CN106839499A - The method of operation of air conditioner and air conditioner - Google Patents
The method of operation of air conditioner and air conditioner Download PDFInfo
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- CN106839499A CN106839499A CN201710083422.3A CN201710083422A CN106839499A CN 106839499 A CN106839499 A CN 106839499A CN 201710083422 A CN201710083422 A CN 201710083422A CN 106839499 A CN106839499 A CN 106839499A
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- compressor
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- air conditioner
- control device
- mass dryness
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
-
- 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
-
- 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
- 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
-
- 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
-
- 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
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
-
- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Air Conditioning Control Device (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The present invention uses R32 to provide a kind of refrigerant, and the method for operation that can make the air conditioner small relative to the load of compressor and air conditioner is problem.A kind of air conditioner (1) and the method for operation of air conditioner (1), the air conditioner (1) is with being at least connected with compressor (14), outdoor heat converter (11), indoor heat converter (21), outdoor expansion valve (13) and indoor expansion valve (23), circulate the freeze cycle and control device (1a) of the refrigerant containing 70 weight % above R32, the pressure ratio of limitation compressor (14), the suction pressure of the refrigerant being set to so as to the higher limit for making the mass dryness fraction of the refrigerant of the entrance side of the compressor (14) during operating higher than 0.85 in compressor (14) is higher and lower.And, with when air conditioner (1) is operated, control device (1a) adjusts the rotary speed of compressor (14), to make pressure ratio such feature smaller than higher limit.
Description
The application be entitled " method of operation of air conditioner and air conditioner ", international filing date be on 2 5th, 2014,
International application no is PCT/JP2014/052612, the division of the application for a patent for invention that national applications number is 201480009568.8
Application.
Technical field
The present invention relates to air conditioner and the method for operation of air conditioner.
Background technology
For example, patent document 1 describe " compressor (1) suck mass dryness fraction more than 0.65 and less than 0.85 R32 refrigerants or
Mass dryness fraction at least containing 70 weight % above R32 is more than 0.65 and less than 0.85 mix refrigerant, and is compressed " (ginseng
See claims).
Citation
Patent document
Patent document 1：No. 3956589 publication of patent
The content of the invention
Invent problem to be solved
In the freeze cycle of air conditioner, the refrigerant shape of the heat exchanger outlet by will be played a role as evaporator
State control carrys out flexible Application evaporation latent heat to greatest extent near saturated gas, improves running efficiency.On the other hand, will be with
R410A(R32+R125：R32 (the HFC32 low compared to global warming coefficient GWP such as 50+50wt%)：Difluoromethane) as refrigeration
In the case of agent use, because the specific heat ratio of R32 is big, so, if in freeze cycle operating, making the refrigerant shape of evaporator outlet
State turns near saturated gas, then the refrigerant temperature of compressor discharge is 10~15 DEG C high or so compared with R410A.Therefore, exist
In the case that R32 is used as refrigerant, it is necessary to when suction port of compressor side makes the mass dryness fraction of refrigerant than using R410A
Mass dryness fraction is small.
Patent document 1 describes the sky that the mass dryness fraction of the refrigerant (R32) of suction port of compressor side is set as 0.65 to 0.85
Tune machine (refrigerator).
But, although if making the mass dryness fraction of suction port of compressor side diminish, the rising of discharge temperature can be suppressed, but, from
The liquid component of the refrigerant of suction port of compressor side suction is more.And, refrigerator oil in compressor by the liquid of refrigerant into
Divide dilution, viscosity reduction, greasy property is deteriorated, asked as the lifetime of compressor such as the abrasion in generation promotion mechanism portion
Topic.
Therefore, R32 is used in refrigerant by the present invention to provide one kind, can make what is diminished relative to the load of compressor
The method of operation of air conditioner and air conditioner is problem.
Means for solving the problems
In order to solve the problem, the present invention makes the freezing with the refrigerant circulation containing 70 weight % above R32
Circulation, the pressure ratio of setting limitation compressor, so as to the upper limit for making the mass dryness fraction of the refrigerant of the entrance side of compressor higher than 0.85
The air conditioner of value and the method for operation of air conditioner.And, with pressure ratio it is smaller than higher limit carry out operating such feature.
Invention effect
In accordance with the invention it is possible to provide one kind is used in refrigerant by R32, can make small relative to the load of compressor
The method of operation of air conditioner and air conditioner.
Brief description of the drawings
Fig. 1 is the figure of the structure for representing the air conditioner about the present embodiment.
Fig. 2 is the Mollier line chart (P-H line charts) of the air conditioner that R32 is used in refrigerant.
In the case that Fig. 3 is the pressure change of the refrigerant of the pressure and outlet side of the refrigerant of the entrance side of compressor
Mollier line chart.
Fig. 4 is the curve map of the relation of the suction pressure and pressure ratio that represent that suction mass dryness fraction is 0.85.
Fig. 5 is the figure of the variable for representing the presumption for being used in suction mass dryness fraction.
Fig. 6 is the flow chart for representing control device and the program for sucking mass dryness fraction being estimated by calculating.
Fig. 7 is the curve map of the relation for representing discharge temperature, condensation temperature and the discharge degree of superheat.
Specific embodiment
Below, embodiments of the invention are simultaneously simultaneously explained suitably referring to accompanying drawing.
Embodiment
Fig. 1 is the figure of the structure for representing the air conditioner about the present embodiment.
The air conditioner 1 of the present embodiment includes outdoor unit 10, indoor set 20 and control device 1a and constitutes.Outdoor unit 10 is wrapped
Include outdoor heat converter 11 (heat source side heat exchanger), outdoor fan 12, outdoor expansion valve 13, compressor 14, accumulator 15 with
And four-way valve 16 and constitute.On the other hand, indoor set 20 includes indoor heat converter 21 (utilizing side heat exchanger), indoor fan
22 and indoor expansion valve 23 and constitute.
