WO2011064927A1 - Dispositif de réfrigération pour contenant - Google Patents

Dispositif de réfrigération pour contenant Download PDF

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Publication number
WO2011064927A1
WO2011064927A1 PCT/JP2010/005558 JP2010005558W WO2011064927A1 WO 2011064927 A1 WO2011064927 A1 WO 2011064927A1 JP 2010005558 W JP2010005558 W JP 2010005558W WO 2011064927 A1 WO2011064927 A1 WO 2011064927A1
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WO
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Prior art keywords
state
refrigerant
opening degree
control unit
target
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PCT/JP2010/005558
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English (en)
Japanese (ja)
Inventor
横原和馬
藤本祐介
岡本敦
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ダイキン工業株式会社
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Publication of WO2011064927A1 publication Critical patent/WO2011064927A1/fr

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    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves

Definitions

  • the present invention relates to a container refrigeration apparatus provided with a supercooling heat exchanger.
  • a container refrigeration apparatus that cools the inside of a container used for sea transportation or the like includes a refrigerant circuit to which a compressor, a condenser, an expansion valve, and an evaporator are connected.
  • the refrigerant circulates to perform a vapor compression refrigeration cycle, the refrigerant flowing through the evaporator absorbs heat from the internal air and evaporates, and the internal air is cooled (see Patent Document 1).
  • the container refrigeration apparatus is provided with a subcooling heat exchanger (economizer heat exchanger) on the downstream side of the condenser to improve cooling performance, and the liquid refrigerant subcooled in the subcooling heat exchanger is used as an evaporator. Supply.
  • a branch path for branching the liquid refrigerant from between the condenser and the supercooling heat exchanger and leading to the supercooling heat exchanger, and a capillary tube for decompressing the refrigerant in the branch path are provided.
  • the liquid refrigerant is supercooled by heat exchange between the refrigerant decompressed in the capillary tube and the liquid refrigerant in the supercooling heat exchanger.
  • the branch path is configured such that the refrigerant obtained by supercooling the liquid refrigerant in the supercooling heat exchanger is introduced into the compression chamber having an intermediate pressure of the compressor. Thereby, the liquid refrigerant can be supercooled without reducing the amount of refrigerant sucked by the compressor, and the cooling performance can be improved.
  • the conventional container refrigeration apparatus employs a capillary tube as a branching pressure reducing mechanism, the refrigerant flow rate in the branching path cannot be appropriately adjusted according to the operating state. For this reason, there is a risk of inconveniences such as deterioration in energy efficiency due to an increase in the cooling capacity of the evaporator more than necessary and damage to the compressor due to wetness.
  • the present invention has been made in view of such points, and in a container refrigeration apparatus including a supercooling heat exchanger, the refrigerant flow rate in the branch path can be adjusted according to the operating state of the cooling operation in the warehouse.
  • the purpose is to do.
  • the present invention is a container refrigeration apparatus equipped with a supercooling heat exchanger, wherein the refrigerant flow rate in the branch path can be adjusted according to the operating state of the cooling operation in the warehouse.
  • the first invention comprises a main circuit (21) in which a compressor (30), a condenser (31), an expansion mechanism (32), and an evaporator (33) for cooling the inside of the cabinet are connected in order,
  • a branch path (23) branched from the liquid pipe of the main circuit (21) and connected to the compression chamber in the intermediate pressure state of the compressor (30) and provided with a pressure reducing mechanism; and the main circuit (21)
  • the branch path (23) having a primary channel (45) connected to the liquid pipe and a secondary channel (46) connected to the downstream side of the decompression mechanism of the branch path (23).
  • the container refrigeration apparatus includes a supercooling heat exchanger (44) for exchanging heat between the decompressed refrigerant and the liquid refrigerant in the main circuit (21).
  • the subcooling expansion valve (48) is a flexible subcooling expansion valve (48). Control means (80) for controlling the opening of the expansion valve (48) is provided.
  • the refrigerant circulates in the main circuit (21), and the internal space is cooled by the evaporator (33).
  • Part of the liquid refrigerant in the main circuit (21) flows into the branch channel (23) and is depressurized by the decompression mechanism, and then flows into the secondary channel (46) of the supercooling heat exchanger (44).
  • the liquid refrigerant in the main circuit (21) flowing through the primary channel (45) is supercooled.
  • the subcooling expansion valve (48) whose opening degree can be freely adjusted is used as the pressure reducing mechanism of the branch passage (23), and the supercooling expansion valve (48) is provided with the control means (80
  • the opening degree is controlled according to the operating state of the cooling operation in the storage. Thereby, the refrigerant
  • control means (80) is configured to superheat the refrigerant on the outflow side of the secondary flow path (46) of the supercooling heat exchanger (44) in the cooling operation.
  • the opening degree control unit (80c, 84a) for controlling the opening degree of the supercooling expansion valve (48) so that the degree falls within a predetermined target range, and the opening degree according to the operating state of the cooling operation.
  • a target changing unit (80d, 84b) that changes the target range of the control unit (80c, 84a).
  • the degree of superheat of the refrigerant after passing through the secondary side flow path (46) of the supercooling heat exchanger (44) is set to a predetermined target by the opening degree control unit (80c, 84a).
  • the opening degree of the supercooling expansion valve (48) is controlled so as to be within the range.
  • the target change unit (80d, 84b) changes the target range of the opening control unit (80c, 84a), and the opening control unit (80c, 84a)
  • the degree of opening of the supercooling expansion valve (48) is controlled so that the degree of superheat of the refrigerant after passing through the secondary side flow path (46) of the heat exchanger (44) becomes the changed target range.
  • the opening degree of the supercooling expansion valve (48) is changed to a higher value.
  • the opening degree of the supercooling expansion valve (48) increases.
  • the refrigerant flow rate in the branch path (23) decreases or increases.
  • the opening degree control unit (80c) is configured to set the target range based on a target refrigerant superheat degree, while the target change unit (80d)
  • an increase signal output unit (80f) that outputs an increase signal to the opening degree control unit (80c) to increase the target refrigerant superheat degree is provided.
  • the increase signal output unit (80f) when the cooling load of the evaporator (33) is reduced, the increase signal output unit (80f) outputs an increase signal to the opening degree control unit (80c).
  • the target refrigerant superheat degree which becomes an index for adjusting the opening degree of the supercooling expansion valve (48) is increased.
  • the opening degree of the supercooling expansion valve (48) decreases, the amount of refrigerant flowing into the secondary side flow path (46) of the supercooling heat exchanger (44) is reduced, and the primary side flow path (45 ), The degree of supercooling of the liquid refrigerant in the main circuit (21) decreases, and the cooling capacity of the evaporator (33) decreases as the cooling load decreases.
  • the target changing section (80d) outputs a reduction signal to the opening degree control section (80c) when the cooling load of the evaporator (33) increases.
  • a reduction signal output unit (80 g) for reducing the target refrigerant superheat degree is provided.
  • the reduction signal output unit (80g) outputs a reduction signal to the opening degree control unit (80c).
  • the target refrigerant superheat degree which becomes an index for adjusting the opening degree of the supercooling expansion valve (48) is reduced.
  • the opening degree of the supercooling expansion valve (48) is increased, the amount of refrigerant flowing into the supercooling heat exchanger (44) is increased, and the degree of supercooling of the liquid refrigerant in the main circuit (21) is increased.
  • the cooling capacity of the evaporator (33) increases as the cooling load increases.
  • the target changing unit (84b) is configured such that the operation state is the secondary side of the supercooling heat exchanger (44) in the main operation after the start of the cooling operation.
  • the target range of the opening control unit (84a) is set to be less than that in the normal operation state of the main operation. It is configured to change to a higher range.
  • the target range of the opening degree control unit (80c) is set by the target change unit (84b) from the normal state. Is also changed to a higher range, and the opening degree of the supercooling expansion valve (48) decreases.
  • the degree of superheat of the refrigerant on the outflow side of the secondary side flow path (46) of the supercooling heat exchanger (44) increases, and the wet state of the refrigerant is eliminated, and the refrigerant flow rate in the branch path (23) Decrease.
  • the target changing unit (84b) is configured so that the target range of the opening degree control unit (84a) is equal to the cooling load of the evaporator (33) in the normal state. It is configured to change so that the cooling load of the evaporator (33) is in a higher range in the low load state where the cooling load of the evaporator (33) is less than the predetermined value than in the high load state where the predetermined value or more.
