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Experimental Study on Heat Transfer and Flow Resistance in Improved Latticework

Journal of Thermal Science V ol.22, No.3 (2013) 250?256

Received: December 2012

Financial support of the National Natural Science Foundation of China (No.200604096).is gratefully acknowledged.

https://www.doczj.com/doc/9113778139.html,

DOI: 10.1007/s11630-013-0620-3 Article ID: 1003-2169(2013)03-0250-07

Experimental Study on Heat Transfer and Flow Resistance in Improved Lat-ticework Cooling Channels

Hongwu Deng 1, Kai Wang 2, Jianqin Zhu 1,*, Wenyan Pan 1

1. National Key Laboratory of Science and Technology on Aero-Engine Aero-Thermodynamics, School of Jet Propul-sion, Beihang University, Beijing 100191, China

2. Institute of Engineering Thermophysics, Chinese Academy of Science, Beijing 100190, China

? Science Press and Institute of Engineering Thermophysics, CAS and Springer-Verlag Berlin Heidelberg 2013

Characteristics of heat transfer and flow resistance of the latticework (vortex) cooling channel with ribs truncated at their two ends were theoretically and experimentally studied compared with regular and smooth channels of the same configuration. The results showed: the heat transfer efficiency of the latticework channel with two slots was better than those of regular and smooth channels of the same configuration, its flow resistance situation in the slotted channel becomes quite complex; The flow resistances of 2 mm- and 4 mm-slotted channels were obvi-ously lower than that of the regular channel, but they are still much higher than that of the smooth channel; Com-pared with the regular channel, the total heat transfer efficiencies of the slotted channels were pretty improved, among them the 4-mm slotted channel has the biggest enhancement. From the experimental results, it is obvious that the latticework channel with proper slots has a great prospect in the design of the inner cooling channels of turbine blades.

Keywords: latticework cooling; turbine blade; truncated ribs; heat transfer; flow resistance.

Introduction

The aerodynamic design of a modern aircraft engine is aimed at its high thrust-weight ratio, big unit volume power output, low fuel consumption rate, and high reli-ability. Increase in the thrust-weight ratio depends on increase in the thermal efficiency of its turbine; while in an advanced gas turbine, one of the effective ways to achieve high thermal efficiency and high power output is to increase its inlet temperature that may be higher than the melting point of the turbine blade material. Therefore, the blades need to be cooled for its safe and long opera-tion.

A rib-turbulator has been developed to enhance the

heat transfer efficiency of internal cooling channels, and widely applied in the design of turbine blades of aero engines. Many theoretical and experimental researches on the heat transfer in ribbed channels have been con-ducted since 1970s. Webb et al. [1] obtained the friction and heat transfer laws in the tubes with internal repeated ribs with different aspect ratios. Han et al. [2] studied the friction and heat transfer in a parallel-plate channel with rib-turbulators and proposed that the angled ribs aligned with 45 degree to the flow direction has better heat transfer performance than the transverse ribs with 90 degrees. Since then, extensive studies on the effects of internal coolant passages with different geometric pa-rameters on heat transfer and flow resistance have been

Hongwu Deng et al. Experimental Study on Heat Transfer and Flow Resistance in Improved Latticework Cooling Channels251

