WO2014068821A1 - 空気調和機 - Google Patents

空気調和機 Download PDF

Info

Publication number
WO2014068821A1
WO2014068821A1 PCT/JP2013/004893 JP2013004893W WO2014068821A1 WO 2014068821 A1 WO2014068821 A1 WO 2014068821A1 JP 2013004893 W JP2013004893 W JP 2013004893W WO 2014068821 A1 WO2014068821 A1 WO 2014068821A1
Authority
WO
WIPO (PCT)
Prior art keywords
expansion valve
opening
refrigerant
opening degree
temperature
Prior art date
Application number
PCT/JP2013/004893
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
大介 豊田
Original Assignee
ダイキン工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to CN201380055419.0A priority Critical patent/CN104736944B/zh
Priority to EP13851368.4A priority patent/EP2918947B1/en
Priority to ES13851368.4T priority patent/ES2660871T3/es
Publication of WO2014068821A1 publication Critical patent/WO2014068821A1/ja

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • 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
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • 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

Definitions

  • the present invention relates to an air conditioner using R32 as a refrigerant, and particularly relates to opening degree control of an expansion valve.
  • the temperature of the refrigerant discharged from the compressor is controlled indirectly by controlling the opening of the expansion valve.
  • the opening degree of the expansion valve is feedback-controlled at a predetermined period.
  • R32 has a relatively high refrigeration capacity per unit volume among various refrigerants, the necessary refrigerant circulation amount in the refrigerant circuit can be reduced, and the refrigerant circulation amount is further reduced in the low load region. Even if the opening degree of the expansion valve is changed in the low load region, the refrigerant circulation amount is very small, so the temperature of the discharged refrigerant does not immediately reach the target temperature. Then, at the next opening degree control, it is assumed that there is still a temperature difference between the temperature of the discharged refrigerant and the target temperature even though the opening degree of the expansion valve is controlled to an appropriate opening degree. The opening of the valve is further changed. When such opening valve control is continued, so-called hunting occurs in which the temperature of the discharged refrigerant repeatedly exceeds or falls below the target temperature. As a result, it becomes difficult to stably control the temperature of the discharged refrigerant.
  • the present invention has been made in view of the above points, and an object of the present invention is to provide an expansion valve capable of stably controlling the temperature of refrigerant discharged from a compressor in an air conditioner using R32 as a refrigerant. It is to construct the opening control.
  • a first invention is a refrigerant circuit in which a compressor (12), an outdoor heat exchanger (14), an expansion valve (15), and an indoor heat exchanger (16) are connected, and an HFC 32 is circulated as a refrigerant to perform a refrigeration cycle.
  • (11) and a control unit (30) that performs opening control for changing the opening of the expansion valve (15) by a predetermined amount so that the temperature of the refrigerant discharged from the compressor (12) becomes a target temperature. It is intended for air conditioners equipped with.
  • the said control part (30) has the said predetermined period longer than the area
  • the opening degree control period becomes long.
  • the temperature of the discharged refrigerant reaches (approaches) the target temperature after the degree is changed and before the next opening degree control is performed. That is, the next opening degree control is performed after the temperature of the discharged refrigerant is stabilized.
  • the second invention is a refrigerant circuit in which a compressor (12), an outdoor heat exchanger (14), an expansion valve (15), and an indoor heat exchanger (16) are connected, and an HFC 32 is circulated as a refrigerant to perform a refrigeration cycle.
  • the said control part (30) has the said predetermined amount smaller in the area
  • the amount of change in the opening is small in the region where the opening of the expansion valve (15) is small, the amount of change in the temperature of the discharged refrigerant by one opening control is small. Therefore, the temperature of the discharged refrigerant does not rise or fall significantly, and the state where the temperature of the discharged refrigerant exceeds or falls below the target temperature can be suppressed.
  • control unit (30) is configured such that the opening of the expansion valve (15) is less than the predetermined value in the region where the opening degree of the expansion valve (15) is less than the predetermined value. Is smaller.
  • the temperature of the discharged refrigerant is stable until the next opening control is performed.
  • the amount of change in the temperature of the discharged refrigerant by one opening control is reduced. Therefore, a state where the temperature of the discharged refrigerant exceeds or falls below the target temperature is reliably avoided.
