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Figure 135 (Continued )
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6 When pumping closed chilled water systems from open tanks, the elevation of the working water level in the open tank must be compared with the minimum static pressure of the building The difference between the two elevations must be recognized, since this static head must be accounted for in any energy evaluation of the system The energy lost is computed as follows: kW lost gal/min head 0746 3960 P E gal/min head 5308 P E (131)
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Pumping Open Thermal Storage Tanks Pumping Open Thermal Storage Tanks 367
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where gal/min head P E
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flow of water from pressurized system pump head required to return the water to the system efficiency of pump efficiency of pump motor for constant-speed pumps or the wire-to-shaft efficiency of the motor and variable-speed drive for variable-speed pumps
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The energy calculation for a system is as follows: Assume that the top of the building is at elevation 730 ft, and the working level in the energy storage tank is 520 ft These elevations are in actual levels above sea level Also, assume that there is an expansion tank located at the top of the building and that 10 psig is maintained in this tank by the makeup water system The pressure gradient required to maintain the 10 psig at the top of the building is 730 (10 231), or 763 ft The pressure gradient for the working water level of the storage tank is 520 ft The pressure difference between the pressure at the top of the building, 763 ft, and the open tank, 520 ft, is 243 ft With 15 ft of pipe friction in the piping between the storage tank and the water system, the total head required for the pump is 258 ft If the system flow is 1000 gal/min, the pump efficiency 83 percent and the wire-to-shaft efficiency of a motor and variable-speed drive is 89 percent, kW lost 1000 258 5308 083 089 658 kW 7 If the static pressure of a closed system is greater than the elevation of the open tank, some means must be used to maintain the minimum pressure at the top of the building There are several methods of achieving this: a Backpressure valves (Fig 134b) can be used, but they should maintain the pressure on top of the building, not the inlet pressure to these valves Self-operating valves should not be used in many cases because the friction of the return water main between the valves and the top of the building is a variable The valves should be equipped with a control system that measures the pressure at the top of the building and adjusts the valve position to maintain that pressure Normally, a pressure transmitter located at the top of the building along with a proportional-integral controller can adjust the valve position to maintain the desired
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pressure on top of the building Usually, this control procedure is adequate for small buildings where the energy loss from the pressurized system to the open tank is minimal b On larger buildings with high pressures, it may be desirable to save this energy lost from the depressurization of the water Figure 135a describes a procedure that can be used, that of a pressure recovery pump This pump is driven by a similar pump equipped with a turbine wheel A typical performance curve for such a turbine is shown in Fig 135b The energy recovered by such a pumping system can vary from 10 to around 67 percent of the pressure difference between the chilled water system and the open tank A variable-speed pump responding to the chilled water system return pressure is installed in series with the recovery pump The variable-speed pump in series with the energy-recovery pump provides a more efficient arrangement for most applications than combining the variable-speed motor with the turbine and energy-recovery pump on one base The difficulty of this one-base arrangement is the fact that the turbine must run at the same speed as the variable-speed pump The turbine should operate at the speed caused by the flow of water from the system and the force on the turbine shaft created by the driven pump The variablespeed pump runs at a speed necessary to maintain the system pressure They are seldom the same speed An excellent article on the savings of the turbine-driven pump in lieu of a heat exchanger and where to use it is available in ASHRAE Transactions DA-88-27-2 by R M Tackett The evaluations included in this article will assist the designer in the evaluation of the cost of these pumps versus heat exchangers to determine the amortization periods c The use of a heat exchanger to overcome the pressure difference between the open tank and the pressurized chilled water system (Fig 136) may not be an efficient procedure for chilled water storage systems because of the temperature drop across the heat exchanger If it is desired to store chilled water at 40 F with a temperature approach of 3 F for the heat exchanger, chilled water must be generated at 37 F, thus increasing the kilowatts per ton of the chiller Also, in like manner, only 43 F water is available for use by the chilled water system The heat exchanger therefore causes a total temperature swing of 6 F The savings in static pressure for high-rise buildings through the use of a heat exchanger must be offset with the friction loss of the heat exchanger as well as this temperature loss across it
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