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PRELIMINARY RESULTS ON PASS1 VE EDDY CURRENT DAWER TECHNOLOGY FOR SSME TURBOWCH I NERY Robert E . Cunningham NASA Lewis Research Center Cleveland, Ohio 44135 ABSTRACT Some preliminary results have been obtained for the dynamic response of a mtor operating over a speed range of 800 to 10,000 rpm. hplitude frequency plots show the lateral vibratory response of an unbalanced rotor wi th and without external damping. R e mode of damping is by means of eddy currents generated with 4 "c" shaped permanent magnets installed a t the lower bearing of I vertically oriented rotor. The lower ball bearing and its damper assmlaly are 'totally imersed in liqui d nitrogen a t a temperature of -1970C (-320QFj. mese preliminary results for a referenced or base l ine passive ed@ current damper assembly show that the ampliQde of synchronous vibration 4 s reduced a t the resonant frequency . Measured damping coefficients were calculated to 9 .086; this cmpares with a theoretically calculated value of 9 .079. INTRODUCTION o Bpirsved performance and durabililtiy of SSME turbopumps will depend, to a large deg~ee,on an effective and predlctabl e mechanism for dfssipatdng v4bratfonal ener* in the rotors. s Properly designed dampers located a t or near bearing supports can be effective in controlling vibrations produced by rotor unbalance, comonly known as synchronous whirl . o Dampers can also be effective in controlling non-synchronous whirl, the type often pwduced by shaft internal hysteresi s, hydrodynami c seals, interference fi ts, tie bolts, etc. o Damg~ers can reduce the dependence on ultra precision balancing or the need for frequent rebal ancing. o Dampers along with properly designed flexible bearing supports can reduce magnwde of transmitted forces thru the ball bearings to the casing, and thus extend ball bearf ng l i fe. o A unique method of dam ing is by means of ed& current generation in a conductor caused to vi ! rate in a mgnetic flux field, o The low temperatures encountered in the turbopumps actually increase the avaj l able enerw di ssi pati on and thereby make this wchani sm an attrac tl ve candidate for SSME turbomachinery. https://ntrs.nasa.gov/search.jsp?R=19850018579 2020-07-11T22:53:19+00:00Z
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Page 1: Some - ntrs.nasa.gov › archive › nasa › casi.ntrs.nasa... · o h obJective of this work 4s to verify by experfmentatfon the der~fveo re0 atf snshi p that deff ne the eddy current

PRELIMINARY RESULTS ON PASS1 VE EDDY CURRENT DAWER TECHNOLOGY FOR SSME TURBOWCH I NERY

Robert E . Cunningham NASA Lewis Research Center

Cleveland, Ohio 44135

ABSTRACT

Some preliminary results have been obtained for the dynamic response of a mtor operating over a speed range of 800 to 10,000 rpm. hpl i tude frequency p lo ts show the lateral vibratory response of an unbalanced rotor w i t h and wi thou t external damping. R e mode of damping is by means of eddy currents generated w i t h 4 "c" shaped permanent magnets installed a t the lower bearing o f I vertically oriented rotor. The lower ball bearing and i ts damper assmlaly are 'totally imersed i n liqui d nitrogen a t a temperature of -1970C (-320QFj. mese preliminary results for a referenced or base l ine passive ed@ current damper assembly show that the ampliQde of synchronous vibration 4 s reduced a t the resonant frequency . Measured damping coefficients were calculated to 9 .086; this cmpares w i t h a theoretically calculated value o f 9 .079.

INTRODUCTION

o Bpirsved performance and durabililtiy of SSME turbopumps will depend, to a large deg~ee, on an effective and predlctabl e mechanism for dfssipatdng v4bratfonal ener* i n the rotors.

s Properly designed dampers located a t or near bearing supports can be effective i n controlling vibrations produced by rotor unbalance, comonly known as synchronous whirl .

o Dampers can also be effective i n controlling non-synchronous whirl, the type often pwduced by shaft internal hysteresi s , hydrodynami c seals, interference f i ts, t i e bolts, etc.

o Damg~ers can reduce the dependence on ultra precision balancing or the need for frequent rebal ancing.

o Dampers along w i t h properly designed flexible bearing supports can reduce magnwde of transmitted forces t h r u the ball bearings to the casing, and t h u s extend ball bearf ng l i fe.

o A unique method of dam ing is by means of ed& current generation i n a conductor caused to v i ! rate i n a mgnetic flux field,

o The low temperatures encountered i n the turbopumps actually increase the avaj l able enerw d i ssi pati on and thereby make this wchani sm an a t t rac tl ve candidate for SSME turbomachinery.

https://ntrs.nasa.gov/search.jsp?R=19850018579 2020-07-11T22:53:19+00:00Z

Page 2: Some - ntrs.nasa.gov › archive › nasa › casi.ntrs.nasa... · o h obJective of this work 4s to verify by experfmentatfon the der~fveo re0 atf snshi p that deff ne the eddy current

o h obJective of this work 4s t o verify by experfmentatfon the der~fveo re0 atf snshi p t h a t deff ne the eddy current damping coefficient,

o A rohting rest apparatus was designed and fabricated Sn order to properly evalua& candidate damper designs over a speed range of 800 t o 10,OQQ rpm while operating i n I i qu id nitrogen a t -1 95oC,

o Measured rotor response t o unbalance forces w i t h and wfthout applfed damping are cmpared to theorettcal results fmm a cwguter code,

'E4 AND CQh\D@kLO%IOW$

o kmnsl~aled the successful attenuation of synchronous vibratfsn a t the f i r s t I;yskem resonance using passive eddy cursent damping f n 1 f quBd n i trogew ,

o Obtained reasonable agreement between theoretical and measured response of an unbalanced rotor f o r both the undamped and damped eases. A n~easut*sd daswpng coefftcient of d = ,086 was obtained while the preddcted dampdng coefficient was calculated to Be 3 .079,

SREWIC OF EBOV B R E N T M P E R WNINF .EmY CURWEM PAWS IN @NMCTOR

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N REW DFI WPRWATUB L1WfD NS? SY 15,888 RPM DESXGN ,STIFF SHAFT

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NO. OF STATIOhS - 15

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S U M M A R Y O F T H E O R E T I C A L V S M E A S U R E D R E S P O N S E F O R L N 2 T E S T R O T O R

ROTOR UNBALANCE, .149 OUNCE - INCHES

SPRING CONSTANT, K, = 11,100 lblin

THEORETICAL RESPONSE

UNDAMPED DAMPED

W 4

RESONANT FREQ. 5400 a (CPM)

MAX. AMPLITUDE AT RESONANCE (MILS)

DAMPING COEFFICIENT

MEASURED RESPONSE

UNDAMPED DAMPED

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S U M M A R Y 0.F T H E O R E T I C A L V S M E A S U R E D P E S P O M S E F O R L N 2 T E S T R O T O R

ROTOR UNBALANCE, .149 OUNCE - INCHES

SPRING CONSTANT, K, = 11,100 lblin

TNEORETICAL RESPONSE MEASURED RESPONSE

UNDAMPED - DAMPED UNDAMPED DAMPED

MAX, AMPLITUDE AT RESaANCE- (MILS) a t 9 6.2 16.1 7.3