CN105074353A - Air conditioner and method for operating air conditioner - Google Patents
Air conditioner and method for operating air conditioner Download PDFInfo
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- CN105074353A CN105074353A CN201480009568.8A CN201480009568A CN105074353A CN 105074353 A CN105074353 A CN 105074353A CN 201480009568 A CN201480009568 A CN 201480009568A CN 105074353 A CN105074353 A CN 105074353A
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- air conditioner
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
- F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/89—Arrangement or mounting of control or safety devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
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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
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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
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
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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
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/027—Compressor control by controlling pressure
- F25B2600/0272—Compressor control by controlling pressure the suction pressure
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
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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
- 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
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
The present invention addresses the problem of providing an air conditioner that uses R32 as a refrigerant and that can reduce the load on a compressor, and a method for operating an air conditioner. Provided is an air conditioner (1), having: a refrigeration cycle in which at least a compressor (14), an outdoor heat exchanger (11), an indoor heat exchanger (21), an outdoor expansion valve (13), and an indoor expansion valve (23) are connected, and refrigerant containing 70 wt% or more of R32 is circulated; and a controller (1a). An upper limit, which regulates the pressure ratio of the compressor (14) so that the dryness fraction of the refrigerant in the intake side of the compressor (14) during operation is higher than 0.85, is set so as to decrease as the intake pressure of refrigerant in the compressor (14) increases. A method for operating the air conditioner (1) is also provided. When the air conditioner (1) is operating, the controller (1a) has the characteristic of adjusting the rotational speed of the compressor (14) so that the pressure ratio is less than the upper limit.
Description
Technical field
The present invention relates to the method for operation of air conditioner and air conditioner.
Background technology
Such as, patent document 1 describes " compressor (1) sucks mass dryness fraction more than 0.65 and the R32 cold-producing medium of less than 0.85 or the mass dryness fraction at least containing more than 70 % by weight R32 are the mix refrigerant of more than 0.65 and less than 0.85, and compresses " (see claims).
At first technical literature
Patent document
Patent document 1: patent No. 3956589 publication
Summary of the invention
Invent problem to be solved
In the freeze cycle of air conditioner, by the refrigerant condition of the heat exchanger outlet played a role as evaporimeter being controlled to carry out flexible Application evaporation latent heat to greatest extent near saturated gas, improve running efficiency.On the other hand, when will global warming coefficient GWP is low compared with R410A (R32+R125:50+50wt%) etc. R32 (HFC32: difluoromethane) use as cold-producing medium, because the specific heat ratio of R32 is large, so, if operate in freeze cycle, make the refrigerant condition of evaporator outlet become near saturated gas, then the refrigerant temperature of compressor discharge is high about 10 ~ 15 DEG C compared with R410A.Therefore, when being used as cold-producing medium by R32, be necessary to make the mass dryness fraction of cold-producing medium in side, suction port of compressor less than mass dryness fraction when using R410A.
Patent document 1 describes the air conditioner (refrigerator) mass dryness fraction of the cold-producing medium of side, suction port of compressor (R32) being set as 0.65 to 0.85.
But, although if make the mass dryness fraction of side, suction port of compressor diminish, then the rising of discharge temperature can be suppressed, the liquid component of the cold-producing medium sucked from side, suction port of compressor is many.And the liquid component dilution that the refrigerator oil in compressor is cooled dose, viscosity reduces, lubrication performance deteriorates, produces the problem that the lifetime of the compressors such as the wearing and tearing in promotion mechanism portion is such.
Therefore, R32 is used in cold-producing medium to provide a kind of by the present invention, and the method for operation of air conditioner and the air conditioner diminished relative to the load of compressor can be made to be problem.
For solving the means of problem
In order to solve described problem, the present invention makes the freeze cycle of the cold-producing medium circulation had containing more than 70 % by weight R32, the pressure ratio of setting limit compression machine, so that the air conditioner of higher limit making the mass dryness fraction of the cold-producing medium of the entrance side of compressor higher than 0.85 and the method for operation of air conditioner.And, there is pressure ratio and carry out such feature that operates littlely than higher limit.
Invention effect
According to the present invention, can provide a kind of and R32 is used in cold-producing medium, the air conditioner little relative to the load of compressor and the method for operation of air conditioner can be made.
Accompanying drawing explanation
Fig. 1 is the figure of the structure of the air conditioner represented about the present embodiment.
Fig. 2 is the Mollier line chart (P-H line chart) of air conditioner R32 being used in cold-producing medium.
Mollier line chart when Fig. 3 is the pressure change of the pressure of the cold-producing medium of the entrance side of compressor and the cold-producing medium of outlet side.
Fig. 4 represents to suck the curve map that mass dryness fraction is the suction pressure of 0.85 and the relation of pressure ratio.
Fig. 5 is the figure representing the variable being used in the presumption sucking mass dryness fraction.
Fig. 6 represents that control device estimates the flow chart of the program sucking mass dryness fraction by calculation.
Fig. 7 is the curve map of the relation representing discharge temperature, condensation temperature and the discharge degree of superheat.
Detailed description of the invention
Below, one side is suitably see accompanying drawing, and one side explains embodiments of the invention.
Embodiment
Fig. 1 is the figure of the structure of the air conditioner represented about the present embodiment.
The air conditioner 1 of the present embodiment comprises off-premises station 10, indoor set 20 and control device 1a and forms.Off-premises station 10 comprises outdoor heat converter 11 (heat source side heat exchanger), outdoor fan 12, outdoor expansion valve 13, compressor 14, accumulator 15 and cross valve 16 and forms.On the other hand, indoor set 20 comprises indoor heat converter 21 (utilizing side heat exchanger), indoor fan 22 and indoor expansion valve 23 and forms.
