U.S. patent number 3,621,906 [Application Number 04/854,386] was granted by the patent office on 1971-11-23 for control system for heat pipes.
This patent grant is currently assigned to General Motors Corporation. Invention is credited to Charles B. Leffert.
United States Patent |
3,621,906 |
Leffert |
November 23, 1971 |
**Please see images for:
( Certificate of Correction ) ** |
CONTROL SYSTEM FOR HEAT PIPES
Abstract
In preferred form, a heat pipe joining a heat source and a heat
sink through an evacuated control section. A reservoir is located
in direct fluid communication with the evacuated control section
and has a predetermined quantity of control fluid therein. A
heat-pipe wick within the control section has its wetness varied in
accordance with changes in the condition of the control fluid to
vary the rate of heat transport between the heat source and heat
sink by the heat pipe itself; "wetness" hereinafter being taken as
the fraction of total interconnected void volume of the wick that
is filled with liquid. In a test device heat transport in the "off"
state was increased by a factor of approximately 6 in the "on"
state.
Inventors: |
Leffert; Charles B. (Troy,
MI) |
Assignee: |
General Motors Corporation
(Detroit, MI)
|
Family
ID: |
25318552 |
Appl.
No.: |
04/854,386 |
Filed: |
September 2, 1969 |
Current U.S.
Class: |
165/272;
165/104.14; 165/104.26; 165/273; 165/274 |
Current CPC
Class: |
F28D
15/06 (20130101); F28F 2200/005 (20130101) |
Current International
Class: |
F28D
15/06 (20060101); G05d 023/185 (); F28d
015/00 () |
Field of
Search: |
;165/32,105 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Davis, Jr.; Albert W.
Claims
What is claimed is:
1. A heat-pipe control system comprising an outer container having
spaced end walls defining a sealed evacuated chamber, a first
tubular member having a closed end, said first tubular member being
supported on one of said end walls to locate said closed end within
said chamber in axial spaced relationship to said end wall, means
including said tubular member defining an evaporator section within
said chamber, a second tubular member having a closed end, said
second tubular member being supported on the other of said end
walls to locate its closed end in axial spaced relationship to said
other end wall and coaxially of said first tubular member, means
including said second tubular member defining a condenser section
within said chamber, means including a depending tube on said outer
container between the closed ends of said first and second tubular
member defining a reservoir having a predetermined amount of
control fluid therein, an inlet to said tube directly communicating
said reservoir with said sealed chamber, means for selectively
heating and cooling said reservoir for causing said control fluid
to be conditioned to vary the vapor pressure within said sealed
chamber, capillary flow means thermally connected between said
condenser and evaporator sections including an unsupported bridge
portion overlying said tube inlet wetted when said vapor pressure
increases within said chamber to increase the rate of heat
transport from said evaporator section to said condenser section,
said bridge portion being dried in response to cooling of said
reservoir and condensation of fluid therein to reduce the rate of
heat transport between said evaporator section and said condenser
section.
2. A heat pipe assembly comprising a sealed evacuated outer
housing, means defining an evaporator at one end of said housing,
means defining a condenser at the opposite end of said housing, a
porous wick located within said housing in spaced relationship
thereto, said porous wick having a first segment thereon in
heat-transfer relationship with said evaporator section, said
porous wick including a second section thereon in heat-transfer
relationship with said condenser section, means defining a
reservoir having a predetermined amount of control fluid therein,
said reservoir having an inlet in direct communication with the
interior of said housing, said wick including an unsupported bridge
portion between said evaporator and said condenser overlying said
tube inlet, control means for varying the condition of said control
fluid within said reservoir to vary the vapor pressure within said
housing for varying the amount of liquid within said unsupported
wick portion thereby to vary the rate of heat transport from said
evaporator section to said condenser section, said reservoir being
a variable volume bellows, said control means including an
electrically energizable resistance heater on said bellows for
heating said bellows to vary the vapor pressure in said housing, a
potentiometer for controlling current in said resistance heater,
means connecting said bellows to said potentiometer for regulating
said potentiometer to reduce energization of said heater on the
occurrence of a predetermined maximum pressure condition in said
bellows.
3. A heat-pipe system including housing means defining a sealed
evacuated chamber, first heat-pipe means located within said sealed
chamber, second heat-pipe means located within said chamber, a
reservoir having a predetermined amount of control fluid therein,
means including an inlet in said housing means communicating said
reservoir with said sealed chamber, means for varying the amount of
control fluid within said reservoir so as to change the vapor
pressure within said sealed chamber, capillary flow means located
within said sealed chamber having a first portion thereon in
heat-transfer relationship with said first heat-pipe means and a
second portion thereon in heat-transfer relationship with said
second heat-pipe means, said capillary flow means including an
unsupported bridge portion between said first and second heat-pipe
means overlying said inlet portion increasing in wetness in
response to an increase in vapor pressure within said sealed
chamber in response to changes in the amount of fluid within said
control reservoir for increasing the rate of heat transport between
said first and second heat-pipe means, said capillary flow means
bridge portion being dried in response to condensation of said
control fluid within said reservoir for reducing the amount of heat
transport from said first heat pipe means to said second heat pipe
means.
