轮机英语翻译课文

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轮机英语课文

轮机英语课文

Lesson 1HOW DOES A MARINE DIESEL ENGINE WORK?The diesel engine is a type of internal combustion engine which ignites the fuel by injecting it into hot, high pressure air in a combustion chamber. The marine diesel engine is a type of diesel engine used on ships. The principle of its operation is as follows:A charge of fresh air is drawn or pumped into the engine cylinder and then compressed by the moving piston to very high pressure.When the air is compressed, its temperature rises so that it ignites the fine spray of fuel injected into the cylinder. The burning of the fuel adds more heat to the air charge, causing it to expand and force the engine piston to do work on the crankshaft which in turn drives the ship's propeller.The operation between two injections is called a cycle, which consists of a fixed sequence of events. This cycle may be achieved either in four strokes or two. In a four-stroke diesel engine, the cycle requires four separate strokes of the piston, i.e. suction, compression, expansion and exhaust. If we combine the suction and exhaust operations with the compression and expansion strokes, the four-stroke engine will be turned into a two-stroke one, as is shown in Figures l (a)-(d).The two-stroke cycle begins with the piston coming up from the bottom of its stroke, i.e. bottom dead centre (BDT), with the air inlet ports or scavenge ports in the sides of the cylinder being opened (Fig. 1 (a)). The exhaust ports are uncovered also. Pressurised fresh air charges into the cylinder, blowing out any residual exhaust gases from the last stroke through the exhaust ports.As the piston moves about one fifth of the way up, it closes the inlet ports and the exhaust ports. The air is then compressed as the piston moves up (Fig. 1 (b)).When the piston reaches the top of its stroke, i.e. the top dead center (TDC), both the pressure and the temperature of the air rise to very high values. The fuel injector injects a fine spray of fuel oil into the hot air and combustion takes place, producing much higher pressure in the gases.The piston is forced downward as the high pressure gases expand (Fig. 1 (c)) until it uncovers the exhaust ports. The burnt gases begin to exhaust (Fig. 1(d)) and the piston continues down until it opens the inlet ports. Then another cycle begins.In the two-stroke engine, each revolution of the crankshaft makes one power or working stroke, while in the four-stroke engine, it takes two revolutions to make one power stroke. That is why a two stroke cycle engine will theoretically develop twice the power of a four stroke engine of the same size. Inefficient scavenging and other losses, however, reduce the power advantage to about 1.8.Each type of engine has its application on board ship. The low speed (i.e. 90 to 120 r/min) main propulsion diesel operates on the two-stroke cycle. At this low speed the engine requires no reduction gearbox between it and propeller. The four-stroke engine (usually rotating at medium speed, between 250 to 750 r/min) is used for alternators and sometimes for main propulsion with a gearbox to provide a propeller speed of between 90 to 120 r/min.READING MATERIALWORKING CYCLESA diesel engine may be designed to work on the two-stroke or on the four-stroke cycle. Both of them are explained below.The Four-Stroke CycleFigure 2 shows diagrammatically the sequence of events throughout the typical four-stroke cycle of two revolutions. It is usual to draw such diagrams starting at TDC (firing) but the explanation will start at TDC (scavenge). Top dead centre is some times referred to as inner dead centre (IDC).Proceeding clockwise round the diagram, both inlet (or suction) and exhaust valves are initially open. (All modern four-stroke engines have poppet valves.) If the engine is naturally aspirated, or is a small high-speed type with a centrifugal turbocharger, the period of valve overlap, i.e. when both valves are open, will be short, and the exhaust valve will close some 10o after top dead centre (ATDC).Propulsion engines and the vast majority of auxiliary generator engines running at speeds below 1,000 r/min will almost certainly be turbocharged and will be designed to allow a generous throughflow of scavenge air at this point in order to control the turbine blade temperature. In this case the exhaust valve will remain open until exhaust valve closure (EVC) at 50-60o ATDC. As the piston descends to outer or bottom dead centre (BDC) on the suction stroke, it will inhale a fresh charge of air. To maximise this, balancing the reduced opening as the valve seats against the slight ram or inertia effect of the incoming charge, the inlet (suction) valve will normally held open until about 25-35o ABTC (145-155o BTDG). This event is called inlet valve closure (IVC). The charge is then compressed by the rising piston until it has attained a temperature of some 550o C. At about 10-20o BTDC (firing), depending on the type and speed of the engine, the injector admits finely atomised fuel which ignites within 2-7o (depending on the type again) and the fuel burns over a period of 30-50o, while the piston begins to descend on the expansion stroke, the piston movement usually helping to induce air movement to assist combustion.At about 120-150o ATDC the exhaust valve opens (EVO), the timing being chosen to promote a very rapid blow-down of the cylinder gases to exhaust. This is done: (a) to preserve as much energy as is practicable to drive the turbocharger, and (b) to reduce the cylinder pressure to a minimum by BDC to reduce pumping work on the 'exhaust' stroke. The rising piston expels the remaining exhaust gas and at about 70-80o BTDC the inlet valve opens (IVO) so that the inertia of the outflowing gas, plus the positive pressure difference, which usually exists across the cylinder by now, produces a through flow of air to the exhaust to ’scavenge’ the cylinder.If the engine is naturally aspirated the IVO is about 10o BTIDC. The cycle now repeats.The Two-Stroke CycleFigure 3 shows the sequence of events in a typical two-stroke cycle, which, as the name implies, is accomplished in one complete revolution of the crank. Two-stroke engines invariably have ports to admit air when uncovered by the descending piston. The exhaust may be via ports adjacent to the air ports and controlled by the same piston (loop scavenge) or via poppet exhaust valves at the other end of the cylinder (uniflow scavenge).Starting at TDC combustion is already under the way and the exhaust opens (EO) at 110-120o ATDC to promote a rapid blow-down before the inlet opens (IO) about 20-30o later (130-150o ATDC). In this way the inertia of the exhaust gases-- moving at about the speed of sound-- iscontrived to encourage the incoming air to flow quickly through the cylinder with a minimum of mixing, because any unexpelled exhaust gas detracts from the weight air entrained for the next stroke.The exhaust should close before the inlet on the compression stroke to maximise the charge, but the geometry of the engine may prevent this if the two events are piston controlled. It can be done in an engine with exhaust valves.At all events the inlet ports will be closed as many degrees ABDC as opened before it (i.e. again 130-150o BTDC) and the exhaust in the same region.Injection commences at about 10-20o BTDC depending on speed and combustion lasts 30-50o, as with the four-stroke.。

轮机英语课文 2

轮机英语课文 2

Lesson 39 Maritime Labour Convention 2006TextThe Maritime Labour Convention(MLC2006)was adopted by ILO in February2006,which provides comprehensive rights and protection at work for the world’s more than 1.2 million seafarers.Regulation 2.3-Hours of work and hours of rest.Purpose:To ensure that seafarers have regulated hours of work or hours of rest.1.Each Member shall ensure that the hours of work or hours of rest for seafarers are regulated.2.Each Member shall establish maximum hours of work or minimum hours of work rest over given periods that are consistent with the provisions in the Code.Standard A 2.3-Hours of work and hours of rest1.For the purpose of this Standard,the term:(a)hours of work means time during which seafarers are required todo work on account of the ship ;(b)Hours of rest means time outside hours of work ;this term does notinclude short breaks.2.Each Member shall within the limits set out in paragraphs 5 to 8 of this Standard fix either a maximum number of hours of work which shall not be exceeded in a given period of time ,or a minimum number of hoursof rest which shall be provided in a given period of time .3.Each Member acknowledges that the normal working hours’standard for seafarers, like that for other workers ,shall be based on an eight -hour day with one day of rest per week and rest on public holidays. However, this shall not prevent the Member from having procedures to authorize or register a collective agreement which determines seafarers’normal working hours on a basis no less favourable than this standard.4.In determining the national standards ,each Member shall take account of the danger posed by the fatigue of seafarers, especially those whose duties involve navigational safety and the safe and secure operation of the ship.5.The limits on hours of work or rest shall be as follows:(a) maximum hours of workshall not exceed:(i)14hours in any seven 24-hour period ;and(ii)72 hours in any seven-day period ;or(b)minimum hours of rest shall not be less than :(i) ten hours in any 24-hour period ;and(ii)77 hours in any seven-day period.6.Hours of rest may be divided into no more than two periods ,one of which shall be at least six hours in length,and the interval between consecutive periods of rest shall not exceed 14 hours .7.Musters,fire-fighting and lifeboat drills, and drills prescribed bynational laws and regulations and by international instruments,shall be conducted in a manner that minimizes the disturbance of rest periods and does not include fatigue.8.When a seafarer is on a call,such as when a machinery space is unattended,the seafarer shall have an adequate compensatory rest period if the normal period of rest is disturbed by call-outs to work.9.If no collective agreement or arbitration award exists or if the competent authority determines that the provisions in the agreement or award in respect of paragraph 7 or 8of this Standard are inadequate,the competent authority shall determine such provisions to ensure the seafarers concerned have sufficient rest.10.Each Member shall require the posting ,in an easily accessible place ,of a table with the shipboard working arrangements,which shall contain for every position at least:(a) the schedule of service at sea and service in port;and(b) the maximum hours of work or the minimum hours of rest required by national laws or regulations or applicable collective agreement.11.The table referred to in paragraph 10 of this Standard shall be established in a standardized format in the working language or languages of the ship and in English.12.Each Member shall require that records of seafarers ’daily hoursof work or of their daily hours of rest be maintained to allow monitoring of compliance with paragraphs 5 to 11 inclusive of this Standard .The records shall be in a Standardized format established by the competent authority taking into account any available guidelines of the International Labour Organization or shall be in any standard format prepared by the Organization,They shall be in the languages required by paragraph 11 of this Standard .The seafarers shall receive a copy of the records pertaining to them which shall be endorsed by the master,or a person authorized by the master,and by the seafarers.13.Nothing in paragraphs 5 and 6of this Standard shall prevent a Member from having national laws or regulations or a procedure for the competent authority to authorize or register collective agreements permitting exceptions to the limits set out .Such exceptions shall,as far as possible ,follow the provisions of this Standard but may take account of more frequent or longer leave periods or the granting of compensatory leave for watchkeeping seafarers or seafarers working on board ships on short voyages.14.Nothing in this Standard shall be deemed to impair the right of the master of a ship to require a seafarer to perform any hours of work necessary for the immediate safety of the ship,persons on board or cargo ,or for the purpose of giving assistance to other ships or persons in distress at sea .Accordingly,the master may suspend the schedule of hoursof work or hours of rest and require a seafarer to perform any hours of work necessary until the normal situation has been restored.As soon as practicable after the normal situation has been restored,the master shall ensure that any seafarers who have performed work in a scheduled rest period are provided with an adequate period of rest.(a)in ships other than passenger ships ,an individual sleeping room shall be provided for each seafarer; in the case of ships of less than3,000gross tannage or special purpose ships ,exemptions from this requirement may be granted by the competent authority after consultation with the shipowners’ and seafarers’ organizations concerned;(b)separate sleeping rooms shall be provided for men and for women;(c)sleeping rooms shall be of adequate size and properly equipped so as to ensure reasonable comfort and to facilitate tidiness;(d)a separate berth for each seafarer shall in all circumstances be provided;(e)the minimum inside dimensions of a berth shall be at least 198 centimetres by 80 centimetres;(f)in single berth seafarers’ sleeping rooms the floor area shall not be less than:(i)4.5square metres in ships of less than 3,000 gross tonnage.(ii)5.5square metres in ships of 3,000 gross tonnage or over but less than 10,000gross tonnage,(iii)7 square metres in ships of 10,000gross tonnage or over.(g)however ,in order to provide single berth sleeping rooms on ships of less than 3,000gross tonnage ,passenger ships and special purpose ships,the competent authority may allow a reduced floor area;(h)in ships of less than 3,000gross tannage other than passenger ships and special purpose ships ,sleeping rooms shall not be less than7square metres;(i)on passenger ships and special purpose ships the floor area of sleeping rooms for seafarers not performing the duties of ships’officers shall not be less than :(i) 7.5 quare metres in rooms accommodating two persons,(ii)11.5quare metres in rooms accommodating three persons,(iii)14.5quare metres in rooms accommodating four persons;(j)on special purpose ships sleeping rooms may accommodate more than four persons;the floor area of such sleeping rooms shall not be less than 3.6 square metres per person;(k)on ships other than passenger ships special purpose ships,sleepingrooms for seafarers who perform the duties of ships’officer,where no private sitting room or day room is provided ,the floor area per person shall not be less than :(i)7.5 square meters in ships of less than 3,000 gross tonnage,(ii)8.5 square meters in ships of less than 3,000 gross tonnage or over but less than 10,000gross tonnage,(iii)10 square meters in ships of less than 10,000 gross tonnage or over;(l) on passenger ships and special purpose ships the floor area for seafarers performing the duties of ships’ officers where no private sitting room or day room in provided ,the floor area per person for junior officers shall not be less than 7.5 square metres and for senior officers not be less than 8.5 square metres ;junior officers are understood to be at the operational level,and senior officers at the management level;(m)The master,the chief engineer and the chief navigating officer shall have ,in addition to their sleeping rooms,an adjoining sittingroom ,day room or equivalent additional space ;ships of less than 3,000 gross may be exempted by the competent authority from this requirement after consultation with the shipowners’ and seafarers’ organizations concerned;(n) for each occupant,the furniture shall include a clothes locker of ample space (minimum 475 litres)and a drawer or equivalent space of notless than 56litres;if the drawer is incorporated in the clothes locker then the combined minimum volume of the clothes locker shall be 500 litres.it shall be fitted with a shelf and be able to be locked by the occupant so as to ensure privacy;(o)each sleeping room shall be provided with a table or desk,which may be of the fixed,drop-leaf or slide-out type,and with comfortable seating accommodation as necessary.。

