Page 431 - Handbook of Energy Engineering Calculations
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lb/h)(specific  heat)  (1.8  conversion  factor).  Or,  temperature  decrease  =
               (2,391,120)/(307,500)(0.72)(1.8)  =  6°C  (10.8°F).  Then,  the  shellside  outlet
               temperature = 105 – 6 = 99°C (210.2°F). Then, the LMTD = (54 – 15)/ln
               (54/15) = 30.4°C (86.7°F) = Δ T .
                                                      m


               3. Make a first-trial calculation of the surface area of this exchanger
               For a first-trial calculation, the approximate surface can be calculated using
                                                                                              2
               an assumed overall heat-transfer coefficient, U, of 250 Btu/(h) (ft ) (°F) (44.1
                     2
               W/m °C). The assumed value of U can be obtained from tabulations in texts
               and handbooks and is used only to estimate the approximate size for a first
               trial:
                                                                                   2
                                    A = 2,391,000/(250× 30.4×1.8) = 175ft (16.3m            2
                  Since the given conditions specify a maximum tube length of 12 ft and a
               minimum tube diameter of 5/8 in, the number of tubes required is:

                                              n = 175(12×0.1636) = 89 tubes
               and the approximate shell diameter will be:
                                      D  = 1.75 ×0.625 ×89       0.47  = 9 in (228.6mm)
                                        a
                  With  the  exception  of  baffle  spacing,  all  preliminary  calculations  have
               been made for the quantities to be substituted into the dimensional equations.
               For the first trial, we may start with a baffle spacing equal to about half the

               shell diameter. After calculating the shellside pressure drop, we may adjust
               the baffle spacing. Also, it is advisable to check the Reynolds number on the
               tubeside to confirm that the proper equations are being used.


               4. Find the maximum number of tubes for this heat exchanger
               To  find  the  maximum  number  of  tubes  (n         max )  in  parallel  that  still  permits

               flow in the turbulent region (N  = 12,600), a convenient relationship is n                max
                                                     Re
               = W /(2d  Z ). In this example, n      max  = 307.5/(2× 0.495 × 1.7) = 183. For any
                          i
                    i
                             i
               number of tubes less than 183 tubes in parallel, we are in the turbulent range
               and can use Eq. (1)
                  From  Table  6,  the  appropriate  expressions  for  rating  are:  Eq.  (1)  for
               tubeside,  Eq.  (11)  for  shell-side,  Eq.  (18)  for  tube  wall,  and  Eq.  (19)  for
               fouling. Eq. (21) and (25), respectively, are used for tubeside and shellside

               pressure drops.
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