U.S. patent application number 12/425719 was filed with the patent office on 2009-10-22 for co2 refrigeration unit.
Invention is credited to Serge DUBE.
Application Number | 20090260389 12/425719 |
Document ID | / |
Family ID | 41198743 |
Filed Date | 2009-10-22 |
United States Patent
Application |
20090260389 |
Kind Code |
A1 |
DUBE; Serge |
October 22, 2009 |
CO2 REFRIGERATION UNIT
Abstract
A refrigeration unit comprises a CO.sub.2 refrigeration circuit
having a CO.sub.2 compression stage in which CO.sub.2 refrigerant
is compressed, a CO.sub.2 condensation stage having a tank in which
CO.sub.2 refrigerant is accumulated in a liquid state, at least one
of pressuring means and an expansion stage to direct the CO.sub.2
refrigerant from the CO.sub.2 condensation stage to a CO.sub.2
evaporation stage in which CO.sub.2 refrigerant absorbs energy to
refrigerate. A condensation circuit has a second refrigerant being
circulated between a second compression stage, a second
condensation stage, a second expansion stage and a second
evaporation stage. A heat-exchanger unit by which the CO.sub.2
refrigerant from the CO.sub.2 refrigeration circuit is in heat
exchange with the second refrigerant in the second evaporation
stage such that the second refrigerant absorbs heat from the
CO.sub.2 refrigerant to at least partially liquefy the CO.sub.2
refrigerant for the CO.sub.2 condensation stage. A defrost circuit
directing defrost CO.sub.2 refrigerant from the CO.sub.2
compression stage to the CO.sub.2 evaporation stage to defrost at
least one evaporator of the CO.sub.2 evaporation stage, the defrost
CO.sub.2 refrigerant being subsequently returned to the CO.sub.2
refrigeration circuit.
Inventors: |
DUBE; Serge; (St-Zotique,
CA) |
Correspondence
Address: |
OGILVY RENAULT LLP
1, Place Ville Marie, SUITE 2500
MONTREAL
QC
H3B 1R1
CA
|
Family ID: |
41198743 |
Appl. No.: |
12/425719 |
Filed: |
April 17, 2009 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
61046004 |
Apr 18, 2008 |
|
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|
Current U.S.
Class: |
62/430 ; 62/502;
62/509; 62/513; 62/515 |
Current CPC
Class: |
F25B 9/008 20130101;
F25B 5/02 20130101; F25B 7/00 20130101; F25B 2400/22 20130101; F25B
2400/23 20130101; C09K 5/041 20130101; F25B 47/022 20130101; F25B
2400/075 20130101; F25B 2309/061 20130101 |
Class at
Publication: |
62/430 ; 62/509;
62/502; 62/513; 62/515 |
International
Class: |
F25D 11/00 20060101
F25D011/00; F25B 39/04 20060101 F25B039/04; F25B 1/00 20060101
F25B001/00; F25B 41/00 20060101 F25B041/00; F25B 39/02 20060101
F25B039/02 |
Claims
1. A refrigeration unit comprising: a CO.sub.2 refrigeration
circuit having a CO.sub.2 compression stage in which CO.sub.2
refrigerant is compressed, a CO.sub.2 condensation stage having a
tank in which CO.sub.2 refrigerant is accumulated in a liquid
state, at least one of pressuring means and an expansion stage to
direct the CO.sub.2 refrigerant from the CO.sub.2 condensation
stage to a CO.sub.2 evaporation stage in which CO.sub.2 refrigerant
absorbs energy to refrigerate; a condensation circuit having a
second refrigerant being circulated between a second compression
stage, a second condensation stage, a second expansion stage and a
second evaporation stage; a heat-exchanger unit by which the
CO.sub.2 refrigerant from the CO.sub.2 refrigeration circuit is in
heat exchange with the second refrigerant in the second evaporation
stage such that the second refrigerant absorbs heat from the
CO.sub.2 refrigerant to at least partially liquefy the CO.sub.2
refrigerant for the CO.sub.2 condensation stage; and a defrost
circuit directing defrost CO.sub.2 refrigerant from the CO.sub.2
compression stage to the CO.sub.2 evaporation stage to defrost at
least one evaporator of the CO.sub.2 evaporation stage, the defrost
CO.sub.2 refrigerant being subsequently returned to the CO.sub.2
refrigeration circuit.
2. The refrigeration unit according to claim 1, wherein the
CO.sub.2 evaporation stage has at least medium-temperature
evaporators and low-temperature evaporators, with a line directing
CO.sub.2 refrigerant exiting the low-temperature evaporators to the
CO.sub.2 compression stage, and with the pressuring means upstream
of the medium-temperature evaporators to feed CO.sub.2 refrigerant
to the medium-temperature evaporators, with another line directing
CO.sub.2 refrigerant exiting the medium-temperature evaporators to
the CO.sub.2 condensation stage.
3. The refrigeration unit according to claim 1, wherein the
CO.sub.2 evaporation stage has at least medium-temperature
evaporators and low-temperature evaporators, with a line directing
CO.sub.2 refrigerant exiting the low-temperature evaporators to the
CO.sub.2 compression stage, and with the expansion stage upstream
of the medium-temperature evaporators to feed CO.sub.2 refrigerant
to the medium-temperature evaporators, with another line directing
CO.sub.2 refrigerant exiting the medium-temperature evaporators to
the CO.sub.2 compression stage.
4. The refrigeration unit according to claim 1, further comprising
a defrost reservoir between the CO.sub.2 evaporation stage and the
CO.sub.2 compression stage to collect the defrost CO.sub.2
refrigerant exiting the defrost circuit, a suction of the CO.sub.2
compression stage connected to the defrost reservoir to collect
CO.sub.2 refrigerant in a gas state for the CO.sub.2 refrigeration
circuit.
5. The refrigeration unit according to claim 4, wherein a discharge
line extends from the CO.sub.2 compression stage to the defrost
reservoir to selectively flush CO.sub.2 refrigerant from the
defrost reservoir through another line extending from the defrost
reservoir to the tank in the CO.sub.2 condensation stage.
6. The refrigeration unit according to claim 1, further comprising
at least one dedicated compressor in the CO.sub.2 compression stage
to collect at least part of the defrost CO.sub.2 refrigerant
exiting the defrost circuit, to compress and discharge the defrost
CO.sub.2 refrigerant to the CO.sub.2 refrigeration circuit.
