EP3604970B1 - Air-conditioning device, railway vehicle air-conditioning device, and method for controlling air-conditioning device - Google Patents

Air-conditioning device, railway vehicle air-conditioning device, and method for controlling air-conditioning device Download PDF

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Publication number
EP3604970B1
EP3604970B1 EP18775602.8A EP18775602A EP3604970B1 EP 3604970 B1 EP3604970 B1 EP 3604970B1 EP 18775602 A EP18775602 A EP 18775602A EP 3604970 B1 EP3604970 B1 EP 3604970B1
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EP
European Patent Office
Prior art keywords
refrigerant
degree
compressor
pressure
air
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EP18775602.8A
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German (de)
English (en)
French (fr)
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EP3604970A1 (en
EP3604970A4 (en
Inventor
Wahei SHINGU
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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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
    • 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
    • F25B49/022—Compressor control arrangements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61D—BODY DETAILS OR KINDS OF RAILWAY VEHICLES
    • B61D27/00—Heating, cooling, ventilating, or air-conditioning
    • 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
    • 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
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
    • 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
    • F25B2600/026—Compressor control by controlling unloaders
    • F25B2600/0262—Compressor control by controlling unloaders internal to the compressor
    • 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
    • F25B2600/2501—Bypass 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the present disclosure relates to an air-conditioning device, a railway vehicle air-conditioner device, and a method for controlling the air-conditioning device.
  • a degree of opening of an expansion valve is adjusted based on a degree of superheat calculated from pressure and temperature of a refrigerant to keep a circulation amount of the refrigerant a proper value in order to enable efficient exchange heat by an indoor heat exchanger.
  • Electronic expansion valves by which the circulation amount of the refrigerant can be precisely controlled are widely used, for example like in JPH1038350A.
  • Other known air-conditioning devices are disclosed in JPS5743171A, JPH11324951, EP0949465A2 , and US20030074910A1 .
  • JPS5743171A discloses an air-conditioning device including a refrigerant circuit in which a compressor, an outdoor heat exchanger, an indoor heat exchanger and an electronic expansion valve are connected to one another via refrigerant piping, the air-conditioning device comprising: a bypass passage communicatively connecting a middle compression chamber and a low pressure space, the middle compression chamber being a chamber to accommodate a refrigerant undergoing compression by the compressor, the low pressure space being a space to accommodate the refrigerant having a pressure lower than a pressure of the refrigerant in the middle compression chamber; a bypass valve to open or close the bypass passage; and a controller.
  • capacity control mechanisms for controlling a compressor capacity are widely applied to air-conditioning devices in order to adjust cooling and heating performance.
  • the capacity control mechanisms include an inverter-type capacity control mechanism that is able to perform stepless control of the capacity of the compressor and a mechanical capacity control mechanism that is able to perform mainly two-stage control of the capacity of the compressor.
  • a change of a capacity of a compressor causes transient fluctuation in compressor suction pressure or refrigerant pressure. For example, a reduction in the capacity of the compressor causes a decrease in an amount of refrigerant discharged from the compressor. As a result, the suction pressor of the compressor increases, thereby causing a temporary increase in a circulation amount of the refrigerant in the indoor heat exchanger. There is a risk that the increase in the circulation amount of the refrigerant in the indoor heat exchanger may cause liquid flood back, in which a portion of the refrigerant that the indoor heat exchanger fails to evaporate returns to the compressor.
  • Such fluctuation is more notably for a compressor equipped with the mechanical capacity control mechanism than with in the inverter-type capacity control mechanism that is able to finely control a rotational frequency.
  • an objective of the present disclosure is to achieve: an air-conditioning device that is able to further suppress occurrence of liquid flood back due to a change of a capacity of the compressor than conventional devices; and an air-conditioning device for railway vehicles.
  • an air-conditioning device includes a compressor, an outdoor heat exchanger, an indoor heat exchanger and an electronic expansion valve that are connected to one another via refrigerant piping to constitute a refrigeration cycle, wherein: the air-conditioning device includes (i) a bypass passage communicatively connecting a middle compression chamber and a low pressure space, the middle compression chamber being a chamber to accommodate a refrigerant undergoing compression by the compressor, the low pressure space being a space to accommodate the refrigerant having a pressure lower than a pressure of the refrigerant in the middle compression chamber, (ii) a bypass valve to open or close the bypass passage, and (iii) a controller to execute degree-of-superheat control in which a degree of opening of the electronic expansion valve is set based on a degree of superheat of a refrigerant; and, based on
  • the air-conditioning device includes a refrigeration circuit in which a compressor, an outdoor heat exchanger, an indoor heat exchanger and an electronic expansion valve are connected to one another via the refrigerant piping, wherein: the air-conditioning device includes a middle compression chamber to accommodate a refrigerant undergoing compression by the compressor, a bypass passage communicating with a low pressure space to accommodate a refrigerant having a pressure lower than a pressure of the refrigerant in middle compression chamber, a bypass valve to open or close the bypass passage, and a controller to execute degree-of-superheat control in which a degree of opening of the electronic expansion valve is set based on a degree of superheat of the refrigerant; and, upon detecting a change request to change a state of the bypass valve from an open state to a closed state, the controller starts facilitation processing in which the degree of opening of the electronic expansion valve is corrected to a value that is greater than the value set by the degree-of-superheat control, and, afterward, the controller changes
  • the degree of opening of the electronic expansion valve is corrected to a value that is less than the value set by the degree-of-superheat control, thereby enabling a decrease in the circulation amount of the refrigerant before a change in the capacity of the compressor has an influence on the fluctuation in the degree of superheat.
  • the device of the present disclosure can suppress occurrence of the liquid flood back due to the change of the capacity of the compressor.
  • An increase in the capacity of the compressor results in an increase in an amount of refrigerant discharged from the compressor, whereby the amount of the refrigerant in the compressor temporarily decreases. Due to the decrease of the amount of the refrigerant in the compressor, a sliding member of the compressor slides with the sliding member in direct contact with another component, whereby there is a possibility of occurrence of an abnormality such as galling.
