-

FTD-ID(RS )I-1i409-76

'FOREIGN TECHNOLOGY DIVISION

fRESULTS CF THE EXPERIMENTAL STUDY OF THE EFFECTON COMPRESSOR PARAMETERS FROM WATER

ADMITTED AT THE INLET TO ACENTRIFUGAL COMPRESSOR

by

A. S. Moskalenko, N. L. Zel'des

DDC

W Y D 9

Approved for public release;distribuition unlimited.

4 &IkH

FTD ID(RS)I-1409-76 yr

EDITED TRANSLATIONFTD-ID(RS)I-1409-76 19 November 1976

RESULTS OF THE EXPERIMENTAL STUDY OF THE EFFECTON COMPRESSOR PARAMETERS FROM WATER ADMITTED ATTHE INLET TO A CENTRIFUqAL COMPRESSOR

By: A. S. Moskalenko, N. L. Zeltdes

English pages: 18

Source: Samoletostroyeniye i Tekhnika Vozdushnogo Flota,Izd-vo Khar'kovskogo Ordena Trudovogo KrasnogoZnameni Gosudarstvennogo Universiteta Imeni A.M. Gor'kogo Khar'kov, 1970, Nr 22, PP. 39-46.

Country of origin: USSR ITranslated by: K. L. DionRequester: FTD/ETDBApproved for nublic release; distribution unlimited.

THIS TRANSLATION IS A RENDITION OF THE ORIGI.HAL FOREIGN TEXT WITHOUT ANY ANALYTICAL OREDITOMIIA! COMMENT. STATEMENTS OR THEORIES PREPARED BY:ADVOCATJOR IMPLIED ARE THOSE OF THE SOURCEAND DO NOT NECESSARILY REFLECY THE POSITION TRANSLATION DIVISIONOR OPINION OF THE FOREIGN TECHNOLOGY DI. FOREIGN TECHNOLOGY DIVISIONVISION. WP-AFB, OHIO.

FTD ID(RS)I-1409-76 Date9 Nov 19 76

& a ~ -

U. S. BOARD ON GEOGRAPHIC NAMES TRANSLITERATION SYSTEM

Block Italic Transliteration Block Italic Transliteration

A a A a A, a P p P p R, rB ( 6 B, b C c C c S, sBa B V, v Tr T m T, tr r re G, g Y y Y y U, u

A 21 a D, d o F, fE e E a Ye, ye; E, e# X x X x Kh, kh

W X AV Zh, zh U L if Ts, ts

3 a 3 1 Z, z HI 4tq Ch, ch1 H i I, i W w if Sh, sh

A R f Y, y U 4 X II Shch, shch

KHK K, k b-A n /7 a L, 1 bl b' M I Y, y

M M M M M, m bb b &H H H .v N, n B3 a .9 h, e0 0 0 0 O, oC I0 0 10 Yu, yu

fln 7 x P, p Ya, yA

*ye initially, after vowels, and after b, b; e elsewhere.When written as 6 in Russian, transliterate as y6 or 6.The use of diacritical marks is preferred, but such marksmay be omitted when ey ediency dictates.

GREEK ALPHABET

Alpha A a £ Nu N vBeta B 8 X1 _

Gamma r y Omicron 0 0

Delta A 5 Pi 11 rr

Epsilon E E f Rho P P 0

Zeta Z r Sigma £ o

Eta H n Tau T T12 Theta 0 e S Upsilon T ulota I I Phi € (P

Kappa K Xt K Chi X XLambda A X Psi Y F

Mu M P ~ Omega QW

FTD-ID(RS)1-1409-76 iA'"'''* ' . . ""': .. . . . ... ..- ,. ,,, -,,,_,,._ , ,, " n dh' .'J A ' ', . ta ,' -. .. ,A ., -rzm wr # 'Is*

' '' , <i -[<-'

RUSSIAN AND ENGLISH TRIGONOMETRIC FUNCTIONS

Russian English

sin sin

Cos COS

tg tan

ctg cot

sec sec

cosec csc

sh sinh

ch cosh

th tanh

cth coth

sch sech

csch csch

arc sin sin-1

arc cos cos-1

arc tg tan 1

arc ctg cot-1

arc sec sec-i

arc cosec csc

arc sh sinh-I

arc ch cosh- 1

arc th tanh -1

arc cth coth - 1

arc sch sech - 1

arc csch csch -1

rot curl

lg log

GRAPHICS DISCLAIMER

All figures, graphics, tables, equations, etc.

merged into this translation were extracted

from the best quality copy available.

