WO2021037979A1 - Système de stockage à froid intégré et procédé pour réaliser un stockage à froid - Google Patents

Système de stockage à froid intégré et procédé pour réaliser un stockage à froid Download PDF

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Publication number
WO2021037979A1
WO2021037979A1 PCT/EP2020/073973 EP2020073973W WO2021037979A1 WO 2021037979 A1 WO2021037979 A1 WO 2021037979A1 EP 2020073973 W EP2020073973 W EP 2020073973W WO 2021037979 A1 WO2021037979 A1 WO 2021037979A1
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WO
WIPO (PCT)
Prior art keywords
cold storage
temperature
htf
bypass
compressor
Prior art date
Application number
PCT/EP2020/073973
Other languages
English (en)
Inventor
Sami Abdulrahman ALBAKRI
Original Assignee
Sab Engineers Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from EP19209171.8A external-priority patent/EP3786545A1/fr
Application filed by Sab Engineers Gmbh filed Critical Sab Engineers Gmbh
Priority to EP20768282.4A priority Critical patent/EP4022231A1/fr
Publication of WO2021037979A1 publication Critical patent/WO2021037979A1/fr

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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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat
    • 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
    • F25B2600/00—Control issues
    • F25B2600/21—Refrigerant outlet evaporator temperature

Definitions

  • the present invention relates to a Cold Storage System and a method for per forming a cold storage and, in particular, to an integrated chiller-storage system in which the chiller is in part combined with the cold storage.
  • Cold Storage Systems find applications in industry as well as in commercial and private contexts.
  • An example of such an application is temperature equalization over day and night cycles in buildings or in industrial plants like e.g. solar panel systems, in particular in countries where differences between daytime and nighttime temperatures are considerable.
  • scientific research confirms that human activities contribute significantly to global climate change, technical facilities in general are facing a challenge to reduce the emission of heat energy and greenhouse gases, and to operate in more energy efficient ways.
  • Cold Storage Sys tems - rather than devices delivering refrigeration without comprising an inte grated cold storage - can be an efficient, economic way to contribute to these objectives.
  • Cold Storage System refers to a system of heat energy transfer com- prising a device designed to retain refrigerated material (the cold storage), which may further encompass means for achieving the refrigeration of this material (a chiller) and for absorbing heat energy (by a heat exchanger) from a particular part of the environment (the consumer) for the duration of predefined periods of time.
  • FIG. 9 depicts a conventional Cold Storage System, comprising a circuit of pipes holding an appropriate medium for the conduction of the heat energy (HTF, heat transfer fluid), moved by a pumping device (here a compressor 12) and passing in series through a chiller 16, a cold storage 14 - which due to the intended func- tionality of the system will be referred to as “charged” if it is capable of absorbing heat energy from the HTF - and a heat exchanger 15 to provide refrigeration to a consumer 31.
  • HTF heat transfer fluid
  • discharging mode a situation in which the Cold Storage System is operated to provide coldness to the consumer 31 via the heat exchanger 15 will be referred to as discharging mode
  • charging mode a situation in which the Cold Storage System is operated to reduce the heat energy in the cold storage 14 (here by means of the chiller 16)
  • charging mode a situation in which the Cold Storage System is operated to reduce the heat energy in the cold storage 14 (here by means of the chiller 16)
  • the chiller 16 includes of a vapor-compression refrigeration system, which effectively absorbs heat energy from the HTF and emits it into the environment via a separate refrigerant (RT) circuit.
  • the RT (which can include e.g. carbon dioxide, ammonia, sulfur dioxide, or non-halogenated hydrocarbons) is set in motion by its own compres sor 162, and passes through a condenser unit 163, an expansion unit 164 (e.g. a valve), and an evaporator 165 where it gets in thermal contact with the HTF, producing the cooling effect via a reverse-Rankine cycle.
  • the HTF circuit and the RT circuit form two separate closed systems, and the heat transfer between HTF and RT takes place using a fluid-fluid-heat exchanger.
  • the present invention relates to a Cold Storage System
  • a compressor or some other sort of pumping device for compressing and enabling a circula- tion of a heat transfer fluid (HTF, as e.g. carbon dioxide, ammonia, or non- halogenated hydrocarbons), a condenser with a condenser unit for cooling the compressed HTF (e.g. by ambient air) and an expansion unit (as e.g. an expan sion valve) for decreasing the pressure of the HTF, thereby further cooling the HTF, and a cold storage with an integrated evaporator, where the cold storage is configured to store the coldness transferred by the HTF.
