EP3658835B1 - Kälteanlage - Google Patents

Kälteanlage

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Publication number
EP3658835B1
EP3658835B1 EP18758929.6A EP18758929A EP3658835B1 EP 3658835 B1 EP3658835 B1 EP 3658835B1 EP 18758929 A EP18758929 A EP 18758929A EP 3658835 B1 EP3658835 B1 EP 3658835B1
Authority
EP
European Patent Office
Prior art keywords
water
enclosure
pressure
liquid
temperature
Prior art date
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.)
Active
Application number
EP18758929.6A
Other languages
English (en)
French (fr)
Other versions
EP3658835A1 (de
EP3658835B8 (de
Inventor
Thomas Vinard
Sébastien BUR
Jérôme Girard
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Alpinov X
Original Assignee
Alpinov X
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Filing date
Publication date
Application filed by Alpinov X filed Critical Alpinov X
Publication of EP3658835A1 publication Critical patent/EP3658835A1/de
Publication of EP3658835B1 publication Critical patent/EP3658835B1/de
Application granted granted Critical
Publication of EP3658835B8 publication Critical patent/EP3658835B8/de
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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
    • F25C1/00—Producing ice
    • F25C1/16—Producing ice by partially evaporating water in a vacuum
    • 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
    • F25C3/04—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 sledging or ski trails; Producing artificial snow
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D31/00—Other cooling or freezing apparatus
    • 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
    • F25B23/00—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect
    • F25B23/006—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect boiling cooling systems
    • 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
    • F25C2303/00—Special arrangements or features for producing ice or snow for winter sports or similar recreational purposes, e.g. for sporting installations; Special arrangements or features for producing artificial snow
    • F25C2303/044—Snow making using additional features, e.g. additives, liquid gas

Definitions

  • This application concerns a refrigeration installation.
  • a refrigeration system can be used in many different applications.
  • An example of the use of a refrigeration installation concerns an air conditioning system, particularly within the framework of an urban cooling network or for a data center.
  • Another example of the use of a refrigeration system concerns an artificial snow production system, for example for snowmaking in ski resorts in the case of low snowfall due to weather conditions or inherent to the geographical location of the resorts.
  • the coefficient of performance is the ratio between the thermal power produced by the system (quantity of heat) hot Q+ ch or quantity of cold heat Q ref ) and the work supplied to the system (work W). It is generally desirable for the COP to be as high as possible, which reflects good energy efficiency of the system and implies low energy consumption, knowing that energy consumption includes the electrical consumption of the system.
  • the first type of artificial snow production system is open to ambient air, such as snow cannons or snow poles, and generally involves spraying a mixture of water and air that crystallizes upon contact with the ambient air.
  • the air may come from a compressed air source, the expansion of which causes snow formation.
  • a drawback of these systems is that they can only operate within limited temperature and humidity ranges, generally below -2°C and above 30% humidity.
  • a second type of artificial snow production system includes open systems, as described in the patent application. WO2012/104787 The electricity consumption of such snowmaking systems typically ranges from 20 kWh to 40 kWh per cubic meter of snow produced, which is lower than that of second- and third-generation snowmaking systems.
  • such systems require the construction of cooling towers and therefore have a construction cost that is too high for large-scale operation.
  • Second types of artificial snow production systems include closed-loop, refrigerator-type systems with a compressor, condenser, expansion valve, and evaporator.
  • COP Coefficient of Performance
  • the power consumption of such snow production systems can be... high, for example from 40 kWh to 120 kWh per cubic meter of snow produced.
  • Fourth-generation artificial snow production systems include closed systems employing cryogenic processes, notably the formation of a mixture of water and a cryogenic gas, such as nitrogen or carbon dioxide. While the COP (Coefficient of Performance) of such a snow production system can be high, the energy required to produce the cryogenic fluid must be taken into account. Consequently, the overall energy consumption of such snow production systems can exceed several hundred kWh per cubic meter of snow produced, resulting in prohibitively high operating costs for large-scale use and significant logistical challenges.
  • COP Coefficient of Performance
  • a refrigeration system particularly for air conditioning or artificial snowmaking systems, with a high COP (Coefficient of Performance), ideally above 6 and preferably above 10, and low power consumption, especially when the refrigeration unit is installed in a snowmaking system with a consumption of less than 5 kWh, preferably less than 3 kWh per cubic meter of snow produced.
  • the refrigeration unit it would be desirable for the refrigeration unit to operate normally over a wide range of ambient temperatures, particularly above freezing, and preferably up to 25°C, or even up to 35°C.
  • the document JP 2004 251541 A discloses a refrigeration installation according to the preamble of claim 1.
  • one objective of an embodiment is to at least partially overcome the disadvantages of the refrigeration installations described above.
  • the COP of the refrigeration installation is greater than 6, preferably greater than 10.
  • Another objective of one embodiment is that the electrical consumption of the refrigeration system is reduced, in particular, when the refrigeration installation is installed in a snow production system, less than 5 kWh per cubic meter of snow produced, preferably less than 3 kWh per cubic meter of snow produced.
  • the refrigeration installation can operate at an ambient temperature between -30 °C and +25 °C, preferably between -30 °C and +35 °C.
  • Another objective of one embodiment is that the cost of constructing the refrigeration installation is reduced.
  • the invention provides for a refrigeration installation according to the subject of claim 1.
  • the installation includes a device for heating water in the gaseous state in the first enclosure intended to supply the compression device.
