Improving Cold-Weather Gas Turbine Inlet Filter Performance

Pneumafil Gas Turbine Inlet Air Anti-Icing Systems

The Gas Turbine inlet filter systems and the turbine itself can be adversely affected when freezing temperatures combine with high moisture content. Damaging effects happen in a very short time and can be both long-lasting and expensive in terms of operational effectiveness and maintenance costs.

The Problem

Hoarfrost, sleet, snow or freezing plume from cooling towers can plug the air filters while ice can be ingested into the unit, structurally compromising the system. This can cause significant increases in the differential pressure across the filters and therefore in the total vacuum pressure at the inlet to the turbine.

The additional negative pressure reduces the available output of the turbine and hence plant revenue. If plugging of filters is excessive and the maximum allowable differential pressure across filters is reached, it is possible to permanently damage filters or shut-down the turbine.

Replacement filters may not be immediately available, requiring prolonged downtime and loss of revenue, unplanned maintenance labor costs.

Ice can form inside the inlet system even when the outdoor temperature is not actually at or below freezing. When the air enters the inlet filter system, it speeds up as it passes through the filter house and inlet duct and silencer.

Velocities increase since the cross section of the duct and compressor inlet is always considerably less than the cross section of the inlet filter house.

This velocity increase causes a decrease in the temperature of the air. The temperature drop can result in condensation of water vapor in the air and depending on the outdoor temperature, possibly the formation of ice on the turbine compressor inlet.

Ice Clogged Filters

Figure 1: Ice clogged filters have been removed to allow some air to pass unfiltered

Some turbines also use inlet guide vanes to restrict airflow into the turbine and allow running at partial load. The restriction of the space between guide vanes as they are closed down can cause even higher velocities and ice formation immediately downstream.

That layer of ice can become dislodged during operation and impact the first or second row compressor blades causing damage to the compressor. If filters are already plugged from ice or snow there are only a few options for corrective action. Operators can remove some filters to relieve pressure to the turbine, but this may leave risk for foreign material ingestion and possible further damage to the turbine.

If ice or snow has only formed or collected on the first stage prefilters, removing only the prefilters may allow continued operation of the turbine with some level of protection but then there is risk of further damage to the more expensive final filters if conditions persist.The turbine may be shut down causing loss of revenue and filters must be replaced.

Operators Removing Snow and Ice from Gas Turbine

Figure 2: Operators attempting to remove snow and ice

Some operators have attempted to simply brush off snow and ice from the filters using brooms or remove filters and try to shake off the snow and ice. This is usually less than fully effective since ice can form within the filter media itself or between pleated media, not just on the surface. There is a very real risk of damaging filters using these methods.

Operators have attempted to spray filters with de-icing fluid. Air Filters are not normally designed for direct contact with liquid chemicals, so there is similar risk of permanently damaging the filters. There is also risk of ingesting some of the de-icing fluid into the turbine causing damage there. Some fluid could hit the ground possibly causing environmental contamination issues.

Snow and Ice on Static Filters

Figure 3: Snow and ice has built up heavily between static filter pleats and is not easily removed

The best solution is to prevent the filters from freezing over in the first place and or prevent the formation of ice at the turbine compressor inlet by providing inlet air heating. This paper will describe several options of inlet air heating solutions.

Before designing a heating system for an inlet filter house, operators should carefully consider the goals of the project: protect the filters from freezing over, prevent ice formation at the compressor inlet or both. This generally informs where the heat must be introduced into the combustion air stream. If only the compressor inlet ‘bell mouth’ area is to be protected, the heat can be injected in the inlet duct downstream of the main combustion air silencer and far downstream of the inlet filters. A solution like this generally results in a lower initial capital cost for the heating system.

Of course, injecting heat downstream of the filters does nothing to prevent filters from freezing over. Injecting heat upstream of the filters generally helps both to protect the filters and prevent ice at the compressor inlet bell mouth but the capital cost of the solution is higher.

The next design decision is to determine total heat load. To prevent ice formation due to the increase in air velocity in the inlet system, the typical recommended design value for inlet air temperature rise is about 12 degrees F (8 degrees C).

The goal is to reduce the relative humidity in the incoming air stream to about 68% RH so that condensation cannot occur and ice cannot form as the combustion air speeds up and cools as it flows through the filter house and inlet duct.

The operator may decide a higher heat load is required based on ingested snow, ice, cooling tower plumes, and other factors. If the inlet heating system is to provide enough heat to actually melt snow or ice that is ingested into the inlet and captured on filters, this greatly increases the heat load since the latent heat of fusion of water is so much more than the heat required to simply raise the temperature of the incoming air.

The site environment should be considered carefully and the mass flow rate of ingested snow or ice must be estimated. It is often difficult to provide enough heat to melt the entire ingested snow and ice load. Therefore, design compromises are often made to limit capability only to melting partial or smaller ingested loads.

In general a value of 0.2 g/m3 of air adds about 10% heat load. Pressure drop on the combustion air flow path and noise are other factors to consider in the heating system design and may impact the choice of the heat source.

Compressor bleed air heating systems have very low combustion air pressure drop, in some cases negligible.

But compressor bleed systems do add noise. Typical self generating noise is 85 dBA SPL @ 1 meter. Silencers and other options are available if lower noise levels are needed. Compressor bleed systems inherently reduce the available turbine power output since a significant portion of the total combustion air is not available for combustion.

The turbine OEM must be consulted to determine the maximum allowable bleed air and the resultant reduction in turbine output.