  • the facilitation processing is started before the open state of the bypass valve is changed to the closed state of the bypass valve, where the facilitation processing is processing in which the degree of opening of the electronic expansion valve is corrected to a value that is greater than the value set by the degree-of-superheat control, and thus the amount of the refrigerant existing in the compressor can be increased.
  • This enables suppression of a sharp decrease of the amount of refrigerant in the compressor due to the change from the open state of the bypass valve to the closed state of the bypass valve. Accordingly, the occurrence of an abnormality such as galling caused by the sliding movement of sliding member that is in direct contact with the other component can be suppressed.
  • the air-conditioning device 10 includes: a compressor 1 to compress a refrigerant; an electronic expansion valve 2 to reduce pressure of the refrigerant; an outdoor heat exchanger 3 to function as a condenser during a cooling operation and to exchange heat between outdoor air and the refrigerant; an indoor heat exchanger 4 to function as an evaporator during the cooling operation and to exchange heat between indoor air and the refrigerant; and a controller 7 to control these components.
  • the controller 7 is connected to a room temperature sensor 14 to measure a temperature in a room equipped with the air-conditioning device 10 and to a remote controller 15 by which a user performs on-off control of the air-conditioning device 10 and inputs a desired set temperature To.
  • the compressor 1 compresses the refrigerant sucked into the compressor, and discharges the refrigerant in the high temperature and high pressure state.
  • the compressor 1 of the present embodiment is configured as a scroll compressor that includes a mechanical capacity control mechanism 60, and is operated at a predetermined constant frequency of compression per unit of time (seconds).
  • the mechanical capacity control mechanism 60 is described later in detail.
  • the outdoor heat exchanger 3 is an outdoor-air heat exchanger to exchange heat between outdoor air taken from outside the room and the refrigerant, and makes heat move from the refrigerant to ambient air during the cooling operation.
  • the indoor heat exchanger 4 is an indoor-air heat exchanger to exchange heat between indoor air and the refrigerant, and makes heat move from indoor air to the refrigerant during the cooling operation.
  • the electronic expansion valve 2 is a component to reduce the pressure of the refrigerant to expand the refrigerant so that the refrigerant has a low temperature and a low pressure, and is an expansion valve for which the degree of opening is variably controllable.
  • a linear expansion valve LEV is used as the electronic expansion valve 2.
  • the compressor 1, the outdoor heat exchanger 3, the electronic expansion valve 2, and the indoor heat exchanger 4 are connected to one another via a refrigerant piping 20 in which the refrigerant flows, thus forming a refrigerant circuit in which the refrigerant circulates.
  • the refrigerant circulates in the refrigerant piping 20 in a direction indicated by a solid arrow in FIG. 1 .
  • the refrigerant is compressed by the compressor 1, so that the refrigerant turns into a gas having a high temperature and a high pressure.
  • the pressure of the refrigerant is decreased by expanding the refrigerant by the electronic expansion valve 2, so that the refrigerant is in a two-phase state of the refrigerant having a low temperature and low pressure.
  • the refrigerant is evaporated and gasified by the indoor heat exchanger 4, and then returns to the compressor 1.
  • the indoor air passes through the indoor heat exchanger 4, the indoor air exchanges heat with the low-temperature refrigerant, thereby decreasing temperature of the indoor air, and then the indoor air is supplied to the interior of the room.
  • a pipe of the refrigerant piping 20 that connects the compressor 1, the outdoor heat exchanger 3, and the electronic expansion valve 2 to one another is referred to as a high pressure refrigerant pipe 26 through which the high pressure refrigerant discharged from the compressor 1 passes.
  • a pipe of the refrigerant piping 20 that connects the electronic expansion valve 2, the indoor heat exchanger 4 and the compressor 1 to one another is referred to as a low pressure refrigerant pipe 25 through which the refrigerant having a pressure lower than the pressure in the higher pressure refrigerant pipe 26 passes.
  • the high pressure refrigerant pipe 26 is connected to a high pressure control refrigerant line 21 into which a portion of the high-pressure refrigerant discharged from the compressor 1 flows.
  • the low pressure refrigerant pipe 25 is connected to a low pressure control refrigerant line 22 into which a portion of the low-pressure refrigerant sucked by the compressor 1 flows.
  • the high pressure control refrigerant line 21 and the low pressure control refrigerant line 22 are connected to a control pressure introduction pipe 23 that communicates with the capacity control mechanism 60.
  • a high pressure control valve 8 is disposed in the high pressure control refrigerant line 21, and a low pressure control valve 9 is disposed in the low pressure control refrigerant line 22.
  • Each of the high pressure control valve 8 and the low pressure control valve 9 includes a solenoid valve that can open or close to switch between circulation and non-circulation of the refrigerant.
  • Both the high pressure control valve 8 and the low pressure control valve 9 are connected to the controller 7 and are opened or closed based on a command from the controller 7.
  • the controller 7 opens one of the high pressure control valve 8 and the low pressure control valve 9 is opened and closes the other.
  • the high pressure control valve 8 is closed and the low pressure control valve 9 is opened, a portion of the low-temperature refrigerant flowing in the low temperature refrigerant pipe 25 flows into the control pressure introduction pipe 23.
  • the high pressure control valve 8 is opened and the low pressure control valve 9 is closed, a portion of the high-temperature refrigerant flowing in the high temperature refrigerant pipe 26 flows into the control pressure introduction pipe 23.
  • the compressor 1 includes a sealed container 50 forming an outer frame of the compressor 1. Also, the compressor 1 includes a fixed scroll 51 that is provided with, as components disposed in the sealed container 50 and functioning as sliding members for compressing the refrigerant, a fixed spiral-shaped body 54 and an orbiting scroll 52 that is provided with an orbiting spiral-shaped body 55.
  • the fixed spiral-shaped body 54 and the orbiting spiral-shaped body 55 are joined such that the fixed spiral-shaped body 54 and the orbiting spiral-shaped body 55 intermesh with each other, thereby forming compression chambers P.