Nomenclature

A cross sectional area of channel Greek symbol

D hydraulic diameterαaverage heat transfer coefficient

F wetted perimeter of the cross-section ηheat transfer enhancement ratio

m mass air flow ρdensity

M condensed mass of water λheat conduction coefficient

p pressure μdynamic viscosity coefficient

p*total pressure of channel v kinematic viscosity coefficient

q heat

flux ξresistance coefficient

r latent heat of water Subscripts and superscripts

Re Reynolds

number 0atmospheric condition Nu Nusselt

number in inlet

R g air gas constant out outlet

T temperature s smooth

channel U flow

velocity w wall

S slot

width

conducted [3]. Won and Ligrani [4] compared heat transfer and flow resistance characteristics of rectangular chan-nels with 45 degrees parallel and crossed ribs and found the parallel ones have better heat transfer efficiencies, but less flow resistances than the crossed ones. Liou et al. [5, 6] studied the heat transfer and flow resistance characteris-tics of ribs which were perpendicular to the channel axes, and obtained the relationships of the average Nusselt number Nu to the flow resistance coefficient. Tanda [7] studied the averaged heat transfer in the channels with continuous and broken ribs in transverse and V-shaped rib configurations, and showed that under pumping power constraint, transverse broken ribs have better thermal performance than transverse continuous ribs. Gupta et al. [8] obtained the local heat transfer distribution in a roughened square channel with continuous, profiled and broken ribs, compared the continuous rib and saw-tooth profiled rib configurations, and proved that the heat transfer enhancement caused by V-broken ribs is higher than those by continuous and profiled ribs. Lei et al. [9] studied the local heat transfer in a square duct roughened by continuous and truncated ribs, and proved that continuous ribs have higher heat transfer efficiency and pressure drop than truncated ribs. Aharwala et al. [10] studied the effects of gap position and gap width of in-clined continuous ribs in a rectangular duct of solar air heater, and observed that the rectangular duct has higher friction and heat transfer factors than the smooth duct. Lee et al. [11] studied heat transfer efficiencies in rotating rectangular channels with V-shaped and angled ribs, and showed that the V-shaped ribs with gaps produce lower heat-transfer efficiency than the V-shaped ribs without gaps due to their shorter sizes, whereas the angled ribs with gaps produce higher heat transfer efficiency than the angled ribs without gaps in both the stationary and rotat-ing cases. Moreover, Lau et al. [12] studied the character-istics of heat transfer and flow resistance in a square channel with angled discrete ribs.

All the above studies were focused on the serpentine cooling channel. However, a latticework (vortex) cooling channel, as a different cooling concept, developed paral-lel to the serpentine one, was extensively utilized in the turbine designs of the former Soviet Union, but received very little attention in the world. Nagoga [13] in 1970s showed that compared with the serpentine channels which have greater total pressure loss, the crossed-rib channels offer higher heat transfer efficiency, and are beneficial to blade strength. Bunker [14] addressed to de-tailed study on latticework (vortex) cooling, and showed that it potentially has some intrinsic advantages, includ-ing higher blade strength and more uniform distribution of heat transfer coefficients. Furthermore, Zhang et al. [15, 16] studied the heat transfer and total pressure loss char-acteristics of rectangular crossed-rib channels.

In this paper, we presented a new configuration of the latticework cooling channel with a variable cross-sec-tional area, investigated experimentally its characteristics of heat transfer and flow resistance, and compared it with other two regular channels with the same configuration. This study was aimed at providing the basis on which new type of turbine blades with latticework coolant channels are designed.

Experimental arrangement and procedures

The schematic of our experimental arrangement is shown in Fig. 1. The arrangement includes the experi-mental segment, cooling air supply system, vapor supply

252J. Therm. Sci., V ol.22, No.3, 2013

system, and data measurement system. The experimental segment consists of three sections, entrance, test, and exit, surrounded by water vapor whose pressure is supplied by a boiler and maintained at 100?C vapor temperature. The vapor region in the device consists of two vapor layers, the test piece is immerged in the inner layer which sur-rounded by the outer layer to reduce the heat loss.

1. Source of cooling air,

2. Floater flow meter,

3. Switch cavity,

4. Entry segment,

5. Test piece,

6. Exit segment,

7. Vapor cavity,

8. Vapor boiler, 9. Thermocouple, 10. Total pressure meter,

11. Condensation water collecting device, 12. Double deck vapor cavity Fig. 1 Schematic of experimental study on heat transfer char-acteristics of latticework channels.

Experiments were performed in the static conditions. The vapor condensation heat transfer method [17] was used in the experiment. The heat transfer system included three parts, as shown in Fig. 2, the vapor condensation on the outside walls of the channel, the heat conduction through walls, and the convective heat transfer between the cooling airs in the channel and the inner wall. Ac-cording to the weight of condensed water measured per unit time and some other parameters, the total heat trans-fer coefficient and the Nusselt number Nu were obtained. The cooling air flow was changed to get the relationship of the Nusselt number to the Reynolds number, Re.

Fig. 2 Schematic of flow courses of vapor condensation heat transfer.

The latticework cooling channel with a rectangular cross-sectional area, called “regular channel”, was first studied. Since the trailing channel of turbine blade had variable cross-sectional area, the latticework cooling channel with a trapezoid cross-sectional area, called “tra-pezoid channel", was then studied. In order to reduce the flow resistance and without dramatically reducing the heat transfer, the ribs of regular channel were truncated at their two channel ends, thus forming two straight slots along the flow direction at each side of the channel (hereon referred to as “slotted channel”). The global and local heat transfer characteristics and the global flow resistances characteristics in these channels were com-pared in three experiments. For comparison, the results of smooth channel, which has the same channel width, height and length as the regular channel, was also pre-sented.

