Статті в журналах: "Seals of compressors"

1

Kirk, R. Gordon, and S. K. Baheti. "Evaluation of Floating Ring Seals for Centrifugal Compressors Using the Finite Element Method." Journal of Vibration and Acoustics 121, no. 1 (January 1, 1999): 131–36. http://dx.doi.org/10.1115/1.2893940.

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The use of liquid ring type oil seals in centrifugal compressors was essential for high pressure applications dating back to the early 1960’s. The analysis of high pressure oil seals was first documented in the literature in the mid-1970’s following a series of compressor instability problems that made it clear that a better understanding of how seals influence the overall rotor stability was necessary. To produce compressor designs at higher speeds requires that an adequate method of predicting the oil seal influence on rotor dynamic stability be available for the designer. With the enhanced capability of personal computers and improved finite element models of the oil film thermal and hydrodynamic solutions, it is now possible to more accurately predict the dynamic characteristics of the oil seals. This paper presents a series of predicted results from a currently available advanced state of the art computer analysis for high pressure oil seals. The evaluation of several high pressure compressor seal designs illustrates the current capability for analytical predictions for various seal bore geometries. Conclusions and recommendations for the design of liquid ring seals are presented, which can give the compressor designer guidance for application to future high performance compressor liquid seal designs.

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2

Raswin, Nuradi Bin. "Analisis Pengujian Dry Gas Seal Type 28AT Tandem untuk Meningkatkan Reliability Dry Gas Seal di Kompresor Setrifugal." SINTEK JURNAL: Jurnal Ilmiah Teknik Mesin 13, no. 2 (December 1, 2019): 73. http://dx.doi.org/10.24853/sintek.13.2.73-79.

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Dry gas seal testing is one of the stages in the repair and maintenance of dry gas seals because without testing dry gas seals will have fatal consequences, which can cause more severe damage to the compressor and repair of humans and the environment. In the operation and maintenance of centrifugal compressors, especially gas compressors, there is often damage to dry gas seals or even if they are not damaged dry gas seals must be kept in a health check so that they can be used optimally and their reliability can be improved. In conducting a health check or repairing dry gas seal, one of the determinants of success is through static and dynamic testing using the DGS test rig or the other. Therefore it is very important in testing this dry gas seal that the author tries to learn how to complete the tests that must be considered in the testing procedure. In this study it can be concluded that the maximum speed used reaches 11429 rpm, when compared to the procedure is 1 - 1,225 x rpm in the compressor then the rotation obtained according to the procedure is (1,225 x 10000 = 12250 rpm maximum), with conditions 11429 rpm already fulfilling standard and is still within tolerance of testing rounds.

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3

Wang, Wei Min, and Wei Zheng An. "Investigation on the Subsynchronous Vibration Fault Diagnosis and Control for Centrifugal Compressor." Applied Mechanics and Materials 34-35 (October 2010): 1488–92. http://dx.doi.org/10.4028/www.scientific.net/amm.34-35.1488.

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Centrifugal compressors are widely used to compressor gas in many different processes within the petroleum and chemical industry. Two vibration types of concern in industrial compressors are synchronous and subsynchronous vibration. The latter, more troubling type of vibration, occurs when non-conservative whirling forces(Cross-coupling) act to excite a lateral natural frequency, which lies below the running speed(subsynchronous vibration). In this paper, more attention is paid to impellers from a rotordynamic standpoint and a synthesis gas compress in ammonia plant is analyzed in order to diagnosis the root cause of vibration fault using the best available resources for seals and bearing. Logarithmic decrement predictions for the full rotor model consisting of all the stages and seals are conducted under different bearing structure. On this basis, a resolvent to improve the rotordynamic stability is presented. The field application result indicates that this method is effective.

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4

Gelin, A., J. M. Pugnet, D. Bolusset, and P. Friez. "Experience in Full-Load Testing of Natural Gas Centrifugal Compressors for Rotordynamics Improvements." Journal of Engineering for Gas Turbines and Power 119, no. 4 (October 1, 1997): 934–41. http://dx.doi.org/10.1115/1.2817077.

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During full-load shop tests under natural gas, two multistage centrifugal compressors exhibited subsynchronous vibrations. Both of them are low-flow, high-pressure, high rotational speed compressors, and are fitted with tilting pad bearings and dry gas seals. A rotating stall problem was first eliminated by a modification of the diffuser geometry. Then, aerodynamic excitations caused the rotors to operate at their stability limit, and high vibration levels were observed at the first natural frequency. A complete rotordynamics analysis was performed in order to model precisely all the fluid–structure interactions. Modifications of the rotor designs were implemented, consisting in optimizing conveniently the bearing pads, replacing the toothed labyrinth seals of the balance pistons by damping honeycomb seals, fitting them with improved shunt hole systems. In addition, the dry gas seals were found to have been damaged, due to thermal effects, and further modifications were implemented to eliminate this problem. Final full load tests demonstrated a satisfactory behavior of both centrifugal compressors.

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5

Sadovskiy, Nikolai, Leonid Strizhak, Anatoliy Simonov, and Mikhail Sokolov. "Some problem of centrifugal compressors upgrading." MATEC Web of Conferences 245 (2018): 09004. http://dx.doi.org/10.1051/matecconf/201824509004.

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The results of computational investigation of the influence of a gas labyrinth seals, oil end seals with floating rings and oil journal bearings lubricating layer stiffness coefficient on centrifugal compressor rotor critical speed are presented and analysed. The main principles of a method for axial forces acting on centrifugal compressor rotor calculation are listed. The method has been developed at the compressor, vacuum and refrigeration technologies department of SPbSTU. In addition, the estimation of method applicability in engineering calculations is given.

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6

Petrovskii, B. S., B. I. Nazarevich, and I. T. Yarema. "Plastic seals of rotor of centrifugal compressors." Chemical and Petroleum Engineering 23, no. 12 (December 1987): 610–12. http://dx.doi.org/10.1007/bf01147526.

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7

Soto, E. A., and D. W. Childs. "Experimental Rotordynamic Coefficient Results for (a) a Labyrinth Seal With and Without Shunt Injection and (b) a Honeycomb Seal." Journal of Engineering for Gas Turbines and Power 121, no. 1 (January 1, 1999): 153–59. http://dx.doi.org/10.1115/1.2816303.

