CN101395435A - Refrigerating apparatus - Google Patents
Refrigerating apparatus Download PDFInfo
- Publication number
- CN101395435A CN101395435A CNA2007800081990A CN200780008199A CN101395435A CN 101395435 A CN101395435 A CN 101395435A CN A2007800081990 A CNA2007800081990 A CN A2007800081990A CN 200780008199 A CN200780008199 A CN 200780008199A CN 101395435 A CN101395435 A CN 101395435A
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- Prior art keywords
- heat exchanger
- cold
- indoor
- producing medium
- side heat
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Classifications
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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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion 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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0232—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with bypasses
- F25B2313/02323—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with bypasses during heating
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
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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
- F25B2500/00—Problems to be solved
- F25B2500/24—Low amount of refrigerant in the system
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2104—Temperatures of an indoor room or compartment
Abstract
A refrigerating apparatus including a refrigerant circuit (10) in which such a refrigerating cycle that the pressure of a refrigerant discharged from a compressor (22) is increased to a critical value or higher. When the heating operation is performed in a first indoor heat exchanger (33a) and a second indoor heat exchanger (33b) is stopped to operate, an indoor expansion valve (34b) corresponding to the indoor heat exchanger (33b) being stopped to operate is fully closed.
Description
Technical field
[0001] the present invention relates to a kind ofly can make a plurality of refrigerating plants that utilize the side heat exchanger separately to heat action, particularly relate to the refrigerant liquid eliminate indigestion in the side heat exchanger that utilizes that is in halted state and deposit countermeasure.
Background technology
[0002] cold-producing medium is circulated and carry out the refrigerating plant of kind of refrigeration cycle, be widely used in aircondition etc.As this aircondition, have that a plurality of indoor units are that be connected with this outdoor unit in outdoor relatively unit mode arranged side by side, so-called many formulas aircondition.
[0003] for example, the aircondition of patent documentation 1 comprises an outdoor unit with compressor and outdoor heat converter (heat source side heat exchanger) and has two indoor units of indoor heat converter (utilizing the side heat exchanger) separately.On two laterals that two indoor heat converters connect respectively, be respectively arranged with motor-driven valve in mode corresponding to each indoor heat converter.
[0004] this aircondition can make each indoor units separately carry out warming operation by the aperture of controlling each motor-driven valve.Particularly, for example when making two indoor units carry out warming operation simultaneously, make both sides' motor-driven valve reach the aperture of regulation and become open mode, cold-producing medium is actively delivered in both sides' the indoor heat converter.Consequently, the cold-producing medium that flows through two indoor heat converters is to the room air heat release, to each indoor heating.On the other hand, for example when only making an indoor units carry out warming operation, open motor-driven valve, and close motor-driven valve corresponding to the indoor units that will stop corresponding to the indoor units that will turn round.Consequently, cold-producing medium is only given the indoor heat converter of the indoor units that will turn round, and the cold-producing medium in this indoor heat converter is to the room air heat release.
Patent documentation 1: Japanese publication communique spy opens flat 8-159590 communique
[0005] when only making an indoor units continuous running as mentioned above, in some cases, the cold-producing medium in the indoor heat converter that stops can condensation, cold-producing medium liquefaction appears and lodge in the indoor heat converter, so-called refrigerant liquid eliminate indigestion deposits cash and resembles.If so liquefaction and accumulating down in the indoor heat converter that stops of cold-producing medium, the refrigerant amount of (heating action) indoor heat converter that flows through running is just a bit not enough, makes the heating capacity of this indoor units descend.
Summary of the invention
[0006] the present invention, described problem researchs and develops out in order to solve just.Its purpose is: prevent that cold-producing medium from utilizing in the side heat exchanger liquefaction and accumulate what stop.
[0007] first invention, with following refrigerating plant as prerequisite, that is: comprise that refrigerant loop 10, this refrigerant loop 10 are to make to have respectively in heat source side loop 21 modes arranged side by side that have compressor 22 and heat exchanger of heat source 23 relatively to utilize side heat exchanger 33a, 33b and utilize motor-driven valve 34a, 34b a plurality of of side heat exchanger 33a, 33b to utilize side loop 31a, 31b to be connected with described heat source side loop 21 and constitute corresponding to this; This refrigerating plant can make each utilize side heat exchanger 33a, 33b branch to open the heating of carrying out from utilizing the cold-producing medium heat release in side heat exchanger 33a, the 33b and move.Described refrigerant loop 10 constitutes: carry out pressure with the ejection cold-producing medium of compressor 22 and be located at kind of refrigeration cycle more than the critical pressure.
[0008] in the refrigerating plant of first invention, can carry out with all utilize side heat exchanger 33a, 33b heat action running (below, this running is called " all running ") and when stopping a part utilizing the heating action of side heat exchanger 33b, utilize the running that side heat exchanger 33a heats action (below, this running is called " part running ") with remaining.
[0009] particularly, by utilizing motor-driven valve 34a, the 34b of side heat exchanger 33a, 33b to reach the regulation aperture respectively, just can carry out described whole running corresponding to each.In other words, when whole running, the ejection cold-producing medium of compressor 22 flows through each and utilizes side heat exchanger 33a, 33b.Consequently, flow through the heat release respectively of each cold-producing medium that utilizes side heat exchanger 33a, 33b, each utilizes side heat exchanger 33a, 33b to heat action.Consequently, each utilizes side heat exchanger 33a, 33b for example to each indoor heating.
[0010] on the other hand, to make each utilize a part among side heat exchanger 33a, the 33b to utilize under the situation that the heating action of side heat exchanger 33b stops, when will being made as the aperture of small aperture or contract fully, make aperture reach the regulation aperture corresponding to the motor-driven valve 34a that utilizes side heat exchanger 33a that will heat action corresponding to the aperture of the motor-driven valve 34b that utilizes side heat exchanger 33b that will stop.Consequently, cold-producing medium only flow through basically heat action utilize side heat exchanger 33a, and the side heat exchanger 33b that utilizes that stops not to heat action.
[0011] under the situation of carrying out the running of described part, along with reducing of the aperture of the motor-driven valve 34b that stops a side, cold-producing medium liquefies gradually and lodges in and stops the utilizing in the side heat exchanger 33b an of side.At this, hydrogen fluorine carbide) etc. (hydrofluorocarbon: cold-producing medium is established under the situation of kind of refrigeration cycle that the ejection pressure of compressor is subcritical pressure boiler for example using HFC, the environment temperature of utilizing side heat exchanger 33b along with this utilize side heat exchanger 33b stop to descend, stop the cold-producing medium condensation gradually thereupon in the side heat exchanger 33b of utilizing of a side.Consequently, cold-producing medium liquefaction and lodging in stops to utilize in the side heat exchanger 33b of a side, thereby the problem of the short of refrigerant that utilizes side heat exchanger 33a of heating action one side can occur flowing through.
