Sidney P. Santos
Gas Composition Effect on Centrifugal Compressor Performance
Sidney Pereira dos Santos, PETROBRAS
Copyright 2003, Pipeline Simulation Interest Group
This paper was prepared for presentation at the PSIG Annual Meeting held in Palm Springs, CA, United States, 20 October – 22 October 2004.
This paper was selected for presentation by the PSIG Board of Directors following review of information contained in an abstract submitted by the author(s). The material, as presented, does not necessarily reflect any position of the Pipeline Simulation Interest Group, its officers, or members. Papers presented at PSIG meetings are subject to publication review by Editorial Committees of the Pipeline Simulation Interest Group. Electronic reproduction, distribution, or storage of any part of this paper for commercial purposes without the written consent of PSIG is prohibited. Permission to reproduce in print is restricted to an abstract of not more than 300 words; illustrations may not be copied. The abstract must contain conspicuous acknowledgment of where and by whom the paper was presented. Write Librarian, Pipeline Simulation Interest Group, P.O. Box 22625, Houston, TX 77227, U.S.A., fax 01-713-586-5955.
Thermo-hydraulic simulations of centrifugal compressors are usually based on a set of information derived from
manufacturer design tools that are used for compressor modeling.
When operating gas pipelines transportation companies use the simulation tool to predict and anticipate the behavior of the gas pipeline under different scenarios. The operation with different gas compositions from different supplies is not uncommon as well as the exposure to gas quality changes whenever contingencies happen to the gas processing plants.
This paper address this important subject, presents a methodology of evaluation, a sensitivity study using different gas qualities and shows the impact on compression overall performance.
A compressor is selected based on a set of conditions and then is checked for performance changes when working with different gas quality. The results are presented for comparison purposes and some suggestions are also presented on how to handle this situation to guarantee that the thermo-hydraulic simulation tools will always provide good results when dealing with natural gas quality changes.
It is not uncommon to operate a gas pipeline with different gas compositions and even in those pipelines where we expect a stable operating condition operating problems from gas supply may cause the gas to be out of specification. The purpose of this paper is to evaluate this scenario and check its influence on centrifugal compressor performance and then suggest a procedure that might help designers, operating companies and also vendors to deal with such a situation.
The development of centrifugal compressor and gas turbine design through the last 20 years has been impressive.
Pipeline compressors now routinely achieve or exceed 85% isentropic efficiency, while exhibiting wide operating
ranges. The study of operating scenarios suggests certain requirements for the compression system. Beyond the quest
for higher compressor peak efficiencies, the operating requirements set forth in this study, as well as in other
references (Kurz, 2001) require a compressor capable of operating over a wide operating range at high efficiency.
A wide operating range in a centrifugal compressor (figure 1) can be achieved by a combination of means. Aerodynamic theory suggests a strong relationship between operating range, efficiency and impeller backsweep . However, there is a practical limit to the amount of backsweep. In particular, increasing backsweep reduces the capability of an impeller of given tip speed to make head. With the capability to use two impellers in a casing, this perceived disadvantage can be eliminated. The operating range is further increased by the use of vaneless diffusers.
The aerodynamic aspects can be considered with the following:
Equation (1), and the subsequent discussion use N in min-1, H in J/kg, and Q in m3/s.
Centrifugal impellers can be described by their specific speed, where a high specific speed depicts a low head, high flow impeller. There is a range of specific speeds where centrifugal impellers tend to exhibit good aerodynamic performance, while both very low and very high specific speeds penalize the performance. Specific speeds between 0.09 and 0.14 tend to yield good efficiency. Mixed flow impellers can extend this range to higher specific speeds.
It must be noted that the actual running speed (N) is determined by the power turbine speed of the gas turbine, unless a gearbox is used. For aerodynamic and mechanical reasons, power turbine speeds are lower for larger gas turbines than for smaller ones. For example, a typical 15-MW (20,000-hp) class gas turbine may have a power turbine speed of about 8500 rpm, while a typical 3.5-MW (5000-hp) class gas turbine may run at about 16,000 rpm.