7. The refrigeration unit according to claim 1, further comprising
a pressure-reducing valve on a discharge line of the CO.sub.2
compression stage, downstream of a defrost line feeding defrost
CO.sub.2 refrigerant to the defrost circuit, to maintain a pressure
of the CO.sub.2 refrigerant in the CO.sub.2 refrigeration circuit
downstream of the pressure-reducing valve lower than the pressure
of the defrost CO.sub.2 refrigerant.
8. The refrigeration unit according to claim 1, wherein the defrost
CO.sub.2 refrigerant is circulated in the CO.sub.2 evaporation
stage of the defrost circuit at a pressure below 700 Psi.
9. The refrigeration unit according to claim 1, wherein the
condensation circuit has a pressure-maintaining line extending from
a discharge of the second compression stage to a suction of the
second compression stage, the pressure-maintaining line being
selectively opened to maintain a minimum operating pressure at a
suction of the second compression stage.
10. The refrigeration unit according to claim 1, further comprising
a line extending from the CO.sub.2 evaporation stage to the
CO.sub.2 condensation stage to direct defrost CO.sub.2 refrigerant
from the defrost circuit to the refrigeration circuit.
11. A refrigeration unit comprising: a casing; a CO.sub.2
refrigeration circuit having a CO.sub.2 compression stage in which
CO.sub.2 refrigerant is compressed, a CO.sub.2 condensation stage
having a tank in which CO.sub.2 refrigerant is accumulated in a
liquid state, at least one of pressuring means and an expansion
stage to direct the CO.sub.2 refrigerant from the CO.sub.2
condensation stage to a CO.sub.2 evaporation stage in which
CO.sub.2 refrigerant absorbs energy to refrigerate, with at least
the CO.sub.2 compression stage, and the CO.sub.2 condensation stage
being in the casing; a condensation circuit having a second
refrigerant being circulated between a second compression stage, a
second condensation stage, a second expansion stage and a second
evaporation stage, at least the second compression stage, the
second expansion stage and the second evaporation stage being in
the casing; and a heat-exchanger unit in the casing by which the
CO.sub.2 refrigerant from the CO.sub.2 refrigeration circuit is in
heat exchange with the second refrigerant in the second evaporation
stage such that the second refrigerant absorbs heat from the
CO.sub.2 refrigerant to at least partially liquefy the CO.sub.2
refrigerant for the CO.sub.2 condensation stage.
12. The refrigeration unit according to claim 11, further
comprising a defrost circuit directing defrost CO.sub.2 refrigerant
from the CO.sub.2 compression stage to the CO.sub.2 evaporation
stage to defrost at least one evaporator, the defrost CO.sub.2
refrigerant being subsequently returned to the CO.sub.2
refrigeration circuit.
13. The refrigeration unit according to claim 11, wherein the at
least one of pressuring means and expansion stage are in the
casing.
14. The refrigeration unit according to claim 11, further
comprising a ventilation circuit in which circulates a third
refrigerant between a third compression stage, a third
condensation/gas cooling stage, a third expansion stage and a third
evaporation stage, at least the third compression stage, the third
condensation/gas cooling stage, and the third expansion stage being
in the casing, with the third evaporation stage adapted to be in a
ventilation duct to absorb heat from ventilation air.
15. The refrigeration unit according to claim 14, further
comprising a heat reclaim stage in a discharge line of the CO.sub.2
compression stage to reclaim heat from the CO.sub.2 refrigerant,
the heat reclaim stage comprising a coil adapted to be in said
ventilation duct to heat ventilation air.
16. The refrigeration unit according to claim 11, further
comprising at least an other one of the refrigeration unit in
another one of the casing, the other one of the refrigeration unit
being without one of the condensation circuit, and being in
heat-exchange relation with the heat-exchange unit of the first one
of the refrigeration unit.
17. A refrigeration unit of the type having a CO.sub.2
refrigeration circuit with a CO.sub.2 compression stage in which
CO.sub.2 refrigerant is compressed, a CO.sub.2 condensation stage
having a tank in which CO.sub.2 refrigerant is accumulated in a
liquid state, an expansion stage to direct the CO.sub.2 refrigerant
from the CO.sub.2 condensation stage to a CO.sub.2 evaporation
stage in which CO.sub.2 refrigerant absorbs energy CO.sub.2
refrigerate, the CO.sub.2 evaporation stage having at least two
evaporators, the refrigeration unit comprising at least one line
connected from the CO.sub.2 condensation stage to one expansion
valve of the expansion stage, the line diverging into at least two
lines each connected to a balancing valve and an own one of the
evaporators, such that CO.sub.2 refrigerant expanded by the one
expansion valve is directed to the at least two evaporators through
the balancing valves.
18. The refrigeration unit according to claim 17, wherein the
expansion stage is in a casing with the CO.sub.2 compression stage
and the CO.sub.2 condensation stage at a distal location from the
CO.sub.2 evaporation stage.
19. The refrigeration unit according to claim 18, wherein the
refrigeration unit is retrofitted to existing evaporators.
20. The refrigeration unit according to claim 17, further
comprising a defrost circuit directing defrost CO.sub.2 refrigerant
from the CO.sub.2 compression stage to the CO.sub.2 evaporation
stage to defrost the evaporators, the defrost refrigerant being
subsequently returned to the CO.sub.2 refrigeration circuit.
Description
CROSS REFERENCE TO RELATED APPLICATION
[0001] This patent application claims priority on U.S. Provisional
Patent Application No. 61/046,004, filed on Apr. 18, 2008, by the
present applicant.
FIELD OF THE APPLICATION
[0002] The present application relates to CO.sub.2 refrigeration
systems, for instance used in commercial applications such as
supermarkets, industrial storage and the like.
BACKGROUND OF THE ART
[0003] With the growing concern for global warming, the use of
chlorofluorocarbons (CFCs) and hydrochlorofluorocarbons (HCFCs) as
refrigerant has been identified as having a negative impact on the
environment. These chemicals have non-negligible ozone-depletion
potential and/or global-warming potential.
[0004] As alternatives to CFCs and HCFCs, ammonia, hydrocarbons,
and CO.sub.2 are used as refrigerants. Although ammonia and
hydrocarbons have negligible ozone-depletion potential and
global-warming potential as does CO.sub.2, these refrigerants are
highly flammable and therefore represent a risk to local safety. On
the other hand, CO.sub.2 is environmentally benign and locally
safe.
SUMMARY OF THE APPLICATION
[0005] It is therefore an aim of the present application to provide
a novel CO.sub.2 refrigeration systems.
