Skip to main content

Why Compressors Fail Part 1

 Part 1 - Refrigerant Flood Back 

Foaming can be clearly seen in the compressor oil sight glass, this is a clear indication of the prescence of liquid refrigerant in the oil.


Refrigerant flood back occurs during the running cycle of the machine. This is where large volumes of liquid refrigerant are returned to the running compressor down through the Suction pipe work, in an uncontrolled manner. Depending on the degree of liquid returning to the compressor, determines as to what damage will occur. This can often be seen as foaming in the compressors’ oil level sight glass.

Here we have evidence of a seizure of the bearing


If liquid is drawn into the cylinder bores, the lubrication to the cylinders and pistons will be washed away causing scoring and overheating in the cylinder, which in turn will lead to small metallic particles contaminating the inside of the machine. This liquid will also dilute the lubricating oil in the compressor sump. As the oil becomes more and morediluted with liquid refrigerant, its ability to lubricate becomes compromised. When this liquid rich oil is drawnup through the crankshaft to lubricate the bearings, con rods, cylinder walls, etc due to friction the refrigerant in the oil starts to Flash Off into a vapour, this then prevents the oil being able to lubricate the necessary parts, and typically the main bearing and the con rods, furthest from the oil pick up point, will quickly dry out and then seize. Sometimes the upper main bearing will wear so badly that it can cause rotor / stator contact and a burnout, or more often, the upper most con rods seize onto the crankshaft and as the motor continues to rotate the crank, thereby breaking the aluminium con rods, and eventually the pistons as well. When liquid has caused con rods to seize onto the crankshaft the crankshaft journal will be found to have aluminium from the con rod welded onto the bearing surface of the crankshaft. This is caused by the liquid refrigerant virtually exploding from the oil due to the heat of friction from the bearing surfaces. As the con rods and pistons are broken, large pieces of debris are thrown around the compressor shell and motor area, these can cause motor winding insulation damage and motor burn out. Very often the initial diagnosis is the motor burn out, but the actual failure was refrigerant flood back.

Here we can see the evidence of aluminium from the con rod being welded on to the crankshaft. This is caused when liquid refrigerant fl ashing off from the oil and washes the lubrication from the bearings


Flood back often occurs during night time operation when the duty requirements are low, and the equipment has excess capacity. Often expansion valves are oversized for the system duty and each time the compressor starts or large product loads are introduced to the plant, the expansion valve will be forced to open, and over feeding of the evaporator, even more so if the superheat setting has been set too low, will be the result. 


Thermostatic expansion valves are forced to open by the suction pressure falling which causes a fall in pressure under the expansion valves’ diaphragm. This pressure fall reacts faster than the charge in the expansion valve bulb and initially the expansion valve is driven open. Until the bulb charge reacts and the bulb pressure starts to 

fall to help close the valve, liquid refrigerant will rush into the evaporator in a virtually uncontrolled manner (The bigger the valve the larger the liquid quantity). Once this liquid reaches the suction pipe work its next port of call is back to the compressor. Monitoring the expansion valve superheat setting under all conditions and setting the superheat to a point that is stable and can be maintained under all load conditions will often cure the problem. Fitting a smaller capacity orifice may be needed to achieve this stable control.


Upgrading to an electronic expansion valve or by fi tting a suction line accumulator may be necessary in systems that cannot be controlled by older conventional controls.


Causes of Liquid Flood Back

1. Low Evaporator loads

2. Oversized equipment

3. Cold room product distribution (poor air circulation in cold room caused by lights, racking etc)

4. Faulty evaporator fans

5. Oil logging in evaporator

6. Poor evaporator defrosting or defrost schedules ( Iced up evaporator / No air fl ow / Poor heat transfer)

7. Oversized Expansion Valve Orifice

7A. Wrong type expansion valve

7B. Expansion valve equalisation tube restricted or blocked (Capillary tube? Oil logged? etc)

7C. Expansion valve bulb strap loose or bulb in the wrong position on the suction pipe.

7D. Superheat Setting too low 


Preventative measures to avoid Refrigerant Flood back

1 Expansion Valve duty must be checked for the correct size orifice

2 Superheat setting must be set for minimum 6-8 Degree K Superheat 

(Thermostatic). Can be lower if electronic EEV used

3 Fit correct size Suction Accumulator with proper oil return function

4 Check and reset Defrost control as necessary

5 Fully check the system operation or re-commission the plant 


NOTE 

Liquid Flood back very often occurs during LOW LOAD conditions, which tends to be during the night, due to the lack of activity such as Door Openings, product movements, fork truck and the cold room Personnel which all give an increase to the plant duty.