And off-premises station 10 is connected by pipe arrangement 30,31 with indoor set 20.
In addition, the air conditioner 1 of the present embodiment forms freeze cycle by compressor 14, outdoor heat converter 11 (heat source side heat exchanger), outdoor expansion valve 13, indoor heat converter 21 (utilizing side heat exchanger) and indoor expansion valve 23, uses R32 (difluoromethane) as the cold-producing medium circulated in this freeze cycle.
In addition, such as, if described patent document 1 describes the cold-producing medium at least containing 70% (70 % by weight) above R32, then the advantage identical with the cold-producing medium containing 100%R32 can be played.Therefore, the cold-producing medium that the air conditioner 1 of the present embodiment uses is not limited to the cold-producing medium containing 100%R32, also can be the cold-producing medium (mix refrigerant) containing more than 70 % by weight R32.
Control device 1a controls off-premises station 10 by the starting of the outdoor fan 12 of off-premises station 10, stopping, the adjustment of valve opening of outdoor expansion valve 13, the adjustment of the rotary speed Fr of compressor 14, the control etc. of cross valve 16.In addition, control device 1a controls indoor set 20 by the adjustment etc. of the valve opening of the starting of indoor fan 22, stopping, indoor expansion valve 23.
When cooling operation, control device 1a controls cross valve 16, is connected by the outlet side of compressor 14, and is connected with pipe arrangement 31 by accumulator 15 with outdoor heat converter 11.And control device 1a drives compressor 14, outdoor fan 12 and indoor fan 22.
The cold-producing medium (gas) compressed by compressor 14 via cross valve 16 inflow outdoor heat exchanger 11, by and condensation cooled with the heat exchange of the outer gas of being blown by outdoor fan 12.Circulated at pipe arrangement 30 via outdoor expansion valve 13 by the cold-producing medium (liquid) of outdoor heat converter 11 condensation, be imported into indoor set 20.
The cold-producing medium (liquid) being imported into indoor set 20 is reduced pressure by indoor expansion valve 23, inflow indoor heat exchanger 21.The cold-producing medium (liquid or gas-liquid two-phase state) of inflow indoor heat exchanger 21 is vaporized by the heat exchange with the room air of being blown by indoor fan 22.Now, heat of vaporization captured by the cold-producing medium (liquid) of being vaporized by indoor heat converter 21 indoor air, cooling room air.
The cold-producing medium (gas) vaporized by indoor heat converter 21 circulates at pipe arrangement 31, is imported into off-premises station 10, circulates at cross valve 16, flows into accumulator 15.Accumulator 15 as liquid refrigerant transiently superfluous flow into time store refrigerant (liquid) surge tank play function, accordingly, prevent the liquid compression of compressor 14.Therefore, in accumulator 15, the mass dryness fraction of cold-producing medium raises, and the cold-producing medium that mass dryness fraction is high flows into compressor 14.
When heating running, control device 1a controls cross valve 16, is connected by the outlet side of compressor 14, and is connected with accumulator 15 by outdoor heat converter 11 with pipe arrangement 31.And control device 1a drives compressor 14, outdoor fan 12 and indoor fan 22.
The cold-producing medium (gas) compressed by compressor 14 circulates at pipe arrangement 31 via cross valve 16, is imported into indoor set 20.Be directed to cold-producing medium (gas) inflow indoor heat exchanger 21 of indoor set 20, by also condensation cooled with the heat exchange of the room air of being blown by indoor fan 22.Now, room air condensation heat is given, heating indoor air by the chilled cold-producing medium of indoor heat converter 21 (gas).By the chilled cold-producing medium of indoor heat converter 21 (liquid) via indoor expansion valve 23, circulate at pipe arrangement 30, be imported into off-premises station 10.The cold-producing medium (liquid) being directed to off-premises station 10 is reduced pressure by outdoor expansion valve 13, inflow outdoor heat exchanger 11.The cold-producing medium (liquid) flowing into outdoor heat converter 11 is vaporized by the heat exchange with the outer gas of being blown by outdoor fan 12, flows into accumulator 15 via cross valve 16.And the cold-producing medium (gas or gas-liquid two-phase state) making mass dryness fraction improve because of accumulator 15 flows into compressor 14.
In addition, the suction pressure sensor 10pb that off-premises station 10 possesses discharge temperature sensor 10ta that the temperature (discharge temperature Td) to the cold-producing medium of being discharged by compressor 14 measures, the pressure (suction pressure Ps) of the discharge pressure sensor 10pa that measures the pressure (discharge pressure Pd) of the cold-producing medium of the outlet side of compressor 14 and the cold-producing medium to the entrance side of compressor 14 measures.
In addition, off-premises station 10 possesses the temperature sensor 10tb that condensation temperature Tc (during cooling operation) or evaporating temperature Te (when heating running) for the cold-producing medium to outdoor heat converter 11 measure, and indoor set 20 possesses the temperature sensor 20ta that evaporating temperature Te (during cooling operation) or condensation temperature Tc (when heating running) for the cold-producing medium to indoor heat converter 21 measure.
In addition, also can make alternative discharge temperature Td, the structure used is measured to the chamber upper temp of compressor 14.
Fig. 2 is the Mollier line chart (P-H line chart) that cold-producing medium uses the air conditioner of R32.