Data reduction and Uncertainty analysis The Reynolds number at the inlet indicates the mag-nitude of air flux. It is defined as

4

Re in in in in in

in

in in in in

D U D U m

F

ρ

μνμ

===

(1) where D in is the hydraulic diameter of the channel at the inlet, D in=4A in/F in. The velocity of air flow at the inlet, U in, can be computed by the mass air flow m through U in= m /ρin A in. The heat flux q =rM/A oτ, where r is latent heat of water, M the mass of condensed water, A O the outer heat transfer area of the channel, and τ the col-lection time of condensed water. The total Nusselt num-ber of the channel, Nu, is defined as

Nu = αD in/λin, (2) where α=q/(T w?T in) , and T w is the temperature of the inner wall.

The resistance coefficient of the channel is

**

2

0.5

in out

in in

p p

U

ξ

ρ

?

=, (3) where p*in and p*out are the total pressures at the inlet and exit of the channel, respectively, and p*in = p in+0.5 22

/in in

m A

ρ

. In this study, the inlet static pressure p in and flux m are measured by a piezometer and a flow meter. At the exit, the actually measured atmospheric pressure p0, is the back pressure, and then the total pressure at the

outlet of the channel is p*out22

00

0.5/out

p m A

ρ

=+ .

When α=117.63 W/(m2℃), following the error trans-fer function, the uncertainty of average heat transfer co-efficient αcould be calculated as:

(

)

6.98%

W in

A T T

α

α

Δ

=

=

?

Hongwu Deng et al. Experimental Study on Heat Transfer and Flow Resistance in Improved Latticework Cooling Channels253

According to Nu = αD in/λin, for the uncertainty of D in and λin can be neglected, the uncertainty of the total Nusselt number of the channel is 6.98%.

Results and discussions

In the experiment, the test passage was proportionally enlarged 5 times compared with the real blade trailing channel. A schematic of the latticework channel is shown in Fig. 3, with the channel's width W= 69.6 mm and length L= 150 mm. For the ribbed channel, the rib height e = 7.5 mm, the rib thickness t = 4 mm, the pitch length p =10 mm, and the rib attacking angle β= 45o. For the regular channel, the channel height H =2× e =15 mm. For the trapezoid channel, the proportionally changing angle is θ. For the slotted channel, the slotted gap width is S.

Fig. 3 Schematic of latticework channels. (a) Ordinary (b) Truncated ribs

Total heat transfer

The total heat transfer characteristics, described by the relationship of the Nusselt number Nu to the Reynolds number Re, of the above-mentioned four kinds of chan-nels are shown in Fig. 4. It can be seen from the figure that 1) the heat transfer in the latticework channel is higher than that in the smooth channel; 2) the heat trans-fer enhancement rate becomes smaller with Re increasing. The first conclusion can be explained that the ribs set in the latticework cooling channel disturb the formation and development of boundary layers, leading to the formation and enhancement of the secondary flow. With Re in-creasing and the secondary flow enhancing, the flow turbulence itself becomes stronger, by which decreases the heat transfer enhancement, thus accounting for the second conclusion. It also can be seen from the figure that the total heat transfer of the trapezoid and slotted channels are larger than that of the regular channel. As Re is smaller (<13,000), the total heat transfer of the slotted channel is larger than that of the variable channel, while as Re is larger (>13,000), it's just the reverse of the previous case.

Fig. 4Total heat transfer of four different kinds of channels.

Total flow resistance

The total flow resistances of the latticework channel and three other kinds of channels are shown in Fig. 5. Compared with the smooth channel, the flow distance in the latticework channel increases due to its configuration. The cross-sectional area is decreased too due to added ribs. The flow resistance, therefore, is increased remark-ably. With Re increasing, the flow resistance coefficient decreases gradually. The flow resistance of the trapezoid channel is larger than that of the regular channel due to the reduced channel cross-sectional area. To reduce the flow resistance caused by ribs without weakening the heat transfer, the ribs of regular channel are truncated at their two ends to form two straight slots along the flow direction at both sides of the channel, as shown in Fig. 3(b), caused the flow resistance to decrease.

Fig. 5 Total flow resistance of four different kinds of chan-nels.

Heat transfer enhancement ratio

The added ribs in the channel enhance the heat trans-fer as well as the flow resistance. It is necessary to take the flow resistance into account when evaluating the heat transfer efficiency of the channel. Therefore, the heat transfer enhancement ratio, a comprehensive dimen-sionless variable, is defined as follows:

1/3

s s

Nu

Nu

ξ

η

ξ

?

??

=??

??

(4)

254J. Therm. Sci., V ol.22, No.3, 2013

where Nu and ξare the Nusselt number and resistance coefficient, respectively. It is clear from Fig. 6 that (1). both the trapezoid channel and the slotted channel have larger heat transfer enhancement ratios than the regular channel; (2). for the slotted channel, its enhancement ratio is larger than 1, while for the regular and trapezoid channels, their enhancement ratios are smaller than 1.

Fig. 6Heat transfer enhancement ratio of three channels.