And, outdoor unit 10 and indoor set 20 are connected by pipe arrangement 30,31.
In addition, the air conditioner 1 of the present embodiment is 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 constitute freeze cycle, used as cold at this
The refrigerant for freezing circulation circulation uses R32 (difluoromethane).
If in addition, for example, described patent document 1 describes at least system containing 70% (70 weight %) above R32
Cryogen, then can play and the refrigerant identical advantage containing 100%R32.Therefore, the air conditioner 1 of the present embodiment is used
Refrigerant to be not limited to the refrigerant containing 100%R32, or the refrigerant containing 70 weight % above R32 (mixed
Close refrigerant).
Control device 1a is by the starting of the outdoor fan 12 of outdoor unit 10, stopping, the valve opening of outdoor expansion valve 13
Regulation, the regulation of the rotary speed Fr of compressor 14, control of four-way valve 16 etc. control outdoor unit 10.In addition, control device
Starting, stopping, regulation of the valve opening of indoor expansion valve 23 that 1a passes through indoor fan 22 etc. controls indoor set 20.
In cooling operation, control device 1a control four-way valves 16, by the outlet side and outdoor heat converter of compressor 14
11 connections, and accumulator 15 and pipe arrangement 31 are connected.And, control device 1a drives compressor 14, outdoor fan 12 and interior
Fan 22.
The refrigerant (gas) compressed by compressor 14 via the inflow outdoor heat exchanger 11 of four-way valve 16, by with by room
The heat exchange of the outer gas of the air-supply of external fan 12 is cooled and condenses.The refrigerant (liquid) condensed by outdoor heat converter 11 via
Outdoor expansion valve 13 circulates in pipe arrangement 30, is imported into indoor set 20.
The refrigerant (liquid) for being imported into indoor set 20 is depressurized by indoor expansion valve 23, inflow indoor heat exchanger 21.Stream
Enter the refrigerant (liquid or gas-liquid two-phase state) of indoor heat converter 21 by with the room air blown by indoor fan 22
Heat exchange and vaporize.Now, the refrigerant (liquid) for being vaporized by indoor heat converter 21 captures heat of vaporization from room air, cold
But room air.
Circulated in pipe arrangement 31 by the vaporized refrigerant of indoor heat converter 21 (gas), outdoor unit 10 is imported into, four
Port valve 16 circulates, and flows into accumulator 15.Accumulator 15 as liquid refrigerant it is transiently superfluous flow into when storage refrigeration
The surge tank function of agent (liquid), accordingly, prevents the liquid compression of compressor 14.Therefore, in accumulator 15, refrigerant
Mass dryness fraction raise, mass dryness fraction refrigerant high flows into compressor 14.
In heating operation, control device 1a control four-way valves 16 connect the outlet side of compressor 14 and pipe arrangement 31, and
Outdoor heat converter 11 and accumulator 15 are connected.And, control device 1a drives compressor 14, outdoor fan 12 and indoor wind
Fan 22.
The refrigerant (gas) compressed by compressor 14 circulates via four-way valve 16 in pipe arrangement 31, is imported into indoor set 20.
Be directed to refrigerant (gas) inflow indoor heat exchanger 21 of indoor set 20, by with the interior blown by indoor fan 22
The heat exchange of air is cooled and condenses.Now, Interior Space is given by the chilled refrigerant (gas) of indoor heat converter 21
Gas condensation heat, heating indoor air.By the chilled refrigerant (liquid) of indoor heat converter 21 via indoor expansion valve 23,
Pipe arrangement 30 circulates, and is imported into outdoor unit 10.The refrigerant (liquid) for being directed to outdoor unit 10 is depressurized by outdoor expansion valve 13, stream
Enter outdoor heat converter 11.Be flowed into the refrigerant (liquid) of outdoor heat converter 11 by with by outdoor fan 12 blow it is outer
The heat exchange of gas and vaporize, via four-way valve 16 flow into accumulator 15.And, the refrigeration that improve mass dryness fraction because of accumulator 15
Agent (gas or gas-liquid two-phase state) flows into compressor 14.
In addition, what the temperature (discharge temperature Td) that outdoor unit 10 possesses the refrigerant to being discharged by compressor 14 was measured
The discharge that discharge temperature sensor 10ta, the pressure (discharge pressure Pd) to the refrigerant of the outlet side of compressor 14 are measured
The suction pressure that pressure sensor 10pa and the pressure (suction pressure Ps) to the refrigerant of the entrance side of compressor 14 are measured
Force snesor 10pb.
In addition, outdoor unit 10 possesses the condensation temperature Tc for the refrigerant to outdoor heat converter 11 (during cooling operation)
Or the temperature sensor 10tb that evaporating temperature Te (during heating operation) is measured, indoor set 20 possesses for indoor heat exchange
The temperature that the evaporating temperature Te (during cooling operation) or condensation temperature Tc (during heating operation) of the refrigerant of device 21 are measured
Sensor 20ta.
Discharge temperature Td is substituted alternatively, it is also possible to make, the chamber upper temp to compressor 14 is measured to use
Structure.
Fig. 2 is the Mollier line chart (P-H line charts) of the air conditioner that refrigerant uses R32.
For example, when air conditioner 1 (referring to Fig. 1) carries out heating operation, the refrigerant (gas) of the state in point A1 by
Compressor 14 compresses, and temperature (specific enthalpy) and pressure rise, and the state as point A2 is imported into indoor set 20.It is imported into indoor set
Indoors in heat exchanger 21 with substantially isobaric condensation, the state (liquid) as point A3 is imported into 20 refrigerant (gas)
Outdoor unit 10.In the state of point A3, the refrigerant (liquid) for being directed to outdoor unit 10 is depressurized by outdoor expansion valve 13, is turned into
The state of point A4, is vaporized by outdoor heat converter 11, the state (gas) as point A1.So, the sky of heating operation is being carried out
In tune machine 1, refrigerant (R32) simultaneously changes in the state of point A1~A4, simultaneously circulates.That is, being pressed by compressor 14
When the refrigerant (gas) of contracting (point A1 → A2) condenses (point A2 → A3) by the indoor heat converter 21 of indoor set 20, in heating chamber
Air.
