CN105074353B - Air conditioner and the method for operation of air conditioner - Google Patents
Air conditioner and the method for operation of air conditioner Download PDFInfo
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- CN105074353B CN105074353B CN201480009568.8A CN201480009568A CN105074353B CN 105074353 B CN105074353 B CN 105074353B CN 201480009568 A CN201480009568 A CN 201480009568A CN 105074353 B CN105074353 B CN 105074353B
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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
-
- 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
-
- 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
- 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
-
- 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 cold-producing medium, and the method for operation that can make the air conditioner little 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), described air conditioner (1) have be 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 cold-producing medium containing the above R32 of 70 weight % freeze cycle and control device (1a), limit the pressure ratio of compressor (14), higher limit to make the mass dryness fraction of the cold-producing medium of the entrance side of the compressor (14) during operating higher than 0.85 is set to that the suction pressure of the cold-producing medium in compressor (14) is higher and lower.And, with when air conditioner (1) operates, control device (1a) adjusts the rotary speed of compressor (14), to make pressure ratio such feature less than higher limit.
Description
Technical field
The present invention relates to the method for operation of air conditioner and air conditioner.
Background technology
For example, patent documentation 1 describe " compressor (1) suction mass dryness fraction more than 0.65 and less than 0.85 R32 cold-producing mediums or
Mass dryness fraction at least containing the above R32 of 70 weight % is more than 0.65 and less than 0.85 mix refrigerant, and is compressed ".
Citation
Patent documentation
Patent documentation 1：No. 3956589 publication of patent
Content of the invention
Invent problem to be solved
In the freeze cycle of air conditioner, the cold-producing medium shape of the heat exchanger outlet by will play a role as vaporizer
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：Low R32 (the HFC32 of global warming coefficient GWP are compared 50+50wt%) etc.：Difluoromethane) as refrigeration
In the case of agent use, due to the specific heat ratio of R32 big, so, if operating in freeze cycle, make the cold-producing medium shape of evaporator outlet
State becomes near saturated gas, then the refrigerant temperature that compressor is discharged is high 10～15 DEG C or so compared with R410A.Therefore, exist
In the case that R32 is used as cold-producing medium, it is necessary to when suction port of compressor side makes the mass dryness fraction ratio of cold-producing medium use R410A
Mass dryness fraction is little.
Patent documentation 1 describes the sky that the mass dryness fraction of the cold-producing medium (R32) of suction port of compressor side is set as 0.65 to 0.85
Tune machine (fridge).
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 cold-producing medium of suction port of compressor side suction is more.And, the refrigerator oil in compressor by the liquid of cold-producing medium into
Dilution, viscosity is divided to reduce, greasy property is deteriorated, and is produced and is asked as the lifetimes of compressor such as the abrasion in promotion mechanism portion
Topic.
Therefore, R32 is used in cold-producing medium to provide one kind by the present invention, can make to diminish 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 circulation of the cold-producing medium containing the above R32 of 70 weight %
Circulation, sets the pressure ratio for limiting compressor, so as to the upper limit for making the mass dryness fraction of the cold-producing medium of the entrance side of compressor higher than 0.85
The method of operation of the air conditioner and air conditioner of value.And, with pressure ratio less than higher limit carry out such feature that operates.
Invention effect
In accordance with the invention it is possible to providing one kind is used in cold-producing medium by R32, the load relative to compressor can be made little
Air conditioner and the method for operation of air conditioner.
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 cold-producing medium.
In the case that Fig. 3 is the pressure change of the cold-producing medium of the pressure and outlet side of the cold-producing medium of the entrance side of compressor
Mollier line chart.
Fig. 4 is the curve chart 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 be represent control device by calculation come estimate suction mass dryness fraction program flow chart.
Fig. 7 is the curve chart of the relation for representing discharge temperature, condensation temperature and discharging the degree of superheat.
Specific embodiment
Below, embodiments of the invention are simultaneously explained suitably referring to accompanying drawing simultaneously.
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 off-premises station 10, indoor set 20 and control device 1a and constitutes.Off-premises station 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 cross valve 16 and constitute.On the other hand, indoor set 20 includes indoor heat converter 21 (using side heat exchanger), indoor fan
22 and indoor expansion valve 23 and constitute.
