CN114459080B - Heat exchanger and air conditioner - Google Patents
Heat exchanger and air conditioner Download PDFInfo
- Publication number
- CN114459080B CN114459080B CN202210239120.1A CN202210239120A CN114459080B CN 114459080 B CN114459080 B CN 114459080B CN 202210239120 A CN202210239120 A CN 202210239120A CN 114459080 B CN114459080 B CN 114459080B
- Authority
- CN
- China
- Prior art keywords
- heat exchange
- supercooling
- section
- common
- heat exchanger
- 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
- 238000004781 supercooling Methods 0.000 claims abstract description 122
- 239000007788 liquid Substances 0.000 claims description 52
- 238000010257 thawing Methods 0.000 abstract description 3
- 239000003507 refrigerant Substances 0.000 description 9
- 230000000694 effects Effects 0.000 description 7
- 238000004378 air conditioning Methods 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 4
- 238000000926 separation method Methods 0.000 description 4
- 230000017525 heat dissipation Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- SAPGTCDSBGMXCD-UHFFFAOYSA-N (2-chlorophenyl)-(4-fluorophenyl)-pyrimidin-5-ylmethanol Chemical compound C=1N=CN=CC=1C(C=1C(=CC=CC=1)Cl)(O)C1=CC=C(F)C=C1 SAPGTCDSBGMXCD-UHFFFAOYSA-N 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 239000004744 fabric Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/14—Heat exchangers specially adapted for separate outdoor units
- F24F1/16—Arrangement or mounting thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/14—Heat exchangers specially adapted for separate outdoor units
- F24F1/18—Heat exchangers specially adapted for separate outdoor units characterised by their shape
-
- 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
- F25B39/04—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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
-
- 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
- F25B41/40—Fluid line arrangements
- F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention provides a heat exchanger and an air conditioner.A common heat exchange area and a supercooling heat exchange area are alternately distributed on a heat exchanger body perpendicular to the heat exchange wind direction; the common heat exchange area is composed of at least one section of common heat exchange section, and the supercooling heat exchange area is composed of at least one section of supercooling heat exchange section. The invention can solve the problem of uneven liquid-separating heat exchange of the heat exchanger flow paths, and the supercooling heat exchange section can not block the heat exchange of the common heat exchange section, thereby ensuring the uniformity of liquid-separating heat exchange of each flow path. Because the supercooling heat exchange section is more effectively dispersed, the influence of uneven air quantity on heat exchange is prevented, and the defrosting efficiency of the heat exchanger under the external working condition of easy frosting is improved. In addition, the diversion point and the confluence point of the heat exchange pipeline are connected by adopting a Y-shaped tee joint, so that the pipeline can be effectively simplified and the cost can be reduced.
Description
Technical Field
The invention relates to the technical field of air conditioners, in particular to a heat exchanger and an air conditioner.
Background
The heat exchanger is one of the important parts of the air conditioning and refrigerating system. In designing an air conditioning system, in addition to the selection of the size of the heat exchanger, the design of the distribution of the heat exchanger flow paths is also very important. In the prior art, in order to increase the heat exchange amount and reduce the pressure drop of a system, the total supercooling heat exchange section of the heat exchanger is generally divided into a plurality of supercooling heat exchange sections to different positions of the heat exchanger; in the flow path scheme shown in fig. 1, 3 rows of heat exchange tubes are provided, and 3 supercooling heat exchange sections P1, P2 and P3 are separated from one row on the windward side, and the rest heat exchange pipelines are common heat exchange sections. The scheme can improve the supercooling degree and the refrigerating capacity of the system, and can avoid the problems of too high flow speed, insufficient heat exchange and rising pressure drop of the refrigerant caused by the fact that all branches are converged into one path of supercooling.
However, in the above scheme, 3 supercooling heat exchange sections are concentrated on a row at the windward side to exchange heat, so that the heat exchange effect of the common heat exchange sections can be affected, and the supercooling heat exchange sections can block the heat exchange between the common heat exchange sections at the leeward side and the wind, so that the liquid separation heat exchange of the heat exchanger flow path is uneven. This negative effect will also be amplified when an maldistribution of the wind field is encountered.
Disclosure of Invention
In view of the above, the invention provides a heat exchanger and an air conditioner, which can solve the problem of uneven liquid separation and heat exchange of a heat exchanger flow path.
