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BACKGROUND
This invention relates to a cryogenic envelope for a transmission line. In
this respect, a preferred embodiment of the invention will be described in
connection with a laminar insulated cryogenic envelope for a flexible
superconducting power transmission line.
In order to be commercially attractive, superconductive power transmission
lines must have low thermal losses and high reliability. Consequently, it
is an object of this invention to provide a transmission line having an
insulated cryogenic envelope that is both reliable and results in a low
heat-leak.
It is not uncommon for Dewar type cryogenic vessels to direct refrigeration
through tubes to shields located between layers of laminar insulation
within the container's vacuum space. Refrigeration tubes present a
problem, however, in that it is difficult to prevent heat from leaking to
them from the members which separate and provide a vacuum seal between the
transmission line and the surrounding vacuum jacket. The illustrated
transmission line, however, includes "reentry" structure for reducing the
heat-leak that is permitted to enter the line's interior.
In the above respect, the transmission of refrigeration from refrigeration
tubes to refrigeration shields presents a problem in that the tubes tend
to expand or contract at a rate that is different from the shields. Hence,
the embodiment about to be described includes a type of shield that is
adapted to maintain good thermal contact with the refrigeration tube, but
nevertheless is free to expand or contract at a different rate.
SUMMARY
In accordance with principles of the invention an elongated cryogenic
envelope is comprised of generally coaxial inner and outer tubes having a
vacuum chamber therebetween. A refrigeration tube runs through the vacuum
chamber in thermal contact with a foil wrapped about the inner tube. In
this manner, the refrigeration tube's cold transmitted to the shield, but
the tube is nevertheless slideable with respect to the shield so that the
refrigeration tube and the shield are permitted to expand or contract at
different rates.
Where a still further reduction in heat-leak is required, the refrigeration
tube enters the vacuum chamber through a "thermal standoff" means whereby
the "thermal distance" between the refrigeration tube and the outer tube
is made large relative to the physical distance therebetween.
BRIEF DESCRIPTION OF THE DRAWINGS
The foregoing and other objects, features, and advantages of the invention
will be apparent from the following more particular description of a
preferred embodiment of the invention, as illustrated in the accompanying
drawings in which like reference characters refer to the same parts
throughout the different views. The drawings are not necessarily to scale,
emphasis instead being placed on illustrating principles of the invention.
FIG. 1a is a schematic illustration of a multi-section cryogenic envelope
for a flexible superconducting power transmission line.
FIG. 1b is a cross sectional view of a segment of a superconducting
power-cable dewar assembly.
FIG. 1c is a sectional view of FIG. 1b taken along the lines c--c thereof.
FIG. 2 schematically illustrates a conventional structure for accommodating
a transfer line's expansion and contraction.
FIG. 3a is a schematic partially sectional view of an expansion-end portion
of a dewar assembly.
FIG. 3b is a schematic partially sectional view of the remainder of FIG.
3b's expansion-end portion connected, through broken away portions, to a
simple-end section.
FIG. 3c is an enlarged fragmentary view of a part of the expansion-end
portion illustrated in FIG. 3b.
FIG. 4 is an enlarged fragmentary view of a "thermal standoff" portion of
the dewar transfer line illustrated in FIGS. 3.
FIG. 5 is a schematic view of the end of an adapter ring partially
illustrated in FIG. 4.
FIG. 6 illustrates a modification of a portion of the structure illustrated
in FIG. 4.
FIG. 7 is an enlarged fragmentary view of a portion of an
inner-tube-bellows structure illustrated in FIG. 2.
FIG. 7a is a schematic end view of guide spacers adjacent a power cable
tube as seen when viewed along the lines a--a in FIG. 7.
FIG. 8 is a pictorial view of a power-cable dewar including a support for a
power-cable tube and refrigerant lines.
FIG. 8a is an end view of a support ring shown in FIG. 8.
FIG. 9 is a pictorial view of another support assembly for supporting only
the refrigerant lines.
FIG. 9a is an end view of a support ring shown in FIG. 9.
