外文文献及翻译-压缩机-泵-制冷工程

外文翻译第20页共20页ChemicalandPetroleumEngineering,Vol.40,Nos.11–12,2004COMPRESSORS,PUMPS,REFRIGERATIONENGINEERINGUPDATINGPISTONPUMPSFOROILPRODUCTIONB.S.Zakharov,1G.N.Sharikov,2andE.G.Kormishin2Thethree-plungeracidtreatmentpumpSIN32andthetwo-cylinderdouble-actingpumpNPTs-32withfourworkingchambers(forcementingunits)havebeenupdatedtocontrolpumpdelivery.Thefluiddeliverydiagramsforpumpsofvariousdesignsareexaminedandthetestresultsarereported.Indrillingandoilproduction,single-actingthree-plunger(triplex)pumpsordouble-actingtwo-cylinder(duplex)pumpsareused.Ininjectingreagents(claydrillingmud,water,cement,acid,etc.)intowells,dependingonthetechnologyapplied，itisrequiredtoinjectthefluidinamountsrangingfromthemaximumtotheminimuminasingleoperation.Ifthebedacceptstheinjectedfluidwell,itbecomesnecessarytomaximizepumpdeliveryforquickcompletionoftheoperation.Ifontheotherhand,thebeddoesnotacceptthefluidwell,itbecomesnecessarytoreducepumpdeliverysoastorestricttheinjectionpressuretothesafelimit.Atpresent,becauseofwearofwell(down-hole)equipment,thepermissibleinjectionpressureisnothigherthan10–15MPa..Thedeliveryofapiston(reciprocating)oraplunger(displacement)typeofpumpcanbecontrolledinthefollowingways:•byinstallingseveralpumpswithidenticalordifferentpumpingcapacities;•bychangingthedriverotationspeed;•byusingcylinders(plungers)oftherequiredsize;•bychannelingapartofthefluidintoabypass;and•bydismountingoneorseveralvalves.Thefirstversionisusedessentiallyindrilling.Inoilproduction,generallyallversionsareusedeitherindividuallyorinsomecombination.Allpumpingunitsdesignedforinjectionofvariousfluids(fluidalmaterials)forcementing,hydraulicformationfracturing,hydraulicsand-jetflushingofsandbridges,andotherflushingoperationsinoilandgaswellsaremountedonthechassisofmotorvehicles(trucks),tractors,caterpillar(tracked)carriers,andspeciallymadecarriages.Theoperatingparametersofthepumps(deliveryandinjectionpressure)dependonthepowerofthedriveandmaximumandminimumspeedoftheengineandthepump.Thepumpdeliverycanbechangedbychangingthenumberofpumpstrokeswithoutstoppingtheenginewiththehelpofagearbox(bygearshifting)andwithstoppingoftheenginebyinstallingcylindersoftherequiredsize.Replacementofthecylinderstakesalotoftimeandisnotalwayspossibleinacontinuousechnologicalprocess.Intheexistingpumpingplants,thedeliveryvariationrangeisinadequate.Attheminimumrotationspeedandcylinderdiameter,thedeliveryremainsextremelyhigh,andforinjectingthefluidintothebedthepressurehastoberaisedabovewhatispermissible.AssignedbyNGDUZainskneft’,Ékogermetcarriedoutupdatingoftwotypesofpumps,namely,SIN32andNPTs-32.Inthethree-plunger(triplex)acidtreatmentpumpSIN32,forreducingtheminimumdeliverydownto1.0m3/h,plungershavingadiameterof125mmwerereplacedwithplungershavingadiameterof55mm.Asaresult,thetheoreticalpumpdeliverywasreducedfrom16downto3.3m3/h.Furtherreductionofthepumpdeliverywasachievedbyreducingtherotationspeedofthevehicleenginetothepossibleminimum(500–600rpm).Simultaneouslywiththis,anewdesignofpackingglands(sealingdevices)ofplungersoftheUPN55typewasdeveloped.ItwasbasedonZakharovmechanicalseal[1],whichdemonstratedhighreliabilityanddurabilityinsucker-rod(oil)pumps.Thesealingunitsandthepistonswithadiameterof55mmweremadefortheSIN32pumpbyÉLKAMneftemashinPerm.ItsfinishingandtestingweredonebyÉkogermetjointlywithNGDUZainskneft’.ThedesignoftheUPN55-typeplungersealisshowninFig.1.Thecombinedsealconsistsofthemainthreestagemechanicalseal4andanelasticsealingcollar2.Eachstageofthemechanicalsealconsistsoftenringsthatareelasticallypressedagainsteachotherandsimultaneouslyagainsttheplungersurface.Theringsarepressedagainsttheplungerinpairsfromtheoppositesides.Thenextpairisturnedrelativetotheprecedingoneby90º.Theringsarepressedintheaxialdirectionbyrubberringsofroundcrosssectionandintheradialdirection,byrubbergirdleswitheccentriccollars.Theplunger5ismadeofsteel45andischromium-platedandthesealingringsareofbronze.Threecartridgeswithmechanicalsealswereinstalledinthehousingbore3withaclearancethathelpsself-centeringofthesealsrelativetotheplunger.Thecartridgesarepressedtogetherbyaroundnut1throughabushingwiththesealingcollar2.Thereareholesinthehousingforinjectingoilanddrainingouttheoverflowintothereceiving(suction)lineofthepump.Incontrasttothewell-knownelasticglands,themechanicalsealdoesnotrequireperiodicadjustmentsandensuresreliableoperationoftheassemblyoveralongperiod[2].UseoftheupdatedSIN32pumphavingaUPN55typeofmechanicalplungersealsconfirmedthattheproposeddesignoperationallyfit.FromAugustthroughDecember2003,NGDUZainskneft’carriedoutsevenbottom-holetreatments(BHT)ofsixwellsusingtheupdatedSIN32pump.Differenttypesoftechnologicaloperationswerecarriedoutinthewells:mudacidBHT,muriatic(hydrochloric)acidBHT,injectionofthereagentsSNPKh-9021,MIAPROM,andRMD,forwhichSIN32andATs-32pumpingunitsweregenerallyused.Ifacidoranyotherreagentcouldnotbeforcedthrough(injected)at12–15MPapressure,alow-capacityunitwasconnectedwiththeSIN32pump.Inthatcase,theinjectionpressuredroppedby2–4MPa。Injectionwascompletedatthethird-gearspeedoftheengine.TheNGDUtechnologistsbelievethatconnectingalow-deliveryunitwithanSIN32pumpoffersthefollowingadvantages:•possibilityforcontinuousinjectionofacidsandreagentsincaseoflowintakecapacityofthebedandforpreventionofopeningupofthefractures(hydraulicfracturing)ofthecollectorandexcessiveriseinflowstringtestingpressure;•extendedoperatinglifeoftheflowstringbyvirtueofpressurestabilizationduringinjection;and•actionoftheacidthroughouttheperforationperiodandmorecompletereactionwiththerockwhentheacidinfiltratesthebed.SincethemaximallypossibledeliveryoftheSIN32pumpisreducedatleastfivefold,NGDUZainskneft’proposedtoperformallBHTsbyinjectingacidsintothebedwiththeaidofalow-capacityunitandallotheroperations,withastandardunit.Inthatcase,however,itwouldbenecessarytoplaceinthewell,insteadofone,twounits,whichhavetobehandled，bytwoteams,i.e.,itwillentailadditionalmanpowerandcosts.Moreover,alow-capacityunitisnotalwaysfullyutilized(doesnotoperatetofullcapacity)andoftenstalls.Thus,foraspecificsizeofthecylinderitisnecessarytoreducethepumpdeliverydowntotheminimumand,consequently,tobroadentherangeofcontrolofthepumpcapacitytowarditsreductionwhilemaintainingmaximallypossibledelivery.Inmultichamberpumps,thisissueisresolvedbyshuttingdown(disengaging)oneorseveralworkingchambers.Induplexplungerpumps,disengagingoneortwochamberswillcausesignificantlyunevendelivery,hydraulicshocks,disruptionofthebalanceofloadsonthedrive,andfailureofthepump.Indouble-actingtwo-cylinder(duplex)pumpshavingfourworkingchambersoftheNPTs-32(9T)type,whichareinstalled,forexample,inATs-32cementingunits,thedeliverycanbereducedbydisengagingtworodchambers,whichisachievedbyremovingtwodelivery(pressure)valves(Fig.2).ThedeliveryoftheNPTs-32typeofpump(duplex)havingfourchambersisQ=2(2F–ƒ)Sn,whereFisthecross-sectionalareaofthecylinderwithadiameterDc,dm2;ƒisthecross-sectionalareaoftherodwithadiameterdr,dm2;Sisthestrokelength,dm;andnisthenumberofdoublestrokesperminute.Ifthedelivery(pressure)valvesareremovedfromtherodchambers,thefour-chamberpumpturnsintoatwo-chamberonewithdifferentiallyactingcylinders.ThedeliveryofsuchapumpQ1=2FSn.Ifthevalvesfromthefrontchambersareremoved,thepumpdeliverycanbedeterminedbytheequationQ2=2(F–ƒ)Sn.Reductionofdeliverybydisengagingtherear(rod)chambersdependsonthefactork1=(2–ƒ/F)andbydisengagingthefrontchambers,onthefactork2=[2+ƒ/(F–ƒ)].Itcanbereadilyseenthatforreducingdeliverythefrontchambershavetobedisengaged.However,theoryandpracticeshowthatdisengagementoftherodchambersismoreadvisable.Thus,inNPTs-32typeofpumphavingcylindersof90,100,115,and127mmdiameterandrodsof45mmdiameterthedeliverycanbereduced1.75–1.87timesbyremovingthevalvesfromtherodchambers.Atlowloads(pressuredropnotmorethan15MPaandminimaldelivery),theengineofthemotorvehicleKrAZ-250canrunsteadilyatarotationspeedof550rpm.Inthesecondgearwithminimumenginerotationspeed,thedeliveryofapumpwithacylinderof90mmdiametercanbereduceddownto1.0m3/h.UnliketheSIN32pump,thedeliveryoftheNPTs-32pumpcanbecontrolledduringthetechnologicaloperationandreducingorraisingthedeliverycanchangethepumpoutput.Removalandinstallationoftwovalvesdonottaketoolong.Letusseehowtheuniformityofpumpdeliverywillchangeuponremovalofthevalves.Itiswellknownthattheinstantaneousoutputofasingle-cylindersingle-actingpumpisq=Frsin=0.5FSsinwhereristheradiusofthecrankandisthecrankshaft-turningangle.Theratioofthemaximuminstantaneousdeliverytotheaveragedeliveryofthepumpiscalledcoefficientofdeliverynonuniformity:=Qmax/Qav.Theaveragedeliveryofafour-chamberpumpinoneturnofthecrankQav=2(2F–ƒ)S/2·3.14.Themaximuminstantaneousdeliveryofapumphavingfourchambersandcranksturningata90°angle(Fig.3a)Qmax=FSsin45°=0.7FS.FortheNPTs-32typeofduplexpump(Dc=90–127mmanddr=45mm),=1.25–1.17.Afterthis,asthedelivery(pressure)valvesareremovedfromtherodchambers,theaveragedeliveryofatwo-chamberdifferential(differentially-acting)pump(Fig.3b)Qav=2FS/2·3.14=FS/3.14.Forsuchpumps,themaximuminstantaneousdeliveryQmax=(F–ƒ)Ssin45°=0.7(F–ƒ)S;=1.65–1.91.Forallothertypesofdeliveryvariationonaccountofremovalofvalves(insuccession,allfrontpressurevalvesorcrosswise,oneofthefrontchambersandanotheroftherodchambersinanothercylinder),thecoefficientwillbemuchhigher.Ingeneral,indifferentialpumps,toreducethenonuniformityinthepumpdelivery,theroddiameterissochosenthatitscross-sectionalareaishalfthatofthecylinder,i.e.,ƒ=0.5F.Inthatcase,thedeliverynonuniformitycoefficientwillbethelowestfortwo-cylinderdifferentialpumps:=0.7·0.5FS·3.14/FS=1.099.Foreachcylinder,inordertogetthecoefficient=1.099,itwillbenecessarytomakearodofafixeddiameter(63,70,80,and90mm,respectively).Butthen,ifthepumpoperateswithallthevalves,therewillbeasubstantialincreaseindeliverynonuniformityanddecreaseinpumpdelivery.IftheNPTs-32pumpisrequiredtooperateintwomodes,itisperhapsadvisabletomakearodof55mmdiameter(forcylindersof90and100mmdiameter)andof70mmdiameter(forcylindersof115and127mmdiameter).Inthatcase,thedeliverynonuniformitycoefficientwillbeidenticalforbothmodesofpumpoperation:=1.35–1.38.Thetheoreticalpumpdeliveryonaccountofincreaseinthediameteroftherodinaduplex-typepumpwilldecreaseroughlyby10%.Letusseehowthedeliverynonuniformitywillchangeifthepressure(delivery)valvesareremovedfromthefrontchambers(Fig.3c).Thedelivery,aswasnoticedearlier,willdecreasemorethantwofold.Theaveragedeliveryofaseries-producedNPTs-32pumpoperatingwithtworod-chambersisQav=2(F–ƒ)S/2·3.14=(0.75–0.87)FS/3.14.Themaximuminstantaneouspumpdelivery(forwardstroke)isQmax=FSsin45°=0.7FS.Theminimuminstantaneousdelivery(backstroke)isQmin=FSsin45°=0.7FS=0.7(0.25–0.125)FS.Thedeliverynonuniformitycoefficientis=(Qmax+Qmin)/Qav=3.87–3.45.Iftheroddiameterofsuchadifferentialpumpisincreased,thedeliverynonuniformitywillincreasefurtherand,therefore,itwillbenecessarytoremovevalvesonlyfromtherodchambers.Inseries-producedNPTs-32typeofpumpshavingfourworkingchambers,thenonuniformityofthefluidflowinthedelivery(pressure)andsuction(intake)lineswillbeidenticalandwilldependontheroddiameter.Thesmallerthecrosssectionalareaoftherod,thegreaterwillthefluidflowuniformitybe.Inthesuction(intake)lineofadifferentialpump,theflownonuniformityincreasesconsiderablybecauseonlytwochambersoperateandthecranksofthecrankshaftareturnedbynot180°,asisusualforsingle-actingtwo-cylinder(duplex)pumps,butby90°.Thedeliverynonuniformitycoefficientinthiscasewillbe=Qmax/Qav=2.199.Suctionconditionsofdifferentialpumps,justasofallothertypesofpistonpumps,canbeimprovedbyinstallingairsuctionsurgechambersinthesuctionlineandplacingthefluidtanksabovethepumpingunit.AnNPTs-32typeofdifferentialpumpwastestedinfieldconditionsintwomodes:withtwofrontworkingchambers(thedeliveryvalveswereremovedfromtherodchambers)andwithtworearrodchambers(thedeliveryvalveswereremovedfromthefrontchambers).Duringthetests,thedeliveryQandthepressurepweremeasuredatvariousrates.Cylinderswithadiameterof115mmandrodswithadiameterof45mmwereinstalledinthepump.ThetestresultsarereportedinTables1and2,respectively.Thetestsofthedifferentialpumpwereperformedintwowells.Inonewell(Table1),theresidualpressurewas10MPaandintheother(Table2),5MPa.ItisevidentfromTable1thatthemeasureddeliveriesareinaccordwiththecalculatedwithdueregardforthevolumetricefficiency.Theaveragevolumetricefficiencyofthepumpoperatingatthesecond-gearspeedis0.77andatthethirdgearspeed,0.65.Withincreaseoftherotationspeed,thevolumetricefficiencydecreasesandpressurefluctuationsrisefrom5to30%.Inspiteofhighdeliverynonuniformitycoefficient(=1.86),thepumpfunctionedsatisfactorily.ItfollowsfromTable2thatthemeasureddeliveriesarenotalwaysinaccordwiththecalculated.Thisissobecauseofwidepressurefluctuations(from70to550%)inthedelivery(pressure)line.Accuratemeasurementoftherotationspeedofanengineatsuchpressurefluctuationsispracticallyimpossible.Thus,itisprovedboththeoreticallyandbymeasurementsthataduplextypeofpumpcanbeconvertedtoadifferentialoneonlybyremovingthedelivery(pressure)valvesfromtherodchamber.Inthisregard,inordertoreducethedeliverynonuniformityofanNPTs-32typeofpump,itisnecessarythattheroddiameterbe55or70mm,dependingonthediameterofthecylinder.Basedonthestudiesmadeandtheoperationaldataobtained,thefollowingstepsmayberecommendedforimprovingtheseries-producedNPTs-32pump:•tomakepumpwithrodoftwodiameters,namely,55and70mm;•todesignvalvesystemwithoptionfordisengagingitautomaticallyormanuallywithoutdisassemblingthepump[3];and•todesignpistonandrodsystemshavingmechanicalseals.REFERENCES1.B.S.Zakharov,PistonandPlungerPumpsforOilProduction[inRussian],OAOVNIIOÉNG,Moscow(2002),p.52.2.N.G.Ibragimov,G.N.Sharikov,E.G.Kormishin,andB.S.Zakharov,ApplicationforInventionNo.2003125236.MechanicalSealofPlungerPump[inRussian],2003.3.N.G.Ibragimov,G.N.Sharikov,E.G.Kormishin,V.S.Isakov,andB.S.Zakharov,ApplicationforUseableModelNo.2004119790.Two-CylinderPistonPump[inRussian].译文化工和石油工程卷40第11刊C12，2004压缩机，泵，制冷工程

