CO2 refrigeration system

Abstract

A CO2 refrigeration system for an ice-playing surface comprises an evaporation stage in which heat is absorbed from an ice-playing surface. CO2 compressors in a compression stage compress CO2 refrigerant subcritically and transcritically. A gas cooling stage has a plurality of heat-reclaim units reclaiming heat from the CO2 refrigerant. A pressure-regulating device is downstream of the gas cooling stage, to control a pressure of the CO2 refrigerant in the gas cooling stage. A reservoir is downstream of the pressure-regulating device for receiving CO2 refrigerant in a liquid state. A controller operates the pressure-regulating device to control the pressure of the CO2 refrigerant in the gas cooling stage as a function of the heat demand of the plurality of heat-reclaim units, the controller causing the pressure of the CO2 refrigerant to reach a transcritical level as a function of a heat demand of the plurality of heat-reclaim units.

Description

FIELD OF THE APPLICATION

The present application relates to refrigeration systems, 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 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.

As alternatives to CFCs and HCFCs, ammonia, hydrocarbons 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 that addresses issues associated with the prior art.

Therefore, in accordance with a first embodiment of the present application, there is provided a CO₂ refrigeration system for an ice-playing surface, comprising: a supra-compression portion comprising a supra-compression stage in which CO₂ refrigerant is supra-compressed and a cooling stage in which the supra-compressed CO₂ refrigerant releases heat; a condensation reservoir accumulating a portion of the CO₂ refrigerant in a liquid state; pressure-regulating means between the supra-compression portion and the condensation reservoir to control a pressure of the supra-compressed CO₂ refrigerant being directed to the condensation reservoir; and an evaporation stage receiving the CO₂ refrigerant from the condensation reservoir, the evaporation stage having a circuit of pipes arranged under the ice-playing surface, whereby the CO₂ refrigerant circulating in the circuit of pipes of the evaporation stage absorbs heat from the ice-playing surface.

Further in accordance with the first embodiment, the system further comprises a secondary refrigerant circuit in which circulates a secondary refrigerant, and wherein the supra-compression portion comprises at least one heat reclaim exchanger related to the secondary refrigerant circuit, the at least one heat reclaim exchanger causing the supra-compressed CO₂ refrigerant to release heat to the secondary refrigerant.

Still further in accordance with the first embodiment, the heat reclaim exchanger and the gas cooling stage are in at least one of a parallel arrangement, and a series arrangement.

Still further in accordance with the first embodiment, the system further comprises at least one water tank in the secondary refrigerant circuit, with the at least one water tank comprising a heat exchanger in which circulates the secondary refrigerant to heat water in the water tank.

Still further in accordance with the first embodiment, the secondary refrigerant circuit further comprises at least one water tank, with the at least one water tank comprising a heat exchanger in which circulates the CO₂ refrigerant to heat water in the water tank.

Still further in accordance with the first embodiment, the secondary refrigerant circuit comprises at least one melting heat exchanger in an ice dump, the melting heat exchanger receiving secondary refrigerant to release heat to zamboni residue in the ice dump.

Still further in accordance with the first embodiment, the system further comprises a suction line extending from a top of the condensation reservoir to an inlet of the supra-compression stage, with a valve in said suction line, such that gaseous CO₂ refrigerant in the condensation reservoir is directed to the supra-compression stage.

Still further in accordance with the first embodiment, the system further comprises a heat exchanger in said suction line for heat exchange between the gaseous CO₂ refrigerant and CO₂ refrigerant exiting the cooling stage.

Still further in accordance with the first embodiment, the system comprises a pressure-controlling unit in said suction line to control a pressure differential between the condensation reservoir and the supra-compression stage.

Still further in accordance with the first embodiment, the system further comprises an expansion stage between the condensation reservoir and the evaporation stage to vaporize the CO₂ refrigerant fed to the circuit of pipes.

Still further in accordance with the first embodiment, the system further comprises at least one pump between the condensation reservoir and the evaporation stage to induce a flow of CO₂ refrigerant to the evaporation stage.

Still further in accordance with the first embodiment, the supra-compression stage compresses the CO₂ refrigerant to a transcritical state.

In accordance with a second embodiment of the present application, there is provided a CO₂ refrigeration system for an ice-playing surface, comprising: a CO₂ refrigerant circuit comprising a condensation reservoir accumulating a portion of the CO₂ refrigerant in a liquid state, and an evaporation stage receiving the CO₂ refrigerant from the condensation reservoir, the evaporation stage having a circuit of pipes arranged under the ice-playing surface, whereby the CO₂ refrigerant circulating in the circuit of pipes of the evaporation stage absorbs heat from the ice-playing surface; an independent refrigerant circuit in heat-exchange relation with the CO₂ refrigerant of the CO₂ refrigerant circuit, the independent refrigerant circuit comprising a compression stage with at least one magnetically-operated compressor to compress a secondary refrigerant, a condensation stage in which the secondary refrigerant releases heat, and an evaporation stage in which the secondary refrigerant is in heat exchange relation with the CO₂ refrigerant circuit by a heat exchanger to absorb heat therefrom.