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Centrifugal compressors are increasingly required to operate at higher pressures, speeds, and fluid density. In these conditions, compressors are susceptible to rotordynamic instabilities. To remedy this situation, labyrinth seals have sometimes been modified by using shunt injection. In shunt injection, the gas is taken from the diffuser or discharge volute and injected into an upstream chamber of the balance-piston labyrinth seal. The injection direction can be radial or against rotation. This study contains the first measured rotordynamic data for labyrinth seals with shunt injection. A comparison has been made between conventional labyrinth seals, labyrinth seals with shunt injection (radial and against rotation), and a honeycomb seal. Labyrinth seals with injection against rotation are better able to control rotordynamic instabilities than labyrinth seals with radial injection; however, the leakage is slightly higher. The leakage comparison for all seals demonstrates that the honeycomb seal has the best flow control. Test data are presented for a top rotor surface velocity of 110 m/sec, a supply pressure of 13.7 bars, and IPr = 0.95 (injection pressure is 1.05 = 1/0.95 times the seal inlet pressure). For these conditions, and considering effective damping, the labyrinth seal with injection against rotation is better than the honeycomb seal when the pressure ratio across the seal PR < 0.45. On the other hand, the honeycomb seal is better when PR > 0.45. The effectiveness of the shunt-injection against rotation in developing effective damping is reduced with increasing rotor surface velocity.

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8

Shevchenko, Serhii. "ANALYSIS OF THE IMPACT OF SPECIAL CONSTRUCTIONS OF GAP SEALS ON THE DYNAMICS OF CENTRIFUGAL MACHINES." ScienceRise, no. 5 (November 11, 2020): 3–13. http://dx.doi.org/10.21303/2313-8416.2020.001485.

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The object of research: the influence of the design features of special gap seals on the dynamic characteristics of centrifugal machines. Investigated problem: harmonization of the consumption and dynamic characteristics of the seals of the rotors of high-speed machines by applying special design methods. Main scientific results: The mechanism and operating conditions of seals with floating rings are described. It is determined that the most effective from the point of view of dynamic characteristics is the variant of the semi-movable ring. Expressions for determining the conditions of angular and radial immobility of a floating ring are obtained. The design options for deformable gap seals, including deformable floating rings, deformable interwheel seals and seals with an axially movable deformable sleeve, have been investigated. The scope of their application for unique machines with high requirements for tightness and vibration reliability has been determined. Variants of the design of labyrinth seals have been investigated. The analysis shows that the dynamic properties of labyrinth seals significantly depend on the relative position of the ridges. Overlapping ridged seals have the worst dynamic performance of the labyrinth seal designs. The honeycomb seal has more favorable dynamic properties, and the well seal has the best combination of consumption and dynamic characteristics. The dynamic characteristics are especially important for the seals of high-speed rotors of centrifugal machines. The area of practical use of the research results: Enterprises that manufacture centrifugal machines: pumps and compressors. Innovative technological product: a methodology for the selection, design and calculation of special designs of gap seals with optimization of dynamic and flow characteristics. Scope of application of the innovative technological product: The obtained research results will be useful in the design and manufacture of centrifugal pumps and compressors for any parameters.

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9

Shade, W. N., and D. W. Legg. "Explosive Decompression Resistance of Centrifugal Compressor O-Ring Seals: A Comparative Test Summary and Procedure." Journal of Engineering for Gas Turbines and Power 110, no. 2 (April 1, 1988): 289–94. http://dx.doi.org/10.1115/1.3240119.

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Explosive decompression is a phenomenon that can destroy O-ring sealing elements in high-pressure (>3.4 MPa) natural gas compressors during rapid venting to atmospheric pressure. A test rig and procedure have been developed to identify important parameters influencing O-ring seal explosive decompression failure, consistent with utilization of these seals in high-pressure centrifugal compressors. The test rig and procedure are described and comparative test results presented.

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10

Childs, Dara W., Luis E. Rodriguez, Vito Cullotta, Adnan Al-Ghasem, and Matthew Graviss. "Rotordynamic-Coefficients and Static (Equilibrium Loci and Leakage) Characteristics for Short, Laminar-flow Annular Seals." Journal of Tribology 128, no. 2 (September 28, 2005): 378–87. http://dx.doi.org/10.1115/1.2164468.

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Test results are presented for laminar-flow seals that are representative of buffered-flow oil seals in centrifugal compressors. The seals are short (L∕D≅0.21), with a diameter of 117mm and a clearance-to-radius ratio 0.0007. A smooth seal, a seal with one central groove, and a seal with three grooves were tested. Groove geometries employed are representative of industrial practice for compressors with a groove-depth to clearance ratio on the order of 6. Tests were conducted at 4000, 7000, and 10,000rpm shaft speed with delta pressures across the seals of 21, 45, and 69bars. For all cases, the flow was laminar. The seals were tested from a centered position out to an eccentricity ratio of 0.7. Static data included leakage and equilibrium loci for a range of loads. Direct and cross-coupled stiffness and damping coefficients and direct mass coefficients were determined from dynamic tests. For the smooth seal, comparisons between measurements and predictions were reasonable for the direct and cross-coupled stiffness and damping coefficients; however, measured added mass coefficients were roughly ten times larger than predicted. Predictions for the grooved seals from a “deep-groove” model that assumed zero pressure oscillations in the grooves greatly over predicted the influence of the grooves. In a centered position, smooth and grooved seals had comparable leakage performance. At higher eccentricity ratios, the grooved seals leaked modestly more. For eccentricity ratios less than approximately 0.3, the grooved seals and the smooth seal had qualitatively similar static and dynamic characteristics. In terms of cross-coupled stiffness coefficients, the grooved seals were less stable than the smooth seal at eccentricity ratios greater than approximately 0.5 but had significantly lower cross-coupled coefficients at reduced eccentricity ratios between zero and 0.3. A grooved centered seal is more stable than a smooth centered seal. The smooth seal had higher damping than the grooved seals and had moderately better centering capabilities.

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11

Shade, W. N., and D. E. Hampshire. "An Experimental Investigation of Oil-Buffered Shaft Seal Flow Rates." Journal of Engineering for Gas Turbines and Power 107, no. 1 (January 1, 1985): 170–80. http://dx.doi.org/10.1115/1.3239679.

