Compressed Air: Compressing Hard

Introduction

Compressed air is an essential part of any manufacturing / processing setup. It is treated as a simple air system without much attention to it, which finally appears as a slow eater of your profit & bottomline.

Compressed air is often overlooked in energy studies also even by experienced energy auditors because many people do not fully understand compressed air equipment, their own system, or what it costs to produce compressed air power. Here is a pie chart representing various cost areas.

Some Facts
For those who are willing to take a look, and utilize golden opportunity for saving,

1. It takes about 8 hp of electrical energy to produce 1-hp-worth of work with compressed air. so it operates at just 12.5% efficiency.
2. 1cfm of air (1.7 M3/hr) cost - $100 per year in energy cost.
3. 2 psig cost — $398 per year in energy cost for every 100-hp.
4. A solenoid valve that stays open – Costs $9000 / year.
5. 50% of the compressed air generated isn’t used for production.
6. Leaks may range from 10 to 30%.

(The values are based on some assumptions: a compressor operates 8,000 hours a year; the cost of electricity is $0.06/kWh and the compressor produces 4.0 cfm at an expenditure of 1 hp (break horsepower) at a discharge temperature of 100°F and 100 psig. )

Considering the recent rise in energy costs an audit of the compressed air system could yield significant savings. Based on my experience in years of plant surveys, here is what is seen typically:

1. Ignoring the electrical cost of compressors.
2. Pressure losses.
3. Air leaks.
4. Running the header pressure higher than required.
5. Pressure regulators operate full open (because they work better that way!).
6. Inappropriate uses for compressed air.
7. Not recovering heat.
8. Inadequate or poor maintenance.
9. Not measuring air usage.
10. Ignoring the cost

There is more to a compressed air system than pipes and a compressor. There is the supply side of the system and the demand side plus generating system itself. The supply side may consist of an inlet filter, compressor(s), an after-cooler, a dryer, a receiver, and header piping.

Chilled water may be required for the after-cooler and dryer. Just operating a 100-hp compressor 24/7, 47-weeks/year will cost about $43,000/year ($0.06/kWh, 90% motor efficiency) in electricity alone.

The demand-side is every application where air is used. A solenoid valve that stays open most of the time could cost you as much as $9,000/year — this is a demand-side loss. Your system works best when the flow and pressure produced by the supply side match the optimum conditions, i.e., minimum flow at lowest pressure, required by the demand side.

Pressure losses are costing you money
There are unnecessary losses on the supply side and on the demand side. Causes are: undersized equipment such as dryers and filters, undersized piping, doglegs, crossing tees, and condensation (oil and water). In a well-designed system, the pressure drops in the piping before the dryer, and after, and to the header, should be negligible; the velocity throughout the system should be less than 20 ft. per second (fps). The dryer and filter should have a drop less than 2 psig — together. If you don’t meet any of these conditions, then you are wasting power and disrupting the unloading controls on your compressors.

Compressed air leaks
After you have addressed problems with your layout, it is time to look at the next ranking problem: leaks. Thirty percent, or more, of lost air in most facilities is from leaks! It takes a cooperative effort to eliminate this cost. You need a leak management program involving maintenance and production.

The goal of the short-term program is to determine which areas of the facility have the most leaks. Short-term means a year, with audits every three months. Inspections should be conducted with an ultrasonic leak locator when the plant is running and when it isn’t.

Goals for the long-term program are broader: educating personnel in operations and maintenance to identify and repair leaks. A material balance should be established for the plant and developed so air use for each department can be defined. Test the balance and update it. Providing incentives for conserving air can help drive down costs.

High header pressure
Every process in your plant that uses compressed air has a minimum pressure required to operate effectively. Except for the pressure drop in the delivery system, which should be minimized, extra pressure is a waste. Lower the pressure, save energy, right? Not when the perceived minimum pressure is high. The politically correct approach is to measure the equipment airflow and pressure required at the demand source. Once this is done, installing a receiver (a small vessel between the regulator and the process) or eliminating a restriction should help you find the real minimum.

