U.S. patent number 3,786,861 [Application Number 05/133,082] was granted by the patent office on 1974-01-22 for heat pipes.
This patent grant is currently assigned to Battelle Memorial Institute. Invention is credited to Philip E. Eggers.
United States Patent |
3,786,861 |
Eggers |
January 22, 1974 |
HEAT PIPES
Abstract
A heat pipe comprising a fluid-tight container 10 for
transferring heat from a source 13 adjacent to an evaporation
region 14 to a sink 15 adjacent to a condenser region 16, a passage
17 for transferring vapor from the evaporator region to the
condenser region, and a wick 18 having high heat conductivity for
transferring condensate from the condenser region back to the
evaporator region by capillary pumping and for conducting heat from
the container in the evaporator region to the evaporation sites 19
and from the condensation sites 20 to the container in the
condenser region. The wick comprises a bundle-like arrangement of
substantially direct, parallel, substantially uniform capillary
channels 21, each about 10.sup..sup.-4 to 10.sup..sup.-1 square
millimeter in cross-sectional area and having a low rugosity
factor, from the condenser region to the evaporator region. Each
end 24,26 of the wick forms an angle 25,27 of about 15.degree. to
60.degree. with the adjacent capillary channels, and may have
porous surfaces, to provide substantial areas for evaporation and
condensation at the ends of the channels.
Inventors: |
Eggers; Philip E. (Worthington,
OH) |
Assignee: |
Battelle Memorial Institute
(Columbus, OH)
|
Family
ID: |
22456926 |
Appl.
No.: |
05/133,082 |
Filed: |
April 12, 1971 |
Current U.S.
Class: |
165/104.26 |
Current CPC
Class: |
F28D
15/046 (20130101) |
Current International
Class: |
F28D
15/04 (20060101); F28d 015/00 () |
Field of
Search: |
;165/105 |
References Cited
[Referenced By]
U.S. Patent Documents
Other References
laub, J. H. et al., "Recirculation of a Two-Phase Fluid by Thermal
and Capillary Pumping," Jet Propulsion Lab, Pasadena, Cal., 12/1961
(Tech. Rep. No. 32-196) pgs. Cover, 8-10..
|
Primary Examiner: Davis, Jr.; Albert W.
Attorney, Agent or Firm: Gray, Mase & Dunson
Claims
I claim:
1. A heat pipe comprising
a fluid-tight container for transferring heat therethrough from a
source adjacent to an evaporation region thereof to a sink adjacent
to a condenser region thereof,
a passage for transferring vapor from the evaporator region to the
condenser region, and
a wick for transferring condensate from the condenser region back
to the evaporator region by capillary pumping and for conducting
heat from the container in the evaporator region to the evaporation
sites and from the condensation sites to the container in the
condenser region,
the wick comprising a bundle-like arrangement of substantially
direct, parallel, substantially uniform capillary channels, each
about 10.sup.-.sup.4 to 10.sup.-.sup.1 square millimeter in
cross-sectional area and having a low rugosity factor, from the
condenser region to the evaporator region,
the end of the wick in the evaporator region forming an acute angle
with the adjacent capillary channels to provide substantial areas
for evaporation of the condensate at the ends of the channels,
and
the end of the wick in the evaporator region having a porous
surface thereon for conveying condensate from the ends of the
adjacent capillary channels to provide additional areas for
evaporation of the condensate.
2. A heat pipe as in claim 1, wherein the cross-sectional area of
the channels is about 40 to 80 percent of the cross-sectional area
of the wick.
3. A heat pipe as in claim 1, wherein the angle is about 15.degree.
to 60.degree..
4. A heat pipe as in claim 1, wherein the end of the wick in the
condenser region forms an acute angle with the adjacent capillary
channels to provide substantial areas for condensation of the vapor
at the ends of the channels.
5. A heat pipe as in claim 4, wherein each angle is about
15.degree. to 60.degree..
6. A heat pipe as in claim 1, wherein the wick comprises a material
having high heat conductivity.
7. A heat pipe as in claim 6, wherein the wick is in tight thermal
contact with the container over substantial areas in the
evaporation region and in the condenser region.
8. A heat pipe as in claim 7, wherein adjacent surfaces in the wick
between the evaporation site and the evaporator region of the
container and between the condensation sites and the condenser
region of the container are in tight thermal contact over
substantial areas to minimize the thermal impedance
therebetween.
9. A heat pipe as in claim 8, wherein the tight thermal contact is
provided by diffusion-bonded surfaces.
