬‬

‫)‪(598‬‬

‫)‪(529‬‬

‫)‪(487‬‬

‫)‪(182‬‬

‫‪115‬‬

‫‪97‬‬

‫‪83‬‬

‫‪73‬‬

‫‪64‬‬

‫‪58‬‬

‫‪370‬‬

‫)‪(894‬‬

‫)‪(770‬‬

‫)‪(674‬‬

‫)‪(605‬‬

‫)‪(543‬‬

‫)‪(501‬‬

‫)‪(188‬‬

‫‪120‬‬

‫‪100‬‬

‫‪86‬‬

‫‪75‬‬

‫‪65‬‬

‫‪59‬‬

‫‪380‬‬

‫)‪(929‬‬

‫)‪(791‬‬

‫)‪(694‬‬

‫)‪(618‬‬

‫)‪(550‬‬

‫)‪(508‬‬

‫)‪(193‬‬

‫‪103‬‬

‫‪88‬‬

‫‪76‬‬

‫‪67‬‬

‫‪60‬‬

‫‪390‬‬

‫)‪(812‬‬

‫)‪(708‬‬

‫)‪(625‬‬

‫)‪(563‬‬

‫)‪(515‬‬

‫)‪(199‬‬

‫‪106‬‬

‫‪90‬‬

‫‪78‬‬

‫‪68‬‬

‫‪62‬‬

‫‪400‬‬

‫)‪(832‬‬

‫)‪(722‬‬

‫)‪(639‬‬

‫)‪(570‬‬

‫)‪(529‬‬

‫)‪(204‬‬

‫ﺩﺭ ﺍﯾﻦ ﺷــﯿﻮﻩ ﻧﯿﺰ ﻣﯽﺗﻮﺍﻥ ﺑﺮﺍﯼ ﺗﻮﻟﯿﺪ ﺁﺏ ﮔﺮﻡ ﺍﺯ ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ‬

‫ﭼﯿﻠﺮ ﺩﻭ ﺍﺛﺮﻩ‬

‫ﻣﺜﺎﻝ‪:‬‬ ‫ﻭﺭﻭﺩﯼ‪:‬‬

‫ﺧﺮﻭﺟﯽ‪:‬‬

‫ﻓﺸﺎﺭ ﻣﻌﺎﺩﻝ ﺑﺨﺎﺭ‪:‬‬ ‫)‪80psig (653kpa‬‬

‫‪ (4.184‬ﺑﺮﺍﯼ ﺁﺏ‬

‫ﻣﻨﺎﺳــﺐ ﺍﺳــﺘﻔﺎﺩﻩ ﻧﻤﻮﺩ‪ .‬ﻣﻘﺪﺍﺭ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ ﺍﺯ ﻣﺎﯾﻊ ﺩﺍﻍ ﺍﺯ‬

‫‪ =mfl‬ﺩﺑﯽ ﺟﺮﻣﯽ ﻣﺎﯾﻊ ﺩﺍﻍ‪(kg/s) lb/h ،‬‬

‫ﻃﺮﯾﻖ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﺗﻌﯿﯿﻦ ﻣﯽﺷﻮﺩ‪:‬‬

‫‪ =T1‬ﺩﻣﺎﯼ ﻣﺎﯾﻊ ﺩﺍﻍ ﻭﺭﻭﺩﯼ ﺑﻪ ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ‪F ( C) ،‬‬

‫)‪(4‬‬

‫‪ =T2‬ﺩﻣﺎﯼ ﻣﺎﯾﻊ ﺩﺍﻍ ﺧﺮﻭﺟﯽ ﺍﺯ ﻣﺒﺪﻝ ﺣﺮﺍﺭﺗﯽ‪F ( C) ،‬‬

‫‪o‬‬

‫‪o‬‬

‫‪o‬‬ ‫‪o‬‬

‫ﺩﺭ ﺻــﻮﺭﺕ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺭﺍﺑﻄــﻪ ﻓــﻮﻕ‪ ،‬ﺍﺧﺘــﻼﻑ‬

‫‪ =qr‬ﻣﻘﺪﺍﺭ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ ‪(KWT) Btu/h‬‬ ‫‪ =Cp,fl‬ﮔﺮﻣــﺎﯼ ﻭﯾﮋﻩ ﻣﺎﯾﻊ ﺩﺍﻍ‪kw,s/kg. C) 1.00 Btu/h.oF ،‬‬ ‫‪o‬‬

‫ﺩﻣــﺎﯼ ﺁﺏ ﺭﻓــﺖ ﻭ ﺑﺮﮔﺸــﺖ ﮊﻧﺮﺍﺗــﻮﺭ ﭼﯿﻠــﺮ ﺟﺬﺑــﯽ‬ ‫‪ (5.5 C) 10 F‬ﺩﺭﻧﻈﺮ ﮔﺮﻓﺘﻪ ﻣﯽﺷﻮﺩ‪.‬‬ ‫‪o‬‬

‫‪o‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺻﻔﺤﻪ ‪ / 23‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫‪ =hf‬ﺍﻧﺘﺎﻟﭙﯽ ﺑﺨﺎﺭ ﺍﺷــﺒﺎﻉ ﺩﺭ ﻓﺸــﺎﺭ ﻣﺮﺑﻮﻃﻪ‪.s/kg) Btu/lb ،‬‬

‫ﻣﺤﺎﺳﺒﻪ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ ﺍﺯ ﺑﺪﻧﻪ ﺗﺠﻬﯿﺰﺍﺕ‬ ‫ﻣﻘﺪﺍﺭ ﮔﺮﻣــﺎﯼ ﻗﺎﺑﻞ ﺑﺎﺯﯾﺎﻓــﺖ ﺍﺯ ﺑﺪﻧﻪ ﻣﻮﺗﻮﺭﻫــﺎﯼ ﺍﺣﺘﺮﺍﻗﯽ‬

‫‪(KWT‬‬ ‫‪ =Ks‬ﺿﺮﯾﺐ ﺗﺼﺤﯿﺢ ﺑﺮﺍﯼ ﻓﻮﻕ ﮔﺮﻡ ﻭ ﻣﺎﺩﻭﻥ ﺳﺮﺩ‪٪100 ،‬‬

‫ﺳﯿﻠﻨﺪﺭ ‪ -‬ﭘﯿﺴﺘﻮﻧﯽ ﺍﺯ ﻃﺮﯾﻖ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﻗﺎﺑﻞ ﻣﺤﺎﺳﺒﻪ ﺍﺳﺖ‪:‬‬

‫ﺍﮔﺮ ﻭﺍﺳﻂ ﮔﺮﻣﺎﯾﯽ ﻧﻬﺎﯾﯽ ﺁﺏ ﺑﺎﺷﺪ ﻣﯽﺗﻮﺍﻥ ﺑﺮﺍﯼ ﺗﻌﯿﯿﻦ ﺩﺑﯽ‬

‫)‪(5‬‬

‫ﺟﺮﻣﯽ ﺍﺯ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﺍﺳﺘﻔﺎﺩﻩ ﻧﻤﻮﺩ‪:‬‬

‫‪ =qj‬ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ‪(KWT) Btu/h ،‬‬ ‫‪ =Mw‬ﺩﺑﯽ ﺟﺮﻣﯽ ﺁﺏ ﮔﺮﺩﺷﯽ ﺩﺭ ﺑﺪﻧﻪ ﻣﻮﺗﻮﺭ‪(kg/s) lb/h ،‬‬

‫)‪(7‬‬

‫‪ =Cp,w‬ﮔﺮﻣﺎﯼ ﻭﯾﮋﻩ ﺁﺏ‪(4.184kw.s/kg.oC) 1.00Btu/h.oF ،‬‬

‫‪ =mw‬ﺩﺑﯽ ﺟﺮﻣﯽ ﺁﺏ‪(kg/s) lb/h ،‬‬

‫‪ =T1‬ﺩﻣﺎﯼ ﺧﺮﻭﺝ ﺍﺯ ﻣﻮﺗﻮﺭ )‪F (oC‬‬

‫‪ =qr‬ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ ﺍﺯ ﺑﺪﻧﻪ ﺗﺠﻬﯿﺰﺍﺕ ﯾﺎ ﮔﺎﺯﻫﺎﯼ ﺩﺍﻍ ﺧﺮﻭﺟﯽ‬

‫‪o‬‬

‫‪ =T2‬ﺩﻣﺎﯼ ﻭﺭﻭﺩﯼ ﻣﻮﺗﻮﺭ )‪F (oC‬‬

‫ﺗﺠﻬﯿﺰﺍﺕ ‪(KWT) Btu/h‬‬

‫‪o‬‬

‫ﺑﺮ ﺍﺳﺎﺱ ﺍﻃﻼﻋﺎﺕ ﺳﺎﺯﻧﺪﮔﺎﻥ‪ ،‬ﺍﺧﺘﻼﻑ ﺩﻣﺎﯼ ﺁﺏ ﻭﺭﻭﺩﯼ ﻭ‬

‫‪ =Cp,w‬ﮔﺮﻣﺎﯼ ﻭﯾﮋﻩ ﺁﺏ‪(4.184 kw.s/kg.oC) 1.00 Btu/lb.oF ،‬‬

‫ﺧﺮﻭﺟﯽ ﺑﺪﻧﻪ ﻣﻮﺗﻮﺭ ﺗﻘﺮﯾﺒﺎ ‪ (28oC) 50oF‬ﺍﺳﺖ‪.‬‬

‫‪ =To‬ﺩﻣﺎﯼ ﺁﺏ ﺧﺮﻭﺟﯽ‪F (oC) ،‬‬

‫‪o‬‬

‫‪ =Ti‬ﺩﻣﺎﯼ ﺁﺏ ﻭﺭﻭﺩﯼ‪F (oC) ،‬‬

‫‪o‬‬

‫ﻣﺤﺎﺳﺒﻪ ﮔﺮﻣﺎﯾﯽ ﺑﺎﺯﯾﺎﻓﺘﯽ ﺑﺨﺎﺭ ﺧﺮﻭﺟﯽ ﺍﺯ ﺗﻮﺭﺑﯿﻦ‬ ‫ﺍﺯ ﻃﺮﯾﻖ ﺟﺪﻭﻝ ﺯﯾﺮ ﻣﯽﺗﻮﺍﻥ ﻓﺸــﺎﺭ ﺑﺨﺎﺭ ﺗﻮﺭﺑﯿﻦ ﮐﻪ ﻣﯽﺗﻮﺍﻧﺪ‬

‫ﺗﻌﯿﯿﻦ ﻣﯿﺰﺍﻥ ﺳﺮﻣﺎﯾﺶ ﻗﺎﺑﻞ ﺩﺳﺘﯿﺎﺑﯽ‬

‫ﭘﺲ ﺍﺯ ﮔﺮﺩﺍﻧﺪﻥ ﺗﻮﺭﺑﯿﻦ ﻣﻮﺭﺩ ﺍﺳــﺘﻔﺎﺩﻩ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﻗﺮﺍﺭ ﮔﯿﺮﺩ ﺭﺍ‬ ‫ﺗﻌﯿﯿﻦ ﻧﻤﻮﺩ‪.‬‬

‫ﺑﺮ ﺍﺳــﺎﺱ ﻣﻘــﺪﺍﺭ ﮔﺮﻣــﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ ﻣــﻮﺭﺩ ﺍﺳــﺘﻔﺎﺩﻩ ﺑﺮﺍﯼ‬ ‫ﺳﺮﻣﺎﯾﺶ ﻭ ﻣﺸــﺨﺺ ﺑﻮﺩﻥ ﺿﺮﯾﺐ ﮐﺎﺭﺍﯾﯽ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﻣﯽﺗﻮﺍﻥ‬ ‫ﻣﻘﺪﺍﺭ ﺳﺮﻣﺎﯾﺶ ﺭﺍ ﺍﺯ ﻃﺮﯾﻖ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﺗﻌﯿﯿﻦ ﻧﻤﻮﺩ‪:‬‬

‫ﻣﺤﺎﺳﺒﻪ ﺩﺑﯽ ﺟﺮﻣﯽ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ‬ ‫ﺍﮔﺮ ﻭﺍﺳــﻂ ﮔﺮﻣﺎﯾﯽ ﻧﻬﺎﯾﯽ ﺑﺨﺎﺭ ﺑﺎﺷــﺪ‪ ،‬ﻣﯽﺗﻮﺍﻥ ﺑﺮﺍﯼ ﺗﻌﯿﯿﻦ‬

‫)‪(8‬‬

‫)‪(6‬‬

‫‪ = COPABC‬ﺿﺮﯾﺐ ﮐﺎﺭﺍﯾﯽ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺑﺮﺍﺳﺎﺱ ﻧﻮﻉ ﺁﻥ‬ ‫‪ =qr‬ﻣﻘﺪﺍﺭ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ‪(KWT) Btu/h ،‬‬

‫‪ =ms‬ﺩﺑﯽ ﺟﺮﻣﯽ ﺑﺨﺎﺭ‪(kg/s) lb/h ،‬‬

‫‪ =qr‬ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ ﺍﺯ ﺑﺪﻧﻪ ﺗﺠﻬﯿﺰﺍﺕ ﯾﺎ ﮔﺎﺯﻫﺎﯼ ﺩﺍﻍ ﺧﺮﻭﺟﯽ‬ ‫ﺗﺠﻬﯿﺰﺍﺕ ‪(KWT) Btu/h‬‬ ‫‪ =hg‬ﺍﻧﺘﺎﻟﭙﯽ ﺑﺨﺎﺭ ﺍﺷــﺒﺎﻉ ﺩﺭ ﻓﺸــﺎﺭ ﻣﺮﺑﻮﻃﻪ‪.s/kg) Btu/lb ،‬‬

‫‪ =C1‬ﺿﺮﯾﺐ ﺗﺒﺪﯾﻞ‪(KWT/KWT) 12000 Btuh/ton ،‬‬

‫ﺗﻌﯿﯿﻦ ﻇﺮﻓﯿﺖ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺑﺮ ﺍﺳﺎﺱ ﻣﻘﺪﺍﺭ ﮔﺮﻣﺎﯼ‬ ‫ﺑﺎﺯﯾﺎﻓﺘﯽ‬ ‫ﺑﺎ ﻣﺸﺨﺺ ﺷﺪﻥ ﻣﻘﺪﺍﺭ ﮔﺮﻣﺎﯼ ﺑﺎﺯﯾﺎﻓﺘﯽ ﻭ ﭼﮕﻮﻧﮕﯽ ﺍﺳﺘﻔﺎﺩﻩ‬

‫‪(KWT‬‬

‫ﺟﺪﻭﻝ )‪ (3‬ﻧﺮﺥ ﺑﺨﺎﺭ ﺩﺭ ﺗﻮﺭﺑﯿﻦ ﭼﻨﺪﻣﺮﺣﻠﻪﺍﯼ‬ ‫ﻧﺮﺥ ﺑﺨﺎﺭ ﺩﺭ ﺧﺮﻭﺟﯽ ﺗﻮﺭﺑﯿﻦ‬ ‫ﺷﺮﺍﯾﻂ ﺩﺭ ﻭﺭﻭﺩﯼ ﺗﻮﺭﺑﯿﻦ‬

‫)‪Ib/h/kW (kJ/skW‬‬ ‫ﺑﺨﺎﺭ ﺑﺎ ﻓﺸﺎﺭ ‪115psig‬‬ ‫)‪(894kPa‬‬

‫ﺑﺨﺎﺭ ﺑﺎ ﻓﺸﺎﺭ ‪12psig‬‬ ‫)‪(185kPa‬‬ ‫‪257‬‬

‫‪55‬‬ ‫)‪(16‬‬ ‫‪29‬‬ ‫)‪(8‬‬ ‫‪17‬‬ ‫)‪(5‬‬ ‫‪14‬‬ ‫)‪(4‬‬

‫‪18‬‬ ‫)‪(5‬‬ ‫‪14‬‬ ‫)‪(4‬‬ ‫‪10‬‬ ‫)‪(3‬‬ ‫‪9‬‬ ‫)‪(3‬‬

‫ﺩﻣﺎ‬ ‫‪o‬‬ ‫)‪F (oC‬‬ ‫‪366‬‬ ‫)‪(185‬‬ ‫‪500‬‬ ‫)‪(260‬‬ ‫‪650‬‬ ‫)‪(340‬‬ ‫‪825‬‬ ‫)‪(440‬‬ ‫‪900‬‬ ‫)‪(480‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﻓﺸﺎﺭ ﺑﺨﺎﺭ‬ ‫)‪psig (kPa‬‬ ‫‪150‬‬ ‫)‪(1100‬‬ ‫‪350‬‬ ‫)‪(2500‬‬ ‫‪400‬‬ ‫)‪(2900‬‬ ‫‪850‬‬ ‫)‪(6000‬‬ ‫‪1250‬‬ ‫)‪(8700‬‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺩﺑﯽ ﺟﺮﻣﯽ ﺍﺯ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﺍﺳﺘﻔﺎﺩﻩ ﻧﻤﻮﺩ‪:‬‬

‫‪ =qc‬ﻣﻘﺪﺍﺭ ﺳﺮﻣﺎﯾﺶ ﺑﺮ ﺣﺴﺐ ﺗﻦ ﺗﺒﺮﯾﺪ ﯾﺎ )‪(KWT‬‬

‫ﺻﻔﺤﻪ ‪ / 24‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺍﺯ ﺁﻥ ﻣﯽﺗﻮﺍﻥ ﻇﺮﻓﯿﺖ ﻧﺎﻣﯽ‪ 1‬ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﻣﻨﺎﺳــﺐ ﺭﺍ ﺑﺮ ﺍﺳــﺎﺱ‬ ‫ﺍﺳــﺘﺎﻧﺪﺍﺭﺩ )‪ (ARI‬ﺗﻌﯿﯿﻦ ﻧﻤﻮﺩ‪ .‬ﺩﺭ ﺍﯾﻦ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ﺷﺮﺍﯾﻂ ﺯﯾﺮ ﺩﺭ‬ ‫ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﺷﺪﻩ ﺍﺳﺖ‪:‬‬ ‫ﺩﻣﺎﯼ ﺁﺏ ﻭﺭﻭﺩﯼ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ ﺑﻪ ﭼﯿﻠﺮ‪(29oC) 85oF :‬‬ ‫ﺩﻣﺎﯼ ﺁﺏ ﺳﺮﺩ ﺧﺮﻭﺟﯽ ﺍﺯ ﭼﯿﻠﺮ‪(7oC) 44oF :‬‬

‫ﺍﻋﻤﺎﻝ ﺿﺮﺍﯾﺐ ﺗﺼﺤﯿﺢ ﺑﺮﺍﯼ ﺩﻣﺎﻫﺎﯼ ﻣﺘﻔﺎﻭﺕ ﺩﺭ ﺍﯾﻦ ﻣﺮﺣﻠﻪ‬ ‫ﺻﻮﺭﺕ ﻣﯽﮔﯿﺮﺩ‪.‬‬ ‫ﻣﻘــﺪﺍﺭ ﮔﺮﻣﺎﯾﯽ ﮐﻪ ﺑﺎﯾﺪ ﺑﻪ ﮐﻤــﮏ ﺁﺏ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ ﺩﻓﻊ‬ ‫ﺷﻮﺩ ﺍﺯ ﻃﺮﯾﻖ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﻗﺎﺑﻞ ﻣﺤﺎﺳﺒﻪ ﺍﺳﺖ‪:‬‬

‫ﻧﮑﺘـﻪ ﻣﻬﻢ‪ :‬ﻣﻄﺎﺑﻖ ﺍﺳــﺘﺎﻧﺪﺍﺭﺩ ‪ ARI‬ﮔﺎﻟﻦ ﺑﺮ ﺗﻦ ﺗﺒﺮﯾﺪ ﺑﺮﺍﯼ‬ ‫ﭼﯿﻠﺮﻫﺎﯼ ﯾﮏﺍﺛﺮﻩ ‪ 3.6‬ﻭ ﺑﺮﺍﯼ ﭼﯿﻠﺮﻫﺎﯼ ﺩﻭ ﺍﺛﺮﻩ ‪ 4.0‬ﻣﻨﻈﻮﺭ ﺷﺪﻩ‬ ‫ﺍﺳــﺖ ﮐــﻪ ﺩﺭ ﻇﺎﻫﺮ ﺍﻣﺮ ﭼﻨﯿــﻦ ﻣﻘﺎﺩﯾﺮﯼ ﺩﺭ ﺗﻌﺎﺭﺽ ﺑﺎ ﻓﻠﺴــﻔﻪ‬ ‫ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ ﺩﻭ ﺍﺛﺮﻩ ﺍﺳــﺖ ﺯﯾﺮﺍ ﻣﯽﺩﺍﻧﯿﻢ ﮐﻪ ﺑﺎ‬ ‫ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ ﺩﻭ ﺍﺛﺮﻩ ﺑﻪ ﺩﻟﯿﻞ ﺍﺳﺘﻔﺎﺩﻩ ﻣﺠﺪﺩ ﺍﺯ‬ ‫ﺑﺨﺎﺭ ﺣﺎﺻﻞ ﺍﺯ ﻋﻤﻠﯿﺎﺕ ﺗﻐﻠﯿﻆ‪ ،‬ﺍﺯ ﻣﻘﺪﺍﺭ ﮔﺮﻣﺎﯼ ﻗﺎﺑﻞ ﺩﻓﻊ ﺗﻮﺳﻂ‬ ‫ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ ﮐﺎﺳــﺘﻪ ﺷــﺪﻩ ﻭ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ ﮐﻮﭼﮏﺗﺮﯼ‬ ‫ﻧﺴــﺒﺖ ﺑﻪ ﺳﯿﺴﺘﻢ ﯾﮏﺍﺛﺮﻩ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﺧﻮﺍﻫﺪ ﺑﻮﺩ ﺍﻣﺎ ﺑﺎﯾﺪ ﺑﺪﺍﻧﯿﻢ‬

‫)‪(9‬‬ ‫‪ =qh-rej‬ﻣﻘﺪﺍﺭ ﮔﺮﻣﺎﯾﯽ ﮐﻪ ﺑﺎﯾﺪ ﺩﻓﻊ ﺷﻮﺩ‪(KWT) Btu/h ،‬‬

‫‪h-rej‬‬

‫ﮐﻪ ﻣﻘﺎﺩﯾﺮ ﺗﻌﯿﯿﻦ ﺷــﺪﻩ ﻓﻮﻕ ﺩﺭ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ‪ ARI‬ﺑﺮ ﭘﺎﯾﻪ ﺍﺧﺘﻼﻑ‬ ‫ﺩﻣﺎﻫﺎﯼ ﺯﯾﺮ ﺑﺮﺍﯼ ﭼﯿﻠﺮﻫﺎﯼ ﯾﮏﺍﺛﺮﻩ‪ ،‬ﺩﻭ ﺍﺛﺮﻩ ﻭ ﺗﺮﺍﮐﻤﯽ ﺍﺳﺖ‪:‬‬

‫‪ =C3‬ﺛﺎﺑﺖ ﺑﺮﺍﺑﺮ ﺑﺎ ‪(4.17kj.s/s.oC.L) 500Btu.min/h.oF.gal‬‬

‫● ﺗﮏ ﺍﺛﺮﻩ‪17 F (9 C) :‬‬

‫‪ =qC‬ﻇﺮﻓﯿﺖ ﺳﺮﻣﺎﯾﺸﯽ ﭼﯿﻠﺮ ﺑﺮ ﺣﺴﺐ ﺗﻦ ﺗﺒﺮﯾﺪ ﯾﺎ )‪(KWT‬‬

‫● ﺩﻭ ﺍﺛﺮﻩ‪12oF (7oC) :‬‬

‫‪ =Kg‬ﮔﺎﻟﻦ ﺑﺮ ﺗﻦ ﺗﺒﺮﯾﺪ ﯾﺎ )‪(KWT. L/S‬‬

‫● ﺗﺮﺍﮐﻤﯽ‪10oF (6oC) :‬‬

‫‪ = ΔTCT‬ﺍﺧﺘﻼﻑ ﺩﻣﺎﯼ ﺁﺏ ﺭﻓﺖ ﻭ ﺑﺮﮔﺸﺖ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ‪،‬‬

‫ﺑﻨﺎﺑﺮﺍﯾــﻦ ﻣﻘﺎﺩﯾــﺮ ‪ 3.6gpm/ton‬ﻭ ‪ 4gpm/ton‬ﺑﺮﺍﯼ ﭼﯿﻠﺮﻫﺎﯼ‬

‫‪o‬‬

‫‪o‬‬

‫ﺟﺬﺑﯽ ﯾﮏﺍﺛــﺮﻩ ﻭ ﺩﻭ ﺍﺛﺮﻩ ﺑﺮ ﭘﺎﯾﻪ ﺍﺧﺘــﻼﻑ ﺩﻣﺎﻫﺎﯼ ﻓﻮﻕ ﺻﺎﺩﻕ‬

‫‪(oC) oF‬‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﭼﯿﻠﺮ ﺩﻭ ﺍﺛﺮﻩ ﻣﻨﻈﻮﺭ ﻣﯽﮔﺮﺩﺩ‪.‬‬

‫ﺑﺮ ﺍﺳــﺎﺱ ﺷــﺮﺍﯾﻂ ﺍﺳــﺘﺎﻧﺪﺍﺭﺩ ﻣﯽﺗﻮﺍﻥ ‪ C3 .K8 .ΔTCT‬ﺭﺍ ﺑﻪ‬

‫ﻫﺴــﺘﻨﺪ‪ .‬ﺑﺮ ﻫﻤﯿﻦ ﺍﺳﺎﺱ ﭼﻨﺎﻧﭽﻪ ﺍﺧﺘﻼﻑ ﺩﻣﺎ ﺩﺭ ﭼﯿﻠﺮ ﺟﺬﺑﯽ‬

‫ﺻﻮﺭﺕ ﻋﺪﺩﯼ ﺛﺎﺑﺖ ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺖ‪ ،‬ﺑﻨﺎﺑﺮﺍﯾﻦ ﺭﺍﺑﻄﻪ ﺑﺎﻻ ﺑﻪ ﺻﻮﺭﺕ‬

‫ﯾﮏﺍﺛﺮﻩ )‪ 10oF (6oC‬ﺩﺭﻧﻈﺮ ﮔﺮﻓﺘﻪ ﺷــﻮﺩ‪ .‬ﻣﻘﺪﺍﺭ ‪ ton/gpm‬ﺑﻪ ‪6.12‬‬

‫ﺯﯾﺮ ﺩﺭ ﺧﻮﺍﻫﺪ ﺁﻣﺪ‪:‬‬

‫ﺧﻮﺍﻫﺪ ﺭﺳﯿﺪ‪:‬‬

‫)‪(10‬‬ ‫‪ =qh-rej‬ﻣﻘﺪﺍﺭ ﮔﺮﻣﺎﯾﯽ ﮐﻪ ﺑﺎﯾﺪ ﺩﻓﻊ ﺷﻮﺩ‪(KWT) Btu/h ،‬‬ ‫‪ =C4‬ﻣﻘﺪﺍﺭ ﺛﺎﺑــﺖ ﺑﺮﺍﺑﺮ ﺑﺎ ‪(2.54KWT/KWT) 30600Btuh/ton‬‬

‫ﺑﺮﺍﯼ ﭼﯿﻠــﺮ ﯾﮏﺍﺛــﺮﻩ ﻭ ‪ (1.87KWT/KWT) 22500Btuh/ton‬ﺑﺮﺍﯼ‬

‫‪/‬‬ ‫ﺑﺮ ﻫﻤﯿﻦ ﺍﺳﺎﺱ ﭼﻨﺎﻧﭽﻪ ﺍﺧﺘﻼﻑ ﺩﻣﺎﯼ ﺁﺏ ﺑﺮﺝﺧﻨﮏﮐﻨﻨﺪﻩ‬ ‫ﺑــﺮﺍﯼ ﭼﯿﻠﺮ ﺩﻭ ﺍﺛﺮﻩ ﺭﺍ ﻧﯿﺰ ﺑﻪ ﺟﺎﯼ ‪ (7oC) 12oF‬ﻣﻌﺎﺩﻝ ‪(6oC)10oF‬‬

‫ﺩﺭ ﻧﻈــﺮ ﮔﯿﺮﯾﻢ‪ ،‬ﮔﺎﻟﻦ ﺑﺮ ﺗــﻦ ﺗﺒﺮﯾﺪ ﺁﺏ ﺑﺮﺝﮐﻨﻨــﺪﻩ ‪ 4.5‬ﺧﻮﺍﻫﺪ‬

‫ﺟﺪﻭﻝ )‪ (5‬ﺗﻌﯿﯿﻦ ﺍﻧﺪﺍﺯﻩ ﭘﻤﭗ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ ﺑﺮﺍﯼ ﭼﯿﻠﺮ ﺟﺬﺑﯽ‬ ‫ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺩﻭ ﺍﺛﺮﻩ‬

‫ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﯾﮏﺍﺛﺮﻩ‬

‫ﻭﺍﺣﺪﻫﺎ‬

‫ﺍﺧﺘﻼﻑ ﺩﻣﺎﯼ ﺁﺏ ﺑﺮﺝ‬

‫)‪4.5 (0.08‬‬

‫)‪6.0 (0.1‬‬

‫)‪gpm/ton (L/s/kW T‬‬

‫)‪10°F (6°C‬‬

‫)‪0.1 (0.021‬‬

‫)‪0.12 (0.025‬‬

‫)‪bhp/ton (kW/kWT‬‬ ‫)‪gpm/ton (L/s/kW T‬‬

‫)‪12°F (7°C‬‬

‫)‪4.1 (0.07‬‬ ‫)‪0.09 (0.019‬‬

‫)‪gpm/ton (LIs/kW T‬‬ ‫)‪bhp/ton (kW/kW T‬‬

‫)‪15°F (8°C‬‬

‫‪-‬‬

‫)‪3.6 (0.06‬‬

‫)‪gpm/ton (L/s/kW T‬‬

‫·)‪17°F (9°C‬‬

‫)‪2.3 (0.04‬‬ ‫)‪0.05 (0.011‬‬ ‫)‪1.8 (0.03‬‬ ‫)‪0.04 (0.008‬‬

‫)‪3.1 (0.06‬‬ ‫)‪0.06 (0.013‬‬ ‫)‪2.45 (0.04‬‬ ‫)‪0.05 (0.011‬‬

‫)‪gpm/ton (L/s/kW T‬‬ ‫)‪bhp/ton (kW/kW T‬‬ ‫)‪gpm/ton (L/s/kW T‬‬ ‫)‪bhp/ton (kW/kW T‬‬

‫)‪20°F (11°C‬‬

‫‬‫‬‫‪-‬‬

‫)‪2.05 (0.04‬‬ ‫)‪0.04 (0.008‬‬ ‫)‪1.75 (0.03‬‬

‫)‪gpm/ton (L/s/kW T‬‬ ‫)‪bhp/ton (kW /kW T‬‬ ‫)‪gpm/ton (L/s/kW T‬‬

‫‪-‬‬

‫)‪0.04 (0.008‬‬

‫)‪bhp/ton (kW/kWT‬‬

‫)‪4.0 (0.07‬‬ ‫)‪3.0 (0.05‬‬ ‫)‪0.06 (0.013‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫)‪25°F (14°C‬‬ ‫)‪30°F (l7°C‬‬ ‫)‪35°F (l9°C‬‬