[0006] Therefore, in accordance with a first embodiment of the
present application, there is provided a refrigeration unit
comprising: a CO.sub.2 refrigeration circuit having a CO.sub.2
compression stage in which CO.sub.2 refrigerant is compressed, a
CO.sub.2 condensation stage having a tank in which CO.sub.2
refrigerant is accumulated in a liquid state, at least one of
pressuring means and an expansion stage to direct the CO.sub.2
refrigerant from the CO.sub.2 condensation stage to a CO.sub.2
evaporation stage in which CO.sub.2 refrigerant absorbs energy to
refrigerate; a condensation circuit having a second refrigerant
being circulated between a second compression stage, a second
condensation stage, a second expansion stage and a second
evaporation stage; a heat-exchanger unit by which the CO.sub.2
refrigerant from the CO.sub.2 refrigeration circuit is in heat
exchange with the second refrigerant in the second evaporation
stage such that the second refrigerant absorbs heat from the
CO.sub.2 refrigerant to at least partially liquefy the CO.sub.2
refrigerant for the CO.sub.2 condensation stage; and a defrost
circuit directing defrost CO.sub.2 refrigerant from the CO.sub.2
compression stage to the CO.sub.2 evaporation stage to defrost at
least one evaporator of the CO.sub.2 evaporation stage, the defrost
CO.sub.2 refrigerant being subsequently returned to the CO.sub.2
refrigeration circuit.
[0007] Further in accordance with the first embodiment, a discharge
of the CO.sub.2 compression stage is fed to the heat-exchanger unit
for releasing heat to then reach the tank of the CO.sub.2
condensation stage.
[0008] Still further in accordance with the first embodiment, the
CO.sub.2 evaporation stage has at least medium-temperature
evaporators and low-temperature evaporators, with a line directing
CO.sub.2 refrigerant exiting the low-temperature evaporators to the
CO.sub.2 compression stage, and with the pressuring means upstream
of the medium-temperature evaporators to feed CO.sub.2 refrigerant
to the medium-temperature evaporators, with another line directing
CO.sub.2 refrigerant exiting the medium-temperature evaporators to
the CO.sub.2 condensation stage.
[0009] Still further in accordance with the first embodiment, the
CO.sub.2 evaporation stage has at least medium-temperature
evaporators and low-temperature evaporators, with a line directing
CO.sub.2 refrigerant exiting the low-temperature evaporators to the
CO.sub.2 compression stage, and with the expansion stage upstream
of the medium-temperature evaporators to feed CO.sub.2 refrigerant
to the medium-temperature evaporators, with another line directing
CO.sub.2 refrigerant exiting the medium-temperature evaporators to
the CO.sub.2 compression stage.
[0010] Still further in accordance with the first embodiment, a
defrost reservoir between the CO.sub.2 evaporation stage and the
CO.sub.2 compression stage collects the defrost CO.sub.2
refrigerant exiting the defrost circuit, a suction of the CO.sub.2
compression stage connected to the defrost reservoir to collect
CO.sub.2 refrigerant in a gas state for the CO.sub.2 refrigeration
circuit.
[0011] Still further in accordance with the first embodiment, a
discharge line extends from the CO.sub.2 compression stage to the
defrost reservoir to selectively flush CO.sub.2 refrigerant from
the defrost reservoir through another line extending from the
defrost reservoir to the tank in the CO.sub.2 condensation
stage.
[0012] Still further in accordance with the first embodiment, at
least one dedicated compressor is provided in the CO.sub.2
compression stage to collect at least part of the defrost CO.sub.2
refrigerant exiting the defrost circuit, to compress and discharge
the defrost CO.sub.2 refrigerant to the CO.sub.2 refrigeration
circuit.
[0013] Still further in accordance with the first embodiment, a
pressure-reducing valve on a discharge line of the CO.sub.2
compression stage, downstream of a defrost line feeding defrost
CO.sub.2 refrigerant to the defrost circuit, maintains a pressure
of the CO.sub.2 refrigerant in the CO.sub.2 refrigeration circuit
downstream of the pressure-reducing valve lower than the pressure
of the defrost CO.sub.2 refrigerant.
[0014] Still further in accordance with the first embodiment, the
defrost CO.sub.2 refrigerant is circulated in the CO.sub.2
evaporation stage of the defrost circuit at a pressure below 700
Psi.
[0015] Still further in accordance with the first embodiment, the
defrost CO.sub.2 refrigerant is circulated in the CO.sub.2
evaporation stage of the defrost circuit at a pressure between 300
and 425 Psi.
[0016] Still further in accordance with the first embodiment to
claim 1, a heat reclaim stage in a discharge line of the CO.sub.2
compression stage reclaims heat from the CO.sub.2 refrigerant.
[0017] Still further in accordance with the first embodiment, the
heat reclaim stage comprises a coil in a ventilation duct to heat
ventilation air.
[0018] Still further in accordance with the first embodiment, the
condensation circuit has a pressure-maintaining line extending from
a discharge of the second compression stage to a suction of the
second compression stage, the pressure-maintaining line being
selectively opened to maintain a minimum operating pressure at a
suction of the second compression stage.
[0019] Still further in accordance with the first embodiment, the
condensation circuit has a second heat-exchanger by which the
second refrigerant exiting the second compression stage selectively
heats the second refrigerant exiting the second condensation stage
to subsequently feed the second refrigerant exiting the second
condensation stage directly to the second compression stage.
[0020] Still further in accordance with the first embodiment, a
line extends from the CO.sub.2 evaporation stage to the CO.sub.2
condensation stage to direct defrost CO.sub.2 refrigerant from the
defrost circuit to the refrigeration circuit.
[0021] In accordance with a second embodiment of the present
application, there is provided a refrigeration unit comprising: a
casing; a CO.sub.2 refrigeration circuit having a CO.sub.2
compression stage in which CO.sub.2 refrigerant is compressed, a
CO.sub.2 condensation stage having a tank in which CO.sub.2
refrigerant is accumulated in a liquid state, at least one of
pressuring means and an expansion stage to direct the CO.sub.2
refrigerant from the CO.sub.2 condensation stage to a CO.sub.2
evaporation stage in which CO.sub.2 refrigerant absorbs energy to
refrigerate, with at least the CO.sub.2 compression stage, and the
CO.sub.2 condensation stage being in the casing; a condensation
circuit having a second refrigerant being circulated between a
second compression stage, a second condensation stage, a second
expansion stage and a second evaporation stage, at least the second
compression stage, the second expansion stage and the second
evaporation stage being in the casing; and a heat-exchanger unit in
the casing by which the CO.sub.2 refrigerant from the CO.sub.2
refrigeration circuit is in heat exchange with the second
refrigerant in the second evaporation stage such that the second
refrigerant absorbs heat from the CO.sub.2 refrigerant to at least
partially liquefy the CO.sub.2 refrigerant for the CO.sub.2
condensation stage.
