U.S. patent number 3,630,041 [Application Number 05/014,040] was granted by the patent office on 1971-12-28 for thermodynamic refrigerator.
This patent grant is currently assigned to U.S. Phillips Corporation. Invention is credited to Alexander Daniels, Frits Karel DE Pre.
United States Patent |
3,630,041 |
Daniels , et al. |
December 28, 1971 |
THERMODYNAMIC REFRIGERATOR
Abstract
A cryogenic refrigeration apparatus operable in accordance with
a thermodynamic cycle such as the Vuilleumier cycle, wherein the
hot and cold chambers are physically separated, and the
corresponding hot and cold displacers are driven reciprocally by
separate motors. Proper pressure variations and phase difference
between the motions of the displacers and the gas transported are
maintained preferably by synchronizing the speeds of the different
motors.
Inventors: |
Daniels; Alexander (Briarcliff
Manor, NY), DE Pre; Frits Karel (White Plains, NY) |
Assignee: |
U.S. Phillips Corporation (New
York, NY)
|
Family
ID: |
21763188 |
Appl.
No.: |
05/014,040 |
Filed: |
February 25, 1970 |
Current U.S.
Class: |
62/6; 62/86 |
Current CPC
Class: |
F25B
9/14 (20130101); F02G 1/0445 (20130101); F02G
2244/50 (20130101); F02G 2250/18 (20130101) |
Current International
Class: |
F02G
1/00 (20060101); F02G 1/044 (20060101); F25B
9/14 (20060101); F25b 009/00 () |
Field of
Search: |
;62/6,86 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Wye; William J.
Claims
What is claimed is:
1. Thermodynamic apparatus operable in accordance with the
Vuillemier regenerative cycle with a heat source comprising:
a. a thermal compressor formed of a hot chamber defining therein a
heating space, a hot displacer reciprocally movable in the hot
chamber, first drive means connected to the hot displacer for
driving same, and first heat exchange means for transferring heat
from said heat source into said heating space,
b. a cold finger formed of a cold chamber defining therein a gas
expansion space and being physically separated from the hot
chamber, a cold displacer reciprocally movable in the cold chamber,
and second drive means being connected to the cold displacer for
driving same and being independent of the first drive means, the
expansion space having a lower average temperature than the heating
space average temperature.
c. duct means interconnecting the hot and cold chambers, with a
working medium flowable cyclically through the duct between said
spaces,
d. second heat exchange means associated with the duct for cooling
same by transferring heat from the medium flowing therethrough to
ambient, and
e. a regenerator associated with each displacer through which the
working medium flows.
2. Apparatus as defined in claim 1 wherein the hot and cold
chambers are formed by cylinders having corresponding bores in
which the displacers are reciprocated.
3. Apparatus as defined in claim 1 wherein the drive means are
electric motors which are synchronized to attain the same speeds
and a selected phase difference.
4. Apparatus as defined in claim 1 wherein the first and second
drive means are electric motors, the first drive means is operated
at a higher speed than the second, the apparatus further comprising
valve means synchronized with the drive means for controlling the
gas flow and pressure variations of said gas.
5. Apparatus as defined in claim 1 further comprising a second cold
finger and second duct means interconnecting the second cold finger
with the thermal compressor.
6. Apparatus as defined in claim 1 comprising a second thermal
compressor, and auxiliary drive means interconnecting the first
drive means and the second compressor, the first and auxiliary
drive means being opposed and balanced to minimize vibration.
7. Apparatus as defined in claim 1, further comprising valve means
for controlling communication of each of said chambers with said
duct means, operation of the valves being synchronized with the two
drive means to provide the desired phase difference between the
displacer motion and the pressure variation.
8. Apparatus as defined in claim 1 further comprising an adsorber
connected between said chambers for removing contaminants from the
gas flowing through the adsorber.
9. Apparatus as defined in claim 1 wherein each regenerator is
disposed within a displacer.