[0012] so, in the present invention, in order to prevent this utilizing the cold-producing medium liquefaction among the side heat exchanger 33b and accumulating of a side that stop, pressure that establishing the ejection cold-producing medium of compressor 22 is the above value of critical pressure.In other words, in the refrigerant loop 10 of refrigerating plant of the present invention, the pressure that makes cryogen is the kind of refrigeration cycle (so-called overcritical circulation) of the above value of critical pressure.Consequently, to stop to utilize of a side among the side heat exchanger 33b be the cold-producing medium that is in critical condition when part lodges in when turning round, so this cold-producing medium can not carry out condensation in utilizing side heat exchanger 33b.In other words, compare with the existing refrigerating plant of the kind of refrigeration cycle of using cold-producing mediums such as HFC, because stop the utilizing among the side heat exchanger 33b an of side of the present invention, cold-producing medium can not carry out phase place and change, so cold-producing medium liquefies in utilizing side heat exchanger 33b and the speed of accumulating is slower.
[0013] second invention, be in first invention, described refrigerating plant also comprises controlling organization 51, when exist simultaneously heat action utilize side heat exchanger 33a and be in halted state utilize the running of side heat exchanger 33b the time, this controlling organization 51 makes corresponding to the motor-driven valve 34b that utilizes side heat exchanger 33b that stops a side becoming full closing state.
[0014] in second invention, when carrying out the running of described part, controlling organization 51 makes corresponding to the motor-driven valve 34b that utilizes side heat exchanger 33b that stops a side becoming full closing state.Consequently, cold-producing medium liquefies gradually and lodges in and stops the utilizing in the side heat exchanger 33b an of side.But, in the present invention,, reduce significantly so liquefy and lodge in the refrigerant amount in the side heat exchanger 33b that utilizes that stops a side because carry out overcritical circulation as mentioned above.
[0015] on the other hand, when so motor-driven valve 34b being made as full closing state, what cold-producing medium only flow through heating action one side utilizes side heat exchanger 33a.In other words, following situation can not appear, that is: cold-producing medium flow through stop a side utilize side heat exchanger 33b, utilize side heat exchanger 33b heat release in vain from this.
[0016] the 3rd invention is in second invention, and through during the first stipulated time t1, described controlling organization 51 is temporarily opened the second stipulated time t2 with this motor-driven valve 34b after closing corresponding to the motor-driven valve 34b that utilizes side heat exchanger 33b that stops a side.
[0017] in the 3rd invention, when carrying out the running of described part, after closing corresponding to the motor-driven valve 34b that utilizes side heat exchanger 33b that stops a side through the regulation the first stipulated time t1 time, controlling organization 51 reaches regulation aperture (aperture that this regulation aperture is preferably more small) with motor-driven valve 34b.In other words, in that part running is carried out under the long situation constantly, even carry out described overcritical circulation, following situation also can occur, that is: cold-producing medium liquefies gradually and lodges in and stops the utilizing in the side heat exchanger 33b an of side.Therefore, when part of the present invention running, when having passed through the first stipulated time t1, open motor-driven valve 34b forcibly, cold-producing medium is only flow through stop to utilize in the side heat exchanger 33b of a side in the second stipulated time t2.Consequently, flow in the second stipulated time t2 by the cold-producing medium in the side heat exchanger 33b that utilizes that stops a side, utilize side heat exchanger 33b and this to utilize the temperature on every side of side heat exchanger 33b just to uprise, cold-producing medium does not liquefy and has accumulated.Afterwards, when having passed through the second stipulated time t2, motor-driven valve 34b becomes full closing state once more.
[0018] the 4th invention is that described each utilizes side heat exchanger 33a, 33b to constitute in the 3rd invention: be configured in indoorly, emit the heat of cold-producing medium to room air; Each utilize side heat exchanger 33a, 33b around be respectively arranged with indoor temperature transmitter 44,45, described indoor temperature transmitter 44,45 detects respectively corresponding to described each and utilizes the indoor temperature of side heat exchanger 33a, 33b; Described refrigerating plant also comprises correcting mechanism 52, and this correcting mechanism 52 is according to corresponding to the indoor temperature transmitter that the utilizes side heat exchanger 33b 45 detected temperature that stop a side either party or both sides among the described first stipulated time t1 and the second stipulated time t2 being carried out revisal.
[0019] in the 4th invention, correcting mechanism 52 is according to the indoor temperature transmitter that the utilizes side heat exchanger 33b 45 detected indoor temperatures that stop a side either party or both sides among the first stipulated time t1 and the second stipulated time t2 being carried out revisal.
[0020] particularly, for example stop a side utilize side heat exchanger 33b around indoor temperature than under the condition with higher, cold-producing medium is difficult for liquefaction and lodges in stopping the utilizing in the side heat exchanger 33b an of side.Therefore, in this case,, just can more than enoughly guarantee that motor-driven valve 34b is in the time of full closing state by making the revisal that the first stipulated time t1 is elongated or the second stipulated time t2 is shortened.Consequently, can avoid cold-producing medium stopping the heat release in vain in the side heat exchanger 33b that utilizes of a side.
[0021] on the other hand, for example stop a side utilize side heat exchanger 33b around the lower situation of indoor temperature under, cold-producing medium liquefies easily and lodges in and stops the utilizing in the side heat exchanger 33b an of side.Therefore, in this case,, just can avoid cold-producing medium liquefaction and lodge in utilizing in the side heat exchanger 33b by the first stipulated time t1 being shortened or making the elongated revisal of the second stipulated time t2.
[0022] in the 5th invention, described refrigerating plant also comprises refrigerant density testing agency 40,41,42,43, and described refrigerant density testing agency 40,41,42,43 detects each respectively and utilizes refrigerant density in side heat exchanger 33a, the 33b; Make become full closing state corresponding to the motor-driven valve 34b that utilizes side heat exchanger 33b that stops a side after, when utilizing the detected refrigerant density of the refrigerant density testing agency 40,41,43 of side heat exchanger 33b greater than the regulation refrigerant density corresponding to this, described controlling organization 51 is temporarily opened this motor-driven valve 34b.
