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Compressor performance test

Many large petrochemical projects involve considerable investment. Plant output value can be measured in staggering amounts of money if value of lost production is calculated. An incorrect pressure switch installed on a compressor may have very little direct financial impact to a compressor manufacturer, but it can cause a loss to the user far in excess of the total value of the compressor package itself. Extra care must therefore be taken in compressor performance tests. In the planning of a pro- ject, testing has to be reviewed to ... [Pg.404]

Figure — This compressor-performance test can be run for any given pressure interval or time duration... Figure — This compressor-performance test can be run for any given pressure interval or time duration...
ISO 5011 2014 Inlet air cleaning equipment for internal combustion engines and compressors — Performance testing SAE J726 Air Cleaner Test Code JIS D 1612 Test methods of air cleaners for automobiles... [Pg.197]

The most straightforward way of proof testing the equipment would be to reproduce site conditions completely. Under such conditions, the testing would easily establish if the compressor performance requirements are met and if the driver and support systems function as intended and are adequate for the purpose. [Pg.407]

Another potential problem is due to rotor instability caused by gas dynamic forces. The frequency of this occurrence is non-synchronous. This has been described as aerodynamic forces set up within an impeller when the rotational axis is not coincident with the geometric axis. The verification of a compressor train requires a test at full pressure and speed. Aerodynamic cross-coupling, the interaction of the rotor mechanically with the gas flow in the compressor, can be predicted. A caution flag should be raised at this point because the full-pressure full-speed tests as normally conducted are not Class IASME performance tests. This means the staging probably is mismatched and can lead to other problems [22], It might also be appropriate to caution the reader this test is expensive. [Pg.413]

Spare rotors are frequently part of a new compressor contract. A deci sion must be made regarding the testing of the spare rotor. The recommended practice is to mechanically run spare rotors, using the same procedures used for the main. As a matter of logistics, the compressor is usually shipped with the last run rotor. If a performance test has been specified, it can be run before the rotors are changed and both rotors performance tested. This would not be economical, however. [Pg.414]

The many problems with correlation and good shop tests discussed in this chapter would seem to lead to the conclusion that one should field test. It is still better, however, if at all possible, to test in the shop. The new compressor field tests should be limited to only those units where performance is in doubt and shop test correlation is just too difficult. A four sidestream multi-component hydrocarbon gas would probably qualify as difficult to shop test. [Pg.429]

Matthews, Terryl, Field Performance Testing to Improve Compressor Reliability, Proceedings of the 10th Turbomachinery Symposium, College Station, TX Texas A M University, 1981, pp. 165-167. [Pg.436]

For a polytropic process the change of state does not take place at constant entropy, hut for an adiabatic process, it does. Heat may he added to or rejected from a gas in a polytropic process. For a polytropic process, the correlating exponent for the PiVi" component is the exponent n, which becomes an important part of the compressor design, n values are determined from performance testing. [Pg.390]

Ail pressure increases when air flows into a system, and decreases when air flows out. Using this principle, here is a simple method to determine air-compressor performance and compressed-air load for plants using reciprocating or positive-displacement compressors (see figure). Accuracy for this test is approximately 10%. [Pg.26]

Bowman, R.C., et al.. Performance testing of a vanadium hydride compressor, Zeitschrift Eur Physikalische Chemie - International Journal of Research in Physical Chemistry Chemical Physics, 1994, 183 p. 245-250. [Pg.355]

Test the compressor on impure hydrogen streams to determine threshold contamination levels (levels at which compressor performance is affected) for water (H2O), O2, CO, and methane (CH4). [Pg.213]

Compressor performance parameters follow basic dimensional analysis and similarity rules which allow to design and test stages at some reference conditions and then apply them at actual (dimensional) conditions. If it were 100% rigorously followed, this process would guarantee a perfect matching of the performance. Unfortunately, in real life this is not always possible for several reasons such as lirst and last stage effects, lateral injections, difSculty of matching Reynolds number, etc. Thus, some corrections are needed to move from the performance stored in the database to the actual machine. There is a trade-off between the complexity of the database and the amount of adaptations which are needed (Fig.14). [Pg.239]

The prototype power conversion equipment, particularly the rotating components, will undergo shop acceptance tests to the fullest extent possible. These are followed by field tests of the partially to fully integrated power conversion system to verify the turbo-machinery aerodynamics and the system hot functions. To limit power input for cost saving, the field tests are planned at partial system pressures and partial to full tuifiine inlet temperatures, using either conventional or nuclear heaters. For example, the FSNL (i.e. full speed, no load) test, which has the main objective of validating the full-size compressor aerodynamics and efficiency, may be carried out at selected partial or rated conditions as indicated on the compressor performance map (Fig. XVI-5). [Pg.498]

FIG XVI-5. Optional FSNL test points marked on the compressor performance map. [Pg.498]

FIG. XVI-IO. Layout of helium gas loop for compressor aerodynamic performance test. [Pg.502]

XVI-8] TAKADA, S. et al.. Program for aerodynamic performance tests of helium gas compressor model of the gas turbine high temperature reactor (GTHTR300), Trans. At. Energy Soc., Japan, 2, No. 3 (2003), 291-300... [Pg.507]

Compressor Performance - Selection, Operation, and Testing of Axial and C trihigai Compressors, by M. T. Gresh, Butterworth-Heinemann, Stoneh, Massachusetts, 1991. [Pg.66]

Off-design studies indicate that system performance is highly sensitive to Brayton turbine and compressor efficiency. The system can sustain only a 1.3% degradation in turbine and compressor efficiency, when taken simuitaneously, and still be able to produce the required 185 kWe at beginning-of-life. This result supports the conclusion obtained from the design sensitivity studies i.e. Brayton turbomadiinery should continue to be a key area of development. Test programs should be implemented to verify satisfactory turbine and compressor performance over component life. [Pg.188]

Accurate turbine and compressor performance maps are needed to fully characterize plant transients. Plant operations like startup and transients like complete loss of load have required extrapolating perfomnance beyond available performance maps. SNPP model accuracy vrith extrapolated performance maps will have significant uncertainty until prototypical test data is obtained. [Pg.578]

This test is performed to verify the struetural integrity of the expander wheels and the eompressor wheels. The expander wheels should be instantaneously oversped during the meehanieal test while assembled on the shaft. Compressor wheels should be oversped during the meehanieal test or, alternatively, in a separate spin test faeility. [Pg.281]

Obviously this test applies only to the centrifugal compressor. The manufacturer normally performs this test whether specified or not. Since the user does have an interest in the test, some discussion of the parameters is in order. API 617 mandates the test, which includes the requirement to spin the impeller at a speed of 115% of the maximum continuous speed for a duration of one minute. [Pg.406]

The preceding experience did lead to a lack of confidence, and it was concluded that an impeller-by-impeller performance check should be carried out theoretically at test speed with the test gas. This idea was carried out on a cold methane compressor with nine impellers. The results of this were fruitful as can be seen from Figure 10-5, and the expected performance at various test speeds calculated in accordance with the code is shown in Figure 10-6. As a result of this work, two test speeds were... [Pg.427]

If not available and the driver is a motor, the local electrical engineers may be coerced into procuring accurate current (CT) and potential (PT) transformers to permit the use of watt meters. The everyday plant CTs and PTs aren t suitable for a quantitative field test. When having to solve a compressor s performance, one will use what is available, but only because it is expedient. [Pg.434]

Sayyed, S., Aerodynamic Shop Testing Multistage Centrifugal Compressor and Predicting Gas Performance, ASME 78-PET-28, New York American Society of Mechanical Engineers, 1978,... [Pg.436]


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