空气压缩机论文中英文对照资料外文翻译文献

PRODUCTION TECHNICAL TRAINING生产培训PRESENTS课程介绍MODULE: Compressors模块：压缩机DESIGNED FORENHANCING OPERATIONS KNOWLEDGE & SKILLS适用于提高操作知识和技能STUDENT PACKAGE学生部分TABLE OF CONTENTS目录If viewing this TOC on a computer, you can move directly to a subject area by pointing with your cursor and single clicking.如果要在计算机上观察这种TOC（目录表），你可以利用光标指点和单击，直接移动到主题区。

I.INTRODUCTION: (6)I．引言II.GAS COMPRESSION AND METHODS OF COMPRESSION (6)II．气体压缩和压缩方法A.C OMPRESSION B ASICS (6)A．压缩基本知识1)Gas Physics (6)1) 气体的物理性质2)Centrifugal Compressor Head Curve (7)2）离心式压缩机压头曲线B.P URPOSES OF C OMPRESSING G AS IN C HEMICAL P ROCESS S YSTEMS (7)B．化学工艺系统中压缩气体的目的C.C OMMON T YPES OF C OMPRESSORS AND T HEIR O PERATION (8)C．常用类别的压缩机及其运转III.CENTRIFUGAL AND AXIAL FLOW COMPRESSORS (9)III. 离心和轴流压缩机A.C ENTRIFUGAL C OMPRESSORS (9)A．离心压缩机1)Uses (9)1）用途2)Major Components and Operation (10)2）主要零部件和运转B.A XIAL F LOW C OMPRESSORS (10)B．轴流压缩机1)Uses (10)1）用途2)Design and Operation (11)2）设计和运转C.C ENTRIFUGAL C OMPRESSOR S EALING/L UBRICATION AND C OMPONENTS..............C．离心压缩机密封/润滑和零部件1)Non-contact Shaft Seals (12)1）非接触轴封a)Labyrinth Seal (12)a）迷宫式密封b)Ported Labyrinth Seal (3)b）带排出孔的迷宫式密封c)Restrictive Ring Seal (4)c）阻流环密封2)Contact Shaft Seals (5)2）接触轴封a)Mechanical Contact Shaft Seal (5)a）机械接触轴封b)Liquid-Film Shaft Seal (6)b）液膜轴封c)Overhead Seal Tank (7)c）高位密封油箱3)Bearings (8)3）轴承a)Journal Bearing (9)a）支持轴承b)Thrust Bearing (9)b）推力轴承c)Tilting-Pad Journal Bearing (9)c）可倾瓦块支持轴承d)Balancing Drums (10)d）平衡盘4)Lube-Oil Systems (13)4）润滑油系统D.C OMMON O PERATING P ROBLEMS IN C ENTRIFUGAL AND A XIAL F LOW C OMPRESSORS C OMPRESSORS (15)D．离心和轴流压缩机的常见运转问题1)Surge Problems (15)1）喘振问题a)Causes of Surge (15)a）喘振原因b)Methods of Correcting Surge (16)b）纠正喘振的方法2)Vibration Problems (16)2）振动问题a)Definitions and General Physics (17)a）定义和一般物理性质b)Monitoring Systems (20)b）监视系统c)Radial Vibration (21)c）径向振动d)Axial Displacement (22)d）轴向位移e)Temperature (23)e）温度f)Vibrating Alarm Systems (23)f）振动报警系统g)Transducer-Failure Alarm (24)g）传感器故障报警h)High-Radial-Vibration Alarm (24)h）大径向振动报警i)Axial-Position Alarm (24)i）轴向位移报警j)High-Temperature Alarm (24)j）高温报警3)Lube and Seal-Oil Systems and Problems (25)3）润滑和密封油系统及问题a)Typical Lube Oil System (25)a）典型的润滑油系统b)Typical Seal Oil System (28)b）典型的密封油系统IV.POSITIVE DISPLACEMENT COMPRESSORS (30)IV. 容积式压缩机A.R ECIPROCATING C OMPRESSORS (30)A．往复式压缩机1)Design Characteristics (30)1）结构特点2)Double-Acting Reciprocating Compressor (39)2）双作用往复式压缩机3)Operation (39)3）操作B.R OTARY C OMPRESSORS (40)B．旋转式压缩机1)Rotary Sliding Vane Compressors (40)1）旋转滑动叶片压缩机2)Rotary Two-Impeller (Lobed) Compressors (41)2）旋转式双叶轮（叶形轮）压缩机3)Rotary Screw Compressor (42)3）旋转式螺杆压缩机4)Rotary Liquid Piston Compressors (43)4）旋转液体活塞压缩机VI.SUMMARY (47)VI．摘要I.INTRODUCTION:引言Compressors are similar in construction to pumps, but operate on different principles since gases are compressible and liquids are not. The primary purpose of compressors is to move air or gases from one place to another and to increase its pressure. Centrifugal and reciprocating compressors are found in many plants. As a Technician, you must be familiar with the design and basic operation of these pieces of equipment and how gases behave when they are compressed.压缩机的结构与泵的类似，但以不同的原理运转，原因是气体可压缩，但液体不能。

空气压缩机名词英语解释时间：2010-7—1 11:40:27，点击：252容积式压缩机positive displacement compressor往复式压缩机（活塞式压缩机）reciprocating compressor回转式压缩机rotary compressor滑片式压缩机sliding vane compressor单滑片回转式压缩机single vane rotary compressor滚动转子式压缩机rolling rotor compressor三角转子式压缩机triangle rotor compressor多滑片回转式压缩机multi-vane rotary compressor滑片blade旋转活塞式压缩机rolling piston compressor涡旋式压缩机scroll compressor涡旋盘scroll固定涡旋盘stationary scroll，fixed scroll驱动涡旋盘driven scroll，orbiting scroll斜盘式压缩机（摇盘式压缩机）swash plate compressor斜盘swash plate摇盘wobble plate螺杆式压缩机screw compressor单螺杆压缩机single screw compressor阴转子female rotor阳转子male rotor主转子main rotor闸转子gate rotor无油压缩机oil free compressor膜式压缩机diaphragm compressor活塞式压缩机reciprocating compressor单作用压缩机single acting compressor双作用压缩机double acting compressor双效压缩机dual effect compressor双缸压缩机twin cylinder compressor闭式曲轴箱压缩机closed crankcase compressor开式曲轴箱压缩机open crankcase compressor顺流式压缩机uniflow compressor逆流式压缩机return flow compressor干活塞式压缩机dry piston compressor双级压缩机compound compressor多级压缩机multistage compressor差动活塞式压缩机stepped piston compound compressor, differential piston compressor 串轴式压缩机tandem compressor，dual compressor截止阀line valve, stop valve排气截止阀discharge line valve吸气截止阀suction line valve部分负荷旁通口partial duty port能量调节器energy regulator容量控制滑阀capacity control slide valve容量控制器capacity control消声器muffler联轴节coupling曲轴箱crankcase曲轴箱加热器crankcase heater轴封crankcase seal, shaft seal填料盒stuffing box轴封填料shaft packing机械密封mechanical seal波纹管密封bellows seal转动密封rotary seal迷宫密封labyrinth seal轴承bearing滑动轴承sleeve bearing偏心环eccentric strap滚珠轴承ball bearing滚柱轴承roller bearing滚针轴承needle bearing止推轴承thrust bearing外轴承pedestal bearing臼形轴承footstep bearing轴承箱bearing housing止推盘thrust collar偏心销eccentric pin曲轴平衡块crankshaft counterweight, crankshaft balance weight 曲柄轴crankshaft偏心轴eccentric type crankshaft曲拐轴crank throw type crankshaft连杆connecting rod连杆大头crank pin end连杆小头piston pin end曲轴crankshaft主轴颈main journal曲柄crank arm，crank shaft曲柄销crank pin曲拐crank throw曲拐机构crank-toggle阀盘valve disc阀杆valve stem阀座valve seat阀板valve plate阀盖valve cage阀罩valve cover阀升程限制器valve lift guard阀升程valve lift阀孔valve port吸气口suction inlet压缩机气阀compressor valve吸气阀suction valve排气阀delivery valve圆盘阀disc valve环片阀ring plate valve簧片阀reed valve舌状阀cantilever valve条状阀beam valve提升阀poppet valve菌状阀mushroom valve杯状阀tulip valve缸径cylinder bore余隙容积clearance volume附加余隙（补充余隙）clearance pocket活塞排量swept volume，piston displacement理论排量theoretical displacement实际排量actual displacement实际输气量actual displacement, actual output of gas 气缸工作容积working volume of the cylinder活塞行程容积piston displacement气缸cylinder气缸体cylinder block气缸壁cylinder wall水冷套water cooled jacket气缸盖(气缸头) cylinder head安全盖(假盖）safety head假盖false head活塞环piston ring气环sealing ring刮油环scraper ring油环scrape ring活塞销piston pin活塞piston活塞行程piston stroke吸气行程suction stroke膨胀行程expansion stroke压缩行程compression stroke排气行程discharge stroke升压压缩机booster compressor立式压缩机vertical compressor卧式压缩机horizontal compressor角度式压缩机angular type compressor对称平衡型压缩机symmetrically balanced type compressor空压机英文菜单及报警信息的中英文对照序号英文报警信息中文报警名称1 Emergencey Stop 紧急制动2 Communication Control 通讯控制3 Invalid Access Code 进入码错误4 No fault stored 无故障信息存储5 No fault reset 无复位指示6 No service indicated 无维修指示7 Remote start enable 远程启动8 Remote start enables 远程停机9 Stop machine first 先停机10 Fan motor fault 风扇电机故障11 High air pressure 空气压力过高12 High oil temp fault 油温过高13 Main motor fault 主电机故障14 Pressure probe fault 压力探测器故障15 Rotation fault 转向故障16 Star/delta fault Y/△故障17 Temperature probe fault 温度探测器故障18 Change air filter 更换空气过滤器19 Chang reclaimer element 更换油分离器滤芯20 High oil 油温过高21 Service due 技术服务时间到22 Max overpress 最高过压（自己复位)23 Total 总时数24 Hours on load 负载时数25 Max。