  • the cooling capacity required for the evaporator (33) is large, and when the operation state is a low load state, the cooling capacity required for the evaporator (33). Is smaller in each stage than in the high load state. Therefore, the degree of superheat of the refrigerant on the outflow side of the secondary side flow path (46) of the supercooling heat exchanger (44) is approximately the same when the operation state is a high load state and when the operation state is a low load state. If the opening degree of the supercooling expansion valve (48) is controlled in this way, the cooling capacity of the evaporator (33) may be insufficient when the load is high, or the evaporator (33) when the load is low. 33) Cooling capacity may be excessive.
  • the target changing unit (84b) changes the target range of the opening degree control unit (84a) depending on whether the driving state is a high load state or a low load state. Yes.
  • the target range of the opening degree control unit (84a) is changed to a high range, and the opening degree of the supercooling expansion valve (48) decreases.
  • coolant flow volume which flows in into the secondary side flow path (46) of a supercooling heat exchanger (44) reduces, and cooling capacity falls.
  • the target change unit (84b) changes the target range of the opening control unit (84a) to a low range, and the opening degree of the supercooling expansion valve (48) Will increase.
  • coolant flow volume which flows in into the secondary side flow path (46) of a supercooling heat exchanger (44) increases, and cooling capacity increases.
  • the opening control unit (84a) is configured to perform feedback control
  • the control means (80) is configured so that the operating state in the main operation is the wet state.
  • a control speed changing unit (84c) that changes the control speed of the opening degree control unit (84a) to be higher than that in the normal state is provided.
  • the control speed of the opening control unit (84a) is changed by the control speed changing unit (84c), and the feedback control of the opening control unit (84a) is performed.
  • the speed is higher than in normal conditions.
  • the opening control section (84a) is configured to perform feedback control
  • the control means (80) is configured to perform the opening control section
  • a control speed changing unit (84c) is provided that changes the control speed of 84a) so that the operation speed is lower in the low load state than in the high load state.
  • the opening degree of the supercooling expansion valve (48) is set so that the speed of feedback control by the opening degree control unit (84a) is approximately the same in the case where the operation state is a high load state and in the case of a low load state.
  • the opening degree control unit (for the change in the superheat degree of the refrigerant on the outflow side of the secondary side flow path (46) of the supercooling heat exchanger (44) 84a) delays the control of the degree of opening of the supercooling expansion valve (48), and the degree of superheat deviates significantly from the target range, so that the liquid refrigerant in the main circuit (21) cannot be supercooled, or wet refrigerant is compressed by the compressor. (30) may be introduced.
  • the supercooling expansion valve is adapted to a slight change in the degree of superheat of the refrigerant on the outflow side of the secondary side flow path (46) of the supercooling heat exchanger (44).
  • the opening control of (48) will follow with sensitivity and the cooling capacity of the evaporator (33) will be fluctuated, causing the refrigerant behavior in the main circuit (21) to become unstable.
  • the control speed changing unit (84c) changes the speed of the feedback control by the opening degree control unit (84a) depending on whether the operation state is a high load state or a low load state. To do. Thereby, for example, when the operation state changes from a high load state to a low load state, the control speed of the opening degree control unit (84a) is reduced, and the secondary side flow path (46) of the supercooling heat exchanger (44) is reduced.
  • the opening control of the supercooling expansion valve (48) does not follow the sensitivity sensitively to a slight change in the degree of superheat of the refrigerant on the outflow side.
  • the control speed of the opening degree control unit (84a) is increased, and the outlet side of the secondary side flow path (46) of the supercooling heat exchanger (44) is increased.
  • the degree of opening control of the supercooling expansion valve (48) follows sensitively to a slight change in the degree of superheat of the refrigerant.
  • the compressor (30) is configured such that the number of rotations changes according to the cooling load of the evaporator (33), and the opening degree control unit (84a)
  • feedforward control is performed based on a change in the rotational speed of the compressor (30).
  • the compressor (30) when the rotation speed of the compressor (30) changes, the refrigerant circulation amount increases and decreases, and the superheat degree of the refrigerant on the outflow side of the secondary side flow path (46) of the supercooling heat exchanger (44) varies. . Therefore, when the compressor (30) is configured so that the rotation speed changes according to the cooling load of the evaporator (33), if the cooling load of the evaporator (33) suddenly changes due to some factor, the feedback control Control may be delayed, and the degree of superheat of the refrigerant on the outflow side of the secondary-side flow path (46) of the supercooling heat exchanger (44) may greatly deviate from the target range. In particular, when the operation state is a high load state, since the change in the cooling load of the evaporator (33) is large, the feedback control by the opening degree control unit (84a) may be delayed.
  • the opening degree control unit (84a) feeds forward based on a change in the rotational speed of the compressor (30) in addition to feedback control when the operating state is a high load state. Control is going to be done.
  • the subcooling expansion valve (48) is controlled by the opening degree control unit (84a) based on the change in the rotational speed of the compressor (30), based on the secondary flow path (46 of the supercooling heat exchanger (44)). ) Is predicted in advance so that the degree of superheat does not greatly deviate from the target range.
  • control means (80) further comprises an on-off valve (47) provided upstream of the supercooling expansion valve (48) of the branch passage (23). Controls the on-off valve (47) to be closed when the operation state of the main operation is the normal state and the cooling load of the evaporator (33) is a low load state less than a predetermined value. In addition, the opening degree control by the opening degree control unit (84a) is stopped.
  • the cooling capacity required by the evaporator (33) when the operation state is a normal state and the cooling load of the evaporator (33) is a low load state that is less than a predetermined value, the cooling capacity required by the evaporator (33). However, since the cooling load of the evaporator (33) is smaller in each stage than in the high load state in which the evaporator (33) is equal to or higher than the predetermined value, the cooling capacity of the evaporator (33) may be excessive.
  • the opening degree control by the opening degree control unit (84a) is stopped, and the upstream of the supercooling expansion valve (48) in the branch path (23).
  • the on-off valve (47) provided on the side is closed to prevent the refrigerant from flowing into the branch path (23). Thereby, the liquid refrigerant of the main circuit (21) is not supercooled in the supercooling heat exchanger (44).
  • the supercooling expansion valve (48) whose opening degree can be freely adjusted is adopted as the pressure reducing mechanism of the branch passage (23), and the control means (80) is provided. It becomes possible to adjust the refrigerant
  • the target changing unit (80d, 84b) changes the target range of the opening degree control unit (80c, 84a) in accordance with a change in the operating state of the cooling operation, thereby branching.
  • the refrigerant flow rate in the passage (23) can be easily changed according to the operating state of the cooling operation.
  • the degree of superheat of the refrigerant after passing through the secondary flow path (46) of the supercooling heat exchanger (44) by the opening degree control unit (80c, 84a) is a predetermined target.
  • the opening degree of the supercooling expansion valve (48) so as to be within the range, wetting of the refrigerant after passing through the secondary side flow path (46) can be prevented. Accordingly, it is possible to prevent liquid compression by avoiding introduction of wet refrigerant into the compression chamber in the intermediate pressure state of the compressor (30).
  • the cooling capacity of the evaporator (33) is unnecessarily increased by reducing the flow rate of the refrigerant flowing into the supercooling heat exchanger (44) according to the decrease in the cooling load.
  • the interior can be cooled without any problems. Therefore, energy efficiency can be improved.
  • the compressor in the container refrigeration apparatus configured to stop the compressor (30) when the internal temperature is lower than the lower limit temperature, when the cooling capacity increases unnecessarily even when the cooling load decreases, the compressor ( There is a risk that the number of times of switching between starting and stopping in 30) will increase and energy consumption will increase.
  • the cooling capacity of the evaporator (33) since the cooling capacity of the evaporator (33) also decreases as the cooling load decreases, the number of switching between starting and stopping of the compressor (30) can be reduced to reduce the energy consumption. The increase can be suppressed.
  • the amount of refrigerant flowing into the supercooling heat exchanger (44) is increased in accordance with an increase in the cooling load, thereby increasing the cooling capacity and sufficiently cooling the interior. Can do.
  • the target changing unit (84b) changes the target range of the opening control unit (84a) to a range higher than the normal state.
  • the opening degree of the supercooling expansion valve (48) can be decreased.
  • the degree of superheat of the refrigerant on the outflow side of the secondary side flow path (46) of the supercooling heat exchanger (44) can be increased to eliminate the wet state of the refrigerant, and the branch path (23)
  • the refrigerant flow rate can be reduced. Therefore, it is possible to prevent damage to the compressor (30) by preventing a large amount of wet refrigerant from being introduced into the compression chamber in the intermediate pressure state of the compressor (30) and avoiding liquid compression. it can.
  • the target change unit (84b) changes the target range of the opening degree control unit (84a) depending on whether the operation state is a high load state or a low load state. Therefore, when the operation state is a high load state, the inside of the warehouse can be cooled with a high cooling capacity, and when the operation state is a low load state, the cooling capacity is prevented from increasing unnecessarily. Can do. That is, the cooling capacity of the evaporator (33) can be adjusted according to the cooling load of the evaporator (33). Therefore, energy efficiency can be improved.