轮机英语新版教材译文(党坤)

轮机英语新版教材译文(党坤)

船舶类型 根据载运货物以及货物装卸方式的不同,船舶可分成不同的种类、船级、类型,详见表 1。 最大的三类船型是集装箱船、散货船(装运散装货物如谷物、煤炭、矿石等)和液货船。 上述船型又可根据船级和船型进行更详细的划分。因此,液货船又可以划分为油船、液化气 体船和散装液体化学品船,但是有些时候是组合式的,比如油船/化学品船。 表 1 仅给出了大体的分类。实际中,还有其他组合船型,如多用途散货集装箱船就是一 例。
二冲程循环从活塞离开其行程底部,即下止点(BDC)向上运行开始,气缸侧面的进气口 即扫气口是打开的(图 2-1(a)),排气口也是打开的。经压缩的新鲜空气充入气缸,通过排气 口将上一行程的残余废气吹出。
船舶可明显划分成不同的三个区域:货舱区、居住区和机舱。根据船舶的类型,每艘船 舶各个部分的大小和功能都多种多样。比如油船,货物区由多个纵向和横向隔壁分割成货舱。 其甲板上下均有大量的货物管系。杂货船有多个货舱,其宽度和船宽相当,沿船长方向由多 个横向隔壁分割而成。甲板装有货物装卸设备,并且货舱开口使用钢制货舱盖封闭。船上居 住区的面积将足够满足船员生活的需要,同时还为驾驶台和通信中心提供空间。机舱大小由 所安装的机器的类型以及必要的辅助设备所决定。不过,客船拥有较大的居住区以满足旅客 的需要。(客船)机舱因为需安装空调、减摇鳍以及其他和旅客相关的设备,所以空间可能会 较大。
低速柴油机 常见的典型低速柴油机的平面图和正面图如图 1-1 所示。在该布置图中,柴油机为六缸 直接驱动式。(图中)唯一可见的辅助设备为位于上层的柴油发电机和下层的空压机。机舱中
3
的其他辅助设备包括另外的发电机、油水分离器、造水机、若干泵和换热器。辅锅炉和废气 换热器可安装于通往烟囱的机舱上部空间。在(机舱)上层,还有各种各样的工作间、仓库和 机械控制室。

《轮机英语》汉英互译

《轮机英语》汉英互译

二、气缸 和气 缸盖
在扫气箱上部,每个气缸装有一个坚固的铸铁框架。这些框架称作气缸体或冷却水套,并
带有垂直法兰,与扫气箱一样,可用螺栓将各框架连成首尾两组。
基座、机架和气缸体用长贯穿螺栓连到一起,形成一个较大的坚实结构,减少了使用时产
生的变形及振动。
气缸套由铸铁制造,缸套表面有时镀铬。气缸套向下延伸到扫气箱。缸套与扫气箱顶部
当活塞上行到行程底部,即上止点(
时空气的压力和温度都上升到很高的数值。此时喷
油器把很细的油雾喷入炽热的空气中,燃烧开始,在气体中产生更高的压力。
随着高压气体的膨胀,活塞被推动下行「图
」直到它打开排气口,燃烧过的气体开始
排 出[ 图
,活塞继续下行直到它打开进气口,另一个循环开始。
在二冲程柴油机中,曲轴转一周产生一个动力行程,即做功行程;而在四冲程柴油机中,曲
使发动机活塞对曲轴做功,随之驱动螺旋桨. 两次 喷油期间 的运转过 程叫一个 工作循环 。它
由一些程序固定的过程组成。这个循环可在二个行程或四个行程内完成。四冲程柴油机的工
作循环需四个独立的活塞行程,即吸气、压缩、膨胀和排气。如果我们把吸气和排气行程与压
缩和膨胀行程结合起来,四冲程柴油机就变成了二冲程柴油机,如图
课文注释
机座在大多数情况下是焊接结构,用螺栓固定在构成船舶双层底的底座上。
该句为复合句,包含由
引导的两个定语从句,分别限制主语
和宾语
它在横向借助于侧楔垫螺栓,在纵向借助于端楔垫螺栓固定。 该句为并列句,由 连 接 。第二个分句省略了“
形机架顶部有一个结实的框架结构叫扫气箱。 该扫气箱分若干段,每段均带有垂直法
兰,通过螺栓可将它们在链传动装置前
缸的部分连成一体,链传动装置后

轮机英语教材后315道翻译

轮机英语教材后315道翻译

1 以任意吃水漂浮在水面上的载货船舶,它的排水量等于船体置换掉的相应质量的水。

;ship in loaded condition 船舶处于有负载的状况;arbitrary 任意的 water line (船的)吃水线,水位;displacement 排水量;equal to 等于,与……相等;relevant mass 相应的质量;displace 取代,置换2 船舶的排水量等于相应装载货物船舶的总重量。

;total weight 总重量;all told 副词,表示总计,总共,合计,用在这里强调是载货船舶总共的质量。

3 哪句话不正确?造船工程师与轮机员在职责上处于截然不同的区域。

;(应该是在一些范围内有所重叠);distinct divisions 截然不同的区域;naval architect 造船工程师,验船师;marine engineer 轮机员4 为什么中速柴油机驱动的船舶需要齿轮箱?为了安装固定螺旋桨轴。

(即螺旋桨轴不是直接由主机带动的,而是连接到齿轮箱的);gearbox 齿轮箱;fix 固定,安装,修理;propeller shaft 螺旋桨轴5 螺旋桨,为了更有效率的工作,必须以相对较低的速度旋转。

;in order to 为了;efficiently 有效率地;relatively 相关的,相对的6 在柴油机里,燃油的燃烧直接提供了热能,而燃烧过的气体混合物则作为工作介质将热能转变为机械能(即推动活塞做往复运动)。

;working medium 工作介质;change … to …将…转变为…;the burned gas mixture 燃烧过的气体混合物,即燃气7 在柴油机里,燃气作为工作介质并将热能转换为机械能,连杆则将往复运动转换为回转运动。

;working medium 工作介质;change … to …将…转变为…;the burned gas mixture 燃烧过的气体混合物,即燃气;reciprocating movement 往复运动;rotary movement 回转运动8 二冲程和四冲程柴油机的区别之一是:二冲程机工作中没有吸气过程。

轮机英语 翻译 lesson 4

轮机英语   翻译 lesson 4

第4 课燃油系统单燃料系统普通(燃油)系统包括从燃料储存舱到气缸喷射的整个燃油流动过程。

就离心分油机推荐使用而言,总是认为燃油在交付时是受到污染的,因此应当在使用前彻底净化以清除固体及液体污染物。

油中的固体污染物主要是铁锈、沙子、灰尘以及精炼过程中的催化剂。

液体污染物主要是水即淡水或者海水。

油中的杂质会致使燃油泵、喷油器损坏,导致缸套磨损加剧和排气阀座损毁。

使用没有充分净化的燃油还可能会加剧气路和透平增压器叶面的脏污。

只有使用离心分油机才能保证燃油有效净化。

最新的渣油离心处理的实验结果表明,尤其是存有分离催化粉末杂质时,离心分油机串联运行,即用分水机/分杂机串联模式,能达到最佳清洁效果。

对于传统的离心分油机来说这个建议是正确的。

对于更现代化的、可以处理在15℃时9密度大于991 kg/m3 燃油的机型来说,应遵循制造商的具体说明。

考虑到某些燃油标准的燃油分级中不包括密度界限和实际交付的燃油有时候密度会超过15℃时991 kg/m3 传统界限这样的实际情况,离心分离处理作了改进,以确保能处理更高密度的燃油。