FTD-ID(RS)I-1409-7 6 ii

DOC 14qPAGE

RESULTIS T 'HE EXPERIMENTAL STUDY OF T~HE EFFECT ON4 COMPRESSOR

PARAMETEBS FROM WATER~ ADMITTED AT THE INL.T TC A CENTRIFUGAL

COMPRESSOR

A. S. Moskaloriko, N. L. %0-1 des

DESIGNATION LIST

sou w wa er

cYX. WMoA. dry air

inaanoe wet

CYXMo Ir

FTD-ID(RS )I-14O9-76

DOC 1409 PAGE 2

In the case of an elemental qas jet mioving in the rotor anti

adsorbing from the compressor impeller work dH, the equation of work

betwepn two infinitely close sections can be written in the form of

thf" g, neralized B(ernouilli equation:

dH = L" + d+dZ + dH,,

where P - pressure, 1 - specilic weight, C - absolute velocity, 7 -

height of arrangement, H - work on overcoming frictional forces.

It is tvident that the work of friction iH is turned into heat and

is imparted to t.h- gas from within in the amount dq,-=AdH,. Ktepin~izi

in mind that with gases the change in potential energy of position d7

is infinitely small in comparison with cthpr forms of energy of the

jet, and multiplying the obtained equation ty A = 1/427 (thermal

equivalent of mechanical wcrk), we obtain finally

AdH =AvdP+ Adi + dq,.

or, in finite form

(1) AH A vdP +A + q,.

FTD-ID (RS)I-109-76

DOC 1l09 PAGE 3

Th purpose. of the compression process in a centrifugal

compressor is to increaEe pressure. The power required to increase

air pressure from P. to must be the loast possible. ConsideringPKthat velocities CO and CK at the entrance and exit of the comFressor

are usually small and close to one another, we find from equation

(1), *U. it,, th* , theorem of mean value of the integral,

K

Al A vdP + q, = Av,, (P, - p) + q,.

or, sustituting

RT

(2) AH ARTHIPK

These equations show that there are only two ways of decreasinq th

wcrk cf compression:

1) decrease the compression of mean specific volume 11, in

c her words, decrease the meal, gas temperatUre during compression 7-

2) decrease the gas dynamic losses

Cooling the air compressed in the compressor by condensers and

jacketc-d devices in elements of the ccpFressor for circulating tl,

FTD-ID(RS)I-I 09-76

- -.

DOC = .09QPAGE

cooliz9 fluid must result in very considerable increase in the woiqht

and dim-ensions of the m1lotor and complicate its construction.

Therefore, in aviation gas-turbine engines, if the compressed air i.-

also cooled, then this is done usually only by the .vaporation of

fluid (water, alcohol, ammonjia etc.) absorbed directly into the flow

cf comj:ressed gas through special nozzles at the compessor e:ntrance

[1]. When liquid Pvaporates in comFressed air, the latter gives off

heat equal to the hoat ot evaporation. This decreases the polytropic

index cf compression, the work necessary to comrress air to a (iven

pressure, and also the temperature at the end of the compression.

Evaporat. ive cooling means are highly effective, and at the present

are also used in turbocomprossors. Esher-Wiess (Switzerland) has

turned out more than 100 centritugal compressors with evaporative

cool in q.

in 1967 the effect of wateL admitted at the entrance to a

compressor on thp operation of the comresscr itself was studie,

experimentally on a staqe of the 1)70-80-001 sb compressor

(, -16; Z 24; 6 = 0.5 mm).