The proposed methodology assumes that the gas volumes to be delivered to the market (Gas Fired Power Plant or Local
Distribution Company) are energy based. Different gas compositions have different LHV (Low Heat Value) and for the
same amount of energy gas volumes may differ significantly impacting compressor performance, temperature and pressure
drop across the pipeline. The following steps were adopted:
1. Identify different gas compositions
2. Run thermo-hydraulic simulations using generic compressor
3. Pre-select compressors and drivers based on the thermo-hydraulic results
4. Check compressors efficiencies
5. Check the overall efficiencies for compressor units (Compressor + Gas turbine)
6. Perform technical and economic evaluation
7. Make the final decision on the equipment selection.
Thermo-hydraulic Simulation – Steady State
The thermo-hydraulic simulations were performed using generic compressors and drivers, in steady state, for three different gas compositions (table 1) and the results are presented (figure 2 and table2).
Pre-selection of Equipment
Pre-selection of equipment was based on gas compositions and conditions taken from the thermo-hydraulic simulations.
To properly design and select compressor stages a few issues should be taken into consideration. The project specifics dictated, in this case, the need to operate at a substantial range of gas specific gravities and, thus, energy content. Since the amount of energy that should be delivered to the consumer is defined, the actual compressor station throughput would also vary substantially.
Due to the different mass flow rate as a cause for the different energy throughput, the need for head that the compressor should build would vary as well. Therefore, the staging that covers these widest range of conditions should be the one that uses latest advances in centrifugal compressor technologies (figure 3) The additional benefit of using modern centrifugal compressors comes from the fact that by knowing the pipeline resistance curve the compressor stage selection can be designed so that all main operating points A, B, and C will lay in the compressor highest efficiency island (figure 4)
This case study focuses on a gas pipeline section between 2 (two) compressors stations (figure 2), designed to operate
with 3 (three) different gas compositions (table 1). The pipeline will operate with the same amount of time with each
gas composition. This hypothetical pipeline delivers 1 x 1012 BTU/D to the market. The gas composition effects on the
gas pipeline and compressor station operation variables and, consequently, on centrifugal compressor performance are
identified and evaluated. The base case operates with a lean natural gas composition named (A) Cabiunas Lean, natural
gas composition named (B) Cabiunas Heavy and a typical gas composition from the Bolivia-Brasil Gas Pipeline named (C)
Gasbol. All these cases were simulated to check their effect on the pre-selected centrifugal compressor. Four
compressor station configurations were evaluated as described below:
Compressor station with 2 (two) Mars 100 units operating with 3 (three) different gas compositions (A), (B) and (C), without stand-by unit. It operates 1/3 of the time with each gas composition. For Composition (B) only recycling is required to keep compressor unit operating above 50% load.
Compressor station with 3 (three) Mars 100 units as Configuration I above but with one stand-by unit.
Compressor station with 2 (two) Mars units and 2 (two) additional Taurus 60 units to handle Composition (B). Provides the benefit of fuel savings but requires incremental Capex and O&M. This configuration also provides some back- up power for the station.
Same as Configuration III but with 3 (three) Mars units.
Diameter: DN 32"
Design code: ANSI B31.8
Max. Allowed Working Pres. – MAOP: 101.2 kgf/cm2 (1440 PSIG)
Pipe material: API 5L X70
Pipe internal roughness (epoxy painted): 0.009 mm (350 minches)
Pipeline Inlet Pressure: 99.84 kgf/cm2 (1420 psig)
Minimum Pipeline Delivery Pressure: 35 kgf/cm2 (498 psig)
Pipeline overall heat transfer: 1.9 Kcal/h.m2.C 0.39 Btu/h.ft2.F
Soil temperature: 16 to 30 C (61 to 86 F)
Depth of burial: 1 m (3 feet)
Maximum Compression ratio: 1.6
Suction and Discharge Header pressure drop: 0.35 kgf/cm2 (5 psi)
After cooler pressure drop: 0.35 kgf/cm2 (5 psi)
After cooler outside temperature: 52.6 C (127 F) Site elevation 100 m (328 feet)
Site Temperature 38 C (100.4 F)
Flow Equation: Colebrook
Centrifugal Compressors - Performance Maps
Centrifugal compressor performance maps (figures 4 and 5), have been pre-selected based on operating conditions and gas compositions using Solar dedicated software.