[0022] Further in accordance with the second embodiment, a defrost
circuit directs defrost CO.sub.2 refrigerant from the CO.sub.2
compression stage to the CO.sub.2 evaporation stage to defrost at
least one evaporator, the defrost CO.sub.2 refrigerant being
subsequently returned to the CO.sub.2 refrigeration circuit.
[0023] Still further in accordance with the second embodiment, the
at least one of pressuring means and expansion stage are in the
casing.
[0024] Still further in accordance with the second embodiment, a
ventilation circuit is provided in which circulates a third
refrigerant between a third compression stage, a third
condensation/gas cooling stage, a third expansion stage and a third
evaporation stage, at least the third compression stage, the third
condensation/gas cooling stage, and the third expansion stage being
in the casing, with the third evaporation stage adapted to be in a
ventilation duct to absorb heat from ventilation air.
[0025] Still further in accordance with the second embodiment, a
heat reclaim stage is provided in a discharge line of the CO.sub.2
compression stage to reclaim heat from the CO.sub.2 refrigerant,
the heat reclaim stage comprising a coil adapted to be in said
ventilation duct to heat ventilation air.
[0026] Still further in accordance with the second embodiment, at
least an other one of the refrigeration unit in another one of the
casing, the other one of the refrigeration unit being without one
of the condensation circuit, and being in heat-exchange relation
with the heat-exchange unit of the first one of the refrigeration
unit.
[0027] In accordance with a third embodiment of the present
application, there is provided a refrigeration unit of the type
having a CO.sub.2 refrigeration circuit with a CO.sub.2 compression
stage in which CO.sub.2 refrigerant is compressed, a CO.sub.2
condensation stage having a tank in which. CO.sub.2 refrigerant is
accumulated in a liquid state, an expansion stage to direct the
CO.sub.2 refrigerant from the CO.sub.2 condensation stage to a
CO.sub.2 evaporation stage in which CO.sub.2 refrigerant absorbs
energy to refrigerate, the CO.sub.2 evaporation stage having at
least two evaporators, the refrigeration unit comprising at least
one line connected from the CO.sub.2 condensation stage to one
expansion valve of the expansion stage, the line diverging into at
least two lines each connected to a balancing valve and an own one
of the evaporators, such that CO.sub.2 refrigerant expanded by the
one expansion valve is directed to the at least two evaporators
through the balancing valves.
[0028] Further in accordance with the third embodiment, the
expansion stage is in a casing with the CO.sub.2 compression stage
and the CO.sub.2 condensation stage at a distal location from the
CO.sub.2 evaporation stage.
[0029] Still further in accordance with the third embodiment, the
refrigeration unit is retrofitted to existing evaporators.
[0030] Still further in accordance with the third embodiment, a
defrost circuit directs defrost CO.sub.2 refrigerant from the
CO.sub.2 compression stage to the CO.sub.2 evaporation stage to
defrost the evaporators, the defrost CO.sub.2 refrigerant being
subsequently returned to the CO.sub.2 refrigeration circuit.
BRIEF DESCRIPTION OF THE DRAWINGS
[0031] FIG. 1 is a block diagram of a CO.sub.2 refrigeration unit
in accordance with a first embodiment of the present
application;
[0032] FIG. 2 is a block diagram of a CO.sub.2 refrigeration unit
in accordance with a second embodiment of the present application,
featuring refrigerant defrost;
[0033] FIG. 3 is a block diagram of CO.sub.2 refrigeration units
sharing a high-pressure condensing circuit, in accordance with a
third embodiment of the present application;
[0034] FIG. 4 is a schematic view of a CO.sub.2 condensation tank,
as used in the CO.sub.2 refrigeration units of FIGS. 1-3;
[0035] FIG. 5 is a schematic plan of the CO.sub.2 refrigeration
unit of FIGS. 1 and 2;
[0036] FIG. 6 is a block diagram of the high-pressure condensing
circuit of the CO.sub.2 refrigeration unit of FIG. 1, in accordance
with another embodiment of the present application;
[0037] FIG. 7 is a block diagram of the CO.sub.2 refrigeration unit
of FIG. 1, with high-temperature evaporation;
[0038] FIG. 8 is a block diagram of a CO.sub.2 refrigeration unit
in accordance with a fourth embodiment of the present application,
featuring medium-temperature compression;
[0039] FIG. 9 is a block diagram of a CO.sub.2 refrigeration unit
in accordance with a fifth embodiment of the present application,
featuring a defrost-reservoir;
[0040] FIG. 10 is a block diagram of the high-pressure condensing
circuit of FIG. 6, with a pressure-maintaining line; and
[0041] FIG. 11 is a block diagram of an expansion arrangement of a
CO.sub.2 refrigeration unit.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0042] Referring now to the drawings, and more particularly to FIG.
1, a CO.sub.2 refrigeration unit in accordance with a first
embodiment of the present application is generally at 10. The
CO.sub.2 refrigeration unit 10 of FIG. 1 is defined by a casing
that encloses parts of a CO.sub.2 refrigeration circuit 12, a
high-pressure condensing circuit 13 cascaded with the CO.sub.2
refrigeration circuit 12, and a ventilation circuit 14. The
CO.sub.2 refrigeration unit 10 is primarily used as a rooftop unit
providing refrigeration for the needs of a building, but may also
be used within a building, for instance in a mechanical room. The
CO.sub.2 refrigeration unit described hereinafter are well suited
for being retro-fitted to existing installations, using the
existing evaporators and/or condensers on site. Some of the
embodiments described hereinafter pertain to a casing enclosing
most components, which casing is readily installed as a whole with
all components ready for operation.
[0043] The CO.sub.2 refrigeration unit 10 provides cooling energy
for medium-temperature and low-temperature refrigerated cabinets
and enclosures in the form of liquid or gaseous CO.sub.2 as fed by
the CO.sub.2 refrigeration circuit 12. Moreover, the CO.sub.2
refrigeration unit 10 provides air-conditioning and heating energy
for a ventilation system, as fed by the ventilation circuit 14.