这样的设备可以把15℃时密度高达1 010 kg/m3 的燃油中的油水充分分离,因此,该密度成为燃油等级中新的密度极限值。

因此如果安装了合适的分油机,发动机完全可以使用高密度的燃油。

分油机应按照厂家说明并联或者串联使用。

设计特性和工作原理燃油系统是重质燃油和柴油共用的加压的系统。

加压的目的主要是避免为使重油达到喷射所需的10~15 cSt 的黏度而进行加温时系统中可能会出现的沸腾和气穴现象(图4-1)。

海上运行从燃油舱来的燃油在进入日用柜之前必须经离心分油机(净化)处理。

燃油从日用柜进入到供油系统。

在供油系统中,燃油经供油泵泵送进入4 bar 压力的循环系统。

供油系统可以包括一个细滤器。

供油泵设溢流阀的旁通管路回油,以此保持循环回路中的压力稳定而不受实际消耗量的影响。

循环回路中的泵将油压从供油压力提高到7~8 bar 的稳定进机压力。

轮机英语翻译课文

轮机英语翻译课文

LESSON 1Diesel enginesThe majority of ships around the world continue to be powered exclusively by diesel engines.世界范围内大多数船舶都是采用柴油机作为动力。

The predominance of diesel engines has come from improved engine efficiencies and designs compared to other forms of propulsion such as steam or gas turbines.与蒸汽机、燃气轮机等形式的动力装置相比,无论是效率上的提高,还是设计上的进步,柴油机都体现出了一定的优势。

Many combinations and configurations of diesel engine power plant exist. All provide the energy to do the work of moving the ship using diesel engines.存在有很多种联合形式及结构形式的柴油机动力装置,他们都能够利用柴油机为船舶提供推动力。

Slow speed diesel engines 低速柴油机Slow speed diesel engines are large, especially tall, and heavy and operate on the two-stroke cycle.低速柴油机是体积较大、缸体较长、机身较重的二冲程柴油机。

These are the largest diesel engines ever built. Engine powers up to 100 000kw are available from a single engine.它们是已建造过的最大型的柴油机,它们的单机可用功率可达100000 kw。

新版轮机英语unit25_Anchor_windlass_and

新版轮机英语unit25_Anchor_windlass_and

The most conventional types of equipment in use are as follows.
Windlasses
This equipment is self-contained (独立的)and normally one prime mover drives two cablelifters and two w a r p e n d s ( 绞 缆 端 ) ,
Average cable speeds vary between 5-7 m/sec during this operation
2.The windlass must be able heave a certain weight of cable at a specified speed(额定转速) .
Due to the low speed of rotation required of the cablelifter whilst heaving anchor,
(345r/min) a high gear reduction (齿轮减速机构) is needed when the windlass is driven by a high speed electric of hydraulic motor.
The cable lifter unit(锚链轮) , show in Fig.25-1, is mounted so as to raise and lower the cable from the spurling pipe(锚链管) ,which is at the top and center of the chain or cable locker(锚链舱) .
Worm geared(涡轮蜗杆) automatic mooring winches are uncommon

船舶轮机英语lesson_11

船舶轮机英语lesson_11

不能喷油通常是由于燃油喷射泵故障。但是,如 果通向喷油阀的燃油管路不能清除空气,即使喷 射泵良好,燃油的注入可能也会延迟。
If there is no fuel injected into the cylinders, the possible causes are fuel gasification( 汽 化 ) due to excess temperature, pressure before fuel injection pumps too low, fuel too cold, except the troubles in the injection pumps. Sluggish(行动迟缓的) movement of maneuvring gear, incorrect adjustment of maneuvring gear, shut-down devices on engine having operated, maneuvring air pressure to governor too low, failure in governor may be the case also. These can be indicated by too low fuel pump index. 如果没有燃油注入气缸,除了油泵的原因外,可能 是由于燃油温度过高导致燃油气化,燃油喷油泵前 压力过低,燃油过冷。操纵机构迟缓,调节不当, 机器停车设备动作,调速器操纵压力过低,调速器 失效。可通过燃油泵刻度过低表示。
It is not uncommon for the lubricating oil pump suction to be clogged with the dirt left in the crankcase after work has been done on the engine. Excessive clearances in the main or crankpin bearings will sometimes be indicated by loss of pressure in the lubricating system before any bearing knock is heard.

轮机英语新教材电子版Lesson18airconditioningsystem

轮机英语新教材电子版Lesson18airconditioningsystem

轮机英语新教材电⼦版Lesson18airconditioningsystem Lesson18 air conditioning systemShips travel the world and are therefore subject to various climatic conditons .the crew of the ship must be provided with reasonable conditions in wihich to work regardless of the weather.Temperture alone is not sufficent measure of condition acceptable to the human body. Relative humidity iin conjunction with temperature more truly determines the environment for human comfort .Relative humidity ,expressed as a percentage, is the ratio of the water vapour pressure in the air tested, to the saturated vapour pressure of air at the same temperature. The fact that less water can be absorbed as air is cooled and more can be absored when it is heated is the major consideration in air conditioning system design. Other factors are the nearness of heat sources, exposure to sunlight, sources of cold and the insulation provided around the space(Fig.18-1).An air conditioning system aims to provide a comfortable working environment regardless of outside conditions. Satisfactory air treatment must involve a relatively "closed" system where the air is circulated and returned. However, some air is "consume" by humans and some machinery so there is a requirement for renewal. Public rooms and accommodation will operate with a reduced percentage of air renewal since the conditionig cost of 100% renewal would be considerable.Air conditioning systems fall into two main classes: individual unit system, in which each room contains its own small refrigeration plant and fan and air cooler; and central systems, where larger refrigeration machinery unit are installed and their out put distributed about the ship by a variety of means.Self-contained units are noisier than central systems, require more maintenance and have been found to have a relatively short life (about 7 years).The single duct system only allows for adjustment of temperature in each room by the occupant manually controlling the air volume admitted. It is thus less flexible than any of the other systems, which allow individual temperature control, at least of sections of the ship if not individual rooms.With ducted systems, the modern tendency is to use "high velocity" in the air ducts with fans generating up to 2550 mbar(250 mm H2O) pressure compared to "low velocity" systems with fans generating up to 520 mbar(50mm H2O). This tendency helps installation as the size of ducts is reduced and prefabricated standard ducts can be used, but it incurs the heavier running costs of more powerful fans. Air terminals lined with sound insulation material are necessary to reduce the noise passing into the room with high velocity systems.In a typical marine pattern self-contained unit, air circulation is usually effected by means of a centrifugal fan, for quiet running, and a direct expansion cooler served by a hermetic compressor. Water cooled condensers are used. As these contain small water passages, choking develops rapidly with direct sea water circulation and a better method is to circulate with fresh water, itself cooled in a sea water/fresh water heat exchanger.Control is on/off by a thermostat sensing the temperature of air returning to the unit.The cooling coil of the central unit may be of the direct expansion, brine or chilled water cooled type.When cooling is by direct expansion, a separate steam heater coil is fitted in the unit for winter heating.With brine or water coolers, a central heater is used so that the same coil serves for summer or winter. Thermostatic control is provided sensing air delivery temperature itself, the temperature of the room, or the return air temperture.All types of thermostats are found in air conditioning systems, direct acting, pneumatic and electrical. In themselves, they are all satisfactory instruments, but the results they achieve are dependent on the correct sitting of their sensing elements. Even the site for a direct acting thermostst to control one single berth cabin must be chosen with care-if it is masked behind curtains, or too far away from the air inlet control will be too sluggish.The correct location for a thermostat to control a block of cabins is more difficult to find . One can pick on a "typical" cabin , but if the occupation opens his porthole he can upset the whole block. Another possibilility is to site the thermostat in the alleyway of the block of cabin . This position may be affected more by an open door or draguht in the alleyway tthan by the temperature of the cabins . Yet another possiblility is to site the thermostat in the recirculation grill is to close to an outside door , this position too can be affected by outside air temperature when the door is open ,rather than by cabin temperature. General operation of the air conditoning installationThe first enssential in operating the air cooling appliances through out the ship is to hhave all thermostats correctly set and correctly functioning . In extreme weather conditions , either hot or coold , control of the plant usually present few diffculties . The capacity of many installations is such that under tropical conditions nearly all control valves move to the full open position. Although automated control has been lost ,internal conditions are by and large acceptable.Control diffculties arise in intermediate weather conditions when there is a call for only a small amout of cooling. The worst case is when part of the ship,say inboard cabins against the engine room , require cooling and other parts ,say exposed upper cabins , require warming .For this intermediate condition,thermostats must be correctly set by trial and error. It is found that a uniform setting of say 21°C throughout the ship is not satisfactory ,but slight variations of a few degrees up or down are needed to suit particular regions of the ship. Unfortunately, these variations in thermostat setting are not always the same for the cooling and heating condition and frequent resetting may be needed for a ship repeatedly passing from cold to warm weather.The control problem is eased if the chilled brine (or water) of systems using chilled liquid circulation is held at about 13°C in the intermediate weather conditions and lowered progressively to about 5°C as tropical weather conditions are approached. When air cooling is in use it is good practice to keep all portholes, windows and doors shut. On passengerships, some public announcement requesting that this be done is worthwhile.A wise precaution for an engineer to take is to go through accommodation and public rooms periodically recording wet and dry bulb temperature. Keeping a log of these reading then serves to identify any malfunctioning of the installation as soon as it arises.The quantity of cooled air delivered by an air conditioning unit should bablance the sum of the quantity of the air recirculated to the quantity mechanically exhausted. The correct bablance between supply and exhaust fans should be checked periodically. Even with filters fitted ducts can become partially blocked can fan performance can fall off to upset the bablance.On older ships, temperature maintenance can be made easier by increasing the ratio of recirculated to fresh air. Most air conditioning units have dampers for adjusting this ratio and the effect of these can be extended after they have reached, full travel by partially blocking fresh air inlets. Care must be taken not to reduce the fresh air so that stuffiness or smells arise.Cleaning or renewal of filters is necessary at baout 3-monthly intervals, the time varying according to location on the ship. Disposable filters can be vacuum-cleaned so that in fact two or three "lives" are obtained before they need to be thrown away.In addition to normal mechanical attention, such as lubrication of bearings, and adjustment of fan belts and cleaning of motors, careful greasing of linkages of automatic controls is necessary.Cooled air ducts should be examined to see that the insulation vapour seal remains in good order. If a plastic film: vapour seal becomes damsged, condensation forms within the film. As well as making the insulation wet and ineffective, the condensation may become serious enough to cause drips and damp parches on ceilings.VentilationVentilation is the provision of a supply of fresh untreated air through a space. Natural ventilation occurs when changes in temperature or air density cause circulation in the space. Mechanical or forced ventilation uses fans for a positive movement of large quantities of air (Fig. 18-2).Natural ventilation is used for some small workshops and stores but is impractical for working areas where machinery is present or a number of people are employed.Forced ventilation may be used in cargo spaces where the movement of air removes moisture or avoids condensation, removes odors or gases,etc.The machinery space presents another area which requires ventilation. As a result of itslarge size and the fact that large volumes of air are consumed a treatment plant would be extremely costly to run. Ventilation is therefore provided the sufficient quantities for machinery air consumption and also to effect cooling. Several axial flow fans provide air through ducting to the various working platforms. The hot air rises in the centre and leaves through louvers or openings, usually in the funnel. The machinery control room, as a separate space, may well be arranged for air conditioning with an individual unit which draws air through trucking from the outside and exhausts back to the atmosphere.Notes1. Air conditioning systems fall into two main classes: individual unit system, in which each room contains its own small refrigeration plant and fan and air cooler; and central systems, where larger refrigeration machinery unit are installed and their out put distributed about the ship by a variety of means.空调系统分为两⼤类,独⽴空调系统和中央空调系统。

