The technician arrives and talks to the owner about the problem. The owner explains to the technician that there has been a gradual increase in case temperatures from 0° to 15° in about three weeks’ time. The owner also explains to the technician that customers are complaining of a warm product load. The owner also lets the technician know that the condensing unit has a 100 percent run time in trying to keep the product cold.
The technician enters the basement and notices that the condensing unit is a three-horsepower, R-404A, semi-hermetic, reciprocating compressor with a forced air condenser. The system also has a TXV and a receiver. The temperature in the basement was 70°. The technician installs gauges on the low and high side of the compressor and takes an amp reading. The pressure on the low side reads 33.5 psig (0°), and the high side read 174 psig (80°). The amp reading was five amps under Rated Load Amps (RLA) on the nameplate. The service technician then puts a temperature probe on the condenser and evaporator outlets in order to get a condenser subcooling and an evaporator superheat reading respectively.
The condenser outlet temperature reads 71° and the evaporator outlet temperature reads 14°. This would give the system 9° of condenser subcooling and 14° of evaporator superheat as shown in equations 1 and 2.
In summary, the system check was:
Evaporating temp.: 0°F (33.5 psig)
Condensing temp.: 80° (174 psig)
Condenser subcooling: 9°
Evaporator superheat: 14°
Basement ambient: 70°
The technician then realizes the unit cannot be low on refrigerant because of the 9° of condenser subcooling telling him that there is liquid in the condenser. Also, evaporator superheat is usually high on systems low on charge.
After thinking a moment, the technician wonders why the condensing temperature is only 10° hotter than the ambient or surrounding temperature in the basement. This is an indication that the condenser is not rejecting very much heat from the system to the basement air. The difference in temperature between the condenser temperature and the ambient air is often called the “Condensing Split,” and it should run from 25-30° on standard-efficiency condensers under normal heat loads.
The technician then sits down and analyzes the system check again. A dirty condenser would give a high condensing temperature and pressure. A dirty evaporator would give a low evaporating temperature and pressure. If the liquid line or metering device was restricted, the evaporating temperature and pressure would be low. The technician wonders what would cause a high evaporating temperature (pressure), low condensing temperature (pressure) with low amp draw.
The technician then realizes that the compressor’s valves or piston rings could be worn and leaking. This would cause leakage of pressure between high and low side of the system as the pistons reciprocated, causing a lower condensing pressure with a higher evaporating pressure. The amp draw also would be low because of this pressure leakage within the cylinders and/or valves.
The technician then pumps the compressor down and examines the valves and valve plate. Sure enough, the valves are not seating properly and are warped. A new set of valves with gaskets for the valve plate and head are installed.
The compressor is evacuated and put into commission. After about one hour of running time, the system pulls down to 0°. A new system check is taken and everything seems to be running right. Both the condensing pressure and evaporating pressure are normal. The technician blames the valve problem on wear and tear since no obvious system or mechanical problems or discoloring existed. The technician then explains his actions to the owner.
The new system check is:
Evaporating temp.: -16° (20 psig)
Condensing temp.: 96° (222 psig)
Condenser subcooling: 8°
Evaporator superheat: 7°
Condenser split: 26°
Basement ambient: 70°
Publication Date:10/01/2007
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