U.S. patent number 3,696,636 [Application Number 04/815,991] was granted by the patent office on 1972-10-10 for method and apparatus for cooling liquids.
Invention is credited to Gaston M. Mille.
United States Patent |
3,696,636 |
Mille |
October 10, 1972 |
METHOD AND APPARATUS FOR COOLING LIQUIDS
Abstract
A process for cooling a fluid circulating in contact with one
face of a heat exchange wall, by cooling the other face of the wall
with a cryogenic liquid sprayed under pressure and by means of
residual gases resulting from the evaporation of this liquid. An
exchanger for carrying out this process includes a tube placed in a
heat-insulated enclosure, in which circulates a fluid to be cooled
and on the walls of which a cryogenic liquid is sprayed. The
exchanger includes means for placing a cryogenic liquid under
pressure and a flow-regulating valve in the pressure line
controlled by a thermostat located at the exchanger outlet.
Inventors: |
Mille; Gaston M. (13 Marseille,
8e, FR) |
Family
ID: |
26214868 |
Appl.
No.: |
04/815,991 |
Filed: |
April 14, 1969 |
Foreign Application Priority Data
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Feb 21, 1969 [FR] |
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6922190 |
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Current U.S.
Class: |
62/399; 62/50.4;
62/389; 165/163; 62/51.1; 165/160 |
Current CPC
Class: |
F28D
7/024 (20130101); F28D 7/106 (20130101); F28D
7/022 (20130101); F17C 3/085 (20130101); F25B
19/005 (20130101); F17C 2221/014 (20130101); F28D
2021/0033 (20130101); F17C 2270/0509 (20130101) |
Current International
Class: |
F28D
7/10 (20060101); F28D 7/02 (20060101); F28D
7/00 (20060101); F17C 3/00 (20060101); F17C
3/08 (20060101); F25B 19/00 (20060101); B67d
005/62 () |
Field of
Search: |
;165/163,156,154,159,160
;62/514,513,98,52,53,399,396,393,64 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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26,027 |
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Mar 1923 |
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FR |
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608,465 |
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Apr 1926 |
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FR |
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697,375 |
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Oct 1930 |
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FR |
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357,824 |
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Dec 1961 |
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CH |
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Primary Examiner: Davis, Jr.; Albert W.
Claims
I claim:
1. A heat exchanger comprising a cryosat having a central cavity
open at one end thereof, a pipe line disposed axially of said
cavity and closed at the end opposite said opening, said line being
connected at the other end to a source of cryogenic liquid under
pressure, said line being pierced over a part of its length with
small diameter orifices through which the cryogenic liquid is
sprayed, an exchanger coil in which the fluid to be cooled
circulates and disposed in the central cavity of said cryostat
around said pipe line in sufficiently close proximity with a
portion of said pipeline for cryogenic liquid sprayed from said
orifices to impinge upon said coil as a liquid for evaporation
thereat, and means directing evaporated cryogenic liquid along a
further portion of said coil for maximized cooling of fluid
circulating through the coil.
2. A heat exchanger according to claim 1 further including means
defining an inner chamber and a surrounding communicating annular
chamber, said coil being formed of two parts in series, said first
part disposed at the end where the fluid to be cooled arrives and
formed of physically separated turns arranged in said annular
chamber, and a second part disposed in said inner chamber in
connection with an exit pipe and formed of contiguous turns of the
same diameter arranged around the end of the central pipeline
pierced with atomization orifices whereby said liquid evaporates
upon striking said second coil part to form cryogenic gas that
flows into said annular chamber over said first coil part.
3. A heat exchanger according to claim 1 in which the coil is
constituted of two parts in series, a first part being disposed at
the end where the fluid to be cooled arrives, and formed of
spaced-apart turns arranged in an annular space which is delimited
by the inner wall of a cryostat and a cylindrical screen and a
second part being disposed at the end where the cooled fluid leaves
and formed of joined turns of the same diameter arranged around the
central pipe pierced with atomization orifices, the diameter of the
coil being such that the fluid to be cooled circulates in a
turbulent regime and the surface of the first part of the coil is
between 40 times and 60 times the total surface of the second part
of the coil.
Description
The object of the present invention is to provide a process for
cooling a fluid by means of atomized cryogenic liquids and to
provide exchanger devices, and installations equipped with these
exchangers for putting this process into practice.
