EP4206551A1 - Apparatus for treating air in arenas and related method of use - Google Patents

Apparatus for treating air in arenas and related method of use Download PDF

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Publication number
EP4206551A1
EP4206551A1 EP22217296.7A EP22217296A EP4206551A1 EP 4206551 A1 EP4206551 A1 EP 4206551A1 EP 22217296 A EP22217296 A EP 22217296A EP 4206551 A1 EP4206551 A1 EP 4206551A1
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EP
European Patent Office
Prior art keywords
air
cooling device
temperature
air flow
thermal treatment
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.)
Pending
Application number
EP22217296.7A
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German (de)
English (en)
French (fr)
Inventor
Paolo VIDAL
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Pv Solutions SRLS
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Pv Solutions SRLS
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Filing date
Publication date
Application filed by Pv Solutions SRLS filed Critical Pv Solutions SRLS
Publication of EP4206551A1 publication Critical patent/EP4206551A1/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F12/006—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an air-to-air heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F12/002—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid
    • F24F12/003—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid using a heat pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F2012/007—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using a by-pass for bypassing the heat-exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/20—Humidity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2221/00—Details or features not otherwise provided for
    • F24F2221/08—Installation or apparatus for use in sport halls, e.g. swimming pools, ice rings

Definitions

  • the present invention relates to an apparatus for treating air and the related method of use.
  • the invention is applicable to arenas, preferably to sports or recreational arenas, by way of example but not limited to sports facilities such as swimming pools or preferably ice arenas, where it is necessary to ensure a controlled temperature while avoiding the formation of condensation or fog and ensuring a certain flow rate of external air exchange.
  • thermo-hygrometric conditions For example, inside an ice arena, or ice rink, the ideal thermo-hygrometric conditions which are usually required envisage a temperature of about 10/12°C and a relative humidity of about 45%.
  • an extremely high humidity rate (close to 100%), in addition to being a source of discomfort for users, also causes the degradation of the arena structures and electrical and sound systems.
  • moisture by condensing, creates continuous drippings making the activity areas less performing.
  • the most common system for resolving the formation of condensation or surface fog, for example inside ice arenas is that which uses an adsorption dehumidifier which operates with a completely separate process air circuit and regeneration air circuit.
  • the dehumidifier sucks in the humid air inside the ice arena, conveys it to a rotor, comprising hygroscopic material on which the moisture remains trapped, and returns the dried air inside the ice arena.
  • the humidity bound to the rotor passes through a second separate treatment stage, called "regeneration", where it is released by exploiting the external air - sucked and suitably heated - and is then conveyed, to the outside.
  • a further disadvantage of these systems is that their operation usually does not take into account the external thermo-hygrometric conditions, as they are operated continuously and independently of the external-thermo-hygrometric conditions.
  • EP3499140A1 describes an air treatment and drying apparatus for air recirculation in a pool or similar spaces, in which there is a generally high temperature and is thus unsuitable for recirculating high flows of cold air in ice arenas or similar arenas. Furthermore, the apparatus described in EP3499140A1 does not allow to perform a control of the vapor quality during heating.
  • EP3438561A1 discloses an apparatus for treating air in a domestic space, in which the relative temperatures and humidity at play are very different from those of an ice arena or the like.
  • WO2019/078774A1 discloses a flow control device for a ventilation apparatus of a Heating, Ventilation and Air Conditioning (HVAC) system for living spaces.
  • HVAC Heating, Ventilation and Air Conditioning
  • an object of the present invention is to make an apparatus for the treatment of air, and to develop a relative method of use, suitable both to keep the required thermo-hygrometric conditions in the internal space of the arena, and to ensure a correct air exchange, in particular avoiding the formation of condensation or fog during the entire period of activity.
  • Another object of the invention is to make an air treatment apparatus and related method of use which is efficient and allows to adapt to the external thermo-hygrometric conditions to dehumidify the internal space of the arena and achieve energy savings.
  • An object is also to make an air treatment apparatus which is suitable for preventing the formation of moisture from condensation inside the space even during periods of inactivity, consequently reducing the maintenance time and costs of the arena.