Such as, when air conditioner 1 (see Fig. 1) carries out heating running, the cold-producing medium (gas) being in the state of an A1 is compressed by compressor 14, temperature (specific enthalpy) and pressure increase, become the state of an A2, be imported into indoor set 20.The cold-producing medium (gas) being imported into indoor set 20 with roughly isobaric condensation, becomes the state (liquid) of an A3, is imported into off-premises station 10 in indoor heat converter 21.Under the state of an A3, the cold-producing medium (liquid) being directed to off-premises station 10 is reduced pressure by outdoor expansion valve 13, becomes the state of an A4, is vaporized by outdoor heat converter 11, becomes the state (gas) of an A1.Like this, carrying out heating in the air conditioner 1 of running, cold-producing medium (R32) one side is in the state transfer of A1 ~ A4, and one side circulates.That is, being compressed by compressor 14 during indoor heat converter 21 condensation (the some A2 → A3) of the cold-producing medium (gas) of (some A1 → A2) by indoor set 20, heating indoor air.
Now, R32 due to compared with R410A specific heat ratio large, so, when being compressed by compressor 14 (some A1 → A2), the temperature (discharge temperature Td) high (Td1) of the cold-producing medium of the outlet side of compressor 14.Such as, discharge temperature Td and R410A compares high about 10 ~ 15 DEG C.Accordingly, there is the permission ceiling temperature being exceeded compressor 14 by the discharge temperature Td of the cold-producing medium that have compressed, apply the situation of excessive load to compressor 14.Therefore, when cold-producing medium uses R32, require to make the discharge temperature Td of the outlet side of compressor 14 low (such as, Td1 → Td2).
Such as, if the valve opening of outdoor expansion valve 13 becomes large, then promote that the temperature in outdoor expansion valve 13 reduces, if in Fig. 2 shown in dotted line, temperature or the mass dryness fraction step-down (some A1 ') of the cold-producing medium of the entrance side of compressor 14 can be made.Accordingly, the discharge temperature Td step-down (some A2 → A2 ') of the cold-producing medium of the outlet side of compressor 14.
But if the state of the cold-producing medium of the entrance side of compressor 14 (some A1 ') becomes the temperature (or specific enthalpy) lower than saturated line C100, then the mass dryness fraction of the cold-producing medium of the entrance side of compressor 14 is lower than 1.00.
The containing ratio of the liquid component of the cold-producing medium that mass dryness fraction is low is many, and the cold-producing medium that some degree are low flows into compressor 14, then the refrigerator oil of compressor 14 dilutes by the liquid component contained by this cold-producing medium, produces the impacts such as the wearing and tearing in promotion mechanism portion.That is, the cold-producing medium that some degree are low flows into compressor 14, then become large relative to the load of compressor 14.Thus, the state that the mass dryness fraction of the cold-producing medium of the entrance side of compressor 14 is superfluously low is also bad.
Therefore, according to the experiment of the dependency relation of the refrigerator oil viscosity reduction in the mass dryness fraction (hereinafter referred to " sucking mass dryness fraction Xs ") of the cold-producing medium of the change (promote wearing and tearing states etc.) of the mechanical performance of investigation compressor 14, the entrance side of compressor 14 and compressor 14, the boundary value making the suction mass dryness fraction Xs of the degraded in mechanical properties (or deterioration is in allowed band) of compressor 14 is 0.85.In other words, suck mass dryness fraction Xs if be aware of higher than 0.85 (Xs > 0.85), then the scope giving compressor 14 impact can be allowed, can make little relative to the load of compressor 14.
Therefore, the air conditioner 1 of the present embodiment is made and is being sucked the structure operated under the mass dryness fraction Xs state higher than 0.85.In addition, the double dot dash line shown in Fig. 2 represents that mass dryness fraction is " etc. mass dryness fraction line C85 " of 0.85.
Fig. 3 is the Mollier line chart of the pressure (discharge pressure Pd) of the pressure (suction pressure Ps) of the cold-producing medium of the entrance side of compressor and the cold-producing medium of outlet side when changing.
Such as, as shown in Figure 3, when ceiling temperature (Tdmax) below the permission ceiling temperature that the discharge temperature Td of the cold-producing medium of the outlet side by compressor 14 maintains compressor 14, represent compressor 14 outlet side cold-producing medium state point (some A2-n:n=1,2,3 ...) there is state change, so that discharge temperature Td notationally limits (single dotted broken line) on the thermoisopleth of temperature (Tdmax).
Such as, when the permission ceiling temperature of compressor 14 is 120 DEG C, the ceiling temperature of the discharge temperature Td of cold-producing medium is set as about 100 DEG C (" Tdmax=100 [DEG C] ").
In addition, saturated line C100 is the line that mass dryness fraction becomes 1.00, represents that " etc. mass dryness fraction line C85 " of mass dryness fraction 0.85 is compared with saturated line C100, specific enthalpy low (illustrating with double dot dash line).And, make suction mass dryness fraction Xs be 0.85, if make the temperature of the cold-producing medium of the entrance of compressor 14 (specific enthalpy) become represent mass dryness fraction 0.85 etc. mass dryness fraction line C85 becomes suction pressure Ps point (some A1-n:n=1,2,3 ...) shown in temperature.
The pressure ratio ε (discharge pressure Pd/ suction pressure Ps) of compressor 14 is decided from the some A1-n determined like this and some A2-n.That is, the pressure ratio ε relative to suction pressure Ps is determined.
As shown in Figure 3, although suction pressure Ps higher (Ps1 → Ps2 → Ps3), more can make discharge pressure Pd high (Pd1 → Pd2 → Pd3), compared with the ratio risen with suction pressure Ps, the ratio that discharge pressure Pd rises is little.That is, suction pressure Ps is higher, is more necessary to make pressure ratio ε little.