4. A heat pipe combination comprising: a first heat pipe having a
first tubular housing with the opposite end thereof closed, a
porous capillary liner on the interior surface of said housing, an
evaporator section on said first heat pipe and a condenser section
thereon, a second heat pipe having a second tubular housing with
the opposite ends thereof closed, a porous capillary liner on the
interior surface of said second housing, an evaporator section on
said second heat pipe and a condenser section thereon, a third
tubular housing having a diameter greater than that of said first
and second tubular housings, said condenser section of said first
heat pipe being located within said third housing at one end
thereof, said evaporator section of said second heat pipe being
located within said third housing at the opposite end thereof,
means including said third housing defining a sealed control
chamber, a control wick of porous material located within said
chamber having a portion thereon in heat-transfer relationship with
said condenser section of said first heat pipe and a second portion
thereon in heat-transfer relationship with said condenser section
of said second heat pipe, means forming a control reservoir having
a predetermined amount of fluid therein, means including an inlet
in said first tubular housing for communicating said control
reservoir with said sealed control chamber, said control wick
including an unsupported bridge portion between said first and
second portions thereof, said unsupported bridge portion overlying
said inlet to be wetted by fluid within said reservoir, means for
varying the condition of said fluid within said reservoir for
changing the vapor pressure within said control chamber so as to
vary the wetness of said unsupported bridge portion of said control
wick thereby to vary the rate of heat transport between said first
and second heat pipes.
5. A heat pipe device comprising: a large diameter tubular housing
having opposite end walls thereon defining an evacuated chamber, a
first tubular member directed into said chamber at one end thereof,
said first member having a closed end located within said large
diameter housing in concentric relationship therewith, a second
tubular member directed into said chamber at the opposite end
thereof, said second member having a closed end thereon located
within said large-diameter pipe in concentric relationship
therewith, said first and second tubular members each having a
closed end located coaxially and in spaced relationship to each
other, a heater located within said first member for directing heat
interiorly of said large-diameter housing, heat-sink means located
within said second member for removing heat from within said
large-diameter housing, a depending tube on said large-diameter
housing intermediate the opposite ends thereof forming a control
reservoir, an inlet to said tube in direct communication with the
interior of said housing, between said spaced, closed ends of said
tubular members, a predetermined amount of control fluid within
said depending tube, means for varying the condition of said fluid
within said tube for controlling the vapor pressure within the
interior of said large diameter housing, a sleeve of capillary flow
material located within said chamber in spaced relationship to said
outer housing have one end thereof fit over the closed end of said
first member and having the opposite end thereof fit over the
closed end of said second member for returning condensed liquid
from the outer surface of the closed end of said second member back
to said closed end of said first member for evaporation by said
heater, said sleeve of capillary flow material including an
unsupported bridge portion overlying said tube inlet having the
wetness therein varied in accordance with changes in the condition
of fluid within said tube for varying the rate of heat transport
from said first member to said second member.
Description
This invention relates to the control of heat-transfer devices and
more particularly to the control of heat transport in a two-phase
heat-transfer device or heat pipe including a capillary structure
for flow of the liquid phase in a first direction and a section for
flow of the vapor phase in an opposite direction.
Heat-pipe devices are heat-transfer arrangements that have an
evacuated section for the flow of vapor from a heat source to a
heat sink and a capillary structure for the return flow of
condensed liquid in an opposite direction back to the heat source
for evaporation.
The devices are characterized by having a high rate of heat
transfer. To date the control of the heat transport rate in such
devices is maintained by varying the temperature differential
between the heat source and the heat sink within the structure.
An object of the present invention is to improve operation of heat
pipes by controlling the heat-transport rate therein by the heat
pipe itself without deliberately varying the temperature of a heat
source and/or heat sink associated therewith.
A further object of the present invention is to control the rate of
heat transfer in a heat pipe having a vapor phase and a liquid
phase that returns through a capillary structure from a condenser
section to an evaporator section and to do so by including means
within the heat pipe itself operative to vary the amount of liquid
within the capillary structure for controlling the rate of heat
transfer between a heat source and a heat sink associated with the
heat pipe.
Still another object of the present invention is to control or shut
off the heat transport through a heat pipe without regulating a
heat source to the heat pipe and to do so by means of a control
reservoir in direct communication with an evacuated control section
of the heat pipe and wherein the control reservoir includes a
predetermined amount of control fluid which has its condition
varied to vary the amount of liquid in a control wick within the
evacuated control section.
In one working embodiment of the invention these and other objects
of the present invention were attained in a two-phase heat pipe
device including an open-ended large-diameter outer housing having
end caps in the opposite end thereof. Means are included to
evacuate the housing.
Each of the end caps supports a copper pipe concentrically within
the first pipe. One of the supported pipes serves as a heat source
for the system and the other of the pipes serves as a heat sink. A
porous control wick or sleeve has one end thereof fit over the heat
input pipe and the opposite end thereof fit over the heat sink pipe
to define a capillary flow structure for the return of liquid from
the heat sink to the heat source.
A tubular reservoir on the outer housing is located approximately
at the midpoint of the ends of the outer housing and serves as a
container for a predetermined amount of control fluid which when
heated increases the vapor pressure within the outer housing. This
causes more liquid in the sleeve wick and an increase in the rate
of heat transport between the heat source and the heat sink.
When the reservoir is cooled the control fluid will condense
therein and reduce the vapor pressure within the outer housing so
as to cause less liquid in the capillary structure of the control
wick thereby to reduce the rate of heat transport between the heat
source and the heat sink.
The method of heat-pipe control is obtained without regulating the
temperature differential between the heat source and the heat sink
of the structure. The arrangement makes it possible to readily
control the heat-transport rate by the heat pipe itself in that the
reservoir and the control fluid therein are part of the heat-pipe
device between the heat source and the heat sink therein.
In the working embodiment and to attain the objects of the present
invention it is important to note that the thermal conductance of
the control section between the heat source and the heat sink, in
the absence of the heat-pipe fluid, is small as compared to the
heat-transport rate that is present when the heat-pipe control
fluid is present in the wick during two-phase heat-pipe transport
operation.
