EP3059522A2 - Unité de réfrigération de transport - Google Patents

Unité de réfrigération de transport Download PDF

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Publication number
EP3059522A2
EP3059522A2 EP16155458.9A EP16155458A EP3059522A2 EP 3059522 A2 EP3059522 A2 EP 3059522A2 EP 16155458 A EP16155458 A EP 16155458A EP 3059522 A2 EP3059522 A2 EP 3059522A2
Authority
EP
European Patent Office
Prior art keywords
heat exchangers
outside
heat exchanger
pressure
outside heat
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.)
Withdrawn
Application number
EP16155458.9A
Other languages
German (de)
English (en)
Other versions
EP3059522A3 (fr
Inventor
Masakazu Kai
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.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP3059522A2 publication Critical patent/EP3059522A2/fr
Publication of EP3059522A3 publication Critical patent/EP3059522A3/fr
Withdrawn legal-status Critical Current

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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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0251—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units being defrosted alternately
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • F25B2313/02533—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements during heating
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0254—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements
    • F25B2313/02542—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements during defrosting
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02791—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using shut-off valves
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/15—Hunting, i.e. oscillation of controlled refrigeration variables reaching undesirable values
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation

Definitions

  • the present invention relates to a transport refrigeration unit having a heat pump-type warming function and mounted on a refrigerated vehicle, a trailer, or the like.
  • a transport refrigeration unit having a heat pump-type warming function has been provided. Examples thereof are described in PTLs 1 and 2.
  • one end sides of a plurality of heat exchangers are connected to a discharge side of a compressor each via a high-pressure gas pipe and a high-pressure on-off valve, and the one end sides of the plurality of heat exchangers are connected to a suction side of the compressor each via a low-pressure gas pipe and a low-pressure on-off valve.
  • Liquid-side pipes including parallel circuits each having a pressure reducing means with an on-off valve function (a means in which an on-off valve and an expansion valve are connected in series with each other, a means using an electric expansion valve having an on-off valve function, etc.) and a check valve are connected to the other end sides of the respective heat exchangers.
  • the liquid-side pipes are connected together in communication. A refrigerant circuit is thereby configured.
  • One of the plurality of heat exchangers is disposed outside a refrigerator as an outside heat exchanger.
  • One or more of the heat exchangers are disposed inside the refrigerator as an inside heat exchanger.
  • a refrigerant flow into the respective heat exchangers is switched by opening or closing the respective high-pressure on-off valves provided in the high-pressure gas pipes, the respective low-pressure on-off valves provided in the low-pressure gas pipes, and the on-off valve functions of the respective pressure reducing means with an on-off valve function provided in the liquid-side pipes.
  • a cooling operation is performed by causing the outside heat exchanger to function as a condenser, and the inside heat exchanger to function as an evaporator.
  • a heat pump warming operation is performed by causing the inside heat exchanger to function as a condenser, and the outside heat exchanger to function as an evaporator.
  • PTLs 3 and 4 disclose a multi-type air-conditioning apparatus, that is, a so-called cooling/heating free multi-type air-conditioning apparatus that can perform a cooling/heating simultaneous operation by employing a refrigerant circuit similar to the above circuit.
  • a plurality of outdoor heat exchangers are disposed in parallel with each other.
  • the frosted plurality of outdoor heat exchangers are alternately defrosted by causing one of the outdoor heat exchangers to function as an evaporator, and another one to function as a condenser while continuing the heating operation by causing a hot gas refrigerant to flow through an indoor heat exchanger.
  • the present invention has been made in view of the above circumstances, and an object thereof is to provide a transport refrigeration unit employing a heat pump warming method, which can prevent a decrease in an inside temperature during defrosting, can perform defrosting within a short time, and can ensure reliability by appropriately adjusting a condensing capacity during a cooling operation, and suppressing frequent starting and stopping of a compressor during thermo-on/off.
  • a transport refrigeration unit includes: a compressor; a plurality of heat exchangers, one end sides of which are connected to a discharge side of the compressor each via a high-pressure gas pipe and a high-pressure on-off valve; low-pressure gas pipes that connect the one end sides of the plurality of heat exchangers to a suction side of the compressor each via a low-pressure on-off valve; and liquid-side pipes that connect together in communication the other end sides of parallel circuits connected to the other end sides of the plurality of heat exchangers and each having a pressure reducing means with an on-off valve function and a check valve, wherein at least two of the plurality of heat exchangers are disposed in parallel with each other outside a refrigerator as outside heat exchangers, at least one of the plurality of heat exchangers is disposed inside the refrigerator as an inside heat exchanger, and when the outside heat exchangers are frosted during a heat pump warming operation in which the outside heat exchangers are caused to function as evaporators
  • the one end sides of the plurality of heat exchangers connected to the discharge side of the compressor each via the high-pressure gas pipe and the high-pressure on-off valve are connected to the suction side of the compressor each via the low-pressure gas pipe and the low-pressure on-off valve.