By "cryogenic liquids" are meant gases liquefied at low temperature
under atmospheric pressure, e.g., liquid nitrogen or liquid carbon
dioxide.
One of the aims of the present invention is to use, as source of
heat, the heat of vaporization of a cryogenic liquid and the heat
of reheating of the gases coming from the vaporization of this
liquid, with a good thermal yield.
Another aim of the present invention is to regulate precisely the
outlet temperature of the cooled fluid by acting on the flow of the
cryogenic liquid.
Another aim of the present invention is to be able to cool
industrially a fluid to very low temperatures and in a large range
of temperatures, e.g., between 0.degree. and -190.degree. , using
liquid nitrogen.
Another aim of the present invention is to use as a cold-producing
agent, a liquefied neutral gas, e.g., nitrogen or carbon dioxide,
which eliminates the risks of contamination of the cooled fluid as
a result of an accidental contact with the cold-producing agent.
This advantage is important for the cooling of certain fragile
products, e.g., physiological liquids, food products,
pharmaceutical products. In the chemical industry or in the field
of atomic energy, an accidental contact in an exchanger between the
cooled fluid and the fluids that are usually used to transport the
heat may involve chemical reactions of even explosions. For this
reason, double-tube exchangers which have a poor efficiency must be
used or else an intermediate fluid which does not run the risk of
reacting with the fluid to be cooled following an accidental
contact must be cooled in a first exchanger, and then this
intermediate fluid must be used in a second exchanger. The use of a
liquefied neutral gas as a heat producing agent according to the
present invention permits eliminating these expensive
precautions.
According to the process of the present invention, a fluid
circulating in contact with one face of a heat-exchange wall is
cooled by placing the other face of this wall in contact with a
sprayed or atomized cryogenic liquid and with the gases from the
vaporization of this liquid.
The spraying of the cryogenic liquid, i.e., the atomization into a
mist of fine droplets, is obtained by projecting the liquid under
pressure through small-diameter orifices. The wall to be cooled is
placed opposite these orifices and the liquid droplets strike this
wall, in contact with which they evaporate.
The atomization increases the contact surface of the liquid and the
wall, in such a way that the evaporation is instantaneous and it
becomes possible to rapidly modify the exchanged calorific power by
regulating the liquid flow. The temperature of the cooled fluid
can, therefore, be regulated with precision. The cold gases from
the evaporation of the cryogenic liquid flow away at the contact of
the exchange wall by absorbing calories for their reheating. The
gases flow away counter-current to the liquid to be cooled, so that
one recovers a considerable part of the large calories or heat
corresponding to the heating of the gases between the evaporation
temperature of the liquid and a temperature close to the inlet
temperature of the fluid to be cooled.
According to one characteristic of the present invention, an
exchanger for putting the process into industrial practice is
composed of elements mounted in parallel, each element being
constituted of three concentric tubes. The central tube is
connected by one of its ends to a source of cryogenic liquid under
an effective pressure between 2 bars and 10 bars. The other end of
the tube is plugged and a part of the periphery of the tube is
pierced with small-diameter orifices through which the cryogenic
liquid is sprayed. The middle tube is the exchanger tube. It is
open at one of its ends for the escape of the residual gases. The
exterior tube is insulated and the fluid to be cooled circulates
between the two ends in a direction opposite to the direction of
outflow of the residual gases. The exchanger tube is made of a good
heat-conducting metal, e.g., copper or stainless steel. Preferably,
fins of the same metal, in helical shape, are fixed to the interior
and exterior walls of the exchanger tube. To improve the
atomization, each orifice of the central tube may be equipped with
an atomizing nozzle of a conventional configuration.
According to another characteristic of the present invention, a
second type of exchanger for putting the described process into
industrial practice is composed of a cryostat, i.e., a double-wall
chamber with vacuum in between. The vacuum is at least
10.sup.-.sup.2 torr, and preferably 10.sup.-.sup.4 torr. The
cryostat is, preferably, the super-insulated type, i.e., its
interior wall is lined with a shield reflecting radiated heat. The
cryostat is made of two independent parts, coupled water-tight,
using two flanges and a collar.