Further objects and advantages of the present invention will be
apparent from the following description, reference being had to the
accompanying drawings wherein a preferred embodiment of the present
invention is clearly shown:
In the drawings:
FIG. 1 is a view in front elevation, partly in section, of a
heat-pipe system including a controller operated in accordance with
the present invention;
FIG. 2 is an enlarged vertical sectional view of the control
section in the system of FIG. 1;
FIG. 3 is a diagrammatic view of a two-phase system showing
heat-pipe transport principles;
FIG. 4 is a view of a heat-transport system including first and
second heat pipes having the rate of heat transport therebetween
regulated by the control of the present invention;
FIG. 5 is another embodiment of a controller suitable for
association with either the system of FIG. 1 or that of FIG. 4;
FIG. 6 is an embodiment of still another controller for association
with the system of the present invention;
FIG. 7 is a chart of the heat transport versus control reservoir
temperature;
FIG. 8 is a vertical cross-sectional view taken along line 8--8 of
FIG. 9 looking in the direction of the arrows; and
FIG. 9 is a fragmentary sectional view of another embodiment of the
invention having first and second heat pipes.
SINGLE HEAT-PIPE ARRANGEMENT
Referring now to the drawings, in FIG. 1 apparatus is illustrated
for controlling the rate of heat transport in a two-phase heat-pipe
arrangement.
It includes a heat pipe 10 having a large diameter tubular outer
containing wall 12 which surrounds a heat source 14 and a heat sink
16. A layer of insulation 15 comprised of three wraps of Refrasil
woven insulation covers the wall between its ends.
Within the outer containing wall 12 is a wick 18 that connects the
heat source 14 and heat sink 16. The connecting wick 18 and the
outer containing wall 12 constitute a heat pipe with an
independently controlled atmosphere.
More particularly, in the illustrated arrangement the heat pipe 10
is shown in association with a glass water cooler 20 which has an
inlet tube 22, a convoluted flow section 24 that is surrounded by a
water jacket 26 and an outlet 28 that is connected directly to the
interior of the outer containing wall 12. The sleeve 26 includes an
inlet fitting 30 and an outlet fitting 32 for the flow of cooling
water through the sleeve 26 and in heat-transfer relationship with
the convoluted flow section 24.
The set up includes a top cock valve 34 and a bottom cock valve
36.
When the valves 34, 36 are opened a predetermined quantity of
heat-pipe fluid can be directed into the interior chamber 38 of the
outer containing wall 12.
In the illustrated arrangement the outer containing wall 12 is made
of glass and has opposite ends that are closed by stainless steel
end caps 40, 42. The cap 40 includes a peripherally mounted O-ring
seal 44 which seals against the outer containing wall 12
continuously around the cap 40. A like continuously formed O-ring
seal element 46 is supported on the periphery of the end cap 42 to
seal the opposite end of the outer containing wall 12.
The heat source 14 more particularly, includes a copper pipe 48
directed through a central opening 50 in the end cap 40 so as to
locate a closed end section 52 on the pipe 48 concentrically with
respect to the outer containing wall 12 within the interior 38 of
the wall 12 axially inwardly of the cap 40 a distance of
approximately one-third of the length of the outer containing wall
12.
The outer surface of the copper pipe 48 is sealed with respect to
the cap 40 by an O-ring seal element 54 which is located within an
annular groove 56 formed in a small diameter outer extension of the
cap 40.
A 200-watt cartridge heater 58 is inserted into the closed end 52
of the pipe 48 at a point within the interior 38 of the outer
containing wall 12. The heater 58 includes lead lines 60, 62
connected to a variable source of power such as a Variac unit 64 so
as to establish a range of thermal inputs through the pipe 48 into
the interior 38 of the heat pipe 10.
The heat sink 16 more particularly, includes an elongated copper
pipe 66 which is directed through a central opening 68 in the end
cap 42. The pipe 66 is thereby supportingly received by the cap 42
so as to locate a closed end section 70 of the pipe 66 axially
inwardly of the end cap 42 to approximately one-third of the length
of the containing wall 12, coaxially of the pipe 48 and
concentrically of the interior 38 as defined by the wall 12.
An inlet pipe 72 of a water cooler 74 extends coaxially and
inwardly of the pipe 66 and includes an outlet 76 located in
close-spaced relationship with the end section 70 of the pipe 66
where the cooling water picks up heat prior to return thereof
through the open end of the pipe 66 which is in communication with
an interior 78 of a header 80. The heated return fluid is directed
through an outlet fitting 82 on the header 80 to suitable drain
means (not shown).
In the illustrated arrangement the pipe 66 is sealed with respect
to the end cap 42 by an annular O-ring 84 which is received within
an annular groove 86 in a small diameter end extension on the cap
42.
A glass tube 88 or control reservoir is formed integrally with the
glass outer containing wall 12 at a point intermediate the ends
thereof so as to extend downwardly from the container 12 as is best
illustrated in FIG. 2. The tube 88 thereby defines a sump volume 90
into which condensed liquid can flow and be collected from within
the interior space 38 of the containing wall 12.
In FIG. 2 the tube 88 is shown partially filled with a
predetermined quantity of control fluid 92. A heater 94 is wound
around the outside surface of the tube 88 for purposes to be
discussed.
In accordance with certain principles of the present invention the
porous wick 18 is in the form of an elongated tubular sleeve member
95 formed of three turns of 60-mesh screen with an outside turn of
1,400-by -200 SS screen. The tubular sleeve 95 has one end 96
thereof fit over the outer surface of the closed end section 52 of
the pipe 48 that houses the cartridge heater 58 and is bonded
thereto by suitable means such as brazing.
Likewise the opposite end 98 of the sleeve 95 fits over the closed
end section 70 of the pipe 66 that makes up part of the heat sink
16 and is bonded thereto by a suitable means such as brazing.
