Ag Petrofac Pulsation Study
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PIPING PULSATION ANALYSIS of a
ARIEL JGE/4 COMPRESSOR with a WAUKESHA L5790GL ENGINE for PETROFAC, LLC
AG EQUIPMENT CO. BROKEN ARROW, OK
JUNE, 2001 ECSI JOB #201-1050
PIPING PULSATION ANALYSIS
of a
ARIEL JGE/4 COMPRESSOR with a WAUKESHA L5790GL ENGINE PETROFAC, LLC
SUBMITTED TO: AG EQUIPMENT BROKEN ARROW, OK
JUNE, 2001
ENGINEERING AND CONSULTING SERVICES, INC. BROKEN ARROW, OK ECSI JOB #201-1050
July 10, 2001
INTRODUCTION Engineering and Consulting Services, Inc. recently performed an acoustical analysis on an Ariel JGE/4 compressor, driven by a Waukesha L5790GL engine. This unit was packaged by AG Equipment Company, Broken Arrow, OK for Petrofac, LLC, Tyler, TX. Included in this acoustic analysis were on-skid suction, interstage, and discharge piping with scrubbers, intercooler and aftercooler. General arrangement piping plans and elevations, scrubber, bottle and cooler details, as well as compressor information including performance analyses were provided by AG Equipment Company. AG predetermined the pulsation bottle and scrubber sizes; these were not modified unless it was determined to be critical to the analysis. API 618, Section 3.9 -Reciprocating Compressor Code was utilized for acceptance criteria. Design approach 2 was considered for all systems. ANALYSIS The computer program, Gas Compressor Pulsation Analysis© , used in this study utilizes classical fluid theory and considers both steady and dynamic (acoustic) flow in the pulsation analysis calculations. The computer program utilizes digital analysis techniques to simulate the acoustic response of the piping system to cylinder harmonic excitation. Cylinders were modeled by considering bore, stroke, rod diameter, clearance, suction and discharge temperatures and pressures, and gas compressibility. The compressor model included speed, connecting rod length and crank phase angles. Two performance analyses were provided for review. This compressor utilizes a side stream between the 1st and 2nd stages to provide the majority of the gas for the 2nd stage compression. Steady state performance was calculated using 1,200 rpm. Gas composition was used to determine fluid mixture physical properties such as density, sonic velocity, viscosity, specific heat ratios and compressibility. Simulation of the piping system included pipe diameters, length, flow rate and pressure drop. Influence of pressure drop on acoustic attenuation with changes in sonic velocity due to steady flow velocity was also included in this study.
Bottles and scrubbers were included in the model. Physical dimensions were obtained from the provided drawings and details. Suction and discharge pressures were held to 170 PSIG and 1,285 PSIG for this analysis. Flow rates used for these models were 3.91 & 4.01 MMSCF/D through the 1st stage and 13.14 & 10.44 MMSCF/D for the 2nd stage operation. A sketch is attached with node numbers identified for reference to the acoustic response spectrums. The spectral response plots of pulsation pressure versus frequency at critical points within each piping system are included.
Recommendations
RECOMMENDATIONS Inlet Piping System Suction Bottle V-2604 (V-2) overall dimensions remain as proposed. Extend inlet to bottle center. Reduce portion in bottle to 3” S XS. Refer to sketch PD-01 for details. Interstage Piping System Discharge Bottle V-2605, V-3, overall dimensions remain as proposed. Extend outlet to bottle center. Reduce portion in bottle to 2 ½” S XS. Refer to sketch PD-02. Change suction bottle V-2606A, V-5, to a 3-chamber design. Overall dimensions should be 14” OD x 72” S-S. Refer to sketch PD-05 for details and critical dimensions. Increase diameter of suction bottle V-2606B to 12 ¾” OD. Install a 1.750” diameter orifice plate at the outlet of discharge bottle V-2605. Install a 2.750” diameter orifice plate at the inlet nozzle of suction bottle V-2606A. Install a 1.625” diameter orifice plate at the inlet nozzle of suction bottle V-2606B. Discharge Piping System Change discharge bottle V-2607A, V-6, to a 3-chamber design. Overall dimensions should be 14” OD x 72” S-S. Refer to sketch PD-06 for details and critical dimensions. Increase diameter of discharge bottle V-2607B to 12 ¾” OD. Refer to sketch PD-08. Install a 1.625” diameter orifice plate at the outlet flange of bottle V-2607A. Install a 1.125” diameter orifice plate at the outlet flange of discharge bottle V-2607B.