And, off-premises station 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 (using side heat exchanger) and indoor expansion valve 23 constitute freeze cycle, used as cold at this
The cold-producing medium for freezing circulation circulation uses R32 (difluoromethane).
In addition, for example, if described patent documentation 1 describes at least system containing 70% (70 weight %) above R32
Cryogen, then can play and the cold-producing medium identical advantage containing 100%R32.Therefore, the air conditioner 1 of the present embodiment is used
Cold-producing medium be not limited to the cold-producing medium containing 100%R32, or cold-producing medium containing the above R32 of 70 weight % is (mixed
Close cold-producing medium).
Control device 1a is by the starting of the outdoor fan 12 of off-premises station 10, stopping, the valve opening of outdoor expansion valve 13
Regulation, the regulation of rotary speed Fr of compressor 14, control of cross valve 16 etc. are controlling off-premises station 10.In addition, control device
1a controls indoor set 20 by the starting of indoor fan 22, stopping, regulation of the valve opening of indoor expansion valve 23 etc..
In cooling operation, control device 1a controls cross valve 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 cold-producing medium (gas) compressed by compressor 14 via 16 inflow outdoor heat exchanger 11 of cross valve, by with by room
The heat exchange of the exogenous QI of the air-supply of external fan 12 is cooled and condenses.The cold-producing medium (liquid) condensed by outdoor heat converter 11 via
Outdoor expansion valve 13 circulates in pipe arrangement 30, is imported into indoor set 20.
The cold-producing medium (liquid) for being imported into indoor set 20 is reduced pressure by indoor expansion valve 23, inflow indoor heat exchanger 21.Stream
Enter the cold-producing medium (liquid or gas-liquid two-phase state) of indoor heat converter 21 by with the room air that is blown by indoor fan 22
Heat exchange and vaporize.Now, the cold-producing medium (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 cold-producing medium of indoor heat converter 21 (gas), be imported into off-premises station 10, four
Port valve 16 circulates, and flows into accumulator 15.Accumulator 15 as liquid refrigerant 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, cold-producing medium
Mass dryness fraction raise, the high cold-producing medium of mass dryness fraction flows into compressor 14.
In heating operation, control device 1a controls cross valve 16, and the outlet side of compressor 14 and pipe arrangement 31 are connected, 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 cold-producing medium (gas) compressed by compressor 14 circulates in 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 with the interior that is blown by indoor fan 22
The heat exchange of air is cooled and condenses.Now, Interior Space is given by 21 chilled cold-producing medium (gas) of indoor heat converter
Gas condensation heat, heating indoor air.By 21 chilled cold-producing medium (liquid) of indoor heat converter via indoor expansion valve 23,
Pipe arrangement 30 circulates, and is imported into off-premises station 10.The cold-producing medium (liquid) for being directed to off-premises station 10 is reduced pressure by outdoor expansion valve 13, stream
Enter outdoor heat converter 11.The cold-producing medium (liquid) of outdoor heat converter 11 is flowed into by outer with blown by outdoor fan 12
The heat exchange of gas and vaporize, via cross 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, off-premises station 10 possesses what the temperature (discharge temperature Td) to the cold-producing medium that is discharged by compressor 14 was measured
Discharge temperature sensor 10ta, the discharge measured by the pressure (discharge pressure Pd) of the cold-producing medium of the outlet side of compressor 14
Pressure transducer 10pa and the suction pressure measured by the pressure (suction pressure Ps) of the cold-producing medium of the entrance side of compressor 14
Force transducer 10pb.
In addition, off-premises station 10 possesses condensation temperature Tc (during cooling operation) for the cold-producing medium to outdoor heat converter 11
Or the temperature sensor 10tb measured by evaporating temperature Te (during heating operation), indoor set 20 possesses for indoor heat exchange
The temperature measured by evaporating temperature Te (during cooling operation) or condensation temperature Tc (during heating operation) of the cold-producing medium of device 21
Sensor 20ta.
Discharge temperature Td is substituted alternatively, it is also possible to make, the chamber upper temp of compressor 14 is carried out measuring to use
Structure.