  • the first enclosure further contains water in a solid state at a temperature less than or equal to the triple point temperature of water.
  • the water circulates in a closed circuit within the installation.
  • the condensation device includes a first heat exchanger outside the second enclosure and means for circulating a first heat transfer fluid around the second enclosure through the first heat exchanger.
  • the first heat transfer fluid is ambient air or water from a stream, body of water or water table.
  • the second pressure in the second enclosure is less than or equal to 10000 Pa (100 mbar), preferably less than or equal to 6000 Pa (60 mbar).
  • the cold power extraction device includes a hydraulic circuit in which some or all of the liquid water present in the first enclosure circulates, the hydraulic circuit including a second heat exchanger located outside the first enclosure.
  • the cold power extraction device comprises a closed hydraulic circuit in which a second heat transfer fluid circulates, the hydraulic circuit comprising a second heat exchanger located outside the first enclosure and a third heat exchanger disposed in the first enclosure.
  • the refrigeration installation includes a third enclosure in which the second heat exchanger is located, delivering the cooling power to the end user, the third enclosure containing, for example, water in a solid state.
  • the heating device includes a source of infrared radiation and/or a source of microwave radiation.
  • the heating device is adapted to heat the water in the gaseous state in the first enclosure intended to supply the compression device by at least 2 °C, preferably by at least 10 °C, more preferably by at least 20 °C.
  • the compression device comprises at least one turbomachine-type compressor, in particular a centrifugal compressor and/or an axial compressor.
  • the compression device comprises a succession of stages, each stage comprising a rotor and a stator.
  • the compression device is a Tesla compressor.
  • the compression device comprises a first stage compressor with a fixed compression ratio and a second stage compressor with a controllable compression ratio.
  • the refrigeration installation further includes, in the first enclosure, a mechanical device for protecting the compression device against the admission of particles in solid and/or liquid state.
  • the refrigeration installation includes a supply line for water in liquid state into the first enclosure.
  • the condensation device includes at least one nozzle for projecting droplets of water in liquid state into the second enclosure.
  • the installation further includes a system for regulating the pressure difference between the second chamber and the first chamber.
  • control system includes a pressure-reducing turbine configured to reduce water pressure. in gaseous state from the second enclosure and pump a mixture containing water in gaseous state and water in liquid state into the first enclosure.
  • the first enclosure comprises at least one reservoir of water in a liquid state and into which said mixture is pumped into the water in a liquid state contained in said reservoir.
  • One embodiment also provides for an artificial snow production system including a refrigeration installation as defined above.
  • One embodiment also provides for an air conditioning system for industrial, collective and private installations including a refrigeration installation as defined above, particularly within the framework of an urban cooling network or for a data center.
  • the invention also provides a method for producing cold according to the subject of claim 14.
  • the process further includes the step of heating water in a gaseous state in the first enclosure intended to be compressed.
  • water refers to the chemical compound H2O , which can be in a liquid, solid, or gaseous state.
  • water in a gaseous state and “water vapor” are used interchangeably hereafter.
  • liquid water and “water in a liquid state” are used interchangeably to refer to pure water in a liquid state or to water in a liquid state corresponding to the solvent of an aqueous solution containing at least one other solute.
  • triple point of water means “triple point of pure water.”
  • the water in the liquid state can correspond to the solvent of an aqueous solution, that is to say, additives can be added to the water in the liquid state.
  • FIG. 1 represents a method of implementing a refrigeration installation 5.
  • the liquid water 14 contained in the tank 12 can be water directly from the mains water supply system, or fresh water, in particular water from a stream or a reservoir.
  • the line 38 can be connected to the line 18.
  • the refrigeration system 5 may also include a system 42 for regulating the pressure difference between the second low-pressure chamber 30 and the first low-pressure chamber 10.
  • the system 42 may be a controlled valve system, a capillary tube system, an expansion turbine system, or a weir system, and is adapted to maintain the pressure difference between the second low-pressure chamber 30 and the first low-pressure chamber 10 at a substantially constant value.
  • the processing module 40 may be a dedicated circuit or may include a processor, for example a microprocessor or a microcontroller, adapted to execute instructions from a computer program stored in memory.
  • the refrigeration system 5 may also include sensors, including temperature sensors, pressure sensors, level sensors, flow sensors, etc., not shown, connected to the processing module 40, particularly for temperature and pressure detection in chambers 10 and 30.
  • the compressor 32 is an axial or centrifugal compressor that delivers a flow of compressed vapor substantially along the compressor's axis of rotation.
  • the compressor comprises a series of compression stages, each stage including a rotor and a stator.
  • the rotor has blades driven in rotation by a drive shaft.
  • the rotor accelerates the gas flow using the energy transmitted by the compressor's drive shaft.
  • the stator has stationary blades. The stator converts the kinetic energy of the gas flow into pressure via its shape.
  • the heating device 22 is preferably a radiant heating device, comprising a source of electromagnetic radiation reaching the water vapor.
  • the heating device 22 includes, for example, an infrared water vapor heating system or, for example, a microwave water vapor heating system.
  • the heating device 22 comprises both an infrared radiation source and a microwave radiation source. Depending on the intended application, the heating device 22 may not be present.
  • the dimensions of the refrigeration system 5 depend on the intended application.
  • the volume of the first low-pressure chamber 10 can range from 1 liter to several thousand cubic meters, specifically from 10 liters to 10,000 liters.