FIG. 10 is a schematic partially sectional view of a flexible section of a
superconducting cable dewar assembly.
FIG. 11 is a partially sectional view of a pump-out valve suitable for use
with a dewar relating to the invention.
FIG. 12 is a partially sectional view of a pump-out valve section equipped
with a relief assembly.
FIG. 13 is a partially sectional view of a vacuum pump-out operator means.
FIG. 14 is a schematic, partially sectional view of a field-joint
arrangement between two expansion end sections.
DESCRIPTION OF A PREFERRED EMBODIMENT
In FIG. 1a, a transmission line is housed in a cryogenic envelope comprised
of a plurality of straight rigid sections 15, each having an expansion-end
portion 16 which can be either joined to another expansion end or joined
to a short flexible section 17. FIG. 1b represents a section through a
small-diameter portion of a typical rigid section of a superconducting
power-cable dewar. The dewar line comprises a stainless steel inner tube
23 which might have about a 4 inch outer diameter and a 0.035 inch wall
thickness. This inner tube serves as the actual support for a
superconducting cable (not shown), which the entire assembly functions to
contain. In order to promote superconducting characteristics of the
contained cable, liquid helium at about 6.degree.K is circulated through
the inner support tube -- often at a pressure of about 15 atmospheres.
The inner stainless steel helium-containing tube 23 is wrapped with
one-quarter inch or so of spirally wrapped multilayer insulation 25. This
multilayer insulation generally comprises layers of glass-fiber paper
alternating with layers of aluminized Mylar to obtain a layer density of
about 44 wraps per inch. Use of the aluminized Mylar minimizes conduction
along the length of the spiral wrap, but plain aluminum foil and
glass-fiber paper are installed at locations near weld areas so that the
Mylar is not burned.
On top of the initial insulation layers is a refrigeration shield comprised
of one or more layers of aluminum foil 26 that is about five thousandths
of an inch or so thick and spirally wrapped about the length of the line.
A first refrigerated line 27 is then installed, and the insulation and
tube are wrapped with a second set of aluminum foil layers 28 which are
also five thousandths of an inch or so thick. Thus, the shield itself 29
comprises two sets of relatively heavy aluminum foil wrapped in touching
contact with the length of the refrigerant line 27. This arrangement
provides adequate contact for transfer to the shield 29, while permitting
independent motion of the tube 27 relative to the foil layers 26 and 28 to
result in a "sliding shield".
In the above regard the helium that is passed through the inner tube 23 is
returned to the helium source, not shown, through the refrigerant tube 27.
Hence, the first "sliding shield" 29, comprised of layers 26 and 28, is
maintained at a temperature of about 10.degree. K depending upon the
temperature rise of the helium as it passes from the source, through the
tube 23, and back again to the source through the tube 27.
The first shield is covered with another one-half inch or so of multilayer
insulation 30; after which a second "sliding shield" assembly is
constructed similar to the first. The second shield comprises spirally
wrapped relatively heavy foil 31 on top of which is layed an outgoing or
"go" refrigerant line 32. Another layer 33 of the relatively heavy foil is
then spirally wrapped along the length of the line over the "go"
refrigerant tube 33. The second shield assembly 34 is then wrapped with
another three-quarters inch or so of multilayer insulation 35.
A third shield assembly 39 is comprised of first and second heavy-foil
layers 36 and 38 which are wrapped on either side of a "return"
refrigerant line 37. Hence, the illustrated structure includes three
"sliding shields" 29, 34, and 39. The first distributes refrigeration
through the return tube 27 at about 10.degree.K; the second distributes
refrigeration from the "go" tube 32 at about 80.degree.-82.degree.K; and
the third distributes refrigeration through the return tube 37 at about
82.degree.-105.degree.K. In this connection, the shield 39 intercepts a
considerably larger portion of the transfer line's heat leak than do the
inner shields 29 and 34. Hence, the larger temperature differential along
return tube 37.