  • the compressor (30) stops when the internal temperature falls below the lower limit temperature
  • the compressor (30) As a result, the number of times of switching between starting and stopping increases, resulting in an increase in energy consumption.
  • the cooling capacity is not unnecessarily increased in a low load state, the number of times of switching between starting and stopping of the compressor (30) is reduced and the consumption energy is increased. Can be suppressed.
  • the target range of the opening degree control unit (84a) is changed to a range higher than the normal state by the target changing unit (84b).
  • the control speed of the opening degree control unit (84a) is changed to a higher speed than the normal state by the control speed changing unit (84c).
  • the control speed changing unit (84c) controls the feedback control speed by the opening degree control unit (84a) depending on whether the operation state is a high load state or a low load state.
  • the behavior of the refrigerant in the main circuit (21) can be maintained in a stable state.
  • the operating state is a high load state
  • the opening degree control unit (84a) feeds forward based on a change in the rotational speed of the compressor (30) in addition to the feedback control.
  • the opening degree control unit (84a) feeds forward based on a change in the rotational speed of the compressor (30) in addition to the feedback control.
  • the refrigerant when the operating state is a low load state, the refrigerant is prevented from flowing into the branch path (23), and the main circuit (21) of the supercooling heat exchanger (44) is prevented.
  • the cooling capacity of the evaporator (33) By stopping the supercooling of the liquid refrigerant, it is possible to prevent the cooling capacity of the evaporator (33) from increasing unnecessarily. Therefore, energy efficiency can be improved.
  • the compressor (30 ) in the container refrigeration apparatus configured to stop the compressor (30) when the internal temperature falls below the lower limit temperature, if the cooling capacity increases unnecessarily in the low load state, the compressor (30 ) May increase the number of times of switching between activation and stop to increase energy consumption.
  • the number of switching between starting and stopping of the compressor (30) can be reduced. An increase in energy consumption can be suppressed.
  • FIG. 1 is a refrigerant circuit diagram of a container refrigeration apparatus according to Embodiment 1 of the present invention.
  • FIG. 2 is a table showing the target refrigerant superheat degree corresponding to the cooling load of the evaporator.
  • FIG. 3 is a flowchart showing a flow of opening degree control of the supercooling expansion valve by the opening degree control unit.
  • FIG. 4 is a refrigerant circuit diagram of the container refrigeration apparatus according to Embodiment 2 of the present invention.
  • FIG. 5 is a flowchart showing a flow of determination of the driving state in the driving state determination unit.
  • FIG. 6 is a flowchart showing a flow of normal control of the supercooling expansion valve by the opening degree control unit.
  • FIG. 1 is a refrigerant circuit diagram of a container refrigeration apparatus according to Embodiment 1 of the present invention.
  • FIG. 2 is a table showing the target refrigerant superheat degree corresponding to the cooling load of the evaporator.
  • FIG. 7 is a table showing the set values in the respective operation states of the upper limit value H1 of the target range of the intermediate superheat degree, the lower limit value L1 of the target range of the intermediate superheat degree, the predetermined time T1, and the predetermined time T2 in FIG.
  • FIG. 8 is an explanatory diagram of a pre-stabilization stage and a post-stabilization stage.
  • FIG. 9 is a table showing set values in the pre-stabilization stage and the post-stabilization stage of the opening change amounts P1 and P2 in FIG.
  • the container refrigeration apparatus (10) cools the interior of a container (not shown) and includes a refrigerant circuit (20).
  • the container refrigeration apparatus (10) also serves as a lid that closes one opening surface of the container body.
  • the refrigerant circuit (20) includes a main circuit (21), a defrost hot gas bypass passage (22), and a supercooling bypass passage (23) for refrigerant supercooling.
  • the main circuit (21) includes a compressor (30), a condenser (31), an electric main expansion valve (32) as an expansion mechanism, and an evaporator (33) in series by a refrigerant pipe (34) in order. Connected and configured. And although the said compressor (30) is not shown in figure, the rotation speed is controlled by an inverter, the rotation speed is controlled in multiple steps, and the operation capacity is variable.
  • the condenser (31) is provided with an external fan (35), while the evaporator (33) is provided with an internal fan (36).
  • the internal fan (36) is configured to supply the cooling air cooled by the evaporator (33) into the internal space.
  • An oil separator (40) is provided on the discharge side of the compressor (30), and a discharge pressure adjusting valve (38) is provided between the oil separator (40) and the condenser (31). Yes.
  • a receiver (41) Between the condenser (31) and the main expansion valve (32), there are a receiver (41), a cooler (42) for electric equipment, a dryer (43), and a plate heat exchanger (44). It is provided in order.
  • the oil return pipe (40a) of the oil separator (40) is connected to the supercooling bypass path (23).
  • the cooler (42) is configured to cool an electric device such as a power element of the inverter.
  • the cooler (42) is provided on the back surface of the printed circuit board, and the electric device is supplied by the high-pressure liquid refrigerant flowing through the condenser (31). It is cooling.
  • the dryer (43) is configured to remove moisture from the liquid refrigerant that has flowed through the condenser (31).
  • the plate heat exchanger (44) supercools the liquid refrigerant that has flowed through the condenser (31), and includes a primary side passage (45) and a secondary side passage (46).
  • the primary side passage (45) is connected to the main circuit (21), and the secondary side passage (46) is connected to the supercooling bypass passage (23).
  • the inflow end of the supercooling bypass passage (23) is connected to the refrigerant pipe (34) between the cooler (42) and the dryer (43), and the outflow end of the supercooling bypass passage (23) is compressed. It is connected to the compression chamber in the intermediate pressure state in the machine (30).
  • first on-off valve (47) On the inflow side of the supercooling bypass passage (23), there is a first on-off valve (47) and an electrically operated supercooling expansion valve (48) which can adjust the opening degree of the pressure reducing mechanism according to the present invention.
  • first on-off valve (47) Corresponding to the first on-off valve (47), the main circuit (21) is provided with a second on-off valve (49) between the branch portion of the supercooling bypass passage (23) and the dryer (43). ing.
  • the plate heat exchanger (44) branches from the main circuit (21) to the supercooling bypass passage (23) and is decompressed by the supercooling expansion valve (48) and the refrigerant flowing through the main circuit (21). And the refrigerant that flows through the main circuit (21) through heat exchange are supercooled.
  • the hot gas bypass path (22) includes a common path (50), and a first bypass path (51) and a second bypass path (52) branched from the common path (50).
  • the common path (50) has an inflow end connected between the oil separator (40) and the discharge pressure adjustment valve (38), and is provided with a third on-off valve (53).
  • Outflow ends of the first bypass path (51) and the second bypass path (52) are connected between the main expansion valve (32) and the evaporator (33), and the second bypass path (52)
  • a drain pan heater (54) for heating the drain pan disposed at the lower portion of the evaporator (33) is provided.
  • the hot gas bypass path (22) is configured to supply high-temperature and high-pressure gas refrigerant discharged from the compressor (30) to the evaporator (33) during the defrost operation when the evaporator (33) is frosted. Has been.
  • the second bypass passage (52) is configured to heat the drain pan during the defrost operation.
  • the discharge side and suction side of the compressor (30) are provided with a high pressure sensor (60) and a high pressure switch (61) for detecting the discharge gas pressure of the compressor (30), and the compressor A low pressure sensor (62) for detecting the suction gas pressure of (30) is provided.
  • a discharge temperature sensor (63) and a suction temperature sensor (64) for detecting the refrigerant temperature are provided on the discharge side and the suction side of the compressor (30).
  • An inflow temperature sensor (65) and an outflow temperature sensor (66) for detecting the refrigerant temperature are provided on the inflow side and the outflow side of the secondary passage (46) of the plate heat exchanger (44). .
  • An inflow temperature sensor (67) and an outflow temperature sensor (68) for detecting the refrigerant temperature are provided on the inflow side and the outflow side of the evaporator (33).
  • the condenser is provided with an outside air temperature sensor (69) for detecting the outside air temperature that is the suction temperature of the condenser. Further, an intake temperature sensor (70) for detecting the intake air temperature and an outlet temperature sensor (71) for detecting the blown air temperature are provided on the air suction side and the blowout side of the evaporator.
  • the container refrigeration apparatus (10) is provided with a controller (80) for controlling the cooling operation by controlling the refrigerant circuit (20).
  • the controller (80) receives signals from the high pressure sensor (60) and the like, and also has a control board for controlling the cooling operation and an inverter control board for controlling the inverter of the compressor (30). Etc. are provided.