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After testing the system, our IQAir Authorized Installer will enter the test results intoa personalized owner’s certificate which certifies your home as one of the healthiest homes in America.IQAir’s Whole-House Air Cleaning System Wins Reviewboard’s Product of the YearWritten by Philip Ferreira, Editor-in-Chief of Reviewboard MagazineThe home we tested the Perfect 16 in was immaculate, but like many homes it had a hidden problem –unhealthy indoor air. We used advanced laser particle counting equipment before and after installation so that our readers could see what they could really expect if they had this system installed in their own home.The Perfect 16 delivers the highest level of air cleaning effectiveness available to homeowners. Reviewboard tested the system in a real home, not in a laboratory, and we saw an almost 95% improvement in air quality.The Perfect 16 retrofits into existing heating and/or air conditioning (HV AC) systems. 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原文Mitigating Explosion Risks in High Pressure Air Injection CompressorsAbstractThis paper describes research undertaken by Encore Acquisition Company and the University of Calgary regarding the flammability safety of synthetic lubricants used in Encore’s compressors in their high pressure air injection (HPAI) projects in Southeastern Montana. With over 2,270 e3m (ST)/d (80MMscfd) of installed air compression capacity discharging at pressures of 31.0 to 34.5 MPa (4,500 to 5,000 psi), a critical aspect of this project is the safe and uninterrupted operation of the compressors. Experience gained by Encore and other HPAI operators shows that the reaction of high pressure air with compressor lubricants in high temperature interstage and discharge regions of the compressors can be a source of trouble (destructive overpressures), even when synthetic diester-based lubricants are employed.Using an Accelerating Rate Calorimeter (ARC), samples of fresh and used synthetic lubricants were heated in the presence of air at initial pressures up to 34.5 MPa (5,000 psi). Self-heating rates and pressure responses were measured.The results highlighted the significant effect of pressure on auto-ignition temperature. Most significantly, the auto-ignition temperature of the diester-based lubricant dropped from the manufacturer’s reported level of 410?C (770?F) at atmospheric pressure to 180?C (365?F) at pressures in the range of 17.2 to 34.5 MPa (2,500 to 5,000 psi). Also, the auto-ignition temperature of used (oxidized) synthetic lubricant was further reduced to values close to the operating temperature levels of the compressors. Finally, it was noted that the auto-ignition temperatures for different brands of diester-based lubricants were all very similar.The significance of this study is not only in the temperature data, but also in the discussion of several significant changes that Encore made to the design and operation of their high pressure air compressors as a result of this study. This information will assist future HPAI operators in designing safe and reliable air compression systems. IntroductionImproved oil recovery of conventional light oils by high pressure air injection (HPAI) is becoming a well known process. With increasing oil demand and dwindling primary and secondary production-based reserves, more producers are showing increasing interest in HPAI. Typical examples of such increasing interest include Encore’s eight injector 17 e3m (ST)/d (6 MMscfd) HPAI project initiated in 2002 in their Pennel Unit that has since expanded to 850 e3m (ST)/d (30 MMscfd) with an ultimate design of 1,700 e3m (ST)/d (60 MMscfd). Air has been continually injected at 34.5 MPa (5,000 psi) for four years in the original portion of the flood. In addition, a new 566 e3m3(ST)/d (20 MMscfd)HPAI project was initiated in the Cedar Creek-Little Beaver East Field located on the Montana/North Dakota border in 2004. This project has 28 injection wells and is operated at 31.0 MPa (4,500psi). Figure 1 isa map indicating Encore’s presence in the Cedar Creek Anticline [over 160 km (100 miles) long] showing the HPAI and waterflood projects sites.Safe and uninterrupted compressor operation is the most important factor in the successful implementation of every HPAI project. To improve operational safety and reliability, ester-based synthetic lubricating oils are widely used in HPAI compressors. The advantages of these synthetic lubricants over petroleum-based lube oils include higher flash point, higher auto-ignition temperature (1, 2)(AIT) and higher detergency (low residue) . These properties significantly minimize explosion risks during compressor operation. The standard test manufacturers use to measure the auto-ig (3) nition temperatures of these lube oils, ASTM E-659 and ASTM (4)D-2155 , are performed at atmospheric pressure. The flammability ranges of hydrocarbon fuels are known to widen with an (5)increase in pressure . Thus, operating below the manufacturer’s recommended AIT would not eliminate the potential risk for an explosive reaction between the air and the compressor lube oil. This was thought to occur in an Encore Acquisition’s HPAI facility in Southeastern Montana.The objective of this work was to investigate the oxidation behaviour of fresh and used (partially oxidized) synthetic ester-based lube oils, Anderol 750 and Anderol 555, at different reaction pressures. The results were compared to those of other ester-based synthetic lube oils; namely, Shell Corena DE 150 and a custom formulated ester-based synthetic oil from Summit Lubricants. The safety improvements Encore implemented based on the results of this investigation are also discussed.Applicability of ARC tests to lube oilThe accelerating rate calorimeter was originally developed for the evaluation of thermal hazard of substances. Detailed description of the ARC apparatus, its theory, experimental procedure and (6-8)data analysis are available in the literature .The classical analysis of ARC test data is based on a simple singular decomposition reaction of the form A → Pro ducts, with the basic assumption that the reaction goes to completion, and the products do not interfere with the reaction mechanism. If the above exothermic reaction occurs adiabatically, all the reaction heat will be used in raising the product’s tempera ture. The resulting selfheat rate can be approximated by the following (6) :()1000d --⎪⎪⎭⎫ ⎝⎛--=n F n FF C T T T T T T k dt T （1） The above equation can be rearranged to the form below (with the pseudo-rateconstant 10-*=n kC k ). ()()dtdT T T T T k n F n F ⋅--=*-10 （2） At the correct reaction order, k * has the same functional dependence on temperature as k*. Hence, experimental thermal decomposition data is used to obtain k* and a graphical iteration is used on the Arrhenius model below to obtain the best fit for the reaction order and the kinetic parameters (6) .()()⎪⎭⎫ ⎝⎛-=-*T R E AC k n 1ln ln 10α （3） Unlike the singular decomposition reaction on which ARC theory is based, formulated synthetic ester-based lube oils often contain various additives to improve their oxidative stability (9.10). The oxidation reactions of these lube oils and other complex mixtures, such as crude oils, seldom go to completion during an ARC test either due to oxygen availability or formation of refractory residual material, even in the presence of excess air. In addition, the observed experimental data such as dT/dt and T need F to be corrected for the thermal inertia of the reaction cell. While self-heating rates upwards of 1,000?C/min are recorded, experimental heater power supply data verified that the ARC is not able to closely track actual self-heating rates in excess of 15 to 18?C/minute. Therefore, measured maximum heating rates of greater than the 15 to 18?C/minute range should be viewed as qualitative indications of elevated oxidation rates rather than as the absolute SHR values. In spite of these limitations, ARC tests have provided useful values for the kinetics parameters for even complex mixtures such as crude oil (11) .Experimental ProcedureMaterialsThe synthetic ester-based lube oils Anderol 750 and Anderol 555 used in this work are of ISO viscosity grade of 150 and 100 , respectively, supplied by Encore. To investigate the effect of inservice oil use on the potential risk of auto-ignition, both fresh and used (partially oxidized) oils were tested. The used oils were sampled from different points along the compressor train. Table 1 summarizes the oil type, location description and the ARC test number in which the oils were used. The Anderol 750 sample used in Test 3 and Test 4 was taken from the final stage scrubber which is after the pulsation bottle and the cooler, while the one used in Test 5 and Test 6 was from the pulsation bottle directly after the final compression stage. Thus, the former Anderol 750 sample had been subjected to a high temperature and pressure for a longer duration. The Anderol 555 used in Tests 9 and 10 was obtained from the last compression stage with a normal operating temperature and pressure of about 149?C (300?F) and 31.0 MPag (4,500 psig). The Shell Corena DE 150 is a 150-ISO viscosity grade oil consisting of about 90 – 99 mass% synthetic esters, and 1 – 10 mass% proprietary polymer additives . The Summit oil is a custom formulated ester-based synthetic lube oil for high pressure air compressors.ARC test ProcedureThe ARC tests were performed in a modified CSI-ARC apparatus. Briefly, the ARC consists of the calorimeter unit with the sample-holder (see Figure 2), power supply, temperature control and main processor units. The main processor is used for setting the run conditions and controlling the experiment. It also processes the results to obtain kinetic and thermal parameters from the experimental data. The two ARCs at the University of Calgary have been extensively and specially modified for reliable operation up to 41.4MPa (6,000 psi), while tracking highly exothermic combustion reactions. They use specially developed 9 cm reaction cells made of Hastelloy-Cweighing approximately 24.3 gm. The instrument is calibrated and drift-checked before each run.In each test, about 0.2 g (Table 1) of the synthetic lube oil sample was loaded in the reaction cell and mounted in the ARC heating assembly, as shown in Figure 2. The ARC tests were performed in a closed mode in which the oil-loaded reaction cell was filled with air to the desired pressure and sealed. No mass exchange occurs across the cell boundary during the test; the cell boundary includes the volume of tubing connection to the pressure gauge. The ARC system was heated to the starting temperature of 50?C and operated in a heat-wait-search (HWS) mode. In the HWS operating mode, the sample was subjected to repeated cycles consisting of heating in steps of 5?C, followed by a 20 minute wait period (for thermal equilibration between the lube oil sample and the reaction cell) and then a search for self-heating. During the latter, the microprocessor searches for a self-heat rate (SHR) greater than a preset value of 0.025?C/min. Once an exotherm is detected, the exothermic (oil oxidation) reaction is allowed to proceed adiabatically. Four test pressures were selected in order to investigate the effect of pressure and to reflect the interstage pressures in the real operation.Results and Discussion temperature and Pressure Profiles The ARC test conditions used for the two synthetic lube oils, Anderol 750 and Anderol 555, are summarized in Table 1. Typical accelerating rate calorimeter responses for the HWS test method are shown in Figures 3 and 4 for fresh Anderol 750 tested at 17.2 MPag (2,500 psig) and at 34.5 MPag (5,000 psig), respectively. The temperature profiles show the ramp of stepwise temperature increase due to the HWS scheme with the occurrence of an exothermic reaction (self-heat) beginning after about 950 min at 180?C (Figure 3). No additional exotherms were detected in the subsequent HWS steps until the maximum operating temperature of the system (500?C) was attained and the system automatically shuts down resulting in the observed rapid cooling. The pressure profile closely followed the temperature profile. The rates of change in temperature and pressure during the exotherm are shown as insets in the above figures. At 34.5 MPag (5,000 psig) test pressure(Figure 4), the major exotherm occurred earlier but at the same starting temperature as the 17.2 MPag (2,500 psig) test (850 min, 180?C).Based on the temperature vs. time responses as shown in Figures 3 and 4, the self-heat rates due to the exothermic reactions of the lube oil and air at different initial pressures are presented in Figures 5 and 6 for the fresh and the used Anderol 750, respectively. Similar SHR plots for fresh and used Anderol 555 are shown in Figure 7, while Figure 8 shows the exothermic self-heating of the Corena DE 150 oil and the custom formulated Summit lubricant. The regions with no data points in the above figures indicate the absence of any detectable exothermic activity in those temperature ranges.Self-heat Rates and AItThe SHR plots in Figures 5 and 6 show a characteristic ramp-up in exothermic activity at the lower temperature end of the data (180–195?C and 155 – 165?C for the fresh and the used Anderol 750, respectively) followed by two distinct pressure dependent behaviours. For the 17.2 MPag (2,500 psig) and the 34.5 MPag (5,000 psig)runs, the initial portion of the self-heat region is followed by an essentially instantaneous 20-330 fold increase in the SHR, and an eventual decline in the latter. Following the initial SHR phase, the runs at 500 psig and 1,000 psig show phases of increasing SHR [albeit much lower than the ones at 17.2 and 34.5 MPag (2,500 and 5,000 psig)] followed by the final decline in the SHR.The self-heat rates are relatively insensitive to the test pressure for self-heat rates of less than 0.3?C/minute. The initial energy generation is believed to be associated with liquid phase reactions for which there is an excess of oxygen and reactive hydrocarbon in the liquid phase. Once the self-heat rates approach a certain level, the liquid phase reactions become controlled by the rate of transfer of oxygen (i.e. on the oxygen partial pressure in the vapour phase and mass transfer resistance), as well as on the concentration of reactive hydrocarbon in the liquid phase. In the absence of the onset of a reaction zone involving the vapour phase, the oxidation reactions responsible for the energy generation will be associated with liquid phase reactions and will terminate when all of the reactive liquid phase hydrocarbon fractions are consumed. This appears to be the case for the 3.4 and 6.9 MPag (500 and 1,000 psig) tests.A comparison of Figures 5 and 6 reveal that under similar test conditions, the oxidized oil starts to react earlier, and at a lower temperature than the fresh oil. This is believed to be due to the formation of liquid phase oxidized species under the in-service conditions of the commercial compressors. The oxidized species (9)participate in a number of liquid phase free radical reactions . The above observations are also true for Anderol 555 (Figure 7).The shape of the self-heat rate curves is indicative of different mechanisms controlling the overall heat generation rate at a given temperature. At the lower temperature regions, the SHR traces exhibit a behaviour which can be approximated using an Arrhenius-type expression which implies a semi-logarithmic relationship between self-heat rate and inverse absolute temperature. This behaviour will appear as a straight line on the self-heat rate plots shown in Figures 5 to 8, inclusive. Over other temperature ranges, the self-heat rates are relatively insensitive to temperature which suggests that mass transfer to, and within the liquid/solid phase, is dominating the self-heating rate.Figure 8 shows that the exothermic self-heating of the Corena DE-150 oil started at essentially the same temperature as the Anderol oils, but the maximum SHR and the final temperature of the major exotherms were significantly lower. The reported AIT of the (13)Corena DE 150 is 443?C . The custom formulated Summit lube oil showed the highest on-set temperature of the major exotherms (195?C) and a final temperature of the major exotherm similar to that of the Anderol oils.The rapid increase in SHR observed at 17.2 MPag (2,500 psig) and at 34.5 MPag (5,000 psig) is believed to be a violent gas-phase reaction, i.e., ignition of a combustible vapour phase of the lube oil-air mixture. In order to initiate and sustain a vapour phase burn, the concentration of hydrocarbon in the vapour phase must be within the flammable region and the temperature must be above the value required for auto-ignition. In the absence of liquid phase compositional data andphase behaviour relationships for the modified components, it is impossible to accurately predict the composition of the vapour phase at the time of initiation of the vapour burn. Based on the assumption that increased test pressure implies lower hydrocarbon vapourization rates at a given temperature, the moles of hydrocarbon in the vapour phase will decrease and the amount of hydrocarbon remaining in the liquid phase will remain higher with increasing total pressure. For a given initial concentration of oxygen in the injected air, the amount of oxygen available in the vapour phase will increase with increasing total pressure. As a result of the combined pressure effects, it is surmised that when the temperature within the reaction cell is above that required for ignition, the hydrocarbon concentrations in the vapour space for the two lower pressure tests falls in the fuel rich region, while the two higher pressure tests fall in the flammable region. Once the vapour phase burn is initiated, the greater amount of heat released for the 34.5 MPag (5,000 psig) test reflects the increased amount of oxygen available to sustain the combustion reaction.The amount of heat generated during the violent vapour phase reaction and the associated pressure increases could lead to a hazardous situation in field operations. It is important to note that these reactions started at <190?C for both the fresh and the oxidized Anderol and the Corena DE 150 lube oils. This temperature is much lower than the AIT of 410?C (ASTM E-659 test at 1 atmosphere) (12)and is well within the nominal operating range (–15 to 230?C) reported by the Anderol manufacturer. It is similarly lower than the (13)reported 443?C AIT of the Corena DE 150 oil . Therefore, it is necessary for HPAI air compressor operators to determine the AITs for their lubricating oils under real operating conditions. The effect of pressure on SHR of fresh and used Anderol 555 at 17.2 MPag (2,500 psig) and at 34.5 MPag (5,000 psig) (Figure 7) are similar to those of Anderol 750. Both Anderol 555 and Anderol 750 have similar AITs and flash points; the former is less viscous at the same (12)temperature .In addition to pressure, the auto-ignition temperature can also be affected by the heating rate. Figure 9 shows the pressurized differential scanning calorimeter (PDSC) response of used Anderol 750 tested at 1,000 psi. At the low heating rate (0.15?C/min), the exothermic reaction occurred at a lower temperature and to a much lower extent compared to the reaction at the higher heating rate (5?C/min). The average sample heating rate during the HWS cycles in the ARC tests was about 0.16?C/min.Termal and Kinetic ParametersThe experimental SHR data was used in conjunction with Equations (1) to (3) to obtain the kinetic parameters of the lube oil-air reactions. Due to the previously discussed limitations in the applicability of the ARC test procedure to the lube oils, only the initial exotherms were fitted with the above equations. The initial exotherms are believed to play a significant role in generating the heat necessary for the subsequent violent vapour phase reactions to occur. No significant changes in oxygen or oil concentration occurred during the initial exotherms; hence, zero order kinetics were found to be appropriate. The calculated Arrhenius activation energy, E , and other thermal parameters of the test systems are summarized in Table 2.Relevance to oilfield hPAI CompressorsThe polarity of ester molecules results in strong intermolecular attraction and low volatility of ester-based lube oils. Due to the low volatility of the ester-based synthetic lube oils, the high compressor operating pressures and the large air throughputs involved in HPAI air compression systems, it is unlikely that sufficient lube oil will evaporate to form a combustible vapour with the compressed air in the process lines. However, combustible mixtures can still form at the compressed air-lube oil interface or in dead spaces within the process streams due to the heat generated by the initial exotherm. Therefore, accumulations of lubricating oils, especially in stagnant regions in the compression system, must be avoided.Safety Improvements at encore Compressor StationSafety is a prime concern at Encore’s HPAI compressor station and modifications to existing and new facilities are always being examined. Early in Encore’s experience with high pressure air compression, focus was given to oil holdup based on offsite operators’ experience. This means that compressor cylinders were rotated 90 degrees if this created better oil drainage. Explosions in air compression facilities have been attributed to the presence of excessive amounts of ester-based lubricant in the compressed air system . Pulsation bottle baffles had holes in the bottom of the plates to allow drainage. All pipe locations that could pool compressor oil were eliminated. This was a good start, however, problems were encountered when the compressors were turned down in rate. It was discovered that the air velocity was key in moving used compressor oil away from the heat source and in dissipating the exothermic heat generated in oil oxidation reactions. In addition, flammability of the vapour phase is very dependent on air velocity. The vapour phase is believed to be fuel lean at normal discharge rates, but it can enter the flammable region in regions where oil is in contact with dead air. Rapid pressurization of areas where oil may be trapped should be avoided. For an ideal gas under adiabatic conditions, the temperature following pressurization equals the inlet absolute temperature times the specific heat ratio. Assuming a specific heat ratio of 1.4 for air and an auto-ignition temperature of 180?C, an inlet air temperature of 50?C combined with a rapid re-pressurization could cause the temperature to exceed the AIT. For the above reasons, Encore has imposed a turndown limit for its compressors based on air velocity considerations.In theory, depressurization of the space above a pool of lubricating oil may also lead to the formation of a flammable mixture. At a given temperature, the lube oil volatility will increase as oxygen partial pressure decreases, so the vapour phase may enter the flammable region from the lean side. Therefore, it is necessary to ensure that pools of oil are not trapped in portions of the piping that are at high temperatures. Operating temperatures for each compression stage should be limited when designing a high pressure air compression facility. This limit will be based on the compressor oil’s AIT at the operating pressure, plus a safety factor accounting for further oil degradation. Lubrication should not be an afterthought of the compression design, but an integral part of it.The final lesson learned from Encore’s field experience is that plant maintenance regarding compressor oil buildup is important. Facilities should be designed withclean-out access ports to bottles, coolers and scrubbers such that they can be easily cleaned on a regular basis. Buildup of carbonaceous deposits and compressor oil can lead to an ignition in the piping with potentially dangerous consequences. ConclusionAccelerating rate calorimeter tests of fresh and used ester-based synthetic lubricating oils, Anderol 750 and Anderol 555, at 3.4 to 34.5 MPag (500 to 5,000 psig) shows that:1. At pressures of 17.2 to 34.5 MPag (2,500 to 5,000 psig), the auto-ignitiontemperature is less than 190?C — well within the nominal operating range of the oil. Hence, it is essential to test the AIT of the lubricating oils for HPAI air compressors at the anticipated operating pressures.2. Used (partially oxidized) oil showed lower AIT compared to identical freshoil.3. Increasing the heating rate of an oxidized Anderol 750 sample delayed theoccurrence of auto-ignition to a higher temperature, and led to greater heat generation.4. The different fresh synthetic oils tested gave a similar response to the ARCheat-wait-search scheme. Test pressure and the state of the lube oil (fresh or oxidized) has a greater influence over the oil type.5. The maximum operating temperatures of HPAI air compressors should bebased on the AIT of the compressor oil at the operating temperature. The compressor facilities should be designed with clean-out access ports to bottles, coolers and scrubbers such that they can be easily cleaned on a regular basis. AcknowledgementsThe authors acknowledge Encore Acquisition Company and Continental Resources for the permission to publish this work. We also thank K. van Fraassen, D. Marentette, M. Hancock and J. Li for the experimental work on ARC and PDSC.NomeNClAtuReA = pre-exponential (Arrhenuis) factorC = reactant concentrationE a = activation energyk = reaction rate constantk* = pseudo-reaction rate constant (10k n C )T = temperaturet = timeSubscripts0 = initial conditionsF = final conditionsAcronymsAIT = auto-ignition temperatureARC = accelerating rate colorimeterCSI = Columbia scientific industriesHPAI = high pressure air injectionHWS = heat-wait-searchNM = not measuredPDSC = pressurized differential scanning calorimeterSHR = self-heat rate(s)第二篇：减轻高压注气压缩机爆炸风险摘要这篇文章阐述了由安可收购公司和卡尔加里大学共同进行的一项研究，这是关于安可公司在蒙大拿州东南部压缩机高压注气（HPAI）工程的合成润滑油燃烧安全性的研究。