  • a compression chamber P that is located at the central portion communicates with the high pressure refrigerant pipe 26.
  • the orbiting scroll 52 eccentrically orbits relative to the fixed scroll 51 at a previously predetermined constant speed, and the compression chambers P are gradually reduced in size from outside low-pressure compression chambers toward inside high-pressure compression chambers.
  • the refrigerant that flows through the low pressure refrigerant pipe 25 into the compressor 1 flows from the outside low-pressure compression chambers of the compression chambers P into the compression chambers P and then flows toward the inside high-pressure compression chambers while being compressed by the orbital movement of the orbiting scroll 52. Afterward, the refrigerant is discharged through a discharge path 53 to the high pressure refrigerant path 26.
  • the fixed scroll 51 is provided with the capacity control mechanism 60 that is to control the capacity of the compressor 1.
  • the capacity control mechanism 60 is configured to include (i) a back pressure passage 61 into which either of the low-pressure refrigerant or the high-pressure refrigerant flows from the control pressure introduction pipe 23, (ii) a back pressure chamber 62 housing the bypass valve 64 and communicating with the back pressure passage 61, (iii) a coil spring 63 elastically supporting the bypass valve 64, and (iv) a bypass passage 65 that is formed in the fixed scroll 51 and used for returning, to a low-pressure space, the refrigerant present in the middle compression chamber and undergoing the compression process.
  • the middle compression chamber is freely determined based on a location at which the bypass passage 65 is formed.
  • the low-pressure space is any portion of the inner space of the compressor 1 in which refrigerant exists that has a pressure lower than the pressure of the refrigerant in the middle compression chamber.
  • the low-pressure space may be located outside the compression chambers P or may be a low-pressure compression chamber located nearer to the outside than the middle compression chamber is.
  • the bypass valve 64 is elastically supported by the coil spring 63.
  • the coil spring 63 may be replaced with another elastic body such as a rubber component.
  • Refrigerant pressure in the control pressure introduction pipe 23 and refrigerant pressure in the middle compression chamber act on the above-described bypass valve 64.
  • the bypass valve 64 opens. In this case, a portion of the refrigerant in the middle compression chamber returns through the bypass passage 65 to the low-pressure space.
  • An operation mode in which, by opening the bypass valve 64, a portion of the refrigerant in the middle compression chamber returns to the low-pressure space in this manner is referred to as an unloading (UL) mode.
  • the refrigerant pressure in the control pressure introduction valve 23 becomes higher than the refrigerant pressure in the middle compression chamber, and the bypass valve 64 closes.
  • the compressed refrigerant is discharged to the discharge path 53.
  • An operation mode in which, by closing the bypass valve 64, the whole of the refrigerant in the middle compression chamber is discharged to the discharge path 53 in this manner is referred to as a full-loading (FL) mode.
  • the low-pressure refrigerant pipe 25 is provided with (i) a refrigerant temperature sensor 11 to detect a refrigerant temperature Tm of the refrigerant sucked by the compressor 1 and (ii) a refrigerant pressure sensor 12 to detect a refrigerant pressure Pm of the refrigerant, where the sensor 12 correspond to pressure detecting means recited in claims.
  • the refrigerant temperature sensor 11, the refrigerant pressure sensor 12, the high pressure control valve 8, the low pressure control valve 9, the electronic expansion valve 2, the room temperature sensor 14 and the remote controller 15 are connected to the controller 7.
  • the controller 7 includes a central processing unit (CPU), a read only memory (ROM), a random access memory (RAM) and the like that are not illustrated in the drawings, and stores various types of programs, a function, fixed data and the like that are used for driving the air-conditioning device 10.
  • the controller 7 executes the various types of programs using the above-described function and data, data inputted from various types of sensors, and the like, so that the controller 7 drives the high-pressure control valve 8 and the low-pressure control valve 9 to make the high-pressure control valve 8 and the low-pressure control valve 9 open or close, adjusts a degree of opening of the electronic expansion valve 2, and executes processing for other operations for driving the air-conditioning device 10.
  • the controller 7 calculates a degree SH1 of superheat of the refrigerant flowing into the compressor 1 from (i) the refrigerant temperature Tm detected by the refrigerant temperature sensor 11 and (ii) the refrigerant pressure Pm detected by the refrigerant pressure sensor 12, and then the controller 7 adjusts the degree of opening of the electronic expansion valve 2 based on the calculated degree SH1 of superheat.
  • the controller 7 compares the calculated degree SH1 of superheat with a previously-stored threshold SHT and adjusts the degree of opening of the electronic expansion valve 2 based on a difference between the degree SH1 of superheat and the threshold SHT.
  • the degree SH1 of superheat is greater than the threshold SHT
  • the degree of opening of the electronic expansion valve 2 increases with increased difference between the degree SH1 of superheat and the threshold SHT, so that the degree SH1 of superheat is reduced.
  • the degree SH1 of superheat is less than the threshold STH
  • the greater the difference between the degree SH1 of superheat and the threshold STH is, the more the degree of opening of the electronic expansion valve 2 is reduced, so that the degree SH1 of superheat is increased.
  • SH1 is equal to the threshold STH
  • the threshold SHT is generally set to 5 to 10 °C, without particular limitation.
  • the controller 7 uses the below-described formula (1) to calculate a difference ⁇ T between (i) a temperature Tr detected by the room temperature sensor 14 and (ii) a set temperature To set by a user through the remote controller 15, and then determines an operation mode of the compressor 1 based on this difference ⁇ T.
  • ⁇ T Tr ⁇ To
  • the controller 7 stores the upper limit value Tu of and the lower limit value T1 of the difference ⁇ T. In a case in which the controller 7 determines that the difference ⁇ T is equal to or greater than the upper limit value Tu, the controller 7 makes the compressor 1 to drive in the full-loading mode. On the other hand, in a case in which the controller 7 determines that the difference ⁇ T is less than the lower limit value T1, the controller 7 makes the compressor 1 to drive in the unloading mode. In contrast, in a case in which the difference ⁇ T is not less than the lower limit value T1 and is less than the upper limit value Tu, the controller makes the air-conditioning device 10 to drive in the current operation mode without changing the operation mode.