Therefore 24 hour logging of the plant operating conditions will often help to pinpoint plant problems that only occur during the night operation, when the plant is unattended.


Why Compressors Fail

This series of Field Service Notes has been designed to assist Technicians and Refrigeration Engineers in understanding the causes of compressor failures, their diagnosis, rectification and prevention.


There are 5 main reasons for compressor failure;

1. Refrigerant Flood Back

2. Flooded Starts

3. Liquid Slugging

4. Overheating

5. Lack of Lubrication


The first 5 of these Field Service Notes will cover the above topics and there will be further Notes covering other causes of failure such as Moisture, Acids, Electrics, Dirt (Copper debris, Welding debris, Ferrous particles etc.)


The answers to what caused a compressor to fail are, in 99.9% of cases, found inside the compressor. During the compressor strip down the evidence as to the cause will be revealed!


Simply replacing a failed compressor with a new compressor without fi nding out why the first compressor failed will most likely simply lead to another failed compressor.


We hope that the information in this series of Field Service Notes will be of assistance to engineers in preventing unnecessary compressor failures in the future.

Comments

Popular posts from this blog

Type of Heat Exchanger

 There are several types of heat exchangers used in HVAC systems, including: 1. Coil Type:     - Chilled water coils     - Hot water coils     - DX (direct expansion) coils     - Evaporator coils     - Condenser coils 2. Shell and Tube Type:     - U-tube heat exchangers     - Straight tube heat exchangers 3. Plate Type:     - Plate and frame heat exchangers     - Plate and shell heat exchangers 4. Finned Tube Type:     - Finned tube heat exchangers 5. Spiral Type:     - Spiral heat exchangers 6. Regenerative Type:     - Regenerative heat exchangers 7. Adiabatic Type:     - Adiabatic wheel heat exchangers 8. Run-Around Coil Type:     - Run-around coil heat exchangers These heat exchangers are used in various applications, including: - Air conditioning - Heating - Ventilation - Refrigeration - Heat recovery - Industrial processes Each type of hea...

HVAC common unit converter chart

 Here's a comprehensive HVAC unit converter chart: Volume Flow Rate 1.CFM (Cubic Feet per Minute) to CMH (Cubic Meters per Hour):  1 CFM ≈ 1.699 CMH 2.CFM to m³/s (Cubic Meters per Second):  1 CFM ≈ 0.000472 m³/s Airflow Velocity 1.FPM (Feet per Minute) to m/s (Meters per Second):  1 FPM ≈ 0.00508 m/s 2.m/s to FPM:  1 m/s ≈ 196.85 FPM Energy and Power 1.BTU/h (British Thermal Units per Hour) to kW (Kilowatts):  1 BTU/h ≈ 0.000293 kW 2.Tons of Refrigeration to kW:  1 Ton ≈ 3.517 kW Pressure 1.Inches of Water Gauge (in wg) to Pascals (Pa):  1 in wg ≈ 249.08 Pa 2.PSI (Pounds per Square Inch) to kPa (Kilopascals):  1 PSI ≈ 6.895 kPa Temperature 1.°F (Fahrenheit) to °C (Celsius):  °C = (°F - 32) × 5/9 2.°C to °F:  °F = °C × 9/5 + 32 Additional Conversions Length 1.Inches to Millimeters:   1 inch = 25.4 mm 2.Feet to Meters:  1 foot = 0.3048 meters Area Square Feet to Square Meters:  1 sq ft = 0.0929 sq m Volume Gallons to L...

VALVES USED IN A CHILLER SYSTEM AND THE TYPICAL VALVE PACKAGE

  VALVES USED IN A CHILLER SYSTEM AND THE TYPICAL VALVE PACKAGE 1.Chilled Water Side Valves ⇒Isolation valve (manual/electric actuated). ⇒ Installed on CHW supply and return lines.  ⇒ Used to isolate chiller for maintenance. 2. Balancing Valve (Manual or Automatic)  ⇒ Ensures correct flow rate to/from chiller.  ⇒ Helps maintain Delta T and proper flow distribution.  ⇒ Located after evaporator outlet (return line). 3. Differential Pressure Bypass Valve (if 2-way valves in system)  ⇒ Prevents excess pressure build-up when terminals shut.  ⇒ Maintains flow through chiller. 4. Flow Switch  ⇒ Senses chilled water flow across evaporator.  ⇒ Safety interlock: trips chiller if flow is lost.  ⇒ Usually paddle type or electronic. 5. Air Vent Valve (Manual or Automatic)  ⇒ Removes air pockets.  ⇒ Placed at high points of piping and chiller headers. 6. Drain Valve  ⇒ For flushing, cleaning, and maintenance.  ⇒ Located at low poin...