  • HTF heat transfer fluid
  • a condenser with a condenser unit for cooling the compressed HTF (e.g. by ambient air)
  • an expansion unit as e.g. an expan sion valve
  • the cold storage is configured to store the coldness transferred by the HTF.
  • the devices are positioned on an HTF circuit, such that the system can operate in a charging mode in which the cold storage is refrigerated (charged), e.g. by the HTF undergoing a reverse-Rankine cycle:
  • the compressor will compress the HTF to a higher pressure (of e.g. 50 bar), thereby also increasing the HTF tem perature.
  • the HTF then enters the condenser unit, where it effectively emits heat energy into the environment (e.g. into the ambient air). After the condenser unit, the HTF enters the expansion valve, where its pressure decreases (e.g. to 10 bar), combined with a (sharp) reduction of its temperature.
  • the cold HTF flows into the cold storage, which it refrigerates by passing through the integrated evapora tor. After leaving the packed bed system, the HTF (which may now be entirely in a gaseous state) will eventually enter the compressor again, and the cycle is re peated.
  • the Cold Storage System further comprises a heat exchanger for de- livering of coldness to a consumer, wherein the heat exchanger is arranged be tween the compressor and the cold storage.
  • the Cold Storage System is operable in a charging mode during which the heat energy stored in the cold storage de creases, or in a discharging mode during which the heat exchanger delivers coldness to the consumer.
  • the heat exchanger can e.g. include a coil through which the HTF streams, ex changing heat with ambient air passed over the coil (e.g. by means of a fan).
  • the heat transfer may be achieved by a single circuit by only using the HTF without using a heat transfer between the HTF and a refrigerant (RT).
  • the cold storage includes an integrated evaporator.
  • the cold storage includes a multi-packed bed sys tem.
  • a packed bed is a vertical vessel including a packing material (a bulk of monodisperse and/or polydisperse solid particles made of e.g. aluminium oxide, steel or ceramic and/or phase change material (PCM)), through which a stream of gas or liquid (here the HTF) passes in order to either deposit or extract heat energy from the packing material, depending on the mode of operation.
  • a packing material a bulk of monodisperse and/or polydisperse solid particles made of e.g. aluminium oxide, steel or ceramic and/or phase change material (PCM)
  • packed beds may be combined into multi-packed bed systems including a plurality (one or more) of such packed beds, and provide efficient, durable, simple to con struct, and scalable thermal energy storage devices.
  • the cold storage therefore includes a multi-packed bed system com prising a plurality of packed beds, which are employed as an evaporator for the HTF in charging mode.
  • the multi-packed bed system further comprises a plurality of packed bed valves, such that the amount of heat transfer fluid flowing through each packed bed is controlled by at least one respective packed bed valve.
  • managing one or more correspondingly adapted charging and discharging processes for the multi -packed bed system is important for an efficient application of the system.
  • Different charging and discharging processes can have different effects on tem perature profiles, longevity, and/ or timescales of the operation of the multi- packed bed system.
  • the Cold Storage System is chiller-free, by which it is understood that the system does not include any further device adapted to reduce the tempera ture of the heat transfer fluid and/or the amount of heat energy stored in the cold storage other than the aforementioned condenser unit and expansion unit.
  • This optional feature in particular instantiates the reduction of complexity of the system mentioned in the introduction.
  • the Cold Storage System further comprises a heat exchanger bypass with a heat exchanger bypass valve, where the heat exchanger bypass is adapted to bypass the heat exchanger and to channel heat transfer fluid from the outlet of the cold storage to the inlet of the compressor, and the heat exchanger bypass valve is adapted to control a flow of heat transfer fluid through the heat ex changer bypass to keep a temperature at the inlet of the compressor at a prede fined range of temperature (e.g. between 20 °C and 30 °C) or around a setpoint temperature (e.g. 25 °C).
  • the compressor operates efficiently only within a specific range of conditions for the HTF.
  • the HTF temperature is related to the volumetric flow rate of the HTF, and larger volumetric flow rates lead to higher power consump tion for the compressor.