  • the liquid-side pipes including the parallel circuits each having the pressure reducing means with an on-off valve function and the check valve are connected to the other end sides of the plurality of heat exchangers, and the other end sides of the liquid-side pipes are connected together in communication. Accordingly, a refrigerant circuit is configured.
  • At least two of the plurality of heat exchangers are disposed in parallel with each other outside the refrigerator as the outside heat exchangers, and at least one of the plurality of heat exchangers is disposed inside the refrigerator as the inside heat exchanger. Therefore, a cooling operation for cooling the inside of the refrigerator can be performed by causing the two outside heat exchangers disposed outside the refrigerator to function as condensers, and the single inside heat exchanger disposed inside the refrigerator to function as an evaporator.
  • the heat pump warming operation for warming the inside of the refrigerator can be also performed by causing the single inside heat exchanger disposed inside the refrigerator to function as the condenser, and the two outside heat exchangers disposed outside the refrigerator to function as the evaporators.
  • the warming operation can be performed efficiently with high capacity by employing the heat pump method.
  • the defrosting operation is performed by stopping the refrigerant distribution to the inside heat exchanger, and causing at least one of the plurality of outside heat exchangers to function as the condenser, and another one of the plurality of outside heat exchangers to function as the evaporator.
  • all of a hot gas refrigerant discharged from the compressor can be supplied to at least one of the frosted outside heat exchangers, and another one of the outside heat exchangers can be caused to function as the evaporator, so that the defrosting operation can be performed with the refrigerant absorbing heat in the evaporator. Therefore, the defrosting of the outside heat exchangers can be performed by using the full capacity (all of the refrigerant) of the heat pump without absorbing heat from inside air, so that a defrosting operation time can be shortened, and a change in an inside temperature during the defrosting operation can be decreased.
  • the plurality of outside heat exchangers may be sequentially subjected to the defrosting operation by sequentially switching the frosted plurality of outside heat exchangers such that at least one of the outside heat exchangers functions as a condenser, and another one of the outside heat exchangers functions as an evaporator.
  • the plurality of outside heat exchangers are sequentially subjected to the defrosting operation by sequentially switching the frosted plurality of outside heat exchangers such that at least one of the outside heat exchangers functions as the condenser, and another one of the outside heat exchangers functions as the evaporator.
  • a refrigerant flow between the plurality of outside heat exchangers is switched by opening or closing the high-pressure on-off valves in the high-pressure gas pipes, the low-pressure on-off valves in the low-pressure gas pipes, and the on-off valve functions of the pressure reducing means with an on-off valve function in the parallel circuits of the liquid-side pipes, which are connected to the respective outside heat exchangers, so that the plurality of outside heat exchangers can be sequentially subjected to the defrosting operation. Therefore, the plurality of outside heat exchangers can be alternately defrosted by using the full capacity (all of the refrigerant) of the heat pump. Thus, the defrosting can be performed within a short time.
  • air blow systems including outside fans for the plurality of outside heat exchangers may be provided independently of each other.
  • the air blow systems including the outside fans for the plurality of outside heat exchangers are provided independently of each other. Therefore, the defrosting operation can be performed by stopping an outside fan for the outside heat exchanger that functions as the condenser, and operating an outside fan for the outside heat exchanger that functions as the evaporator, during the defrosting operation. Consequently, it is possible to efficiently perform the defrosting within a short time by increasing an amount of heat absorbed in the outside heat exchanger that functions as the evaporator, and dissipating the heat in the outside heat exchanger to be defrosted.
  • the warming operation when a difference between an inside temperature and a set temperature has a specified value or more during the defrosting operation, the warming operation may be performed by opening the high-pressure on-off valve in the high-pressure gas pipe connected to the inside heat exchanger, and distributing a high-pressure gas refrigerant to the inside heat exchanger.
  • the warming operation when the difference between the inside temperature and the set temperature has the specified value or more during the defrosting operation, the warming operation may be performed by opening the high-pressure on-off valve in the high-pressure gas pipe connected to the inside heat exchanger, and distributing the high-pressure gas refrigerant to the inside heat exchanger. Therefore, even when the inside temperature rapidly changes due to some reason during the defrosting operation and the difference with the set temperature exceeds the specified value, it is possible to perform the warming operation while continuing the defrosting operation by partly introducing the hot gas refrigerant from the compressor into the inside heat exchanger only by opening the high-pressure on-off valve. Consequently, the inside temperature is not lowered to a specified value or less during the defrosting operation, a quality of a load can be guaranteed by keeping temperature controllability even during the defrosting, and reliability of the transport refrigeration unit can be improved.
  • the condensing capacity may be adjusted by reducing the operation number of the plurality of outside heat exchangers.
  • the condensing capacity is adjusted by reducing the operation number of the plurality of outside heat exchangers. Therefore, for example, in a case in which the cooling operation is performed under a condition in which an outside air temperature is relatively low, the condensing capacity becomes excessive with respect to a heat exchange amount of the inside heat exchanger when all of the plurality of outside heat exchangers are operated. Thus, a pressure in a high pressure-side circuit is lowered, and a differential pressure between high and low pressures becomes too small to deviate from a flow rate adjustable range of an expansion valve.
