CN106766325B - Low-temperature air-conditioning system and air-conditioning - Google Patents
Low-temperature air-conditioning system and air-conditioning Download PDFInfo
- Publication number
- CN106766325B CN106766325B CN201611046317.4A CN201611046317A CN106766325B CN 106766325 B CN106766325 B CN 106766325B CN 201611046317 A CN201611046317 A CN 201611046317A CN 106766325 B CN106766325 B CN 106766325B
- Authority
- CN
- China
- Prior art keywords
- heat exchanger
- separator
- refrigerant
- low
- valve port
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000004378 air conditioning Methods 0.000 title claims abstract description 59
- 238000010438 heat treatment Methods 0.000 claims abstract description 23
- 238000009835 boiling Methods 0.000 claims abstract description 13
- 239000003507 refrigerant Substances 0.000 claims description 105
- 238000001704 evaporation Methods 0.000 claims description 52
- 230000008020 evaporation Effects 0.000 claims description 49
- 238000009833 condensation Methods 0.000 claims description 30
- 230000005494 condensation Effects 0.000 claims description 30
- 238000005057 refrigeration Methods 0.000 claims description 17
- 230000005520 electrodynamics Effects 0.000 claims description 5
- 230000000694 effects Effects 0.000 abstract description 11
- 239000000470 constituent Substances 0.000 abstract description 5
- 239000007788 liquid Substances 0.000 description 25
- 239000002826 coolant Substances 0.000 description 16
- 238000004781 supercooling Methods 0.000 description 9
- 238000000926 separation method Methods 0.000 description 8
- 230000005484 gravity Effects 0.000 description 7
- 239000012530 fluid Substances 0.000 description 6
- 230000008859 change Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 239000000243 solution Substances 0.000 description 5
- 238000005516 engineering process Methods 0.000 description 4
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 230000002427 irreversible effect Effects 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 239000000498 cooling water Substances 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 235000013399 edible fruits Nutrition 0.000 description 2
- 230000002708 enhancing effect Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 241000009298 Trigla lyra Species 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 230000002631 hypothermal effect Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000008439 repair process Effects 0.000 description 1
- 238000010025 steaming Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B39/00—Evaporators; Condensers
-
- 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
-
- 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
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
-
- 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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The present invention provides a kind of low-temperature air-conditioning system and air-conditionings, wherein, a kind of low-temperature air-conditioning system, it include: compressor, four-way valve, indoor heat exchanger, outdoor heat exchanger and throttling set, first valve port of four-way valve is connected with compressor, and the second valve port of four-way valve is connected with indoor heat exchanger, and the third valve port of four-way valve is connected with outdoor heat exchanger, further include: supplementary heat exchanger is connected with the outdoor heat exchanger；The first of first separator, the first separator is connected with supplementary heat exchanger, and second mouthful of the first separator is connected with indoor heat exchanger, and the 4th mouthful through supplementary heat exchanger and four-way valve of the third mouth of the first separator is connected.According to the technical solution of the present invention, in the way of non-azeotropic mixed working medium realization low-temperature heating, it effectively increases low boiling point and enters the constituent content of evaporator, and then improve evaporability of the heat exchanger under extremely low environment temperature, enhance the effect of air-conditioning system low-temperature heating.
Description
Technical field
The present invention relates to fields of home appliance technology, in particular to a kind of low-temperature air-conditioning system and a kind of air-conditioning.
Background technique
With the improvement of people ' s living standards with the enhancing of awareness of saving energy, for air-conditioning with its energy conservation, control is flexibly, easy to install
The features such as with maintenance, vast average family is come into, and have been more and more widely used.However, under low-temperature condition, due to
Evaporating temperature is relatively low, and evaporator is easy factors, the heats for causing refrigerant to absorb from air such as frosting and substantially reduces, heating effect
Fruit is deteriorated, and influences the using effect of user, often results in the complaint of client.
Therefore, a kind of low-temperature air-conditioning system how is designed, improves the constituent content that low boiling point enters evaporator, and then improve
The effect of evaporability of the heat exchanger under extremely low environment temperature, enhancing air-conditioning system low-temperature heating becomes technology urgently to be resolved
Problem.
Summary of the invention
The present invention is directed to solve at least one of the technical problems existing in the prior art or related technologies.
For this purpose, an object of the present invention is to provide a kind of low-temperature air-conditioning systems.
It is another object of the present invention to propose a kind of air-conditioning.
To achieve the above object, technical solution according to the first aspect of the invention proposes a kind of low-temperature air-conditioning system,
It include: compressor, four-way valve, indoor heat exchanger, outdoor heat exchanger and throttling set, the first valve port and the compressor phase of four-way valve
Even, the second valve port of four-way valve is connected with indoor heat exchanger, and the third valve port of four-way valve is connected with outdoor heat exchanger, further includes:
Supplementary heat exchanger is connected with outdoor heat exchanger；The first of first separator, the first separator is connected with supplementary heat exchanger, the
Second mouthful of one separator is connected with indoor heat exchanger, and the third mouth of the first separator is through the 4th of supplementary heat exchanger and four-way valve the
Mouth is connected.