Lesson 13轮机英语

Lesson 13轮机英语

Unit 2 Auxiliary Machinery Lesson 13 Marine Boilers and TheirConstructionA boiler in one form or another will be found on every type of ship. Where the main machinery is steam powered, one or more large water -tube boilers will be fitted to produce steam at very high temperatures and pressures. On a diesel main machinery vessel, a smaller (usually fire tube type) boiler will be fitted to provide steam for the various ship services. Even within the two basic design types, water tube and fire tube, a variety of designs and variations exist.A boiler is used to heat feed water in order to produce steam. The energyreleased by the burning fuel in the boiler furnace is stored (as temperature and pressure) in the steam produced. All boilers have a furnace or combustion chamber where fuel is burnt to release its energy. Air is supplied to the boiler furnace to enable combustion of the fuel to take place. A large surface area between the combustion chamber and the water enables the energy of combustion, in the form of heat, to be transferred to the water.A drum must be provided where steam and water can separate. There must also be a variety of fittings and controls to ensure that fuel oil, air and feed water supplies are matched to the demand for steam. Finally there must be a number of fittings or mountings which ensure the safeoperation of the boiler.In the steam generation process the feed water enters the boiler where it is heated and becomes steam. The feed water circulates from the steam drum to the water drum and is heated in the process. Some of the feed water passes through tubes surrounding the furnace, i.e. water wall and floor tubes, where it is heated and returned to the steam drum. The steam is produced in a steam drum and may be drawn off for use from here. It is known as wet or saturated steam in this condition because it will contain small quantities of water. Alternatively the steam may pass to a super heater which is located within the boiler. Here steam is further heated and "dried", i.e. all traces of water areconverted into steam. This superheated steam then leaves the boiler for use in the system. The temperature of superheated steam will be above that of the steam in the drum. An attemperator, i.e. a steam cooler, may be fitted in the system to control the superheated steam temperature.The type of the marine boilerThere are two distinct types of marine boilers in use on board ship, the fire-tube boiler in which the hot gases from the furnaces pass through the tubes while the water is on the outside, and the water-tube boiler in which the water through the inside of the tubes while the hot furnace gases pass around the outside.Water tube boilerThe water tube boiler is employed for high pressure, hightemperature, and high capacity steam applications, e.g. providing steam for main propulsion turbines or cargo pump turbines. Fire tube boiler are used for auxiliary purposes to provide smaller quantities of low pressure steam on diesel engine powered ships.Fire tube boilerThe fire tube boiler is usually chosen for low pressure steam production on vessels requiring steam for auxiliary purposes. Operation is simple and feed water of medium quality may be employed. The name "tank boiler " is sometimes used for fire tube boiler because of their large water capacity. The terms "smoke tube" and "donkey boiler" and also in use.Cochran boilersThe modern vertical Cochran boiler has a fully spherical furnace and is known as the "spheroid". The furnace and is known as the"spheroid". The furnace is surrounded by water and therefore requires no refractory lining. The hot gases make a single pass through the horizontal tube bank before passing away to exhaust. The use of small bore tubes fitted with retarders ensures better heat transfer and cleaner tubes as a result of the turbulent gas flow.Spanner boilersThe spanner vertical fire tube boiler uses a patented design of tube known as "Swirlyflo". The special twist of the tube is said to improve heat transfer.Double evaporation boilersA double evaporation boiler uses two independent systems for steam generation and therefore avoids any contamination between the primary and secondary feed water. The prinary circuit is in effect a conventional water tube boiler which provides steam to the heating coils of a steam-to-steam generator, which is the secondary system. The complete boiler is enclosed in a pressured casing.Auxiliary steam plant systemThe auxiliary steam installation provided in modern diesel powered tankers usually uses all exhaust gas heat exchanger at the base of tile funnel and one or perhaps two water tube boilers. Saturated or superheated steam may be obtained from the auxiliary boiler. At sea it acts as a steam receiver for the exhaust gas heat exchanger, which is circulated through it. In port it is oil fired in the usual way.Exhaust gas boilersAuxiliary boilers on diesel main propulsion ships, other than tankers, are usually of composite form, enabling steam generation using oil tiring or the exhaust gases from the diesel engine. With this arrangement the boiler acts as the heat exchanger and raises steam in its own drum.The boiler constructionWater tube boilers, which use small diameter tubes and have small steam drums, enables the generation or production of steam at high temperatures and pressures. The weight of the-boiler is much less than an equivalent fire tube boiler and the steam raising process is much quicker. Design arrangements are flexible, efficiency is high and the feed water has a good natural circulation. These are some of the many reasons reasons why the water tube boiler has replaced the fire tube boiler as the major steam producer.Early water tube boilers used a single drum. Headers were connected to the drum by short, bent pipes with straight tubes between the headers. The hot gases from the furnace passed over the tubes, often in a single pass.A later development was the bent tube design. This boiler has twodrums, an integral furnace and is often referred to as the "D"type because of its shape.The furnace is at the side of the two drums and is surrounded on all sides by walls of tubes. These water wall tubes are connected either to upper and lower headers or a lower header and the steam drum. Upper headers are connected by return tubes to the steam drum. Between the steam drum and the smaller water drum below, large numbers of smaller diameter generating tubes are fitted. These provide the main heat transfer surfaces for steam generation. Large bore pipes or down comers are fitted between the steam and water drum to ensure good natural circulation of the water. In the arrangement shown, the super heater is located between the drums,protected from the very hot furnace gases by several rows of screen tubes. Refractory material or brickwork is used on the furnace floor , the burner wall and also behind the water walls. The double casing of the boiler provides a passage for the combustion air to the air control or register surrounding the burner.The need for a wider range of superheated steam temperature controlled to other boiler arrangements being used . The original External Super heater "D"(ESD) type of boiler used a primary andsecondary super heater located after the main generating tube bank. An attemperator located in the combustion air path was used to control the steam temperature.The later ESD II type boiler was similar in construction to the ESD.I but used a control unit( an additional economiser) between the primary and secondary super heaters. Linked dampers directed the hot gases over the control unit or the super heater depending upon the superheat temperature required. The control unit provided a bypass path for the gases when low temperature superheating was requred.In the ESD III boiler the burners are located in the furnace roof, which provides a long flame path and even heat transfer throughout the furnace. In the boiler shown in Fig. 13-3, the furnace is fully water-cooled and of monowall construction, which is produces from finned tubes welded together to form a gastight casing. With monowall construction no refractory material is necessary in the furnace.The furnace side, floor and roof tubes are welded into the steam and water drums. The front and rear walls are connected at other end toupper and lower waterwall headers. The lower waterwall headers are connected by external downcomers from the steam drum and the upper waterwall headers are connected to the steam drum by riser tubes,The gases leaving the furnace pass through screen tubes which are arranged to permit flow between them. The large number of tubes results in considerable heat transfer before the gases reach the secondary superheater. The gases then flow over the primary superheater and the economiser before passing to exhaust. The dry pipe is located in the steam drum to obtain reasonably dry saturated steam from the boiler. This is then passed to the primary superheater and then to the secondary superheater. Steam temperature control is achieved by the use of an attemperator, located in the steam drum, operating between the primary and secondary superheaters.Radiant type boiler are a more recent development, in which the radiant heat of combustion is absorbed to raise steam, by infrared radiation. This usually requires roof firing and a considerable height in order to function efficiently. Both the furnace and the outer chamber are fully watercooled. There is no conventional bank of generating tubes. The hot gases leave the furnace through an openingat the lower end of the screen wall and pass to the outer chamber. The outer chamber contains the convection heating surfaces which include the primary and secondary superheaters. Superheat temperature control is by means of an attemperator in the steam drum. The hot gases, after leaving the primary superheater, pass over a steaming economiser. This is a heat exchanger in which the steam- water mixture is flowing parallel to the gas. The furnace gases finally pass over a conventional economiser on their way to the funnelFurnace wall constructionThe problems associated with furnace refractory materials, particularly on vertical walls, have resulted in twowaterwall arrangements without exposed refractory. These are known as "tangent tube" and "monowall" or "membrane wall".In the tangent tube arrangement closely pitched tubes are backed by refractory,insulation and the boiler casing. In the monowall or membrane wall arrangement the tubes have a steel strip welded between them to form a completely gas tight enclosure. Only a layer of insulation and cladding is required on the outside of this construction.The monowall construction eliminates the problems of refractory and expanded joints. However , in the event of tube failure, a welded repair must be placed over the failed tube to protect the insulation behind it. With tangent tube construction a tailed tube can be plugged and the boiler operated normally without further attention.Notes1.All boiler have a furnace or combustion chamber where fuel is burnt to release its energy. Air is supplied to the boiler furnace to enable combustion of the fuel to take place.所有的锅炉都会有一个熔炉或是燃烧室,燃料在里面燃烧,释放出能量。