Now, R32 due to compared with R410A specific heat ratio it is big, so, when being compressed by compressor 14 (point A1 → A2), press
The temperature (discharge temperature Td) height (Td1) of the refrigerant of the outlet side of contracting machine 14.For example, discharge temperature Td is high compared with R410A
10~15 DEG C or so.Accordingly, the discharge temperature Td that there is the refrigerant being compressed by exceedes the permission ceiling temperature of compressor 14,
Apply the situation of excessive load to compressor 14.Therefore, when refrigerant uses R32, it is desirable to make the outlet side of compressor 14
Discharge temperature Td low (for example, Td1 → Td2).
If for example, the valve opening of outdoor expansion valve 13 becomes big, promoting the temperature reduction in outdoor expansion valve 13, if Fig. 2
Shown in middle dotted line, the temperature of the refrigerant of the entrance side of compressor 14 or mass dryness fraction step-down (point A1 ') can be made.Accordingly, compressor
The discharge temperature Td step-downs (point A2 → A2 ') of the refrigerant of 14 outlet side.
But, if the state (point A1 ') of the refrigerant of the entrance side of compressor 14 turns into the temperature lower than saturated line C100
(or specific enthalpy), then the mass dryness fraction of the refrigerant of the entrance side of compressor 14 is lower than 1.00.
The containing ratio of the liquid component of the low refrigerant of mass dryness fraction is more, if the low refrigerant of mass dryness fraction flows into compressor 14, by
Liquid component contained by the refrigerant dilutes the refrigerator oil of compressor 14, produces the influence such as the abrasion in promotion mechanism portion.
That is, if the low refrigerant of mass dryness fraction flows into compressor 14, become big relative to the load of compressor 14.Thus, compressor 14
The superfluously low state of mass dryness fraction of refrigerant of entrance side and bad.
Therefore, the change state of abrasion (promote etc.) of the mechanical performance according to investigation compressor 14, compressor 14 enter
The phase of the viscosity reduction of the refrigerator oil in the mass dryness fraction (hereinafter referred to as " suction mass dryness fraction Xs ") and compressor 14 of the refrigerant of mouth side
The experiment of pass relation, makes the suction mass dryness fraction Xs's of the degraded in mechanical properties (or, deteriorate in allowed band) of compressor 14
Boundary value is 0.85.In other words, it is known that if suction mass dryness fraction Xs is higher than 0.85 (Xs ＞ 0.85), compressed can allow for giving
The scope of the influence of machine 14, can make small relative to the load of compressor 14.
Therefore, the air conditioner 1 of the present embodiment makes the structure operated in the state of high than 0.85 in suction mass dryness fraction Xs.Separately
Outward, the double dot dash line shown in Fig. 2 represents " etc. mass dryness fraction line C85 " that mass dryness fraction is 0.85.
Fig. 3 is the pressure of the refrigerant of the pressure (suction pressure Ps) and outlet side of the refrigerant of the entrance side of compressor
Mollier line chart in the case of (discharge pressure Pd) change.
For example, as shown in figure 3, the discharge temperature Td of the refrigerant of the outlet side of compressor 14 is being maintained into compressor 14
Allow ceiling temperature below ceiling temperature (Tdmax) in the case of, represent compressor 14 outlet side refrigerant shape
Point (the point A2-n of state：N=1,2,3 ...) generating state change, so that discharge temperature Td notationally limits temperature (Tdmax)
On thermoisopleth (single dotted broken line).
For example, in the case where the permission ceiling temperature of compressor 14 is for 120 DEG C, by the upper of the discharge temperature Td of refrigerant
Limit temperature is set as 100 DEG C or so (" Tdmax=100 [DEG C] ").
In addition, saturated line C100 is the line that mass dryness fraction turns into 1.00, " etc. mass dryness fraction line C85 " and the saturated line of mass dryness fraction 0.85 are represented
C100 is compared, and specific enthalpy is low (being illustrated with double dot dash line).And, suction mass dryness fraction Xs to be made is 0.85, as long as making compressor 14
The temperature (specific enthalpy) of the refrigerant of entrance turn into represent mass dryness fraction 0.85 etc. turn into the point of suction pressure Ps on mass dryness fraction line C85
(point A1-n：N=1,2,3 ...) shown in temperature.
Pressure ratio ε (the discharge pressure Pd/ suction pressures of compressor 14 are determined from such point A1-n for determining and point A2-n
Ps).That is, determining the pressure ratio ε relative to suction pressure Ps.
As shown in Figure 3, although suction pressure Ps (Ps1 → Ps2 → Ps3) higher, discharge pressure Pd (Pd1 high can more be made
→ Pd2 → Pd3), but compared with the ratio that suction pressure Ps rises, the ratio that discharge pressure Pd rises is small.That is, inhaling
Enter pressure Ps higher, be more necessary to make pressure ratio ε small.
Fig. 4 is to represent that suction mass dryness fraction turns into the curve map of the relation of 0.85 suction pressure and pressure ratio, and transverse axis represents suction
Enter pressure Ps, the longitudinal axis represents pressure ratio ε (discharge pressure Pd/ suction pressure Ps).
In addition, " the ε U " shown in Fig. 4 is the maximum of pressure ratio ε.In addition, solid line represents that suction mass dryness fraction Xs is higher than 0.85
The higher limit (pressure ratio upper limit ε max) of pressure ratio ε.Pressure ratio upper limit ε max are limitation pressure ratio ε, to make suction mass dryness fraction Xs
The higher limit higher than 0.85, limits the compression (the rotary speed Fr of compressor 14) of refrigerant, to make pressure ratio ε turn into pressure
Than below upper limit ε max, accordingly, Xs is higher than 0.85 for suction mass dryness fraction.