  • Another object of the invention is to make an apparatus and a method for air treatment which allow air to be exchanged and recirculated effectively both in arenas hosting swimming pools, in which medium high temperatures and high humidity are envisaged, and in ice arenas, in which the thermo-hygrometric conditions envisage a temperature of about 10/12°C and a relative humidity of about 45%, regardless of the external temperature.
  • an apparatus for the treatment of air in an arena comprises first and second air movement means configured to generate an incoming air flow and an outgoing air flow.
  • Said apparatus further comprises at least one heat exchanger crossed between said air flows and at least one device for the thermal treatment of said incoming air flow, in which said at least one exchanger and said at least one device are able to manage the exchange of air between an external space and an internal space of said arena.
  • the apparatus further comprises at least one cooling device disposed between said exchanger and said thermal treatment device along the path of the incoming air flow.
  • a control unit comprised in said apparatus is configured to determine at least the flow rates of said air flows and the operating temperatures of said at least one exchanger and said at least one thermal treatment device, so as to maintain the internal temperature and the vapor quality in the internal space within a range of predefined values.
  • the control unit is also configured to adjust the operation and possibly the operating temperatures of the at least one cooling device in a coordinated manner with those of the heat exchanger and the thermal treatment device.
  • the at least one cooling device can be selectively activated by the control unit as a function of the internal temperature and the external temperature of the arena. That is, the cooling device can be selectively activated and deactivated as a function of needs.
  • the presence and the possibility of selectively activating the at least one cooling device make the apparatus according to the invention versatile and adaptable to use both in different types of arenas and in different climatic conditions, so as to ensure the maintenance of the desired hygrometric characteristics and the desired vapor quality within the arena in each season.
  • control unit can be configured to control said air movement means, said heat exchanger, and said at least one thermal treatment device, in order to manage the exchange of air between the external space and the internal space in relation to environmental parameters detected by detector devices, determining said flow rates of incoming and outgoing air flows and operating temperatures.
  • Said apparatus further comprises environmental parameter detector devices comprising at least one detector of said internal temperature and a detector of said vapor quality.
  • the detector devices also comprise an external temperature detector, suitable for detecting at least the temperature of the space outside the arena.
  • thermo-hygrometric conditions in the internal space of the arena, combining the exchange of air with the action of dehumidification and temperature control, as well as significant savings in terms of energy consumption, and it is not necessary to install special equipment for the exchange of air.
  • the use of the internal temperature and the vapor quality as setting values on which to base the adjustment of the ventilation means and the operating temperatures allows to have an absolute reference value which is suitable for any environmental condition.
  • Said absolute reference allows the system to self-regulate, modifying the internal temperature so as to always set the conditions so as to respect the set vapor quality value.
  • the apparatus according to the invention allows the air to be introduced into the arena under the thermo-hygrometric conditions suitable for maintaining the established conditions.
  • the apparatus according to the invention allows to exploit the external thermo-hygrometric conditions to dehumidify the internal space almost free of charge, without using adsorption systems which are expensive.
  • said treatment apparatus comprises at least one further thermal treatment device of the air, selected from a heating or cooling device, selectively activatable by said control unit as a function of internal and external temperatures.
  • the at least one further thermal treatment device is configured to only treat the incoming air flow and does not interfere with the outgoing air flow.
  • thermo-hygrometric parameters It is thus possible to optimize temperature control, reducing the time to reach the desired thermo-hygrometric parameters.
  • the apparatus comprises at least one heating device positioned upstream of said heat exchanger and configured to heat the incoming air flow. It is thereby possible to prevent the freezing of parts of the heat exchanger, with incoming air flow at a temperature lower than or equal to about 2°C.
  • the apparatus comprises the at least one cooling device disposed between the heat exchanger and the air thermal treatment device, selectively activatable at least when the external temperature is higher than the desired internal temperature. It is thereby possible to effectively reduce any moisture contained therein and allow the easier maintenance of the vapor quality in the desired range of values.
