CA2766361A1 - Co2 refrigeration system for ice-playing surface - Google Patents
Co2 refrigeration system for ice-playing surface Download PDFInfo
- Publication number
- CA2766361A1 CA2766361A1 CA2766361A CA2766361A CA2766361A1 CA 2766361 A1 CA2766361 A1 CA 2766361A1 CA 2766361 A CA2766361 A CA 2766361A CA 2766361 A CA2766361 A CA 2766361A CA 2766361 A1 CA2766361 A1 CA 2766361A1
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- CA
- Canada
- Prior art keywords
- refrigerant
- circuit
- evaporation
- heat
- condensation
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25C—PRODUCING, WORKING OR HANDLING ICE
- F25C3/00—Processes or apparatus specially adapted for producing ice or snow for winter sports or similar recreational purposes, e.g. for sporting installations; Producing artificial snow
- F25C3/02—Processes or apparatus specially adapted for producing ice or snow for winter sports or similar recreational purposes, e.g. for sporting installations; Producing artificial snow for ice rinks
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
- F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Lubricants (AREA)
Abstract
A CO2 refrigeration system comprising a transfer circuit for heat exchange between a supracompression circuit of CO2 refrigerant, and an evaporation circuit of CO2 refrigerant. A transfer circuit absorbs heat from the CO2 refrigerant of the evaporation circuit, and releases heat to the CO2 refrigerant of the supracompression circuit. The supracompression circuit comprises a compression stage in which CO2 refrigerant is compressed to at least a supra-compression state, a cooling stage in which the CO2 refrigerant from the compression stage releases heat, and a pressure-regulating unit in a line extending from the cooling stage to the evaporation heat exchanger to maintain a pressure differential therebetween. The evaporation circuit receives CO2 refrigerant having released heat in the condensation heat exchanger. The evaporation circuit comprises a condensation reservoir in which CO2 refrigerant is accumulated in a liquid state, and an evaporation stage in which the CO2 refrigerant from the condensation reservoir absorbs heat to cool an ice-playing surface, to then return to one of the condensation reservoir and the condensation exchanger.
Description
FIELD OF THE APPLICATION
The present application relates to refrigeration systems used to refrigerate ice-playing surfaces such as a skating rinks, curling sheets, etc, and more particularly to refrigeration systems using CO2 refrigerant.
BACKGROUND OF THE ART
With the growing concern for global warming, the use of chlorofluorocarbons (CFCs) and hydrochlorofluoro-carbons (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.
As alternatives to CFCs and HCFCs, ammonia, hydro-carbons and CO2 are used as refrigerants. Although ammonia and hydrocarbons have negligible ozone-depletion potential and global-warming potential as does CO2, these refrigerants are highly flammable and therefore represent a risk to local safety.
On the other hand, CO2 is environmentally benign and locally safe.
SUMMARY OF THE APPLICATION
It is therefore an aim of the present disclosure to provide a CO2 refrigeration system for ice-playing surfaces that addresses issues associated with the prior art.
Therefore, in accordance with the present application, there is provided a CO2 refrigeration system comprising a transfer circuit for heat exchange between a supracompression circuit of CO2 refrigerant, and an evaporation circuit of CO2 refrigerant; a transfer circuit in which a transfer refrigerant circulates between a condensation heat exchanger to absorb heat from the CO2 refrigerant of the evaporation circuit, and an evaporation heat exchanger to release heat to the CO2 refrigerant of the supracompression circuit; the supracompression circuit comprising a compression stage in which CO2 refrigerant having absorbed heat in the evaporation heat exchanger is compressed to at least a supracompression state, a cooling stage in which the CO2 refrigerant from the compression stage releases heat, and a pressure-regulating unit in a line extending from the cooling stage to the evaporation heat exchanger to maintain a pressure differential therebetween; the evaporation circuit receiving CO2 refrigerant having released heat in the condensation heat exchanger, the evaporation circuit comprising a condensation reservoir in which CO2 refrigerant is accumulated in a liquid state, and an evaporation stage in which the CO2 refrigerant from the condensation reservoir absorbs heat to cool an ice-playing surface, to then return to one of the condensation reservoir and the condensation exchanger.