[0044] The CO.sub.2 refrigeration circuit 12 is a closed circuit in
which liquid/gaseous CO.sub.2 circulates. The CO.sub.2
refrigeration circuit 12 has a compression stage, in which gaseous
CO.sub.2 is compressed by one or more compressors. The compressed
CO.sub.2 then reaches a condensation stage 21, in which the
compressed CO.sub.2 releases energy. The condensation stage 21
features a condensation tank in heat exchange with the
high-pressure condensing circuit 13, as will be described
hereinafter. The cascaded relation with the high-pressure
condensing circuit 13 is due to the limitations in ambient
temperature condensation for the CO.sub.2. The high-pressure
condensing circuit 13 provides refrigerant at a temperature
allowing condensation of the CO.sub.2.
[0045] Liquid CO.sub.2 then exits the condensation stage 21 and the
CO.sub.2 refrigeration circuit 12 to reach the refrigerated units
(e.g., refrigerated cabinets or enclosures) within the
building.
[0046] In the embodiment of FIG. 1, the liquid CO.sub.2 is directed
either to medium-temperature refrigerated units (e.g., for
non-frozen goods, such as produce, meats, dairy) or low-temperature
refrigerated units (e.g., for frozen goods).
[0047] In the medium-temperature branch, liquid CO.sub.2 is fed to
the evaporation stage 23 by pressuring means 22 (in or out of the
casing of the refrigeration unit 10). The pressuring means 22 are a
pump or like mechanical device suitable to direct the flow of
liquid CO.sub.2 to the evaporation stage 23. The evaporation stage
23 comprises one or more evaporators located in refrigerated
enclosures or cabinets. The evaporators are in a heat-exchange
relation with a fluid, such as air, blown thereon. The evaporators
absorb heat from the air, to provide the refrigerated units with
cold energy. The liquid CO.sub.2 exiting the medium-temperature
evaporation stage 23 is then directed to the condensation stage
21.
[0048] In the low-temperature branch, liquid CO.sub.2 is fed to the
expansion stage 24. The expansion stage 24 features expansion
valves to vaporize the liquid CO.sub.2, so as to subsequently feed
gaseous CO.sub.2 to the low-temperature evaporation stage 25. The
evaporation stage 25 comprises one or more evaporators located in
refrigerated enclosures or cabinets, typically enclosing frozen
goods. The evaporators are in a heat-exchange relation with a
fluid, such as air, blown thereon. The evaporators absorb heat from
the air, to provide the refrigerated units with cold energy. The
gaseous CO.sub.2 exiting the low-temperature evaporation stage 25
is then directed to the compression stage 20.
[0049] It is pointed out that the higher volumetric capacity/high
working pressures of CO.sub.2 enable the use of small-dimension
lines toward the evaporation stages 23 and 25, and back to the
compression stage 20.
[0050] It is commonly known to reclaim heat from refrigerant
downstream of the compression stage 20, as the heat is otherwise
lost in the condensation stage. In the embodiment of FIG. 1, the
CO.sub.2 refrigeration circuit 12 has a heat reclaim coil 26, in
heat exchange relation with the ventilation circuit 14. The heat
reclaim stage 26 is a dehumidifier coil that is for instance
positioned in a ventilation duct to dehumidify air-conditioning
air. The dehumidifier coil may alternatively or concurrently be a
heating coil in a ventilation duct to heat the ventilation air. It
is pointed out that the CO.sub.2 directed to the heat reclaim stage
26 is in a transcritical state. The heat reclaim 26 can be used for
other purposes, for instance to heat water. It is considered to
interrelate all heat reclaim coils 26 (e.g., for various units 10,
10' or the like) with one circuit in which another refrigerant
circulates, to accumulate heat from the heat reclaim coils 26.
[0051] Still referring to FIG. 1, a valve is provided on the line
connecting the heat reclaim stage 26 to the condensation stage 21.
The valve is a modulating or floating valve, or any other suitable
type of valve, that controls the condensation pressure in the heat
reclaim stage 26. The condensation pressure is increased or lowered
as a function of the exterior/interior temperature, as an example.
Other configurations are considered to control the pressure in the
heat reclaim stage 26.
[0052] In FIG. 7, a CO.sub.2 refrigeration unit similar to the
CO.sub.2 refrigeration unit 10 of FIG. 1 is illustrated with
high-temperature evaporation, for instance for refrigerated
cabinets for fruits and vegetables. The circuit features an
expansion stage 28 and the evaporators 29, and a dedicated
compressor at the suction of the evaporators 29. An inlet
regulating valve 20B' is optionally provided in the discharge line
of the dedicated compressor 20B to maintain suitable operating
pressures for the dedicated compressor 20B. Alternative features
and configurations (e.g., defrost) are available for the CO.sub.2
refrigeration unit for FIG. 7, but are not illustrated for
simplicity purposes.
[0053] Still referring to FIG. 1, the high-pressure condensing
circuit 13 is a closed circuit cascaded with the CO.sub.2
refrigeration circuit 12. A chemical refrigerant (i.e., synthetic
refrigerant, glycol or the like) circulates in the high-pressure
condensing circuit 13. In the embodiment of FIG. 1, the
high-pressure condensing circuit 13 is at least partially enclosed
in the casing of the CO.sub.2 refrigeration unit 10.
[0054] The condensing circuit 13 has a compression stage 30, in
which at least one compressor produces high-pressure gas
refrigerant. The compressors of the compression stage 30 are
conventional compressors, variable-speed ammonia compressors or
oil-free magnetic-bearing compressors, such as Danfoss-Turbocor
compressors. The gas refrigerant is directed from the compression
stage 30 to the condensation stage 31, in which the refrigerant
releases heat. It is contemplated to provide the condensation stage
31 with a condenser coil and fans that will expel heat to the
environment. The condenser coil and fans may be existing units from
a retrofitted system.
[0055] The refrigerant is then directed to an expansion stage 32,
wherein the refrigerant is vaporized to subsequently reach the
heat-exchange evaporation stage 33. In the heat-exchange
evaporation stage 33, the refrigerant absorbs heat from the gaseous
CO.sub.2 in the condensation stage 21 of the CO.sub.2 refrigeration
circuit 12. The refrigerant is then directed to the compression
stage 30 to complete the refrigeration cycle.