  • said at least one cooling device can be deactivated and, when deactivated, can be selectively associated with defrosting means: it is thus possible to bring the temperature of the incoming air flow around or below 0°C, allowing an effective and rapid reduction of any moisture contained therein while avoiding the blockage of the cooling device itself, due to the formation of ice in its parts.
  • the apparatus according to the invention can comprise two cooling devices disposed in cascade to each other, and in which the second has lower operating temperatures than the first cooling device; in this case the defrosting means can be associated with the second defrosting device and can also be operated automatically at predefined intervals.
  • said second air movement means can comprise a perimeter recovery channel of the internal space of the arena.
  • the perimeter recovery channel for example a perimeter recovery channel of an ice rink, can be configured to prevent, with its suction action, the formation of fog.
  • an apparatus 10 for treating air in an arena comprises at least first and second air movement means 11a, 11b, environmental parameter detector devices 12, a thermal treatment assembly 13 and a control unit 14.
  • the apparatus 10 is in any case intended to be applicable to any arena, for example preferably to a sports or recreational arena, for which a controlled temperature is to be ensured, to avoid the formation of condensation or surface fog in the internal space and to ensure a certain flow rate of external air exchange.
  • the first air movement means 11a can be configured to generate an incoming air flow F1. They can comprise air suction means 15, configured to suck air from the outside and send it to the thermal treatment assembly 13, provided with air flow rate regulation elements 18 and/or air movement elements 23 and at least one delivery channel 45.
  • the air movement elements 23 can be positioned downstream of a thermal treatment device 27 of the thermal treatment assembly 13.
  • the downstream positioning of the thermal treatment device 27 allows a greater uniformity of the air flow into the internal space 101, for example of the ice rink as depicted in fig. 2 .
  • the air movement elements 23 are positioned inside the thermal treatment assembly 13 and downstream of a thermal treatment device 27.
  • the second air movement means 11b can be configured to generate an outgoing air flow F2. They can comprise air expulsion means 16, configured to expel air from the thermal treatment assembly 13 outside the ice arena 100, provided with air flow rate regulation elements 20 and/or air movement elements 21 and at least one recovery channel 46.
  • the air movement elements 21 can be positioned downstream of a heat exchanger 26 of the thermal treatment assembly 13.
  • the positioning of the air movement elements 21 downstream of the heat exchanger 26 allows to optimize the operation of the heat exchanger 26.
  • the apparatus 10 can further comprise internal movement means 17, configured to move air inside the thermal treatment assembly 13 and to and from the internal space 101 of the ice arena 100.
  • Internal space 101 of the ice arena 100 is intended as the space comprising the ice rink 102, bleachers, stairs, and the like, where athletes and the public can be found.
  • the internal movement means 17 can comprise air flow rate adjustment elements 22a, 22b, 22c, 22d.
  • the air flow rate adjustment elements 22b, 22c, 22d can be positioned inside the thermal treatment assembly 13.
  • the air flow rate adjustment elements 18, 20, 22a, 22b, 22c, 22d can be valves, gates, dampers, configured for continuous adjustment or for on/off-type adjustment or the like.
  • the air movement elements 21, 23 can be motor fans, fans, aspirators, or the like.
  • Said delivery channel 45 and recovery channel 46 can be pipes, conduits, ducts, or the like, able to create a circulation circuit for the air flow, as depicted in fig. 2 .
  • the delivery channel 45 can comprise nozzles 50 for the exit of air.
  • the recovery channel 46 can comprise an upper recovery channel 48 and a perimeter recovery channel 49, comprising air suction inlets 51, 52.
  • the inlets 52 of the perimeter recovery channel 49 can be positioned in correspondence with the ice rink 102, in particular positioned at a height from the rink 102 which is as low as possible, as a function of on structural conditions, regulations and the like.
  • the inlets 52 can be positioned at a height of less than 2 meters, preferably less than 1.5 meters, even more preferably 1 meter, even more preferably less than 50 cm.
  • the inlets 52 can in any case be provided in the proximity of the floor.
  • the environmental parameter detector devices 12 can be sensors or detection devices of environmental parameters such as temperature, humidity, vapor quality, and the like.
  • the detector devices 12 can comprise at least one detector 24 of internal temperature Ti and a detector 25 of relative humidity and/or vapor quality TdVi of the internal space 101.