BRIEF DESCRIPTION OF DRAWINGS
Fig. 1 is a block diagram of a CO2 refrigeration system for ice-playing surface in accordance with an embodiment of the present application, with CO2 refrigerant in a circuit under the ice-playing surface; and Fig. 2 is a block diagram of a CO2 refrigeration system for ice-playing surface in accordance with an embodiment of the present application, with CO2 refrigerant cooling brine of a circuit under the ice-playing surface.
DESCRIPTION OF PREFERRED EMBODIMENTS
Referring to the drawings and more particularly to Fig. 1, there is illustrated a CO2 refrigeration system 1 for ice-playing surface, while Fig. 2 illustrates a CO2 refrigeration system 2 for ice-playing surface similar to that of Fig. 1, whereby like reference numerals will refer to like elements.
=
The present application relates to refrigeration systems used to refrigerate ice-playing surfaces such as a skating rinks, curling sheets, etc, and more particularly to refrigeration systems using CO2 refrigerant.
BACKGROUND OF THE ART
With the growing concern for global warming, the use of chlorofluorocarbons (CFCs) and hydrochlorofluoro-carbons (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.
As alternatives to CFCs and HCFCs, ammonia, hydro-carbons and CO2 are used as refrigerants. Although ammonia and hydrocarbons have negligible ozone-depletion potential and global-warming potential as does CO2, these refrigerants are highly flammable and therefore represent a risk to local safety.
On the other hand, CO2 is environmentally benign and locally safe.
SUMMARY OF THE APPLICATION
It is therefore an aim of the present disclosure to provide a CO2 refrigeration system for ice-playing surfaces that addresses issues associated with the prior art.
Therefore, in accordance with the present application, there is provided a CO2 refrigeration system comprising a transfer circuit for heat exchange between a supracompression circuit of CO2 refrigerant, and an evaporation circuit of CO2 refrigerant; a transfer circuit in which a transfer refrigerant circulates between a condensation heat exchanger to absorb heat from the CO2 refrigerant of the evaporation circuit, and an evaporation heat exchanger to release heat to the CO2 refrigerant of the supracompression circuit; the supracompression circuit comprising a compression stage in which CO2 refrigerant having absorbed heat in the evaporation heat exchanger is compressed to at least a supracompression state, a cooling stage in which the CO2 refrigerant from the compression stage releases heat, and a pressure-regulating unit in a line extending from the cooling stage to the evaporation heat exchanger to maintain a pressure differential therebetween; the evaporation circuit receiving CO2 refrigerant having released heat in the condensation heat exchanger, the evaporation circuit comprising a condensation reservoir in which CO2 refrigerant is accumulated in a liquid state, and an evaporation stage in which the CO2 refrigerant from the condensation reservoir absorbs heat to cool an ice-playing surface, to then return to one of the condensation reservoir and the condensation exchanger.
BRIEF DESCRIPTION OF DRAWINGS
Fig. 1 is a block diagram of a CO2 refrigeration system for ice-playing surface in accordance with an embodiment of the present application, with CO2 refrigerant in a circuit under the ice-playing surface; and Fig. 2 is a block diagram of a CO2 refrigeration system for ice-playing surface in accordance with an embodiment of the present application, with CO2 refrigerant cooling brine of a circuit under the ice-playing surface.
DESCRIPTION OF PREFERRED EMBODIMENTS
Referring to the drawings and more particularly to Fig. 1, there is illustrated a CO2 refrigeration system 1 for ice-playing surface, while Fig. 2 illustrates a CO2 refrigeration system 2 for ice-playing surface similar to that of Fig. 1, whereby like reference numerals will refer to like elements.
=
In Fig. 1, the CO2 refrigeration system 1 has a CO2 evaporation circuit 10.
The CO2 evaporation circuit 10 comprises a condensation reservoir 12 accumulating CO2 refrigerant in a liquid and gaseous state.
The CO2 evaporation circuit 10 is in a heat-exchange relation with a condensation circuit that absorbs heat from the CO2 refrigerant.
