U.S. patent number 3,590,597 [Application Number 04/847,917] was granted by the patent office on 1971-07-06 for cooling apparatus employing the joule-thomson effect.
This patent grant is currently assigned to The Hymatic Engineering Company Limited. Invention is credited to David Neil Campbell.
United States Patent |
3,590,597 |
Campbell |
July 6, 1971 |
COOLING APPARATUS EMPLOYING THE JOULE-THOMSON EFFECT
Abstract
The second stage in a miniature cryogenic two-stage cooler,
working on the Joule-Thomson principle, is supplied with gaseous
refrigerant which passes from a supply under pressure through one
path of a tubular heat exchanger, to an expansion nozzle, after
which the expanded gas returns through the other path of the heat
exchanger to cool the incoming second stage gas. In the first
stage, a precooling refrigerant in liquid form is supplied to a
metering nozzle which, having no heat exchanger, is accommodated
within the heat exchanger of the second stage, and this refrigerant
evaporates to precool the second stage refrigerant. The nozzle of
each stage is automatically controlled to vary the flow of
refrigerant in accordance with the demand for cooling.
Inventors: |
Campbell; David Neil (Redditch,
EN) |
Assignee: |
The Hymatic Engineering Company
Limited (Redditch, EN)
|
Family
ID: |
10396772 |
Appl.
No.: |
04/847,917 |
Filed: |
August 6, 1969 |
Foreign Application Priority Data
|
|
|
|
|
Aug 6, 1968 [GB] |
|
|
37477/68 |
|
Current U.S.
Class: |
62/51.2 |
Current CPC
Class: |
F25B
9/02 (20130101); F25B 2309/023 (20130101); F25B
2309/022 (20130101) |
Current International
Class: |
F25B
9/02 (20060101); F25b 019/00 () |
Field of
Search: |
;62/222,514,467 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Perlin; Meyer
Claims
What we claim as our invention and desire to secure by Letters
Patent is:
1. Cooling apparatus of the type in which cooling is produced by
expansion, through a nozzle, of a refrigerant in gaseous form under
pressure, which before expansion at the nozzle is at a temperature
below its inversion temperature, including two stages in the second
of which a second stage refrigerant from a supply in gaseous form
is passed through one path of a heat exchanger, expanded through an
expansion nozzle and passed back through the other path of the heat
exchanger to cool the incoming second stage refrigerant, a
precooling first stage in which a precooling refrigerant is
supplied in liquid form under pressure through a metering nozzle to
a space at reduced pressure where it evaporates to cool the second
stage refrigerant before the latter passes through the heat
exchanger, and means for automatically controlling the effective
area of the nozzle of each stage so that the amount of refrigerant
flowing through each nozzle may be governed by the requirement of
cooling at that stage.
2. Cooling apparatus as claimed in claim 1 in which the apparatus
is generally of tubular form, the heat exchanger comprising a
finned tube wound to helical form with the second stage refrigerant
flowing through it in one direction and past its outside in the
opposite direction, the second stage expansion nozzle being at the
cold end of the heat exchanger while the first stage metering
nozzle is enclosed within its warm end.
3. Cooling apparatus as claimed in claim 2 in which the second
stage expansion nozzle includes a needle valve controlled by a
bellows the pressure upon which is determined by said automatic
control means which includes a sensor comprising a vapor bulb with
an extended tail extending down to a pool of liquefied
refrigerant.
4. Cooling apparatus as claimed in claim 3 in which the first stage
metering nozzle includes a needle valve controlled by a bellows the
pressure upon which is determined by said automatic control means
which also includes a sensor bulb secured to a curved plate fitting
within the body of the heat exchanger at about the level of the
metering nozzle so as to respond primarily to the temperature of
the heat exchanger at that part of the apparatus.
5. Cooling apparatus as claimed in claim 4 in which a cup is
secured to the inside of the body of the heat exchanger, just below
the metering nozzle, to collect liquid refrigerant formed by the
first stage refrigerant, and at the corresponding part of the
length of the heat exchanger the helical finned tube is not finned
and is soldered to the outer surface of the heat exchanger tube so
as to transmit heat from the second stage refrigerant in the cup
within the body.
6. Cooling apparatus as claimed in claim 5 wherein the refrigerant
is Freon in liquid form supplied under pressure and at atmospheric
temperature.