  • the HTF is generally at a high temperature (which may be related to an ambient temperature, and can be e.g. 50 °C).
  • the heat exchanger bypass reduces this temperature and thereby the volumetric flow rate of the HTF before the HTF enters the compressor, and therefore has a positive effect on the efficiency of the compressor.
  • the efficiency of the cold storage to absorb heat energy from the HTF in dis charging mode can vary over time, which can lead to a varying HTF temperature at the exit of the cold storage, and therefore also at the inlet of the heat exchang er. This, in turn, can mean that the heat exchanger does not absorb heat energy from the environment and thus not deliver coldness to the consumer in a con stant way.
  • the Cold Storage System therefore further comprises a cold storage bypass with a cold storage bypass valve, wherein the cold storage bypass is adapted to bypass the cold storage and to channel heat transfer fluid from the inlet of the cold storage to the inlet of the heat exchanger, and the cold storage bypass valve is adapted to control a flow of heat transfer fluid through the cold storage bypass line to keep a temperature at the inlet of the heat exchanger at a predefined range of temperature or around a setpoint temperature.
  • the setpoint temperature may be selectable by the consumer, and should lie above the low or ultra-low temperature at which the HTF exits the cold storage, but below the ambient air temperature (examples for the setpoint temperature could be 8 °C, 14 °C, or 16 °C). According to embodi ments, the operation of the cold storage bypass does not interfere with the oper ation of the aforementioned heat exchanger bypass.
  • the Cold Storage System includes only a single compressor, and no further pumping device.
  • the system can be in charging mode, during which the HTF is refrigerated over time, and the heat energy in the cold storage decreases.
  • This can have the effect that the compressor is required to work under varying HTF temperature condi tions over the course of the charging process.
  • varying condi tions can again have a negative effect on the efficiency of the compressor.
  • the Cold Storage System therefore further comprises a chiller/ cold storage bypass with a chiller/cold storage bypass valve, wherein the chiller/cold storage bypass is adapted to bypass the condenser and the cold storage and to channel heat transfer fluid from a position between the compressor and the condenser unit and from a position after the expansion valve to the inlet of the compressor when the Cold Storage System is operated in a charging mode, and wherein the chiller/cold storage bypass valve is adapted to control a flow of heat transfer fluid through the chiller bypass to keep a temperature at the inlet of the compressor at a predefined range of temperature or around a setpoint tempera ture.
  • the Cold Storage System further comprises a control unit configured to control one or more of the following: periods of time where the Cold Storage System is in a charging mode and in a discharging mode, respectively,
  • the heat exchanger bypass valve in order to keep, in discharging mode, the temperature of the heat exchange fluid at the inlet of the compressor in a predefined temperature range or around a setpoint temperature (e.g. 25 °C),
  • the cold storage bypass valve in order to keep, in discharging mode, the temperature of the heat exchange fluid at the inlet of the heat ex changer in a predefined temperature range or around a setpoint tem perature (which could be selectable by the consumer), - the chiller/ cold storage bypass valve, in order to keep, in charging mode, the temperature of the heat exchange fluid at the inlet of the compressor in a predefined temperature range or around a setpoint temperature (e.g. 10 °C),
  • control unit controls the periods of time where the Cold Storage System is in charging and in discharging mode following readings of an external temperature and/or following the day and night cycle.
  • the present invention also pertains to a method for performing a cold storage, comprising:
  • the function of an evapora tor included in a conventional chiller of a Cold Storage System comprising a multi -packed bed system as cold storage is taken over by the multi-packed bed system, while the condenser unit and the expansion unit are included directly in the HTF circuit.
  • a conventional chiller including a separate RT circuit, and in particular an RT compressor and an RT evaporator, is therefore no longer re quired in the Integrated Cold Storage System.
  • An RT compressor and the HTF compressor will be replaced with a single compressor, while the multi -packed bed system will be used as an evaporator.
  • the cold HTF flows into the cold storage, where it transfers the coldness to the packing material.
  • the HTF fluid will be evaporated, given its latent heat of evaporation to the packing material.
  • the heat transfer is achieved by a single circuit only using the HTF, without using a heat transfer between the HTF and an RT. This new concept has positive impacts on the system efficiency, in vestment and operation costs.