  • the controller (80) includes a cooling capacity adjustment unit (80a) for adjusting the cooling capacity of the evaporator (33) according to the cooling load of the evaporator (33) during the cooling operation.
  • the cooling capacity adjustment unit (80a) includes a cooling load detection unit (80b), an opening degree control unit (80c), and a target refrigerant superheat degree output unit (80d).
  • the cooling load detector (80b) detects the cooling load of the evaporator (33) (the heat load in the cabinet, that is, the required cooling amount). Specifically, the internal temperature is detected, and the temperature difference between the internal temperature and the set temperature is detected as a cooling load.
  • the cooling load detection unit (80b) uses the value detected by the suction temperature sensor (70) as the internal temperature in the refrigeration mode where the set temperature is -10.0 ° C or lower, and is refrigerated where the set temperature is -9.9 ° C or higher. In the mode, the detected value of the blowing temperature sensor (71) is set as the internal temperature.
  • running state is divided into four states according to the cooling load which the cooling load detection part (80b) detected.
  • the opening degree control unit (80c) has a refrigerant superheat degree on the outlet side of the secondary passage (46) of the plate heat exchanger (44) (hereinafter simply referred to as “intermediate superheat degree (intermediate SH)”).
  • the opening degree of the supercooling expansion valve (48) is controlled to be within a predetermined range (predetermined target range) based on the target refrigerant superheat degree (target intermediate SH).
  • the intermediate superheat degree (intermediate SH) is a value obtained by subtracting the refrigerant temperature on the inflow side from the refrigerant temperature on the outflow side of the secondary passage (46) of the plate heat exchanger (44). It is calculated by subtracting the detection value of the inflow temperature sensor (65) from the detection value of 66).
  • the predetermined range is set to target intermediate SH ⁇ intermediate SH ⁇ target intermediate SH + ⁇ T (predetermined value).
  • the target refrigerant superheat degree output unit (80d) controls the opening degree of the supercooling expansion valve (48) by the opening degree control part (80c) according to the cooling load detected by the cooling load detection part (80b).
  • the target refrigerant superheat degree (target intermediate SH), which is an index for the determination, is determined.
  • the target refrigerant superheat output unit (80d) constitutes a target changing unit according to the present invention that changes the target range of the opening degree control unit (80c) according to the operating state of the cooling operation.
  • the target refrigerant superheat degree output unit (80d) includes an initial value output unit (80e), an increase signal output unit (80f), and a reduction signal output unit (80g).
  • the initial value output unit (80e) determines an initial value of the target refrigerant superheat degree (target intermediate SH) according to the cooling load detected by the cooling load detection unit (80b), and sends a signal to the opening degree control unit (80c). To input the initial value of the target refrigerant superheat degree.
  • a target refrigerant superheat degree (target intermediate SH) corresponding to four stages of cooling loads (temperature difference between the internal temperature and the set temperature (SP)) is set in advance. For example, when the temperature difference between the internal temperature and the set temperature (SP) is larger than 10 ° C., the initial value of the target refrigerant superheat degree (target intermediate SH) is determined to be 3 ° C.
  • the increase signal output unit (80f) outputs an increase signal to the opening control unit (80c), and the opening control unit (80f) In 80c), the target refrigerant superheat degree (target intermediate SH), which serves as an index for adjusting the opening degree of the supercooling expansion valve (48), is increased.
  • target refrigerant superheat degree target intermediate SH
  • the relationship between the cooling load and the target refrigerant superheat degree (target intermediate SH) shown in the table of FIG. 2 is adapted.
  • the target refrigerant superheat degree (target intermediate SH) is increased.
  • the reduction signal output unit (80g) outputs a reduction signal to the opening control unit (80c) to control the opening control.
  • the part (80c) is configured to reduce the target refrigerant superheat degree (target intermediate SH) that serves as an index for adjusting the opening degree of the supercooling expansion valve (48).
  • target intermediate SH target refrigerant superheat degree
  • the relationship between the cooling load and the target refrigerant superheat degree (target intermediate SH) shown in the table of FIG. 2 is adapted.
  • the target refrigerant superheat degree (target intermediate SH) is reduced.
  • the controller (80) performs the supercooling expansion so that the refrigerant flow rate of the supercooling bypass passage (23) is adjusted according to the four operating states corresponding to the four stages of cooling loads.
  • the controller (80) performs four operations within a predetermined target range of the intermediate superheat (intermediate SH) of the opening control unit (80c) by the target refrigerant superheat output unit (80d).
  • coolant flow rate of a cooling bypass channel (23) is adjusted according to four driving
  • the third on-off valve (53) is closed, and the first on-off valve (47) and the second on-off valve (49) are open.
  • the refrigerant discharged from the compressor (30) is condensed by the condenser (31), then decompressed by the main expansion valve (32), and evaporated by the evaporator (33). After that, it returns to the compressor (30). This refrigerant circulation is repeated. Then, the internal air is cooled by the evaporator (33), and the cooling air is supplied into the internal space by the internal fan (36).
  • the supercooling expansion valve (48) is controlled to an initial opening set in advance by the opening controller (80c) at the start of the cooling operation, and then opened according to the cooling load of the evaporator (33). The degree is changed. Details thereof will be described in detail in the cooling capacity adjustment operation.
  • defrosting is performed to open the third on-off valve (53) and close the main expansion valve (32) and the discharge pressure adjustment valve (38).
  • the high-temperature refrigerant gas discharged from the compressor (30) is supplied to the evaporator (33), and the frost in the evaporator (33) is removed.
  • the cooling capacity adjusting unit (80a) performs the refrigerating capacity adjusting operation for adjusting the cooling capacity according to the cooling load of the evaporator (33).
  • the cooling load detector (80b) detects the cooling load of the evaporator (33).
  • the detected value of the suction temperature sensor (70) is set to the warehouse temperature, and the temperature set in the warehouse is set.
  • a temperature difference from the temperature (SP) is defined as a cooling load.
  • the detected value of the blowout temperature sensor (71) is set to the inside temperature, and the inside temperature and the set temperature (SP) The difference in temperature is the cooling load.
  • the initial value output unit (80e) of the target refrigerant superheat output unit (80d) determines an initial value of the target refrigerant superheat degree (target intermediate SH) according to the cooling load detected by the cooling load detection unit (80b). Then, a signal is output to the opening degree control unit (80c) to input an initial value of the target refrigerant superheat degree (target intermediate SH). For example, when the temperature difference between the internal temperature and the set temperature (SP) is 15 ° C., the initial value (for example, 3 ° C.) of the target refrigerant superheat degree (target intermediate SH) is determined, and the opening degree control unit (80c) Enter the initial value (3 ° C) in.
  • the opening degree control unit (80c) calculates the intermediate superheat degree (intermediate SH) from the detected values of the inflow temperature sensor (65) and the outflow temperature sensor (66), and the intermediate superheat degree (intermediate SH) is the target refrigerant superheat degree.
  • the opening degree of the supercooling expansion valve (48) is controlled so as to be within a predetermined range (3 ° C. ⁇ intermediate SH ⁇ 3 ° C. + ⁇ T) with reference to the initial value (3 ° C.). Although details will be described later, when the intermediate superheat degree (intermediate SH) is smaller than a predetermined range (3 ° C. ⁇ intermediate SH ⁇ 3 ° C.
  • the degree of opening of the supercooling expansion valve (48) is reduced while When the degree of superheat (intermediate SH) is greater than a predetermined range (3 ° C. ⁇ intermediate SH ⁇ 3 ° C. + ⁇ T), the opening degree of the supercooling expansion valve (48) is increased.
  • the increase signal output unit (80f) is transferred to the opening control unit (80c).
  • An increase signal is output, and the target refrigerant superheat degree in the opening degree control unit (80c) is increased.
  • the target refrigerant superheat degree (target intermediate SH) in the opening degree control unit (80c) is increased by the increase signal output unit (80f). Is increased from 3 ° C to 5 ° C.
  • the opening degree control unit (80c) Decreases the opening of the supercooling expansion valve (48).
  • the amount of refrigerant flowing into the secondary passage (46) of the plate heat exchanger (44) decreases, and the degree of supercooling of the liquid refrigerant in the main circuit (21) flowing through the primary passage (45) is small. Therefore, the cooling capacity of the evaporator (33) is reduced.
  • the target refrigerant superheat degree (target intermediate SH) in the opening degree control unit (80c) is increased by the increase signal output unit (80f).
  • the opening degree control unit (80c) Decreases the opening of the supercooling expansion valve (48). As a result, the cooling capacity of the evaporator (33) further decreases.