Further in accordance with the second embodiment, the system further comprises a line extending from a top of the condensation reservoir to the heat exchanger, such that gaseous CO₂ refrigerant in the condensation reservoir is directed to the independent refrigerant circuit.

Still further in accordance with the present disclosure, there is provided a CO₂ refrigeration system for an ice-playing surface, comprising: a compression portion comprising: a compression stage comprising at least one compressor in which CO₂ refrigerant is compressed to a transcritical state; a gas cooling stage in which the CO₂ refrigerant compressed to the transcritical state releases heat by heat exchange with a gas; pressure-regulating means downstream of the gas cooling stage to control a pressure of the CO₂ refrigerant in the compression portion of the CO₂ refrigeration system; and an oil circuit in the CO₂ refrigeration system, the oil circuit collecting oil downstream of the at least one compressor in the compression stage, the oil circuit directing the oil upstream of the at least one compressor for the CO₂ refrigerant fed to the compressor to have an oil content.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a block diagram of a CO₂ refrigeration system in accordance with an embodiment of the present application;

FIG. 2 is a block diagram of the CO₂ refrigeration system of FIG. 1, with an example of operating pressures for a cold climate application;

FIG. 3 is a block diagram of the CO₂ refrigeration system of FIG. 1, with an example of operating pressures for a warm climate application; and

FIG. 4 is a schematic view of a line used with the CO₂ refrigeration system, in accordance with another embodiment of the present application.

FIG. 5 is a block diagram of a CO₂ refrigeration system in accordance with another embodiment,

FIG. 6 is a schematic view of a line configuration for a refrigeration unit, in accordance with yet another embodiment of the present application;

FIG. 7 is a block diagram of a CO₂ refrigeration system in accordance with another embodiment, with dedicated compression for defrost;

FIG. 8 is a block diagram of a CO₂ refrigeration system in accordance with another embodiment, e.g., for a skating rink application;

FIG. 9 is a block diagram of a CO₂ refrigeration system in accordance with another embodiment, with a supra-compression providing defrost;

FIG. 10 is a block diagram of a CO₂ refrigeration system in accordance with another embodiment, with cascaded compression;

FIG. 11 is a block diagram of a CO₂ refrigeration system in accordance with another embodiment, with suction accumulation upstream of a supra-compression stage;

FIG. 12 is a block diagram of a CO₂ refrigeration system in accordance with another embodiment, with a heat-exchanger for defrost refrigerant; and

FIG. 13 is a schematic view of a desiccant system in accordance with another embodiment of the present application.

DESCRIPTION OF PREFERRED EMBODIMENTS

Referring to FIG. 1, a CO₂ refrigeration system in accordance with an embodiment is illustrated at 1. The CO₂ refrigeration system 1 has a CO₂ refrigeration circuit comprising a CO₂ compression stage 10. CO₂ refrigerant is compressed in the compression stage 10, and is subsequently directed via line 11 to a condensation reservoir 12, or to a heat-reclaim stage 13.

The condensation reservoir 12 accumulates CO₂ refrigerant in a liquid and gaseous state, and is in a heat-exchange relation with a condensation circuit that absorbs heat from the CO₂ refrigerant. The condensation circuit is described in further detail hereinafter. Moreover, a transcritical circuit and a defrost circuit may supply CO₂ refrigerant to the condensation reservoir 12, as is described in further detail hereinafter.

The heat-reclaim stage 13 is provided to absorb heat from the CO₂ refrigerant exiting from the compression stage 10. The heat-reclaim stage 13 may take various forms, such as that of a heat exchanger by which the CO₂ refrigerant is in heat exchange with an alcohol-based refrigerant circulating in a closed loop. As another example, the heat-reclaim stage 13 features coils by which the CO₂ refrigerant releases heat to a water tank.

Line 14 directs CO₂ refrigerant from the condensation reservoir 12 to an evaporation stage via expansion valves 15. As is shown in FIG. 1, the CO₂ refrigerant is supplied in a liquid state by the condensation reservoir 12 into line 14. The expansion valves 15 control the pressure of the CO₂ refrigerant, which is then fed to either low-temperature evaporation stage 16 or medium-temperature evaporation stage 17. Both the evaporation stages 16 and 17 feature evaporators associated with refrigerated enclosures, such as closed or opened refrigerators, freezers or the like. It is pointed out that the expansion valves 15 may be part of a refrigeration pack in the mechanical room, as opposed to being at the refrigeration cabinets. As a result, flexible lines (e.g., plastic non-rigid lines) could extend from the expansion valves 15 to diffuser upstream of the coils of the evaporation stages 16 and 17. The valves 15 may be at the refrigeration cabinets, at the refrigeration pack in a mechanical room, or any other suitable location.

CO₂ refrigerant exiting the low-temperature evaporation stage 16 is directed to the CO₂ compression stage 10 via line 18 to complete a refrigeration cycle. A heat exchanger 19 is provided in the line 18, and ensures that the CO₂ refrigerant is fed to the compression stage 10 in a gaseous state. Other components, such as a liquid accumulator, may be used as an alternative to the heat exchanger 19. As described hereinafter, the heat exchanger 19 may be associated with a condensation circuit.

