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

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Table A.11. Characteristics of niobium. J ' C Oan!.i•t 2 It °C /40-4 t° C . 106 1 0 C 200 2.3,6 20 1,1 20 7,0 .300 24,4 200 1,08 300 7,38 400 23,3 30P 1,06 400 7,54 500 25,o 400 1,06 500 7,61 550 22,7 500 1,0. 600, 7,86 KEY: (1) daN/mm 2 600 1,07 700 8,02 700 1,07 P100 •8,18 1027 1,07 IP27 8,0 1527 8,6 2027 9,1 d, daH/M 1 100- 20";0 40 6080100 2.00 400J 600 1000 2000* 40•00 8000 Fig. A.13. Rupture strength of niobium alloys. KEY: (1~) dV,N/mm 2 ; (2) hour. 648
Figures A.12 and A.13 present curves of short-term and long-term [rupture] strength of niobium alloys, plotted as a result of processing many literature sources. Molybdenum and its alloys Table A.5 presents the mechanical properties of molybdenum and some of its alloys, and Table A.6 gives data on the modulus of elasticity and the coefficient of linear expansion. Figures A.14 and A.15 illustrate the curves of short-.term and long-term [rupture] strength for molybdenum alloys. 80---- - II 70 -- -- - 60-.---. . 50 600 W 1100 WOO1200 V100 1600 M~OO VCý Fig. A. lit. Sho~rt-term strength of' molybdenum~ alloys. KEY: (1) daN/mm'?. 649
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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
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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
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o•/. or Oer 17,0 5,0 16,0-2 4,5 5
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- 0CX=, 9 - 280- 270- 110 0,15 __ -
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11 0,7 2,- 7,5 - '2,4- a'l 0,5 02 0
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55- . \, 105 50-100 45 ' 95 S85 "J
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Let us examine two cases: disk) and
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4. 100 0,6- WoO, ~: 1 0,94 493,8 3,
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0,7 3,3 -3,3 0,6 -3,2 0,15 3,0 2,9
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f~rc 200 -PC.; 190 40 170 30 I/t 0,
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a) arB 0 if the disk does not bear
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I I I I II I , Substituting this so
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Z= lz 1 x _-, 9 S1- 0,TF,1 o~ 5o o
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ii 0,1 42 0,3 ,4 0,50q6 0,7 08 0,9
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The expression for a* is obtained f
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, The'actual stresses on the bounda
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ý4.1 j L. - - c* m oc ~ .7 lira___
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C,4 C4C4 I IC4) CI tz +3Il + + CC.)
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C.. C4 0 C4 C I -T I -J . C :.d C?3
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Widely used methods are those based
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Solving the last equation relative
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Substituting the difference (awl -
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0 g h•con- - o7 g , 0,7 .Op • o
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iJ relaxation) occurs and with stea
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In the examired theory during plast
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Let, us p w I I ! • Let, us proce
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Rupture sets in only when plastic f
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£@ 1 hdr .1 (o) hr r(3.102) Usuall
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I Since the shaft is elastic, then,
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I I SI hence r M! rad/s ,(3.104) de
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y ii y0 \ 1 0-1 H t ieemNw idn 5ai7
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Critical angular velocities- of a s
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We assume that the disk and shaft a
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Expanding the determinant of (3.113
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y=aP-P+a, 2 M; a 21aiP+a22M# (3.119
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(1) ((2) O~7~C.• o~P'7t7- A O6/UC
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Wihen X = w, forward synchronous pr
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we find For forward synchronous pre
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•+ , , ; Im• S, -I i I I- I' su
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When analyzing the natural frequenc
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Vz 7M 7 ' z (KR--K-) z z (R (3.137)
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The concept of forced vibrations. t
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Resonance modes can be shown on the
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' C Yon no'. ern12 •. -p. 4 a..(a
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I ~ I 'Existing methods of damping
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Vibrations in rotors on hydrostatic
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SQTi •-fT 1 (O,0625VI)Y+1-0, 1-(p
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During the forward speed of the piv
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~t The coefficients of hydraulic fr
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of forces in the absence of pivot v
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To solve the problem of the vibrati
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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
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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
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The subscript "cep" e ~'~;+ f~dx. 0
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-- - ' 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
Page 474 and 475:
then "- D(0 + ) B& 3 ( +,u) aAt EAh
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Then instead of At(z) we shall writ
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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
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The mechanical strength of heat exc
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All the welding seams on the pipes
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I I! .jn the design of a heat excha
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.The following types of corrosion a
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To •clean lithium q the oxygen an
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t I * I where p is the permissible
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Additional tensile (compressive) st
Page 498 and 499:
Calculation formulas are valid unde
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The compliance parameter is determi
Page 502 and 503:
-KI 1- SI ' 2I -log VJ L0 Fig. 4.38
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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 ).
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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
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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
Page 546 and 547:
Hence generalized stress is SV2= f
Page 548 and 549:
Let us 3train a free shell loaded w
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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 (
Page 560 and 561:
,_ . l90 _. h-ID NI -rcz Lit 'w. a)
Page 562 and 563:
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
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K i... Linear shearing forces, obta
Page 576 and 577:
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 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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