And, " PsL " is the suction pressure Ps that the pressure ratio ε for making suction mass dryness fraction Xs be 0.85 turns into maximum " ε U ".
That is, suction pressure Ps " PsL " regions below are that the pressure ratio ε for turning into 0.85 for making suction mass dryness fraction Xs exceedes maximum
The region of " ε U ".
In addition, " PsU " is the higher limit of the suction pressure Ps in air conditioner 1.And, suction pressure Ps's shown in Fig. 4
Lower limit " PsL " and higher limit " PsU ", the maximum of pressure ratio ε " ε U " are the characteristic values of air conditioner 1, are empty according to each
The design load that tune machine 1 is determined.
As shown in figure 4, pressure ratio upper limit ε max are lower limit " PsL " region (Ps≤PsL) below in suction pressure Ps
Maximum " ε U " (ε max=ε U) as pressure ratio, in region (Ps ＞ PsL) suction pressure Ps higher than lower limit " PsL ",
Represented by following formula (1).
ε max=ε U- (ε U- ε L)/(PsU-PsL) × (Ps-PsL) ... (1)
As shown in figure 3, because suction pressure Ps is higher, pressure ratio ε is smaller, so, as shown in figure 4, pressure ratio upper limit ε
Max is also suction pressure Ps higher and lower.
And, in the air conditioner 1 (referring to Fig. 1) of the present embodiment, control device 1a (referring to Fig. 1) is with compression refrigerant
(R32), so as to the rotary speed Fr for making pressure ratio upper limit ε max of the pressure ratio ε ratios as shown in formula (1) small, compressor 14 is operated
(referring to Fig. 1).That is, control device 1a adjusts the rotary speed Fr of compressor 14, to make pressure ratio ε than in pressure ratio
Limit ε max are small.Accordingly, the suction mass dryness fraction Xs of air conditioner 1 is maintained must be higher than 0.85.
In addition, control device 1a (referring to Fig. 1) can also be the rotary speed Fr for adjusting compressor 14, to make pressure ratio
Structures of the ε close to pressure ratio upper limit ε max.For example, it is smaller than pressure ratio upper limit ε max in pressure ratio ε, and require to increase air conditioning capacity
When, control device 1a can also be that the rotary speed Fr for making compressor 14 rises, and improve the structure of pressure ratio ε.So constituting
In the case of control device 1a, air conditioner 1 (referring to Fig. 1) is operated in suction mass dryness fraction Xs close in the state of 0.85.
In the air conditioner 1 shown in Fig. 1, discharge pressure sensor 10pa metering discharge pressure Pd, and suction pressure sensing
Device 10pb metering suction pressures Ps.And, control device 1a adjusts the rotary speed Fr of compressor 14, air conditioner 1 is heated fortune
Turn, to measure variable and discharge pressure sensor 10pa from the suction pressure Ps of suction pressure sensor 10pb meterings
Discharge pressure Pd variable calculation pressure ratio ε (discharge pressure Pd (variable)/suction pressure Ps (variable)) turn into
The pressure ratio upper limit ε max calculated by formula (1).
Here, or substitute discharge pressure sensor 10pa and suction pressure sensor 10pb a side or double
Side, and possess the structure of the sensor (temperature sensor) of metering condensation temperature Tc and evaporating temperature Te.
In heating operation, the temperature sensor 20ta that condensation temperature Tc can be possessed by indoor heat converter 21 is (referring to figure
1) measure, temperature sensor 10tb (referring to Fig. 1) meterings that evaporating temperature Te can be possessed by outdoor heat converter 11.
In general, temperature sensor is more cheap than pressure sensor, by substituting pressure sensor (discharge pressure sensor
10pa, suction pressure sensor 10pb), temperature in use sensor (temperature sensor 10tb, temperature sensor 20ta) can be obtained
To cheap air conditioner 1.
In addition, the air conditioner 1 (referring to Fig. 1) of the present embodiment can also be configured to control device 1a (referring to Fig. 1) by drilling
Calculate to estimate suction mass dryness fraction Xs.And, control device 1a can also be control compressor 14 (referring to Fig. 1), to make presumption
Structure suction mass dryness fraction Xs higher than 0.85.
Fig. 5 is the figure of the variable for representing the presumption for being used in suction mass dryness fraction, and Fig. 6 is to represent that control device is pushed away by calculating
Surely the flow chart of the program of mass dryness fraction is sucked.
In the case of the control device 1a presumption suction mass dryness fractions Xs that the air conditioner 1 of the present embodiment possesses, according to Fig. 6 institutes
The program shown, by with discharge temperature Td, discharge pressure Pd, suction pressure Ps, compressor 14 rotary speed Fr and refrigerant
(R32) the calculation based on physical property values, presumption suction mass dryness fraction Xs.And, control device 1a makes air conditioner 1 operate (example
Such as, heating operation), to make the suction mass dryness fraction Xs of presumption higher than 0.85.In addition, control device 1a is configured to make air conditioner
During 1 operating, in the circulation of regulation, presumption (calculation) suction mass dryness fraction Xs.
Referring to Fig. 6, illustrate control device 1a and estimated by calculating suction mass dryness fraction Xs program (suitably with reference to Fig. 1~
5)。
The variable of the discharge temperature Td that control device 1a is measured according to discharge temperature sensor 10ta, discharge pressure sensing
The variable and pressure of the suction pressure Ps that the variable of the discharge pressure Pd of device 10pa meterings, suction pressure sensor 10pb are measured
The variable of the rotary speed Fr of the rotary speed meter (not shown) metering that contracting machine 14 possesses, obtains discharge temperature Td, row
Go out rotary speed Fr (step S1) of pressure Pd, suction pressure Ps and compressor 14.
And, control device 1a is according to discharge temperature Td and discharge pressure Pd the calculation discharge gas specific enthalpy hd (steps for obtaining
Rapid S2).