Fig. 4 represents to suck the curve map that mass dryness fraction becomes the suction pressure of 0.85 and the relation of pressure ratio, and transverse axis represents suction pressure Ps, and the longitudinal axis represents pressure ratio ε (discharge pressure Pd/ suction pressure Ps).
In addition, " ε U " shown in Fig. 4 is the maximum of pressure ratio ε.In addition, solid line represents the higher limit (pressure ratio upper limit ε max) sucking the mass dryness fraction Xs pressure ratio ε higher than 0.85.Pressure ratio upper limit ε max is that limiting pressure compares ε, to make the higher limit that suction mass dryness fraction Xs is higher than 0.85, the compression (the rotary speed Fr of compressor 14) of restriction cold-producing medium, to make pressure ratio ε become pressure ratio below upper limit ε max, accordingly, mass dryness fraction Xs is sucked higher than 0.85.
And, " PsL " be make suction mass dryness fraction Xs be 0.85 pressure ratio ε become the suction pressure Ps of maximum " ε U ".That is, suction pressure Ps " PsL " region is below the region that pressure ratio ε for making suction mass dryness fraction Xs become 0.85 exceedes maximum " ε U ".
In addition, " PsU " is the higher limit of the suction pressure Ps in air conditioner 1.And the maximum " ε U " of the lower limit " PsL " of the suction pressure Ps shown in Fig. 4 and higher limit " PsU ", pressure ratio ε is the characteristic value of air conditioner 1, it is the design load determined according to each air conditioner 1.
As shown in Figure 4, pressure ratio upper limit ε max is the maximum " ε U " (ε max=ε U) that lower limit " PsL " region below (Ps≤PsL) becomes pressure ratio at suction pressure Ps, in the region (Ps > PsL) that suction pressure Ps is higher than lower limit " PsL ", represented by following formula (1).
εmax＝εU-(εU-εL)/(PsU-PsL)×(Ps-PsL)…(1)
As shown in Figure 3, because suction pressure Ps is higher, pressure ratio ε is less, so as shown in Figure 4, pressure ratio upper limit ε max is also that suction pressure Ps is higher and lower.
And, in the air conditioner 1 (see Fig. 1) of the present embodiment, control device 1a (see Fig. 1) is with compressed refrigerant (R32), to make pressure ratio ε compare by the little rotary speed Fr of the pressure ratio upper limit ε max shown in formula (1), running compressor 14 (see Fig. 1).That is, control device 1a regulates the rotary speed Fr of compressor 14, to make pressure ratio ε specific pressure less than upper limit ε max.Accordingly, the suction mass dryness fraction Xs of air conditioner 1 is maintained higher than 0.85.
In addition, control device 1a (see Fig. 1) also can be the rotary speed Fr regulating compressor 14, to make pressure ratio ε close to the structure of pressure ratio upper limit ε max.Such as, little than upper limit ε max at pressure ratio ε specific pressure, and when requiring to increase air conditioning capacity, control device 1a makes the rotary speed Fr of compressor 14 rise, and improves the structure of pressure ratio ε.When forming control device 1a like this, air conditioner 1 (see Fig. 1) operates under suction mass dryness fraction Xs is close to the state of 0.85.
In the air conditioner 1 shown in Fig. 1, discharge pressure sensor 10pa measures discharge pressure Pd, and suction pressure sensor 10pb measures suction pressure Ps.And, control device 1a regulates the rotary speed Fr of compressor 14, air conditioner 1 is made to heat running, so that the pressure ratio ε (discharge pressure Pd (variable)/suction pressure Ps (variable)) of the variable calculation of the discharge pressure Pd making the variable of the suction pressure Ps measured from suction pressure sensor 10pb and discharge pressure sensor 10pa measure becomes the pressure ratio upper limit ε max calculated by formula (1).
Here, also can be the one side or both sides of alternative discharge pressure sensor 10pa and suction pressure sensor 10pb, and possess the structure of the sensor (temperature sensor) of metering condensation temperature Tc and evaporating temperature Te.
When heating running, temperature sensor 20ta (see Fig. 1) metering that condensation temperature Tc can be possessed by indoor heat converter 21, temperature sensor 10tb (see Fig. 1) metering that evaporating temperature Te can be possessed by outdoor heat converter 11.
In general, temperature sensor specific pressure sensor is cheap, by alternative pressure sensor (discharge pressure sensor 10pa, suction pressure sensor 10pb), serviceability temperature sensor (temperature sensor 10tb, temperature sensor 20ta), can obtain cheap air conditioner 1.
In addition, the air conditioner 1 (see Fig. 1) of the present embodiment also can be configured to control device 1a (see Fig. 1) and estimate suction mass dryness fraction Xs by calculation.And control device 1a controls compressor 14 (see Fig. 1), to make the structure that the suction mass dryness fraction Xs of presumption is higher than 0.85.
Fig. 5 is the figure representing the variable being used in the presumption sucking mass dryness fraction, Fig. 6 is represent that control device estimates the flow chart of the program sucking mass dryness fraction by calculation.
When the control device 1a that the air conditioner 1 of the present embodiment possesses estimates suction mass dryness fraction Xs, according to the program shown in Fig. 6, by the calculation based on the physical property values of the rotary speed Fr of discharge temperature Td, discharge pressure Pd, suction pressure Ps, compressor 14 and cold-producing medium (R32), presumption sucks mass dryness fraction Xs.And control device 1a makes air conditioner 1 operate (such as, heating running), to make the suction mass dryness fraction Xs of presumption higher than 0.85.In addition, control device 1a is configured to when making air conditioner 1 operate, and in the circulation of regulation, presumption (calculation) sucks mass dryness fraction Xs.