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An experimental investigation was conducted to identify an optimum oil-buffered shaft seal for use on centrifugal compressors, with the primary objective being minimal seal oil exposure to process gases that cause seal oil degradation or are toxic. Types of seals tested included smooth bore cylindrical bushings, spiral groove cylindrical bushings, radial outward-flow face seals, and radial inward-flow face seals. The influence of shaft speed, gas pressure, seal oil differential pressure, oil bypass flow rate, and oil supply temperature on process side seal oil flow rate was determined. The investigation revealed some surprising relationships between seal oil flow rates and the escape of process gas.

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12

Reedy, S. W., and R. G. Kirk. "Advanced Analysis of Multi-Ring Liquid Seals." Journal of Vibration and Acoustics 114, no. 1 (January 1, 1992): 42–46. http://dx.doi.org/10.1115/1.2930232.

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The equilibrium position of multi-ring seal assemblies is of major importance to the designer of high pressure centrifugal compressors. Typical computer codes now use a curve-fit of the Short Bearing Sommerfeld Number for eccentricity evaluation with the assumption that all rings in the assembly will always operate at the same eccentricity. The results from the recently developed seal analysis program, SEALS, have shown that the equal eccentricity assumption for multi-ring seals is questionable. This paper will review the analysis procedure used in SEALS, and present the results of an eccentricity evaluation comparison with a seal analysis program currently being used in industry.

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13

Matuszewski, Leszek, and Piotr Bela. "New Designs of Magnetic Fluid Seals for Reciprocating Motion." Polish Maritime Research 28, no. 4 (December 1, 2021): 151–59. http://dx.doi.org/10.2478/pomr-2021-0057.

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Abstract The operating conditions of magnetic fluid seals during reciprocating motion are so different from those observed in rotating motion that the use of their conventional structures for reciprocating motion seals yields no good results. The analysis of the sealing mechanism of magnetic fluid seals in reciprocating motion shows that the operation of these seals is affected by the carry-over phenomenon and magnetic fluid film deformation in the sealing gap, which depends on the velocity of the reciprocating motion. The reduced amount of magnetic fluid in the sealing gap caused by the reciprocating motion of the shaft is the main reason for seal failures. The paper presents a short characterisation of magnetic fluid sealing technology, the principle of sealing, the operation of the magnetic fluid and the seal failure mechanism in linear motion of the shaft. Moreover, some new structural designs of hybrid seals, being combinations of typical hydraulic seals with magnetic fluid seals for reciprocating motion, and some examples of magnetic fluid sealing structures for hydraulic cylinders and piston compressors which have practical application values are presented.

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14

Schwerdtfeger, Markus. "Leakage test examination of shaft seals for CO2 refrigerant compressors." ATZ worldwide 111, no. 6 (June 2009): 38–43. http://dx.doi.org/10.1007/bf03225080.

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15

TYMOSHCHUK, Oleksandr. "DEVELOPMENT AND ANALYSIS OF THE ACCURACY OF ENGINEERING METHODS FOR DETERMINATION OF INTERACTION VOLUME FOR CALCULATION OF THE TIGHTNESS OF NON-LUBRICATING CYLINDER-PISTON SEALS." Herald of Khmelnytskyi National University 303, no. 6 (December 2021): 256–59. http://dx.doi.org/10.31891/2307-5732-2021-303-6-256-259.

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Based on the theory of stochastic processes, methods of engineering calculation of the contact volume for the calculation of the tightness of non-lubricating cylinder-piston seals of compressors have been developed. The result is the creation of methods for calculating the tightness (duration of gas flow) in non-lubricating cylinder-piston metal-polymer seals, as well as assessing the accuracy of the created methods for piston seals. The article considers the elastic contact of a strongly anisotropic rough surface (polymer surface) with a smooth (metal) surface. The dependence of the intercontact gas volume on the complex of contact conditions based on the theory of stochastic fields is investigated. An estimate of the error that occurs when replacing the exact formula for calculating the contact volume with an approximate formula is performed. The values calculated according to the exact and calculated formula of the consolidated inflow differ by no more than 0.17 percent. Accurate methods for calculating the tightness of non-lubricating cylinder-piston seals for molecular and viscous modes of gas flow, which is the basis for practical calculations of the tightness of the seals of non-lubricating pneumatic compressors, are theoretically substantiated and developed. The dependence of the contact volume, the effective level of deformation and the average height of the gap on the set of contact conditions has been studied. It is established that at low loads the deformation level, the effective deformation level, the reduced contact volume and the reduced average gap height are numerically equal. The values calculated by the exact and calculated formula of the contact volume differ by no more than 0.17 percent at K 1 and no more than 0.00029 percent at K> 1.

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16

Lelgemann, K. D. "The Design, Selection, and Application of Oil-Free Screw Compressors for Fuel Gas Service." Journal of Engineering for Gas Turbines and Power 117, no. 1 (January 1, 1995): 74–80. http://dx.doi.org/10.1115/1.2812784.

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Fuel gas compressors installed in cogeneration systems must be highly reliable and efficient machines. The screw compressor can usually be designed to meet most of the gas flow rates and pressure conditions generally required for such installations. To an ever-increasing degree, alternative sources are being found for the fuel gas supply, such as coke-oven gas, blast-furnace gas, flare gas, landfill gas, and synthesis gas from coal gasification or from pyrolysis. A feature of the oil-free screw compressor when such gases are being considered is the isolation of the gas compression space from the bearing and gear lubrication system by using positive shaft seals. This ensures that the process gas cannot be contaminated by the lubricating oil, and that there is no risk of loss of lubricant viscosity by gas solution in the oil. This feature enables the compressed gas to contain relatively high levels of particulate contamination without danger of “sludge” formation, and also permits the injection of water or liquid solvents into the compression space, to reduce the temperature rise due to the heat of compression, or to “wash” any particulate matter through the compressor.

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17

Pellegrino, Antonio, Maria Jesus Perez-Martin, Kalin Dragnevski, Giuseppe Zumpano, and Nik Petrinic. "Temperature and strain rate dependent mechanical response of METCO 601 aluminium-polyester abradable seal coating." EPJ Web of Conferences 183 (2018): 04012. http://dx.doi.org/10.1051/epjconf/201818304012.