  • the controller 7 starts restriction processing in which the degree of opening of the electronic expansion valve 2 is corrected, by subtraction, to a degree of opening that is smaller, by a given degree ⁇ a of opening, than a degree of opening set based on the degree SH1 of superheat.
  • the given degree ⁇ a of opening is a degree of opening necessary for suppressing an increase in the amount of the flow of the refrigerant caused by the change from the closed state of the bypass valve 64 to the open state of the bypass valve 64, and the given degree ⁇ a of opening is freely selected.
  • degree of opening of the electronic expansion valve 2 is preferably corrected, by subtraction of the given degree ⁇ a of opening, to a value of a degree of opening at which the electronic expansion valve 2 permits flow of the refrigerant by the amount that corresponds to the lower limit of the heat-exchange capacity of the indoor heat exchanger 4.
  • the given degree ⁇ a of opening is preferably set in consideration of the amount of the refrigerant in the compressor 1.
  • the amount of the refrigerant discharged from the compressor 1 temporarily increases even if the amount of the refrigerant sucked by the compressor 1 remains unchanged, so that the amount of the refrigerant in the compressor 1 is temporarily rapidly reduced.
  • the rapid reduction in the amount of the refrigerant in the compressor 1 causes the orbiting spiral-shaped body 55 to slide directly on the fixed spiral-shaped body 54 without the refrigerant existing therebetween, thereby causing a risk that an abnormality such as galling may occur.
  • the controller 7 changes the operation mode of the compressor 1 to the full-loading mode after executing facilitation processing in which the degree of opening of the electronic expansion valve 2 is corrected by adding a given degree of opening ⁇ b to the degree of opening set based on the degree SH1 of superheat.
  • the given degree of opening ⁇ b is a degree of opening necessary for suppressing a rapid decrease in the amount of the refrigerant in the compressor 1 that is caused by the change from the open state of the bypass valve 64 to the closed state of the bypass valve 64, and the given degree of opening ⁇ b is freely set.
  • the degree of opening of the electronic expansion valve 2 is preferably set to a value at which the electronic expansion valve 2 permits flow of the refrigerant in the amount corresponding to the upper limit of the heat-exchange capacity of the indoor heat exchanger 4, without particular limitation.
  • the controller 7 is taken to calculate the degree SH1 of superheat based on the refrigerant temperature Tm detected by the refrigerant temperature sensor 11 and the refrigerant pressure Pm detected by the refrigerant pressure sensor 12 and then to constantly calculate an appropriate degree of opening of the electronic expansion valve 2 based on this degree SH1 of superheat.
  • the controller 7 Upon starting of the driving of the compressor 1, the controller 7 first calculates, based on the above-described formula (1), the difference ( ⁇ T) between the temperature Tr detected by the room temperature sensor 14 and the set temperature inputted by the user (Step S10).
  • the controller 7 determines whether the calculated difference ⁇ T is equal to or greater than the previously-stored upper limit value Tu (Step S11). In a case in which the controller 7 determines that the difference ⁇ T is less than the upper limit value Tu (No in Step S11), the controller 7 determines whether the difference ⁇ T is less than the lower limit value T1 (Step S12).
  • the controller 7 determines that the difference ⁇ T is not less than the lower limit value T1 (No in Step S12), that is, in a case in which the controller 7 determines that the difference ⁇ T is less than the upper limit value Tu and is equal to or greater than the lower limit value T1, a change of the operation mode of the compressor 1 is not made. In this case, the controller 7 does not make a correction of the degree of opening of the electronic expansion valve 2.
  • the controller 7 changes the operation mode of the compressor 1 to the unloading mode.
  • the controller 7 first determines whether the operation mode of the compressor 1 is the full-loading mode (Step S13).
  • the bypass valve 64 in an open state, so that the controller determines that the compressor 1 is in the unloading mode.
  • the bypass valve 64 is in a closed state, so that the controller determines that the compressor 1 is in the full-loading mode.
  • the determination as to whether the compressor 1 is in the unloading mode or in the full-loading mode is made by determining whether either of the low pressure control valve 9 and the high pressure control valve 8 is in the open state, the determination of the operation mode of the compressor 1 may be made by another publically well-known manner.
  • the determination of the operation mode of the compressor 1 may be made on the basis of the refrigerant pressure Pm in the control pressure introduction pipe 23 or using a sensor to detect opening or closing of the bypass valve 64, without particular limitation, and other publicly-well know manners may be used.
  • the controller 7 determines that the operation mode of the compressor 1 is not the full-loading mode (No in Step S13), that is, in a case in which the controller 7 determines that the operation mode of the compressor 1 is the unloading mode, the operation mode is unchanged, and correction of the degree of opening of the electronic expansion valve 2 is not made.
  • the controller 7 determines that the operation mode of the compressor 1 is the full-loading mode (Yes in Step S13)
  • the controller 7 changes the operation mode of the compressor 1 to the unloading mode (Step S14) and then starts restriction processing (Step S15).
  • the controller 7 corrects the degree of opening of the electronic expansion valve by subtracting the given degree of opening ⁇ a from the degree of opening of the electronic expansion valve 2 that is calculated based on the degree SH1 of superheat, and then the degree of opening of the electronic expansion valve 2 is set to the corrected degree of opening.
  • the controller 7 determines whether an elapsed time period Ta of time elapsed since the start of the restriction processing is equal to or longer than a given time period T1 (Step S16).
  • the given time period T1 is a time period that is sufficient to reduce the refrigerant pressure Pm, and is freely set.
  • the given time period T1 is preferably a period of time taken by a certain amount of refrigerant to pass through the electronic expansion valve 2, where the certain amount of refrigerant corresponds to an amount of refrigerant that is returned from the middle compression chamber to the low-pressure space.
