Assumed power plant details are given in Table 1 was written more than 30 years ago but comparisonwith more recent programs,using the NIST [11] propertysubroutines,showed negligible differences in theresulting output.The wet steam cycle calculations

Assumed power plant details are given in Table 1 was written more than 30 years ago but comparisonwith more recent programs,using the NIST [11] propertysubroutines,showed negligible differences in theresulting output.The wet steam cycle calculations
Assumed power plant details are given in Table 1
was written more than 30 years ago but comparison
with more recent programs,using the NIST [11] property
subroutines,showed negligible differences in the
resulting output.
The wet steam cycle calculations were based on
starting assumptions for the evaporation and condensing
temperatures.The former of these was based
on what was regarded as a convenient upper pressure
limit that could be allowed for in a screw expander,
assuming bearing loads that can be readily withstood
by standard bearings with a satisfactory operating life.
The latter was taken as 100 ◦C in order to avoid any
problems associated with the need for a deaeration
system,should condensation take place at subatmospheric
pressure.
With these conditions fixed,an optimum cycle could
be derived by matching the heat source to the cycle,
including all the parameters accounted for in the ORC
software but without the need for iterative calculations,
using only a large Excel spreadsheet and steam
properties derived from tables.Repetitive calculations
were,however,carried out to determine the pinch
point values in the heat exchangers that gave a minimumtotal
surface area per unit output and thesewere
taken as the best points.
The wet steam cycle calculations were carried out
in parallel with performance estimates of the size and
efficiency of the screw expanders needed to produce
the required output using in-house software developed
for this purpose [12].Thus,the cycle calculations
were performed initially with assumed values for the
expander efficiency.The results were then used to
estimate the expander performance.The cycle calculations
were then repeated with the revised efficiency
estimates.This procedure was less complex and more
economical in running time than attempting to produce
a program to iterate all the variables in a single
calculation.

Assumed power plant details are given in Table 1 was written more than 30 years ago but comparisonwith more recent programs,using the NIST [11] propertysubroutines,showed negligible differences in theresulting output.The wet steam cycle calculations
人工翻译,太花时间了.
假设的电厂详情在表1中给出,(这）是30多年前写的,但是用NIST（美国国家标准和技术学会）的属性子程序与比较近的计划做了比较,结果表明,最终输出的差别可以忽略不计.
湿蒸汽循环的计算是基于对蒸发温度和凝聚温度的起始的假设.其中前者是基于被认为是一个实用的压力上限（这个上限是螺旋膨胀机中可以允许的）,假设承载的负荷由具有满意工作寿命的标准轴承能够很容易承受.而后者取为100◦,以避免与必须采用脱气系统而带来的任何问题,应在低于大气压的压力下发生凝聚.
在这些条件确定的情况下,一个最佳的循环可以通过将热源与循环周期匹配,包括出ORC软件中说明的,但无需进行迭代计算的所有参数,仅使用一较大的Excel电子数据表和由表格推出的蒸汽性质.然而,为了确定热交换中的夹点（pinch point）值,进行了重复计算,这些夹点值给出了每单位输出的最小总表面积,而它们被取作为最佳的点.
湿蒸汽循环的计算是与螺旋膨胀机大小和效率的性能估计同步进行的,这里的螺旋膨胀机是用为此目的而开发的自建软件产生所需的输出所需要的.因此,循环计算最初是以膨胀机效率的假设值进行的.然后,结果被用来估算膨胀机的性能.再然后,循环计算以修订后的估计效率重复进行.这个过程不是那么复杂,在运行时间上比试图设计一个程序迭代单一计算中所有变量更加经济.