CO₂ refrigerant exiting the medium-temperature evaporation stage 17 is directed to the transcritical circuit as is described hereinafter.

A condensation circuit has a heat exchanger 20. The heat exchanger 20 is in fluid communication with the condensation reservoir 12, so as to receive CO₂ refrigerant in a gaseous state. The condensation circuit is closed and comprises a condensation refrigerant that also circulates in the heat exchanger 20 so as to absorb heat from the CO₂ refrigerant.

In the condensation circuit, the condensation refrigerant circulates between the heat exchanger 20 in which the condensation refrigerant absorbs heat, a compression stage 21 in which the condensation refrigerant is compressed, and a condensation stage 22 in which the condensation refrigerant releases heat. The compression stage 21 may use Turbocor™ compressors. In an example, the condensation stage 22 features heat reclaiming (e.g., using a heat exchanger with a heat-transfer fluid) in parallel or in series with other components of the condensation stage 22, so as to reclaim heat from the CO₂ refrigerant. Although not shown, the condensation circuit may be used in conjunction with the heat exchanger 19, so as to absorb heat from the CO₂ refrigerant being directed to the compression stage 10. In this case, the condensation refrigerant is in a heat-exchange relation with the CO₂ refrigerant.

It is pointed out that the condensation circuit may be used with more than one CO₂ refrigeration circuit. In such a case, the condensation circuit features a plurality of heat exchangers 20, for instance with one for each of the CO₂ refrigeration circuits.

Examples of the condensation refrigerant are refrigerants such as R-404 and R-507, amongst numerous examples. It is observed that the condensation circuit may be confined to its own casing as illustrated in FIG. 1. Moreover, considering that the condensation circuit is preferably limited to absorbing heat from stages on a refrigeration pack (e.g., condensation reservoir 12, suction header in line 18), the condensation circuit does not contain a large volume of refrigerant when compared to the CO₂ refrigeration circuit, of a secondary refrigerant circuit defined hereinafter.

The transcritical circuit (i.e., supra-compression circuit) is provided to compress the CO₂ refrigerant exiting from the medium-temperature evaporation stage 17 to a transcritical state, for heating purposes, or supra-compressed state. In both compression states, the CO₂ refrigerant is pressurized in view of maintaining the condensation reservoir 12 at a high enough pressure to allow vaporized CO₂ refrigerant to be circulated in the evaporation stages 16 and 17, as opposed to liquid CO₂ refrigerant.

A line 30 relates the medium-temperature evaporation stage 17 to a heat exchanger 31 and subsequently to a supra-compression stage 32. The heat exchanger 31 is provided to vaporize the CO₂ refrigerant fed to the transcritical compression stage 32. The supra-compression stage 32 features one or more compressors (e.g., Bock™, Dorin™), that compress the CO₂ refrigerant to a supra-compressed or transcritical state.

In the transcritical state, the CO₂ refrigerant is used to heat a secondary refrigerant via heat-reclaim exchanger 34. In the heat-reclaim exchanger 34, the CO₂ refrigerant is in a heat-exchange relation with the secondary refrigerant circulating in the secondary refrigerant circuit 35. The secondary refrigerant is preferably an environmentally-sound refrigerant, such as water or glycol, that is used as a heat-transfer fluid. Because of the 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 is 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 re-injecting the CO₂ refrigerant in the condensation reservoir 12. 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. 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.

In warmer climates in which the demand for heat is smaller, the CO₂ refrigerant is compressed to a supra-compressed state, namely at a high enough pressure to allow the expansion of the CO₂ refrigerant at the exit of the condensation reservoir 12, so as to reduce the amount of CO₂ refrigerant circulating in the refrigeration circuit. A by-pass line is provided to illustrate that the heat-reclaim exchanger 24 and the gas cooling stage 36 are optional for warmer climates.

The gas cooling stage 36 may feature a fan blowing a gas refrigerant on coils. The speed of the fan may be controlled as a function of the heat demand of the heat reclaim exchanger 34. For an increased speed of the fan, there results an increase in the temperature differential at opposite ends of the gas cooling stage 36.

Lines 37 and 38 return the CO₂ refrigerant to the condensation reservoir 12, and thus to the refrigeration circuit. The line 37 feeds the heat exchanger 31 such that the CO₂ refrigerant exiting the stages 34 and 36 release heat to the CO₂ refrigerant fed to the supra-compression stage 32. Accordingly, the CO₂ refrigerant fed to the supra-compression stage 32 is in a gaseous state.

In the case of transcritical compression, a CO₂ transcritical pressure-regulating valve 39 is provided to maintain appropriate pressures at the stages 34 and 36, and in the condensation reservoir 12. The CO₂ transcritical pressure-regulating valve 39 is for instance a Danfoss™ 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.

The condensation circuit and the supra-compression circuit allow the condensation reservoir 12 to store refrigerant at a relatively medium pressure. Accordingly, no pump may be required to induce the flow of refrigerant from the condensation reservoir 12 to the evaporation stages 16 and 17. As CO₂ refrigerant is vaporized downstream of the expansion valves 15, the amount of CO₂ refrigerant in the refrigeration circuit is reduced, especially if the expansion valves 15 are in the refrigeration pack.