Local heat transfer

To analyze the local heat transfer, the transfer passage is divided into three sections, the inlet, middle, and outlet sections, along the flow direction. By measuring the condensed water mass and calculating the Nu numbers in each section, the local heat transfer characteristics of the latticework channels are obtained. Fig.7 showed the rela-tionships of local and total Nu numbers to the Reynolds number Re along the flow direction in the regular chan-nel with ribs. It can be seen that there are little difference for both local and total heat transfer characteristics, which can be explained as a fully developed flow passing through all the three flow sections, similar ribs configu-rations lead to similar heat transfer characteristics.

Fig. 7 Local and total Nu numbers of regular channel at diff-erent positions.

The local and total heat transfer characteristics of the trapezoid channel are shown in Fig.8. The local Nusselt number decreases gradually along the flow direction. The differences between the three local Nusselt numbers are approximately the same for different Re numbers. In the trapezoid channel, the cross-sectional area reduces gradually along the flow direction, the heat transfer coef-ficient drops along flow direction, even though the air-flow velocity increases.

Fig. 8 Local and total Nu numbers of trapezoid channel at different positions.

Fig. 9 shows the flow resistance characteristics of the slotted channel with S = 4 mm. Similar to the total Nu number, the local Nu numbers increase as the Re number increasing, and the increasing rates maintain approxi-mately constant. The slots cut on both sides of the regular channel cause changes in flow structures within the channels, so the altering trend of the local Nu number of the flow within all the subsections along the flow direc-tion becomes complicated. The middle section has the largest local Nu number while the inlet section has the smallest one.

Fig. 9Total and local Nu numbers of slotted channel with 4 mm slot width.

Slotted channels with different gap widths

According to the above discussion, without weakening its heat transfer characteristics, the slotted channel with S = 4 mm reduces the flow resistance, therefore it has bet-ter comprehensive heat transfer characteristics. In order to study the effect of the slot width on both heat transfer and flow resistance, the other three channels with S = 2 mm, 6 mm, and 8 mm were tested.

It is obvious from Fig. 10 that, the larger the gap width is, the smaller the total heat transfer, with the exception of the channel with S = 4 mm which has the highest total heat transfer. The heat transfer enhanced by crossed-ribs can be explained by the flow performance and the lat-ticework structure in the channels. According to the pressure distribution along the flow direction showed in Fig. 3(b), the most complicated areas in the crossed-rib channel are near the side walls where the air flow turned around. Two slots cut at both sides of the channel change

Hongwu Deng et al. Experimental Study on Heat Transfer and Flow Resistance in Improved Latticework Cooling Channels255

Fig. 10Total Nu numbers of slotted channel compared with regular and smooth channels

the direction of air flow, some of which is reflected by the wall and the rest flows directly through the slotted slots. Therefore, the flow behavior near both sides is very complex, and the disturbed air region in the channel is larger. For the channels with narrower slots, although the heat transfer area does not shrink too much, the flow in channels is pretty disturbed which enhances the heat transfer. When the slots become wider, more air flows directly through the slots, the disturbed region becomes smaller, the heat transfer area is decreased obviously, and the enhancement effect of heat transfer is weakened. As the slots became wider, the form of crossed-rib channel is more like the smooth channel, and the heat transfer effect declines further.

Fig. 11 Total flow resistance of slotted channel compared with regular and smooth channels.

The flow resistance characteristics of all the slotted channels compared with regular and smooth channels are shown in Fig. 11. It is clear from the figure that the flow resistances of all the slotted channels with different slot widths are much higher than that of the smooth channel. With the Re number increasing, the flow resistances of the 2 mm and 4 mm slotted channels decrease gradually. When the Re number is larger, the flow resistances be-come almost constant. Variations in the flow resistance with the Re number are more complicated for the 6 mm and 8 mm channels. When the Re number is small, the flow velocity also is small. So there are large differences in the flow velocity at the inlet of channels when the slots are widened to a considerable distance, causing the flow resistance to fluctuate acutely. When the Re number is large, changes in the flow resistance are similar to that of the 2 mm and 4 mm slotted channels.

It is also clear from Fig. 11 that the flow resistance curves of the 2 mm channel is higher than that of the 4 mm one, while those of 2 mm and 4 mm channels are obviously smaller than that of the regular one, reducing by more than a half. That is because the areas of ribs are reduced because they are truncated, and the frictions be-tween air current and ribs are reduced too. The flow re-sistances of 6 mm and 8 mm channels are above the curves of 2 mm and 4 mm channels.