  • the volume of the second low-pressure chamber 30 can range from 1 liter to one thousand cubic meters, specifically from 1 liter to 10,000 liters.
  • the volume of liquid water 14 in the tank 12 can range from 1 liter to several thousand cubic meters, specifically from 1 liter to 3,000 m3 , and in particular from 9 liters to 9,999 liters.
  • the refrigeration installation 5 includes a primary vacuum pump, not shown, connected to the first low-pressure chamber 10 and/or to the second low-pressure chamber 30.
  • FIG. 2 represents an enthalpy-pressure diagram of water illustrating the operation of the refrigeration system 5 at the beginning of its operation.
  • the reference points A to G in figure 2 illustrate successive states through which water passes circulating in the refrigeration system 5.
  • Point A represents liquid water that will be introduced into tank 12 via pipe 18, for example, to fill tank 12 at the start of operation of system 5.
  • the pressure of the liquid water at point A has a first pressure value
  • the temperature of the liquid water at point A has a first temperature value.
  • the first pressure value is greater than or equal to 0.1 MPa (1 bar), for example, greater than or equal to 0.1 MPa (1 bar) and less than or equal to 10 MPa (100 bar).
  • the first temperature value is greater than or equal to 5 °C, for example, greater than or equal to 5 °C and less than or equal to 10 °C.
  • the water supplied to tank 12 comes, for example, from a water distribution network to which the refrigeration system 5 is connected.
  • the first temperature value can then correspond to the temperature of the water supplied by the distribution network.
  • the pressure of the liquid water 14 decreases from the first pressure value to the pressure in the first low-pressure chamber 10, which is at a second pressure value. This corresponds to the transition from point A to point B.
  • the second pressure value is equal to the saturated vapor pressure of the liquid water 14 present in the tank 12.
  • the second pressure value in the first low-pressure chamber 10 is typically between 600 Pa (6 mbar) and 2500 Pa (25 mbar), preferably between 600 Pa (6 mbar). and 1500 Pa (15 mbar).
  • the pressure in the first low-pressure chamber 10 can be 870 Pa (8.7 mbar).
  • the temperature of the liquid water introduced into the reservoir 12 during the pressure drop remains essentially constant and equal to the first temperature value.
  • the temperature of the liquid water 14 in the tank 12 is at a second temperature value.
  • the second temperature value is substantially equal to the first temperature value, so that the temperature of the water introduced into the tank 12, whose pressure has decreased, does not change substantially.
  • Evaporation occurs of some of the liquid water 14 in the reservoir 12, which will raise the water temperature from the first value to the second value. This corresponds to the transition from point B to point C. Since the pressure in the low-pressure chamber 10 is equal to the saturated vapor pressure of the water at the second temperature value, the vaporization is a boiling of the liquid water 14, which notably includes the formation of bubbles 43 (see figure 1 ) in liquid water 14. Water vapor is then obtained in the first low-pressure chamber 10 at the second temperature and pressure value.
  • the protective element 20 prevents liquid water from splashing onto the compressor 32 or from spilling out of the tank 12 when the liquid water 14 boils.
  • the protective element 12 can also increase the heat exchange surface area by including parts that penetrate the liquid water.
  • all or part of the water vapor in the first low-pressure chamber 10 is heated by the heating device 22.
  • the temperature of a portion of the water vapor in the first low-pressure chamber 10 then changes from the second temperature value to a third value of temperature.
  • the steam is pumped by the compressor 32 into the part of the first chamber 10 where it is heated. This corresponds to the transition from point C to point D.
  • the third temperature value is greater than or equal to 0 °C and less than or equal to 100 °C.
  • the third temperature value is at least 2 °C higher than the second temperature value, preferably at least 10 °C higher, and more preferably at least 20 °C higher.
  • the steam pressure during the heating step does not change substantially and remains substantially equal to the second pressure value.
  • the use of the radiant heating device 22 makes it possible to heat all the water vapor that feeds the compressor 32. Indeed, it would be difficult with a conduction or convection heating device to heat all the water vapor that feeds the compressor 32 due to the low pressure and consequently the very low density of matter in the first chamber 10 at low pressure.
  • the steam heated to the third temperature value feeds the compressor 32, which discharges the compressed steam into the second chamber 30 at low pressure. This corresponds to the transition from point D to point E.
  • the compression ratio of the compressor 32 is greater than or equal to 2 and, for example, less than or equal to 14.
  • the pressure in the second chamber 30 at low pressure is equal to a third pressure value that is at least a factor of 2 higher than the second pressure value.
  • the third pressure value is greater than or equal to 600 Pa (6 mbar) and less than or equal to 10,000 Pa (100 mbar), preferably less than or equal to 6,000 Pa (60 mbar).
  • the third pressure value is approximately 1740 Pa (17.4 mbar).
  • the compression of water vapor by compressor 32 results in the water vapor heating up. whose temperature goes from the third temperature value to a fourth temperature value, higher than the third temperature value.
  • the compressed water vapor in the low-pressure chamber 30 is cooled and then liquefied into cooled liquid water by the condenser 34. This corresponds to the transition from point E to point F and the transition from point F to point G.
  • the water pressure during the cooling and liquefaction stages does not change significantly and remains equal to the third pressure value.
  • the water temperature varies from the fourth temperature value to a fifth temperature value strictly lower than the fourth temperature value. For example, for a third pressure value of 1740 Pa (17.4 mbar), the fifth temperature value could be 15.3 °C.