‫ﺻﻔﺤﻪ ‪ / 25‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺷﺪ‪ .‬ﺑﻨﺎﺑﺮﺍﯾﻦ ﺗﺤﺖ ﺷــﺮﺍﯾﻂ ﺑﺮﺍﺑﺮ ﺩﺑﯽ ﺁﺏ ﺑﺮﺝﺧﻨﮏﮐﻨﻨﺪﻩ ﺑﺮﺍﯼ‬

‫ﺑﻪ ﮐﻤﮏ ﺟــﺪﻭﻝ )‪ (5‬ﻭ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﻣﯽﺗﻮﺍﻥ ﺍﻧﺪﺍﺯﻩ ﭘﻤﭗ ﺑﺮﺝ‬

‫ﭼﯿﻠﺮﻫﺎﯼ ﺩﻭ ﺍﺛﺮﻩ ﺑﻪ ﻣﺮﺍﺗﺐ ﮐﻤﺘﺮ ﺍﺯ ﭼﯿﻠﺮﻫﺎﯼ ﯾﮏﺍﺛﺮﻩ ﺍﺳﺖ ﻭ ﺍﯾﻦ‬

‫ﺧﻨﮏﮐﻨﻨﺪﻩ ﺑﺮﺍﯼ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ ﺭﺍ ﺑﺮ ﻣﺒﻨﺎﯼ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ‪ARI‬‬

‫ﻣﻘــﺪﺍﺭ ﺣﺪﻭﺩ ‪ 27‬ﺗﺎ ‪ 30‬ﺩﺭﺻﺪ ﺧﻮﺍﻫــﺪ ﺑﻮﺩ )ﺩﺭ ﺿﻤﻦ ﺑﺎﯾﺪ ﺗﻮﺟﻪ‬

‫ﺗﻌﯿﯿﻦ ﻧﻤﻮﺩ‪.‬‬

‫ﺩﺍﺷﺘﻪ ﺑﺎﺷﯿﻢ ﮐﻪ ﺍﺧﺘﻼﻑ ﺩﻣﺎﻫﺎ ﺑﺮ ﺣﺴﺐ ﻓﺎﺭﻧﻬﺎﯾﺖ ﻭ ﺳﺎﻧﺘﯽﮔﺮﺍﺩ‬ ‫)‪(14‬‬

‫ﺑﻪ ﺻﻮﺭﺕ ﺍﻋﺪﺍﺩ ﺑﺪﻭﻥ ﺍﻋﺸﺎﺭ‪ ،‬ﮐﺎﻣﻼ ﺑﺮﻫﻢ ﻣﻨﻄﺒﻖ ﻧﯿﺴﺘﻨﺪ(‪.‬‬ ‫ﺍﻋــﺪﺍﺩ ‪ (2.54KWT/KWT) 30600Btuh/ton‬ﺑــﺮﺍﯼ ﭼﯿﻠﺮﻫﺎﯼ‬ ‫ﯾﮏﺍﺛﺮﻩ ﻭ ‪ (1.87KWT/KWT) 22500Btuh/ton‬ﺑﺮﺍﯼ ﭼﯿﻠﺮﻫﺎﯼ ﺩﻭ‬

‫‪ = CWPkwh‬ﺍﻧﺮﮊﯼ ﺍﻟﮑﺘﺮﯾﮑﯽ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﭘﻤﭗ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ‬ ‫ﺩﺭ ﻃﻮﻝ ﺳﺎﻝ )‪(kwh/yr‬‬

‫ﺍﺛﺮﻩ ﻧﯿﺰ ﮐﻪ ﺑﻪ ﻋﻨﻮﺍﻥ ‪ C4‬ﺩﺭ ﺭﺍﺑﻄﻪ ﺑﺎﻻ ﻣﻨﻈﻮﺭ ﺷﺪﻩﺍﻧﺪ‪ ،‬ﺑﺮ ﺍﺳﺎﺱ‬ ‫ﺗﻮﺿﯿﺤﺎﺕ ﻓﻮﻕ ﭼﻨﯿﻦ ﺑﻪ ﺩﺳﺖ ﺁﻣﺪﻩﺍﻧﺪ‪:‬‬

‫‪ = K2‬ﻣﻘﺪﺍﺭ ﺍﺳﺘﺨﺮﺍﺝ ﺷﺪﻩ ﺍﺯ ﺟﺪﻭﻝ )‪ (5‬ﺑﺮ ﺣﺴﺐ ﺍﺳﺐ ﺑﺮ‬ ‫ﺗﻦ )‪ (bhp/ton‬ﯾﺎ ﮐﯿﻠﻮﻭﺍﺕ ﺑﺮ ﮐﯿﻠﻮﻭﺍﺕ )‪(kw/kwT‬‬ ‫‪ = AMcap‬ﻇﺮﻓﯿــﺖ ﻧﺎﻣﯽ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺑﺮ ﺣﺴــﺐ ﺗﻦ ﺗﺒﺮﯾﺪ ﯾﺎ‬

‫)‪(11‬‬

‫ﮐﯿﻠﻮﻭﺍﺕ )‪(kwT‬‬

‫ﺑﺮﺍﯼ ﭼﯿﻠﺮ ﯾﮏﺍﺛﺮﻩ = ‪500×6.12×10 = 30600Btu/ton‬‬

‫‪ = H1‬ﺳﺎﻋﺎﺕ ﮐﺎﺭﮐﺮﺩ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺩﺭ ﻃﻮﻝ ﺳﺎﻝ )‪(h/yr‬‬

‫ﺑﺮﺍﯼ ﭼﯿﻠﺮ ﺩﻭ ﺍﺛﺮﻩ = ‪500×4.5×10 = 22500Btu/ton‬‬

‫‪ = C2‬ﺿﺮﯾﺐ ﺗﺒﺪﯾﻞ‪0.7457kw/hp (1 kw/kwT) ،‬‬

‫ﺗﺎﻣﯿﻦ ﺍﻧﺮﮊﯼ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ‬

‫‪ = ηCWP‬ﺑﺎﺯﺩﻩ ﭘﻤﭗ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ )‪(٪‬‬

‫ﺑﺮ ﺍﺳــﺎﺱ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﻭ ﻫﻤﯿﻦﻃﻮﺭ ﺟﺪﻭﻝ )‪ (4‬ﻣﯽﺗﻮﺍﻥ ﻣﻘﺪﺍﺭ‬ ‫ﺍﻧﺮﮊﯼ ﺍﻟﮑﺘﺮﯾﮑﯽ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺭﺍ ﺗﻌﯿﯿﻦ ﻧﻤﻮﺩ‪:‬‬ ‫)‪(12‬‬

‫‪K2 × AMcap × H1 × C2‬‬ ‫‪ηCWP‬‬

‫= ‪CWPkwh‬‬

‫‪AMkwh = K1×AMcap×H1‬‬

‫‪ = AMkwh‬ﺍﻧﺮﮊﯼ ﺍﻟﮑﺘﺮﯾﮑﯽ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺑﺮ ﺣﺴــﺐ‬ ‫ﮐﯿﻠﻮﻭﺍﺕﺳﺎﻋﺖ ﺩﺭ ﺳﺎﻝ )‪(kwh/yr‬‬ ‫‪ = K1‬ﻣﻘﺪﺍﺭ ﺍﺳــﺘﺨﺮﺍﺝ ﺷــﺪﻩ ﺍﺯ ﺟﺪﻭﻝ )‪ (4‬ﺑﺮ ﺣﺴﺐ )‪Kw/‬‬

‫‪ = AMcap‬ﻇﺮﻓﯿﺖ ﻧﺎﻣﯽ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺑﺮ ﺣﺴﺐ ﺗﻦ ﯾﺎ ﮐﯿﻠﻮﻭﺍﺕ‬ ‫)‪(kwT‬‬

‫ﺑﺮﺍﺳــﺎﺱ ‪ 60‬ﻓــﻮﺕ )‪ (179kPa‬ﻫﺪ ﻭ ﺑــﺎﺯﺩﻩ ‪ 80‬ﺩﺭﺻﺪﯼ ﻣﻮﺗﻮﺭ‬ ‫ﺗﻌﯿﯿﻦ ﺷﺪﻩ ﺍﺳــﺖ‪ .‬ﭼﻨﺎﻧﭽﻪ ﺩﺭ ﺭﺍﺑﻄﻪ )‪ (14‬ﻣﻘﺪﺍﺭ ‪ H1‬ﺭﺍ ﺩﺭﻧﻈﺮ‬ ‫ﻧﮕﯿﺮﯾــﻢ‪ ،‬ﻧﺮﺥ ﺗــﻮﺍﻥ ﺍﻟﮑﺘﺮﯾﮑﯽ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﺑﻪ ﺻــﻮﺭﺕ ﮐﻠﯽ ﺑﺮﺍﯼ‬ ‫ﭘﻤﭗﻫﺎﯼ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ ﺗﻌﯿﯿﻦ ﺧﻮﺍﻫﺪ ﺷﺪ‪.‬‬ ‫ﺟــﺪﻭﻝ )‪ (6‬ﻭ ﺭﺍﺑﻄــﻪ ﺯﯾﺮ ﻧﯿــﺰ ﺍﻧﺮﮊﯼ ﺍﻟﮑﺘﺮﯾﮑــﯽ ﻣﻮﺭﺩ ﻧﯿﺎﺯ‬ ‫ﻓﻦﻫﺎﯼ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺭﺍ ﺗﻌﯿﯿﻦ ﻣﯽﮐﻨﺪ‪:‬‬ ‫)‪(15‬‬

‫‪ = H1‬ﺳﺎﻋﺎﺕ ﮐﺎﺭﮐﺮﺩ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺩﺭ ﻃﻮﻝ ﺳﺎﻝ )‪(h/yr‬‬

‫‪ = CTFkwh‬ﺍﻧﺮﮊﯼ ﺍﻟﮑﺘﺮﯾﮑﯽ ﻓﻦ ﺑﺮﺝ )‪(kwh/yr‬‬

‫ﺩﺭ ﺟﺪﻭﻝ )‪ (4‬ﻣﻘﺪﺍﺭ ﻇﺮﻓﯿﺖ ﺑﺮ ﺣﺴﺐ )‪ (kwT‬ﺑﺮ ﺍﺳﺎﺱ ﺷﺮﺍﯾﻂ‬

‫‪ = K3‬ﻣﻘﺪﺍﺭ ﺍﺳﺘﺨﺮﺍﺝﺷــﺪﻩ ﺍﺯ ﺟﺪﻭﻝ )‪ (6‬ﺑﺮ ﺣﺴــﺐ )‪bhp/‬‬

‫‪ ARI‬ﺗﻌﯿﯿﻦ ﺷــﺪﻩ ﺍﺳﺖ‪ .‬ﻣﻄﺎﺑﻖ ﺍﯾﻦ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ‪ ،‬ﺩﻣﺎﯼ ﺁﺏ ﺳﺮﺩ‬ ‫ﺭﻓــﺖ ‪ (7ºC) 44ºF‬ﻭ ﺩﻣﺎﯼ ﺁﺏ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ ‪ (29ºC) 85ºF‬ﺩﺭ‬

‫‪K × AMcap × H1 × C2 × K4‬‬ ‫‪CTFkwh/yr = 3‬‬ ‫‪ηCTF‬‬

‫‪ (ton‬ﯾﺎ )‪(kw/kwT‬‬

‫ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﻣﯽﺷﻮﺩ ﻭ ﻫﻢﭼﻨﯿﻦ ﻓﺸﺎﺭ ﺑﺨﺎﺭ ﺑﺮﺍﯼ ﭼﯿﻠﺮﻫﺎﯼ ﯾﮏﺍﺛﺮﻩ‬

‫‪ = AMcap‬ﻇﺮﻓﯿﺖ ﻧﺎﻣﯽ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺑﺮ ﺣﺴﺐ ﺗﻦ ﯾﺎ )‪(kw‬‬

‫)‪ 12psig (184kPa‬ﻭ ﺑــﺮﺍﯼ ﭼﯿﻠﺮﻫﺎﯼ ﺩﻭﺍﺛــﺮﻩ )‪115psig (896kPa‬‬

‫‪ = H1‬ﺳﺎﻋﺎﺕ ﮐﺎﺭﮐﺮﺩ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺩﺭ ﻃﻮﻝ ﺳﺎﻝ )‪(h/yr‬‬

‫ﻣﻨﻈﻮﺭ ﻣﯽﺷﻮﺩ‪ .‬ﺑﺮﺍﯼ ﺗﻌﯿﯿﻦ ﻧﺮﺥ ﺗﻘﺎﺿﺎﯼ ﺍﻟﮑﺘﺮﯾﮑﯽ ﻓﺎﺭﻍ ﺍﺯ ﺯﻣﺎﻥ‬

‫‪ = C2‬ﺿﺮﯾﺐ ﺗﺒﺪﯾﻞ ‪(1 kw/kwT) 0.7457 kw/hp‬‬

‫‪ = K4‬ﺿﺮﯾــﺐ ﺗﺒﺪﯾﻞ‪ .‬ﺩﺭﺻﺪ ﮐﺎﺭﮐﺮﺩ ﻓــﻦ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ‬

‫ﮐﺎﺭﮐﺮﺩ ﭼﯿﻠﺮﻫﺎﯼ ﺟﺬﺑﯽ ﻣﯽﺗﻮﺍﻥ ﺍﺯ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﺍﺳﺘﻔﺎﺩﻩ ﮐﺮﺩ‪:‬‬ ‫)‪(13‬‬

‫‪AMkw = K1×AMcap‬‬

‫‪ = AMkw‬ﺍﻧﺮﮊﯼ ﺍﻟﮑﺘﺮﯾﮑﯽ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺑﺮ ﺣﺴــﺐ‬

‫)ﺩﺭ ﻋﻤﻞ ﻓﻦ ﺑﺮﺝ ﺑﻪ ﻃﻮﺭ ﭘﯿﻮﺳﺘﻪ ﺭﻭﺷﻦ ﻧﯿﺴﺖ ﻭ ﺑﻪ ﺗﻨﺎﺳﺐ‬ ‫ﺑﺎﺭ ﻣﻤﮑﻦ ﺍﺳــﺖ ﺍﻭﻗﺎﺗﯽ ﺧﺎﻣﻮﺵ ﺑﺎﺷﺪ‪ .‬ﺷــﺮﺍﯾﻂ ﺁﺏﻭﻫﻮﺍﯾﯽ ﻭ‬

‫ﮐﯿﻠﻮﻭﺍﺕ )‪(kw‬‬ ‫‪ = K1‬ﻣﻘﺪﺍﺭ ﺍﺳــﺘﺨﺮﺍﺝ ﺷﺪﻩ ﺍﺯ ﺟﺪﻭﻝ )‪ (4‬ﺑﺮ ﺣﺴﺐ )‪Kw/‬‬

‫ﻣﻘﺪﺍﺭ ﺑﺎﺭ ﺩﺭ ﻣﻘﺪﺍﺭ ﮐﺎﺭﮐﺮﺩ ﻓﻦ ﻣﻮﺛﺮ ﺍﺳــﺖ ﺍﻣﺎ ﺑﻪ ﺻﻮﺭﺕ ﺗﺠﺮﺑﯽ‬ ‫ﺍﯾﻦ ﺿﺮﯾﺐ ﺭﺍ ‪ 0.4‬ﺩﺭﻧﻈﺮ ﻣﯽﮔﯿﺮﻧﺪ‪(.‬‬

‫‪ (kwT‬ﯾﺎ )‪(kw/ton‬‬ ‫‪ = AMcap‬ﻇﺮﻓﯿﺖ ﻧﺎﻣﯽ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﺑﺮ ﺣﺴﺐ ﺗﻦ ﯾﺎ ﮐﯿﻠﻮﻭﺍﺕ‬ ‫)‪(kwT‬‬

‫)‪(٪‬‬

‫‪ = ηCTF‬ﺑﺎﺯﺩﻩ ﻣﻮﺗﻮﺭ ﻓﻦ )‪(٪‬‬ ‫ﺑﺮﺍﯼ ﺗﻌﯿﯿﻦ ﺗﻮﺍﻥ ﺍﻟﮑﺘﺮﯾﮑﯽ ﻓﻦ ﯾﺎ ﻓﻦﻫﺎﯼ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫‪ (kwT‬ﯾﺎ )‪(kw/ton‬‬

‫ﺩﺭ ﺟﺪﻭﻝ ﻓــﻮﻕ )‪ bhp/ton (kw/kwT‬ﭘﻤﭗ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ‬

‫ﺻﻔﺤﻪ ‪ / 26‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺟﺪﻭﻝ )‪ (6‬ﺗﻌﯿﯿﻦ ﺍﻧﺪﺍﺯﻩ ﻓﻦ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ ﺑﺮﺍﯼ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﻭ ﺗﻌﯿﯿﻦ ﺿﺮﯾﺐ ‪k3‬‬ ‫ﭼﯿﻠﺮ ﺩﻭ ﺍﺛﺮﻩ‬

‫ﭼﯿﻠﺮ ﯾﮏﺍﺛﺮﻩ‬

‫‪bhp/ton‬‬

‫‪bhp/ton‬‬

‫)‪(kW/kWT‬‬

‫)‪(kW/kWT‬‬

‫ﻧﻮﻉ ﻓﻦ‬

‫ﺍﺧﺘﻼﻑ ﺩﻣﺎﯼ ﺁﺏ ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ‬

‫)‪0.11 (0.023‬‬

‫)‪0.13 (0.028‬‬

‫ﺟﺮﯾﺎﻥ ﻣﺤﻮﺭﯼ‬

‫)‪l0°F (6°C‬‬

‫)‪0.23 (0.049‬‬

‫)‪0.27 (0.057‬‬

‫ﮔﺮﯾﺰ ﺍﺯ ﻣﺮﮐﺰ‬

‫)‪0.09 (0.019‬‬

‫)‪0.11 (0.023‬‬

‫ﺟﺮﯾﺎﻥ ﻣﺤﻮﺭﯼ‬

‫)‪0.19 (0.040‬‬

‫)‪0.23 (0.049‬‬

‫ﮔﺮﯾﺰ ﺍﺯ ﻣﺮﮐﺰ‬

‫)‪0.08 (0.017‬‬

‫)‪0.09 (0.019‬‬

‫ﺟﺮﯾﺎﻥ ﻣﺤﻮﺭﯼ‬

‫)‪0.17 (0.036‬‬

‫)‪0.19 (0.040‬‬

‫ﮔﺮﯾﺰ ﺍﺯ ﻣﺮﮐﺰ‬

‫ﻣﯽﺗﻮﺍﻧﯿﻢ ﺍﺯ ﺭﺍﺑﻄﻪ ﻓﻮﻕ ﺑﺪﻭﻥ ﻣﻘﺪﺍﺭ ‪ H1‬ﺍﺳﺘﻔﺎﺩﻩ ﮐﻨﯿﻢ‪:‬‬ ‫)‪(16‬‬

‫‪K3 × AMcap × C2 × K4‬‬ ‫‪ηCTF‬‬

‫)‪20°F (11°C‬‬

‫‪ =K9‬ﻣﻘﺎﺩﯾــﺮ ﺑﻪ ﺩﺳــﺖ ﺁﻣﺪﻩ ﺍﺯ ﻧﻤﻮﺩﺍﺭ )‪ (1‬ﯾﺎ )‪ (2‬ﺑﺮ ﺣﺴــﺐ‬ ‫ﺩﺭﺻﺪ )‪(٪‬‬

‫= ‪CTFkw‬‬

‫‪ =q c-p-l‬ﺧﺮﻭﺟﯽ ﺳﺮﻣﺎﯾﺸﯽ ﺗﺤﺖ ﺑﺎﺭ ﺟﺰﯾﯽ ﺑﺮ ﺣﺴﺐ ﺗﻦ ﺗﺒﺮﯾﺪ‬ ‫ﯾﺎ )‪(KWT‬‬

‫ﺑﺎﺭﻫﺎﯼ ﺟﺰﯾﯽ‬

‫‪ =C1‬ﺛﺎﺑﺖ‪(1 KWT/KWT) 12000 Btuh/ton ،‬‬

‫ﻋــﺪﻡ ﻧﯿﺎﺯ ﺑﻪ ﺗﺎﻣﯿﻦ ﺑﺎﺭ ﮐﻞ ﺩﺭ ﺑﺴــﯿﺎﺭﯼ ﺍﺯ ﺍﻭﻗــﺎﺕ ﻭ ﮐﺎﺭﮐﺮﺩ‬ ‫ﭼﯿﻠــﺮ ﺟﺬﺑﯽ ﺗﺤﺖ ﺑﺎﺭﻫــﺎﯼ ﺟﺰﯾﯽ‪ ،‬ﺍﺣﺘﯿﺎﺝ ﺳﯿﺴــﺘﻢ ﺑﻪ ﻭﺭﻭﺩﯼ‬ ‫ﺍﻧــﺮﮊﯼ ﮔﺮﻣﺎﯾﯽ ﺭﺍ ﻧﯿﺰ ﮐﻢ ﻣﯽﮐﻨﺪ‪ .‬ﻧﻤﻮﺩﺍﺭﻫﺎﯼ )‪ (1‬ﻭ )‪ (2‬ﺑﻪ ﺗﺮﺗﯿﺐ‬ ‫ﻧﻤﺎﯾﺶﺩﻫﻨﺪﻩ ﻇﺮﻓﯿﺖ ﺑﺎﺭﻫﺎﯼ ﺟﺰﯾﯽ ﺑﺮ ﺍﺳﺎﺱ ﺩﺭﺻﺪ ﺑﺎﺭ ﻭ ﺩﺭﺻﺪ‬ ‫ﺍﻧﺮﮊﯼ ﮔﺮﻣﺎﯾﯽ ﻭﺭﻭﺩﯼ ﭼﯿﻠﺮ ﺟﺬﺑﯽ ﯾﮏﺍﺛﺮﻩ ﻭ ﺩﻭ ﺍﺛﺮﻩ ﻫﺴﺘﻨﺪ‪.‬‬

‫ﺑﺮﺭﺳـﯽ ﺑﺮﺧﯽ ﮔﺰﯾﻨﻪﻫـﺎﯼ ﺩﯾﮕﺮ ﻭ ﻣﻘﺎﯾﺴـﻪ ﺁﻥ ﺑﺎ‬ ‫ﮔﺰﯾﻨﻪ ﻣﻨﺘﺨﺐ‬ ‫ﺩﺭ ﺑﺮﺧــﯽ ﭘﺮﻭﮊﻩﻫﺎ ﺷــﺮﺍﯾﻂ ﺍﯾﺠﺎﺏ ﻣﯽﮐﻨﺪ ﮐــﻪ ﮔﺰﯾﻨﻪﻫﺎﯼ‬ ‫ﻣﺘﻔﺎﻭﺗــﯽ ﮐﻪ ﻫﺮ ﯾﮏ ﻗﺎﺑﻠﯿﺖ ﺍﻧﺘﺨﺎﺏ ﺩﺍﺭﻧــﺪ ﺑﻪ ﻃﻮﺭ ﻣﺠﺰﺍ ﻣﻮﺭﺩ‬ ‫ﺍﺭﺯﯾﺎﺑﯽ ﻭ ﻣﺤﺎﺳــﺒﻪ ﻗﺮﺍﺭ ﮔﯿﺮﻧﺪ ﻭ ﺑﺎ ﮔﺰﯾﻨﻪ ﻣﻨﺘﺨﺐ ﺍﻭﻟﯿﻪ ﻣﻘﺎﯾﺴﻪ‬ ‫ﺷﻮﻧﺪ ﺗﺎ ﺟﺎﯼ ﻫﯿﭻ ﺷﮏ ﻭ ﺷﺒﻬﻪﺍﯼ ﺩﺭ ﺍﻧﺘﺨﺎﺏ ﺑﻬﯿﻨﻪ ﺑﺎﻗﯽ ﻧﻤﺎﻧﺪ‪.‬‬

‫ﺩﺭﺻﺪ ﮔﺮﻣﺎﯼ ﻭﺭﻭﺩﯼ‬

‫ﺩﺭﺻﺪ ﮔﺮﻣﺎﯼ ﻭﺭﻭﺩﯼ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫)‪15°F (8°C‬‬

‫ﺩﻣﺎﯼ ﺁﺏ ﻭﺭﻭﺩﯼ‬ ‫ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ‬

‫ﺩﻣﺎﯼ ﺁﺏ ﻭﺭﻭﺩﯼ‬ ‫ﺑﺮﺝ ﺧﻨﮏﮐﻨﻨﺪﻩ‬

‫ﺩﺭﺻﺪ ﺑﺎﺭ‬

‫ﻧﻤﻮﺩﺍﺭ )‪ (1‬ﻧﻤﻮﺩﺍﺭ ﺩﺭﺻﺪ ﺑﺎﺭ ﻭ ﺩﺭﺻﺪ ﺍﻧﺮﮊﯼ ﮔﺮﻣﺎﯾﯽ ﻭﺭﻭﺩﯼ ﭼﯿﻠﺮ‬ ‫ﺟﺬﺑﯽ ﯾﮏﺍﺛﺮﻩ‬

‫ﺑﺮﺍﯼ ﺗﻌﯿﯿﻦ ﮔﺮﻣﺎﯼ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﺩﺭ ﺗﺎﻣﯿﻦ ﺑﺎﺭﻫﺎﯼ ﺟﺰﯾﯽ ﻣﯽﺗﻮﺍﻥ‬

‫ﺩﺭﺻﺪ ﺑﺎﺭ‬

‫ﻧﻤﻮﺩﺍﺭ )‪ (2‬ﻧﻤﻮﺩﺍﺭ ﺩﺭﺻﺪ ﺑﺎﺭ ﻭ ﺩﺭﺻﺪ ﺍﻧﺮﮊﯼ ﮔﺮﻣﺎﯾﯽ ﻭﺭﻭﺩﯼ ﭼﯿﻠﺮ‬ ‫ﺟﺬﺑﯽ ﺩﻭ ﺍﺛﺮﻩ‬

‫ﺍﺯ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﺍﺳﺘﻔﺎﺩﻩ ﻧﻤﻮﺩ‪:‬‬ ‫)‪(17‬‬

‫‪qh-p-l = K9 × q c-p-l × C1‬‬

‫ﭘﯽﻧﻮﺷﺖ‬

‫‪ = qh-p-l‬ﮔﺮﻣﺎﯼ ﻭﺭﻭﺩﯼ ﺑﺮﺍﯼ ﺗﺎﻣﯿﻦ ﺑﺎﺭ ﺟﺰﯾﯽ‪(KWT) Btuh ،‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫‪1 - Nominal capacity‬‬

‫ﺻﻔﺤﻪ ‪ / 27‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻋﻠﻤﻰ‬

‫ﻣﺤﺎﺳﺒﺎﺕ ﻛﻮﺭﻩ ﻫﻮﺍﻯ ﮔﺮﻡ‬ ‫ﺍﻧﻮﺍﻉ‬

‫ﮔﺮﻣﺎ ﻫﺴﺘﻨﺪ‪.‬‬

‫ﮐــﻮﺭﻩ ﻫﻮﺍﯼ ﮔــﺮﻡ ﺑﻪ ﻋﻨﻮﺍﻥ ﯾﮑــﯽ ﺍﺯ ﺗﺠﻬﯿــﺰﺍﺕ ﻣﻮﻟﺪ ﮔﺮﻣﺎ‬ ‫ﻧﻮﻋﯽ ﻭﺳــﯿﻠﻪ ﮔﺮﻣﮑﻦ ﻣﺴــﺘﻘﯿﻢ ﻫﻮﺍ ﺍﺳــﺖ ﻭ ﺍﺯ ﻧﻈﺮ ﮔﺮﺩﺵ ﻫﻮﺍ‬ ‫ﺩﺭ ﺩﻭ ﮔﺮﻭﻩ ﻃﺒﯿﻌــﯽ )ﺑﺪﻭﻥ ﻓﻦ( ﻭ ﺍﺟﺒﺎﺭﯼ )ﻓﻦﺩﺍﺭ( ﻃﺒﻘﻪﺑﻨﺪﯼ‬ ‫ﻣﯽﺷﻮﺩ‪ .‬ﺩﺭ ﺳﯿﺴﺘﻢ ﻃﺒﯿﻌﯽ‪ ،‬ﺑﻨﺎﺑﺮ ﺍﺻﻞ ﻭﺯﺵ ﮔﺮﻣﺎﯾﯽ‪ ،‬ﻫﻮﺍ ﭘﺲ‬ ‫ﺍﺯ ﮔﺮﻡ ﺷﺪﻥ ﺑﻪ ﻋﻠﺖ ﺳﺒﮑﯽ ﺻﻌﻮﺩ ﮐﺮﺩﻩ ﻭ ﭘﺲ ﺍﺯ ﺳﺮﺩ ﺷﺪﻥ ﺑﻪ‬ ‫ﻃﺮﻑ ﭘﺎﯾﯿﻦ ﺣﺮﮐﺖ ﻣﯽﮐﻨﺪ‪ .‬ﺑــﺮﺍﯼ ﺑﻬﺮﻩﮔﯿﺮﯼ ﺍﺯ ﺍﯾﻦ ﻭﯾﮋﮔﯽ‪ ،‬ﺩﺭ‬ ‫ﺍﻃﺮﺍﻑ ﺟﺪﺍﺭ ﺧﺎﺭﺟﯽ ﮐﻮﺭﻩ‪ ،‬ﺟﺪﺍﺭ ﺩﯾﮕﺮﯼ ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﻣﯽﺷــﻮﺩ‬ ‫ﮐﻪ ﻗﺴﻤﺖ ﻓﻮﻗﺎﻧﯽ ﺍﯾﻦ ﻓﻀﺎ ﺗﻮﺳﻂ ﮐﺎﻧﺎﻝ ﺑﻪ ﻧﻘﺎﻁ ﻣﺨﺘﻠﻒ ﻣﺘﺼﻞ‬ ‫ﻣﯽﺷــﻮﺩ ﻭ ﮐﺎﻧﺎﻝﻫﺎﯼ ﻣﺘﺼﻞ ﺑﻪ ﺑﺨﺶ ﺯﯾﺮﯾﻦ ﻧﯿﺰ‪ ،‬ﺑﺮﮔﺸﺖ ﺩﺍﺩﻥ‬ ‫ﺳﯿﺴــﺘﻢ ﻭﺯﺵ ﻃﺒﯿﻌﯽ ﻧﺴــﺒﺖ ﺑﻪ ﺳﯿﺴــﺘﻢ ﺍﺟﺒﺎﺭﯼ ﺑﺎﺯﺩﻩ‬ ‫ﮐﻤﺘﺮﯼ ﺩﺍﺭﺩ ﻭ ﺑﻪ ﺩﻟﯿﻞ ﺳــﺮﻋﺖ ﮐﻢ ﺟﺮﯾــﺎﻥ ﻫﻮﺍ‪ ،‬ﺍﺑﻌﺎﺩ ﮐﺎﻧﺎﻝﻫﺎ‬ ‫ﺑﺰﺭﮒﺗﺮ ﻣﯽﺷــﻮﻧﺪ‪ .‬ﺑﻪ ﻃﻮﺭ ﻣﻌﻤﻮﻝ ﮐﻮﺭﻩﻫــﺎﯼ ﻫﻮﺍﯼ ﮔﺮﻡ ﺍﺯ ﻧﻮﻉ‬ ‫ﻓﻦﺩﺍﺭ ﻣﻮﺭﺩ ﺍﺳــﺘﻔﺎﺩﻩ ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﻧﺪ ﻭ ﺳــﺮﻋﺖ ﮔﺮﻣﺎﯾﺶ ﺩﺭ ﺁﻧﻬﺎ‬ ‫ﺑﯿﺸــﺘﺮ ﺍﺳــﺖ‪ .‬ﻓﻦ ﺍﯾﻦﮔﻮﻧﻪ ﮐﻮﺭﻩﻫﺎ ﻣﻌﻤﻮﻻ ﺍﺯ ﻧﻮﻉ ﮔﺮﯾﺰ ﺍﺯ ﻣﺮﮐﺰ‬