See Fig. 6, illustrate that control device 1a estimates the program (suitably with reference to figure 1 ~ 5) sucking mass dryness fraction Xs by calculation.
The variable of the rotary speed Fr of the not shown rotary speed meter metering that the variable of the suction pressure Ps that the variable of the discharge pressure Pd that the variable of the discharge temperature Td that control device 1a measures according to discharge temperature sensor 10ta, discharge pressure sensor 10pa measure, suction pressure sensor 10pb measure and compressor 14 possess, obtains the rotary speed Fr (step S1) of discharge temperature Td, discharge pressure Pd, suction pressure Ps and compressor 14.
And control device 1a calculates Exhaust Gas specific enthalpy hd (step S2) according to the discharge temperature Td obtained and discharge pressure Pd.
As shown in Figure 5, Exhaust Gas specific enthalpy hd represents the specific enthalpy of the cold-producing medium of the outlet side of compressor 14.
In addition, control device 1a supposes to suck mass dryness fraction Xs (step S3), and then, according to the physical property values (physical property values of R32) of suction pressure Ps and cold-producing medium, the calculation enthalpy of saturated liquid hsL of suction pressure Ps and the saturated gas specific enthalpy hsG (step S4) of suction pressure Ps.
Such as, in step S3, control device 1a is using the assumed value of the presumed value of the suction mass dryness fraction Xs in front circulation calculation as suction mass dryness fraction Xs.
In addition, control device 1a, according to the approximate expression preset, calculates enthalpy of saturated liquid hsL and the saturated gas specific enthalpy hsG (step S4) of suction pressure Ps.Preferably this approximate expression is the approximate expression preset as the characteristic type of R32.
And control device 1a uses suction mass dryness fraction Xs, the enthalpy of saturated liquid hsL of calculation and the saturated gas specific enthalpy hsG of calculation of supposition, according to following formula (2), calculation sucks specific enthalpy hs (step S5).
Xs＝(hs-hsL)/(hsG-hsL)…(2)
In addition, the suction specific enthalpy hs of control device 1a according to suction pressure Ps, calculation and the physical property values of R32, calculation sucks specific entropy Ss (step S6), and then, according to suction specific entropy Ss, the discharge pressure Pd of calculation and the physical property values of R32, calculation adiabatic compression Exhaust Gas specific enthalpy hd ' (step S7).
Be configured to, in step s 6, control device 1a, according to the approximate expression preset, calculates the suction specific entropy Ss in suction pressure Ps and suction specific enthalpy hs.Preferably this approximate expression is characteristic type as R32 and the approximate expression that is preset.
In addition, the adiabatic compression Exhaust Gas specific enthalpy hd ' that control device 1a calculates in the step s 7 as shown in Figure 5, the specific enthalpy of the discharge pressure Pd cold-producing medium representing at the suction mass dryness fraction Xs supposed in step s3 control device 1a makes the efficiency (compressor efficiency η t) of compressor 14 be isentropic Compression (the η t=1) of " 1 ".Isentropic Compression represented by dashed line in Fig. 5.
In this case, compressor efficiency (tentative efficiency) the η t of the suction mass dryness fraction Xs supposed in step s3 relative to control device 1a of compressor 14
real' represent by following formula (3).
ηt
real’＝(hd’-hs)/(hd-hs)…(3)
Control device 1a according to the Exhaust Gas specific enthalpy hd calculated in step s 2, the suction specific enthalpy hs calculated in step s 5 and the adiabatic compression Exhaust Gas specific enthalpy hd ' that calculates in the step s 7, from the tentative efficiency eta t of formula (3) calculation
real' (step S8).
In addition, efficiency (actual efficiency) the η t of the reality of compressor 14
realrepresent by following formula (4).
ηt
real＝f(Xs、Pd、Ps、Fr)…(4)
In addition, " f (Xs, Pd, Ps, Fr) " is using sucking the rotary speed Fr of mass dryness fraction Xs, discharge pressure Pd, suction pressure Ps and compressor 14 as variable to represent the function of the characteristic of compressor 14, is the function preset according to the form of each compressor 14.
And, control device 1a according to the rotary speed Fr of the suction mass dryness fraction Xs supposed in step s3, the discharge pressure Pd obtained in step sl, suction pressure Ps and compressor 14, from formula (4) calculation actual efficiency η t
real(step S9).
Control device 1a calculates the tentative efficiency eta t calculated in step s 8
real' divided by the actual efficiency η t calculated in step s 9
realratio (η t
real'/η t
real) (step S10), if this value is more than the lower limit of regulation, and below set upper limit value (step S10 → Yes), then the suction mass dryness fraction Xs supposed in step s3 is determined the presumed value for sucking mass dryness fraction Xs.
On the other hand, as ratio (the η t calculated in step slo
real'/η t
real) the lower limit of value deficiency regulation or the situation larger than set upper limit value (step S10 → No) under, control device 1a makes program be restored to step S3, and supposition sucks mass dryness fraction Xs again, performs the program of step S3 ~ step S10.
Such as, as ratio (the η t calculated in step slo
real'/η t
real) value deficiency regulation lower limit when, control device 1a will make suction mass dryness fraction Xs to tentative efficiency eta t
real' become value that large direction the changed assumed value as new suction mass dryness fraction Xs.