It can be seen from Fig. 11 the relationship of the re-sistance coefficient ξ to the Reynolds number Re, that the variation in ξ of the smooth channel always is in the range of 0.23 ~ 0.37, which is pretty smaller than those of the latticework channels. For the latticework channels with ribs, it is due to the addition of ribs that greatly re-duce the channel areas, meanwhile, that make the flow in the channels become extremely irregular, leading to sig-nificant increase in the flow resistance. Careful analysis should be given to the channels with different slot widths. The flow resistances of the channels with 2 mm and 4 mm slot widths, and as well as their trends, decrease rapidly with the Re number increasing until smaller than 0.8 x 104; after which, they tend to be almost constant. While the flow resistances of the channels with 6 mm and 8 mm slot widths fluctuate dramatically in the range of 80 ~ 190, with the Re number increasing and smaller than about 0.8 x 104; with Re being bigger than about 0.8 x 104, the variations in ξ become similar to other chan-nels, decrease slowly and tend to be almost constant.

Fig.12 shows the heat transfer efficiencies of all the slotted and regular channels, among which, the total heat transfer efficiency of the 4 mm channel is the highest, the heat transfer efficiencies of the 8 mm channel and the regular channel are pretty close.

Fig. 12 Heat transfer enhancement ratio of slotted channel compared with regular channel.

256J. Therm. Sci., V ol.22, No.3, 2013

Conclusions

The heat transfer and flow resistance of three kinds of latticework (vortex) channels have been experimentally studied. According to the study, the heat transfer effi-ciencies of regular latticework channels are better than that of the smooth channel, while their flow resistances are greatly increased because of an addition of ribs to them.

The heat transfer of slotted latticework channels are better than those of regular latticework and smooth channels with the same configuration. The flow structure or distribution in the slotted channels becomes quite complex. The flow resistance of 2 mm and 4 mm chan-nels are obviously lower than that of regular channel, but they are still much higher than that of smooth channel. Compared to regular channel, the total heat transfer effi-ciencies of slotted channels are fairly improved, among them the 4mm slotted channel has the biggest enhance-ment.

From the experimental results, it can be seen that lat-ticework channel with proper slots has a bright prospect in the design of the inner cooling channels of turbine blades.

Acknowledgment

We are grateful for the support of the National Natural Science Foundation of China (No.200604096). References

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1998.