Line 14 directs CO2 refrigerant from the condensation reservoir 12 to an evaporation stage, with a flow of CO2 refrigerant induced by pump and/or an expansion valve(s) as generally indicated as 15.
As is shown in Fig. 1, the CO2 refrigerant is then fed to the ice-playing surface evaporation stage 17.
The ice-playing surface evaporation stage 17 of = 15 Fig. 1 consists of a circuit of pipes positioned under the ice-playing surface, in which the CO2 refrigerant circulates to absorb heat from fluid being frozen to form the ice-playing surface, or to maintain the ice-playing surface frozen.
CO2 refrigerant exiting the evaporation stage 17 is directed to the condensation reservoir 12, by way of line 18.
The CO2 evaporation circuit 10 is in a heat-exchange relation with a transfer circuit 20. The transfer circuit 20 is for instance of the type in which a transfer refrigerant (e.gõ alcohol-based such as glycol, water, brine or the like) cycles. A condensation heat exchanger 21 is in fluid communication with the condensation reservoir 12, so as to receive CO2 refrigerant in a gaseous state, whereby the transfer refrigerant absorbs heat from the CO2 refrigerant in the heat exchanger 21.
According to an embodiment, the condensation heat exchanger 21 has a coil that is positioned inside the condensation reservoir 12.
The condensation heat exchanger 21 may also receive CO2 refrigerant directly from line 14, or from line 18. The transfer circuit 20 is a closed circuit featuring lines 22 and 23 as well as pump 24 to cycle the transfer refrigerant between the heat exchanger 21 and an evaporation heat exchanger 31 of a supra-compression circuit 30.
Accordingly, the transfer refrigerant absorbs heat from the CO2 refrigerant circulating in the CO2 evaporation circuit 10, and releases the heat to the CO2 refrigerant circulating in the supra-compression circuit 30.
In the transfer circuit 20, the condensation refrigerant circulates between the heat exchanger 21 in which the transfer refrigerant absorbs heat, and the heat exchanger 31 in which the transfer refrigerant absorbs heat.
The supra-compression circuit 30 (i.e., transcritical circuit if operated at transcritical pressures) is provided to compress CO2 refrigerant to a transcritical state, for heating purposes, or supra-compressed state.
The heat exchanger 31 vaporizes the CO2 refrigerant fed to a supra-compression stage 32. The supra-compression stage 32 features one or more compressors (e.g., BockTM, DorinTm) , that compress the CO2 refrigerant to a supra-compressed or transcritical state.
Upon exiting the supra-compression stage 32, the CO2 refrigerant must be cooled by a cooling stage, embodiments of which are defined herein.
In the supra-compressed or transcritical state, the CO2 refrigerant is used to heat a secondary refrigerant via heat-reclaim exchanger 34, via line 33. In the heat-reclaim exchanger 34, the CO2 refrigerant is in a heat-exchange relation with a secondary refrigerant circulating in the secondary refrigerant circuit 35. Alternatively, the heat-reclaim exchanger 34 may be part of a coil of a convection heating unit, etc. In an embodiment, the heat-reclaim exchanger 34, whether directly or via the secondary circuit, is used to heat the water used in the ice-playing surface complex (for meeting the hot water demand for showers, etc), for heating the surroundings of the ice-playing surface, or for melting zamboni residue in the ice dump, among other possibilities.
The secondary refrigerant is preferably an environmentally-sound refrigerant, such as water or glycol (although other refrigerants could be used as well), that is used as a heat-transfer fluid.
Because of the supra-compressed or transcritical state of the CO2 refrigerant, the secondary refrigerant circulating in the circuit 35 reaches a high temperature. Accordingly, due to the high temperature of the secondary refrigerant, lines of smaller diameter may be used for the secondary refrigerant circuit 35. It is pointed out that the secondary refrigerant circuit 35 may be the largest of the circuits of the refrigeration system 1 in terms of quantity of refrigerant.
Therefore, the compression of the CO2 refrigerant into a transcritical state by the transcritical circuit allows the lines of the secondary refrigerant circuit 35 to be reduced in terms of diameter.
A gas cooling stage 36 is provided in the transcritical circuit.