The intermediate section of sleeve 95 serves to bridge the end
sections 52, 70 and defines a control section path between the heat
source 14 and the heat sink 16 that has a thermal conductance when
the pipe is "off" which is small compared to the thermal
conductance when the heat pipe is operative.
To obtain an operative heat pipe the control-section chamber 38 is
evacuated of air by applying a vacuum to the inlet tube 22 and
maintaining the cock valves 34, 36 open. Following air evacuation,
a predetermined charge of liquid is directed through the inlet tube
22 to flow through the convoluted flow section 24 and the outlet
tube 28 into the interior 38 of the outer containing wall 12 making
sure there is still an excess of liquid still in inlet 22 above
valve 34 when it is shut to ensure no entrance of air. Valve 36 is
then closed and the only heat transfer medium within the chamber 38
is that of the predetermined quantity of heat-pipe liquid.
When the chamber 38 is so evacuated the heat transfer medium
remaining therein is in a two-phase state of the type shown in FIG.
3 which is a representative illustration of the type of fluid
dynamics found in heat pipes.
More particularly, as illustrated in FIG. 3, the heat pipe includes
a capillary structure having a controlled porosity upon which the
principle of operation of a closed heat-pipe transfer circuit is
dependent.
The capillary structure finds its counterpart in the porous wick 18
in the embodiment of FIGS. 1 and 2.
The sealed evacuated pipe finds its counterpart in the outer
containing wall 12 and the tube container end caps 40, 42. The
evaporator section in the illustrated arrangement is at the heat
source 14 and a condenser section is at the heat sink 16.
The heat-transfer medium sealed within the chamber 38 is found in
both the liquid state and the vapor state; the porous capillary
structure seen in FIG. 3 is substantially saturated with the liquid
phase of the heat-transfer medium while the remainder of the
chamber 38 is filled with the heat-transfer medium in the vapor
state under evacuated conditions.
The Variac 64 is operated to turn on the cartridge heater 58 so as
to produce a heat input at the heat source 14 and to the chamber
38. Concurrently, water is flowed through the water cooler 74 in
the pipe 66 for removing heat from the control section chamber
38.
In the embodiment of FIGS. 1 and 2 the vapor at the evaporator end
at the heat source 14, will be at a pressure P.sub.2 which is
higher than a pressure P.sub.1 of the vapor at the right end of the
device represented by the heat sink 16. This is because the vapor
is produced in the heat-source area of the chamber 38 and is at a
higher temperature. The result is that vapor flows from the heat
source or evaporator end of the device to the right as viewed in
FIGS. 1 and 2 to the condenser or heat sink 16 thereof.
The pressure balance equation for a heat pipe (gravity free
condition) is:
.DELTA.P.sub.M =.DELTA.P.sub.L +.DELTA.P.sub.V
Where .DELTA.P.sub.M is the capillary driving force term,
.DELTA.P.sub.L is the liquid pressure drop through the wick, and
.DELTA.P.sub.V is the pressure drop through the vapor or P.sub.2
-P.sub.1, as previously expressed.
For the gravity-free condition the capillary pumping pressure is
generated almost entirely at the vapor-liquid meniscus interface in
the evaporator section, i.e.,
where .gamma. is the surface tension of the liquid, .theta. is the
contact angle and r.sub.2 is the radius of curvature of the
meniscus in the pores.
The maximum pumping pressure
where r.sub.c is the effective pore radius of the wick and
represents the minimum value for r.sub.2, i.e., r.sub.c r.sub.2
.infin.and .DELTA.P.sub.M .DELTA.P.sub.c.
The strain on the meniscus from evaporation puts the liquid under
tension to provide for the liquid pressure drop .DELTA.P to return
the liquid from the condenser to the evaporator. Also this strain
compresses the vapor in the evaporator to provide for the vapor
pressure drop .DELTA.P.sub.v.
The total maximum force available for pumping (.DELTA.P.sub.C) can
be regulated by varying the effective pore radius (r.sub.c) of the
wick.
The pressure drop for liquid flow through the annular wick 95 is
given by the following expression for laminar flow:
where
.mu. = liquid viscosity
v.sub.1 = volume flow rate
.epsilon. = void fraction (screen porosity)
l = length of heat pipe wick
A = cross-sectional area of annular wick
b = tortuosity factor
r.sub.c = effective pore radius of the wick
For a homogeneous wick, a small value of effective pore radius
r.sub.c would increase the available pumping force .DELTA.P.sub.c
but it would also increase the resistive pressure drop term
.DELTA.P.sub.1. Thus, there is an optimum value of r.sub.c
depending upon the heat load, heat-pipe size and fluid used, and
these optimum equations are available in the heat-pipe
literature.
When the liquid reaches the heat source 14 end of the annular
screen 95 it is heated by the heater 58 causing the liquid to
evaporate and flow through the chamber 38 as a vapor. The vapor
pressure at this point is at a pressure P.sub.2 which as stated
above is greater than that of the opposite end of the device
thereby to maintain a continuous left-to-right flow of vapor in the
device which is counterflow to the path of liquid flow through the
porous wick 18.
The above-described dynamics of the two-phase heat-transfer system
is sufficient for purposes of describing the present invention. In
order to control the dynamics of the two-phase system, heretofore,
temperatures at the evaporator and condenser ends of the closed
evacuated pipe portion of the heat pipe have been varied to control
the differential vapor pressures therein which in turn regulates
the rate of vapor transfer as well as the rate of the counterflow
liquid phase.
In accordance with certain principles of the present invention heat
transport through a heat pipe is controlled without regulation of
the heat-source temperature or that of the heat sink. In order to
evaluate the results in the working embodiment of the invention
illustrated in FIGS. 1 and 2 the following instrumentation is
included.