Description
This invention relates to cooling apparatus of the type employing
the Joule-Thomson effect, that is to say in which cooling is
produced by expansion, through a nozzle, of a refrigerant in
gaseous form under pressure, which before expansion at the nozzle
is at a temperature below its inversion temperature.
The invention is particularly, though not exclusively, concerned
with such coolers which are of miniature size, for example for
cooling infrared detectors to the temperature of liquid nitrogen.
In a typical construction the complete cooler is largely situated
within a cylindrical heat exchanger having a length of between 2
and 3 inches and a diameter of about a third of an inch and wound
with a helical coil of finned tubing of which the diameter over the
fins is less than one-twentieth of an inch. In general it is a
requirement not only that the cooler itself should be of extremely
small size, but in addition that the supply of compressed
refrigerant required should also be as small and light as
possible.
It is known that each refrigerant has a temperature, known as its
inversion temperature, at which no cooling is produced by the
Joule-Thomson effect, that is to say by expanding the refrigerant
gas through an expansion nozzle. Above the inversion temperature
such expansion actually produces a rise of temperature, and it is
only below it that it produces a cooling effect. Moreover at
temperatures only slightly below the inversion temperature the
cooling effect is correspondingly slight and if a substantial
cooling effect is required the expansion must be carried out from a
temperature substantially below the inversion temperature.
Thus in the case of Joule-Thomson coolers employing refrigerants
with an inversion temperature below atmospheric temperature it is
essential to employ more than one stage, so as to precool the
refrigerant before expansion, but even in the case of refrigerants,
such as air or nitrogen, having an inversion temperature
substantially above atmospheric temperatures, the efficiency can be
considerably improved by employing a precooling stage. This,
however, has generally not been done in coolers of the type with
which the invention is concerned since the space available has not
been sufficient to accommodate a precooling stage.
According to the present invention cooling apparatus includes two
stages in the second of which a second stage refrigerant from a
supply in gaseous form is passed through one path of a heat
exchanger, expanded through an expansion nozzle and passed back
through the other path of the heat exchanger to cool the incoming
second stage refrigerant, and a precooling first stage in which a
precooling refrigerant is supplied in liquid form under pressure
through a metering nozzle to a space at reduced pressure where it
evaporates to cool the second stage refrigerant before the latter
passes through the heat exchanger, the effective area of the nozzle
of each stage being automatically controlled in accordance with a
parameter depending upon the relationship between cooling supplied
and cooling demanded at that stage.
In one form of the invention the apparatus is generally of tubular
form, the heat exchanger comprising a finned tube wound to helical
form with the second stage refrigerant flowing through it in one
direction and past its outside in the opposite direction, the
second stage expansion nozzle being at the cold end of the heat
exchanger while the first stage metering nozzle is enclosed within
its warm end.
In the above-noted cooling apparatus designed, for example, for
cooling infrared detectors to the temperature of liquid nitrogen,
the effective area of the nozzle of a Joule-Thomson cooler is
automatically controlled, as by means of a needle valve, in
accordance with a parameter depending on the relationship between
cooling supplied and cooling demanded. This may be in accordance
with a temperature at a point in the cold end of the cooling
apparatus. In general, however, the apparatus will serve to produce
a pool of liquid refrigerant, generally at atmospheric pressure,
and in this case there cannot be any variation of temperature so
long as the liquid is in equilibrium with its vapor. Thus in the
preferred arrangements described, the control is not directly in
accordance with the temperature of the refrigerant but in
accordance with the level of the liquid refrigerant which comes
into contact with a sensor as the level rises, and controls the
temperature of the sensor. Other arrangements may be employed in
which the control is in accordance with some other or intermediate
function depending upon the supply and demand for cooling, for
example the sensor may have an extended tail affording a path for
the flow of heat to the liquid refrigerant, the length of which
path varies with the level of refrigerant. Again the sensor may be
in heat exchange relationship with parts of the apparatus above the
pool of liquid refrigerant so that its temperature will depend
partly upon the level of liquid refrigerant and partly on the
temperature of the vapor escaping from the nozzle.
