Design and Stress Analysis of Extraterrestrial ... - The Black Vault

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£@ 1 hdr .1 (o) hr r(3.102) Usually, nr 1.2-1.5 and the safety factor is n .1.-1.8. IAn 350
Analysis of critical shaft speed With the use of turbines of rapidly revolving shafts a phenomenonf called "critical rpm" was detected. It was noticed that during the slow rotation of a rotor no noticeable vibrations are observed. The rotor rotates smoothly. With the achievement of a certain number of revolutions the rotor begins, without visible cause, to vibrate sharply, which can lead to the breakdown of a clearly strong shaft. in revolutions the rotor again begins to rotate quietly. With a further increase The rpm at whic" a shaft loses stability and begins to vibrate is called critical. Stress analysis of shafts is studied in courses on the strength of materials and machine parts. Therefore, in this section we shall examine only the questions of transient stability of shafts. Let us consider a shaft arranged vertically (for the elimination of the effect of its weight) in the middle cross section of which is attached a disk with mass m. Let us assume that the mass of the shaft is low as compared with the mass of the disk; however, the shaft possesses elastic properties. Let us also assume that the center of gravity of the disk c is displaced relative to the geometric center 01 by quantity e (Fig. 3.62). We further assume that supports allowing the shaft to rotate freely are absolutely rigid. When the rotor only begins to rotate and the elastic axis of the shaft is still a straight line (Fig. 3.62a), then, as a result of the displacement of the disk's c¢nter of gravity with respect to the axis of rotation, there appears centrifugal force mew 2 . Under the effect of this force the shaft begins to be deflected, which, in turn, leads to an increase in the centrifugal force 2 (Fig. 3.62b): PC m(y + eOw 351
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FTD:-MT-24-1462-71 FOREIGN TECHNOLO
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tUNCLASSIFIED - Security Ct-9-1uifl
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t IABLE OF CONTENTS U. S. Board on
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5.2. Ion motors ...................
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II jah _X JOLIGAETECbtSODN USA N NL
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,.is the calculation Of thermal str
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S1 In stress analysis the calculati
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"I 3 f !7 2 II 3 I 44; a ' 3 I 4 2
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)I requires special protection of t
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electrical power of the power insta
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Extraterrestrial motors in power fr
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S1' , . that a part operatesbefore!
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Fig. 1.3. Diagram of an ERE with me
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Table 1.3 shows the working media,
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I I The schematic of a nuclear ther
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Fig. 1.5. converter. Diagram of an
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The advantage of this arrangement i
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A complex system or any part of it,
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I I Stages and content of operation
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'the use of earlier systems and uni
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Structural diagram of operations Th
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. . . . . __.. . . . . .. .. . . .
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-- indication of state, transmissio
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Stages ERE, I. Analysis of the tech
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Space vehicle (SV) jParts jettisone
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Spc veil (SV)!- 0 4. ho 0. 4)Z - H4
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~tto 4- jo 0o (utd~nb 'Sa vtho- 4)i
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'Li However, 'this list can be chan
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- S developed. Or course, there are
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Sthat From the design and operation
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As the number or tests builds up-an
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II P 'Po. = -ý SFig. 1.20. Curves
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Stress is the intensity of the inte
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strength criterion only when even s
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JV Strength- reserve is the ratio o
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'2 1 I III I, . - I - S We know tha
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i J However, when the operating tim
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Plastic deformations in the latter
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Let us examine the basic design rel
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I I The constants B and n are deter
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Along with equation (1.18) we use e
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Iftesting continues, as shown in Fi
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I I Based on the known deformation
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6%Fx (a) Fig. 1,31., Uniaxial (a) a
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The element is in plastic state (1
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Total operating time of the sample
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I:! Substituting expression (1.35)
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Function B(T) is found after determ
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first We shall express stresses in
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etween it and the stressed state of
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a) b) c) Fig. 1.36. Determining the
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other conditions being equal, the c
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The fuel elements also rest on a li
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As the reflector and moderator in t
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Let us examine the examples of weld
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Between these shells passes a fluid
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The procedure for welding a two-lay
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A fuel element is a closed pressuri
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1 2A S(a) II • • /Fig. 2.8. Con
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The reflector material 5 (beryllium
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Figure 2.12 is a sketch of a fast n
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I. ! ~ ~~. . ........... li .... I
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I jZ ICIS qo 'Im klol
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THERMAL STRESSES IN FUEL ELEMENTS T
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Ora-O"when r=a; when r=b. (2.8) Sub