Low-temperature air-conditioning system according to the technique and scheme of the present invention realizes gas by the first separator under gravity
Being automatically separated for body and liquid, effectively increases gaseous coolant and enters the constituent content of evaporator, and then improve heat exchanger and exist
Evaporability under extremely low environment temperature enhances the effect of air-conditioning system low-temperature heating.
The low-temperature air-conditioning system of above-mentioned technical proposal according to the present invention can also have following technical characteristic:
Above-mentioned technical proposal according to the present invention, it is preferable that supplementary heat exchanger includes: condensation part and evaporation part, wherein cold
Solidifying portion includes: first interface, and first interface is connected with outdoor heat exchanger；And second interface, second interface and the first separator
First be connected；Evaporation part includes: first entrance, and first entrance is connected with the third mouth of the first separator；And first go out
Mouthful, first outlet is connected by the first pipeline with the 4th valve port of four-way valve.
In the technical scheme, heating circulation when, the first separator separation after liquid refrigerants with come from outdoor heat exchanger
Gaseous coolant mixing after, supplementary heat exchanger evaporation part is entered by the first entrance of supplementary heat exchanger, supplementary heat exchanger evaporation
Portion's evaporation endothermic；And the gaseous coolant after the separation of the first separator, entered by the second interface of supplementary heat exchanger condensation part auxiliary
Heat exchanger is helped, exchanges heat with the refrigerant of evaporation part, is further condensed, is increased the degree of supercooling of refrigerant, facilitate increase system
Refrigerating capacity, subsequently into outdoor heat exchanger evaporation endothermic, and then improve the heating effect of air-conditioning.When refrigeration cycle, refrigerant
It is flowed by the first interface of supplementary heat exchanger, the first separator is then flow to by second interface.
Above-mentioned technical proposal according to the present invention, it is preferable that further include: the second separator, the entrance connection of the second separator
In on the first pipeline, the outlet of the second separator is connected with the air inlet of compressor, and refrigerant flows through second point by the first pipeline
From device, it flow in compressor.
In the technical scheme, mixing refrigerant enters the second separator by the first pipeline, separates by the second separator
Afterwards, liquid refrigerants is discharged, prevents compressor sucking liquid refrigerants and damage, the gaseous coolant after separation flow to compressor, mentions
The high air injection enthalpy-increasing effect of compressor, and then improve the service life of compressor.
Above-mentioned technical proposal according to the present invention, it is preferable that further include: the second pipeline is connected to the first interface of condensation part
With outdoor heat exchanger, refrigerant in cooling mode, the condensation part of supplementary heat exchanger is flow to by outdoor heat exchanger by the second pipeline,
Refrigerant flow to outdoor heat exchanger by the second pipeline in a heating mode, by the condensation part of supplementary heat exchanger；Third pipeline, connection
The third mouth of the evaporation part of supplementary heat exchanger and the first separator, refrigerant flow to supplementary heat exchanger from the third mouth of the first separator
Evaporation part.
In the technical scheme, when refrigeration cycle, refrigerant flow to supplementary heat exchanger from outdoor heat exchanger by the second pipeline
Condensation part, into supplementary heat exchanger after be further subcooled, improve primary flow path refrigerant degree of supercooling, to improve entire air-conditioning system
The exchange capability of heat of system.When heating circulation, refrigerant flow to outdoor heat exchanger by the second pipeline by the condensation part of supplementary heat exchanger,
Refrigerant passes through outdoor heat exchanger evaporation endothermic, becomes the gaseous coolant of low-temp low-pressure.Third pipeline is used for the first separator point
The liquid refrigerants separated out is flowed to the evaporation part of supplementary heat exchanger, and evaporation part makes liquid refrigerants evaporation endothermic.
Above-mentioned technical proposal according to the present invention, it is preferable that further include: first throttling device is set on the second pipeline, control
Freeze flow velocity and pressure of the matchmaker in the second pipeline；Second throttling device is set on third pipeline, is controlled in third pipeline,
Refrigerant is flow to the flow velocity and pressure of the evaporation part of supplementary heat exchanger by the third mouth of the first separator.
In the technical scheme, when refrigerant flow to supplementary heat exchanger by outdoor heat exchanger, by first throttling device, become
The refrigerant of medium temperature and medium pressure can make supplementary heat exchanger that preferably refrigerant further be subcooled.It can be adjusted by second throttling device
Save the flow velocity and pressure of the refrigerant flowed out from the first separator.
Above-mentioned technical proposal according to the present invention, it is preferable that further include: control device is connected with four-way valve, with first segment
Stream device is connected with second throttling device.
In the technical scheme, control device can change the connection direction of four-way valve, in conjunction with first throttling device and
Two throttling sets, can pressure, flow velocity and direction to refrigerant control.