最新式的活塞泵专用油产品

B.S.Zakharov,G.N.Sharikov,和EGKormishin2

SIN32酸处理泵的三缸柱塞泵和两缸双作用泵的工作NPTs-32与四室(对影响固井优质率的单位)已经被更新,以便控制泵流量。用于各种流体输送泵的设计图进行检查和测试结果的报告。

在钻井和石油生产中，单作用三柱塞（三缸）泵或双作用两缸（双面）泵的使用。

在注射试剂(粘土钻井泥浆、水、水泥、酸等)到油井里,凭借自身的技术应用型£¬则需注入流体总量从最高到最低限度在一次操作步骤里面。假如机架注入流畅的流体，有必要最大限度的对泵的排量的操作快速完成。如果在另一方面，机架未能接受良好的流体，有必要以减少泵排量，以限制注射压力，控制在安全范围内。目前，由于井（井下）设备的磨损，其允许注射

的压力不高于10到15兆帕..

一个活塞（往复式）或柱塞（位移）类型的泵可控制在以下几个方面：

•通过安装几组具有相同或不同能力的泵获得不同的泵输送能力;

•通过改变驱动旋转转速;

•通过改变泵要求的要求的气缸（活塞）的尺寸；

•通过引导到一部分流体到一个旁路，

•用一个或几个拆装阀。

第一个版本主要用于钻井。在石油生产中，一般都使用单独或在某些组合的版本。

所有的抽油机设计各种液体注射fluidal)对影响固井优质率的材料所有抽油机组注入各种流体（流体材料）泥浆，水力压裂，液压砂喷射冲洗，及其他石油和天然气井的作业是安装在汽车（卡车）机箱，拖拉机，卡特彼勒（跟踪）载流子，和特制的车厢。

泵的（流量和注射压力）的操作参数取决于驱动器和发动机和泵最高和最小高动力。该泵流量的改变可以通过齿轮变速器（通过齿轮位移）在不停止发动机的情况下改变其泵的冲程，并在发动机停止时可通过安装所需气缸尺寸调节排量。对柱塞更换需要花费很多时间，柱塞的更换往往具有不可连续性。在现有的泵机装置，流量的变化范围是不够规范的。以最低转速和最小气缸直径、排量仍非常高，并注入底座流体的压力将高于可允许的范围。图1.UPN55-type密封相结合的SIN32柱塞泵

由NGDUZainskneft，kogermet进行了两种类型的泵的更新，即SIN32和NPTs-32.

在三柱塞（三缸）酸处理泵SIN32排量减少到最低1.0流量立方米/小时，柱塞直径125毫米，替换为活塞直径55毫米。以至于，泵理论输送率从16下降到3.3立方米/小时泵的流量进一步减少，通过减少发动机转速到可能的最低速度（500到600每分钟转速）。

同时，随着这一点，一种有关于填函料（密封装置）新的设计得到发展。正是以扎哈罗夫的机械密封[1]为基础，这展示了高可靠性和耐久性抽油杆（油）泵。密封装置和一个55毫米直径的活塞为SIN32泵|LKAMneftemash而做最终的完成和测试测试由kogermet和NGDUZainskneft完成。

该UPN55型柱塞密封设计如图1所示联合后的阀座主要由threestage机械密封4和弹性密封轴环2组成。机械密封的每个阶段都包括十个弹性环，同时对柱塞表面施加压力。密封环挤压在