[0056] In the embodiment of FIG. 1, the high-pressure condensing
circuit 13 is fully enclosed in the casing of the CO.sub.2
refrigeration unit 10. Accordingly, the volume of refrigerant
required to operate the condensing circuit 13 is reduced when
compared to a similar rooftop refrigeration unit having lines
extending to the refrigerated cabinets and enclosures within a
building. Instead, CO.sub.2 is used as high-volume refrigerant, and
CO.sub.2 is considered less harmful to the environment.
[0057] Referring to FIG. 1, the ventilation circuit 14 is a closed
circuit in which circulates a chemical refrigerant. In the
embodiment of FIG. 1, the ventilation circuit 14 is fully enclosed
in the casing of the CO.sub.2 refrigeration unit 10, with a
ventilation duct circulating air in the CO.sub.2 refrigeration unit
10. Alternatively, some parts of the ventilation circuit 14 may
extend into the building, such as evaporation coils, the
compression stage 40 and the condensation stage 41.
[0058] The ventilation circuit 14 has a compression stage 40, in
which at least one compressor compresses the refrigerant to a gas
state. The gas refrigerant is directed from the compression stage
40 to the condensation stage 41, in which the refrigerant releases
heat. It is contemplated to provide the condensation stage 41 with
a condenser coil and fans that will expel heat to the environment.
It is pointed out that the condensation stage 41 may simply be a
gas-cooling stage as the refrigerant does not necessarily change
phase, for instance if CO.sub.2 refrigerant is used. To simplify
the illustrations, stage 41 is referred to as condensation
stage.
[0059] The refrigerant is then directed to an expansion stage 42,
wherein the refrigerant is vaporized to subsequently reach the
evaporation stage 43. In the evaporation stage 43, the refrigerant
absorbs heat ventilation air, so as to produce air-conditioned air.
The refrigerant is then directed to the compression stage 40 to
complete the refrigeration cycle.
[0060] The ventilation circuit 14 is optional in the CO.sub.2
refrigeration unit 10, as some buildings may not need
air-conditioning, or might already have independent
air-conditioning units. The ventilation circuit 14 may be in its
own casing, and shared amongst a plurality of ventilation
ducts.
[0061] Referring to FIG. 2, a CO.sub.2 refrigeration unit is
illustrated at 10'. The CO.sub.2 refrigeration unit 10' is similar
to the CO.sub.2 refrigeration unit 10 of FIG. 1, but features
refrigerant defrost by way of a defrost circuit. Accordingly, like
elements between the CO.sub.2 refrigeration units 10 and 10' will
bear like reference numerals.
[0062] The defrost circuit of the CO.sub.2 refrigeration unit 10'
has refrigerant lines A extending from the compression stage 20 to
the evaporation stages 23 and 25, to feed hot gaseous CO.sub.2
refrigerant to the evaporation stages 23 and/or 25. Although not
illustrated, suitable valves, pressure controls and/or regulators
are provided in the lines A and in the evaporation stages 23 and 25
to temporarily stop the flow of cooling refrigerant to the
evaporators, so as to proceed with the defrost of evaporators from
the stages 23 and 25. For instance, the defrost refrigerant may be
fed to the low-temperature evaporation stage 25 upstream of the
expansion stage 24, so as not to have a defrost line extending from
the compression stage 20 to the refrigerated cabinet. Suitable
valves are thus required to feed defrost refrigerant to the
low-temperature evaporation stage 25, including for instance a
by-pass solenoid valve and line to by-pass the expansion stage 24.
It is preferred that any CO.sub.2 refrigerant in a liquid state
from the refrigeration circuit be flushed out of the evaporators 23
and/or 25 prior to a defrost cycle. This is performed by exposing
the evaporators 23 and/or 25 (where applicable) to the suction of
the compression stage 20 while cutting the feed of CO.sub.2
refrigerant from the condensation stage 21. The flush allows the
defrosting of the evaporators 23 and/or 25 more efficiently, and in
less time.
[0063] At the outlet of a defrost evaporator from the stages 23 and
25, the defrost CO.sub.2 is directed to any other stage of the
CO.sub.2 refrigeration circuit 12 that can receive the CO.sub.2 in
the state it is in. In the embodiment of FIG. 2, the defrost
CO.sub.2 is directed to the compression stage 20. It is considered
to provide a dedicated compressor 20B that will be dedicated to
receiving defrost CO.sub.2, and feeding defrost CO.sub.2 to the
defrost circuit, as illustrated by line A. Line B is provided at
the evaporation stages 23 and 25 to direct defrost CO.sub.2 to the
dedicated compressor 20B, or to mix with condensed CO.sub.2 in the
tank 50 of the condensation stage 20, or downstream of the
condensation stage 20, with a valve B' facilitating this latter
option. The other compressors 20A receive the CO.sub.2 circulating
in the refrigeration cycle, from the low-temperature evaporation
stage 25. Other configurations are also considered.
[0064] An inlet regulating valve 20A' is optionally provided in the
discharge of the compressors 20A so as to ensure that the pressure
in the discharge line is suitable for the compressors 20A. The
valve 20A' may also be used to direct some refrigerant of the
compressors 20A to the defrost line A, as illustrated in FIG.
2.
[0065] It is also observed that the pressuring means 22 are within
the casing of the CO.sub.2 refrigeration unit 10', and are
therefore part of the roof-top unit. However, the pressuring means
22 may also be positioned adjacent to the medium-temperature
evaporators 23 within the building, as is illustrated in FIG.
1.
[0066] Referring to FIG. 3, a plurality of CO.sub.2 refrigeration
units are illustrated at 10''. The CO.sub.2 refrigeration units
10'' are similar to the CO.sub.2 refrigeration unit 10 of FIG. 1,
but without the high-pressure condensing circuit 13 within the
casing of the refrigeration unit. Accordingly, like elements
between the CO.sub.2 refrigeration units 10 and 10'' will bear like
reference numerals.
[0067] In the embodiment of FIG. 3, the CO.sub.2 refrigeration
units 10'' share the high-pressure condensing circuit 13. As in
some instances the condensing load of the CO.sub.2 refrigerant is
relatively low, it is considered to share amongst at least two
refrigeration units a high-pressure condensing circuit 13.
Accordingly, by sharing the high-pressure condensing circuit 13,
the CO.sub.2 refrigeration units 10'' represent a cost-efficient
solution. All refrigeration units 10'' are in a heat-exchange
relation with the heat-exchange evaporation stage 33 of the
high-pressure condensing circuit 13. Although three CO.sub.2
refrigeration units 10'' are illustrated in the embodiment of FIG.