Experimental Results

DOC 1409 PAGE 5

ExPerimOnta. stullies were. codute onl CCurressor revoltificn of

n i 5200 r/mia, n =7100 r/mir, n = 900 r/.in, ni = 11,000 r/min, v

12,500 r/Mi1, n =14,.000l, n 15,S00 r/min with differont positions

ot the but terf ly valv .

Tho t low rat(-) of water varifes from 10 91s to 130 q/s

T hk first. exp er im ents ticcun t red I if fic ulIti S caused I- y t hk

drops hitting the thermocouples at the cornrresE-Cr entrance.

L Computations of static t4E rperatulres in t hq sniallos+ sipction of

the measurinq devicc, mt thec comprecsor entraince, and A fttr tho

ccmress;,,or, conduct.M trom th tables of qjdS-dyratic ftunction,,; [21,

showod thut the-: st iti c tem~perature an t he ccmprvssor entrance oit.i

from tl- total temp-cature by rot more than 0.1?. Thorefore a

protectivo doflect ot was 1,laced on one ot the two theryocouV.es.

A,'.(n judging thp rc'.qii1ts of the experimental stiudy, it mu.t lt

k (-, [t i- minld that tho inj~ctior of water occurred in a comprcL-s~or

desiyn*'ui for Iry compres.s-icn.

* Denrce~ of Prrssur-3 Tncreasc

DOC 1409) r,t E

Tl~t main advantatle of Wlit(L injaction on thp compros'sor ortratict

is tho~ irxreise of achievable yLePssure inCLease. The affect. r'sut inj

in r(,.sure- incroas- is similar to the ettect fromt the supply of

cooled air to the ccmpr(-sSoi ertrance when the dpqrpee ot pross-urc'

incroa- with givon ivilble work bcces largEr.

sotuot imos tho prossur-~ is increasc-d in a wind tunn.ol which has

no mochanical equipmont by means of ccclinq due to the ('vaporation of

liquid in air flow (31.

Whon wit.or is inj-cv-,d itrto a tlow of a3ir movinq atlongJ a channel

of constant cross snet ion witlicut --nerqy suipl1y t rom without,~ it i.,

possible to .-t-paratp three conditions (4). In tho first sot of

conii tion,,; tht, spoed of air ro]ative tc drc . is latcqe. 7Iherctfore +11

Affect ot channel. re -isranc prodoiminat es, and st aqnation ressv-xre

decreasks i.n spito cf the fact that thc rate of vaporization i.,

iraximum. In that timte th.e drops becomp heatcd anti very rapidlyI

achiev(* t( mperatturver, close, to the dew Vcint. At such a temnporat ure

the oo1ivoiol hePit qoos 'ntirely to vaporizat icn. After achiceving t he

diew point, the temrneaturo ot d drop rCMaiPS pract ically corstan+ *

in) Iw secoijd s't of conditions the- relative spe"ed, and

DOC 140(l PAGE 7

conlsoqu-tty also tht, resi;El4.rcc, be'cope v' ry -mall, andi vaori7.atim

cf tht .ops, predomintes. Total pressurox fcw incrreasps, allb.eo.I

qrceatcr than its initial valuic. In view of the decrpis-p in eir

velocity iii this set ot condiltions. after a periodl Of dCC(% PLa tikon

the dreps achievte th" 311-ad Of biii. after which they move mn4

rapidly than the t;ai aind tic correspondiny resistanC~c m.

ri-qativt,. This mnt accoImpariy an increaseG in totdl prtlssurc. i1owt, voup

thv ntiod -'ffect is, execlticnd I ly -,Pal 1 since the sp~o of tho~ Orop

remain.- v,.Ly clos- to that of the air.

