【導讀】本文提供了一個公平的比較準則，得到了對于兩種類型機器普遍適用的效。這個比較基于用戶最感興趣的要求提出的。影響和在不同負載水平的影響給出了評估。際壓縮過程的工作效率。難點在于正確定義適當的系統邊界，包括與之相關的壓。需要討論在壓縮過程中的機械損失。線規(guī)定，或者是受壓縮機的工作時間和自身退化的影響。管道使用的壓縮設備涉及到往復式和離心式壓縮機。機或者是電動馬達來驅動。所用的燃氣輪機，總的來說，是兩軸發(fā)動機，電動馬。達使用的是變速馬達或者變速齒輪箱?！案咚佟眴挝?，其中低速整體單位是燃氣發(fā)動機和壓縮機在一個曲柄套管內。流入和流出離心式壓縮機的流量可以視為“穩(wěn)態(tài)”。系統邊界的效率計算通常是用吸入和排出的噴嘴。含所有內部泄露途徑，尤其是從平衡活塞式或分裂墻滲漏的循環(huán)路徑。，在描述軸承和密封件的摩擦損失以及風阻損失時可以達到98%和99%。制解調器控制系統通過打開一個循環(huán)閥來控制這種情況。出于這個原因，幾乎所

　　

【正文】 pressors and adjusted flow rate by changing the number of machines activated. This capacity and load could be finetuned by speed or by a number of small adjustments (load steps) made in the cylinder clearance of a single unit. As pressors have grown, the burden for capacity control has shifted to the individual pressors. Load control is a critical ponent to pressor operation. From a pipeline operation perspective, variation in station flow is required to meet pipeline delivery mitments, as well as implement pany strategies for optimal operation (., line packing, load anticipation).From a unit perspective, load control involves reducing unit flow (through unloaders or speed)to operate as close as possible to the design torque limit without overloading the pressor or driver The critical limits on any load map curve are rod load limits and HP/torque limits for any given station suction and discharge control generally will establish the units within a station that must be operated to achieve pipeline flow targets. Local unit control will establish load step or speed requirements to limit rod loads or achieve torque control. The mon methods of changing flow rate are to change speed, change clearance, or deactivate a cylinderend (hold the suction valve open). Another method is an infinitestep unloader, which delays suction valve closure to reduce volumetric efficiency. Further, part of the flow can be recycled or the suction pressure can be throttled thus reducing the mass flow while keeping the volumetric flow into the pressor approximately constant. Control strategies for pressors should allow automation, and be adjusted easily during the operation of the particular, strategies that require design modifications to the (for example: rewheeling of a centrifugal pressor, changing cylinder bore, or adding fixed clearances for a reciprocating pressor)are not considered here. It should be noted that with reciprocating pressors, a key control requirement is to not overload the driver or to exceed mechanical limits. Operation The typical steady state pipeline operation will yield an efliciency behavior as outlined in Figure 4. This figure is the result of evaluating the pressor efTiciency along a pipeline steady state operating characteristic. Both pressors would be sized to achieve their best efficiency at 100% flow, while allowing for 10% flow above the design flow. Different mechanical efficiencies have not been considered for this parison. The reciprocating pressor efl39。iciency is derived nom valve efficiency measurements in Ref 5 (Noall, M., W. Couch, 2021) with pression efficiency and losses due to pulsation attenuation devices added. The efficiencies are achievable with low speed pressors. High speed reciprocating pressors may be lower in efficiency. Figure 4: Compressor Efficiency af different flow rates based on operation aiong a steady state pipeline characteristic. Figure 4 shows the impact of the increased valve losses at lower pressure ratio and lower flow for reciprocating machines, while the efficiency of the centrifugal pressor stays more or less constant. Conclusions Efficiency definitions and parison between different types of pressors require close attention to the definition of the boundary conditions for which the efficiencies are defined as well as the operating scenario in which they are employed. The mechanical efficiency plays an important role when efficiency values are used to calculate power consumption. If these definitions are not considered, discussions of relative merits of different systems bee inaccurate and misleading. REFERENCES 1 Kurz . R.. K. Brun. 2021. EfTiciency Definition and Load Management for Reciprocating and Centrifugal C ompressors, ASME Paper GT2OO727O81. 2 Kurz. R., M. Lubomirsky, 2021. Asymttietric Solution for Compressor Station Spare Capacity.ASMt: Paper 202190069. 3 Ohanian. S.. R. Kurz. 2021, Series or Parallel Arrangement in a TwoUnit Compressor Station. JEng for GT and Power. . 4 Kurz. R.. 2021. The Physies of Centrifugal Compressor Performance. Pipeline Simulation Interest Group. Palm Springs. CA. 5 Noall, M.. W. Couch. 2021, Performance and Endurance Tests of Six Mainline Compressor Valves in Natural Gas Compression Service. Gas Machinery Conference. Salt Lake City. UT.