中英文对照外文翻译空压机使用及维护说明书1 安全预防措施1.1 一般信息压缩空气和电都很危险。

在对空压机进行任何维前，一定要切断、锁住和标记电源并将空压机中的全部释放。

操作过程中所有保护措施必须到位并将门/盖关闭。

空压机的安装必须符合公认的电气操作规范，并符地的卫生与安全规定。

请只使用安全溶剂清洁空压机和辅助设备。

1.2 压缩空气一定要使机器在额定的压力下运作，而且要让所有相关人员都知道该额定压力。

安装在机器上的所有空气压力设备或与该机器相连的所有空气压力设备都必须有安全工作压力额定值并且该额定值不得低于机器的额定压力。

如果有几台压缩机与一个公用下游设备连接，则必须安装有效的止回阀和隔离阀，并用工作程序控制，从而使一台机器不会被另一台机器意外加压或过度加压。

如果安全阀安装在隔离阀和空压机之间，则它必须具有足够的容量用于释放空压机中的空气。

由于排放出来的空气中含有少量的压缩机润滑油，因此要注意下游设备的适应性。

如果排出的空气最后排放在一个有限的空间内，则必须提供足够的通风设备。

使用不带金属保护装置的塑料壳体过滤器会有危险。

影响其安全的因素可能是合成润滑油，也可能是矿物油中使用的添加剂。

金属碗应该用于高压系统。

压缩空气决不能同任何形式的呼吸设备或口罩直接相连。

每次使用压缩空气时都必须使用适当的个人保护设备。

所有含压部件，尤其是弹性软管及其接头，都必须定期检查，做到毫无缺陷，如发现缺陷，必须根据本《手册》的说明进行更换。

如处置不当，压缩空气可能会带来危险。

操作之前要切记将系统中的压力全部释放，并确保机器不能意外启动。

要避免身体与压缩空气接触。

应定期检查位于分离槽内的安全阀是否工作正常。

无论何时通过减压安全阀释放压力，都是由于系统装置中压力过高。

应立即查找压力过高的原因。

1.3 原料机器制造过程中使用了下述材料，如使用不当，可能会危害身体健康：防护性润滑脂防锈剂空压机冷却剂详细信息请参阅冷却剂材料安全数据表。

压缩机英文资料压缩机英文资料The latter two are used extensively in the design of refrigeration equip ment. If you place two objects together so that they remain touching, and one is hot and one is cold, heat will flow from the hot object into the cold object. This is called conduction. This is an easy concept to grasp and is rather like gravitational potential, where a ball will try to roll down an inclined plane. If you were to fan a hot plate of food it w ould cool somewhat. Some of the heat from the food would be carried away by the air molecules. When heat is transferred by a substance in the ga seous state the process is called convection. And if you kicked a glowing hot ember away from a bonfire, and you watched it glowing dimmer and dimmer, it is cooling itself by radiating heat away. Note that an object doesn't�t have to be glowing in order to radiate heat, all things use c ombinations of these methods to come to equilibrium with their surroundi ngs. So you can see that in order to refrigerate something, we must finda way to expose our object to something that is colder than itself andnature will take over from there. We are getting closer to talking about the actual mechanics of a refrigerating system, but there are some othe r important concepts to discuss first.The States of MatterThey are of course; solid, liquid and gas. It is important to note that heat must be added to a substance to make it change state from solid to liquid and from liquid to a gas. It is just as important to note that he at must be removed from a substance to make it change state from a gas t o a liquid and from a liquid to a solid.The Magic of Latent HeatLong ago it was found that we needed a way to quantify heat. Something m ore precise than "less heat" or "more heat" or "a great deal of heat" wa s required. This was a fairly easy task to accomplish. They took 1 Lb. of water and heated it 1 degree Fahrenheit. The amount of heat that was required to do this was called 1 BTU (British Thermal Unit). The refriger ation industry has long since utilized this definition. You can for exam ple purchase a 6000 BTUH window air conditioner. This would be a unit th at is capable of relocating 6000 BTU's of heat per hour. A larger unit capable of 12,000 BTUH could also be called a one Ton unit. There are 12, 000 BTU's in 1 Ton.To raise the temperature of 1 LB of water from 40 degrees to 41 degrees would take 1 BTU. To raise the temperature of 1 LB of water from 177 deg rees to 178 degrees would also take 1 BTU. However, if you tried raising the temperature of water from 212 degrees to 213 degrees you would not be able to do it. Water boils at 212 degrees and would prefer to change into a gas rather than let you get it any hotter. Something of utmost im portance occurs at the boiling point of a substance. If you did a little experiment and added 1 BTU of heat at a time to 1 LB of water, you woul d notice that the water temperature would increase by 1 degree each time. That is until you reached 212 degrees. Then something changes. You woul d keep adding BTU's, but the water would not get any hotter! It would ch ange state into a gas and it would take 970 BTU's to vaporize that pound of water. This is called the Latent Heat of Vaporization and in the cas e of water it is 970 BTU's per pound.So what! you say. When are you going to tell me how the refrigeration ef fect works? Well hang in there, you have just learned about 3/4 of what you need to know to understand the process. What keeps that beaker of wa ter from boiling when it is at room temperature? If you say it's because it is not hot enough, sorry but you are wrong. The only thing that keep s it from boiling is the pressure of the air molecules pressing down on the surface of the water. When you heat that water to 212 degrees and th en continue to add heat, what you are doing is supplying sufficient ener gy to the water molecules to overcome the pressure of the air and allow them to escape from the liquid state. If you took that beaker of water t o outer space where there is no air pressure the water would flash into a va pour. If you took that beaker of water to the top of Mt. Everest wh ere there is much less air pressure, you would find that much less heat would be needed to boil the water. (it would boil at a lower temperature than 212 degrees). So water boils at 212 degrees at normal atmospheric pressure. Lower the pressure and you lower the boiling point. Therefore we should be able to place that beaker of water under a bell jar and hav e a vacuum pump extract the air from within the bell jar and watch the w ater come to a boil even at room temperature. This is indeed the case!A liquid requires heat to be added to it in order for it to overcome theair pressure pressing down on its' surface if it is to evaporate into a gas. We just learned that if the pressure above the liquids surface is reduced it will evaporate easier. We could look at it from a slightly di fferent angle and say that when a liquid evaporates it absorbs heat from the surrounding area. So, finding some fluid that evaporates at a handi er boiling point than water (IE: lower) was one of the first steps requi red for the development of mechanical refrigeration.Chemical Engineers spent years experimenting before they came up with the perfect chemicals for the job. They developed a family of hydroflourocarbon refrigerants which had extremely low boiling points. These chemica ls would boil at temperatures below 0 degrees Fahrenheit at atmospheric pressure. So finally, we can begin to describe the mechanical refrigerat ion process.Main ComponentsThere are 4 main components in a mechanical refrigeration system. Any co mponents beyond these basic 4 are called accessories. The compressor isa va pour compression pump which uses pistons or some other method to compress the refrigerant gas and后两个是广泛用于制冷设备的设计。

毕业设计外文资料翻译附件1：外文资料翻译译文一维多级轴流压缩机性能的解析优化摘要 对多级压缩机的优化设计模型，本文假设固定的流道形状以入口和出口的动叶绝对角度，静叶的绝对角度和静叶及每一级的入口和出口的相对气体密度作为设计变量，得到压缩机基元级的基本方程和多级压缩机的解析关系。

用数值实例来说明多级压缩机的各种参数对最优性能的影响。

关键词 轴流压缩机 效率 分析关系 优化1 引言轴流式压缩机的设计是工艺技术的一部分，如果缺乏准确的预测将影响设计过程。

至今还没有公认的方法可使新的设计参数达到一个足够精确的值，通过应用一些已经取得新进展的数值优化技术，以完成单级和多级轴流式压缩机的设计。

计算流体动力学（CFD ）和许多更准确的方法特别是发展计算的CFD 技术，已经应用到许多轴流式压缩机的平面和三维优化设计。

它仍然是使用一维流体力学理论用数值实例来计算压缩机的最佳设计。

Boiko 通过以下假设提出了详细的数学模型用以优化设计单级和多级轴流涡轮：（1）固定的轴向均匀速度分布（2）固定流动路径的形状分布，并获得了理想的优化结果。

陈林根等人也采用了类似的想法，通过假设一个固定的轴向速度分布的优化设计提出了设计单级轴流式压缩机一种数学模型。

在本文中为优化设计多级轴流压缩机的模型，提出了假设一个固定的流道形状，以入口和出口的动叶绝对角度，静叶的绝对角度和静叶及每一级的入口和出口的相对气体密度作为设计变量，分析压缩机的每个阶段之间的关系，用数值实例来说明多级压缩机的各种参数对最优性能的影响。