  • Fig. l shows an embodiment of an Integrated Cold Storage System.
  • Fig. 2 exhibits a comparison between a conventional Cold Storage System with two fluid circuits and an Integrated Cold Storage System with a combined circuit.
  • Fig. 3A shows a process layout for an embodiment of an Integrated Cold Storage System in charging mode.
  • Fig. 3B displays HTF temperature against time across the condenser for an embodiment as displayed in Fig. 3A.
  • Fig. 4A shows a process layout for an embodiment of an Integrated Cold Storage System comprising a chiller/cold storage bypass, in charg ing mode.
  • Fig. 4 ⁇ > displays HTF temperature against time across the condenser for an embodiment as displayed in Fig. 4A.
  • Fig. 5 shows from top to bottom three consecutive steps (a), (b), (c) for charging an embodiment of an Integrated Cold Storage System comprising a chiller/cold storage bypass, for a case where the cold storage is a multi-packed bed system and the plurality of packed beds is charged selectively.
  • Fig. 6 shows settings for charging an embodiment of an Integrated Cold
  • Fig. 7A shows a process layout for an Integrated Cold Storage System com prising a heat exchanger bypass and a cold storage bypass, in dis charging mode.
  • Fig. 7B displays HTF temperature against time at a position X3 in the HTF circuit for a system as shown in Fig. 7A, for a case where the system comprises the cold storage bypass as well as for a case where the system does not comprise the cold storage bypass.
  • Fig. 7C displays HTF temperature against time at a position X5 in the HTF circuit for a system as shown in Fig. 7A, for a case where the system comprises the heat exchanger bypass as well as for a case where the system does not comprise the heat exchanger bypass.
  • Fig. 8 shows from top to bottom three consecutive steps (a), (b), (c) for discharging an embodiment of an Integrated Cold Storage System comprising a heat exchanger bypass and a cold storage bypass, for a case where the cold storage is a multi-packed bed system and the plurality of packed beds is discharged selectively.
  • Fig. 9 shows a conventional Cold Storage System including a chiller.
  • Fig. l shows an embodiment of a Cold Storage System according to the present invention.
  • the system comprises a compressor 12, a condenser unit 131, an ex pansion unit 132, a cold storage 14, and a heat exchanger 15, placed in this order along a heat transfer fluid (HTF) circuit 11.
  • the condenser unit 131 and the ex- pansion unit 132 are grouped together in a dashed box, which will be referred to collectively as condenser 13.
  • the HTF cools (charges) the cold storage 14, e.g. by undergoing a reverse Rankine cycle.
  • the HTF is set in motion by the compressor 12 and enters, e.g. in a state of superheated vapor, into the conden ser unit 131. During condensation, the HTF emits heat energy into the ambient air 32. Now e.g. in a state of saturated liquid, the HTF enters the expansion unit 132 where it experiences a rapid pressure decrease, thereby reducing its temper ature.
  • the HTF which may now e.g.
  • the HTF enters the compressor 12 again, which closes the circuit.
  • the heat exchanger 15 When the system is in discharging mode, the heat exchanger 15 is in operation and delivers coldness to the consumer 31.
  • the heat exchanger 15 may e.g. com prise a coil, over which ambient air 32 is passed by a fan 151.
  • the condenser unit 131 and the ex pansion unit 132 may or may not be switched on.
  • the HTF is at low (e.g. be low -10 °C) or ultra-low (e.g. -50 °C) temperature at the exit of the cold storage 14.
  • the HTF temperature at the outlet of the heat exchanger 15 is high; this temperature can e.g. be related to the ambient temperature and may be at about 50 °C.
  • the temperature of the HTF is furthermore increased when the HTF passes through the compressor 12.
  • Fig. 2 illustrates schematically the difference between a conventional Cold Stor age System on the left, and the present Integrated Cold Storage system on the right. In both cases, a process layout for a respective charging mode is depicted.
  • a solid outer circle represents an HTF circuit 11 (marked as “outer circuit” in the figure), along which the HTF is set in motion by a compressor 12 in counterclockwise direction.
  • the HTF passes through a refrig- erant (RT) evaporator 165, and through a cold storage 14.