  • Step S16 Upon determination that the elapsed time period Ta is shorter than the given time period T1 (No in Step S16), the restriction processing continues, and upon determination that the elapsed time period Ta is equal to or longer than the given time period T1 (Yes in Step S16), the restriction processing ends (Step S17). That is, the correction of the degree of opening of the electronic expansion valve 2 ends.
  • Step S18 determines, in the above-described manner, whether the compressor 1 is in the unloading mode.
  • Step S18 Upon determination that the compressor 1 is in the unloading mode (Yes in Step S18), on the grounds that the difference ⁇ T is equal to or greater than the upper limit value Tu and the operation mode is the unloading mode, the controller 7 determines that a request to change the operation mode from the unloading mode to the full-loading mode is made.
  • the controller 7 starts facilitation processing before changing the operation mode to the full-loading mode (Step S19).
  • the controller 7 corrects the degree of opening of the electronic expansion valve by adding the given degree of opening ⁇ b to the degree of the opening of the electronic expansion valve 2 calculated based on the degree SH1 of superheat, and then the controller 7 sets the degree of opening of the electronic expansion valve 2 to a degree of opening obtained by the correction.
  • the controller 7 determines whether an elapsed time period Tb of time elapsed since the start of the facilitation processing is equal to or longer than a given time period T2 (Step S20).
  • the given time period T2 is a period of time that it takes for the compressor 1 to secure therein an amount of refrigerant that does not cause malfunction of the compressor 1 despite a rapid increase in an amount of refrigerant discharged from the compressor 1 due to a change of the operation mode, and is freely set.
  • the given time period T2 is preferably a period of time that is takes for the compressor 1 to secure therein an amount of the refrigerant corresponding to the amount of refrigerant that is returned from the middle compression chamber to the low-pressure space.
  • Step S21 Upon determination that the elapsed time period Tb is shorter than the given time period T2 (No in Step S20), the facilitation processing continues. However, upon determination that the elapsed time period Tb is equal to or longer than the given time period T2 (Yes in Step S20), the facilitation processing (Step S21). That is, the controller 7 terminates the correction of the degree of opening of the electronic expansion valve 2. Also, the operation mode of the compressor 1 is changed to the full-loading mode (Step S21).
  • the controller 7 determines that the compressor 1 is not in the unloading mode (No in Step S18), that is, in a case in which the controller 7 determines that the compressor 1 is in the full-loading mode, the operation mode of the compressor 1 is not changed. In this case, the controller 7 does not correct the degree of opening of the electronic expansion valve 2.
  • Step S22 the controller 7 determines whether the operation of the air-conditioning device 10 is finished. In a case in which the controller 7 determines that the operation of the air-conditioning device 10 is finished (Yes in Step S22), the controller 7 terminates this process. In a case in which the controller 7 determines that the air-conditioning device 10 is still in operation (No in Step S22), processing returns to Step S10 and this processing continues.
  • FIG. 4 illustrates one example of each of transitions of (a) the degree of opening of the electronic expansion valve 2, (b) the temperature Tr detected by the room temperature sensor 14 and the set temperature To, (c) the refrigerant pressure Pm detected by the refrigerant pressure sensor 12, and (d) the operation mode of the compressor 1, in a case in which the process illustrated in FIG. 3 is performed.
  • one example of the transition of the refrigerant pressure Pm caused by execution of the above-described restriction processing and facilitation processing is plotted as a solid line, and one example of the transition of the refrigerant pressure Pm without execution of the above-described restriction processing and facilitation processing is plotted as a long dashed double-dotted line.
  • one example of the transition of the operation mode of the compressor 1 caused by execution of the above-described restriction processing and the above-described facilitation processing is plotted as a solid line, and one example of the transition of the operation mode of the compressor 1 without execution of the above-described restriction processing and facilitation processing is plotted as a dash-dotted line.
  • the compressor 1 when the difference ⁇ T between the set temperature To and the detected temperature Tr is equal to or greater than the upper limit value Tu, the compressor 1 is operated in the full-loading mode (times t0 to t1).
  • the controller 7 changes the operation mode of the compressor 1 from the full-loading mode to the unloading mode.
  • the controller 7 starts the restriction processing in which the given angle ⁇ a is subtracted from the degree of opening of the electronic expansion valve 2 calculated based on the degree SH1 of superheat (time t1). This restriction processing continues over the given time period T1 (time t1 to t2).
  • the controller 7 Upon executing the restriction processing, the degree of opening of the electronic expansion valve 2 decreases, thereby causing a reduction in an amount of the refrigerant flowing in the low pressure refrigerant pipe 25. As a result, a temporary rise in the refrigerant pressure Pm is suppressed. After the given time period T1 elapses, the controller 7 terminates the restriction processing (time t2).
  • the controller 7 determines that a request to change the operation mode is made. In this case, before the operation mode is changed from the unloading mode to the full-loading mode, the controller 7 starts the facilitation processing in which the degree of opening of the electronic expansion valve 2 is corrected by adding the given degree ⁇ b of opening to the degree of opening calculated from the degree SH1 of superheat (the time t3). The facilitation processing continues over the given time period T2 (time t3 to t4). The operation mode is maintained as the unloading mode.
  • the controller 7 Upon executing the facilitation processing, the degree of opening of the electronic expansion valve 2 is increased, thereby causing an increase in an amount of the refrigerant flowing in the low pressure refrigerant pipe 25, and thus the refrigerant pressure Pm increases (time t3 to t4).
  • the controller 7 terminates the facilitation processing (time t4). That is, the controller 7 terminates the correction of the degree of opening of the electronic expansion valve 2. Also, the controller 7 changes the operation mode of the compressor 1 from the unloading mode to the full-loading mode.
  • Embodiment 1 as described above can exhibit the following effects.