2 基元级的基本方程考虑图1所示由n 级组成的轴流压缩机, 其某一压缩过程焓熵图和中间级的速度三角形见图2和图3，相应的中间级的具体焓熵图如图4，按一维理论作级的性能计算。

按一般情况列出轴流压缩机中气体流动的能量方程和连续方程,工作流体和叶轮的速度。

在不同级的轴向流速不为常数，即考虑i j u u ≠,i j c c ≠ (i j ≠) 时的能量和流量方程。

中英文对照资料外文翻译文献离心式和往复式压缩机的工作效率特性往复式压缩机和离心式压缩机具有不同的工作特性，而且关于效率的定义也不同。

本文提供了一个公平的比较准则，得到了对于两种类型机器普遍适用的效率定义。

这个比较基于用户最感兴趣的要求提出的。

此外，对于管道的工作环境影响和在不同负载水平的影响给出了评估。

乍一看，计算任何类型的压缩效率看似是很简单的：比较理想压缩过程和实际压缩过程的工作效率。

难点在于正确定义适当的系统边界，包括与之相关的压缩过程的损失。

除非这些边界是恰好定义的，否则离心式和往复式压缩机的比较就变得有缺陷了。

我们也需要承认，效率的定义，甚至是在评估公平的情况下，仍不能完全回应操作员的主要关心问题：压缩过程所需的驱动力量是什么？要做到这一点，就需要讨论在压缩过程中的机械损失。

随着时间的推移效率趋势也应被考虑，如非设计条件，它们是由专业的流水线规定，或者是受压缩机的工作时间和自身退化的影响。

管道使用的压缩设备涉及到往复式和离心式压缩机。

离心式压缩机用燃气轮机或者是电动马达来驱动。

所用的燃气轮机，总的来说，是两轴发动机，电动马达使用的是变速马达或者变速齿轮箱。

往复压缩机是低速整体单位或者是可分的“高速”单位，其中低速整体单位是燃气发动机和压缩机在一个曲柄套管内。

后者单位的运行在750-1,200rpm 范围内（1,800rpm 是更小的单位）并且通常都是由电动马达或者四冲程燃气发动机来驱动。

效率要确定任何压缩过程的等熵效率，就要基于测量的压缩机吸入和排出的总焓(h)，总压力(p)，温度(T)和熵(s)，于是等熵效率s η变为：)],(),([)],(),([suct suct disch disch suct suct suct disch s T p h T p h T p h s p h --=η (Eq.1)并且加上测量的稳态质量流m ，吸收轴功率为：)],(),([.suct suct disch disch m T p h T p h m p -=η (Eq.2)考虑机械效率m η。

4.7压缩机机组安装Installation of compressor4.7.1就位前应做好下列工作：the following work should be done beforecompressor emplacement——将汽轮机的凝汽器初步就位，其安装标高宜比设计标高低20mm～25mm；Place the turbine condenser in position, let the installation elevation20-25mm lower than the design data.——预先安装好机组下部在机组就位后无法安装的管道及管件等；Pre-install the pipes and fittings which cannot be installed after emplacement.——仔细清除底座底面的油污及铁锈，并涂刷一层水泥浆；Carefully clean the underside of the base plate, remove oil and rust, and one layer of cement mortarwill be coated on the plate's underside.4.7.2 Installation and alignment of the compressor shall generally be carried out inorder as follows:(1). Carry out treatments, such as chipping and fitting, on foundation furface.(2). Set line.(3). Place the frame of crankshaft and cross-guides on the liner provisionally and setanchor bolts.(4). Align the frame provisionally.(5). Mount crankshaft and confirm the deflection of crankshaft arms.(6). Pour mortar into anchor boxes.(7). After the mortar solidification, align the frame finally by tightening the anchorbolts.(8). Align compressor shaft with motor shaft.(9). Reconfirm the deflection of crankshaft arms.(10). Mount cross-heads and connection-rod.(11). Set other parts and accessories.Explanation:① Leveling of the frame in the crankshaft direction shall be carried out on the upper finished surfaces of both sides of the frame paralled to crankshaft, and leveling in the cross-guide direction shall be carried out the sliding surfaces of cross-guides.②Main bearings and crankshaft shall be mounted on the frame in accordance with the following procedures:a. Adjust main bearings to keep deflection of crankshaft arms within the specified toloerance.b. Confirm that the clearance between main bearing metal and crankshaft journal is as specified by the munufacturer, and contacting traces on the sliding surface of main bearings metal is uniform.c.4.7.3 Insallation and alignment requirements(1)4.7.2各缸体整体就位，穿好地脚螺栓，地脚螺栓的光杆部分应无油污，螺纹部分应涂抹油脂。

螺杆压缩机外文文献翻译、中英文翻译、外文翻译英文原文Screw CompressorsN. Stosic I. Smith A. KovacevicScrew CompressorsMathematical Modellingand Performance CalculationWith 99 FiguresABCProf. Nikola StosicProf. Ian K. SmithDr. Ahmed KovacevicCity UniversitySchool of Engineering and Mathematical SciencesNorthampton SquareLondonEC1V 0HBU.K.e-mail:n.stosic@/doc/d6433edf534de518964bcf 84b9d528ea81c72f87.htmli.k.smith@/doc/d6433edf534de51896 4bcf84b9d528ea81c72f87.htmla.kovacevic@/doc/d6433edf534de51 8964bcf84b9d528ea81c72f87.htmlLibrary of Congress Control Number: 2004117305ISBN-10 3-540-24275-9 Springer Berlin Heidelberg New York ISBN-13 978-3-540-24275-8 Springer Berlin Heidelberg New YorkThis work is subject to copyright. All rights are reserved, whether the whole or part of the material is concerned, specifically the rights of translation, reprinting, reuse of illustrations, recitation, broadcasting, reproduction on microfilm or in any other way, and storage in data banks. Duplication of this publication or parts thereof is permitted only under the provisions of the German Copyright Law of September 9, 1965, in its current version, and permission for use must always be obtained from Springer. Violations are liable for prosecution under the GermanCopyright Law.Springer is a part of Springer Science+Business Media/doc/d6433edf534de518964bcf84b9d 528ea81c72f87.html_c Springer-Verlag Berlin Heidelberg 2005Printed in The NetherlandsThe use of general descriptive names, registered names, trademarks, etc. in this publication does not imply,even in the absence of a specific statement, that such names are exempt from the relevant protective laws and regulations and therefore free for general use.Typesetting: by the authors and TechBooks using a Springer LATEX macro packageCover design: medio, BerlinPrinted on acid-free paper SPIN: 11306856 62/3141/jl 5 4 3 2 1 0PrefaceAlthough the principles of operation of helical screw machines, as compressors or expanders, have been well known for more than 100 years, it is only during the past 30 years thatthese machines have become widely used. The main reasons for the long period before they were adopted were their relatively poor efficiency and the high cost of manufacturing their rotors. Two main developments led to a solution to these difficulties. The first of these was the introduction of the asymmetric rotor profile in 1973. This reduced the blowhole area, which was the main source of internal leakage by approximately 90%, and thereby raised the thermodynamic efficiency of these machines, to roughly the same level as that of traditional reciprocating compressors. The second was the introduction of precise thread milling machine tools at approximately the same time. This made it possible to manufacture items of complex shape, such as the rotors, both accurately and cheaply.From then on, as a result of their ever improving efficiencies, high reliability and compact form, screw compressors have taken an increasing share of the compressor market, especially in the fields of compressed air production, and refrigeration and air conditioning, and today, a substantial proportion of compressors manufactured for industry are of this type.Despite, the now wide usage of screw compressors and the publication of many scientific papers on their development, only a handful of textbooks have been published to date, which give a rigorous exposition of the principles of their operation and none of these are in English.The publication of this volume coincides with the tenth anniversary of the establishment of the Centre for Positive Displacement Compressor Technology at City University, London, where much, if not all, of the material it contains was developed. Its aim is to give an up to date summary of the state of the art. Its availability in a single volume should then help engineers inindustry to replace design procedures based on the simple assumptions of the compression of a fixed mass of ideal gas, by more up to date methods. These are based on computer models, which simulate real compression and expansion processes more reliably, by allowing for leakage, inlet and outlet flow and other losses, VI Preface and the assumption of real fluid properties in the working process. Also, methods are given for developing rotor profiles, based on the mathematical theory of gearing, rather than empirical curve fitting. In addition, some description is included of procedures for the three dimensional modelling of heat and fluid flow through these machines and how interaction between the rotors and the casing produces performance changes, which hitherto could not be calculated. It is shown that only a relatively small number of input parameters is required to describe both the geometry and performance of screw compressors. This makes it easy to control the design process so that modifications can be cross referenced through design software programs, thus saving both computer resources and design time, when compared with traditional design procedures.All the analytical procedures described, have been tried and proven on machines currently in industrial production and have led to improvements in performance and reductions in size and cost, which were hardly considered possible ten years ago. Moreover, in all cases where these were applied, the improved accuracy of the analytical models has led to close agreement between predicted and measured performance which greatly reduced development time and cost. Additionally, the better understanding of the principles of operation brought about by such studies has led to an extension of the areas of application of screw compressors and expanders.It is hoped that this work will stimulate further interest in an area, where, though much progress has been made, significant advances are still possible.London, Nikola StosicFebruary 2005 Ian SmithAhmed KovacevicNotationA Area of passage cross section, oil droplet total surfacea Speed of soundC Rotor centre distance, specific heat capacity, turbulence model constantsd Oil droplet Sauter mean diametere Internal energyf Body forceh Specific enthalpy h = h(θ), convective heat transfer coefficient betweenoil and gasi Unit vectorI Unit tensork Conductivity, kinetic energy of turbulence, time constant m Massm˙ Inlet or exit mass flow rate m˙ = m˙ (θ)p Rotor lead, pressure in the working chamber p = p(θ)P Production of kinetic energy of turbulenceq Source term˙Q Heat transfer rate between the fluid and the compressor surroundin gs˙Q= ˙Q(θ)r Rotor radiuss Distance between the pole and rotor contact points, control volume surfacet TimeT Torque, Temperatureu Displacement of solidU Internal energyW Work outputv Velocityw Fluid velocityV Local volume of the compressor working chamber V = V (θ)˙VVolume flowVIII Notationx Rotor coordinate, dryness fraction, spatial coordinatey Rotor coordinatez Axial coordinateGreek Lettersα Temperature dilatation coefficientΓ Diffusion coefficientε Dissipation of kinetic energy of turbulenceηi Adiabatic efficiencyηt Isothermal efficiencyηv Volumetric efficiencySpecific variableφ Variableλ Lame coefficientμ Viscosityρ Densityσ Prand tl numberθ Rotor angle of rotationζ Compound, local and point resistance coefficientω Angular speed of rotationPrefixesd differentialΔ IncrementSubscriptseff Effectiveg Gasin Inflowf Saturated liquidg Saturated vapourind Indicatorl Leakageoil Oilout Outflowp Previous step in iterative calculations SolidT Turbulentw pitch circle1 main rotor, upstream condition2 gate rotor, downstream conditionContents1Introduction. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . ………………………. . . . . . . . . . . . . . . 1 1.1 Basic Concepts . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. .. . . . . . . . . 4 1.2 Types of Screw Compressors . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. . . . . ….. . . . . . . .7 1.2.1 The Oil Injected Machine . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . …... . .71.2.2 The Oil Free Machine . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. . . . . . . . . . . ….... .7 1.3 Screw Machine Design . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. . . . . . . . . . . . . . . .8 1.4 Screw Compressor Practice . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. . . . . . . . . . . . . . . . .101.5RecentDevelopments . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 12 1.5.1RotorProfiles . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. . . . . 13 1.5.2CompressorDesign . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 17 2ScrewCompressorGeometry. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . 192.1 The Envelope Method as a Basis for the Profiling of Screw CompressorRotors . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . ………………………….. . . . . ….. . . . . . . . 19 2.2 Screw Compressor Rotor Profile s . . . . . . . . . . . . . . . . . . . . …. . . . . . . . . . . . . . . . . . . ….. . . 20 2.3 Rotor ProfileCalculation . . . . . . . . . . . . . . . . . . . . . . . . . . . …………………………. . . . . .23 2.4 Review of Most Popular Rotor Profiles . . . . . . . . . . . . . . . ………………………….. . . . . . 23 2.4.1 Demonstrator Rotor Profile (“N” Rotor Generated) . . ………………………………….. . 24 2.4.2 SKBK Profile . . . . . . . . . . . . . . . . . . . . . . . . . . . ……………………………... . . . . . . . . .26 2.4.3 Fu Sheng Profile . . . . . . . . . . . . . . . . . . . . . . . . . ………………………………. . . . . . . . .27 2.4.4 “Hyper”Profile . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . ………………………………. . .27 2.4.5 “Sigma” Profile . . . . . . . . . . . . . . . . . . . . . . .. . . . . . ………………………………. . . . . .28 2.4.6 “Cyclon” Profile . . . . . . . . . . . . . . . . . . . . . . . . . . . . ………………………………. . . . . .28 2.4.7 Symmetric Prof ile . . . . . . . . . . . . . . . . . . . . . . . . . . . ……………………………… . . . . .29 2.4.8 SRM “A” Profile . . . . . . . . . . . . . . . . . . . . . . . . . . ……………………………… . . . . . . .30 2.4.9 SRM “D” Profile . . . . . . . . . . . . . . . . . . . . . . . . . . . ……………………………… . . . . . .31 2.4.10 SRM “G” Profile . . . . . . . . . . . . . . . .. . . . . . . . …………………………….. . . . . . . . . .32 2.4.11 City “N” Rack Generated Rotor Profile . . . . . . . . . . . ………………………………… . . 32 2.4.12 Characteristics of “N” Profile . . . . . . . . . . . . . . . . . . . ………………………………. . . . 34 2.4.13 Blower Rot or Profile . . . . . . . . . . . . . . . . . . . . …………………………….. . . . . . . . . . . 39 X Contents2.5 Identification of Rotor Positionin Compressor Bearings . . . . . . . . . . . . . . . . . . . . . . . . . . …………………………….. . . . . . . .40 2.6 Tools for Rotor Manufacture . . . . . . . . . . . . . . . . . . . . . . …………………………. . . . . . . .45 2.6.1 Hobbing Tools . . . . . . . . . . . . . . . . . . . . . . . . . . ………….…..………………. . . . . . . . . .45 2.6.2 Milling and Grinding Tools . . . . . . . . . . . . . . . . . . . ……………………………….... . . . . 482.6.3 Quantification of ManufacturingImperfections . . . . . ……………………………….... . . 483 Calculation of Screw Compressor Performance . . . . . . . . . . ………………………………. . . 49 3.1 One Dimensional Mathematical Model . . . . . . . . . . . . . . …………………………... . . . . . .49 3.1.1 Conservation Equationsfor Control Volume and Auxiliary Relationships . . . . ............................................... . . 50 3.1.2 Suction and Discharge Ports . . . . . . . . . . . . . . . . . . . ....................................... . . . . 53 3.1.3 Gas Leakages . . . . . . . . . . . . . . . . . . . . . . . . . . .................................... . . . . . . . . . .54 3.1.4 Oil or Liquid Injection . . . . . . . . . . . ...................................... . . . . . . . . . . . . . . . . . 55 3.1.5 Computation of Fluid Properties . . . . . . . . ........................................ . . . . . . . . . . . 57 3.1.6 Solution Procedure for Compressor Thermodynamics . (58)3.2 Compressor Integral Parameters . . . . . . . . . . . . . . . . . . . ………………………….. . . . . . . . 59 3.3 Pressure Forces Actingon Screw Compressor Rotors . . . . . . . . . . . . . . . . . . . . . . ................................... . . . . . . . 61 3.3.1 Calculation of Pressure Radial Forces and Torque . . . . .. (61)3.3.2 Rotor Bending Deflections . . . . . . . . . . . . . . . . . . . . . ……………………………….. . . . 64 3.4 Optimisation of the Screw Compressor Rotor Profile,Compressor Design and Operating Parameters . . . . . . . . . . ……………………………….. . . . 65 3.4.1 OptimisationRationale . . . . . . . . . . . . . . . . . . . . . . . . ……………………………….. . . . 65 3.4.2 Minimisation Method Usedin Screw CompressorOptimisation . . . . . . . . . . . ……………………………………… . . . . . . 67 3.5 Three Dimensional CFD and Structure Analysisof a Screw Compressor . . . . . . . . . . . . . . . . . . . . . . . . . …………………………….. . . . . . . . .71 4 Principles of Screw Compressor Design. . . . . . . . . . . …………………………… . . . . . . . . 77 4.1 Clearance Management. . . . . . . . . . . . . . . . . . . . . . . . ………….….………… . . . . . . . . . .78 4.1.1 Load Sustainability . . . . . . . . . . . . . . . . . . . . . . . . . . . . ………….………………….. . . .79 4.1.2 Compressor Size and Scale . . . . . . . . . . . . . . ………………………………. . . . . . . . . . . 80 4.1.3 RotorConfiguration . . . . . . . . . . . . . . . . . . . . . . . ……………………………... . . . . . . .82 4.2 Calculation Example:5-6-128mm Oil-Flooded Air Compressor . . . . . . . . . . . . . . . ……………………………... . . . 824.2.1 Experimental Verification of the Model . . . . . . . . . . . ………………………………. . . . 845 Examples of Modern Screw Compressor Designs . . . . . . . ……………………………… . . . 89 5.1 Design of an Oil-Free Screw CompressorBased on 3-5 “N” Rotors . . . . . . . . . . . . . . . . . . . . . . . . . . ……………………………. . . . . . . 90 5.2 The Design of Familyof Oil-Flooded Screw Compressors Basedon 4-5 “N” Rotors . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . …………………………… . . . . . . .93 Contents XI.5.3 Design of Replacement Rotorsfor Oil-FloodedCompressors . . . . . . . . . . . . . . . . . . . . . . . . . . . ................................. . .96 5.4 Design of Refrigeration Compressors . . . . . . . . . . . . . . . .............................. . . . . . . 100 5.4.1 Optimisation of Screw Compressors for Refrigeration . . . (102)5.4.2 Use of New Rotor Profiles . . . . . . . . . . . . . . . . . . . . . . . . . . (103)5.4.3 Rotor Retrofits . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . ……………………………. . . 103 5.4.4 Motor Cooling Through the Superfeed Port in Semihermetic Compressors . . . . . . . . . . . . . . . . . . . …………………………………… . . . 103 5.4.5 Multirotor Screw Compressors . . . . . . . . . . . . . . . . . …………………………….... . . . . 104 5.5 Multifunctional Screw Machines . . . . . . . . . . . . . . . . . . ……………………….. . . . . . . . . 108 5.5.1 Simultaneous Compression and Expansionon One Pair of Rotors . . . . . . . . . . . . . . . . . . . . . . . . . . ............................................ . 108 5.5.2 Design Characteristics of Multifunctional Screw Rotors .. (109)5.5.3 Balancing Forces on Compressor-Expander Rotors . …………………..……………. . . 1105.5.4 Examples of Multifunctional Screw Machines . . . . . . . . (111)6Conclusions. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . …………………… . . . . . . . . . 117A Envelope Method of Gearin g . . . . . . . . . . . . . . . . . . . . . . . . ………………………… . . . . . 119B Reynolds TransportTheorem. . . . . . . . . . . . . . . . . . . . . . . …………………………. . . . . . . 123C Estimation of Working Fluid Propertie s . . . . . . . . . . . . . . . …………………………….. . . . 127 Re ferences. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . ………………… . . . . . . . . . . 133中文译文螺杆压缩机N.斯托西奇史密斯先生A科瓦切维奇螺杆压缩机计算的数学模型和性能尼古拉教授斯托西奇教授伊恩史密斯博士艾哈迈德科瓦切维奇工程科学和数学北安普敦广场伦敦城市大学英国电子邮件：n.stosic@/doc/d6433edf534de518964bcf 84b9d528ea81c72f87.htmli.k.smith@/doc/d6433edf534de51896 4bcf84b9d528ea81c72f87.htmla.kovacevic@/doc/d6433edf534de51 8964bcf84b9d528ea81c72f87.html国会图书馆控制号：2004117305isbn-10 3-540-24275-9 纽约施普林格柏林海德堡isbn-13 978-3-540-24275-8 纽约施普林格柏林海德堡这项工作是受版权保护,我们保留所有权利。