In one arrangement in accordance with the present invention the
second stage expansion nozzle is arranged and controlled as
described above and includes a needle valve controlled by a bellows
the pressure upon which is determined by a sensor comprising a
vapor bulb with an extended tail extending down to the pool of
liquefied refrigerant. The first stage is generally similar but in
this case the sensor bulb is secured to a curved plate fitting
within the body of the heat exchanger at about the level of the
metering nozzle so as to respond primarily to the temperature of
the heat exchanger at that part of the apparatus. Just below the
metering nozzle a cup is secured to the inside of the body of the
heat exchanger to collect liquid refrigerant formed by the first
stage refrigerant, and at the corresponding part of the length of
the heat exchanger the helical finned tube is not finned but is
soldered to the outer surface of the heat exchanger tube so as to
transmit heat from the second stage refrigerant within it to the
liquified first stage refrigerant in the cup within the body.
The invention may be put into practice in various ways but one
specific embodiment will be described by way of example with
reference to the accompanying drawing which shows a two-stage
cooling device.
In this embodiment the invention is applied to a two-stage cooler
of miniature size, perhaps 3 inches in length and one-third inch in
diameter comprising two stages. The first, precooling, stage is
supplied with Freon which is stored in liquid form, under pressure
but at atmospheric temperature, and is admitted past a metering
orifice to a space where it can expand to atmospheric pressure,
thereby effecting precooling. It operates with nitrogen in gaseous
form under pressure which is fed through the inner path of a
helical tube heat exchanger to an expansion nozzle where it expands
and cools due to the Joule-Thomson effect, producing a pool of
liquid nitrogen, while the remaining gas escapes by the outer path
of the heat exchanger, i.e. past the outside of the helical finned
tube, cooling the incoming nitrogen.
The cooling apparatus is of elongated form, and for purposes of
description it will be assumed that it is placed vertically with
its cold end at the bottom. The apparatus includes an annular heat
exchanger 10 comprising a tubular body 11 around which is helically
wound a finned coiled tube 12. An external coaxial tube 13, which
may be the inner wall of a Dewar flask, is located around the
finned coil and the space 14 between the body and the external tube
provides a path for exhaust gas flowing past the fins to cool the
incoming high-pressure working fluid within the helical tube. The
lower end of the external tube is closed to provide a reservoir
(not shown) in which the liquid working fluid can accumulate. This
lower end may be combined with the device to be cooled so that the
liquid nitrogen is in fact in contact with that device. The upper
end of the helical finned tube 12 communicates with a lateral
coupling 18 for connection to the supply of nitrogen under
pressure. Its lower end communicates with an expansion nozzle 22
which is arranged to be controlled by means of a needle valve 23
which is itself controlled by a bellows 24.
Thus at its lower end the tubular body of the heat exchanger has
secured in it a stout metal ring 28. Secured to a point under this
ring, and thus offset from the axis of the heat exchanger, is the
expansion nozzle 22, while a sensor bulb 30 depends from a
diametrically opposite point. To support the expansion nozzle 22 a
threaded socket 32 is secured to the ring and receives the upper
end of a screwed sleeve 33 on the lower end of which is threaded a
screwed plug 34 in which the expansion nozzle 22 is formed. The
screwed sleeve also serves to retain a porous plug 35 or filter
through which the working fluid is compelled to pass on its way to
the expansion nozzle 22 so as to condense and filter out any
impurities which might otherwise block the expansion nozzle.
The bellows 24, situated coaxially within the lower part of the
tubular body 11 of the heat exchanger, has its lower end secured to
the ring 28 while its upper end is closed by and secured to a
tubular operating member 25 which extends down through it and
through the ring and at its lower end carries the moving part of a
valve incorporating the floating needle valve 23. The upper end of
the needle valve projects into the expansion orifice while its
lower end is of conical form engaging a seating formed in a screwed
plug 26 threaded into a thimble 27 which is rigidly secured as by
welding to the lower end of the tubular operating rod 25. The
thimble has secured to it a shroud 39 in the form of a partial cage
formed of wire gauge which allows free escape of exhaust vapor
while intercepting any liquid droplets to prevent them from
impinging on the sensor. The tubular operating rod 25 is provided
with an S-shaped guide blade 29 serving to keep it centered and
prevent it from being tilted by the offset pressure on the needle
valve.