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I The exponential logarithmic depen
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I I of the cylinder between two adj
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EuI~, 21,2 Eat, • bb 2-(1 ---xInb
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-a - Fig. 2.18. Thermal stresses in
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I a It is necessary that n > 1l. If
Page 142 and 143:
The locus of points equidistant fro
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Equations of equilibrium for an axi
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Fig. 2.23. Equilibrium of a shell e
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:I I I I The first equilibrium equa
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The wall stress of this sphere is d
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I These formulas enable us to plot
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. . . S_.. I i. stresses. Maximum i
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Shells in the reactors which we sha
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axial stresses. Simplicity fully Ju
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abl-ab (R+AR)d-•Rdf AR ab Rd? R (
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V 1! II Point 3 corresponds to the
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SI Now we seek the pressure of the
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!I As is apparent from Fig. 2.39, t
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I I I I '' 9 capacity of a shell in
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SI a i f fit~ Z.rl -= •.r nl--~ ~
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We plot the unknown curve p = f(AR)
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-.. -, 7 ''°-^ ...... I}" L7,50s.
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I" Table 2.2. (Cont d) (1) V(. )3 (
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W/ dr (2.48) "The sign is negative
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Ve designate th6 relaitie -momenits
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a a I a A4l "• dr; P= pr dr idy;
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'(2.61) or in shortened form, V 2 V
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4i In this case, the constant C2 in
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will be If the external force is co
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I W -P [(a2 -I a +(•1 -r2)In a ("
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+) If we find that Wmax • h, the
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I I W c I , I- a , I. ' We cut the
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- (0,,i66.0,239. 10-6-0,484.0,33. 1
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-n I I I I Pig, 2.56. Determining t
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In some cases, it is assumed that t
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6e, I Smat a a SI r.+0P6h2a .. 'fro
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In designing a source it is necessa
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removal, for example, in a containe
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- 2d I I I ______ -. - I 2o ( 'I Z
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Ir dp;- N,= N, .(-N,,lr d$ + d (3,I
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It is perfectly obvious that the el
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dr dr, dMr, dr2 d, d2or 1 3 dr dr "
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I ! i I I The quality of the device
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The mirror surface, in this case, i
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Fig. 2.69. Thermal trap with contro
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i ffased on this factor, fuel eleme
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In extremely small pores (pore c) t
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why fuel elements with a solid elec
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Peazeemnl (l) Fig. 2.73. A regenera
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I. II As a result' of the- process,
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'4I '21
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U k IIl + (n2lpiim)() Fig. 2.78. Co
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I I I I Figure 1.3 shows one of the
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• C a is the axial velocity of th
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Figure 3.1 shows working blades of
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Fig. 3.11. Union of disk with shaft
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I *1 warping, the material of the h
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(a) (b) Fig. 3.6. Dry-fri'ction bea
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ing groove, and through the incline
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I '' S Albng with the variation in
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Friction and wear in such a bearing
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The transition from the oversaturat
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O a) CO- 4) U'% 0 4Z Oo .~ 0 t'24a)
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I _____ ', "I I The Na-K pump consi
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E- W2l.i rx.
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w is the angular velocity of disk r
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; I ' | * * I I j I l7 I II I' *
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and, finally, dPa 2.ir( 2r a dr z z
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Flexural stresses at any point' of
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Another means of unloading consists
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0 I I I In cae wetakii CO/7eHU~e *1
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Determining the frequencies of inhe
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Differentiating this equation, we f
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Equation '(3.?5) is a differentiale
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Functions S, T, U and V during diff
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1 JVQP (3.30') Fig. 3.24. Forms of
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Then the bendinv moment is t ! ! EI
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'!..... " - ;-~ .- .-.. ~ - - J I T
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Figure 3.25 shows the operation of
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2 I ' whe, For plottfng the donvert
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satisfies the bounaary conditions o
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- o0 CC 0 CL P% c - t- -. C4 t C Ci
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The angular velocity w Aof natural
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I. Each of the harmonics of the ang
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At each of the points of interse-ti
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The actual frequency of natural ben
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1 I i , II ' t S S "•< i, I S, 3.