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.

The refrigeration system 1 may be provided with a refrigerant defrost system. In FIG. 1, a portion of the CO₂ refrigerant exiting from the compression stage 10 is directed to the evaporation stages 16 and 17. Although not shown, appropriate valves and pressure-reducing devices are provided to stop the flow of cooling CO₂ refrigerant in the evaporators in view of the defrost. The defrost CO₂ refrigerant releases heat to defrost any frost build-up on the evaporators of the evaporation stages 16 and/or 17.

Although not shown, other compression configurations may be used to supply defrost refrigerant to the evaporators, such as dedicated compressors, cascaded compressors of the like.

Line 41 directs the defrost CO₂ refrigerant having released heat to the defrost reservoir 42. The defrost reservoir 42 accumulates the defrost CO₂ refrigerant, and features a line 43 with a control valve (e.g., exhaust valve, check valve), so as to allow gaseous CO₂ refrigerant to be sucked back into the CO₂ refrigeration circuit by the CO₂ compression stage 10. The defrost reservoir 42 is an option, as the evaporation stages 16 and 17 may direct the refrigerant to other reservoirs or accumulators of any other refrigeration system presenter herein.

A flush of the defrost reservoir 42 may be performed periodically, so as to empty the defrost reservoir 42. Accordingly, lines 44 and 45, with appropriate valves, allow the flush of the liquid CO₂ refrigerant from the defrost reservoir 42 to the condensation reservoir 12.

A pressure-reducing valve 46 may be provided in the line 40 or line 11 to regulate a pressure of the defrost CO₂ refrigerant fed to the evaporation stage 16 and/or 17 for defrost. Valves, such as check valve 47, are as relief valves for the evaporation stages 16 and 17. For instance, in case of a power shortage, the CO₂ refrigerant in the evaporators may increase in pressure. Accordingly, the check valves 47 open at a threshold pressure to allow the CO₂ refrigerant to reach the defrost reservoir 42.

Considering that the compressors of the CO₂ compression stage 10 or of the compression stage 21 are low-consumption compressors, these compressors may be operated during a power outage to maintain suitable refrigerating conditions in the evaporation stages 16 and 17. The compressors of the compression stage 21 may also be Turbocor™ compressors.

As an alternative to the defrost circuit, the evaporators of the evaporation stages 16 and 17 may be equipped with electric coils for the electric defrost of the evaporators.

In an embodiment, the casing enclosing the condensation circuit may also comprise an air-conditioning unit 50. Accordingly, the roof-top equipment associated with the refrigeration system 1 is provided in a single casing, thereby facilitating the installation thereof. Moreover, it is considered to unite as many components of the refrigeration system 1 in a single refrigeration pack. For instance, the compressors of the CO₂ compression stage 10, the condensation reservoir 12, the expansion valves 15, and optionally the compressors from the supra-compression stage 32, as well as the defrost reservoir 42 may all be provided in a same pack, with most of the lines joining these components. The installation is therefore simplified by such a configuration.

In order to illustrate the operating pressures of the CO₂ refrigeration system 1 in cold and warm climates, FIGS. 2 and 3 are respectively provided with pressure values. It is pointed out that all values are just an illustration, whereby pressure values could be higher or lower. FIG. 2 shows operating pressures for the CO₂ refrigeration system 1 as used in cold climates (e.g., winter conditions in colder regions), with a demand for heat by the secondary refrigerant circuit 35. FIG. 3 shows operating pressures for the CO₂ refrigeration system as used in warm climates (e.g., summer conditions, warmer regions).

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.

Referring to FIG. 3, there is illustrated a safety valve circuit 55 so as to ensure that the refrigerant pressure in the coils of the evaporation stages 16 and 17 does not exceed a given maximum value (e.g., 410 Psi), which may result in damages to the coils. The safety valve circuits 55 extends from the evaporation stages 16 and 17 (e.g., lines at the exit of the coils) to the defrost reservoir 42. A safety valve 56 is provided in the circuit, and operates by monitoring the pressure in the coils and opening as a result of the pressure reaching the maximum value. The defrost reservoir 42 then absorbs the excess pressure by receiving the refrigerant. The defrost reservoir 42 subsequently discharges the refrigerant using the lines described previously.

Referring to FIG. 4, a line that may be used in the CO₂ refrigeration system 1 is illustrated at 60. The line 60 is a flexible hose adapted to support the relatively high pressures associated with CO₂ refrigerant. One suitable example of flexible hose is the “Transfer Oil” hydraulic hose by Gomax™. The hose 60 is rodded into a conduit of sleeves 61 of an insulating material, such as urethane, positioned end to end to cover the length of hose 60. A plurality of hoses 60 may be used with a single sleeve 61, provided the inner diameter of the sleeve 61 is large enough to receive the hoses 60. Therefore, by the use of flexible hoses, the installation of the lines is simplified. Previous lines required welding operation to join tubes of metallic material.