What if a high pressure really is needed? You may want to supply the local high-pressure need with a secondary, smaller, “booster” rather than drive the whole system at a higher pressure. The filter press (Figure 3) required a 100-psig minimum while the rest of the chemical plant ran well on 90 psig.

Pressure regulators operate full open
Often the process regulator is wide open at the header pressure because the “droop” wasn’t allowed for. The regulator may be correctly sized but the gulp of air required is more than the line can supply. If, during the delay, there isn’t enough volume to hold the demand pressure, then the pressure falls. Production is negatively affected and the operator opens the regulator up to full line pressure. This is called “artificial demand.”

A fix for this problem is a receiver. This will hold the pressure until the regulator opens.

Inappropriate uses for compressed air
This can be the most difficult problem to solve. The previous example could represent an inappropriate use of compressed air if electrical power is available. Some other applications could be:

1. Cooling for electric cabinet
2. Vacuum (eductors)
3. Blowing, or blasting
4. Pumps (air-diaphragm)
5. Air hoists
6. Air vibrators and,
7. Sparging (agitating with air)

For other applications, such as cooling electric cabinets, it’s easier to justify less-expensive alternatives. Cabinet cooling is often required to prolong the life of electronic equipment. Compressed air seems like a tempting choice. However, it’s apparent from Table 1 that it doesn’t make economic sense. There are several cost-efficient methods of cooling that are available, including vortex cooling, heat pipe, thermoelectric refrigeration, ambient air, and standard refrigeration.

In vortex cooling, compressed air is chilled by expansion and bled into a cabinet. Hot air in the cabinet is educted to the outside by the flow of the chilled compressed air. To economize on air and prevent condensation of moisture, vortex units should be equipped with an automatic temperature shutoff. Although the cost saving isn’t as significant as other alternatives, such as heat pipe and refrigeration, vortex cooling works up to 200°F.

Blowing cash away
Another common waste of compressed air, apparent to anyone who has visited a packaging area, is the use of air to blow products or dust. A ¼-in. line will flow 32 cfm at 80 psig. An open-ended blow tube represents an annual loss of more than $3,800. Regardless of the application, several guidelines should be applied to compressed air being used for open blow-off:

1. Use anything else whenever possible
2. Use low pressure air from a blower — the lower the pressure the lower the cost
3. Regulate the flow to the lowest effective pressure — know the pressure!
4. Use a venturi nozzle or air inducers to reduce compressed air used
5. Shut-off blow-off air (automatically) when not needed for production.

Air amplifiers, or inducers, will reduce compressed air flow, where a mechanical method, such as a wiper, cannot replace blow-off. Air amplifiers use “venturi” action to pull in ambient air and mix it directly into the compressed air stream. The ratio of ambient air drawn in can be substantial. Amplification ratios up to 25:1 are possible. Using 10 cfm of compressed air can produce up to 250 cfm of blow-off air. This is a savings of 15 cfm of compressed air per ¼-in. blow-off.

Although air-operated diaphragm pumps are not very energy efficient, they tolerate aggressive conditions well and are not seriously damaged if run dry. Also, they are not a serious hazard in intrinsically safe environments. If an electric pump — diaphragm, centrifugal or progressive cavity — can be made to work, it will usually be cost-effective. When an air-diaphragm pump is the still the best choice, reduce the utility costs by either shutting off the air if the pump is not needed, or lowering the supply pressure. Generally, when a pump must operate for long periods, an electric pump will save money over an air-diaphragm pump.

Air hoists and air vibrators are sometimes chosen when electricity is not available or where the area is intrinsically safe. This safety issue is generally not a concern with pumps and agitators where isolation is easier. Hoists and vibrators pose other concerns. Air hoists used only occasionally have a high incidence of unnoticed air leaks. High-pressure air is required by air vibrators to be effective; economically, they are often a poor choice — except where small size is needed.

Sparging with air may be necessary if the product is sensitive, e.g., friable, or where mixing mechanically is not economical or practical. One example where mechanical mixing might be uneconomical would be where a tank is very long, requiring an agitator with a long shaft. Another would be where air is available but electricity is not. If mixing by sparging is the best solution, doing so at the lowest possible pressure reduces the cost. Use low-pressure air supplied by a blower, if available. Use a step-down regulator on compressed air, if only high-pressure air is available.