Fig. 2 is Mollier line chart (P-H line chart) of the cold-producing medium using the air conditioner of R32.
For example, when air conditioner 1 (referring to Fig. 1) carries out heating operation, the cold-producing medium (gas) of the state in point A1 by
Compressor 14 compresses, and temperature (specific enthalpy) and pressure rise, and become the state of point A2, are imported into indoor set 20.It is imported into indoor set
20 cold-producing medium (gas) becomes the state (liquid) of point A3, is imported into indoors in heat exchanger 21 with substantially isobaric condensation
Off-premises station 10.In the state of point A3, the cold-producing medium (liquid) for being directed to off-premises station 10 is reduced pressure by outdoor expansion valve 13, is become
The state of point A4, is vaporized by outdoor heat converter 11, becomes the state (gas) of point A1.So, in the sky for carrying out heating operation
In tune machine 1, cold-producing medium (R32) simultaneously changes in the state of point A1～A4, simultaneously circulates.That is, being pressed by compressor 14
When the cold-producing medium (gas) of contracting (point A1 → A2) condenses (point A2 → A3) by the indoor heat converter 21 of indoor set 20, heating is indoor
Air.
Now, R32 due to compared with R410A specific heat ratio big, so, when being compressed by compressor 14 (point A1 → A2), press
The temperature (discharge temperature Td) height (Td1) of the cold-producing medium of the outlet side of contracting machine 14.For example, discharge temperature Td height compared with R410A
10～15 DEG C or so.Accordingly, discharge temperature Td that there is the cold-producing medium being compressed by exceedes the permission ceiling temperature of compressor 14,
To the situation that compressor 14 applies excessive load.Therefore, when cold-producing medium uses R32, it is desirable to make the outlet side of compressor 14
Discharge temperature Td low (for example, Td1 → Td2).
For example, if the valve opening of outdoor expansion valve 13 becomes big, the temperature in outdoor expansion valve 13 is promoted to reduce, if Fig. 2
Shown in middle dotted line, temperature or the mass dryness fraction step-down (point A1 ') of the cold-producing medium of the entrance side of compressor 14 can be made.Accordingly, compressor
The discharge temperature Td step-down (point A2 → A2 ') of the cold-producing medium of 14 outlet side.
But, if the state of the cold-producing medium of the entrance side of compressor 14 (point A1 ') becomes the temperature lower than saturated line C100
(or specific enthalpy), 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 low cold-producing medium of mass dryness fraction is more, if the low cold-producing medium of mass dryness fraction flows into compressor 14, by
The refrigerator oil of compressor 14 is diluted by the liquid component contained by the cold-producing medium, and producing the abrasion in promotion mechanism portion etc. affects.?
That is, if the low cold-producing medium of mass dryness fraction flows into compressor 14, the load relative to compressor 14 becomes big.Thus, compressor 14
The superfluously low state of mass dryness fraction of cold-producing medium of entrance side bad.
Therefore, the change state of abrasion (promote etc.) according to the mechanical performance of investigation compressor 14, compressor 14 enter
The phase that the viscosity of the refrigerator oil in the mass dryness fraction (hereinafter referred to as " suction mass dryness fraction Xs ") of the cold-producing medium of mouth side and compressor 14 reduces
The experiment of pass relation, makes suction mass dryness fraction Xs 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 compressed can allow for giving higher than 0.85 (Xs ＞ 0.85)
The scope that machine 14 affects, can make the load relative to compressor 14 little.
Therefore, the structure operated in the state of high in suction mass dryness fraction Xs made than 0.85 by the air conditioner 1 of the present embodiment.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 cold-producing medium of the pressure (suction pressure Ps) and outlet side of the cold-producing medium of the entrance side of compressor
Mollier line chart in the case of (discharge pressure Pd) change.
For example, as shown in figure 3, discharge temperature Td of the cold-producing medium of the outlet side of compressor 14 is being maintained compressor 14
Allow ceiling temperature below ceiling temperature (Tdmax) in the case of, represent compressor 14 outlet side cold-producing medium shape
Point (the point A2-n of state：N=1,2,3 ...) generating state change, notationally limit temperature (Tdmax) so as to discharge temperature Td
On isothermal line (single dotted broken line).