10. A heat pipe as in claim 8, wherein the tight thermal contact is
provided by braze-bonded surfaces.
11. A heat pipe as in claim 1, wherein the cross-sectional area of
each capillary channel is about 10.sup.-.sup.4 to
2.times.10.sup.-.sup.2 square millimeter.
Description
BACKGROUND OF THE INVENTION
This invention relates to heat transfer devices of the type
commonly referred to as heat pipes.
The conventional heat pipe consists of a sealed container lined
with a "wicking" structure that is saturated with a liquid or
working fluid at a temperature corresponding to liquidus
temperature for a given saturation pressure. Thus, the operating
temperature is a function of the heat sink temperature and the
pressure-temperature characteristic of the selected working fluid.
Heat is added to one region of the heat pipe, referred to as the
evaporator region, and the liquid at the exposed end of the wick
structure evaporates, generally into a central vapor channel. Thus,
the thermal input is assimilated in the evaporator section of the
heat pipe via the latent heat of vaporization of the working fluid.
This vaporization phenomena results in a vapor pressure gradient
which causes the generated vapor to flow from the evaporator region
through a vapor channel to a condenser region where the vapor
condenses onto the opposite end of the wick, giving up its latent
heat of vaporization. This phase change phenomena, which occurs at
very nearly constant temperature, provides highly efficient
transport of thermal energy.
The evaporation of liquid at the vapor-liquid interface in the
evaporator region causes the residual liquid to retreat into the
capillary structure producing a meniscus radius of curvature and a
contact angle that are smaller in the evaporator region than in the
condenser region where the condensate is deposited. This difference
effects a pressure gradient which pumps liquid through the wicking
structure from the condenser region back to the evaporator region
to complete the working fluid transfer cycle.
In order to be an effective heat transfer device, the heat pipe
must be optimized to properly merge the physical characteristics of
the working fluid with the geometric constraints and the desired
operational temperature range. The maximum thermal power per unit
temperature difference between the extreme end points of the heat
pipe that can be transferred in a heat pipe of fixed dimensions, is
determined by
A. the pumping capability of the wick structures,
b. the thermophysical properties, particularly the thermal
conductivity of the materials of construction employed for the wick
and containment vessel and methods of attachment (i.e., thermal
impedances between shell and wick in the evaporator and condenser
sections),
c. the physical properties of the working fluid, such as surface
tension, contact angle, latent heat of vaporization, viscosity of
the liquid and gas phases, density of the liquid and gas phases,
and vapor pressure, over the temperature range of interest,
d. the onset of boiling of the fluid in the evaporator regions, due
to superheating of the fluid induced by high heat fluxes,
e. the onset of entrainment, i.e., the counterflow shear between
the liquid on the wick and the vapor in the vapor passage, and
f. the vapor phase sonic limit, i.e., the "upper-limit" velocity at
which vapor can be transferred from the evaporator to the condenser
regions of the heat pipe.
The key component of the heat pipe is the wick structure, which
performs the following four basic functions:
1. Liquid pumping. Results from surface tension forces developed in
wick pores at the liquid-vapor interface; small pores are
desirable, particularly in the evaporator region.
2. Liquid-flow path. Liquid drawn from the condenser to the
evaporator flows in wick channels; large, smooth-wall channels are
desirable for low hydrodynamic losses.
3. Radial heat-flow path. Thermal energy transferred by evaporation
or condensation is conducted through a liquid-wick composite
structure; high thermal conductivity of both wick and liquid is
desirable.
4. Liquid-vapor flow separation. At high-performance conditions,
the counterflow shear between the liquid and vapor phases becomes
important; fine pores or even a solid separation layer is desirable
at the liquid-vapor interface in the adiabatic regions of
high-performance heat pipes.
Capillary wick structures of the prior art include (1) woven cloth,
fiberglass, or metal mats, or screens, (2) porous metal or ceramic
tubes (generally made from sintered powders), and (3) parallel
grooved channels (e.g., as shown by U.S. Pat. No. 3,402,767). These
wick structures are generally positioned contiguous to the inside
wall of the sealed container and are limited in performance by the
tortuous liquid-flow paths in the case of mats, screens or porous
tubes, and by channel shape and size in the case of the parallel
grooved channels.
The parallel capillary channel wick structure of the present
invention provides significant increases in the heat pumping
capacity over the conventional wick structures. A multiplicity of
parallel capillary channels provide a significant reduction in
hydrodynamic losses when compared with the tortuous channels of
typical sintered powder wicks, or the metal felt or screen wicks
commonly used. The parallel capillary channel wick structure of the
present invention has the following advantages over conventional
wick designs:
a. high fluid conductance of the wick flow passages,
b. reproducible wick structure (in terms of porosity and pore shape
and size),
c. higher effective thermal conductivity between the container, the
working fluid, and the wick, and
d. wide variety of materials that can be used in the fabrication of
the wick, such as nickel, copper, and stainless steel.