The outer heavy-foil layer 38 of the return shield 39 is wrapped with
another three-quarters of an inch or so of multilayer insulation 40; and
the entire structure is then placed within an outer jacket 41. In this
connection, the illustrated embodiment employs an outer jacket 41 of
carbon steel material with a 10 inch outside diameter and a 0.120 inch
wall thickness. Experience indicates that stainless steel outer jackets,
when maintained in certain adverse environments, tend to develop
"pinholes". Accordingly, when the carbon steel jacket 41 is conventionally
wrapped with tarred paper or the like, the reliability of the dewar is not
adversely affected, but the structure is markedly less expensive.
A typical cryogenic envelope for superconducting power cables is subjected
to wide thermal changes. For example, the outer jacket might be subjected
to ambient temperatures from 110.degree. F (570.degree.R) or more to minus
30.degree.F (430.degree.R) or less; and, large contractive forces are also
generated when the above described shields are operated at temperatures
such as 10.degree.K, 80.degree.K, and 105.degree.K, respectively. When
such temperature extremes are involved, one can expect the inner tube 23,
for example, to contract about 2 inches over a tube length of about 60
feet. Consequently, such structures require a provision for accommodating
the structure's contraction during cool-down; and expansion in the event
it becomes necessary to warm up the structure in order to make repairs.
FIG. 2 illustrates a conventional method of accommodating the contraction
of the inner line of a cryogenic line. Therein, a 60 foot length of inner
line 42 (corresponding to 23 above) is welded at 43a and 43b to an outer
jacket 44. By insertion of bellows 45 into line 42, the contraction which
occurs in 42 during cooldown merely causes the bellows 45 to expand and in
that manner avoids the creation of excessive forces at welds 43. Where, as
here, there is high pressure in the inner line, however, the bellows 45
tends to blow up and expand in diameter so that it ceases to be functional
as a thermal movement means. Such problems are eliminated by structure
such as that to be described shortly.
FIGS. 3a and 3b illustrate a cross section through a rigid section 15b in
FIG. 1 -- FIG. 3a showing part of the expansion-end portion; and FIG. 3b
showing the small diameter portion and the remainder of the expansion end
portion. In this respect, the expansion end portion will be described from
right to left beginning in the middle of FIG. 3b and continuing from the
right side of FIG. 3a. Therein, (FIG. 3c) the outer tube 41 is welded to
an extension ring 55 at 56. In turn, the extension ring 55 is welded at 57
to an outer protective sleeve 58. This protective sleeve 58 slides over an
enlarged outer jacket member 59 at a sliding joint 60 which permits
ambient pressure to enter the volume 61 between a stainless steel bellows
62 and the protective sleeve 58. In this regard, one end of the bellows 62
is welded at 63 to an adaptor ring 64 which, in turn, is welded at 65 to
the tube 41. The other end of the bellows 62 is welded at 66 to a sleeve
67 which permits that portion of tube 41 to slide within the sleeve. The
sleeve 67, however, is welded at 69 to another extension ring 70 which, in
turn, is welded at 71 to the enlarged outer jacket 59.
As will be described more fully later, a vacuum is maintained over most of
the transfer line's length in the volume 72 between the inner tube 23 and
the transfer line's outer walls 41 and 59 (except for volume 61).
Consequently, although the bellows 62 is subjected to ambient pressure in
its surrounding volume 61, it interior is at a vacuum.
The vacuum in volume 72 may communicate with the inner side of the bellows
via the space 68 between line 41 and sleeve 67, as shown in FIG. 3c for
example, or communication may be made by a hole 75 in line 41 in the
bellows area.
Two of the refrigerant lines 32 and 37 extend from thermal returns such as
32a and support spacers such as 32b (to be described more fully shortly)
into a coiled configurations 32c and 37c as illustrated in FIG. 3a. In
this connection, for purposes of simplicity, only the refrigerant tubes 32
and 37 are illustrated, but the tube 27 is similarly coiled. That is the
refrigerant line 27 (not shown in FIG. 3) is closely coiled about the
inner tube 23; the "go" refrigerant tube 32 is coiled about the tube 27;
and the refrigerant return line 37 has the largest coils as illustrated.