It includes a thermocouple 100 on the water input of the cooler 74
and a thermocouple 102 on the output thereof. Further, a
thermocouple 104 is located on the outer surface of the containing
wall 12 adjacent the end cap 42 and beneath the layer of thermal
insulation 15 surrounding the outer surface of the containing wall
12. Another thermocouple 106 is located adjacent the end cap 40 on
the outer surface of wall 12 adjacent cap 40.
Diametrically opposite the thermocouple 104 on the wall 12 is
located a thermocouple 108. Another thermocouple 110 is located at
a point on the wall 12 diametrically opposite the thermocouple
106.
The temperature of the outer skin of the reservoir tube 88 is
measured by a thermocouple 112.
An additional thermocouple 114 is located on the end of the pipe 48
located outside of the end cap 40. In the illustrated arrangement
the thermocouple 114 is intended to detect the temperature of the
heat source represented by the cartridge heater 58.
Since the thermocouple is located outside the heat pipe it is
obvious that it does not measure the true heat-pipe evaporator
temperature but is a value which is greater than that temperature
by an amount proportional to the heat-input rate.
Also, the thermocouple 112 on the reservoir does not necessarily
represent the true vapor temperature in the heat pipe because in
the working embodiment, to prove feasibility, the heater 94 is a
hot air fan directed against the reservoir and in some cases
against the bottom of the outer containing wall 12 in the vicinity
of the reservoir tube 88.
For purposes of evaluating the vapor temperature within the
heat-pipe assembly 10 of FIGS. 1 and 2, it is believed that the
temperature of any of the couples 104, 106, 108, 110 is best chosen
to most accurately reflect the vapor temperature within the control
section chamber 38.
The following table is a quantitative listing of heat-pipe control
tests. Temperatures are shown for thermocouple locations 104, 108,
112, 114. Thermocouple temperature measurements at 100, 102 and the
water flow rate establish a dynamic calorimeter for measuring the
rate of heat rejection (Q.sub.2 or P .sub.out ) into the heat sink.
Q or P.sub.in is established by ammeter 116 and voltmeter 117
measurements by instrumentation shown in FIG. 2. ##SPC1##
RUN I
This demonstrates that the transport rate of a dry wick 18 is
relatively low in the order of 21 watts. The balance of the input
heat which was 39 watts is dissipated in the form of thermal
conduction through the stainless steel end caps or other connection
losses. These losses are present since in the working embodiment
there is no insulation used on the end caps or the exposed end of
the heater housing. The input of 39 watts is selected to avoid a
rapid rise in the temperature of the heat source and burnout of the
cartridge heater 58.
In most of the runs illustrated in the summary table, a 10-ml.
charge of H.sub.2 0 is included in the reservoir tube 88 and serves
as the only heat transfer medium with the control section chamber
38 evacuated. In any case where the amount of control fluid changes
appropriate comment will be made. In run I the water is condensed
in the reservoir 90.
RUN II
This demonstrates ordinary steady state "on" conditions for
heat-pipe operation. Under these circumstances the amount of fluid
92 in the reservoir tube 88 is slightly heated and the heat-source
temperature is actually reduced from that where the wick 18 is dry.
Under these "on" conditions the 10-ml. water charge is vaporized
into chamber 38 and cooled at the end 98 of the wick by the water
flow through the closed pipe section 70 within the chamber 38 to
condense and return by capillary action through the porous
structure represented by wire mesh sleeve 92 to the evaporator end
96. Under these circumstances heat-transport rate is increased by a
factor of at least 6 as compared to the first run where the heat
pipe was "off" and the 10 ml. of control fluid was collected within
the reservoir 88.
RUN III
In this run the operation is not under steady state conditions
since the heat-source temperature is increasing. However, it is run
at a higher power input level than in run II. At a heat-source
temperature of 183.degree. C. the run terminates. This run
indicates what the limit of maximum heat-transport ability is for
the wick 18. The limit is thought to be due to a radial heat
transport limit across the bonded section between the sleeve 95 and
the pipes 48, 66 at 96 and 98, respectively. The heat-transport
limit of the device at 167 watts as shown in the summary table is
not considered to be an axial limit, that is, not due to the
maximum heat transport limit according to the previous equation
.DELTA.P.sub.c =.DELTA.P.sub.v +.DELTA.P.sub.L, but rather one
dependent on the radial conduction characteristics at these
points.
RUN IV
This shows that the actual heat input into the system through the
control section represented by the reservoir tube 88 is small. In
this test, the heat input by the cartridge heater 58 is turned off
and full heat by a hot air blast is applied to the reservoir tube
88. As noted, the full wattage output is in the order of 37 watts.
This represents the upper bound and the heat supplied to the
reservoir 88 during the "on" tests of runs II and III would be less
inasmuch as the internal parts were hotter in those runs.
RUNS V THROUGH VIII
These runs show the proportioning control ability of the devices
illustrated. Runs V and VI were made to show that the device is
able to be turned "on" when the wick is already hot and dry as the
case in run I. With the control heat initially off and the wick at
a steady state temperature of 122.degree. C., heat is applied to
the water reservoir 88 by a hot air blower. The heat-source
temperature at thermocouple 114 rapidly decreases to a temperature
of 39.degree. C. as heat is transported to the condenser through
the now-wetted porous wick represented by the sleeve or wire mesh
95. During this run the input power is then increased to bring the
temperatures of thermocouple 114 up to the same level of
approximately 122.degree. C. at the wick following wetting of the
sleeve 95. By varying the power input it is found that a new steady
state condition for maximum input power is possible in the range of
--62 watts as shown in run VI. Under these conditions the wattage
output even though the wick 95 is damp, drops to 61 watts under
steady state conditions. This is a drop from the on output of 130
watts as shown in run II. It is obtained mostly (since
T.sub.114(II) >T.sub.114(VI)) by dropping the control
temperature at reservoir 88 from 76.degree. C. during run II to
44.degree. C. at run VI. This shows the capability of proportional
control in the system.