  • the value of the vapor quality TdVi can be calculated based on the internal temperature Ti and the relative humidity detected.
  • the detector devices 12 can also comprise external parameter detectors, such as a detector 28 of the external temperature Te and/or a detector 19 of relative external humidity and/or a detector of external vapor quality TdVe.
  • the value of the vapor quality TdVe can be calculated based on the external temperature Te and the external relative humidity.
  • the apparatus 10 can further comprise non-environmental parameter detector devices, such as sensors for flow, flow rate, fog, the number of people or the like, not depicted in the figures.
  • non-environmental parameter detector devices such as sensors for flow, flow rate, fog, the number of people or the like, not depicted in the figures.
  • the thermal treatment assembly 13 can comprise at least the aforesaid heat exchanger 26 and air thermal treatment device 27.
  • the exchanger 26 can be of the cross-flow type, configured for heat exchange between the incoming F1 and outgoing F2 air flows, for the pre-treatment or treatment of the incoming air flow F1 for energy saving purposes.
  • the heat exchanger 26 can heat the incoming air flow F1; on the other hand, if the external temperature Te is higher than that desired in the internal space 101, the heat exchanger 26 can cool it.
  • the predefined value Ti_set of the internal temperature Ti is the temperature which is desired to be kept in the internal space 101 of the ice arena 100.
  • the value Ti set can be comprised between 10 and 12 °C.
  • the air thermal treatment device 27 can be configured to bring the air to the desired temperature in the space 101.
  • the thermal treatment device 27 can be able to heat and possibly cool the air, preferably to heat it.
  • the thermal treatment device 27 can be associated with heating means 36 and/or with cooling means 37, allowing a selective activation of one or the other by acting on fluid flow control means 43.
  • the thermal treatment device 27 can comprise only heating means 36 or cooling means 37, or both.
  • the control unit 14 can be a microprocessor, a computer, a server, a PLC, an electronic platform, or the like.
  • the control unit 14 can comprise, in a known manner, at least one memory module and the processing module, configured respectively to store and execute control algorithms of the apparatus 10, and interface elements with an operator for setting at least the desired values of temperature Ti_set and vapor quality TdVi_set.
  • the processing module can be one or more processors of any type of local or remote processor, able to execute the aforesaid program.
  • the memory module can be one or more of those commercially available, such as random access memory (RAM), read-only memory (ROM), floppy disk, hard disk, mass memory, or any other form of digital storage, local or remote.
  • Said control algorithms can be configured to receive in input, or calculate, environmental parameters or non-environmental parameters, such as internal temperature Ti, external temperature Te, internal vapor quality TdVi, external vapor quality TdVe, flow, flow rate, presence of fog on the rink 102, number of people inside the ice arena 100 and the like, and to process them for controlling at least said air movement means 11a, 11b and the thermal treatment assembly 13.
  • environmental parameters or non-environmental parameters such as internal temperature Ti, external temperature Te, internal vapor quality TdVi, external vapor quality TdVe, flow, flow rate, presence of fog on the rink 102, number of people inside the ice arena 100 and the like.
  • the latent moisture load to be neutralized is formed only by the water vapor produced by the people present in the ice arena 100: the air flow rate necessary to neutralize it will be automatically managed by the control unit 14 as a function of the number of people.
  • the required internal vapor quality TdVi_set can be less than 5 g/kg dry air (d.a.), preferably less than 4 g/kg d.a., even more preferably substantially equal to or less than 3.77 g/kg d.a.
  • Table 1 Temperature 12.00 °C Relative humidity 43.00 % Saturation pressure 1,402.59 Pa Vapor pressure 603.11 Pa Vapor quality 3.72 gr/Kg d.a.
  • control unit 14 is configured at least to regulate the air flow rate of the air movement means 11a, 11b and the heat exchange temperatures of said exchanger 26 and said at least one air thermal treatment device 27 to keep the vapor quality TdVi in the internal space 101 at the desired value TdVi_set or in near thereto.