巴尔扎克简介

巴尔扎克简介(1799~1850) 法国小说家.1799年5月20日生于巴黎以南的图尔城, 1850年8月18日卒于巴黎.巴尔扎克的一生,处于19世纪前半期的50年,经历了拿破仑帝国的战火纷飞的岁月,动荡不安的封建复辟王朝,以及以阴谋复辟帝制的路易□波拿巴为总统的第二共和国.他用总标题为《人间喜剧》的一系列小说,反映了剧烈的社会变革时期的法国生活. 巴尔扎克出生后不久就被送到附近的乡村去寄养. 上小学后一直到中学毕业,他始终寄住在宿舍里,没有能回 家过一段比较长的日子,享受家庭生活的温暖.离开家庭的童年生活的痛苦使他毕生难忘. 巴尔扎克的父亲原姓巴尔沙,是个精明强干的人. 他来自农村,幼年时跟当地教士学了一点文化,中年致富,在外省当过副市长,供应军粮的承包商,在巴黎经营过呢绒商业,当过巴黎驻军的军需负责人,是一个白手起家的资产者. 1816年,17岁的巴尔扎克结束中学的学业后进大学法科,并在文科旁听.18岁时,先后在诉讼代理人和公证人的办事处当见习生或书记. 从20岁开始,巴尔扎克决定从事文学创作.他在巴黎贫民区租了一间房顶上的阁楼,由父母供给极有限的一点生活费,埋头写作.他的第一部作品是五幕诗体悲剧《克伦威尔》,这是一部完全失败的作品,没有引起任何人的兴趣.接连又写了十多部小说,有的是自己所写,有的是和别人合写.这一阶段他所写的小说全用笔名发表.这些作品并没有给他带来生活所需要的物质条件,他只好暂时放弃文学.1826年借钱出版了一部普及版的《莫里哀全集》,接着又出版一部拉封丹寓言诗集, 销路不佳,亏损负债9,000法郎.后又借债经营印刷厂和铸字厂,均以赔本告终.他前后负债共达6万多法郎. 从1828年夏季开始,巴尔扎克决定重新回到文学事业上来.他写了一部以布列塔尼封建势力武装叛乱反对共和国为题材的小说《最后一个舒昂党人》(后来编入《人间喜剧》,改名《舒昂党的人们》).这是巴尔扎克所写的第一部严肃的文学作品,第一次用巴尔扎克真姓名发表.此书问世,初步奠定了作者在文学界的地位. 接着发表小说《婚姻生理学》,在读者之间引起广泛注意.1831年他的新著《驴皮记》出版,巴尔扎克立即成为法国最负盛名的作家之一. 1819到1829年,是巴尔扎克在文学事业上的探索阶段.从1829年开始,一直到1848年,是他创作《人间喜剧》的时期,也是他文学事业的全盛时期.他用超人的才智与精力,在不到20年的时间内,共创作小说91部.平均每年产生作品四,五部之多.他每日伏案一般都在10小时以上,常常连续工作18小时.有时文思如泉涌,或者为了赶写稿子,他一连几天废寝忘餐,夜以继日地劳动.根据阿尔贝·贝干教授提供的材料,巴尔扎克的杰作《高老头》(原名《高立欧老爹》)是他用三天三夜一气呵成的. 什么是《人间喜剧》的作者的创作动力人们说是因为他负债过多,需要用稿费还债.巴尔扎克年轻时经营印刷出版业确曾负债巨万.但从他成为名重一时的小说家之后,他的收入丰厚,出版商争着和他签订合同,不惜重金预约他尚未完成或尚未动笔的小说稿,早年的债务早已还清.名作家巴尔扎克生活阔绰,醉心于豪华的排场.他在巴黎同时安置了几处住宅和别墅,出门坐最富丽的马车,驾着骏马;仆役都穿制服;他也服饰华贵, 出入于名门大户的沙龙.由此可见,他的勤奋创作,绝对不是由于贫困. 巴尔扎克从年轻时开始就自信有很高的文学才能, 对文学有极大的抱负.他不舍昼夜地勤奋写作,主要因为有一股激情在内心沸腾,促使他充分发挥自己的才能, 要求在文艺界做一番伟大的事业.在他的书室里,有一座作为摆饰的小型拿破仑塑像.在塑像座盘边上,巴尔扎克亲笔写着:"他用宝剑未能完成的大业,我将用笔杆来完成." 巴尔扎克要完成的伟大事业就是《人间喜剧》这座巍峨的文学里程碑.第一次在这位小说家笔下出现《人间喜剧》这个名词是在1813年.毫无疑问,《人间喜剧》的命名是受但丁长诗《神圣喜剧》(中译《神曲》)标题的启发.1841年,巴尔扎克确定了这个庞大的创作计划.当时有四家出版商和巴尔扎克签订合同,合资承包《人间喜剧》的出版工作.1842年,巴尔扎克写了《人间喜剧·导言》,阐述他写作这部史无前例的文学巨著的宗旨.1845年巴尔扎克亲笔写的《人间喜剧总目》,一直保存到现在.根据这个《总目》,《人间喜剧》分为三大部分:《风俗研究》,《哲理研究》和《分析研究》. 《风俗研究》内容最为丰富,包括小说最多.因此这一部分又分为六个门类:1.《私人生活场景》,2.《外省生活场景》,3.《巴黎生活场景》,4.《政治生活场景》, 5.《军队生活场景》,6.《乡村生活场景》.《私人生活场景》包括32部小说,其中4部当时已有提纲,尚未起稿.已经完成的28部之中包括著名的《高老头》(1834), 《猫滚球布店》(1830),《夏倍上校》(1832)和《三十岁的女人》(1831~1834)等.《外省生活场景》包括17 部小说,其中6部尚未完成;已经发表的11部中包括《欧也妮·葛朗台》(1833),《幽谷百合》(1835)和《幻灭》(1837~1843)等.《巴黎生活场景》共有20部小说, 其中6部尚未产生;在已经发表的小说中有《金目少女》 (1834),《纽沁根银行》(1838),《塞沙·皮罗多兴衰记》(1837),