CUSTOMER JOB NO. UNIT NO. SYSTEM Inlet Piping System
01113 K-2601
CONTACT: Ed Jackson ECSI NO. 201-1018
MODIFICATIONS Suction Bottle V-2604 (V-2) overall dimensions remain as proposed. Extend inlet to bottle center. Reduce portion in bottle to 3” S XS. Refer to sketch PD-01 for details.
ORIFICE SIZE
∆ PRESS. PSI / %
DATE: 01/20/01
COMMENTS API design approach 2 design limit for this system is between 0.3% and 4.5%, depending on pipe diameter and frequency. The modified system should meet API guidelines for both cases reviewed. Bottle unbalanced shaking forces are low. The maximum force will be 15 lbs, or less.
Interstage Piping System
API design approach 2 recommended limit for this system is between 0.2% and 4.9%, depending on pipe diameter and frequency.
Discharge Bottle V-2605 (V-3) overall dimensions remain as proposed. Extend outlet to bottle center. Reduce portion in bottle to 2 ½” S XS. Refer to sketch PD-02.
The modified system should meet API guidelines for the cases studied.
Change suction bottle V-2606A (V-5) to a 3chamber design. Overall dimensions should be 14” OD x 72” S-S. Refer to sketch PD-05 for details and critical dimensions.
Bottle unbalanced shaking forces are low. The maximum force expected will be in the double hung suction bottle. These forces will be 200 lbs, or less. Unbalanced forces in the other bottles are 15 lbs, or less.
Increase diameter of suction bottle V-2606B to 12 ¾” OD. Install an orifice plate at the outlet of discharge bottle V-2605.
1.750”
3.94 / 0.83
Install an orifice plate at the inlet nozzle of suction bottle V-2606A.
2.750”
2.32 / 0.49
Install an orifice plate at the inlet nozzle of suction bottle V-2606B.
1.625”
3.55 / 0.75
Discharge Piping System
API recommended design limit is between 0.2% and 3.0%, depending on pipe diameter and frequency.
Change discharge bottle V-2607A (V-6) to a 3-chamber design. Overall dimensions should be 14” OD x 72” S-S. Refer to sketch PD-06 for details and critical dimensions. Increase diameter of discharge bottle V-2607B to 12 ¾” OD. Refer to sketch PD-08.
The modified system meets API criteria for the two cases reviewed, except in the recycle / bypass lines. These lines exceed API limits but should not cause problems. The maximum forces in these lines will be less than 50 lbs at 2x running speed.
Install an orifice plate at the outlet flange of bottle V-2607A.
1.625”
7.39 / 0.57
Install an orifice plate at the outlet flange of discharge bottle V-2607B.
1.125”
11.01 / 0.85 Bottle unbalanced shaking forces are low. The maximum force should be 180 lbs, or less.