液压系统和气压系统外文文献翻译、中英文翻译Hydraulic system and Peumatic SystemHui-xiong wan1,Jun Fan2Abstract:Hydraulic system is widely used in industry, such as stamping, grinding of steel type work and general processing industries, agriculture, mining, space technology, deep sea exploration, transportation, marine technology, offshore gas and oil exploration industries, in short, Few people in their daily lives do not get certain benefits from the hydraulic technology. Successful and widely used in the hydraulic system's secret lies in its versatility and ease of maneuverability. Hydraulic power transmission mechanical systems as being not like the machine geometry constraints, In addition, the hydraulic system does not like the electrical system, as constrained by the physical properties of materials, it passed almost no amount of power constraints.Keywords: Hydraulic system,Pressure system,FluidThe history of hydraulic power is a long one, dating from man’s prehistoric efforts to harness the energy in the world around him. The only source readily available were the water and the wind—two free and moving streams.The watermill, the first hydraulic motor, was an early invention. One is pictured on a mosatic at the Great Palace in Byzantium, dating from the early fifth century. The mill had been built by the Romans. But the first record of a watermill goes back even further, to around 100BC, and the origins may indeed have been much earlier. The domestication of grain began some 5000 years before and some enterprising farmer is bound to have become tired of pounding or grinding the grain by hand. Perhaps,in fact, the inventor were some farmer’s wives. Since the often drew the heavy jobs.Fluid is a substance which may flow; that is, its constituent particles may continuously change their positions relative to one another. Moreover, it offers no lasting resistance to the displacement, however great, of one layer over another. This means that, if the fluid is at rest, no shear force (that is a force tangential to the surface on which it acts) can exist in it.Fluid may be classified as Newtonian or non--Newtonian. In Newtonian fluid there is a linear relation between the magnitude of applied shear stresses and the resulting rate of angular deformation. In non—Newtonian fluid there is a nonlinear relation between the magnitude of applied shear stress and the rate of angulardeformation.The flow of fluids may be classified in many ways, such as steady or non steady, rotational or irrotational, compressible or incompressible, and viscous or no viscous.All hydraulic systems depend on Pascal’s law, such as steady or pipeexerts equal force on all of the surfaces of the container.In actual hydraulic systems, Pas cal’s law defines the basis of results which are obtained from the system. Thus, a pump moves the liquid in the system. The intake of the pump is connected to a liquid source, usually called the tank or reservoir. Atmospheric pressure, pressing on the liquid in the reservoir, forces the liquid into the pump. When the pump operates, it forces liquid from the tank into the discharge pipe at a suitable pressure.The flow of the pressurized liquid discharged by the pump is controlled by valves. Three control functions are used in most hydraulic systems: (1) control of the liquid pressure, （2）controlof the liquid flow rate, and (3) control of the direction of flow of the liquid.Hydraulic drives are used in preference to mechanical systems when(1) powers is to be transmitted between point too far apart for chains or belts; (2) high torque at low speed in required; (3) a very compact unit is needed; (4) a smooth transmission, free of vibration, is required;(5) easy control of speed and direction is necessary; and (6) output speed is varied steplessly.Fig. 1 gives a diagrammatic presentation of the components of a hydraulic installation. Electrically driven oil pressure pumps establish an oil flow for energy transmission, which is fed to hydraulic motors or hydraulic cylinders, converting it into mechanical energy. The control of the oil flow is by means of valves. The pressurized oil flow produces linear or rotary mechanical motion. The kinetic energy of the oil flow is comparatively low, and therefore the term hydrostatic driver is sometimes used. There is little constructional difference between hydraulic motors and pumps. Any pump may be used as a motor. The quantity of oil flowing at any given time may be varied by means of regulating valves( as shown in Fig.7.1) or the use of variable-delivery pumps.The application of hydraulic power to the operation of machine tools is by no means new, though its adoption on such a wide scale as exists at present is comparatively recent. It was in fact in development of the modern self-contained pump unit that stimulated the growth of this form of machine tool operation.Hydraulic machine tool drive offers a great many advantages. One of them is that it can give infinitely-variable speed control over wide ranges. In addition, they can change the direction ofdrive as easily as they can vary the speed. As in many other types of machine, many complex mechanical linkages can be simplified or even wholly eliminated by the use of hydraulics.The flexibility and resilience of hydraulic power is another great virtue of this form of drive. Apart from the smoothness of operation thus obtained, a great improvement is usually found in the surface finish on the work and the tool can make heavier cuts without detriment and will last considerably longer without regrinding.Hydraulic and pneumatic systemThere are only three basic methods of transmitting power:electrical,mechanical,and fluid power.Most applications actually use a combination of the three methods to obtain the most efficient overall system. To properly determine which principle method to use,it is important to know the salient features of each type. For example, fluid systems can transmit power more economically over greater distances than can mechanical types. However, fluid systems are restricted to shorter distances than are electrical systems.Hydraulic power transmission system are concerned with the generation, modelation, and control of pressure and flow，and in general such systems include:1.Pumps which convert available power from the prime mover to hydraulic power at the actuator.2.Valves which control the direction of pump-flow, the level of power produced, and the amount of fluid-flow to the actuators. The power level is determined by controlling both the flow and pressure level.3.Actcators which convert hydtaulic power to usable mechanical power output at the point required.4.The medium, which is a liquid, provides rigid transmission and control as well as lubrication of componts, sealing in valves, and cooling of the system.5.Conncetots which link the various system components, provide power conductors for the fluid under pressure, and fluid flow return to tank(reservoir).6.Fluid storage and conditioning equipment which ensure sufficient quality and quantity as well as cooling of the fluid.Hydraulic systems are used in industrial applications such as stamping presses, steel mills, and general manufacturing, agricultural machines, mining industry,aviation, space technology, deep-sea exploration, transportion, marine technology, and offshore gas and petroleum exploration. In short, very few people get through a day of their lives without somehow benefiting from the technology of hydraulicks.The secret of hydraulic system’s success and widespread use is its versatility and manageability. Fluid power is not hindered by the geometry of the machine as is the case in mechanical systems. Also, power can be transmitted in almost limitless quantities because fluid systems are not so limited by the physical limitations of materials as are the electrical systems. For example, the performance of an electromangnet is limited by the saturation limit of steel. On the other hand, the power limit of fluid systems is limited only by the strength capacity of the material.Industry is going to depend more and more on automation in order to increase productivity. This includes remote and direct control of production operations, manufacturing processes, and materials handling. Fluid power is the muscle of automationbecause of advantages in the following four major categories.1.Ease and accuracy of control. By the use of simple levers and push buttons, the operator of a fluid power system can readily start, stop, speed up or slow down, and position forces which provide any desired horsepower with tolerances as precise as one ten-thousandth of an inch.2.Multiplication of force. A fluid power system(without using cumbersome gears, pulleys, and levers) can multiply forces simply and efficiently from a fraction of an ounce to several hundred tons of output.3.Constant force or torque. Only fluid power systems are capable of providing contant force or torque regardless of speed changes. This is accomplished whether the work output moves a few inches per hour, several hundred inches per minute, a few revolutions per hour, or thousands of revolutions per minute.4.Simplicity, safely, economy. In general, fluid power systems use fewer moving parts than comparable mechanical or electrical systems. Thus, they are simpler to maintain and operate. This, in turn, maximizes safety, companctness, and reliability. For example, a new power steering control designed has made all other kinds of power systems obsolete on many off-highway vehicles. The steering unit consists of a manually operated directional control valve and meter in a single body. Because the steering unit is fully fluid-linked, mechanical linkages, universal joints, bearings, reduction gears, etc, are eliminated. This provides a simple, compact system. In addition, very little input torque is required to produce the control needed for the toughest applications. This is important where limitations of control space require a small steering wheel and it becomes necessary to reduce operatot\r fatique.Additonal benefits of fluid power systems include instantly reversible motion, automatic protection against overloads, and infinitely variable speed control. Fluid power systems also have the highest horsepower per weight ratio of any known power source. In spite of all these highly desirable features of fluid power, it is not a panacea for all power transmission problems. Hydraulic systems also have some drawbacks. Hydraulic oils are messy, and leakage is impossible to completely eliminate. Also, most hydraulic oils can cause fires if an oils occurs in an area of hot equipment.Peumatic SystemPneumatic systems use pressurized gases to tansmit and control power. A s the name implies, pneumatic systems typically use air(rather than some other gas) as the fluid medium because air is a safe, low-cost, and readily available fluid. It is particularly safe in environments where an electrical spark could ignite leaks from system components.In pneumatic systems ,compressors are used to compress and supply the necessary quantities of air. Compressors are typically of the piston, vane or screw type. Basically a compressor increases the pressure of a gas by reducing its volume as described by the perfect gas laws.Pneumatic systems normally use a large centralized air compressor which is considered to be an infinite air source similar to an electrical system where you merely plug into an electrical outlut for electricity. In this way, pressurized air can be piped from one source to various locations throughout an entire industrial plant. The air then flows through a pressue regulator which redeces the pressure to the desired level for the particular circuit application. Because air is not a good lubircant（contains about 20% oxygen）, pneumaticssystems required a lubricator to inject a very fine mist of oil into the air discharging from the pressure regulator. This prevents wear of the closely fitting moving parts of pneumatic components.Free air from the atmosphere contains varying amounts of moisure. This moisure can be harmful in that it can wash away lubricants and thus cause excessive wear and corrosion. Hence ,in some applications ,air driers are needed to remove this undesirable moisture. Since pneumatics systems exhaust directly into the atmosphere, they are capable of generating excessive noise. Therefore, mufflers are mounted on exhaust ports of air valves and actuators to reduce noise and prevent operating personnel from injury resulting not only from exposure to noise but also from high-speed airborne particles.There are several reasons for considering the use of pneumatic systems instead of hydraulic systems. Liquids exhibit greater inertia than do gases. Therefore, in hydraulic systems the weight of oil is a potential problem when accelerating and decelerating actuators and when suddenly opening and closing valves. Due to Newton’s law of motion(force equals mass multiplied by acceleration), the force required to accelerate oil is many times greater than that required to accelerate an equal volume of air. Liquids also exhibit greater viscosity than do gases. This results in larger frictional pressure and power losses. Also ,since hydraulic systems use a fluid foreign to the atmosphere, they require special reservoirs and noleak system designs. Pneumatic system use air which is exhausted directly back into the surrounding environment. Generally speaking, pneumatic systems are less expensive than hydraulic systems.However, because of the compressibility of air, it isimpossible to obtain precise controlled actuator velocities with pneumatic systems. Also, precise positioning control is not obtainable. While pneumatics pressures are quite low due to compressor design limitations(less than 250 psi), hydraulic pressures can be as high as 10000 psi. Thus, hydraulics can be high-power systems, whereas pneumatics are confined to low-power applications. Industrial applications of pneumatics systems are growing at a rapid pace. Typical examples include stamping, drilling, hoist, punching, clamping, assembling, riveting, materials handling, and logic controlling operations.液压系统和气压系统万辉雄1，范军2摘要：液压系统在工业中应用广泛，例如冲压、钢类工件的磨削及一般加工业、农业、矿业、航天技术、深海勘探、运输、海洋技术，近海天然气和石油勘探等行业，简而言之，在日常生活中很少有人不从液压技术得到某些益处。