In any case it is clear that the change in the condition of the
control fluid within the sump 90 can cause the sleeve 92 to be dry
to effectively stop or turn off the heat pipe. Under conditions the
screen 95 is damp or wet the axial heat transport is thereby turned
on and modulated. In run VII an intermediate level of heat output
is represented. It is attained by varying the heat input to 79
watts for a vapor temperature corresponding to about 58.degree. C.
Under this test, sufficient heat could not be supplied through
blowing hot air against the reservoir tip to bring the control
section up to a temperature in the range of 44.degree. C. at the
thermocouple 112. Accordingly, the hot air was, in addition to
being blown against the tip, also directed against the underside of
the outer container wall in the vicinity of the reservoir tube 88.
Also, in the run an appreciable amount of heat was supplied by the
hot air blower to the heat pipe cooler (.apprxeq.28 watts) where
the measured heat output was a total of 87 watts. The air blower
heat at the cooler (.apprxeq.28 watts) in run VII was determined by
run VIII which was obtained by shutting off the input of electrical
power with the hot air blower still continuously being run in the
same location.
In order to fully understand the proportioning control aspect of
these runs it should be kept in mind that the "on" data listed on
table I are the maximum steady state values for the electrical
power input. For a particular vapor pressure or "control
temperature" at reservoir 88, the heat pipe would operate properly
at any value of power P.sub.in <P.sub.in max.
FIG. 7 shows a chart of the control of vapor transport of heat by
control of the fluid vapor pressure in a control section of the
heat pipe.
The chart shows the net heat out of the embodiment of the heat pipe
illustrated in FIGS. 1 and 2. The net heat transported by two-phase
fluid flow or Q.sub.(net) is obtained by subtracting from the
measured heat output an estimated value for Q (metal conduction)
and the Q (from reservoir) or the heat that was placed into the
system through the reservoir tube 88. These points are plotted
versus the estimated vapor temperatures as obtained by
thermocouples 104, 108.
MULTIHEAT PIPE ARRANGEMENTS
In another embodiment of the invention it is proposed that a plural
system of heat pipes be arranged in association with a heat-pipe
controller of the type previously discussed.
Thus, in FIG. 4 of the drawings an arrangement is illustrated that
includes a first heat pipe 120 joined to a control section 122
which is in turn joined to a second heat pipe 124.
In this arrangement a fluid charging unit 126 is included that has
an inlet 128 through a cock valve 130 to a convoluted flow section
132 surrounded by a cooling-water jacket 134. The convoluted
section 132 communicates through an outlet 136 and a cock valve 138
to an inlet opening 140 through a glass tube 142 having the
opposite ends open.
The water jacket 134 includes an inlet 144 and an outlet 146
therefrom.
In this arrangement the control section 122 is formed by the glass
tube 142 in cooperation with end caps 148, 150 therein which seal
the opposite open ends thereof. An annular O-ring 152 on the outer
periphery of the cap 148 seals to the glass tube 142. A like
annular O-ring 154 in the end cap 150 seals against the inside
diameter at the opposite ends of the glass tube 142.
Together the glass tube 142 and sealed end caps 148, 150 define an
evacuated chamber 156 into which liquid can be directed through the
unit 126.
The heat pipe 120 more particularly includes an elongated pipe 158
which is closed at its opposite ends by end plates 160, 162. The
pipe 158 is directed through a central opening 164 in the end cap
148 to be supportingly received and located with a condenser
section 166 of the heat pipe 120 interiorly of the chamber 156
about one-third the length of tube 142.
An evaporator section 168 of the heat pipe 120 is located within
the interior 170 of a heat source representatively shown as hot air
plenum 172 which includes a hot air inlet 174 and an air return
176.
In this embodiment of the invention the heat pipe 120 includes a
tubular porous sleeve 178 that extends throughout the length of the
pipe 158 and is bonded in good thermal-conductive relationship with
the inside surface of the pipe 158 throughout the lengths of the
evaporator and condenser sections of heat pipe 120.
The sleeve 178 can be made of a wire mesh porous wick material to
have a predetermined degree of capillary action of the type
described with respect to the wick section in the first embodiment
of the invention.
The heat pipe 124 includes an elongated tubular section 180
directed through a central opening 182 in the end cap 150 to be
supported thereby and directed into coaxial alignment with the pipe
120 at a point generally concentrically of the tube 142 and axially
inwardly thereof about one-third the length of tube 142.
The tubular section 180 is closed at its opposite end by end caps
184, 186.
The heat pipe 124 also includes an interiorly located tubular wick
188 which is formed of a porous material having a suitable
capillary action like that of the tubular sleeve 178.
Both of the heat pipes 120, 124 are sealed with respect to their
supporting end caps 148, 150 by O-ring elements 190, 192
respectively.
In this arrangement the heat pipe 124 includes an evaporator
section 194 located within the control chamber 156 axially inwardly
of the cap 150 which takes up heat input from the heat pipe
120.
The heat pipe 124 further includes a condenser section 196 that is
located within the interior 198 of a water-cooled jacket 200 having
a water inlet 202 and a return fitting 204.
Additionally, in this embodiment of the invention a control
reservoir 206 is formed as a depending tubular member from the
underside of the glass tubular 208 in 142 to define a sump or
liquid collection volume 208 in which is located a predetermined
charge of control fluid 210.