Conclusions
CONCLUSIONS Compressor packages are fabricated utilizing complicated sub assemblies such as skid, motor/engine base, compressor base, scrubbers, pipe supports and others. Every effort should be used to insure a rigid assembly during construction; scrubbers and pipe supports should be welded to supporting I-beams and not just to the decking. With the compressor, bottle, scrubber, and piping system constructed as per the above system analysis, along with adequate piping clamps, and proper cylinder/bottle bracing and supports, an acceptable level of vibration should be obtained. Compressor cylinder passages and valve interactions are generally not included in the compressor model. Reliable, and exact, information on cylinder passages and valve natural frequencies is difficult to obtain. It is assumed that the cylinder manufacturer has designed the passages to minimize the effects of reflected pulsation pressure waves in the valve area. Normally, natural frequencies of the valves are substantially different than the frequency of any reflected pulsation. However, experience has shown that in some instances, a system that meets API design criteria may have unacceptable valve life. These systems will require further analysis to eliminate the problem. Engineering and Consulting Services, Inc. has used proven advanced design techniques and utilized state-of-the-art computer simulations and computer modeling in an attempt to accurately represent actual system response. The programs used in this study have been used successfully for analysis, design and troubleshooting of gas piping systems in onshore and offshore field gas compressor stations, gas processing plants, fuel gas booster stations, pipeline transmission stations, refineries, and chemical plants. Well over a thousand studies have been successfully performed in the last 15 years. In general, very good comparisons of measured pulsation pressures to calculated pressures have been obtained. If differences exist, calculated pulsation pressures are usually found to be somewhat higher than measured pressures. However, compressor systems are governed by complex relationships and piping interactions; and often react differently than expected. Therefore, Engineering and Consulting Services, Inc., and its representatives, make no claims or guarantees to the accuracy or correctness of the data presented in this report. ECSI cannot be held responsible for results different than those predicted. Do not hesitate to contact us if you have questions, or need additional information concerning this study.
Tom Steeper, P.E. Senior Mechanical Engineer
Piping Systems
Inlet Piping System Acoustic analysis of the inlet gas system included the on-skid inlet piping, suction scrubber V-2602 (V-1), suction bottle V-2604 (V-2), by-pass line to valves 2373, relief valve PSV-2625 and the 1st stage cylinder. Modifications to the proposed suction bottle are necessary to achieve adequate attenuation of the pulsation pressures. Overall dimensions of proposed suction bottle V-2604 (V-2) should remain as proposed. Extend the inlet nozzle in to the bottle center. Reduce the portion of inlet nozzle in bottle to 3” S XS pipe. Extending the inlet nozzle reduced the level and frequency of the bottle unbalanced forces. Refer to sketch PD-01 for critical dimensions and details. API design approach 2 recommended pulsation limit for this system vary between 0.3% and 4.5%, depending on diameter and frequency of interest. This system will meet API design criteria with the recommended modifications. The system response should be acceptable. Unbalanced shaking forces in the suction bottle will be low. Maximum force is expected to be less than 15 lbs. Maximum forces in the by-pass line at valves 2373 are low as well. Refer to the attached plots labeled 1S1.PLT for selected nodal pulsation pressure responses on the following pages. Recommendation: Extend the inlet nozzle in to the bottle center. Reduce the portion of inlet nozzle in bottle to 3” S XS pipe.
INLET PIPING SYSTEM
Interstage Piping System The acoustic analysis of this piping system consists of the 1st stage cylinder, discharge bottle V-2605 (V-3), cooler AC-2602, scrubber V-2603 (V-4), relief valve PSV-2628, suction bottles V-2606A (V-5) and V-2606B (V-7), 2nd stage cylinders, and related piping. This system also includes a side-stream connection to scrubber V-2603. Modifications to the proposed bottles and piping are necessary to achieve acceptable attenuation of the pulsation pressures. Overall dimensions of proposed discharge bottle V-2605 should remain as proposed. Extend the outlet nozzle in to bottle center. Reduce the portion of outlet nozzle in bottle to 2 ½” S XS pipe. Extending the inlet nozzle reduced the level and frequency of the bottle unbalanced forces. Refer to sketch PD-02 for critical dimensions