高中语文 名著导读《高老头》巴尔扎克简介素材 新人教版必修3

巴尔扎克简介 巴尔扎克(Honore de Balzac,1799~1850),他是19世纪法国伟大的批判现实主义作家,欧洲批判现实主义文学的奠基人和杰出代表。一生创作96部长、中、短篇小说和随笔,总名为《人间喜剧》。其中代表作为《欧也妮·葛朗台》、《高老头》。100多年来,他的作品传遍了全世界,对世界文学的发展和人类进步产生了巨大的影响。马克思、恩格斯称赞他“是超群的小说家”、“现实主义大师”。 巴尔扎克出生于一个法国大革命后致富的资产阶级家庭,法科学校毕业后,拒绝家庭为他选择的受人尊敬的法律职业,而立志当文学家。为了获得独立生活和从事创作的物质保障,他曾试笔并插足商业,从事出版印刷业,但都以破产告终。这一切都为他认识社会、描写社会提供了极为珍贵的第一手材料。他不断追求和探索,对哲学、经济学、历史、自然科学、神学等领域进行了深入研究,积累了极为广博的知识。 1829年,巴尔扎克完成长篇小说《朱安党人》,这部取材于现实生活的作品为他带来巨大声誉,也为法国批判现实主义文学放下第一块基石,巴尔扎克将《朱安党人》和计划要写的一百四五十部小说总命名为《人间喜剧》,并为之写了《前言》,阐述了他的现实主义创作方法和基本原则,从理论上为法国批判现实主义文学奠定了基础。 巴尔扎克在艺术上取得巨大成就,他在小说结构方面匠心独运,小说结构多种多样,不拘一格、并善于将集中概括与精确描摹相结合,以外形反映内心本质等手法来塑造人物,他还善于以精细人微、生动逼真的环境描写再现时代风貌。恩格斯称赞巴尔扎克的《人间喜剧》写出了贵族阶级的没落衰败和资产阶级的上升发展,提供了社会各个领域无比丰富的生动细节和形象化的历史材料,“甚至在经济的细节方面(如革命以后动产和不动产的重新分配),我学到的东西也要比从当时所有职业历史学家、经济学院和统计学家那里学到的全部东西还要多”。(恩格斯:《恩格斯致玛·哈克奈斯》) 巴尔扎克以自己的创作在世界文学史上树立起不朽的丰碑。

《葛底斯堡演讲》三个中文译本的对比分析

《葛底斯堡演讲》三个中文译本的对比分析 葛底斯堡演讲是林肯于19世纪发表的一次演讲,该演讲总长度约3分钟。然而该演讲结构严谨,富有浓郁的感染力和号召力,即便历经两个世纪仍为人们津津乐道,成为美国历史上最有传奇色彩和最富有影响力的演讲之一。本文通过对《葛底斯堡演讲》的三个译本进行比较分析,从而更进一步加深对该演讲的理解。 标签:葛底斯堡演讲,翻译对比分析 葛底斯堡演讲是美国历史上最为人们所熟知的演讲之一。1863年11月19日下午,林肯在葛底斯堡国家烈士公墓的落成仪式上发表献词。该公墓是用以掩埋并缅怀4个半月前在葛底斯堡战役中牺牲的烈士。 林肯是当天的第二位演讲者,经过废寝忘食地精心准备,该演讲语言庄严凝练,内容激昂奋进。在不足三分钟的演讲里,林肯通过引用了美国独立宣言中所倡导的人权平等,赋予了美国内战全新的内涵,内战并不仅是为了盟军而战,更是为了“自由的新生(anewbirthoffreedom)”而战,并号召人们不要让鲜血白流,要继续逝者未竞的事业。林肯的《葛底斯堡演讲》成功地征服了人们,历经多年仍被推崇为举世闻名的演说典范。 一、葛底斯堡演说的创作背景 1.葛底斯堡演说的创作背景 1863年7月1日葛底斯堡战役打响了。战火持续了三天,战况无比惨烈,16万多名士兵在该战役中失去了生命。这场战役后来成为了美国南北战争的一个转折点。而对于这个位于宾夕法尼亚州,人口仅2400人的葛底斯堡小镇,这场战争也带来了巨大的影响——战争遗留下来的士兵尸体多达7500具,战马的尸体几千具,在7月闷热潮湿的空气里,腐化在迅速的蔓延。 能让逝者尽快入土为安,成为该小镇几千户居民的当务之急。小镇本打算购买一片土地用以兴建公墓掩埋战死的士兵,然后再向家属索要丧葬费。然而当地一位富有的律师威尔斯(DavidWills)提出了反对意见,并立即写信给宾夕法尼亚州的州长,提议由他本人出资资助该公墓的兴建,该请求获得了批准。 威尔斯本打算在10月23日邀请当时哈佛大学的校长爱德华(EdwardEverett)来发表献词。爱德华是当时一名享有盛誉的著名演讲者。爱德华回信告知威尔斯,说他无法在那么短的时间之内准备好演讲,并要求延期。因此,威尔斯便将公墓落成仪式延期至该年的11月19日。 相比较威尔斯对爱德华的盛情邀请,林肯接到的邀请显然就怠慢很多了。首先,林肯是在公墓落成仪式前17天才收到邀请。根据十九世纪的标准,仅提前17天才邀请总统参加某一项活动是极其仓促的。而威尔斯的邀请信也充满了怠慢,

