U.S. patent number 3,811,496 [Application Number 05/303,270] was granted by the patent office on 1974-05-21 for heat transfer device.
This patent grant is currently assigned to U.S. Philips Corporation. Invention is credited to George Albert Apolonia Asselman, Adrianus Petrus Dirne.
United States Patent |
3,811,496 |
Asselman , et al. |
May 21, 1974 |
HEAT TRANSFER DEVICE
Abstract
A heat transfer device (heat pipe) in which the layer of
material having a capillary structure for the transport of
condensate from the condensor to the evaporator is formed by
helically wound wire which has grooves transversely to the axis of
the wire.
Inventors: |
Asselman; George Albert
Apolonia (Emmasingel, Eindhoven, NL), Dirne; Adrianus
Petrus (Emmasingel, Eindhoven, NL) |
Assignee: |
U.S. Philips Corporation (New
York, NY)
|
Family
ID: |
19814427 |
Appl.
No.: |
05/303,270 |
Filed: |
November 2, 1972 |
Foreign Application Priority Data
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 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Davis, Jr.; Albert W.
Attorney, Agent or Firm: Trifari; Frank R.
Claims
1. A heat transfer device comprising a closed tubular container
having at one end a first tube wall section, at the other end a
second tube wall section, and an intermediate third tube wall
section, said container comprising a heat transfer medium which
absorbs thermal energy from the first tube wall section while
changing from the liquid phase into the vapour phase and delivers
thermal energy to the second tube wall section while changing from
the vapour phase into the liquid phase, the container furthermore
comprising a layer of material having a capillary structure and
covering the tube wall for the transport of condensed medium from
the second in the first tube wall section, characterized in that
the layer of material is formed by at least one wire which is wound
helically against the tube wall in the direction of the tube axis
and which comprises several capillary grooves distributed over the
length of the wire and extending transversely to the wire axis over
at least that part of the
2. In a heat-pipe heat transfer device formed as a closed container
having walls whose inner surfaces define a tubular bore which has a
longitudinal axis, said bore comprising a first section extending
from one end of the bore inward, a second section extending from
inward from the other end of the bore, and a third section
intermediate said first and second sections, the device further
including within said bore a heat transfer medium which changes
from liquid to vapor phase upon absorbing thermal energy and
changes from vapor to liquid phase while giving up thermal energy,
the improvement in combination therewith, a helically wound wire
within said bore with the outer surface of the wire adjacent said
bore surface and said helical axis thereof generally aligned with
said bore axis, said wire further comprising on at least that part
of its outer surface adjacent said bore surface, capillary grooves
which extend generally transversely of the wire axis, whereby said
grooves and bore surface comprise a capillary structure and said
medium when condensed to a liquid will be
3. A heat transfer device according to claim 2 wherein the
capillary grooves in the wire section which covers the first tube
wall section have a smaller hydraulic diameter and center distance
than the capillary
4. A heat transfer device according to claim 2 wherein the
capillary grooves in the wire section which covers the second tube
wall section have a smaller hydraulic diameter and center distance
than the capillary
5. A heat transfer device according to claim 2 wherein the helical
wound wire is a helical spring whose resilience urges same outward
to engage
6. A heat transfer device according to claim 5 wherein the helical
spring is tubular having walls which define a closed cavity, the
device further comprising in said cavity a filling medium the
pressure of which, at least at the operating temperature of the
device, is higher than the pressure of said medium in the container
for urging the helical spring against said bore surface due to the
influence of the pressure differential across the
7. Apparatus according to claim 2 wherein said wound wire comprises
turns and the turns in said third section of the bore are mutually
engaged which thereby form a tubular section that separates the
bore through said turns
8. Apparatus according to claim 2 wherein said capillary grooves in
the wire situated in said first section extend throughout the
circumference of
9. A heat transfer device according to claim 8 wherein the filling
medium
10. A heat-pipe heat transfer device comprising a closed container
having walls whose inner surfaces define a tubular bore which has a
longitudinal axis, said bore comprising a first section extending
from one end of the bore inward, a second section extending inward
from the other end of the bore, and a third section intermediate
said first and second sections, the device further comprising
within said bore a heat transfer medium which changes from liquid
to vapor phase upon absorbing thermal energy and changes from vapor
to liquid phase while giving up thermal energy, and a helically
wound wire within said bore with the outer surface of the wire
adjacent said bore surface and said helical axis thereof generally
aligned with said bore axis, said wire further comprising on at
least that part of its outer surface adjacent said bore surface,
capillary grooves which extend generally transversely of the wire
axis, whereby said grooves and bore surface comprise a capillary
structure and said medium when condensed to a liquid will be
transportable along said bore by capillary action therein.