中英文对照外文翻译Small COMPRESSORCompressor refrigeration system is the core and heart of its decision to the refrigeration system capabilities and features. This paper not only energy efficient, noise and vibration and refrigeration agent analyzed small refrigeration compressor technical performance, Analysis also have appeared in recent years, the new, special small compressor main feature for us small refrigeration compressor future development trend of laying a technological foundation.As we all know, the compressor refrigeration system is the core and heart. Compressor and decided that the cooling system capacity and features. In a sense, the cooling system design and matching of the compressor is the ability demonstrated. Therefore, countries in the world are all in the refrigeration industry refrigeration compressor research invested a tremendous amount of energy, new research direction, and research results continue to emerge. Compressor technology and performance level with each passing day.1.A compressor Efficiency StudyCompressor refrigeration system is the core energy components, improve the efficiency of refrigeration systems of the most direct and effective means is to increase the efficiency of the compressor, It will bring the energy consumption decreased significantly. Moreover, can only avoid the system take measures (such as simply increasing heat exchanger area, etc.) caused by the consumption of materials increased. In recent years, as world energy shortage situation worsens day by day, more and more attention to various energy-saving work the energy efficiency ofproducts made by the ever-increasing demands. Due to losses such as friction, leakage, harmful heat, the electrical loss, flow resistance, noise vibration of existence, Compressor work far below the actual efficiency of theoretical efficiency. Therefore, from a theoretical point of view, any reduction in a loss of arbitrary measures to improve the efficiency of the compressor. The objective facts have led to the energy saving compressor scope, direction, width, research topics and results varied.On the current international energy-efficient compressors research concentrated mainly in a few areas : research lubrication properties Compressor parts of the friction bearings to reduce friction characteristics of power, improve the efficiency of the compressor; reduce leakage losses to improve the efficiency of the compressor; using frequency modulation technology or refrigeration system through the effort with the user load to match the best energy saving In this regard the particular frequency technology has been relatively mature well known and not repeat them here. Valve Research is an old topic but it is also an eternal topic, Improvement of the valve designed to improve the efficiency of the compressor also Nagamochi endless harvest. Research in this area many times, from the valve material, sports law, optimizing the structure of the applicable theory, exhaustive testing methods. In short, energy-saving compressors on the research in recent years has become one of the refrigeration industry first hot issues.In recent years, domestic refrigeration compressor industry to studyenergy-saving products are also giving great concern. Progress larger products mainly refrigerator compressor industry. In China efficient refrigerators GEF projects to promote and support, both the enterprises for energy-efficient products is the understanding of the performance of refrigerator compressors have a qualitative leap. At present, domestic enterprises refrigerator compressor products of the highest energy efficiency has reached 1.95%. Refrigerator compressor domestic enterprises to take a lot of technical measures such as high efficiency motors or synchronous motor, concave valves, Plane thrust bearing, low viscosity lubricants, the new Getter muffler,reducing friction losses, and achieved great results. The main problem is the lack of domestic enterprises currently free technology, the technology has to imitate the line mainly, Most of the enterprises to build their own technology infrastructure also unconscious, nor the interest, and this restricts the development of technological capacity.Relative to the refrigerator compressor industry, domestic energy-efficientair-conditioning compressor study it was not perturbed, Over the years the efficiency of the compressor is no substantive change, greater market demand makes most of the air-conditioning compressor enterprises will concentrate on expanding production on. With the nation on the air conditioner energy efficiency standards set for the further improvement of China's air conditioner exports various perils of showing, domestic air-conditioning compressor of this short-sighted enterprises will be unable to adapt to the energy-saving development of the situation. Enterprise also on the follow-up is weak.2. Compressor noise and vibration studyCurrently, the noise has been regarded as one of the serious pollution. Household refrigeration equipment as the source of power and heart, refrigeration compressor noise, to be a measure of its performance as an important indicator. In fact, to a compressor speaking, Most of the noise is due to shell by some noise from the source excitation (such as springs, refrigerant pressure pulsation, exhaust pipe, lubricants etc. excited). But compressor noise sources and pathways complex and diverse, which gives the compressor noise silencer brought great difficulties.On the compressor noise, vibration and foreign scholars have conducted a large number of long-term research. Here in this regard to the main research results are summarized below :The main refrigeration compressor noise Exaggerative inlet, exhaust radiation aerodynamic noise, mechanical moving parts of machinery noise and noise-driven motor three components :2.1 Aerodynamic noiseCompressor inlet airflow noise is due to the intake manifold pressure pulsation in the elections. Inlet-frequency noise and the intake manifold gas Lane same frequency pulsating with the speed of the compressor. Compressor exhaust noise is due to air in the exhaust pipe caused by fluctuating pressures. Exhaust noise than the inlet noise weak, so the compressor aerodynamic noise generally Inlet mainly noise2.2 Mechanical NoiseCompressor mechanical noise, including members of the general impact and friction, the piston vibration, noise impact of the valve, These noise with randomness, was puted.2.3Electromagnetic noiseCompressor electromagnetic noise is generated by the motor. Motor noise and aerodynamic noise and mechanical noise is weaker compared. Noise source compressor inlet, exhaust, aerodynamic noise, the strongest, followed by mechanical noise and electromagnetic noise. Through in-depth studies, we can further that the main compressor noise from the vibration (from the Department of spring, Refrigeration medium pressure pulsation and smoke exhaust pipe and lubricants have incentive) to the ambient medium spread formation noise. On the effort to reduce compressor noise, much of the literature (abbreviated) proposed a series of measures and the Noise and Vibration Reduction program :① increase rigid shell structure to improve the overall resonance frequency reduces vibration amplitude;② curvature of the shell to avoid mutation, the surface, and the natural frequency is inversely proportional to the radius of curvature. shell shape it should be the smallest curvature radius;③ spring bearing flags will be moved to higher rigid position;④ shell should be used as little as possible of the plane; bending stress and the stress coupling membrane (just on the surface) will shell itself is fairly rigid. Therefore compressor shell to be used as little as possible planar structure;⑤ avoid the exhaust pipe and condenser incentive, optimizing exhaust flow pulsation, Exhaust pipe used in the introduction of additional volume to the elimination of pressure fluctuation spectrum of high-order harmonics;⑥ non-symmetric shell shape; Symmetrical three-dimensional structure means that the axis, along the main axis biggest stress of least resistance. Therefore it is asymmetrical shell structure means that the compressor can be greatly reduced along the axis direction of a force while the probability;⑦ set inlet, exhaust muffler, the closed Compressor Muffler generally muffler. It uses Cross Section, resonant cavity caused acoustic impedance changes in reflectivity or sound energy consumption. or use acoustic-acoustic send phase difference of 180 degrees to offset the muffler of noise. Shell compressor in the lateral closed Unicom a Helmholtz resonator, namely : Helmholtz resonator from the chamber through the neck hole and shell compressor connected into the internal cavity, to reduce compressor cavity stimulated acoustic modal amplitude. The results showed :resonator resonance frequency modulation of the actual compressor cavity stimulated the greatest vibration modes, will be substantially reduced resonance peak response spectrum and lead to significant change. However, it will affect the appearance and the compressor refrigerator settings, the research results are not yet applied to products.Lubricants and residual volume-coil motor windings will lead to the same types of bulk compressor levels between different (from levels average). By changing the shell external support to increase torsional stiffness and reduce vibration surface; Noise study the complex requirements of researchers has strong theory, the enterprise has good skills base and the need for greater investment and a longer timeframe. This is domestic enterprises compressor one of the weak links, which is now basically in the qualitative phase of experimental research, Along with a great chance and randomness.3. new refrigerants ApplicationBased on the new environmental requirements of refrigerant compressor refrigeration industry is a hot issue. As for the refrigerator product R22 refrigerant substitutes the end of the work, new refrigerant compressor in the past few years mainly concentrated in the air conditioning industry. Apart from the now relatively mature R410A, R407C the study, The largest is the hot issue of CO2 compressor. This is the only issue for a briefing.CO2 currently on the research and application of concentrated mainly in three aspects : one is the most urgent need of alternative refrigerants applications, such as automotive air conditioning, as refrigerant emissions, environmental harm, must be adopted as soon as possible without endangering the environment refrigerants; the other is to consider the characteristics of CO2 cycle, the most favorable to the use of this cycle of occasions, If heat pump water heater is to supercritical CO2 in hot conditions decentralization there is a significant temperature slip will help heat Water heated to a higher temperature characteristics of the focus of public attention; anotherone is CO2 into account the nature of heat transfer properties and characteristics of using CO2 as a refrigerant, taking into account CO2 good cold flow properties and heat transfer characteristics, use it as a cascade refrigeration cycle cryogenic stage refrigerants.Compressor transcritical carbon dioxide as an air conditioning system efficiency and reliability of the most affected parts, It should be fully integrated supercritical carbon dioxide cycle specific characteristics of a new design. Like ammonia and CO2, the adiabatic exponent K value higher, up 1.30, it may result in the compressor discharge temperature high, However, as the needs of CO2 compressor pressure ratio small, there is no need for cooling the compressor itself. Adiabatic index is high pressure over the small, I can reduce the gap compressor further expansion of the volume losses to the higher volume efficiency compressors. After experimental and theoretical research, Jurgen Horst SUB and found Kruse, reciprocating compressor is a good film sliding seal as the preferred CO2 system. 8:3 its carbon dioxide compressor exhaust valve for improved Exhaust improved compressor efficiency of carbon dioxide increased by 7%.As the carbon dioxide pressure is far greater than the traditional critical circulatory pressure, compressor shaft seal design requirements than the original compressor is much higher, compressor shaft seal leakage over a period of time is still hampered Actually, the main reason.Danfoss, Denso, ZEXEL such as carbon dioxide compressor has entered the stage of small batch production.The IEA in March 1999, the Joint Japan, Norway, Sweden, Britain and the United States to activate the "Selected Issue on CO2 as working fluid Compression Systems in the "three-year project.Beginning in 1994, BMW, DAIMLERBENZ VOL O, Germany's Volkswagen and Danfoss. Péchiney and other European companies launched the famous "RACE" to the joint project, the Joint European well-known universities, automotive air conditioning manufacturers and other developed CO2 automotive air-conditioning system. Subregion Motor Company has production equipment CO2 carair-conditioning systems of cars, Germany KONVECTA production to the quality of CO2 in the air-conditioned Buses run from 1996 to date. DANFOSS, the Obrist Austria, the United Kingdom have developed a carbon dioxide compressor motor. Japan DENSO, ZEXEL CO2 compressor has entered the stage of mass production.With major manufacturers inputs, the type of CO2 compressor with ordinary motor compressor trend line major swing to determine the displacement swashplate, scroll and the main variable displacement.4. New principle of refrigeration compressorsIn recent years, the new structure and working principle of refrigeration compressor made a more progress, mainly linear compressor, Elliptic compressors, compressor rotor Swing, spiral vane compressor, in the past, the author has been described in the article, here will not repeat it.Linear compressor which is the domestic refrigerator compressor industry the focus of attention. In 2004 the International Compressor Engineering Conference has five linear compressor on the article. LG and researchers still Sunpower two main companies. The past two years, several domestic enterprises in the refrigerator compressor to the development of the linear compressor, However, enterprises have the technical foundation for the domestic financial strength and the limitations of scientific research institutions, believe in a short period of time can not enter the stage of industrialization.5 the classification of the refrigeration compressor5.1 reciprocating compressorReciprocating compressor is a kind of traditional refrigeration compressor, the biggest characteristic is to achieve the capacity and pressure than any of the design. Although it is widely applied, but the market share is gradually reduced.So far, the fridge (including small freezing and cold storage device) host compound compressor is ever to give priority to. Through the optimal design of valve structure, friction pair, reciprocating refrigerator compressor refrigeration coefficient of power refrigerating capacity (units) by 1.0 (w/w) of the early ninety s to today's 1.8 or so; In addition to the energy saving technology progress, and environmental protection is closely related to the refrigerant alternative technology has also made gratifying progress, refrigerator system in our country has a large number of using R600 hydrocarbons, such as small refrigeration device is also used the new working substance such as everything. To further improve the efficiency of the reciprocating compressor refrigerator, to reduce the system noise is still the development direction of it.5.2 linear compressorStill make reciprocating linear compressor, due to the linear motion of the motor can be directly drives the piston reciprocating motion, so as to avoid the complexity of the crank connecting rod mechanism and the resulting mechanical power consumption. Linear compressor assembly as the refrigerator system has appeared, the refrigeration coefficient of linear refrigerator compressor has more than 2.0 (w/w), market prospects look good. The main problem is the design of the compressor oil system and the effective control of linear motor displacement limit point and the corresponding anti-collision cylinder technology.5.3 the swash plate compressorSwash plate compressor is also a kind of variant structure of reciprocating compressor, is mainly used in automotive air conditioning system at present. Afterdecades of development, the swash plate compressor has become a very mature model, in possession of more than 70 of the automotive air conditioning compressor market. In spite of this, because it still belongs to the series of reciprocating structure, so in the car air conditioning system can effect comparing (refrigeration coefficient) and only around 1.5, weight and volume is big, big. Because of the mature of swashplate automobile air conditioning compressor technology, combined with technology, further improvement in the foreseeable future, will continue to maintain a certain market share, but in a certain displacement range by substituting is inevitable.5.4 rotor compressorRotor compressor in the 1970 s by the attention of domestic, it represents the structure including the rolling piston type, sliding-vane, etc. On the rolling piston type is widely used in household air conditioner at present, there are also some applications on the refrigerator. This kind of compressor don't need air suction valve, make it suitable for variable speed operation, which can improve system performance by frequency conversion control. In order to ensure high power (3 p) of the motor output power in the performance of the rolling piston compressor, the domestic research and development and the end of last century, double rotor rolling piston compressor, is now on the market. Double rotor on the rolling piston compressor structure has two advantages: (1) force of the rotating system be improved, the machine vibration and noise is reduced; (2) increase the standalone swept volume and improve the output power of the motor.Below 3 p air conditioning unit, temporarily can not replace a good model of the rolling piston compressor. So improve the efficiency of the compression process, reduce noise and motor speed control and the R410A and other related technical issues after new refrigerating agent, etc., is a research direction of the rolling piston compressor.Sliding vane compressor is a kind of rotor compressor, mainly used to provide compressed air, displacement is in commonly 0.3-3 m3 / min, the market share is low.Rotary vane compressor sliding vane compressor is a kind of transition structure, because of its better starting performance, the compression process torque change is not big, at present is mainly used for miniature cars and some smaller displacement plumbing vehicle air conditioning system. The dynamic characteristics under high speed is the main technology of this compressor research direction.5.5 screw compressorScrew compressor with small size, light weight, easy to maintenance etc., is a model of the fast development in refrigeration compressor. On the one hand, the screw type line, structural design has made considerable progress, on the other hand, the introduction of special screw rotor milling especially grinding, improve the machining precision and machining efficiency of key parts, makes the performance of screw compressor has been effectively improved, industrialization production of the necessary hardware also has the safeguard. At present, the screw compressor is given priority to with compressed air, in medium ReBengShi air conditioning has successful application in the system. Due to increasing the reliability of the screw compressor work within the scope of the medium refrigerating capacity has gradually replace of reciprocating compressor and occupied most of the centrifugal compressor market. 5.6 scroll compressorScroll compressor has been rapid development in the past ten years, the structure of the basic theory, research and development to achieve large-scale industrial production, industrial prototype constitutes the compressor technology development new luminescent spot. The development of numerical control processing technology to realize the mass production, the vortex compressor incomparable performance advantage is the precondition of its vast in the market. A few short years, has been in the field of cabinet air conditioning holds an absolute advantage. In cabinet air conditioning system, scroll compressor refrigeration coefficient has amounted to 3.4 (w/w); In the field of automotive air conditioning, the refrigeration coefficient of scroll compressor has amounted to 2.0 (w/w), and shows strong competition potential. The development of the vortex compressor is to enlarge itsrange of refrigerating capacity, further improve the efficiency, using alternative working medium and lower the manufacturing cost, etc.Since there is no valve, compression force and torque and small changes in the structure make it more suitable for the advantages of frequency control of motor speed operation, it also become the main direction of scroll compressor technology development. Development of scroll compressor of variable displacement mechanism is the key point of the development of the technology. At present, the use of axial sealing technology, "flexible" theory can realize cooling/heating capacity of 10% to 100% within the scope of the regulation.Due to the vortex compressor suction exhaust characteristic of almost continuous, low starting torque and liquid impact resistance, created the condition for parallel use of vortex compressor. In parallel with the vortex compressor can greatly increase the cooling capacity of the unit, can increase from the current single 25 horsepower to single unit 100 horsepower (4 sets of single parallel), and makes the cold quantity adjustment is more reasonable, give full play to the single machine with the highest efficiency. But single in parallel, one of the biggest problems is the oil return is not the average of the unit when using single machine burning phenomenon.3.1.5 centrifugal compressorAt present in large quantity of cold (greater than 1500 kw) remain within the scope of advantage, this is mainly benefited from the cold quantity range, it has incomparable system overall efficiency. The movement of the centrifugal compressor parts little and simple, and its manufacturing precision is much lower than the screw compressor, these are the characteristics of the manufacturing cost is relatively low, and reliable. Relatively speaking, the development of centrifugal compressor is slow, due to the challenges of the screw compressor and absorption chiller. Centrifuge market capacity is around 700 ~ between 1200, because under the premise that the current technology, the machine is mainly used for air conditioning of large buildings, demand is limited. In recent years because of the large infrastructure projects are built, the centrifugal refrigeration and air conditioning compressor is becoming a hot spot ofattention again. Solve surge phenomenon, improve the volume adjustment and the adaptability to change with working condition, miniaturization technology is the main development direction of the centrifugal compressor technology.3.1.6 other structure formsSingle tooth of the compressor, some structures, such as cross slider compressor unique positive displacement compressor also has a certain degree of development, but has not been formed in the domestic production capacity.5. Special refrigeration compressorsAlthough domestic enterprises household refrigeration compressors long accustomed to large-scale production mode, we are accustomed to the number of effectiveness. However, the fierce price competition situation, as products become increasingly lower profit margins, When the production of millions of compressors can only make a few million dollars of profit, some on special refrigeration compressors can be regarded as a way out. Special refrigeration compressor exhaustive, it is impossible in this enumeration. But their common feature is their production scale is small, a single high-profit products faster transition, In most cases the need for the user's requirements designed. These products lead to more and more domestic enterprises to the compressor. If the number of domestic enterprises are developing or already have production capacity of the refrigerator compressor truck翻译小型制冷压缩机研究压缩机是制冷系统的核心和心脏，它决定了制冷系统的能力和特征。