For example, in the case where the permission ceiling temperature of compressor 14 is 120 DEG C, by the upper of discharge temperature Td of cold-producing medium
Limit temperature is set as 100 DEG C or so (" Tdmax=100 [DEG C] ").
In addition, saturated line C100 is mass dryness fraction become 1.00 line, represent " etc. mass dryness fraction line C85 " and the saturated line of mass dryness fraction 0.85
C100 is compared, specific enthalpy 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 cold-producing medium of entrance become represent mass dryness fraction 0.85 etc. become the point of suction pressure Ps on mass dryness fraction line C85
(point A1-n：N=1,2,3 ...) shown in temperature.
Determine pressure ratio ε (the discharge pressure Pd/ suction pressure of compressor 14 from the point A1-n and point A2-n for so determining
Ps).That is, determining pressure ratio ε relative to suction pressure Ps.
As shown in Figure 3, although suction pressure Ps higher (Ps1 → Ps2 → Ps3), discharge pressure Pd height (Pd1 can more be made
→ Pd2 → Pd3), but compared with the ratio risen with suction pressure Ps, the ratio that discharge pressure Pd rises is little.That is, inhaling
Enter pressure Ps higher, be more necessary to make pressure ratio ε little.
Fig. 4 is to represent that suction mass dryness fraction becomes the curve chart of 0.85 suction pressure and the relation of 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 is to limit pressure ratio ε, to make suction mass dryness fraction Xs
The higher limit higher than 0.85, limits the compression (rotary speed Fr of compressor 14) of cold-producing medium, to make pressure ratio ε become pressure
Than below upper limit ε max, accordingly, suction mass dryness fraction Xs is higher than 0.85.
And, " PsL " is suction pressure Ps that pressure ratio ε for making suction mass dryness fraction Xs be 0.85 becomes maximum " ε U ".?
That is, suction pressure Ps " PsL " area below is to exceed maximum for pressure ratio ε for making suction mass dryness fraction Xs become 0.85
The region of " ε U ".
In addition, " PsU " is the higher limit of suction pressure Ps in air conditioner 1.And, suction pressure Ps shown in Fig. 4
Lower limit " PsL " and higher limit " PsU ", the maximum " ε U " of pressure ratio ε are the characteristic values of air conditioner 1, are empty according to each
The design load that tune machine 1 determines.
As shown in figure 4, pressure ratio upper limit ε max is lower limit " PsL " area below (Ps PsL) in suction pressure Ps
Become the maximum " ε U " (ε max=ε U) of pressure ratio, in the suction pressure Ps region higher than lower limit " PsL " (Ps ＞ PsL),
Represented by following formula (1).
ε max=ε U- (ε U- ε L)/(PsU-PsL) × (Ps-PsL) ... (1)
As shown in figure 3, as 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 (referring to Fig. 1) of the present embodiment, control device 1a (referring to Fig. 1) is with compression refrigerant
(R32), rotary speed Fr to make pressure ratio upper limit ε max of the pressure ratio ε ratio shown in formula (1) little, operate compressor 14
(referring to Fig. 1).That is, control device 1a adjusts rotary speed Fr of compressor 14, to make pressure ratio ε than in pressure ratio
ε max are little for limit.Accordingly, 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 rotary speed Fr for adjusting compressor 14, to make pressure ratio
ε is close to the structure of pressure ratio upper limit ε max.For example, less 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 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) operates in the state of suction mass dryness fraction Xs is close to 0.85.
In the air conditioner 1 shown in Fig. 1, discharge pressure sensor 10pa measures discharge pressure Pd, and suction pressure sensing
Device 10pb measures suction pressure Ps.And, control device 1a adjusts rotary speed Fr of compressor 14, makes air conditioner 1 heat fortune
Turn, to make variable and the metering of discharge pressure sensor 10pa from 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)) become
The pressure ratio upper limit ε max calculated by formula (1).
, or the side or double of discharge pressure sensor 10pa and suction pressure sensor 10pb is substituted here
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 transducer, by substituting pressure transducer (discharge pressure sensor
10pa, suction pressure sensor 10pb), using temperature sensor (temperature sensor 10tb, temperature sensor 20ta), can obtain
Arrive 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
The suction mass dryness fraction Xs structure 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 calculation
Surely the flow chart for sucking the program of mass dryness fraction.