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Abradable coatings are utilised as sacrificial materials in low-pressure compressor casings, and in intermediate and high pressure compressors and seals. The adoption of abradable coatings allows for the clearance between compressor blades and casing to be minimised, increasing the overall efficiency of the engine. Quasi-static and dynamic experiments at different temperatures are conducted to characterise the mechanical response of a thermally-sprayed abradable seal coating. The material is composed of an aluminium continuum matrix and fairly well-dispersed polyester particles. Stress versus strain histories are measured in uniaxial tension and compression at strain rates ranging from 10-3 to 102 s-1, via non-standard experimental techniques. The material displays sensitivity to the strain rate and to the imposed temperature. The mechanical behaviour is brittle in tension while it exhibits higher strains to failure in compression. The material is characterised by a pronounced tension/compression asymmetry.

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18

Wang, Yu-Ming, and Zhen-Qing Chen. "Effective Use of Buffer Gas Sleeve-Type Seals in Centrifugal Compressors." Tribology Transactions 31, no. 3 (January 1988): 376–81. http://dx.doi.org/10.1080/10402008808981837.

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19

Schaller, Andreas, Novin Darvishsefat, and Eberhard Schlücker. "Simulation and Experimental Investigation of Labyrinth Seals for Reciprocating Piston Compressors." Chemical Engineering & Technology 41, no. 5 (April 6, 2018): 1043–50. http://dx.doi.org/10.1002/ceat.201700698.

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20

Baheti, S. K., and R. G. Kirk. "Analysis of High Pressure Liquid Seal Ring Distortion and Stability Using Finite Element Methods." Journal of Tribology 121, no. 4 (October 1, 1999): 921–26. http://dx.doi.org/10.1115/1.2834156.

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The evaluation of floating bushing ring oil seals is of great importance for designs of high pressure centrifugal compressors. This is a result of their enhanced damping capacity at low speeds and their strong destabilizing action at speeds in excess of twice the compressor first critical speed. Accurate prediction of oil seal leakage and exit temperature is very important from the standpoint of the pump and cooler selection for the seal oil console. The previous research has performed thermohydrodynamic (THD) analysis of bushing seal rings with various geometries. The current work is to evaluate the influence of the mechanical deformation on the thermohydrodynamic analysis of the bushing seal ring. The finite element method is used to predict the mechanical deformation of the bushing seal ring due to oil pressure and to solve the nonlinear and coupled Reynolds and energy equations for the pressure and temperature distributions, respectively. The perturbation technique is used to evaluate the stiffness and damping coefficients of the oil seals. Eigenvalue analysis is performed to study the dynamic stability of the compressor rotor. Results comparing the seal leakage, seal oil outlet temperatures, stiffness and damping coefficients, growth factors and damped natural frequencies from the THD analyses with and without the influence of the mechanical deformation of the bushing seal ring are presented. The results indicate that under high pressure conditions the influence of the mechanical deformation of the bushing seal ring on the seal performance is very significant.

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21

XI, JINXIANG, and DAVID L. RHODE. "Rotordynamics of Impeller Eye Seals with Wear-Damaged Teeth in Centrifugal Compressors." Tribology Transactions 49, no. 3 (September 2006): 328–37. http://dx.doi.org/10.1080/05698190600678655.

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22

Wyssmann, H. R. "Rotor Stability of High Pressure Multistage Centrifugal Compressors." Journal of Vibration and Acoustics 110, no. 2 (April 1, 1988): 185–92. http://dx.doi.org/10.1115/1.3269497.

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A major factor influencing rotor stability of multistage high pressure centrifugal turbocompressors are the forces caused by the fluid-rotor interaction in the interstage and balance piston gas seals. An example of a fully 3-D labyrinth flow solution shows that using time averaged Navier-Stokes solutions are still excessive in computer time and hence cannot be used for practical applications. The paper gives a theory based on a two-volume bulk flow model for the prediction of the rotor-dynamic coefficients used for rotor stability calculation by complex eigenvalue analysis. Comparisons of predicted coefficients with measurements carried out on a high pressure compressor and on labyrinth seal test stands are given. The theoretically predicted phenomenon that labyrinth damping is retained even at zero inlet swirl of the leakage flow is confirmed. An example of a stability analysis of a high pressure natural gas compressor is given, where the stability margin increases with fluid pressure, i.e., density, provided seal swirl is controlled.

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23

Ivanov, V. M., Yu V. Kozhukhov, and A. M. Danylyshyn. "IMPROVING THE QUALITY OF DESIGNING LOW-FLOW STAGES OF CENTRIFUGAL COMPRESSORS DUE TO VERIFICATION AND VALIDATION OF CALCULATED CFD MODELS." Izvestiya of Samara Scientific Center of the Russian Academy of Sciences 22, no. 6 (2020): 48–56. http://dx.doi.org/10.37313/1990-5378-2020-22-6-48-56.

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The quality of the produced centrifugal compressors largely depends on the design quality of the flow path. In order to carry out high-quality design of low-flow stages of centrifugal compressors, in this work, a numerical model of a low-flow stage is verified and validated, which are based on modern methods of computational fluid dynamics - CFD (computational fluid dynamics) as part of CALS technologies. In the numerical model of the step, clearances and labyrinth seals were modeled. The issues of using intergrid interfaces, application of turbulence and roughness models are considered. The obtained settings of the numerical model were used to validate seven model stages for the range of the optimal conditional flow rate Φopt = 0.008-0.018 at Mu = 0.785-0.804. The simulation results were compared with experimental data.

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24

Gunter, Edgar J. "Lund’s Contribution to Rotor Stability: The Indispensable and Fundamental Basis of Modern Compressor Design." Journal of Vibration and Acoustics 125, no. 4 (October 1, 2003): 462–70. http://dx.doi.org/10.1115/1.1605978.