Description
BACKGROUND OF THE INVENTION
The invention relates to a heat transfer device comprising a closed
tubular container having at one end a first tube wall section, at
the other end a second tube wall section, and an intermediate third
tube wall section. The container comprises a heat transfer medium
which absorbs thermal energy from the first tube wall section while
changing from the liquid phase into the vapour phase and delivers
thermal energy to the second tube wall section while changing from
the vapour phase into the liquid phase. The container furthermore
comprises a layer of material having a capillary structure and
covering the tube wall for transporting condensed medium from the
second to the first tube wall section.
Devices of this type are known from the U.S. Pats. Specifications
Nos. 3,229,759 and 3,402,767. With such devices, often termed heat
pipes, large quantitites of thermal energy can be transmitted
substantially without temperature drop, without using a pumping
device and without further moving parts. Liquid heat transfer
medium which evaporates near the first tube wall section
(evaporation zone) moves in the vapour phase to the second tube
wall section (condensation zone) as a result of the lower vapour
pressure there due to the slightly lower temperature at that area.
The vapour condenses on the second tube wall section while
delivering the heat of evaporation, after which the condensate is
returned through the layer of material having a capillary structure
on the basis of capillary action to the first tube wall section to
be evaporated there again. On its way, the condensate passes the
third tube wall section (transport zone).
The layer of material having a capillary structure ensures that
condensate can flow back in all circumstances from the second to
the first tube wall section, even against gravity or without
gravity field. Gauzes of wire or band-shaped material often serve
as a layer of material having a capillary structure in heat
pipes.
A drawback of the use of gauzes is that the condensate transport
capacity and hence the heat transfer capacity of the device is
restricted by it. This is caused by the fact that the large number
of wires of the gauze structure which extend transversely to the
direction of condensate transport inhibit flow of condensate.
For the transport of condensate, use is sometimes made of grooves
which are especially provided for that purpose in the tube wall.
The drawback of this construction is that it is difficult,
time-consuming and expensive to provide the grooves in the wall
with the required precision.
It is the object of the present invention to provide a heat
transfer device of the type described in which a large condensate
transport capacity of the material layer having a capillary
structure is associated with a simple and cheap manufacture and
construction of the layer.
SUMMARY OF THE INVENTION
In order to realize this objective the heat transfer device
according to the invention is characterized in that the layer of
material is formed by at least one wire which is wound helically
against the tube wall in the direction of the tube axis and which
is provided with several capillary grooves which are distributed
over the length of the wire, and extend transversely to the axis of
the wire over at least that part of the circumference of the wire
which faces the adjacent tube wall surface.
The grooves can be provided in the wire in an easy and admissible
manner. The wire which is provided with grooves may then be wound
helically and be inserted into the tubular container in the wound
condition so as to fit accurately. It is alternatively possible to
arrange the wire against the tube wall in the container while
winding.
In this manner a layer of material having a capillary structure is
obtained in a simple manner in which the capillary grooves in the
wire also bounded by the tube wall extend mainly in the axial
direction, namely the condensate transport direction, of the
device. The present system of grooves may have the same large
condensate transport capacity as heat transfer devices having axial
grooves in the wall of the tubular container.
Of course, the wire should be wound with such a pitch that gaps
between the turns do not become too large. When the gap width is
too large, heat transfer medium condensate remains no longer caught
in the capillary structure and the operation of the device is
disturbed.
In a favorable embodiment of the device according to the invention
the turns of the wire section which covers the third tube wall
section mutually engage each other. This presents a few advantages.