  • the apparatus 10 can comprise at least one further air thermal treatment device 29, 30, 31, which can be selectively activated by the control unit 14, as a function of the internal temperature Ti and the internal vapor quality TdVi and, where appropriate, the external temperature Te and the external vapor quality TdVe.
  • the thermal treatment device 29, 30, 31 can be able to heat and/or cool the air.
  • the at least one further thermal treatment device can be chosen from a heating device 29 or a cooling device 30, 31.
  • the apparatus 10 can comprise a heating device 29 disposed upstream of said exchanger 26.
  • the heating device 29 can be associated with heating means 36 by fluid flow control means 44.
  • the apparatus 10 can comprise at least one cooling device 30, 31 disposed between said exchanger 26 and said thermal treatment device 27.
  • the apparatus 10 comprises at least one heating device 29 disposed upstream of the at least one exchanger 26 and at least one cooling device 30, 31 disposed between the at least one exchanger 26 and the thermal treatment device 27.
  • control unit 14 can also be configured to regulate the operation and possibly the operating temperatures of the at least one cooling device 30, 31 and/or the heating device 29, if present, in a manner coordinated with those of the heat exchanger 26 and the thermal treatment device 27.
  • the cooling device 31 can be deactivatable and a bypass path B outside said cooling device 31 can be provided, able to allow the passage of said incoming air flow F1 when the cooling device 31 is deactivated.
  • said cooling device 31 can be deactivated by the operation of respective adjustment means 22b, 22c which deviate the flow towards the bypass path B, excluding the path A.
  • the cooling device 31 When deactivated, the cooling device 31 is connectable to defrosting means 32; when activated, the cooling device 31 is connectable to cooling means 37.
  • the apparatus can comprise fluid flow control means 33, such as valves 34 and circulation pumps 35, for selectively associating the cooling device 31 with defrosting means 32 or with cooling means 37; said control means 33 can be configured as switching means.
  • fluid flow control means 33 such as valves 34 and circulation pumps 35, for selectively associating the cooling device 31 with defrosting means 32 or with cooling means 37; said control means 33 can be configured as switching means.
  • a second cooling device 31 is located in cascade to a first cooling device 30 and is configured to operate at lower temperatures with respect thereto.
  • the defrosting means 32 can be connected to only the second cooling device 31.
  • the defrosting means 32 are connectable to both of the cooling devices 30, 31.
  • the apparatus 10 can comprise fluid flow control means 38, such as valves 39 and circulation pumps 40, configured to associate the cooling device 30 with cooling means 37.
  • fluid flow control means 38 such as valves 39 and circulation pumps 40, configured to associate the cooling device 30 with cooling means 37.
  • the apparatus 10 can comprise a filtering battery 47, for the filtration of incoming air for the elimination of impurities and dust.
  • the thermal treatment devices 29 can be heating devices or heat exchangers configured to cooperate with heating means 36 or the like; the thermal treatment devices 30, 31 can be a heat exchanger configured to cooperate with cooling means 37 and/or with defrosting means 32 or the like.
  • the cooling means 37 can be or comprise in a known manner a refrigeration assembly - or chiller - or a multi-purpose chiller or the like.
  • the heating means 36 and the defrosting means 32 can be or comprise in a known manner one or more of heat pumps, boilers, multi-purpose chillers, total heat recovery systems of cooling means 37 or heat storage tanks fed in turn by air treatment means 55 comprising one or more of heat pumps 54, boilers, multi-purpose chillers, total heat recovery systems, storage tanks and/or the like.
  • the efficiency of the apparatus 10 is greater with respect to the known adsorption dehumidification systems. Even more advantageously, if the apparatus 10 allows total heat recovery, the evaporation of moisture does not require further energy consumption.
  • the defrosting means 32 can coincide with the heating means 36.
  • the operation of the apparatus 10 for the treatment of air in arenas 100 described so far, which corresponds to the method according to the present invention, comprises the steps described below.
  • the method of use envisages providing an apparatus 10 for air treatment comprising air movement means 11a, 11b, environmental parameter detector devices 12, a thermal treatment assembly 13 and a control unit 14.
  • the method of use provides to:
  • the method can further provide to detect the vapor quality TdVe in the external space 200.