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(In view of the smallness of angle
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dr dr r d• _._._.• .d~t 1 •t-
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7WI - For conical disks equation (3
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Hyperbolic disks. If the, thickness
Page 314 and 315: o•/. or Oer 17,0 5,0 16,0-2 4,5 5
Page 316 and 317: - 0CX=, 9 - 280- 270- 110 0,15 __ -
Page 318 and 319: 11 0,7 2,- 7,5 - '2,4- a'l 0,5 02 0
Page 320 and 321: 55- . \, 105 50-100 45 ' 95 S85 "J
Page 322 and 323: Let us examine two cases: disk) and
Page 324 and 325: 4. 100 0,6- WoO, ~: 1 0,94 493,8 3,
Page 326 and 327: 0,7 3,3 -3,3 0,6 -3,2 0,15 3,0 2,9
Page 328 and 329: f~rc 200 -PC.; 190 40 170 30 I/t 0,
Page 330 and 331: a) arB 0 if the disk does not bear
Page 332 and 333: I I I I II I , Substituting this so
Page 334 and 335: Z= lz 1 x _-, 9 S1- 0,TF,1 o~ 5o o
Page 336 and 337: ii 0,1 42 0,3 ,4 0,50q6 0,7 08 0,9
Page 338 and 339: The expression for a* is obtained f
Page 340 and 341: , The'actual stresses on the bounda
Page 342 and 343: ý4.1 j L. - - c* m oc ~ .7 lira___
Page 344 and 345: C,4 C4C4 I IC4) CI tz +3Il + + CC.)
Page 346 and 347: C.. C4 0 C4 C I -T I -J . C :.d C?3
Page 348 and 349: Widely used methods are those based
Page 350 and 351: Solving the last equation relative
Page 352 and 353: Substituting the difference (awl -
Page 354 and 355: 0 g h•con- - o7 g , 0,7 .Op • o
Page 356 and 357: iJ relaxation) occurs and with stea
Page 358 and 359: In the examired theory during plast
Page 360 and 361: Let, us p w I I ! • Let, us proce
Page 362 and 363: Rupture sets in only when plastic f
Page 366 and 367: I Since the shaft is elastic, then,
Page 368 and 369: I I SI hence r M! rad/s ,(3.104) de
Page 370 and 371: y ii y0 \ 1 0-1 H t ieemNw idn 5ai7
Page 372 and 373: Critical angular velocities- of a s
Page 374 and 375: We assume that the disk and shaft a
Page 376 and 377: Expanding the determinant of (3.113
Page 378 and 379: y=aP-P+a, 2 M; a 21aiP+a22M# (3.119
Page 380 and 381: (1) ((2) O~7~C.• o~P'7t7- A O6/UC
Page 382 and 383: Wihen X = w, forward synchronous pr
Page 384 and 385: we find For forward synchronous pre
Page 386 and 387: •+ , , ; Im• S, -I i I I- I' su
Page 388 and 389: When analyzing the natural frequenc
Page 390 and 391: Vz 7M 7 ' z (KR--K-) z z (R (3.137)
Page 392 and 393: The concept of forced vibrations. t
Page 394 and 395: Resonance modes can be shown on the
Page 396 and 397: ' C Yon no'. ern12 •. -p. 4 a..(a
Page 398 and 399: I ~ I 'Existing methods of damping
Page 400 and 401: Vibrations in rotors on hydrostatic
Page 402 and 403: SQTi •-fT 1 (O,0625VI)Y+1-0, 1-(p
Page 404 and 405: During the forward speed of the piv
Page 406 and 407: ~t The coefficients of hydraulic fr
Page 408 and 409: of forces in the absence of pivot v
Page 410 and 411: To solve the problem of the vibrati
Page 412 and 413: I I k i = Ib the projections of dis
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3 The general solution to (3.160) c
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(3.166) Thus, near the boundary of
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2 1z or 2.. .• .. :. • C .2,e.