First of all, the winding of said wire section is much simpler but
the engaging turns also constitute a closed surface which separates
medium condensate in the transport zone from medium vapour present
in said zone. Due to the absence of a free phase surface area of
heat transfer medium in vapour and in liquid form in the transport
zone, no liquid particles from the layer of material having
capillary structure can be dragged along by medium vapour. As a
result of this a large heat transfer capacity is maintained.
A further favorable embodiment of the heat transfer device
according to the invention is characterized in that the capillary
grooves in the wire section which covers the first part of the tube
wall extend throughout the circumference of the wire.
In the first section of the tube wall forming the evaporation zone,
it must be possible for heat transfer medium to evaporate freely
from the capillary structure. By providing the wire section which
covers the first section of the tube wall with circumferential
grooves, the advantage is obtained from a point of view of winding
technology that the turns can engage each other while medium
evaporating on the first section of the tube wall can nevertheless
freely reach the vapour space since the circumferential grooves
ensure apertures in the continuous row of turns of wire.
According to the invention, the capillary grooves in the wire
section which covers the second section of the tube wall may also
extend throughout the circumference of the wire. It must be be
possible for medium vapour to condense freely on the second tube
wall section forming the condensation zone. This remains the case
when the turns of the wire section which covers the second tube
wall section engage each other, since the circumferential grooves
again constitute apertures in the closed row of turns.
With the above-described measures a heat transfer device is thus
possible in which all the wire turns engage each other which makes
the device extremely suitable for simple and cheap series
production.
A further favorable embodiment of the heat transfer device
according to the invention is characterized in that the capillary
grooves in the wire section which covers the first tube wall
section have a smaller hydraulic diameter and center distance than
the capillary grooves in the wire section covering the third tube
wall section.
Within this scope, the hydraulic diameter is defined as 4 .times.
(surface cross-section/circumference) of the groove. Since
comparatively many and small grooves are present per unit of length
of wire in the wire section which covers the first tube wall
section (evaporation zone) a large capillary suction force is
produced, the driving force for condensate transport, relative to
the wire section which covers the third tube wall section
(transport zone) and which comprises comparatively few and large
grooves. Due to the few large grooves the flow losses in the
transport zone are small. All this is of particular advantage in
heat transfer devices having transport zones and/or evaporation
zones of a large length.
In many small grooves in the evaporation zone which extend
throughout the circumference of the wire, a large liquid vapour
phase area is available in said zone. Thus, a large heat flux (heat
flow per unit of tube wall surface) in the evaporation zone and
hence comparatively small dimensions of the first tube wall section
are possible.
According to the invention, the capillary grooves in the wire
section which covers the second tube wall section may have a
smaller hydraulic diameter and center distance than the capillary
grooves in the wire section covering the third tube wall
section.
Due to the comparatively many and small grooves in the wire section
which cover the second tube wall section, the condensation zone, a
large capillary force is produced in said zone which ensures the
transport of condensate to the third tube wall section, the
transport zone. Since comparatively few and large grooves are
present in the transport zone, transport of condensate through said
zone again takes place easily, substantially without flow losses.
All this is of particular advantage in heat transfer devices having
a condensation zone and/or a transport zone of a large length.
Furthermore, a good removal of condensate in the condensation zone
is possible, in particular when a large vapour/liquid phase area is
available as a result of the many and small circumferential
(annular) grooves.
In a further favorable embodiment of the heat transfer device
according to the invention, the helically wound wire is a helical
spring which engages the tube wall by resilience. This offers the
advantage that an extra connection of the wire against the tube
wall, for example by sintering, is not necessary.
In certain circumstances, however, it may occur that the resilience
of the helical spring diminishes under the influence of the usually
high operating temperatures of the heat transfer device in such
manner that the pressure force becomes too small and the helical
spring works loose from the tube wall during operation. As a result
of this the helical spring is no longer useful for the return of
condensate. Hence the operation of the device is disturbed while
danger for boiling-dry and tearing of the first tube wall section
serving as evaporation occurs.
In order to avoid this drawback, in a favorable embodiment of the
invention, the helical spring is internally hollow. The closed
cavity contains a filling medium the pressure of which, at least at
the operating temperature of the device, is higher than the
pressure in the container, and the helical spring remains pressed
against the tube wall under the influence of the pressure
differential across it.