3, a high-pressure condensing circuit 13 can be shared by two or
more of the CO.sub.2 refrigeration units 10''. Moreover, the
high-pressure condensing circuit 13 may be in its own rooftop
casing, or may be in one of the CO.sub.2 refrigeration units 10''
that are part of the network of CO.sub.2 refrigeration units 10''
sharing the high-pressure condensing circuit 13.
[0068] Referring to FIG. 4, a CO.sub.2 condensation tank is shown
at 50. The tank 50 is a pressure vessel receiving gaseous CO.sub.2
from the compression stage 20 and possibly from the heat reclaim
stage 26. The gaseous CO.sub.2 is then directed to the
heat-exchange evaporation stage 33 of the circuit 13, in which heat
from the gaseous CO.sub.2 is absorbed by the refrigerant
circulating in the circuit 13. By the heat exchange, the gaseous
CO.sub.2 is at least partially liquefied and returns to the tank 50
through line D. Accordingly, liquid CO.sub.2 51 accumulates in the
tank 50, and by gravity accumulates in the bottom of the tank 50,
as is illustrated in FIG. 4. Liquid CO.sub.2 51 supplied from the
bottom of the tank 51 is then directed to the evaporation stages 23
and 25. Gaseous CO.sub.2 from the tank 50 may also be directed to a
suction of a CO.sub.2 dedicated compressor, by having a
pressure-reduction valve 52 or like means between the tank 50 and
the dedicated compressor.
[0069] In FIG. 4, a schematic view of the tank 50 is provided.
Although not shown, it is however pointed out that all suitable
valves, pressure controls and/or regulators are provided in order
to ensure the heat exchange between the gaseous CO.sub.2 and the
refrigerant from the high-pressure refrigeration circuit 13 in the
heat-exchange evaporation stage 33.
[0070] In order to reduce material costs, it is considered to have
the condensation stages 31 and 41 share condenser components in the
casing of the refrigeration unit 10, as is illustrated in FIG. 5.
For instance, fans, water cooling systems and the like are
preferably shared by the coils of the condensation stages 31 and
41.
[0071] Referring to FIG. 8, there is illustrated another embodiment
of a CO.sub.2 refrigeration unit at 80 similar to the CO.sub.2
refrigeration units 10, 10' and 10''. Accordingly, like elements
will bear like reference numerals. The CO.sub.2 refrigeration unit
80 has a medium-temperature compression stage 81, the suction of
which collects refrigerant from the medium-temperature evaporation
stage 23. The CO.sub.2 refrigerant is in a suitable gas/liquid
state, having been expanded via an expansion stage 82 prior to
reaching the medium-temperature evaporation stage 23, with suitable
means (e.g., accumulators, heat exchangers) that may prevent liquid
refrigerant from reaching the compression stage 81, and that lower
the pressure of refrigerant fed to the compression stage 20/81.
[0072] The discharge of the low-temperature compression stage 20
and of the medium-temperature compression stage 81 is then directed
to the condensation stage 21, optionally via the heat reclaim stage
26, as described above for the CO.sub.2 refrigeration units 10, 10'
and 10''. Alternatively, the discharge of the compression stages 20
and/or 81 may be fed directly to the heat-exchange evaporation
stage 33 via line 83 prior to reaching the condensation reservoir
21 in a liquid state. This configuration may also be used for the
CO.sub.2 refrigeration units 10, 10' and 10''. Although not shown,
the CO.sub.2 refrigeration unit 80 may be equipped with a defrost
circuit, as set for above for the CO.sub.2 refrigeration units 10,
10' and 10''.
[0073] Referring to FIG. 9, there is illustrated another embodiment
of a CO.sub.2 refrigeration unit at 90 similar to the CO.sub.2
refrigeration units 10, 10', 10'' and 80. Accordingly, like
elements will bear like reference numerals. The CO.sub.2
refrigeration unit 90 has a defrost reservoir 91, positioned
between the suction of the dedicated compression stage 20B and the
low-temperature evaporation stage 25. The suction of the dedicated
compression stage 20B is typically on top of the defrost reservoir
91, such that CO.sub.2 refrigerant in a gas state is collected
thereby.
[0074] In order to periodically flush the liquid contents of the
defrost reservoir 91, a line 92 extends from the discharge of the
compression stages 20A and 20B, with appropriate valves (not
shown). The line 92 is selectively opened to direct the discharge
into the defrost reservoir 91, and flush the liquid CO.sub.2
refrigerant into the condensation reservoir 21 via line 93 (also
provided with appropriate valves).
[0075] It is observed that pressure-reducing valve 94 may be
connected to a discharge line of the compression stages 20A and/or
20B, so as to ensure that the defrost refrigerant is fed to the
evaporators of the evaporation stages 23/25 at a higher pressure
than in the condensation reservoir 21. This is to ensure a flow of
defrost refrigerant back into the refrigeration circuit after
defrost.
[0076] In FIG. 9, both the pressuring means 22 and the expansion
stage 24 are in the casing of the CO.sub.2 refrigeration unit 90.
This configuration is therefore well suited for retro-fitting
existing evaporators to the refrigeration unit 90, as lines are
drawn from the casing to the evaporators. The various
configurations of the CO.sub.2 refrigeration unit 90 may be used
for the CO.sub.2 refrigeration units 10, 10', 10'' and/or 80.
[0077] The CO.sub.2 refrigeration units 10, 10', 10'', 80 and 90
are equipped with a processing unit that ensures the proper
operation of the refrigeration cycles.
[0078] According to one embodiment, the processing unit controls
the operation of the electrically powered components of the
refrigeration units 10, 10', 10'', 80 and 90. The processing unit
will be programmed with procedures to operate the CO.sub.2
refrigeration units 10, 10', 10'', 80 and 90 in a cost-effective
fashion, while optimizing energy consumption.
[0079] In an embodiment, all fans of the evaporators of the
evaporation stages 23 and 25 are controlled by the processor unit
of the CO.sub.2 refrigeration units 10, 10', 10'', 80 and 90.
According to this feature, fans are automatically turned off when
an evaporator of the stages 23 and/or 25 goes into a defrost cycle,
as commanded by the processor unit which also controls the
operation of defrost cycles. Accordingly, all defrost commands are
centralized through the processor unit.