The invention provides a heat exchanger, wherein a common heat exchange area and a supercooling heat exchange area are alternately distributed on a heat exchanger body perpendicular to the heat exchange wind direction;
The common heat exchange area is composed of at least one section of common heat exchange section, and the supercooling heat exchange area is composed of at least one section of supercooling heat exchange section.
Preferably, the individual subcooling heat exchange zones are connected in parallel.
Preferably, the supercooling heat exchange region comprises a first supercooling heat exchange section and a second supercooling heat exchange section connected in parallel.
Preferably, the individual common heat exchange zones are connected in parallel.
Preferably, the common heat exchange zone comprises a first common heat exchange section and a second common heat exchange section connected in parallel.
Preferably, each subcooling heat exchange section is connected in series with at least one common heat exchange section.
Preferably, the heat exchanger is provided with a total liquid inlet pipeline and a total liquid outlet pipeline;
The liquid outlet of the total liquid inlet pipeline is connected with the common heat exchange sections of the common heat exchange areas;
The liquid inlet of the total liquid outlet pipeline is connected with the supercooling heat exchange sections of the supercooling heat exchange areas, and the liquid outlet of the total liquid outlet pipeline is connected with the throttling device;
At least one row of common heat exchange sections are arranged in the common heat exchange area facing the heat exchange wind direction, and at least one row of supercooling heat exchange sections are arranged in the supercooling heat exchange area facing the heat exchange wind direction.
Preferably, the common heat exchange section cloth tube specifications of each common heat exchange zone are the same, or the supercooling heat exchange section cloth tube specifications of each supercooling heat exchange zone are the same.
Preferably, the split point and the confluence point of the heat exchange pipeline of the heat exchanger are connected by adopting a Y-shaped tee joint.
The beneficial effects of the invention are as follows: the supercooling heat exchange section can not block the heat exchange of the common heat exchange section, so that the uniformity of liquid separation heat exchange of each flow path is ensured, and the supercooling heat exchange section is more effectively dispersed, so that the influence of uneven air quantity on heat exchange is prevented; the split point and the confluence point of the heat exchange pipeline are connected by adopting a Y-shaped tee joint, so that the pipeline can be effectively simplified and the cost can be reduced; under the external working condition of easy frosting, the flow path distribution structure of the heat exchanger can improve the defrosting efficiency and the energy efficiency.
Drawings
The invention is described in detail below with reference to examples and figures, wherein:
Fig. 1 is a tube layout of a heat exchanger according to prior art 1.
Fig. 2 is a tube layout of the heat exchanger according to the prior art 2.
Fig. 3 is a schematic diagram of a tube layout of the heat exchanger of the present invention.
Fig. 4 is a piping scheme of the first embodiment of the present invention.
Fig. 5 is a piping scheme of a second embodiment of the present invention.
Fig. 6 is a piping scheme of a third embodiment of the present invention.
Detailed Description
In order to make the technical problems, technical schemes and beneficial effects to be solved more clear, the invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention.
Thus, reference throughout this specification to one feature will be used in order to describe one embodiment of the invention, not to imply that each embodiment of the invention must be in the proper motion. Furthermore, it should be noted that the present specification describes a number of features. Although certain features may be combined together to illustrate a possible system design, such features may be used in other combinations not explicitly described. Thus, unless otherwise indicated, the illustrated combinations are not intended to be limiting.
The principles of the present invention are described in detail below with reference to the drawings and examples.
FIG. 1 shows a prior art solution in which the heat exchange flow path splits into 3 heat exchange branches L1, L2 and L3, wherein the L1 branch comprises an M1 common heat exchange section and a P1 subcooling heat exchange section; the L2 shunt comprises an M2 common heat exchange section and a P2 supercooling heat exchange section; the L3 branch circuit comprises an M3 common heat exchange section and a P3 supercooling heat exchange section. The drawbacks of this solution are: because the three supercooling heat exchange sections P1, P2 and P3 are concentrated on the windward side for heat exchange, the heat exchange between the common heat exchange section on the leeward side and wind is blocked, so that the heat dissipation of part of the common heat exchange sections is affected, and the heat exchange of liquid is uneven. This negative effect will also be amplified when an maldistribution of the wind field is encountered.
Fig. 2 shows another prior art scheme, in which a total of 4 heat exchange branches L1, L2, L3 and L4 are arranged on a heat exchanger, each heat exchange branch is divided into two parallel common heat exchange sections, and then the total of 8 common heat exchange sections are converged and mixed and then enter a total supercooling heat exchange section P. After the refrigerant completes heat exchange in the total supercooling heat exchange section P, the refrigerant flows to the throttling device through the total liquid outlet pipe 2.