The cryostat comprises a central cavity communicating with the
outside through a neck. Along the axis of this central cavity is
arranged a pipe line, plugged at one of its ends, the other end
being connected to a source of cryogenic liquid under pressure. A
part of the length of this pipeline is pierced with small-diameter
orifices through which the cryogenic liquid is atomized.
The fluid to be cooled circulates in a coil arranged in the
cryostat cavity.
According to one characteristic of this exchanger, the coil is
constituted of two parts in series. The first of these parts, in
the direction of flow of the fluid, is formed of separate single
turn coils arranged in an annular space delimited by the inner wall
of the cryostat and a circular screen. The residual gases from the
vaporization of the cryogenic liquid circulate in this space,
between the turns of the coil, before escaping through the neck of
the cryostat.
The second part of the coil is formed of contiguous turns, arranged
in a layer around the part of the central pipe line pierced with
atomizing orifices. The atomized cryogenic liquid is projected
against the half-periphery of the coil aimed toward the center and
evaporates in contact with the coil.
According to one characteristic of the present invention, the
surface of the first part of the coil is between 40 and 60 times
the total surface of the second part of the coil.
According to another characteristic of the present invention, a
device for cooling a fluid according to the described process
comprises in combination, a supply reservoir containing a cryogenic
liquid, a small-capacity auxiliary buffer-reservoir, means for
transferring the cryogenic liquid into the buffer-reservoir, means
for keeping the cryogenic liquid in the buffer-reservoir at a
constant pressure between 2 bars and 10 bars, a cooler-exchanger of
one of the types described in the preceding, a heat-insulated pipe
line connecting the buffer-reservoir to the central piping of this
exchanger, and a flow-regulating valve of a type capable of
operating at the temperatures of the cryogenic liquid placed on
this pipe line whose opening is modulated by an electronic device
with derivative action, proportional and integral, controlled by a
temperature sensitive element placed on the coil at the outlet of
the exchanger.
There is provided means for keeping the cryogenic liquid under
pressure in the buffer-reservoir as, for example, a cryogenic pump
immersed in the supply reservoir and controlled automatically by a
pressure sensitive device placed in a buffer-reservoir.
The various characteristics and advantages of the present invention
will appear in the following description of several methods of
realization of the objects of this invention given by way of
example, without limiting character, with reference to the attached
drawings wherein:
FIG. 1 is a central sectional view of an exchanger element in
accordance with this invention;
FIG. 2 is a central sectional view of an exchanger placed in a
cryostat; and
FIG. 3 is a schematic view of a cooling system incorporating the
present invention.
The exchanger element represented in FIG. 1 is composed of three
concentric tubes. The central tube 1, of small diameter, is
connected at the lower end thereof to a source of cryogenic liquid
under pressure, as indicated by the arrow. It is pierced, over at
least a part of its length, with small diameter orifices 4 through
which the cryogenic liquid is sprayed. The upper end of the tube 1
is closed.
The middle or central tube 2 may be denominated as an exchanger
tube formed of a good heat-conducting metal. The tube 2 is closed
at its lower end 6. The upper end 7 of the tube 2 is open to
exhaust the residual gases resulting from evaporation of the
cryogenic liquid.
Fixed to the interior and exterior walls of central tube 2 are fins
10 made of a good heat-conducting metal and preferably having a
helical configuration. The purpose of these fins 10 is to increase
the exchange surface, to retard the rate of escape of the residual
gases and to increase the length of travel of the fluid to be
cooled.
An outside tube 3 is disposed about the above described elements
and is covered on the outside thereof with a heat insulator 11. The
outer tube 3 is closed at both ends. The upper part of tube 3 is
connected to an inlet line 8 for entrance of the fluid to be
cooled. At the lower part of tube 3, the cooled fluid passes out
through a pipe line 9. The operation of this exchanger element is
as follows.
The cryogenic liquid is introduced into the tube 1 and is projected
onto the inner walls of tube 2 as a mist of fine droplets. It
evaporates in contact with these walls, obtaining its heat of
evaporation from the fluid to be cooled through the wall of the
exchanger tube 2. The residual gases of the cryogenic liquid become
heated by circulating in contact with the wall of the exchanger
tube. The circulation of the gases and the fluid to be cooled
occurs counter-current. When more refrigeration power is required
than can be provided by one exchanger element, several elements are
connected in parallel; the central tubes being connected to a
common collector. Likewise, the connections for intake 8 and exit 9
of the fluid to be cooled are connected to two collectors. A
flow-regulating valve is placed on the cryogenic liquid inlet pipe
line and its opening is modulated by an electronic device
controlled by a temperature sensitive device placed on the outlet
of the cooled liquid.