11, tli t hirl s-t of rordlit iors tbc air tomp:-ritutc' 9 as a ros-ult

of contjnkiaus lecroaso bfcn'% rutficicntly cice to tho~ t(-mpot rtUli

cf thc ii1ops, 'API th- Irop aian~ttr is so0 siral1 thit tho ra 4 t, ct

evaporat ion be com.s v;--ry low. Wi1 1 friction now bcom-'s th(N.

predowin i.:r 41 fetffect and tho apnunt rif total prcssurp ichipvin-j a

certain rii rximum vA lv'i ala in heo ins to decri-ase.

OCt, Of ths' mnost i mportanit paramxtcrs is the initidl. diamt~t-r of

the. drop. Whcr) it. chanj1cs ths' lkerikth of the channol necessary to

vaporizo i jiven imount. of linuid changes aFproximdto1y J.fl propoltion

to tho stilUirc, ot thiN diamotor [14].

Fov -xtrotp Ly har ;t drop diamt-trbrs the rate of vapocizati on can

to su .l tilAt t hc se-cond -.et ef coradjticns com~leoly djsapp-'ar.

bDOC 14014 tAGF 8

ri~iu I qraI0hs t he. chanir, in relative dorr of pLessur"

fi:r'- - (ra i of (JLI6 tI U* increds"' %ith injfnct ion- o f

wA tor to, to 1Jiroo of prlmsuie- lncreAsip without 4ater injection) as,(0..

a functiont of thv rclatijve tiow rate of the water ~ *f

MaXin'utiP dO(Irte ot J 'S~trt. inrr-aso with watfer inject ion tor a qiver.

set of cotmprotser OpoLatinc cordjtions when n = l)1)00O r/cuir, Z

7/hi 7 po, i tion ot buttitl y va lvso) is achieved at G a .02f6 r V

wat cr/q ki ry ti r 1. Th- ski-qrpp oi prosure increase is 2. 1% qrA" 1

than t , (tVqreo' ot protisurt, increasEu withcut watwc inipction. Up to

0.1 h oaio.oru tposieices- ()02(t~er~dtive*i'qre ot[Los~regymas

Conti 1n.1o1i:ly. III *his cais ' up to 7, sa 0.01 the rclativo ditaqLFP of

p r ossl~~ ii ro itcoak i~s . iniqn iticaini ly. which is causodI by +h. Io

fI cw t ct th.- wio. and by tl* I- ow vaporizoition rato, si~~. I

flozz1 i,- V~opo Lat nq Oui -.mall1 ditforont iais at iEuch a f1low Lato.'* i

CI ; I ow r~itt o 0 14 t hr, rd-, of 4-1rcrpasp i~ s~l cnioor'Itlyis Crass

:Ira Ac.j hi \C.eV in 3 1nt ji MU'ft~ , r--- br~;ins to decreast- at 7 > 0.02t).sa eyxe

Thin i- oxp,,Iainod by th-- fact tl~at wher G -0.026 thp Moist ~Iir is iii

r ~thercio of :at urait iri ard tuithor j rcrea~e in the flow rat, c!t tho-

watcr lo-n; niot caus-- .i t*:;,mp'-LaturP decuelasil i.e., at (dQnsity

inctL",i. hut only roiilts in alditional encrgy losses. frictional

lozso r b' *wvpn tho d1rop.- of wa teL ani air, tetwce n drops ot vi ~c-ri.n,'

C ha 11 wd *I;,s impa ct 1s- du-, to -ircps of water strikin te

-4

c= 1409 PAGE 9

Llades.

Flow Rato of Dry Air

The changc, in flow rate of dry air is graphed on Fig. 2.

When the amount of water fed into the flow increases, the mass

flow per second of dry air rises continuously. This is explained by

fhe ircrease in air density due to the Fressure increase and also due

to the temperature drop. Up to a relative water flow rate G = 0.014

the flow rate of air rises somewhat more slowly than on section =

0.014-0.025. The maximum flcw rate of dry air occurs at G 0.025. Tn

this set of conditions the flow rate of dry air is 4.8% greater than

the flow rate of dry air without injection of water. With a

suhsequent increase in the flow rate of water, i.e., when G > 0.025,

the flow rate of dry air begins to drop. This is explained by the

fact tfiat the temperE ure after the com[ressor remains virtually

constant, but. pressure decreases due to the additional energy loss

caused by the presence of unvaporized water particles in the flow.