  • the higher the compression ratio the more readily the water can be condensed at high ambient temperatures, and the faster the condensation can be achieved.
  • the liquid water produced by the condenser 34 is discharged from the tank 30 at low pressure through the pipe 38.
  • the pipe 38 is connected to the pipe 18 so that the liquid water discharged from the enclosure 30 is returned to the tank 12.
  • Condensation causes pumping by vacuum, linked to the difference in specific volume between liquid water and gaseous water (ratio of approximately 1600 to 200000 between the liquid and gaseous phases), which maintains a vacuum level in the chambers 10 and 30.
  • the maintenance of the pressure difference between the low-pressure chamber 30 and the low-pressure chamber 10 is achieved by the processing module 40 which controls for this purpose the heating device 22, the compressor 32, the condenser 34, the system 42 and possibly the primary vacuum pump.
  • the primary vacuum pump operates at the start-up of the refrigeration system 5 until the pressure in the first low-pressure chamber 10 reaches the saturated vapor pressure at the first temperature value.
  • the pump can then be stopped and the pressure in the enclosure 10 is maintained by the depression generated at the condenser 34 and the mechanical work of the compressor 32.
  • the vacuum pump can also participate, if necessary, in maintaining the pressure in the first enclosure 10 at low pressure.
  • THE figures 3 And 4 each represent an enthalpy-pressure diagram of the water illustrating the operation of the refrigeration system 5 in steady state respectively for an open cycle and for a closed cycle.
  • reservoir 12 is filled with liquid water 14. Additional water is supplied via pipe 18 to reservoir 12 to compensate for liquid water losses from reservoir 12, for example continuously or intermittently. In the case of an open cycle, the additional water is located at point A ( figure 3 ). In the case of a closed cycle, the additional liquid water comes from the condensates recovered in enclosure 30 and is therefore located at point G.
  • the pressure in the first low-pressure chamber 10 decreases simultaneously with the decrease in the temperature of the liquid water 14 in the tank 12 to remain equal to the saturated vapor pressure at the temperature of the liquid water 14 in the tank 12.
  • the maintenance of the pressure in chamber 10 at the saturated vapor pressure at the temperature of the liquid water 14 in the tank 12 is achieved by the treatment module 40 which controls for this purpose the heating device 22, the compressor 32 and the condenser 34, the system 42 and possibly the primary vacuum pump.
  • the temperature of the liquid water 14 in the reservoir 12 decreases until it reaches the triple point temperature of water, which, for example, at a pressure of 611 Pa (6.11 mbar) is equal to 0.01 °C. Ice crystals 15 then form in the reservoir 12, corresponding to the transition between points B' and B" on the figures 3 And 4
  • the temperature of the liquid water 14 in the reservoir 12 remains substantially constant and equal to the triple point temperature of pure water, and the pressure in the first low-pressure chamber 10 is substantially equal to the saturated vapor pressure at the triple point temperature of water.
  • the temperature of the liquid water 14 in the reservoir 12 remains substantially constant and equal to a temperature lower than the triple point temperature of pure water, and the pressure in the first low-pressure chamber 10 is substantially equal to the saturated vapor pressure of water in equilibrium with the pressure of water in the liquid state at a temperature lower than the triple point temperature of water.
  • the water is then present in the first low-pressure chamber 10 simultaneously in the gaseous, liquid, and vapor states. the solid state.
  • the temperature of the liquid water 14 in the tank 12 decreases to a temperature less than 10 °C above the triple point temperature of water, preferably less than 5 °C.
  • the water is then present in the first enclosure 10 at low pressure simultaneously in the gaseous and liquid states.
  • the heating stage corresponding to the transition between points C and D aims to increase the temperature of the water vapor in the low-pressure chamber 10 by at least 2 °C, preferably by at least 10 °C, and preferably by at least 20 °C.
  • the compression ratio of the compressor 32 can be adjusted to maintain substantially the same third pressure value in the second low-pressure chamber 30.
  • the compression ratio of the compressor 32 is, for example equal to 3 and the third pressure value in the second low-pressure chamber 30 is equal to 1830 Pa (18.3 mbar).
  • the fifth value of the temperature of the liquid water produced by the condenser 34 at 1830 Pa (18.3 mbar) is, for example, equal to 16.05 °C for an ambient temperature of approximately 6 °C.
  • the cold power extraction device 24 removes the ice crystals 15 as they form in the reservoir 12. The subsequent use of the ice crystals depends on the intended application.
  • ice crystals are collected to produce artificial snow.
  • a refrigeration system can be provided to lower the temperature of the collected ice and/or a pumping unit to evaporate residual water, thus cooling and drying the ice.
  • a device for chopping and aerating the produced ice can also be included.
  • the ice crystals 15 present in the reservoir 12 can play the role of a cold source.
  • the condenser 34 is adapted to liquefy the water vapor in the second low-pressure chamber 30 by means of heat exchange between the water vapor in the second low-pressure chamber 30 and a refrigerant.
  • the refrigerant is the air outside the refrigeration system 5.
  • the condenser 34 may include means for air mixing, for example, the propeller fan 36 as shown in figure 1 Air mixing is schematically represented by arrow 44.
  • the condenser 34 may include a Venturi fan or a thermosiphon.
  • the condenser 34 may include a heat exchanger unit. water-vapor liquid in enclosure 30 and a liquid-air or liquid/liquid exchanger group outside enclosure 30, the cooling fluid circulating between these two exchangers.