Above-mentioned technical proposal according to the present invention, it is preferable that control device further include: be in heating in low-temperature air-conditioning system
Under mode, the first valve port of control is connected to the second valve port, and the 4th valve port is connected to third valve port, and refrigerant can be by compressor through four-way
The refrigerant flowed out by first outlet can also be mixed with the refrigerant that indoor heat exchanger flows out and be flow into outdoor heat exchanger by valve flow
Second separator；And in the case where low-temperature air-conditioning system is in refrigeration mode, the first valve port of control is connected to third valve port, the 4th valve
It mouthful is connected to the second valve port, refrigerant can be flowed in indoor heat exchanger by compressor through four-way valve, can also will be by first outlet stream
Refrigerant out mixes with the refrigerant that outdoor heat exchanger flows out and flow to the second separator.
In the technical scheme, under heating mode, the first valve port and the second valve port are connected, and the 4th valve port and third valve port connect
Logical, compressor air-discharging enters four-way valve from the first valve port, then flows out from the second valve port, reaches indoor heat exchanger and condenses heat release,
Enter the first separator by second mouthful of the first separator later, gas and liquid realize automatic point under gravity
From liquid refrigerants send to second throttling device and throttles, and subsequently into the evaporation part channel for heat exchange of supplementary heat exchanger, liquid refrigerants steams
Hair heat absorption；Another way gaseous coolant enters the condensation part of supplementary heat exchanger from the first separator top, hands over the refrigerant of evaporation part
Heat exchange amount further condenses, and increases degree of supercooling of the cryogenic fluid before first throttling device throttling, facilitates increase system
Refrigerating capacity.After first throttling device throttles, into outdoor heat exchanger evaporation endothermic, become the gaseous coolant of low-temp low-pressure,
The second separator is reached after converging with the refrigerant from supplementary heat exchanger evaporation part, finally flows back to compressor, completes entire circulation.
Under refrigeration mode, the first valve port is connected to third valve port, and the 4th valve port is connected to the second valve port.Compressor air-discharging warp
It crosses the first valve port and enters four-way valve, outdoor heat exchanger is then entered by third valve port and condenses heat release, is then passed through first throttle
After control device tentatively throttles, the refrigerant for becoming middle pressure medium temperature is further condensed into the condensation part of supplementary heat exchanger, is increased
Refrigerant fluid enters the room the degree of supercooling of heat exchanger, facilitates the refrigerating capacity of increase system.Refrigerant enters first point later
From device, gas is automatically separated with liquid realization under gravity, wherein liquid refrigerants send to second throttling device and throttles
Afterwards, it into the evaporation part evaporation endothermic of supplementary heat exchanger, after then converging with the low-temp low-pressure refrigerant from indoor heat exchanger, arrives
Up to the second separator, the suction line of compressor is returned to, completes refrigeration cycle.
Any of the above-described a technical solution according to the present invention, it is preferable that refrigerant includes: that the different refrigerant of a variety of boiling points is mixed
Mixed non-azeotropic refrigerant made of conjunction.
In the technical scheme, mixed non-azeotropic refrigerant does not have azeotropic point, and when level pressure is evaporated, temperature constantly changes by low
It is slid to height；Level pressure is then exactly the opposite when condensing.Therefore, condensation process cooling water is continually changing, using this characteristic, is subtracted
The heat transfer irreversible loss of small condenser and evaporator is improved the efficiency of refrigeration cycle.
Any of the above-described a technical solution according to the present invention, it is preferable that throttling set includes: electromagnetic type expansion valve, electronic
Formula expansion valve.
In the technical scheme, by the way that throttling set is selected as electromagnetic type expansion valve or electrodynamic type expansion valve, Ke Yishi
Existing condensing pressure controls the flow of refrigerant, to reach to the coolant throttle decompression in pipeline to the throttling of evaporating pressure.
A kind of air-conditioning that the technical solution of second aspect of the present invention provides includes any one technology of first aspect present invention
The low-temperature air-conditioning system that scheme provides, therefore the air-conditioning has the whole of the low-temperature air-conditioning system of any of the above-described a technical solution offer
Beneficial effect, details are not described herein.
Additional aspect and advantage of the invention will be set forth in part in the description, and will partially become from the following description
Obviously, or practice through the invention is recognized.
Detailed description of the invention
Fig. 1 shows a low-temperature air-conditioning system schematic diagram of embodiment according to the present invention.
100 low-temperature air-conditioning systems, 102 compressors, 104 four-way valves, the first valve port of a, the second valve port of b, c third valve port, d
Four valve ports, 106 indoor heat exchangers, 108 outdoor heat exchangers, 110 second separators, 112 first pipelines, 114 second pipelines, 116
First throttling device, 118 third pipelines, 120 second throttling devices, 122 first separators, 124 supplementary heat exchangers, e first,
Second mouthful of f, g third mouth.
Specific embodiment
To better understand the objects, features and advantages of the present invention, with reference to the accompanying drawing and specific real
Applying mode, the present invention is further described in detail.It should be noted that in the absence of conflict, the implementation of the application
Feature in example and embodiment can be combined with each other.