As shown in figure 5, discharge gas specific enthalpy hd represents the specific enthalpy of the refrigerant of the outlet side of compressor 14.
In addition, control device 1a assumes suction mass dryness fraction Xs (step S3), and then, according to suction pressure Ps and the thing of refrigerant
Reason property value (physical property values of R32), the saturated air of the enthalpy of saturated liquid hsL and suction pressure Ps of calculation suction pressure Ps
Body specific enthalpy hsG (step S4).
For example, in step S3, control device 1a will be dry as suction in the presumed value of the suction mass dryness fraction Xs of preceding circulation calculation
Spend the assumed value of Xs.
In addition, control device 1a according to approximate expression set in advance, calculate suction pressure Ps enthalpy of saturated liquid hsL and
Saturated gas specific enthalpy hsG (step S4).It is preferred that the approximate expression is as the characteristic type approximate expression set in advance of R32.
And, control device 1a uses the saturated air of the suction mass dryness fraction Xs, the enthalpy of saturated liquid hsL of calculation and calculation that assume
Body specific enthalpy hsG, according to following formula (2), calculation suction specific enthalpy hs (step S5).
Xs=(hs-hsL)/(hsG-hsL) ... (2)
In addition, control device 1a is according to suction pressure Ps, the physical property values of suction the specific enthalpy hs and R32 of calculation, calculation
Suction specific entropy Ss (step S6), and then, the physical property values of suction specific entropy Ss, discharge pressure Pd and R32 according to calculation, calculation
Adiabatic compression discharges gas specific enthalpy hd ' (step S7).
It is configured to, in step s 6, control device 1a calculates suction pressure Ps and suction according to approximate expression set in advance
Suction specific entropy Ss in specific enthalpy hs.It is preferred that the approximate expression is the approximate expression being preset as the characteristic type of R32.
In addition, the adiabatic compression discharge gas specific enthalpy hd ' that control device 1a is calculated in the step s 7 is as shown in figure 5, represent
Enter to exercise efficiency (the compressor effect of compressor 14 in the refrigerant of the suction mass dryness fraction Xs assumed in step s3 to control device 1a
Rate η t) for " 1 " isentropic Compression (η t=1) in the case of discharge pressure Pd specific enthalpy.Constant entropy pressure is represented by dashed line in Fig. 5
Contracting.
In this case, the pressure of the suction mass dryness fraction Xs assumed in step s3 relative to control device 1a of compressor 14
Contracting engine efficiency (tentative efficiency) η treal' represented with following formula (3).
ηtreal'=(hd '-hs)/(hd-hs) ... (3)
Control device 1a is according to the discharge gas specific enthalpy hd for calculating in step s 2, the suction specific enthalpy calculated in step s 5
The hs and adiabatic compression discharge gas specific enthalpy hd ' for calculating in the step s 7, from the tentative efficiency eta t of formula (3) calculationreal' (step
S8)。
In addition, actual efficiency (actual efficiency) the η t of compressor 14realRepresented with following formula (4).
ηtreal=f (Xs, Pd, Ps, Fr) ... (4)
In addition, " f (Xs, Pd, Ps, Fr) " is by suction mass dryness fraction Xs, discharge pressure Pd, suction pressure Ps and compressor 14
Rotary speed Fr represented as variable compressor 14 characteristic function, be to be set in advance according to the form of each compressor 14
Fixed function.
And, control device 1a is according to the suction mass dryness fraction Xs for assuming in step s3, the discharge pressure for obtaining in step sl
The rotary speed Fr of power Pd, suction pressure Ps and compressor 14, from formula (4) calculation actual efficiency η treal(step S9).
The tentative efficiency eta t that control device 1a calculations are calculated in step s 8real' divided by the reality calculated in step s 9
Efficiency eta trealRatio (η treal’/ηtreal) (step S10), if the value is more than the lower limit of regulation, and in the higher limit of regulation
Below (step S10 → Yes), then the suction mass dryness fraction Xs that will be assumed in step s3 is determined as sucking the presumed value of mass dryness fraction Xs.
On the other hand, as ratio (the η t for calculating in step sloreal’/ηtreal) the not enough regulation of value lower limit or than rule
In the big situation of fixed higher limit (step S10 → No), control device 1a makes program be restored to step S3, assumes that suction is dry again
Degree Xs, performs the program of step S3~step S10.
For example, ratio (the η t that ought be calculated in step sloreal’/ηtreal) the not enough regulation of value lower limit in the case of,
Control device 1a will make suction mass dryness fraction Xs to tentative efficiency eta treal' become the value of big direction change as new suction mass dryness fraction
The assumed value of Xs.
Additionally, it is preferred that control device 1a and " η t in step sloreal’/ηtreal" lower limit of regulation that is compared with
And the calculation precision of suction mass dryness fraction Xs of the higher limit according to required by etc. suitably sets.If for example, making the lower limit be
" 0.999 ", makes higher limit for " 1.001 ", then control device 1a can estimate (calculation) suction according to the error of " ± 0.1% " and do
Degree Xs.
And, control device 1a (referring to Fig. 1) simultaneously estimates (calculation) suction mass dryness fraction Xs, one by the program shown in Fig. 6
Face makes air conditioner 1 (referring to Fig. 1) operate (for example, heating operation).Now, control device 1a controls air conditioner 1, to make presumption
Suction mass dryness fraction Xs it is higher than 0.85.Specifically, control device 1a adjusts the rotary speed Fr of compressor 14, adjusts pressure ratio ε,
It is higher than 0.85 by calculating estimated suction mass dryness fraction Xs to make.
Control device 1a declines by calculating estimated suction mass dryness fraction Xs, during close to 0.85, makes the rotation of compressor 14
Rotary speed Fr reductions, make pressure ratio ε step-downs.For example, control device 1a control compressors 14, to make with as the pressure ratio upper limit
The rotary speed Fr reductions of the compressor 14 of the rotary speed Fr operatings of ε max.Accordingly, discharge pressure Pd reductions, compressor 14
The refrigerant of entrance side is difficult to humidity, and suction mass dryness fraction Xs rises.