  • the method can generally provide to use at least one further air thermal treatment device 29, 30, 31, selected from a heating device 29 or cooling devices 30, 31 and selectively activatable as a function of the environmental conditions.
  • the method can provide to activate the cooling device 31 for dehumidification when the vapor quality TdVe in the external space 200 is higher than the internal vapor quality TdVi.
  • the cooling device 31 can be activated only when necessary, it being possible to perform the dehumidification free of charge when the vapor quality TdVe in the external space 200 is lower than the internal vapor quality TdVi, as described below.
  • the method can provide at least two different operating modes: a first mode in conditions of external temperature Te lower than a predefined value Ti_set of the internal temperature Ti and a second mode in conditions of external temperature Te higher than the predefined value Ti_set.
  • the first operating mode can be for example during the winter period, in which the external temperatures Te can assume values up to -10 °C, or less, and in which the external vapor quality TdVe is lower than the required internal vapor quality TdVi set.
  • the dehumidification can simply occur by the input of external air: the incoming air flow F1 of dry air, coming into contact with the humid air in an internal space 101, is saturated and is expelled by the outgoing air flow F2 with a higher vapor quality; thereby there is a continuous transport of matter (water vapor) between the incoming and outgoing air, resulting in the dehumidification of the area inside the arena.
  • thermo hygrometric condition the need for air exchange coincides with the dehumidification of the air inside the arena 100, which occurs without the use of other dehumidification means and, therefore, with significant savings of energy and economic resources.
  • the exchanger 26 can act as a condenser, because the temperature of the incoming air flow F1 is lower than that of the outgoing air flow F2 coming from inside the arena 100.
  • the method can then provide to heat the incoming air flow F1 by the heat exchanger 26 and/or the thermal treatment device 27. In particular, it can provide to pre-heat the incoming air flow F1 by means of said exchanger 26 and further heat it by means of the thermal treatment device 27.
  • the method can provide to pre-heat the external air, for example at temperatures comprised between about 0 and 2°C or higher, by means of a heating device 29 positioned upstream of said exchanger 26. Thereby, a possible formation of frost in correspondence with the exchanger 26 is avoided.
  • the second operating can be implemented during the summer period, in which the external temperatures Te can assume values up to 20 °C or more and in which the external vapor quality TdVe is higher than the required internal vapor quality TdVi_set.
  • the method can provide to cool the external air by means of the exchanger 26. It can further provide to further cool the air by means of the at least one cooling device 30, 31, if present.
  • the method can provide to dehumidify the incoming air flow F1 to about 2/3 of the desired total dehumidification by means of the first cooling device 30.
  • the method can provide to feed the cooling device 30 by means of a cooling fluid having a temperature comprised between -1 and 4°C, preferably below 0°C, preferably substantially -1°C.
  • the method can provide to send the air in output from the first cooling device 30 to the second cooling device 31, when this is activated, or to the at least one thermal treatment device 27, when the cooling device 31 is deactivated.
  • the method can provide to feed the second cooling device 31 with a cooling fluid having a temperature comprised between 0 and -5°C, preferably below 0°C, still more preferably substantially -5°C.
  • the method can provide to perform an automatic defrosting procedure, in particular of the second cooling device 31 when two or more cooling devices 30, 31 are provided.
  • the method can provide to activate or deactivate said cooling device 31, closing the path A by means of adjustment elements 22b and diverting the incoming air flow F1 towards the bypass path B.
  • the cooling device 31 When deactivated, the cooling device 31 can be connected to defrosting means 32, while when activated, it can be connected to cooling means 37.
  • the cooling means 37 can be controlled by the control unit 14, based on the temperature and vapor pressure levels of the air in input to the internal space 101 of the ice arena 100.
  • the aforesaid temperature and vapor pressure levels of the air in input can be detected by temperature probes 41 and vapor pressure probes 42.
  • the essential condition for reaching the required vapor quality TdVi_set is to have a cooling fluid circulating within the cooling device 31 with a fluid temperature below 0°C. This condition inevitably causes frost to form on the surface of the cooling device 31 itself.