  • the condensation of water in enclosure 30 does not require the use of a refrigeration machine.
  • the production of liquid water by the condenser 34 can be achieved using ambient air as soon as the ambient air temperature is below the fifth desired temperature value.
  • ambient air can be used as soon as its temperature is below 16 °C, preferably below 6 °C to obtain a temperature difference of at least 10 °C across the heat exchanger.
  • the maximum possible ambient air temperature allowing the use of ambient air as a refrigerant by the condenser 34 is determined, in particular, by the compression ratio of the compressor 32. With a compression ratio of 10, a saturated vapor pressure of 6000 Pa (60 mbar) can be achieved in the second low-pressure chamber 30, and a fifth temperature value of 36 °C can be obtained without difficulty as soon as the ambient air temperature is below 30 °C.
  • the refrigeration system 5 can be used as soon as the ambient temperature is below 20 °C for artificial snow production and below 35 °C for air conditioning.
  • the theoretical COP of the refrigeration installation 5 is in the order of 19 to 20.
  • Table I below shows, for an application to artificial snow production, and as a function of ambient air temperature, the electrical consumption, expressed in kilowatts per cubic meter of snow produced, of the refrigeration unit 5 (INV) represented in figure 1 , a snow cannon-type installation (AA1), a snow pole-type installation (AA2), a low-temperature evaporation installation (AA3) pressure between 0.01 MPa (100 mbar) and 0.02 MPa (200 mbar) and a refrigerator type installation (AA4).
  • the electrical consumption per cubic meter of snow produced by the refrigeration installation 5 is significantly lower than that of refrigeration installations of the refrigerator type (AA4) and low pressure evaporation between 0.01 MPa (100 mbar) and 0.02 MPa (200 mbar) (AA3).
  • liquid water supplied by the condenser 34 is not reused. In another embodiment, the water supplied by the condenser 34 is reused to supply the reservoir 12.
  • FIG 5 is a partial and schematic view of a more detailed embodiment of the low-pressure tank 10 of the refrigeration system 5 of the figure 1 .
  • the protective element 20 comprises a membrane or screen 46 covering the free surface of the liquid water 14.
  • the membrane or screen 46 is permeable to water vapor and substantially impermeable to liquid water.
  • the protective element 20 may further comprise elements immersed in the liquid water 14, not shown, which regulate the generation of bubbles 43 during the boiling of the liquid water 14.
  • baffles 48 can be arranged in the part of the enclosure 10 in which the steam is heated by the heating device 22.
  • the baffles 48 allow the path of the steam to be lengthened. up to the inlet of compressor 32 to obtain the heating of the water vapor up to the desired temperature.
  • FIG. 6 is a partial and schematic cross-sectional view of a more detailed embodiment of the device 24 for recovering water in the solid state of the refrigeration installation 5.
  • the device 24 is adapted to extract water in a solid state from the reservoir 12. Such an embodiment is particularly suitable in the case where the refrigeration installation 5 is used for the production of artificial snow.
  • the device 24 may include a secondary chamber 50 connected to the reservoir 12 by a lower pipe 52 and an upper pipe 54, located above the lower pipe 52.
  • a pump 56 provided on the upper pipe 54 is adapted to circulate the contents of the reservoir 12 to the secondary chamber 50
  • a pump 58 provided on the lower pipe 52 is adapted to circulate the contents of the secondary chamber 50 back to the reservoir 12.
  • the pressure in the secondary chamber 50 may be higher than in the reservoir 12, for example, equal to atmospheric pressure, so that there is no boiling in the secondary chamber 50.
  • the ice crystals then accumulate above the liquid water 62 by settling into a floating mass of ice 60.
  • the device 24 includes means 64 for extracting the ice crystals 60, including, for example, a screw conveyor or a bucket elevator.
  • Device 24 may be part of an air conditioning or refrigeration system and may comprise a closed circuit through which a refrigerant circulates, including a first heat exchanger 66 disposed in the reservoir 12 and a second heat exchanger 68 located outside the enclosure 10.
  • the first heat exchanger 66 is not present and the circulating fluid in the heat exchanger 68 corresponds to the liquid water 14 present in the tank 12.
  • FIG 8 is a partial, schematic cross-sectional view of an embodiment of a refrigeration system 70.
  • the refrigeration system 70 comprises all the elements of the refrigeration system 5 shown in figure 1 The difference is that it further includes means according to the invention for maintaining the liquid water in a supercooled state within the first chamber 10 at low pressure.
  • the means for maintaining the liquid water in a supercooled state may include an agitator 72 adapted to stir the water in the liquid state within the first chamber 10 at low pressure.
  • the agitator 72 comprises, for example, a bar or a propeller rotated within the liquid water 14.
  • the means for maintaining the liquid water in a supercooled state include at least one additive added to the water in the liquid state. This additive, when mixed with the water, results in a solution whose freezing point is lower than the freezing point of water without the additive.
  • the temperature of the liquid water 14 in the first low-pressure chamber 10 may be lower than the triple point temperature of water, and is, for example, at a temperature that can vary from -40 °C to -1 °C, preferably from -20 °C to -1 °C.
  • the operation of the refrigeration system 70 is identical to the operation described previously for the refrigeration system 5, except that the temperature of the liquid water in the first low-pressure chamber 10 may be lower than the triple point temperature of water.