  • RT refrig- erant
  • a dotted inner circle (marked as “inner circuit” in the figure) represents an RT circuit 161, along which as key components of a vapor-compression refrigeration system are placed: an RT compressor 162, an RT condenser unit 163, an RT expansion unit 164 and an RT evaporator 165.
  • the RT which may e.g.
  • the HTF circuit and the RT circuit are sepa rate closed systems which are in thermal contact within the RT evaporator 165, where the heat transfer between HTF and RT takes place using a fluid-fluid-heat exchanger.
  • the HTF In charging mode, the HTF is moved by means of the compressor 12, refrigerated by passing heat energy to the RT in the RT evaporator 165, and in turn refrigerates (charges) the cold storage 14.
  • a compressor 12, a condenser unit 131, an expan- sion unit 132 and a cold storage 14 are positioned in this order along an HTF circuit 11 (marked as “combined circuit” in the figure).
  • the cold storage system 14 comprises an evaporator 145, in which the HTF can absorb heat energy, thereby refrigerating (charging) the cold storage 14.
  • the HTF undergoes a cycle analogous to that of the RT in the left part of the figure: Com- pression by the compressor 12, condensation and release of heat energy into the ambient air 32 in the condenser unit 131, temperature reduction in the expan sion unit 132, and absorption of heat energy in the evaporator 145 included in the cold storage 14.
  • a particular instance where an evaporator 145 is naturally included in the cold storage 14 occurs if the cold storage 14 is a multiple-packed bed system. In this case, evaporation of the HTF occurs within the packed beds upon passing through particles of a packing material.
  • embodiments integrate both inner and outer circuits into a combined circuit. This can be achieved by replacing the evaporator with the multi-packed bed system.
  • a single compressor enables the HTF circulation between the con- denser 13 and the cold storage (multi-packed bed system) 14.
  • a single compressor 12 is used, instead of two separated compressors for HTF (compressor 12) and RT (RT compressor 162) on the left.
  • a single fluid (refrigerant) is used instead of separated fluids (HTF and RT) on the left.
  • an evaporator 145 is integrated in the cold storage 14. This is in particular realised if the cold storage comprises a multi-packed bed system. In consequence there is no need for heat energy exchange be tween the HTF and the RT in an RT evaporator 165. Furthermore, the heat transfer between the HTF and the particles of the packing material in the multi-packed bed system can be very high if said heat transfer is based on the latent heat of HTF evaporation.
  • a system according to the right part of the figure has a better scalability compared with a system according to the left part of the figure.
  • Fig. 3A shows a process layout for an embodiment of a Cold Storage System comprising a compressor 12, a condenser unit 131, an expansion unit 132 and a cold storage 14, placed in this order along a heat transfer fluid (HTF) circuit 11, in charging mode.
  • HTF heat transfer fluid
  • the HTF is compressed, heated and set in motion by the compressor 12.
  • the HTF pressure at position X6 after the compressor 12 maybe e.g. 50 bar.
  • the HTF then enters the condenser unit 131, where it emits heat energy into e.g. the ambient air 32.
  • the HTF enters the expansion unit 132 (e.g. an expansion valve), where it undergoes depressurization and temperature re duction, such that HTF pressure and temperature at position X after the expan sion unit 132 are e.g. 10 bar and -50 °C, respectively.
  • the HTF enters the cold storage 14, where it passes through an integrated evaporator 145 and absorbs heat energy from (i.e., charges) the cold storage 14.
  • Fig. 3B shows, for a Cold Storage System as displayed in Fig. 5A, a qualitative plot of the HTF temperature against time at the positions X5 before the com pressor 12 and X6 after the compressor 12. As the cold storage 14 is charged over time, the HTF temperature at the outlet of the cold storage 14 goes down, and the compressor 12 operates under HTF temperature conditions varying over time.
  • Fig. 4A shows a process layout for an embodiment of a Cold Storage System comprising a compressor 12, a condenser unit 131, an expansion unit 132 and a cold storage 14, placed in this order along a heat transfer fluid (HTF) circuit 11, in charging mode.
  • the Cold Storage System further comprises a chiller/cold storage bypass 23, which connects a position X6 before the condenser unit 131 and a position X7 after the expansion unit 132 with a position X2 before the compressor 12.
  • the HTF is compressed, heated and set in motion by the compressor 12.