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In the early design of compressors and turbines, it was of importance to locate the rotor critical speeds so as to insure that a turbo rotor would not be operating at a critical speed. As compressor and turbine design became more sophisticated, a more detailed analysis of the rotor damped critical speeds and rotor log decrements was necessary. With compressors and turbines operating at higher speeds, under high power levels, and at multiples of the first critical speed, the problem of stability or self-excited whirling is of paramount importance. The onset of self-excited motion may lead to large amplitudes of motion with possible destructions of the rotor or the inability of the compressor to operate at peak power levels. Encountering this phenomenon with a compressor on an off-shore oil platform can mean millions of dollars of lost production. Self-excited whirling can be caused by fluid-film bearings, seals, Alford-type cross-coupling forces, or internal shaft friction, to name a few of the excitation mechanisms. The problem of computing the approximate values of the rotor log decrement under full speed and loading conditions requires the solution of a complex eigenvalue problem. The computation of the rotor complex roots is an order of magnitude more difficult than the problem of undamped critical speed calculations. J. W. Lund presented the first practical numerical procedure for computing turbo-rotor log decrements. The mathematical transfer matrix method pioneered by Lund has allowed industry to develop and stabilize a vast array of rotating machinery leading to the savings to industry of millions of dollars. Without the procedures of Lund, for example, it would not have been possible to resolve stability problems encountered with both the hydrogen and oxygen space shuttle pumps. This paper briefly presents some of the attributes of the Lund stability procedure and its unique characteristics.

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25

Memmott, E. A. "Stability Analysis and Testing of a Train of Centrifugal Compressors for High Pressure Gas Injection." Journal of Engineering for Gas Turbines and Power 121, no. 3 (July 1, 1999): 509–14. http://dx.doi.org/10.1115/1.2818502.

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This paper describes the rotor dynamic stability analysis and the PTC-10 Class 1 test of a three body centrifugal compressor train for high pressure natural gas injection service. This train had a full load full pressure string test on hydrocarbon gasses to a final discharge pressure of 500 BAR (7250 PSIA). Each compressor is of the back to back configuration, and is equipped with tilting pad seals, damper bearings, and a honeycomb labyrinth at the division wall with shunt holes. The driver is a gas turbine.

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26

Yucel, U., and J. Y. Kazakia. "Analytical Prediction Techniques for Axisymmetric Flow in Gas Labyrinth Seals." Journal of Engineering for Gas Turbines and Power 123, no. 1 (May 12, 2000): 255–57. http://dx.doi.org/10.1115/1.1340630.

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Labyrinth seals are commonly found in turbines and compressors. Their objective is to control gas leakage from high pressure regions to low pressure regions. The correct prediction and control of this leakage is crucial for the efficient and economic operation of turbomachinery. In this paper we present approaches for obtaining the above prediction in a simple analytical and explicit method. Both constant and pressure dependent flow coefficients are incorporated in the present study which extends to the higher inlet/outlet pressure differences. The results obtained with our methods compare favorably with the ones obtained by both numerical and experimental techniques. In many cases there is hardly a distinction between our results and the numerical prediction.

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27

Dorokhin, V. P., A. V. Yanko, O. V. Nasakin, and E. A. Shevtsova. "Testing of materials for end seals of compressors used in mobile air conditioners." Chemical and Petroleum Engineering 23, no. 3 (March 1987): 123–25. http://dx.doi.org/10.1007/bf01156778.

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28

Al-Ghasem, Adnan, G. L. Morrison, and John P. Platt. "Experimental and Numerical Investigation of a Gas Compressor Windback Seal." Journal of Tribology 129, no. 1 (September 18, 2006): 129–34. http://dx.doi.org/10.1115/1.2401205.

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The effectiveness of a computational fluid dynamics (CFD) commercial code to accurately predict the leakage rate for a windback seal was evaluated. The windback seal under consideration has a rectangular cavity and is similar in design to a gas tooth on stator annular labyrinth seal. The main difference is the windback seal has only one tooth, which continuously winds around the shaft like a screw thread. These seals are used in gas compressors to isolate the gas face seal from bearing oil. A purge gas is passed through the seal into the bearing housing. The helical design allows the seal to clear itself of any oil contamination. The objective is to determine if CFD simulations can be used along with a few experimental tests to study windback seals of this design. Comparison of measurement and predictions for a simple rectangular cavity windback seal shows predictions and measurements comparing very well with maximum differences of 5% for leakage rate. The variation of leakage with shaft speed and pressure ratio across the seal is accurately predicted by the CFD simulations.

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29

Sprowl, Tony B., and Dara W. Childs. "A Study of the Effects of Inlet Preswirl on the Dynamic Coefficients of a Straight-Bore Honeycomb Gas Damper Seal." Journal of Engineering for Gas Turbines and Power 129, no. 1 (March 1, 2004): 220–29. http://dx.doi.org/10.1115/1.2227416.

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Honeycomb seals are frequently used as replacements for labyrinth seals in high-pressure centrifugal compressors to enhance rotordynamic stability. A concern exists that this enhanced stability will be lost if the honeycomb cavities become clogged. Static and dynamic tests were conducted on a honeycomb and a smooth seal (representing the honeycomb seal with completely clogged cells) at the same constant clearances using air with a supply pressure of 70 bars. The test matrix included three speeds, three pressure ratios, and three inlet preswirl conditions. The results show increased leakage, decreased synchronous stiffness, and decreased dynamic stability for the smooth seal with preswirled flow. The results strongly support the use of swirl brakes at the entrance of a honeycomb seal if clogging is a concern. Comparisons between test results and predictions from a two-control-volume theory by Kleynhans and Childs showed excellent agreement in general.

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30

Childs, Dara W., Matthew Graviss, and Luis E. Rodriguez. "Influence of Groove Size on the Static and Rotordynamic Characteristics of Short, Laminar-Flow Annular Seals." Journal of Tribology 129, no. 2 (January 5, 2007): 398–406. http://dx.doi.org/10.1115/1.2647471.

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Test results are presented for a smooth seal and three centrally grooved seals that are representative of buffered-flow oil seals in centrifugal compressors. The seals are short (L∕D≅0.21), with a diameter of 117mm and a nominal radial clearance of 0.085mm, netting the clearance-to-radius ratio 0.0015. The grooves have groove depth to clearance ratios (Dg∕Cr) of 5, 10, and 15. Test conditions include three shaft speeds from 4000rpm to 10,000rpm, three inlet oil pressures from 24bar to 70bar, and seal eccentricity ratios from 0 (centered) to 0.7. Dynamic results include stiffness, damping, and added-mass coefficients; static results include stator position, attitude angles, and seal leakage. Stiffness, damping, and mass coefficients plus leakage are compared for the seal geometries. Results show that all rotordynamic coefficients consistently decrease with increasing seal groove depths, and seal leakage is largely unchanged. Comparisons are also made between experimental results and predictions from a computer program based on a Reynolds + energy equation model. The model includes the assumption that a groove is large enough to create separate lands within the seal, creating a zero or negligible pressure perturbation within the groove. Test results show that even the deepest groove depth tested is not deep enough to satisfy this assumption.