  • the target refrigerant superheat degree (target intermediate SH) in the opening degree control unit (80c) is increased by the increase signal output unit (80f).
  • the opening degree control unit (80c) Decreases the opening of the supercooling expansion valve (48). As a result, the cooling capacity of the evaporator (33) further decreases.
  • the internal temperature in a state where the internal temperature is stable near the set temperature (the temperature difference between the internal temperature and the set temperature (SP) is 1 ° C. or less), the internal temperature also increases as the external temperature rapidly increases. May rise rapidly.
  • the reduction signal output unit (80g) outputs a reduction signal to the opening control unit (80c), The target refrigerant superheat degree in the opening degree control unit (80c) is reduced.
  • the target refrigerant superheat degree (target intermediate SH) in the opening degree control unit (80c) is reduced by the reduction signal output unit (80g). Is reduced from 20 ° C. to 10 ° C.
  • the opening degree control unit (80c) is supercooled. Increase the opening of the expansion valve (48).
  • the target refrigerant superheat degree in the opening degree control unit (80c) is set by the reduction signal output unit (80g).
  • (Target intermediate SH) is reduced from 10 ° C. to 5 ° C.
  • the target refrigerant superheat degree (target intermediate SH) in the opening degree control unit (80c) is reduced by the reduction signal output unit (80g).
  • the reduction signal output unit (80g) Is reduced from 5 ° C to 3 ° C.
  • the opening degree control unit (80c) is supercooled. Increase the opening of the expansion valve (48). As a result, the cooling capacity of the evaporator (33) is further improved.
  • the evaporator (33) By reducing the amount of refrigerant flowing into the secondary passage (46) of the plate heat exchanger (44) as the cooling load of the evaporator (33) decreases, the evaporator (33) On the other hand, by increasing the amount of refrigerant flowing into the secondary passage (46) of the plate heat exchanger (44) as the cooling load of the evaporator (33) increases, The cooling capacity of the evaporator (33) can be improved. That is, the cooling capacity of the evaporator (33) can be adjusted according to the cooling load of the evaporator (33).
  • the opening degree control unit (80c) first compares the intermediate superheat degree (intermediate SH) with the target refrigerant superheat degree (target intermediate SH) in step St1. When the state of “intermediate SH ⁇ target intermediate SH” continues for 30 seconds or more, the process proceeds to St2 and the opening degree of the supercooling expansion valve (48) is decreased by 1 pls. On the other hand, if “intermediate SH ⁇ target intermediate SH” in step St1, the routine proceeds to St3.
  • step St3 the intermediate superheat degree (intermediate SH) and the target refrigerant superheat degree (target intermediate SH) + ⁇ T are compared, and when the state of “intermediate SH> target intermediate SH + ⁇ T” continues for 30 seconds or more, Shifting to St4, the opening degree of the supercooling expansion valve (48) is increased by 1 pls.
  • step St5 the opening degree of the supercooling expansion valve (48) is maintained at the current state.
  • the intermediate superheat degree (intermediate SH) is within a predetermined range based on the target refrigerant superheat degree (target intermediate SH) (target intermediate SH ⁇ intermediate SH ⁇ target intermediate SH + ⁇ T).
  • target intermediate SH target refrigerant superheat degree
  • target intermediate SH target refrigerant superheat degree
  • a supercooling expansion valve (48) whose opening degree can be freely adjusted is adopted as the pressure reducing mechanism of the supercooling bypass passage (23), and the supercooling expansion valve (48)
  • the controller (80) controls the refrigerant flow rate in the supercooling bypass channel (23) according to the operating state, the refrigerant flow rate in the supercooling bypass channel (23) in the cooling operation is It becomes possible to adjust appropriately according to.
  • the target refrigerant superheat degree output unit (80d) constituting the target changing unit is intermediate between the opening degree control unit (84a) according to the change in the operating state of the cooling operation.
  • the refrigerant flow rate of the supercooling bypass passage (23) can be easily changed according to the operating state of the cooling operation.
  • the opening degree of the supercooling expansion valve (48) is adjusted by the opening degree control unit (80c) so that the intermediate superheat degree (intermediate SH) is within a predetermined target range.
  • the opening degree control unit (80c) By controlling this, wetting of the refrigerant after passing through the secondary passage (46) of the plate heat exchanger (44) can be prevented. Accordingly, it is possible to prevent liquid compression by avoiding introduction of wet refrigerant into the compression chamber in the intermediate pressure state of the compressor (30).
  • the cooling capacity adjustment section (80a) is provided, so that the cooling of the evaporator (33) is performed according to the cooling load of the evaporator (33) during the cooling operation.
  • Ability can be adjusted.
  • an opening degree control unit (80c) and an increase signal output unit (80f) are provided, and the amount of refrigerant flowing into the plate heat exchanger (44) according to the decrease in the cooling load of the evaporator (33) is controlled.
  • the cooling capacity is increased by increasing the amount of refrigerant flowing into the plate heat exchanger (44) in accordance with the increase in the cooling load of the evaporator (33). It can be increased to sufficiently cool the interior.
  • the stable state (the internal temperature and the set temperature) in which the cooling load of the evaporator (33) has decreased.
  • the temperature difference between the main circuit (21) and the liquid refrigerant in the main circuit (21) is supercooled by passing the refrigerant through the supercooling bypass passage (23) even in a state where the temperature difference between the main circuit (21) is small, for example, Since the capacity is unnecessarily large, the internal temperature falls below the lower limit temperature and the compressor (30) stops. Thereby, there is a possibility that the number of times of switching between starting and stopping of the compressor (30) increases and energy consumption increases.
  • the target refrigerant superheat degree (target intermediate SH) is changed to an extremely high value (for example, 20 ° C.) when the cooling load is reduced to a stable state.
  • the supercooling expansion valve (48) is almost fully closed, and the refrigerant does not flow through the supercooling bypass passage (23), and the liquid refrigerant in the main circuit (21) is excessive in the plate heat exchanger (44). It will not be cooled. Therefore, according to the container refrigeration apparatus (10), even when the compressor (30) is configured to stop when the internal temperature falls below the lower limit temperature, the compressor (30) is activated. It is possible to suppress an increase in energy consumption by suppressing an increase in the number of times of stop switching.
  • the controller (80) includes an operation state determination unit (81) for determining an operation state during the cooling operation, a compressor control unit (82) for controlling the rotation speed of the compressor (30), a main expansion valve ( A main expansion valve control section (83) for controlling the opening degree of 32) and a supercooling expansion valve control section (84) for controlling the opening degree of the supercooling expansion valve (48).
  • the operation state determination unit (81) determines the operation state during the cooling operation.
  • four states startup, intermediate wetness, pull-down, and stability
  • the start-up operation is performed until a predetermined time elapses from the start of the operation, and the main operation is performed after the start-up operation ends. While the start-up operation is being performed, the operation state is the start state.
  • the operation state of the actual operation includes a normal state and an intermediate wet state (wet state), and the normal state is further divided into a pull-down state (high load state) and a stable state (low load state).
  • the determination operation of each operation state by the operation state determination unit (81) will be described in detail.
  • the operation state determination unit (81) first determines in step St11 whether or not it is in the activated state.
  • the operation state determination unit (81) is within 10 minutes from the start of the compressor (30), or 10 minutes from a change in operation by changing the set temperature (for example, change from the refrigeration mode to the refrigeration mode). If it is within the range, the process proceeds to step St12, and it is determined that the operation state is the start state (during start operation). If a driving
  • step St13 the operation state determination unit (81) determines that the intermediate pressure refrigerant on the outlet side of the secondary passage (46) of the plate heat exchanger (44) It is determined whether or not an intermediate wet state satisfying a predetermined wet condition is satisfied.
  • the operating state determination unit (81) is a refrigerant on the outflow side of the secondary passage (46) of the plate heat exchanger (44) when the superheat degree of the refrigerant discharged from the compressor (30) is less than 10 ° C.
  • intermediate superheat When the degree of superheat (hereinafter simply referred to as “intermediate superheat (intermediate SH)”) is less than 3 ° C., the intermediate pressure on the outflow side of the secondary passage (46) of the plate heat exchanger (44) It is determined that the predetermined condition that the refrigerant gets wet is satisfied, and the process proceeds to step St14, where it is determined that the operation state is the intermediate wet state. If a driving
  • the degree of superheat of the refrigerant discharged from the compressor (30) is obtained by subtracting the saturation temperature corresponding to the high pressure detected by the high pressure sensor (60) from the value detected by the discharge temperature sensor (63).
  • Is calculated by The intermediate superheat degree (intermediate SH) is a value obtained by subtracting the refrigerant temperature on the inflow side from the refrigerant temperature on the outflow side of the secondary passage (46) of the plate heat exchanger (44). It is calculated by subtracting the detection value of the inflow temperature sensor (65) from the detection value of 66).