[0023] in the 5th invention, when carrying out the running of described part, make become full closing state corresponding to the motor-driven valve 34b that utilizes side heat exchanger 33b that stops a side after, the refrigerant density in the side heat exchanger 33b utilized that stops a side detecting in refrigerant density testing agency 40,41,43.In other words, cold-producing medium testing agency 40,41,43 detects indirectly according to this refrigerant density and lodges in the refrigerant amount in the side heat exchanger 33b of utilizing that stops a side.Greater than regulation during refrigerant density, the cold-producing medium that is judged as volume lodges in and stops the utilizing in the side heat exchanger 33b an of side in this detected refrigerant density, and controlling organization 51 is temporarily opened motor-driven valve 34b.Consequently, can avoid stopping to utilize the cold-producing medium liquefaction among the side heat exchanger 33b and accumulating of a side.
[0024] the 6th invention is in any invention in first to the 5th invention, is filled with carbon dioxide as cold-producing medium in described refrigerant loop 10.
[0025] according to the 6th invention, in refrigerant loop 10, uses the overcritical circulation of carbon dioxide.
[0026] the 7th invention is in any invention in second to the 5th invention, and described refrigerating plant comprises that also discharging jet respectively crosses the switching mechanism that each utilizes the ejiction opening of the air behind side heat exchanger 33a, the 33b and opens and closes described ejiction opening respectively freely; Described each switching mechanism constitutes: open the ejiction opening that utilizes side heat exchanger 33b that heats action, and close the ejiction opening that utilizes side heat exchanger 33a that stops a side.
[0027] in the refrigerating plant of the 7th invention, utilize side heat exchanger 33a, 33b to be provided with a plurality of ejiction openings corresponding to each.In addition, in each ejiction opening, be provided with the switching mechanism that this ejiction opening is opened or closed.At this, when whole running, the switching mechanism of all ejiction openings all becomes open mode, utilizes the air after being heated among side heat exchanger 33a, the 33b to spray to indoor etc. from each ejiction opening at each.On the other hand, when part when turning round, the switching mechanism that heats the ejiction opening that utilizes side heat exchanger 33a of a side becomes open mode, and the switching mechanism that stops the ejiction opening that utilizes side heat exchanger 33b of a side becomes closed condition.Consequently, can prevent among the side heat exchanger 33b that this heat of utilizing side heat exchanger 33b inside that stops a side from loosing through ejiction opening and go stopping to utilize of a side to indoor other spaces of waiting.Therefore, the environment temperature of utilizing side heat exchanger 33b that can suppress to stop a side descending, and can avoid cold-producing medium to liquefy in this utilizes side heat exchanger 33b efficiently and accumulates.
The effect of-invention-
[0028] according to the present invention, a plurality of side heat exchanger 33a, 33b branches that utilize are opened in the refrigerating plant that heats action, the pressure of establishing the ejection cold-producing medium of forcing press 22 is the overcritical circulation of the above value of critical pressure.Therefore, be the aperture of small aperture or contract fully even when the running of described part, establish the aperture of the motor-driven valve 34b that stops a side, cold-producing medium also is difficult for stopping to utilize in side heat exchanger 33a, the 33b liquefaction and accumulating of a side.Therefore,, the problem of the short of refrigerant that utilizes side heat exchanger 33a that flows through heating action one side can be solved, the heating efficiency of utilizing side heat exchanger 33a of action one side can be obtained heating fully according to the present invention.
[0029] particularly in second invention, when carrying out making the motor-driven valve 34b that stops a side becoming full closing state when part turns round.Therefore, according to second invention, what ownership cryogen all was sent to heating action one side utilizes side heat exchanger 33a, thereby can avoid cold-producing medium stopping the heat release in vain in the side heat exchanger 33b that utilizes of a side.Therefore, according to the present invention, can seek to heat the raising of the heating efficiency of utilizing side heat exchanger 33a of a side, and then can seek COP (the coefficient of performance: the raising coefficient of performance) of this refrigerating plant.
[0030] in addition, in the 3rd invention, when carrying out the part running, make the motor-driven valve 34b that temporarily is made as full closing state after having passed through the first stipulated time t1, only open the second stipulated time t2.Therefore,, part running is being carried out under the long situation constantly according to the 3rd invention, can positively solve stop a side utilize cold-producing medium liquefaction in the side heat exchanger 33b and the problem of accumulating, can guarantee the reliability of this refrigerating plant.
[0031] particularly in the 4th invention, when part when turning round, according to stop a side utilize side heat exchanger 33b around indoor temperature the first stipulated time t1 or the second stipulated time t2 are carried out revisal.Therefore, according to the 4th invention, can positively avoid the generation of following problems, that is: the contract fully time lengthening of motor-driven valve 34b is to the above time of required time, makes cold-producing medium liquefaction and lodging in stop to utilize in the side heat exchanger 33b of a side.In addition, according to the 4th invention, can positively avoid the generation of following phenomenon, that is: the time lengthening of opening of motor-driven valve 34b arrives the above time of required time, makes cold-producing medium stop the heat release in vain in the side heat exchanger 33b that utilizes of a side.
[0032] in addition, in the 5th invention, when part detects the refrigerant density in the side heat exchanger 33b utilized that stops a side when turning round, if this refrigerant density greater than the regulation refrigerant density, is just temporarily opened the motor-driven valve 34b that is in full closing state.In other words, in the 5th invention, obtain indirectly and lodged in the refrigerant amount in the side heat exchanger 33b of utilizing that stops a side, when this refrigerant amount is many, open motor-driven valve 34b.Therefore, can positively avoid cold-producing medium and stop to utilize in the side heat exchanger 33b liquefaction and accumulating of a side.
[0033] says again,,, just can use the overcritical circulation of the lower natural cold-producing medium of critical-temperature (natural refrigerant) by using carbon dioxide as cold-producing medium according to the 6th invention.
[0034] in addition, according to the 7th invention, because when partly turning round, close the ejiction opening that utilizes side heat exchanger 33b that stops a side with switching mechanism, descend so can suppress this environment temperature of utilizing side heat exchanger 33b, can further avoid cold-producing medium in utilizing side heat exchanger 33b, to liquefy efficiently and accumulate.
Description of drawings
[0035] Fig. 1 is the piping diagram of the refrigerant loop of the related aircondition of embodiment.
Fig. 2 is the piping diagram that shows the mobility status in the refrigerant loop of cold-producing medium when whole warming operations.
Fig. 3 is the piping diagram that shows the mobility status in the refrigerant loop of cold-producing medium when the part warming operation.
Fig. 4 is the p-h figure (enthalpy-entropy diagram: Mollierdiagram) of the related overcritical circulation of embodiment.
Fig. 5 is the p-h figure (enthalpy-entropy diagram) of the related kind of refrigeration cycle of conventional example.
Fig. 6 is the piping diagram of the mobility status of cold-producing medium when the part warming operation of the refrigerant loop of the aircondition that shows that variation is related.