  • An abnormal suction pressure of the compressor may be thereby caused.
  • the condensing capacity is adjusted by reducing the operation number of the plurality of outside heat exchangers.
  • the differential pressure between the high and low pressures can be maintained within an appropriate range. Therefore, it is possible to stably operate the transport refrigeration unit by appropriately adjusting the capacity on the outside heat exchanger-side corresponding to the heat exchange amount of the inside heat exchanger, and thereby keeping an operation balance.
  • heat exchangers having different capacities from each other may be employed as the plurality of outside heat exchangers.
  • the heat exchangers having different capacities from each other are employed as the plurality of outside heat exchangers.
  • the condensing capacity in the plurality of outside heat exchangers in multi-stages greater than the number of the outside heat exchangers by selecting working statuses of the heat exchangers. Therefore, the condensing capacity can be finely adjusted under various outside air temperatures and inside set temperature conditions corresponding to the conditions, and the operation can be more stably performed by maintaining the high and low pressure difference within an appropriate range. Consequently, it is possible to improve the reliability of the transport refrigeration unit.
  • a transport refrigeration unit includes: a compressor; a plurality of heat exchangers, one end sides of which are connected to a discharge side of the compressor each via a high-pressure gas pipe and a high-pressure on-off valve; low-pressure gas pipes that connect the one end sides of the plurality of heat exchangers to a suction side of the compressor each via a low-pressure on-off valve; and liquid-side pipes that connect together in communication the other end sides of parallel circuits connected to the other end sides of the plurality of heat exchangers and each having a pressure reducing means with an on-off valve function and a check valve, wherein at least two of the plurality of heat exchangers are disposed in parallel with each other outside a refrigerator as outside heat exchangers, at least one of the plurality of heat exchangers is disposed inside the refrigerator as an inside heat exchanger, and when an operation time of the compressor is a specified time or less during thermo-off after an inside temperature reaches a set temperature, the compressor is continuously operated until
  • the one end sides of the plurality of heat exchangers connected to the discharge side of the compressor each via the high-pressure gas pipe and the high-pressure on-off valve are connected to the suction side of the compressor each via the low-pressure gas pipe and the low-pressure on-off valve.
  • the liquid-side pipes including the parallel circuits each having the pressure reducing means with an on-off valve function and the check valve are connected to the other end sides of the plurality of heat exchangers, and the other end sides of the liquid-side pipes are connected together in communication. Accordingly, a refrigerant circuit is configured.
  • At least two of the plurality of heat exchangers are disposed in parallel with each other outside the refrigerator as the outside heat exchangers, and at least one of the plurality of heat exchangers is disposed inside the refrigerator as the inside heat exchanger. Therefore, a cooling operation for cooling the inside of the refrigerator can be performed by causing the two outside heat exchangers disposed outside the refrigerator to function as condensers, and the single inside heat exchanger disposed inside the refrigerator to function as an evaporator.
  • the heat pump warming operation for warming the inside of the refrigerator can be also performed by causing the single inside heat exchanger disposed inside the refrigerator to function as the condenser, and the two outside heat exchangers disposed outside the refrigerator to function as the evaporators.
  • thermo-on/off are normally repeated. In this case, if the thermo-on/off are performed within a short time, starting and stopping of the compressor are frequently repeated, resulting in a malfunction and a decrease in service life.
  • the operation time of the compressor is the specified time or less during the thermo-off, the compressor is continuously operated until the operation time exceeds the specified time by stopping the refrigerant distribution to the inside heat exchanger, and causing one of the plurality of outside heat exchangers to function as the condenser, and another one of the plurality of outside heat exchangers to function as the evaporator.
  • the frequent starting and stopping of the compressor can be prevented by continuously operating the compressor until the operation time of the compressor exceeds the specified time during the thermo-off, and idling the refrigeration unit by using one of the plurality of outside heat exchangers as the condenser, and another one as the evaporator. Therefore, start/stop frequency of the compressor can be suppressed, and the reliability can be ensured.
  • the cooling operation for cooling the inside of the refrigerator can be performed by causing the two outside heat exchangers disposed outside the refrigerator to function as the condensers, and the single inside heat exchanger disposed inside the refrigerator to function as the evaporator.
  • the heat pump warming operation for warming the inside of the refrigerator can be also performed by causing the single inside heat exchanger disposed inside the refrigerator to function as the condenser, and the two outside heat exchangers disposed outside the refrigerator to function as the evaporators. Therefore, the warming operation can be performed efficiently with high capacity by employing the heat pump method.
  • all of the hot gas refrigerant discharged from the compressor can be supplied to at least one of the frosted outside heat exchangers, and another one of the outside heat exchangers can be caused to function as the evaporator, so that the defrosting operation can be performed with the refrigerant absorbing heat in the evaporator. Therefore, the defrosting of the outside heat exchangers can be performed by using the full capacity (all of the refrigerant) of the heat pump without absorbing heat from inside air, so that the defrosting operation time can be shortened, and a change in the inside temperature during the defrosting operation can be decreased.