‫ﻗﻄﻌــﺎﺕ ﺍﺻﻠــﯽ ﮐﻮﺭﻩﻫﺎﯼ ﻫــﻮﺍﯼ ﮔﺮﻡ ﻋﺒﺎﺭﺗﻨﺪ ﺍﺯ ﻣﺸــﻌﻞ‪،‬‬ ‫ﻣﺤﻔﻈــﻪ ﺍﺣﺘﺮﺍﻕ ﻭ ﻓﻦ‪ .‬ﮐﻮﺭﻩﻫﺎﯼ ﻫــﻮﺍﯼ ﮔﺮﻡ ﺑﺎ ﺗﻮﺟﻪ ﺑﻪ ﺍﻣﮑﺎﻥ‬ ‫ﺗﻌﻮﯾﺾ‪ ،‬ﭘﺎﮐﺴــﺎﺯﯼ ﻭ ﺭﻃﻮﺑﺖﺯﻧﯽ ﻫﻮﺍ ﻣﯽﺗﻮﺍﻧﻨﺪ ﺩﺍﺭﺍﯼ ﺗﺠﻬﯿﺰﺍﺕ‬ ‫ﺟﻨﺒــﯽ ﺑﻪ ﻣﻨﻈﻮﺭ ﻧﯿﻞ ﺑﻪ ﻣﻘﺎﺻﺪ ﯾﺎﺩ ﺷــﺪﻩ ﻧﯿﺰ ﺑﺎﺷــﻨﺪ‪ .‬ﺩﺭ ﺍﯾﻦ‬ ‫ﺻــﻮﺭﺕ ﮐﻮﺭﻩ ﻫﻮﺍﯼ ﮔﺮﻡ ﺿﻤﻦ ﺗﺎﻣﯿــﻦ ﮔﺮﻣﺎﯾﺶ ﻓﻀﺎﻫﺎ ﻣﯽﺗﻮﺍﻧﺪ‬ ‫ﻓﺮﺍﯾﻨﺪ ﻣﻄﺒﻮﻉﺳﺎﺯﯼ ﻫﻮﺍ ﺭﺍ ﻧﯿﺰ ﺑﻪ ﻋﻬﺪﻩ ﮔﯿﺮﺩ‪.‬‬

‫ﺗﻌﯿﯿﻦ ﻇﺮﻓﯿﺖ ﻭ ﺍﻧﺘﺨﺎﺏ ﮐﻮﺭﻩﻫﺎﯼ ﻫﻮﺍﯼ ﮔﺮﻡ‬ ‫ﺳﻪ ﻣﻘﺪﺍﺭ‪ ،‬ﻇﺮﻓﯿﺖ ﮔﺮﻣﺎﯾﯽ‪ ،‬ﺩﺑﯽ ﻫﻮﺍﯼ ﮔﺮﻡ ﻭ ﻓﺸﺎﺭ ﺍﺳﺘﺎﺗﯿﮏ‬ ‫ﺷﺒﮑﻪ ﮐﺎﻧﺎﻝ ﺩﺳﺘﻤﺎﯾﻪ ﺍﺻﻠﯽ ﺗﻌﯿﯿﻦ ﻇﺮﻓﯿﺖ ﻭ ﺍﻧﺘﺨﺎﺏ ﮐﻮﺭﻩﻫﺎﯼ‬ ‫ﻫﻮﺍﯼ ﮔﺮﻡ ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﻧﺪ‪ .‬ﻇﺮﻓﯿﺖ ﮔﺮﻣﺎﯾﯽ ﺑﺮ ﺍﺳــﺎﺱ ﻣﺤﺎﺳﺒﺎﺕ‬ ‫ﺍﺗﻼﻑ ﺣﺮﺍﺭﺕ ﺳــﺎﺧﺘﻤﺎﻥ ﯾﺎ ﻓﻀﺎﯾﯽ ﮐﻪ ﻗﺮﺍﺭ ﺍﺳــﺖ ﮔﺮﻡ ﺷﻮﺩ ﺑﻪ‬ ‫ﺩﺳــﺖ ﺁﻣﺪﻩ ﻭ ﺩﺑﯽ ﻫــﻮﺍﯼ ﺣﺎﻣﻞ ﺑﺎﺭ ﮔﺮﻣﺎﯾــﯽ ﺭﺍ ﻧﯿﺰ ﻣﯽﺗﻮﺍﻥ ﺍﺯ‬ ‫ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﺗﻌﯿﯿﻦ ﻧﻤﻮﺩ‪:‬‬ ‫‪Btu/hr‬‬ ‫‪1.08t 2  t1 ‬‬

‫ﺍﺳﺖ‪.‬‬ ‫ﮐــﻮﺭﻩ ﻫﻮﺍﯼ ﮔــﺮﻡ ﺭﺍ ﺍﺯ ﻧﻈﺮ ﺳــﻮﺧﺖ ﻣﺼﺮﻓﯽ ﻧﯿــﺰ ﻣﯽﺗﻮﺍﻥ‬ ‫ﻃﺒﻘﻪﺑﻨﺪﯼ ﻧﻤﻮﺩ‪ .‬ﺑﺮ ﺍﯾﻦ ﺍﺳــﺎﺱ ﺑﻨﺎ ﺑﻪ ﻧﻮﻉ ﻣﺸﻌﻞ ﻣﻤﮑﻦ ﺍﺳﺖ‬

‫‪cfm ‬‬

‫‪ =cfm‬ﻣﻘﺪﺍﺭ ﻫﻮﺍﯼ ﺣﺎﻣﻞ ﺑﺎﺭ ﮔﺮﻣﺎﯾﯽ ﺑﺮ ﺣﺴــﺐ ﻓﻮﺕ ﻣﮑﻌﺐ‬ ‫ﺩﺭ ﺩﻗﯿﻘﻪ‬

‫ﮐﻮﺭﻩﻫﺎ ﺍﺯ ﻧﻮﻉ ﮔﺎﺯﺳــﻮﺯ ﯾﺎ ﮔﺎﺯﻭﯾﯿﻞﺳــﻮﺯ ﺑﺎﺷــﻨﺪ ﻭ ﺍﺯ ﺳﻮﯼ ﺩﯾﮕﺮ‬

‫‪ =Btu/hr‬ﺑــﺎﺭ ﮔﺮﻣﺎﯾﯽ ﻓﻀﺎ ﮐﻪ ﺑﺮ ﺍﺳــﺎﺱ ﻣﺤﺎﺳــﺒﺎﺕ ﺍﺗﻼﻑ‬

‫ﻣﻤﮑﻦ ﺍﺳــﺖ ﻧﻮﻉ ﻣﺸــﻌﻞ ﮐﻮﺭﻩﻫﺎ ﻓﺎﺭﻍ ﺍﺯ ﻧﻮﻉ ﺳــﻮﺧﺖ‪ ،‬ﺍﺯ ﻧﻮﻉ‬

‫ﺣﺮﺍﺭﺕ ﺳﺎﺧﺘﻤﺎﻥ ﺑﻪ ﺩﺳﺖ ﻣﯽﺁﯾﺪ‪ ،‬ﺑﺮ ﺣﺴﺐ ﺑﯽﺗﯽﯾﻮ ﺑﺮ ﺳﺎﻋﺖ‬

‫ﻓﻦﺩﺍﺭ ﯾﺎ ﺍﺗﻤﺴﻔﺮﯾﮏ ﺑﺎﺷــﻨﺪ‪ .‬ﮐﻮﺭﻩﻫﺎﯼ ﻫﻮﺍﯼ ﮔﺮﻡ ﺫﻏﺎﻝ ﺳﻨﮕﯽ‬

‫‪ =1.08‬ﺣﺎﺻﻞﺿــﺮﺏ ﺟﺮﻡ ﻣﺨﺼﻮﺹ ﻫﻮﺍ ﺩﺭ ﮔﺮﻣﺎﯼ ﻭﯾﮋﻩ ﻫﻮﺍ‬

‫ﻧﯿﺰ ﺍﺯ ﺟﻤﻠﻪ ﻭﺍﺣﺪﻫﺎﯼ ﮔﺮﻡﮐﻨﻨﺪﻩ ﺍﺳــﺖ ﮐﻪ ﺍﻣﺮﻭﺯﻩ ﺩﺭ ﺍﯾﺮﺍﻥ ﻫﯿﭻ‬

‫ﺩﺭ ﻭﺍﺣﺪ ﺯﻣﺎﻥ‬

‫ﮐﺎﺭﺑــﺮﺩﯼ ﻧــﺪﺍﺭﺩ‪ .‬ﺩﺭ ﮐﻨــﺎﺭ ﮐﻮﺭﻩﻫﺎﯼ ﻫﻮﺍﯼ ﮔﺮﻡ ﮐــﻪ ﻫﺮ ﯾﮏ ﺑﺎ‬

‫‪(0.0749 lb/ft 3  0.24 Btu/lb.o F  60)  1.08‬‬

‫ﮔﻮﻧﻪﺍﯼ ﺍﺯ ﺳﻮﺧﺖﻫﺎﯼ ﻓﺴﯿﻠﯽ‪ ،‬ﺟﺎﻣﺪ‪ ،‬ﻣﺎﯾﻊ ﻭ ﮔﺎﺯ ﮐﺎﺭ ﻣﯽﮐﻨﻨﺪ‪،‬‬ ‫ﻣﯽﺗــﻮﺍﻥ ﺍﺯ ﮐﻮﺭﻩﻫﺎﯼ ﻫﻮﺍﯼ ﮔﺮﻡ ﺍﻟﮑﺘﺮﯾﮑــﯽ ﻧﯿﺰ ﯾﺎﺩ ﮐﺮﺩ‪ .‬ﺩﺭ ﺍﯾﻦ‬

‫‪ =t2‬ﺣﺪﺍﮐﺜﺮ ﺩﻣﺎﯼ ﻫﻮﺍﯼ ﻭﺭﻭﺩﯼ ﺑﻪ ﺍﺗﺎﻕ ﺑﺮ ﺣﺴــﺐ ﻓﺎﺭﻧﻬﺎﯾﺖ‬

‫ﻧــﻮﻉ ﮐﻮﺭﻩﻫﺎ‪ ،‬ﻣﻘﺎﻭﻣﺖ ﯾﺎ ﮐﻮﯾﻞﻫﺎﯼ ﺍﻟﮑﺘﺮﯾﮑﯽ ﻣﻨﺒﻊ ﺍﺻﻠﯽ ﺗﺎﻣﯿﻦ‬

‫ﮐﻪ ﻣﻌﻤﻮﻻ ‪ 105‬ﺩﺭﺟﻪ ﻓﺎﺭﻧﻬﺎﯾﺖ )‪ 40‬ﺩﺭﺟﻪ ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ( ﺩﺭ ﻧﻈﺮ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﻫﻮﺍ ﺭﺍ ﺑﺮﻋﻬﺪﻩ ﺩﺍﺭﻧﺪ‪.‬‬

‫ﺳﺎﺧﺘﺎﺭ ﻭ ﻗﻄﻌﺎﺕ ﺍﺻﻠﯽ‬

‫ﺻﻔﺤﻪ ‪ / 28‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﮔﺮﻓﺘﻪ ﻣﯽﺷﻮﺩ‪.‬‬

‫ﮔﯿﺮﺩ‪) :‬ﻣﻘﺮﺭﺍﺕ ﻣﻠﯽ ﺳﺎﺧﺘﻤﺎﻥ(‬

‫‪ =t1‬ﺩﻣﺎﯼ ﺯﻣﺴﺘﺎﻧﯽ ﻃﺮﺡ ﺩﺍﺧﻞ ﻓﻀﺎ ﺑﺮ ﺣﺴﺐ ﻓﻀﺎ‬

‫ﺍﻟﻒ‪ -‬ﺣﺪﺍﻗﻞ ﻓﺎﺻﻠﻪ ﺗﺎ ﻧﺰﺩﯾﮏﺗﺮﯾﻦ ﺩﯾﻮﺍﺭ‪ 15 :‬ﺳــﺎﻧﺘﯽﻣﺘﺮ )‪6‬‬

‫ﺑﻪ ﻃــﻮﺭ ﺳﺮﺍﻧﮕﺸــﺘﯽ ﻣﯽﺗﻮﺍﻥ ﺑــﻪ ﺍﺯﺍﯼ ﻫــﺮ ‪12000Btu/hr‬‬

‫ﻇﺮﻓﯿــﺖ ﮔﺮﻣﺎﯾﯽ ﻣﻘﺪﺍﺭ ﺗﻘﺮﯾﺒﯽ ﻫﻮﺍﯼ ﺣﺎﻣــﻞ ﺑﺎﺭ ﮔﺮﻣﺎﯾﯽ ﺭﺍ ﺑﯿﻦ‬ ‫‪ 300‬ﺗــﺎ ‪ 400‬ﻓﻮﺕ ﻣﮑﻌــﺐ ﺩﺭ ﺩﻗﯿﻘﻪ )‪ 8.5‬ﺗــﺎ ‪ 11‬ﻣﺘﺮﻣﮑﻌﺐ ﺩﺭ‬ ‫ﺩﻗﯿﻘﻪ( ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺖ‪.‬‬

‫ﺏ‪ -‬ﺣﺪﺍﻗﻞ ﻓﺎﺻﻠﻪ ﺗﺎ ﻣﻮﺍﺩ ﺳــﻮﺧﺘﻨﯽ‪ 30 :‬ﺳــﺎﻧﺘﯽﻣﺘﺮ )‪12‬‬ ‫ﺍﯾﻨﭻ(‬ ‫ﺝ‪ -‬ﻓﻀﺎﯼ ﺩﺳﺘﺮﺳــﯽ ﺩﺭ ﺟﻠﻮ ﺩﺳﺘﮕﺎﻩ ﻭ ﻣﺤﻞ ﻧﺼﺐ ﻣﺸﻌﻞ‪:‬‬

‫ﺗﻌﯿﯿﻦ ﻓﺸــﺎﺭ ﺍﺳــﺘﺎﺗﯿﮏ ﻓﻦ ﮐﻮﺭﻩ ﻧﯿﺰ ﺗﺎﺑﻌﯽ ﺍﺯ ﻣﻘﺪﺍﺭ ﻫﻮﺍﯼ‬ ‫ﺣﺎﻣﻞ ﺑﺎﺭ ﮔﺮﻣﺎﯾﯽ ﻭ ﺍﺑﻌﺎﺩ ﻭ ﻃﻮﻝ ﺷﺒﮑﻪ ﮐﺎﻧﺎﻝﮐﺸﯽ ﺍﺳﺖ‪.‬‬

‫ﺣﺪﺍﻗﻞ ‪ 45‬ﺳﺎﻧﺘﯽﻣﺘﺮ )‪ 18‬ﺍﯾﻨﭻ(‬ ‫ﺩ‪ -‬ﻓﻀﺎﯼ ﺍﻃﺮﺍﻑ ﺩﺳﺘﮕﺎﻩ‪ :‬ﺣﺪﺍﻗﻞ ‪ 30‬ﺳﺎﻧﺘﯽﻣﺘﺮ )‪ 12‬ﺍﯾﻨﭻ(‬

‫ﺩﺭ ﺗﻌﯿﯿــﻦ ﻇﺮﻓﯿﺖ ﮔﺮﻣﺎﯾﯽ ﮐﻮﺭﻩ ﻫﻮﺍﯼ ﮔﺮﻡ ﻻﺯﻡ ﺍﺳــﺖ ﮐﻪ‬

‫● ﺳﻄﺢ ﻣﻘﻄﻊ ﺁﺯﺍﺩ ﻭ ﺑﺪﻭﻥ ﻣﺎﻧﻊ ﻫﺮ ﯾﮏ ﺍﺯ ﮐﺎﻧﺎﻝﻫﺎﯼ ﻫﻮﺍﯼ‬

‫ﺑﯿﻦ ‪ 10‬ﺗﺎ ‪ 30‬ﺩﺭﺻﺪ ﺑﻪ ﻣﻘﺪﺍﺭ ﻣﻨﺘﺠﻪ ﺍﺯ ﻣﺤﺎﺳﺒﺎﺕ ﺍﺗﻼﻑ ﺣﺮﺍﺭﺗﯽ‬

‫ﺗﺎﺯﻩ‪ ،‬ﺑﺮﮔﺸﺖ ﻭ ﺭﻓﺖ ﻧﺒﺎﯾﺪ ﺍﺯ ‪ 4.4‬ﻣﯿﻠﯽﻣﺘﺮ ﻣﺮﺑﻊ ﺑﺮﺍﯼ ﻫﺮ‬

‫ﺳﺎﺧﺘﻤﺎﻥ ﺑﺎﺑﺖ ﺍﺗﻼﻑ ﺩﻭﺩﮐﺶ ﻭ ﺷﺒﮑﻪ ﮐﺎﻧﺎﻝ ﺍﺿﺎﻓﻪ ﺷﻮﺩ‪.‬‬

‫ﻭﺍﺕ ﻇﺮﻓﯿﺖ ﮐﻮﺭﻩ ﮐﻤﺘﺮ ﺑﺎﺷﺪ )ﻣﻘﺮﺭﺍﺕ ﻣﻠﯽ ﺳﺎﺧﺘﻤﺎﻥ(‪.‬‬ ‫● ﺗﺎﻣﯿﻦ ﻫﻮﺍﯼ ﺗﺎﺯﻩ ﯾﺎ ﺑﺮﮔﺸــﺖ ﮐﻮﺭﻩ ﻫــﻮﺍﯼ ﮔﺮﻡ ﺍﺯ ﺣﻤﺎﻡ‪،‬‬

‫ﻣﻘﺮﺭﺍﺕ ﻭ ﺗﻮﺻﯿﻪﻫﺎ‬ ‫● ﻧﺼــﺐ ﮐﻮﺭﻩﻫﺎﯼ ﻫﻮﺍﯼ ﮔﺮﻡ ﺩﺭ ﻓﻀﺎﻫﺎﯾﯽ ﻣﺎﻧﻨﺪ ﺭﺍﻫﺮﻭﻫﺎﯼ‬ ‫ﺩﺳﺘﺮﺳﯽ ﻭ ﺧﺮﻭﺝ ﺍﺿﻄﺮﺍﺭﯼ ﺳﺎﻟﻦﻫﺎﯼ ﺍﺟﺘﻤﺎﻋﺎﺕ‪ ،‬ﺗﺌﺎﺗﺮ‬ ‫ﻭ ﺳﯿﻨﻤﺎ ﻣﺠﺎﺯ ﻧﯿﺴﺖ )ﻣﻘﺮﺭﺍﺕ ﻣﻠﯽ ﺳﺎﺧﺘﻤﺎﻥ(‪.‬‬ ‫● ﺑــﺮﺍﯼ ﻧﺼﺐ ﮐــﻮﺭﻩ ﻫﻮﺍﯼ ﮔﺮﻡ ﺑﺎﯾﺪ ﻧــﮑﺎﺕ ﺯﯾﺮ ﻣﺪﻧﻈﺮ ﻗﺮﺍﺭ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺍﯾﻨﭻ(‬

‫ﺗﻮﺍﻟــﺖ‪ ،‬ﺩﺳﺘﺸــﻮﯾﯽ‪ ،‬ﺁﺷــﭙﺰﺧﺎﻧﻪ‪ ،‬ﭘﺎﺭﮐﯿﻨــﮓ ﻭ ﻓﻀﺎﻫﺎﯼ‬ ‫ﭘﺮﺧﻄﺮ ﻣﺠﺎﺯ ﻧﯿﺴﺖ )ﻣﻘﺮﺭﺍﺕ ﻣﻠﯽ ﺳﺎﺧﺘﻤﺎﻥ(‪.‬‬ ‫● ﺑﺮﮔﺸــﺖ ﻫﻮﺍﯼ ﯾﮏ ﻭﺍﺣﺪ ﺁﭘﺎﺭﺗﻤﺎﻧﯽ ﻧﺒﺎﯾﺪ ﺗﻮﺳﻂ ﺩﺳﺘﮕﺎﻩ‬ ‫ﺑﻪ ﻭﺍﺣــﺪ ﺁﭘﺎﺭﺗﻤﺎﻧﯽ ﺩﯾﮕﺮ ﻓﺮﺳــﺘﺎﺩﻩ ﺷــﻮﺩ )ﻣﻘﺮﺭﺍﺕ ﻣﻠﯽ‬ ‫ﺳﺎﺧﺘﻤﺎﻥ(‪.‬‬

‫ﺳﺎﺯﻧﺪﻩ ﻣﺮﻏﻮﺏﺗﺮﯾﻦ ﻓﻦﮐﻮﯾﻞ ﺳﺎﺧﺖ ﺍﯾﺮﺍﻥ‬ ‫ﻓﻦﮐﻮﯾﻞﻫﺎﯼ ﻃﺮﺡ ﺻﺒﺎ ﺳﺎﺧﺘﻪﺷﺪﻩ ﺍﺯ ﻣﺮﻏﻮﺏﺗﺮﯾﻦ ﻣﻮﺍﺩ ﺍﻭﻟﯿﻪ ﻭ‬ ‫ﭘﯿﺸﺮﻓﺘﻪﺗﺮﯾﻦ ﻣﺘﺪﻫﺎﯼ ﺳﺎﺧﺖ ﻭ ﺗﺠﻬﯿﺰﺍﺕ ﺑﺴﯿﺎﺭ ﭘﯿﺸﺮﻓﺘﻪ‪ ،‬ﺩﺭ‬ ‫ﺍﻏﻠﺐ ﮐﺎﺭﺑﺮﯼﻫﺎﯼ ﻣﺴﮑﻮﻧﯽ‪ ،‬ﺗﺠﺎﺭﯼ ﻭ ﺍﺩﺍﺭﯼ‪ ،‬ﻧﯿﺎﺯ ﺑﻬﺮﻩﺑﺮﺩﺍﺭﺍﻥ‬ ‫ﺍﯾﻦ ﺗﺠﻬﯿﺰﺍﺕ ﺭﺍ ﺑﺮﻃﺮﻑ ﻣﯽﻧﻤﺎﯾﺪ‪.‬‬

‫ﻓﻦﮐﻮﯾﻞ ﺻﺒﺎ‪ ،‬ﺑﻬﺘﺮﯾﻦ ﻓﻦﮐﻮﯾﻞ ﺍﯾﺮﺍﻧﯽ ﺩﺭ ﺍﯾﺮﺍﻥ ﻭ ﺧﺎﻭﺭﻣﯿﺎﻧﻪ‬ ‫ﻭ ﺗﻨﻬﺎ ﺭﻗﯿﺐ ﺳﺮﺳﺨﺖ ﻓﻦﮐﻮﯾﻞﻫﺎﯼ ﺍﺭﻭﭘﺎﯾﯽ ﺩﺭ ﺍﯾﺮﺍﻥ‬ ‫‪ ۰۲۲۹-۴۵۸۴۹۷۳-۷‬ﻭ ‪۰۲۱-۸۸۷۳۹۸۸۰-۲‬‬ ‫ﺷﻤﺎﺭﻩﻫﺎﯼ ﺗﻤﺎﺱ‪۰۲۲۹-۴۵۸۴۹۷۳-۷ :‬‬ ‫‪۰۲۱--۸۸۵۰۴۷۷۰‬‬ ‫‪۰۲۱‬‬ ‫‪۸۸۵۰۴۷۷۰-۴‬‬ ‫ﻭ ‪-۴‬‬ ‫ﺷﻤﺎﺭﻩ ﻓﺎﮐﺲ‪:‬‬

‫‪ ۰۲۱‬ﻭ ‪۰۲۲۹ -۴۵۸۵۰۷۹‬‬ ‫‪۰۲۱--۸۸۷۶۶۷۹۴‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺻﻔﺤﻪ ‪ / 29‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻓﻨﻰ‬

‫ﻣﻨﺎﺑﻊ ﺗﻮﻟﻴﺪ ﺁﺏﮔﺮﻡ ﻣﺼﺮﻓﻰ‬ ‫ﻓــﺎﺭﻍ ﺍﺯ ﻣﻨﺎﺑﻊ ﺗﻮﻟﯿﺪ ﺁﺏﮔﺮﻡ ﻣﺼﺮﻓﯽ ﻣﺴــﺘﻘﯿﻢ ﻣﺎﻧﻨﺪ ﺍﻧﻮﺍﻉ‬ ‫ﺁﺏﮔﺮﻣﮑﻦﻫــﺎ‪ ،‬ﮐــﻪ ﻫﻤﮕــﯽ ﺩﺍﺭﺍﯼ ﺗﺠﻬﯿــﺰﺍﺕ ﻣﻮﻟــﺪ ﮔﺮﻣﺎﯾﺶ‬ ‫ﺍﻟﮑﺘﺮﯾﮑــﯽ‪ ،‬ﺳــﻮﺧﺖ ﻓﺴــﯿﻠﯽ ﯾﺎ ﺧﻮﺭﺷــﯿﺪﯼ ﻫﺴــﺘﻨﺪ؛ ﻣﻨﺎﺑﻊ‬ ‫ﺁﺏﮔﺮﻡ ﻏﯿﺮﻣﺴــﺘﻘﯿﻢ ﻣﺎﻧﻨﺪ ﻣﻨﺎﺑﻊ ﺁﺏﮔﺮﻡ ﮐﻮﯾﻞﺩﺍﺭ ﻭ ﺩﻭﺟﺪﺍﺭﻩ ﺩﺭ‬ ‫ﺗﺎﺳﯿﺴــﺎﺕ ﮔﺮﻣﺎﯾﺶ ﻣﺮﮐﺰﯼ ﮐﺎﺭﺑﺮﺩ ﻓﺮﺍﻭﺍﻧــﯽ ﺩﺍﺭﻧﺪ‪ .‬ﺩﺭ ﺍﯾﻦﮔﻮﻧﻪ‬ ‫ﻣﻨﺎﺑﻊ ﺳــﯿﺎﻝ ﺍﻭﻟﯿﻪ ﮔــﺮﻡ ﻣﺎﻧﻨﺪ ﺑﺨﺎﺭ‪ ،‬ﺁﺏ ﺩﺍﻍ ﯾــﺎ ﺁﺏﮔﺮﻡ ﺑﺎﻋﺚ‬ ‫ﺗﻮﻟﯿﺪ ﺁﺏﮔﺮﻡ ﻣﺼﺮﻓﯽ ﻣﯽﺷﻮﻧﺪ‪ .‬ﺩﺭ ﺍﯾﻦﮔﻮﻧﻪ ﻣﻨﺎﺑﻊ ﻋﻤﻞ ﺗﻮﻟﯿﺪ ﻭ‬ ‫ﺫﺧﯿﺮﻩﺳﺎﺯﯼ ﺑﻪ ﻫﻤﺮﺍﻩ ﻫﻢ ﺍﻧﺠﺎﻡ ﻣﯽﺷﻮﺩ‪ ،‬ﺍﻣﺎ ﺩﺭ ﺑﺮﺧﯽ ﻣﻮﻟﺪﻫﺎﯼ‬

‫ﺳﺎﻧﺘﯽﮔﺮﺍﺩ( ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﻣﯽﺷﻮﺩ‪.‬‬ ‫‪ =8.33‬ﻭﺯﻥ ﻣﺨﺼﻮﺹ ﺁﺏ )‪(lb/gal‬‬ ‫‪ =r‬ﺍﺭﺯﺵ ﺣﺮﺍﺭﺗﯽ ﺳﻮﺧﺖ )ﺑﺮﺍﯼ ﺳﻮﺧﺖ ﻣﺎﯾﻊ ﺑﺮ ﺣﺴﺐ ‪Btu/‬‬

‫‪ lb‬ﻭ ﺑﺮﺍﯼ ﺳﻮﺧﺖ ﮔﺎﺯﯼ ‪(Btu/ft3‬‬ ‫‪ =Ef‬ﺑــﺎﺯﺩﻩ ﺁﺏﮔﺮﻣﮑﻦ )ﺑﺮﺍﯼ ﺁﺏﮔﺮﻣﮑﻦﻫﺎﯼ ﻧﻔﺘﯽ ‪ 65‬ﻭ ﺑﺮﺍﯼ‬ ‫ﺁﺏﮔﺮﻣﮑﻦﻫﺎﯼ ﮔﺎﺯﯼ ‪ 85‬ﺗﺎ ‪ 90‬ﺩﺭﺻﺪ ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﻣﯽﺷﻮﺩ‪(.‬‬

‫ﺗﻌﯿﯿﻦ ﺗﻮﺍﻥ ﺁﺏﮔﺮﻣﮑﻦ ﺑﺮﻗﯽ‬ ‫‪D 8.33 t‬‬ ‫‪P w‬‬ ‫‪3412‬‬

‫ﺁﺏﮔﺮﻡ ﻣﺼﺮﻓﯽ ﻣﺎﻧﻨﺪ ﺍﻧﻮﺍﻉ ﻣﺒﺪﻝﻫﺎﯼ ﭘﻮﺳﺘﻪ ﻟﻮﻟﻪ ﯾﺎ ﻣﺒﺪﻝﻫﺎﯼ‬ ‫ﻣﻤﮑﻦ ﺍﺳــﺖ ﺩﺭ ﻣﺨﺰﻥ ﺟﺪﺍﮔﺎﻧﻪﺍﯼ ﺫﺧﯿﺮﻩ ﯾﺎ ﺑﻪ ﻃﻮﺭ ﻣﺴــﺘﻘﯿﻢ‬

‫‪ =Dw‬ﻣﻘﺪﺍﺭ ﺁﺏﮔﺮﻡ ﻣﺼﺮﻓﯽ )‪(gph‬‬

‫ﻣﻮﺭﺩ ﺍﺳﺘﻔﺎﺩﻩ ﻗﺮﺍﺭ ﮔﯿﺮﺩ‪.‬‬

‫‪ =Δt‬ﺍﺧﺘﻼﻑ ﺩﻣﺎﯼ ﺁﺏ ﺳــﺮﺩ ﻭﺭﻭﺩﯼ ﻭ ﺁﺏﮔﺮﻡ ﺧﺮﻭﺟﯽ )‪(oF‬‬

‫ﺑــﻪ ﻃﻮﺭ ﮐﻠﯽ ﺩﻣﺎﯼ ﺁﺏ ﻭﺭﻭﺩﯼ ﺑﻪ ﻣﻨﺒﻊ ﺑﯿﻦ ‪ 40‬ﺗﺎ ‪ 60‬ﺩﺭﺟﻪ‬ ‫ﻓﺎﺭﻧﻬﺎﯾﺖ )‪ 4.5‬ﺗﺎ ‪ 15‬ﺩﺭﺟﻪ ﺳﺎﻧﺘﯽﮔﺮﺍﺩ( ﻭ ﺩﻣﺎﯼ ﺁﺏﮔﺮﻡ ﺧﺮﻭﺟﯽ‬

‫ﮐــﻪ ﻣﻌﻤــﻮﻻ ﺑﯿﻦ ‪ 80‬ﺗﺎ ‪ 100‬ﺩﺭﺟــﻪ ﻓﺎﺭﻧﻬﺎﯾﺖ )‪ 45‬ﺗــﺎ ‪ 55‬ﺩﺭﺟﻪ‬ ‫ﺳﺎﻧﺘﯽﮔﺮﺍﺩ( ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﻣﯽﺷﻮﺩ‪.‬‬