The curve map of the refrigerant density that Fig. 7 is the inlet that shows the indoor heat converter that stops a side from embodiment till the outlet and the situation of change of refrigerant temperature.
The curve map of the refrigerant density that Fig. 8 is the inlet that shows the indoor heat converter that stops a side from conventional example till the outlet and the situation of change of refrigerant temperature.
Symbol description
[0036] 1-aircondition (refrigerating plant); 10-refrigerant loop; Loop, 21-outside (heat source side loop); 22-compressor; 23-outdoor heat converter (heat source side heat exchanger); 33a-first indoor heat converter (utilizing the side heat exchanger); 33b-second indoor heat converter (utilizing the side heat exchanger); The indoor expansion valve of 34a-first (motor-driven valve); The indoor expansion valve of 34b-second (motor-driven valve); 44-the first indoor temperature transmitter (indoor temperature transmitter); 45-the second indoor temperature transmitter (indoor temperature transmitter); 51-controlling organization; 52-correcting mechanism.
The specific embodiment
[0037] below, describes embodiments of the present invention with reference to the accompanying drawings in detail.
[0038] the related refrigerating plant of embodiment constitutes and can heat and that freeze, so-called many formulas aircondition 1 to indoor.As shown in Figure 1, this aircondition 1 comprises and is arranged on an outdoor outdoor unit 20 and is arranged on first and second indoor units 30a, 30b in the different chamber.
[0039] in described outdoor unit 20, is provided with the loop, outside 21 that constitutes the heat source side loop.In the described first indoor units 30a, be provided with formation and utilize first indoor loop 31a of side loop, in the described second indoor units 30b, be provided with second indoor loop 31b that formation is utilized side loop.
[0040] each loop, indoor 31a, 31b are connected with this loop, outside 21 in loop, relative outside 21 modes arranged side by side by first connecting pipe 11 and second connecting pipe 12.Consequently, in this aircondition 1, constitute cold-producing medium circulation and carry out the refrigerant loop 10 of kind of refrigeration cycle.In this refrigerant loop 10, be filled with carbon dioxide as cold-producing medium.
[0041] in loop, outside 21, is provided with compressor 22, outdoor heat converter 23, outdoor expansion valve 24 and four-way change-over valve 25.Compressor 22 is scroll compressors of totally enclosed type and high pressure dome type.Electric power offers this compressor 22 by frequency converter.In other words, compressor 22 can change the rotary speed that changes compressor motor by the output frequency that makes frequency converter, thereby changes the capacity of this compressor 22.Outdoor heat converter 23 is intersection fin (cross fin) formula fin tube type heat exchangers, constitutes the heat source side heat exchanger.In this outdoor heat converter 23, between cold-producing medium and outdoor air, carry out heat exchange.Outdoor expansion valve 24 is made of the electric expansion valve that can regulate aperture.
[0042] four-way change-over valve 25 has first to the 4th valve port.First valve port of this four-way change-over valve 25 is connected with the bleed pipe 22a of compressor 22, and second valve port is connected with outdoor heat converter 23, and the 3rd valve port is connected with the suction line 22b of compressor 22, and the 4th valve port is connected with first connecting pipe 11.Four-way change-over valve 25 can switch following two states, that is: the state that first valve port and the 4th valve port interconnect and second valve port and the 3rd valve port interconnect (in Fig. 1 with the state shown in the solid line) and first valve port and second valve port interconnects and the 3rd valve port and the 4th valve port interconnect state (state in Fig. 1 shown in the with dashed lines).
[0043] be provided with the first lateral 32a in the loop 31a of first indoor, the end of this first lateral 32a is connected with first connecting pipe, 11 1 sides, and the other end is connected with second connecting pipe, 12 1 sides.In this first lateral 32a, be provided with the first indoor heat converter 33a and the first indoor expansion valve 34a.Be provided with the second lateral 32b in the loop 31b of second indoor, the end of this second lateral 32b is connected with first connecting pipe, 11 1 sides, and the other end is connected with second connecting pipe, 12 1 sides.In this second lateral 32b, be provided with the second indoor heat converter 33b and the second indoor expansion valve 34b.
[0044] each indoor heat converter 33a, 33b are intersection fin type fin tube type heat exchangers, constitute respectively and utilize the side heat exchanger.In each indoor heat converter 33a, 33b, between cold-producing medium and room air, carry out heat exchange.
[0045] the first indoor expansion valve 34a and the second indoor expansion valve 34b are motor-driven valves, constitute respectively and can regulate the electric expansion valve of aperture.The first indoor expansion valve 34a is arranged on second connecting pipe, 12 1 sides among the first lateral 32a.The second indoor expansion valve 34b is arranged on second connecting pipe, 12 1 sides among the second lateral 32b.The first indoor expansion valve 34a can regulate the flow of the cold-producing medium that flows through the first indoor heat converter 33a; The second indoor expansion valve 34b can regulate the flow of the cold-producing medium that flows through the second indoor heat converter 33b.
[0046] in refrigerant loop 10, is provided with high-pressure sensor 40, high pressure temperature sensor 41, first refrigerant temperature sensors 42 and second refrigerant temperature sensors 43.High-pressure sensor 40 detects the pressure of the ejection cold-producing medium of compressor 22.High pressure temperature sensor 41 detects the temperature of the ejection cold-producing medium of compressor 22.First refrigerant temperature sensors 42 is arranged on the outlet of the first indoor heat converter 33a, and the temperature that just flows out first indoor heat converter 33a cold-producing medium is afterwards detected.Second refrigerant temperature sensors 43 is arranged on the outlet of the second indoor heat converter 33b, and the temperature that just flows out second indoor heat converter 33b cold-producing medium is afterwards detected.
[0047] in addition, the first indoor heat converter 33a in the first indoor units 30a near be provided with first indoor temperature transmitter 44.This first indoor temperature transmitter 44 detects the ambient air temperature of the first indoor heat converter 33a.Near the second indoor heat converter 33b of the second indoor units 30b, be provided with second indoor temperature transmitter 45.This second indoor temperature transmitter 45 detects the ambient air temperature of the second indoor heat converter 33b.
[0048] in the refrigerant loop 10 of the aircondition 1 of present embodiment, the pressure of establishing the ejection cold-producing medium of compressor 22 is that the above value of critical pressure is carried out kind of refrigeration cycle (overcritical circulation).In addition, in this aircondition 1, the first indoor units 30a and the second indoor units 30b are separately turned round.In other words, in this aircondition 1, the running that can carry out when indoor units 30a heats with first, making the second indoor units 30b be in halted state (below, this running is called the part warming operation) and the running that heats with the first indoor units 30a and the second indoor units 30b these two kinds of indoor units 30a, 30b (below, this running is called whole warming operations).