In this manner, thermal motion of the refrigerant tubes is accommodated by
their thusly coiled portions.
When the three refrigerant tubes pass through the ends of an individual
length of transfer line, care must be exercised so that the refrigeration
of the tube is not transferred to the transfer line's carbon steel outer
jacket. This is because the carbon steel jacket might get brittle and
break if it were subjected to the extreme cold of the refrigeration tubes
-- particularly the 10.degree.R tube 27. Also heat leak to the tubes 32
and 37 would be excessive and would represent a waste of refrigeration.
Consequently, as illustrated in FIGS. 3; and in more detail in FIG. 4, the
ends of the transfer line sections include "thermal standoff" portions
where the refrigeration tubes pass from one transfer line section to
another.
In the above regard, the three refrigeration tubes pass through a stainless
steel adapter ring 81, an end view of which is schematically illustrated
in FIG. 5. An epoxy fiberglass tube 82, concentric with line 23, is glued
to the adaptor ring 81 and extends to the left about 14 inches or so where
it is glued to a similarly sized stainless steel tube 83 which, in turn,
is welded to another adaptor ring 84 extending between the tube 83 and the
enlarged outer jacket member 59. In this manner, high thermal-resistance
heat paths are maintained between the outer shell 59 and the adaptor ring
surrounding the various refrigeration tubes. In a similar manner, a high
thermal-resistance heat path is maintained between the adaptor ring 81 and
the inner line 23. In this instance, another epoxy fiberglass tube 82a
(also concentric with line 23) is glued to the adaptor ring at 81a and
extends to the left about 14 inches or so where it is glued to a similarly
sized stainless steel tube 83a which, in turn, is welded to another
adaptor ring 84a extending between the tube 83a and inner line 23.
Additionally, the refrigeration tubes such as 32 extend within surrounding
supplemental stainless steel tubes 85. These tubes 85 are welded to the
adaptor ring 81 such as at 86; and are also welded to the refrigeration
line itself at 87.
A close fit is maintained between refrigerant tubes 32 and 37 and
supplemental tubes 85 so that the tubes 32 and 37 effectively refrigerate
the adaptor ring 81. For clarity, the drawings have been enlarged, but the
tubes 32 and 37 are almost in sliding contact with their enlosing tubes 85
thus maintaining the adaptor ring 81 at substantially the temperature of
the warmer refrigerator tube in the range between 80.degree.-105.degree.K.
The third refrigerant tube 27 (FIG. 6) is separated from its enclosing
tube 85 by means of a spirally wrapped separating-cord 91. In this manner,
heat transfer from adaptor ring 81 to line 27 is via enclosing tube 85,
then the cord 91, made of low conductive glass fibers, and thence to tube
27. Hence, this ensures a long complex heat path between the adaptor ring
81 at a temperature of 80.degree.-105.degree.K and the tube 27 carrying
refrigerant at about 10.degree.K.
In the above regard, the thermal standoff tubes just described can be of
varying lengths. Also, materials other than epoxy-fiberglass and stainless
steel can be used. The materials and dimensions should be such, however,
that heat leak between ambient air and the 80.degree.K refrigerant tube is
less than about 3.5 BTU per hour per square inch of cross section of tube
wall material; and less than about 0.25 BTU per hour per square inch of
cross section of tube wall material between the 80.degree.K tube and
liquid helium temperature. Additionally, although the thermal standoff
portions of the transfer line have only been described in connection with
the expansion ends of a given line length, it will be understood by those
skilled in the art that the opposite ends of the sections of transfer
line, such as at 37a in FIG. 3b, are similarly structured.
As indicated above, the inner tube 23 is also equipped with a thermal
compensation structure to accommodate thermal movement of the inner tube
23 within the various other portions of the transfer line -- As above,
"thermal movement" referring to expansion or contract of the tube caused
by thermal changes. In this regard, with reference to the left end of FIG.