Not recovering heat
Compressing a gas generates a lot of heat. However, 85% to 90% of the motor horsepower used to run a rotary screw air compressor can be recovered in the form of heated air or water. Similar recovery, in the form of heated water, is possible with water-cooled compressors. It takes 8 hp of electrical energy to produce 1 hp of air power. That means that a portion of the 7 hp of unused energy is available as heat. Recouped heat can be used in many ways:

Space heaters
Heating process water
Boiler make-up
Running a “heat of compression” desiccant dryer.

Fix it when it breaks
This seems to be the modus operandi with utilities. Too often maintenance on compressed air is viewed as an expense when it is really an opportunity for savings. Maintenance on the supply side has a direct impact on plant energy use.

A high pressure drop in filters and separators is a problem we see a lot. If you knew what power costs per psig, then you would probably re-evaluate your schedule for changing separators and filters. A typical pressure drop for a new oil separator is 2-3 psig. After two years, the pressure drop may be 10-12 psig. With the cost of $200/year per 1 psig ($0.06/kWh), and assuming replacement elements cost $550/each, it is prudent to change the elements somewhere between 3-4 psig.

Measurement
If you don’t measure it, you can’t manage it! Do you have a material balance for compressed air? Are the minimum flow and minimum pressure documented for all of your equipment? Are you monitoring your compressor cycle times and power usage? Is anyone keeping track of tie-ins for new equipment or do you have a single 1-in. pipe feeding five packaging machines when a separate line should have been built for all five machines? Do you have flow meters installed at key points in your piping network — if so, when were they last calibrated? Most of the plants we have audited have flow meters on the main air supply but few in the production areas, with calibration every 10 years, whether they need it or not! As for pressure, we generally find that no test points or gages are installed in critical interconnecting pipes.

What can you do to initiate a plan for monitoring your compressed air? Install test points for pressure gauges at the compressor discharge, before the pre-filter and dryer, after the after-filter and throughout the demand side of the piping. This is especially true for loops where a series of equipment is supplied (Figure 7). Install flow meters at branches in the system. After you have installed flow meters, try to solve the material balance. Most of the time, you will find you missed something.

Another common problem is gage accuracy. Although it may be useful to install gauges to monitor pressures at the demand points, don’t use these values in calculations! Unless instruments are periodically calibrated, and this goes for flow meters as well, they will drift. Because even calibrated gauges can differ in accuracy, measure differential pressures throughout the network with a single test gage. For our purposes, we rely on high quality digital gages. We use the same gauge, which has been calibrated prior to being employed. This is the only way to know what is going on.

Sometime during the discussion about a measurement plan someone will ask about measuring the dew point in the system. Technically, this is known as the pressure dew point (PDP). The damage that moisture causes to some equipment will be itemized as justification for a humidity meter. Generally, measuring the PDP is unnecessary. If you have a moisture problem eliminate it! Some industries, such as pharmaceuticals, food, cosmetics and fine chemicals (refer to ISO 8573.1) may have air quality standards that require permanent monitoring of humidity. These instruments are delicate and need annual calibration.

A well-managed system
How do you know when your air compressor system is performing at maximum efficiency?

A conservation program is in-place, air quality meets standards, and pressure drops have been eliminated on both the demand-side and supply-side. The trouble is that the cost savings are impressive but the power usage is still a little higher than expected — what’s wrong? The chart shows that power doesn’t respond to demand, i.e., flow: reduced demand should mean less power — right? What is needed is an air management system to assure that all compressors run at full-load efficiency. This system must have software capable of analyzing operating condition, compressor load condition, and adjusting to pressure change — either rises or decay. The net result will be all units on at full demand (load), one on at partial load, and all other off, 80% to 85% of the time.

Another component of a well-managed system is keeping it in tune. This requires an annual check-up, and a monitoring system. Monitoring systems are available to do this on a continuous basis.