  • the controller (30) is configured such that the predetermined period decreases as the opening degree decreases in a region where the opening degree of the expansion valve (15) is less than the predetermined value. It is getting longer step by step.
  • any one of the first to fourth inventions when the opening of the expansion valve (15) becomes less than the predetermined value, the amount of change in the opening of the expansion valve (15) The amount of change in the refrigerant flow rate in the expansion valve (15) is small.
  • the refrigerant flow rate in the region where the opening degree is less than the predetermined value, does not change so much with respect to the change amount of the opening degree. It does not change. Therefore, the time for the temperature of the discharged refrigerant to reach the target temperature is further increased, but in the region where the opening degree is less than the predetermined value, the predetermined period becomes longer or the change amount of the opening degree becomes smaller. Conditions that exceed or fall below the temperature are effectively avoided.
  • the cycle of the opening degree control is made longer than the region where the opening degree is greater than the predetermined value.
  • the refrigerant circulation amount in (11) is small, the temperature of the discharged refrigerant reaches the target temperature (approaching) after the opening of the expansion valve (15) is changed and the next opening control is performed.
  • the next opening degree control can be performed after the temperature of the discharged refrigerant is stabilized. Therefore, in the next opening degree control, the amount of change of the opening degree can be set appropriately, thereby avoiding a state in which the temperature of the discharged refrigerant exceeds or falls below the target temperature. As a result, hunting of the temperature of the discharged refrigerant can be prevented, and the temperature of the discharged refrigerant can be stably controlled.
  • the change amount of the opening degree is made smaller in the region where the opening degree of the expansion valve (15) is less than the predetermined value than in the region where the opening value is greater than or equal to the predetermined value. ),
  • the amount of change in the temperature of the discharged refrigerant by one opening degree control can be reduced.
  • the opening degree control period is made longer and the change amount of the opening amount is made smaller than in the region where the opening value is greater than the predetermined value. Therefore, it is possible to reliably avoid a state in which the temperature of the discharged refrigerant exceeds or falls below the target temperature. Thus, the temperature of the discharged refrigerant can be reliably controlled.
  • the opening degree control period is increased stepwise as the opening degree becomes smaller.
  • the temperature of the discharged refrigerant can surely reach the target temperature before the control is performed.
  • the temperature of the discharged refrigerant can be reliably controlled.
  • the refrigerant circulation amount in the refrigerant circuit (11) does not change so much with respect to the change amount of the opening degree.
  • the time for the refrigerant temperature to reach the target temperature will be longer, but since the opening degree control period is lengthened and the change amount of the opening degree is reduced according to the region below the predetermined value, the discharge A state where the temperature of the refrigerant exceeds or falls below the target temperature can be effectively avoided. Therefore, it is possible to effectively prevent hunting of the temperature of the discharged refrigerant.
  • FIG. 1 is a piping diagram illustrating the configuration of the air conditioner according to the first embodiment.
  • FIG. 2 is a flowchart illustrating the opening degree control of the expansion valve according to the first embodiment.
  • FIG. 3 is a table showing the relationship between the opening area of the expansion valve and the sampling time.
  • FIG. 4 is a graph showing the relationship between the opening degree of the expansion valve and the refrigerant flow rate.
  • FIG. 5 is a flowchart illustrating the opening degree control of the expansion valve according to the second embodiment.
  • FIG. 6 is a table showing the relationship between the opening range of the expansion valve and the opening change amount.
  • the air conditioner (10) of the present embodiment includes a refrigerant circuit (11) and performs switching between a cooling operation and a heating operation.
  • the refrigerant circuit (11) includes a compressor (12), a four-way switching valve (13), an outdoor heat exchanger (14), an expansion valve (15), and an indoor heat exchanger (16).
  • a closed circuit is configured.
  • the refrigerant circuit (11) is filled with R32 (HFC32 (difluoromethane)) as a refrigerant, and is configured such that the refrigerant circulates to perform a vapor compression refrigeration cycle.