3a and FIG. 7, a cylindrical adaptor 93 is welded to the inner tube 23 and
also to one end of a stainless steel bellows 94. The other end of the
bellows 94 is welded to a sliding-ring sleeve 95 which is slightly spaced
from the tube 23. In this manner, the vacuum from the volume 72 is free to
enter the inside of bellows 94 through the space 96. Another adaptor ring
97 is welded between the sliding-ring sleeve 95 and a bellows retaining
sleeve 98; and, as further illustrated in FIG. 7a, relatively rectangular
cross-sectioned guide spacers 99 are welded to the outside of the inner
tube 23 so that the inner surface of the bellows retaining sleeve 98
slides thereover. Also, a flexure reduction ring 100 is welded to the end
of the bellows retaining sleeve 98 to reduce flexure tendencies of the
bellows assembly and the tube 23.
Flared end portions 101 of the adjoining tube sections 23 are not sealed.
Hence, high pressure helium from within tube 23 is permitted to enter
volume 102 between the retaining sleeve 98 and the bellows 94.
Consequently, the bellows 94 is surrounded by high pressure helium while
the interior volume 105 of the bellows is exposed to the vacuum of volume
72.
In the above regard, it should be noted that, although adjoining tube
sections 23 are not joined (as at the flared portions 101) adjoining
portions of the bellows retaining sleeves 98 are welded as at 107 in order
to provide the pressure chamber 102. Also, if desired, additional guide
spacers such as 109 (similar to 99) can be placed along the tube 23 in the
same manner as was described in connections with the guide spacers 99.
In operation, as the inner tube 23 contracts upon cool down, the space at
the flared portions 101 of the tube 23 is permitted to increase; and the
bellows 94 contracts in order to maintain vacuum-pressure seals at welds
111 and 113 between the inner tube 23 and the bellows adaptor sleeve 98.
At the same time, the rigidity of the bellows retaining sleeve 98 prevents
the bellows 94 from buckling as do the various guide spacers 99 and 109
and the flexure prevention ring 100.
Support spacers are provided at intervals within the dewar line in order to
support the inner tube as well as the refrigerant lines. The support
spacers are of two basic types. The more complex spacer is designated by
numeral 121 in FIG. 8. In a preferred embodiment of a 60 foot dewar
section, there are two complex support members 121 located at 20 foot
intervals. Member 121 supports both the inner container 23 and the
refrigerant tubes 27, 32 and 37; and comprises an outer aluminum ring 123
and an inner aluminum ring 125 which is installed about the
cable-containing tube 23. Three hollow epoxy-fiberglass spokes 129 have
titanium tips 131 and extend outwardly from the inner aluminum ring 125
and through the outer ring 123 to the transfer line's outer shell 41. In
this manner, the central conduit 23 is centrally supported within the
composite structure by means of the low thermally conductive spokes 129
and the inner ring 125.
Referring now to FIG. 8a the refrigerant tube 27 is supported by an epoxy
fiberglass projection 133 which is affixed to the inner ring 125.
Similarly, the refrigerant line 32 is supported by an epoxy fiberglass
projection 135 affixed to the outer ring 123; and the refrigerant line 37
is supported by a somewhat shorter epoxy fiberglass projection 137 which
extends inwardly from the outer aluminum ring 123. Hence, merely by
adjusting the size and location of the projections, the tubes can be
spaced at selected radial distances from the central conduit 27 and at
selected circumferential locations around the conduit.
By means of the FIG. 8 structure, refrigeration in the 10.degree. K
refrigeration line 27 is isolated from the inner ring 125; and, because of
the low thermally-conductive nature of the spokes 129, the inner ring's
refrigeration is not effectively transmitted to the outer ring 123. The
80.degree. refrigeration line 32 and the 105.degree.K refrigeration line
37 are directly affixed to the outer ring 123, but because the low
thermally-conductive projection 135 is longer than the low
thermally-conductive projection 137, a relatively small amount of the "go"
refrigeration tubes's cold is transmitted to the outer ring 123.