  • the frequent starting and stopping of the compressor can be prevented by continuously operating the compressor until the operation time of the compressor exceeds the specified time during the thermo-off, and idling the refrigeration unit by using one of the plurality of outside heat exchangers as the condenser, and another one as the evaporator. Therefore, the start/stop frequency of the compressor can be suppressed, and the reliability can be ensured.
  • Fig. 1 shows a refrigerant circuit diagram of a transport refrigeration unit according to the first embodiment of the present invention.
  • Figs. 2 and 3 show configuration diagrams of a refrigerant circuit during the defrosting operation.
  • Fig. 4 shows a control flowchart of the defrosting operation.
  • the present invention is applied to an integrated transport refrigeration unit 1 that cools or warms the inside of a refrigerator called a van body that is mounted on a bed side of a refrigerated vehicle or the like.
  • the present invention is not necessarily limited to the integrated transport refrigeration unit, and it goes without saying that the present invention can be widely applied to general transport refrigeration units
  • a refrigerant circuit 2 of the transport refrigeration unit 1 includes a compressor 3 (here, a motor-driven compressor is employed), a high-pressure gas port 5 that is connected to a discharge pipe 4 of the compressor 3, a plurality of (three in the present example) high-pressure gas pipes 6A, 6B, and 6C that branch from the high-pressure gas port 5, high-pressure on-off valves (solenoid valves) 7A, 7B, and 7C that are provided in the high-pressure gas pipes 6A, 6B, and 6C, respectively, and a plurality of heat exchangers 8A, 8B, and 8C, one end sides of which are connected to the high-pressure gas pipes 6A, 6B, and 6C, respectively.
  • a compressor 3 here, a motor-driven compressor is employed
  • a high-pressure gas port 5 that is connected to a discharge pipe 4 of the compressor 3
  • a plurality of (three in the present example) high-pressure gas pipes 6A, 6B, and 6C that branch from the high-
  • Two heat exchangers 8A and 8B out of the plurality of heat exchangers 8A, 8B, and 8C are disposed at an outer portion of the refrigerator, that is, outside the refrigerator as an outside heat exchanger (A)8A and an outside heat exchanger (B)8B, respectively.
  • the remaining one is disposed inside the refrigerator as an inside heat exchanger 8C.
  • the low-pressure gas port 11 is connected to the compressor 3 via a suction pipe 12.
  • one ends of parallel circuits 13A, 13B, and 13C that are configured by connecting series circuits of expansion valves 15A, 15B, and 15C and on-off valves (solenoid valves) 16A, 16B, and 16C, respectively, in parallel with check valves 14A, 14B, and 14C are connected to the other end sides of the outside heat exchanger (A)8A, the outside heat exchanger (B)8B, and the inside heat exchanger 8C.
  • the other ends of the parallel circuits 13A, 13B, and 13C are connected to a high-pressure liquid port 17, so that liquid-side pipes 18A, 18B, and 18C that are connected together in communication are provided. Accordingly, the heat pump-type refrigerant circuit 2 having a closed cycle is configured.
  • the series circuits of the expansion valves 15A, 15B, and 15C and the on-off valves (the solenoid valves) 16A, 16B, and 16C are referred to as pressure reducing means having an on-off valve function in the present invention.
  • a configuration in which the expansion valve and the on-off valve (the solenoid valve) separate from each other are connected in series with each other is employed herein, a valve having an integrated configuration may be employed. Alternatively, the configuration may be substituted by an electric expansion valve having an on-off valve function.
  • the "pressure reducing means having an on-off valve function" that collectively indicates the above configurations is used.
  • the inside heat exchanger 8C is disposed in an inside air circulation path on a unit side so as to face the inside of the refrigerator, and the other devices are disposed on a unit body side that is installed outside the refrigerator.
  • An inside fan 19 is attached to the inside heat exchanger 8C, so that inside air can be circulated through the inside heat exchanger 8C.
  • Outside fans 20A and 20B are attached to the outside heat exchanger (A)8A and the outside heat exchanger (B)8B, respectively, so that independent air blow systems that blow outside air to the outside heat exchanger (A)8A and the outside heat exchanger (B)8B are configured.
  • the high-pressure gas port 5, the low-pressure gas port 11, and the high-pressure liquid port 17 may be omitted by directly connecting the high-pressure gas pipes 6A, 6B, and 6C to the discharge pipe 4, the low-pressure gas pipes 9A, 9B, and 9C to the suction pipe 12, and the liquid-side pipes 18A, 18B, and 18C together, respectively.
  • the high-pressure liquid port 17 may be substituted by a receiver.
  • a cooling operation and a heat pump warming operation are performed as described below.
  • the cooling operation is an operation performed by causing each of the outside heat exchanger (A)8A and the outside heat exchanger (B)8B to function as a condenser, and the inside heat exchanger 8C to function as an evaporator.
  • the high-pressure on-off valves 7A and 7B are opened, and the high-pressure on-off valve 7C is closed in the high-pressure gas pipes 6A, 6B, and 6C.