Referring to FIG. 5, an alternative embodiment of the CO₂ refrigeration system 1 of FIGS. 1-3 is illustrated at 70. The CO₂ refrigeration systems 1 and 70 have numerous common stages and lines, whereby like elements will bear like reference numerals. One difference between the CO₂ refrigeration systems 1 and 70 is the absence of a condensation circuit such as the one having the heat exchanger 20 in FIGS. 1-3. Rather, the CO₂ refrigerant in the condensation reservoir 12 is cooled by the transcritical circuit (i.e., supra-compression circuit) featuring the heat exchanger 31.

Therefore, a line 71 extends from the condensation reservoir 12 and directs CO₂ refrigerant to the hot side of the heat exchanger 31, which heat exchanger 31 is optional and is used to vaporize the CO₂ refrigerant if necessary. The line 71 may be collecting gas CO₂ refrigerant at a top of the condensation reservoir 12 to direct the CO₂ refrigerant to the heat exchanger 31. A pressure-reducing valve 72 is provided in line 71 to ensure that the CO₂ refrigerant reaches the heat exchanger 31 at a suitable pressure. The CO₂ refrigerant goes through the supra-compression circuit in the manner described previously, so as to lose heat, and return to the condensation reservoir 12 primarily in a liquid state.

It is pointed out that the configuration of the CO₂ refrigeration system 70 of FIG. 5 is such that a single refrigerant, namely CO₂ refrigerant, is used therein.

Referring to FIG. 6, an alternative line configuration is shown at 80, which line configuration is typically used to supply refrigerant to large refrigeration units (e.g., in freezer rooms). Line 81, typically a large diameter line, diverges into a plurality of smaller lines, from an expansion valve 82. Each smaller line may have a valve 83, and each feeds an own smaller refrigeration unit 84. As a result, some of the units 84 may be turned off, so as to meet more precisely the cool demand of an enclosure.

Referring to FIG. 7, yet another embodiment of a CO₂ refrigeration system is illustrated at 90. The CO₂ refrigeration systems 1 and 90 have numerous common stages and lines, whereby like elements will bear like reference numerals. One difference between the CO₂ refrigeration systems 1 and 90 is the presence of at least one dedicated compressor 10′ to compress defrost refrigerant. The discharge of the dedicated compressor 10′ goes at least partially to the defrost circuit, whereas the discharge of the other compressors 10 is directed to the refrigeration circuit. A line and valve (not shown) may be used to direct some excess refrigerant from the dedicated compressor 10′ to the refrigeration circuit. The CO₂ dedicated compressor 10′ may also be used to flush the defrost reservoir 42.

As an alternative, defrost could be made by directing refrigerant from the supra-compression circuit, into the defrost circuit, using an appropriate pressure-reducing valve.

Referring to FIG. 8, yet another embodiment of a CO₂ refrigeration system is illustrated at 100. The CO₂ refrigeration systems 70 (FIG. 5) and 90 have numerous common stages and lines, whereby like elements will bear like reference numerals. The CO₂ refrigeration system 100 is well suited for applications requiring low-temperature cooling, such as ice-skating rinks and industrial freezer applications.

The CO₂ refrigeration system 100 may be configured to operate without the CO₂ compression stages, due to the heat removal capacity of the supra-compression circuit. In such a configuration, a pump may circulate the refrigerant in the refrigeration circuit, from the condensation reservoir 12 to the low-temperature evaporation 16. In the ice-skating rink applications, the various heat absorbing components (e.g., the heat reclaim stage 13, the heat reclaim exchanger 34) may be used to melt zamboni residue in an ice dump. It is preferred not to use the supra-compression circuit when the CO₂ refrigeration system 100 is operated in warmer countries. The CO₂ refrigeration system 100 is more efficient with CO₂ compression in such climates.

Considering the nature of the refrigerant, plastic tubing or non-rigid lines may be used as an alternative to the rigid metallic lines previously used, between the mechanical room and the stages of the systems, such as the condensation stage 12 and the evaporation stages 16 and 17. One known type of pipes that can be used is Halcor Cusmart pipes, and features a non-rigid copper core with a plastic insulation sleeve about the core. Such configurations are cost-efficient in that no weld joints are required to interconnect pipes, as is the case for rigid metallic lines. Gutters, for instance having a trapezoid cross-section, may be used as a guide for lines.

Referring to FIG. 9, yet another embodiment of a CO₂ refrigeration system is illustrated at 110. The CO₂ refrigeration systems 1 and 110 have numerous common stages and lines, whereby like elements will bear like reference numerals. One difference between the CO₂ refrigeration systems 1 and 110 is line 111 directing CO₂ refrigerant from the supra-compression stage 32 to the evaporator stages 16 and 17 for defrost. Accordingly, the CO₂ refrigerant fed to the evaporation stage 16/17 is at a relatively high pressure—valve 114 may be provided to lower the pressure of the CO₂ refrigerant to an appropriate level (e.g., 500 Psi). The defrost refrigerant is then directed to the defrost reservoir 42. A valve 112 is provided to control the amount of defrost refrigerant from the reservoir 42 reintegrating the refrigeration cycle. Moreover, in order to maintain a suitable compression ratio in view of the operating pressure of the condensation reservoir 12, a pressure-reducing valve 113 is provided in the line 11, so as to reduce the pressure of the CO₂ refrigerant feeding the condensation reservoir 12.