  • the four-way selector valve (13) has a fourth port for the discharge pipe of the compressor (12), a second port for the suction pipe of the compressor (12), and a first port for outdoor heat exchange.
  • the end of the heat exchanger (14) and the third port are connected to the end of the indoor heat exchanger (16), respectively.
  • the four-way selector valve (13) includes a first state (state indicated by a solid line in FIG. 1) in which the first port and the fourth port communicate with each other and a second port and a third port communicate with each other, It is configured to be switchable to a second state (state indicated by a broken line in FIG. 1) in which the two ports communicate and the third port and the fourth port communicate.
  • the outdoor heat exchanger (14) functions as a condenser and the indoor heat exchanger (16) functions as an evaporator.
  • the refrigerant circulates in In the refrigerant circuit (11), when the four-way switching valve (13) switches to the second state, the indoor heat exchanger (16) functions as a condenser and the outdoor heat exchanger (14) functions as an evaporator.
  • the refrigerant circulates in That is, the four-way switching valve (13) constitutes a switching mechanism that switches the refrigerant circulation direction in the refrigerant circuit (11).
  • the compressor (12) is configured as a variable capacity type whose operating frequency is adjusted by an inverter circuit.
  • the opening of the expansion valve (15) is variable by a pulse motor.
  • the outdoor heat exchanger (14) is configured such that the refrigerant exchanges heat with outdoor air, and the indoor heat exchanger (16) exchanges heat between the refrigerant and indoor air.
  • the air conditioner (10) is provided with various sensors and a control unit (30) that controls the operating frequency of the compressor (12) and the opening of the expansion valve (15).
  • the refrigerant circuit (11) is provided with a discharge pipe temperature sensor (21), an outdoor heat exchanger temperature sensor (22), and an indoor heat exchanger temperature sensor (23).
  • the discharge pipe temperature sensor (21) detects the temperature of the discharge pipe of the compressor (12) (hereinafter referred to as discharge pipe temperature Tp).
  • the discharge pipe temperature Tp corresponds to the temperature of the refrigerant discharged from the compressor (12).
  • the outdoor heat exchanger temperature sensor (22) detects the temperature of the refrigerant in the outdoor heat exchanger (14), and the indoor heat exchanger temperature sensor (23) detects the temperature of the refrigerant in the indoor heat exchanger (16).
  • the temperature detected by the outdoor heat exchanger temperature sensor (22) corresponds to the refrigerant condensation temperature Tc during the cooling operation, and corresponds to the refrigerant evaporation temperature Te during the heating operation.
  • the detected temperature of the indoor heat exchanger temperature sensor (23) corresponds to the refrigerant evaporation temperature Te during the cooling operation, and corresponds to the refrigerant condensation temperature Tc during the heating operation.
  • the control unit (30) controls the opening degree of the expansion valve (15) in a predetermined cycle (hereinafter, referred to as “cooling operation” and “heating operation”) so that the discharge pipe temperature Tp of the compressor (12) becomes the target discharge pipe temperature Tpa. Sampling time t).
  • the control unit (30) is configured to change the sampling time t according to the current opening degree region of the expansion valve (15). Details of the opening degree control will be described later.
  • the four-way selector valve (13) switches to the first state in the refrigerant circuit (11).
  • the refrigerant discharged from the compressor (12) dissipates heat to the outdoor air and condenses in the outdoor heat exchanger (27).
  • the condensed refrigerant is decompressed (expands) when passing through the expansion valve (15).
  • the decompressed refrigerant absorbs heat from the indoor air and evaporates in the indoor heat exchanger (16), and the indoor air is cooled and supplied to the room. Thereby, indoor cooling is performed.
  • the refrigerant evaporated in the indoor heat exchanger (16) is compressed by the compressor (12) and discharged again.
  • the four-way switching valve (13) switches to the second state in the refrigerant circuit (11).
  • the refrigerant discharged from the compressor (12) dissipates heat and condenses in the indoor air in the indoor heat exchanger (16), and the indoor air is heated. Thereby, indoor heating is performed.
  • the condensed refrigerant is decompressed (expands) when passing through the expansion valve (15).
  • the decompressed refrigerant absorbs heat from the outdoor air and evaporates in the outdoor heat exchanger (14).
  • the evaporated refrigerant is compressed by the compressor (12) and discharged again.