[0049] and, in aircondition 1, be provided with the controller 50 that is used for when described part warming operation, controlling the aperture of each indoor expansion valve 34a, 34b.In this controller 50, be provided with controlling organization 51 and correcting mechanism 52.The back describes the control situation that this controller 50 carries out the aperture of each indoor expansion valve 34a, 34b in detail.
[0050]-the running action-
Then, the running action to the related aircondition 1 of present embodiment describes.In this aircondition 1, can use running that each indoor units 30a, 30b heat and the running of freezing with each indoor units 30a, 30b.Below, the warming operation of this aircondition 1 is described.Remark additionally, when this warming operation, four-way change-over valve 25 is set at Fig. 2 and state shown in Figure 3, switches and carry out described whole warming operation and part warming operation.
[0051]＜whole warming operations 〉
When whole warming operation, make the first indoor expansion valve 34a and the second indoor expansion valve 34b reach the regulation aperture.As shown in Figure 2, the cold-producing medium that is compressed to behind the above pressure of critical pressure with compressor 22 flows in the first lateral 32a and the second lateral 32b through four-way change-over valve 25 and first connecting pipe, 11 branches.
[0052] cold-producing medium after flowing in the first lateral 32a flows through the first indoor heat converter 33a.In the first indoor heat converter 33a, cold-producing medium is to the room air heat release.In other words, the heating of carrying out room air is heated in the first indoor heat converter 33a is moved, and heats to being provided with first the indoor of indoor units 30a.Cold-producing medium after flowing out from the first indoor heat converter 33a flows in second connecting pipe 12 through the first indoor expansion valve 34a.
[0053] on the other hand, the cold-producing medium after flowing in the second lateral 32b flows through the second indoor heat converter 33b.In the second indoor heat converter 33b, cold-producing medium is to the room air heat release.In other words, the heating of carrying out room air is heated in the second indoor heat converter 33b is moved, and heats to being provided with second the indoor of indoor units 30b.Cold-producing medium after flowing out from the second indoor heat converter 33b flows in second connecting pipe 12 through the second indoor expansion valve 34b.
[0054] cold-producing medium behind the interflow reduces pressure when flowing through outdoor expansion valve 24 in second connecting pipe 12, flows through outdoor heat converter 23 then.In outdoor heat converter 23, cold-producing medium evaporates from the outdoor air heat absorption.Cold-producing medium behind delivery chamber's outer heat-exchanger 23 is inhaled in the compressor 22 through four-way change-over valve 25.In compressor 22, this cold-producing medium is compressed to pressure more than the critical pressure.
[0055]＜the part warming operation 〉
When the part warming operation, carry out when indoor heat converter 33a heats action with first, making running that the heating action of the second indoor heat converter 33b stops or the heating that when indoor heat converter 33b heats action with second, makes the first indoor heat converter 33a to move the running that stops.At this, heat the typical example that operates as of action only to make the first indoor heat converter 33a, describe with reference to Fig. 3.
[0056] when this part warming operation, the controlling organization 51 of controller 50 reaches the regulation aperture with the first indoor expansion valve 34a, and the second indoor expansion valve 34b is set at full closing state.Under the situation of opening the first indoor expansion valve 34a, in the first indoor heat converter 33a, carry out aforesaid heating action.On the other hand, be under the situation of full closing state at the second indoor expansion valve 34b, cold-producing medium does not flow through the second indoor expansion valve 34b.Therefore, cold-producing medium does not circulate in the second indoor heat converter 33b, and the second indoor heat converter 33b becomes halted state.
[0057] under the situation that the second indoor heat converter 33b is stopped, cold-producing medium lodges among the second indoor heat converter 33b gradually.Yet in the aircondition 1 of present embodiment, the pressure of also establishing the ejection cold-producing medium of compressor 22 when this part warming operation is the overcritical circulation of the value more than the critical pressure.Therefore, though the environment temperature of the second indoor heat converter 33b along with the second indoor heat converter 33b stop to descend, the cold-producing medium in the second indoor heat converter 33b can condensation yet.Therefore, compare with the refrigerating plant that for example carries out subcritical refrigeration cycle with HFC etc., cold-producing medium liquefaction and lodge among the second indoor heat converter 33b speed slowly very.
[0058] with reference to Fig. 4 and Fig. 5, the explanation more detailed in addition to described thing.Remark additionally, Fig. 4 shows the p-h figure of overcritical circulation present embodiment, that use carbon dioxide; That Fig. 5 shows is existing, use the p-h figure of the subcritical refrigeration cycle of HFC.
[0059] in conventional example shown in Figure 5, the pressure of the ejection cold-producing medium of compressor is less than critical pressure.Particularly, such as the refrigerant pressure after the compression of this kind of refrigeration cycle is 2.7MPa; Refrigerant temperature after the compression of this kind of refrigeration cycle is 80 ℃; Refrigerant density
1 is 85kg/m
3On the other hand, under the situation of this cold-producing medium condensation in indoor heat converter, the pressure 2.7MPa of condensed cold-producing medium; Condensed refrigerant temperature is 37 ℃; Refrigerant density
For example be 996kg/m
3In other words, in existing kind of refrigeration cycle, the refrigerant density of outlet one side of indoor heat converter
The refrigerant density of relative inlet side
The density ratio
Be 11.72.
[0060] on the other hand, in present embodiment shown in Figure 4, the pressure of the ejection cold-producing medium of compressor is the above value of critical pressure.Particularly, such as the refrigerant pressure after the compression of this circulation is 10MPa; Refrigerant temperature after the compression of this circulation is 80 ℃; Refrigerant density
Be 221kg/m
3On the other hand, under the situation of this cold-producing medium heat release in indoor heat converter, the refrigerant pressure after the heat release is 10MPa; Condensed refrigerant temperature is 35 ℃; Refrigerant density
Be 713kg/m
3In other words, in the overcritical circulation of present embodiment, the refrigerant density of outlet one side of indoor heat converter
The refrigerant density of relative inlet side
The density ratio
Be 3.23.
[0061] as mentioned above, with the density ratio before and after the indoor heat converter of conventional example and present embodiment
By comparison, the density of conventional example is than the density ratio greater than present embodiment, and the density of conventional example is than being more than three times of density ratio of present embodiment.In other words, in existing kind of refrigeration cycle, under the situation of cold-producing medium condensation in the indoor heat converter that stops a side, because the density of this cold-producing medium is very high, and volume is very little, so cold-producing medium is constantly delivered in the indoor heat converter.Therefore, according to conventional example, cold-producing medium in the indoor heat converter that stops a side, liquefy and the velocity ratio of accumulating very fast.