Moreover, the refrigeration system 110 has a line 115 (with appropriate valves) selectively directing refrigerant from the supra-compression stage 32 to the defrost reservoir 42, to flush the reservoir 42 when required. It is pointed out that the heat exchangers 19 and 31 are optional, as is the condensation circuit featuring the compression stage 21.

Referring to FIG. 10, yet another embodiment of a CO₂ refrigeration system is illustrated at 120. The CO₂ refrigeration systems 70 and 120 have numerous common stages and lines, whereby like elements will bear like reference numerals. The CO₂ refrigeration system 120 has a cascaded arrangement for the two stages of CO₂ compression, namely compression stage 10 and supra-compression stage 32. More specifically, the refrigerant discharge from the compression stage 10 is fed to a suction accumulator 121, and CO₂ refrigerant in a gas state is sucked from a top of the accumulator 121 by the supra-compression stage 32.

The suction accumulator 121 also receives CO₂ refrigerant from the evaporation stage 17, optionally via heat exchanger 31. Gas CO₂ refrigerant from the condensation reservoir 12 may also be directed to the suction accumulator 121. The liquid CO₂ refrigerant from the suction accumulator 121 may be directed to the compression stage 10.

In order to maintain suitable conditions for the refrigerant at the inlet of the compression stage, a first suction accumulator 122 is provided downstream of the compression stage 10, which suction accumulator 122 receives CO₂ refrigerant from the suction accumulator 121 through a line (e.g., capillary) having a heat exchanger 123 for heat exchange with a discharge of the supracompression stage 32, or with a discharge of the compression stage 10. Moreover, liquid refrigerant from the suction accumulator 122 may be heated by line 124, in heat exchange with the discharge of the compression stage 10 or with supracompression stage 32, or simply by using an electric heater. The line 124 may then direct the vaporized refrigerant to the suction of the compression stage 10. In an embodiment, the line 124 collects liquid CO₂ refrigerant and oil at a bottom of the suction accumulator 122. Accordingly, the vaporized refrigerant has an oil content when fed to the compressors of the compression stage 10. The oil is then recuperated for instance in the suction accumulator 121. A similar loop may be performed to feed a mixture of CO₂ refrigerant and oil to the supra-compression stage 32.

In the embodiment in which the line 124 directs vaporized refrigerant to the suction of the compression stage 10, a valve 125 is provided in that case to maintain a pressure differential between the suction accumulator 122 and the suction of the compression stage 10, to allow the flow of refrigerant from line 124 into CO₂ compression stage 10. It is considered to use other components than suction accumulator 121, suction accumulator 122, line 124 and heat exchanger 123 to vaporize the refrigerant, such as a heating element, an air conditioning system, a heat exchanger and the like. It is also considered that CO₂ refrigerant leaving suction accumulator 121 and suction accumulator 122 be directed elsewhere in the CO₂ refrigeration system.

The cascaded compressor configuration of FIG. 10 is well suited to preserve the oil in the compression stage 10. More specifically, oil accumulating in the suction accumulator 121 is returned to the suction accumulator 122 via the line of heat-exchanger 123. The oil may then be sucked with refrigerant by the compression stage 10. Accordingly, the oil cycles between stages 10, 121 and 122. A similar cycle may be used for feeding an oil and refrigerant mixture to the supra-compression stage 32.

The defrost of the evaporation stages 16 and 17 may be performed at low pressure so as to avoid damaging the evaporator coils. Accordingly, the refrigeration cycle 120 may be retrofitted to existing evaporator coils, considering the relatively low defrost pressures. The defrost CO₂ refrigerant may be fed by the compression stage 10, or by the supra compression stage 32, with valve 46 controlling the pressure.

In order to protect the evaporator coils from high defrost pressures, a set of lines 126 extends from the evaporator coils to any reservoir or accumulator of the refrigeration system 120. For instance, the lines 126 are connected to one of the accumulators 121 and 122 while being separated by a valve 127. The valve 127 opens if the pressure in the evaporator coils is above a given threshold. Accordingly, if the defrost pressure in the evaporator coils is too high, the defrost CO₂ refrigerant is discharged to one of the accumulators 121 and 122, whereby the CO₂ refrigerant stays in the refrigeration system 120. As another safety measure, a pressure-relief valve system 128 is provided on the appropriate accumulators, such as 122 as shown but alternatively on the accumulator 121 or on the condensation reservoir 12.

For instance, the method for relieving CO₂ refrigerant pressure from evaporators during a defrost cycle comprises providing a pressure-relief valve for each evaporator line, the pressure relief-valve opening at a pressure threshold. CO₂ refrigerant is then fed to evaporators in the evaporator line to defrost the evaporator. The evaporators are exhausted from the CO₂ refrigerant with the pressure-relief valve when the CO₂ refrigerant pressure is above the pressure threshold; and directing the exhausted CO₂ refrigerant to an accumulator in a refrigeration cycle.