  • the controller (30) controls the opening of the expansion valve (15) for a predetermined sampling time so that the discharge pipe temperature Tp of the compressor (12) becomes the target discharge pipe temperature Tpa during the cooling operation and the heating operation. Perform every t (sec). Specifically, the control unit (30) feedback-controls the opening degree of the expansion valve (15) according to the flowchart shown in FIG.
  • step ST1 it is determined whether or not a predetermined sampling time t has elapsed since the previous drive of the expansion valve (15) (change in opening of the expansion valve (15)). Move on to ST2.
  • the target discharge pipe temperature Tpa is set.
  • the target discharge pipe temperature Tpa is such that the superheat degree of the suction refrigerant of the compressor (12) (that is, the superheat degree of the outlet refrigerant of the heat exchanger (14, 16) functioning as an evaporator) is a predetermined value. Is set to the value That is, in this embodiment, the superheat degree of the suction refrigerant is indirectly controlled by controlling the discharge pipe temperature Tp.
  • the target discharge pipe is based on the condensation temperature Tc and the evaporation temperature Te, which are detected temperatures of the outdoor heat exchanger temperature sensor (22) and the indoor heat exchanger temperature sensor (23), respectively.
  • a temperature Tpa is set.
  • the target discharge pipe temperature Tpa is obtained by the following mathematical formula. Note that ⁇ , ⁇ , and ⁇ shown below are predetermined coefficients.
  • Target discharge pipe temperature Tpa ⁇ ⁇ condensation temperature Tc ⁇ ⁇ evaporation temperature Te + ⁇
  • the process proceeds to step ST3.
  • the current discharge pipe temperature Tp measured by the discharge pipe temperature sensor (21) is input to the control section (30).
  • the opening change amount ⁇ P (pulse) of the expansion valve (15) necessary for the input current discharge pipe temperature Tp to become (approach) the target discharge pipe temperature Tpa is set.
  • the opening degree of the expansion valve (15) increases, the refrigerant circulation amount increases in the heat exchangers (14, 16) functioning as an evaporator, so the degree of superheat of the outlet refrigerant decreases, and as a result, the discharge pipe temperature Tp becomes descend.
  • the refrigerant circulation amount decreases in the heat exchanger (14, 16) functioning as an evaporator, so the degree of superheat of the outlet refrigerant increases, and as a result, the discharge pipe temperature Tp increases.
  • the control unit (30) is provided in advance with a table (fuzzy table) for setting the opening change amount ⁇ P.
  • a table fuzzy table
  • an opening change amount ⁇ P is determined according to a deviation between the discharge pipe temperature Tp and the target discharge pipe temperature Tpa and a change amount per unit time of the discharge pipe temperature Tp. Therefore, the control unit (30) calculates the deviation and calculates the change amount per unit time from the discharge pipe temperature Tp at the previous opening degree control and the current discharge pipe temperature Tp.
  • An opening change amount ⁇ P is set from the deviation and the change amount.
  • step ST5 the control unit (30) drives the expansion valve (15) so that the opening degree of the expansion valve (15) is increased or decreased by the opening change amount ⁇ P. .
  • a new sampling time t is set. That is, the sampling time t is maintained or changed.
  • the sampling time t is set to a different value depending on the opening region of the expansion valve (15).
  • the minimum opening to the maximum opening of the expansion valve (15) are divided into three opening regions (a large opening region, a medium opening region, and a small opening region). is doing.
  • the large opening range is a range from the first predetermined value Px to the maximum opening
  • the middle opening range is a range from the second predetermined value Py to the first predetermined value Px
  • the small opening range is from the minimum opening.
  • the range is less than the second predetermined value Py.
  • step ST6 the sampling time t is set to “ta (sec)” when the current opening P of the expansion valve (15) is in the large opening region, and “ tb (sec) ", and in the case of a small opening range, it is set to” tc (sec) ".
  • the current opening degree P of the expansion valve (15) indicates the opening degree of the expansion valve (15) after being driven in step ST5 (after the opening degree P is changed).
  • the magnitude relationship among ta, tb, and tc is ta ⁇ tb ⁇ tc.
  • the area where the opening degree P of the expansion valve (15) is less than the first predetermined value Px is greater than the area where the opening degree P is equal to or greater than the first predetermined value Px.
  • Sampling time t is longer.
  • the sampling time t is increased stepwise as the opening P decreases in a region where the opening P of the expansion valve (15) is less than the first predetermined value Px. That is, in this embodiment, the sampling time t is set longer as the opening degree P of the expansion valve (15) becomes smaller.