轮机英语 翻译 lesson 6

轮机英语  翻译 lesson 6

第6 课起动系统柴油机是按所需方向,以适当顺序向各缸通入压缩空气起动的。

所供压缩空气以30~40bar 的压力存于气罐或气瓶内,随时可用。

有时压缩空气通过减压阀降压以备他用。

空气瓶靠空压机充气。

船级社对空气系统的设计包括空气瓶和空压机的数量及容量、辅助及放残设备的设置有严格要求。

所储存的压缩空气量可进行多达12 次的起动。

起动空气系统通常装有连锁装置,若其他设备没准备好,则不允许柴油机起动。

压缩空气通过大口径管道进入遥控操作的止回阀或自动阀,进而到达气缸起动阀。

气缸起动阀开启,空气进入相应的气缸。

气缸起动阀及自动遥控阀由控制空气系统控制。

按所需运转方向,每个气缸起动阀在(活塞)经过上止点后立即开启,在排气口适当开启前关闭。

这13样,在压缩空气经主管路进入柴油机的起动系统时,至少进入活塞处于对应做功冲程某一位置的某些缸中,结果,施加于活塞上的压力迫使柴油机转动。

当达到足够高转速,如30 r/min 时,起动空气切断,燃油喷入,使气缸发火并正常连续运转。

控制空气来自主空气管并通入由柴油机起动操纵杆控制的起动控制阀。

当操作起动手柄时,控制空气使控制导阀手动开启或(当驾驶台安装控制系统时)靠气动液压缸开启。

控制空气也通入空气分配器。

空气分配器通常由柴油机凸轮轴驱动,它将控制空气通入气缸起动阀。

此控制空气按所需运转方向以恰当的顺序通入。

当不用气缸起动阀时靠弹簧保持关闭。

当它由控制空气打开时,压缩空气便直接从空气瓶进入气缸。

柴油机着火后,起动手柄拉回。

控制空气控制阀回复到关闭位置,控制空气管路和遥控空气起动阀放气并使其关闭。

起动空气系统连有许多连锁装置,以保护机器及人身安全。

它们是:1.盘车机连锁阀。

在盘车机没脱开时,该阀可切断起动空气控制管路,防止柴油机起动。

2.控制空气连锁阀。

在柴油机运行时,当主控制杆操纵控制空气连锁阀时,防止起动空气系统工作。

控制空气在起动进行时,即在主控制手柄离开起动位置前,控制空气连锁阀保持开启,但在此之后保持关闭,且在主控制手柄移回停车位置前不再打开。

轮机英语30课翻译

轮机英语30课翻译
至两台发电机有相同的电压。The circuit breaker connecting the second machine to the bus‐bar
can now be closed and the field current adjusted to enable the generator to take its share of the
动辅助设备的电动机,也用于甲板机械、照明、通风和空气调节设备。A constanபைடு நூலகம் supply of
electricity is essential for safe ship and machinery operation, and therefore standby or additional
flame, i.e. contain any fire or explosion.它必须能阻止火焰的传递,也就是能容纳任何火焰或爆
炸。
Alternating current supply 交流电的供电
The Supply to a distribution system will usually come form(from?) two or more generators
and the bus‐bars, so that one instrument can display, one of a number of values. 这使他们能相
互切换,例如,相与相之间,或并入发电机与汇流排之间,这样一个仪表能显示多个测量值
中的一个。The wattmeter measures the power being used in a circuit, which, because of the

轮机英语新版教材译文(党坤)

轮机英语新版教材译文(党坤)
5
r/min)用于发电机,并且有时做推进主机,用减速箱提供 90~120 r/min 的转速。
工作循环
柴油机可设计成二冲程循环或以四冲程循环工作,二者解释如下: 四冲程循环 图 2-2 示出了典型的两转四冲程循环的过程顺序。该图通常从上止点(TDC,发火)开始 绘制,因此就从上止点(TDC,扫气)开始解释。上止点又叫内止点。 沿该图顺时针看,开始时进排气阀都是打开的(所有现代四冲程柴油机均有气阀机构)。 如果柴油机是自然换气或带有径流增压器的小型高速机,气阀的重叠时间,即两气阀同时开 启的时间将很短。排气阀将在上止点后(ATDC) 100 左右关闭。
在机座上平面装有若干铸铁或锻钢制成的 A 形机架,机架安装在机座的横梁上,并用 螺栓固定。A 形机架顶部有一个结实的框架结构叫扫气箱。该扫气箱分若干段,每段均带有 垂直法兰,通过螺栓可将它们在链传动装置前 1~3 缸的部分连成一体,链传动装置后 4 缸 ~6 缸的部分连成一体。链传动装置将曲轴和凸轮轴连在一起,封闭在链传动箱的壳体内。
7
第 3 课 柴油机结构
机座和机架
在大多数情况下机座是焊接结构,用螺栓固定在构成船舶双层底的底座上。它在横向借 助于侧楔垫螺栓,在纵向借助于端楔垫螺栓固定。
曲轴安放在机座横梁的轴承上,这些轴承称作主轴承。每个轴承由两块轴瓦组成,两块 轴瓦由在机座上加工出的瓦座支撑,用双头螺栓和轴承盖固定,即推力轴承位于发动机的尾 部,可同机座制成一体,也可同机座分开。
带齿轮减速器的中速柴油机 图 1-2 所示的火车轮渡船的机舱布置采用四台中速柴油机(500 r/min )。其齿轮装置以 170 r/min 的转速双螺旋驱动两个变距桨。减速装置驱动轴带发电机,用于提供海上所需电力。 在最低高度的机舱空间中,这种在机舱底部还布置有各种各样的泵及辅助机械。废气锅炉及 其烟囱位于左右两舷,紧靠船体板。

新版轮机英语unit21_oil treatment

新版轮机英语unit21_oil treatment

The hole diameter(孔直径) of the disc to be tried first appears directly from the nomogram.
However, in practical operation the best result is obtained by using the gravity disc with largest hole diameter
that will not cause a break in the liquid seal in the bowl or an emulsification (乳化) in the water outlet.
The dirty oil is admitted into the centre of the bowl(分离 筒) ,passes up through a stack (一叠) of discs(分离盘) and out through the top.
The purifying process
whereas a disc with smaller hole diameter will position the interface closer to the bowl centre.
The nomogram(诺谟图) is an aid to select a tentative(试验) gravity disc when the density of the oil at a given temperature is known.
Water is fed into the bowl to remake the liquid seal(水 封) ,the oil feed reopened ,and separation continues.