Chemical and Petroleum Engineering, Vol. 40, Nos. 11–12, 2004COMPRESSORS, PUMPS, REFRIGERATION ENGINEERING UPDATING PISTON PUMPS FOR OILPRODUCTIONB. S. Zakharov,1 G. N. Sharikov,2and E. G. Kormishin2The three-plunger acid treatment pump SIN32 and the two-cylinder double-acting pump NPTs-32 with four working chambers (for cementing units) have been updated to control pump delivery. The fluid delivery diagrams for pumps of various designs are examined and the test results are reported.In drilling and oil production, single-acting three-plunger (triplex) pumps or double-acting two-cylinder (duplex) pumps are used.In injecting reagents (clay drilling mud, water, cement, acid, etc.) into wells, depending on the technology applied，it is required to inject the fluid in amounts ranging from the maximum to the minimum in a single operation. If the bed accepts the injected fluid well, it becomes necessary to maximize pump delivery for quick completion of the operation. If on the other hand, the bed does not accept the fluid well, it becomes necessary to reduce pump delivery so as to restrict the injection pressure to the safe limit. At present, because of wear of well (down-hole) equipment, the permissible injectionpressure is not higher than 10–15 MPa..The delivery of a piston (reciprocating) or a plunger (displacement) type of pump can be controlled in the following ways:• by installing several pumps with identical or different pumping capacities;• by changing the drive rotation speed;• by using cylinders (plungers) of the required size;• by channeling a part of the fluid into a bypass; and• by dismounting one or several valves.The first version is used essentially in drilling. In oil production, generally all versions are used either individually or in some combination.All pumping units designed for injection of various fluids (fluidal materials) for cementing, hydraulic formation fracturing, hydraulic sand-jet flushing of sand bridges, and other flushing operations in oil and gas wells are mounted on the chassis of motor vehicles (trucks), tractors, caterpillar (tracked) carriers, and specially made carriages.The operating parameters of the pumps (delivery and injection pressure) depend on the power of the drive and maximum and minimum speed of the engine and the pump. The pump delivery can be changed by changing the number of pump strokes without stopping the engine with the help of a gearbox (by gear shifting) and with stopping of the engine by installing cylinders of the required size. Replacement of the cylinders takes a lot of time and is not always possible in a continuous echnological process. In the existing pumping plants, the delivery variation range is inadequate. At the minimum rotation speed and cylinder diameter, the delivery remains extremely high, and for injecting the fluid into the bed the pressure has to be raised above what is permissible.Assigned by NGDU Zainskneft’, Ékogermet carried out updating of two types of pumps, namely, SIN32 and NPTs-32.In the three-plunger (triplex) acid treatment pump SIN32, for reducing the minimum delivery down to 1.0 m3/h,plungers having a diameter of 125 mm were replaced with plungers having a diameter of 55 mm. As a result, the theoretical pump delivery was reduced from 16 down to 3.3 m3/h. Further reduction of the pump delivery was achieved by reducing the rotation speed of the vehicle engine to the possible minimum (500–600 rpm).Simultaneously with this, a new design of packing glands (sealing devices) of plungers of the UPN55 type was developed.It was based on Zakharov mechanical seal [1], which demonstrated high reliability and durability in sucker-rod (oil) pumps. The sealing units and the pistons with a diameter of 55 mm were made for the SIN32 pump by ÉLKAMneftemash in Perm. Its finishing and testing were done by Ékogermet jointly with NGDU Zainskneft’.The design of the UPN55-type plunger seal is shown in Fig. 1. The combined seal consists of the main threestage mechanical seal 4 and an elastic sealingcollar 2. Each stage of the mechanical seal consists of ten rings that are elastically pressed against each other and simultaneously against the plunger surface. The rings are pressed against theplunger in pairs from the opposite sides. The next pair is turned relative to the preceding one by 90º. The rings are pressed in the axial direction by rubber rings of round cross section and in the radial direction, by rubber girdles with eccentric collars. The plunger 5 is made of steel 45 and is chromium-plated and the sealing rings are of bronze. Threecartridges with mechanical seals were installed in the housing bore 3 with a clearance that helps self-centering of the seals relative to the plunger. The cartridges are pressed together by a round nut 1 through a bushing with the sealing collar 2. There are holes in the housing for injecting oil and draining out the overflow into the receiving (suction) line of the pump.In contrast to the well-known elastic glands, the mechanical seal does not require periodic adjustments and ensures reliable operation of the assembly over a long period [2]. Use of the updated SIN32 pump having a UPN55 type of mechanical plunger seals confirmed that the proposed design operationally fit.From August through December 2003, NGDU Zainskneft’ carried out s even bottom-hole treatments (BHT) of six wells using the updated SIN32 pump. Different types of technological operations were carried out in the wells: mud acid BHT, muriatic (hydrochloric) acid BHT, injection of the reagents SNPKh-9021, MIAPROM, and RMD, for which SIN32 and ATs-32 pumping units were generally used. If acid or any other reagent could not be forced through (injected) at 12–15 MPa pressure, a low-capacity unit was connected with the SIN32 pump. In that case, the injection pressure dropped by 2–4 MPa。