  • the aforesaid defrosting method allows to repair such a criticality.
  • the defrosting method can be activated autonomously, at regular cycles, for example every 2 or 3 hours.
  • the control unit 14 can manage the defrosting method, for example by detecting the presence of frost or ice, by means of detectors not depicted in the figures.
  • the defrosting method can provide at least part of the following steps:
  • the process can provide air movement elements 21, 23 to maintain a predetermined and constant flow rate even during the defrosting method.
  • the method can provide at least some of the following operating conditions:
  • the start-up operating condition can provide only the recirculation of internal air.
  • the start-up operating condition can provide to operate in said first mode with external temperature conditions Te lower than a predefined value Ti_set or in said second mode with external temperature conditions Te higher than the predefined value Ti set.
  • the air suction means 15 and the air expulsion means 16 can be controlled, in a known manner, to withdraw the air from the recovery channel 46, closing the access to the external air.
  • the apparatus 10 can be started, in internal recirculation, to increase or decrease the internal temperature Ti up to the value Ti_set, depending on the external temperature conditions Te.
  • the air movement elements 21, 23 can keep a predetermined and constant flow rate during the start-up phase.
  • the maintenance operating condition can provide only for internal recirculation and maintenance of the internal temperature Ti and the vapor quality TdVi. If the vapor quality TdVi is higher than the set critical condition, the cooling device 31 and, possibly, the cooling device 30 can be activated in the maintenance operating condition. The defrosting method can then be activated.
  • the exchange operating condition with all external air can provide for operation with only external air, excluding internal recirculation, and the maintenance of the internal temperature Ti and the vapor quality TdVi.
  • the operation of the apparatus 10 during the exchange operating condition with all external air is substantially the same as the maintenance operating condition.
  • the flow rate of the air movement elements 21, 23 can be modulated, for example on the basis of the number of spectators present.
  • the modular internal air recirculation and external air exchange mixed operating condition can provide to control the air suction means 15 and the air exhaust means 16 so as to modulate the internal air recirculation and external air exchange flow rate, with varying and otherwise settable percentages, from 0% external air exchange and 100% internal air recirculation, to 100% external air exchange and 0% internal air recirculation.
  • the operation of the apparatus 10 during the modular mixed external air exchange and internal air recirculation operating condition is substantially the same as the maintenance operating condition.
  • the method can provide, in order to optimize consumption, to increase the efficiency and/or yield of the heating, to activate one or more of the aforesaid heat pumps, boilers, multi-purpose chillers, total heat recovery systems of the thermal treatment assembly 13, in particular of the cooling means 37, or of the air treatment means 55.
  • an activation sequence of heat sources of air treatment means 55 can provide:
  • the energy recovered in the form of heat from the total recuperator during the operation of a chiller is greater than the refrigeration effect by about 30%; therefore, when the chiller is active, the recovered heat makes the entire system self-sufficient, cancelling the cost necessary to heat the carrier fluid by means of the boiler or the heat pump 54.
  • the method can provide to increase the efficiency of the apparatus 10 by sending the outgoing air flow F2, prior to emission into the external space 200, to a heat pump 54 ( fig. 3 ), to increase the temperature of the incoming air to its evaporating coil: the increase in the COP (Coefficient Of Performance) of a heat pump is directly proportional to the increase in the temperature of the incoming air to its evaporating coil.
  • a heat pump 54 fig. 3
  • the method can provide to increase the efficiency of the apparatus 10 by sending the air withdrawn from the space 200 to the evaporating coil of a heat pump 54 and subsequently to the thermal treatment assembly 13, in particular to the heat exchanger 26: the vapor quality of the air in output from the evaporator is always lower than that in the space 200, since the passage of the air through the exchange surface of the evaporator, which is at a lower temperature than the ambient temperature Te, determines the dehumidification thereof ( fig. 4 ).
  • the aforesaid heat pump can for example be the heat pump 54 of air treatment means 55 or a heat pump comprised in the thermal treatment assembly 13.