  • FIG 9 is a partial, schematic cross-sectional view of a more detailed embodiment of part of the refrigeration system of the figure 8 , in which the cold power extraction device 24 in the tank 12 has the structure shown in figure 7
  • the second exchanger 68 of device 24 is located in an enclosure 80 containing
  • the liquid water 82 is cooled in the chamber 80 until it becomes solid water 84.
  • the pressure in the chamber 80 may advantageously be greater than the saturated vapor pressure of water at its triple point temperature, and be, for example, at atmospheric pressure.
  • the first heat exchanger 66 is not present, and the liquid circulating in the heat exchanger 68 corresponds to the liquid water 14 present in the reservoir 12.
  • FIG. 10 is a partial, schematic cross-sectional view of one embodiment of a refrigeration system 90.
  • the refrigeration system 90 comprises all the elements of the refrigeration system 5 shown in figure 1 The difference is that the single tank 12 of the refrigeration system 5 is replaced by N tanks 12 ⁇ sup> 1 ⁇ /sup> to 12 ⁇ sup>N ⁇ /sup> located in the first low-pressure chamber 10, where N is an integer from 1 to 100.
  • the water supply line 18 is connected to each tank 12 ⁇ sup> 1 ⁇ /sup> to 12 ⁇ sup> N ⁇ /sup>.
  • the heating device 22 is shown as an example inside the compressor inlet line 32, which opens into the first low-pressure chamber 10.
  • the liquid water recovery line 38 from the condenser 34 is connected to the line 18, and the liquid water recovered by the line 38 is pumped into the tanks 12N to 12N by means of a pump 92, for example, a positive displacement pump.
  • the pump 92 may be omitted, resulting in the circulation of liquid water in the lines 18 and 38. only the pressure difference between chambers 10 and 30.
  • the condenser 34 includes nozzles 94 for projecting liquid water into the second chamber 30 at low pressure in the form of droplets 96, three nozzles 94 being shown by way of example in Figure 10
  • the cold droplets 96 promote the condensation of the water vapor expelled into the second low-pressure chamber 30 by the compressor 32, by multiplying the vapor/liquid interfaces that facilitate the adsorption of water vapor.
  • the liquid water is collected in a reservoir 98, formed, for example, by the bottom of the second low-pressure chamber 30.
  • the line 38 recovers some of the liquid water present in the reservoir 98.
  • the condenser 34 also includes a hydraulic circuit 100 through which some of the liquid water from the reservoir 98 circulates, supplying the nozzles 94 with cooled water.
  • the hydraulic circuit 100 includes a pump 102 for circulating the liquid water and a heat exchanger 104 located outside the second low-pressure chamber 30, for example, a heat exchanger cooled by ambient air.
  • the condenser 34 includes means, for example, the fan 36 described previously, for circulating ambient air through the heat exchanger 104.
  • the heat exchanger 104 can be cooled by another source, for example, a stream.
  • the liquid water expelled from the nozzles 94, which has been cooled by the heat exchanger 104, is, for example, at ambient temperature.
  • the temperature of the droplets 96 at the outlet of the nozzles 94 is at least 10 °C lower than the temperature of the liquid water supplying the hydraulic circuit 100.
  • the pressure differential control system 42 between the second low-pressure chamber 30 and the first low-pressure chamber 10 comprises a conduit 106 connected to the second low-pressure chamber 30 in the portion of the chamber 30 containing steam Water, pipe 106 being equipped with a controllable flow control valve 108, supplies an expansion turbine 110.
  • the outlet of turbine 110 is connected to a pipe 112 which supplies each reservoir 12N .
  • Turbine 110 receives steam at the pressure of the second low-pressure chamber 30, which is already cooled by the droplet condenser 34, and provides a two-phase mixture comprising liquid water and steam. The rotational speed of turbine 110 is adjusted so that the discharged steam has the desired pressure.
  • the liquid water has been cooled by expansion and the steam is substantially at the desired pressure in the first low-pressure chamber 10.
  • the steam expelled through pipe 112 into each tank 12N can advantageously act as an agitator for the liquid water present in tanks 12N and further promotes the cooling of the liquid water contained in tanks 12N .
  • the turbine 110 and the valve 108 can be controlled by the processing module 40, not shown in the diagram . Figure 10 .
  • the cold power extraction device 24 in the tanks 121 to 12N comprises a hydraulic circuit 114 connected to the tanks 121 to 12N through which some of the water present in the tanks 121 to 12N circulates.
  • the hydraulic circuit 114 includes a pump 116 for circulating the liquid water and a heat exchanger 118 located outside the first low-pressure enclosure 10, for example, a heat exchanger cooperating with a heat exchanger 120 of another hydraulic circuit 122 connected to a device 124 to be cooled.
  • the hydraulic circuit 114 can be connected to the pipe 18 for the discharge of the liquid water circulating in the hydraulic circuit 114 to the tanks 12 1 to 12 N.
  • the turbocharger 32 comprises two successive stages 130 and 132.
  • the first stage 130 has a fixed compression ratio, for example, approximately 3, and the second stage 132 has a controllable variable compression ratio.
  • the rotational speed of the second turbomachine 132 can be controlled by the processing module 40, not shown in the figure.
  • each stage 130, 132 corresponds to a turbocharger.
  • the first stage 130 controls the flow rate of steam extracted from the first chamber 10 at low pressure.
  • the second stage 132 sets the pressure of the steam discharged into the second chamber 30 at low pressure.
  • the condenser 34 is a condenser in which the water vapor is cooled and liquefied by the ambient air
  • other types of condenser 34 may be used, for example, a liquid-cooled condenser.