So, suction mass dryness fraction Xs is estimated by control device 1a (referring to Fig. 1), and operates air conditioner 1 (referring to Fig. 1),
To make the suction mass dryness fraction Xs of presumption higher than 0.85, more reliably can maintain suction mass dryness fraction Xs must be higher than 0.85.
In addition, the control device 1a (referring to Fig. 1) of the present embodiment can also make air conditioner 1 (referring to Fig. 1) heating operation,
To make discharge degree of superheat TdSH (=Td-Tc) of the difference as condensation temperature Tc and discharge temperature Td no more than set in advance
The structure of desired value.
Fig. 7 is the curve map of the relation for representing discharge temperature, condensation temperature and the discharge degree of superheat, (the row with the longitudinal axis as temperature
Go out temperature Td, condensation temperature Tc, discharge degree of superheat TdSH), it is discharge pressure Pd with transverse axis.
In addition, the solid line of Fig. 7 represents condensation temperature Tc, single dotted broken line represents discharge temperature Td.And, dotted line represents each
The desired value (target superheat degree SHtgt) of the discharge degree of superheat TdSH of discharge pressure Pd.As it was previously stated, discharge degree of superheat TdSH is
The difference (Td-Tc) of discharge temperature Td and condensation temperature Tc under identical discharge pressure Pd, its target superheat degree SHtgt is such as
Set as shown in dotted line in Fig. 7.
The intrinsic value (physical property values) of condensation temperature Tc is with discharge pressure Pd is accordingly determined refrigerant, control dress
Put the variable calculation condensation temperature Tc of the discharge pressure Pd that 1a can be measured according to discharge pressure sensor 10pa (referring to Fig. 1).
For example, the discharge pressure Pd that control device 1a can be measured according to discharge pressure sensor 10pa, discharges from representing
The approximate expression calculation condensation temperature Tc of the relation of pressure Pd and condensation temperature Tc.It is preferred that the approximate expression is as the characteristic type of R32
The approximate expression being preset.
In addition, in shown in Fig. 7, due to being setting (border discharge pressure in discharge pressure Pd：When Pda), row
Go out ceiling temperatures (Tdmax) of the temperature Td as compressor 14, so, it is higher than border discharge pressure (Pda) in discharge pressure Pd
Region, sets target degree of superheat SHtgt, to make discharge temperature Td turn into ceiling temperature (Tdmax).
Discharge temperature Td and root that control device 1a (referring to Fig. 1) is measured from discharge temperature sensor 10ta (referring to Fig. 1)
The condensation temperature Tc calculation discharge degrees of superheat TdSH calculated according to the variable of discharge pressure Pd.And, control device 1a makes air-conditioning
Machine 1 (referring to Fig. 1) heating operation, to make the discharge degree of superheat TdSH of calculation close to target superheat degree shown in dotted lines in Figure 7
SHtgt.For example, in the case where the discharge degree of superheat TdSH of calculation is lower than target superheat degree SHtgt, control device 1a makes outdoor
The valve opening of expansion valve 13 diminishes.Suppress the temperature reduction of the refrigerant of outdoor expansion valve 13, discharge temperature Td rises.The opposing party
Face, because suction pressure Ps and discharge pressure Pd are not changed in such degree, so, the change of condensation temperature Tc is small.According to
This, discharge degree of superheat TdSH (Td-Tc) rises, close to target superheat degree SHtgt.
So, control device 1a controls outdoor expansion valve 13, adjusts its valve opening, to make the discharge degree of superheat of calculation
TdSH is maintained at the vicinity of target superheat degree SHtgt.
For example, in the upper limit (ceiling temperature) of setting discharge temperature Td, the rotary speed of regulation compressor 14 (referring to Fig. 1)
Fr, so that in the case that discharge temperature Td turns into ceiling temperature, with the change of the rotary speed Fr of compressor 14, discharge pressure
Pd and discharge temperature Td changes.And, suction both mass dryness fraction Xs and discharge pressure Pd and discharge temperature Td accordingly change.According to
This, in order to will suction mass dryness fraction Xs maintain must be higher than 0.85, control device 1a (referring to Fig. 1) synthetically adjusts discharge pressure Pd and row
Go out temperature Td, the control of air conditioner 1 (referring to Fig. 1) becomes complicated.
On the other hand, in sets target degree of superheat SHtgt, the valve opening of regulation outdoor expansion valve 13 (referring to Fig. 1) makes row
Go out degree of superheat TdSH close in the case of target superheat degree SHtgt, discharge pressure Pd is not changed in such degree, discharge temperature
Td changes.Therefore, suction mass dryness fraction Xs and discharge pressure Pd accordingly changes.
Thus, control device 1a (referring to Fig. 1) maintains suction mass dryness fraction Xs as long as the valve opening of regulation outdoor expansion valve 13
Must be higher than 0.85, the control of air conditioner 1 (referring to Fig. 1) becomes simple.
In addition, as it was previously stated, make control device 1a (referring to Fig. 1) adjust compressor 14 rotary speed Fr, to make
Pressure ratio ε close to pressure ratio upper limit ε max structure, further, can also be control device 1a regulation outdoor expansion valve 13 valve open
Degree, to make discharge degree of superheat TdSH close to the structure of target superheat degree SHtgt.
For example, smaller than pressure ratio upper limit ε max in pressure ratio ε, the discharge degree of superheat TdSH of calculation is than target superheat degree
SHtgt hours, control device 1a rose the rotary speed Fr of compressor 14, improved pressure ratio ε, and make outdoor expansion valve 13
Valve opening diminishes, and discharge degree of superheat TdSH is increased.