‫ﺍﺯ ﻣﻨﺒــﻊ ‪ 140‬ﺩﺭﺟــﻪ ﻓﺎﺭﻧﻬﺎﯾﺖ )‪ 60‬ﺩﺭﺟﻪ ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ( ﺩﺭ ﻧﻈﺮ‬

‫‪ =3412‬ﺿﺮﯾﺐ ﺗﺒﺪﯾﻞ ﮐﯿﻠﻮﻭﺍﺕ ﺑﻪ ﺑﯽﺗﯽﯾﻮ ﺩﺭ ﺳﺎﻋﺖ‬

‫ﮔﺮﻓﺘﻪ ﻣﯽﺷﻮﺩ‪.‬‬

‫ﺑﺎ ﺩﺭ ﺍﺧﺘﯿﺎﺭ ﺩﺍﺷــﺘﻦ ﻣﻘــﺪﺍﺭ ﮔﺮﻣﺎﯼ ﻣﻮﺭﺩ ﻧﯿــﺎﺯ ﺑﺮﺍﯼ ﺗﻬﯿﻪ‬ ‫ﺁﺏﮔــﺮﻡ ﻣﺼﺮﻓﯽ ﻣﯽﺗــﻮﺍﻥ ﺍﺯ ﻃﺮﯾﻖ ﺭﺍﺑﻄﻪ ﺳــﺎﺩﻩﺗﺮ ﺯﯾﺮ ﻧﯿﺰ ﺗﻮﺍﻥ‬

‫ﺗﻌﯿﯿﻦ ﻣﻘﺪﺍﺭ ﺳﻮﺧﺖ ﺁﺏﮔﺮﻣﮑﻦﻫﺎ‬ ‫ﺍﺯ ﻃﺮﯾﻖ ﺭﻭﺍﺑﻂ ﺯﯾﺮ ﻣﯽﺗﻮﺍﻥ ﺩﺑﯽ ﻭﺯﻧﯽ ﻭ ﺩﺑﯽ ﺣﺠﻤﯽ ﺳﻮﺧﺖ‬

‫ﺍﻟﮑﺘﺮﯾﮑﯽ ﺭﺍ ﺑﺮ ﺣﺴﺐ ‪ kw‬ﺗﻌﯿﯿﻦ ﻧﻤﻮﺩ‪:‬‬

‫‪Q‬‬ ‫‪3412‬‬

‫‪8.33D w t‬‬ ‫ﻓﺴﯿﻠﯽ‬ ‫ﻣﺎﯾﻊ ﻭ ﮔﺎﺯﯼ ﺑﺮﺍﯼ ﺁﺏﮔﺮﻣﮑﻦﻫﺎﯼ ﻣﺴﺘﻘﯿﻢ ﮐﻪ ﺑﺎ‬ ‫ﺳﻮﺧﺖ ‪W ‬‬

‫ﮐﺎﺭ ﻣﯽﮐﻨﻨﺪ ﺭﺍ ﺗﻌﯿﯿﻦ ﻧﻤﻮﺩ‪:‬‬

‫‪P‬‬

‫‪r  Ef‬‬

‫‪8.33D w t‬‬ ‫‪r  Ef‬‬

‫‪V‬‬

‫‪ =8.33‬ﻭﺯﻥ ﻣﺨﺼﻮﺹ ﺁﺏ )‪(lb/gal‬‬ ‫ﻣﻘﺪﺍﺭ ﺑﺮﻕ ﻣﺼﺮﻓﯽ ﺑﺮ ﺣﺴﺐ ﮐﯿﻠﻮﻭﺍﺕ ﺳﺎﻋﺖ ﺭﺍ ﻧﯿﺰ ﻣﯽﺗﻮﺍﻥ‬ ‫ﺍﺯ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﺗﻌﯿﯿﻦ ﻧﻤﻮﺩ‪:‬‬

‫‪ =W‬ﺩﺑﯽ ﺳﻮﺧﺖ ﻣﺎﯾﻊ )‪(lb/hr‬‬

‫‪D t‬‬ ‫‪KWH  0.00275 w‬‬ ‫‪Ef‬‬

‫‪ =V‬ﻣﻘﺪﺍﺭ ﮔﺎﺯ ﻣﺼﺮﻓﯽ )‪(ft3/hr‬‬ ‫‪ =Dw‬ﻣﻘﺪﺍﺭ ﺁﺏﮔﺮﻡ ﻣﺼﺮﻓﯽ )‪(gph‬‬ ‫‪ =Δt‬ﺍﺧﺘﻼﻑ ﺩﻣﺎﯼ ﺁﺏ ﺳﺮﺩ ﻭﺭﻭﺩﯼ ﺑﺎ ﺁﺏﮔﺮﻡ ﺧﺮﻭﺟﯽ )‪(oF‬‬ ‫ﮐــﻪ ﻣﻌﻤــﻮﻻ ﺑﯿﻦ ‪ 80‬ﺗﺎ ‪ 100‬ﺩﺭﺟــﻪ ﻓﺎﺭﻧﻬﺎﯾﺖ )‪ 45‬ﺗــﺎ ‪ 55‬ﺩﺭﺟﻪ‬

‫ﺗﻌﯿﯿﻦ ﺑﺎﺭ ﮔﺮﻣﺎﯾﯽ ﻣﻨﺎﺑﻊ ﺁﺏﮔﺮﻡ ﻏﯿﺮﻣﺴﺘﻘﯿﻢ‬ ‫ﻇﺮﻓﯿﺖ ﮔﺮﻣﺎﯾﺸــﯽ ﻣﻨﺎﺑﻊ ﺩﻭﺟﺪﺍﺭﻩ ﯾﺎ ﻣﻨﺎﺑﻊ ﮐﻮﯾﻞﺩﺍﺭ ﺁﺏﮔﺮﻡ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺻﻔﺤــﻪﺍﯼ‪ ،‬ﺁﺏﮔــﺮﻡ ﻣﺼﺮﻓﯽ ﺑﻪ ﺻﻮﺭﺕ ﻟﺤﻈﻪﺍﯼ ﺗﻮﻟﯿﺪ ﺷــﺪﻩ ﻭ‬

‫‪ =P‬ﺗﻮﺍﻥ ﺍﻟﮑﺘﺮﯾﮑﯽ )‪(kw‬‬

‫ﺻﻔﺤﻪ ‪ / 30‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺍﺯ ﻃﺮﯾﻖ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﻗﺎﺑﻞ ﻣﺤﺎﺳﺒﻪ ﺍﺳﺖ‪:‬‬

‫‪Vt  D m  Df  Ds‬‬

‫‪Q  D w 8.33 t‬‬

‫‪ =Vt‬ﺣﺠﻢ ﻣﻨﺒﻊ )‪(gal‬‬ ‫‪ =Dm‬ﺣﺪﺍﮐﺜﺮ ﻣﺼﺮﻑ ﺁﺏﮔﺮﻡ ﺑﺮ ﺣﺴﺐ ﮔﺎﻟﻦ ﺩﺭ ﺳﺎﻋﺖ ﮐﻪ ﺍﺯ‬

‫‪ =Q‬ﻇﺮﻓﯿﺖ ﮔﺮﻣﺎﯾﯽ ﻣﻨﺒﻊ )‪(Btu/hr‬‬

‫ﻃﺮﯾﻖ ﺟﺪﻭﻝ )‪ (1‬ﺗﻌﯿﯿﻦ ﻣﯽﺷﻮﺩ‪.‬‬

‫‪ =Dw‬ﻣﻘﺪﺍﺭ ﻭﺍﻗﻌﯽ ﺁﺏﮔﺮﻡ ﻣﺼﺮﻓﯽ )‪(gph‬‬ ‫)ﺍﯾﻦ ﻣﻘﺪﺍﺭ ﺣﺎﺻﻞﺿﺮﺏ ﺣﺪﺍﮐﺜﺮ ﻣﺼﺮﻑ ﺁﺏﮔﺮﻡ ﺩﺭ ﺳــﺎﻋﺖ‬

‫‪ =Df‬ﺿﺮﯾﺐ ﺗﻘﺎﺿﺎ ﺑﺮ ﻣﺒﻨﺎﯼ ﺟﺪﻭﻝ )‪(1‬‬ ‫‪ =Ds‬ﺿﺮﯾﺐ ﺫﺧﯿﺮﻩ ﻣﻨﺒﻊ ﺑﺮ ﻣﺒﻨﺎﯼ ﺟﺪﻭﻝ )‪(1‬‬

‫ﺩﺭ ﺿﺮﯾﺐ ﺗﻘﺎﺿﺎ ﺍﺳﺖ‪(.‬‬ ‫‪ =Δt‬ﺍﺧﺘﻼﻑ ﺩﻣﺎﯼ ﺁﺏ ﺳﺮﺩ ﻭﺭﻭﺩﯼ ﻭ ﺁﺏﮔﺮﻡ ﺧﺮﻭﺟﯽ )‪(oF‬‬ ‫)ﺍﯾﻦ ﻣﻘﺪﺍﺭ ﻣﻌﻤﻮﻻ ﺑﯿﻦ ‪ 80‬ﺗﺎ ‪ 100‬ﺩﺭﺟﻪ ﻓﺎﺭﻧﻬﺎﯾﺖ )‪ 45‬ﺗﺎ ‪55‬‬

‫ﺩﺭﺟﻪ ﺳﺎﻧﺘﯽﮔﺮﺍﺩ( ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﻣﯽﺷﻮﺩ‪(.‬‬

‫● ﻣﻨﺒﻊ ﺁﺏﮔﺮﻡ ﺑﺎﯾﺪ ﺩﺭ ﺳﻄﺤﯽ ﺗﺮﺍﺯ ﻧﺼﺐ ﺷﻮﺩ‪.‬‬

‫‪ =8.33‬ﻭﺯﻥ ﻣﺨﺼﻮﺹ ﺁﺏ )‪(lb/gal‬‬

‫● ﻇﺮﻓﯿــﺖ ﺫﺧﯿﺮﻩ ﺁﺏﮔﺮﻡ ﺑﺮﺍﯼ ﻫﺮ ﻭﺍﺣﺪ ﻣﺴــﮑﻮﻧﯽ ﻧﺒﺎﯾﺪ ﺍﺯ‬

‫ﺗﻌﯿﯿﻦ ﻣﻘﺪﺍﺭ ﺑﺨﺎﺭ ﻻﺯﻡ ﺑﺮﺍﯼ ﻣﻨﺎﺑﻊ ﮐﻮﯾﻞﺩﺍﺭ‬

‫‪Qt‬‬ ‫‪q‬‬

‫‪Ds ‬‬

‫ﺳﺎﺧﺘﻤﺎﻥ(‪.‬‬ ‫ﺑﺎﺷﺪ )ﻣﻘﺮﺭﺍﺕ ﻣﻠﯽ ﺳﺎﺧﺘﻤﺎﻥ(‪.‬‬

‫‪ =Qt‬ﺑﺎﺭ ﮔﺮﻣﺎﯾﯽ ﻣﻨﺒﻊ )‪(Btu/hr‬‬

‫● ﺩﻣــﺎﯼ ﺗﻨﻈﯿﻢ ﺷــﯿﺮ ﺍﻃﻤﯿﻨــﺎﻥ ﺑﺎﯾﺪ ﺣﺪﺍﮐﺜــﺮ ‪ 99‬ﺩﺭﺟﻪ‬

‫‪ =q‬ﮔﺮﻣﺎﯼ ﻧﻬﺎﻥ ﺑﺨﺎﺭ )‪(Btu/lb‬‬ ‫)ﺍﯾﻦ ﻣﻘﺪﺍﺭ ﺩﺭ ﺑﺨﺎﺭ ﻓﺸﺎﺭ ﺿﻌﯿﻒ ‪ 970‬ﺑﯽﺗﯽﯾﻮ ﺑﺮ ﭘﻮﻧﺪ ﺍﺳﺖ‪(.‬‬ ‫ﻇﺮﻓﯿــﺖ ﺗﻠﻪ ﺑﺨﺎﺭ ﻧﯿﺰ ﺳــﻪ ﺑﺮﺍﺑــﺮ ﺩﺑﯽ ﺑﺨــﺎﺭ ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻪ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫‪ 110‬ﻟﯿﺘﺮ )‪ 29‬ﮔﺎﻟﻦ ﺁﻣﺮﯾﮑﺎﯾﯽ( ﮐﻤﺘﺮ ﺑﺎﺷﺪ )ﻣﻘﺮﺭﺍﺕ ﻣﻠﯽ‬ ‫● ﻣﺨﺰﻥ ﺁﺏﮔﺮﻡ ﺑﺎﯾﺪ ﻣﺠﻬﺰ ﺑﻪ ﺷــﯿﺮ ﺍﻃﻤﯿﻨﺎﻥ ﻭ ﺷﯿﺮ ﺗﺨﻠﯿﻪ‬

‫‪ =Ds‬ﺩﺑﯽ ﺑﺨﺎﺭ )‪(lb/hr‬‬

‫ﻣﯽﺷﻮﺩ‪.‬‬

‫ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ )‪ 210‬ﺩﺭﺟﻪ ﻓﺎﺭﻧﻬﺎﯾﺖ( ﺑﺎﺷﺪ )ﻣﻘﺮﺭﺍﺕ ﻣﻠﯽ‬ ‫ﺳﺎﺧﺘﻤﺎﻥ(‪.‬‬ ‫● ﻓﺸــﺎﺭ ﺗﻨﻈﯿﻢ ﺷــﯿﺮ ﺍﻃﻤﯿﻨﺎﻥ ﺑﺎﯾﺪ ﺑﺮﺍﺑﺮ ﺣﺪﺍﮐﺜﺮ ﻓﺸﺎﺭ ﮐﺎﺭ‬ ‫ﻣﺠــﺎﺯ ﺁﺏﮔﺮﻣﮑــﻦ ﻭ ﺣﺪﺍﮐﺜــﺮ ‪ 1035‬ﮐﯿﻠﻮﭘﺎﺳــﮑﺎﻝ )‪10‬‬

‫ﺗﻌﯿﯿﻦ ﺩﺑﯽ ﺁﺏﮔﺮﻡ ﻣﺪﺍﺭ ﺍﻭﻟﯿﻪ ﻣﻨﺎﺑﻊ‬

‫ﺍﺗﻤﺴﻔﺮ( ﺑﺎﺷﺪ )ﻣﻘﺮﺭﺍﺕ ﻣﻠﯽ ﺳﺎﺧﺘﻤﺎﻥ(‪.‬‬

‫ﻣﻘــﺪﺍﺭ ﺁﺏﮔﺮﻡ ﯾﺎ ﺁﺏ ﺩﺍﻍ ﻣــﺪﺍﺭ ﺍﻭﻟﯿﻪ ﻣﻨﺎﺑﻊ ﮐــﻪ ﺑﺮﺍﯼ ﮔﺮﻡ‬ ‫ﻧﻤﻮﺩﻥ ﺁﺏ ﻣﺼﺮﻓﯽ ﻣﻮﺭﺩ ﺍﺳــﺘﻔﺎﺩﻩ ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﺩ‪ ،‬ﺍﺯ ﻃﺮﯾﻖ ﺭﺍﺑﻄﻪ‬ ‫ﺯﯾﺮ ﻗﺎﺑﻞ ﻣﺤﺎﺳﺒﻪ ﺍﺳﺖ‪:‬‬

‫ﻣﻘﺮﺭﺍﺕ ﻭ ﺗﻮﺻﯿﻪﻫﺎ‬

‫‪Qt‬‬ ‫‪8.33 60 t‬‬

‫‪D‬‬

‫ﺑﻪ ﺩﯾﻮﺍﺭ ﻣﺤﻞ ﻧﺼﺐ ﻣﺤﮑﻢ ﺷﻮﻧﺪ‪.‬‬ ‫● ﺑﺮﺍﯼ ﺫﺧﯿﺮﻩﺳــﺎﺯﯼ ﺁﺏﮔﺮﻡ ﺑﯿﺶ ﺍﺯ ‪ 1000‬ﻟﯿﺘﺮ )‪ 260‬ﮔﺎﻟﻦ‬ ‫ﺁﻣﺮﯾﮑﺎﯾﯽ( ﺑﻬﺘﺮ ﺍﺳــﺖ ﺍﺯ ﻣﻨﺎﺑﻊ ﺁﺏﮔﺮﻡ ﮐﻮﯾﻞﺩﺍﺭ ﺑﻪ ﺟﺎﯼ‬ ‫ﻣﻨﺎﺑﻊ ﺩﻭﺟﺪﺍﺭﻩ ﺍﺳﺘﻔﺎﺩﻩ ﺷﻮﺩ‪.‬‬

‫‪ =D‬ﺩﺑﯽ ﺳﯿﺎﻝ ﮔﺮﻡﮐﻨﻨﺪﻩ )ﺁﺏﮔﺮﻡ ﯾﺎ ﺩﺍﻍ( )‪(gpm‬‬

‫● ﺑﻬﺘﺮ ﺍﺳــﺖ ﭘﻤﭗ ﺳــﯿﺮﮐﻮﻻﺗﻮﺭ ﺟﺪﺍﮔﺎﻧــﻪﺍﯼ ﺑﺮﺍﯼ ﮔﺮﺩﺵ‬

‫‪ =Qt‬ﺑﺎﺭ ﮔﺮﻣﺎﯾﯽ ﻣﻨﺒﻊ )‪(Btu/hr‬‬ ‫‪ =Δt‬ﺍﺧﺘﻼﻑ ﺩﻣﺎﯼ ﺳــﯿﺎﻝ ﮔﺮﻡﮐﻨﻨﺪﻩ ﺩﺭ ﻭﺭﻭﺩﯼ ﻭ ﺧﺮﻭﺟﯽ‬ ‫ﮐــﻪ ﻣﻌﻤﻮﻻ ‪ 30‬ﺩﺭﺟﻪ ﻓﺎﺭﻧﻬﺎﯾﺖ )‪ 16‬ﺩﺭﺟﻪ ﺳــﺎﻧﺘﯽﮔﺮﺍﺩ( ﺩﺭ ﻧﻈﺮ‬ ‫ﮔﺮﻓﺘﻪ ﻣﯽﺷﻮﺩ‪(oF) .‬‬

‫ﺁﺏﮔــﺮﻡ ﺩﺭ ﻣﻨﺎﺑﻊ ﮐﻮﯾــﻞﺩﺍﺭ ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﺷــﻮﺩ ﺗﺎ ﺩﺭ‬ ‫ﻓﺼﻮﻟﯽ ﮐﻪ ﺳﺎﺧﺘﻤﺎﻥ ﻧﯿﺎﺯﻣﻨﺪ ﮔﺮﻣﺎﯾﺶ ﻧﯿﺴﺖ‪ ،‬ﺍﯾﻦ ﭘﻤﭗ‬ ‫ﺑﺎ ﻣﺼﺮﻑ ﺑﺮﻕ ﮐﻤﺘﺮ ﮔﺮﺩﺵ ﺁﺏ ﺩﺭ ﻣﻨﺒﻊ ﺭﺍ ﻣﯿﺴﺮ ﺳﺎﺯﺩ‪.‬‬ ‫ﺩﺭ ﻏﯿﺮ ﺍﯾﻦ ﺻﻮﺭﺕ ﺑﻬﺘﺮ ﺍﺳﺖ ﺣﺪﺍﻗﻞ ﻇﺮﻓﯿﺖ ﺩﻭ ﯾﺎ ﭼﻨﺪ‬

‫‪ =8.33‬ﻭﺯﻥ ﻣﺨﺼﻮﺹ ﺁﺏ )‪(lb/gal‬‬

‫ﭘﻤﭗ ﻣﻮﺍﺯﯼ ﺳﯿﺴــﺘﻢ ﺑﺮﺍﺑﺮ ﺑﺎ ﻇﺮﻓﯿﺖ ﺩﺑﯽ ﻣﻨﺒﻊ ﺁﺏﮔﺮﻡ‬

‫‪ =60‬ﯾﮏ ﺳﺎﻋﺖ )‪ 60‬ﺩﻗﯿﻘﻪ(‬

‫ﺑﺎﺷــﺪ ﺗﺎ ﺩﺭ ﻓﺼﻞ ﺗﺎﺑﺴﺘﺎﻥ ﺑﺪﻭﻥ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﭘﻤﭗ ﻣﺠﺰﺍ‬

‫ﺗﻌﯿﯿﻦ ﺣﺠﻢ ﻣﻨﺒﻊ ﺁﺏﮔﺮﻡ ﻏﯿﺮﻣﺴﺘﻘﯿﻢ‬

‫ﺑﺘــﻮﺍﻥ ﺍﺯ ﯾﮏ ﭘﻤﭗ ﺳﯿﺴــﺘﻢ ﺑﻪ ﻣﻨﻈﻮﺭ ﮔــﺮﺩﺵ ﺁﺏ ﺩﺭ‬

‫ﺣﺠــﻢ ﻣﻨﺒﻊ ﺑﻪ ﮐﻤﮏ ﺟﺪﺍﻭﻝ ﺗﻌﯿﯿﻦ ﺣﺪﺍﮐﺜﺮ ﻣﺼﺮﻑ ﺁﺏﮔﺮﻡ‬ ‫ﻭ ﺿﺮﯾﺐ ﺗﻘﺎﺿﺎ ﺍﺯ ﻃﺮﯾﻖ ﺭﺍﺑﻄﻪ ﺯﯾﺮ ﺗﻌﯿﯿﻦ ﻣﯽﺷﻮﺩ‪.‬‬

‫● ﺑﻬﺘﺮ ﺍﺳﺖ ﮐﻪ ﺁﺏﮔﺮﻣﮑﻦﻫﺎﯼ ﻣﺨﺰﻧﯽ ﺣﺪﺍﻗﻞ ﺑﺎ ﺩﻭ ﺗﺴﻤﻪ‬

‫ﻣﻨﺒﻊ ﺑﻬﺮﻩﺑﺮﺩﺍﺭﯼ ﻧﻤﻮﺩ‪.‬‬ ‫● ﻣﻨﺒﻊ ﺁﺏﮔﺮﻡ ﺑﺎﯾﺪ ﮐﺎﻣﻼ ﻋﺎﯾﻖ ﺷﻮﺩ‪.‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺻﻔﺤﻪ ‪ / 31‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫● ﺩﺭ ﻣﻘﺎﺑﻞ ﮐﻮﯾﻞ ﺑﺎﯾﺪ ﻓﻀﺎﯼ ﮐﺎﻓﯽ ﺑﺮﺍﯼ ﺑﯿﺮﻭﻥ ﮐﺸــﯿﺪﻥ ﺁﻥ‬

‫ﻭﺯﻥ ﻟﻮﻟﻪﻫﺎ ﮐﺎﻣﻼ ﻣﻬﺎﺭ ﺷﺪﻩ ﻭ ﺑﻪ ﻓﻠﻨﭻ ﮐﻮﯾﻞ ﻭﺍﺭﺩ ﻧﺸﻮﺩ‪.‬‬

‫ﻭﺟﻮﺩﺩﺍﺷﺘﻪ ﺑﺎﺷﺪ‪ .‬ﺑﻪ ﺍﯾﻦ ﻣﻨﻈﻮﺭ ﺑﺮﺍﯼ ﺍﺗﺼﺎﻝ ﻟﻮﻟﻪﻫﺎ ﺑﻪ‬

‫● ﺩﻣﺎﺳــﻨﺞ ﺭﻭﯼ ﻣﻨﺒﻊ ﺑﺎﯾﺪ ﺑﻪ ﺻﻮﺭﺕ ﻣﻮﺭﺏ ﻧﺼﺐ ﺷــﻮﺩ ﺗﺎ‬ ‫ﺍﻣﮑﺎﻥ ﺧﻮﺍﻧﺪﻥ ﺁﻥ ﺍﺯ ﭘﺎﯾﯿﻦ ﻭﺟﻮﺩ ﺩﺍﺷﺘﻪ ﺑﺎﺷﺪ‪.‬‬

‫ﮐﻮﯾﻞ ﺑﺎﯾﺪ ﻣﻬﺮﻩﻣﺎﺳﻮﺭﻩ ﯾﺎ ﻓﻠﻨﭻ ﺩﺭ ﻧﻘﺎﻁ ﻧﺰﺩﯾﮏ ﺑﻪ ﮐﻮﯾﻞ‬

‫● ﭘﻤﭗ ﺑﺮﮔﺸــﺖ ﺁﺏﮔــﺮﻡ ﻣﺼﺮﻓﯽ ﺑﺎﯾﺪ ﺩﺍﺋﻢﮐﺎﺭ ﺑﺎﺷــﺪ ﻭ ﺩﺭ‬

‫ﭘﯿﺶﺑﯿﻨﯽ ﺷﻮﺩ‪.‬‬

‫ﺻﻮﺭﺕ ﻧﯿﺎﺯ ﺑﻪ ﺻﻮﺭﺕ ﺩﺳﺘﯽ ﺧﺎﻣﻮﺵ ﺷﻮﺩ‪.‬‬

‫● ﺑﺴﺖﻫﺎﯼ ﺁﻭﯾﺰ ﺑﺎﯾﺪ ﺑﻪ ﮔﻮﻧﻪﺍﯼ ﺗﻨﻈﯿﻢ ﺷﻮﻧﺪ ﮐﻪ ﺑﺎﺭ ﻧﺎﺷﯽ ﺍﺯ‬

‫ﺟﺪﻭﻝ )‪ (1‬ﺣﺪﺍﮐﺜﺮ ﻣﺼﺮﻑ ﺁﺏﮔﺮﻡ )‪ (gph‬ﺑﺮ ﺍﺳﺎﺱ ﻟﻮﺍﺯﻡ ﺑﻬﺪﺍﺷﺘﯽ ﻭ ﻧﻮﻉ ﮐﺎﺭﺑﺮﯼ ﺳﺎﺧﺘﻤﺎﻥ ﺑﺮﺍﯼ ﺗﻌﯿﯿﻦ ﺣﺠﻢ ﻣﻨﺒﻊ ﺁﺏ ﮔﺮﻡ‬

‫ﺩﺳﺘﺸﻮﯾﯽ ﺧﺼﻮﺻﯽ‬

‫‪2‬‬

‫‪2‬‬

‫‪2‬‬

‫‪2‬‬

‫‪2‬‬

‫‪2‬‬

‫‪2‬‬

‫‪2‬‬

‫‪2‬‬

‫ﺩﺳﺘﺸﻮﯾﯽ ﻋﻤﻮﻣﯽ‬

‫‪4‬‬

‫‪6‬‬

‫‪8‬‬

‫‪6‬‬

‫‪8‬‬

‫‪12‬‬

‫‪6‬‬

‫‪-‬‬

‫‪15‬‬

‫ﻭﺍﻥ‬

‫‪20‬‬

‫‪20‬‬

‫‪30‬‬

‫‪20‬‬

‫‪20‬‬

‫‪-‬‬

‫‪-‬‬

‫‪20‬‬

‫‪-‬‬

‫ﻇﺮﻓﺸﻮﯾﯽ‬

‫‪15‬‬

‫‪50 - 150‬‬

‫‪-‬‬

‫‪-‬‬

‫‪15‬‬

‫‪20 - 100‬‬

‫ﭘﺎﺷﻮﯾﻪ‬

‫‪3‬‬

‫‪3‬‬

‫‪12‬‬

‫‪3‬‬

‫‪3‬‬

‫‪12‬‬

‫‪-‬‬

‫‪3‬‬

‫‪3‬‬

‫ﺳﯿﻨﮏ ﺁﺷﭙﺰﺧﺎﻧﻪ‬

‫‪10‬‬

‫‪20‬‬

‫‪-‬‬

‫‪20‬‬

‫‪30‬‬

‫‪20‬‬

‫‪20‬‬

‫‪10‬‬

‫‪20‬‬

‫ﺳﯿﻨﮏ ﺁﺑﺪﺍﺭﺧﺎﻧﻪ‬

‫‪5‬‬

‫‪10‬‬

‫‪-‬‬

‫‪10‬‬

‫‪10‬‬

‫‪-‬‬

‫‪10‬‬

‫‪10‬‬

‫‪10‬‬

‫ﺩﻭﺵ‬

‫‪30‬‬

‫‪150‬‬

‫‪225‬‬

‫‪75‬‬

‫‪75‬‬

‫‪225‬‬

‫‪30‬‬

‫‪30‬‬

‫‪225‬‬

‫ﻭﺍﻥ ﺭﺧﺘﺸﻮﯾﯽ‬

‫‪20‬‬

‫‪28‬‬

‫‪-‬‬

‫‪28‬‬

‫‪28‬‬

‫‪-‬‬

‫‪-‬‬

‫‪-‬‬

‫‪-‬‬

‫ﺿﺮﯾﺐ ﺗﻘﺎﺿﺎ )‪(Df‬‬

‫‪0.30‬‬

‫‪0.30‬‬

‫‪0.40‬‬

‫‪0.25‬‬

‫‪0.25‬‬

‫‪0.40‬‬

‫‪0.30‬‬

‫‪0.30‬‬

‫‪0.40‬‬

‫ﺿﺮﯾـﺐ ﺫﺧﯿﺮﻩﺳـﺎﺯﯼ ﻣﻨﺒﻊ‬ ‫)‪(DS‬‬

‫‪1.25‬‬

‫‪0.90‬‬

‫‪1.00‬‬

‫‪0.60‬‬

‫‪0.80‬‬

‫‪1.00‬‬

‫‪2.00‬‬

‫‪2.00‬‬

‫‪1.00‬‬

‫ﻧﻮﻉ ﺳﺮﻭﯾﺲ‬

‫‪20 - 100 50 - 200 50 - 150‬‬

‫ﻓﻦﮐﻮﯾﻞ ﺻﺒﺎ‪ ،‬ﺑﻬﺘﺮﯾﻦ ﻓﻦﮐﻮﯾﻞ ﺍﯾﺮﺍﻧﯽ ﺩﺭ ﺍﯾﺮﺍﻥ ﻭ ﺧﺎﻭﺭﻣﯿﺎﻧﻪ‬ ‫ﻭ ﺗﻨﻬﺎ ﺭﻗﯿﺐ ﺳﺮﺳﺨﺖ ﻓﻦﮐﻮﯾﻞﻫﺎﯼ ﺍﺭﻭﭘﺎﯾﯽ ﺩﺭ ﺍﯾﺮﺍﻥ‬ ‫‪ ۰۲۲۹-۴۵۸۴۹۷۳-۷‬ﻭ ‪۰۲۱-۸۸۷۳۹۸۸۰-۲‬‬ ‫ﺷﻤﺎﺭﻩﻫﺎﯼ ﺗﻤﺎﺱ‪۰۲۲۹-۴۵۸۴۹۷۳-۷ :‬‬ ‫‪۰۲۱--۸۸۵۰۴۷۷۰‬‬ ‫‪۰۲۱‬‬ ‫‪۸۸۵۰۴۷۷۰-۴‬‬ ‫ﻭ ‪-۴‬‬ ‫ﺷﻤﺎﺭﻩ ﻓﺎﮐﺲ‪:‬‬

‫‪ ۰۲۱‬ﻭ ‪۰۲۲۹ -۴۵۸۵۰۷۹‬‬ ‫‪۰۲۱--۸۸۷۶۶۷۹۴‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺁﭘﺎﺭﺗﻤﺎﻥ‬