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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)
  • Combustion & Propulsion (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Physical Water Treatments (AREA)

Claims (14)

  1. Kälteanlage (5; 70), umfassend:
    ein erstes Gehäuse (10), das Wasser in flüssigem Zustand (14) bei einer Temperatur unterhalb der Temperatur des Tripelpunkts von Wasser, Wasser in gasförmigem Zustand (11) bei einem ersten Druck, der bis auf 10 % genau dem Sättigungsdampfdruck des Wassers in dem Gleichgewicht mit dem Druck des Wassers in flüssigem Zustand (14) in dem ersten Gehäuse entspricht, und Wasser in festem Zustand (15) bei einer Temperatur unterhalb der Temperatur des Tripelpunkts von Wasser enthält, wobei das erste Gehäuse (10) mindestens einen Vorratsbehälter (12; 121 bis 12N) für Wasser in flüssigem Zustand umfasst;
    Mittel zum Halten des flüssigen Wassers in dem Überschmelzzustand in dem ersten Gehäuse (10), wobei die Mittel mindestens ein dem Wasser in flüssigem Zustand hinzugefügtes Additiv umfassen;
    ein zweites Gehäuse (30) bei einem zweiten Druck, der strikt über dem ersten Druck um mindestens einen Faktor zwei liegt;
    eine Kompressionsvorrichtung (32), die das erste Gehäuse mit dem zweiten Gehäuse verbindet, die geeignet ist, eine Kompressionsrate von mehr als zwei zu liefern;
    eine Kondensationsvorrichtung (34), die teilweise in dem zweiten Gehäuse untergebracht und geeignet ist, das Wasser in dem gasförmigen Zustand in dem zweiten Gehäuse in Wasser in dem flüssigen Zustand zu kondensieren; und
    eine Vorrichtung (24) zur Extraktion von Kälteleistung in dem ersten Gehäuse;
    Kälteanlage, dadurch gekennzeichnet, dass sie eine Vorvakuumpumpe umfasst, die mit dem ersten Gehäuse (10) und/oder dem zweiten Gehäuse (30) verbunden ist, und dass die Kompressionsvorrichtung (32) zwei aufeinanderfolgende Stufen (130, 132) umfasst, wobei jede Stufe (130, 132) einem Turbokompressor entspricht, mit einer ersten Kompressionsstufe (130) mit festem Kompressionsverhältnis und einer zweiten Kompressionsstufe (132) mit steuerbarem Kompressionsverhältnis, wobei die Drehzahl des zweiten Turbokompressors von einem Abgasmanagementmodul (40) gesteuert wird.
  2. Kälteanlage nach Anspruch 1, wobei die erste Stufe (130) den Wasserdampfdurchsatz steuert, der aus dem ersten Gehäuse (10) extrahiert wird, und die zweite Stufe (132) den Druck des in das zweite Gehäuse (30) geförderten Wasserdampfs festlegt.
  3. Kälteanlage nach einem der Ansprüche 1 oder 2, wobei die Temperatur des flüssigen Wassers (14) in dem Behälter (12; 121 bis 12N ) im Wesentlichen konstant und gleich einer Temperatur unter der Tripelpunkttemperatur des Reinwassers bleibt und wobei der Druck des ersten Gehäuses (10) im Wesentlichen gleich dem Sättigungsdampfdruck des Wassers in dem Gleichgewicht mit dem Druck des Wassers in dem flüssigen Zustand bei der Temperatur unter der Tripelpunkttemperatur des Wassers ist.
  4. Kälteanlage nach einem der Ansprüche 1 oder 2, wobei die Temperatur des flüssigen Wassers (14) in dem Behälter (12; 121 bis 12N ) größer oder gleich der Tripelpunkttemperatur des Reinwassers ist.
  5. Anlage nach einem der Ansprüche 1 bis 4, ferner umfassend ein System (42) zur Regelung der Druckdifferenz zwischen dem zweiten Gehäuse (30) und dem ersten Gehäuse (10), umfassend eine Entspannungsturbine (110), die so eingerichtet ist, dass sie Wasser in dem gasförmigen Zustand aus dem zweiten Gehäuse (30) entspannt und ein Gemisch enthält, das Wasser in dem gasförmigen Zustand und Wasser in dem flüssigen Zustand in das erste Gehäuse (10) fördert, wobei das Gemisch in dem flüssigen Zustand in das Wasser in dem Behälter zurückgeführt wird.
  6. Kälteanlage nach einem der Ansprüche 1 bis 5, umfassend eine Heizvorrichtung (22) des Wassers in gasförmigem Zustand in dem ersten Gehäuse (10), das zu der Versorgung der Kompressionsvorrichtung (32) bestimmt ist, wobei die Heizvorrichtung (22) eine Quelle einer Mikrowellenstrahlung und/oder eine Quelle einer Infrarotstrahlung umfasst.
  7. Anlage nach einem der Ansprüche 1 bis 6, wobei das Wasser in einem geschlossenen Kreislauf durch die Anlage zirkuliert.
  8. Kälteanlage nach einem der Ansprüche 1 bis 7, wobei die Kondensationsvorrichtung (34) einen ersten Wärmetauscher außerhalb des zweiten Gehäuses (30) und Mittel (36) zur Zirkulation eines ersten Wärmeträgermediums durch das erste Wärmeträgerfluid umfasst, wobei das erste Wärmeträgerfluid vorzugsweise Umgebungsluft oder Wasser eines Wasserlaufs, eines Wasserraums und/oder einer Wasserfläche ist.