Air T omperature Change After Compressor

C t- ~ - a4-~ a k~AflfrlLi

DC = 1409 PAGE 10

The change in temperature on the compressor (T-T*) is graphed

as a function of the water flow rate (Z) on Fig. 3, and characterizes

the rate of water evaporation. On section G = 0-0.01 the degree of

temperature decrease is somewhat less than on section 0 =

0.01-0.0185. The reason for this is that when the water flow rate is

low, the differential on the nozzle is small, the quality of spray is

bad and therefore the rate of evaporaticn is lower.

When the flow rate of water increases, the spray becomes finer

and the rate of evaporation increases. When the flow rate of the

water excedes 0.0185 the relative moisture content approaches unity;

therefore the degree of pressure drop decreases. With a flow rate of

G= 0.034, temperature is virtually equal to the temperature at G =

C.025., This indicatps that a state of sajturation is setting in.

Dependcnce of Power Hr:quired by Compressor Upon Flow Rate of Water

An increase in the flow rate of water means that the powor

required by the compressor per 1 kq dry air decreases continuourly;

4!

DOC = 1409 PAGE 11

this is a consequence ot the decrease in mean specific volume duripg

compression, in other words, a decrease in the mean air temperature

during compression (Fig. 4).

When the flow rate of water increases, a different law governing

change in power is observed. Change in flow rate of water from 0 to

0.014 results in a decrease in required power by 3.2 and a decrease

in relative water flow rate from 0.014 to 0.025 results in a power

drop by 10.8%, which is explained by the higher quality of liquid

spray at increased flow rates. In conditions with a water flow rate

of 0.025 power changes insignificantly.

Decrease in power with water injection amcunts to 15% The

obtaincd results shcw good agreement with values introduced by V. F.

Ris 5].

Percent of Water Evaporation

Tho relative content of water at the temperature exit is

determined by the condensation method.

The results of processing experimental data indicate that prior

DOC = 1409 PAGE 12

to the state of saturation in the compresscr the entire amount of

water fed through the nozzle evaporates. This is ensured by the good

atomization of the nozzle, the characteristics of which were taken on

a special installation.

The effect of a differential on the nozzle on the degree of

fineness of atomization was studied. The results of the study

indicate that an increase in pressure differential on the nozzle

causes the diameter of the drop to decrease, at first rapidly, then

more slowly.

Total evaporation of water particles in the compressor is alsc

indicated by the amount of vaporized water as ottained from the

equation of energy balance written for the 'entrance-exit" section of

the compressor.

The temperature values fixed at a certain distance from the

section in which temperature is measured after the compressor, also

indicate total evaporation cf water in the compressor. These values

differ from temeratures recorded immediately on exit from the

compressor in the amount at, which considers heat exchange on the

"section K-control section" segment. Moreover, during moist

compression At is virtually equal to At in dry compression.

DOC =1409 PAGE 13,.1

Conclusions

1. Injection of water on suction intc a ccmpressor for the

purpos- of evaporative cooling of air consideratly decreases the

temperature of the latter on exit from the comFr.ssor.

Thus, with a water flow rate on the order cf 0.025 the air

temperature on the compressor exit decreases by approximately 43oc

with an ambient temperature of 11.8-13.1 0 C and relative- ambient

humidity 0 = 41-421%.

2. During compressor tests total evaporation of the injected

moisture occurred to the state of saturaticn with different turns and

ditffrent positions oi the butterfly valve.

3. vaporative cooling of air during compression in a

centrifuqal compressor operating at n = ccnst decreases the power

required by the compressor.

4. Fvaporative cooling increases the degree of pressure ris- and

increases the flow rate of the air.