10. Apparatus operable in accordance with a thermodynamic
regenerative cycle such as the Vuilleumier and Stirling cycles, and
with a heat source comprising:
a. compression means including a compression chamber defining
therein a compression space, a piston reciprocally movable in the
chamber, and first drive means connected to the piston for driving
same,
b. a cold finger formed of a cold chamber defining therein an
expansion space and being physically separated from the compression
chamber, a cold displacer reciprocally movable in the cold chamber,
and second drive means being connected to the cold displacer for
driving same and being independent of the first drive means, the
expansion space having a lower average temperature than the heating
space average temperature,
c. means for synchronizing the speed of the two drive means at a
selected phase difference,
d. duct means interconnecting the compression and cold chambers,
with a working medium flowable cyclically through the duct between
said spaces,
e. second heat exchange means associated with the duct for cooling
same by transferring heat from the medium flowing therethrough to
ambient, and
f. a regenerator associated with the displacer through which the
working medium flows.
11. Apparatus as defined in claim 10 wherein said drive means are
electric motors.
12. Apparatus as defined in claim 10 wherein the regenerator is
disposed within the displacer.
Description
BACKGROUND OF THE INVENTION
This invention is in the field of cyogenic refrigeration apparatus
and thermodynamic cycles on which such apparatus operate, and
particularly the field of refrigeration means operating on a cycle
such as the Vuilleumier regenerative cycle as related to the
idealized Stirling cycle.
In refrigeration apparatus operating on a Stirling regenerative
cycle, there are typically five interconnected elements, namely a
compression space, a cooler, a regenerator, a freezer, and an
expansion space. In such devices the helium gas, working medium is
first compressed in the compression space, then cooled in the
cooler, and next flowed through a regenerator where additional heat
from the gas is extracted and stored. Upon exiting the regenerator
the gas flows into the expansion chamber where cold is produced and
finally extracted by means of a freezer component. Subsequently,
the gas is returned through the regenerator, where it reabsorbs the
stored heat and flows again to the compression chamber to complete
a cycle.
Although ideally three elements (compression space, regenerator,
and expansion space) are sufficient to explain the operation of
such cycles, in most practical machines, the cooler and freezer
elements have been added in order to effect adequate heat transfer
between the gas in the compression and expansion spaces and the
surroundings; the cooler and freezer elements thus compensate for
the poor thermal contact and heat transfer capability between the
working gas and the two cylinders. In the Stirling cycle apparatus
as thus described, there is established variable volume compression
and expansion spaces having different average temperatures, with a
motor provided to drive the displacers in a suitable phase
relationship, whereby the gas is successively compressed and
expanded.
The Vuilleumier cycle differs from the Stirling cycle primarily in
its means for establishing pressure variations in the gas for
compression and expansion. In known Vuilleumier cycle
refrigerators, there are within a single housing, two chambers and
a connecting duct, a displacer piston reciprocally movable in each
chamber, and a single electric motor with a dual connecting rods
for driving the two displacers at exactly the same speed and in a
90.degree. or other phase difference. Heat is added into one
chamber with a higher gas pressure resulting in the working space,
thus establishing a thermal compressor in substitute for the
mechanical compressor of the Stirling cycle. In this Vuilleumier
device the heated and compressed gas flows from the hot space
through regenerator material in the corresponding displacer,
through the connecting duct which includes heat exchanger means to
transfer heat to the ambient, then through a second regenerator in
the cold chamber displacer, with cold finally produced in the
remote space of the nonheated cylinder.
The pressure variations in the cold volume of this Vuilleumier
device are produced by the motion of the hot displacer in the
following way. If the hot displacer is "down," much of the helium
is in the hot area, the average helium temperature will be high,
and the pressure will be high everywhere in the working space. On
the other hand, if the displacer is "up," very little of the helium
is in the hot area, the average helium temperature will be low, and
the pressure will be low. Therefore, as long as the hot displacer
moves up and down in the correct phase relationship to the motion
of the cold displacer, the required pressure and volume variations
are produced in the cold expansion space, and cold is produced
according to the equation of Q= pdV; this equation defines cold
production per period in the various thermodynamic cycles, with the
same cold produced in a given expansion volume no matter how the
pressure variation is produced.