The application of heating coils or heated vanes will likely add some measurable pressure drop to the combustion airflow path and this will result in some loss of turbine power output.

Using heating coils also requires additional piping for the return side of the fluid and also potentially re-circulation pumps. If steam is used, the condensate must be addressed. Pressure drop of glycol coils is likely to be higher than steam coils.

Deciding on a heat source solution

Compressor Bleed Air Systems

The most common type of inlet heating system is known as compressor bleed heat system. It uses a portion of the combustion air, bled off from the turbine compressor section which has been self-heated due to compression. The air is removed from the compressor at a piping connection on the compressor casing and recirculated back to the main inlet airflow.

This air from the compressor may be in the range of 500 F to 700 F and at 100 to 120 PSI depending on the turbine model and the stage of compression the air is bled from. The turbine OEM should be consulted first to confirm if a connection to the compressor casing exists and if the removal of some portion of the compressed inlet air is possible.

Low Pressure Compressor Bleed System

Figure 4: Example of a low pressure compressor bleed system. Routes low pressure hot air to face of system (note the thermal insulation on supply line). This system is capable of lowest self-noise but requires a large, centralized silencer (not shown) to attenuate noise of expansion.

It is known that multiple units of Siemens Westinghouse W501F (Siemens SGT5000F) SGT 8000H, GE 7FA, Mitsubishi M701F, M501G, and Alstom GT-11N2 model turbines have implemented compressor bleed air inlet heating systems. The turbine OEMs have integrated such solutions as options to their base plant offerings in many cases.

System design requires the following inputs:

  • Actual volumetric flow of combustion air
  • Mass flow of compressor bleed air
  • Compressor bleed air temperature
  • Compressor bleed air pressure
High Pressure Compressor Bleed System

Figure 5: Example of a high pressure compressor bleed system. Pressure reducing, noise attenuating dispersion nozzles are mounted on the vertical pipe risers.

Protecting the filters means first introducing the heat into the airflow upstream of the filters. This makes a larger heating array than if the only need is to keep ice from forming at the compressor inlet. In turn this also helps protect the inlet filters from freezing.

There are two options for dispersing the hot air in front of the filters: a high pressure system or a low pressure system. In the high pressure system the hot air is delivered nearly at the pressure it is bled off from the compressor.

The distribution system is constructed of piping. The dispersion of the air is accomplished with nozzles that reduce the pressure, attenuate noise and disperse the air radially from each nozzle. The number and placement of nozzles is determined in the detail design phase but it is often over 100 on a large turbine inlet.

The low pressure solution uses a pressure-reducing valve between the compressor bleed connection on the turbine and the filter inlet. The air can then be passed through lighter gauge ducting (but generally larger in cross section) and a central silencer is used to reduce the noise. Additional branch ducting is used on the inlet face with slots to disperse the hot air across the face of the inlet.

Infrared Heating systems

Infra-Red (IR) heating can also be used but generally for small applications, perhaps less than 50 MW size turbine generators. This is simply due to the fact that a large inlet requires extensive power wiring to energize a large infrared heating element array.

But, if the infrared system is connected directly to the electrical grid it can be energized independently from the turbine. This may be an advantage if a cold start in winter weather is desired.

Heating Coils

A heating system can be designed with steam or glycol circulated through traditional fin and tube coils mounted in the inlet air stream.

The disadvantage to using glycol as the fluid is that it introduces the need for either a heat exchanger or for a separate boiler to heat the fluid.

Steam Coil Module

Figure 6: Example of a steam coil module completed at the factory ready for shipment to site

There is probably both added initial capital and operating cost for the boiler or heat exchanger and the fluid circulation pump and return piping. Fin and tube type coils are generally heavy, requiring that inlet filter supports be analyzed structurally to ensure the weight can be properly supported.

Heated Vanes

Figure 7: Example of a heated vanes with electrical resistance heating elements included

Steam has been used in some sites by piping steam from the HRSG back to steam coils mounted in the inlet. The piping runs are generally longer and must be well insulated and the condensate must be returned to the system.

Heated vanes

Heated vanes are a relatively new development for inlet heating. Vertical vanes have long been used as moisture separators and they perform this function very well. But using them in freezing temperatures has always been a shortcoming.

Heated Vanes with Hot Fluid Circulation

Figure 8: Example of heated vanes using hot fluid circulation tubing

Collected water can freeze in the drainage slots or hooks causing moisture carryover. Worse, the entire opening between individual vanes can be blocked with snow and ice. A novel development has been the use of either electric resistance elements or tubes circulating hot fluid around the vanes to prevent the freezing.

The electric resistance type are available with heating capacities up to 9.6 kw/m2. The capacity of the fluid types depends on the fluid temperature.

Nederman Pneumafil routinely provides engineered solutions to reduce costly repairs and unplanned downtime caused by cold temperatures and wet weather. In every opportunity the local site conditions are reviewed with the operator, the design goals are agreed and a solution is developed. It must be noted that operators often want a guarantee that installing such a system will never shut down again due to snow and ice, in order to justify their capital investment.

Heated Vanes with Electrical Resistance

Figure 9: Example of heated inlet vanes with electrical resistance installed

Generally such guarantees are very difficult to provide and the system performance is simply defined by how much heat is added. Mother nature and the weather are as unpredictable as ever and any occurrence of actual outdoor conditions outside the agreed upon design conditions can still possibly lead to downtime or reduced output.

However, a heating installation will absolutely reduce the amount of downtime or lost revenue compared to a system without such protection.