The gas cooling stage 36 absorbs excess heat from the CO2 refrigerant in the transcritical state, in view of directing the CO2 refrigerant to the heat exchanger 31.
Although it is illustrated in a parallel relation with the heat-reclaim exchanger 34, the gas cooling stage 36 may be in series therewith, or in any other suitable arrangement.
Moreover, a geothermal gas cooling stage 37 may be provided, to use the geothermal cool to absorb heat.
Although not shown, appropriate valves are provided so as to control the amount of CO2 refrigerant directed to the gas cooling stage 36, in view of the heat demand from the heat-reclaim exchanger 34.
Moreover, a bypass line may be provided to bypass the heat-reclaim exchanger 34, the gas cooling stage 36 and the geothermal gas cooling 37.
A CO2 pressure-regulating valve 39 is provided to maintain appropriate pressures at the stages 34 and 36, and in the heat exchanger 31. The CO2 transcritical pressure-regulating valve 39 is for instance a DanfossTM valve. Any other suitable pressure-control device may be used as an alternative to the valve 39, such as any type of valve or loop.
It is considered to operate the supra-compression circuit (i.e., supra compression 32) with higher operating pressure.
CO2 refrigerant has a suitable efficiency at a higher pressure.
More specifically, more heat can be extracted when the pressure is higher.
Referring to Fig. 2, the CO2 refrigeration system 2 is similar to the CO2 refrigeration system 1, but comprises an evaporation exchanger 16, by which the CO2 refrigerant of the evaporation circuit 10 absorbs heat from a closed circuit of pipes of the ice-playing surface refrigeration stage 17.
An alternative refrigerant circulates in the closed circuit of pipes of the ice-playing surface refrigeration stage 17, such as brine, glycol, or the like.
Although not fully illustrated, numerous valves are provided to control the operation of the CO2 refrigeration system 1 as described above.
Moreover, a controller ensures that the various stages of the refrigeration system 1 operate as described, for instance by having a plurality of sensors places throughout the refrigeration system 1.
Numerous other components may be added to the refrigeration systems 1 and 2 (e.g., valves, tanks, pumps, compressors, pressure-relief systems, etc.), to support the configurations illustrated in Figs. 1 and 2.
It is within the ambit of the present invention to cover any obvious modifications of the embodiments described herein, provided such modifications fall within the scope of the appended claims.
The CO2 evaporation circuit 10 comprises a condensation reservoir 12 accumulating CO2 refrigerant in a liquid and gaseous state.
The CO2 evaporation circuit 10 is in a heat-exchange relation with a condensation circuit that absorbs heat from the CO2 refrigerant.
Line 14 directs CO2 refrigerant from the condensation reservoir 12 to an evaporation stage, with a flow of CO2 refrigerant induced by pump and/or an expansion valve(s) as generally indicated as 15.
As is shown in Fig. 1, the CO2 refrigerant is then fed to the ice-playing surface evaporation stage 17.
The ice-playing surface evaporation stage 17 of = 15 Fig. 1 consists of a circuit of pipes positioned under the ice-playing surface, in which the CO2 refrigerant circulates to absorb heat from fluid being frozen to form the ice-playing surface, or to maintain the ice-playing surface frozen.
CO2 refrigerant exiting the evaporation stage 17 is directed to the condensation reservoir 12, by way of line 18.
The CO2 evaporation circuit 10 is in a heat-exchange relation with a transfer circuit 20. The transfer circuit 20 is for instance of the type in which a transfer refrigerant (e.gõ alcohol-based such as glycol, water, brine or the like) cycles. A condensation heat exchanger 21 is in fluid communication with the condensation reservoir 12, so as to receive CO2 refrigerant in a gaseous state, whereby the transfer refrigerant absorbs heat from the CO2 refrigerant in the heat exchanger 21.
According to an embodiment, the condensation heat exchanger 21 has a coil that is positioned inside the condensation reservoir 12.
The condensation heat exchanger 21 may also receive CO2 refrigerant directly from line 14, or from line 18. The transfer circuit 20 is a closed circuit featuring lines 22 and 23 as well as pump 24 to cycle the transfer refrigerant between the heat exchanger 21 and an evaporation heat exchanger 31 of a supra-compression circuit 30.