In specific conditions, it may be required to cool the CO₂ refrigerant fed to the evaporation stages 16 and/or 17 during the refrigeration cycle. Accordingly, a heat-exchanger system 129, for instance with an expansion valve, may direct refrigerant from the line 71 and feed same to the heat-exchanger system 129, to cool the CO₂ refrigerant fed to the evaporation stages 16 and/or 17.

The valve 39 is controlled (e.g., modulated) to maximize the heat reclaim via the heat reclaim exchanger 34. When the heat demand is high (e.g., during Winter in colder climates), the valve 39 may maintain a high refrigerant pressure downstream of the compression stage 32, to ensure the heat reclaim exchanger 34 extracts as much heat as possible from the CO₂ refrigerant. The amount of refrigerant sent to the gas cooling stage 36 is controlled simultaneously.

Referring to FIG. 11, yet another embodiment of a CO₂ refrigeration system is illustrated at 130. The CO₂ refrigeration systems 1 and 130 have numerous common stages and lines, whereby like elements will bear like reference numerals. The CO₂ refrigeration system 130 is particularly well suited for hot climate applications. In the CO₂ refrigeration system 130, the discharge of the compression stage 10 is directed to the heat exchanger 20 prior to reaching the condensation reservoir 12, for relatively low pressure condensation. Alternatively, the refrigerant exiting the heat exchanger 20 may be directed to the suction accumulator 133, thereby bypassing the condensation reservoir 12. A gaseous portion of the CO₂ refrigerant in the condensation reservoir 12 is directed via line 131 and pressure-reducing valve 132 into the heat exchanger 31 to reach the suction accumulator 133. The CO₂ refrigerant passing through the heat exchanger 31 absorbs heat from the CO₂ refrigerant exiting the supra-compression circuit via line 134. A line 135 relates a top of the suction accumulator 133 to the supra-compression stage 32, to feed gaseous CO₂ refrigerant to the compressors. Liquid CO₂ refrigerant may be directed to another suction accumulator 136, at the suction of the compression stage 10, in similar fashion to the CO₂ refrigeration system 120 of FIG. 10 (with appropriate heat exchange with the discharge of stage 10 if necessary). The supra-compression circuit is typically used to reclaim heat, while the evaporation stages 16 and 17 are part of a HVAC unit, amongst other possibilities.

Referring to FIG. 12, yet another embodiment of a CO₂ refrigeration system is illustrated at 140. The CO₂ refrigeration systems 1 and 140 have numerous common stages and lines, whereby like elements will bear like reference numerals. The CO₂ refrigeration system 140 has a heat exchanger 141 collecting defrost CO₂ refrigerant at the outlet of the evaporators 16/17, to vaporize the defrost CO₂ refrigerant and return same into the refrigeration cycle, namely to feed the suction of the compression stage 10 via line 142 or the supra-compression stage 32 via line 143. The heat exchanger 141 allows heat exchange between the defrost CO₂ refrigerant and the CO₂ refrigerant exiting the supra-compression stage 32 via lines 144, and may also be any other heat source (e.g. electric heater, heat reclaim, air-conditioning unit, or the like).

An air-conditioning unit 145 may be in fluid communication with the defrost reservoir 42 so as to use the defrost CO₂ refrigerant accumulated therein for air-conditioning purposes. The discharge of the air-conditioning unit 145 may be returned to the suction of the supra-compression stage 32, amongst other possibilities. In the various refrigerant systems described above, it is pointed out that the defrost refrigerant may be fed to the evaporators of stages 16 and 17 from either direction (as opposed to being fed in a direction opposed to that of refrigerant in the refrigeration cycle). Moreover, it is considered to provide the valves controlling the flow of defrost refrigerant to the evaporators 16 and 17 in the refrigeration pack, and have a plurality of lines for each single valve.

Referring to FIG. 13, a desiccant system is generally shown at 150. The desiccant system 150 may be used with any of the refrigeration systems described above, or with other refrigeration systems, to dry air being entered into a building for ventilating or refrigerating purposes. The desiccant system 150 is a closed circuit in which circulates a desiccant fluid.

The system 150 has a dryer 151, upon which exterior air flows when entering the building. The dryer 151 is a structural device upon which the desiccant fluid is sprayed. For instance, the dryer 151 may provide a honeycomb body. The desiccant fluid sprayed on the dryer 151 is in a suitable cooled state to absorb humidity from the warm exterior air entering the building. The desiccant fluid reaches a substantially liquid state after the absorption of humidity, and drips into pan 152 (or any other collector).

By way of a line and pump, the desiccant fluid passes through a heating exchanger 153 to be heated. Although not shown, the heating exchanger 153 may be connected to one of the above-referred refrigeration circuits, so as to provide the necessary energy to heat the desiccant fluid. Alternatively, the heating exchanger 153 may have an electric coil or the like.

The desiccant fluid, in a heated state, is then sprayed onto a humidifier 154. The humidifier 154 is similar to the dryer 151 in construction, but releases water to the exterior air. The desiccant fluid is heated as a function of the exterior temperature, for the desiccant fluid to release the previously-absorbed water to the air. The liquid desiccant is then collected in another pan 155 (or the like).