A final component is training. Operating and maintaining a compressed air system requires the efforts and talents of many people. To be effective, these people must understand how your system works and how interdependency of its components affects cost. It has been our experience that this type of training pays off quickly.

Energy savings go directly to the bottom line. Saving money in compressed air will not only reduce costs it will increase plant production

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Cooling Towers: Not the Coolest One

INTRODUCTION
Cooling tower is basically a heat exchanging device in which heat exchange takes place by virtue of mass transfer potential between process fluid (cooling water) and utility fluid (ambient air). Hence, it performs evaporative cooling of water.

Cooling tower is an equally critical section in a plant because the on-stream utilization of main plants and efficiency of the manufacturing process depends on the performance of cooling towers also. It’s the most neglected area of the plant where huge potential of savings lie within the existing tower volumes.

This article is covering certain practical aspects of cooling tower performance & its operation.

NEED
Very high cost of cooling water e.g. RS. 2 to 6 /m3 of treated water doesn’t permit plant operators to operate in an open loop cycle in the cooling water circuit. Hence, the closed loop cycle is selected in almost all process plants all over the world.

In a closed loop cycle, the power consumption required for cooling the water (in cooling tower fans only while considering pumping cost as almost same in both the cases) varies from 0.02 to 0.04 kWh/m3 of water so, the cost of cooling of water ranges from RS. 0.02 to 0.20/m3 in Indian conditions. This is almost 100 times lesser than the cost of cooling water in a once through cycle. That’s why it is customary to use cooling towers in any chemical process industry, especially in hot climatic conditions.

THEORY
Cooling towers work on the humidification principal, which is driven by the mass transfer potential between cooling water & ambient air. However, in actual operation it is a combination of different driving forces between water & air. Contrarily, the cooling tower design is considered based on the enthalpy difference as driving force, because this is the least driving force available throughout the tower at any point of time. This occurs when the passing air is completely saturated. In all other cases, more than one driving forces are available between air & water. So, the most popular merkel equation is only a conservative way of modeling of a cooling tower.

However, merkel equation is considered to be the most effective way of designing a cooling tower by many engineering institutions & academies. For details of merkel equation please refer Cooling Towers: Design & Operation on www.cheresources.com

CONSTRUCTION
It’s a packed bed tower in which structured packings are used in a stacked loading pattern. Conventionally, these packings are called fills. These fills are means of providing larger surface area within a confined available volume as it is used in many conventional applications e.g. in distillation, absorption, saturators etc.

Construction-wise cooling towers are of two types mechanical draft & natural draft towers. Natural draft towers are very large stack type towers in which flow of air is through buoyancy force because of density difference. Mechanical draft towers are having induced/forced draft fans, which help in flowing air through the circulating water. These are sub classified based on flow pattern of air through the tower e.g. cross flow & counter flow towers.

OPERATION
Cooling towers are designed based on the worst condition of ambient air in terms of highest wet bulb in the area which prevails for one or two months only; during the year and, maximum cooling load from the process side as considered in the over design of process equipments. Also, the self, inherent design margin is always available in these towers because of their availability in standard size modules. Hence, every cooling tower practically has many margins in the existing tower volume for the desired cooling of water e.g.

• Maximum Wet bulb during the year.
• Maximum cooling load from process side.
• Capacity margins from process side.
• Self-inherent design margins due to modular construction.

Therefore, the cooling towers must give better results than anticipated in the design. The direct measurement of cooling towers performance is the approach of cooling at the outlet of tower. Hence, even if towers are operating at design value then too it is underutilized. We’ll see in the next paragraphs that how it is happening in actual operation.

1. Effect of Water Temperature
   
   The first impact of design margins from the process side is that normally cooling water flow is kept same as envisaged in the original design & process side heat load may be lower (due to capacity over design or for any other reason). Therefore, the cooling tower operates at lower cooling water return temperature (the temperature of cooling water at the inlet of tower).
   