The sensor bulb 30 communicates through a hole in the ring 28 with
the interior of the tubular body of the heat exchanger surrounding
the bellows, so that the pressure in the vapor bulb of the sensor
is communicated to the outside of the bellows, and as the pressure
rises it tends to push the bellows down, withdrawing the needle
valve 23 from the expansion orifice 22 and increasing the flow of
refrigerant to increase the amount of cooling. The sensor bulb
terminates a little below the level of the orifice and is provided
with an extended tail 31 of metal projecting down some distance
further. Thus as the level of liquid refrigerant rises it first
comes into contact with the end of the extended tail so that heat
flowing from the sensor bulb has to flow through its whole length.
As the level of liquid refrigerant rises the extent of cooling of
the sensor bulb increases progressively, giving a smooth control of
the needle valve, and preventing hunting.
In accordance with the present invention the upper part of the heat
exchanger contains a first stage precooler supplied with Freon kept
liquid under pressure. The first stage is provided with a control
valve 53 which constructionally is very similar to that of the
second stage, although it should be noted that in this case it is
merely a metering valve for liquid, and not an expansion valve
employing the Joule-Thomson effect as in the second stage. The
first stage valve is situated coaxially with the heat exchanger and
cooperates with a seating 54 carried by the lower end of an
admission tube 55 the upper end of which is secured in a head 56 at
the top of the exchanger and communicates with a lateral coupling
57 through which liquid Freon is supplied to it. As in the second
stage a thimble 61 seating the lower end of the needle valve 53, is
carried at the lower end of a tubular operating member 62 the upper
end of which is secured to the upper end of a bellows 63. In this
case the bellows is offset from the axis of the heat exchanger and
is accommodated in a chamber surmounting the head 56 at the top of
the heat exchanger. Thus the operating member extends up on one
side of the tubular inlet pipe 55 carrying the seating 54 at its
lower end, while at a diametrically opposite position a tube 67
forming a sensor bulb 69 extends down from an opening 70 in the
head and has its lower end flattened and secured to a curved shoe
72 engaging the inner face of the tubular body of the heat
exchanger. The sensor bulb 69 contains a volatile liquid, for
example Freon, so that the outside of the bellows 63 is subjected
to its vapor pressure which varies in accordance with the
temperature of the heat exchanger in the region of the first-stage
orifice formed by the seating 54.
Within the tubular body of the heat exchanger, just below the first
stage orifice, there is mounted a cup 75 the cylindrical wall of
which is in heat exchange relationship with the body of the heat
exchanger and which accommodates any Freon which may be liquefied
by the first stage. The cup contains a perforated heat collector 76
of tubular form so as to assist in transmitting heat from the body
of the heat exchanger to any liquid Freon in the cup.
The part of the helical tube 12 surrounding the cup is deprived of
its fins and wound in a close-pitched helix 77 round the body of
the heat exchanger to which it is soldered so as to provide
effective heat exchange between it and the cup.
It is believed that the operation of the apparatus will be clear
from the description given above. In an apparatus having no
automatic control it is of course necessary to provide a flow of
refrigerant sufficient to provide for the least advantageous
conditions, that is to say when the maximum cooling is required by
the load and the ambient temperature is at a maximum. Under other
conditions a much smaller flow of refrigerant would suffice for
requirements, and accordingly the amount of refrigerant that must
be provided in the supply is in fact far greater than is necessary.
Thus considerable economy is possible by providing automatic
control even of a single stage Joule-Thomson cooler. As indicated
above, however, the efficiency of a Joule-Thomson cooler is rather
low if the refrigerant starts at a temperature only a little below
the inversion temperature, and hence in these conditions waste of
refrigerant can still occur even though there is automatic control.
The present arrangement, by providing precooling, increases the
efficiency of the Joule-Thomson second stage and thereby economizes
in the supply of compressed nitrogen, while adding little or
nothing to the bulk or weight of the cooler. In this case the
automatic control is at least equally important in economizing the
supply of liquid Freon. This is particularly the case since in
normal ambient temperatures the precooling may not be required,
since the exhaust nitrogen from the second stage may sufficiently
precool the incoming nitrogen for that stage to give efficient
operation of the Joule-Thomson expansion cooling. Thus the
precooling by liquid Freon is primarily required when the apparatus
is used at ambient temperatures where the efficiency of
Joule-Thomson cooling would otherwise diminish in a single stage
cooler.
* * * * *