The tip or control reservoir 206 is selectively heated by suitable
heating means representatively illustrated as being a resistance
wire element 212.
As was the case in the first embodiment, the control section 122
includes a tubular wick element or wire sleeve 214 having one end
216 thereof fit over the outer surface of the pipe 158 at the end
thereof located within the chamber 156.
More particularly, the end 216 can be bonded to the outer surface
of the pipe 158 at this point to obtain good thermal conductive
transfer therebetween.
The opposite ends 218 of the wick 214 fits over the end of the pipe
180 located within the control chamber 156 and is bonded thereto
for like thermal-conduction properties.
The sleeve wick 214 thereby serves to bridge between the condenser
section 166 of the heat pipe 120 and the evaporator section 194 of
the heat pipe 124.
In this embodiment of the invention, each of the heat pipes 120,
124 include a two-phase fluid system of the type described with
respect to FIG. 3 above. Hence, in the case of the heat pipe 120
heat input at the hot air plenum 172 will produce an evaporator
section at 168 form whence the heat-transfer medium will vaporize
to flow to the right through the interior of the pipe 158 into the
vicinity of the cooler temperature and represented by the
evaporator section 168.
The heat-transfer medium in the control section 122, when the
control section 122 is turned "off" is condensed as a predetermined
quantity of liquid 210 within the tip or control reservoir 206. The
sleeve wick 214 thereby is maintained substantially dry and the
heat transfer through the control section 122 from heat pipe 120 to
heat pipe 124 is reduced to that of the thermal conductance of the
sleeve 214 which is substantially reduced from the rate of heat
transport found in heat-pipe assemblies that are "on."
However, when the heat pipe is "on" as when the heater 212 causes
the condition of the control fluid or liquid 210 to be in the vapor
state, the sleeve wick 214 is wetted so as to produce a normal
heat-pipe action of the type described with reference to FIG.
3.
Under these conditions the evaporator section 216 of the controller
122 causes the heat-transfer media within the evacuated sealed
chamber 156 to become vaporized and flow through the chamber 156 to
the opposite end of the control section 122 where it is condensed
on wick end 218. The liquid is returned by capillary action through
the sleeve wick element 214 back to the evaporator section to
complete the heat-pipe action cycle.
The section 194 of the heat pipe 124 is at a higher temperature
than the section 196 thereof. It, thus, serves as an evaporator
section in the heat pipe 124 and causes the two-phase heat transfer
medium inside pipe 124 to evaporate at the section 194 and flow as
a vapor to the cooler end surrounded by the water-jacket housing
200. The vapor condenses at 196 and flows as a liquid in the
opposite direction through the sleeve wick 188 back to evaporator
194 to complete the heat-pipe cycle.
The wetted control section 122 has a substantially greater rate of
heat transport than when the wick 214 is dry whereby the heat
transfer from the heated end of the heat pipe 120 to the cooled end
of the second heat pipe 124 is great as compared to when the
control section 122 is "off."
In the scheme illustrated in FIG. 4 the rate of transport from the
heat input end at the heat source 172 to the heat output or sink
end represented by the water jacket 200 is that established by heat
pipes of the type illustrated in series and wherein the control
section 122 while itself being a heat pipe serves as a means
independent of the temperature difference between source 172 and
sink 200 for regulating the total transport rate from the heat
source to the heat sink.
While the control reservoir and the heat-transfer medium therein
used to control the rate of heat transport has been shown as a
liquid heated and vaporized to cause a greater vapor pressure
within the control chamber, in the embodiments of FIGS. 5 and 6
other kinds of control reservoirs are illustrated having a
predetermined amount of control fluid therein and means to change
the condition of the control fluid so as to vary the rate of heat
transport of an associated heat pipe by changing the degree of
dryness or wetness of a wick component in the pipe.
More particularly, in each case a control reservoir is illustrated
that is intended for use at a point in a heat-pipe system like that
occupied in the embodiments of FIGS. 1 and 2 and FIG. 4 by the
tubular reservoir and a surrounding resistance heater.
In the embodiment of FIG. 5 a reservoir housing 213 is illustrated
that is adapted to be connected to the outer tubular housing 215 of
a control section of a heat-pipe system through a reduced diameter
neck 217. Within a large diameter bore 219 of the housing 213 is
located a reciprocating piston 221 having a peripheral seal 220
therein that sealingly engages the inside wall at the diameter
219.
A piston rod 222 is connected at one end to the piston 221 and has
the opposite end thereof connected to an end plug 224 of a flexible
bellows 226. The piston rod 222 is pivotally connected by a pin 228
through one end of a oscillating actuating lever 230. The fulcrum
for the lever 230 is defined by a pin 232 fixedly secured to a
support base 234.
In the illustrated arrangement the flexible bellows 226 connects to
a large diameter open end of the housing 213 and is sealed by the
plug 224 to define a sealed, movable link between the actuating
lever 230 and the piston rod 222 for reciprocating the piston 218
within the large diameter section 216 so as to vary the effective
volume of a control chamber 236 located between the upper face of
the piston 221 and the interior 238 of the tubular outer housing
215 of the control section.
In this arrangement the volume of the control chamber is varied by
mechanical control and the temperature within the reservoir 236 is
maintained less than the temperature of the heat pipe which is
controlled by the mechanism. Thus, when the volume of the chamber
236 is reduced by moving the piston 221 upwardly within the section
219 the vapor pressure within the chamber 238 is increased to
produce greater wetting of the capillary wick within the heat pipe
and will result in increased heat-transport rates. Temperature and
heat capacity of housing 215 quickly vaporizes fluid entering
reservoir 236.