A further characteristic of the Vuilleumier refrigerator is that
the power required to drive the displacers may be small, since the
only forces on the displacers are those due to the pressure drop of
the helium flowing through them and to the mechanical friction.
Furthermore, since there is a heat input at the hot chamber, and at
the cold finger where an object is cooled, it follows that the heat
rejection to the ambient equals the sum of these amounts, plus the
small amount of heat equal to the motor input.
The above equation for cold production should be considered with
respect to conditions on which it is based, namely the cold
production during one cycle in a volume into which (and out of
which) a gas can flow only via an ideal regenerator. This is the
situation encountered in both the idealized Stirling and
Vuilleumier regenerative cycles, with these cycles differing only
in the way they produce the periodic pressure variations, since the
cold-volume variations are always due to a sinusoidal motion of a
displacer piston. One of the unique features of the Vuilleumier
refrigerator is that its constant volume process with no mechanical
compression, results in low bearing loads, long mechanical like,
and quiet operation; also such construction is compact and has
minimized dead space, as shown in the drawings.
Known Vuilleumier cycle refrigerators are constructed generally as
described above, with the stated features and advantages; however,
such apparatus has a number of major limitations and disadvantages.
Since both hot and cold displacers are contained within a single
housing, it is inherent in the apparatus design that the heat
source applied to the hot chamber is in close proximity to the cold
chamber. In situations where the source of heat is available only
at a point remote from the place where cold production is to be
provided, a long heat pipe would be required to bring the heat to
the hot chamber, with corresponding expense and complications; in
such cases, the Vuilleumier cycle refrigerator would not be
desirable. Furthermore, there are now various situations calling
for cold production in a given location, with the dissipation of
any heat into this area being intolerable. Thus the presence, near
the cold production area, of the heat source, or the hot chamber,
or even a heat pipe would render prior Vuilleumier refrigerators
impractical.
Another limitation in these devices concerns the cyclic pressure
variations of the gas caused by movement of the displacers with a
proper phase difference. To achieve this phase relationship while
cycling the hot and cold displacers at the same speed, known
devices use a single motor with dual connecting rods. Since it has
been established that the cold displacer must be reciprocated
relatively slowly to minimize flow losses therein, a consequence is
an equally slow-running hot displacer and resulting design
inflexibility.
SUMMARY OF THE INVENTION
The present invention is an improvement of the Vuilleumier cycle
refrigerator apparatus which overcomes the various structural and
functional limitations described above in the prior art. To
accomplish these improvements the basic structure of a typical
known Vuilleumier refrigerator has been so significantly altered
that the hot and cold cylinders are physically separated, with an
independent electric motor drive means for each. With this new
arrangement the hot and cold displacers can be operated by motors
having synchronized speeds or different speeds; and both the hot
chamber and the heat source may be located quite remote from the
area of cold production. Where the new apparatus has motors
operable at different speeds, the hot and cold chambers
interconnected by tubes, include valves synchronized with each
displacer, whereby the desired pressure variations in the gas are
obtained. Also connected between the hot and cold sides can be an
adsorber to remove contaminants of the flowing gas stream. In a
further embodiment, a single thermal compressor formed by a
hot-side cylinder, displacer, and electric motor, may cooperate
with a plurality of remote cold fingers. In each of the above
embodiments the cold and hot chambers and their associated
displacers and drive means are designed to be physically separated
and independent of each other, except for interconnecting duct
means.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a schematic view of a prior art Vuilleumier cycle
refrigeration apparatus.
FIG. 2 is a schematic view of apparatus similar to that of FIG.
1.
FIG. 3 is a schematic view of the new split-cycle refrigerator.
FIG. 4 is a further embodiment of the new invention in FIG. 3.
FIG. 5 is a further embodiment of the invention in FIG. 3.