   The impact of lower return water temperature is that the cooling approach must reduce by ~50% of the difference in the design & actual return water temperature. For example: If a tower is designed for 4°C approach for the cooling of water from 44°C to 34°C and actual return water temperature is 42°C then you must get an approach of 3°C instead of 4°C. The range of cooling will be 9°C against design value of 10°C. Thus, if your return water temperature is 42°C against design value of 44°C and you are getting design approach of 4°C that means your cooling tower is operating inefficiently.
2. Effect of Wet Bulb
   Similarly, since the tower is designed based on the wet bulb of 30°C, which prevails only for around two months during the year, it has to run at lower wet bulb temperature e.g. say 28°C for rest of the year. In this case, the approach of cooling will go up by ~50% of the difference between design & actual wet bulb resulting in actual approach of 5°C instead of 4°C. However, total range of cooling will also increase in this case by ~50% of the difference in actual & design wet bulb i.e. 44°C to 33°C means range of cooling will increase from 10°C to 11°C.
   
   Yes, one should not infer from these two examples that the thumb rules expressed here are valid for any changes in the temperatures. Instead, it is always governed by the equilibrium conditions & for larger changes one should go for proper evaluation procedure as described later in this article.
3. Effect of Water Loading
   Cooling towers are normally supplied in standard modules called tower cells. Therefore, the cooling water is distributed equally on each cell in parallel configuration. However, in actual operation it deviates from what it should be (Average water flow/cell). This causes for example 80% water on one cell & total water flow being the same it will be 120% on the other. Even the same cell might have different water loading on both sides of distribution deck. This much deviation may result in ~5-10% rise in cooling approach.
4. Effect of Air Distribution
   Similarly, the imbalance in air loading in each side of every cell may cause 1.5 times more negative impact as compared to effect of disturbed water loading. Thus, 20% deviation in air distribution may cause ~10-15% rise in cooling approach.
5. Effect of Air Short Circuiting
   By now it is clear that operators has to regularly monitor the performance of their cooling tower especially at different loads & at different ambient conditions. More appropriately, the comparison of actual approach with the design approach is not a good & actual indicator of its performance.

PERFORMANCE MONITORING
Following are the general guidelines for evaluating the operational performance of the cooling towers.

• Scheduled monitoring should be followed especially covering all seasonal changes.
• Intermittent & need based monitoring at different loads.
• Adjustment of water loading.
• Regular inspection for air short circuiting, fills displacement, end side gaps in the walls.

According to Merkel Equation, one can go as per the following procedure for the performance evaluation of an existing cooling tower.

1. Measure Air velocity through the tower in each cell.
2. Consider Design Wet bulb of inlet air & L/G as given in data sheet.
3. Exit wet bulb temperature of air by the heat balance on waterside.
4. Given the exit density of wet air find out exit dry bulb, which should lie, in between its wet bulb & water inlet temperature.
5. Now find out the inlet dry bulb temperature of air from the heat balance on airside. Of course, these two heat balances of airside & waterside must be same.
6. Now calculate the equilibrium enthalpy of wet air at inlet & outlet corresponding to the water temperature of that side.
7. Find the difference in equilibrium enthalpy & actual enthalpy of wet air & take reciprocal of it, for each increment in water temperature from the bottom to top of the cooling tower.
8. Sum up the average of reciprocals between two intervals & thus reach to the top of cooling tower.
9. This will give you the No of transfer units overall NTUG. This is the parameter, which is useful in predictions because the available numbers of transfer units are going to remain same in all cases.
10. Now find KaV factor by multiplying NTUG with the airflow rate. This factor is the indicator of rate of mass transfer between water & air and is analogous to mass transfer coefficient in distillation/absorption unit operation.
11. Repeat procedure from item 1 - 10 for actual operation & find out the cold-water temperature & expected ATE.
12. Compare expected ATE with actual ATE to find out the performance of cooling tower.
13. Establish reasons for the deviation found in item 12.
14. Take corrective actions for improvement.

This Article is not yet complete, I will refine it & add more info later when I get some time.