  • the HTF pressure at position X6 after the compressor 12 maybe e.g. 50 bar.
  • the HTF then enters the condenser unit 131, where it emits heat energy into e.g. the ambient air 32.
  • the HTF enters the expansion unit 132 (e.g. an expansion valve), where it undergoes depressurization and temperature re duction, such that HTF pressure and temperature at the position X7 are e.g. 10 bar and -50 °C, respectively.
  • the chiller/cold storage bypass 23 e.g. 10 bar and -50 °C
  • the HTF temperature at position X5 before the compressor 12 and at position X6 after the compressor 12 can be regulated.
  • a system according to the present figure, compared to a system according to Fig. 3B, has the advantage that the compressor 12 can be operated at higher efficiency.
  • the chiller/cold storage bypass valve 231 may, for example, be a three-way valve so that it can control the bypass of the condenser 13 and/ or the cold storage 14.
  • the part of the HTF which exits the expansion unit 132 but does not enter the chiller/cold storage bypass 23 continues on the HTF circuit and enters the cold storage 14, where it passes through an integrated evaporator 145 and absorbs heat energy from (i.e., charges) the cold storage 14.
  • Fig. 4B shows, for a Cold Storage System as displayed in Fig. 6A, a qualitative plot of the HTF temperature against time at the positions X5 before the com pressor 12 and X6 after the compressor 12.
  • the HTF temperature at position X2 after the outlet of the cold storage 14 is kept constant at a setpoint temperature (e.g. 10 °C), by means of controlling the mass flow of HTF through the chiller/cold storage bypass 23 via the chiller/cold storage bypass valve 231.
  • the compressor 12 operates under constant HTF temperature conditions.
  • Fig. 5 shows, from top to bottom, three consecutive steps (a), (b), (c) for charg ing a Cold Storage System comprising a compressor 12, condenser 13, and a cold storage 14, placed in this order along a circuit of heat transfer fluid (HTF).
  • the condenser 13 includes a condenser unit 131 and an expansion unit 132, which are not displayed in the figure.
  • the Cold Storage System further comprises a chiller/cold storage bypass 23, and a cold storage bypass 22.
  • the cold storage 14 is a multi-packed bed system of three packed beds 141, 142, 143 connected together in parallel.
  • the chiller/ cold storage bypass valve 231 is operated to control the temperature at the inlet of the compressor 12.
  • the cold storage bypass valve 221 is closed.
  • the three consecu tive steps comprise, in turn, (a) charging the first packed bed 141. This is achieved if the control valve 1407 between the entries of the first and second packed bed and the control valve 1406 between the entries of the second and third packed bed are closed. The control valves between the exits of the first and second packed bed 1409 and between the exit of the second and third packed bed 1408 are opened. Therefore, the HTF flows via the point X7 through the first packed bed 141, and from there through the packed bed valves 1409 and 1408 to the point Xo.
  • the chiller/cold storage bypass valve 231 may, for example, be a three-way valve so that it can control the bypass of the condenser 13 and/or the cold storage 14.
  • Fig. 6 shows the settings for charging an embodiment of a Cold Storage System a compressor 12, condenser 13, and a cold storage 14, placed in this order along a circuit of heat transfer fluid (HTF).
  • the condenser 13 includes a condenser unit 131 and an expansion unit 132, which are not displayed in the figure.
  • the Cold Storage System further comprises a chiller/cold storage bypass 23, and a cold storage bypass 22.
  • the cold storage 14 is a multi-packed bed system of three packed beds 141, 142, 143 connected together in parallel.
  • the chiller/cold storage bypass valve 231 is operated to control the temperature at the inlet of the compressor 12.
  • the cold storage by pass valve 221 is closed.
  • the packed bed valves 1406, 1407, 1408 and 1409 are open, and the three packed beds 141, 142, 143 are charged at the same time.
  • the chiller/cold storage bypass valve 231 may again be a three-way valve so that it can control the bypass of the condenser 13 and/or the cold storage 14.
  • Fig. 7A shows an embodiment of a Cold Storage System comprising a compres sor 12, a cold storage 14, and a heat exchanger 15, placed in this order along an HTF circuit 11.
  • the system further comprises the heat exchanger bypass 21 and a cold storage bypass 22.