  • the expansion valve (15) of the present embodiment has a change in the refrigerant flow rate in the expansion valve (15) with respect to the amount of change in the opening P when the opening P is less than the first predetermined value Px. It has the property that the amount is reduced. That is, in the expansion valve (15), the amount of change in the refrigerant flow rate is small even if the opening P is changed by the same opening change amount ⁇ P in the middle opening region and the small opening region. Furthermore, in the opening control of the expansion valve (15) of the present embodiment, the opening at which the relationship between the opening P and the refrigerant flow rate in the expansion valve (15) changes is set to the first predetermined value Px. .
  • step ST6 When a new sampling time t is set in step ST6, the process returns to step ST1 and the next opening degree control is performed. That is, in step ST1, it is determined whether or not a newly set sampling time t has elapsed since the expansion valve (15) was driven.
  • the refrigerant flow rate in the expansion valve (15) decreases, and the refrigerant circulation amount in the refrigerant circuit (11) decreases.
  • the refrigerant circulation amount is very small in the region where the opening degree P of the expansion valve (15) is small. In the opening range where the refrigerant circulation amount is small, even if the opening P of the expansion valve (15) is changed, the discharge pipe temperature Tp does not increase or decrease easily, and it takes time to reach the target discharge pipe temperature Tpa. .
  • the opening degree control is performed at the same sampling time t as the region where the opening degree P of the expansion valve (15) is large (large opening degree region), the opening degree P of the expansion valve (15) actually becomes an appropriate opening degree.
  • the next opening degree control is performed in the transition period in which the discharge pipe temperature Tp is changing toward the target discharge pipe temperature Tpa.
  • the sampling time t becomes longer as the opening degree P of the expansion valve (15) becomes smaller, so the opening degree P of the expansion valve (15).
  • the next opening degree control can be performed after the discharge pipe temperature Tp reaches (approaches) the target discharge pipe temperature Tpa. In other words, the discharge pipe temperature Tp can reach the target discharge pipe temperature Tpa and be stabilized before the next opening degree control is performed.
  • the region where the opening degree P of the expansion valve (15) is less than the predetermined value (first predetermined value Px) is greater than the region where the opening value P is equal to or greater than the predetermined value (first predetermined value Px).
  • the sampling time t (opening control cycle) for opening control is made longer. Therefore, even when the refrigerant circulation amount in the refrigerant circuit (11) is small, the discharge pipe temperature Tp is changed to the target discharge pipe temperature Tpa after the opening degree of the expansion valve (15) is changed and the next opening degree control is performed. It can be reached (approached). That is, the next opening degree control can be performed after the discharge pipe temperature Tp is stabilized.
  • the deviation between the discharge pipe temperature Tp and the target discharge pipe temperature Tpa can be detected appropriately, so that the opening change amount ⁇ P can be set appropriately.
  • the state where the discharge pipe temperature Tp exceeds or falls below the target discharge pipe temperature Tpa can be avoided.
  • hunting of the discharge pipe temperature Tp can be prevented, and the discharge pipe temperature Tp can be stably controlled.
  • the sampling time t is further increased in the opening range smaller than the first predetermined value Px and less than the second predetermined value Py. That is, in the region where the opening degree P of the expansion valve (15) is less than a predetermined value (first predetermined value Px), the opening control sampling time t is increased stepwise as the opening degree P decreases. For this reason, even if the refrigerant circulation amount approaches the minimum circulation amount, the discharge pipe temperature Tp can be reliably reached (approached) to the target discharge pipe temperature Tpa before the next opening degree control is performed. Therefore, the discharge pipe temperature Tp can be reliably controlled stably.
  • the refrigerant circuit (11) has an opening degree change amount ⁇ P for the characteristic of the expansion valve (15).
  • the refrigerant circulation amount does not change so much (see FIG. 4). Therefore, in a region where the opening degree P of the expansion valve (15) is less than a predetermined value (first predetermined value Px), the time for the discharge pipe temperature Tp to reach (approach) the target discharge pipe temperature Tpa becomes longer.
  • the discharge pipe temperature Tp becomes the target discharge pipe temperature Tpa. It is possible to effectively avoid a state of exceeding or falling below. Therefore, hunting of the discharge pipe temperature Tp can be effectively prevented.
