A condenser is designed for a maximum heat load $1500$ x $10$ Btu$/$hr at

the condenser pressure of $2\mathrm{.}0$ in$.$ Hg abs$.$ The water inlet temperature is

$66\mathrm{.}7$ F$.$ The condenser Admiralty tube $(60$ feet long$)$ has a $1$ in$.$ OD$-18$

BWG and a cleanliness factor of $85\%.$ The water velocity in the tube is $6\mathrm{.}9$

fps$.$ Calculate the condenser heat transfer surface area and pump horsepower. $9-10.$ A condenser is designed for a maximum heat load $\backslash (1500\backslash$times $10^\{6\}\backslash$mathrm$\{$Btu$\}/\backslash$mathrm$\{$hr$\}\backslash )$ at the condenser pressure of $\backslash (2\mathrm{.}0\backslash$mathrm$\{$in$\}.\backslash$mathrm$\{$Hg$\}\backslash )$ abs$.$ The water inlet temperature is $66\mathrm{.}7$ F$.$ The condenser Admiralty tube $(60$ feet long$)$ has a $\backslash (1\backslash$mathrm$\{$in$\}\backslash ).$ OD$-18$ BWG and a cleanliness factor of $\backslash (85\backslash \%\backslash ).$ The water velocity in the tube is $6\mathrm{.}9$ fps$.$ Calculate the condenser heat transfer surface area and pump horsepower.

Assume that the condenser has a single pass and the total external hydraulic loss is $80$ ft $.$

$9-11.$ The condenser designed in Problem $9-10$ is changed into a dual$-$pressure condenser by adding a partition on the steam side. Other conditions are identical to those in Problem $9-10.$ Estimate the reduction in condenser pressure.