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31

Wellborn, S. R., I. Tolchinsky, and T. H. Okiishi. "Modeling Shrouded Stator Cavity Flows in Axial-Flow Compressors." Journal of Turbomachinery 122, no. 1 (February 1, 1999): 55–61. http://dx.doi.org/10.1115/1.555427.

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Experiments and computational analyses were completed to understand the nature of shrouded stator cavity flows. From this understanding, a one-dimensional model of the flow through shrouded stator cavities was developed. This model estimates the leakage mass flow, temperature rise, and angular momentum increase through the cavity, given geometry parameters and the flow conditions at the interface between the cavity and primary flow path. This cavity model consists of two components, one that estimates the flow characteristics through the labyrinth seals and the other that predicts the transfer of momentum due to windage. A description of the one-dimensional model is given. The incorporation and use of the one-dimensional model in a multistage compressor primary flow analysis tool is described. The combination of this model and the primary flow solver was used to reliably simulate the significant impact on performance of the increase of hub seal leakage in a twelve-stage axial-flow compressor. Observed higher temperatures of the hub region fluid, different stage matching, and lower overall efficiencies and core flow than expected could be correctly linked to increased hub seal clearance with this new technique. The importance of including these leakage flows in compressor simulations is shown. [S0889-504X(00)00501-8]

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32

Baheti, S. K., and R. G. Kirk. "Finite Element Thermohydrodynamic Analysis of Two-Lobe Oil Seals Used in High Pressure Centrifugal Compressors." Tribology Transactions 41, no. 4 (January 1998): 554–62. http://dx.doi.org/10.1080/10402009808983782.

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33

Baheti, S. K., and R. G. Kirk. "Thermo-Hydrodynamic Solution of Floating Ring Seals for High Pressure Compressors Using the Finite-Element Method." Tribology Transactions 37, no. 2 (January 1994): 336–46. http://dx.doi.org/10.1080/10402009408983302.

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34

Baha, Vadym, Natalia Lishchenko, Serhiy Vanyeyev, Jana Mižáková, Tetiana Rodymchenko, and Ján Piteľ. "Numerical Simulation of Gas Flow Passing through Slots of Various Shapes in Labyrinth Seals." Energies 15, no. 9 (April 19, 2022): 2971. http://dx.doi.org/10.3390/en15092971.

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Labyrinth seals are widely used in centrifugal compressors, turbines, and many other pneumatic systems due to their simplicity of design, reliability, and low cost. The calculation scheme for the movement of the working medium in a labyrinth seal is constructed by analogy with the movement of the working medium through holes with a sharp edge. Annular and flat slots, holes, and such a factor as the shaft rotation with a calculated sector of 3 degrees were studied. The purpose of the study is to determine the flow coefficient when the working medium flows through slots of various shapes. To achieve this purpose, modeling of the working medium flow in the FlowVision software was performed. The mass flow and flow coefficients are determined for the studied slot shapes. The convergence of the calculation results was determined by comparing the values of the mass flow rate at the inlet and outlet of the slot. Differences in visualizations of the flow for the studied variants of slots were established. The resulting difference should be taken into account in practical calculations of the working medium mass flow through the slot using a conditional flow rate factor which is determined by the slot design.

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35

Villasmil, Larry A., Dara W. Childs, and Hamn-Ching Chen. "Understanding Friction Factor Behavior in Liquid Annular Seals With Deliberately Roughened Surfaces." Journal of Tribology 127, no. 1 (January 1, 2005): 213–22. http://dx.doi.org/10.1115/1.1828071.

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Multistage centrifugal pumps and compressors are among the most widely used pieces of rotating machinery in industry. A typical application demands the arrangement of several impellers or wheels mounted on a shaft that spins within a stationary case. Annular seals are the most common sealing devices used in this type of machinery. The annular seal design affects both (i) machinery performance in terms of energy conversion efficiency, and (ii) stability due to the interaction within the rotor and the stator through the fluid flow within the seals. Traditionally, the “bulk-flow” theory due to Hirs (ASME J. Lubrication Technol., pp. 137–146) has been used to estimate annular seals leakage and dynamic coefficients. To predict the flow behavior through the seal, this theory relies on empirical friction factor correlations. While leakage is well predicted, the dynamic coefficients are not. The discrepancy is attributed to the friction factor model. Several experiments have produced seal leakage data indicating that friction factor increases as the seal clearance is increased, contradicting predictions based on Moody’s pipe-friction model. A Computational Fluid Dynamics (CFD) commercial code was used to simulate flat-plate-channel-flow experimental tests of water flowing with deliberately roughened surfaces, showing an increase of friction factor with clearance increase. The higher friction factor characteristics of these deliberately roughened surfaces are governed by their ability to develop a high static pressure in the trailing face of each roughness cavity, while the wall shear stresses on the smooth land play a secondary role. In a certain Reynolds number range, the maximum friction factor observed on a specific roughness pattern size is independent of the actual clearance, which we have referred to as the friction-factor-to-clearance indifference behavior. This phenomenon is found to be related to the roughness cavity size and its length-to-clearance ratio.

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36

D’Souza, Rohan J., and Dara W. Childs. "A Comparison of Rotordynamic-Coefficient Predictions for Annular Honeycomb Gas Seals Using Three Different Friction-Factor Models." Journal of Tribology 124, no. 3 (May 31, 2002): 524–29. http://dx.doi.org/10.1115/1.1456086.