In addition, preferably control device 1a and " η t in step slo
real'/η t
real" lower limit of regulation that compares and higher limit suitably set according to the calculation precision etc. of required suction mass dryness fraction Xs.Such as, if make lower limit be " 0.999 ", make higher limit be " 1.001 ", then control device 1a can estimate (calculation) according to the error of " ± 0.1% " and suck mass dryness fraction Xs.
And control device 1a (see Fig. 1) one side sucks mass dryness fraction Xs by program presumption (calculation) shown in Fig. 6, one side makes air conditioner 1 (see Fig. 1) operate (such as, heating running).Now, control device 1a controls air conditioner 1, to make the suction mass dryness fraction Xs of presumption higher than 0.85.Specifically, control device 1a regulates the rotary speed Fr of compressor 14, regulates pressure ratio ε, to make by calculating the suction mass dryness fraction Xs estimated higher than 0.85.
Control device 1a is declining by calculating the suction mass dryness fraction Xs that estimating, close to 0.85 time, the rotary speed Fr of compressor 14 is reduced, makes pressure ratio ε step-down.Such as, control device 1a controls compressor 14, so that the rotary speed Fr making the compressor 14 of the rotary speed Fr running becoming pressure ratio upper limit ε max reduces.Accordingly, discharge pressure Pd reduces, and the cold-producing medium of the entrance side of compressor 14 is difficult to humidity, sucks mass dryness fraction Xs and rises.
Like this, suck mass dryness fraction Xs by control device 1a (see Fig. 1) presumption, and air conditioner 1 (see Fig. 1) is operated, to make the suction mass dryness fraction Xs of presumption higher than 0.85, can more positively suction mass dryness fraction Xs be maintained higher than 0.85.
In addition, the control device 1a (see Fig. 1) of the present embodiment makes air conditioner 1 (see Fig. 1) heat running, to make the discharge degree of superheat TdSH (=Td-Tc) as the difference of condensation temperature Tc and discharge temperature Td be no more than the structure of the desired value preset.
Fig. 7 is the curve map of the relation representing discharge temperature, condensation temperature and the discharge degree of superheat, and taking the longitudinal axis as temperature (discharge temperature Td, condensation temperature Tc, discharge degree of superheat TdSH), take transverse axis as discharge pressure Pd.
In addition, the solid line of Fig. 7 represents condensation temperature Tc, and single dotted broken line represents discharge temperature Td.And dotted line represents the desired value (target superheat degree SHtgt) of the discharge degree of superheat TdSH of each discharge pressure Pd.As previously mentioned, discharge the difference (Td-Tc) that degree of superheat TdSH is discharge temperature Td under identical discharge pressure Pd and condensation temperature Tc, its target superheat degree SHtgt such as in Fig. 7 shown in dotted line set.
Condensation temperature Tc is the intrinsic value (physical property values) of the cold-producing medium that determines accordingly with discharge pressure Pd, the variable calculation condensation temperature Tc of the discharge pressure Pd that control device 1a can measure according to discharge pressure sensor 10pa (see Fig. 1).
Such as, the discharge pressure Pd that control device 1a can measure according to discharge pressure sensor 10pa, calculates condensation temperature Tc from the approximate expression of the relation representing discharge pressure Pd and condensation temperature Tc.Preferably this approximate expression is the approximate expression be preset as the characteristic type of R32.
In addition, in the example shown in Fig. 7, owing at discharge pressure Pd being setting (border discharge pressure: time Pda), discharge temperature Td becomes the ceiling temperature (Tdmax) of compressor 14, so, discharge the high region of pressure (Pda) at discharge pressure Pd than border, setting target superheat degree SHtgt, to make discharge temperature Td become ceiling temperature (Tdmax).
The discharge temperature Td that control device 1a (see Fig. 1) measures from discharge temperature sensor 10ta (see Fig. 1) and discharge degree of superheat TdSH according to the condensation temperature Tc calculation that the variable of discharge pressure Pd calculates.And control device 1a makes air conditioner 1 (see Fig. 1) heat running, to make the discharge degree of superheat TdSH of calculation close to target superheat degree SHtgt shown in dotted lines in Figure 7.Such as, when the discharge degree of superheat TdSH calculated is lower than target superheat degree SHtgt, control device 1a makes the valve opening of outdoor expansion valve 13 diminish.Suppress the temperature of the cold-producing medium of outdoor expansion valve 13 to reduce, discharge temperature Td rises.On the other hand, because suction pressure Ps and discharge pressure Pd does not change such degree, so the change of condensation temperature Tc is little.Accordingly, discharge degree of superheat TdSH (Td-Tc) to rise, close to target superheat degree SHtgt.
Like this, control device 1a controls outdoor expansion valve 13, regulates its valve opening, to make the discharge degree of superheat TdSH of calculation be maintained near target superheat degree SHtgt.
Such as, in the upper limit (ceiling temperature) of setting discharge temperature Td, regulate the rotary speed Fr of compressor 14 (see Fig. 1), when becoming ceiling temperature to make discharge temperature Td, along with the change of the rotary speed Fr of compressor 14, discharge pressure Pd and discharge temperature Td change.And, suck both mass dryness fraction Xs and discharge pressure Pd and discharge temperature Td and change accordingly.Accordingly, in order to be maintained by suction mass dryness fraction Xs higher than 0.85, control device 1a (see Fig. 1) synthetically adjusts discharge pressure Pd and discharge temperature Td, and the control of air conditioner 1 (see Fig. 1) becomes complicated.