  • step St15 the operation state determination unit (81) determines whether or not the cooling load of the evaporator (33) is in a pull-down state that is a predetermined value or more.
  • the operation state determination unit (81) is configured such that the internal temperature is not within the set temperature range (out range), or the internal temperature is within the set temperature range (in range) within 20 minutes, or If it is within 10 minutes from the thermo-ON or within 10 minutes from the end of the defrost operation, it is determined that the cooling load of the evaporator (33) is greater than or equal to a predetermined value, and the process proceeds to step St16. to decide. If a driving
  • step St15 the operation state determination unit (81) determines that the cooling load of the evaporator (33) is less than the predetermined value, and proceeds to step St17, where the operation state is stable. Judge that there is. If a driving
  • the compressor control unit (82) controls the rotation speed of the compressor (30) so that the internal temperature becomes constant.
  • the detected value of the suction temperature sensor (70) is the internal temperature in the refrigeration mode where the set temperature is -10.0 ° C or lower, and the blowout temperature sensor (in the refrigeration mode where the set temperature is -9.9 ° C or higher).
  • the detected value of 71) is the internal temperature.
  • the main expansion valve control unit (83) controls the main expansion valve so that the superheat degree of the refrigerant sucked by the compressor (30) (hereinafter simply referred to as “superheat degree (SH)”) is within a predetermined target range. (32) is configured to control the opening degree.
  • the degree of superheat of the refrigerant sucked by the compressor (30) is obtained by subtracting the saturation temperature corresponding to the low pressure detected by the low pressure sensor (62) from the value detected by the suction temperature sensor (64). Is calculated by Further, the predetermined target range of the degree of superheat (SH) may be changed according to the operation state determined by the operation state determination unit (81).
  • the supercooling expansion valve controller (84) is configured to control the opening degree of the supercooling expansion valve (48) so that the intermediate superheat degree (intermediate SH) falls within a predetermined target range.
  • the supercooling expansion valve control unit (84) includes an opening degree control unit (84a), a target range changing unit (target changing unit) (84b), a control speed changing unit (84c), And a quantity changing unit (84d).
  • the opening degree control unit (84a) feedback-controls the opening degree of the supercooling expansion valve (48) so that the intermediate superheat degree (intermediate SH) is within a predetermined target range (L1 ⁇ intermediate SH ⁇ H1). It is configured. Specific opening degree control will be described later.
  • the target range changing unit (84b) is in an operating state in which a predetermined target range of the intermediate superheat degree (intermediate SH) in the feedback control by the opening degree control unit (84a) is determined by the operating state determining unit (81). It is configured to change accordingly.
  • the said control speed change part (84c) is comprised so that the control speed in the feedback control by the said opening degree control part (84a) may be changed according to the driving
  • the control amount changing unit (84d) is configured to change the control amount in the feedback control by the opening degree control unit (84a) according to the operating state determined by the operating state determining unit (81). .
  • the third on-off valve (53) is closed, and the first on-off valve (47) and the second on-off valve (49) are open.
  • the refrigerant discharged from the compressor (30) is condensed by the condenser (31), then decompressed by the main expansion valve (32), and evaporated by the evaporator (33). After that, it returns to the compressor (30). This refrigerant circulation is repeated. Then, the internal air is cooled by the evaporator (33), and the cooling air is supplied into the internal space by the internal fan (36).
  • defrosting is performed to open the third on-off valve (53) and close the main expansion valve (32) and the discharge pressure adjustment valve (38).
  • the high-temperature refrigerant gas discharged from the compressor (30) is supplied to the evaporator (33), and the frost in the evaporator (33) is removed.
  • the opening degree control unit (84a) of the supercooling expansion valve control unit (84) is configured so that the intermediate superheat degree (intermediate SH) is within a predetermined target range (L1 ⁇ intermediate SH ⁇ H1). Feedback control of the opening of (48).
  • the opening degree control unit (84a) of the supercooling expansion valve control unit (84) lowers the intermediate superheat degree (intermediate SH) and the lower limit of the predetermined target range. It is compared with the value L1, and it is determined whether or not the state of “intermediate SH ⁇ L1” has continued for a predetermined time T1 or more. When the state of “intermediate SH ⁇ L1” continues for the predetermined time T1 or more, the opening degree of the supercooling expansion valve (48) is decreased by P1 (step St22).
  • the intermediate superheat degree (intermediate SH) is compared with the upper limit value H1 of the predetermined target range, and “intermediate SH> H1 It is determined whether or not the state of "" continues for a predetermined time T2 or more (step St23).
  • the degree of opening of the supercooling expansion valve (48) is increased by P2 (step St24).
  • the opening degree of the supercooling expansion valve (48) is maintained (step St25).
  • the opening degree control unit (84a) repeats the above steps St21 to St25 so that the intermediate superheat degree (intermediate SH) is within a predetermined range (L1 ⁇ intermediate SH ⁇ H1). Control the opening of (48).
  • a predetermined target range of the intermediate superheat degree (intermediate SH) is set by the target range changing unit (84b) of the supercooling expansion valve control unit (84) according to the operating state of the cooling operation. Is changed.
  • the target range changing unit (84b) sets the predetermined target range of the intermediate superheat degree (intermediate SH) in the feedback control by the opening degree control unit (84a) to the activated state.
  • the target range changing unit (84b) sets the predetermined target range of the intermediate superheat degree (intermediate SH) in the feedback control by the opening degree control unit (84a) to the activated state.
  • 5 ° C to 15 ° C in the case of pull-down in the range of 0 ° C to 10 ° C in the case of pull-down, in the range of 10 ° C to 15 ° C in the case of intermediate wetness, in the case of stable state Change to a range of 3 ° C to 13 ° C.
  • the target range changing unit (84b) changes the target range of the intermediate superheat degree (intermediate SH) to a relatively high range and closes and controls the supercooling expansion valve (48). This prevents the refrigerant from getting wet after passing through the secondary passage (46), and avoids liquid compression due to the introduction of the wet refrigerant into the compression chamber in the intermediate pressure state of the compressor (30). Can do.
  • the lower limit value of the target range of the intermediate superheat degree in the starting state is set lower than the lower limit value of the target range of the intermediate wet state described later in the secondary state in the starting state (starting operation). This is to ensure the refrigerant flow rate in the subcooling bypass passage (23) to the extent that the liquid refrigerant can be supercooled while preventing the refrigerant from getting wet after passing through the side passage (46).
  • the target range of the intermediate superheat degree (intermediate SH) in the activated state it is possible to prevent the refrigerant from getting wet while increasing the cooling capacity in the evaporator (33).
  • the target range changing unit (84b) determines the intermediate superheat degree when the operation state in the main operation after the start-up operation (start-up state) is not a normal state (pull-down state, stable state) but an intermediate wet state.
  • the target range of (intermediate SH) is changed to a range higher than that in the normal state.
  • the degree of opening of the supercooling expansion valve (48) is decreased, the degree of intermediate superheat (intermediate SH) is increased, the wet state of the refrigerant is avoided, and the refrigerant flow rate in the supercooling bypass path (23) is decreased. To do. Therefore, it is possible to suppress the wet compression of the refrigerant in the compression chamber in the intermediate pressure state of the compressor (30) and liquid compression.
  • the opening degree of the supercooling expansion valve (48) is controlled so that the intermediate superheat degree (intermediate SH) is the same in the case where the operation state is the pull-down state and the case where the operation state is the stable state,
  • the cooling capacity of the evaporator (33) will be insufficient when it is in the state, and there is a possibility that the cooling capacity of the evaporator (33) will be excessive when it is in the stable state.
  • the target range changing unit (84b) has an opening degree control unit (84a) depending on whether the operation state is a pull-down state or a stable state in the main operation after the start-up operation (start-up state) ends.
  • the target range of the intermediate superheat degree (intermediate SH) is changed. Specifically, for example, when the operating state changes from the pull-down state to the stable state, the target range changing unit (84b) changes the target range of the intermediate superheat degree (intermediate SH) to a higher range than the pull-down state. Thereby, the opening degree of the supercooling expansion valve (48) is decreased, and the flow rate of the refrigerant flowing into the secondary side passage (46) of the plate heat exchanger (44) is decreased.
  • the target range changing unit (84b) changes the target range of the intermediate superheat degree (intermediate SH) to a lower range than the stable state.
  • the opening degree of a supercooling expansion valve (48) increases, and the refrigerant
  • the cooling amount of the liquid refrigerant in the main circuit (21) increases, the cooling capacity of the evaporator (33) can be increased, and the interior can be cooled with high cooling capacity.