In operation, the support spokes 129 are loaded in compression with only
two of the spokes touching the inner surfaces of the outer jacket 41 (in
some cases only one spoke might touch). Hence, there is a lower heat leak
to the outer ring 123 than if all three of the spokes touched the outer
jacket. Also, the titanium tips 131 on the spokes 129 permit them to be
slid into the outer jacket 41 during construction without unduly abrading
the inner surface of the outer jacket 41 or wearing down the spokes.
The refrigerant lines 27, 32 and 37 are also supported by intermediate
supports 139 at about 10 foot intervals as illustrated in FIG. 9. Therein,
titanium tipped hollow epoxy fiberglass spokes 141 are affixed to an
aluminum ring 142 which surrounds, but does not touch, the inner conduit
23. In this manner, there is no heat transfer from the inner conduit 23
through the intermediate support rings 139 to the outer jacket 41. In this
respect, the illustrated spokes 141 are of varying lengths (FIG. 9a) so
that the support member 139 can be eccentrically located to accommodate
the various refrigerant lines as will now be discussed.
An epoxy fiberglass projection 143 is fastened to the outer surface of the
inner conduit 23 by means of a suitable pad or projection 145. This
projection 143 supports the 10.degree.K refrigeration line in a manner so
that it does not touch the aluminum ring 142. Hence, none of refrigeration
line 27's cold is transmitted to the support member 139. The other two
refrigeration lines, on the other hand, are supported by projections 147
and 149 which are also constructed of a low thermally-conductive epoxy
fiberglass and affixed to the outside of the support ring 142. With this
arrangement there is no heat leak via the supports to the inner line 23,
and, as before, the heat leak to the ring 142 is minimal because of the
low conductivity of the spoke or spokes which contact the outer vacuum
jacket. Also, as above, the refrigerant tubes can be selectively radially
and circumferentially spaced with respect to the main conduit 23.
FIG. 10 is a more detailed illustration of a short flexible line section
designated by numeral 17 in FIG. 1. These flexible dewar line sections
permit modest changes of direction of the line, in the range of about
20.degree. to 30.degree.. Relatively short flexible sections are used,
because it has been determined that using shorter sections by themselves,
rather than as part of a longer section, minimizes lateral forces which
tend to increase the number of spacers and/or increase the size of the
support members.
The flexible section 17 basically comprises two rigid ends having the same
outer diameter as the expansion ends described above. Thus a flexible
section might be comprised of two rigid ends each approximately 2 feet
long with a 6 foot long flexible portion between these ends. The rigid
ends are designed to mate with the expansion ends of the rigid-line
sections so that complete flexible sections may be installed as required
as shown in FIG. 1a to provide overall line flexibility. In this respect,
FIG. 10 is a partially cut-away side view of a short flexible line section
17 without complete end assembly details. The inner line is made flexible
by use of a suitable flexible section made of conventional flex hose 153
wrapped with an external braid 155 to restrain the flexible hose and
permit it to withstand operating pressures.
To provide for thermal expansion, the refrigerant tubes are made flexible
in a manner similar to that utilized in the thermal expansion sections
(FIG. 3a). Specifically, the refrigerant tubes such as illustrated by
coils 157 and 159 of tubes 32 and 37, are wound into helical coils with
the respective coil diameters of the lines being such that they are spaced
from the inner pipe and also have room for the laminated insulation 160
between them. Although not illustrated, tube 27 of FIG. 9 is also thusly
coiled.
The outer vacuum jacket also comprises a flexible line made of a
conventional flex hose 161 wrapped with an external braid 163, which
serves pirmarily to protect the convolutions of the flex hose from damage.
Since there is a greater need for space required by the flex hoses, coiled
tubes, and insulation; the inside diameter of the outer flex hose is about
the same as an expansion end section as noted above.
Each of the illustrated 60 foot dewar line sections is provided with two
vacuum pump-out ports located approximately 15 feet from each end, so that
the maximum pumping path for each port does not exceed about 15 feet.
Two basic types of pump-out devices are provided. One provides only a
pump-out function while the other includes a relief device. In one
preferred embodiment each main dewar line section contains one of each,
while each field joint section (to be described shortly) includes a
pump-out having a relief device.