Reference is now made to FIG. 2 representing a further embodiment
of this invention incorporating an exchanger of a preferred type
having heat insulation which considerably reduces heat losses
through the walls. A cryostat, of a conventional design is shown to
be constituted of two walls, an external wall 12 and an internal
wall 13 between which is created a vacuum between 10.sup..sup.-2
torr and 10.sup..sup.-4 torr. This cryostat is of the
super-insulated type, i.e., the outside face of wall 13 is covered
with a reflecting screen 14 intended to stop heat radiation. This
cryostat has the general shape of a cylindrical bottle equipped
with an open neck and is formed of two parts, each forming a
water-tight enclosure. These two parts are joined through the
intermediary of two flanges 15 and 16 welded to the two walls. The
flange 16 carries a groove 17 in which is placed a toric joint 18.
The two clamps are held in water-tight contact by a collar 19 which
engages the external conical face of the flanges.
An adsorbent material 20 is placed between the two walls in contact
with the inner wall. The function of this material is to maintain
the vacuum, adsorbing the molecules from the degassing of the
walls.
Two valves 21 and 22 separately extend through the outer walls of
each of the parts of the cryostat to avoid bursting of the latter
in case of an abnormal increase in the pressure. These valves at
the same time serve to connect a vacuum pump for evacuating the
cryostat. Circular hoops 23 are arranged about the periphery of the
cryostat. The bottom of the cryostat is convex and through its
periphery rests on a flat support 24.
A pipe line 27 is arranged along the axis of the cryostat. It is
closed at the lower end thereof. It is connected by its upper end
to a source of cryogenic liquid under pressure and is
heat-insulated. For example, the pipe is constituted, from the top
down to a horizontal screen 28, by a double-wall tube with a vacuum
in between.
The part of pipe line 27 located below the screen 28 is pierced
with small diameter orifices 29 through which the cryogenic liquid
is sprayed.
The fluid to be cooled enters the cryostat through the neck by a
pipe line 30 and exits through a pipe line 31. Three coils are
arranged in an annular space delimited by the inner wall of the
cryostat and by a cylindrical screen 33. These three coils are
connected in parallel by a collector 32 to the pipe line 30. The
three coils are arranged along three levels of different diameter.
The separate turns do not touch. The residual gases from the
evaporation of the cryogenic liquid circulate, rising between the
turns, and escape through the opening of the neck.
Each of the three coils is extended by a second part formed of
joined turns 34 arranged along helices of the same diameter, which
encircle the lower end of the tube 27 pierced with atomization
orifices. At the upper part, the three coils are joined in parallel
by a collector 35 to the outlet 31. A temperature sensitive device
36, e.g., a thermocouple, is placed on collector 35 which
corresponds to the zone where the temperature of the fluid to be
cooled is the lowest.
The coil section is chosen as a function of the flow of the fluid
to be cooled and the number of coils mounted in parallel, so that
the fluid circulates in a turbulent mode inside the coil at a speed
greater than 2 meters per second.
With such an exchanger operating with liquid nitrogen one has an
exchange coefficient, per square meter of wetted surface of the
coil and per hour, equal to 2,200 kilocalories in the zone
operating in the gaseous phase, and equal to 22,000 kilocalories in
the zone placed in the liquid phase. In this zone, the effective
exchange surface of the coil is equal to half the total surface,
since only one half of the tubes receives the projections of liquid
droplets. Experience shows that the best general yield is obtained
when the total refrigerating power of the exchanger is divided into
two equal parts between the gas and liquid phase zones. The surface
of the coils placed in the annular space operating in the gaseous
phase is equal to about 50 times the total surface of the coil
placed inside the screen 33. In practice, the ratio of the surfaces
will be between 40 times and 60 times.