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A two-control-volume bulk-flow model is used to predict rotordynamic coefficients for an annular, honeycomb-stator/smooth-rotor gas seal. The bulk-flow model uses Hirs’ turbulent-lubrication model, which requires a friction factor model to define the shear stresses at the rotor and stator wall. Rotordynamic coefficients predictions are compared for the following three variations of the Blasius pipe-friction model: (i) a basic model where the Reynolds number is a linear function of the local clearance, fs=ns Rems (ii) a model where the coefficient is a function of the local clearance, and (iii) a model where both the coefficient and exponent are functions of the local clearance. The latter models are based on data that shows the friction factor increasing with increasing clearances. Rotordynamic-coefficient predictions shows that the friction-factor-model choice is important in predicting the effective-damping coefficients at a lower frequency range (60∼70 Hz) where industrial centrifugal compressors and steam turbines tend to become unstable. At a higher frequency range, irrespective of the friction-factor model, the rotordynamic-coefficient predictions tend to coincide. Blasius-based Models which directly account for the observed increase in stator friction factors with increasing clearance predict significantly lower values for the destabilizing cross-coupled stiffness coefficients.

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37

Radionenko, Oleksandr, Myroslav Kindrachuk, Oleksandr Tisov, and Andrii Kryzhanovskyi. "FEATURES OF TRANSITION MODES OF FRICTION SURFACES WITH PARTIALLY REGULAR MICRORELIEF." Aviation 22, no. 3 (November 13, 2018): 86–92. http://dx.doi.org/10.3846/aviation.2018.6204.

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Textured surfaces with partially regular micro relief (PRMR) are reported to be an effective means to control lublication. It was found they are good wear debris trap and suppliers of lubricant directly to the actual friction area. Their tribological properties depend on the clearance between mating surfaces, relative slip speed, direction of motion. These parameters change the lubrication regime, and vice versa changing geometry of PRMR it is possible to predict and control lubrication regime for given conditions. Application of micro textured surface is prospective for high precision sliding units – valve slides of oil and hydraulic systems, faces of gear pump gears, ring-to-cylinder interface of aircraft reciprocating engines etc. providing high service life. On other side, changing texture parameters it is possible to stop the leakage of fluid through the gap, what may be efficiently utilized in aircraft non-contacting mechanical (hydrodynamic and hydrostatic) seals of gas compressors and gear mechanisms. This paper discloses some peculiarities of transition lubrication regimes for textured surfaces in lubricated contact.

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38

Zuev, A. V. "Calculation and optimization of shaft end seals for high-pressure centrifugal compressors based on the analysis of friction, dynamics, and thermoelastic hydrodynamic processes." Chemical and Petroleum Engineering 28, no. 3 (March 1992): 154–58. http://dx.doi.org/10.1007/bf01147760.

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39

Hu, Xiao Peng, and Peng Yun Song. "Theoretic Analysis of the Effect of Carbon Dioxide Real Gas on the Performance of the T-Groove Dry Gas Seal." Advanced Materials Research 634-638 (January 2013): 3815–20. http://dx.doi.org/10.4028/www.scientific.net/amr.634-638.3815.

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Dry gas seals have widely used in many centrifugal compressors and other rotating machinery. The gas performance of the dry gas seal is generally regarded as an ideal gas when the gas seal is investigated, designed, and operated. However some real gases performance may be quite different from the ideal gas when the gas pressure is high. In this paper, the carbon dioxide (CO2) was taken as an example in some T-groove dry gas seal, and the virial equation of state, which expresses the effect of real gas, was used, and the finite difference method (FDM) was adopted to solve the Reynolds equation of gas lubrication. The effects of real gas on the opening force (Fo) and radial leakage (Q) of the T-groove gas seal had been obtained. The results show that the seal performance (Fo, Q) will be underestimated when the real carbon dioxide is considered as an ideal gas. In calculation conditions, Fo and Q were maximum underestimated 4.16% and 19.25% respectively when Po was 5MPa and ns was variable and the real carbon dioxide was considered as an ideal gas; Fo and Q were maximum underestimated 7.48%, and 29.25% respectively, when ns was 3000r/min and Po was variable and the real carbon dioxide was considered as an ideal gas.

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40

Wagner, Laurence F., and Paul E. Allaire. "Tilting-Pad Journal Bearings—Frequency-Dependent Dynamic Coefficients and Pivot Flexibility Effects." Lubricants 10, no. 2 (February 3, 2022): 20. http://dx.doi.org/10.3390/lubricants10020020.

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Tribologists have generally accepted that the dynamic modeling of tilting-pad journal bearings (TPJB) must consider the frequency dependency of the dynamic properties. Industrial compressors, turbines, and other rotating machines are subjected to instability drivers, such as blades, impellers, and seals, leading to dominant vibratory frequencies that are generally quite different from rotational frequency. Though the literature has provided related methods and numerical results, full understanding of the physics of TPJB frequency dependency is not generally available to the design community, and theorists and experimentalists are often not in agreement. This investigation hinges on a single-pad, two degree-of-freedom model that creates a basis for understanding the various geometries and operating conditions related to frequency dependency for a full bearing. The analytical results indicate that both stiffness and damping coefficients show frequency dependency, and that the dependency is primarily associated with the pad rotational damping and the flexibility of the pivot contact region that provides support for the pad. Understanding the role of pivot flexibility in combination with the fluid film provides a key to improving agreement between theory and experiment. This article is a revised and expanded version of the paper presented at the ASME 2019 Turbo Expo in Phoenix, Arizona from 17 to 21 June. The paper number was GT2019-90195 and it was titled “On the Frequency Dependency of Tilting-Pad Journal Bearings”.

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41

Qian, Zuoqin, Chen Xu, and Jie Ren. "Thermal analysis of a novel single-effect absorption refrigeration system using water/ionic liquid as working fluids." Thermal Science, no. 00 (2022): 38. http://dx.doi.org/10.2298/tsci201026038q.