轮机中英文翻译

轮机中英文翻译

HYDRODYNAMIC DAMPING OF THE TORSIONAL VIBRATIONS OF THE SYSTEMSHAFT-SHIP'S PROPELLERFor ships' power plants with an internal combustion engine, whose important component is the propeller and shaft, a very topical question is the refinement of existing methods and the devising of new methods of calculating torsional resonance vibrations. This will make it possible to accurately determine the state of dynamic stress of the installation, and consequently also to determine the possibility of fatigue failure of its most heavily loaded elements.At present, calculations of the torsional vibrations of ships' propeller shafts, amounting to obtaining the amplitude response of the system, are carried out by taking into account the damping which, as a rule, is due to friction in the internal combustion engine, in elastic couplings, and the friction of the propeller against the water [1]. Investigations in recent years showed that the damping of torsional vibrations in consequence of energy dissipation in the material of the propeller shafts is slight, and it is therefore usually neglected.Therefore, the prevalent role in the damping of the torsional vibrations of ships' power plants belongs to structural and hydrodynamic damping, whose studyand refinement is at present the object of researchers' ,endeavors.Damping of the propeller in the ship's power plant is the most important form of damping outside the engine in all forms of vibrations, except the so-called motor vibrations at which the amplitudes of the free vibrations in the shaft section are small. However, it is very difficult to obtain a formula for calculating the damping effect of the propeller, because it depends on an entire complex of factors such as the geometry of the propeller, the number of blades, the vibration frequency, etc. That is also the reason why the corresponding formulas determining the damping of the propeller were obtained experimentally on simulating installations, and they are not very accurate. Moreover, the formulas suggested by different authors yield different results when used in the same calculations.The methods used at present in the investigation and calculation of torsionalvibrations of ships' propeller shafts are based, as a rule, on the approximate method worked out by Terskikh [2]; this method entails the replacement of the real friction in the system by two nominal components, one of which has the properties of linear friction, and consequently, has a quadratic dependence of work on amplitude, and the other has the properties of dry friction with linear dependence of work on amplitude.In practice, friction in the elements of a ship's propeller shaft is not linear; however, the nonlinear problem of the damping properties of different components of the ship's power plant, especially of the propeller, led to difficulties in the solution of nonlinear differential equations, and in view of this, various approximate methods are used in practice, but they are not very accurate.Therefore, one of the ways of improving the accuracy of the calculations of torsional resonance vibrations is to continue the theoretical and experimental investigations, whose object would be to determine more accurately the elements of the propeller shaft and to solve the nonlinear problem of torsional resona nce vibrations.The question of taking into account the energy dissipation due to hysteresis losses in the material in the calculation of mechanical vibrations has received sufficient attention; this included the elaboration of physically substantiated methods of calculating the vibrations of systems, which was done very successfully by the use of asymptotic methods of nonlinear mechanics [3].Up to the present, however, there do not exist any reliable methods of calculating vibrations for other kinds of energy losses (structural and aerodynamic damping).Pisarenko [4] suggested a new approach which makes it possible to solve the problem of taking into account not only the hysteretic energy dissipation In the material, but also stnlctural as well as aerodynamic kinds of damping, on the basis of a single method whose essence is that all kinds of energy losses in the vibrating system, regardless of their origin, are represented in the form of some hysteresis loops, separately for each kind of loss, and the areas of the hysteresis loops then characterize the respective part of the energy out of the peak value of potential energy of a unit volume of cylically deformed material of an elastic element of the vibratingsystem ("spring") with the given amplitude of deformation (stress),Here we have to proceed from the following nonlinear correlations between stress ξand relative deformation σ in any single cyclically deformed element (spring) with peak value of deformation a ξfor the ascending and descending motion leading ina cycle to the formation of the hysteresis loop [5]:2n n 3=E 28ξσξδξξξ⎡⎤⎛⎫±-⎢⎥ ⎪⎝⎭⎣⎦ (1)where E is the modulus of elasticity of the material; δ is the logarithmic decrement of the vibrations. Arrows pointing to the right refer to the ascending branch of the hysteresis loop; arrows pointing to the left refer to the descending branch.By introducing into (1) the decrement as a function of the factor on which it depends, we can generalize the approach used in taking hysteresis losses in the material into account to the case of taking other energy losses into account, losses that are due to any arbitrary causes, because in all cases energy is dissipated which was integrally accumulated in the vibrating system and which consists of the sum of the energies of unit volumes of the cyclically deformed material of an elastic element of the system (spring), and the latter is a function of the amplitude of deformation (stress). llais approach therefore makes it possible to use a single method.By integrating with respect to the volume of the cyclically deformed material, we can take into account any energy losses, summing them as hysteresis loops having the same shape whose magnitude depends on the level of the vibration decrements contained in the equation of the loop and obtained experimentally as a function of some factor. The above-mentioned hysteresis loops characterizing the energy losses in a unit volume of cyclically deformed mate; rial with deformation amplitude a ε may, generalized and schematically, be represented in the form()2n n 3=E 28M K ad ξσξδδδξξξ⎡⎤⎛⎫±++-⎢⎥ ⎪⎝⎭⎣⎦ (2)where M δ is the vibration decrement characterizing the energy dissipation in thecyclically deformed material itself, which, as was shown above, depends on thedeformation amplitude; K δ is the vibrational decrement characterizing energy lossesin fixed joints (structural damping), which, as a rule, depends on the magnitude of the reactive moment acting in the node; ad δ is tile aerodvnamic vibration decrement,which may depend on various factors in dependence on the nature of the environment and its interaction with the vibrating elements.Thus, proceeding from relation (2) and taking into account the decrements it contains as functions of the respective factors, we may, by the methods of nonlinear mechanics [3], envisaging energy losses to be taken into account by integration with respect to the volume of tile cyclically deformed material of the vibrating system, construct the amplitude response of the latter in the resonance and near-resonance zones that are of interest to us; this will make it possible to evaluate the state of dynamic stress of the investigated system.Extending the above approach to the case of hydrodynamic damping of apropeller with critical vibrations of the propeller shaft, we devise, in analogy withexpression (1), equations describing the outline of the hysteresis loop corresponding to the given type of damping, and we adopt them as initial ones:2a a 328h G γτγδγγγ⎡⎤⎛⎫=±-⎢⎥ ⎪⎝⎭⎣⎦ (3)where G is tile shear modulus; h δ, hydrodynamic vibration decrement; a γ, amplitudeof the cyclic torsional deformation; and γ, running value of the relative shear deformation.In order to simplify further calculations, we represent formula (3) in the forms y τττ±= (4)where y τ is the stress,y τ=γG (5) s τis the frictional stress,2328s h a a G γτδγγγ⎛⎫=±- ⎪⎝⎭ (6) We assume that the cyclic deformation of the material ychanges with timecosinusoidallcos a γγθ= (7)Wherew t θ= (8) Taking (7) into account, we write expression (6) in the form()2312cos cos 8h G τδθθ=±- (9)Shear deformation of an element of the material of a circular rod, situated a t thedistance p from the center of its cross section, is determined by the formulad dx ϕγρρϕ'== (10)where ϕ is the angle of torsion of the rod; x is the axis of coordinates in the direction of the axis of the rod.The peak value of shear at the given point is equal tom axa m d dx ϕγρρϕ⎛⎫'== ⎪⎝⎭ (11) If we substitute (i0) into (5), and (11) into (9), we obtain:y G τρϕ'= (12)()2312cos cos 8m h G τδρϕθθ'=±- (13) Taking (12) and (13) into account, we write expression (3) in the form ()2312cos cos 8h G G τρϕδρϕθθ''=±- (14) The magnitude of the torque acting in the cross section of the rod is determinedby the formulaM dF τρ=⎰ (15)For a rod with completely circular cross section and outer radius max ρ=4, Eq.(15), taking (14) into account, assumes the form()4230023212cos cos 44r m h M d G G d πτρπρρϕπϕθθδρρ''==±⨯-⎰⎰ (16)or()21312c o s c o s 4p m M G I G I ϕπϕθθ''=±- (17) where 2/4r I P π= is the polar moment of inertia;310rh I d δρρ=⎰ (18) Since ()p p y G I G I d dx M ϕϕ'== is the elastic torque in an arbitrary cross section ofthe rod, Eq. (17) may be written in abbreviated form as follows:y s M M M =± (19)where s M is the "braking" torque due to hydrodynamic damping of the propeller inconsequence of its friction with the water, which, in accordance with expression (17), may be represented in the following manner:()21312cos cos 4m M G I πϕθθ'=±- (20) Where;/m m d const l dx l ϕϕϕϕϕ''==== (21)ϕ is the full angle of torsion of a rod with length l at any instant, determined by the expressiony y p M lG I ϕϕ== (22)not taking into account the energy dissipation in consequence of the hydrodynamic damping of the propeller subjected to torsional vibrations; m ϕis its peak value.In fact, the angle of rotation of the end section of the rod with length l , taking hydrodynamic damping into account, can be determined on the basis of expressions(19), (20), and (22) by the formulas y p p M l M lG I G I ϕϕ==+ (23)We denote the second term on the right-hand side of expression (23)s ϕ :()21312cos cos 4s m s p p M l I G I I πϕϕθθ==±- (24) Then Eq. (23), characterizing the true angle of rotaton of the end section of the rod at any instant , may be written in abbreviated form as follows:y s ϕϕϕ=+(25) In investigations and calculations, the propeller shaft is reduced to a system consisting of concentrated masses that have only inertial properties, and of joints that have only elastic properties.Figure I shows the initial structural simulator of the investigated system propeller shaft-propeller, which is an elastic rod with a disk at the end. The mass of the shaft, which has only elastic properties, may be neglected in comparison with the mass of the disk.The forced torsional vibrations are effeeted under the influence of small periodic angular displacements 0ϕ of the constraint, proportional to the small parameter[]6εin the plane parallel to the plane of the disk:0cos q w t ϕε= (26)where q ε is the peak value of the angle of rotation of the constrained section of therod, max 0)(ϕε=q ; w is the angular frequency of the vibrations of the constrained rod.Then the expression of the total angle of rotation of the end section of the rod, i .e .of the disk, at any instant may be written in the form0cos q wt ϕϕϕϕε=+=+ (27)where ϕ is the full angle of torsion determined by Eq. (25), and taking this into account,we write expression (27) as follows:cos y s q wt ϕϕϕε=++(28)If we apply to the system the torque of the inertial forces of the disk, using therebyLagrange's second-order equation, we obtain the differential equation of the motion of the disk at the end of the rod:Fig.1. Structural simulator of a torsionalvibration system with one degree of freedom.