A pump-out valve 170 is depicted in FIG. 11 and comprises a housing 171
threaded on its outer end 173 to accept a threaded protective cap 175
which is sealed vacuum-tight with teflon tape, not shown. The outward
opening of the pump-out valve plug 177, which is sealed with an O-ring
179. It is the function of the protective cap to prevent continuing entry
of air, thus avoiding oxidation of the O-ring. Hence, it is desirable that
the void volume 131 between the cap and the O-ring is kept to a minimum.
In the event the O-ring should develop a leak, only the volume of air 181
will enter the system; this minor amount would readily be cryopumped. The
non-threaded end of the pump-out device is sealed into the outer jacket of
the dewar line, such that its inner opening 183 is in communication with
the internal dewar line structure.
FIG. 12 illustrates a pump-out unit 170 equipped with a relief assembly.
Therein, an adaptor housing 185 is threaded at 187 onto the pump-out
device in place of the protective cap 175. A relief valve 189 is in turn
threaded into the opposite end of the adaptor housing and comprises a
valve plug 191 sealed within the valve opening by O-ring 193. This valve
plug is held in place by internal biasing spring 195; and dust cap 197 is
snap-fitted over the outside opening of the relief valve to protect it
from air, moisture, and dirt.
Adapter housing 185 has a suitable internal volume so that the plug 177 of
the pump-out unit is capable of moving upwards to permit gas to pass
around it as shown in Phantom in FIG. 12. The relief valve 189 can be
pumped so that the volume 199 between the pump out plug O-ring 179 and the
relief valve 189 is evacuated. In this regard, the housing 185 is fitted
with a Bourdon tube vacuum gauge 201, which is set in contact with the
internal volume 199 of the housing. This gauge serves to indicate whether
there is a vacuum leak at the O ring 179, or whether the plug 177 has been
pushed out during a warm-up cycle.
In the event of a pressure rise, valve plug 177 is unseated from its sealed
position and emerges into the volume 199 of the adaptor housing 185, where
it is supported by a blow-out support member 203. If the pressure rise is
sufficient to unseat relief valve 191 against the bias of spring 195,
protective cap 197 readily pops off to provide pressure relief.
When the relief valve is pumped-out and the pump is removed, a small amount
of air may enter the volume including 199 between the pump-out plug O-ring
179 and the relief valve 199, such that the final pressure of the internal
volume of the housing might approximate 5000 microns. This, however, does
not significantly adversely affect the transfer lines's operation.
A vacuum pump-out operator designed to attach to a pump-out assembly is
depicted in FIG. 13; and a similar operator is used in connection with the
relief valve. The vacuum pump-out operator 211 includes an operator
housing 213 fitted with an operator stem 215 movably sealed within the
housing by O-rings 217. The stem can be axially maneuvered within the
housing through manipulation of operator knob 219. The valve plug 177 (and
relief valve 191) is provided with a centrally threaded hole 221 to which
a threaded tip 223 of the operator stem is secured.
In operation, the operator housing is slid over the pump out housing and is
secured to the pump-out housing by a fastening screw 225, with an O-ring
227 accomplishing a seal between the two housings. The operator stem 215
is then pushed inwardly until it mates with the threaded opening 221 in
the valve plug 177. Once the stem 215 is threaded into the valve plug hole
it is pulled outwardly, thus removing the valve plug 177 from its sealed
position so that a vacuum port 229 communicates with the internal volume
of the pump-out device and, through the valve, with the internal volume of
the dewar line assembly.
Assembling a line several miles long or even several thousand feet in
length results in the field joining of factory-built dewar line sections.
FIG. 14 illustrates a structure for accomplishing these field joints. In
this respect, as noted above in connection with FIG. 7, the ends 101 of
the cable conduit 23 are flared. Hence, there is little possibility for a
superconducting cable to catch on the inner joints as the cable is pulled
through the conduit 23. Moreover, the ends 101 are not joined as such.