The wick structure can be fabricated with extremely uniform pore
diameters ranging from 10 to 300 microns and having porosities in
the range of 40 to 80 percent. The advantages of the wick structure
of the present invention result in an order of magnitude increase
in the heat pumping capacity as compared with conventional sintered
powder wick structures.
In the present heat pipe diffusion-bonded, and optionally
braze-bonded, wick-container composite structures serve to minimize
the thermal impedance associated with conduction heat transfer
across the container-wick interface and through the wick structure
leading to the sites of evaporation. In addition, a surface porous
coating is applied to the parallel capillary channel wick in the
evaporator region. This porous coating serves to increase the
number of evaporation sites and, hence, decreases the thermal
impedance associated with the transfer of heat from the wick to the
center region of the capillary meniscus where evaporation is
actually taking place.
One of the advantages of the parallel capillary channel wick is its
"restart capability," the capability of resaturating the wick and
any optional arteries or grooves once the working fluid in the
liquid state has been removed. For example, composite wicks (such
as the artery-containing wick and the grooved-channel wick with
screen) are difficult to "restart" since the capillary pumping
action required is inversely proportional to the effective
capillary diameter. Hence, in the case of the wick containing an
"enlarged" artery, the capillary pumping action is usually
inadequate to resaturate the wick, particularly if the heat pipe is
oriented such that capillary pumping must work against gravity. The
"temporary removal" of working fluid (in the liquid state) from
portions of the wick may result from (1) shock- or
vibration-induced loss, (2) "burn-out" of wick under excessive heat
load conditions, (3) exceeding the critical temperature of the
working fluid, and (4) freeze-out in condenser region of heat pipe
before vaporization ceases in evaporator region. If any of the
above or other adverse conditions cause liquid displacement from
the wick to below some critical level, viz, the capillary/artery
interface, then the composite wick may be difficult if not
impossible to restart in situ. Since the capillaries are of uniform
size in the present concept, the restarting, or resaturating of the
wick, is readily achieved.
SUMMARY OF THE INVENTION
A typical heat pipe according to the present invention comprises a
fluid-tight container for transferring heat therethrough from a
source adjacent to an evaporation region thereof to a sink adjacent
to a condenser region thereof, a passage for transferring vapor
from the evaporator region to the condenser region, and a wick for
transferring condensate from the condenser region back to the
evaporator region by capillary pumping and for conducting heat from
the container in the evaporator region to the evaporation sites and
from the condensation sites to the container in the condenser
region, the wick comprising a bundle-like arrangement of
substantially direct, parallel, substantially uniform capillary
channels, each about 10.sup.-.sup.4 to 10.sup.-.sup.1 square
millimeter in cross-sectional area and having a low rugosity
factor, from the condenser region to the evaporator region, the end
of the wick in the evaporator region forming an acute angle with
the adjacent capillary channels to provide substantial areas for
evaporation of the condensate at the ends of the channels.
The cross-sectional area of the channels typically is about 40 to
80 percent of the cross-sectional area of the wick, and the end of
the wick in the evaporator region may have a porous surface thereon
for conveying condensate from the ends of the adjacent capillary
channels to provide additional areas for evaporation of the
condensate.
The end of the wick in the condenser region preferably also forms
an acute angle with the adjacent capillary channels to provide
substantial areas for condensation of the vapor at the ends of the
channels, and each angle preferably is about 15.degree. to
60.degree..
The wick should comprise a material having high heat conductivity,
and should be in tight thermal contact with the container over
substantial areas in the evaporation region and in the condenser
region. Adjacent surfaces in the wick between the evaporation site
and the evaporator region of the container and between the
condensation sites and the condenser region of the container should
also be in tight thermal contact over substantial areas to minimize
the thermal impedance therebetween. The tight thermal contact
typically is provided by diffusion-bonded or braze-bonded
surfaces.
Where nonmetallic liquids are used in the heat pipes, the
cross-sectional area of each capillary channel should be about
10.sup.-.sup.4 to 2.times.10.sup.-.sup.2 square millimeter.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a longitudinal cross-sectional view of a typical heat
pipe according to the present invention.
FIG. 2 is a transverse cross-sectional view taken in the plane 2--2
of FIG. 1.
FIG. 3 is an enlarged fragmentary section of the encircled area 3
in FIG. 1.
FIG. 4 is a longitudinal cross-sectional view of another typical
heat pipe according to the present invention.
FIGS. 5-9 are transverse cross-sectional views of other typical
embodiments of the invention.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
FIG. 1 shows a typical preferred embodiment of a heat pipe
according to the present invention comprising a fluid-tight
container 10 formed of a hollow cylindrical body member 11 sealed
at each end with an end plate 12. The container 10 preferably is
made of a material having high thermal conductivity, such as
nickel, for transferring heat therethrough from a source, indicated
schematically at 13, adjacent to an evaporation region 14 of the
container 10 to a sink, indicated schematically at 15, adjacent to
a condenser region 16 of the container 10. A passage 17 is provided
for transferring vapor from the evaporator region 14 to the
condenser region 16, and a wick 18 is provided for transferring
condensate from the condenser region 16 back to the evaporator
region 14 by capillary pumping and for conducting heat from the
container 10 in the evaporator region 14 to the evaporation sites
19 at the evaporator end 24 of the wick 18 and from the
condensation sites 20 at the condenser end 26 to the container 10
in the condenser region 16.
The wick 18 comprises a bundle-like arrangement of substantially
direct, parallel, substantially uniform capillary channels 21 each
about 10.sup.-.sup.4 to 10.sup.-.sup.1 square millimeter in
cross-sectional area and having a low rugosity factor (approaching)
unity), from the condenser region 16 to the evaporator region 14.
As used herein, "bundle-like arrangement" means that in an end view
or cross-sectional view, as in FIGS. 2 and 5-9, the channels appear
as an array (rows and columns as in FIG. 5) or a substantially
similar two-dimensional arrangement (as in FIGS. 6-9). A
bundle-like arrangement provides substantial advantages over a
single row or circle of channels such as those along the inside of
the tube in the heat pipe of United States Pat. No. 3,402,767 of
Bohdansky. In Bohdansky's arrangement it is easy to provide a large
evaporation area simply by having the channels open along the inner
side. However, the number of channels that can be provided in a
single layer is limited. Where many layers are used, as in the
bundle-like arrangement in the present invention, many more
channels are available and a much larger quantity of condensate can
be transported in a given time. As used herein, "having a low
rugosity factor (approaching unity)" means that impedance to the
flow of fluid is substantially the minimum that is possible for the
cross-sectional area, which requires primarily that the
cross-sectional shape be substantially circular, square, or other
shape of low eccentricity such that the distance across is nearly
the same in all directions. Also, it is required that the inner
surfaces of the capillary channels be reasonably smooth in order to
minimize viscous losses.
The end 24 of the wick 18 in the evaporator region 14 forms an
acute angle 25 with the adjacent capillary channels 21 to provide
substantial areas 19 for evaporation of the condensate at the
evaporator ends of the channels 21. This is important to provide a
large enough total evaporation area in a plurality of layers of
channels. The end 26 of the wick 18 in the condenser region 16
preferably also forms an acute angle 27 with the adjacent capillary
channels 21 to provide substantial areas 20 for condensation of
vapor at the condenser ends of the channels 21. Each angle 25,27
preferably is about 15.degree. to 60.degree.. The cross-sectional
area of the channels 21 preferably is about 40 to 80 percent of the
entire cross-sectional area of the wick 18.
As shown in the FIG. 3, the end 24 of the wick 18 in the evaporator
region 14 may be provided with a porous surface, as indicated at
28, for conveying condensate from the ends 19 of the adjacent
capillary channels 21 to provide additional areas at 28 for
evaporation of the condensate.
Like the container 10, the wick 18 preferably is made of a material
having high heat conductivity. The wick 18 should be in tight
thermal contact with the container 10 over substantial areas in the
evaporator region 14 and in the condenser region 16. Where the
container 10 and the wick 18 are formed separately, the tight
thermal contact may be provided by a very tight press fit, as by
heating the container 10 to a substantially higher temperature than
that of the wick 18 when they are placed together, or by diffusion
bonding the contiguous surfaces, or by brazing them together.
The wick 18 may comprise a substantially solid member, except for
the channels 21 therein, as in FIGS. 2, 7, and 8, or it may be
formed from more than one piece, as in FIGS. 5, 6, and 9, with
adjacent surfaces in the end 24 of the wick 18 between the
evaporation sites 19 and the evaporator region 14 of the container
10, and in the end 26 between the condensation sites 20 and the
condenser region 16 of the container 19, in tight thermal contact
over substantial areas to minimize the thermal impedance between
the evaporation sites 19 and the container 10 and between the
condensation sites 20 and the container 10. The tight thermal
contact may be provided by diffusion bonding or brazing the
contiguous surfaces.
Where the channels 21 are substantially circular in cross-section,
the diameter of each should be about 10 to 300 microns (about
10.sup.-.sup.4 to 10.sup.-.sup.1 square millimeter in
cross-sectional area) to provide the optimum capillary pumping
action. Where nonmetallic liquids are to be transported through the
channels 21, the diameter should be in the low portion of the
range, about 10 to 130 microns (about 10.sup.-.sup.4 to 2.times.
10.sup.-.sup.2 square millimeters), for optimum capillary pumping
action. The size of the angle 25 at the evaporator end 24 of the
wick 18 and the size of the angle 27 at the condenser end 26 of the
wick 18 depend primarily on the lengths of the adjacent head source
13 and heat sink 15 since the object of the tapered sections is to
distribute the evaporation and condensation sites over the
available surfaces of the heat source and sink. As shown in FIG. 4,
at 30 and 31, the end region may be curved so that the angle varies
in size along the end region 24 or 26. Within the range of about
15.degree. to 60.degree. the exact size of the angle is not
critical.
FIG. 4 also shows another variation that can be made in the heat
pipe of FIG. 1, namely that in part or all of the adiabatic region
32, between the evaporator region 14 and the condenser region 16,
the wick 18 may be omitted, and the condensate from the condenser
region 16 may return from the condenser end wick 26 through the
annular open space 33 to the evaporator end wick 24. However, a
heat pipe as shown in FIG. 4 is not self-starting. The space 33
must be substantially full of fluid immediately before and
continually during operation of the heat pipe.
The annular space 33 in FIG. 4 may contain a wick 18 as in FIG. 1.
Where desired, especially where the region 32 is longer than the
wick 18 can be made conveniently, several sections of wick 18 may
be arranged in tandem along the length of the annular space 33.
Preferably each section of wick 18 should be spaced a fraction of a
millimeter from the adjacent section so as not to block the passage
of condensate through the heat pipe as might happen if the channels
21 in successive sections of the wick 18 did not substantially
register with one another.
FIGS. 2 and 5-9 illustrate ways in which the wick 18 may be formed.
In FIGS. 2, 7, and 8, the channels 21 may be formed by rods that
are embedded in the wick 18 when it is cast or formed in any other
convenient way, the rods being subsequently removed by any
convenient method such as melting or chemical dissolution. The
passages 17 in FIGS. 2 and 7 may be formed in similar ways or by
using cores of sand or other appropriate material in the forming
process.
FIG. 8 illustrates the fact that the passage 17 need not be
surrounded by the wick 18. A longitudinal cross-sectional view of
the heat pipe in FIG. 8 is the same as FIG. 1 with the lower part
of the wick 18 omitted.
The heat pipe in FIG. 9 is similar to that in FIG. 2 except that
the channels 21 comprise the spaces between adjacent rods or wires
34 arranged in a bundle between the container 10 and the passage
17.
The heat pipe in FIG. 6 is similar to that in FIG. 9 except that
the passages 21 comprise the spaces between adjacent portions of a
thin corrugated member 35 and a contiguous thin flat member 36
wound in a spiral around the passage 17 and mounted inside the
container 10. In FIG. 5 also the channels 21 comprise the spaces
between the adjacent surfaces of a thin corrugated member 35 and a
thin flat member 36 but with the members 35 and 36 stacked
alternately inside the container 10 and around the passage 17. In
FIGS. 5 and 6 the flat members 36 may be omitted if the corrugated
members 35 are arranged in such a manner as to assure that adjacent
peaks and valleys are sufficiently out of registry to provide the
spaces required for the channels 21.
Of course the drawings are not to scale or even roughly in
proportion. The container 10 typically has an outside diameter of
less than one-half inch and a length of 2 inches or greater. One
typical heat pipe as in FIGS. 1 and 6 using ammonia as the heat
transfer fluid is about 0.19 inch in outside diameter and 6 inches
long. Another, as in FIGS. 1 and 2 and using liquid nitrogen, is
about 0.25 inch in outside diameter and 3 inches long.
While the forms of the invention herein disclosed constitute
presently preferred embodiments, many others are possible. It is
not intended herein to mention all of the possible equivalent forms
or ramifications of the invention. It is to be understood that the
terms used herein are merely descriptive rather than limiting, and
that various changes may be made without departing from the spirit
or scope of the invention.
* * * * *