DESCRIPTION OF THE PREFERRED EMBODIMENT
As shown in FIG. 1, the prior art Vuilleumier cycle refrigerator
has a hot chamber 11, a cold finger 12, and a connecting duct 13
and cooler 14. FIG. 2 is similar with hot and cold sides 11' and
12' and a combination duct and cooler 13' and 14'. Within each hot
chamber is displacer 15 and its internal regenerator 16, and within
each cold finger is its displacer and regenerator 17 and 18. A
single electric motor 19 drives the two displacers in FIGS. 1 and 2
at the same speed, in a 90.degree. phase relationship. The apparata
thus described are closed systems, each within a single housing 20.
Disposed about a portion of the hot cylinders 11, 11' is shown a
heat exchanger 21 for transferring heat from an external source
into the hot chamber and heating the gas therein.
As shown in FIG. 1 the cyclic gas flow pattern is as follows. After
the gas is heated in chamber 11 with a resulting pressure increase,
it flows through regenerator 16 to heat exchangers 14 where it is
cooled, then through regenerator 18 to expansion space 12a with
resulting cold production. A freezer element not shown would be
used to transfer the cold to a device or area to be refrigerated
and the gas then returns to complete the cycle.
Motor 19 has two connecting rods 22 and 23 for driving the hot and
cold displacers respectively at the same speed, and at a 90.degree.
phase difference which might be varied as required. In the device
disclosed cold production of 1 watt at 77.degree. K. would be
achieved with a heat input of 115 watts at 1,000.degree. K., 5 watt
motor, and intermediate cooling at 350.degree. K.
The first shown embodiment of the new invention in FIG. 3 has a
thermal compressor 25 and its motor 26, and a separate cold finger
27 with its motor 28. While the motors are physically separated,
they are operated at the same speed, so that the reciprocal
movements of the thermal compressor displacer 29 and the cold
finger displacer 30 will also be identical, but at a suitable phase
difference. One preferable method for attaining synchronized
operation of the motors with a selected phase difference would be
to use electronic control means.
Interconnecting the hot and cold sides 25 and 27 is a single duct
31; with this arrangement the gas will be cyclically moved between
the hot and cold sides with the desired pressure variations, with
no requirement for valves to control the gas flow. Also present is
heat exchanger 32, either separate or part of duct 31, for
transferring heat from an external source into the hot chamber 25
and a second heat exchanger 33 for removing certain heat of
compression before the gas is expanded in the cold finger. Any heat
rejection associated with the thermal compressor and its associated
motor, and any vibrations from these elements may be isolated from
the cold finger, and also may be spaced quite remotely. It is also
possible to replace the thermal compressor 25 with a different,
mechanical compressor, and still retain the other structural
features described above.
A variation of the embodiment of FIG. 3 is shown in FIG. 4 where
motors 40 and 41 for the thermal compressor 42 and the cold finger
43 respectively are run at different speeds, preferably with the
cold finger displacer at a low speed to minimize flow losses and
the hot displacer at a relatively higher speed as determined by
design considerations. When the motors are run at different speeds,
the desired cyclic gas pressure variations will be obtained by
synchronizing valves 44, 45, 46 and 47 with the displacer
movements. These valves are associated with pressure chamber 48
wherein the higher pressure gas is stored and cyclically released
to the cold finger and a low-pressure chamber 48a. Heat exchanger
49 provides cooling for the gas subsequent to its heating and
pressure stage in the hot chamber 42.
A still further embodiment of the present invention is shown in
FIG. 5 where there are two thermal compressors 50 and 51 driven by
a single motor 42. Connected to each compressor is a pair of cold
fingers 53, 54 and 55, 56. Since each of the four cold fingers has
its own electric motor, interdependent of, but synchronized with
the compression drive means 52, there will be cold production by
the cold fingers at a plurality of locations, all remote from the
heat source and from the thermal compressors, without a need for
valves.
In any of the above embodiments an adsorber, 31a may be added in
the connecting duct 31 of FIG. 3 between the hot and cold sides,
for removing contaminants in the gas as it flows cyclically. From
the point of view of flexibility in use, these and other
embodiments may utilize various heat sources, including electrical
heat, propane, and isotopes.
* * * * *