In the case of 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 that shows, by with discharge temperature Td, discharge pressure Pd, suction pressure Ps, rotary speed Fr of compressor 14 and cold-producing medium
(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), suction mass dryness fraction Xs to make presumption is 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 estimated by calculation suction mass dryness fraction Xs program (suitably with reference to Fig. 1～
5).
The variable of discharge temperature Td that control device 1a is measured according to discharge temperature sensor 10ta, discharge pressure sensing
The variable of discharge pressure Pd of device 10pa meterings, the variable of suction pressure Ps of suction pressure sensor 10pb meterings and pressure
The variable of rotary speed Fr of the rotary speed meter metering (not shown) 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 discharges gas specific enthalpy hd (step according to the discharge temperature Td and discharge pressure Pd calculation for obtaining
Rapid S2).
As shown in figure 5, discharge 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 assumes suction mass dryness fraction Xs (step S3), and then, according to suction pressure Ps and the thing of cold-producing medium
Reason property value (physical property values of R32), calculates the enthalpy of saturated liquid hsL of suction pressure Ps and the saturated air of suction pressure Ps
Body specific enthalpy hsG (step S4).
For example, in step S3, control device 1a will be dry as suction for the presumed value of suction mass dryness fraction Xs in front circulation calculation
The assumed value of degree Xs.
In addition, control device 1a according to approximate expression set in advance, calculate the enthalpy of saturated liquid hsL of suction pressure Ps and
Saturated gas specific enthalpy hsG (step S4).It is preferred that the approximate expression is the characteristic type approximate expression set in advance as R32.
And, saturated airs of the control device 1a using suction mass dryness fraction Xs, the enthalpy of saturated liquid hsL of calculation and calculation for assuming
Body specific enthalpy hsG, according to following formula (2), calculation suction specific enthalpy hs (step S5).
Xs=(hs-hsL)/(hsG-hsL) ... (2)
In addition, physical property values of the control device 1a according to suction pressure Ps, suction specific enthalpy hs of calculation and R32, calculation
Suction specific entropy Ss (step S6), and then, according to the physical property values of suction specific entropy Ss, discharge pressure Pd and R32 of calculation, calculation
Adiabatic compression discharges gas specific enthalpy hd ' (step S7).
It is configured to, in step s 6, control device 1a is according to approximate expression set in advance, calculation suction pressure Ps and suction
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 that control device 1a is calculated in the step s 7 discharges gas specific enthalpy hd ' as shown in figure 5, representing
In efficiency (the compressor effect that the cold-producing medium of suction mass dryness fraction Xs assumed in step s3 by control device 1a enters to exercise compressor 14
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 suction mass dryness fraction Xs for being assumed relative to control device 1a in step s3 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 suction specific enthalpy that discharges gas specific enthalpy hd, calculate in step s 5 that calculates in step s 2
Hs and the adiabatic compression for calculating in the step s 7 discharge gas specific enthalpy hd ', from tentative efficiency eta t of formula (3) calculationreal' (step
S8).
In addition, efficiency (actual efficiency) the η t of the reality 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 represent as variable compressor 14 characteristic function, be to be set according to the form of each compressor 14 in advance
Fixed function.
And, control device 1a is according to suction mass dryness fraction Xs for assuming in step s3, the discharge pressure for obtaining in step sl
Rotary speed Fr of power Pd, suction pressure Ps and compressor 14, calculates actual efficiency η t from formula (4)real(step S9).
Tentative efficiency eta t that control device 1a calculations are calculated in step s 8real' divided by the reality that calculates in step s 9
Efficiency eta trealRatio (η treal’/ηtreal) (step S10), if the value is more than the lower limit of regulation, and the higher limit in regulation
Below (step S10 → Yes), then suction mass dryness fraction Xs for assuming in step s3 is determined as the presumed value of suction 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 again suction is dry
Degree Xs, the program of execution step S3～step S10.