By way of a line and pump, the desiccant fluid passes through a cooling exchanger 156 to be cooled. Although not shown, the cooling exchanger 156 may be connected to one of the above-referred refrigeration circuits, so as to provide the necessary energy to cool the desiccant fluid. The desiccant fluid is cooled as a function of the exterior temperature, for the desiccant to absorb water from the outdoor air entering the building. Once it is cooled, the desiccant fluid is directed to the dryer 151.

Claims

1. A CO2 refrigeration system for an ice-playing surface, comprising: a compression stage in which CO2 refrigerant is compressed and an evaporation stage in which heat is absorbed from the ice-playing surface;a plurality of CO2 compressors in the compression stage for compressing the CO2 refrigerant subcritically and transcritically;a gas cooling stage includes at least a plurality of heat-reclaim units reclaiming heat from the CO2 refrigerant compressed in the compression stage;a pressure-regulating device downstream of the gas cooling stage, the pressure-regulating device operable to control a pressure of the CO2 refrigerant in the gas cooling stage as a function of a heat demand of the plurality of heat-reclaim units; anda reservoir downstream of the pressure-regulating device for receiving the CO2 refrigerant in a liquid state,a controller operating the pressure-regulating device to control the pressure of the CO2 refrigerant in the gas cooling stage as a function of the heat demand of the plurality of heat-reclaim units, the controller, via its operating of the pressure-regulating device, causing the pressure of the CO2 refrigerant to reach a transcritical level as a function of a heat demand of the plurality of heat-reclaim units.

2. The CO2 refrigeration system according to claim 1, wherein the evaporation stage of the CO2 refrigeration system receives the CO2 refrigerant from the reservoir of the CO2 refrigeration system and has a circuit of pipes arranged under the ice-playing surface, whereby the CO2 refrigerant circulates in the circuit of pipes to absorb heat from the ice-playing surface.

3. The CO2 refrigeration system according to claim 1, further comprising a secondary refrigerant circuit in which circulates a secondary refrigerant, and wherein at least one of the heat-reclaim units has at least one heat-reclaim exchanger related to the secondary refrigerant circuit, the at least one heat-reclaim exchanger causing the CO2 refrigerant to release heat to the secondary refrigerant.

4. The CO2 refrigeration system according to claim 3, further comprising at least one water tank in the secondary refrigerant circuit, with the at least one water tank comprising a heat exchanger in which circulates the secondary refrigerant to heat water in the water tank.

5. The CO2 refrigeration system according to claim 3, wherein the secondary refrigerant circuit further comprises at least one water tank, with the at least one water tank comprising a heat exchanger in which circulates the CO2 refrigerant to heat water in the water tank.

6. The CO2 refrigeration system according to claim 1, wherein a portion of the heat-reclaim units are in a parallel arrangement.

7. The CO2 refrigeration system according to claim 1, wherein a portion of the heat-reclaim units are in a series arrangement.

8. The CO2 refrigeration system according to claim 2, further comprising at least one expansion valve to vaporize the CO2 refrigerant fed to the circuit of pipes.

9. The CO2 refrigeration system according to claim 1, further comprising at least one pump downstream of the reservoir to direct liquid CO2 refrigerant to the evaporation stage.

10. The CO2 refrigeration system according to claim 1, wherein at least one of the heat-reclaim units comprises at least one fan blowing air on a coil in which circulates the CO2 refrigerant.

11. The CO2 refrigeration system according to claim 1, further comprising an oil circuit in the CO2 refrigeration system, the oil circuit collecting oil downstream of at least one of the compressors in the compression stage, the oil circuit directing the oil upstream of the compressors for the CO2 refrigerant fed to said compressor to have an oil content.

12. The CO2 refrigeration system according to claim 11, wherein the oil circuit is connected to a bottom of the reservoir to collect the oil.

13. The CO2 refrigeration system according to claim 12, further comprising an accumulator upstream of the compressors, the oil circuit directing the oil from the reservoir to the accumulator, a suction line extending from the accumulator to at least one of the compressors for directing the CO2 refrigerant with oil content to said compressor.

14. The CO2 refrigeration system according to claim 13, further comprising a heat exchanger in the suction line to vaporize the CO2 refrigerant with oil content, the suction line collecting liquid CO2 refrigerant with oil content from a bottom of the accumulator.

15. The CO2 refrigeration system according to claim 1, wherein the pressure-regulating device is a modulating valve controlled to maximize the heat reclaim as a function of the heat demand of the plurality of heat-reclaim units.

16. The CO2 refrigeration system according to claim 1, wherein the controller, via its operating of the pressure-regulating device, causes the pressure of the CO2 refrigerant to reach a pressure of at least 1400 Psi as a function of the heat demand during a winter month period, the controller, via its operating of the pressure-regulating device, causing the pressure of the CO2 refrigerant to reach a pressure including 550 Psi as a function of the heat demand during a summer month period, wherein an outdoor temperature is warmer in the summer month period than in the winter month period.