  • the heat exchanger bypass 21 starts on the HTF circuit 11 at position Xi after the cold storage 14, bypasses the heat exchanger 15, and ends on the HTF circuit 11 at position X5 after the heat exchanger 15.
  • the cold storage bypass 22 starts on the HTF circuit at position X6 after the compressor 12, by passes the cold storage 14, and ends on the HTF circuit at position X3 before the heat exchanger 15.
  • the Cold Storage System is displayed in discharging mode, where the heat exchanger 15 is in operation and delivers coldness to (i.e., ab sorbs heat energy from) a consumer 31.
  • the temperature of the HTF at the outlet of the cold storage 14 is initially at a low (e.g. below -10 °C) or ultra-low (e.g. -50 °C) temperature. Depending on the type of cold storage employed, this temperature rises over time, e.g. due to the deposit of heat energy through the HTF in the cold storage 14.
  • the heat exchanger 15 can be realized e.g. as a coil, through which cooling is delivered to the consumer 31 by a flow of ambient air 32 passing over the coil by means of a fan 151. In this setup, the amount of cooling delivered to the consumer 31 depends on the HTF temperature at the inlet of the heat exchanger 15.
  • the cold storage bypass 22 delivers HTF of higher tem perature from the position X6 after the compressor 12 to the inlet of the heat exchanger 15. Controlling the flow rate of HTF through the cold storage bypass 22 by means of the cold storage bypass valve 221, a constant setpoint tempera ture at the inlet of the heat exchanger 15 can be achieved. Therefore, by means of the cold storage bypass 22, the heat exchanger 15 can deliver coldness to the consumer 31 in a way which is controlled and constant over time. In addition, by means of the cold storage bypass 22 the amount of heat energy entering the Cold Storage System through the heat exchanger 15 is controlled, which can be uti lized for a controlled discharging process of the cold storage 14.
  • the HTF temperature at the outlet X4 of the heat exchanger 15 is high; it may depend on the ambient temperature, and can be e.g. 50 °C. Compression of the HTF at the correspondingly high volumetric flow rate would lead to a high power consumption for the compressor 12.
  • the hot HTF which has passed through the heat exchanger 15 is mixed with the cold HTF that has passed through the heat exchanger bypass 21, such that the temperature of the HTF at the inlet of the compressor 12 is reduced (e.g. to 25 °C) relative to the temperature of the HTF at the outlet X4 of the heat ex changer 15.
  • the HTF temperature slightly increases (to e.g. +35 °C at position X6 after the compressor 12).
  • the HTF enters the cold storage 14, where it deposits the heat energy and is cooled down. This completes the HTF circuit.
  • the reduction of HTF temperature by means of the heat exchanger bypass 21 at a position X5 before the compressor 12 decreases the HTF volumetric flow rate in the compressor 12, and allows an operation of the compressor 12 at a lower power consumption.
  • the reduction of HTF temperature before the compressor 12 decreases the HTF temperature at the inlet of the cold storage 14, which depending on the type of cold storage employed can be further utilized for a controlled discharging process of the cold storage 14.
  • Fig. 7B shows, for a system as displayed in Fig. A, the effect of the cold storage bypass 22 on the temperature of the HTF at position X3 on the HTF circuit, before the HTF enters the heat exchanger 15. Without the cold storage bypass 22, the HTF temperature at position X3, and thus at the inlet of the heat ex changer 15, rises over time. With the cold storage bypass 22 in place, the tem perature can be stabilized at a fixed setpoint. Since the intention is that this set- point can be selected by the consumer 31, three different cases of such setpoints (8 °C, 14 °C, 16 °C) are displayed.
  • Fig. 7C shows, for a system as displayed in Fig. 7A, the temperature against time of the HTF at position X5 before the inlet of the compressor 12, for a case where the system does not comprise versus a case where the system does comprise the heat exchanger bypass 21.
  • the temperature at position X5 in the displayed example is constant in time.
  • the temperature of the HTF at the position X5 before the inlet of the compressor 12 is high (e.g. 50 °C)
  • the temperature of the HTF at the position X5 before the inlet of the compressor 12 is reduced to a lower temperature (e.g. 25 °C) due to the cold HTF passing through the heat exchanger bypass 21.