  • Embodiment 2 A second embodiment of the present invention will be described.
  • the opening control of the expansion valve (15) is changed in the air conditioner (10) of the first embodiment. That is, in the first embodiment, the sampling time t is lengthened in a region where the opening degree P of the expansion valve (15) is less than a predetermined value, but in this embodiment, the sampling time t is kept constant in such a region.
  • the change amount ⁇ P was made small.
  • the control unit (30) of the present embodiment controls the opening degree of the expansion valve (15) according to the flowchart shown in FIG.
  • the control operations in steps ST1 to ST3 are the same as those in the first embodiment.
  • step ST4 as in the first embodiment, the opening change amount ⁇ P (pulse) of the expansion valve (15) necessary for the current discharge pipe temperature Tp to become (approaching) the target discharge pipe temperature Tpa is set. Is done.
  • the control unit (30) includes a fuzzy table in which an opening change amount ⁇ P is determined according to a deviation between the discharge pipe temperature Tp and the target discharge pipe temperature Tpa and a change amount per unit time of the discharge pipe temperature Tp. Is provided in advance.
  • the opening change amount ⁇ P is set to a different value depending on the opening region of the expansion valve (15).
  • the opening area of the expansion valve (15) is divided into three areas, a large opening area, a medium opening area, and a small opening area, as in the first embodiment.
  • the opening change amount ⁇ P is set to “ ⁇ Pa (pulse)” when the current opening P of the expansion valve (15) is in the large opening region, and is “ It is set to “ ⁇ Pb (pulse)”, and in the small opening range, it is set to “ ⁇ Pc (pulse)”.
  • the magnitude relationship among ⁇ Pa, ⁇ Pb, and ⁇ Pc is ⁇ Pa> ⁇ Pb> ⁇ Pc.
  • the opening degree control of the expansion valve (15) of the present embodiment the area where the opening degree P of the expansion valve (15) is less than the first predetermined value Px is greater than the area where the opening degree P is equal to or greater than the first predetermined value Px.
  • the opening change amount ⁇ P is small. Furthermore, in the present embodiment, the opening change amount ⁇ P decreases stepwise as the opening P decreases in a region where the opening P of the expansion valve (15) is less than the first predetermined value Px. That is, in this embodiment, the opening degree change amount ⁇ P is set to be smaller as the opening degree P of the expansion valve (15) becomes smaller.
  • the opening P of the expansion valve (15) is small.
  • the opening change amount ⁇ P becomes smaller as the time elapses.
  • step ST5 When the opening change amount ⁇ P is set in step ST4, in step ST5, the control unit (30) causes the expansion valve (15) to increase or decrease the opening of the expansion valve (15) by the opening change amount ⁇ P. Drive. When the expansion valve (15) is driven, the process returns to step ST1 and the next opening degree control is performed.
  • the opening degree control of the expansion valve (15) in the present embodiment when the opening degree P of the expansion valve (15) is less than a predetermined value (first predetermined value Px), the predetermined value (first predetermined value Px) or more. Since the opening degree change amount ⁇ P is made smaller than that in the above region, when the refrigerant circulation amount of the refrigerant circuit (11) is small, the change amount of the discharge pipe temperature Tp by one opening degree control can be reduced. it can. Thereby, since the discharge pipe temperature Tp does not rise or fall significantly, the state where the discharge pipe temperature Tp exceeds or falls below the target discharge pipe temperature Tpa can be avoided. As a result, hunting of the discharge pipe temperature Tp can be prevented, and the discharge pipe temperature Tp can be stably controlled. Other functions and effects are the same as those of the first embodiment.
  • the opening of the expansion valve (15) as in the second embodiment is performed.
  • the degree of opening change ⁇ P may be decreased as the degree P decreases.
  • the opening region of the expansion valve (15) is divided into three, but it may be divided into two or four or more.
  • the second predetermined value Py is omitted from the first predetermined value Px and the second predetermined value Py. Is preferred.
  • the air conditioner (10) of each of the above embodiments may be capable of executing only one of the cooling operation and the heating operation.
  • the present invention is useful for an air conditioner including a refrigerant circuit that performs a vapor compression refrigeration cycle by circulating R32 as a refrigerant.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
PCT/JP2013/004893 2012-10-31 2013-08-19 空気調和機 WO2014068821A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201380055419.0A CN104736944B (zh) 2012-10-31 2013-08-19 空调机
EP13851368.4A EP2918947B1 (en) 2012-10-31 2013-08-19 Air conditioner
ES13851368.4T ES2660871T3 (es) 2012-10-31 2013-08-19 Acondicionador de aire