On the other hand, at setting target superheat degree SHtgt, regulate the valve opening of outdoor expansion valve 13 (see Fig. 1), when making discharge degree of superheat TdSH close to target superheat degree SHtgt, discharge pressure Pd does not change such degree, and discharge temperature Td changes.Therefore, suck mass dryness fraction Xs and discharge pressure Pd to change accordingly.
Thus, control device 1a (see Fig. 1) is as long as regulate the valve opening of outdoor expansion valve 13, and maintained by suction mass dryness fraction Xs higher than 0.85, the control of air conditioner 1 (see Fig. 1) becomes simple.
In addition, as previously mentioned, make the rotary speed Fr that control device 1a (see Fig. 1) regulates compressor 14, to make pressure ratio ε close to the structure of pressure ratio upper limit ε max, have again, also can be the valve opening that control device 1a regulates outdoor expansion valve 13, to make discharge degree of superheat TdSH close to the structure of target superheat degree SHtgt.
Such as, little than upper limit ε max at pressure ratio ε specific pressure, when the discharge degree of superheat TdSH of calculation is less than target superheat degree SHtgt, control device 1a makes the rotary speed Fr of compressor 14 rise, improve pressure ratio ε, and the valve opening of outdoor expansion valve 13 is diminished, make discharge degree of superheat TdSH increase.
According to this structure, pressure ratio ε is maintained near pressure ratio upper limit ε max, discharges degree of superheat TdSH and is maintained near target superheat degree SHtgt.Accordingly, the suction mass dryness fraction Xs of air conditioner 1 (see Fig. 1) can be maintained the state close to 0.85 by control device 1a (see Fig. 1), can set high by discharge temperature Td.Accordingly, air conditioner 1 operates under the state that discharge temperature Td is high as far as possible, can use evaporation latent heat flexibly to maximum limit, the operating condition that implementation efficiency is high.
As mentioned above, the control device 1a of the present embodiment shown in Fig. 1 is when making air conditioner 1 heat running, control compressor 14 and outdoor expansion valve 13, regulate the rotary speed fr of discharge temperature Td, discharge pressure Pd, suction pressure Ps and compressor 14, suction mass dryness fraction Xs is maintained higher than 0.85.Accordingly, even if when using R32 as cold-producing medium, also discharge temperature Td can be maintained the ceiling temperature (Tdmax) of compressor 14 below.In addition, the load that the liquid component contained by can making in cold-producing medium gives compressor 14 is little.
In addition, the present invention is not limited to aforesaid embodiment.Such as, described embodiment be in order to easy understand the present invention is described and the embodiment be described in detail, the inventive embodiment possessing illustrated entire infrastructure might not be defined in.
In addition, also can be the structure of an embodiment part for the structure of certain embodiment being replaced into other, in addition, can also be the structure of the embodiment adding other in the structure of certain embodiment.
Such as, although explanation is above the situation that air conditioner 1 (see Fig. 1) carries out heating running, even if when air conditioner 1 carries out cooling operation, control device 1a (see Fig. 1) controls air conditioner 1 similarly.
Control device 1a, when making air conditioner 1 carry out cooling operation, regulates the rotary speed Fr of compressor 14 and the valve opening of indoor expansion valve 23, is maintained by suction mass dryness fraction Xs higher than 0.85, further, maintained near higher limit by discharge degree of superheat TdSH.
That is, control device 1a regulates the rotary speed Fr of compressor 14, so that the pressure ratio upper limit ε max making pressure ratio ε become to calculate according to formula (1).
In addition, control device 1a is calculated by the program shown in Fig. 6 and estimates and sucks mass dryness fraction Xs, controls air conditioner 1, to make the suction mass dryness fraction Xs of presumption higher than 0.85.
Further, control device 1a regulates the valve opening of indoor expansion valve 23, to make discharge degree of superheat TdSH close to the target superheat degree SHtgt preset.
Like this, control device 1a controls compressor 14 and indoor expansion valve 23, makes air conditioner 1 cooling operation.
In addition, the control device 1a (see Fig. 1) of the present embodiment is in the step S4 shown in Fig. 6, by the approximate expression preset, the structure of calculation enthalpy of saturated liquid hsL, but, such as, also can be the structure reflection of the relation representing suction pressure Ps and enthalpy of saturated liquid hsL being stored in not shown storage part.
If make such structure, then control device 1a in the step S4 shown in Fig. 6, according to suction pressure Ps, with reference to this reflection, can calculate enthalpy of saturated liquid hsL.Accordingly, load during control device 1a calculation enthalpy of saturated liquid hsL can be alleviated.
Equally, also can make the structure reflection of the relation representing suction pressure Ps and saturated gas specific enthalpy hsG being stored in not shown storage part, can also be the structure reflection of the relation representing suction pressure Ps and suction specific entropy Ss being stored in not shown storage part.
In addition, also can be the structure reflection of the relation representing discharge pressure Pd and condensation temperature Tc being stored in not shown storage part.
In addition, the present invention is not the invention being defined in aforesaid embodiment, suitably can carry out design alteration in the scope of the purport not departing from invention.
Such as, as shown in Figure 1, although the compressor 14 of the air conditioner 1 of the present embodiment is provided in off-premises station 10, also can be the structure that compressor 14 is provided in indoor set 20.
In addition, also can be alternative cross valve 16 and possess the structure of multiple open and close valve (not shown).When possessing the structure of multiple open and close valve, if make at least possess to the open and close valve connecting the outlet side of compressor 14 and the pipe arrangement of outdoor heat converter 11 and carry out opening and closing, to be connected accumulator 15 and the pipe arrangement of pipe arrangement 31 and carry out opening and closing open and close valve, the pipe arrangement of the outlet side and pipe arrangement 31 that are connected compressor 14 carried out to the open and close valve of opening and closing and the pipe arrangement of junction chamber outer heat-exchanger 11 and accumulator 15 carried out to the structure of these 4 open and close valves of open and close valve of opening and closing.