  • the present embodiment can more preferably suppress occurrence of the situation in which the orbiting spiral-shaped body 55 slides on the fixed spiral-shaped body 54 with the fixed spiral-shaped body 54 and the orbiting scroll 50 directly coming into contact with each other.
  • FIGS. 5 and 6 A method of controlling an air-conditioning device 10 according to Embodiment 2 is described with reference to FIGS. 5 and 6 together with FIGS. 1 to 4 .
  • reference signs that are the same as in Embodiment 1 denote components that are the same, and steps that are the same are assigned step reference numbers that are the same. Accordingly, detailed description of these components and these steps is omitted as appropriate.
  • FIG. 5 illustrates a control flowchart of control of the air-conditioning device 10 according to Embodiment 2. Operation of a controller 7 according to Embodiment 2 is described with reference to FIG. 5 .
  • Steps S15 to S17 of the flowchart of FIG. 3 are replaced with Steps S30 to S34, and the other steps are the same. Accordingly, description of the contents of similar control is omitted.
  • the controller 7 determines whether the refrigerant pressure Pm detected by the refrigerant pressure sensor 12 is equal to or greater than a threshold PI (corresponding to a first given pressure recited in claims) (Step S30). It is preferable that the threshold PI corresponds to a refrigerant pressure at which the refrigerant the amount of which corresponds to the upper limit of the heat-exchange capacity of the indoor heat exchanger 4 passes.
  • the controller 7 determines whether an elapsed time period Tc since a change of the operation mode to the unloading mode is equal to or longer than a given time period T3 (Step S31).
  • the given time period T3 is a period of time for a temporarily-increasing suction pressure to return to a steady state after a change of the operation mode of the compressor 1 to the unloading mode, and is freely set.
  • the given time period T3 is preferably set to a time period during which a certain amount of refrigerant passes through the electronic expansion valve 2, where the certain amount of refrigerant corresponds to an amount of refrigerant that is returned from the middle compression chamber to the low-pressure space.
  • Step S31 In a case in which the controller 7 determines that the elapsed time period Tc of time elapsed since the change of the operation mode to the unloading mode is shorter than the given time period T3 (No in Step S31), processing returns to Step S30. However, in a case in which the controller 7 determines that the elapsed time period Tc since the change of the operation mode to the unloading mode is equal to or longer than the given time period T3 (Yes in Step S31), the processing is terminated for now.
  • Step S32 the controller 7 starts the restriction processing (Step S32). Subsequently, the controller 7 determines whether an elapsed time period Ta since the start of the restriction processing is equal to or longer than the given time period T1 (Step S33). In a case in which the controller 7 determines that the elapsed time period Ta since the start of the restriction processing is less than the given time period T1 (No in Step S33), processing returns to Step S33. In a case in which the controller 7 determines that the elapsed time period Ta since the start of the restriction processing is equal to or longer than the given time period T1 (Yes in Step S33), this processing (Step S34) ends.
  • FIG. 6 illustrates one example of each of transitions of (a) the degree of opening of the electronic expansion valve 2, (b) the temperature Tr detected by the room temperature sensor 14 and the set temperature To, (c) the refrigerant pressure Pm detected by the refrigerant pressure sensor 12, and (d) the operation mode of the compressor 1, in a case in which the process illustrated in FIG. 5 is performed.
  • one example of the transition of the refrigerant pressure Pm caused by execution of the above-described restriction processing and facilitation processing is plotted as a solid line, and one example of the transition of the refrigerant pressure Pm without execution of the above-described restriction processing and facilitation processing is plotted as a dashed double-dotted line.
  • one example of the transition of the operation mode of the compressor 1 caused by execution of the above-described restriction processing and facilitation processing is plotted as a solid line, and one example of the transition of the operation mode of the compressor 1 without execution of the above-described restriction processing and facilitation processing is plotted as a dash-dotted line.
  • the controller 7 monitors the refrigerant pressure Pm over the given time period T3 (time t1 to t7).
  • the controller 7 starts the restriction processing in which a correction is made by subtracting the given degree ⁇ a of opening from the degree of opening of the electronic expansion valve 2 calculated based on the degree SH1 of superheat (time t5). This restriction processing continues over the given time period T1 (time t5 to t6).
  • the present embodiment can exhibit the following effect in addition to the effects described in Embodiment 1.
  • the restriction processing is started, and, in a case in which the refrigerant pressure Pm is less than the threshold PI, the restriction processing is not started. Accordingly, the restriction processing is started even if the refrigerant pressure Pm is sufficiently low, thereby suppressing an excessive reduction in an amount of the circulating refrigerant. Accordingly, a reduction in the cooling capacity can be suppressed.
  • FIG. 7 A method of controlling an air-conditioning device 10 according to Embodiment 3 is described with reference to FIG. 7 together with FIGS. 1 to 3 .
  • reference signs that are the same as in Embodiment 1 denote components that are the same, and steps that are the similar are assigned step reference numbers that are the same, and accordingly detailed description of such is omitted as appropriate.
  • FIG. 7 is an explanatory drawing illustrating a control flowchart of control of the air-conditioning device 10 according to Embodiment 3. Operation of a controller 7 according to Embodiment 3 is described with reference to FIG. 7 .
  • processing for starting up the air-conditioning device 10 (steps S1 to S3) is added to the flowchart of FIG. 3 , and the other steps of the flowchart of FIG. 7 are the same as those in FIG. 3 . Accordingly, description of the contents of control that are similar is omitted.
  • the refrigerant in the compressor 1 has a low temperature, so that the refrigerant in the compressor 1 is in a state in which the refrigerant easily dissolves into lubricant.
  • so-called oil foaming is a phenomenon in which the refrigerant dissolving in the lubricant rapidly evaporates due to a reduction in a pressure in the compressor 1 when the compressor 1 is started up. Occurrence of the oil foaming may result in risk that the frothy lubricant in the compressor 1 is discharged to the outside of the compressor 1.