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012239888A JP5672290B2 (ja) 2012-10-31 2012-10-31 空気調和機
JP2012-239888 2012-10-31

Publications (1)

Publication Number Publication Date
WO2014068821A1 true WO2014068821A1 (ja) 2014-05-08

Family

ID=50626779

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2013/004893 WO2014068821A1 (ja) 2012-10-31 2013-08-19 空気調和機

Country Status (5)

Country Link
EP (1) EP2918947B1 (zh)
JP (1) JP5672290B2 (zh)
CN (1) CN104736944B (zh)
ES (1) ES2660871T3 (zh)
WO (1) WO2014068821A1 (zh)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6512596B2 (ja) * 2015-03-30 2019-05-15 オリオン機械株式会社 加熱装置
JP6566693B2 (ja) * 2015-04-03 2019-08-28 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
JP2018071909A (ja) * 2016-10-31 2018-05-10 三菱重工サーマルシステムズ株式会社 冷凍装置、冷凍システム
CN111356885B (zh) * 2017-11-22 2022-02-01 三菱电机株式会社 空调机

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0334564U (zh) 1989-08-10 1991-04-04
JPH06265222A (ja) * 1993-03-11 1994-09-20 Mitsubishi Heavy Ind Ltd 空気調和機の膨張弁制御装置
JPH09236299A (ja) * 1996-02-29 1997-09-09 Daikin Ind Ltd 空気調和装置の運転制御装置
JP2001174075A (ja) * 1999-12-14 2001-06-29 Daikin Ind Ltd 冷凍装置
JP2002286301A (ja) * 2001-03-27 2002-10-03 Hitachi Ltd 冷凍サイクル
JP2012122677A (ja) 2010-12-09 2012-06-28 Mitsubishi Electric Corp 空気調和機

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4089139B2 (ja) * 2000-07-26 2008-05-28 ダイキン工業株式会社 空気調和機
JP3988779B2 (ja) * 2005-09-09 2007-10-10 ダイキン工業株式会社 冷凍装置
JP4596426B2 (ja) * 2005-09-21 2010-12-08 日立アプライアンス株式会社 熱源装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0334564U (zh) 1989-08-10 1991-04-04
JPH06265222A (ja) * 1993-03-11 1994-09-20 Mitsubishi Heavy Ind Ltd 空気調和機の膨張弁制御装置
JPH09236299A (ja) * 1996-02-29 1997-09-09 Daikin Ind Ltd 空気調和装置の運転制御装置
JP2001174075A (ja) * 1999-12-14 2001-06-29 Daikin Ind Ltd 冷凍装置
JP2002286301A (ja) * 2001-03-27 2002-10-03 Hitachi Ltd 冷凍サイクル
JP2012122677A (ja) 2010-12-09 2012-06-28 Mitsubishi Electric Corp 空気調和機

Also Published As

Publication number Publication date
JP5672290B2 (ja) 2015-02-18
EP2918947A4 (en) 2016-09-21
CN104736944B (zh) 2016-08-10
EP2918947B1 (en) 2018-01-03
EP2918947A1 (en) 2015-09-16
CN104736944A (zh) 2015-06-24
ES2660871T3 (es) 2018-03-26
JP2014089006A (ja) 2014-05-15

Similar Documents

Publication Publication Date Title
TWI540293B (zh) Air conditioning device
TWI573969B (zh) 串聯式浮動中介溫度熱幫浦系統
US10006678B2 (en) Air-conditioning apparatus
US8522568B2 (en) Refrigeration system
CN110337570B (zh) 空调装置
JP5783215B2 (ja) 空気調和装置
JP2009014212A (ja) 冷凍装置
US11920841B2 (en) Air-conditioning apparatus
JP2005147456A (ja) 空気調和装置
JP5672290B2 (ja) 空気調和機
JP2016041987A (ja) 圧縮機／ポンプ切換式の冷却装置
JP2001280669A (ja) 冷凍サイクル装置
JP2008241065A (ja) 冷凍装置及び冷凍装置の油戻し方法
JP6758506B2 (ja) 空気調和装置
JP2011007482A (ja) 空気調和装置
JP2008151386A (ja) 空気調和機
JP2006258331A (ja) 冷凍装置
JP2007298218A (ja) 冷凍装置
JP2015068608A (ja) 空気調和装置
JP6896076B2 (ja) 冷凍サイクル装置
JP2009236346A (ja) 冷凍装置
JP2009008346A (ja) 冷凍装置
JPWO2020174685A1 (ja) 冷凍サイクル装置
WO2015140950A1 (ja) 空気調和装置
WO2020174684A1 (ja) 冷凍サイクル装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 13851368

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 2013851368

Country of ref document: EP