[0062] relative therewith, in the present embodiment, even cold-producing medium heat release in the indoor heat converter that stops a side, because the density of this cold-producing medium is lower, so the volume of this cold-producing medium is also not too little.Therefore, the cold-producing medium that is sent in the indoor heat converter is not many, consequently, cold-producing medium in the indoor heat converter that stops a side, liquefy and the speed of accumulating also slow.
[0063] on the other hand, this part warming operation is being carried out under the long situation constantly the still increase gradually of amount that cold-producing medium liquefies and accumulates in the second indoor heat converter 33b.So, when the controlling organization 51 of present embodiment makes the second indoor expansion valve 34b become full closing state to have passed through the first stipulated time t1 later at beginning part warming operation, the second indoor expansion valve 34b is opened the second stipulated time t2 with small aperture.Like this, cold-producing medium just flows through in the second indoor heat converter 33b with small flow, and the temperature around the second indoor heat converter 33b and this second indoor heat converter 33b rises.Consequently, cold-producing medium liquefies in the second indoor heat converter 33b and the problem of accumulating is resolved.Afterwards, when having passed through the second stipulated time t2, controlling organization 51 makes the second indoor expansion valve 34b become full closing state once more.
[0064] in addition, cold-producing medium at beginning part warming operation and after making the second indoor expansion valve 34b become full closing state liquefaction and the amount in the second indoor heat converter 33b of lodging in depend on the environment temperature of the second indoor heat converter 33b.In other words, when the indoor temperature that is provided with the second indoor heat converter 33b is relatively low, cold-producing medium in the second indoor heat converter 33b, liquefy and the speed of accumulating very fast, and when this indoor temperature when higher, cold-producing medium liquefy and the speed of accumulating very slow.Therefore, the correcting mechanism 52 of the controller 50 of present embodiment detect by indoor temperature transmitter 45 the indoor heat converter 33b that stops a side around indoor temperature, according to this indoor temperature the described first stipulated time t1 and the second stipulated time t2 are carried out revisal again.
[0065] particularly, under second indoor temperature transmitter 45 situation that detected indoor temperature is lower during when beginning part warming operation, correcting mechanism 52 carries out revisal, shortens the first stipulated time t1.On the other hand, under the lower situation of second indoor temperature transmitter 45 detected indoor temperature when having passed through the first stipulated time t1, correcting mechanism 52 carries out revisal, prolongs the second stipulated time t2.Consequently, because the time that makes the second indoor expansion valve 34b become full closing state when the part warming operation shortens, in the second indoor heat converter 33b, liquefy and accumulate so can prevent cold-producing medium.Remark additionally, the described revisal that the first stipulated time t1 and the second stipulated time t2 are carried out, also can be the revisal that the arbitrary stipulated time among the first stipulated time t1 and the second stipulated time t2 is carried out, also can be the revisal that this two kinds of times of the first stipulated time t1 and the second stipulated time t2 are carried out.
[0066] on the other hand, detected indoor temperature is than under the condition with higher during when beginning part warming operation at second indoor temperature transmitter 45, and correcting mechanism 52 carries out revisal, prolongs the first stipulated time t1.On the other hand, detected indoor temperature is than under the condition with higher when having passed through the first stipulated time t1 at second indoor temperature transmitter 45, and correcting mechanism 52 carries out revisal, shortens the second stipulated time t2.Consequently because the time that when the part warming operation, makes the second indoor expansion valve 34b become open mode shorten, so cold-producing medium can heat release in vain in stopping the second indoor heat converter 33b of a side.
[0067]-effect of embodiment-
In said embodiment, a plurality of indoor heat converter 33a, 33b branch is opened in the aircondition 1 that heats action, the pressure of establishing the ejection cold-producing medium of compressor 22 is the overcritical circulation of the above value of critical pressure.Therefore, even make the aperture of the indoor expansion valve 34b that stops a side become full closing state when the part warming operation, cold-producing medium can condensation in stopping the indoor heat converter 33b of a side yet.Therefore, according to present embodiment, can slow down the speed that cold-producing medium liquefies and accumulates significantly in stopping the indoor heat converter 33b of a side.Consequently, can avoid cold-producing medium and in heating the indoor heat converter 33a of action, sink into not enough state, can obtain heating the heating capacity of the indoor heat converter 33a of action one side fully.
[0068] in addition, in said embodiment, when carrying out the part warming operation, make the indoor expansion valve 34b that stops a side becoming full closing state.Therefore, according to described embodiment, can prevent cold-producing medium heat release in vain in stopping the indoor heat converter 33b of a side.Therefore, can seek the raising of the COP (coefficient of performance) of this aircondition 1.
[0069] and, in said embodiment, will work as the indoor expansion valve 34b that temporarily is made as full closing state when carrying out the part warming operation and after through the first stipulated time t1, open the second stipulated time t2.Therefore, according to described embodiment, problem the part warming operation being carried out constantly also can positively solve under the long situation liquefaction in the indoor heat converter 33b that cold-producing medium stopping a side and accumulating can positively prevent to sink into not enough state among the indoor heat converter 33a of cold-producing medium when the heating action.
[0070] in addition, in said embodiment, when the part warming operation, the first stipulated time t1 and the second stipulated time t2 are carried out revisal according to the indoor temperature around the indoor heat converter 33b that stops a side.Therefore, according to described embodiment, can avoid and following situation occur, that is: the contract fully time ratio required time of indoor expansion valve 34b is long, and cold-producing medium liquefies in stopping the indoor heat converter 33b of a side and accumulates.In addition,, can avoid the following situation that occurs according to described embodiment, that is: indoor expansion valve 34b to open the time ratio required time long, cold-producing medium heat release in vain in stopping the indoor heat converter 33b of a side.Therefore, can further improve the COP (coefficient of performance) of this aircondition 1.
[0071]-variation of the aperture of indoor expansion valve control-
In said embodiment, when the part warming operation, the indoor expansion valve 33a, the 33b that stop a side are opened and closed after becoming full closing state to this indoor expansion valve 34b according to the first stipulated time t1 and the second stipulated time t2.Yet, also can carry out as shown in Figure 6 control to the aperture of indoor expansion valve 34b, replace the described control that the aperture of indoor expansion valve 34b is carried out.
[0072] when the part warming operation of this variation, high-pressure sensor 40 detected refrigerant pressure, high pressure temperature sensor 41 detected refrigerant temperature, first refrigerant temperature sensors, 42 detected refrigerant temperature and second refrigerant temperature sensors, 43 detected refrigerant temperatures are exported to controller 50.In this controller 50, obtain the density of the cold-producing medium of the indoor heat converter 33b that stops a side when flowing through the part warming operation according to the detected value of described each sensor 40,41,42,43.In other words, described each sensor 40,41,42,43 is configured to the refrigerant density testing agency that the refrigerant density to the indoor heat converter 33b that stops a side detects.