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I 3.2. THERMOEMISSION ENERGY CONVER
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STRUCTURAL DIAGRAMS AND DESIGN OF C
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In the creation of the design serio
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I £ The nortcoming in this design
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'I, Fig. 3.92. Overall view of reac
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Figure 3.93 is a diagram of an elec
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We shall set up one of 'he shell se
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E3 e 2 , --e 1 , o A= B 3 , 0 --E 1
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worst efficiency. In the table the
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7,7 417 1 2 Fig. 3.96. Diagram of a
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A thermoelectric converter consists
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I 1A 7ý,, -- Fig. 3.101. Controlla
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Photoelectric Converters In a photo
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of 140 W with allowance for all los
Page 448 and 449:
Radiator coolers are divided into s
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2 A Fig. 4.2. A conical flexible un
Page 452 and 453:
Folding conical, radiators. As seen
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* ,. I- ] 2 : I KEY: ()aA (V)w °+
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point does not exceed the temperatu
Page 458 and 459:
The subscript "cep" e ~'~;+ f~dx. 0
Page 460 and 461:
-- - ' P l -- u -A - a .' • U1 1.
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AL Fig. 11.11. Determining thermal_
Page 464 and 465:
In the cross section of pipes and r
Page 466 and 467:
o> . .. Fig. 4.14. Stress diagrams
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1 I I I Thermal stresses in a a, fl
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We shall use Hooke's law for a two-
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i.e., the plate bends along a spher
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then "- D(0 + ) B& 3 ( +,u) aAt EAh
Page 476 and 477:
Then instead of At(z) we shall writ
Page 478 and 479:
Heat exchangers in which the heat t
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which is done by introducing into t
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-.............. . a U-shaped jacket
Page 484 and 485:
The mechanical strength of heat exc
Page 486 and 487:
All the welding seams on the pipes
Page 488 and 489:
I I! .jn the design of a heat excha
Page 490 and 491:
.The following types of corrosion a
Page 492 and 493:
To •clean lithium q the oxygen an
Page 494 and 495:
t I * I where p is the permissible
Page 496 and 497:
Additional tensile (compressive) st
Page 498 and 499:
Calculation formulas are valid unde
Page 500 and 501:
The compliance parameter is determi
Page 502 and 503:
-KI 1- SI ' 2I -log VJ L0 Fig. 4.38
Page 504 and 505:
Case 3. The shell is loaded simulta
Page 506 and 507:
The value of n for thin cylindrical
Page 508 and 509:
In the general case, critical time
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when ).
Page 512 and 513:
Axial displacement of compensator:
Page 514 and 515:
CHAPTER V MOTORS 5.1. PLASMA MOTORS
Page 516 and 517:
Pulsed pinch plasma motor This inot
Page 518 and 519:
In the plasma generator unit the ev
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If an external magnetic field is cr
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forces Fig. 5.5. acting Simplified
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Z I . . .. . . Pulsed plasma face-t
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The grain of the working medium is
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J 4J 0 0 514 ~
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I I Forces T e, while acting normal
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where D - 12 "). Let us return to e
Page 534 and 535:
It is significant also that when n