()22c o s y s d I c q wt dt ϕϕϕε++= (29) where c is the torsional rigidity of the rod,pGI c l = (30)L, length of the rod; and I, moment of inertia of the mass of the disk relative to the x axis of the rod, which is perpendicular to the plane of the disk.For the component o~ the angle of rotation of the end section of the rod s ϕ , the values in the ascending motion s ϕ and in descending motion s ϕ are different, inconsequence of which Eq. (29) is nonlinear. The given nonlinearity of "hysteretic" origin, which is due to hydrodynamic damping, is very slight, and it is expedient to express this by introducing the small parameter εinto the corresponding term of Eq.(29): :()22c o s y d I c f q w t dt ϕϕεϕε⎡⎤++=⎢⎥⎣⎦ (31)Where()()21312cos cos 4m s pI f I πϕεϕϕθθ==±- (32)We introduce the following notation:2cl pGI lI ρ== (33)()()2f ρεϕεϕ=Φ (34) where p is the natural angular frequency of the torsional vibrations of the system. In view of (33) and (34), Eq. (31) may he written in the form()2212cos d q wt dt ϕρϕεεϕ+=-Φ (35) where 1/q q I =;()()222312cos cos 4m p I I πρϕεϕθθ⎡⎤Φ=-±-⎢⎥⎢⎥⎣⎦(36) Following the methods of Krylov and Bogolyubov [7], we will seek the general solution of Eq. (35) with weak distortion in the form of an expansion into a series with powers of the small parameter ε:()()()21122cos u wt u u wt u u wt ϕϕεψεψ=++++++⋅⋅⋅⎡⎤⎡⎤⎣⎦⎣⎦ (37) Where w t ϕτ+=; w is the angular frequency of the distorting force; τ, phase of the vibrations;and ψ, phase shift.The magnitudes u and ψ are functions of time, and they are determined from the differential equations()()()()()()212212212p+B B p w +B B duA u A u dtd u u dtd u u dt εετεεψεε=++⋅⋅⋅=++⋅⋅⋅=-++⋅⋅⋅或 (38)Fig. 2. Dependence of the hydrodynamic decrement on the frequency of the forced torsionalvibrations. (The dots show the experimentalvalues of the hydrodynamic decrements.)where()()212B B w u u ρεε=+++⋅⋅⋅ 2012ψψεψεψ=+++⋅⋅⋅ With vibrations in the resonance zones, when the phase shift ψ is a constant magnitude,it may be assumed that the amplitude u and the phase τ do not depend on the phase shift ψ,and they may be determined by using the differential equation(38).The terms 1u and u2 of the series (37) are periodic functions of τ with theperiod 2π.Thus, the solution of Eq. (35) reduces to finding the functions u1(u, T); u2(u, T) .... ,At(u); A2(u) ..... B1(u) ; B2(u) .....We will omit the procedure of solving Eq. (35), since its method was explained in detail in [3], and we present the final expressions for determining the phase shift in the first approximation and for plotting the amplitude response of the investigated system, taking hydrodynamic damping into account:112cos 1p u I q I ψε⎛⎫=±-- ⎪ ⎪⎝⎭(39)2111q 3142u pp I w I pI I επ⎛⎫⎛⎫=-±- ⎪ ⎪ ⎪⎝⎭⎝⎭(40)In Eqs. (39) and (40) the unknown is 1I , which is determined on the basis of (18) from the expression310rh I d δρρ=⎰The hydrodyanmic decrement contained in this formula may be represented in the formh h1h2h3δδδδ=++ (41)where h 1δ is the component of the hydrodynamic decrement that depends on the frequency of the forced torsional vibrations; h2δ, component of the hydrodynamic decrement that depends on the rotational frequency of the propeller shaft with the propeller carrying out forced torsional vibrations; and h3δ, component of the hydrodynamic decrement that depends on the speed of the flow of water past the propeller in forced torsional vibrations.The above components of the hydrodynamic decrement may in turn be represented by the following expressions :111m axh m k k t γδγ∂⎛⎫==⎪∂⎝⎭ (42) Where11k tg α= (43)is the proportionality factor, sec; 1a , slope of the straight line ()w f h =δ to the axis of the abscissas, obtained experimentally (Fig. 2); m γ, pack value of the shear deformation rate22h k n δ= (44)where 2k is the proportionality factor, 1sec sec -⋅,22k tg α= (45)2αis the slope of the straight line ()n f h =δ to the axis of abscissas obtained byexperiment (Fig. 3a); n, rotational frequency of the propeller, 1sec -⋅rev ;33h k V δ= (46)where 3k is the proportionality factor, 1sec -⋅m33k tg α= (47)3α is the slope of the straight line ()V f h =δto the axis of abscissas obtained byexperiment (Fig. 3b); V is the flow rate of water past the propeller, 1sec -⋅mLet us examine in more detail the expression for 1h δ. It is known from Eqs. (10) and (21) thatd dxϕγρρϕ'==;d const dxlϕϕϕ'===Then the shear deformation may be expressed in the following way:lϕγρ= (48)where ϕ, in solving Eq. (35) in the first approximation, is equal to()cos u wt ϕψ=+ (49)With this taken into account, the expression for shear defromation assumes the form()cos u wt lρψγ+=(50)If we substitute (50) into (42) and differentiate, we obtain:()11cos uw wt k lρψδ+=- (51)For the case of the peak value of the shear deformation rate, which is being investigate here, ()sin 1wt ψ+=. Then we have31h uwk lρδ= (52)Substituting (52), (44), and (46) into Eq. (18), we write:311230ruw I k k n k V d l ρρρ⎛⎫=++⎪⎝⎭⎰(53) If we integrate expression (53) and substitute r = d/2 into the r e s u l t , where d is the shaft diameter, we obtain finally :()34112316064k uwd dI k n k V l=++ (54)where w = p in the first approximation, in accordance with (38).If we substitute (54) into (39) and (40), we have:()321230125cos 1u k w du k n k V l q ψπε⎡⎤++⎢⎥=±-⎢⎥⎢⎥⎢⎥⎣⎦(55)Fig. 3. Dependence of the hydrodynamic decrement on the rotational frequency of the propeller (a) and on the flow rate around the propeller (b). (Notation is the same as in Fig. 2.)Fig. 4. Theoretical amplitude responses of the investigated system for different rotationalfrequencies of the propeller: 1) res w = 620.271sec -,n = 0,V = 0; 2) res w = 618.831sec -,n =1.67 rev.1sec -,V = O; 3) res w = 617.39 1sec -,n = 3.33 rev.1sec -, V = 0; 4) res w = 615.951sec-, n = 5.00 rev.1sec -, V = O;5) res w = 614.58 1sec -, n = 6.67 rev'1sec -,V = 0; 6) res w= 613.08 1sec -,,n =8.33 rev.1sec -, V = 0; 7) res w = 611.701sec -, n = i0 rev. 1sec -, V = O. (For comparison, tile dots show the experimentally obtained resonance frequencies.)()()2122311231335212082uk w d k n k Vuk w d q wl k n k V p l u επ⎡⎤++⎢⎥⎡⎤⎛⎫=-++±-⎢⎥ ⎪⎢⎥⎣⎦⎝⎭⎢⎥⎣⎦(56)where the coefficeints kl, k2, k3 are calculated by Eqs. (43), (45), and (47) on the basis of experimental data.Equations (55), (56)enable us to determine the phase shift and to plot the amplitude response with critical vibrations of the propeller shaft, taking hydrodynamic damping of the propeller into account.For experimental investigations with the object of confirming the above theoretical conclusions, the device K-80 was built; it is described in detail in [8].To calculate the vibration decrements, we used the energy method, according to which relative energy dissipation is determined by the formula [9]frW W f ψ-=∏(57)where W is the total power expended on the excitation of torsional vibrations, W; fr W , power expended on overcoming friction in the device itself, W; f, frequency of the steady-state torsional vibrations of the propeller, Hz; and ∏, potential energy of the twisted shaft, corresponding to the amplitude of the steady-state vibrations.We represent the correlation between the relative energy dissipation and the logarithmi decrement of the vibrations in the form [I0]2ψδ=(58)Fig. 5. Theoretical amplitude responses of the investigated .system for different flow rates: 1)res w = 620.27 1sec-, V = 0, n = 0; 2) res w = 619.181sec -, V = 0.5m.1sec -, n = 0; 3) res w =618.081sec -, V = 1.0 m 1sec -, n = 0; 4) res w = 616.991sec -, V = 1.5 m.1sec -, n = 0; 5) res w = 615.941sec -, V = 2.0 m.1sec - , n = 0; 6)res w = 614.861sec -, V = 2.5 m.1sec -, n =0. (The meaning of the dots is the same as in Fig. 4.)Fig. 6. Theoretical amplitude responses of the investigated system: 1)res w = 620.271sec-, n =0, V = 0; 2) res w = 618.831sec -, n = 1.67 rev. 1sec -, V = 0; 3) res w =618.081sec -, n = O, V = 1m.1sec-; 4) res w = 611.331sec -, n = 1.67 rev.1sec -, V =1 m.1sec - (file meaning of the dots isthe same as in Fig. 4.)where δ is the vibration decrement. Taking Eqs. (57) and (58) into account, we write the expression for determining the hydrodynamic decrement of the propeller in the following form2fr W W f δ-=∏(59)Figure 2 shows the experimentally obtained dependence of the hydrodynamicdecrement on the frequency of the forced torsional vibrations of the propeller; it is a straight line at the angle a1 to the axis of abscissas.Figures 3a, b show the experimentally determined dependences of the hydrodynamic decrement on the rotational frequency of the propeller and on the flow rate of the water past the propeller; they are straight lines at the angles a2 and a3, respectively, to the axis of abscissas.Using the experimentally found angles a1, a2, and a3, we calculate by Eqs. (43), (45), and (47) the coefficients kl, k2, and k3, and with their aid we can determine the phase shift by Eqs.(55)and(56)and plot the amplitude responses of the investigated system for different rotational frequencies of the propeller and different flow rates of the water past the propeller.Figures 4-6 present the resonance curves obtained by calculation.A comparison of the resonance frequencies obtained by calculation using the formulas of the theoretical section with those experimentally determined shows the error of calculation lies within the limits 0.3-0.4%.This ensures an accuracy sufficient for engineering calculations.CONCLUSIONS1.It follows from an analysis of the obtained results that a propeller in a vibrating system exerts a damping effect which makes it possible to greatly reduce vibration amplitude and dynamic stress. Moreover,calculation of the torsional vibrations of a ship’s propeller shaft taking hydrodynamic damping of the propeller into account makes the resonance frequencies 2-5%more accurate ,even with relatively small hydrodymic decrements.Obviously,for those types of propeller shafts where the damping of the propeller is predominant, the accuracy of the resonance frequencies will be substantially enhanced.2. Since we know the experimentally obtained dependences of the hydrodynamic decrement of the vibrations of the propeller on the frequency of the forced torsional vibrations, on the rotational frequency of the propeller, and on the flow rate of the water past the propeller, and also the principal characteristics of the conditions underwhich the propeller will operate (rotational frequency of the main engine in all operational regimes, and the speed of the ship), we can calculate and plot the amplitude responses of the system propeller-shaft-propeller,thereby determining the resonance frequencies and the regions in which the torsional vibrations will have large amplitudes.3. The suggested approach of theoretically evaluating the state of dynamic stress of ships' propeller shafts subjected to vibrations, taking into account the principal kinds of energy losses in the vibrating system occurring under real operating conditions, is well confirmed by experimental data obtained on a simulator specially devised for this purpose, and it may be recommended for the stress analysis of ships' propellers at the design stage, with the object of predicting their state of dynamic stress in operation.船舶螺旋桨轴系扭振的流体阻尼船舶内燃机动力装置主要有螺旋桨和轴的组成,其计算扭振的主要问题是现有方法的改良和发明新的计算方法。