Accordingly, the transfer refrigerant absorbs heat from the CO2 refrigerant circulating in the CO2 evaporation circuit 10, and releases the heat to the CO2 refrigerant circulating in the supra-compression circuit 30.
In the transfer circuit 20, the condensation refrigerant circulates between the heat exchanger 21 in which the transfer refrigerant absorbs heat, and the heat exchanger 31 in which the transfer refrigerant absorbs heat.
The supra-compression circuit 30 (i.e., transcritical circuit if operated at transcritical pressures) is provided to compress CO2 refrigerant to a transcritical state, for heating purposes, or supra-compressed state.
The heat exchanger 31 vaporizes the CO2 refrigerant fed to a supra-compression stage 32. The supra-compression stage 32 features one or more compressors (e.g., BockTM, DorinTm) , that compress the CO2 refrigerant to a supra-compressed or transcritical state.
Upon exiting the supra-compression stage 32, the CO2 refrigerant must be cooled by a cooling stage, embodiments of which are defined herein.
In the supra-compressed or transcritical state, the CO2 refrigerant is used to heat a secondary refrigerant via heat-reclaim exchanger 34, via line 33. In the heat-reclaim exchanger 34, the CO2 refrigerant is in a heat-exchange relation with a secondary refrigerant circulating in the secondary refrigerant circuit 35. Alternatively, the heat-reclaim exchanger 34 may be part of a coil of a convection heating unit, etc. In an embodiment, the heat-reclaim exchanger 34, whether directly or via the secondary circuit, is used to heat the water used in the ice-playing surface complex (for meeting the hot water demand for showers, etc), for heating the surroundings of the ice-playing surface, or for melting zamboni residue in the ice dump, among other possibilities.
The secondary refrigerant is preferably an environmentally-sound refrigerant, such as water or glycol (although other refrigerants could be used as well), that is used as a heat-transfer fluid.
Because of the supra-compressed or transcritical state of the CO2 refrigerant, the secondary refrigerant circulating in the circuit 35 reaches a high temperature. Accordingly, due to the high temperature of the secondary refrigerant, lines of smaller diameter may be used for the secondary refrigerant circuit 35. It is pointed out that the secondary refrigerant circuit 35 may be the largest of the circuits of the refrigeration system 1 in terms of quantity of refrigerant.
Therefore, the compression of the CO2 refrigerant into a transcritical state by the transcritical circuit allows the lines of the secondary refrigerant circuit 35 to be reduced in terms of diameter.
A gas cooling stage 36 is provided in the transcritical circuit.
The gas cooling stage 36 absorbs excess heat from the CO2 refrigerant in the transcritical state, in view of directing the CO2 refrigerant to the heat exchanger 31.
Although it is illustrated in a parallel relation with the heat-reclaim exchanger 34, the gas cooling stage 36 may be in series therewith, or in any other suitable arrangement.
Moreover, a geothermal gas cooling stage 37 may be provided, to use the geothermal cool to absorb heat.
Although not shown, appropriate valves are provided so as to control the amount of CO2 refrigerant directed to the gas cooling stage 36, in view of the heat demand from the heat-reclaim exchanger 34.
Moreover, a bypass line may be provided to bypass the heat-reclaim exchanger 34, the gas cooling stage 36 and the geothermal gas cooling 37.
A CO2 pressure-regulating valve 39 is provided to maintain appropriate pressures at the stages 34 and 36, and in the heat exchanger 31. The CO2 transcritical pressure-regulating valve 39 is for instance a DanfossTM valve. Any other suitable pressure-control device may be used as an alternative to the valve 39, such as any type of valve or loop.
It is considered to operate the supra-compression circuit (i.e., supra compression 32) with higher operating pressure.
CO2 refrigerant has a suitable efficiency at a higher pressure.
More specifically, more heat can be extracted when the pressure is higher.