[0073] particularly, for example when carrying out the part warming operation the same with described embodiment, controlling organization 51 at first makes the aperture of the second indoor expansion valve 34b become full closing state.On the other hand, this part warming operation is being carried out under the long situation constantly, cold-producing medium liquefies gradually and lodges in the second indoor heat converter 33b.
[0074], in the controlling organization 51 of this variation, obtains refrigerant density in the second indoor heat converter 33b that stops a side according to refrigerant pressure and refrigerant temperature at this.Particularly, for example become under the situation that stops a side at the second indoor heat converter 33b, controller 50 is according to high-pressure sensor 40 detected refrigerant pressures, obtain the refrigerant density of the second indoor heat converter 33b with high pressure temperature sensor 41 detected refrigerant temperatures and with being positioned at second refrigerant temperature sensors, the 43 detected refrigerant temperatures that stop a side.In other words, the detected refrigerant pressure of high-pressure sensor 40 equates with refrigerant pressure in the second indoor heat converter 33b basically.On the other hand, can regard the temperature that flows into the cold-producing medium in the second indoor heat converter 33b as with high pressure temperature sensor 41 detected refrigerant temperatures, in addition, with the temperature of second refrigerant temperature sensors, 43 detected refrigerant temperatures for the cold-producing medium that from the second indoor heat converter 33b, flows out.Therefore, obtain the mean temperature of cold-producing medium in indoor heat converter 33b according to these inflow refrigerant temperatures and outflow refrigerant temperature.Say again, obtain the average refrigerant density of cold-producing medium in the second indoor heat converter 33b according to this average refrigerant temperature and described refrigerant pressure.
[0075] refrigerant density of obtaining by described way is to show the index that lodges in the refrigerant amount in the second indoor heat converter 33b.The controlling organization 51 of this variation at beginning part warming operation and after making the second indoor expansion valve 34b become full closing state when the refrigerant density of obtaining according to the detected value of each sensor 40,41,43 during greater than the regulation refrigerant density, be judged as cold-producing medium and in the second indoor heat converter 33b, accumulate often, thereby temporarily open the second indoor expansion valve 34b.Consequently, can positively solve the problem that cold-producing medium liquefies and accumulates in the second indoor heat converter 33b.
[0076] remarks additionally, when the first indoor heat converter 33a being stopped and heating the part warming operation of action, obtain the refrigerant density of the first indoor heat converter 33a according to high-pressure sensor 40, high pressure temperature sensor 41 and the detected value that is positioned at first refrigerant temperature sensors 42 that stops a side with the second indoor heat converter 33b.In this case, open the first indoor expansion valve 34a during greater than the regulation refrigerant density, solve the problem that cold-producing medium liquefies and accumulates in the first indoor heat converter 33a when this refrigerant density.
[0077]-effect of variation-
In this variation, when the part warming operation, the refrigerant density in the indoor heat converter 33b that stops a side being detected, temporarily open the indoor expansion valve 34b that is in full closing state in this refrigerant density under greater than the situation of regulation refrigerant density.In other words, in this variation, obtain the refrigerant amount that has lodged in the indoor heat converter 33b that stops a side indirectly, when this refrigerant amount becomes many, open indoor expansion valve 34b.Therefore, can positively avoid cold-producing medium liquefies in stopping the indoor heat converter 33b of a side and accumulates.
[0078] in addition, in this variation, when the part warming operation, in refrigerant loop 10, also carry out overcritical circulation.Like this, just can slow down cold-producing medium significantly and be positioned at each indoor heat converter 33a, 33b liquefaction that stops a side and the speed of accumulating.
[0079] and, if in refrigerant loop 10, carry out overcritical circulation as mentioned above, just can also more correctly learn the average refrigerant temperature of the indoor heat converter 33b that stops a side.Particularly, as shown in Figure 8, in prior art (carrying out the technology that high pressure is the kind of refrigeration cycle of subcritical pressure boiler), density (refrigerant temperature) situation of change of cold-producing medium when the inlet of the indoor heat converter that stops a side flows to till the outlet linear not obvious.This is because in the prior art, cold-producing medium condensation and carry out phase place and change in the indoor heat converter that stops a side.Therefore, if will correctly learn the refrigerant amount that lodges in the indoor heat converter, just be necessary the refrigerant density (refrigerant temperature) at a plurality of positions (for example, three more than the position) is detected, thereby the quantity of required temperature sensor is many.
[0080] on the other hand, as shown in Figure 7, in the present embodiment, the linearity of density (refrigerant temperature) situation of change of cold-producing medium when the inlet of the indoor heat converter 33b that stops a side flows to till the outlet clearly.This is because in the present embodiment, and the above cold-producing medium of critical pressure lodges in the indoor heat converter 33b, thereby the cold-producing medium in the indoor heat converter 33b does not carry out the phase place variation always when flowing to outlet from inlet.Therefore, in the present embodiment, can be by as above-mentioned variation, obtaining the refrigerant density of inlet and outlet, come correctly to predict the density situation of cold-producing medium when the inlet of indoor heat converter 33b flows to outlet according to being stored in tables of data (data table) in the controller 50 (about the data of the situation of change of refrigerant density or refrigerant temperature etc.) in advance.Then, can be by judging the time (timing) of opening indoor expansion valve 34a, 34b according to the refrigerant density of utilizing described way to obtain, come more positively to avoid cold-producing medium and in stopping the indoor heat converter 33b of a side, liquefy and accumulate.
[0081]＜other embodiments 〉
In the related aircondition 1 of described embodiment, also the louver(-vre) switching mechanisms such as (louver) that opens and closes described each ejiction opening freely can be set respectively on each ejiction opening of the air after discharging jet is crossed each to utilize side heat exchanger 33a, 33b respectively.When aforesaid part turns round, also can only close corresponding to the ejiction opening that utilizes side heat exchanger 33b that stops a side with switching mechanism.In this case, can suppress to lodge in the heat of utilizing the cold-producing medium in the side heat exchanger 33b that stops a side going to the interior space through ejiction opening is diffusing.Therefore, can suppress to utilize the environment temperature of side heat exchanger 33b to descend, can avoid cold-producing medium more efficiently and in utilizing side heat exchanger 33b, liquefy and accumulate.Remark additionally, be preferably switching mechanism such as louver(-vre) with seal encapsulants such as (packing) be arranged on louver(-vre) around so that improve sealing after ejiction opening sealed.
[0082] remark additionally, embodiment recited above is suitable examples basically, not to the present invention, the intention that adopts the scope of object of the present invention and uses thereof to be limited.