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Technologies Required

Currently, I am looking for the following Technologies

1. Ethanolamine using Ammonia & Ethylene Oxide.
2. Concentration techniques to improve MEG concentration from a mixture of 11% MEG & Water.
3. Nonyl Phenol.
4. Amyl Alcohol recovery from Fusel Oil.

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CO2 : Bone of Contention

Interest in recovery of carbon dioxide (CO2) from flue gases / any other gas is being propelled by multiple factors, which may vary from merchant CO2 market, Enhanced oil recovery (EOR), and pressure of GHG emissions. In fact, it has always been a problem to all.

Issues

1. Low CO2 Partial Pressure Flue gases have very low CO2 partial pressures because they are typically available at or near atmospheric pressure with CO2 concentrations of typically 5 to 15 vol% except other gases e.g. Distillery Biogas or Waste gas from reactors where it can go as high as 50-60% also.

The overall energy consumption invariably results in unattractive economics due to compression requirement which is higher than the cost of recovered CO2. The only commercial absorbents active enough for recovery of dilute CO2 from atmospheric pressure gas are monoethanolamine (MEA) and other primary amines including the newly developed hindered amines.

2. High Flue Gas Temperature Hot flue gases can cause solvent degradation and decrease absorber efficiency. The flue gas must be cooled to a water dew point of 50 °C prior to entering the absorber. This is accomplished through an scrubber which may require SO2 OR H2S scrubbing also if need be, or in a direct contact water cooler. This DCC can be used as a good resources for low grade waste heat using heat pump.

3. Regeneration Energy. Absorbents that are effective at low pressure requires higher regeneration energy due to higher chemical activity. The design challenges are to minimize regeneration energy by selecting a solvent with a relatively low reaction energy, and to use low-value heat sources to provide this energy.

4. Other Components. Other gaseous components e.g. SOx, NOx, H2S etc. are the major problematic constituents which complicate the overall design efficiency of the CO2 recovery system. They add to many additional steps e.g. removal & pre-treatment. Also cause corrosion & therefore metallurgical demands also goes up for the system design adding to capital requirement.

5. Foriegn Material. Flue gases generally carry ash, soot etc hence require filtration/separation of them as they tend to foul solvents/absorbents on permanent basis. Since, solvents are generally very costly manufacturers can't afford to loose them.

6. Value or Uses. This is the biggest factor which controls the entire business strategy for CO2 recovery plants. The major uses are, as mentioned above, merchant market which is mainly dry ice market and EOR market where full potential is stil not tapped and technology is also in the intital phase.

7. Nitrogen. A gas which does nothing but compel to do everything. In most of the cases, the nitrogen content is so high which occupies space, reduces effective partial pressure of CO2, carries heat & solvent and can cause up to 50% higher capital requirement compared to the case if nitrogen is not there. BUT, the removal of nitrogen itself is a matter of great deal, so better to leave it unless volumes are large enough.

8. Mode. System design also depend on the final objective of CO2 removal system. The costs are significantly different if CO2 is to be recovered in comparison to the case when the purpose is removal only.

Technologies

Different technologies which are available currently vary widely as can be seen below.

1. Chemical Absorption. As discussed earlier, the low pressure system can work only on chemical solvents other technologies are out of context when partial pressure of CO2 is less. The probable pressure range may vary from 5 to 10 Atm of partial pressure below which only chemical absorbents are feasible such as Potassium Carbonate based systems, MEA based systems or in the latest developments hindered amines.

The operating costs are higher in this case due to higher reactivity of the solvent with CO2 & hence, need more heat input.

2. Physical Absorption. When CO2 partial pressure is more than either physical or compbination of chemical & physical solvents can be used to minimize the operating costs depending on the requirement of final level of CO2 in feed gas i.e. total CO2 recovery. Water is the cheapest solvent out of them. Others such solvents may be Selexol etc.

3. Membrane Process. Membranes suffer from both the cost of compression and heat exchange to obtain a high pressure feed and also they produce an impure CO2. The pressure range may start at 25 Atm level. There are currently no commercial applications of membranes for recovery of CO2 from flue gases, though they have been used in large EOR projects to recycle CO2 from the associated gas. The presence of fly ash and the effects of trace components such as SOx, & NOx are also potential complications.