  • the degree of opening of the electronic expansion valve 2 is fixed at a given degree ⁇ c of opening (corresponding to a start-up degree of opening recited in claims) at the time when the air-conditioning device 10 is started up, thereby increasing an amount of the refrigerant flowing into the compressor 1 during the start-up of the air-conditioning device 10, and suppressing a reduction in pressure in the compressor 1.
  • the operation mode of the compressor 1 is set to the unloading mode during the start-up of the air-conditioning device 10, whereby an amount of the refrigerant discharged from the compressor 1 is reduced, and thus a reduction in the pressure in the compressor 1 is more favorably suppressed.
  • the processing at the start of operation of the air-conditioning device 10 according to the present embodiment is described with reference to FIG. 7 .
  • the controller 7 fixes the degree of opening of the electronic expansion valve 2 at the previously-predetermined given degree ⁇ c of opening (Step S1).
  • the given degree ⁇ c of opening is a degree of opening necessary for supplying to the interior of the compressor 1 an amount of the refrigerant that does not cause occurrence of the oil foaming despite a reduction in pressure in the compressor 1 caused by discharging the refrigerant from the compressor 1 during the start-up of the compressor 1.
  • the given degree ⁇ c of opening is most preferably a maximum degree of opening that the electronic expansion valve 2 can have.
  • the controller 7 sets the operation mode of the compressor 1 to the unloading mode (Step S2). Afterward, the controller 7 determines whether an elapsed time period Td since the start of the operation of the air-conditioning device 10 is equal to or longer than a given time period T4 (Step S3).
  • the given time period T4 is a period of time necessary for causing the air-conditioning device to make a transition to a steady state after finishing the start-up of the air-conditioning device 10.
  • the given time period T4 may be set to a previously determined period of time for the degree SH1 of superheat to converge at a certain range after the start-up of the air-conditioning device 10, where such a period of time may be previously found by measurement.
  • the given time period T4 may be set to a previously determined period of time for the refrigerant discharged from the compressor 1 to circulate in the refrigerant piping 20 to return to the compressor 1 again, where such a period of time may be previously found by measurement.
  • Step S3 In a case in which the controller 7 determines that the elapsed time period Td of time elapsed since the start of the operation of the air-conditioning device 10 is shorter than the given time period T4 (No in Step S3), processing returns to return to Step S3. However, in a case in which the controller 7 determines that the elapsed time period Td since the start of the operation of the air-conditioning device 10 is equal to or longer than the given time period T4 (Yes in Step S3), processing proceeds to Step S10.
  • the present embodiment can exhibit the following effect in addition to the effects described in Embodiments 1 and 2.
  • the degree of opening of the electronic expansion valve 2 is fixed at the given degree ⁇ c of opening and the operation mode of the compressor 1 is set to the unloading mode at the time when the air-conditioning device 10 is started up, a reduction in the pressure in the compressor 1 during the start-up of the air-conditioning device 10 can be suppressed. Accordingly, occurrence of liquid flood back and oil foaming during the start-up of the air-conditioning device 10 can be suppressed.
  • Embodiment 4 An air-conditioning device 10 according to Embodiment 4 is described with reference to FIGS. 8 and 9 .
  • Embodiment 4 an example of an application of the air-conditioning device 10 of Embodiment 1 or 2 to a railroad vehicle is described.
  • reference signs that are the same as in Embodiment 1 or 2 denote components that are the same, and steps that are the similar are assigned step reference numbers. Accordingly, detailed description of such components and steps is omitted as appropriate.
  • FIG. 8 is a view illustrating the appearance of a vehicle 70 equipped with the air-conditioning device 10 of the present embodiment.
  • FIG. 8 illustrates a case in which the air-conditioning device 10 is mounted on a roof of the vehicle.
  • the air-conditioning device 10 may be disposed under a floor of the vehicle.
  • the compressor 1 is arranged such that the discharge side of the compressor is located upward so that a center shaft line of the compressor 1 inclines at an inclination angle A relative to a horizontal plane.
  • the inclination angle A is preferably 0° to 15°, more preferably 0° to 10°, and most preferably 0° to 5°.
  • Lubricant 31 for lubricating the fixed spiral-shaped body 54, the orbiting spiral-shaped body 55 and the like is stored in the compressor 1. If the compressor 1 is arranged such that the shaft center line of the compressor 1 is parallel to the horizontal plane for the purpose of the reduction in height of the air-conditioning device, there is a risk that the lubricant 31 together with the compressed refrigerant may discharge into the refrigerant piping 20. Also, in a case in which the liquid flood back occurs, there is a risk that the lubricant 31 may discharge into the refrigerant piping 20.
  • the present embodiment exhibits the following effects in addition to exhibiting effects similar to the effects described in Embodiments 1 to 3.
  • the reduction in height of the air-conditioning device 10 can be achieved and the discharge of the lubricant 31 can be suppressed.
  • an air-conditioning device 10 may include an accumulator 28 disposed in the middle of the refrigerant piping 20 connecting the indoor heat exchanger 4 and the compressor 1, a four-way valve 29 to switch flow passages of the refrigerant, a hot gas bypass 27 to bypass the refrigerant discharged from the compressor 1 to the inflow side of the compressor 1, and a solenoid 32 to switch between passage and non-passage of the refrigerant through the hot gas bypass 27.
  • the refrigerant is compressed by the compressor 1 to become a gas at high temperature and pressure, and then the refrigerant is condensed to be liquefied by the indoor heat exchanger 4. Afterward, the refrigerant is made to expand by using the electronic expansion valve 2 to reduce the pressure of the refrigerant, so that the refrigerant becomes two phases at low temperature and pressure. Afterward, the refrigerant is evaporated and gasified by the outdoor heat exchanger 3, passes through the accumulator 28, and then returns to the compressor 1.
  • the air in the vehicle exchanges heat with the high temperature refrigerant, so that the air in the vehicle becomes high temperature air for return to the interior of the vehicle.
  • the cooling operation is different from the heating operation only in a direction of flow of the refrigerant in the refrigerant circuit, as described above. Other matters and the structures of the operations are the same.