The results obtained for this case study helped to identify some interesting points related to compressor unit
pre-selection under different operating conditions and gas compositions. The first configuration is closely related to
the improvement in the design and manufacturing of pipeline centrifugal compressors, as presented previously and uses
Solar C452 centrifugal compressor with Solar Mars 100 – 15000 for Compositions (A), (B) and (C).
The second point is related to the opportunity of operating Composition (B) with a dedicated compressor using Solar Taurus 60 and Solar C402 centrifugal compressor (figure 6).
Solar C452 with Mars 100 – 15000
Solar C452 centrifugal compressor with Mars 100 – 15000 gas turbine can operate with all three Compositions (A, B and C) in the best efficiency region of the performance map (figure 4).
The analysis including Solar Mars 100 gas turbine driver was important to evaluate the turbo-compressor unit ( figure 6 ) and presented some other important aspects to be considered. The operating point for Composition (B) requires 41.59% of gas turbine available power (figure 7) and, therefore, would require the gas turbine to operate outside of its lean-premix mode (figure 7). Composition (B) can not be operated with just one Mars unit (figure 4) since the operation point is in the centrifugal compressor stonewall and low efficiency area (~69%). One Mars unit does not have power enough to operate with Composition (B). To handle this situation, recycling (or suction valve throttle as an option) has been considered and its economic impact due to fuel usage, capex and O&M has been quantified.
For Composition (B) without recycling, the overall efficiency is 19.93% (22.8% of GT x 87.40% of CC) and 20.81% (24.2% of GT x 85.98% of CC) with recycling.
Solar C402 with Taurus 60 – 7800
For this selection (figures 5 and 8) the overall efficiency goes up to 23.03% (27.0% of GT x 85.30% of CC), operating at 83.08% of gas turbine available power. In this case the overall efficiency is higher than in the previous alternative and allows SoloNox operation. The fuel savings related the better overall efficiency amount to 15.9 MMBTU/h-unit (figure 9).
To make a good decision designer needs to take the operating aspect into account and also perform the economic evaluation of the alternatives.
For the economic evaluation of the alternative of installing 2 (two) Taurus 60 – 7800 compressor units to operate with
Composition (B), compared to keeping the operation with 2 (two) or 3 (three) Mars 100 – 15000 (Configurations I and
II) with recycling, the following assumptions were adopted:
• Construction schedule: 2 years
• Capex (2 Taurus 60 – 7800) : 11.80 MMUS$
• O&M (without Fuel): 1.070 MMUS$
– Maintenance (5% of Capex): 0.590 MMUS$
– Overhaul/year (2 Taurus 60): 0.480 MMUS$
• Depreciation: 20 years
• Taxes: 40%
• Fuel for Mars 100 (recycling): 62.4 MMBTU/h-unit
• Fuel for Taurus 60: 46.50 MMBTU/h-unit
• Operating time with Comp. (B): 1/3 of the year
• Fuel savings/year (Taurus 60): 2.790 MMUS$
• Incremental Transportation Cap.: 0.019 MMSCMD
• Transportation Rate: N/A
• Fuel price: 10.00 US$/MMBTU
• Discount rate: 12% a year
Economic Evaluation Criteria
The compressor station project with 2 (two) or 3 (three) Mars 100 -15000 compressor units has the following economic results:
Economic life: 20 years
Discount rate: 12% per year
Configuration I (2 Mars)
Gross revenue: 21.90 MMUS$/year
O&M 2.82 MMUS$/year
Gas Fuel 13.11 MMUS$/year
Configuration II (3 Mars)
Gross revenue: 24.38 MMUS$/year
O&M 3.29 MMUS$/year
Gas Fuel 13.11 MMUS$/year
The economic evaluation focussed only on the alternatives differences related to the potential installation of 2 (two) Solar Taurus 60 compressor units to operate with Composition (B). This alternative requires additional investment, increses O&M costs but, due to its better overall performance, avoids the costs related to fuel gas as listed below. The installation effects of 2 (two) Taurus units are exactly the same for Configurations III and IV as below.