When the piston 221 is moved downwardly within the section 219 the
volume of the control chamber 236 is increased so as to expose more
of the cold wall of housing 213 and condense more of the fluid and
thereby reduce the amounts of fluid (and wetness) of the wick in
the control section 238 which thereby reduce the heat-transport
rate through the section.
In the embodiment of FIG. 6 a controller 250 is illustrated adapted
to replace a tube reservoir of the type illustrated in the
embodiment of FIGS. 1 and 2. In this arrangement the controller 250
includes a movable bellows section 252 having a variable volume
interior 254 which is in direct fluid communication through a small
diameter neck 256 with the interior 258 of a tubular outer housing
a control section like the tubular outer housing 142 in the
embodiment of FIG. 4.
In the illustrated arrangement an electrical resistance element 262
is wound around the convolutions of the bellows 252 and is
connected across a power source by lead lines 264, 266. A
potentiometer 267 is connected between line 266 and element 262. It
includes a resistance 268 and a movable contact carrying arm 270.
It is operated by a lever 272 pivotally connected to a depending
extension 274 on the base of the bellows 252 by a pin 276.
The controller of FIG. 6 is intended to be an automatic heat-pipe
pressure control. If the pressure within the heat pipe increases
beyond a predetermined set point, the bellows 252 will expand to
increase the volume of the chamber 254. Concurrently, the
potentiometer contact carrying arm 270 is moved with respect to the
variable resistance 268 to include greater resistance in the
winding or electrical resistance element 262 between lead lines
264, 266. As a result, automatically, the heater current is
decreased and the temperature in the chamber 254 will also reduce
to produce a reduction in the vapor pressure within the system both
to control the rate of heat transport and to serve as a pressure
relief within the system.
Another system for controlling the operation of heat pipes is
illustrated in FIGS. 8 and 9.
In this embodiment a heat-pipe controller is proposed to prevent
any part of the main heat-pipe structure from approaching the
heater or heat-source temperature. This is desirable wherein the
heat-transfer media is one that can decompose at the temperature of
the heat source.
In the illustrated arrangement an evaporator end of a primary heat
pipe 300 is illustrated having a tubular pipe 302 closed at its end
by means including a plug 304. The heat pipe 300 includes a sleeve
wick 306 that is made of a suitable porous capillary flow material.
In the illustrated arrangement the wick 306 is suitably bonded to
the inner surface of the pipe 302 completely circumferentially
therearound and extends throughout the length of the pipe 302.
Located in concentric relationship with the heated end of the
primary heat pipe 300 is a control heat pipe 308 that includes an
outer tubular housing 310 that is located in spaced-surrounding
relationship with the heated end of the primary heat pipe 300 at a
point radially outwardly therefrom.
In the illustrated arrangement the housing 310 has an open end
closed by a plug 312 and a radially inwardly bent end 314 which is
formed as a small diameter neck 316 at the end of the housing 310
fit into close, sealed engagement with the outer circumference of
the outer surface of the pipe 302.
On the outer surface of the evaporator end of the primary heat pipe
302 is located a sleeve wick 318 of porous material which extends
from the plugged end 304 of the pipe 302 to a point closely
adjacent the end 314 of the housing 310 of the control heat pipe
308.
Additionally, a sleeve wick 320 of a larger diameter than sleeve
wick 318 is located in surrounding circumferential relationship
therewith at a point spaced radially outwardly of the sleeve 318.
Furthermore, the sleeve 320 is bonded to the inner surface of the
tubular housing 310 between the plug 312 and a point immediately
adjacent the end 314 of pipe 308.
Between the sleeve wicks 318, 320 is located an annular space 322
which extends completely throughout the length of the tubular
housing 310. The space 322 constitutes a vapor passageway which is
in communication with the inlet neck 324 to a control reservoir 326
that defines a sump or liquid collection region 328.
In the illustrated arrangement an electrical resistance element 330
is wound on the outer surface of the reservoir 326 so as to
condition a predetermined quantity of control fluid 332 in the
reservoir 326 to vary the amount of liquid in the wicks 318, 320
for the purposes to be discussed.
In the illustrated arrangement, a heat source 333 is located around
the primary heat pipe 300 and the radially outwardly located
control heat pipe 308. It includes a housing 334 located in
radially outwardly spaced relationship with the outer surface of
the tubular housing 310. The housing 334 includes an end wall 336
and an axially directed continuously formed flange 338 that is
located in sealed relationship with the outer surface of the
tubular housing 310 at the point which it is bent radially inwardly
at 314.
A suitable layer of thermal insulation 440 surrounds the heat
source 333.
In this case only the outside components and the vapor of the fluid
of the radial control heat pipe 308 ever see the heat-source
temperature.
In this design the wick of the radial control heat pipe includes
the radially outermost sleeve wick 320, the sleeve wick 318 and a
plurality of sandwiched radial sections 335 of wick material which
connects the sections 318, 320 as best illustrated in FIG. 9. Each
of the sections 335 is located through the axial extent of space
322 and circumferentially spaced from one another as seen in FIG.
8.
Here the vapor flows radially inwardly from the wick section 318 to
wick 320 and the condensate of the heat pipe flows radially outward
via the wick sections 335. As discussed in the previous embodiments
of the invention when the temperature of the control reservoir 326
is increased by the resistance heater 330 the vapor pressure will
be increased within the elongated vapor spaces between the axially
directed short-length wick strips 335 so as to closely maintain the
rate of heat transport from the heat source 333 to the evaporator
section of the primary heat pipe 300 at a level where the
temperature under steady state conditions in the primary heat pipe
300 will always be maintained less than that of the heat
source.
While embodiments of the present invention, as herein disclosed
constitute preferred forms, it is to be understood that other forms
might be adopted.
* * * * *