Referring to Fig. 2, the CO2 refrigeration system 2 is similar to the CO2 refrigeration system 1, but comprises an evaporation exchanger 16, by which the CO2 refrigerant of the evaporation circuit 10 absorbs heat from a closed circuit of pipes of the ice-playing surface refrigeration stage 17.
An alternative refrigerant circulates in the closed circuit of pipes of the ice-playing surface refrigeration stage 17, such as brine, glycol, or the like.
Although not fully illustrated, numerous valves are provided to control the operation of the CO2 refrigeration system 1 as described above.
Moreover, a controller ensures that the various stages of the refrigeration system 1 operate as described, for instance by having a plurality of sensors places throughout the refrigeration system 1.
Numerous other components may be added to the refrigeration systems 1 and 2 (e.g., valves, tanks, pumps, compressors, pressure-relief systems, etc.), to support the configurations illustrated in Figs. 1 and 2.
It is within the ambit of the present invention to cover any obvious modifications of the embodiments described herein, provided such modifications fall within the scope of the appended claims.
Claims (9)
1. A CO2 refrigeration system comprising a transfer circuit for heat exchange between a supracompression circuit of CO2 refrigerant, and an evaporation circuit of CO2 refrigerant;
a transfer circuit in which a transfer refrigerant circulates between a condensation heat exchanger to absorb heat from the CO2 refrigerant of the evaporation circuit, and an evaporation heat exchanger to release heat to the CO2 refrigerant of the supracompression circuit;
the supracompression circuit comprising a compression stage in which CO2 refrigerant having absorbed heat in the evaporation heat exchanger is compressed to at least a supracompression state, a cooling stage in which the CO2 refrigerant from the compression stage releases heat, and a pressure-regulating unit in a line extending from the cooling stage to the evaporation heat exchanger to maintain a pressure differential therebetween;
the evaporation circuit receiving CO2 refrigerant having released heat in the condensation heat exchanger, the evaporation circuit comprising a condensation reservoir in which CO2 refrigerant is accumulated in a liquid state, and an evaporation stage in which the CO2 refrigerant from the condensation reservoir absorbs heat to cool an ice-playing surface, to then return to one of the condensation reservoir and the condensation exchanger.
a transfer circuit in which a transfer refrigerant circulates between a condensation heat exchanger to absorb heat from the CO2 refrigerant of the evaporation circuit, and an evaporation heat exchanger to release heat to the CO2 refrigerant of the supracompression circuit;
the supracompression circuit comprising a compression stage in which CO2 refrigerant having absorbed heat in the evaporation heat exchanger is compressed to at least a supracompression state, a cooling stage in which the CO2 refrigerant from the compression stage releases heat, and a pressure-regulating unit in a line extending from the cooling stage to the evaporation heat exchanger to maintain a pressure differential therebetween;
the evaporation circuit receiving CO2 refrigerant having released heat in the condensation heat exchanger, the evaporation circuit comprising a condensation reservoir in which CO2 refrigerant is accumulated in a liquid state, and an evaporation stage in which the CO2 refrigerant from the condensation reservoir absorbs heat to cool an ice-playing surface, to then return to one of the condensation reservoir and the condensation exchanger.
2. The CO2 refrigeration system according to claim 1, wherein the evaporation stage of the evaporation circuit comprises a heat exchanger being connected to an ice-playing surface refrigeration circuit in which cycles a second refrigerant, such that the CO2 refrigerant absorbs heat from the second refrigerant in the heat exchanger.
3. The CO2 refrigeration system according to claim 1, wherein the evaporation stage of the evaporation circuit comprises pipes under the ice-playing surface in which circulates the CO2 refrigerant to refrigerate the ice-playing surface.
4. The CO2 refrigeration system according to claim 3, further comprising at least one pump in the evaporation circuit to induce a flow of the CO2 refrigerant in a liquid state in the pipes under the ice-playing surface.
5. The CO2 refrigeration system according to claim 1, wherein the cooling stage comprises at least one of a gas-cooling unit, a heat-reclaim exchanger, and a geothermal gas cooling unit.
6. The CO2 refrigeration system according to any one of claims 1 to 5, wherein the condensation heat exchanger is positioned in a line extending from the condensation reservoir to the evaporation stage.