The most likely applications for membranes are in small skid-mounted plants where an impure CO2 product is acceptable and offshore applications that can take advantage of their compact size and low weight. Membrane-amine and membrane-cryogenic separation hybrids have been considered for special applications such as offshore locations where again their compact size and low weight are beneficial.

4. Cryogenic Separation. Cryogenic separation of CO2 is still at conceptual stage due to very low concentration & hence, cryo level cooling requirement. For more info on this you can look at my article at http://cheresources.com/ammonia.shtml.

5. PSA Separation. Carbon dioxide separation through PSA is offered in the Low Cost Ammonia Process (LCA). PSA is scalable and may be more economical because of efficient carbon dioxide recovery at higher pressures. However, further development in this direction is essential for the recovery of high purity carbon dioxide as desired in many cases. However it is comparatively better than Membrane process in terms of tolerability limits for feed gas for membranes.

Costs

A. Fixed COST FACTORS

1. Equipment Size

Cost of CO2 removal or recovery vary depending on many factors.

The first & most important is the total gas flow rate which directly affects the equipment size. Interestingly, the CO2 concentration in the feed gas does not affect the absorber column sizing. The absorber column dia is directly proportional to square root of gas volume flows in (Nm3/hr) & can be approximated with a mutiplying factor of 0.8 to 1.5, thus can be represented as below.

Absorber Column Dia (Meter) = A x (Feed Gas Flow)^0.5

Where,

A = 0.8 to 1.5

Feed Gas flow is in Nm3/Hr

Clearly, the CO2 concentration is not in the role which is indirectly included in total gas flow.

However, it affects the height of the column directly. A factor is a function of absorbent properties. Currently availabe best solvents can offer A = 0.8 or more.

Similarly Stripper can be approximated by the following equation.

Stripper Column Dia (Meter) = S x Da x (Vol% CO2 in Feed)^0.5
Where,
S = 0.25 to 0.5
Da = Absorber Dia calculated above

Please note that these are the approximations only for preliminary cost estimates for carrying out design feasibility studies.

3. Solvent Circulation

The solvent circulation rate can be correlated to CO2 partial pressure which is the governing factor depending on the nature of solvent. For physical solvents, circulation will be more due to higher vapor pressure of CO2 over solution whereas it will be less for chemical solvents.

Circulation rate (Te/hr) = C x CO2 partial pressure in feed gas (Atm.)

Where,

C = solvent factor which is,

= 200 for chemical solvents &

= 200 - 300 for physical solvents.

B. VARIABLE COST FACTORS

4. Energy Costs

Steam consumption in totality varies widely among different type of solvents. It ranges from 500 Kcal/Te of CO2 to 1000 Kcal/Te of CO2. The best part is that all the heat required is low level heat upto 3-4 Atm pressure.

5. Power Costs

Major power consumers are flue gas blowers and solvent circulation pumps. Based on above equations power consumption comes close to the following correlation.

Power Load (Pumps) kW = P x CO2 partial pressure in Atm.

Where,

P = 120 to 160

For flue gas blower, it varies according to the CO2 concentration in feed gas.

Blower Power kW = B x Feed gas flow Nm3/hr.

Where,

B = 0.040

Other costs include various utilities including cooling water, Solvent losses etc out of which solvent losses are the major portion & may vary from 5 - 10 % of the total operating cost.

Conclusion

The technology to recover CO2 from flue gases is commercially available and, though mature, is being significantly improved. The process economics greatly depends on the size of the plant. This paper provides approximates for establishing preliminary estimates of fixed & operating costs. A 1000 te/d plant of conservative design can produce CO2 for $30/tonne or from coal-fired flue gas. However, 4600 te/d single-train plants are possible. Economy of scale, together with the ongoing development in improving the solvent properties (e.g. MHI has developed an hindered amine based solvent KS-1 which is supposed to reduce the production cost for low pressure systems such as recovery from flue gases), have the potential of delivering CO2 at a price much lesse than that of the reference 1000 te/d plant.

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