  • the target range of the intermediate superheat degree (intermediate SH) by the target range changing unit (84b), the cooling capacity of the evaporator (33) is adjusted according to the cooling load of the evaporator (33). be able to. Therefore, energy efficiency can be improved.
  • control of the feedback control by the opening control unit (84a) is performed by the control speed changing unit (84c) of the supercooling expansion valve control unit (84) according to the operating state of the cooling operation.
  • the speed is changed according to the driving state.
  • the control speed changing unit (84c) determines the determination time (predetermined time T1) in step St21 of feedback control (see FIG. 6) by the opening degree control unit (84a) and The control speed is changed by changing the determination time (predetermined time T2) in step St23. More specifically, the control speed is increased by shortening each determination time, while the control speed is reduced by increasing each determination time.
  • the control speed changing unit (84c) sets the determination time (predetermined time T1) in step St21 of the feedback control (see FIG.
  • step St23 by the opening degree control unit (84a) to 5 seconds in the start-up state, pull-down state Is changed to 60 seconds, 20 seconds for the intermediate wet state, and 240 seconds for the stable state, while the determination time (predetermined time T2) in step St23 is set to 5 seconds for the activated state.
  • the pull-down state the time is changed to 60 seconds, in the intermediate wet state, 20 seconds, and in the stable state, the time is changed to 180 seconds.
  • the control speed changing unit (84c) changes each of the predetermined time T1 and the predetermined time T2 of the opening degree control unit (84a) to 5 seconds, which is the shortest determination time, in the startup state immediately after the start of operation. Change the control speed to the highest speed.
  • the opening degree control of the supercooling expansion valve (48) closely follows the change of the intermediate superheat degree (intermediate SH)
  • the intermediate superheat degree (intermediate SH) is quickly converged within a predetermined target range. Can be made.
  • the control speed changing unit (84c) controls the opening when the operation state in the main operation after the start-up operation (start-up state) is not a normal state (pull-down state, stable state) but an intermediate wet state.
  • Each of the predetermined time T1 and the predetermined time T2 of the part (84a) is changed to 20 seconds shorter than that in the normal state, and the control speed is changed to a higher speed than that in the normal state.
  • the intermediate superheat degree (intermediate SH) increases rapidly, and the wet state of the refrigerant is quickly avoided, and the refrigerant flow rate in the supercooling bypass passage (23) decreases quickly. Therefore, it is possible to suppress the wet compression of the refrigerant in the compression chamber in the intermediate pressure state of the compressor (30) and liquid compression.
  • the opening degree control of the supercooling expansion valve (48) by the opening degree control unit (84a) is delayed with respect to the change in the intermediate superheat degree (intermediate SH), and the intermediate superheat degree is delayed.
  • intermediate SH is greatly deviated from the target range, so that the liquid refrigerant in the main circuit (21) cannot be supercooled, or wet refrigerant is introduced into the compressor (30).
  • the opening control of the supercooling expansion valve (48) is sensitively followed by a slight change in the intermediate superheat degree (intermediate SH), and the evaporator (33 ),
  • the behavior of the refrigerant in the main circuit (21) may become unstable.
  • the control speed changing unit (84c) changes the speed of feedback control by the opening degree control unit (84a) depending on whether the operation state is a pull-down state or a stable state. Specifically, for example, when the driving state changes from the pull-down state to the stable state, the predetermined time T1 of the opening degree control unit (84a) is changed from 60 seconds to 240 seconds and the predetermined time T2 is changed from 60 seconds to 180 seconds. It is changed and the control speed is reduced. As a result, the opening degree control of the supercooling expansion valve (48) does not follow the sensitivity to a slight change in the intermediate superheat (intermediate SH), so that the refrigerant behavior in the main circuit (21) is stabilized. Can be maintained.
  • the predetermined time T1 of the opening degree control unit (84a) is changed from 240 seconds to 60 seconds and the predetermined time T2 is changed from 180 seconds to 60 seconds. Will increase.
  • the opening degree control of the supercooling expansion valve (48) comes to follow the slight change of the intermediate superheat degree (intermediate SH) sensitively, the intermediate superheat degree (intermediate SH) is greatly increased from the target range. It can be prevented from coming off. Therefore, it is possible to ensure the supercooling of the liquid refrigerant in the main circuit (21), and it is possible to prevent the refrigerant in the supercooling bypass path (23) from getting wet and prevent the compressor (30) from being damaged.
  • control in the feedback control by the opening degree control unit (84a) is performed by the control amount changing unit (84d) of the supercooling expansion valve control unit (84) according to the operation state of the cooling operation. The amount is changed.
  • the control amount changing unit (84d) performs steps St22 and St24 in FIG. 6 in the “pre-stabilization stage” from the start state to the stable state.
  • the opening change amounts P1 and P2 are each changed to 5 pls, and in the “post-stabilization stage” from the time when the stable state is reached to the start-up state again, the opening change amounts P1 and P2 in steps St22 and St24 in FIG. Change to 1 pls. That is, during the period from the start state to the stable state, control is performed so that the control amount is increased and the stable state is quickly reached.
  • the control amount is decreased, and the opening degree change of the supercooling expansion valve (48) follows the change in the intermediate superheat degree (intermediate SH) sensitively and the stable state is impaired. Control to not.
  • the container refrigeration apparatus (10) also employs a supercooling expansion valve (48) whose opening degree can be freely adjusted as a pressure reducing mechanism for the supercooling bypass path (23), as in the first embodiment,
  • a controller (80) for controlling the supercooling expansion valve (48) so that the refrigerant flow rate of the supercooling bypass passage (23) is adjusted according to the operating state the supercooling bypass passage (23 ) Can be appropriately adjusted according to the operating state.
  • the target change part (84b) is the target range of the intermediate superheat degree (intermediate SH) of an opening degree control part (84a) according to the change of the driving
  • the refrigerant flow rate of the supercooling bypass passage (23) can be easily changed according to the operating state of the cooling operation.
  • the opening degree of the supercooling expansion valve (48) is adjusted by the opening degree control unit (84a) so that the intermediate superheat degree (intermediate SH) is within a predetermined target range.
  • the opening degree control unit (84a) By controlling this, wetting of the refrigerant after passing through the secondary passage (46) of the plate heat exchanger (44) can be prevented. Accordingly, it is possible to prevent liquid compression by avoiding introduction of wet refrigerant into the compression chamber in the intermediate pressure state of the compressor (30).
  • the target changing unit (84b) is the intermediate superheat degree (intermediate SH) of the opening degree control unit (84a).
  • the opening degree of the supercooling expansion valve (48) can be reduced.
  • the intermediate superheat degree (intermediate SH) can be increased to eliminate the wet state of the refrigerant, and the refrigerant flow rate in the supercooling bypass passage (23) can be reduced. Therefore, a large amount of wet refrigerant can be prevented from being introduced into the compression chamber in the intermediate pressure state of the compressor (30), and liquid compression can be avoided.
  • the target changing unit (84b) causes the intermediate superheat degree (84a) of the opening degree control unit (84a) to be different depending on whether the operation state is the pull-down state or the stable state.
  • the target range of the intermediate SH By changing the target range of the intermediate SH), the interior can be cooled with a high cooling capacity when the operation state is a pull-down state, and unnecessarily cooling capacity when the operation state is a stable state. Can be prevented from increasing. That is, the cooling capacity of the evaporator (33) can be adjusted according to the cooling load of the evaporator (33). Therefore, energy efficiency can be improved.
  • the container refrigeration apparatus configured to stop the compressor (30) when the internal temperature falls below the lower limit temperature
  • the compressor (30) The number of times of switching between activation and stop increases and energy consumption increases.
  • the container refrigeration apparatus (10) since the cooling capacity is not increased unnecessarily in a stable state, the number of times of switching between starting and stopping of the compressor (30) is reduced and energy consumption is reduced. Can be suppressed.
  • the target change unit (84b) sets the target of the intermediate superheat degree (intermediate SH) of the opening degree control unit (84a).
  • the range is changed to a range higher than the normal state, and the control speed changing unit (84c) changes the control speed of the opening degree control unit (84a) to a higher speed than the normal state.
  • the intermediate superheat degree (intermediate SH) can be increased quickly so that the wet state of the refrigerant can be quickly eliminated, and the refrigerant flow rate in the supercooling bypass passage (23) can be reduced quickly. Therefore, the intermediate wet state can be quickly eliminated.