[0080] The processor unit is also programmed to restart the
components of the CO.sub.2 refrigeration units 10, 10' and 10'' in
case of a power outage. According to one sequence of command, the
fans of the evaporator stages 23 and 25 in a refrigeration cycle
are turned on gradually to avoid a high load on the CO.sub.2
refrigeration circuit 12, so as to maintain the pressure of
CO.sub.2 below the relief threshold. Moreover, the pressure of
CO.sub.2 is monitored throughout the refrigeration circuit 12 to
avoid having the CO.sub.2 pressure go above the relief threshold.
In an example, if the CO.sub.2 pressure in the tank 50 is too high,
the processing unit may stop some of the fans in the evaporation
stages 23 and 25 to reduce the load, and avoid the relief of
CO.sub.2. The operator of the system is warned by an alarm of the
high pressure.
[0081] In case of an extended power outage, the processor unit of
the CO.sub.2 refrigeration units 10'' of FIG. 3 may be operated in
a preservation mode from the limited power supply of a power
generator. In such a case, it is considered to operate the
refrigeration units 10'' one after the other, each for a given
amount of time, so as to optimize the use of the limited power
supply of the power generator. In these cases, it is considered to
operate the oil-free magnetic-bearing compressors of the
compression stages 20 and 30, and potentially of the compression
stage 40, and to operate the compressors at the minimum.
[0082] In order to minimize energy consumption, it is considered to
have variable compressors of the CO.sub.2 refrigeration units 10,
10', 10'', 80 and 90 for some or all compression stages, namely
stages 20, 30 and 40. Also, the CO.sub.2 refrigeration circuit 12
is typically provided with pressure relief valves to exhaust
CO.sub.2 above a given pressure threshold. In the event of a power
outage, the restart of the compression stage 20 may cause the
CO.sub.2 pressure to be above the relief threshold, whereby it is
preferred to use variable compressors in the compression stage 20
to gradually build the pressure in the circuit 12 so as to avoid
the relief of CO.sub.2. The temperature of the CO.sub.2 is
controlled by the variation of the speed of the compressors from
the compression stage 20. Moreover, the compressors of the stages
20, 30 and/or 40 preferably operate in floating control so as to
produce a floating head pressure, and minimize energy
consumption.
[0083] Although the CO.sub.2 refrigeration units of FIGS. 1 to 3
show at least two of the CO.sub.2 refrigeration circuit 12, the
high-pressure condensing circuit 13 cascaded with the CO.sub.2
refrigeration circuit 12, and the ventilation circuit 14 in the
same roof-top casing, it is considered to have the three circuits
12, 13 and 14 each in its own casing.
[0084] The CO.sub.2 refrigeration units 10, 10', 10'', 80 and 90
described previously are used in different climates, but are
particularly well suited for warmer climates, in that the CO.sub.2
defrost circuit can be operated at relatively low pressures. More
specifically, the pressure of the CO.sub.2 defrost refrigerant is
typically below 700 Psi, but preferably ranges between 300 and 425
Psi. These low pressures result from the low pressures in the
refrigeration circuit, and more particularly in the condensation
stage 21. The CO.sub.2 refrigerant is kept at a low pressure by the
heat-exchange relation with the secondary refrigerant in the
high-pressure condensing circuit 13.
[0085] Referring to FIG. 6, an alternative embodiment of the
high-pressure condensing circuit is illustrated at 13'. The primary
function of the high-pressure condensing circuit 13' is to cool the
CO.sub.2 refrigerant of the CO.sub.2 refrigeration circuit 12.
[0086] In one embodiment, the compressors of the compression stage
30 are oil-free magnetic-bearing compressors, which operate under
specific conditions. In such a case, it is required to maintain the
pressure of the refrigerant above given thresholds. Accordingly, an
optional loop featuring a heat exchanger 60 is provided in the
circuit 13' to increase the pressure at the compression stage 30.
The loop has a valve 61 that directs hot refrigerant from the
discharge of the compression stage 30 to the heat exchanger 60 via
lines 62. In the heat exchanger 60, the hot refrigerant is in
heat-exchange with cold refrigerant exiting the condensation stage
31. The cold refrigerant exiting the condensation stage 31 is
directed to the heat exchanger 60 via line 63 to absorb heat from
the hot refrigerant, and then reaches the suction line of the
compression stage 30, thereby mixing with refrigerant exiting from
the evaporation stage 33, to increase the pressure in the suction
line. As illustrated in FIG. 6, by way of example, a valve 63' such
as an expansion valve is provided to adjust the pressure prior to
the heat exchanger 60. The valve 63' represents one of numerous
other possibilities for controlling the pressure in the heat
exchanger 60. The hot refrigerant exiting the heat exchanger 60 is
then returned upstream of the condensation stage 31, via line
62.
[0087] It is also considered to provide heat reclaim 64. In an
example, heat reclaim 64 is a heat exchanger by which a refrigerant
such as glycol absorbs heat from the refrigerant of the condensing
circuit 13'. A glycol circuit may then circulate hot glycol through
the facilities, for instance for an auxiliary heating system.
[0088] Referring to FIG. 10, there is provided an additional
pressure-maintaining line 100 extending from the discharge of the
compression stage 30 to the suction of the compression stage 30. A
control valve 101 is provided in the line 100 for appropriate
control of the flow of refrigerant. The pressure-maintaining line
100 ensures that a suitable pressure is maintained at the suction
of the compression stage 30. As some types of compressors (e.g.,
oil-free magnetic compressors) stop operating below a given
pressure, the pressure-maintaining line 100 keeps the compression
stage 30 in operation.
[0089] Referring to FIG. 11, an expansion arrangement is generally
shown 110, and is particularly well suited for any of the CO.sub.2
refrigeration units 10, 10', 10'', 80 and 90, with suitable
modifications. As illustrated in the CO.sub.2 refrigeration unit 90
of FIG. 9, the expansion stage 24 is in the casing of the units 10,
10', 10'', 80 or 90. In the expansion arrangement 110, at least one
of the expansion valves 24 is shared by different evaporators 25.
More specifically, a line 111 extends from the expansion valve 24
to a plurality of the evaporators 25, with a balancing valve 112
being provided upstream of each evaporator 25, to ensure that the
evaporators 25 are fed with CO.sub.2 refrigerant at similar
conditions. In the event that defrost refrigerant is subsequently
fed to any one of the evaporators 25, a bypass line with, for
instance, a check valve 113 is provided upstream of the evaporators
25. It is pointed out that the expansion valve 24 may be out of the
casing, and in proximity to the evaporators 25.
* * * * *