According to the structure, pressure ratio ε is maintained at the vicinity of pressure ratio upper limit ε max, and discharge degree of superheat TdSH is maintained at
The vicinity of target superheat degree SHtgt.Accordingly, control device 1a (referring to Fig. 1) can be dry by the suction of air conditioner 1 (referring to Fig. 1)
Degree Xs is maintained close to 0.85 state, discharge temperature Td can be set into height.Accordingly, air conditioner 1 is most in discharge temperature Td
May be operated in the state of height, flexibly can use evaporation latent heat to maximum limit, realize the operating condition of efficiency high.
As described above, the control device 1a of the present embodiment shown in Fig. 1 is when 1 heating operation of air conditioner is made, control compression
Machine 14 and outdoor expansion valve 13, the rotary speed of regulation discharge temperature Td, discharge pressure Pd, suction pressure Ps and compressor 14
Fr, suction mass dryness fraction Xs is maintained must be higher than 0.85.Accordingly, even if in the case where R32 is used as refrigerant, it is also possible to will arrange
Go out temperature Td and maintain the ceiling temperature (Tdmax) of compressor 14 below.In addition, liquid component contained during refrigerant can be made
The load for giving compressor 14 is small.
In addition, the present invention is not limited to foregoing embodiment.For example, described embodiment is in order to be readily appreciated that to say
The bright present invention and the embodiment that is described in detail, are not necessarily limited to the implementation of the invention of the entire infrastructure for possessing illustrated
Example.
Alternatively, it is also possible to be the structure that a part for the structure of certain embodiment is replaced into other embodiments, in addition,
Can also be the structure that other embodiments are added in the structure of certain embodiment.
For example, although explanation above is the situation that air conditioner 1 (referring to Fig. 1) carries out heating operation, but, even if in sky
In the case that tune machine 1 carries out cooling operation, control device 1a (referring to Fig. 1) similarly controls air conditioner 1.
Control device 1a in the case where making air conditioner 1 carry out cooling operation, adjust compressor 14 rotary speed Fr with
And the valve opening of indoor expansion valve 23, suction mass dryness fraction Xs is maintained must be higher than 0.85, further, discharge degree of superheat TdSH is maintained
Near higher limit.
That is, control device 1a adjusts the rotary speed Fr of compressor 14, to make pressure ratio ε turn into according to formula
(1) the pressure ratio upper limit ε max for calculating.
In addition, control device 1a is calculated by the program shown in Fig. 6 and estimated suction mass dryness fraction Xs, air conditioner 1 is controlled, so as to
Make the suction mass dryness fraction Xs of presumption higher than 0.85.
Further, control device 1a adjusts the valve opening of indoor expansion valve 23, to make discharge degree of superheat TdSH close in advance
The target superheat degree SHtgt of setting.
So, control device 1a controls compressor 14 and indoor expansion valve 23, make the cooling operation of air conditioner 1.
In addition, the control device 1a (referring to Fig. 1) of the present embodiment is in the step S4 shown in Fig. 6, by presetting
Approximate expression, the structure of calculation enthalpy of saturated liquid hsL, but, for example, it is also possible to be that would indicate that suction pressure Ps and saturated solution ratio
Structure of the image storage of the relation of enthalpy hsL in storage part (not shown).
If making such structure, control device 1a can in the step S4 shown in Fig. 6, according to suction pressure Ps,
With reference to the image, calculation enthalpy of saturated liquid hsL.Hereby it is possible to negative when mitigating control device 1a calculation enthalpy of saturated liquid hsL
Lotus.
Equally, it is also possible to which the image for making the relation that would indicate that suction pressure Ps and saturated gas specific enthalpy hsG is stored not
The structure of the storage part for illustrating, can also be that the image of the relation that would indicate that suction pressure Ps and suction specific entropy Ss is stored not
The structure of the storage part for illustrating.
Image alternatively, it is also possible to be the relation that would indicate that discharge pressure Pd and condensation temperature Tc is stored (not shown)
The structure of storage part.
Additionally, the present invention is not limited to the invention of foregoing embodiment, can be in the scope of the purport for not departing from invention
Suitably it is designed change.
For example, as shown in Figure 1, although the compressor 14 of the air conditioner 1 of the present embodiment is provided in outdoor unit 10, but,
It can also be structure that compressor 14 is provided in indoor set 20.
Alternatively, it is also possible to be the structure for substituting four-way valve 16 and possessing multiple open and close valves (not shown).Possessing multiple
In the case of the structure of open and close valve, as long as making the outlet side and outdoor heat converter 11 at least possessed to connecting compressor 14
Open and close valve that open and close valve that pipe arrangement is opened and closed, the pipe arrangement to connection accumulator 15 and pipe arrangement 31 are opened and closed, connection is compressed
Open and close valve that the outlet side of machine 14 and the pipe arrangement of pipe arrangement 31 are opened and closed and to connection outdoor heat converter 11 and accumulator 15
The open and close valve that pipe arrangement is opened and closed this 4 structures of open and close valve.
Symbol description
1：Air conditioner；1a：Control device；11：Outdoor heat converter (heat source side heat exchanger)；13：Outdoor expansion valve is (swollen
Swollen valve)；14：Compressor；21：Indoor heat converter (utilizes side heat exchanger)；23：Indoor expansion valve (expansion valve)；Fr：Rotation
Speed；Pd：Discharge pressure；Ps：Suction pressure；SHtgt：Target superheat degree (desired value of the discharge degree of superheat)；Tc：Condensation temperature
Degree；Td：Discharge temperature；TdSH：The discharge degree of superheat；Xs：Suction mass dryness fraction (mass dryness fraction of the refrigerant of the entrance side of compressor)；ε：Pressure
Power ratio；εmax：The pressure ratio upper limit (higher limit of pressure ratio).