The section of passage of the gases around the turns of the coil in
the annular space is calculated in such a way, that the gases
circulate in a turbulent manner at a speed greater than 6 meters
per second for a normal operating condition of the exchanger. A
stack of perforated screens 37 is placed across the neck to support
the tubes and to retard the speed of escape of the residual
gases.
The provision of the cryostat in two parts allows placing the
interior equipment in the lower part of the cryostat which is then
capped by the upper part. Maintenance operations can be carried out
inside the cryostat without destroying the vacuum in the two halves
of the latter.
FIG. 3 represents schematically the assembly of a cooling
installation in an application specific to the clarification of
wines. The installation unit is constituted by a supply reservoir
44 containing liquid nitrogen at atmospheric pressure. In this
nitrogen is immersed a pump 45, of a known model, suitable for
operating at the temperature of -195.degree. .
This pump delivers the liquid nitrogen to a buffer-reservoir 46 of
small capacity. A pressostat or pressure responsive device 47,
placed on this reservoir, controls the start and stop of pump 45
and maintains in the reservoir an effective pressure on the order
of 5 bars.
The buffer reservoir 46 is connected to the central pipe line of
exchanger 42 by a heat-insulated conduit, e.g., a double-jacketed
tube with a vacuum in-between. A flow-regulating valve 48, of a
type that can operate at the temperature of liquid nitrogen, is
placed in this pipe line. The opening of this valve is modulated by
a device 49 controlled by the temperature responsive device 50
placed in the exchanger. The temperature responsive device is a
type that converts the temperature to voltage e.g., a thermocouple.
The device 49 is an electronic device which compares this voltage
with a reference voltage proportional to the outlet temperature
desired, which has been set. The voltage difference is amplified.
If the valve 48 is pneumatic, the potential difference acts on a
pressure converter with derivative action, proportional and
integral, which modulates the opening of the regulating valve 48. A
branch of valve 48, equipped with an electrovalve 51, is provided
for placing of the exchanger into rapid operation.
The device represented by FIG. 3 is an application to the
clarification of wines. It is known that the tartaric acid
contained in wine precipitates when the temperature falls. In the
case of sparkling wines, in particular champagne, since the bottles
can no longer be unstoppered before consumption, it is necessary to
cool the wine in the neighborhood of the freezing temperature
before the bottling. The wine, at ambient temperature, is contained
in a container 40. It is pumped by a pump 41 and, after having
passed through the exchanger, it is collected in a container
43.
The regulating device 49 is set at a temperature very slightly
higher than the freezing temperature of the wine, e.g., one-tenth
of a degree higher. The experiments carried out show that a very
stable temperature of the wine is obtained at the outlet of the
exchanger, the variations being less than one-thirtieth of a
degree.
The advantages of the present invention are as follows: The cost of
installation of a cooling device is reduced with respect to that of
existing refrigerating machines.
Maintenance costs are reduced.
It is possible to cool to very low temperatures, and the same
device permits operating in a very broad temperature range, e.g.,
from 0.degree. to -190.degree., with liquid nitrogen. This
advantage is important to research laboratory equipment. It allows
subjection of a circulating fluid to substantial thermal
shocks.
By using as cryogenic liquid neutral liquefied gases, such as
nitrogen or carbon dioxide, any fluid whatsoever to be cooled can
be caused to pass directly into the exchanger without risking
contamination of the latter as a result of an accidental contact
with the cooling agent. The refrigerating powers per unit of
surface are high, which permits realizing exchangers of small size.
The installations are noiseless and can be placed directly on the
operating sites.
As a result of the rapidity of the heat exchanges in the liquid
phase zone, it is possible to affect the outlet temperature of the
fluid very rapidly by regulating the flow of cryogenic liquid. The
result of this is the possibility for very precise temperature
control which permits specific applications, such as e.g., the
clarification of wines.
When the exchanger is charged with liquid nitrogen, it is possible,
for certain applications, such as e.g., the cold preservation of
food products or physiological liquids, to use residual gases as
the neutral atmosphere in which these cooled products are placed,
which improves their preservation.
Tests conducted with an exchanger of the cryostat type, charged
with liquid nitrogen at an effective pressure of 3 kilos per square
centimeter and cooling a fluid to the temperature of -20.degree.,
have shown that the refrigerating yield was 80 kilo-large calories
per liter of liquid nitrogen.
* * * * *