When the heat transfer device is out of operation and at room
temperature, the pressure of the filling medium in the helical
spring need not always be higher than the pressure which prevails
in that case in the container but it may then be equal to or even
lower than the pressure in the container. The resilience of the
helical spring at room temperature usually is sufficient to keep
the spring pressed against the tube wall. At room temperature the
pressure in the container is otherwise usually low since the
container is often evacuated in order that the
evaporation-condensation process of the heat transfer medium can
run off smoothly.
All kinds of material which are solid, liquid or gaseous at room
temperature may be considered as a filling medium, provided the
vapour pressure and gas pressure, respectively, of said materials
is higher than the pressure in the container at any rate at the
operating temperature of the device and possibly also at room
temperature.
For example, if sodium is present as a heat transfer medium in the
otherwise evacuated container, for example, potassium or calcium
may be used as a filling medium.
In a favorable embodiment of the invention the filling medium is an
inert gas. This offers the advantage that in the case of an
unexpected leakage of the helical spring, no chemical reactions
occur between the heat transfer medium and the filling medium. In
that case the device is not damaged.
The invention will be described in greater detail with reference to
the drawings diagrammatically and not to scale a few embodiments of
the heat transfer device.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1a shows in elevation view in section the heat transfer device
of this invention.
FIG. 1b shows a cross-sectional view of the device taken along
lines 1b--1b in FIG. 1a.
FIG. 1c shows a longitudinal sectional view of the grooves of FIG.
1a.
FIG. 1d is a sectional view of the wire taken along line 1d--1d in
FIG. 1c.
FIG. 2a, 3a, 4a and 5 show other embodiments of the heat transfer
device in sectional, elevation views.
FIG. 2b is a cross-sectional view taken on the line IIb--IIb in the
evaporation zone of the device shown in FIG. 2a.
FIGS. 2c and 2d are a longitudinal cross-sectional view and a
cross-sectional view of wire which is provided with circumferential
grooves, which wire is present on the first and the second tube
wall section 2 and 3, respectively.
FIG. 3b is a sectional view taken on the line IIIb--IIIb of FIG.
3a.
FIG. 4a shows in sectional, elevation view another embodiment of
this invention.
FIG. 4b is a sectional view of the device taken along line IVb--IVb
in FIG. 4a.
FIG. 5 is an elevation view in section of another embodiment of the
device of this invention.
Reference numeral 1 in FIG. 1a denotes a closed cylindrical
container having at one end a first tube wall section 2 and at the
other end a second tube wall section 3 separated from each other by
an intermediate third tube wall section 4. The container 1
comprises a suitably chosen quantity of sodium as a heat transfer
medium and is otherwise evacuated.
On the cylindrical inner wall of the container 1 is present a wire
5 which is wound helically in the axial direction of the cylinder.
The wire comprises grooves which extend transversely to the wire
axis over half the circumference of the wire and which face the
adjoining tube wall surface. The grooves in the wire are shown in
detail in FIG. 1c which is a longitudinal sectional view of the
wire. The turns of the wire 5 in the container 1 engage each other
very closely in this case so that there are very narrow gaps
between the turns.
During operation, liquid sodium absorbs thermal energy through the
first tube wall section 2 serving as an evaporator from a heat
source not shown, as a result of which said, sodium evaporates. Via
successively the narrow gaps between the turns of the wire section
which covers the first tube wall section 2 and the duct inside the
wire turns, sodium vapour then flows to the second tube wall
section 3 (condensor) as a result of the lower vapour pressure
there due to a slightly lower temperature at that area.
The sodium vapour condenses on the second tube wall section while
giving off thermal energy. The condensate then flows through the
grooves in the wire 5 on the basis of capillary action, while using
the surface tension of the condensate, back to the first tube wall
section 2 to be evaporated there again. The third tube wall section
4 constitutes a transport zone.
In the heat transfer devices shown in FIGS. 2 to 5, the same
reference numerals are used for parts corresponding to the device
shown in FIG. 1 except that numerals of FIG. 2 have (') added, FIG.