‫ﺑﺎﺷﮕﺎﻩ‬

‫ﻭﺭﺯﺷﮕﺎﻩ‬

‫ﺑﯿﻤﺎﺭﺳﺘﺎﻥ‬

‫ﻫﺘﻞ‬

‫ﮐﺎﺭﺧﺎﻧﻪ‬

‫ﺍﺩﺍﺭﯼ‬

‫ﺧﺎﻧﻪ‬ ‫ﻭﯾﻼﯾﯽ‬

‫ﻣﺪﺭﺳﻪ‬

‫ﺻﻔﺤﻪ ‪ / 32‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻓﻨﺎﻭﺭﻯ‬

‫ﻣﻼﺣﻈﺎﺕ ﺍﺟﺮﺍﻳﻰ ﺑﺮﺍﻯ‬ ‫ﻧﺼﺐ ﺗﺎﺳﻴﺴﺎﺕ ﺩﺭ ﺳﺎﺧﺘﻤﺎﻥ‬ ‫ﻣﻮﻗﻌﯿﺖ ﺍﺳﺘﻘﺮﺍﺭ‬ ‫ﻣﻮﻗﻌﯿﺖ ﻗﺮﺍﺭﮔﯿﺮﯼ ﺗﺠﻬﯿﺰﺍﺕ ﺩﺭ ﺯﯾﺮ ﮐﻒ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫‪03 UMC‬‬

‫‪03 IRC‬‬

‫‪ ‬ﺗﮑﯿﻪﮔﺎﻩﻫﺎﯼ ﻣﺮﺑﻮﻁ ﺑﻪ ﺗﺠﻬﯿﺰﺍﺕ ﺑﺎﯾﺪ ﺑﺎﻻﺗﺮ ﺍﺯ ﺳﻄﺢ ﺗﺮﺍﺯ ﻗﺮﺍﺭ ﮔﯿﺮﻧﺪ‪.‬‬

‫‪{904.3}3‬‬

‫& ]‪[1305.1.4.1‬‬ ‫‪[2408.4]2‬‬

‫‪ ‬ﺍﯾﻦ ﺗﮑﯿﻪﮔﺎﻩﻫﺎ ﺑﺎﯾﺪ ﺣﺪﺍﻗﻞ ﺩﺭ ﻓﺎﺻﻠﻪ ‪ 6in‬ﺑﺎﻻﺗﺮ ﺍﺯ ﺳﻄﺢ ﺗﺮﺍﺯ ﻗﺮﺍﺭ ﮔﯿﺮﻧﺪ‪ .‬ﺿﻤﻦ ﺁﻥ ﮐﻪ ﺍﮔﺮ ﺳﺎﺯﻧﺪﻩ ﺩﺭ‬ ‫ﺍﯾﻦ ﺯﻣﯿﻨﻪ ﺩﺳﺘﻮﺭﺍﻟﻌﻤﻠﯽ ﺭﺍ ﺍﺭﺍﺋﻪ ﮐﺮﺩﻩ ﺑﺎﺷﺪ‪ ،‬ﺍﯾﻦ ﺩﺳﺘﻮﺭﺍﻟﻌﻤﻞ ﺑﺎﯾﺪ ﻣﻌﯿﺎﺭ ﻗﺮﺍﺭ ﮔﯿﺮﺩ‪.‬‬

‫‪{904.3}5‬‬

‫& ]‪[1305.1.4.1‬‬ ‫‪[2408.4]4‬‬

‫‪ ‬ﺍﺑﻌﺎﺩ ﺩﺍﻻﻥﻫﺎﯾﯽ ﮐﻪ ﺗﺠﻬﯿﺰﺍﺕ ﺩﺭ ﺩﺍﺧﻞ ﺁﻥ ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﻧﺪ ﺣﺪﺍﻗﻞ ﺑﺎﯾﺪ ‪ 22in{30in}×30in‬ﺑﺎﺷﺪ‪.‬‬

‫‪{305.0}6‬‬

‫]‪[1305.1.4.1‬‬

‫‪ ‬ﺩﺭﯾﭽﻪﻫﺎﯼ ﺑﺎﺯﺩﯾﺪ ﺣﺪﺍﮐﺜﺮ ﺑﺎﯾﺪ ﺑﻪ ﺍﻧﺪﺍﺯﻩ ‪ 20ft‬ﺍﺯ ﻣﺤﻞ ﻗﺮﺍﺭﮔﯿﺮﯼ ﺗﺠﻬﯿﺰﺍﺕ ﻓﺎﺻﻠﻪ ﺩﺍﺷﺘﻪ ﺑﺎﺷﻨﺪ‪.‬‬

‫‪{n/a}7‬‬

‫]‪[1305.1.4.1‬‬

‫‪ ‬ﮐﻠﯿﻪ ﻻﻣﭗﻫﺎ ﻭ ﺗﺎﺳﯿﺴﺎﺕ ﺭﻭﺷﻨﺎﯾﯽ ﻧﺼﺐ ﺷﺪﻩ ﺩﺭ ﻧﺰﺩﯾﮑﯽ ﮐﻮﺭﻩﻫﺎ ﺑﺎﯾﺪ ﻣﺠﻬﺰ ﺑﻪ ﯾﮏ ﮐﻠﯿﺪ ﺭﻭﺷﻦ ﻭ‬ ‫ﺧﺎﻣﻮﺵ ﺩﺭ ﻗﺴﻤﺖ ﺩﺭﺏ ﻭﺭﻭﺩﯼ ﺑﺎﺷﻨﺪ‪.‬‬

‫‪{n/a}7‬‬

‫]‪[1305.1.4.3‬‬

‫‪ ‬ﮐﻠﯿﻪ ﭘﺮﯾﺰﻫﺎﯼ ﺑﺮﻕ ﺑﺎﯾﺪ ﺩﺭ ﻓﺎﺻﻠﻪ ﺣﺪﺍﻗﻞ ‪ 25ft‬ﺍﺯ ﺗﺠﻬﯿﺰﺍﺕ ﻧﺼﺐ ﺷﺪﻩ ﺑﺎﺷﻨﺪ‪ ،‬ﺿﻤﻦ ﺁﻥ ﮐﻪ ﻣﺪﺍﺭ ﺁﻥﻫﺎ ﻧﺒﺎﯾﺪ‬ ‫ﺑﺎ ﻣﺪﺍﺭ ﺗﺎﻣﯿﻦ ﺑﺮﻕ ﺗﺠﻬﯿﺰﺍﺕ ﺍﻟﮑﺘﺮﯾﮑﯽ ﯾﮑﯽ ﺑﺎﺷﺪ‪.‬‬

‫}‪{309.0‬‬

‫]‪[1305.1.4.3‬‬

‫‪ ‬ﮔﻮﺩﺍﻝﻫﺎﯼ ﺍﯾﺠﺎﺩ ﺷﺪﻩ ﺑﺮﺍﯼ ﻧﺼﺐ ﺗﺠﻬﯿﺰﺍﺕ ﺑﺎﯾﺪ ﺑﻪ ﻋﺮﺽ ﺣﺪﺍﻗﻞ ‪) 12in‬ﺑﺮﺍﯼ ﺳﻤﺖ ﮐﻨﺘﺮﻝ ﺣﺪﺍﻗﻞ ‪(30in‬‬ ‫ﻭ ﺍﺯ ﻗﺴﻤﺖ ﭘﺎﯾﯿﻦ ‪ 6in‬ﻓﺎﺻﻠﻪ ﺩﺍﺷﺘﻪ ﺑﺎﺷﻨﺪ‪.‬‬

‫‪{n/a}8‬‬

‫]‪[1305.1.4.2‬‬

‫}‪{604.1,2‬‬

‫]‪[1601.3.6‬‬

‫‪{n/a}8‬‬

‫]‪F3 [1305.1.4‬‬

‫‪ ‬ﺣﺪﺍﻗﻞ ﻓﺎﺻﻠﻪ ﺑﯿﻦ ﮐﺎﻧﺎﻝ ﻭ ﺯﻣﯿﻦ ﺑﺎﯾﺪ ‪ 4in‬ﺑﺎﺷﺪ‪.‬‬ ‫‪ ‬ﺩﺭﺻﻮﺭﺗﯽﮐﻪ ﻋﻤﻖ ﮔﻮﺩﺍﻝ ﺍﯾﺠﺎﺩ ﺷﺪﻩ ﺑﺮﺍﯼ ﻗﺮﺍﺭﮔﯿﺮﯼ ﺗﺠﻬﯿﺰﺍﺕ ﺑﯿﺶ ﺍﺯ ‪ 12in‬ﺑﺎﺷﺪ‪ ،‬ﺧﻂ ﻋﺒﻮﺭﯼ ﺍﺯ‬ ‫ﺩﺍﺧﻞ ﮔﻮﺩﺍﻝ ﺑﺎﯾﺪ ﺑﻪ ﺍﻧﺪﺍﺯﻩ ‪ 4in‬ﺑﺎﻻﺗﺮ ﺍﺯ ﮐﻒ ﺑﺘﻨﯽ ﯾﺎ ﺳﯿﻤﺎﻧﯽ ﻗﺮﺍﺭ ﮔﺮﻓﺘﻪ ﺑﺎﺷﺪ‪.‬‬

‫ﮐﺎﻧﺎﻝ‬

‫ﮐﻮﺭﻩ‬

‫ﻟﻮﻟﻪ ﺗﻬﻮﯾﻪ‬

‫ﻣﻮﻗﻌﯿﺖ ﻗﺮﺍﺭﮔﯿﺮﯼ ﺗﺠﻬﯿﺰﺍﺕ ﭘﺸﺖﺑﺎﻣﯽ‬

‫ﺣﺪﺍﻗﻞ ﻓﺎﺻﻠﻪ ﺑﯿﻦ ﺟﺪﺍﺭﻩ‬ ‫ﺟﺎﻧﺒﯽ ﺗﺠﻬﯿـﺰﺍﺕ ﻭ ﺩﯾﻮﺍﺭ‬ ‫ﺑﺎﯾﺪ ‪ 30in‬ﺑﺎﺷﺪ‪.‬‬

‫‪ ‬ﮐﻠﯿﻪ ﺗﺠﻬﯿﺰﺍﺕ ﭘﺸﺖﺑﺎﻣﯽ ﺑﺎﯾﺪ ﺑﺮ ﻣﺒﻨﺎﯼ‬ ‫‪ SDC D1 & D2‬ﻃﺮﺍﺣﯽ ﺷﺪﻩ ﺑﺎﺷﻨﺪ‪.‬‬

‫ﺩﺭ ﺻﻮﺭﺗﯽ ﮐﻪ ﻋﻤﻖ ﺩﺍﻻﻥ ﺍﯾﺠﺎﺩ ﺷﺪﻩ ﺩﺭ ﺯﯾﺮ ﮐﻒ ﺑﺮﺍﯼ ﻗﺮﺍﺭﮔﯿﺮﯼ ﺗﺠﻬﯿﺰﺍﺕ ﺑﯿﺶ ﺍﺯ ‪12in‬‬ ‫ﺑﺎﺷﺪ‪ ،‬ﺑﺎﯾﺪ ﺯﯾﺮ ﺁﻥ ﯾﮏ ﺑﺴﺘﺮ ﺑﺘﻨﯽ ﺑﻪ ﺿﺨﺎﻣﺖ ﺣﺪﺍﻗﻞ ‪ 4in‬ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﺷﻮﺩ‪.‬‬

‫ﺗﺼﻮﯾﺮ )‪ (2‬ﮐﻮﺭﻩ ﮔﺮﻣﺎﯾﺸﯽ‬

‫‪ ‬ﺍﻟﺰﺍﻣــﺎﺕ ﯾﺎﺩ ﺷــﺪﻩ ﺷــﺎﻣﻞ ﺗﺠﻬﯿﺰﺍﺕ‬ ‫ﻓﻬﺮﺳــﺖ ﺷــﺪﻩ ﺩﺭ ﻣﮑﺎﻥﻫــﺎﯼ ﺧﺎﺭﺟﯽ‬ ‫ﺳﺎﺧﺘﻤﺎﻥ ﻣﯽﺷﻮﺩ‪{PMI} .‬‬ ‫‪ ‬ﺳﮑﻮﯼ ﻗﺮﺍﺭﮔﯿﺮﯼ ﺗﺠﻬﯿﺰﺍﺕ ﺣﺪﺍﻗﻞ ﺑﺎﯾﺪ‬ ‫‪ 30in‬ﺑﺎﺷﺪ‪.‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫‪03 IRC 03 UMC‬‬ ‫}‪{304.4‬‬

‫]‪[1307.2‬‬

‫}‪[2406.3] {904.10.1.1‬‬

‫}‪{305.0‬‬

‫]‪[1305.1‬‬

‫ﺻﻔﺤﻪ ‪ / 33‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻭﺿﻌﯿﺖ ﺩﺳﺘﺮﺳﯽ ﺑﻪ ﺗﺠﻬﯿﺰﺍﺕ ﻧﺼﺐ ﺷﺪﻩ ﺩﺭ ﺩﺍﺧﻞ ﺳﺎﺧﺘﻤﺎﻥ‬ ‫ﻭﺿﻌﯿﺖ ﺩﺳﺘﺮﺳﯽ‬

‫ﻭﺿﻌﯿﺖ ﺩﺳﺘﺮﺳﯽ‬

‫‪03 IRC 03 UMC‬‬

‫‪ ‬ﺣﺪﺍﻗﻞ ﻓﻀﺎﯼ ﻣﻮﺭﺩ ﻧﯿﺎﺯ ﺑﺮﺍﯼ ﮐﺎﺭﮐﺮﺩ ﺳﻤﺖ‬ ‫ﮐﻨﺘﺮﻝ ﺑﺎﯾﺪ ‪ 30in‬ﺑﺎﺷﺪ‪.‬‬

‫}‪{305.0‬‬

‫]‪[1305.1‬‬

‫}‪{305.0X‬‬

‫]‪[1305.1‬‬

‫‪ ‬ﺗﺠﻬﯿــﺰﺍﺕ ﻣﮑﺎﻧﯿﮑــﯽ ﺑﺎﯾﺪ ﺍﺯ ﻋــﺮﺽ ﺩﺭﺏ‬ ‫ﻭﺭﻭﺩﯼ ﺍﺗﺎﻕ ﻣﺮﺑﻮﻃﻪ ﻋﺒﻮﺭ ﮐﻨﻨﺪ‪.‬‬

‫ﺩﺭﺏ ﺍﺗﺎﻕ ﺗﺠﻬﯿﺰﺍﺕ ﻣﮑﺎﻧﯿﮑﯽ ﺣﺪﺍﻗﻞ ﺑﺎﯾﺪ‬

‫‪{305.0} 30in‬‬

‫ﺑﺎﺷﺪ‪.‬‬

‫ﻣﯽﺗﻮﺍﻥ ﺗﺎ ‪ 18in‬ﻧﯿﺰ ﮐﺎﻫﺶ ﺩﺍﺩ‪.‬‬ ‫‪ ‬ﻋﺮﺽ ﺩﺭﺏ ﻭﺭﻭﺩﯼ ﺍﺗﺎﻕ ﺗﺠﻬﯿﺰﺍﺕ ﻣﮑﺎﻧﯿﮑﯽ‬ ‫ﺣﺪﺍﻗﻞ ﺑﺎﯾﺪ ‪ 24in‬ﺑﺎﺷﺪ‪.‬‬

‫}‪{305.1‬‬

‫‪ ‬ﻓﻀــﺎﯼ ﮐﺎﺭﯼ ﻣﻮﺟﻮﺩ ﺩﺭ ﻫﻨــﮕﺎﻡ ﺑﺎﺯ ﺑﻮﺩﻥ‬

‫‪ ‬ﺗﻨﻬﺎ ﺍﺳﺘﺜﻨﺎﯼ ﻣﻮﺭﺩ ﺍﺧﯿﺮ ﺗﺠﻬﯿﺰﺍﺕ ﮔﺮﻣﺎﯾﺸﯽ‬ ‫ﻣﻮﺭﺩ ﺍﺳﺘﻔﺎﺩﻩ ﺩﺭ ﺍﺗﺎﻕﻫﺎﺳﺖ ﮐﻪ ﻓﺎﺻﻠﻪ ﺁﻥﻫﺎ ﺭﺍ‬

‫‪03 IRC 03 UMC‬‬

‫‪{n/a}1‬‬

‫‪F2‬‬ ‫]‪[1305.1.2‬‬

‫‪F2‬‬ ‫]‪[1305.1.2‬‬

‫‪F2‬‬ ‫]‪[1305.1.2‬‬

‫ﺣﺪﺍﻗﻞ ﻓﺎﺻﻠﻪ ﺗﺠﻬﯿﺰﺍﺕ ﻣﮑﺎﻧﯿﮑﯽ ﺍﺯ ﺑﺎﻻ‪ ،‬ﭘﺎﯾﯿﻦ‬ ‫ﻭ ﺩﯾﻮﺍﺭ ﺟﺎﻧﺒﯽ ﺑﺎﯾﺪ ‪ 3in‬ﺑﺎﺷﺪ‪) .‬ﺍﯾﻦ ﻓﺎﺻﻠﻪ ﺗﺎ‬ ‫ﺩﯾﻮﺍﺭﻫﺎﯼ ﺣﺎﻓﻆ ﺑﺎﯾﺪ ‪ 1in‬ﺑﺎﺷﺪ‪ ،‬ﺿﻤﻦ ﺁﻥ ﮐﻪ ﺍﮔﺮ‬ ‫ﺳﺎﺯﻧﺪﻩ ﺩﺭ ﺍﯾﻦ ﺯﻣﯿﻨﻪ ﺩﺳﺘﻮﺭﺍﻟﻌﻤﻠﯽ ﺭﺍ ﺍﺭﺍﺋﻪ ﮐﺮﺩﻩ‬ ‫ﺑﺎﺷﺪ‪ ،‬ﺍﯾﻦ ﺩﺳﺘﻮﺭﺍﻟﻌﻤﻞ ﺑﺎﯾﺪ ﻣﻌﯿﺎﺭ ﻗﺮﺍﺭ ﮔﯿﺮﺩ‪(.‬‬ ‫ﺣﺪﺍﻗﻞ ﻋﺮﺽ ﺩﺭﺏ ﻭﺭﻭﺩﯼ ﺍﺗﺎﻕ‬ ‫ﺗﺠﻬﯿﺰﺍﺕ ﻣﮑﺎﻧﯿﮑﯽ ﺑﺎﯾﺪ ‪ 24in‬ﺑﺎﺷﺪ‪.‬‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﻋﺮﺽ ﺍﺗﺎﻕ ﺗﺠﻬﯿﺰﺍﺕ ﻣﮑﺎﻧﯿﮑﯽ ﺣﺪﺍﻗﻞ‬ ‫ﺑﺎﯾﺪ ﺑﻪ ﺍﻧﺪﺍﺯﻩ ‪ 12in‬ﺍﺯ ﻋﺮﺽ ﺗﺠﻬﯿﺰﺍﺗﯽ‬ ‫ﮐﻪ ﺩﺭ ﺁﻥ ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﺩ ﺑﯿﺸﺘﺮ ﺑﺎﺷﺪ‪.‬‬

‫ﻓﺎﺻﻠﻪ ﻟﺒﻪ ﺗﺠﻬﯿﺰﺍﺕ ﻣﮑﺎﻧﯿﮑﯽ ﺑﺎ ﺩﺭﺏ ﻭﺭﻭﺩﯼ‬ ‫ﺣﺪﺍﻗﻞ ﺑﺎﯾﺪ ﺑﻪ ﺍﻧﺪﺍﺯﻩ ‪ 6in‬ﺑﺎﺷﺪ‪.‬‬ ‫ﺣﺪﺍﻗﻞ ﻓﺎﺻﻠﻪ ﻟﺒﻪ ﺗﺠﻬﯿﺰﺍﺕ ﻣﮑﺎﻧﯿﮑﯽ ﺗﺎ ﻟﺒﻪ ﺩﺭﺏ ﻭﺭﻭﺩﯼ ﺩﺭ‬ ‫ﺣﺎﻟﺖ ﺑﺎﺯ ﺑﺎﯾﺪ ‪ 30in‬ﺑﺎﺷﺪ‪.‬‬

‫ﺗﺼﻮﯾﺮ )‪ (1‬ﺩﺭﺏ ﺩﺳﺘﺮﺳﯽ ﺑﻪ ﻣﺤﻞ ﻧﺼﺐ ﺗﺠﻬﯿﺰﺍﺕ ﻣﮑﺎﻧﯿﮑﯽ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺻﻔﺤﻪ ‪ / 34‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻧﺤﻮﻩ ﺍﺳـﺘﻘﺮﺍﺭ ﺗﺠﻬﯿـﺰﺍﺕ ﺩﺭ ﺍﺗﺎﻕ ﺯﯾﺮ‬ ‫ﺷﯿﺮﻭﺍﻧﯽ‬

‫‪03 UMC‬‬

‫‪ ‬ﺩﺭﯾﭽﻪ ﻭﺭﻭﺩﯼ ﺍﺗﺎﻕ ﺯﯾﺮ ﺷﯿﺮﻭﺍﻧﯽ ﺑﺎﯾﺪ‬ ‫ﺣﺪﺍﻗﻞ ‪ 22in×30in‬ﺑﺎﺷــﺪ ﺗﺎ ﺍﻣﮑﺎﻥ ﻋﺒﻮﺭ‬ ‫ﺗﺠﻬﯿﺰﺍﺕ ﻭ ﻭﺳﺎﯾﻞ ﻣﺮﺑﻮﻃﻪ ﺍﺯ ﻭﺭﻭﺩﯼ ﺁﻥ‬ ‫ﻭﺟﻮﺩ ﺩﺍﺷﺘﻪ ﺑﺎﺷﺪ‪.‬‬

‫}‪F4 [1305.1.3] {305.0‬‬

‫‪ ‬ﺩﺭﺻﻮﺭﺗﯽﮐــﻪ ﺍﻣــﮑﺎﻥ ﻋﺒﻮﺭ ﻭﺳــﺎﯾﻞ ﺍﺯ‬ ‫ﺩﺭﯾﭽﻪ ﻭﺭﻭﺩﯼ ﻭﺟﻮﺩ ﺩﺍﺷﺘﻪ ﺑﺎﺷﺪ ﻣﯽﺗﻮﺍﻥ‬ ‫ﺍﺑﻌﺎﺩ ﺁﻥ ﺭﺍ ﺗﺎ ‪ 20in×30in‬ﻧﯿﺰ ﮐﺎﻫﺶ ﺩﺍﺩ‪.‬‬

‫‪{n/a}9‬‬

‫]‪[1305.1.3‬‬

‫‪ ‬ﺣﺪﺍﮐﺜﺮ ﻓﺎﺻﻠﻪ ﺗﺠﻬﯿﺰﺍﺕ ﻧﺼﺐ ﺷﺪﻩ‬ ‫ﺩﺭ ﺍﺗﺎﻕ ﺯﯾﺮ ﺷــﯿﺮﻭﺍﻧﯽ ﺗﺎ ﺩﺭﯾﭽﻪ ﻭﺭﻭﺩﯼ‬ ‫ﺑﺎﯾﺪ ‪ 20ft‬ﺑﺎﺷﺪ‪.‬‬

‫}‪{n/a‬‬

‫]‪F4 [1305.1.3‬‬

‫‪ ‬ﻋﺮﺽ ﮐﻔﯽﻫﺎﯼ ﯾﮑﭙﺎﺭﭼﻪ ﻧﺼﺐ ﺷﺪﻩ‪،‬‬ ‫ﺍﺯ ﺗﺠﻬﯿﺰﺍﺕ ﺗﺎ ﺩﺭﯾﭽــﻪ ﻭﺭﻭﺩﯼ ﺍﺗﺎﻕ ﺯﯾﺮ‬ ‫ﺷﯿﺮﻭﺍﻧﯽ ﺣﺪﺍﻗﻞ ﺑﺎﯾﺪ ‪ 24in‬ﺑﺎﺷﺪ‪.‬‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫‪03 IRC‬‬

‫ﻣﻨﺒﻊ ﺍﺷﺘﻌﺎﻝ ﺑﺎﯾﺪ ﺣﺪﺍﻗﻞ‬ ‫ﺩﺭ ﻓﺎﺻﻠـﻪ ‪18in‬ﺑﺎﻻﺗـﺮ ﺍﺯ‬ ‫ﮐﻒ ﮔﺎﺭﺍﮊ ﻗـﺮﺍﺭ ﮔﯿﺮﺩ‪ ،‬ﻣﮕﺮ‬ ‫ﺩﺭ ﻣﻮﺍﻗﻌﯽ ﮐﻪ ﻣﺸﻌﻞ ﺁﻥ ﺍﺯ‬ ‫ﻧﻮﻉ ‪ FVIR‬ﺑﺎﺷﺪ‪.‬‬

‫ﺗﮑﯿﻪﮔﺎﻩ ﻣﺤﺎﻓﻆ‬ ‫‪9‬‬

‫‪F4 [1305.1.3] {305.1}10‬‬

‫‪ ‬ﺣﺪﺍﻗــﻞ ﺍﺑﻌــﺎﺩ ﺳــﮑﻮﯼ ﮐــﻒ ﺍﺗﺎﻕ‬ ‫ﺯﯾﺮﺷﯿﺮﻭﺍﻧﯽ ﺩﺭ ﺳﻤﺖ ﺳﺮﻭﯾﺲ ﺗﺠﻬﯿﺰﺍﺕ‬ ‫ﺑﺎﯾﺪ ‪ 30in×30in‬ﺑﺎﺷﺪ‪.‬‬

‫‪{n/a}9‬‬

‫‪ ‬ﺩﺭﺻﻮﺭﺗﯽﮐــﻪ ﺍﻣــﮑﺎﻥ ﺳــﺮﻭﯾﺲ ﯾــﺎ‬ ‫ﺗﻌﻮﯾــﺾ ﺗﺠﻬﯿــﺰﺍﺕ ﺍﺯ ﻃﺮﯾــﻖ ﺩﺭﯾﭽﻪ‬ ‫ﻭﺭﻭﺩﯼ ﺍﺗﺎﻕ ﺯﯾﺮ ﺷــﯿﺮﻭﺍﻧﯽ ﻭﺟﻮﺩ ﺩﺍﺷﺘﻪ‬ ‫ﺑﺎﺷــﺪ‪ ،‬ﻧﯿﺎﺯﯼ ﺑﻪ ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻦ ﺩﺍﻻﻧﯽ‬ ‫ﻣﺠﺰﺍ ﺑﺮﺍﯼ ﺗﺠﻬﯿﺰﺍﺕ ﻧﯿﺴﺖ‪.‬‬

‫‪{n/a}9‬‬

‫‪ ‬ﮐﻠﯿﺪ ﺭﻭﺷــﻦ ﻭ ﺧﺎﻣﻮﺵ ﺗﺎﺳﯿﺴــﺎﺕ‬ ‫ﺭﻭﺷــﻨﺎﯾﯽ ﺑﺎﯾﺪ ﺩﺭ ﮐﻨــﺎﺭ ﺩﺭﯾﭽﻪ ﻭﺭﻭﺩﯼ‬ ‫ﺍﺗﺎﻕ ﺯﯾﺮ ﺷــﯿﺮﻭﺍﻧﯽ ﺩﺭﻧﻈﺮ ﮔﺮﻓﺘﻪ ﺷــﺪﻩ‬ ‫ﺑﺎﺷﺪ‪.‬‬

‫‪F4 [1305.1.3.1] {n/a}9‬‬

‫]‪F4 [1305.1‬‬

‫ﺗﺼﻮﯾﺮ )‪ (4‬ﭼﮕﻮﻧﮕﯽ ﻗﺮﺍﺭﮔﯿﺮﯼ ﮐﻮﺭﻩ ﺩﺭ ﺩﺍﺧﻞ ﮔﺎﺭﺍﮊ‬

‫ﻣﻮﻗﻌﯿـﺖ ﻗﺮﺍﺭﮔﯿﺮﯼ ﺗﺠﻬﯿـﺰﺍﺕ ﺩﺭ ﺩﺍﺧﻞ‬ ‫ﮔﺎﺭﺍﮊ‬ ‫‪ ‬ﻣﻨﺒﻊ ﺍﺷﺘﻌﺎﻝ ﺑﺎﯾﺪ ﺣﺪﺍﻗﻞ ﺑﻪ ﺍﻧﺪﺍﺯﻩ ‪18in‬‬

‫]‪[1305.1.3X‬‬

‫ﺍﺯ ﮐﻒ ﮔﺎﺭﺍﮊ ﻓﺎﺻﻠﻪ ﺩﺍﺷﺘﻪ ﺑﺎﺷﺪ‪.‬‬

‫‪03 UMC‬‬

‫}‪{308.0‬‬

‫‪03 IRC‬‬

‫‪[1307.3,‬‬ ‫]‪2408.2‬‬

‫‪ EXC ‬ﻣﮑﺎﻥﻫــﺎﯼ ﻣﺠﺰﺍﯾﯽ ﮐﻪ ﺑﺎ ﻫﻮﺍﯼ‬ ‫ﮔﺎﺭﺍﮊ ﺩﺭ ﺍﺭﺗﺒﺎﻁ ﻧﺒﺎﺷــﺪ ﺑﺮﺍﯼ ﻧﺼﺐ ﻣﺸﻌﻞ‬

‫}‪{308.0‬‬

‫]‪[2408.2‬‬

‫ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻪ ﺷﺪﻩ ﺑﺎﺷﺪ‪{PMI} .‬‬ ‫‪ ‬ﯾﮑﯽ ﺩﯾﮕــﺮ ﺍﺯ ﻣﻮﺍﺭﺩ ﺍﺳــﺘﺜﻨﺎ ﺗﺠﻬﯿﺰﺍﺕ‬ ‫‪ FVIR‬ﻫﺴﺘﻨﺪ‪.‬‬

‫‪{304.1}11‬‬

‫‪F47‬‬ ‫‪[2408.2X]11‬‬

‫‪ ‬ﮐﺎﻧﺎﻟــﯽ ﮐﻪ ﺩﺭ ﻣﯿﺎﻥ ﺩﯾﻮﺍﺭﻫﺎﯼ ﻣﻘﺎﻭﻡ ﺩﺭ‬ ‫ﺑﺮﺍﺑﺮ ﺁﺗﺶ ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﺩ ﺣﺪﺍﻗﻞ ﺑﺎﯾﺪ ﺍﺯ ﻭﺭﻕ‬