  9. Kälteanlage nach einem der Ansprüche 1 bis 8, wobei:
    die Vorrichtung (24) zur Extraktion von Kälteleistung einen Hydraulikkreislauf umfasst, in dem ein Teil oder das gesamte in dem ersten Gehäuse (10) vorhandene Wasser in flüssigem Zustand zirkuliert, wobei der Hydraulikkreislauf einen zweiten Wärmetauscher (68) umfasst, der sich außerhalb des ersten Gehäuses befindet; oder
    die Vorrichtung (24) zur Extrakation von Kälteleistung einen geschlossenen Hydraulikkreislauf umfasst, in dem ein zweites Wärmeträgerfluid zirkuliert, wobei der Hydraulikkreislauf einen zweiten Wärmetauscher (68), der sich außerhalb des ersten Gehäuses befindet, und einen dritten Wärmetauscher (66), der in dem ersten Gehäuse (10) angeordnet ist, umfasst.
  10. Kälteanlage nach einem der Ansprüche 1 bis 9, umfassend in dem ersten Gehäuse eine Schutzvorrichtung (20) der Kompressionsvorrichtung (32) gegen das Eindringen von Partikeln in festem und/oder flüssigem Zustand.
  11. Anlage nach einem der Ansprüche 1 bis 10, wobei die Kondensationsvorrichtung (34) mindestens eine Düse (94) zum Spritzen von Wassertröpfchen (96) in flüssigem Zustand in das zweite Gehäuse (30) umfasst.
  12. Klimatisierungssystem für Industrieanlagen, umfassend eine Kälteanlage nach einem der Ansprüche 1 bis 11.
  13. System zur Erzeugung von künstlichem Schnee, umfassend eine Kälteanlage (5) nach einem der Ansprüche 1 bis 11.
  14. Verfahren zur Kälteerzeugung, umfassend folgende Schritte:
    Einbringen von Wasser in flüssigem Zustand (14) in ein erstes Gehäuse (10) auf eine Temperatur unterhalb der Temperatur des Tripelpunkts des Wassers, Bilden von Wasser in gasförmigem Zustand bei einem ersten Druck, der bis auf 10 % genau dem Sättigungsdampfdruck des Wassers in dem Gleichgewicht mit dem Druck des Wassers in flüssigem Zustand in dem ersten Gehäuse entspricht, Halten des flüssigen Wassers in Überschmelzung in dem ersten Gehäuse (10) durch Mittel, die mindestens ein dem Wasser in flüssigem Zustand hinzugefügtes Additiv umfassen, und Bilden von Wasser in festem Zustand (15) bei einer Temperatur unter der Temperatur des Tripelpunkts des Wassers;
    Verdichten von gasförmigem Wasser aus dem ersten Gehäuse in ein zweites Gehäuse mit einem zweiten Druck, der strikt über dem ersten Druck um mindestens einen Faktor zwei liegt, durch eine Kompressionsvorrichtung (32), umfassend zwei aufeinanderfolgende Stufen (130, 132), wobei jede Stufe (130, 132) einem Turbokompressor entspricht, mit einer ersten Kompressionsstufe (130) mit festem Kompressionsverhältnis und einer zweiten Kompressionsstufe (132) mit steuerbarem Kompressionsverhältnis, wobei die Drehzahl des zweiten Turbokompressors von einem Abgasmanagementmodul (40) gesteuert wird;
    Kondensieren des gasförmigen Wassers in dem zweiten Gehäuse in flüssigem Wasser; und
    Extrahieren von Kälteleistung in das erste Gehäuse.
EP18758929.6A 2017-07-28 2018-07-25 Kälteanlage Active EP3658835B8 (de)

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FR1757207A FR3069624B1 (fr) 2017-07-28 2017-07-28 Installation frigorifique
PCT/FR2018/051907 WO2019020940A1 (fr) 2017-07-28 2018-07-25 Installation frigorifique

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FR3117200B1 (fr) 2020-12-04 2023-01-13 Alpinov X Machine pour la fabrication de particules d’eau à l’état solide, de type particules de glace ou de neige
FR3117199B1 (fr) * 2020-12-04 2022-12-16 Alpinov X Evaporateur pour installation frigorifique délimitant deux enceintes d’évaporation respectivement à haute pression et basse pression et séparées par un écran de filtration
CN115325722B (zh) * 2022-08-16 2023-11-07 中国人民解放军海军特色医学中心 一种高压氧舱制冷系统

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CN111094879A (zh) 2020-05-01
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EP3658835A1 (de) 2020-06-03
AU2018307454B2 (en) 2024-04-11
CN111094879B (zh) 2022-03-04
EP3658835B8 (de) 2025-12-17
AU2018307454A1 (en) 2020-03-19
JP2020535382A (ja) 2020-12-03
WO2019020940A1 (fr) 2019-01-31
US20210156603A1 (en) 2021-05-27
BR112020001728B1 (pt) 2023-11-14
BR112020001728A2 (pt) 2020-07-21
JP7158476B2 (ja) 2022-10-21
KR102539042B1 (ko) 2023-05-31
EA039194B1 (ru) 2021-12-16
EA202090341A1 (ru) 2020-06-17
FR3069624A1 (fr) 2019-02-01
FR3069624B1 (fr) 2019-10-18

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