3 have (") added, FIG. 4 have (r) added, and FIG. 5 have (s) added.
In the heat transfer device shown in FIG. 2a, the turns of wire 5'
readily engage each other. The wire sections which cover the first
and the second tube wall section 2' and 3' have grooves which
extend throughout the circumference of the wire as is shown in
detail in the longitudinal sectional view of FIG. 2c and in a
cross-sectional view of the wire shown in FIG. 2d. The wire section
which covers the third tube wall section 4' on the contrary has
grooves which extend only over a part of the circumference of the
wire. The last-mentioned wire section has fewer and larger grooves
than the wire sections which cover the first and the second tube
wall section 2' and 3'. Since all the wire turns engage each other
mutually, winding is very simple. The continuous row of turns at
the area of the third tube wall section 4' beautifully forms a
partition between sodium condensate and sodium vapour. Sodium
vapour on its way from the first to the second tube wall section
cannot drag along condensate drops of the third tube wall section
4', which would mean a reduction of the heat transfer capacity of
the device. Due to the few coarse grooves in the wire section on
the third tube wall section 4' the condensate flowing through it
will have small flow losses.
The many small circumferential grooves extending transversely to
the wire axis over the circumference of the wire in the wire
section which covers the first tube wall section provide apertures
in the continuous row of turns so that sodium can freely evaporate
via said apertures of the relevant wall section. They furthermore
ensure a large liquid vapour phase surface area so that a large
heat flow can be conveyed through a surface unit of the tube wall
section. Finally they produce a large capillary suction force which
ensures the transport of condensate.
Analogous construction of the wire section which covers the second
tube wall section provides the advantage of an easy removal of
condensate owing to on the one hand the many apertures in the
closed row of turns and on the other hand the large capillary
suction force.
The heat transfer device shown in FIG. 3 comprises a tubular
container 1" which has parts of different diameters and which is
rectangular in cross-section. Instead of one helically wound wire,
two helical springs 6 and 7 are present which remain pressed
against the walls of the container by resilience. The helical
spring 6 covers the first tube wall section 2" while the helical
spring 7 covers the second tube wall section 3" and the third tube
wall section 4". Helical spring 6 only has circumferential grooves
divided over the whole wire length transversely to the wire axis;
helical spring 7 only over the wire section which covers the second
tube wall section 3".
FIG. 4a shows a cylindrical heat transfer device in which the first
tube wall section 2r bounds a cylindrical space which is present
within the dimensions of the heat transfer device. The device is
otherwise the same as that of FIG. 2.
FIG. 5 shows a heat transfer device in which a helical spring 8 is
present in a closed container is which spring comprises
circumferential grooves which extend transversely to the wire axis
and are distributed over the whole length of the wire. Helical
spring 8 is internally hollow. The cavity 9 constitutes a closed
space in which a quantity of argon is present as a filling medium.
When the operating temperature of the heat transfer device is, for
example, 1100.degree.K, the vapour pressure of the sodium in the
otherwise evacuated container 1 is 450 Torr (1 Torr = 1 mm mercury
pressure). By a suitable chosen quantity of argon in the helical
spring 8 it is achieved that at the said high temperature the argon
pressure in the spring is higher than 450 Torr, for example, 2
atmosphere. When the resilient of the helical spring 8 at the
operating temperature of 1100.degree.K is insufficient to ensure
that the helical spring remains engaging the container wall, as a
result of which the operation of the device would be disturbed, the
difference in pressure across the helical spring 8 ensures that the
spring nevertheless remains positively pressed against the
container wall. Should leakage of the helical spring 8 occur, the
outflowing argon as an inert gas will not enter into chemical
reactions with the sodium. The heat transfer device then remains
free from further damage. Of course, all kinds of other embodiments
of the heat transfer device are possible within the scope of the
present invention, in addition to those shown.
When several wires are used in one heat transfer device, said wires
may mutually have different diameters and/or be manufactured from
different materials. Wires having a comparatively small diameter
could then cover the first and the second tube wall section while a
wire having a comparatively large diameter is used for the third
tube wall section. Furthermore, one or more wound wires can be
combined with one or more helical springs in one heat transfer
device.
* * * * *