巴尔扎克

巴尔扎克 1、巴尔扎克的文学史地位 巴尔扎克是法国伟大的小说家,是19世纪批判现实主义文学的主要代表。在20年间呕心沥血写作实践中,巴尔扎克在世界文学史上构筑了一座举世无双的巍峨大厦——《人间喜剧》,而他自己则成了“文学中的拿破仑”。 马克思非常推崇巴尔扎克,认为他“对现实关系具有深刻理解”。恩格斯赞誉他的作品有着“了不起的革命辩证法”,并在《致玛·哈克奈斯》一信中对他作了精辟的论述。 2、生平与创作概况 A.全称: xx·xx·巴尔扎克 B.本姓: xx C.生卒____年__月__日: 1799.5.20— 1850.8.18 D.出生地: xx E.家庭: 中产阶级之家 F.教育:1816年结束中学学业 G.主要经历:

1819-1829年,开始写作小说; 1825年起出版图书,开办印刷厂,铸造铅字,以欠债6万法郎告终; 1828-1850年,全力创作《人间喜剧》。 H.主要成就: 包括90余部长篇小说、中篇小说、短篇小说的文学巨著《人间喜剧》。 3、巴尔扎克的创作道路 1819-1829年,探索阶段;1819年,立志当作家。1820年,写作悲剧《克伦威尔》失败,开始创作神怪小说,也未获成功。此后至1828年前,屡屡经商失败,债台高筑。1828年夏起重走文学道路。1929年以真名发表历史小说《朱安党人》,初获成功,在文坛站稳脚跟。 1829-1845年,黄金时代;巴尔扎克怀着做“文学上的拿破仑”的雄心壮志,孜孜不倦地创作,建构着《人间喜剧》这座艺术大厦,接连发表了许多杰作,如《高布赛克》 (1830)、《驴皮记》 (1831)、《xx·xx》 (1833)、《xx》 (1834)、《无神论者做弥撒》 (1836)、《xx银行》 (1837)、《幻灭》(1837-1843)和《农民》 (1845)等。 1846-1850年,晚期。1848年前,巴尔扎克陆续完成了《贝姨》

译文对比分析

话说宝玉在林黛玉房中说"耗子精",宝钗撞来,讽刺宝玉元宵不知"绿蜡"之典,三人正在房中互相讥刺取笑。 杨宪益:Pao-yu,as we saw, was in Tai-yu?s room telling her the story about the rat spirits when Pao-chai burst in and teased him for forgetting the “green wax” allusion on the night of the Feast of Lanterns. 霍克斯: We have shown how Bao-yu was in Dai-yu?s room telling her the story of the magic mice; how Bao-Chai burst in on them and twitted Bao-yu with his failure to remember the …green wax? allusion on the night of the Lantern Festival; and how the three of them sat teasing each other with good-humored banter. 对比分析:杨宪益和霍克斯在翻译“耗子精”采用来了不同的处理方法,前者使用了异化”rat spirits”,后者用的是归化法”magic mice”,使用归化法更受英美读者的亲乃。但是二者同时采用了增译法,增添了the story,原文并没有。在翻译“宝玉不知绿烛之典”的“不知”,英文1用的是“forgetting”,而译文2用的是“with failure to ”,显然译文2更符合英美的表达习惯。 那宝玉正恐黛玉饭后贪眠,一时存了食,或夜间走了困,皆非保养身体之法。幸而宝钗走来,大家谈笑,那林黛玉方不欲睡,自己才放了心。 杨宪益:Pao-yu felt relieved as they laughed and made fun of each other, for he had feared that sleeping after lunch might give Tai-yu indigestion or insomnia that night, and so injure her health. Luckily Pao-chai?s arrival and the lively conversation that followed it had woken Tai-yu up. 霍克斯: Bao-yu had been afraid that by sleeping after her meal Dai-yu would give herself indigestion or suffer from insomnia through being insufficiently tired when she went to bed at night, but Bao-chai?s arrival and the lively conversation that followed it banished all Dai-yu?s desire to sleep and enabled him to lay aside his anxiety on her behalf. 对比分析:译文一对原文语序进行了调整,先说了“放心”,再说“担心”,但并不如不调整顺序的逻辑强。译文二只是用了一个“but”就把原文意思分层了两层,逻辑更加清晰,符合西方人注重逻辑的习惯。原文中的“谈笑”是动词,而两个译文版本都是译的“the lively conversation”,是名词,体现了汉语重动态,英文重静态的特点。 忽听他房中嚷起来,大家侧耳听了一听,林黛玉先笑道:"这是你妈妈和袭人叫嚷呢。那袭人也罢了,你妈妈再要认真排场她,可见老背晦了。" 杨宪益:Just then, a commotion broke out in Pao-yu?s apartments and three of th em pricked up their ears. “It?s your nanny scolding Hai-jen,” announced Tai-yu. “There?s nothing wrong with Hai-jen, yet your nanny is for ever nagging at her. Old age has befuddled her.”

《傲慢与偏见》译文对比分析

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