Symbol description
1: air conditioner; 1a: control device; 11: outdoor heat converter (heat source side heat exchanger); 13: outdoor expansion valve (expansion valve); 14: compressor; 21: indoor heat converter (utilizing side heat exchanger); 23: indoor expansion valve (expansion valve); Fr: rotary speed; Pd: discharge pressure; Ps: suction pressure; SHtgt: target superheat degree (discharging the desired value of the degree of superheat); Tc: condensation temperature; Td: discharge temperature; TdSH: discharge the degree of superheat; Xs: suck mass dryness fraction (mass dryness fraction of the cold-producing medium of the entrance side of compressor); ε: pressure ratio; ε max: the pressure ratio upper limit (higher limit of pressure ratio).
Claims (5)
1. an air conditioner, is characterized in that, has freeze cycle and control device,
Described freeze cycle is at least connected with compressor, heat source side heat exchanger, utilizes side heat exchanger and expansion valve, circulates and contains the cold-producing medium of more than 70 % by weight R32,
By the pressure ratio of limit compression machine, to make the mass dryness fraction of the described cold-producing medium in the entrance side of compressor described in this higher limit higher than 0.85 be set to, the suction pressure of the described cold-producing medium in described compressor is higher and become lower,
In the running, described control device
Regulate the rotary speed of described compressor, to make described pressure ratio less than described higher limit.
2. air conditioner as claimed in claim 1, is characterized in that, sets the desired value of the discharge degree of superheat after the condensation temperature corresponding with the discharge pressure of described cold-producing medium deducted from the discharge temperature of the described cold-producing medium described compressor in described compressor,
In the running, described control device
Regulate the rotary speed of described compressor, to make described pressure ratio close to described higher limit, and regulate the valve opening of described expansion valve, to make the described discharge degree of superheat close to described desired value.
3. air conditioner as claimed in claim 1 or 2, is characterized in that, in the running, and described control device
At least by with the discharge temperature of the described cold-producing medium in described compressor,
The discharge pressure of the described cold-producing medium in described compressor,
Described suction pressure in described compressor
With the rotary speed of described compressor
Based on calculation, estimate described mass dryness fraction,
And then, regulate the rotary speed of described compressor, to make the described mass dryness fraction of presumption higher than 0.85.
4. the method for operation of an air conditioner, it is characterized in that, performed by the control device of air conditioner, described air conditioner has freeze cycle, described freeze cycle is at least connected with compressor, heat source side heat exchanger, utilizes side heat exchanger and expansion valve, circulate and contain the cold-producing medium of more than 70 % by weight R32, by the pressure ratio of limit compression machine, to make the mass dryness fraction of the described cold-producing medium in the entrance side of compressor described in this higher limit higher than 0.85 be set to, the suction pressure of the described cold-producing medium in described compressor is higher and become lower
Have the program of the suction pressure calculation pressure ratio according to the described cold-producing medium in the discharge pressure of the described cold-producing medium in described compressor and described compressor,
With the rotary speed regulating described compressor, to make the program that the described pressure ratio of calculation is less than described higher limit.
5. the method for operation of air conditioner as claimed in claim 4, it is characterized in that, also have: at least by the calculation based on the rotary speed of the described suction pressure in the discharge pressure of the described cold-producing medium in the discharge temperature of described cold-producing medium in described compressor, described compressor, described compressor and described compressor, estimate the program of the mass dryness fraction of described cold-producing medium
With the rotary speed regulating described compressor, to make the program that the mass dryness fraction of the described cold-producing medium of presumption is higher than 0.85.
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| CN201710083422.3A CN106839499B (en) | 2013-03-27 | 2014-02-05 | The method of operation of air conditioner and air conditioner |
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| JP2013-067133 | 2013-03-27 | ||
| JP2013067133A JP5981376B2 (en) | 2013-03-27 | 2013-03-27 | Air conditioner and method of operating air conditioner |
| PCT/JP2014/052612 WO2014156313A1 (en) | 2013-03-27 | 2014-02-05 | Air conditioner and method for operating air conditioner |
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| CN106403334A (en) * | 2016-09-13 | 2017-02-15 | 克莱门特捷联制冷设备(上海)有限公司 | Refrigerating system capable of performing optimizing control on pressure ratio of water chilling unit |
| CN111059683A (en) * | 2019-12-03 | 2020-04-24 | 珠海格力电器股份有限公司 | Control method for preventing liquid impact of suction belt liquid of compressor and air conditioner |
| CN112228972A (en) * | 2020-10-21 | 2021-01-15 | 青岛海信日立空调系统有限公司 | Multi-split air conditioning system |
| CN113614469A (en) * | 2019-03-26 | 2021-11-05 | 富士通将军股份有限公司 | Air conditioner |
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| JP6266942B2 (en) * | 2013-10-10 | 2018-01-24 | 日立ジョンソンコントロールズ空調株式会社 | Air conditioner |
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| Publication number | Publication date |
|---|---|
| WO2014156313A1 (en) | 2014-10-02 |
| JP2014190632A (en) | 2014-10-06 |
| CN105074353B (en) | 2017-03-15 |
| CN106839499A (en) | 2017-06-13 |
| CN106839499B (en) | 2019-05-21 |
| JP5981376B2 (en) | 2016-08-31 |
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