For example, as ratio (the η t for calculating 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 higher limit is suitably set according to required calculation precision of suction mass dryness fraction Xs etc..For example, if making the lower limit be
" 0.999 ", makes higher limit for " 1.001 ", then control device 1a can estimate (calculation) suction and do according to the error of " ± 0.1% "
Degree Xs.
And, control device 1a (referring to Fig. 1) simultaneously sucks mass dryness fraction Xs by program presumption (calculation) shown in Fig. 6, and one
Face makes air conditioner 1 (referring to Fig. 1) operating (for example, heating operation).Now, control device 1a controls air conditioner 1, to make presumption
Suction mass dryness fraction Xs higher than 0.85.Specifically, control device 1a adjusts rotary speed Fr of compressor 14, adjusts pressure ratio ε,
Higher than 0.85 by calculating estimated suction mass dryness fraction Xs to make.
Control device 1a is being declined by calculating estimated suction mass dryness fraction Xs, when being close to 0.85, makes the rotation of compressor 14
Rotary speed Fr reduces, and makes pressure ratio ε step-down.For example, control device 1a controls compressor 14, to make to become the pressure ratio upper limit
Rotary speed Fr of the compressor 14 of the rotary speed Fr operating of ε max reduces.Accordingly, discharge pressure Pd reduces, compressor 14
The cold-producing medium of entrance side is difficult to humidity, and suction mass dryness fraction Xs rises.
So, by control device 1a (referring to Fig. 1) presumption suction mass dryness fractions Xs, and air conditioner 1 (referring to Fig. 1) operating is made,
Suction mass dryness fraction Xs to make presumption is higher than 0.85, and 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 less than set in advance
The structure of desired value.
Fig. 7 is the curve chart of the relation for representing discharge temperature, condensation temperature and discharging the degree of superheat, (the row with the longitudinal axis as temperature
Go out temperature Td, condensation temperature Tc, discharge degree of superheat TdSH), with transverse axis as discharge pressure Pd.
In addition, the solid line of Fig. 7 represents that condensation temperature Tc, single dotted broken line represent discharge temperature Td.And, dotted line represents each
The desired value (target superheat degree SHtgt) of discharge degree of superheat TdSH of discharge pressure Pd.As it was previously stated, discharge degree of superheat TdSH being
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.
Condensation temperature Tc is the intrinsic value of the cold-producing medium accordingly determined with discharge pressure Pd (physical property values), control dress
Variable calculation condensation temperature Tc of discharge pressure Pd that 1a can be measured is put according to discharge pressure sensor 10pa (referring to Fig. 1).
For example, control device 1a can be discharged from representing according to discharge pressure Pd of discharge pressure sensor 10pa metering
Approximate expression calculation condensation temperature Tc of the relation of pressure Pd and condensation temperature Tc.It is preferred that the approximate expression is the characteristic type as R32
The approximate expression being preset.
In addition, in shown in Fig. 7, due to being that setting (discharges pressure in border in discharge pressure Pd：When Pda), row
Going out temperature Td becomes the ceiling temperature (Tdmax) of compressor 14, so, it is high pressure (Pda) to be discharged in discharge pressure Pd than border
Region, target setting degree of superheat SHtgt, to make discharge temperature Td become 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)
Degree of superheat TdSH is discharged according to the condensation temperature Tc calculation that the variable of discharge pressure Pd is calculated.And, control device 1a makes air-conditioning
Machine 1 (referring to Fig. 1) heating operation, to make discharge degree of superheat TdSH of calculation be close to target superheat degree shown in dotted lines in Figure 7
SHtgt.For example, in the case where 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.The temperature of the cold-producing medium of outdoor expansion valve 13 is suppressed to reduce, discharge temperature Td rises.The opposing party
Face, as suction pressure Ps and discharge pressure Pd are not changed in such degree, so, the change of condensation temperature Tc is little.According to
This, discharges degree of superheat TdSH (Td-Tc) and rises, be 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) for setting discharge temperature Td, the rotary speed of compressor 14 (referring to Fig. 1) is adjusted
Fr, so that in the case that discharge temperature Td becomes ceiling temperature, with the change of rotary speed Fr of compressor 14, discharge pressure
Pd and the change of discharge temperature Td.And, suction mass dryness fraction Xs is accordingly changed with both discharge pressure Pd and discharge temperature Td.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, the valve opening of outdoor expansion valve 13 (referring to Fig. 1), the row of making, in target setting degree of superheat SHtgt, are adjusted
Go out in the case that degree of superheat TdSH is close to target superheat degree SHtgt, discharge pressure Pd is not changed in such degree, discharge temperature
Td changes.Therefore, suction mass dryness fraction Xs is accordingly changed with discharge pressure Pd.