  • the total power required in cooling and dehumidification can substantially correspond to 190 kW, in heating to 286 kW, for a vapor quality TdVi of about 2.49; with the sending to the thermal treatment assembly 13 of air through the heat pump 54, the total power required in cooling and dehumidification can substantially correspond to 0 W, in heating to 180 kW, for the same vapor quality TdVi.
  • the method can provide to suck air from the internal space 101 only through a perimeter recovery channel 49 of the rink 102, closing an upper recovery channel 48. Thereby, damp air, and possibly fog, present on the rink 102 can be drawn by means of suction through air suction inlets in correspondence with the rink 102.
  • the apparatus 10 With an external temperature Te of -5°C, a relative humidity of 100% and an external vapor pressure TdVe of 2.48, the apparatus 10 according to the present invention has a consumption of about electric 130 kW.
  • the known adsorption dehumidification system - under the same conditions - has a consumption of about electric 226 kW.
  • the apparatus 10 according to the present invention unlike the known adsorption system, also performs, with a consumption of slightly more than half, two other functions: the exchange of the internal air and the heating of that which withdraws from the outside.
  • the latent load In summer, the latent load, already highlighted in winter, must be added to that related to the humidity present in the external air. Keeping the number of people and the exchange rate equal, with an external temperature Te of 15°C, a relative humidity of 75% and an external vapor pressure TdVe of 7.95, the total amount of water vapor to be condensed is equal to 218.92 kg/h.
  • the apparatus 10 - under suitable internal conditions to avoid the formation of fog and/or condensation and for an internal vapor pressure TdVi of 3.46 - has a consumption of about electric 170 kW.
  • the known adsorption dehumidification system has an electrical consumption which is not proportional to that of summer, as the relative humidity conditions of the internal space are not the same. This is due to the fact that the absolute humidity in winter is lower than that in summer.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Separation Of Gases By Adsorption (AREA)
  • Central Air Conditioning (AREA)
EP22217296.7A 2022-01-04 2022-12-30 Apparatus for treating air in arenas and related method of use Pending EP4206551A1 (en)

Applications Claiming Priority (1)

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IT102022000000068A IT202200000068A1 (it) 2022-01-04 2022-01-04 Apparato per il trattamento di aria in palazzetti e relativo procedimento d'uso

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110065372A1 (en) * 2002-12-02 2011-03-17 Volker Spiegel Recreation Room and Method of Adjusting the Room Atmosphere
FR3002026A1 (fr) * 2013-02-14 2014-08-15 Performance Energetique Lpe Installation et procede de regulation thermique multizone
EP3438561A1 (en) 2017-08-02 2019-02-06 Kris Vanrenterghem Air handling unit with internal heat pump
WO2019078774A1 (en) 2017-10-20 2019-04-25 Swegon Operations Ab FLOW CONTROL ARRANGEMENT FOR AIR VENTILATION SYSTEM
EP3499140A1 (fr) 2017-12-13 2019-06-19 Sustain'air Centrale de traitement d'air double flux et à dessiccation adaptée aux bâtiments d'activité aquatique, et procédé de pilotage d'une telle centrale
KR20200049022A (ko) * 2018-10-31 2020-05-08 주식회사 도우이앤이 공기조화시스템의 배기열 회수 장치

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110065372A1 (en) * 2002-12-02 2011-03-17 Volker Spiegel Recreation Room and Method of Adjusting the Room Atmosphere
FR3002026A1 (fr) * 2013-02-14 2014-08-15 Performance Energetique Lpe Installation et procede de regulation thermique multizone
EP3438561A1 (en) 2017-08-02 2019-02-06 Kris Vanrenterghem Air handling unit with internal heat pump
WO2019078774A1 (en) 2017-10-20 2019-04-25 Swegon Operations Ab FLOW CONTROL ARRANGEMENT FOR AIR VENTILATION SYSTEM
EP3499140A1 (fr) 2017-12-13 2019-06-19 Sustain'air Centrale de traitement d'air double flux et à dessiccation adaptée aux bâtiments d'activité aquatique, et procédé de pilotage d'une telle centrale
KR20200049022A (ko) * 2018-10-31 2020-05-08 주식회사 도우이앤이 공기조화시스템의 배기열 회수 장치

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