In the following description, numerous specific details are set forth in order to facilitate a full understanding of the present invention, still, the present invention may be used also
To be implemented using other than the one described here other modes, therefore, protection scope of the present invention is not limited to following public affairs
The limitation for the specific embodiment opened.
It is specifically described below with reference to low-temperature air-conditioning system 100 of the Fig. 1 to embodiment according to the present invention.
As shown in Figure 1, the low-temperature air-conditioning system 100 of embodiment according to the present invention includes: compressor 102, four-way valve
104, indoor heat exchanger 106, outdoor heat exchanger 108 and throttling set, the first valve port a and 102 phase of compressor of four-way valve 104
Even, the second valve port b of four-way valve 104 is connected with indoor heat exchanger 106, the third valve port c and outdoor heat exchanger of four-way valve 104
108 are connected, further includes: supplementary heat exchanger 124 is connected with outdoor heat exchanger 108；First separator 122, the first separator 122
First e be connected with supplementary heat exchanger 124, second mouthful of f of the first separator 122 is connected with indoor heat exchanger 106, first point
Third mouth g from device 122 is connected through supplementary heat exchanger 124 and the 4th valve port d's of four-way valve 104.
The low-temperature air-conditioning system 100 of embodiment according to the present invention, it is real under gravity by the first separator 122
Existing gas and liquid are automatically separated, by non-azeotropic mixed working medium realize low-temperature heating in the way of, effectively increase low boiling point
Into the constituent content of evaporator, and then evaporability of the heat exchanger under extremely low environment temperature is improved, enhances low temperature sky
The effect of adjusting system low-temperature heating.
Low-temperature air-conditioning system 100 according to the abovementioned embodiments of the present invention, can also have following technical characteristic:
According to that above embodiment of the present invention, it is preferable that supplementary heat exchanger 124 includes: condensation part and evaporation part, wherein
Condensation part includes: first interface, and first interface is connected with outdoor heat exchanger 108；And second interface, second interface with first point
First from device 122 is connected；Evaporation part includes: first entrance, and first entrance is connected with the third mouth of the first separator 122；
And first outlet, first outlet are connected by the first pipeline 112 with the 4th valve port d of four-way valve 104.
In this embodiment, heating circulation when, the first separator 122 separation after higher boiling liquid refrigerants with from outdoor
After the gaseous coolant mixing of heat exchanger 108,124 right side of supplementary heat exchanger is entered by the first entrance of supplementary heat exchanger 124
Evaporation part, supplementary heat exchanger evaporation part evaporation endothermic；And the low boiling point gaseous coolant after the separation of the first separator 122, by auxiliary
It helps the second interface of the condensation part in 124 left side of heat exchanger to enter supplementary heat exchanger 124, exchanges heat with the refrigerant of evaporation part, into
The condensation of one step, increases the degree of supercooling of refrigerant, facilitates the refrigerating capacity of increase system, evaporates subsequently into outdoor heat exchanger 108
Heat absorption, and then improve the heating effect of air-conditioning.When refrigeration cycle, refrigerant is flowed by the first interface of supplementary heat exchanger, so
The first separator is flow to by second interface afterwards.
According to that above embodiment of the present invention, it is preferable that further include: the second separator 110, the entrance of the second separator 110
It is connected on the first pipeline 112, the outlet of the second separator 110 is connected with the air inlet of compressor 102, and refrigerant passes through the first pipe
Road 112 flows through the second separator 110, flow in compressor 102.
In this embodiment, mixing refrigerant enters the second separator 110 by the first pipeline 112, by the second separator
After 110 separation, liquid refrigerants is discharged, prevents compressor 102 from sucking liquid refrigerants and damaging, the gaseous coolant after separation is flow to
Compressor 102, improves the air injection enthalpy-increasing effect of compressor 102, and then improves the service life of compressor 102.
According to one embodiment of present invention, it is preferable that further include: the second pipeline 114 is connected to the first interface of condensation part
With outdoor heat exchanger 108, refrigerant flow to supplementary heat exchanger by the second pipeline 114 in cooling mode, by outdoor heat exchanger 108
124 condensation part, refrigerant in a heating mode, flow to outdoor by the second pipeline 114 by the condensation part of supplementary heat exchanger 124 and change
Hot device 108；Third pipeline 118, is connected to the evaporation part of supplementary heat exchanger 124 and the third mouth of the first separator 122, and refrigerant is from the
The third mouth g of one separator 122 flow to the evaporation part of supplementary heat exchanger 124.