DOC =1409 PAGE 14

5. The introduction of evaporative cooling cau.:;es the

characteristic curves of the compressor (Fig. 5) to shift somewhat

into the regioti of high flow rate in ccnnection with the increasfe i n

air density on the exit from the impeller.

6. it is necessary to study the effect of the positions ot the

water nozzle relative to the VNA intake edges on the compressor and

the degree of f inenoss; of atomizat ion on the required power and

efficiency of the compressor.

'I7. During the comnpressor operation (300 hours) no salt deposits

were ohSOLved on the rotor or the U~ade diffuser.

8. Watter was obs*,rve-d in the oil line of the lubrication system

during the: expe~rime-nt. This indicates that the use of evaporativ"

me-ans of cooling requires structural measures tc prevent water from

qetting into the oil.

DIFLIOGBAPIY

1. PeCSmweU AsiDraTeati. I'lep. c aitra. 11OA peat. H-. r. ay~paascoro. 6OM1pOr3. 1962.2. TadGtrwu r1130111itaiemaec~iox (4)yHKUHi. IHCTIITYT m.n .BP1OU 1B

MnmaicTepera a ADiaUHOHHOfl npombialeH0c'H CCCP, 1956. i E.14 Baatu,13.-B3. 1. T. H a in r i c k, WV. L. B e I d e. Some Investigations With wet Compression,

Transactions of the ASME, v. 15, 1953, M~ 3.4. Ociooni ra3oBOA AIIHBMI4KiI. PenaaKTop r. 3imnmotic. flep. c allrj. noa. pet. r. H. Ba.

5. B. 0. P mc. fklTpode)KHue Kxrnfpeccopiib&c maw~lnhi . Muwriia, M.-I. 9.

DOC =- 14 09 PAGE 15

- i:

B~SX

'-1

- . - ~ -- --/

ID * I

II

DOC 1409 PAGE 16

Fig. 1. -elative de groe of r.ressure inctease &" plotted against

the flow rate of water when n 15,500 r/min and Z - 7/16.

4x40

[ ~.i...

l ii

Fig. 2. Flow rate of dry air plotted against water flow rate when n

15,500 r/niin and Z = 7/16 -01MSo f lcw rate cf dry air with

injection of water).

FTD-ID(RS)I-11409-76

.--. , . -

DOC =1409 PAGE I1

pm I. uz.

F16 - --.- 1

0" ; s

#WCYX- - *1-

00

10 CYX 03A.

= '3.--- licyx. sou.- - - -

Kicyx. 03,.

0,025 [KS CYX- . J-

FTD-ID(RS) i-1J409-76

DOC - 1409 PAGE

Fig. 3. Change of temperature in compressor as a function of water

flow when n = 15,500 r/win an4 Z - 7/16.

Fiq. 4. Power required by ccmpressor as a function of water flow rat,,

at n 15,-,00 r/uin and 7 = 7/16.

-i

I

Fig. 5. Characteristic curves of compressor at n = 15,500 r/niri ald

different wator flow ratc:

Key: (1) kg/cm 2 , (2) kg/s.

FTD-ID(RS)I-1409-76

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DOCUMENTATION PAGE READ InUSTRUCTIOn 'REPORT ,PFORE COMPLETING FORMPORT NU . GOVT ACCESSION NO. D. RECIPIENTI CATALOG NUMIIM

FTD-ID(RS)I-1409-76 _4. TITLE (and Subitl.) 5. TYPE OF REPORT & EIO0 COVERED

RESULTS OF THE EXPERIMENTAL STUDY OF THEEFFECT ON COMPRESSOR PARAMETERS FROM WATER 'Pan latinnADMITTED AT THE INLET TO A CENTRIGUGAL S. PERFORMIG ORO. REPORT NUMB;RCOMPESSOROO. AU1.1R()

S. CONTRACT OR GRANT NUMRERfa)

A. S. Moskalenko, N. L. Zel'des

S. PERFORMING ORGANIZATION NAME AND ADRESS to. RRkRARMKL NT. PROJ ECT TAIK

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