柱塞的两个对侧面。接下来的一对相对于原来的转一个90度。环是压在圆截面橡胶圈轴向和径向方向，通过橡胶环束缚轴偏心。柱塞5是由45号钢，是镀铬和密封环镀铜组成的。三组

机械密封盒安装在箱体钻孔部位3，以利于泵的自动定心。使用这个方案被压在一起的一个圆螺母1通过套管与密封圈2结合。有孔的外壳注入了石油终止啦泵输出端的溢流。

相较于著名的弹性汽封，机械密封不需定期调整，这确保了程序长期可靠的运行[2]。使用最新的SIN32机械柱塞泵证实，拟议的设计密封UPN55类型在操作上是了可行的。

从八月到2003年12月NGDUZainskneft完成了7井底的六口井的处理（BHT）使用的最新SIN32泵。不同类型的操作技术，进行了井：泥酸甲苯，盐酸（盐酸）酸甲苯，试剂的SNPKh-9021注射，MIAPROM和RMD，为此SIN32和ATS-32抽油机被普遍使用。如果酸或任何其他试剂无法通过（注入）在12-15MPa的压力下，低容量的装置将与SIN32泵相连接。在这种情况下，注射压力下降2-4兆帕¡注射操作在发动机的第三档速度完成。图2.液压原理图的一部分:a）两缸泵和四个工作腔(双);b)与differentially-acting圆柱体,1)前面(头)工作室(横截面积F);2)后方(杆)室(横截面积F-ƒ);3)压力(交货)阀;4)吸(摄入)阀门;(5)杆截面ƒ)。TheNGDU技术专家认为，连接带有低配送单位的SIN32泵将提供下列优点：

•连续注入的可能性酸试剂,并在试剂如果较低的注射入机构,在防治过大的破损(水力压裂)的情况下和过度上涨压力下,测试出流量的压力。•凭借稳定的压力可以延长注射液管柱使用寿命;及

•在整个行动期间，穿孔与摇晃时，酸试剂更完整的浸润机构。

此后SIN32泵最大可能减少五倍流量，NGD​​UZainskneft提出了一种通过注射执行所有BHTs酸借助于一个low-capacity单元和所有其他操作,与标准件在这种情况下,然而,也有必要放置好,代替一个,两个单元,它们必须处理两队的,也就是说,它将需要额外的人力及成本此外，低容量的单位并不总是被充分利用（不运作满负荷），往往不起作用。

因此，对于一个特定大小的气缸，有必要以减少泵输出到最低限度，因此，以拓展其在减少对泵流量能力的控制范围，同时最大可能的保持限度的泵流量。

在多室泵，这个问题停止（分离）了一个或多个工作线程。

在双缸柱塞泵，脱离一个或两个分庭将造成明显不均匀排量，液压冲击，扰乱了驱动器上的负载平衡，导致泵的故障。

在双动两缸（双面），有四个工作腔32（9齿）类型已经安装。比方说，在ATS32固井单位，排量可通过减少分离两柱塞杆，从而降低两个阀流量（压力）（图2）。

NPTs-32型泵流量（双面），有四个腔室，是

其中F是DM2的汽缸横截面面积；f是活塞杆横截面面积，S为行程长度，n为每分钟双笔画数。

如果流量（压力）阀从活塞杆上移除，那么四腔泵变成两个间隔不同的气缸。这种输出泵Q1=2FSn。图3.图中的液体交付的活塞泵:1)duplex-type和b,c)differential-type(当前面和杆工作腔,分别在运作)。

如果正面的阀门被移除后，泵输送可以由第二方程式

减少泵排量取决于系数k1=(2–ƒ/F)和k2=[2+ƒ/(F–ƒ)]。它可以很容易地看出，对于减少排量是被分离开的。然而，理论和实践表明，活塞杆脱离是更明智的。

因此，泵NPTs-32型气缸具有90，100，115，127毫米和45毫米直径杆可减少泵排量通过移除活塞杆气阀1.75-1.87个杆长。在低负载（压力降不超过15MPa和最小的流量），对发动机KrAZ-250可以稳固的运行在550rpm的发动机转速。在与发动机转速最低第二齿轮，泵用的90毫米直径圆筒传递会降到1.0立方米/小时

不像