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where B is a coefficient; n is the
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Bend w is an elastic bend of the sh
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Thus, a linear law of temperature g
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;' -- e--- 1= - (20MO cosVxJr- Q 0
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Table 5. 1. 3x __ _ _ V I '0 I ! 0
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Hence generalized stress is SV2= f
Page 548 and 549:
Let us 3train a free shell loaded w
Page 550 and 551:
tt Solution is sought from formula
Page 552 and 553:
The value of wp is found from formu
Page 554 and 555:
We determine 1.29 1.29 D' Eh3 1,45
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Table 5.2. CT- p ,INI'•I.R 1. po-
Page 558 and 559:
. sin ir P ( 2P2C 4 ) + eP cos ,x (
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,_ . l90 _. h-ID NI -rcz Lit 'w. a)
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Computation of w'" is made in ,line
Page 564 and 565:
Table I 5.3. (2(2) (1 l10 _ _ _ _ _
Page 566 and 567:
We integr'ate this equation once mo
Page 568 and 569:
Table 5.4. _ _ _ () Kit)I ) (3) ( U
Page 570 and 571:
These formulas show that on the fre
Page 572 and 573:
pR _prtgii h (5.39) where R is the
Page 574 and 575:
K i... Linear shearing forces, obta
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1.1: deformation correspondz to-the
Page 578 and 579:
The assumed law of At enables us to
Page 580 and 581:
'I Thus, the solution to the nonhom
Page 582 and 583:
The diagram of the shell is shown i
Page 584 and 585:
Tne z?.ell dimension~, in our probl
Page 586 and 587:
Stresses in a circular diret.ion or
Page 588 and 589:
w lW 2- W- =--, (); r- '=r g "I ; r
Page 590 and 591:
I, * I I Suzt-ttuting conditions (5
Page 592 and 593:
-7 The obtained equation is a homog
Page 594 and 595:
PRINCIPAL AND OF MOTORS STRUCTURAL
Page 596 and 597:
The ionizer unit consists of the io
Page 598 and 599:
-ii 4 I medium 6 and heater 7. The
Page 600 and 601:
!8 41 C Fig. 5. 37. The positive io
Page 602 and 603:
Soldering the porous plate with the
Page 604 and 605:
I I I . 1 2 Fig. 5.39. Design of io
Page 606 and 607:
i,, 1B) 6".R1 Fig. 5.41. Plate elec
Page 608 and 609:
electrons from the cathode and then
Page 610 and 611:
Stress analysis of motor elements A
Page 612 and 613:
A- Fig. 5.47. Motor unit design. 4z
Page 614 and 615:
Let us project all forces acting on
Page 616 and 617:
I- (' l1dx dy '-7dx =0; Ox=O Rý tg
Page 618 and 619:
I The quaotity Scx consists of thre
Page 620 and 621:
The angle of shift is the variation
Page 622 and 623:
V Iv Yvox a, R&tgo Ox Oy z 2Ow+ 2 0
Page 624 and 625:
7 3- h 2 h 2 iY dz; 1Y=- -h'2 -h 2
Page 626 and 627:
F 2Ea / 2r 3 + a3 , A G _ L(aa3) 0
Page 628 and 629:
I dimension r, dr. We apply to the
Page 630 and 631:
We drop • from equations (5.86) -
Page 632 and 633:
1-IL'L + z A. 2 o,-1_€ ('~-1,2-lm
Page 634 and 635:
Function F(r) can be found from the
Page 636 and 637:
We integrate this equation twice. T
Page 638 and 639:
Here A 1 = (2)/(3,)(z + 1)(z + 3);
Page 640 and 641:
- Absolutely flexible membrane If a
Page 642 and 643:
2500- 2000 1500 -/ 1000 Y - 500 4j-
Page 644 and 645:
Movement of the bellows also depend
Page 646 and 647:
Is The coefficient kla! calculated
Page 648 and 649:
Fig. 5.65. Stress analysis of a bel
Page 650 and 651:
Table A.l. Mechanical properties of
Page 652 and 653:
.(ii (2) A, 6r,/M,.ajpa £'40- 6 dH
Page 654 and 655:
A shortcoming of graphite is the no
Page 656 and 657:
0 (1) (2) 40 6-16- i!• 2 [K1/MM 2
Page 658 and 659:
E ( dafi/MM 1 2 U) 2_ou . Iv 5000 1
Page 660 and 661:
I I I3 Table A.3. (Continued)' (1a)
Page 662 and 663:
Table A.11. Characteristics of niob
Page 664 and 665:
Table A.5. Mechanical properties of
Page 666 and 667:
Tungsten and its alloys Figure A.16
Page 668 and 669:
, - ,, I Table A.8. Modulus of elas
Page 670 and 671:
Bibliography 1. A it;ý' Ip e e Bn.
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Design and Stress Analysis of Extraterrestrial ... - The Black Vault

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