  • the control speed changing unit (84c) performs feedback control of the opening degree control unit (84a) depending on whether the operation state is a pull-down state or a stable state. We are going to change the speed. Thereby, when the operation state is a stable state, the behavior of the refrigerant in the main circuit (21) can be maintained in a stable state. On the other hand, when the operation state is a pull-down state, it is possible to prevent the intermediate superheat degree (intermediate SH) from greatly deviating from the target range, and therefore ensure that the liquid refrigerant in the main circuit (21) is supercooled. In addition, it is possible to prevent the compressor (30) from being damaged by preventing the refrigerant in the supercooling bypass (23) from getting wet.
  • Modification 1 of Embodiment 2 The container refrigeration apparatus (10) of the first modification is obtained by partially changing the control by the opening degree control unit (84a) of the controller (80) of the second embodiment. Specifically, in the first modification, the opening degree control unit (84a) changes the rotation speed of the compressor (30) in addition to the feedback control when the operation state in the main operation is a pull-down state. Based on this, feedforward control is performed.
  • the compressor (30) is comprised by the compressor control part (82) so that the rotation speed of a compressor (30) may be controlled so that the internal temperature becomes set temperature.
  • the compressor (30) is configured such that the rotational speed changes according to the cooling load of the evaporator (33) (the thermal load in the warehouse, that is, the required cooling amount).
  • the cooling load of the evaporator (33) changes suddenly for some reason, the control is delayed in the feedback control, and the intermediate superheat (intermediate SH) may be greatly deviated from the target range.
  • the operation state is a pull-down state
  • the change in the cooling load of the evaporator (33) is large, so that the feedback control by the opening degree control unit (84a) may be delayed.
  • the opening degree control unit (84a) feeds based on the change in the rotation speed of the compressor (30) in addition to the feedback control.
  • the configuration is such that forward control is performed.
  • the supercooling expansion valve (48) predicts the change of the intermediate superheat degree (intermediate SH) based on the change of the rotation speed of the compressor (30) by the opening degree control unit (84a), and the intermediate superheat The degree (intermediate SH) is controlled in advance so as not to greatly deviate from the target range.
  • the opening degree control unit (84a) is in a state where “intermediate SH ⁇ L1” in step St21 of the feedback control (see FIG. 6). Even if is not continued for the predetermined time T1 or longer, the process proceeds to step St22, and the opening degree of the supercooling expansion valve (48) is decreased by P1.
  • the opening degree control unit (84a) is in a state where “intermediate SH> H1” in step St23 of the feedback control (see FIG. 6) for a predetermined time T2. Even if not continued, the process proceeds to step St24, and the opening degree of the supercooling expansion valve (48) is increased by P2.
  • the opening degree control unit (84a) changes the rotation speed of the compressor (30) in addition to the feedback control.
  • feedforward control it is possible to prevent the intermediate superheat degree (intermediate SH) from greatly deviating from the target range. Accordingly, the liquid refrigerant in the main circuit (21) can be preferably supercooled in the pull-down state.
  • the container refrigeration apparatus (10) according to the second modification is obtained by partially changing the control by the controller (80) according to the second embodiment.
  • the controller (80) is configured such that the first on-off valve (47) on the inflow side of the supercooling bypass passage (23) when the operation state in the main operation of the refrigeration operation is a stable state. Is controlled to be in a closed state, and the opening degree control by the opening degree control unit (84a) is stopped.
  • the compressor (30) is configured to stop when the internal temperature falls below the lower limit temperature. Therefore, if the cooling capacity is unnecessarily increased when the operation state in the main operation of the refrigeration operation is stable, the number of times of switching between the start and stop of the compressor (30) increases, which may increase the energy consumption. There is.
  • the controller (80) stops the opening degree control by the opening degree control unit (84a), and the first on-off valve (47) is opened. By closing, inflow of the refrigerant into the supercooling bypass passage (23) is prevented. Thereby, since the liquid refrigerant of the main circuit (21) is not supercooled in the plate heat exchanger (44), it is possible to prevent the cooling capacity of the evaporator (33) from being unnecessarily increased. Therefore, according to the second modification, the increase in energy consumption can be suppressed by reducing the number of times the compressor (30) is activated and stopped.
  • the controller (80) stops the opening degree control by the opening degree control unit (84a) and the first on-off valve (47 ) Is closed to prevent the refrigerant from flowing into the supercooling bypass passage (23).
  • the target range changing unit (84b) causes the opening degree control unit (84a)
  • the target range may be changed to an extremely high value (for example, 15 ° C. to 20 ° C.).
  • the present invention is useful for a container refrigeration apparatus provided with a supercooling heat exchanger.
  • Container refrigeration equipment 21 Main circuit 23 Supercooling bypass (branch) 30 Compressor 31 Condenser 32 Main expansion valve (expansion mechanism) 33 Evaporator 44 Plate heat exchanger (supercooled heat exchanger) 45 Primary channel (primary channel) 46 Secondary passage (secondary passage) 47 1st open / close valve (open / close valve) 48 Supercooling expansion valve 80 Controller (control means) 80c Opening control unit 80d Target refrigerant superheat output unit (target change unit) 80f Increase signal output unit 80g Reduction signal output part 81 Operation state judgment part 84a Opening control unit 84b Target range change part (target change part) 84c Control speed changing part

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

L'invention porte sur un dispositif de réfrigération (10) pour un contenant qui comprend : un circuit principal (21) ; un trajet de dérivation de sur-refroidissement (23) qui diverge à partir d'une canalisation de liquide du circuit principal (21) pour se raccorder à une chambre de compression d'un compresseur (30) et qui comporte un mécanisme de réduction de pression ; et un échangeur de chaleur de sur-refroidissement (44) qui a un passage côté primaire (45) raccordé à la canalisation de liquide du circuit principal (21) et un passage côté secondaire (46) raccordé au côté aval d'un détendeur de sur-refroidissement (48) du trajet de dérivation de sur-refroidissement (23). Le mécanisme de réduction de pression est configuré par le détendeur de sur-refroidissement (48) dont le degré d'ouverture peut être réglé à volonté. L'invention comporte une unité de commande (80) destinée à commander le degré d'ouverture du détendeur de sur-refroidissement (48) de telle sorte que le débit du fluide frigorigène dans le trajet de dérivation de sur-refroidissement (23) est régulé en fonction de l'état de fonctionnement dans une opération de refroidissement de l'intérieur du contenant.
PCT/JP2010/005558 2009-11-25 2010-09-10 Dispositif de réfrigération pour contenant WO2011064927A1 (fr)

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EP2951512A1 (fr) * 2013-01-31 2015-12-09 Carrier Corporation Système frigorifique de transport à compartiments multiples ayant un économiseur
US10260779B2 (en) 2011-06-13 2019-04-16 Aresco Technologies, Llc Refrigeration system and methods for refrigeration
JP7474911B1 (ja) 2023-08-08 2024-04-25 日立ジョンソンコントロールズ空調株式会社 冷凍サイクル装置

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US10414241B2 (en) 2016-06-30 2019-09-17 Emerson Climate Technologies, Inc. Systems and methods for capacity modulation through eutectic plates
US10315495B2 (en) * 2016-06-30 2019-06-11 Emerson Climate Technologies, Inc. System and method of controlling compressor, evaporator fan, and condenser fan speeds during a battery mode of a refrigeration system for a container of a vehicle
US10569620B2 (en) 2016-06-30 2020-02-25 Emerson Climate Technologies, Inc. Startup control systems and methods to reduce flooded startup conditions
EP3862649A4 (fr) * 2018-10-02 2022-01-12 Mitsubishi Electric Corporation Appareil à cycle frigorifique

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JPH1038387A (ja) * 1996-07-23 1998-02-13 Daikin Ind Ltd 空気調和機の運転制御装置
JP2002340422A (ja) * 2001-05-16 2002-11-27 Mitsubishi Heavy Ind Ltd 冷凍ユニットおよびその制御方法
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JP2011252637A (ja) * 2010-06-01 2011-12-15 Panasonic Corp 冷凍サイクル装置及びその制御方法
US10260779B2 (en) 2011-06-13 2019-04-16 Aresco Technologies, Llc Refrigeration system and methods for refrigeration
US10989445B2 (en) 2011-06-13 2021-04-27 Aresco Technologies, Llc Refrigeration system and methods for refrigeration
US11549727B2 (en) 2011-06-13 2023-01-10 Aresco Technologies, Llc Refrigeration system and methods for refrigeration
EP2951512A1 (fr) * 2013-01-31 2015-12-09 Carrier Corporation Système frigorifique de transport à compartiments multiples ayant un économiseur
EP2951512B1 (fr) * 2013-01-31 2022-03-30 Carrier Corporation Système frigorifique de transport à compartiments multiples ayant un économiseur
JP7474911B1 (ja) 2023-08-08 2024-04-25 日立ジョンソンコントロールズ空調株式会社 冷凍サイクル装置

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