-industrial applicibility-
[0083] as mentioned above, a plurality of to utilize the side heat exchanger separately to add thermally operated can making In the refrigerating plant cold-producing medium is adopted in the problem that liquefies in the side heat exchanger and accumulate of utilizing that stops a side When getting countermeasure, the present invention as this countermeasure of great use.
Claims (7)
1. refrigerating plant, comprise refrigerant loop, this refrigerant loop is to make to have respectively in the heat source side loop mode arranged side by side that has compressor and heat exchanger of heat source relatively to utilize the side heat exchanger and utilize motor-driven valve a plurality of of side heat exchanger to utilize side loop to be connected with described heat source side loop and constitute corresponding to this; This refrigerating plant can make each utilize the side heat exchanger separately to carry out it is characterized in that from utilizing the heating action of the cold-producing medium heat release in the side heat exchanger:
Described refrigerant loop constitutes: carry out pressure with the ejection cold-producing medium of compressor and be located at kind of refrigeration cycle more than the critical pressure.
2. refrigerating plant according to claim 1 is characterized in that:
Described refrigerating plant also comprises controlling organization, when exist simultaneously heat action utilize the side heat exchanger and be in halted state utilize the running of side heat exchanger the time, this controlling organization makes corresponding to the motor-driven valve that utilizes the side heat exchanger that stops a side becoming full closing state.
3. refrigerating plant according to claim 2 is characterized in that:
Through during the first stipulated time t1, the second stipulated time t2 temporarily opened this motor-driven valve by described controlling organization after closing corresponding to the motor-driven valve that utilizes the side heat exchanger that stops a side.
4. refrigerating plant according to claim 3 is characterized in that:
Described each utilizes the side heat exchanger to constitute: be configured in indoorly, emit the heat of cold-producing medium to room air;
Each utilize the side heat exchanger around be respectively arranged with indoor temperature transmitter, described indoor temperature transmitter detects respectively corresponding to described each and utilizes the indoor temperature of side heat exchanger;
Described refrigerating plant also comprises correcting mechanism, and this correcting mechanism is according to corresponding to the detected temperature of the indoor temperature transmitter that utilizes the side heat exchanger that stops a side either party or both sides among described first stipulated time t1 and the described second stipulated time t2 being carried out revisal.
5. refrigerating plant according to claim 2 is characterized in that:
Described refrigerating plant also comprises refrigerant density testing agency, and described refrigerant density testing agency detects each respectively and utilizes refrigerant density in the side heat exchanger;
Make become full closing state corresponding to the motor-driven valve that utilizes the side heat exchanger that stops a side after, when utilizing the detected refrigerant density of the refrigerant density testing agency of side heat exchanger greater than the regulation refrigerant density corresponding to this, described controlling organization is temporarily opened this motor-driven valve.
6. according to each the described refrigerating plant in the claim 1 to 5, it is characterized in that:
In described refrigerant loop, be filled with carbon dioxide as cold-producing medium.
7. according to each the described refrigerating plant in the claim 2 to 5, it is characterized in that:
Described refrigerating plant comprises that also discharging jet respectively crosses the switching mechanism that each utilizes the ejiction opening of the air behind the side heat exchanger and opens and closes described ejiction opening respectively freely;
Described each switching mechanism constitutes: open the ejiction opening that utilizes the side heat exchanger that heats action, and close the ejiction opening that utilizes the side heat exchanger that stops a side.
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| JP078157/2006 | 2006-03-22 | ||
| JP2006078157A JP4797727B2 (en) | 2006-03-22 | 2006-03-22 | Refrigeration equipment |
| PCT/JP2007/054405 WO2007108319A1 (en) | 2006-03-22 | 2007-03-07 | Refrigerating apparatus |
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| US (1) | US20090019879A1 (en) |
| EP (1) | EP1998123B1 (en) |
| JP (1) | JP4797727B2 (en) |
| KR (1) | KR100988712B1 (en) |
| CN (2) | CN101395435B (en) |
| AU (1) | AU2007228237B2 (en) |
| ES (1) | ES2671446T3 (en) |
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- 2007-03-07 US US12/224,720 patent/US20090019879A1/en not_active Abandoned
- 2007-03-07 KR KR1020087021871A patent/KR100988712B1/en not_active IP Right Cessation
- 2007-03-07 WO PCT/JP2007/054405 patent/WO2007108319A1/en active Application Filing
- 2007-03-07 EP EP07737919.6A patent/EP1998123B1/en active Active
- 2007-03-07 AU AU2007228237A patent/AU2007228237B2/en not_active Ceased
- 2007-03-07 CN CN2007800081990A patent/CN101395435B/en not_active Expired - Fee Related
- 2007-03-07 CN CN201010263292XA patent/CN101907366B/en not_active Expired - Fee Related
- 2007-03-07 TR TR2018/07246T patent/TR201807246T4/en unknown
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103168205A (en) * | 2010-10-20 | 2013-06-19 | 大金工业株式会社 | Air conditioner |
| CN104764097A (en) * | 2015-04-08 | 2015-07-08 | 珠海格力电器股份有限公司 | Air-conditioning system, air-conditioner and control method thereof |
| CN107532835A (en) * | 2015-04-23 | 2018-01-02 | 三菱电机株式会社 | Refrigerating circulatory device |
| CN107532835B (en) * | 2015-04-23 | 2020-03-24 | 三菱电机株式会社 | Refrigeration cycle device |
| CN106871385A (en) * | 2017-04-13 | 2017-06-20 | 青岛海尔空调器有限总公司 | A kind of air-conditioner and control method |
| CN114234301A (en) * | 2021-12-13 | 2022-03-25 | 广东芬尼克兹节能设备有限公司 | Dehumidifier and accumulated liquid prevention control method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20080091853A (en) | 2008-10-14 |
| TR201807246T4 (en) | 2018-06-21 |
| AU2007228237B2 (en) | 2010-08-05 |
| EP1998123A1 (en) | 2008-12-03 |
| EP1998123A4 (en) | 2011-03-02 |
| CN101395435B (en) | 2012-07-18 |
| CN101907366B (en) | 2012-11-21 |
| US20090019879A1 (en) | 2009-01-22 |
| AU2007228237A1 (en) | 2007-09-27 |
| JP2007255750A (en) | 2007-10-04 |
| WO2007108319A1 (en) | 2007-09-27 |
| CN101907366A (en) | 2010-12-08 |
| JP4797727B2 (en) | 2011-10-19 |
| EP1998123B1 (en) | 2018-05-02 |
| ES2671446T3 (en) | 2018-06-06 |
| KR100988712B1 (en) | 2010-10-18 |
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