Thus, suction mass dryness fraction Xs is maintained by control device 1a (referring to Fig. 1) as long as adjusting the valve opening of 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 is close to the structure of pressure ratio upper limit ε max, further, can also be control device 1a adjust outdoor expansion valve 13 valve open
Degree, to make discharge degree of superheat TdSH be close to the structure of target superheat degree SHtgt.
For example, less than pressure ratio upper limit ε max in pressure ratio ε, discharge degree of superheat TdSH of calculation is than target superheat degree
SHtgt hours, control device 1a rise rotary speed Fr of compressor 14, improve 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, discharges degree of superheat TdSH and 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 to height.Accordingly, air conditioner 1 is most in discharge temperature Td
May operate in the state of height, can flexibly 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, adjust the rotary speed of 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 cold-producing medium, it is also possible to will row
Go out temperature Td and maintain the ceiling temperature (Tdmax) of compressor 14 below.In addition, contained liquid component in cold-producing medium can be made
The load for giving compressor 14 is little.
In addition, the present invention is not limited to aforesaid embodiment.For example, described embodiment is said in order to easy to understand
The bright present invention and the embodiment that is described in detail, are not necessarily limited to the enforcement 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, maintaining degree of superheat TdSH is discharged
Near higher limit.
That is, control device 1a adjusts rotary speed Fr of compressor 14, to make pressure ratio ε become 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 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 be close in advance
The target superheat degree SHtgt of setting.
So, control device 1a control compressors 14 and indoor expansion valve 23, make 1 cooling operation of air conditioner.
In addition, the control device 1a (referring to Fig. 1) of the present embodiment is in step S4 shown in Fig. 6, by presetting
Approximate expression, calculate enthalpy of saturated liquid hsL structure, but, for example, it is also possible to be to would indicate that suction pressure Ps and saturated solution ratio
The image of the relation of enthalpy hsL is stored in the structure of storage part (not shown).
If making such structure, control device 1a can in step S4 shown in Fig. 6, according to suction pressure Ps,
With reference to the image, enthalpy of saturated liquid hsL is calculated.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 in 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 in not
The structure of the storage part for illustrating.
(not shown) alternatively, it is also possible to be that the image of the relation that would indicate that discharge pressure Pd and condensation temperature Tc is stored in
The structure of storage part.
Additionally, the present invention is not limited to the invention of aforesaid embodiment, can be in the scope of the purport without departing from invention
Change is suitably designed.
For example, 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, but,
It can also be structure that compressor 14 is provided in indoor set 20.
Alternatively, it is also possible to be substitute cross valve 16 and possess the structure of multiple open and close valves (not shown).Multiple possessing
In the case of the structure of open and close valve, as long as make at least possessing outlet side and outdoor heat converter 11 to connection compressor 14
Open and close valve that pipe arrangement is opened and closed, the open and close valve is opened and closed by the pipe arrangement for connecting accumulator 15 and pipe arrangement 31, to connection compression
Open and close valve that the pipe arrangement of the outlet side of machine 14 and pipe arrangement 31 is opened and closed and to connecting outdoor heat converter 11 and accumulator 15
The structure of the open and close valve that pipe arrangement is opened and closed this 4 open and close valves.
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 (using side heat exchanger)；23：Indoor expansion valve (expansion valve)；Fr：Rotation
Speed；Pd：Discharge pressure；Ps：Suction pressure；SHtgt：Target superheat degree (discharges the desired value of the degree of superheat)；Tc：Condensation temperature
Degree；Td：Discharge temperature；TdSH：Discharge the degree of superheat；Xs：Suction mass dryness fraction (mass dryness fraction of the cold-producing medium of the entrance side of compressor)；ε：Pressure
Power ratio；εmax：The pressure ratio upper limit (higher limit of pressure ratio).