  • the low-pressure on-off valves 10A and 10B are closed, and the low-pressure on-off valve 10C is opened in the low-pressure gas pipes 9A, 9B, and 9C.
  • the on-off valves 16A and 16B are closed, and the on-off valve 16C is opened in the parallel circuits 13A, 13B, and 13C of the liquid-side pipes 18A, 18B, and 18C.
  • a high-temperature and high-pressure refrigerant gas discharged from the compressor 3 is guided to the outside heat exchanger (A)8A and the outside heat exchanger (B)8B through the discharge pipe 4, the high-pressure gas port 5, and the high-pressure gas pipes 6A and 6B, and is condensed into a liquid therein.
  • the liquid refrigerant is guided to the high-pressure liquid port 17 through the check valves 14A and 14B of the parallel circuits 13A and 13B, and the liquid-side pipes 18A and 18B.
  • the high-pressure liquid refrigerant joining in the high-pressure liquid port 17 is thermally insulated and expanded through the liquid-side pipe 18C, and the on-off valve 16C and the expansion valve 15C in the parallel circuit 13C, is then guided to the inside heat exchanger 8C, and is evaporated therein by cooling inside air.
  • the gas refrigerant returns to the compressor 3 through the low-pressure on-off valve 10C, the low-pressure gas pipe 9C, the low-pressure gas port 11, and the suction pipe 12.
  • the refrigerant is circulated in a cycle as described above. Accordingly, the inside of the refrigerator is cooled.
  • the heat pump warming operation is an operation performed by causing the inside heat exchanger 8C to function as a condenser, and each of the outside heat exchanger (A)8A and the outside heat exchanger (B)8B to function as an evaporator.
  • the high-pressure on-off valves 7A and 7B are closed, and the high-pressure on-off valve 7C is opened in the high-pressure gas pipes 6A, 6B, and 6C.
  • the low-pressure on-off valves 10A and 10B are opened, and the low-pressure on-off valve 10C is closed in the low-pressure gas pipes 9A, 9B, and 9C.
  • the on-off valves 16A and 16B are opened, and the on-off valve 16C is closed in the parallel circuits 13A, 13B, and 13C of the liquid-side pipes 18A, 18B, and 18C.
  • a high-temperature and high-pressure refrigerant gas discharged from the compressor 3 is guided to the inside heat exchanger 8C through the discharge pipe 4, the high-pressure gas port 5, and the high-pressure gas pipe 6C, and is condensed into a liquid therein by dissipating heat to warm the inside of the refrigerator.
  • the liquid refrigerant is guided to the high-pressure liquid port 17 through the check valve 14C of the parallel circuit 13C, and the liquid-side pipe 18C.
  • the high-pressure liquid refrigerant introduced into the high-pressure liquid port 17 is thermally insulated and expanded through the liquid-side pipes 18A and 18B, and the on-off valves 16A and 16B and the expansion valves 15A and 15B in the parallel circuits 13A and 13B, is then guided to the outside heat exchangers (A)8A and (B)8B, and is turned into an evaporative gas therein by absorbing heat from outside air.
  • the gas refrigerant returns to the compressor 3 through the low-pressure on-off valves 10A and 10B, the low-pressure gas pipes 9A and 9B, the low-pressure gas port 11, and the suction pipe 12.
  • the refrigerant is circulated in a cycle as described above. Accordingly, the inside of the refrigerator is warmed.
  • the high-pressure on-off valve 7A in the high-pressure gas pipe 6A, the on-off valve 16B in the parallel circuit 13B, and the low-pressure on-off valve 10B in the low-pressure gas pipe 9B are opened, and the high-pressure on-off valve 7B in the high-pressure gas pipe 6B, the on-off valve 16A in the parallel circuit 13A, and the low-pressure on-off valve 10A in the low-pressure gas pipe 9A are closed as shown in Fig. 2 .
  • the hot gas refrigerant discharged from the compressor 3 is thereby introduced into the outside heat exchanger (A)8A, and is caused to dissipate heat to defrost the outside heat exchanger (A) 8A.
  • the refrigerant condensed into a liquid by defrosting the outside heat exchanger (A)8A is thermally insulated and expanded by the expansion valve 15B in the parallel circuit 13B, is introduced into the outside heat exchanger (B)8B, and is evaporated thereby by absorbing heat from outside air. After that, the gas refrigerant is sucked into the compressor 3 through the low-pressure gas pipe 9B, the low-pressure gas port 11, and the suction pipe 12. The refrigerant is circulated in a cycle as described above.
  • a refrigeration cycle is configured by using one of the plurality of outside heat exchangers (A)8A and (B)8B disposed outside the refrigerator as the condenser, and the other as the evaporator as described above, so that the frosted outside heat exchanger (A)8A can be defrosted.
  • the outside fan 20A for the outside heat exchanger (A)8A is stopped, and the outside fan 20B for the outside heat exchanger (B)8B is operated.