  • Fig. 8 shows, from top to bottom, three consecutive steps (a), (b), (c) for dis charging an embodiment of a Cold Storage System comprising a compressor 12, a cold storage 14, and a heat exchanger 15, placed in this order along an HTF circuit 11, further comprising a heat exchanger bypass 21 and a cold storage by pass 22, for the exemplary case where the cold storage 14 is a multi-packed bed system of three packed beds 141, 142, 143 connected together in parallel.
  • the cold storage bypass valve 221 is operated to control the temperature at the inlet of the heat exchanger 15 to be at a setpoint tempera ture.
  • the heat exchanger bypass 21 is used to control, via the heat exchanger bypass valve 211, the temperature of the HTF at point X5 before the compressor 12.
  • the heat exchanger bypass 21 is not ex plicitly drawn in the figure.
  • the three consecutive steps comprise, in turn,
  • (a) Discharging the third packed bed 143 which is achieved by closing the packed bed valve 1404 at the exit of first packed bed 141, the packed bed valve 1403 at the exit of second packed bed 142, as well as the packed bed valve 1401 between the inlets of the first and second packed bed and the packed bed valve 1400 between the inlets of the second and third packed bed.
  • the packed bed valve 1402 at the exit of the third packed bed 143 and the packed bed valve 1405 between the exits of the packed beds 142 and 143 and the heat exchanger 15 are opened. Therefore, the HTF flows from the compressor 12 to the heat exchanger 15 via the third packed bed 143 and the cold storage bypass 22.
  • the entry Xi of the heat exchanger bypass 21 is located after the third packed bed 143.
  • the HTF flows from the compressor 12 to the heat exchanger 15 via the second packed bed 142 and the cold storage bypass 22.
  • the entry Xi of the heat exchanger bypass 21 is located after the second packed bed 142.
  • the discharge control valves between the inlets of the first and second packed bed 1401, between the inlets of second and third packed beds 1400 and the packed bed valve 1405 between the exits of packed beds 142 and 143 and the heat exchanger 15 are opened. Therefore, the HTF flows from the compressor 12 to the heat exchanger 15 via the first packed bed 141 and the cold storage bypass 22.
  • the entry Xi of the heat exchanger bypass 21 is located after the first packed bed 141.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

Un système de stockage à froid comprend : un compresseur (12) pour comprimer et permettre la circulation d'un fluide caloporteur (HTF)) ; un condenseur (13) avec une unité de condenseur (131) pour refroidir le HTF comprimé et une unité de détente (132) pour diminuer la pression du HTF, refroidissant ainsi davantage le HTF ; et un stockage à froid (14) avec un évaporateur intégré (145), le stockage à froid (14) étant configuré pour stocker la froid transférée par le HTF.
PCT/EP2020/073973 2019-08-30 2020-08-27 Système de stockage à froid intégré et procédé pour réaliser un stockage à froid WO2021037979A1 (fr)

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EP19194734 2019-08-30
EP19194734.0 2019-08-30
EP19209171.8 2019-11-14
EP19209171.8A EP3786545A1 (fr) 2019-08-30 2019-11-14 Système de stockage à froid intégré

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10337889B3 (de) * 2003-08-18 2004-12-09 Webasto Thermosysteme Gmbh Klimatisierungssystem für ein Kraftfahrzeug und Verfahren zum Betreiben eines Klimatisierungssystems
US20060288727A1 (en) * 2005-06-24 2006-12-28 Denso Corporation Cold storage tank unit and refrigeration cycle apparatus using the same
WO2014111012A1 (fr) * 2013-01-21 2014-07-24 深圳市庄合智能产业科技有限公司 Système d'équilibrage interne de froid et de chaleur combinant une unité au bromure de lithium et un stockage de froid

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10337889B3 (de) * 2003-08-18 2004-12-09 Webasto Thermosysteme Gmbh Klimatisierungssystem für ein Kraftfahrzeug und Verfahren zum Betreiben eines Klimatisierungssystems
US20060288727A1 (en) * 2005-06-24 2006-12-28 Denso Corporation Cold storage tank unit and refrigeration cycle apparatus using the same
WO2014111012A1 (fr) * 2013-01-21 2014-07-24 深圳市庄合智能产业科技有限公司 Système d'équilibrage interne de froid et de chaleur combinant une unité au bromure de lithium et un stockage de froid

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