In this embodiment, when refrigeration cycle, refrigerant flow to auxiliary from outdoor heat exchanger 108 by the second pipeline 114 and changes
The condensation part of hot device 124, into supplementary heat exchanger 124 after be further subcooled, improve primary flow path refrigerant degree of supercooling, to improve
The exchange capability of heat of entire air-conditioning system.When heating circulation, refrigerant passes through the second pipeline by the condensation part of supplementary heat exchanger 124
114 flow to outdoor heat exchanger 108, and refrigerant passes through 108 evaporation endothermic of outdoor heat exchanger, becomes the gaseous coolant of low-temp low-pressure.The
Three pipelines 118 are used to flow the liquid refrigerants that the first separator 122 is isolated to the evaporation part of supplementary heat exchanger 124, evaporation
Portion makes liquid refrigerants evaporation endothermic.
According to one embodiment of present invention, it is preferable that further include: first throttling device 116 is set on the second pipeline,
Control flow velocity and pressure of the refrigerant in the second pipeline；Second throttling device 120 is set on third pipeline, is controlled in third pipe
In road, refrigerant is flow to the flow velocity and pressure of the evaporation part of supplementary heat exchanger 124 by the third mouth of the first separator.
In this embodiment, when refrigerant flow to supplementary heat exchanger 124 by outdoor heat exchanger 108, pass through first throttling device
116, become the refrigerant of medium temperature and medium pressure, can make supplementary heat exchanger 124 that preferably refrigerant further be subcooled.Pass through the second throttling
The flow velocity and pressure of the adjustable refrigerant flowed out from the first separator 122 of device 120.
According to the abovementioned embodiments of the present invention, it is preferable that further include: control device is connected with four-way valve 104, with first
Throttling set 116 is connected with second throttling device 120.
In this embodiment, control device can change the connection direction of four-way valve 104, in conjunction with first throttling device 116
With second throttling device 120, can pressure, flow velocity and direction to refrigerant control.
According to the abovementioned embodiments of the present invention, it is preferable that control device further include: be in heating mould in low-temperature air-conditioning system
Under formula, the first valve port a of control is connected to the second valve port of b, and the 4th valve port of d is connected to c third valve port, and refrigerant can be by compressor 102
It flows in outdoor heat exchanger 108 through four-way valve 104, the refrigerant flowed out by first outlet and indoor heat exchanger 106 can also be flowed
Refrigerant mixing out flow to the second separator 110；And in the case where low-temperature air-conditioning system is in refrigeration mode, the first valve port a is controlled
It is connected to third valve port c, the 4th valve port d is connected to the second valve port b, and refrigerant can flow to room through four-way valve 104 by compressor 102
In interior heat exchanger 106, the refrigerant flowed out by first outlet can also be mixed with the refrigerant that outdoor heat exchanger 108 flows out and flow to second
Separator 110.
In this embodiment, under heating mode, the first valve port a and the second valve port b are connected, the 4th valve port d and third valve port c
Connection, the exhaust of compressor 102 enter four-way valve 104 from the first valve port a, then flow out from the second valve port b, reach indoor heat exchanger
106 condensation heat releases, enter the first separator 122 by second mouthful of the first separator 122 later, under gravity gas
It is automatically separated with liquid realization, liquid refrigerants send to second throttling device 120 and throttles, subsequently into the steaming of supplementary heat exchanger 124
Hair portion channel for heat exchange, liquid refrigerants evaporation endothermic；Another way gaseous coolant enters auxiliary heat-exchanging from 122 top of the first separator
The condensation part of device 124 exchanges heat with the refrigerant of evaporation part, further condenses, increases cryogenic fluid in first throttling device
Degree of supercooling before 116 throttlings, facilitates the refrigerating capacity of increase system.After the throttling of first throttling device 116, changed into outdoor
Hot 108 evaporation endothermic of device, becomes the gaseous coolant of low-temp low-pressure, after converging with the refrigerant from 124 evaporation part of supplementary heat exchanger
The second separator 110 is reached, compressor 102 is finally flowed back to, completes entire circulation.
Under refrigeration mode, the first valve port a is connected to third valve port c, and the 4th valve port d is connected to the second valve port b.Compressor
102 exhausts enter four-way valve 104 by the first valve port a, then enter outdoor heat exchanger 108 by third valve port c and condense heat release,
After being then passed through the tentatively throttling of first throttling device 116, become the refrigerant of middle pressure medium temperature, into the condensation of supplementary heat exchanger 124
Portion further condenses, increases the degree of supercooling that refrigerant fluid enters the room heat exchanger 106, facilitate the refrigeration of increase system
Amount.Refrigerant enters the first separator 122 later, and gas is automatically separated with liquid realization under gravity, wherein liquid is cold
Matchmaker send to the throttling of second throttling device 120, into the evaporation part evaporation endothermic of supplementary heat exchanger 124, then and from interior
After the low-temp low-pressure refrigerant of heat exchanger 106 converges, the second separator 110 is reached, the suction line of compressor 102 is returned to, completed
Refrigeration cycle.
According to the abovementioned embodiments of the present invention, it is preferable that refrigerant includes: that the different refrigerant of a variety of boiling points mixes
Mixed non-azeotropic refrigerant.