Claims (5)
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, has utilized side heat exchanger and expansion valve, circulates
Cold-producing medium containing the above R32 of 70 weight %,
The suction pressure of cold-producing medium higher limit being set in the compressor higher limit becomes lower,
The pressure ratio of the compressor is constrained to the higher limit mass dryness fraction ratio for making the cold-producing medium in the entrance side of the compressor
0.85 is high,
In the running, the control device
The rotary speed of the compressor is adjusted, to make the pressure ratio less than the higher limit.
2. air conditioner as claimed in claim 1, it is characterised in that set the discharge of the cold-producing medium from the compressor
Temperature has deducted the discharge degree of superheat after the condensation temperature corresponding with the discharge pressure of the cold-producing medium in the compressor
Desired value,
In the running, the control device
The rotary speed of the compressor is adjusted, to make the pressure ratio be close to the higher limit, and the expansion valve is adjusted
Valve opening, so as to make described discharge the degree of superheat be close to the desired value.
3. air conditioner as claimed in claim 1 or 2, it is characterised in that in the running, the control device
Discharge temperature at least through the cold-producing medium in the compressor,
The discharge pressure of the cold-producing medium in the compressor,
The suction pressure in the compressor
Rotary speed with the compressor
Based on calculation, estimate the mass dryness fraction,
Further, the rotary speed of the compressor is adjusted, and the mass dryness fraction to make presumption is higher than 0.85.
4. a kind of method of operation of air conditioner, it is characterised in that executed by the control device of air conditioner, the air conditioner has cold
Freeze circulation, the freeze cycle has been at least connected with compressor, heat source side heat exchanger, has utilized side heat exchanger and expansion valve, stream
Turn the cold-producing medium containing the above R32 of 70 weight %, the suction of cold-producing medium higher limit being set in the compressor
The pressure higher limit becomes lower, and the pressure ratio of the compressor is constrained to make the compressor by the higher limit
The mass dryness fraction of the cold-producing medium in entrance side is higher than 0.85,
There is the suction according to the cold-producing medium in the discharge pressure and the compressor of the cold-producing medium in the compressor
Enter pressure calculation pressure ratio program,
With the rotary speed for adjusting the compressor, so as to the program for making the pressure ratio of calculation less than the higher limit.
5. the method for operation of air conditioner as claimed in claim 4, it is characterised in that also have：At least through with the compression
In the discharge pressure of the cold-producing medium in the discharge temperature of the cold-producing medium in machine, the compressor, the compressor
Calculation based on the rotary speed of the suction pressure and the compressor, estimates the program of the mass dryness fraction of the cold-producing medium
With the rotary speed for adjusting the compressor, so as to the program for making the mass dryness fraction of the cold-producing medium of presumption 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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| CN201710083422.3A Active CN106839499B (en) | 2013-03-27 | 2014-02-05 | The method of operation of air conditioner 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 |
| WO2017017767A1 (en) * | 2015-07-27 | 2017-02-02 | 三菱電機株式会社 | 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 |
| CN111059683B (en) * | 2019-12-03 | 2021-04-02 | 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 |
| 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 |
| CN115930392B (en) * | 2022-12-22 | 2024-11-05 | 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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| JP2003240310A (en) * | 2002-02-20 | 2003-08-27 | Hitachi Ltd | Air conditioner and outdoor machine used in the same |
| JP2003262385A (en) * | 2002-03-12 | 2003-09-19 | Hitachi Ltd | Air conditioner |
| CN101408355B (en) * | 2007-10-09 | 2010-09-01 | 株式会社神户制钢所 | Freezing device and running method thereof |
| CN102667354A (en) * | 2009-09-28 | 2012-09-12 | 东芝开利株式会社 | Air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106839499B (en) | 2019-05-21 |
| JP2014190632A (en) | 2014-10-06 |
| JP5981376B2 (en) | 2016-08-31 |
| CN106839499A (en) | 2017-06-13 |
| WO2014156313A1 (en) | 2014-10-02 |
| CN105074353A (en) | 2015-11-18 |
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