  • the high-pressure on-off valve 7B in the high-pressure gas pipe 6B, the on-off valve 16A in the parallel circuit 13A, and the low-pressure on-off valve 10A in the low-pressure gas pipe 9A are opened, and the high-pressure on-off valve 7A in the high-pressure gas pipe 6A, the on-off valve 16B in the parallel circuit 13B, and the low-pressure on-off valve 10B in the low-pressure gas pipe 9B are closed as shown in Fig. 3 .
  • the hot gas refrigerant discharged from the compressor 3 is thereby introduced into the outside heat exchanger (B)8B, and is caused to dissipate heat to defrost the outside heat exchanger (B)8B.
  • the outside fan 20B for the outside heat exchanger (B)8B as the condenser is stopped, and the outside fan 20A for the outside heat exchanger (A)8A as the evaporator is operated.
  • Fig. 4 shows the control flowchart of the above defrosting operation.
  • step S1 When control is started, it is determined whether the outside heat exchanger (A)8A and the outside heat exchanger (B)8B satisfy a defrosting start condition in step S1. When the outside heat exchangers (A)8A and (B)8B do not satisfy the defrosting start condition, it is determined as No, and the control moves to END. On the other hand, when it is determined as YES, the control proceeds to step S2, in which the refrigerant circuit 2 is switched to a circuit (a cycle) for defrosting the outside heat exchanger (A)8A. This corresponds to the switching in the above (2).
  • the respective on-off valves (the respective solenoid valves) are opened or closed, and the respective outside fans are operated or stopped as described above.
  • step S2 When the switching action is completed in step S2, the control proceeds to step S3, in which supply of the refrigerant to the inside heat exchanger 8C is stopped. This corresponds to the control in the above (1). The warming operation inside the refrigerator is thereby stopped.
  • step S3 the control proceeds to step S4, in which it is determined whether the defrosting of the outside heat exchanger (A)8A is completed. Whether the defrosting is completed may be determined by a known method, for example, in which a temperature of the outside heat exchanger is detected.
  • step S4 When it is determined that the defrosting of the outside heat exchanger (A)8A is completed in step S4, the control proceeds to step S5, in which the switching action of the opening and closing of the respective on-off valves (the respective solenoid valves), and the operating and stopping of the respective outside fans equivalent to step S2 is executed in order to continuously perform the defrosting of the outside heat exchanger (B)8B.
  • step S6 In which it is determined whether the defrosting of the outside heat exchanger (B)8B is completed.
  • step S7 In which an inside temperature adjustment operation is resumed.
  • the plurality of (two) outside heat exchangers (A)8A and (B)8B are disposed in parallel with each other in the heat pump-type refrigerant circuit 2.
  • the plurality of outside heat exchangers (A)8A and (B)8B are caused to function as the evaporator, and the inside heat exchanger 8C is caused to function as the condenser, so that the inside of the refrigerator can be subjected to the heat pump warming operation. Therefore, the warming operation can be performed efficiently with high capacity by employing the heat pump method.
  • the defrosting cycle is configured by causing one of the plurality of outside heat exchangers (A)8A and (B)8B to function as the condenser, and the other to function as the evaporator in a state in which the warming operation is interrupted by stopping the refrigerant supply to the inside heat exchanger 8C.
  • the defrosting can be sequentially alternately performed with the refrigerant absorbing heat from outside air in either the outside heat exchanger (A)8A or the outside heat exchanger (B)8B.
  • the defrosting of the plurality of outside heat exchangers (A)8A and (B)8B can be performed by using the full capacity (all of the refrigerant) of the heat pump without absorbing heat from inside air, so that a defrosting operation time can be shortened, and a change in an inside temperature during the defrosting operation can be decreased.
  • each of the outside heat exchangers 8A and 8B can be defrosted by using the full capacity (all of the refrigerant) of the heat pump.
  • the defrosting can be performed within a short time.
  • the air blow systems including the outside fans 20A and 20B are provided independently of each other for the plurality of outside heat exchangers 8A and 8B. Therefore, the defrosting operation can be performed by stopping the outside fan 20A or 20B for the outside heat exchanger 8A or 8B that functions as the condenser, and operating the outside fan 20A or 20B for the outside heat exchanger 8A or 8B that functions as the evaporator, during the defrosting operation. Consequently, it is possible to efficiently perform the defrosting within a short time by increasing an amount of heat absorbed in the outside heat exchanger 8A or 8B that functions as the evaporator, and dissipating the heat in the outside heat exchanger 8A or 8B to be defrosted.
  • the two outside heat exchangers (A)8A and (B)8B are operated as the condensers during the cooling operation, a high pressure is lowered too much in some cases with a condensing capacity becoming excessive when an outside air temperature is low or the like.
  • the condensing capacity may be adjusted by monitoring the high pressure, stopping any of the outside heat exchangers (A)8A and (B)8B (the outside heat exchanger (B)8B in a case of Fig. 5 ) as shown in Fig. 5 when the high pressure is lowered too much, and thereby reducing the operation number.
  • the high-pressure on-off valve 7B in the high-pressure gas pipe 6B connected to the outside heat exchanger (B)8B is closed, the low-pressure on-off valve 10B is opened, and the outside fan 20B is stopped, so that the outside heat exchanger (B)8B is brought into a stopped state.