轮机英语 翻译 lesson 10

轮机英语  翻译 lesson  10

第10 课传动系统传动系统将发动机的动力传递给螺旋桨。

传动系统由轴系、轴承以及末端的螺旋桨组成。

通过螺旋桨的推力传动系统传给船体。

系统中不同的部件包括推力轴、一个或多个中间轴以及尾轴。

这些轴系由推力轴承、中间轴承及其尾轴承支撑。

尾轴两端都有一密封装置,由螺旋桨及其螺帽一起实现密封。

图10-1 示出了传动系统的各个部件的名称、位置及其用途。

20图10-1 传动系统推力轴承推力轴承将螺旋桨的推力传给船体。

因此,为正常工作,其必须牢固地安装于坚固的底座或框架上。

推力轴承可以是主动力装置的一个独立装置或其一组成部件。

正车和倒车推力轴承都需安装,并且其本身须足够坚固以承受正常的负荷和振动。

独立的推力轴承的盖壳分为两半,由拂配紧固(图10-2)。

承受推力的推力块为楔形,安装在壳体内,一面浇有白合金。

图10-2 中,推力块沿3/4推力环圆周布置,并将推力传递给壳体的下半部。

其他类型的设计采用完整的环状推力块。

刮油器将推力环收集的滑油刮走并引入,继而从推力块和推力轴承溢出。

推力轴带有独立法兰,用以与发动机或齿轮箱轴以及中间轴和用以传递推力的推力环相连。

当推力轴为发动机一组成部分时,与发动机底座螺栓连接方式类似,推力轴承的壳体通常采用螺栓连接。

发动机滑油系统提供一定压力的滑油对轴承系统进行动压润滑。

轴承在结构方面的其他细节与独立式推力轴承类似。

图10-2 推力轴承轴系轴承轴系轴承有两种:尾轴承和其他轴承。

尾轴承有上下两个轴承盖,用以承受螺旋桨的质量和在尾轴的前端产生垂直向上的推力。

其他类型的轴承仅起支撑轴系重量,因此仅有下轴承盖。

21图10-3 所示为中间轴轴承。

在该轴承中,常用的轴瓦由可绕支点转到动的轴承块代替。

楔形轴承块能更好地承受过载,并且能维持较厚的润滑油膜。

润滑从下半轴承盖油槽开始,甩油环浸入油中随轴转动时带油。

轴承的冷却通过在轴承盖低部的管状冷却器中循环水实现。

图10-3 隧道轴承尾轴管轴承尾轴管轴承有两个重要作用。

轮机英语 翻译 lesson 9

轮机英语  翻译 lesson  9

第9 课主机的运行与养护操作程序中、低速柴油机的起动和操作的程序完全相似。

当采用可换向减速齿轮箱或变距桨时主机不必逆转。

如下给出的为主机正确操作程序的要点。

当有厂家说明书时,应参照说明书。

备车1.在主机起动前,应通过在缸套中循环的热水对主机进行暖机,以使主机各部分相对膨胀。

2.检查各补给柜、滤器、阀件,并放残。

3.起动滑油泵、循环水泵,并观察回流情况。

4.检查所有控制设备和报警装置是否工作正常。

5.打开示功旋塞,合上盘车机,转动主机几转,如果气缸中有水将会被排出。

6 检查燃油系统,并用热油对系统进行循环。

7.如果辅助扫气泵为手动起动,应将其起动。

8.脱开盘车机,如果可能,在关闭示功旋塞前,应使用空气转动主机。

9.主机现在已备好。

备车时间的长短取决于主机的尺寸。

起动1.将转向手柄置于正车或倒车位置(转向手柄可与车钟手柄做成一体),此时,凸轮轴相对曲轴处于某位置以转动用于燃油喷射、气阀启闭的各种凸轮。

2.将操车手柄置于“起动”,此时,压缩空气将按正确的顺序依次进入气缸,从而起动主机。

(另外)可使用单独的起动按钮来起动主机。

3.当主机转速达到发火转速时,将操车手柄移至“运转”位置,油喷入气缸,燃烧开始并加速主机运转,此时,起动空气停止进入气缸。

换向18当机动航行时:1.起动辅助鼓风机(若手动起动)。

2.切断燃油,主机转速会迅速降低。

3.将方向手柄置于倒车位置。

4.压缩空气进入气缸,从而使主机倒车转动。

5.当主机在压缩空气作用下倒车转动时,燃油喷入气缸,燃烧过程开始,而压缩空气停止进入气缸。

全速航行时:1.起动辅助鼓风机(若手动起动)。

2.主机停油。

3.可以使用压缩空气使主机降速。

4.当主机停车后,将方向手柄置于倒车位置。

5.压缩空气进入气缸,使主机倒车转动,燃油供入气缸以加速主机运转。

此时,压缩空气停止供入气缸。

维修柴油机在原理上相当简单,且仅需较少的日常维护,虽然该维护对于柴油机维持较长的使用寿命至关重要。

轮机英语翻译lesson8

轮机英语翻译lesson8

轮机英语翻译lesson8第一篇:轮机英语翻译lesson8第8 课换气过程内燃机工作循环的一个基本部分是新鲜空气的进入与废气的排出。

这就是换气过程。

扫气是指用新鲜空气吹出废气。

充气是指将新鲜空气充入气缸以备压缩。

至于增压,是在一定压力下把大量空气吹入气缸。

老式柴油机采用“自然换气”—在大气压下吸入新鲜空气。

通过在吸气管和气缸之间采用合适的压气机增加充气密度,使进入每个工作冲程的空气重量增加,因此可燃烧更多的燃油,相应的,每缸输出功率增加。

在大多数现代柴油机上,采用废气涡轮增压实现空气密度的增加。

在涡轮增压装置中,一个由柴油机排气驱动的涡轮直接和离心压气机相连。

无论是四冲程机还是二冲程机均可增压。

应当注意,增压对非增压柴油机而言,并非只是设备的增加。

增压柴油机必须能经受所增加的压力及所产生的热负荷。

对换气过程而言,进入气缸的空气压力高于排气总管的压力十分必要。

由于废气涡轮增压器在低转速下不能提供足够的空气,就二冲程柴油机而言,通常配备一台电动辅助鼓风机。

高增压发动机使用串联(多级)涡轮增压。

增压后的空气通过冷却来增加空气的密度。

涡轮风机或涡轮增压器是在同一根轴相对的两端装废气涡轮和压气机。

压气机和涡轮之间彼此密封。

在新充的新鲜空气被压缩之前,每个气缸充分地驱除废气十分必要,否则新充新鲜空气将被循环的残余废气污染。

而且,若新充空气因与废气混合与热的缸壁及活塞接触而被加热,则循环的温度会毫无必要地增加。

在四冲程柴油机中,从进气阀打开到排气阀关闭,其间有一个适度的重叠。

在重叠期间流过气缸的空气流产生有益的冷却效果。

这将有助于增加容积效率,并确保循环温度较低,而且还使作用在涡轮叶片上的废气温度相对较低。

而在二冲程柴油机中,这一重叠受到柴油机设计特点的限制,进排气的轻微混合确实存在。

低速二冲程柴油机有多种不同的扫气方式。

无论哪一种都是从向下运动的活塞打开进气口开始至向上运动的活塞关闭进气口为止。

扫气空气的流动线路取决于柴油机气口的形状设计以及排气布置。

轮机英语34课翻译

轮机英语34课翻译
The warming through period should extend over a period of approximately four hours. 整个暖机
过程应持续约4h。
Check through the crankcase, etc. for any tools, obstructions, or waste material and remove
telephones to the bridge and Chief Engineer’s office. 确认机舱车钟功能正常,同时查看(机舱)
与驾驶台和轮机长办公室间的通话。
Check the reversing and control gear, running direction safety interlocks, auto‐shut‐down
from all the bearings and then close up the crankcase. 起动滑油泵,在工作压力下检查各轴承
油流是否均匀一致,之后关闭曲拐箱。On engines having oil cooled pistons the lubricating oil
pre‐heater must be put into operation and the rate of heating so arranged that the temperature
air system. 向空气瓶打气至最高压力,将空气瓶及空气系统放残。The scavenge drains should
be cracked open. The drains from diaphragm glands should be slightly open. 稍稍开启扫气箱放
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LESSON 1Diesel enginesThe majority of ships around the world continue to be powered exclusively by diesel engines.世界范围内大多数船舶都是采用柴油机作为动力。

The predominance of diesel engines has come from improved engine efficiencies and designs compared to other forms of propulsion such as steam or gas turbines.与蒸汽机、燃气轮机等形式的动力装置相比,无论是效率上的提高,还是设计上的进步,柴油机都体现出了一定的优势。

Many combinations and configurations of diesel engine power plant exist. All provide the energy to do the work of moving the ship using diesel engines.存在有很多种联合形式及结构形式的柴油机动力装置,他们都能够利用柴油机为船舶提供推动力。

Slow speed diesel engines 低速柴油机Slow speed diesel engines are large, especially tall, and heavy and operate on the two-stroke cycle.低速柴油机是体积较大、缸体较长、机身较重的二冲程柴油机。

These are the largest diesel engines ever built. Engine powers up to 100 000kw are available from a single engine.它们是已建造过的最大型的柴油机,它们的单机可用功率可达100000 kw。

They are tall to allow for long strokes which improve engine efficiency .the large physical allow for long strokes which improve engine efficiency.较长的缸体能提供一个较长的冲程,有助于提高柴油机的效率。

The large physical size of the engine and components leads to slow rotational speed with speeds up to 300rpm considered to be slow.柴油机及其部件的物理体积较大,导致其回转速度较低,尽管能够加速到300 rpm,但还是被认为是低速机。

For equivalent power output, the two-stroke diesel engine is significantly lighter than its comparable four-stroke relative.对于相同的功率输出,相对于四冲程柴油机,二冲程柴油机的重量明显轻很多。

This is most apparent for large power requirements where the two-stroke engine produces much more power for the same weight.对于大功率需求场合这是一个最明显的优势,二冲程柴油机能够在相同的重量情况下,发出更大的功率。

Large, slow speed, two-stroke marine diesel engines offer the advantages of:大型、低速、二冲程船用柴油机的优点如下:1.Burning poorer quality, cheaper fuel 燃烧劣质、低价的燃油2.Providing large power from a single, less complicated machine comprising fewer individual cylinders andmoving parts一个仅有几个独立汽缸和运动部件组成的、低复杂程度的柴油机就能提供较大的功率。

3.Having a low rotational speed allowing them to be directly coupled to the propeller and removing the need fortransmission machinery such as clutches and gearboxes etc, 回转速度较低,能够直接和螺旋桨连接,不需要像离合器、齿轮箱等的中间传动机构。

4.Being reversible and thus eliminating the need for reversing gear or controllable pitch propellers.Merchant ships driven by slow speed diesel engine will usually have a single large main engine directly coupled to a single fixed pitch propeller. The thrust forces from the propeller will be transferred to the hull of the ship through a thrust bearing built into a thrust block, the thrust block may be built as part of the slow speed engine, and this system is supported by diesel generators providing the ship’s electrical power.因为能够倒转,所以就不需要换向机构和可调距螺旋桨。

利用低速柴油机驱动的商船,通常只有一台直接连到定距桨上的大型主机。

Medium speed, four –stroke diesel engines 中速四冲程柴油机Medium speed engines operate in speed ranges from 300 to 900 rpm. The majority of medium speed engines operate on the four-stroke cycle.中速机的运转速度范围是300 —900 rpm,大多数的中速机都是四冲程柴油机。

They are most common as the propulsion engines in smaller ships, ro-ro and passenger ships. They are used widely as the electrical power generation engines in most merchant cargo ships.它们在小型船舶、滚装船舶以及客船上应用较多,在大多数的商用货船上被广泛用做发电机的原动机。

Four-stroke engines have more moving parts, are more complex and produce less power for equivalent weight compared to two-stroke slow speed engines. Medium speed engines do, however, offer several advantages which make them attractive for marine applications.四冲程柴油机有较多的运动部件,也更加复杂一些,跟二冲程低速柴油机相比相同的重量发出的功率较少。

然而,中速柴油机也有一些导致它们在船上使用的优点。

1.The engines are compact----they are not long or high, this allows them to fit in engine rooms with low headspace such as those in ro-ro ships. Fitted under the vehicle deck. 它们不长也不高,机型紧凑,这就使它们适合安装在空间较低的机舱当中,比如在滚装船上,它们就安装在汽车甲板的下面。

2.Medium speed engines use less oil than slow speed engines.中速机比低速机更省油。

3.Recent developments have produced medium speed engines capable of burning low quality heavy fuel oil.近年来的发展也使中速机能够燃用低质燃料油4.Engines of considerable power, to 25,000kw and more, have been developed, allowing a large power system tobe achieved with compact engines and engine room. This makes them suitable for passenger ship applications where the smaller the space provided for engines and machinery the more space is available for paying passengers. 25,000kw甚至更大功率的中速机已经被开发出来,这就使得能够利用较小体积的柴油机和较小空间的机舱达到较大的功率。

这样就适合在客船上安装使用中速机,柴油机和机械设备占用的空间较小,能够为旅客提供出更多的可用空间。

Most medium-speed diesel engines are non–reversible meaning that a controllable pitch propeller is usually employed to cater for astern thrust.大多数的中速柴油机是不可倒转的,这就意味着通常要利用变距桨实现向后的推力。

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