‫ﻣﺤﻞ ﻗﺮﺍﺭﮔﯿﺮﯼ ﻻﻣﭗ‬

‫}‪{n/a‬‬

‫]‪[309.1.1‬‬

‫ﻧﻤﺮﻩ ‪ 26‬ﺳﺎﺧﺘﻪ ﺷﻮﺩ‪.‬‬ ‫ﺩﺭﯾﭽﻪ‬

‫ﮐﻠﯿﺪ ﺭﻭﺷﻦ ﻭ ﺧﺎﻣﻮﺵ ﻻﻣﭗ ﺑﺎﯾﺪ ﺩﺭ‬ ‫ﮐﻨﺎﺭ ﺩﺭﺏ ﻭﺭﻭﺩﯼ ﻧﺼﺐ ﺷﺪﻩ ﺑﺎﺷﺪ‪.‬‬

‫ﺗﺼﻮﯾﺮ )‪ (3‬ﭼﮕﻮﻧﮕﯽ ﻧﺼﺐ ﮐﻮﺭﻩ ﺩﺭ ﺍﺗﺎﻕ ﺯﯾﺮ ﺷﯿﺮﻭﺍﻧﯽ‬

‫ﻣﻮﻗﻌﯿـﺖ ﻗﺮﺍﺭﮔﯿﺮﯼ ﺗﺠﻬﯿـﺰﺍﺕ ﺩﺭ ﺩﺍﺧﻞ‬ ‫ﮔﺎﺭﺍﮊ‬

‫‪03 UMC‬‬

‫‪03 IRC‬‬

‫‪ ‬ﻫﯿﭻﯾــﮏ ﺍﺯ ﺩﻫﺎﻧﻪﻫــﺎﯼ ﻭﺭﻭﺩﯼ ﮐﺎﻧﺎﻝ‬ ‫ﻧﺒﺎﯾﺪ ﺩﺭ ﺩﺍﺧﻞ ﮔﺎﺭﺍﮊ ﻗﺮﺍﺭ ﮔﺮﻓﺘﻪ ﺑﺎﺷﺪ‪.‬‬

‫}‪{n/a‬‬

‫]‪[309.1.1‬‬

‫‪ ‬ﺗﺠﻬﯿﺰﺍﺕ ﺩﺍﺧــﻞ ﮔﺎﺭﺍﮊ ﺑﺎﯾﺪ ﺑﻪ ﻧﻮﻋﯽ ﺩﺭ‬ ‫ﺑﺮﺍﺑﺮ ﺿﺮﺑﻪﻫﺎﯼ ﺍﺣﺘﻤﺎﻟﯽ ﻣﺤﺎﻓﻈﺖ ﺷﻮﻧﺪ ﻭ‬ ‫ﯾﺎ ﺑﺮ ﺭﻭﯼ ﺳــﮑﻮﯾﯽ ﮐﻪ ﺣﺪﺍﻗﻞ ‪ 6ft‬ﺑﺎﻻﺗﺮ ﺍﺯ‬ ‫ﮐﻒ ﮔﺎﺭﺍﮊ ﻗﺮﺍﺭ ﺩﺍﺭﺩ ﻧﺼﺐ ﺷﻮﻧﺪ‪.‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫‪F5 [1307.3.1,‬‬ ‫}‪{308.0‬‬ ‫]‪2408.3X‬‬

‫ﺻﻔﺤﻪ ‪ / 35‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻧﺼﺐ ﺗﺠﻬﯿﺰﺍﺕ‬ ‫ﻣﻼﺣﻈﺎﺕ ﻧﺼﺐ ﺗﺠﻬﯿﺰﺍﺕ‬

‫‪03 UMC‬‬

‫‪ ‬ﺩﺭ ﺻــﻮﺭﺕ ﻧﺼــﺐ ﺗﺎﺳﯿﺴــﺎﺕ ﺟﺪﯾــﺪ‬ ‫ﺩﺭ ﺩﺍﺧﻞ ﺳــﺎﺧﺘﻤﺎﻥ ﺑﺎﯾﺪ ﭘــﻼﻥ ﺟﺪﯾﺪ ﯾﺎ‬ ‫ﺗﻐﯿﯿﺮﺍﺕ ﺍﻋﻤﺎﻝ ﺷــﺪﻩ ﺩﺭ ﺩﺍﺧﻞ ﺳﺎﺧﺘﻤﺎﻥ‬ ‫ﺑﻪ ﺗﺎﯾﯿﺪ ﻣﺮﺍﺟﻊ ﺫﯾﺼﻼﺡ ﺑﺮﺳﺪ‪.‬‬

‫}‪{114.2‬‬

‫]‪[105.7‬‬

‫‪ ‬ﺗﻤﺎﻣﯽ ﺗﺠﻬﯿﺰﺍﺕ ﻧﺼﺐ ﺷــﺪﻩ ﺩﺭ ﺩﺍﺧﻞ‬ ‫ﺳــﺎﺧﺘﻤﺎﻥ ﺑﺎﯾﺪ ﺑﻪ ﻃﻮﺭ ﮐﺎﻣﻞ ﻓﻬﺮﺳــﺖ ﻭ‬ ‫ﻋﻼﻣﺖﮔﺬﺍﺭﯼ ﺷﺪﻩ ﺑﺎﺷﻨﺪ‪.‬‬

‫}‪{n/a‬‬

‫]‪[1302.1‬‬

‫‪ ‬ﮐﻠﯿــﻪ ﺗﺠﻬﯿــﺰﺍﺕ ﺑﺎﯾــﺪ ﺑــﺮ ﻣﺒﻨــﺎﯼ‬ ‫ﺩﺳﺘﻮﺭﺍﻟﻌﻤﻞﻫﺎﯼ ﺳﺎﺯﻧﺪﻩ ﻧﺼﺐ ﺷﻮﻧﺪ‪.‬‬

‫}‪{304.1‬‬

‫‪ ‬ﮐﻠﯿﻪ ﺗﻐﯿﯿﺮﺍﺕ ﯾﺎ ﺍﺻﻼﺣﺎﺕ ﺍﻧﺠﺎﻡ ﺷــﺪﻩ‬ ‫ﺩﺭ ﺩﺍﺧﻞ ﺳﺎﺧﺘﻤﺎﻥ ﺑﺮﺍﯼ ﻧﺼﺐ ﺗﺠﻬﯿﺰﺍﺕ‬ ‫ﺑﺎﯾﺪ ﺑﺮ ﻣﺒﻨﺎﯼ ﮐﺪﻫﺎﯼ ﺟﺎﺭﯼ ﺍﻧﺠﺎﻡ ﮔﯿﺮﺩ‪.‬‬

‫}‪{104.1‬‬

‫‪ ‬ﺍﮔﺮ ﺗﺠﻬﯿﺰﺍﺗﯽ ﻗﺪﯾﻤﯽ ﺳﺎﺧﺘﻤﺎﻥ‪ ،‬ﺑﻌﺪ ﺍﺯ‬ ‫ﺍﻧﺘﺸﺎﺭ ﻭﯾﺮﺍﯾﺶ ﺟﺪﯾﺪ ﮐﺪﻫﺎ‪ ،‬ﺑﺎ ﺍﻟﺰﺍﻣﺎﺕ ﮐﺪ‬ ‫ﺟﺪﯾﺪ ﻣﻄﺎﺑﻘﺖ ﻧﺪﺍﺷﺘﻪ ﺑﺎﺷﻨﺪ‪ ،‬ﺩﺭﺻﻮﺭﺗﯽﮐﻪ‬ ‫ﺭﻋﺎﯾﺖ ﻧﮑﺎﺕ ﺍﯾﻤﻨﯽ ﻧﯿﺎﺯﯼ ﺑﻪ ﺍﻋﻤﺎﻝ ﺗﻐﯿﯿﺮ‬ ‫ﺩﺭ ﺁﻥ ﻧﯿﺴﺖ‪.‬‬

‫}‪{104.2‬‬

‫‪ ‬ﺩﺭ ﺗﻤﺎﻣــﯽ ﻣﻮﺍﺭﺩ‪ ،‬ﺗﺎﺳﯿﺴــﺎﺕ ﻣﮑﺎﻧﯿﮑﯽ‬ ‫ﺭﺍ ﺩﺭ ﺍﺭﺗﻔﺎﻋﯽ ﺑﺎﻻﺗﺮ ﺍﺯ ﺍﺭﺗﻔﺎﻉ ﺳــﺮﺭﯾﺰ ﻧﺼﺐ‬ ‫ﮐﻨﯿﺪ‪.‬‬

‫}‪{n/a‬‬

‫‪ ‬ﮐﻠﯿﻪ ﺳﯿﺴــﺘﻢﻫﺎﯼ ﻣﮑﺎﻧﯿﮑــﯽ ﻧﯿﺎﺯﻣﻨﺪ‬ ‫ﺗﻌﻤﯿﺮ ﻭ ﻧﮕﻬﺪﺍﺭﯼ ﺻﺤﯿﺢ ﻭ ﻣﻨﻈﻢ ﻫﺴﺘﻨﺪ‪.‬‬

‫}‪{104.4‬‬

‫‪ ‬ﻫﻤﻮﺍﺭﻩ ﺑﺎﯾﺪ ﺭﺍﻩﻫﺎﯼ ﺩﺳﺘﺮﺳــﯽ ﻣﻨﺎﺳﺐ‬ ‫ﺑﺮﺍﯼ ﺳﺮﻭﯾﺲ ﯾﺎ ﺗﻌﻮﯾﺾ ﺗﺠﻬﯿﺰﺍﺕ ﻭ ﻭﺳﺎﯾﻞ‬ ‫ﻧﺼﺐ ﺷــﺪﻩ ﺩﺭ ﺩﺍﺧﻞ ﺳــﺎﺧﺘﻤﺎﻥ ﺩﺭ ﻧﻈﺮ‬ ‫ﮔﺮﻓﺘﻪ ﺷﻮﺩ‪.‬‬

‫}‪{305.0‬‬

‫‪03 IRC‬‬

‫ﻣﻼﺣﻈﺎﺕ ﻧﺼﺐ ﺗﺠﻬﯿﺰﺍﺕ‬ ‫‪‬‬

‫ﭘﯿــﺶ ﺍﺯ ﺭﺍﻩﺍﻧــﺪﺍﺯﯼ ﺗﺠﻬﯿــﺰﺍﺕ‪،‬‬

‫ﺑﺴــﺘﻪﺑﻨﺪﯼﻫﺎﯼ ﺁﻥﻫﺎ ﺑﺎﯾﺪ ﺍﺯ ﺩﺳﺘﮕﺎﻩ ﺟﺪﺍ‬

‫}‪{304.1‬‬

‫]‪[1401.1‬‬

‫ﺷﻮﺩ‪.‬‬ ‫‪ ‬ﺍﻧﺪﺍﺯﻩ ﺗﺠﻬﯿﺰﺍﺕ ﺩﺭ ﻫﺮ ﮐﺎﺭﺑﺮﺩ ﺧﺎﺹ ﺑﺎﯾﺪ‬

‫‪[1401.1,‬‬ ‫]‪2408.1‬‬

‫ﺑﺎ ﺍﺳــﺘﻔﺎﺩﻩ ﺍﺯ ﺭﻭﺵﻫﺎﯼ ﻣﻮﺭﺩ ﺗﺎﯾﯿﺪ ﺍﻧﺠﺎﻡ‬

‫}‪{304.1‬‬

‫]‪[1401.3‬‬

‫ﮔﯿﺮﺩ‪.‬‬ ‫‪ ‬ﮐﻠﯿﻪ ﺗﺠﻬﯿﺰﺍﺕ ﻭ ﺗﺎﺳﯿﺴــﺎﺕ ﻧﺼﺐ ﺷﺪﻩ‬ ‫ﺩﺭ ﺧــﺎﺭﺝ ﺍﺯ ﺳــﺎﺧﺘﻤﺎﻥ ﺑﺎﯾﺪ ﻓﻬﺮﺳــﺖ ﻭ‬

‫}‪{304.1‬‬

‫]‪[1401.4‬‬

‫ﻋﻼﻣﺖﮔﺬﺍﺭﯼ ﺷﺪﻩ ﺑﺎﺷﻨﺪ‪.‬‬ ‫]‪[1202.1‬‬

‫‪ ‬ﻣﻨﺒــﻊ ﺣﺮﺍﺭﺗــﯽ ﻧﺼﺐ ﺷــﺪﻩ ﺩﺭ ﺩﺍﺧﻞ‬ ‫ﺳــﺎﺧﺘﻤﺎﻥ ﺑﺎﯾــﺪ ﻗﺎﺑﻠﯿﺖ ﺗﺎﻣﯿــﻦ ﺣﺪﺍﻗﻞ‬ ‫ﺩﻣﺎﯼ ‪ 68ºF‬ﺭﺍ ﺩﺭ ﺍﺭﺗﻔــﺎﻉ ‪ 3ft‬ﺑﺎﻻﺗﺮ ﺍﺯ ﮐﻒ‬

‫}‪{bldg‬‬

‫]‪[303.8‬‬

‫ﺑﺮﺍﯼ ﻫﺮ ﯾﮏ ﺍﺯ ﺍﺗﺎﻕﻫﺎ ﺩﺍﺷﺘﻪ ﺑﺎﺷﺪ‪.‬‬ ‫]‪[1202.1‬‬

‫‪ ‬ﺗﺎﻣﯿﻦ ﺷــﺮﺍﯾﻂ ﯾﺎﺩ ﺷــﺪﻩ ﺑﺎ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ‬

‫}‪{n/a‬‬

‫‪ ‬ﮐﻠﯿــﻪ ﺩﺭﯾﭽﻪﻫــﺎﯼ ﺗﻬﻮﯾــﻪ‪ ،‬ﺩﺭﭘﻮﺵﻫﺎ ﻭ‬ ‫‪[1401.5,‬‬

‫ﺍﺟــﺰﺍﯼ ﺟﺎﻧﺒﯽ ﺳﯿﺴــﺘﻢﻫﺎ ﺑﺎﯾﺪ ﺑــﺮ ﻣﺒﻨﺎﯼ‬

‫‪2407.7]12‬‬

‫ﺩﺳﺘﻮﺭﺍﻟﻌﻤﻞﻫﺎﯼ ﺳﺎﺯﻧﺪﻩ ﻧﺼﺐ ﺷﻮﻧﺪ‪.‬‬

‫}‪{802.6.1.1‬‬

‫‪[303.8]13‬‬

‫‪[1804.2.1,‬‬ ‫]‪2427.6.5‬‬

‫‪ ‬ﮐﻠﯿــﻪ ﺗﺠﻬﯿﺰﺍﺕ ﻭ ﻣﺘﻌﻠﻘﺎﺕ ﺁﻥﻫﺎ ﺑﺎﯾﺪ ﺑﺎ‬ ‫]‪[1202.3‬‬

‫ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﻗﻼﺏ ﯾﺎ ﺗﮑﯿﻪﮔﺎﻩﻫﺎﯼ ﻣﻨﺎﺳﺐ ﺑﻪ‬

‫}‪{304.4‬‬

‫]‪[1307.2‬‬

‫ﻧﺼﺐ ﺷﻮﻧﺪ‪.‬‬ ‫]‪[1401.2‬‬

‫‪ ‬ﺳــﻮﺭﺍﺥﮐﺎﺭﯼ‪ ،‬ﺑﺮﺵ ﻭ ﯾــﺎ ﻣﺤﮑﻢ ﮐﺮﺩﻥ‬ ‫ﺗﺠﻬﯿﺰﺍﺕ ﺑﺎ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﺗﺴﻤﻪ ﺑﺎﯾﺪ ﺑﺮ ﻣﺒﻨﺎﯼ‬

‫‪F71–74‬‬ ‫}‪{n/a‬‬

‫ﮐﺪﻫﺎﯼ ﺳﺎﺧﺘﻤﺎﻥ ﺍﻧﺠﺎﻡ ﮔﯿﺮﺩ‪.‬‬

‫‪[1308.1,‬‬ ‫]‪2405.1‬‬

‫‪ ‬ﺗﺤﺖ ﻫﯿﭻ ﺷــﺮﺍﯾﻄﯽ ﺗﻐﯿﯿﺮ‪ ،‬ﺑﺎﺭﮔﺬﺍﺭﯼ ﯾﺎ‬ ‫}‪[1304.1] {307.1.5‬‬

‫ﺍﻓﺰﻭﺩﻥ ﺑﺎﺭ ﺍﺿﺎﻓﯽ ﺑﻪ ﺧﺮﭘﺎﻫﺎﯼ ﺳــﺎﺧﺘﻤﺎﻥ‬ ‫ﻧﺒﺎﯾﺪ ﺑﺪﻭﻥ ﺗﺎﯾﯿﺪ ﻣﮑﺘﻮﺏ ﺍﻓﺮﺍﺩ ﻭﺍﺟﺪ ﺷﺮﺍﯾﻂ‬ ‫ﺍﻧﺠﺎﻡ ﭘﺬﯾﺮﺩ‪.‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫}‪{n/a‬‬

‫‪[2405.2]14‬‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﮔﺮﻡﮐﻦﻫﺎﯼ ﻗﺎﺑﻞ ﺣﻤﻞ ﻗﺎﺑﻞ ﻗﺒﻮﻝ ﻧﯿﺴﺖ‪.‬‬

‫ﺭﻭﺷــﯽ ﮐﻪ ﻣﻮﺭﺩ ﺗﺎﯾﯿﺪ ﺑﺎﺷﺪ ﺩﺭ ﻣﺤﻞ ﺧﻮﺩ‬

‫‪ ‬ﺑﻬﺮﻩﺑــﺮﺩﺍﺭﯼ ﺍﺯ ﮐﻠﯿﻪ ﺗﺠﻬﯿــﺰﺍﺕ ﺑﺎﯾﺪ ﺑﺮ‬ ‫ﻣﺒﻨــﺎﯼ ﺩﺳــﺘﻮﺭﺍﻟﻌﻤﻞﻫﺎﯼ ﺳــﺎﺯﻧﺪﻩ‪ ،‬ﺑﺎ‬ ‫ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﺳــﻮﺧﺘﯽ ﮐﻪ ﻃﺮﺍﺣﯽ ﺳﯿﺴﺘﻢ‬ ‫ﺑﺮ ﻣﺒﻨــﺎﯼ ﺁﻥ ﺍﻧﺠﺎﻡ ﮔﺮﻓﺘﻪ ﯾﺎ ﮐﯿﺖ ﻣﺒﺪﻟﯽ‬ ‫ﮐﻪ ﺳــﺎﺯﻧﺪﻩ ﺑﻪ ﻫﻤﺮﺍﻩ ﺩﺳــﺘﮕﺎﻩ ﺍﺭﺍﺋﻪ ﮐﺮﺩﻩ‬ ‫ﺍﻧﺠﺎﻡ ﮔﯿﺮﺩ‪.‬‬

‫‪03 UMC‬‬

‫‪03 IRC‬‬

‫ﺻﻔﺤﻪ ‪ / 36‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﺗﺨﺼﺼﻰ‬

‫ﻗﻮﺍﻧﻴﻦ ﻓﻦ‬ ‫ﺩﺭ ﺗﻤﺎﻡ ﻗﻮﺍﻧﯿﻦ ﻓﻦ‪:‬‬ ‫ﺷﻤﺎﺭﻩ‬

‫ﻣﺘﻐﻴﺮﻫﺎﻯ ﻭﺍﺑﺴﺘﻪ‬

‫ﻭ‬ ‫ﻣﺘﻐﻴﺮﻫﺎﻯ ﻣﺴﺘﻘﻞ‬

‫ﻣﻨﺤﻨﯽ ﻣﺒﻨﺎ ﺑﻪ ﺩﺳﺖ ﻣﯽﺁﯾﺪ‪ .‬ﻣﺜﻼ‪ ،‬ﻧﻘﻄﻪ ‪ (N1=650)E‬ﺍﺯ ﻧﻘﻄﻪ‬ ‫‪ (N2=600)D‬ﺑﻪ ﺻﻮﺭﺕ ﺯﯾﺮ ﻣﺤﺎﺳﺒﻪ ﻣﯽﺷﻮﺩ‪:‬‬ ‫ﺑﺎ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﻗﺎﻧﻮﻥ ﻓﻦ ‪ 1a‬ﺩﺭ ﻧﻘﻄﻪ ‪:E‬‬

‫ﺑﻨﺎﺑﺮﺍﯾﻦ ﻣﻨﺤﻨﯽ ‪ N=650 ،P1f1‬ﺗﮑﻤﯿﻞ ﺷــﺪﻩ ﺭﺍ ﻣﯽﺗﻮﺍﻥ ﺑﺎ‬ ‫ﻣﺤﺎﺳــﺒﻪ ﻧﻘﺎﻁ ﺍﺿﺎﻓﯽ ﺍﺯ ﺩﺍﺩﻩﻫﺎﯼ ﻣﻮﺟﻮﺩ ﺩﺭ ﻣﻨﺤﻨﯽ ﻣﺒﻨﺎ‪ ،‬ﻣﺜﻼ‬ ‫ﻧﻘﻄﻪ ‪ G‬ﺍﺯ ﻧﻘﻄﻪ ‪ ،F‬ﺍﯾﺠﺎﺩ ﻧﻤﻮﺩ‪.‬‬ ‫ﺍﮔﺮ ﻧﻘﺎﻁ ﻣﻌﺎﺩﻝ ﺭﺗﺒﻪﺑﻨﺪﯼ ﺑﻪ ﻫﻢ ﻭﺻﻞ ﺷﻮﻧﺪ‪ ،‬ﭼﻨﺎﻥ ﮐﻪ ﺗﻮﺳﻂ‬ ‫ﺧﻄﻮﻁ ﻧﻘﻄﻪﭼﯿﻦ ﻧﺸﺎﻥ ﺩﺍﺩﻩ ﺷﺪﻩ ﺍﺳﺖ‪ ،‬ﺍﯾﻦ ﻧﻘﺎﻁ ﻫﻤﮕﯽ ﺑﺮ ﺭﻭﯼ‬ ‫ﺳﻬﻤﯽﻫﺎﯾﯽ ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﻧﺪ ﮐﻪ ﺑﻪ ﻭﺳﯿﻠﻪ ﺭﺍﺑﻄﻪﯼ ﻧﺸﺎﻥ ﺩﺍﺩﻩ ﺷﺪﻩ‬ ‫ﺩﺭ ﻣﻌﺎﺩﻟﻪ )‪ (1‬ﺑﯿﺎﻥ ﻣﯽﺷﻮﻧﺪ‪.‬‬

‫ﻣﻨﺤﻨﻰ ‪Ptf‬‬ ‫ﻣﺤﺎﺳﺒﻪ ﺷﺪﻩ‬

‫‪ a‬ﺯﻳﺮﻧﻮﻳﺲ ‪ 1‬ﻧﺸﺎﻥ ﻣﻰﺩﻫﺪ ﻛﻪ ﻣﺘﻐﻴﺮ ﻣﺮﺑﻮﻁ ﺑﻪ ﻓﻦ ﻣﻮﺭﺩ ﻧﻈﺮ ﻣﻰﺑﺎﺷﺪ‪.‬‬ ‫‪ b‬ﺯﻳﺮﻧﻮﻳﺲ ‪ 2‬ﻧﺸﺎﻥ ﻣﻰﺩﻫﺪ ﻛﻪ ﻣﺘﻐﻴﺮ ﻣﺮﺑﻮﻁ ﺑﻪ ﻓﻦ ﺁﺯﻣﺎﻳﺶ ﺷﺪﻩ ﻣﻰﺑﺎﺷﺪ‪.‬‬ ‫‪ Ptf c‬ﻳﺎ ‪Psf‬‬

‫ﻓﺸﺎﺭ ﻛﻞ‪Pa ،‬‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺑﺎ ﺍﺳﺘﻔﺎﺩﻩ ﺍﺯ ﻗﺎﻧﻮﻥ ﻓﻦ ‪:1b‬‬

‫ﺩﺍﺩﻩﻫــﺎﯼ ﻋﻤﻠﮑﺮﺩ ﻓﻦ ﺑﺮ ﺍﺳــﺎﺱ ﻫﻮﺍﯼ ﺧﺸــﮏ ﺩﺭ ﺷــﺮﺍﯾﻂ‬ ‫ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ‪ 101.325kPa‬ﻭ )‪ 20 oC (1.204kg/m3‬ﺍﺳﺖ؛ ﻣﮕﺮ ﺍﯾﻦ‬ ‫ﮐﻪ ﺧﻼﻑ ﺁﻥ ﺫﮐﺮ ﺷــﺪﻩ ﺑﺎﺷﺪ‪ .‬ﺩﺭ ﮐﺎﺭﺑﺮﺩﻫﺎﯼ ﻭﺍﻗﻌﯽ ﺷﺎﯾﺪ ﻻﺯﻡ ﺷﻮﺩ‬

‫ﻣﻨﺤﻨﻰ ‪Ptf‬‬ ‫ﻣﺒﻨﺎ‬

‫ﮐﻪ ﻓﻦ‪ ،‬ﻫﻮﺍ ﯾﺎ ﮔﺎﺯ ﺩﺍﺭﺍﯼ ﭼﮕﺎﻟﯽ ﺩﯾﮕﺮﯼ ﺭﺍ ﺟﺎﺑﻪﺟﺎ ﮐﻨﺪ‪ .‬ﺗﻐﯿﯿﺮ ﭼﮕﺎﻟﯽ‬ ‫ﻣﯽﺗﻮﺍﻧﺪ ﺑﻪ ﺩﻟﯿﻞ ﺩﻣﺎ‪ ،‬ﺗﺮﮐﯿﺐ ﮔﺎﺯ ﯾﺎ ﺍﺭﺗﻔﺎﻉ ﺑﺎﺷﺪ‪ .‬ﻋﻤﻠﮑﺮﺩ ﻓﻦ ﺗﺤﺖ‬ ‫ﺗﺎﺛﯿﺮ ﭼﮕﺎﻟﯽ ﮔﺎﺯ ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﺩ‪ .‬ﺩﺭ ﺍﻧﺪﺍﺯﻩ ﻭ ﺳﺮﻋﺖ ﺛﺎﺑﺖ‪ ،‬ﻓﺸﺎﺭ ﻭ ﺗﻮﺍﻥ‬ ‫)ﺍﺳﺐ ﺑﺨﺎﺭ( ﺑﺎ ﻧﺴﺒﺖ ﭼﮕﺎﻟﯽ ﮔﺎﺯ ﺑﻪ ﭼﮕﺎﻟﯽ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ﻫﻮﺍ ﺑﺎ ﻧﺴﺒﺖ‬ ‫ﻣﺴﺘﻘﯿﻢ ﺗﻐﯿﯿﺮ ﻣﯽﮐﻨﺪ‪.‬‬ ‫ﮐﺎﺭﺑــﺮﺩ ﻗﻮﺍﻧﯿﻦ ﻓﻦ ﺑﺮﺍﯼ ﺗﻐﯿﯿﺮ ﺩﺭ ﺳــﺮﻋﺖ ﻓﻦ )‪ (N‬ﺩﺭ ﯾﮏ ﻓﻦ‬ ‫ﺑﺎ ﺍﻧﺪﺍﺯﻩ ﻣﺸﺨﺺ ﻧﺸﺎﻥ ﺩﺍﺩﻩ ﻣﯽﺷﻮﺩ‪ .‬ﻣﻨﺤﻨﯽ ﻣﺤﺎﺳﺒﻪ ﺷﺪﻩ ‪ Pt‬ﺍﺯ‬

‫ﻧﺮﺥ ﺟﺮﻳﺎﻥ ﺣﺠﻤﻰ‪s/m٣ ،‬‬

‫ﺍﺧﺘﻼﻑ ﻓﺸﺎﺭ )‪1/s × (kpa‬‬ ‫‪ × 40350‬ﺑﺎﺯﺩﻩ ﻓﻦ × ﺑﺎﺯﺩﻩ ﻣﻮﺗﻮﺭ‬

‫= ﺗﻮﺍﻥ ﻓﻦ‪kw،‬‬

‫ﻓﻦﻫﺎﯼ ﮐﻮﭼﮏ ﺑﺎ ﺑﺎﺯﺩﻫﯽ ‪ 0.4‬ﺗﺎ ‪0.5‬‬ ‫ﻓﻦﻫﺎﯼ ﺑﺰﺭﮒ ﺑﺎ ﺑﺎﺯﺩﻫﯽ ‪ 0.55‬ﺗﺎ ‪0.65‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫)ﻣﻌﻤﻮﻝ(‬

‫ﺻﻔﺤﻪ ‪ / 37‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻣﻘﺎﻻﺕ‬

‫ﺑﺮﺭﺳﻰ ﻣﻮﺍﺭﺩ ﺍﻗﺘﺼﺎﺩﻯ ﻭ ﻫﺰﻳﻨﻪﻫﺎﻯ‬ ‫ﺳﻴﺴﺘﻢﻫﺎﻯ ﺳﺮﻣﺎﻳﺶ ﺗﺒﺨﻴﺮﻯ‬ ‫ﺍﻧﺮﮊﯼ ﺍﺟﺮﺍ ﻣﯽﺷﻮﻧﺪ‪ .‬ﻣﻮﺿﻮﻋﺎﺕ ﺩﯾﮕﺮ‬

‫ﺍﺳﺖ‪ .‬ﺍﻃﻼﻋﺎﺕ ﻭﺭﻭﺭﺩﯼ ﺗﺤﻠﯿﻞﻫﺎﯼ‬

‫ﺗﺤﻠﯿﻞ ﺳــﺎﺯﻣﺎﻥ ﻣﺤﯿﻂ ﺯﯾﺴﺖ ﺍﺯ‬

‫ﺍﯾﻦ ﺗﺤﻠﯿﻞ ﺩﺭ ﺧﺼﻮﺹ ﻧﺼﺐ‪ ،‬ﺍﻧﺮﮊﯼ‪،‬‬

‫ﻫﺰﯾﻨــﻪ ﺩﻭﺭﻩ ﺑﻬﺮﻩﺑــﺮﺩﺍﺭﯼ )‪،(LCC‬‬

‫ﺳــﻪ ﻧﻮﻉ ﻣﺘﻔﺎﻭﺕ ﺍﺯ ﺧﻨﮏﮐﻨﻨﺪﻩﻫﺎﯼ‬

‫ﻧﮕﻬــﺪﺍﺭﯼ‪ ،‬ﺑﺎﺯﯾﺎﺑــﯽ ﻭ ﺍﺭﺯﺵ ﺯﻣﺎﻧــﯽ‬

‫ﺷــﺎﻣﻞ ﺑﺮﻧﺎﻣﻪ ﺷﺒﯿﻪﺳﺎﺯﯼ ﺳﺎﺧﺘﻤﺎﻥ‬

‫ﭘﻮﻝ ﺍﺳــﺖ‪ .‬ﻋﻤــﺮ ﺗﻤــﺎﻡ ﻭﺍﺣﺪﻫﺎ ‪20‬‬

‫ﻭ ﻧﺮﻡﺍﻓــﺰﺍﺭ ﺗﺤﻠﯿﻠﯽ ﺧﻨﮏﮐﻨﻨﺪﻩﻫﺎﯼ‬

‫ﺳــﺎﻝ ﺑﺮﺁﻭﺭﺩ ﺷﺪﻩ ﺍﺳﺖ‪ .‬ﭘﯿﺸﻨﻬﺎﺩﺍﺕ‬

‫ﺗﺒﺨﯿﺮﯼ ‪ KOOLKALK‬ﺍﺳــﺖ‪ .‬ﺍﯾﻦ‬

‫ﻣﺪﻝﺳﺎﺯﯼ ﺷﺪﻩ ﺩﯾﮕﺮ ﻋﺒﺎﺭﺗﻨﺪ ﺍﺯ‪:‬‬

‫ﺑﺮﻧﺎﻣﻪﻫــﺎ ﺩﺭﺑﺮﮔﯿﺮﻧــﺪﻩ ﻫﺰﯾﻨﻪﻫــﺎﯼ‬

‫ﻣﻮﺍﺭﺩ ﺍﻗﺘﺼﺎﺩﯼ‬

‫ﺗﺒﺨﯿــﺮﯼ ﻭ ﯾﮏ ﺳﯿﺴــﺘﻢ ﻣﺸــﺘﺮﮎ‬ ‫ﺍﻧﺒﺴــﺎﻁ ﻣﺴﺘﻘﯿﻢ ﻣﺒﺮﺩﻫﺎ‪ ،‬ﺑﻪ ﻣﻨﻈﻮﺭ‬ ‫ﻣﻘﺎﯾﺴﻪ ﻣﺼﺮﻑ ﺍﻧﺮﮊﯼ ﻭ ﺳﻄﺢ ﺁﺳﺎﯾﺶ‬ ‫ﺻــﻮﺭﺕ ﮔﺮﻓﺘﻪ ﺍﺳــﺖ‪ .‬ﺳــﭙﺲ ﺍﯾﻦ‬ ‫ﺗﺤﻠﯿﻞﻫﺎ ﺩﺭ ﭼﻬﺎﺭ ﺷﻬﺮ ﻣﺨﺘﻠﻒ ﺍﯾﺎﻟﺖ‬ ‫ﻧﯿﻮﻣﮑﺰﯾﮑﻮ ﺗﮑﺮﺍﺭ ﺷﺪ‪ .‬ﯾﮏ ﺩﺑﯿﺮﺳﺘﺎﻥ‬ ‫ﮐﻪ ﺁﺭﺍﯾﺶ ﻭ ﻧﻮﻉ ﺗﺠﻬﯿﺰﺍﺕ ﺳﺮﻣﺎﯾﺸﯽ‪،‬‬ ‫ﺳــﺎﺧﺘﻤﺎﻥ ﻭ ﺑﺮﻧﺎﻣﻪﻫﺎﯼ ﺳﺎﮐﻨﯿﻦ ﺁﻥ‬ ‫ﺭﺍ ﻣﻨﻌﮑﺲ ﻣﯽﻧﻤﻮﺩ‪ .‬ﻓﺼﻞ ﺗﺎﺑﺴــﺘﺎﻥ‬ ‫ﺑــﺮﺍﯼ ‪ 6‬ﺳــﺎﻋﺖ ﮐﺎﺭﮐﻨــﺎﻥ ﺍﺟﺮﺍﯾﯽ ﻭ‬ ‫ﺧﺪﻣﺎﺗــﯽ ﺑﻪ ﻋﻨــﻮﺍﻥ ﻧﻤﻮﻧــﻪ ﺩﺭ ﻧﻈﺮ‬ ‫ﮔﺮﻓﺘــﻪ ﺷــﺪ‪ .‬ﺗﻨﻈﯿﻢ‪/‬ﺍﻓــﺖ ﺩﻣــﺎ ﺩﺭ‬ ‫ﺷــﺐ ﻭ ﭘﺎﯾﺎﻥ ﻫﻔﺘﻪ ﺩﺭ ﺗﻤﺎﻡ ﻧﻤﻮﻧﻪﻫﺎ‬