7. The CO2 refrigeration system according to any one of claims 1 to 5, wherein a line extends from a top of the condensation reservoir to the condensation heat exchanger to feed gaseous CO2 refrigerant to the condensation heat exchanger.
8. The CO2 refrigeration system according to any one of claims 1 to 5, wherein the condensation heat exchanger is a coil in the condensation reservoir.
9. The CO2 refrigeration system according to any one of claims 1 to 8, wherein the CO2 refrigerant in the supra-compression circuit is compressed to a transcritical state.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA2766361A CA2766361A1 (en) | 2012-01-30 | 2012-01-30 | Co2 refrigeration system for ice-playing surface |
| US13/753,611 US20140007603A1 (en) | 2012-01-30 | 2013-01-30 | Co2 refrigeration system for ice-playing surface |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA2766361A CA2766361A1 (en) | 2012-01-30 | 2012-01-30 | Co2 refrigeration system for ice-playing surface |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2766361A1 true CA2766361A1 (en) | 2013-07-30 |
Family
ID=48901211
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA2766361A Abandoned CA2766361A1 (en) | 2012-01-30 | 2012-01-30 | Co2 refrigeration system for ice-playing surface |
Country Status (2)
| Country | Link |
|---|---|
| US (1) | US20140007603A1 (en) |
| CA (1) | CA2766361A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110285596A (en) * | 2019-07-12 | 2019-09-27 | 山东神舟制冷设备有限公司 | A kind of pure CO2Refrigerating system of ice rink |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11029068B2 (en) | 2013-05-03 | 2021-06-08 | Hill Phoenix, Inc. | Systems and methods for pressure control in a CO2 refrigeration system |
| US11125483B2 (en) | 2016-06-21 | 2021-09-21 | Hill Phoenix, Inc. | Refrigeration system with condenser temperature differential setpoint control |
| US11796227B2 (en) | 2018-05-24 | 2023-10-24 | Hill Phoenix, Inc. | Refrigeration system with oil control system |
| US11397032B2 (en) | 2018-06-05 | 2022-07-26 | Hill Phoenix, Inc. | CO2 refrigeration system with magnetic refrigeration system cooling |
| US10663201B2 (en) | 2018-10-23 | 2020-05-26 | Hill Phoenix, Inc. | CO2 refrigeration system with supercritical subcooling control |
| CN114739070B (en) * | 2022-02-28 | 2024-03-26 | 天津大学 | Transcritical carbon dioxide double-stage compression ice making system and control method |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3751935A (en) * | 1971-12-02 | 1973-08-14 | Calmac Manuf Corp | Method and system for creating and maintaining an ice slab |
| US5575159A (en) * | 1995-06-02 | 1996-11-19 | Dittell; Edward W. | Heat energy transfer system |
| US7065979B2 (en) * | 2002-10-30 | 2006-06-27 | Delaware Capital Formation, Inc. | Refrigeration system |
| US6796139B2 (en) * | 2003-02-27 | 2004-09-28 | Layne Christensen Company | Method and apparatus for artificial ground freezing |
| US20080223074A1 (en) * | 2007-03-09 | 2008-09-18 | Johnson Controls Technology Company | Refrigeration system |
| CA2599769C (en) * | 2007-08-30 | 2011-11-01 | Mayekawa Mfg. Co., Ltd. | System and method for creating rink ice and utilizing high-temperature heat generated when creating rink ice |
| EP2229562B1 (en) * | 2008-01-17 | 2018-09-05 | Carrier Corporation | Carbon dioxide refrigerant vapor compression system |
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2012
- 2012-01-30 CA CA2766361A patent/CA2766361A1/en not_active Abandoned
-
2013
- 2013-01-30 US US13/753,611 patent/US20140007603A1/en not_active Abandoned
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110285596A (en) * | 2019-07-12 | 2019-09-27 | 山东神舟制冷设备有限公司 | A kind of pure CO2Refrigerating system of ice rink |
Also Published As
| Publication number | Publication date |
|---|---|
| US20140007603A1 (en) | 2014-01-09 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |
Effective date: 20170710 |