  • the operation number of the outside heat exchangers 8A and 8B is thereby reduced to adjust (lower) the condensing capacity.
  • the differential pressure between the high and low pressures can be maintained within an appropriate range. Therefore, it is possible to stably operate the transport refrigeration unit 1 by appropriately adjusting the capacity on the outside heat exchangers 8A and 8B-side corresponding to the heat exchange amount of the inside heat exchanger 8C, and thereby keeping an operation balance.
  • heat exchangers having different capacities from each other can be employed as the plurality of outside heat exchangers 8A and 8B.
  • the condensing capacity in the two outside heat exchangers 8A and 8B in three stages, which is greater than the number of the outside heat exchangers 8A and 8B by selecting working statuses of the heat exchangers. Therefore, the condensing capacity can be finely adjusted under various outside air temperatures and inside set temperature conditions corresponding to the conditions, and the operation can be more stably performed by maintaining the high and low pressure difference within an appropriate range. Consequently, it is possible to improve reliability of the transport refrigeration unit 1.
  • the refrigerant distribution to the inside heat exchanger 8C is stopped as shown in Figs. 2 and 3 during the defrosting operation of the outside heat exchangers 8A and 8B.
  • the warming operation may be performed by opening the high-pressure on-off valve 7C in the high-pressure gas pipe 6C connected to the inside heat exchanger 8C, and distributing the high-pressure gas refrigerant to the inside heat exchanger 8C in view of protecting a load.
  • the number of the outside heat exchangers 8A and 8B is not limited to two, and a configuration in which three or more outside heat exchangers are disposed in parallel with each other may be employed.
  • the inside heat exchanger 8C a configuration in which a plurality of inside heat exchangers are disposed in parallel with each other, the respective inside heat exchangers are separately disposed in a plurality of chambers divided in the refrigerator may be employed. In this case, of course, the plurality of divided chambers can be cooled or warmed at the same time. It is also possible to perform the cooling and warming operations at the same time, for example, by cooling one of the chambers, and warming another of the chambers.
  • the present embodiment differs from the first embodiment described above in that start/stop frequency of the compressor 3 can be reduced by using the plurality of outside heat exchangers 8A and 8B. Since the other points are similar to those of the first embodiment, a description thereof is omitted.
  • the transport refrigeration unit 1 is subjected to a thermo-on/off operation after the inside temperature reaches a set temperature by the cooling operation or the warming operation.
  • the present embodiment intends to suppress excessive starting and stopping of the compressor 3 at that time.
  • thermo-on/off On/off operation
  • a time in which the transport refrigeration unit 1 is thermo-on is short, the starting and stopping of the compressor 3 are frequently repeated, resulting in a malfunction and a decrease in service life. The reliability is thereby deteriorated.
  • a refrigeration cycle is configured by use of the plurality of outside heat exchangers 8A and 8B disposed in parallel with each other in a state in which the cooling operation or the warming operation is stopped by stopping the refrigerant distribution to the inside heat exchanger 8C, and the compressor 3 is stopped after being continuously operated for a specified length of time. The frequent starting and stopping is thereby prevented.
  • step S11 When control is started, it is determined whether the thermo-off condition is satisfied in step S11. When it is determined as No, the control directly moves to END. When it is determined as YES, the control proceeds to step S12. In step S12, it is determined whether an ON time (an operation time) of the compressor 3 exceeds a specified time that is previously set. When it is determined as YES, the control moves to step S17, in which the operation of the compressor 3 is directly stopped, and a thermo-off state is obtained.
  • step S13 in which the refrigerant circuit 2 is switched to the following operation circuit (an idling circuit), and the compressor 3 is continuously operated.
  • the operation circuit constitutes a circuit in which the refrigerant from the compressor 3 is circulated sequentially through the high-pressure gas port 5, the outside heat exchanger (A)8A, the high-pressure liquid port 17, the on-off valve 16B, the outside heat exchanger (B)8B, and the low-pressure gas port 11 by opening the high-pressure on-off valve 7A, the on-off valve 16B, and the low-pressure on-off valve 10B, closing the high-pressure on-off valve 7B, the on-off valve 16A, and the low-pressure on-off valve 10A, and further switching on the outside fans 20A and 20B in order to configure the refrigeration cycle in which one of the plurality of (two) outside heat exchangers 8A and 8B, e.g., the outside heat
  • step S14 the control proceeds to step S14, in which the high-pressure on-off valve 7C, the on-off valve 16C, and the low-pressure on-off valve 10C are closed, and the refrigerant distribution to the inside heat exchanger 8C is stopped, so that the thermo-off state is obtained.
  • the compressor 3 is directly and continuously operated by configuring the above refrigeration cycle.
  • step S15 in the above state, in which it is determined whether a thermo-on restoring condition is satisfied.
  • step S18 a process of starting the refrigerant supply to the inside heat exchanger 8C is performed.
  • the control then proceeds to step S19.