  • the lubricant flows in the hot gas bypass path 27 and then flows into the compressor 1 again even if the lubricant discharges from the compressor 1, so that the depletion of the lubricant in the compressor 1 can be suppressed. Also, since the liquid refrigerant is stored in the accumulator, occurrence of the liquid flood back can be effectively suppressed.
  • the value ⁇ T is taken to be a value obtained by subtracting the set temperature To from the detected temperature Tr.
  • the difference ⁇ T is preferably set to the absolute value of the value obtained by subtracting the set temperature To from the detected temperature Tr.
  • the high pressure control valve 8 and the low pressure control valve 9 are solenoid valves to switch between passage and non-passage of the refrigerant.
  • the present disclosure is not limited to such solenoid valves.
  • the high pressure valve 8 and the low pressure valve 9 may be linear valves configured as electronic valves having an adjustable degree of opening.
  • the degree SH1 of superheat is calculated based on the temperature of and the pressure of the refrigerant flowing into the compressor 1.
  • Temperature sensors may be disposed at an inlet portion and an outlet portion of the indoor heat exchanger 4, and the degree SH1 of superheat may be calculated based on temperatures detected by these temperature sensors. Even in this case, the air-conditioning device according to the present embodiment can exhibit effects similar to those described in the above-described embodiments.
  • Embodiment 3 the example in which the air-conditioning device is mounted on the railroad vehicle is described.
  • the air-conditioning device may be installed in a house, a building, a warehouse, an automobile or the like. Even in these cases, the device according to the present embodiment can exhibit effects similar to those described in Embodiment 3.
  • the degree of opening of the electronic expansion valve 2 is corrected by subtracting the previously-determined given degree ⁇ a of opening from the degree of opening set based on the degree SH1 of superheat.
  • the restriction processing of the present disclosure is not limited to such a manner.
  • the restriction processing used in the present disclosure may be any processing in which the degree of opening of the electronic expansion valve 2 is corrected so as to be less than a degree of opening that is set on the basis of the degree SH1 of superheat.
  • the degree of opening of the electronic expansion valve 2 may be corrected to the minimum degree of opening possible for the electronic expansion valve 2.
  • the higher the refrigerant pressure Pm at the start of the restriction processing the more the given degree ⁇ a of opening may be increased.
  • the given degree ⁇ a of opening may be adjusted based on a result of such monitoring.
  • the restriction processing is terminated upon continuation of the restriction processing for the given time period T1.
  • a time period of the restriction processing of the present disclosure is not limited to the given time period T1 and can be changed as appropriate.
  • the higher the refrigerant pressure Pm at the start of the restriction processing the longer period the given time period T1 may be set to.
  • the restriction processing may be terminated when the refrigerant pressure Pm reduces to a given pressure P2 of the refrigerant.
  • the pressure P2 of the refrigerant is preferably set to the pressure that the refrigerant has in a case in which an amount of the refrigerant corresponding to the upper limit of the heat-exchange capacity of the indoor heat exchanger 4 passes through the low pressure refrigerant pipe 25.
  • the degree of opening of the electronic expansion valve 2 is corrected by adding the previously-determined given degree ⁇ b of opening to the degree of opening set based on the degree SH1 of superheat.
  • the facilitation processing of the present disclosure is not limited to such configuration.
  • the facilitation processing used in the present disclosure may be any processing in which the degree of opening of the electronic expansion valve 2 is corrected so as to be greater than a degree of opening that is set on the basis of the degree SH1 of superheat.
  • the degree of opening of the electronic expansion valve 2 may be corrected to the maximum degree of opening possible for the electronic expansion valve 2.
  • the lower the refrigerant pressure Pm at the start of the facilitation processing the more the given ⁇ b of opening may be reduced.
  • the given degree ⁇ b of opening may be adjusted based on a result of the monitoring of the refrigerant pressure Pm.
  • the facilitation processing is terminated upon continuation over the previously-defined given time period T2.
  • a time period during which the facilitation processing of the present disclosure is executed is not limited to the time period T2 and can be changed as appropriate.
  • the lower the refrigerant pressure Pm at the start of the facilitation processing the longer the given time period T2 may be set.
  • the facilitation processing may be terminated when the refrigerant pressure Pm rises to a previously-determined pressure P3 of the refrigerant.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
EP18775602.8A 2017-03-29 2018-03-23 Air-conditioning device, railway vehicle air-conditioning device, and method for controlling air-conditioning device Active EP3604970B1 (en)

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JPS5743171A (en) * 1980-08-29 1982-03-11 Matsushita Electric Ind Co Ltd Refrigerant flow rate controller
JPS5867275U (ja) * 1981-10-31 1983-05-07 株式会社東芝 冷凍サイクル装置
JP2735188B2 (ja) * 1987-03-20 1998-04-02 株式会社日立製作所 空気調和装置
JPS6330930Y2 (ja) * 1987-07-03 1988-08-18
JPH0293660U (ja) * 1989-01-13 1990-07-25
JP2646914B2 (ja) * 1991-11-05 1997-08-27 三菱電機株式会社 冷凍装置
JP3558788B2 (ja) 1996-07-25 2004-08-25 株式会社エヌ・ティ・ティ ファシリティーズ 空気調和機およびその制御方法
JPH11294332A (ja) * 1998-04-08 1999-10-26 Matsushita Electric Ind Co Ltd 冷凍サイクルの圧縮機
JPH11324951A (ja) * 1998-05-19 1999-11-26 Mitsubishi Electric Corp 空気調和機
WO2001094859A1 (en) * 2000-06-07 2001-12-13 Samsung Electronics Co., Ltd. System for controlling starting of air conditioner and control method thereof
JP4363036B2 (ja) * 2002-12-19 2009-11-11 ダイキン工業株式会社 冷凍装置
JP4767133B2 (ja) * 2006-08-31 2011-09-07 三菱電機株式会社 冷凍サイクル装置
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EP3604970A4 (en) 2020-04-15
JPWO2018180985A1 (ja) 2019-06-27

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