In this embodiment, mixed non-azeotropic refrigerant does not have an azeotropic point, when level pressure is evaporated, temperature constantly change by as low as
Height sliding；Level pressure is then exactly the opposite when condensing.Using this characteristic, condensation process cooling water is continually changing, evaporation process
Cooled object temperature is that the alternating temperature feature that constantly reduces is adapted, reduce it is covert during heat transfer temperature difference, reduced
The irreversible loss of journey, and then the heat transfer irreversible loss for reducing condenser and evaporator enables the efficiency of refrigeration cycle to mention
It is high.When the temperature difference between evaporating temperature and cooled object temperature, condensation temperature and surrounding medium temperature is smaller, refrigeration cycle
Efficiency is higher.
Any of the above-described a embodiment according to the present invention, it is preferable that first throttling device 116 include: electromagnetic type expansion valve,
Electrodynamic type expansion valve；And second throttling device 120 includes: electromagnetic type expansion valve, electrodynamic type expansion valve.
In this embodiment, electromagnetic type expansion valve and electrodynamic type expansion valve can control the folding size of spool, Jin Erke
With the flow velocity of refrigerant, flow direction and pressure in control piper.
Embodiment one:
As shown in Figure 1, user opens air-conditioning when winter it is cold, air-conditioning is transferred under heating mode, at this time the first valve
Mouthful a and the second valve port b is connected, and the 4th valve port d is connected to third valve port c, and mixed working fluid is after compressor 102 compresses, by the
One valve port a enters four-way valve 104, then flows out from the second valve port b, reaches indoor heat exchanger 106 and condenses heat release, wherein higher boiling
Component is largely condensed into liquid, and low boiling working fluid still maintains as gaseous state.Pass through the first separator 122 later, in gravity
Under the action of the realization of gas and liquid be automatically separated, the higher boiling liquid refrigerants separated passes through 120 section of second throttling device
After stream, into supplementary heat exchanger on the right side of evaporation part evaporation endothermic；Another way low boiling point gaseous coolant, from the of the first separator
Enter the condensation part on the left of supplementary heat exchanger flatly, exchange heat with the refrigerant of evaporation part, further condenses, increase refrigeration stream
Degree of supercooling of the body before the throttling of first throttling device 116, facilitates the refrigerating capacity of increase system, then, fills by first throttle
After setting 116 throttlings, into outdoor heat exchanger evaporation endothermic, become the gaseous coolant of low-temp low-pressure, is steamed with from evaporative condenser
After the refrigerant of hair side converges, the second separator 6 is reached, returns to compressor into air intake duct pipeline, enhances the injection effect of compressor
Fruit improves the whole capability of compressor 102.
A kind of air-conditioning that the embodiment of second aspect of the present invention provides includes any one embodiment of first aspect present invention
The air-conditioning system of offer, therefore the air-conditioning has whole beneficial effects of the air-conditioning system of any of the above-described a embodiment offer, herein
It repeats no more.
The technical scheme of the present invention has been explained in detail above with reference to the attached drawings, the invention proposes a kind of low-temperature air-conditioning system,
Using the Component Separation Performance of Ternary of non-azeotropic mixed working medium, the constituent content that low boiling point enters evaporator is effectively increased, is improved
Evaporability of the heat exchanger under more low ambient temperature enhances air-conditioning so as to improve the problem of air-conditioning system low temperature capability deficiency
The ability of system hypothermia heating.
The foregoing is only a preferred embodiment of the present invention, is not intended to restrict the invention, for the skill of this field
For art personnel, the invention may be variously modified and varied.All within the spirits and principles of the present invention, made any to repair
Change, equivalent replacement, improvement etc., should all be included in the protection scope of the present invention.
Claims (10)
1. a kind of low-temperature air-conditioning system, comprising: compressor (102), four-way valve (104), indoor heat exchanger (106), outdoor heat exchange
First valve port (a) of device (108) and throttling set, the four-way valve (104) is connected with the compressor (102), the four-way
Second valve port (b) of valve (104) is connected with the indoor heat exchanger (106), the third valve port (c) of the four-way valve (104) with
The outdoor heat exchanger (108) is connected, which is characterized in that further include:
Supplementary heat exchanger (124) is connected with the outdoor heat exchanger (108)；
The first (e) of first separator (122), first separator (122) is connected with the supplementary heat exchanger (124),
Second mouthful (f) of first separator (122) is connected with the indoor heat exchanger (106), first separator (122)
Third mouth (g) is connected through the supplementary heat exchanger (124) with the 4th valve port (d) of the four-way valve (104).
2. low-temperature air-conditioning system according to claim 1, which is characterized in that the supplementary heat exchanger (124) includes: condensation
Portion and evaporation part, wherein
The condensation part includes: first interface, and the first interface is connected with the outdoor heat exchanger (108)；And second connect
Mouthful, the second interface is connected with the first of first separator (122)；
The evaporation part includes: first entrance, and the first entrance is connected with the third mouth of first separator (122)；With
And first outlet, the first outlet are connected by the first pipeline (112) with the 4th valve port (d) of the four-way valve 114.