Consequently, there is not even any welding residue for the cable to snag
upon. The remaining elements of the section ends are joined together,
however, as will now be described with reference to FIG. 14.
For joining the thermal expansion ends of the dewar line, the stainless
steel standoff sleeves 83 are fastened by butt weld 231 provided with
backup ring 233. This arrangement results in two particularly desirable
features. Welding of the sleeve eliminates the need for a rough surfaced
backup ring located in the inner line 23; and, as noted above, the
openings occurring at the joined ends 101 of the flared inner line 23
permit the flow of helium from the inner container 23, to the outside
volume 102 of the inner line expansion bellows 92.
After the weld 231 has been completed, the refrigerant tubes 27, 32, and 37
are joined by means of couplings such as 235, which are silver soldered to
the respective refrigerant line ends.
Prior to connecting the outer carbon-steel vacuum jacket sections 59,
absorbent and chemical getters such as 239 are added and the joint is
suitably insulated throughout with multilayer insulation 241. In this
respect, charcoal or the like is placed adjacent the surface of the inner
helium line 23 to getter oxygen and nitrogen; and a small amount of
palladium oxide or the like is placed in the vicinity of the transfer
line's warm outer jacket 59 to properly getter hydrogen gas. These getter
substances are installed in both the shop-fabricated evacuated sections;
and in the field-evacuated joints.
The outer vacuum jackets 59 are provided with adapters 245 over which
sleeve sections 247 are positioned. The outer pipes are then effectively
joined such as by welding, and the joint spaces thereby sealed.
After the entire field joint has been completed, the volume within the
joint is field evacuated and sealed off with vacuum seal and relief
devices 250 such as described above in connection with FIGS. 11-13.
In sizing the tubes carrying the refrigerant, an allowable temperature rise
is selected for the refrigerant gas, which, in effect, determines the
maxium temperature of the outer shield. For 2,500 feet of 4 inches
diameter inner line, for example the refrigeration requirement at a
nominal outer shield temperature of 80.degree.K is 1,187 BTU per hour. If
a temperature rise of 31.degree.K is allowed, then the amount of helium
refrigerant required in pounds of helium per hour equals 1,187/(56 .times.
1.4) = 15 pounds/hour of helium. Under these conditions the pressure drop
in a one-half inch inner diameter refrigerant line is 7.9 psi on the go
run and 11.2 psi on the return run for helium at inlet conditions of 80
psi and 136.degree.R. Since the bulk of the heat load is to the warmer
shield, the temperature rise of the helium in the go run is only a few
degrees with the balance of the rise occurring in the return run. At the
end of the transmission line near a refrigerator unit, the temperature
difference between the two refrigerant lines is about 50.degree.R, while,
at the distant end, the temperature of the two lines will be virtually the
same.
Not only does the innermost refrigerant line 27 provide a convenient means
for returning cold helium to its source, but also the use of this line
reduces the required flow of coolant helium, since it reduces the heat
leak actually reaching the inner line to almost zero. Thus, the helium
flow in line 27 is only that required to remove the electrical heat losses
at the allowable temperature rise within the inner container. The helium
flowing in this return line, however, is permitted to rise above the
maximum temperature allowed in the container 23 itself in order to
accommodate the heat flux resulting from heat transfer from the
80.degree.K shield.
The above described structures result in a transfer line having heat fluxes
that are considerably less than comparably sized transfer lines that are
presently commercially available. For example, the overall heat flux on
the above described rigid line is only about one-quarter to one-third that
of a presently available commercial structure; and the heat flux to the
above described flexible sections are about comparable to the same
commercial structure.
While the invention has been particularly shown and described with
reference to preferred embodiments thereof, it will be understood by those
skilled in the art that various changes in form and detail may be made
therein without departing from the spirit and scope of the invention. For
example, various types of cryogenic insulation can be inserted into the
transfer line's vacuum spaces; and, particularly where it is not desired
to recover the refrigerant gases in tubes 32 and 37, it might be desirable
to circulate liquid nitrogen therethrough rather than gaseous helium as
described above.
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