• Incremental O&M (without Fuel): 1.34 MMUS$
• Fuel savings/year (Taurus 60): 2.76/3 MMUS$
Fuel savings impact positively on pipeline transportation capacity since fuel gas will not be transported to the compressor station and, therefore, is a source of incremental revenue for the Transportation Company. In this case study the amount of incremental capacity, in the range of 0,019 MMSCMD or 0.675 MMSCFD (one third of the year) was considered to be too small to be included in the economic evaluation.
Two Base Cases were considered: Compressor station with 2 (two) Mars 100 – 15000 and Compressor Station with 3 (three) Solar Mars 100 – 15000 both operating the 3 (three) diferents Compositions (A), (B) and (C).
The economic evaluation of the 2 (two) base cases was performed to produce NPV equal to ZERO. The revenues for these 2 (two) base cases must recover the required investment at a discount rate of 12% and economc life of 20 (twenty) years.
The impact on the compressor station project NPV, when installing 2 (two) Taurus 60 was quantified and the results are presented (figures 10, 11 and 12).
A sensitivity study is presented to show how each selected variable such as gas fuel price, operating time and discount rate would affect the operation and investment decision.
Figure 10 shows the sensitivity analysis with the following conditions:
Economic life: 20 years
Discount rates: from 6 to 12%
Fuel gas price: from 6 to 12 US$/MMBTU
Figure 11 as figure 10 but with economic life of 20 years.
Figure 12 shows the sensitivity analysis with the following conditions:
Economic life: 10 and 20 years
Discount rate: 12 %
Fuel gas price: 10 US$/MMBTU
Operation time: from 30 to 95%
Whenever the operation time for Composition (B) differs from 33% of the year the remaining time is split equally between Compositions (A) and (C).
As can be seen from figures 10 and 11 the alternative of installing 2 (two) Taurus 60 compressor units is not feasible
for all combinations of fuel gas prices and discount rates that produce negative NPVs, and is feasible for those that
produce positive NPVs.
The alternative of using Solar Mars 100 – 15000 compressor units with a certain amount of recycling presents good economic results and will be preferred whenever the sensitivity described above for Composition (B) with Taurus 60 presents negative results for NPV.
These results underline the importance of performing a technical and economic evaluation for the alternatives available for compressor station configuration (Santos, 2004) and unit sizing. Designers must always quantify the alternatives and make a decision taking all the technical and economic aspects into consideration.
In conclusion, gas composition affects compressor units overall efficiency but this aspect has to be carefully addressed to prevent biased decisions related to equipment selection.
- Kurz, R., Ohanian, S. and Lubomirsky, M., 2003, "On Compressor Station Layout", Proceedings of ASME TURBOEXPO 2003.
- antos, S. P., 2004, "Series or Parallel Arrangement for a Compressor Station? – A recurring Question That Needs a Convincing Answer." Pipeline Simulation Interest Group
The authors want to thank PETROBRAS and Solar Turbines Incorporated for making this information available to the PSIG members and also Rainer Kurz, Oil and Gas Systems Analysis Manager of Solar Turbines for reviewing the paper and providing pertinent comments.
About the Author
Sidney Pereira dos Santos, the author, is a Senior Consultant at PETROBRAS Gas Business Unit, has a
BS in Mechanical Engineering and a MBA in Corporate Finance, 19 years in the oil and gas pipeline design at PETROBRAS.
He has been deeply involved in most of the gas pipeline projects such as the Bolivia-Brazil project and the ongoing
gas pipeline expansion in Brazil and has been conducting technical and economic studies and conceptual design for the
Phone: +55 21 8167-0134
e-mail: [email protected]