and details. Replace the proposed suction bottle V-2606A with a 3-chamber design. Overall dimensions should be 14” OD x 72” S-S. Choke tube dimensions should be 2” S Std x 34 ½” long. The inlet nozzle should be reduced to 3” S Std in the bottle. Cylinder nozzles should be held to approximately 10” OAL (Over All Length). Refer to sketch PD-05 for critical dimensions and details. Increase the diameter of suction bottle V-2606B (V-7) to 12 ¾” OD. Cylinder nozzles should be held to approximately 10” OAL. Install a 1.750” diameter orifice plate at the outlet of discharge bottle V-2605. The maximum pressure drop resulting from this orifice plate will be 0.83%, or 3.94 PSI. Additionally, install a 2.750” diameter orifice plate at the inlet nozzle of suction bottle V2606A. The pressure drop associated with this orifice plate will be 0.49%, or 2.32 PSI. Finally, install a 1.625” diameter orifice plate at the inlet nozzle of suction bottle V2606B. The maximum pressure drop resulting from this orifice plate will be 0.75%, or 3.55 PSI. API recommended pulsation limit for this system vary between 0.2% and 4.9%, depending on line diameter and frequency. This system should meet API design criteria with the recommended changes. The system response should be acceptable. Bottle unbalanced shaking forces are low. The maximum force expected will be in the double hung suction bottle. These forces will be 200 lbs, or less. Unbalanced forces in the other bottles are 15 lbs, or less. Refer to the attached plots labeled 1IS15.PLT for selected nodal pulsation pressure responses. Recommendation: Extend outlet nozzle to bottle center on discharge bottle V-2605. Reduce the portion of outlet nozzle in bottle to 2 ½” S XS pipe. Replace the proposed suction bottle V-2606A with a 3-chamber design. Choke tube dimensions should be 2” S Std x 34 ½” long. The inlet nozzle should be
reduced to 3” S Std in the bottle. Increase the diameter of suction bottle V-2606B to 12 ¾” OD. Install a 1.750” diameter orifice plate at the outlet of discharge bottle V-2605. Additionally, install a 2.750” diameter orifice plate at the inlet nozzle of suction bottle V-2606A. Finally, install a 1.625” diameter orifice plate at the inlet nozzle of suction bottle V2606B.
Interstage Piping System
Interstage Piping System Continued
Discharge Piping System The acoustic analysis of the discharge piping system consists of the 2nd stage cylinders, discharge bottles V-2607A (V-6), relief valve PSV-2627, by-pass line to valves 2373, cooler AC-2603 and related piping. Modifications to the proposed discharge bottles and piping are necessary to achieve acceptable attenuation of the pulsation pressures. Replace the proposed discharge bottle V-2607A with a 3-chamber design. Overall dimensions should be 14” OD x 72” S-S. Choke tube dimensions should be 1 ½” S 160 x 34 ½” long. The inlet nozzle should be reduced to 2 ½” S XS in the bottle. Cylinder nozzles should be held to approximately 10” OAL (Over All Length). Refer to sketch PD-06 for critical dimensions and details. Change the overall dimensions of proposed discharge bottle V-2607B to 12 ¾” OD x 18” S-S (no change). Extend the outlet nozzle into the bottle center. Reduce the portion of outlet nozzle in bottle to 1 ½” S 160 pipe. Refer to sketch PD-07 for details. Install a 1.625” diameter orifice plate at discharge bottle V-2607A outlet flange. Pressure drop associated with this orifice plate should be a maximum of 0.57%, or 7.39 PSI. Additionally, install a 1.125” diameter orifice plate at discharge bottle V-2607B outlet flange. Pressure drop associated with this orifice plate will be 0.85%, or 11.01 PSI, maximum. API recommended pulsation limit for this system vary between 0.2% and 3.0%, depending on pipe diameter and frequency. The modified system meets API criteria for the two cases reviewed, except in the recycle / bypass lines. These lines exceed API limits but should not cause problems. The maximum forces in these lines will be less than 50 lbs at 2x running speed. Unbalanced shaking forces in the discharge bottles will be low. Maximum force is expected to be 180 lbs, or less. Maximum forces in the by-pass line at valves 2373 will be low, as well. Refer to the attached plots labeled 1D14.PLT for selected nodal pulsation pressure responses. Recommendation: Replace the proposed discharge bottle V-2607A with a 3-chamber design. Overall dimensions should be 14” OD x 72” S-S. Choke tube dimensions should be 1 ½” S 160 x 34 ½” long. The inlet nozzle should be reduced to 2 ½” S XS in the bottle. Cylinder nozzles should be held to approximately 10” OAL. Change the diameter of proposed discharge bottle V-2607B to 12 ¾” OD. Install a 1.625” diameter orifice plate at discharge bottle V-2607A outlet flange. Additionally, install a 1.125” diameter orifice plate at discharge bottle V-2607B outlet flange.
DISCHARGE PIPING SYSTEM
DISCHARGE PIPING SYSTEM Continued
Technical Data
ARIEL JGE/4 COMPRESSOR with a WAUKESHA L5790GL ENGINE for PETROFAC, LLC
AG EQUIPMENT CO. BROKEN ARROW, OK
JUNE, 2001 ECSI JOB #201-1050
PIPING PULSATION ANALYSIS
of a
ARIEL JGE/4 COMPRESSOR with a WAUKESHA L5790GL ENGINE PETROFAC, LLC
SUBMITTED TO: AG EQUIPMENT BROKEN ARROW, OK
JUNE, 2001
ENGINEERING AND CONSULTING SERVICES, INC. BROKEN ARROW, OK ECSI JOB #201-1050
July 10, 2001
INTRODUCTION Engineering and Consulting Services, Inc. recently performed an acoustical analysis on an Ariel JGE/4 compressor, driven by a Waukesha L5790GL engine. This unit was packaged by AG Equipment Company, Broken Arrow, OK for Petrofac, LLC, Tyler, TX. Included in this acoustic analysis were on-skid suction, interstage, and discharge piping with scrubbers, intercooler and aftercooler. General arrangement piping plans and elevations, scrubber, bottle and cooler details, as well as compressor information including performance analyses were provided by AG Equipment Company. AG predetermined the pulsation bottle and scrubber sizes; these were not modified unless it was determined to be critical to the analysis. API 618, Section 3.9 -Reciprocating Compressor Code was utilized for acceptance criteria. Design approach 2 was considered for all systems. ANALYSIS The computer program, Gas Compressor Pulsation Analysis© , used in this study utilizes classical fluid theory and considers both steady and dynamic (acoustic) flow in the pulsation analysis calculations. The computer program utilizes digital analysis techniques to simulate the acoustic response of the piping system to cylinder harmonic excitation. Cylinders were modeled by considering bore, stroke, rod diameter, clearance, suction and discharge temperatures and pressures, and gas compressibility. The compressor model included speed, connecting rod length and crank phase angles. Two performance analyses were provided for review. This compressor utilizes a side stream between the 1st and 2nd stages to provide the majority of the gas for the 2nd stage compression. Steady state performance was calculated using 1,200 rpm. Gas composition was used to determine fluid mixture physical properties such as density, sonic velocity, viscosity, specific heat ratios and compressibility. Simulation of the piping system included pipe diameters, length, flow rate and pressure drop. Influence of pressure drop on acoustic attenuation with changes in sonic velocity due to steady flow velocity was also included in this study.
Bottles and scrubbers were included in the model. Physical dimensions were obtained from the provided drawings and details. Suction and discharge pressures were held to 170 PSIG and 1,285 PSIG for this analysis. Flow rates used for these models were 3.91 & 4.01 MMSCF/D through the 1st stage and 13.14 & 10.44 MMSCF/D for the 2nd stage operation. A sketch is attached with node numbers identified for reference to the acoustic response spectrums. The spectral response plots of pulsation pressure versus frequency at critical points within each piping system are included.
Recommendations
RECOMMENDATIONS Inlet Piping System Suction Bottle V-2604 (V-2) overall dimensions remain as proposed. Extend inlet to bottle center. Reduce portion in bottle to 3” S XS. Refer to sketch PD-01 for details. Interstage Piping System Discharge Bottle V-2605, V-3, overall dimensions remain as proposed. Extend outlet to bottle center. Reduce portion in bottle to 2 ½” S XS. Refer to sketch PD-02. Change suction bottle V-2606A, V-5, to a 3-chamber design. Overall dimensions should be 14” OD x 72” S-S. Refer to sketch PD-05 for details and critical dimensions. Increase diameter of suction bottle V-2606B to 12 ¾” OD. Install a 1.750” diameter orifice plate at the outlet of discharge bottle V-2605. Install a 2.750” diameter orifice plate at the inlet nozzle of suction bottle V-2606A. Install a 1.625” diameter orifice plate at the inlet nozzle of suction bottle V-2606B. Discharge Piping System Change discharge bottle V-2607A, V-6, to a 3-chamber design. Overall dimensions should be 14” OD x 72” S-S. Refer to sketch PD-06 for details and critical dimensions. Increase diameter of discharge bottle V-2607B to 12 ¾” OD. Refer to sketch PD-08. Install a 1.625” diameter orifice plate at the outlet flange of bottle V-2607A. Install a 1.125” diameter orifice plate at the outlet flange of discharge bottle V-2607B.
CUSTOMER JOB NO. UNIT NO. SYSTEM Inlet Piping System
01113 K-2601
CONTACT: Ed Jackson ECSI NO. 201-1018
MODIFICATIONS Suction Bottle V-2604 (V-2) overall dimensions remain as proposed. Extend inlet to bottle center. Reduce portion in bottle to 3” S XS. Refer to sketch PD-01 for details.
ORIFICE SIZE
∆ PRESS. PSI / %
DATE: 01/20/01
COMMENTS API design approach 2 design limit for this system is between 0.3% and 4.5%, depending on pipe diameter and frequency. The modified system should meet API guidelines for both cases reviewed. Bottle unbalanced shaking forces are low. The maximum force will be 15 lbs, or less.
Interstage Piping System
API design approach 2 recommended limit for this system is between 0.2% and 4.9%, depending on pipe diameter and frequency.
Discharge Bottle V-2605 (V-3) overall dimensions remain as proposed. Extend outlet to bottle center. Reduce portion in bottle to 2 ½” S XS. Refer to sketch PD-02.
The modified system should meet API guidelines for the cases studied.
Change suction bottle V-2606A (V-5) to a 3chamber design. Overall dimensions should be 14” OD x 72” S-S. Refer to sketch PD-05 for details and critical dimensions.
Bottle unbalanced shaking forces are low. The maximum force expected will be in the double hung suction bottle. These forces will be 200 lbs, or less. Unbalanced forces in the other bottles are 15 lbs, or less.
Increase diameter of suction bottle V-2606B to 12 ¾” OD. Install an orifice plate at the outlet of discharge bottle V-2605.
1.750”
3.94 / 0.83
Install an orifice plate at the inlet nozzle of suction bottle V-2606A.
2.750”
2.32 / 0.49
Install an orifice plate at the inlet nozzle of suction bottle V-2606B.
1.625”
3.55 / 0.75
Discharge Piping System
API recommended design limit is between 0.2% and 3.0%, depending on pipe diameter and frequency.
Change discharge bottle V-2607A (V-6) to a 3-chamber design. Overall dimensions should be 14” OD x 72” S-S. Refer to sketch PD-06 for details and critical dimensions. Increase diameter of discharge bottle V-2607B to 12 ¾” OD. Refer to sketch PD-08.
The modified system meets API criteria for the two cases reviewed, except in the recycle / bypass lines. These lines exceed API limits but should not cause problems. The maximum forces in these lines will be less than 50 lbs at 2x running speed.
Install an orifice plate at the outlet flange of bottle V-2607A.
1.625”
7.39 / 0.57
Install an orifice plate at the outlet flange of discharge bottle V-2607B.
1.125”
11.01 / 0.85 Bottle unbalanced shaking forces are low. The maximum force should be 180 lbs, or less.
Conclusions
CONCLUSIONS Compressor packages are fabricated utilizing complicated sub assemblies such as skid, motor/engine base, compressor base, scrubbers, pipe supports and others. Every effort should be used to insure a rigid assembly during construction; scrubbers and pipe supports should be welded to supporting I-beams and not just to the decking. With the compressor, bottle, scrubber, and piping system constructed as per the above system analysis, along with adequate piping clamps, and proper cylinder/bottle bracing and supports, an acceptable level of vibration should be obtained. Compressor cylinder passages and valve interactions are generally not included in the compressor model. Reliable, and exact, information on cylinder passages and valve natural frequencies is difficult to obtain. It is assumed that the cylinder manufacturer has designed the passages to minimize the effects of reflected pulsation pressure waves in the valve area. Normally, natural frequencies of the valves are substantially different than the frequency of any reflected pulsation. However, experience has shown that in some instances, a system that meets API design criteria may have unacceptable valve life. These systems will require further analysis to eliminate the problem. Engineering and Consulting Services, Inc. has used proven advanced design techniques and utilized state-of-the-art computer simulations and computer modeling in an attempt to accurately represent actual system response. The programs used in this study have been used successfully for analysis, design and troubleshooting of gas piping systems in onshore and offshore field gas compressor stations, gas processing plants, fuel gas booster stations, pipeline transmission stations, refineries, and chemical plants. Well over a thousand studies have been successfully performed in the last 15 years. In general, very good comparisons of measured pulsation pressures to calculated pressures have been obtained. If differences exist, calculated pulsation pressures are usually found to be somewhat higher than measured pressures. However, compressor systems are governed by complex relationships and piping interactions; and often react differently than expected. Therefore, Engineering and Consulting Services, Inc., and its representatives, make no claims or guarantees to the accuracy or correctness of the data presented in this report. ECSI cannot be held responsible for results different than those predicted. Do not hesitate to contact us if you have questions, or need additional information concerning this study.
Tom Steeper, P.E. Senior Mechanical Engineer
Piping Systems
Inlet Piping System Acoustic analysis of the inlet gas system included the on-skid inlet piping, suction scrubber V-2602 (V-1), suction bottle V-2604 (V-2), by-pass line to valves 2373, relief valve PSV-2625 and the 1st stage cylinder. Modifications to the proposed suction bottle are necessary to achieve adequate attenuation of the pulsation pressures. Overall dimensions of proposed suction bottle V-2604 (V-2) should remain as proposed. Extend the inlet nozzle in to the bottle center. Reduce the portion of inlet nozzle in bottle to 3” S XS pipe. Extending the inlet nozzle reduced the level and frequency of the bottle unbalanced forces. Refer to sketch PD-01 for critical dimensions and details. API design approach 2 recommended pulsation limit for this system vary between 0.3% and 4.5%, depending on diameter and frequency of interest. This system will meet API design criteria with the recommended modifications. The system response should be acceptable. Unbalanced shaking forces in the suction bottle will be low. Maximum force is expected to be less than 15 lbs. Maximum forces in the by-pass line at valves 2373 are low as well. Refer to the attached plots labeled 1S1.PLT for selected nodal pulsation pressure responses on the following pages. Recommendation: Extend the inlet nozzle in to the bottle center. Reduce the portion of inlet nozzle in bottle to 3” S XS pipe.
INLET PIPING SYSTEM
Interstage Piping System The acoustic analysis of this piping system consists of the 1st stage cylinder, discharge bottle V-2605 (V-3), cooler AC-2602, scrubber V-2603 (V-4), relief valve PSV-2628, suction bottles V-2606A (V-5) and V-2606B (V-7), 2nd stage cylinders, and related piping. This system also includes a side-stream connection to scrubber V-2603. Modifications to the proposed bottles and piping are necessary to achieve acceptable attenuation of the pulsation pressures. Overall dimensions of proposed discharge bottle V-2605 should remain as proposed. Extend the outlet nozzle in to bottle center. Reduce the portion of outlet nozzle in bottle to 2 ½” S XS pipe. Extending the inlet nozzle reduced the level and frequency of the bottle unbalanced forces. Refer to sketch PD-02 for critical dimensions and details. Replace the proposed suction bottle V-2606A with a 3-chamber design. Overall dimensions should be 14” OD x 72” S-S. Choke tube dimensions should be 2” S Std x 34 ½” long. The inlet nozzle should be reduced to 3” S Std in the bottle. Cylinder nozzles should be held to approximately 10” OAL (Over All Length). Refer to sketch PD-05 for critical dimensions and details. Increase the diameter of suction bottle V-2606B (V-7) to 12 ¾” OD. Cylinder nozzles should be held to approximately 10” OAL. Install a 1.750” diameter orifice plate at the outlet of discharge bottle V-2605. The maximum pressure drop resulting from this orifice plate will be 0.83%, or 3.94 PSI. Additionally, install a 2.750” diameter orifice plate at the inlet nozzle of suction bottle V2606A. The pressure drop associated with this orifice plate will be 0.49%, or 2.32 PSI. Finally, install a 1.625” diameter orifice plate at the inlet nozzle of suction bottle V2606B. The maximum pressure drop resulting from this orifice plate will be 0.75%, or 3.55 PSI. API recommended pulsation limit for this system vary between 0.2% and 4.9%, depending on line diameter and frequency. This system should meet API design criteria with the recommended changes. The system response should be acceptable. Bottle unbalanced shaking forces are low. The maximum force expected will be in the double hung suction bottle. These forces will be 200 lbs, or less. Unbalanced forces in the other bottles are 15 lbs, or less. Refer to the attached plots labeled 1IS15.PLT for selected nodal pulsation pressure responses. Recommendation: Extend outlet nozzle to bottle center on discharge bottle V-2605. Reduce the portion of outlet nozzle in bottle to 2 ½” S XS pipe. Replace the proposed suction bottle V-2606A with a 3-chamber design. Choke tube dimensions should be 2” S Std x 34 ½” long. The inlet nozzle should be
reduced to 3” S Std in the bottle. Increase the diameter of suction bottle V-2606B to 12 ¾” OD. Install a 1.750” diameter orifice plate at the outlet of discharge bottle V-2605. Additionally, install a 2.750” diameter orifice plate at the inlet nozzle of suction bottle V-2606A. Finally, install a 1.625” diameter orifice plate at the inlet nozzle of suction bottle V2606B.
Interstage Piping System
Interstage Piping System Continued
Discharge Piping System The acoustic analysis of the discharge piping system consists of the 2nd stage cylinders, discharge bottles V-2607A (V-6), relief valve PSV-2627, by-pass line to valves 2373, cooler AC-2603 and related piping. Modifications to the proposed discharge bottles and piping are necessary to achieve acceptable attenuation of the pulsation pressures. Replace the proposed discharge bottle V-2607A with a 3-chamber design. Overall dimensions should be 14” OD x 72” S-S. Choke tube dimensions should be 1 ½” S 160 x 34 ½” long. The inlet nozzle should be reduced to 2 ½” S XS in the bottle. Cylinder nozzles should be held to approximately 10” OAL (Over All Length). Refer to sketch PD-06 for critical dimensions and details. Change the overall dimensions of proposed discharge bottle V-2607B to 12 ¾” OD x 18” S-S (no change). Extend the outlet nozzle into the bottle center. Reduce the portion of outlet nozzle in bottle to 1 ½” S 160 pipe. Refer to sketch PD-07 for details. Install a 1.625” diameter orifice plate at discharge bottle V-2607A outlet flange. Pressure drop associated with this orifice plate should be a maximum of 0.57%, or 7.39 PSI. Additionally, install a 1.125” diameter orifice plate at discharge bottle V-2607B outlet flange. Pressure drop associated with this orifice plate will be 0.85%, or 11.01 PSI, maximum. API recommended pulsation limit for this system vary between 0.2% and 3.0%, depending on pipe diameter and frequency. The modified system meets API criteria for the two cases reviewed, except in the recycle / bypass lines. These lines exceed API limits but should not cause problems. The maximum forces in these lines will be less than 50 lbs at 2x running speed. Unbalanced shaking forces in the discharge bottles will be low. Maximum force is expected to be 180 lbs, or less. Maximum forces in the by-pass line at valves 2373 will be low, as well. Refer to the attached plots labeled 1D14.PLT for selected nodal pulsation pressure responses. Recommendation: Replace the proposed discharge bottle V-2607A with a 3-chamber design. Overall dimensions should be 14” OD x 72” S-S. Choke tube dimensions should be 1 ½” S 160 x 34 ½” long. The inlet nozzle should be reduced to 2 ½” S XS in the bottle. Cylinder nozzles should be held to approximately 10” OAL. Change the diameter of proposed discharge bottle V-2607B to 12 ¾” OD. Install a 1.625” diameter orifice plate at discharge bottle V-2607A outlet flange. Additionally, install a 1.125” diameter orifice plate at discharge bottle V-2607B outlet flange.
DISCHARGE PIPING SYSTEM
DISCHARGE PIPING SYSTEM Continued
Technical Data
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