Claims (7)
1. a kind of air conditioner, it is characterised in that with freeze cycle and control device,
The freeze cycle has been at least connected with compressor, heat source side heat exchanger, using side heat exchanger and expansion valve, circulate
Refrigerant containing 70 weight % above R32,
In heating operation, the control device adjusts the rotary speed of the compressor, described in the compressor
The suction pressure of refrigerant is higher, then the pressure ratio of the compressor is smaller, and is controlled, to make the compressor
The mass dryness fraction of the refrigerant in entrance side is higher than 0.85.
2. a kind of air conditioner, it is characterised in that with freeze cycle and control device,
The freeze cycle has been at least connected with compressor, heat source side heat exchanger, using side heat exchanger and expansion valve, circulate
Refrigerant containing 70 weight % above R32,
In cooling operation, the control device adjusts the rotary speed of the compressor, described in the compressor
The suction pressure of refrigerant is higher, then the pressure ratio of the compressor is smaller, and is controlled, to make the compressor
The mass dryness fraction of the refrigerant in entrance side is higher than 0.85.
3. air conditioner as claimed in claim 1, it is characterised in that
The expansion valve includes the outdoor expansion valve of outside,
The control device is controlled by adjusting the rotary speed of the compressor and the valve opening of the outdoor expansion valve
System, so that the mass dryness fraction of the refrigerant in the entrance side for making the compressor is higher than 0.85.
4. air conditioner as claimed in claim 2, it is characterised in that
The expansion valve includes the indoor expansion valve of indoor,
The control device is controlled by adjusting the rotary speed of the compressor and the valve opening of the indoor expansion valve
System, so that the mass dryness fraction of the refrigerant in the entrance side for making the compressor is higher than 0.85.
5. air conditioner as claimed in claim 1 or 2, it is characterised in that
The control device is controlled, to make the mass dryness fraction of presumption higher than 0.85.
6. air conditioner as claimed in claim 1 or 2, it is characterised in that at least through with the refrigeration in the compressor
The suction pressure in discharge pressure, the compressor of the refrigerant in the discharge temperature of agent, the compressor and
Calculation based on the rotary speed of the compressor, estimates the mass dryness fraction, the rotary speed of the compressor is adjusted, to make
The mass dryness fraction of presumption is higher than 0.85.
7. the air conditioner as any one of claim 1 to 6, it is characterised in that the refrigerant includes 100% R32.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013067133A JP5981376B2 (en) | 2013-03-27 | 2013-03-27 | Air conditioner and method of operating air conditioner |
| JP2013-067133 | 2013-03-27 | ||
| CN201480009568.8A CN105074353B (en) | 2013-03-27 | 2014-02-05 | Air conditioner and the method for operation of air conditioner |
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| CN201480009568.8A Division CN105074353B (en) | 2013-03-27 | 2014-02-05 | Air conditioner and the method for operation of air conditioner |
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| CN106839499A true CN106839499A (en) | 2017-06-13 |
| CN106839499B CN106839499B (en) | 2019-05-21 |
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| CN201710083422.3A Active CN106839499B (en) | 2013-03-27 | 2014-02-05 | The method of operation of air conditioner and air conditioner |
| CN201480009568.8A Active CN105074353B (en) | 2013-03-27 | 2014-02-05 | Air conditioner and the method for operation of air conditioner |
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| Country | Link |
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| JP (1) | JP5981376B2 (en) |
| CN (2) | CN106839499B (en) |
| WO (1) | WO2014156313A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
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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 |
| JP6495064B2 (en) * | 2015-03-26 | 2019-04-03 | 三菱重工サーマルシステムズ株式会社 | Air conditioning system control device, air conditioning system, air conditioning system control program, and air conditioning system control method |
| EP3147587B1 (en) * | 2015-07-27 | 2018-03-21 | Mitsubishi Electric Corporation | Air conditioning device |
| JP6594698B2 (en) * | 2015-08-10 | 2019-10-23 | 三菱重工サーマルシステムズ株式会社 | Refrigeration and air conditioning equipment |
| 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 |
| CN108168146A (en) * | 2018-02-02 | 2018-06-15 | 韩军 | A kind of refrigeration and discharge superheat control method in heat pump unit |
| JP6975850B2 (en) * | 2019-01-17 | 2021-12-01 | 日立ジョンソンコントロールズ空調株式会社 | Air conditioner |
| JP7172664B2 (en) * | 2019-01-30 | 2022-11-16 | 株式会社富士通ゼネラル | AIR CONDITIONER, CONTROL DEVICE FOR AIR CONDITIONER, CONTROL METHOD AND PROGRAM THEREOF |
| JP6886129B2 (en) * | 2019-03-26 | 2021-06-16 | 株式会社富士通ゼネラル | Air conditioner |
| CN112066463A (en) * | 2020-09-18 | 2020-12-11 | 广东积微科技有限公司 | Control method and heat control device for chassis heater of air conditioner outdoor unit and air conditioner |
| CN112228972B (en) * | 2020-10-21 | 2022-04-19 | 青岛海信日立空调系统有限公司 | Multi-split air conditioning system |
| CN113654223B (en) * | 2021-07-19 | 2022-09-06 | 青岛海尔空调器有限总公司 | Method for determining target exhaust gas temperature |
| CN115930392A (en) * | 2022-12-22 | 2023-04-07 | 珠海格力电器股份有限公司 | Control method of air conditioning system, air conditioning system and medium |
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| Publication number | Publication date |
|---|---|
| JP2014190632A (en) | 2014-10-06 |
| CN105074353B (en) | 2017-03-15 |
| WO2014156313A1 (en) | 2014-10-02 |
| CN106839499B (en) | 2019-05-21 |
| CN105074353A (en) | 2015-11-18 |
| JP5981376B2 (en) | 2016-08-31 |
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Effective date of registration: 20180629 Address after: Tokyo, Japan, Japan Applicant after: Hitachi Johnson Controls Air Conditioning Co., Ltd. Address before: Hongkong aoteng Plaza No. 8 Linze street, Kowloon Bay China 12 floor Applicant before: Johnson Controls Hitachi air conditioning technology (Hongkong) Co., Ltd. |
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