序号中文英文1空压机Air compressor2压缩机Compressor3活塞式空压机Piston compressor4螺杆式空压机Screw compressor5滑片式空压机Vane compressor6离心式空压机Centrifugal compressor7涡旋式空压机Scroll compressor8无油空压机Oil-free compressor9移动式空压机Portable compressor10喷油螺杆空压机Oil injected screw compressor11储气罐Air Tank12压力表Pressure gauge13油管Oil Tube14风冷却器Air Cooler15油冷却器Oil Cooler16水冷却器Water Cooler17电机Motor18机头Air end19进气阀Inlet valve20温控阀Thermostatic valve21压力传感器Pressure sensor22吸附式干燥机Adsorption drier23冷冻式干燥机Freeze drier24吸附剂Adsorbent25冷煤Refrigerant26过滤器Filter27管路过滤器Pipeline filter28高效过滤器High efficiency air filter 29精密过滤器Fine filter30滤芯Filter element31除尘滤芯Dust removal filter32除油滤芯Oil removal filter33活性碳滤芯Activated carbon filter 34灭菌滤芯Sterilization filter35露点Dew point36压力露点Pressure dew point37自动排水器Automatic drain valve 38电子排水器Electronic drain valve 39智能排水器Intelligent drain valve 40机油Oil41油滤Oil filter42空滤Air filter43空滤总成Air filter housing44油分Air/Oil separator45外置油分Spin-on Air/Oil separator 46法兰Flange47外径Outside diameter48内径Inside diameter49高度Height50跑油Run oil51压差Differential pressure52干燥机Air drier53旋入式过滤器Spin-on Filter54维修包service kit55售后市场after market56压缩空气compressed air57软管Tube58汽水分离器steam separator59油水分离器oil-water separator 60安全芯safe filter61联轴器flex62卸荷阀unloading valve63最小压力阀Min pressure valve 64旁通阀by pass valve65单向阀check valve66替代品replacement67检测阀check valve68垫圈washer69库存store70止动板Lock plate71Motor speed 马达转速zr37vsd(zr45vsd)Delivery air 输送空气压力zr250zr250。

Sources of Pressure -Pumps and CompressorsFundamentally most pumps suitable for pumping hydraulic fluid will operate with air or gas, although most oil pumps make poor air compressors, and some compressors will not operate with incompressible fluid without modification.General considerations. The main requirements of a hydraulic pump capable of delivering sufficiently great a pressure to be of practical use, are:a. Means for controlling fluid leakage either by special seals of close working clearances.b. A substantially uniform, non-pulsating delivery.c. The absence of trapping of fluid during rotation, since the fluid is for all practical purpose incompressible.d. Mechanical balance to a sufficient degree to enable the pump to be run as fast as possible, to reduce bulk for a given output.e. Adequate provision for minimizing the effect of distortion of the working parts, casings, ect., due to the internal pressure in the pump.f. Low clearance volumes so that the pump will act momentarily during priming, or with aerated fluid, as a compressor, to discharge the air through the delivery line, instead of leaving It trapped in the pump.g. Adequate inlet valve or port provision to enable the pump to creat a good suction, or alternatively, as in the case of aircraft, to operate at high altitude, and with relatively thick fluids. It should be noted that the time of opening of the inlet valve or port is almost as important as the size of the port.The main requirements of a good compressor are:a. The smallest possible clearance volume compatible with mechanical clearance; this is because any gas compressed in the clearance volume will expand again instead of being discharged, and will thus adversely affect not only the output of the pump, but the maxium pressure that can be achieved.b. Except on low-pressure pumps, two or more stages of compression with as much intercooling between stages as possible. This is desirable, firstly, to reduce the wastage of work and output due to the gas being compressed adiabatically instead of isothermally, and, secondly, to reduce the overall loss of output due to clearance volume.c. Pre-compression of the air in the pump up to the pressure of the delivery line. Although the normal reciprocating pump with an automatic or spring-load delivery valve will ensure this, some of the rotary compressors have to be ported specially to obtain pre-compression, and with some it is nor possible at into the pump, and thewhole volume has again to be compressed. A rotary compressor with pre-compression cannot be operated with hydraulic fluid.d. Provision for air or water cooling of the cylinder so that the temperature of the air in the compression cannot be operated with hydraulic pump.e. Means for controlling gas leakages during compression either by pistonrings on a reciprocating piston compressor, or fine clearance on the rotary types.f. Adequate inlet valve area to prevent throttling of the incoming air, with the consequent loss of volumetric efficiency.The main types of pump and compressor use pistons, meshing gears or rotating vanes, these having been found to give good high pressure performance. Other types of pumps, such as centrifugal pumps or turbo-compressors, are not used for pressure systems as they do not produce high enough pressure to be useful.Variable Speed Hydraulic SystemsIt is particularly important on many hydraulic systems, as on machine tools, to be able to vary the speed of operation at will. This can be carried out in the following ways, sometimes more than one way being combined:a. By varying the pump output manually;b. By using several pumps in combinations;c. By restricting or throttling the output of a automatically variable delivery pump, or a pump accumulator system, or by throttling the inlet;d. By by-passing part of the pump output with a flow dividing valve;e. By varying the volume of the operating jack.1.Variation in pump delivery. Pump delivery can be varied bya. Alteration in its speed;b. Alteration of its stroke in a variable stroke type of pump;c. Using two or more pumps of different delivery in parallel so that by stopping and starting the pumps in various combinations different total deliveries can obtained.The first system is an easy one when the pump is electrically driven, although the electric motor involved is comparatively complicated for normal requirements. Mechanical variable speed gear boxes have been used successfully with constant speed electric drive.Several of the pump mechanisms previously described can readily be adapted to give a varying output by reducing the working strok manually by means of a controlwheel, etc.The third system is simple enough, but varies the output in fixed steps. Two pumps in parallel can give three ranges of output corresponding toPump A, Pump B, Pump A plus B.Three pumps in parallel can give seven steps corresponding toPump A, Pump A plus B, Pump B plus C,Pump B, Pump A plus C, Pump A plus B plus C.Pump C.Since, however, variable stroke pumps are readily available, such a complication as three pumps in parallel hardly seems worthwhile although the two-pump system is probably excellent for such duties as presses, etc. where a great of the working stroke is at low pressure, where a pump for the final working stroke. Automatic isolation of the low pump can be effected by a valve. Any normal type of automatic cut-out will operate in the low-pressure system to by-pass it, without interference from the other pump.2. Restriction of Pump Output. With a variable delivery pump the flow of oil to the system proper can be metered through a restriction, the delivery of the pump automatically adjusting itself to the reduced flow. An automatic flow control valve or throttle is to be preferred to a simple restrictor. This is an extremely simple system, but is liable to variation of speed owing to change in viscosity of the oil, temperature effects, etc. And the metering restriction may have to be adjusted from time to time to keep the speed constant. On the other hand, it is possible to evolve a restriction compensated for changes. By fitting the flow control valve in either jack line, control in one directions only can be exercised, but note that as the volumes of the jack returning to tank may not be same in both directions, the degree of speed control may not be similar.e of Flow dividing Valves. The flow dividing valves of various types are used to control the speed of a system by –passing part of the pump output, even if at the expense of a slight wastage of power. It is possible to use a selector incorporating several ports, which in turn control of fluid past several different flow dividing valves, giving different rates of flow for each position of the selector.4.Variation in hack volume. Another means of obtaining variable speed from a constant delivery pump is use jacks of different volumes (i.e. at different pressures), either in parallel, or using a multi-volume construction. If, for example, the machinetool side, etc, is filled with two operating jacks, by suitable selection varying speed of operation can be obtained corresponding toa. Use of jack A;b. Use of jack B;c. Use of jack A and B.If B=2A, the speeds are in the order 1,2,3. The combination of two pumps can obviously give 9 speeds, but at the expense of considerably more complication than would appear to be present with a variable delivery pump.Electrohydraulic Servo Systems1.Electrohydraulic systems use low-power electrical signals (of less than say 1 W) for precisely controlling the movements of large power hydraulic pistons and motors (which may be rated at say 7460W or more). The ‘interface’ between the electrical (control) equipment and the hydraulic (power) equipment is the so-called ‘electrohydraulic servo value’. These values are used on systems which must respond both quickly and accurately: aircraft controls are one example and numerically controlled machine tools another, although increasingly stringent specifications for other types of plant are extending their use into most fields. Many mechanisms which use other method s of control particulary if they already employ hydraulics could benefit from incorporating electrohydraulic techniques.Aseessing the suitability of an electronhydraulic servo value for a particular application requires some insight into the features of different valve types which this paper aims to give by explaining their dynamic characteristics. At the end of this paper are also some comments about electrical (control) supplies for such valves.The dynamics analysis of the hydraulic components within a value follows from the previous text and an outline of the dynamic featuresassociated with electromagnetic actuators will be included here a combination of both analyses would simulate a complete valve. However, it is rarely necessary to take full account of most valve s’ dynamic characteristics because their response is usually much more rapid than those of the systems they are used to control. This paper is intended more to give sufficient background information for effectively using such valves than for designing them.2.Flow Control ValveElectrohydraulic flow control valves have a moving coil or moving iron device which positions a main control spool with a high degree of accuracy. The moving coil or moving iron component is called the ‘armature’ and small deflections of the armature cause displacements of the spool either directly by a mechanical link or indirectly via pilot pressure. The main spool can be of the three–way or four-way type and maxium spool displacements are commonly less than 2mm. The widths of spool lands and valve and bore may be as small as 5μm. Particles of ‘dirt’in the fluid should be smaller than the radial clearance, for example smaller than 5μm or 0.0002 in. Each port opening caused by movement of the spool acts as an orifice metering fluid to and from the load.压力之源——泵和压缩机从原理上讲，泵送流体的大多数泵都可以泵送空气或气体，尽管大多数油泵几乎不作为空气压缩机来用，而某些压缩机未作调整则不可以输送非压缩性流体。

空压机空分【中英文实用版】英文文档：Title: Compressors and Air SeparationCompressors are mechanical devices designed to increase the pressure of a gas or air.They are widely used in various industries, such as manufacturing, mining, and oil refining, to enhance the efficiency of processes that require compressed air.The basic principle of a compressor involves drawing in low-pressure air and then reducing its volume by increasing its speed or using a series of pistons or screws.This compressed air can then be used to power tools, operate pneumatic systems, or serve as a feedstock in chemical reactions.On the other hand, air separation is a process used to separate the components of air into their individual gases, such as oxygen, nitrogen, and氩.This process is crucial in industries that require pure gases for manufacturing or research purposes.One common method of air separation is through the use of cryogenic distillation, where air is compressed and cooled to liquefy it.The liquid air is then separated into its components based on their boiling points, with oxygen and氮气being the primary products.Both compressors and air separation systems play vital roles in numerous industrial applications.Understanding their principles andapplications is essential for engineers and technicians working in these fields.中文文档：标题：空压机与空分空压机是一种机械设备，用于增加气体或空气的压力。

模拟气体运动的快速压缩机M.G. MEERE1, B. GLEESON1 and J.M. SIMMIE2Department of Mathematical Physics, NUI, Galway, Ireland2Department of Chemistry, NUI, Galway, IrelandReceived 25 July 2001; accepted in revised form 8 May 2002摘要:本文介绍了一种模型，其描述了天然气等气体混合物在快速压缩机器里压力，密度和温度的变化。

该模型包括一个耦合系统的非线性偏微分方程，还有正式的渐进化数字的解决方案。

使用渐近技术，一个简单的离散型算法表达了气体的压力，温度和密度的演化，核心数据来源于记录室的记录。

结果表明，使用实验数据该模型有有较好的计算和预测能力。

关键词：快速压缩机，震动波，奇异摄动理论1 导言1.1 快速压缩机一种快速压缩机器设备用来研究自燃的气体混合物在高压和高温条件下，尤其是在自动点火内燃机中（见[ 1-3 ]）。

一个典型的内燃机处于一个非常肮脏的和复杂的环境中，这也促使压缩机器的科学研究朝更清洁和更简单的设置方向着快速发展。

图1说明了两个活塞式快速压缩机器的基本情况。

然而，单活塞机，活塞在一头，另一端是结实的墙壁，更典型。

在本篇论文中，对单活塞和双活塞压缩机均有详尽的阐述。

快速压缩机器操作非常简单----活塞压缩处于封闭状态的气体混合物。

封闭的压缩气体造成气体压力，温度和密度迅速增加。

图1 （a），1 （b）和1（c）分别快速压缩机器之前，期间和之后的压缩情况。

这台爱尔兰国立大学的体积压缩机器初步比例最后为1:12 ，这个值也是其他机器的典型值。

在结束压缩时混合气体由于被压缩，温度升高，可能发生自燃现象。

在图2中，我们描述了H2/O2/N2/Ar混合物气体的压力概况（来自于布雷特的有关压力的文献）。

在这图，时间t = 0对应于压缩结束。