  • step S19 the high-pressure on-off valves 7A to 7C, the on-off valves 16A to 16C, and the low-pressure on-off valves 10A to 10C are switched, so that the refrigerant circuit 2 is switched to an original cooling operation cycle or an original warming operation cycle, that is, a cooling operation cycle in which the inside heat exchanger 8C is used as the evaporator, and the outside heat exchangers 8A and 8B are used as the condensers, or a heat pump warming operation cycle in which the inside heat exchanger 8C is used as the condenser, and the outside heat exchangers 8A and 8B are used as the evaporators. A thermo-on operation is thereby performed. Similar actions are subsequently repeated.
  • step S15 When it is determined that the thermo-on restoring condition is not satisfied in step S15, the control proceeds to step S16, in which it is determined whether the ON time (the operation time) of the compressor 3 exceeds the specified time. When it is determined as NO, the control returns to step S15, and actions in steps S15 and S16 are repeated. When it is determined that the operation time of the compressor 3 exceeds the specified time (YES) in step S16, the control proceeds to step S17, in which a process of turning off the compressor 3 to stop the operation is performed. Similar actions are subsequently repeated.
  • the compressor 3 can be always operated for the specified length of time or more by configuring the refrigeration cycle by use of the plurality of outside heat exchangers 8A and 8B, and idling the refrigeration unit 1 even when the thermo-off state is obtained. It is thus possible to prevent the frequent starting and stopping of the compressor 3. Therefore, the start/stop frequency of the compressor 3 can be suppressed, and the reliability can be ensured. Particularly in a case of a refrigerator, the inside of which is divided into a plurality of chambers, the thermo-on/off are repeated within a short time due to temperature interference between the chambers. Even in such a case, the frequent starting and stopping of the compressor can be prevented by continuously operating the compressor until the operation time of the compressor exceeds the specified time during the thermo-off.
  • the present invention is not limited to the invention according to the above embodiments, and can be modified as appropriate within the scope of the invention.
  • the present invention is not limited thereto. It goes without saying that the present invention can be similarly applied to a direct-connection-type transport refrigeration unit that drives an open-type compressor by a vehicle running engine via an electromagnetic clutch, or a sub-engine-type transport refrigeration unit including a dedicated sub-engine that drives a refrigeration unit.
  • the present invention can be similarly applied to a separated transport refrigeration unit in which an inside unit installed inside a refrigerator and an outside unit installed outside the refrigerator are separated as well as the integrated transport refrigeration unit 1.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Defrosting Systems (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP16155458.9A 2015-02-19 2016-02-12 Unité de réfrigération de transport Withdrawn EP3059522A3 (fr)

Applications Claiming Priority (1)

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JP2015030709A JP6426024B2 (ja) 2015-02-19 2015-02-19 輸送用冷凍ユニット

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EP3059522A3 EP3059522A3 (fr) 2016-12-14

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Publication number Priority date Publication date Assignee Title
JP2018096632A (ja) 2016-12-14 2018-06-21 三菱重工サーマルシステムズ株式会社 冷媒回路システム、制御装置及び制御方法
JP7235473B2 (ja) * 2018-10-24 2023-03-08 三菱重工サーマルシステムズ株式会社 冷凍装置
CN112665203A (zh) * 2020-12-11 2021-04-16 珠海格力电器股份有限公司 制冷机组、制冷控制方法及空调器

Citations (4)

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Publication number Priority date Publication date Assignee Title
JPH0355474A (ja) 1989-07-21 1991-03-11 Sanyo Electric Co Ltd 冷暖房装置
JPH0926219A (ja) 1996-07-30 1997-01-28 Sanyo Electric Co Ltd 多室型冷暖房装置
JP2013234784A (ja) 2012-05-08 2013-11-21 Mitsubishi Heavy Ind Ltd 輸送用冷凍装置
JP5535510B2 (ja) 2009-03-31 2014-07-02 三菱重工業株式会社 陸上輸送用冷凍装置

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Publication number Priority date Publication date Assignee Title
JPS5523844A (en) * 1978-08-02 1980-02-20 Sanyo Electric Co Heattpumpptype refrigerator
JPH03236570A (ja) * 1990-02-14 1991-10-22 Toshiba Corp 空気調和機
EP1197710B1 (fr) * 2000-10-13 2006-09-27 Eaton-Williams Group Limited Installation de pompe à chaleur
JP2008134025A (ja) * 2006-11-29 2008-06-12 Corona Corp ヒートポンプ式加熱装置
JP6053201B2 (ja) * 2013-02-06 2016-12-27 ダイキン工業株式会社 冷凍装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0355474A (ja) 1989-07-21 1991-03-11 Sanyo Electric Co Ltd 冷暖房装置
JPH0926219A (ja) 1996-07-30 1997-01-28 Sanyo Electric Co Ltd 多室型冷暖房装置
JP5535510B2 (ja) 2009-03-31 2014-07-02 三菱重工業株式会社 陸上輸送用冷凍装置
JP2013234784A (ja) 2012-05-08 2013-11-21 Mitsubishi Heavy Ind Ltd 輸送用冷凍装置

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