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Based on the demand of improving the cooling performance of traditional absorption refrigeration system, a novel single-effect refrigeration system(SEARS) with assisted compressors using water/ionic liquids(ILs)as working fluids was comprehensively analyzed. In present work, four kind of ILs:1-butyl-3-methylimidazoliumdibutylphosphate[BMIM][DBP], 1-methyl-3-methylimidazoliumdimethylphosphate[MMIM][DMP], 1-ethyl-3-methylimidazolium dimethylphosphate[EMIM][DMP]and 1-ethyl-3-methylimidazolium acetate[EMIM][AC], which was studied as working fluid in absorption system at the first time, was modeled and simulated in both systems. Thermodynamic properties of new SEARS were numerically analyzed by non-random two-liquid(NRTL) models and the mass and energy conservation equations. The effects of compression ratio(pr) and temperature on the coefficient of performance(COP) and exergetic efficiency(ECOP) were graphed and discussed. The simulating results showed the potential of IL to be used as substitute for traditional working fluids. Moreover, comparison results suggested the system with auxiliary compressors was better than the traditional system for its lower heat source temperature and higher cooling performance. It was better to increase the pr of the compressor located between the absorber and the evaporator than to increase the pr of the compressor located between the generator and the condenser.

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42

de los Santos, M. A., S. Cardona, and J. Sa´nchez-Reyes. "A Global Simulation Model for Hermetic Reciprocating Compressors." Journal of Vibration and Acoustics 113, no. 3 (July 1, 1991): 395–400. http://dx.doi.org/10.1115/1.2930197.

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This article presents a simulation model for reciprocating hermetic compressors. The acoustical behavior of both admission and discharge circuits is analyzed by invoking the discrete element model. Cavities are considered as elastic elements and ducts as rigid elements with inertia according to this model. Reed valves are modeled as systems of three degrees of freedom, and are studied by using modal analysis. The percussive version of Lagrange equations is used to describe the impact between valves and stops or seats. Results from the theoretical model are checked with those experimentally obtained for a real compressor.

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43

Ross, Stephen L., and M. Theodore Gresh. "Compressor seals for hydrogen recycle service." Sealing Technology 2003, no. 5 (May 2003): 5–8. http://dx.doi.org/10.1016/s1350-4789(03)05013-x.

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44

Romero, Fernando. "New seals solve compressor vibration problem." Sealing Technology 2006, no. 4 (April 2006): 12–14. http://dx.doi.org/10.1016/s1350-4789(06)71128-x.

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45

Kirk, R. G. "Transient Response of Floating Ring Liquid Seals." Journal of Tribology 110, no. 3 (July 1, 1988): 572–77. http://dx.doi.org/10.1115/1.3261688.

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The design and analysis of pressure balanced seals are important to the designers and users of turbomachinery which require floating element seals. The design objective for compressor seals differs from that of the engineered pump seal but the common factor includes the ability to predict the dynamic response of the floating ring seal relative to the rotor shaft. Steady-state calculations can be used to study possible operating conditions for compressor designs, but they do not include accurate account of rotor shaft response and ring spin torque. In addition, engineered pump seal applications are such that the ring is expected to track shaft movement during start-up and shut-down transients when reduced pressures and leakage produce laminar flow sealing conditions. The analysis presented in this paper gives the designer the ability to evaluate seal ring dynamic transient response, including friction stick-slip on the axial sealing face and the ring spin torque interaction with the antirotation element. The analysis results presented in this paper were obtained from a personal computer program written specifically for seal transient analysis.

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46

Yurko, Volodymyr, and Vasyl Martsynkovskyy. "Influence of Changing the End Floating Seal Dynamic Characteristics on the Centrifugal Compressor Vibration State." Applied Mechanics and Materials 630 (September 2014): 356–64. http://dx.doi.org/10.4028/www.scientific.net/amm.630.356.

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There were considered the technical decisions aimed to modernization of the end floating seals for the centrifugal compressor that increased the limit of the rotor system dynamic stability and reduced the vibration levels.

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47

Botros, K. K. "Transient Phenomena in Compressor Stations During Surge." Journal of Engineering for Gas Turbines and Power 116, no. 1 (January 1, 1994): 133–42. http://dx.doi.org/10.1115/1.2906782.

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Transient phenomena are generally inherent in the operation of compressor stations: These are either fast or slow transients. A model describing the governing equation for the gas dynamics, control system, compressor and turbine shaft inertias has been developed. The effect of these inertias is manifested by an example of a compressor station operating near the surge control line. Another example deals with a station that has a cooler placed in the recycle path. This alters the rate at which the compressor shaft decelerates upon shutdown and may cause backward spinning depending on the relative magnitude of the shaft inertia with respect to the cooler volume. Backward spinning of compressor shaft has detrimental effects on dry seals and is undesirable. It was found that by keeping the recycle valve closed upon shutdown, the rate of shaft deceleration will be reduced.

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48

Heshmat, Hooshang, Andrew Zhou, Zhaohui Ren, Said Jahanmir, and James F. Walton, II. "Oil-Free Bearings and Seals for Centrifugal Hydrogen Compressor." Tribology Online 8, no. 1 (2013): 44–63. http://dx.doi.org/10.2474/trol.8.44.

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49

Pan, Coda H. T. "Influence of Compressibility on the Helical Viscous Compressor." Journal of Tribology 123, no. 1 (July 20, 2000): 108–17. http://dx.doi.org/10.1115/1.1327581.

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The pressurization-flow characteristic of a helical viscous compressor is basic to the design of precision air bearings and non-contact gas seals which make use of the spiral-grooved surface feature. The method of Compressible Narrow Groove Analysis (CNGA) makes possible mapping of the pressurization-flow characteristic of a helical viscous compressor for a wide range of the compressibility number. In this manner, design features previously established by Quasi-Incompressible Narrow Groove Analysis (QINGA) are examined with respect to the influence of local compressibility.

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50

Hendricks, R. C. "Brush Seal Performance and Durability Issues Based on T-700 Engine Test Results." International Journal of Rotating Machinery 1, no. 2 (1995): 117–28. http://dx.doi.org/10.1155/s1023621x95000029.

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The integrity and performance of brush seals have been established. Severe bench and engine tests have shown high initial wear or rub-in rates, material smearing at the interface, and bristle and rub-runner wear, but the brush seals did not fail. Short-duration (46 hr) experimental T-700 engine testing of the compressor discharge seal established over 1-percent engine performance gain (brush versus labyrinth). Long-term gains were established only as leakage comparisons, with the brush at least 20 percent better at controlling leakage. Long-term materials issues, such as wear and ultimately seal life, remain to be resolved. Future laeeds are cited for materials and analysis tools that account for heat generation, thermomechanical behavior, and tribological pairing to enable original equipment manufacturers to design high-temperature, high-surface-speed seals with confidence.

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