3. low-temperature air-conditioning system according to claim 2, which is characterized in that further include:
Second separator (110), the entrance of second separator (110) are connected on first pipeline (112), and described
The outlet of two separators (110) is connected with the air inlet of the compressor (102), and refrigerant is flowed by first pipeline (112)
Through second separator (110), it flow in the compressor (102).
4. low-temperature air-conditioning system according to claim 3, which is characterized in that further include:
Second pipeline (114) is connected to first interface and the outdoor heat exchanger (108) of the condensation part, and refrigerant is in refrigeration mould
Under formula, the condensation of the supplementary heat exchanger (124) is flow to by second pipeline (114) by the outdoor heat exchanger (108)
Portion, the refrigerant in a heating mode, are flowed by the condensation part of the supplementary heat exchanger (124) by second pipeline (114)
To the outdoor heat exchanger (108)；
Third pipeline (118) is connected to the evaporation part of the supplementary heat exchanger (124) and the third of first separator (122)
Mouth (g), the refrigerant flow to the evaporation of the supplementary heat exchanger (124) from the third mouth (g) of first separator (122)
Portion.
5. low-temperature air-conditioning system according to claim 4, which is characterized in that further include:
First throttling device (116) is set on second pipeline (114), controls the refrigerant in second pipeline (114)
Interior flow velocity and pressure；
Second throttling device (120) is set on the third pipeline (118), and control is described in the third pipeline (118)
Refrigerant is flow to the flow velocity and pressure of the evaporation part of the supplementary heat exchanger (124) by the third mouth (g) of first separator (122)
By force.
6. low-temperature air-conditioning system according to claim 5, which is characterized in that further include:
Control device is connected with the four-way valve (104), with the first throttling device (116) and the second throttling device
(120) it is connected.
7. low-temperature air-conditioning system according to claim 6, which is characterized in that the control device further include:
In the case where the low-temperature air-conditioning system is in heating mode, first valve port (a) and second valve port (b) are controlled even
Logical, the 4th valve port (d) is connected to the third valve port (c), and the refrigerant can be by the compressor (102) through the four-way
Valve (104) flows in the outdoor heat exchanger (108), can also be by the refrigerant flowed out by the first outlet and the room
The refrigerant mixing of interior heat exchanger (106) outflow flow to second separator (110)；And
In the case where the low-temperature air-conditioning system is in refrigeration mode, first valve port (a) and the third valve port (c) are controlled even
Logical, the 4th valve port (d) is connected to second valve port (b), and the refrigerant can be by the compressor (102) through the four-way
Valve (104) flows in the indoor heat exchanger (106), can also be by the refrigerant flowed out by the first outlet and the room
The refrigerant mixing of external heat exchanger (108) outflow flow to second separator (110).
8. the low-temperature air-conditioning system according to any one of claim 3 to 7, which is characterized in that
The refrigerant includes: the mixed non-azeotropic refrigerant that the different refrigerant of a variety of boiling points mixes.
9. low-temperature air-conditioning system according to any one of claim 1 to 7, which is characterized in that
The throttling set includes: electromagnetic type expansion valve, electrodynamic type expansion valve.
10. a kind of air-conditioning, which is characterized in that including low-temperature air-conditioning system described in any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611046317.4A CN106766325B (en) | 2016-11-22 | 2016-11-22 | Low-temperature air-conditioning system and air-conditioning |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611046317.4A CN106766325B (en) | 2016-11-22 | 2016-11-22 | Low-temperature air-conditioning system and air-conditioning |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106766325A CN106766325A (en) | 2017-05-31 |
| CN106766325B true CN106766325B (en) | 2019-08-06 |
Family
ID=58975385
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201611046317.4A Active CN106766325B (en) | 2016-11-22 | 2016-11-22 | Low-temperature air-conditioning system and air-conditioning |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106766325B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107677008A (en) * | 2017-11-09 | 2018-02-09 | 青岛海尔空调器有限总公司 | The air-conditioning heating circulatory system and air conditioner |
| CN109974321A (en) * | 2019-03-18 | 2019-07-05 | 嘉兴学院 | A kind of compound liquid storage device of rotary type intelligent freezer compressor |
| CN112539452B (en) * | 2020-12-18 | 2021-12-03 | 珠海格力电器股份有限公司 | Multi-split air conditioner and control method thereof |
Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6449853A (en) * | 1987-08-21 | 1989-02-27 | Toshiba Corp | Refrigeration cycle device |
| JPH04324072A (en) * | 1991-04-25 | 1992-11-13 | Sanden Corp | Refrigeration circuit for non-azeotropic refrigerant |
| JPH08285410A (en) * | 1995-04-12 | 1996-11-01 | Sanyo Electric Co Ltd | Freezer device |
| JPH10160267A (en) * | 1996-11-25 | 1998-06-19 | Hitachi Ltd | Air conditioner |
| CN200972281Y (en) * | 2006-11-21 | 2007-11-07 | 华南理工大学 | Large temp. differential self-cascade heat pump with segregator |
| CN201621894U (en) * | 2010-01-29 | 2010-11-03 | 武汉新世界制冷工业有限公司 | High-efficient screw-type auto-cascade refrigerating system |
| CN201653011U (en) * | 2010-04-15 | 2010-11-24 | 广东美的电器股份有限公司 | Heat pump system of air conditioner |
| CN201757533U (en) * | 2010-05-31 | 2011-03-09 | 西安交通大学 | Self-cascade heat pump with intermediate throttling element |
| CN102066852A (en) * | 2008-06-16 | 2011-05-18 | 三菱电机株式会社 | Non-azeotropic refrigerant mixture and refrigeration cycle device |
| AU2014100193A4 (en) * | 2014-02-28 | 2014-04-03 | Allied Refrigeration And Engineering Pty. Limited | Application of Carbon Dioxide to a Mixed-Gas Auto-Cascade Refrigeration System |
| CN205208992U (en) * | 2015-10-15 | 2016-05-04 | 德阳九鼎智远知识产权运营有限公司 | Natural cascade refrigeration system of intelligence |
-
2016
- 2016-11-22 CN CN201611046317.4A patent/CN106766325B/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6449853A (en) * | 1987-08-21 | 1989-02-27 | Toshiba Corp | Refrigeration cycle device |
| JPH04324072A (en) * | 1991-04-25 | 1992-11-13 | Sanden Corp | Refrigeration circuit for non-azeotropic refrigerant |
| JPH08285410A (en) * | 1995-04-12 | 1996-11-01 | Sanyo Electric Co Ltd | Freezer device |
| JPH10160267A (en) * | 1996-11-25 | 1998-06-19 | Hitachi Ltd | Air conditioner |
| CN200972281Y (en) * | 2006-11-21 | 2007-11-07 | 华南理工大学 | Large temp. differential self-cascade heat pump with segregator |
| CN102066852A (en) * | 2008-06-16 | 2011-05-18 | 三菱电机株式会社 | Non-azeotropic refrigerant mixture and refrigeration cycle device |
| CN201621894U (en) * | 2010-01-29 | 2010-11-03 | 武汉新世界制冷工业有限公司 | High-efficient screw-type auto-cascade refrigerating system |
| CN201653011U (en) * | 2010-04-15 | 2010-11-24 | 广东美的电器股份有限公司 | Heat pump system of air conditioner |
| CN201757533U (en) * | 2010-05-31 | 2011-03-09 | 西安交通大学 | Self-cascade heat pump with intermediate throttling element |
| AU2014100193A4 (en) * | 2014-02-28 | 2014-04-03 | Allied Refrigeration And Engineering Pty. Limited | Application of Carbon Dioxide to a Mixed-Gas Auto-Cascade Refrigeration System |
| CN205208992U (en) * | 2015-10-15 | 2016-05-04 | 德阳九鼎智远知识产权运营有限公司 | Natural cascade refrigeration system of intelligence |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106766325A (en) | 2017-05-31 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN211739588U (en) | Air conditioner capable of improving heat exchange performance | |
| CN103175344B (en) | Cold-region used multi-connected heat pump system and control method thereof | |
| WO2019091241A1 (en) | Cooling circulation system for air conditioning, and air conditioner | |
| CN107178833B (en) | Heat recovery external machine system and air conditioning system | |
| CN104061705A (en) | Two-stage compression air conditioning system and control method thereof | |
| CN106524610A (en) | Air conditioning system and air conditioner | |
| CN106322814A (en) | Air conditioning system and air conditioner | |
| CN105180489B (en) | A kind of mixture throttling refrigerating machine and its refrigerating method for adapting to variable parameter operation | |
| CN106766325B (en) | Low-temperature air-conditioning system and air-conditioning | |
| CN100507401C (en) | Capacity adjustable vortex compressor refrigeration system with mediate loop installed with ejector | |
| CN109737624A (en) | A kind of dual temperature refrigeration system and its control method | |
| CN203964436U (en) | Two-stage compression air conditioning system | |
| CN106996657A (en) | Air regulator | |
| CN109579356B (en) | Temperature control multi-online heat pump system with heat recovery function and control method | |
| CN104764241A (en) | Air conditioner | |
| CN106403347B (en) | Low-temperature air-conditioning system and air-conditioning | |
| CN109442788A (en) | Defrosting method of air conditioner and air conditioner | |
| CN103528136B (en) | Fresh air handling units and control system thereof | |
| CN108119953A (en) | Splitting heat pump air conditioner device | |
| CN208765303U (en) | air conditioning system | |
| CN216347034U (en) | Heat exchange system and air conditioner with same | |
| CN106556175A (en) | Air-conditioning system and air-conditioning | |
| CN105526735B (en) | A kind of efficient big temperature rise two-stage throttling two stages of compression heat pump water-heating machine | |
| CN215930176U (en) | Refrigerating system | |
| CN212362485U (en) | Heat pump system with double suction and exhaust |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |