U.S. patent number 3,857,441 [Application Number 05/017,106] was granted by the patent office on 1974-12-31 for heat pipe wick restrainer.
This patent grant is currently assigned to Westinghouse Electric Corporation. Invention is credited to Frank G. Arcella.
United States Patent |
3,857,441 |
Arcella |
December 31, 1974 |
HEAT PIPE WICK RESTRAINER
Abstract
This invention relates in general to heat pipes and more
particularly to a tubular heat pipe wick restrainer which includes
a tubular member with an outside diameter equal to the desired
inside diameter of the wick structure. The tubular member has
circumferentially placed holes which allow the heat pipe working
fluid to evaporate and condense at the evaporator and condenser
sections respectively.
Inventors: |
Arcella; Frank G. (Bethel Park,
PA) |
Assignee: |
Westinghouse Electric
Corporation (Pittsburgh, PA)
|
Family
ID: |
21780758 |
Appl.
No.: |
05/017,106 |
Filed: |
March 6, 1970 |
Current U.S.
Class: |
165/104.26;
29/890.032 |
Current CPC
Class: |
F28D
15/046 (20130101); Y10T 29/49353 (20150115) |
Current International
Class: |
F28D
15/04 (20060101); F28d 015/00 () |
Field of
Search: |
;165/105 ;29/157.3R |
References Cited
[Referenced By]
U.S. Patent Documents
Other References
deverall, J. E. et al. High Thermal Conductances Devices, Los
Alamos Scientific Laboratory, Los Alamos, New Mexico (LA-3211),
April, 1965 (Microfische), pgs. 1 and 29..
|
Primary Examiner: Davis, Jr.; Albert W.
Attorney, Agent or Firm: Abeles; D. C.
Claims
I claim as my invention:
1. A heat pipe comprising a sealed tubular outer casing, a tubular
wick structure positioned in said outer casing and closely received
by the inner surface thereof, and a tubular substantially
nonresilient, wick restrainer position within said casing and
closely received by the inner surface of said wick structure, said
wick restrainer being formed to provide uniform support to said
wick structure, to maintain the same in engagement with said inner
surface of said outer casing.
2. The heat pipe of claim 1 wherein said wick restrainer has an
outside diameter approximately equal to the desired inside diameter
of the wick structure, said wick restrainer extending over the
evaporator and condenser regions of the heat pipe and being
perforated along the evaporator and condenser regions to allow the
heat pipe working fluid respectively to evaporate at the wick/vapor
interface of the evaporator section and condense at the wick/vapor
interface of the condenser section.
3. The heat pipe of claim 2 wherein said perforation in said wick
restrainer has a diameter approximately equal to one-third of the
outside diameter of said wick restrainer.
4. The heat pipe of claim 2 wherein the perforations in said wick
restrainer are arranged in a hexagonal pattern.
5. The heat pipe of claim 2 wherein the perforations are arranged
in a pattern extending over the entire surface of said wick
restrainer.
6. The heat pipe of claim 1 wherein said wick restrainer is
rigid.
7. The heat pipe of claim 1 wherein said tubular wick structure
comprises wire mesh screen.
Description
BACKGROUND OF THE INVENTION
This invention pertains to heat pipes and more particularly to a
new heat pipe wick support.
In accordance with the present state-of-the-art, heat pipe wicks
are manufactured by various methods such as by fabricating channels
into the heat pipe walls by a broaching process. The channels,
which permit unrestricted fluid flow from the heat pipe condenser
to the evaporator section, are covered by fine mesh screen to
establish greater capillary wicking forces. Composite wicks have
also been manufactured by placing layers of heavy mesh screen (30
to 60 mesh) beneath the wick/vapor interface layers of fine mesh
screen (200 to 400 mesh). Another technique comprises the
fabrication of open annulus wicks by swaging several turns of
screen wound between two copper tubes. The copper tubes are then
etched away and the porous rigid wick is sinter bonded. Upon
insertion into a heat pipe with an open annulus between the wick
and heat pipe walls, this wick presents an optimum arrangement for
liquid metal charged heat pipes.
While these fabrication techniques have yielded heat pipes which
are both homogeneous in pore size and porosity and chemically
compatible with the heat pipe working fluids, they have not
provided wicks that maintain uniform contact with the heat pipe
inner surfaces. Such uniform contact is a necessary pre-requisite
for optimum heat pipe operation. Thus, retaining the wick against
the heat pipe inner walls has been a problem. The prior art has
employed several methods to correct this deficiency. One such
method comprises threading a drawn helical spring through the wick
material and releasing the spring so that the coils press the wick
against the heat pipe inner walls. The problem with this method is
that the spring provides non-uniform support over the wick surface
area causing constrictions at the spring/wick interfaces which
inhibit the capillary action of the wick. This method has
particularly proved to be impractical in high temperature heat
pipes where at elevated temperatures the spring loses its tension
and sags, thereby releasing the wick from the heat pipe walls and
creating gaps which result in hot spots, which may burn through the
heat pipe walls. Another method employed has been to produce wicks
by the aforementioned swaging process. The resulting wicks are
tight, homogeneous, free standing, channeled structures. These
wicks, however, can soften after a time at elevated temperatures
and sag, or be pushed away from the walls by the working fluid.
Other wicks have been fabricated by seam welding strips of wick
material into tubes and inserting them into heat pipe tubes. Again
no uniform restraining device presses the wick to the tube
wall.
In order to maintain optimum heat pipe operation the wick support
structure must also be able to prevent fluid loses at the
vapor-fluid interface caused by the high velocity vapors traveling
between the evaporator and condenser sections (entrainment). None
of the aforementioned techniques have been able to cope with this
problem and the result has been to starve the evaporator region of
the heat pipe.
SUMMARY OF THE INVENTION
Briefly, this invention overcomes the difficulties experienced by
the prior art by utilizing a tubular heat pipe wick restrainer
which comprises a tubular member with an outside diameter
approximately equal to the desired inside diameter of the wick
structure. The tubular member has circumferentially placed holes
which permit the heat pipe working fluid to evaporate and condense
at the evaporator and condenser sections respectively. The
resulting restrainer is both porous and retains good
circumferential strength. This circumferential rigidity permits
uniform pressure to be exerted on the wick structure.
The wick structure is tightly rolled onto the restrainer tube,
possibly tack welded to it, and inserted into the heat pipe tube. A
tight fit can be employed, or a sliding fit can be used if the wick
assembly is to be swaged. Thus the restrainer tube: (1) uniformly
presses the wick onto the heat pipe inner walls; (2) permits easier
heat pipe assembly and processing; and (3) presents a
non-homogeneous surface at the liquid/vapor interface to break up
the vapor flow path along the wick liquid/vapor interface. This
last property prevents the rapid vapor flow from pulling fluid out
of the wick (entrainment) and thus starving the evaporator
region.
BRIEF DESCRIPTION OF THE DRAWINGS
For a better understanding of an exemplary embodiment of this
invention, reference may be had to the accompanying drawings, in
which:
FIG. 1 is an isometric view of a heat pipe embodying the principles
of this invention, having a portion thereof cut away for
clarity;
FIG. 2 is an isometric view of the heat pipe of FIG. 1, broken away
in layers, and is illustrative of the position of the restrainer
tube with respect to the other elements of the heat pipe; and
FIG. 3 is a development of a portion of the heat pipe wick
restrainer tube of FIG. 2 and is illustrative of a hole pattern
which may be utilized with this invention.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring now to the heat pipe illustrated in FIGS. 1 and 2, it
will be appreciated that a heat pipe 10 constructed in accordance
with the principles of this invention includes an evacuated chamber
12 whose inside walls are lined with a capillary structure, or wick
14, that is saturated with a volatile fluid. A tubular support
member, or restrainer 30, having an outside diameter approximately
equal to the desired inside diameter of the wick structure 14, is
positioned within the evacuated chamber 12 against the wick 14
which closely receives the support member 30 in the center thereof.
The support member 30 exerts uniform pressure on the inner surface
of the wick 14 so as to restrain the wick 14 against the inner
walls of the heat pipe 10. The support member 30 has
circumferentially placed holes 32, which allow the working fluid to
evaporate and condense at the evaporator section 16 and condenser
section 18 respectively.
The operation of the heat pipe combines two familiar principles of
physics; vapor heat transfer and capillary action. Vapor heat
transfer serves to transport the heat energy from the evaporator
section 16 at one end of the pipe to the condenser section 18 at
the other end. Capillary action returns the condensed working fluid
back to the evaporator section 16 to complete the cycle.
The working fluid absorbs heat at the evaporator section 16 and
changes from its liquid state to a vapor state. The amount of heat
necessary to cause this change of state is the latent heat of
vaporization. As the working fluid vaporizes, the pressure at the
evaporator section 16 increases. The vapor pressure sets up a
pressure differential between the ends of the heat pipe, and this
pressure differential causes the vapor, and thus the heat energy,
to move towards the condenser section 18. When the vapor arrives at
the condenser section 18, it is subjected to a temperature lower
than that of the evaporator section 16 and condenses, thereby
releasing the thermal energy stored in its heat of vaporization at
the condenser section 18 of the heat pipe. As the vapor condenses
the pressure at the condenser section 18 decreases so that the
necessary pressure differential for continued vapor heat flow is
maintained. Movement of the fluid from the condenser section 18
back to the evaporator section 16 is accomplished by capillary
action within the wick 14, which connects the condenser 18 to the
evaporator 16.
In order to provide optimum heat pipe operation the heat pipe wick
14 must maintain uniform contact with the inner walls of the heat
pipe tube 20 and means must be provided for preventing fluid loses
in the wick 14 at the wick/vapor interface, due to the high
velocity vapor flow along this interface (sometimes approaching
sonic velocities).
This invention maintains the aforementioned criteria by utilizing
the heat pipe wick restrainer 30, illustrated in FIG. 2. The heat
pipe wick restrainer, or support 30, includes a tubular member 34
with an outside diameter approximately equal to the desired inside
diameter of the heat pipe wick 14. The tubular member 34 has
circumferentially placed holes 32 which allow the heat pipe working
fluid to evaporate and condense at the evaporator and condenser
sections respectively. The holes 32 are desirably arranged in a
pattern, such as the hexagonal pattern illustrated in FIG. 3, and
extend over the entire circumference of the restrainer. For closest
packing, it is suggested that the outside diameter of the holes 32,
should be approximately one-third the restrainer tube outside
diameter. The resulting restrainer is approximately 50 percent
porous and retains good circumferential strength. This
circumferential rigidity permits uniform pressure to be exerted on
the wick structure 14.
It is to be understood that the size of the holes and the hole
pattern may vary depending upon the heat pipe wick structure and
its intended use. For example, the holes may be positioned at the
evaporator and condenser sections without extending over the entire
length of the restrainer tube, and the size of the holes may vary
with the wick surface area required to produce the desired rate of
vaporization and condensation of the working fluid.
It is also to be understood that the tubular member 34 need not be
of circular cylindrical configuration, but may be desirably
designed to conform to any geometric shape the heat pipe wick may
form. What has been shown and described is merely an exemplary
embodiment of this invention and it is not intended to be
limitative thereof.
Thus the restrainer tube: (1) uniformly presses the wick onto the
heat pipe inner walls; (2) permits easier heat pipe assembly and
(3) presents a non-homogeneous surface to break up the vapor flow
path along the wick liquid/vapor interface. This last property
prevents the rapid vapor flow from pulling fluid out of the wick
and thus starving the evaporator region.
* * * * *