‫‪ = DX + IEC‬ﺳــﺮﻣﺎﯾﺶ ﺗﺮﺍﮐﻤــﯽ‬

‫ﺳﯿﺴﺘﻢﻫﺎ ﻣﯽﺷﻮﺩ‪.‬‬

‫ﯾﮑﭙﺎﺭﭼﻪ ﻫﻤﺮﺍﻩ ﺑﺎ ﺳــﺮﻣﺎﯾﺶ ﺗﺒﺨﯿﺮﯼ‬ ‫ﻏﯿﺮﻣﺴﺘﻘﯿﻢ‬

‫‪ D EC‬ﮐــﻪ ﺩﺭ ﺭﺩﻩ ﺳﯿﺴــﺘﻢﻫﺎﯼ‬

‫‪ = D EC‬ﺳﯿﺴــﺘﻢﻫﺎﯼ ﺗﺒﺨﯿــﺮﯼ‬ ‫‪ = D + I EC‬ﺑﺴــﺘﺮ ﺻﻠﺐ ﻣﺴﺘﻘﯿﻢ‬

‫ﮐﻤﺘﺮﯾــﻦ ﻫﺰﯾﻨــﻪ ﺩﻭﺭﻩ ﺑﻬﺮﻩﺑﺮﺩﺍﺭﯼ ﺭﺍ‬

‫ﻫﻤﺮﺍﻩ ﺑﺎ ﺳﯿﺴﺘﻢ ﺗﺒﺨﯿﺮﯼ ﻏﯿﺮﻣﺴﺘﻘﯿﻢ‬

‫ﺩﺍﺭﺍ ﺍﺳﺖ‪ .‬ﺩﻭﻣﯿﻦ ﺳﯿﺴﺘﻢ ﮐﻢﻫﺰﯾﻨﻪ‪،‬‬

‫ﺍﻃﻼﻋــﺎﺕ ﺯﯾــﺮ ﺍﺯ ﻓﺎﯾﻞﻫــﺎﯼ‬

‫ﺳﯿﺴــﺘﻢﻫﺎﯼ ﻣﺮﮐــﺐ ﻣﺴــﺘﻘﯿﻢ ‪-‬‬

‫ﺧﺮﻭﺟﯽ ﺑﺮﻧﺎﻣﻪ ﺗﺤﻠﯿﻠــﯽ ﻫﺰﯾﻨﻪ ﺩﻭﺭﻩ‬

‫ﻏﯿﺮﻣﺴــﺘﻘﯿﻢ ﻫﺴــﺘﻨﺪ‪ .‬ﺟﺎﻟﺐ ﺍﺳﺖ‬

‫ﺑﻬﺮﻩﺑﺮﺩﺍﺭﯼ ‪ 1.5BLCC‬ﺑﻪ ﺩﺳﺖ ﺁﻣﺪﻩ‬

‫ﺑﺪﺍﻧﯿــﺪ ﮐــﻪ ﺳﯿﺴــﺘﻢﻫﺎﯼ ﺗﺒﺨﯿﺮﯼ‬

‫ﺟﺪﻭﻝ )‪ :(1‬ﻣﻘﺎﯾﺴﻪ ﻫﺰﯾﻨﻪ ﺩﻭﺭﻩ ﺑﻬﺮﻩﺑﺮﺩﺍﺭﯼ‬

‫ﻧﺪﺍﺷﺖ‪.‬‬

‫ﺗﺤﻠﯿـﻞ‬ ‫ﺑﻬﺮﻩﺑﺮﺩﺍﺭﯼ‬

‫ﺗﺒﺨﯿــﺮﯼ ﻣﺴــﺘﻘﯿﻢ ﺑﺎ ﺑﺴــﺘﺮ ﺻﻠﺐ‬ ‫ﻗﺮﺍﺭ ﻣﯽﮔﯿﺮﺩ‪ ،‬ﺳﯿﺴــﺘﻤﯽ ﺍﺳــﺖ ﮐﻪ‬

‫ﻣﺴﺘﻘﯿﻢ ﺑﺎ ﺑﺴﺘﺮ ﺻﻠﺐ‬

‫ﻟﺤﺎﻅ ﺷﺪ‪ .‬ﻫﯿﭻ ﺳﺎﯾﻪ ﺧﺎﺭﺟﯽ ﻭﺟﻮﺩ‬

‫ﻫﺰﯾﻨﻪﻫـﺎﯼ‬

‫ﻧﺘﺎﯾﺞ ﺑﯿﺎﻧﮕﺮ ﺁﻥ ﺍﺳﺖ ﮐﻪ ‪ECGM-‬‬

‫ﻫﺰﯾﻨﻪﻫﺎﯼ ﻧﺴﺒﯽ ﺳﯿﺴﺘﻢﻫﺎ‬ ‫)ﺑﻪ ﺗﺮﺗﯿﺐ ﺻﻌﻮﺩﯼ ﺑﺮ ﻃﺒﻖ ﻫﺰﯾﻨﻪ ﺍﻭﻟﯿﻪ(‬

‫ﺩﻭﺭﻩ‬ ‫ﺳﯿﺴﺘﻢ‬

‫ﻫﺰﯾﻨﻪ ﺍﻭﻟﯿﻪ‬

‫ﻫﺰﯾﻨﻪ ﭼﺮﺧﻪ ﺩﻭﺍﻡ‬

‫ﺍﻧﺒﺴﺎﻁ ﻣﺴﺘﻘﯿﻢ‬

‫‪327،178$‬‬

‫‪$ 796،689‬‬

‫ﻣﺠﻤــﻮﻉ ﻫﺰﯾﻨﻪﻫــﺎﯼ ﻣﺮﺑــﻮﻁ ﺑﻪ ﺩﻭ‬

‫ﺍﻧﺒﺴﺎﻁ ﻣﺴﺘﻘﯿﻢ ‪ +‬ﺗﺒﺨﯿﺮﯼ ﻏﯿﺮﻣﺴﺘﻘﯿﻢ‬

‫‪340،530$‬‬

‫‪$ 876،781‬‬

‫ﻧﻮﻉ ﺳﯿﺴــﺘﻢﻫﺎ ﺍﻧﺠﺎﻡ ﻣﯽﺷﻮﺩ‪ .‬ﺍﯾﻦ‬

‫ﺗﺒﺨﯿﺮﯼ ﻣﺴﺘﻘﯿﻢ ﺑﺎ ﺑﺴﺘﺮ ﺻﻠﺐ‬

‫‪343،918$‬‬

‫‪$ 571،024‬‬

‫ﺑﺴﺘﺮ ﺻﻠﺐ ﻣﺴﺘﻘﯿﻢ ‪ +‬ﺗﺒﺨﯿﺮﯼ ﻏﯿﺮﻣﺴﺘﻘﯿﻢ‬

‫‪396،254$‬‬

‫‪$ 597،417‬‬

‫ﺍﯾــﻦ ﻣﺮﺣﻠــﻪ ﺑﻪ ﻣﻨﻈﻮﺭ ﻣﻘﺎﯾﺴــﻪ‬

‫ﺗﺤﻠﯿﻞﻫــﺎ ﺑﯿﺸــﺘﺮ ﺩﺭ ﺯﻣﯿﻨﻪ ﻣﺼﺮﻑ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺑﻪ ﻋﻨﻮﺍﻥ ﻧﻤﻮﻧﻪ ﻃﺮﺍﺣﯽ ﺍﻧﺘﺨﺎﺏ ﺷﺪ‬

‫‪ = DX‬ﺳﺮﻣﺎﯾﺶ ﺗﺮﺍﮐﻤﯽ ﯾﮑﭙﺎﺭﭼﻪ‬

‫ﺗﺨﻤﯿﻨﯽ ﻣﺮﺑﻮﻁ ﺑﻪ ﻧﺼﺐ ﻭ ﻧﮕﻬﺪﺍﺭﯼ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺻﻔﺤﻪ ‪ / 38‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻏﯿﺮﻣﺴﺘﻘﯿﻢ ‪ -‬ﺍﻧﺒﺴﺎﻁ ﻣﺴﺘﻘﯿﻢ ﻫﺰﯾﻨﻪ‬

‫ﺩﺭ ﺁﻧﺠﺎ ﻣﻮﺛﺮ ﻧﯿﺴــﺖ‪ ،‬ﺑﻪ ﺁﺳــﺎﯾﺶ ﻭ‬

‫ﺍﺩﺍﺭﻩ ﺍﻣﻮﺭ ﺍﺳــﺖ ﻭ ﺑﺴﯿﺎﺭﯼ ﺍﺯ ﺍﻭﻗﺎﺕ‬

‫ﺳﺎﻟﯿﺎﻧﻪ ﺍﻧﺪﮐﯽ ﺩﺭ ﻣﺼﺮﻑ ﺍﻧﺮﮊﯼ ﺩﺍﺭﻧﺪ‬

‫ﺯﻧﺪﮔﯽ ﺩﺭ ﻣﺤﯿﻂﻫﺎﯼ ﺗﺒﺮﯾﺪﯼ ﻋﺎﺩﺕ‬

‫ﮐﺎﺭ ﺗﻌﻮﯾــﺾ ﻗﻄﻌﺎﺕ ﻣﻌﯿﻮﺏ ﺭﺍ ﺍﻧﺠﺎﻡ‬

‫ﺍﻣﺎ ﺑﻪ ﻭﺍﺳــﻄﻪ ﻫﺰﯾﻨﻪ ﺍﻭﻟﯿــﻪ ﺑﺎﻻﺗﺮ ﻭ‬

‫ﺧﻮﺍﻫﻨﺪ ﮐﺮﺩ‪ .‬ﭘﻮﺳــﺖ ﻓــﺮﺩﯼ ﮐﻪ ﺩﺭ‬

‫ﻣﯽﺩﻫﻨــﺪ‪ .‬ﻫﺰﯾﻨﻪ ﺗﻌﻤﯿﺮ ﻭ ﻧﻮﺳــﺎﺯﯼ‬

‫ﻧﮕﻬﺪﺍﺭﯼ ﺑﯿﺸﺘﺮ‪ ،‬ﺑﺎﻻﺗﺮﯾﻦ ﻫﺰﯾﻨﻪ ﺩﻭﺭﻩ‬

‫ﻣﺤﯿﻂ ﻣﺮﻃﻮﺏ ﺯﻧﺪﮔــﯽ ﻣﯽﮐﻨﺪ‪ ،‬ﺩﺭ‬

‫ﺳﯿﺴﺘﻢﻫﺎﯼ ﺗﻬﻮﯾﻪ ﻣﻄﺒﻮﻉ ﺭﺍ ﻣﯽﺗﻮﺍﻥ‬

‫ﺑﻬﺮﻩﺑــﺮﺩﺍﺭﯼ ﺭﺍ ﺑــﻪ ﺧــﻮﺩ ﺍﺧﺘﺼﺎﺹ‬

‫ﻫــﻮﺍﯼ ﺧﺸــﮏ ﺟﻨﻮﺏ ﻏﺮﺑــﯽ ﺩﭼﺎﺭ‬

‫ﻭﺳﯿﻠﻪﺍﯼ ﺑﺮﺍﯼ ﺧﻂ ﺑﻮﺩﺟﻪ ﺑﻪ ﻣﻨﻈﻮﺭ‬

‫ﺩﺍﺩﻩﺍﻧــﺪ‪ .‬ﺑﺎ ﺍﯾﻦ ﻭﺟــﻮﺩ‪ ،‬ﺩﺭ ﻣﻨﺎﻃﻖ‬

‫ﺗﺮﮎﺧﻮﺭﺩﮔﯽ ﻣﯽﺷــﻮﺩ‪ ،‬ﻭ ﺳﺮﻣﺎﯾﺶ‬

‫ﭘﺮﺩﺍﺧــﺖ ﻫﺰﯾﻨﻪﻫــﺎﯼ ﻣﻌﻮﻗﻪ ﺗﻌﻮﯾﺾ‬

‫ﻣﻌﺘﺪﻝ ﺷــﻤﺎﻟﯽ ﯾﺎ ﻣﺮﺗﻔﻊﺗﺮ ﺍﺯ ﺳﻄﺢ‬

‫ﺗﺮﺍﮐﻤﯽ ﺑﻪ ﺁﻥﻫﺎ ﺍﺣﺴــﺎﺱ ﺧﺸــﮑﯽ‬

‫ﻭ ﻧﮕﻬﺪﺍﺭﯼ ﺗﺠﻬﯿــﺰﺍﺕ ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺖ‬

‫ﺩﺭﯾــﺎ‪ ،‬ﺑﻪ ﺩﻟﯿــﻞ ﯾﮑﭙﺎﺭﭼﮕــﯽ ﮔﺮﻣﺎ ﺑﺎ‬

‫ﻣﯽﺩﻫــﺪ ﺩﺭﺣﺎﻟﯽﮐﻪ ﺩﺭ ﻣﺤﯿﻂ ﺗﻬﻮﯾﻪ‬

‫ﺍﻣﺎ ﺑﺮﺧﯽ ﻣﻨﺎﻃﻖ ﺍﻭﻟﻮﯾﺖﻫﺎﯼ ﺩﯾﮕﺮﯼ‬

‫ﺑﺎﺯﯾﺎﺑﯽ ﺍﻧﺮﮊﯼ‪ ،‬ﻫﺰﯾﻨﻪ ﺩﻭﺭﻩ ﺑﻬﺮﻩﺑﺮﺩﺍﺭﯼ‬

‫ﺷــﺪﻩ ﺗﺮﺍﮐﻤﯽ ﺍﺣﺴــﺎﺱ ﺳــﺮﺯﻧﺪﮔﯽ‬

‫ﺭﺍ ﺗﻌﯿﯿــﻦ ﮐﺮﺩﻩﺍﻧــﺪ‪ .‬ﺩﺭ ﺑﺮﺧــﯽ ﺍﺯ‬

‫ﺳﯿﺴــﺘﻢﻫﺎﯼ ﺗﺒﺨﯿﺮﯼ ﻏﯿﺮﻣﺴﺘﻘﯿﻢ ‪-‬‬

‫ﻣﯽﮐﻨﻨــﺪ‪ .‬ﺍﻓــﺮﺍﺩﯼ ﮐــﻪ ﻧﺴــﺒﺖ ﺑﻪ‬

‫ﻧﻤﻮﻧﻪﻫﺎ‪ ،‬ﻫﺰﯾﻨﻪﻫﺎﯼ ﻧﻮﺳﺎﺯﯼ ﻣﺮﺑﻮﻁ‬

‫ﺍﻧﺒﺴــﺎﻁ ﻣﺴــﺘﻘﯿﻢ‪ ،‬ﮐﺎﻫﺶ ﻣﯽﯾﺎﺑﺪ‪.‬‬

‫ﺁﻻﯾﻨﺪﻩﻫﺎﯼ ﻫﻮﺍﯼ ﺩﺍﺧﻠﯽ ﺣﺴﺎﺳﯿﺖ‬

‫ﺑﻪ ﻣﺴــﺎﺋﻞ ﺳﯿﺎﺳﯽ ﻭ ﺍﻧﺘﺨﺎﺑﺎﺗﯽ ﺷﺪﻩ‬

‫ﺗﺮﮐﯿــﺐ ﺻﺮﻓﻪﺟﻮﯾﯽﻫــﺎﯼ ﺑﺎﺯﯾﺎﺑــﯽ‬

‫ﺷــﺪﯾﺪ ﺩﺍﺭﻧﺪ‪ ،‬ﺩﺭ ﺻﻮﺭﺕ ﻋﺪﻡ ﻭﺟﻮﺩ‬

‫ﻭ ﻣﺪﺍﺭﺱ ﮐﻨﺘــﺮﻝ ﺍﻧﺪﮐﯽ ﺑﺮ ﺭﻭﯼ ﺍﯾﻦ‬

‫ﮔﺮﻣــﺎ ﻭ ﺍﻧﺪﻭﺧﺘﻪﻫﺎﯾــﯽ ﺩﺭ ﻋﺪﻡ ﻧﯿﺎﺯ‬

‫ﻋﻼﺋــﻢ ﺑﯿﻤــﺎﺭﯼ ﺍﺯ ﺟﻤﻠــﻪ ﮔﺮﻓﺘﮕﯽ‬

‫ﺑﺮﻧﺎﻣﻪ ﺩﺍﺭﻧﺪ‪ .‬ﺩﺭ ﻧﺘﯿﺠﻪ‪ ،‬ﺗﺠﻬﯿﺰﺍﺕ ﺭﺍ‬

‫ﺑــﻪ ﮔﺮﻡﮐﻨﻨﺪﻩﻫــﺎﯼ ﺑﺰﺭﮒﺗــﺮ‪ ،‬ﺗﻤﺎﻡ‬

‫ﻣﺠﺎﺭﯼ ﺑﯿﻨﯽ ﯾﺎ ﺳــﻮﺯﺵ‪ ،‬ﺧﺸــﮑﯽ‪،‬‬

‫ﻣﯽﺗﻮﺍﻥ ﺑﺮﺍﯼ ﻣﺪﺗــﯽ ﺑﯿﺶ ﺍﺯ ﺍﻧﺘﻈﺎﺭ‬

‫ﺟﻨﺒﻪﻫﺎﯼ ﺍﻗﺘﺼﺎﺩﯼ ﺍﯾﻦ ﺳﯿﺴﺘﻢﻫﺎ ﺭﺍ‬

‫ﺧﺎﺭﺵ ﯾﺎ ﺳــﻮﺯﺵ ﭼﺸﻢﻫﺎ‪ ،‬ﺭﺧﻮﺕ ﻭ‬

‫ﺑﻪﮐﺎﺭ ﺍﻧﺪﺍﺧﺖ‪.‬‬

‫ﺑﻬﺒﻮﺩ ﻣﯽﺑﺨﺸﺪ‪.‬‬

‫ﺑﯽﺣﺎﻟﯽ‪ ،‬ﺳﺮﺩﺭﺩ ﻭ ﺗﺸﺪﯾﺪ ﺍﺧﺘﻼﻻﺗﯽ‬

‫ﻫﺰﯾﻨﻪ ﮐﺎﺭﺑﺮﯼ‬

‫ﺁﺳﺎﯾﺶ ﺩﺭ ﻣﻘﺎﯾﺴﻪ ﺑﺎ ﻫﺰﯾﻨﻪ‬

‫ﺍﺯ ﻗﺒﯿــﻞ ﺁﺳــﻢ‪ ،‬ﺍﮔﺰﻣﺎ ﻭ ﺳــﯿﻨﻮﺯﯾﺖ‬

‫ﺑــﺎ ﺩﺭ ﻧﻈــﺮ ﮔﺮﻓﺘــﻦ ﻫﺰﯾﻨﻪﻫﺎﯼ‬

‫ﻣﻘﺎﯾﺴــﻪ ﺁﺳــﺎﯾﺶ ﺑﺎ ﻫﺰﯾﻨــﻪ‪ ،‬ﺑﺮ‬

‫ﺍﺣﺴــﺎﺱ ﺁﺳــﺎﯾﺶ ﻣﯽﮐﻨﻨﺪ‪ .‬ﻋﻮﺍﻣﻞ‬

‫ﮐﺎﺭﺑــﺮﯼ‪ ،‬ﺍﺯ ﺍﻫﻤﯿﺖ ﻫﺰﯾﻨﻪﻫﺎﯼ ﺍﻭﻟﯿﻪ‬

‫ﻣﺒﻨﺎﯼ ﻣﻨﻄﻘﻪ ﺁﺳــﺎﯾﺶ ‪ ASHRAE‬ﻭ‬

‫ﺍﯾﻦﭼﻨﯿﻨﯽ ﺩﺭ ﺣﺪﻭﺩﻫــﺎﯼ ﻧﻤﻮﺩﺍﺭﯼ‬

‫ﮐﺎﺳــﺘﻪ ﻣﯽﺷﻮﺩ‪ .‬ﺍﯾﻦ ﻫﺰﯾﻨﻪﻫﺎ ﺷﺎﻣﻞ‬

‫ﺗﺤﻠﯿﻞﻫﺎﯼ ﺍﺭﺍﺋﻪ ﺷﺪﻩ ﺩﺭ ﺯﻣﯿﻨﻪ ﻫﺰﯾﻨﻪ‬

‫ﺩﺭ ﻧﻤــﻮﺩﺍﺭ ﺳــﺎﯾﮑﺮﻭﻣﺘﺮﯾﮏ ﻣﻨﻌﮑﺲ‬

‫ﻣﺨﺎﺭﺝ ﺍﻧﺮﮊﯼ‪ ،‬ﻧﮕﻬــﺪﺍﺭﯼ‪ ،‬ﻣﺎﻟﯿﺎﺕ‪،‬‬

‫ﺩﻭﺭﻩ ﺑﻬﺮﻩﺑــﺮﺩﺍﺭﯼ ﺍﻧﺠــﺎﻡ ﻣﯽﺷــﻮﺩ‪.‬‬

‫ﻧﻤﯽﺷﻮﻧﺪ‪.‬‬

‫ﻣﺠــﻮﺯ ﻭ ﺗﻌﻤﯿﺮﺍﺕ ﺍﺩﻭﺍﺭﯼ ﻣﯽﺷــﻮﺩ‪.‬‬

‫ﺑــﺮﺍﯼ ﺍﻧﺠــﺎﻡ ﺍﯾــﻦ ﻣﻘﺎﯾﺴــﻪ ﻣﺒﻨﺎﯼ‬

‫ﻋﺎﻣــﻞ ﺩﯾﮕــﺮ ﮐــﻪ ﺩﻗﯿﻘــﺎ ﺩﺭ‬

‫ﻫﺰﯾﻨﻪﻫﺎﯼ ﻣﺮﺑﻮﻁ ﺑﻪ ﺑﺎﺯﯾﺎﺑﯽ‪ ،‬ﻣﻌﻤﻮﻻ‬

‫ﻣﻌﻘــﻮﻝ ﺩﯾﮕــﺮﯼ ﻧﯿــﺰ ﻭﺟــﻮﺩ ﺩﺍﺭﺩ‪.‬‬

‫ﺗﺤﻠﯿﻞﻫــﺎﯼ ﻣﺮﺑﻮﻁ ﺑــﻪ ﻫﺰﯾﻨﻪ ﺩﻭﺭﻩ‬

‫ﺟﺰﯾﯽ ﻭ ﺍﻧﺪﮎ ﺍﺳﺖ‪ .‬ﻫﺰﯾﻨﻪ ﻧﮕﻬﺪﺍﺭﯼ‬

‫ﺍﺣﺴﺎﺱ ﺁﺳــﺎﯾﺶ ﺑﻪ ﻃﻮﺭ ﮔﺴﺘﺮﺩﻩﺍﯼ‬

‫ﺑﻬﺮﻩﺑﺮﺩﺍﺭﯼ ﻣﻨﻌﮑﺲ ﻧﻤﯽﺷﻮﺩ‪ ،‬ﺩﻭﺍﻡ‬

‫ﺳﯿﺴــﺘﻢﻫﺎﯼ ﻣﺨﺘﻠﻒ ﺗﻬﻮﯾﻪ ﻣﻄﺒﻮﻉ‪،‬‬

‫ﺑﺎ ﺳﻦ‪ ،‬ﺟﻨﺴﯿﺖ‪ ،‬ﭘﻮﺷﺶ‪ ،‬ﻓﺮﻫﻨﮓ ﻭ‬

‫ﺳﺎﺧﺘﻤﺎﻥ ﺍﺳﺖ‪ .‬ﻋﻤﺮ ﺳﺎﺧﺘﻤﺎﻥﻫﺎﯾﯽ‬

‫ﻇﺎﻫــﺮﺍ ﺑﺎ ﯾﮑﺪﯾﮕﺮ ﻣﺘﻔﺎﻭﺕ ﺍﺳــﺖ ﺍﻣﺎ‬

‫ﺍﻧﺘﻈﺎﺭﺍﺗﯽ ﺑﺮ ﺍﺳﺎﺱ ﺗﺠﺮﺑﯿﺎﺕ ﭘﯿﺸﯿﻦ‬

‫ﮐــﻪ ﺑﻪ ﻋﻨــﻮﺍﻥ ﻧﻤﻮﻧﻪ ﺫﮐﺮ ﺷــﺪ‪20 ،‬‬

‫ﺩﺭ ﻭﺍﻗﻊ‪ ،‬ﭘﺮﺳﻨﻞ ﻧﮕﻬﺪﺍﺭﯼ ﺗﺠﻬﯿﺰﺍﺕ‪،‬‬

‫ﺗﻮﺳــﻂ ﺳﯿﺴــﺘﻢﻫﺎﯼ ﺭﻓﺎﻫــﯽ ﺗﻐﯿﯿﺮ‬

‫ﺳــﺎﻝ ﻓــﺮﺽ ﻣﯽﺷــﻮﺩ‪ ،‬ﺑــﺎ ﻓــﺮﺽ‬

‫ﺗﻌﺪﺍﺩ ﺳــﺎﻋﺎﺕ ﻣﺸــﺎﺑﻬﯽ ﺭﺍ ﺩﺭ ﻫﻔﺘﻪ‬

‫ﺧﻮﺍﻫﺪ ﮐﺮﺩ‪ .‬ﺩﺭﮎ ﺍﯾﻦ ﻣﻮﺿﻮﻉ ﺳﺎﺩﻩ‬

‫ﺍﯾﻨﮑــﻪ ﺗﺠﻬﯿﺰﺍﺕ ﺁﻥ ﭘــﺲ ﺍﺯ ﻋﻤﺮ ﺑﻨﺎ‬

‫ﺑﺪﻭﻥ ﺗﻮﺟﻪ ﺑﻪ ﻧﻮﻉ ﺳﯿﺴﺘﻢ ﻧﺼﺐ ﺷﺪﻩ‬

‫ﺍﺳﺖ ﮐﻪ ﭼﻄﻮﺭ ﻓﺮﺩﯼ ﮐﻪ ﻫﻤﯿﺸﻪ ﺩﺭ‬

‫ﺗﻌﻮﯾﺾ ﺷــﻮﺩ‪ .‬ﻋﻤﺮ ﻭﺍﻗﻌﯽ ﺗﺠﻬﯿﺰﺍﺕ‬

‫ﺻﺮﻑ ﻧﮕﻬﺪﺍﺭﯼ ﺳﯿﺴﺘﻢﻫﺎ ﻣﯽﮐﻨﻨﺪ‪.‬‬

‫ﻣﺤﯿﻄﯽ ﮔﺮﻡ ﻭ ﺑﺪﻭﻥ ﺗﻬﻮﯾﻪ ﮐﺎﺭ ﮐﺮﺩﻩ‬

‫ﺩﺭ ﺗﺠﻬﯿﺰﺍﺕ ﺗﻬﻮﯾــﻪ ﻣﻄﺒﻮﻉ ﺑﺰﺭﮒ ﻭ‬

‫ﺑﺰﺭﮒﺗﺮﯾــﻦ ﻣﺘﻐﯿــﺮ ﺩﺭ ﻫﺰﯾﻨﻪﻫــﺎﯼ‬

‫ﺍﺳــﺖ‪ ،‬ﺣﺘﺎ ﺍﺯ ﯾﮏ ﻓــﻦ ﺗﻬﻮﯾﻪ ﺑﺮﺍﯼ‬

‫ﻣــﻮﺭﺩ ﺍﺳــﺘﻔﺎﺩﻩ ﺩﺭ ﻣــﺪﺍﺭﺱ‪ ،‬ﻏﺎﻟﺒﺎ‬

‫ﻣﺮﺑﻮﻁ ﺑﻪ ﺩﺳﺘﮕﺎﻩﻫﺎﯼ ﺗﻬﻮﯾﻪ ﻣﻄﺒﻮﻉ‬

‫ﺁﺳﺎﯾﺶ ﻧﺴــﺒﯽ ﺑﻬﺮﻩ ﻣﯽﺑﺮﺩ‪ .‬ﺍﻓﺮﺍﺩﯼ‬

‫ﺑﯿﺶ ﺍﺯ ‪ 20‬ﺳﺎﻝ ﺍﺳــﺖ‪ .‬ﺩﺭ ﺑﺴﯿﺎﺭﯼ‬

‫ﺑﯿﺶ ﺍﺯ ﻋﻤﺮ ﻭﺍﻗﻌﯽ ﺁﻥ‪ ،‬ﺍﻧﺮﮊﯼ ﺍﺳﺖ‪.‬‬

‫ﮐﻪ ﺩﺭ ﻗﺴــﻤﺖﻫﺎﯾﯽ ﺍﺯ ﮐﺸﻮﺭ ﺯﻧﺪﮔﯽ‬

‫ﺍﺯ ﻣﻨﺎﻃﻖ‪ ،‬ﭘﺮﺳــﻨﻞ ﮐﺎﺭﺩﺍﻥ ﻭ ﻣﺠﺮﺑﯽ‬

‫ﺍﮔﺮ ﺳﺮﻣﺎﯾﻪﮔﺬﺍﺭﯼ ﺯﻭﺩ ﻫﻨﮕﺎﻣﯽ ﺑﺮﺍﯼ‬

‫ﻣﯽﮐﻨﻨــﺪ ﮐﻪ ﺳﯿﺴــﺘﻢﻫﺎﯼ ﺗﺒﺨﯿﺮﯼ‬

‫ﺭﺍ ﻣﻨﺼــﻮﺏ ﮐﺮﺩﻩﺍﻧﺪ ﮐﻪ ﻭﻇﯿﻔﻪ ﺁﻥﻫﺎ‬

‫ﻃﺮﺍﺣﯽ ﯾﮏ ﺳﯿﺴــﺘﻢ ﺗﻬﻮﯾﻪ ﻣﻄﺒﻮﻉ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﺻﻔﺤﻪ ‪ / 39‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻣﻨﺎﺳــﺐ ﺑﺎ ﮐﻨﺘﺮﻝ ﭘﯿﺸــﺮﻓﺘﻪ ﺻﻮﺭﺕ‬ ‫ﺑﮕﯿﺮﺩ ﮐﻪ ﺍﺯ ﺣﺪﺍﻗﻞ ﺍﻧﺮﮊﯼ ﺍﺳــﺘﻔﺎﺩﻩ‬ ‫ﻧﻤﺎﯾﺪ‪ ،‬ﺁﻥ ﺳﯿﺴــﺘﻢ‪ ،‬ﺯﻣﺎﻥ ﺯﯾﺎﺩﯼ ﺭﺍ‬ ‫ﺑﯿــﺶ ﺍﺯ ﻫﺰﯾﻨﻪﻫﺎﯼ ﺍﻧــﺪﮎ ﮐﺎﺭﺑﺮﯼ‪،‬‬ ‫ﺑﺮﺍﯼ ﺧﻮﺩ ﺻﺮﻑ ﻣﯽﮐﻨﺪ‪.‬‬ ‫ﺳﯿﺴﺘﻢﻫﺎﯼ ﺳﺮﻣﺎﯾﺶ ﺗﺒﺨﯿﺮﯼ‪،‬‬ ‫ﮐﻤﺘــﺮ ﺍﺯ ﯾﮏ ﭼﻬﺎﺭﻡ ﺍﻧــﺮﮊﯼ ﻣﺼﺮﻓﯽ‬ ‫ﺗﻮﺳــﻂ ﺳﯿﺴــﺘﻢﻫﺎﯼ ﺗﺮﺍﮐﻢ ﺑﺨﺎﺭ ﺭﺍ‬ ‫ﺍﺳــﺘﻔﺎﺩﻩ ﻣﯽﮐﻨﻨﺪ ﺩﺭ ﺣﺎﻟﯽﮐﻪ ﻣﯿﺰﺍﻥ‬ ‫ﺁﺏ ﻣﺼﺮﻓﯽ ﺁﻥﻫــﺎ ﻧﯿﺰ ﺍﺯ ﺁﺏ ﻣﺼﺮﻓﯽ‬ ‫ﻧﯿﺮﻭﮔﺎﻩﻫﺎ ﺑــﺮﺍﯼ ﺗﻮﻟﯿﺪ ﺍﻟﮑﺘﺮﯾﺴــﯿﺘﻪ‬

‫ﺑﻪ ﺷﺮﺡ ﺯﯾﺮ ﺍﺳﺖ‪:‬‬

‫●‬

‫ﺧﻨﮏﮐﻨﻨﺪﻩﻫــﺎﯼ ﺗﺒﺨﯿﺮﯼ =‬

‫‪ 0.0973‬ﺩﻻﺭ ﺩﺭ ﻫﺮ ﺳﺎﻋﺖ‬

‫●‬

‫ﺧﻨﮏﮐﻨﻨﺪﻩﻫــﺎﯼ ﺗﺮﺍﮐﻤﯽ =‬

‫ﻧﺸﻮﺩ‪ ،‬ﺟﺮﺍﯾﻢ ﺳﻨﮕﯿﻨﯽ ﺗﻌﯿﯿﻦ ﺧﻮﺍﻫﺪ‬ ‫ﺷــﺪ‪ .‬ﺗﺨﻠــﻒ ﺍﺯ ﻗﻮﺍﻧﯿــﻦ‪ ،‬ﻣﻮﺿﻮﻋﯽ‬ ‫ﺑﺴﯿﺎﺭ ﺟﺪﯼ ﺍﺳــﺖ ﮐﻪ ﺭﻭﺯﺍﻧﻪ ﺟﺮﺍﯾﻢ‬ ‫ﻧﻘــﺪﯼ ﺭﺍ ﺗــﺎ ‪ 25000‬ﺩﻻﺭ ﺑــﻪ ﺩﻧﺒﺎﻝ‬

‫‪ 0.9237‬ﺩﻻﺭ ﺩﺭ ﻫﺮ ﺳﺎﻋﺖ‬

‫ﺧﻮﺍﻫﺪ ﺩﺍﺷــﺖ‪ .‬ﺟﺮﺍﯾــﻢ ﮐﯿﻔﺮﯼ ﻧﯿﺰ‬

‫ﺷﺮﺍﯾﻂ ﻧﮕﻬﺪﺍﺭﯼ‬

‫ﺷﺎﻣﻞ ﻣﺠﺎﺯﺍﺕ ﺣﺒﺲ ﺗﺎ ‪ 5‬ﺳﺎﻝ ﺑﺮﺍﯼ‬

‫ﻫﺮ ﯾﮏ ﺍﺯ ﺳﯿﺴــﺘﻢﻫﺎﯼ ﺗﺒﺨﯿﺮﯼ‬ ‫ﻭ ﺗﺮﺍﮐﻤــﯽ ﺑــﺮﺍﯼ ﻋﻤﻠﮑﺮﺩ ﺩﺭﺳــﺖ‪،‬‬ ‫ﺑﺎﺯﺩﻫﯽ ﺍﻧﺮﮊﯼ ﻭ ﮔﺴﺘﺮﺵ ﻃﻮﻝ ﻋﻤﺮ ﺑﻪ‬ ‫ﻧﮕﻬﺪﺍﺭﯼ ﺍﺩﻭﺍﺭﯼ ﺍﺣﺘﯿﺎﺝ ﺩﺍﺭﻧﺪ‪ .‬ﻫﺰﯾﻨﻪ‬ ‫ﻣﺮﺑــﻮﻁ ﺑﻪ ﺁﻥ ﻧﯿﺰ ﺩﺭ ﻣﻘﺎﯾﺴــﻪ ﻫﺰﯾﻨﻪ‬

‫ﺗﺨﻠﻔــﺎﺕ ﻋﻤــﺪﯼ ﯾﺎ ﺳــﻬﻮﯼ ﻭ ﺑﺮﺍﯼ‬ ‫ﺍﻋﺘﺮﺍﻓﺎﺕ ﻧﺎﺩﺭﺳــﺖ ﻭ ﻋــﺪﻡ ﮔﺰﺍﺭﺵ‪،‬‬ ‫ﺗــﺎ ‪ 2‬ﻣﺠﺎﺯﺍﺕ ﺣﺒــﺲ ﺩﺭ ﻧﻈﺮ ﮔﺮﻓﺘﻪ‬ ‫ﻣﯽﺷﻮﺩ‪ .‬ﺳــﺎﺯﻣﺎﻥ ﻣﺤﯿﻂ ﺯﯾﺴﺖ ﺩﺭ‬ ‫ﻧﻈﺮ ﺩﺍﺭﺩ ﺑﻪ ﺍﻓــﺮﺍﺩﯼ ﮐﻪ ﻣﺘﺨﻠﻔﺎﻥ ﻭ‬ ‫ﻣﺠﺮﻣﺎﻥ ﺭﺍ ﺗﺤﻮﯾﻞ ﺩﻫﻨﺪ‪ ،‬ﺑﺮ ﺍﺳــﺎﺱ‬

‫ﻻﺯﻡ ﺟﻬﺖ ﻣﻘﺪﺍﺭ ﻣﺸــﺎﺑﻬﯽ ﺳﺮﻣﺎﯾﺶ‬

‫ﺩﻭﺭﻩ ﺑﻬﺮﻩﺑــﺮﺩﺍﺭﯼ ﻟﺤﺎﻅ ﻣﯽﺷــﻮﺩ‪.‬‬

‫ﺗﺮﺍﮐﻤــﯽ ﺑﺨﺎﺭ‪ ،‬ﮐﻤﺘﺮ ﺍﺳــﺖ‪ .‬ﺷــﺎﯾﺪ‬

‫ﻧﯿﺎﺯﻣﻨﺪﯼﻫﺎ ﺷﺎﻣﻞ ﺭﺍﻩﺍﻧﺪﺍﺯﯼ ﺳﯿﺴﺘﻢ‬

‫ﻗﯿﻤﺖ ﺳﯿﺴﺘﻢﻫﺎﯼ ﺳﺮﻣﺎﯾﺶ ﺗﺒﺨﯿﺮﯼ‬

‫ﺩﺭ ﺗﺎﺑﺴــﺘﺎﻥ‪ ،‬ﻣﺘﻮﻗــﻒ ﻧﻤﻮﺩﻥ ﺁﻥ ﺩﺭ‬

‫‪ 10000‬ﺩﻻﺭ ﭘﺎﺩﺍﺵ ﺩﻫﺪ‪ .‬ﺍﯾﻦ ﺗﺨﻠﻔﺎﺕ‬

‫ﺑﯿﺶ ﺍﺯ ﻗﯿﻤﺖ ﭼﯿﻠﺮ ﺗﺮﺍﮐﻢ ﺑﺨﺎﺭ ﺑﺎﺷﺪ‬

‫ﺯﻣﺴﺘﺎﻥ‪ ،‬ﺑﺎﺯﺭﺳــﯽ ﻭ ﺗﻨﻈﯿﻢ ﺩﻭﺭﻩﺍﯼ‬

‫ﺣﺘﺎ ﻣﯽﺗﻮﺍﻧﺪ ﺷﺎﻣﻞ ﺗﻌﻮﯾﺾ ﯾﮏ ﻭﺍﺷﺮ‬

‫ﺍﻣﺎ ﺑﺎﺯﭘﺮﺩﺍﺧﺖ ﺁﻥ ﺑﺮ ﻣﺒﻨﺎﯼ ﺷــﺮﺍﯾﻂ‬

‫ﺁﻥ ﻣﯽﺑﺎﺷﺪ‪.‬‬

‫ﯾﺎ ﻣﻬﺮﻭﻣﻮﻡ ﺳﺎﺩﻩ ﺑﺎﺷﺪ‪.‬‬

‫ﺑﺮﻧﺎﻣــﻪ ﭘــﺎﺩﺍﺵ ﺑــﻪ ﺷــﻬﺮﻭﻧﺪﺍﻥ‪ ،‬ﺗﺎ‬

‫ﺳﯿﺴﺘﻢﻫﺎﯼ ﺗﺮﺍﮐﻤﯽ ﺍﺯ ﺟﻤﻠﻪ ﺑﺎﺯﺭﺳﯽ‬

‫ﺍﺯ ﺳﯿﺴــﺘﻢﻫﺎﯼ ﺗﺮﺍﮐﻤــﯽ ﻣﺴــﺘﻠﺰﻡ‬

‫ﻫﺰﯾﻨﻪﻫــﺎﯼ ﺁﺏ ﻭ ﺑــﺮﻕ ﻣﺼﺮﻓﯽ‬

‫ﻭ ﺗﻨﻈﯿــﻢ ﻧﯿﺰ ﻣﺸــﺎﺑﻪ ﺳﯿﺴــﺘﻢﻫﺎﯼ‬

‫ﮔﺬﺭﺍﻧﺪﻥ ﺍﻣﺘﺤﺎﻧﺎﺗﯽ ﺍﺳﺖ ﮐﻪ ﺑﺎﯾﺪ ﺩﺭ‬

‫ﺩﺭ ﺍﻭﺝ ﺳــﺎﻋﺎﺕ ﻣﺼــﺮﻑ ﺩﺭ ﻓﺼــﻞ‬

‫ﺗﺒﺨﯿﺮﯼ ﺍﺳﺖ ﻭ ﺷﺎﻣﻞ ﺍﻧﺒﺴﺎﻁ ﺗﺴﻤﻪ‬

‫ﺑﺮ ﮔﯿﺮﻧﺪﻩ ﻣﻮﺿﻮﻋﺎﺕ ﺯﯾﺮ ﺑﺎﺷﺪ‪:‬‬

‫ﺗﺎﺑﺴــﺘﺎﻥ‪ ،‬ﺑــﻪ ﻣﻨﻈــﻮﺭ ﻣﻘﺎﯾﺴــﻪ‬

‫ﺩﺭ ﻓﻦ‪ ،‬ﺗﻨﻈﯿﻢ ﺩﻣﭙﺮﻫﺎ ﻭ ﮐﺎﻟﯿﺒﺮﺍﺳﯿﻮﻥ‬

‫ﺗﺨﻠﯿﻪ ﺍﺯﻥ؛ ﻗــﺮﺍﺭﺩﺍﺩ ﻫﻮﺍﯼ ﺗﻤﯿﺰ‬

‫ﻫﺰﯾﻨﻪﻫﺎﯼ ﺳﺮﻣﺎﯾﺸــﯽ ﯾﮑﺴﺎﻥ ﻭ ﻗﺎﺑﻞ‬

‫ﮐﻨﺘﺮﻝ ﻣﯽﺷﻮﺩ‪ .‬ﺳﯿﺴﺘﻢﻫﺎﯼ ﺗﺮﺍﮐﻤﯽ‬

‫ﻭ ﭘﺮﻭﺗــﮑﻞ ﻣﻮﻧﺘــﺮﺍﻝ؛ ﻣﻘﺮﺭﺍﺕ ﺑﺨﺶ‬

‫ﺍﺟﺮﺍ ﺩﺭ ‪ 2600‬ﻓﻮﺕ ﻣﺮﺑﻊ ﺍﺯ ﻣﺴــﺎﺣﺖ‬

‫ﺑﻪ ﻧﮕﻬﺪﺍﺭﯼ ﺩﯾﮕﺮﯼ ﻧﯿﺰ ﻣﺎﻧﻨﺪ ﺑﺮﺭﺳﯽ‬

‫‪608‬؛ ﺭﻭﻏــﻦ ﻭ ﻣﺒﺮﺩﻫــﺎﯼ ﺟﺎﯾﮕﺰﯾﻦ؛‬

‫ﮐﻼﺱﻫﺎﯼ ﺳﯿﺎﺭ‪ ،‬ﻣﺤﺎﺳﺒﻪ ﻣﯽﺷﻮﻧﺪ‪.‬‬

‫ﺳــﯿﻨﯽ ﺁﺏﭼﮑﻪ ﺩﺭ ﺯﯾــﺮ ﮐﻼﻑ ﺗﺒﺨﯿﺮ‬

‫ﺗﺒﺮﯾــﺪ؛ ﺑﺎﺯﯾﺎﺑــﯽ‪ ،‬ﺑﺎﺯﺳــﺎﺯﯼ ﻭ ﺍﺣﯿﺎ؛‬

‫ﺍﮔــﺮ ﭼﻪ ﺁﺏ ﺩﺭ ﻭﺍﺣﺪﻫﺎﯼ ﺳــﺮﻣﺎﯾﺶ‬

‫ﻭ ﺗﻌﻮﯾﺾ ﻓﯿﻠﺘﺮﻫــﺎ ﺍﺣﺘﯿﺎﺝ ﺩﺍﺭﻧﺪ ﮐﻪ‬

‫ﻓﻨــﻮﻥ ﺑﺎﺯﯾﺎﺑــﯽ؛ ﺗﺨﻠﯿــﻪ ﺁﺏﺯﺩﺍﯾﯽ؛‬

‫ﺗﺒﺨﯿــﺮﯼ ﻭ ﻧﯿﺮﻭﮔﺎﻩﻫﺎﯼ ﺗﻮﻟﯿﺪ ﺑﺮﻕ ﺑﻪ‬

‫ﺍﯾﻦ ﮐﺎﺭﻫﺎ ﺭﺍ ﺗﻮﺳــﻂ ﺑﯿﺸــﺘﺮ ﭘﺮﺳﻨﻞ‬

‫ﺍﯾﻤﻨﯽ؛ ﺣﻤﻞ ﻭ ﻧﻘﻞ؛ ﺗﺸﺨﯿﺺ ﻧﺸﺖ؛‬

‫ﻣﺼﺮﻑ ﻣﯽﺭﺳﺪ‪ ،‬ﻫﺰﯾﻨﻪ ﺁﺏ ﻣﻮﺭﺩ ﻧﯿﺎﺯ‬

‫ﻧﮕﻬﺪﺍﺭﯼ ﺳﯿﺴﺘﻢﻫﺎﯼ ﺗﻬﻮﯾﻪ ﻣﻄﺒﻮﻉ‬

‫ﻧﯿﺎﺯﻣﻨﺪﯼﻫﺎﯼ ﺗﻌﻤﯿﺮ ﻧﺸــﺘﯽ؛ ﻓﻨﻮﻥ‬

‫ﻧﯿﺮﻭﮔﺎﻩ ﺑﺎ ﻫﺰﯾﻨﻪ ﺑﺮﻕ ﺍﺩﻏﺎﻡ ﻣﯽﺷــﻮﺩ‬

‫ﻣﯽﺗــﻮﺍﻥ ﺍﻧﺠﺎﻡ ﺩﺍﺩ‪ .‬ﺑــﺎ ﺍﯾﻦ ﻭﺟﻮﺩ‪،‬‬

‫ﺑﺎﺯﯾﺎﺑﯽ؛ ﻓﻨﻮﻥ ﺗﺨﻠﯿﻪ؛ ﻧﯿﺎﺯﻣﻨﺪﯼﻫﺎﯼ‬

‫ﺑﻨﺎﺑﺮﺍﯾــﻦ‪ ،‬ﺍﯾﻦ ﻣﺒﻠﻎ ﺩﺭ ﺍﯾﻦ ﻗﺴــﻤﺖ‬

‫ﻫﻨﮕﺎﻣــﯽ ﮐــﻪ ﻣﻮﺿﻮﻉ ﻧﮕﻬــﺪﺍﺭﯼ ﺍﺯ‬

‫ﺑﺎﺯﯾﺎﺑﯽ؛ ﺗﺒﺮﯾﺪ؛ ﺍﯾﻤﻨﯽ؛ ﻧﯿﺎﺯﻣﻨﺪﯼﻫﺎﯼ‬

‫ﺍﺿﺎﻓﻪ ﻧﻤﯽﺷــﻮﺩ‪ .‬ﺍﯾﻦ ﻣﺤﺎﺳــﺒﺎﺕ‪،‬‬

‫ﮐﻤﭙﺮﺳــﻮﺭﻫﺎ ﺑــﻪ ﻣﯿــﺎﻥ ﻣﯽﺁﯾــﺪ‪ ،‬ﺑﺮ‬

‫ﺍﺗﺎﻕ ﺗﺠﻬﯿﺰﺍﺕ ﺑﺮ ﺍﺳﺎﺱ ﺍﺳﺘﺎﻧﺪﺍﺭﺩ ‪15‬‬

‫ﻣﺠﻤــﻮﻉ ﻫﺰﯾﻨﻪﻫــﺎﯼ ﻗﯿﺪ ﺷــﺪﻩ ﺩﺭ‬

‫ﺍﺳﺎﺱ ﺑﻨﺪ ‪ 608‬ﻣﻘﺮﺭﺍﺕ ﻫﻮﺍﯼ ﺗﻤﯿﺰ‪،‬‬

‫‪) ASHRAE‬ﺣﺲﮔﺮ ﻓﻘﺪﺍﻥ ﺍﮐﺴــﯿﮋﻥ‬

‫ﻗﺒﻮﺽ ﺁﺏ ﻭ ﺑﺮﻕ ﺭﺍ ﺷــﺎﻣﻞ ﻣﯽﺷﻮﺩ‪.‬‬

‫ﺑﻪ ﭘﺮﺳــﻨﻞ ﺁﻣﻮﺯﺵﺩﯾﺪﻩ ﻭ ﺗﺎﯾﯿﺪ ﺷﺪﻩ‬

‫ﺑــﺎ ﺗﻤﺎﻡ ﻣﺒﺮﺩﻫﺎ(‪ .‬ﻣــﻮﺭﺩ ﺁﺧﺮ‪ ،‬ﻣﻮﺍﺭﺩ‬

‫ﻣﺠﻤــﻮﻉ ﻫﺰﯾﻨﻪﻫــﺎﯼ ﮐﺎﺭﺑــﺮﯼ ﺩﺭ‬

‫ﺗﻮﺳــﻂ ﺳــﺎﺯﻣﺎﻥ ﻣﺤﯿﻂ ﺯﯾﺴﺖ ﻧﯿﺎﺯ‬

‫ﺍﯾﻤﻨﯽ ﻗﺎﺑﻞ ﺍﺳﺘﻌﻤﺎﻝ ﺑﺎ ﻣﺒﺮﺩﻫﺎ ﺭﺍ ﺩﺭ‬

‫ﺳﺮﻣﺎﯾﺶ‪ ،‬ﺩﺭ ﺍﻭﺝ ﺳﺎﻋﺎﺕ ﺳﺮﻣﺎﯾﺸﯽ‬

‫ﺍﺳﺖ‪ .‬ﺩﺭ ﺻﻮﺭﺗﯽﮐﻪ ﺍﯾﻦ ﺷﺮﺍﯾﻂ ﺍﺣﺮﺍﺯ‬

‫ﯾﮏ ﻓﻀﺎﯼ ﻣﺤﺼﻮﺭ ﻧﺸﺎﻥ ﻣﯽﺩﻫﺪ‪.‬‬

‫ﺁﺏ ﻭ ﻫﻮﺍ ﺍﺯ ﺷــﺶ ﻣﺎﻩ ﺗﺎ ﭘﻨﺞ ﺳــﺎﻝ‬ ‫ﻣﺘﻐﯿﺮ ﺍﺳﺖ‪.‬‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﻧﯿﺎﺯﻣﻨﺪﯼﻫــﺎﯼ ﻧﮕﻬــﺪﺍﺭﯼ ﺩﺭ‬

‫ﺭﻭﻧﺪ ﺗﺎﯾﯿﺪ ﺗﮑﻨﺴﯿﻦﻫﺎﯼ ﻧﮕﻬﺪﺍﺭﯼ‬

‫ﺻﻔﺤﻪ ‪ / 40‬ﺷﻤﺎﺭﻩ ‪40‬‬

‫ﻧﻜﺘﻪ‬

‫ﻣﺤﺎﺳﺒﺎﺕ ﺳﺮﺍﻧﮕﺸﺘﻰ‬ ‫ﺭﻭﺷﻨﺎﻳﻰ‬ ‫‪ -1‬ﺍﺩﺍﺭﺍﯼ‪ ،‬ﺗﺠﺎﺭﯼ‬ ‫‪ .a‬ﺩﻓﺎﺗﺮ ﻋﻤﻮﻣﯽ‬

‫ﺳﺎﻟﻤﻨﺪﺍﻥ‬

‫‪ 1.5-3.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ 1.0-2.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -20‬ﻓﺮﻭﺷـﮕﺎﻩﻫﺎﯼ ﮐﻔـﺶ‪ ،‬ﻟﺒـﺎﺱ‪،‬‬

‫‪ .b‬ﺩﻓﺎﺗﺮ ﺧﺼﻮﺻﯽ‬

‫‪ -10‬ﺍﻣﺎﮐﻦ ﻋﻤﻮﻣﯽ ﺑﯿﻤﺎﺭﺳﺘﺎﻥﻫﺎ‬

‫ﺟﻮﺍﻫﺮﺍﺕ‪ ،‬ﻟﻮﺍﺯﻡ ﺁﺭﺍﯾﺶ‪ ،‬ﺁﺭﺍﯾﺸﮕﺎﻩﻫﺎ ﻭ‬

‫‪ 2.0-5.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ 1.5-2.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ .c‬ﺍﺗﺎﻕﻫﺎﯼ ﮐﻨﻔﺮﺍﻧﺲ ﻭ ﮔﺮﺩﻫﻤﺎﯾﯽ‬ ‫‪ 2.0-6.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -2‬ﺑﺎﻧﮏﻫﺎ‪ ،‬ﺩﺍﺩﺳﺮﺍﻫﺎ‪ ،‬ﺳﺎﺧﺘﻤﺎﻥﻫﺎﯼ‬ ‫ﺷﻬﺮﺩﺍﺭﯼ‪ ،‬ﺳﺎﻟﻦﻫﺎﯼ ﺍﺟﺘﻤﺎﻋﺎﺕ‬ ‫‪ 2.0-5.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫ﭼﻴﻠﺮ ﺟﺬﺑﻰ ﮔﺎﺯﺳﻮﺯ‬

‫ﺑﯿﻤﺎﺭﺳـﺘﺎﻥ‪ ،‬ﺍﺗﺎﻕﻫـﺎﯼ ﺁﺳﺎﯾﺸـﮕﺎﻩ‬

‫‪ -19‬ﻓﺮﻭﺷﮕﺎﻩﻫﺎﯼ ﺑﺰﺭﮒ ﻭ ﺗﮏﻓﺮﻭﺷﯽ‬ ‫‪ 2.0-6.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -3‬ﭘﺎﺳـﮕﺎﻩﻫﺎﯼ ﭘﻠﯿﺲ‪ ،‬ﺍﯾﺴﺘﮕﺎﻩﻫﺎﯼ‬ ‫ﺁﺗﺶﻧﺸﺎﻧﯽ‪ ،‬ﺩﻓﺎﺗﺮ ﭘﺴﺖ‬ ‫‪ 2.0-3.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -4‬ﺍﺑﺰﺍﺭ ﺩﻗﯿﻖ‬ ‫‪ 3.0-10.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -5‬ﺍﺗﺎﻕﻫﺎﯼ ﮐﺎﻣﭙﯿﻮﺗﺮ‬ ‫‪ 1.5-5.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -6‬ﺭﺳﺘﻮﺭﺍﻥﻫﺎ‬ ‫‪ 1.5-3.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -7‬ﺁﺷﭙﺰﺧﺎﻧﻪﻫﺎ‬ ‫‪ 1.5-2.5‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -8‬ﺳـﺎﻟﻦﻫﺎﯼ ﺍﻧﺘﻈﺎﺭ‪ ،‬ﮐﺎﻓﯽﺷـﺎﭖﻫﺎ‪،‬‬ ‫ﺑﺎﺷﮕﺎﻩﻫﺎ‬ ‫‪ 1.5-2.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -9‬ﺍﺗﺎﻕﻫـﺎﯼ ﺑﺴـﺘﺮﯼ ﺑﯿﻤـﺎﺭﺍﻥ ﺩﺭ‬

‫ﺩﺍﺭﻭﺧﺎﻧﻪﻫﺎ‬

‫‪ -11‬ﻣﺮﺍﮐﺰ ﭘﺰﺷـﮑﯽ‪/‬ﺩﻧﺪﺍﻥ ﭘﺰﺷـﮑﯽ‪،‬‬

‫‪ -21‬ﺳﻮﭘﺮﻣﺎﺭﮐﺖﻫﺎ‬ ‫‪ 1.5-3.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫ﮐﻠﻨﯿﮏﻫﺎ ﻭ ﺍﺩﺍﺭﺍﺕ‬ ‫‪ 1.5-2.5‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -22‬ﭘﺎﺳﺎﮊﻫﺎ ﻭ ﻣﺮﺍﮐﺰ ﺧﺮﯾﺪ‬ ‫‪ 1.5-2.5‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -12‬ﺍﻣﺎﮐﻦ ﻣﺴﮑﻮﻧﯽ‬ ‫‪ 1.0-4.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -13‬ﺁﭘﺎﺭﺗﻤﺎﻥﻫـﺎ )ﯾـﮏ ﺧﻮﺍﺑـﻪ‪ ،‬ﺩﻭ‬ ‫ﺧﻮﺍﺑﻪ(‬

‫‪ -14‬ﺍﻣﺎﮐﻦ ﻋﻤﻮﻣﯽ ﻫﺘﻞﻫﺎ ﻭ ﻣﺘﻞﻫﺎ‬ ‫‪ 1.0-3.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -15‬ﺧﻮﺍﺑﮕﺎﻩﻫﺎ ﻭ ﻣﻬﻤﺎﻧﺴـﺮﺍﯼ ﻫﺘﻞﻫﺎ‬ ‫ﻭ ﻣﺘﻞﻫﺎ‬ ‫‪ 1.0-3.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ 2.0-6.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪-17‬‬

‫ﺍﻏﺬﯾﻪﻓﺮﻭﺷﯽﻫﺎ‬ ‫‪ 1.5-2.5‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -18‬ﮐﺘﺎﺑﺨﺎﻧﻪﻫﺎ ﻭ ﻣﻮﺯﻩﻫﺎ‬ ‫‪ 1.0-3.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫ﻳﻜﺘﺎ ﺗﻬﻮﻳﻪ ﺍﺭﻭﻧﺪ‬ ‫ﺍﺻﺎﻟﺖ ﺗﻬﻮﻳﻪ ﻣﻄﺒﻮﻉ‬

‫‪ -25‬ﮐﻠﯿﺴﺎﻫﺎ‬ ‫‪ 1.0-3.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬ ‫‪ -26‬ﺳﺎﻟﻦﻫﺎﯼ ﺑﺎﺯﯼ ﺑﻮﻟﯿﻨﮓ‬ ‫‪ 1.0-2.5‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫‪ -16‬ﮐﻼﺱﻫﺎﯼ ﺩﺭﺱ‬

‫ﺳـﺎﻟﻦﻫﺎﯼ‬

‫‪ -23‬ﺯﻧﺪﺍﻥﻫﺎ‬ ‫‪ 1.0-2.5‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬ ‫‪ -24‬ﺳﺎﻟﻦﻫﺎ ﺳﺨﻨﺮﺍﻧﯽ ﻭ ﺗﺌﺎﺗﺮ‬ ‫‪ 1.0-3.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬ ‫* ﺭﻭﺷــﻨﺎﯾﯽ ﻭ ﻧﻮﺭﭘــﺮﺩﺍﺯﯼ ﺻﺤﻨﻪ‬ ‫ﻧﻤﺎﯾﺶ ﺭﺍ ﺷﺎﻣﻞ ﻧﻤﯽﺷﻮﺩ‪.‬‬

‫‪ 1.0-4.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫ﻏﺬﺍﺧـﻮﺭﯼ‬

‫‪ 1.0-3.0‬ﻭﺍﺕ ﺑﺮ ﻓﻮﺕ ﻣﺮﺑﻊ‬

‫ﺗﺬﮐﺮﺍﺕ‪:‬‬ ‫ﻭ‬

‫‪ .1‬ﻣﻘﺎﺩﯾــﺮ ﺭﻭﺷــﻨﺎﯾﯽ ﺑــﺮﺍﯼ ﺍﮐﺜــﺮ‬ ‫ﺳــﺎﺯﻩﻫﺎﯼ ﻫﻮﺷــﻤﻨﺪ ﺍﻧــﺮﮊﯼ ﻣﻘﺎﺩﯾــﺮ‬ ‫ﭘﺎﯾﯿﻦﺗﺮﯼ ﺧﻮﺍﻫﺪ ﺑﻮﺩ‪.‬‬ ‫‪ .2‬ﺟﺎﻧﻤﺎﯾﯽﻫــﺎﯼ ﺭﻭﺷــﻨﺎﯾﯽ ﻭﺍﻗﻌﯽ‬ ‫ﺑﺎﯾﺪ ﺟﻬﺖ ﻣﺤﺎﺳﺒﻪ ﺑﺎﺭﻫﺎﯼ ﺭﻭﺷﻨﺎﯾﯽ ﺩﺭ‬ ‫ﻫﻨﮕﺎﻡ ﻧﯿﺎﺯ‪ ،‬ﻣﻮﺭﺩ ﺍﺳﺘﻔﺎﺩﻩ ﻗﺮﺍﺭ ﮔﯿﺮﻧﺪ‪.‬‬