In this scheme, 8 common heat exchange sections are concentrated at the upper part of the heat exchanger to form a common heat exchange area 110, the total supercooling heat exchange section P forms a supercooling heat exchange area 210 at the bottom of the heat exchanger, and heat exchange air blows through the heat exchanger from the right side and exchanges heat with the common heat exchange area 110 and the supercooling heat exchange area 210.
The drawbacks of this solution are: the supercooling heat exchange section of the heat exchanger is concentrated at one place, so that supercooling heat exchange is too concentrated, and the heat dissipation effect can be seriously affected when the heat exchange environment is affected. In addition, the supercooling heat exchange section of the scheme has large pressure difference and high flow velocity, so that the supercooling effect cannot be fully exerted.
In order to solve the problems of uneven liquid-separating heat exchange and poor supercooling heat exchange effect of a heat exchanger flow path in the prior art, the invention provides a novel heat exchanger, and aims to improve the heat exchanger distribution pipe and the flow path in the prior art.
The present invention proposes a heat exchanger as shown in fig. 3, wherein the heat exchange wind direction moves from the right side to the left side of the heat exchanger, the main body of the heat exchanger is alternately distributed with a common heat exchange area and a supercooling heat exchange area perpendicular to the heat exchange wind direction, and the heat exchanger sequentially comprises a first common heat exchange area 110, a first supercooling heat exchange area 210, a second common heat exchange area 120, a second supercooling heat exchange area 220, a third common heat exchange area 130 and a third supercooling heat exchange area 230 from top to bottom.
The first general heat exchange area 110 is formed by a general heat exchange section M1, the first supercooling heat exchange area 210 is formed by a supercooling heat exchange section P1, the second general heat exchange area 120 is formed by a general heat exchange section M2, the second supercooling heat exchange area 220 is formed by a supercooling heat exchange section P2, the third general heat exchange area 130 is formed by a general heat exchange section M3, and the third supercooling heat exchange area 230 is formed by a supercooling heat exchange section P3.
The common heat exchange sections M1, M2 and M3 and the supercooling heat exchange sections P1, P2 and P3 are coiled on the heat exchanger body to form a tube. The pipe arrangement distance and the pipe diameters of all sections can be adjusted according to the shape of the heat exchanger body and the specific air quantity of all parts of the heat exchanger body. The optimal pipe distribution scheme is that the common heat exchange section adopts a uniform pipe distribution specification, and the supercooling heat exchange section also adopts a uniform pipe distribution specification, namely, the pipe distribution pipe diameters, materials, densities and trend of the common heat exchange sections M1, M2 and M3 are the same, and the pipe distribution pipe diameters, materials, densities and trend of the supercooling heat exchange sections P1, P2 and P3 are the same, so that the pressure, the refrigerant flow rate and the temperature of each heat dissipation flow path are more balanced.
In this embodiment, the common heat exchange areas are connected in parallel, and at the same time, the supercooling heat exchange areas are also connected in parallel, and each supercooling heat exchange section is connected in series with at least one common heat exchange section. Specifically, the common heat exchange section M1 is connected in series with the supercooling heat exchange section P1, the common heat exchange section M2 is connected in series with the supercooling heat exchange section P2, the common heat exchange section M3 is connected in series with the supercooling heat exchange section P3, and so on; in addition, each supercooling heat exchange section including P1, P2 and P3 is connected in parallel, and the refrigerant flows to the supercooling heat exchange section through the common heat exchange section during heat exchange and flows to the throttling device after converging.
In addition, the supercooling heat exchange section is more effectively dispersed, so that the influence of uneven heat exchange air quantity on supercooling heat exchange is reduced.
Example 1
The invention provides an embodiment shown in fig. 4 for a specific tube arrangement mode of the heat exchanger.
In this embodiment, the heat exchanger is divided into 4 heat exchange areas from top to bottom, namely, a first ordinary heat exchange area 110, a first supercooling heat exchange area 210, a second ordinary heat exchange area 120, and a second supercooling heat exchange area 220. The common heat exchange area is composed of common heat exchange section pipes, and the supercooling heat exchange area is composed of supercooling heat exchange section pipes.
In this embodiment, the common heat exchange sections of each common heat exchange area have the same specification, and each common heat exchange section comprises a first common heat exchange section A1, a second common heat exchange section A2, a third common heat exchange section A3 and a fourth common heat exchange section A4 which are connected in parallel. The supercooling heat exchange sections of each supercooling heat exchange zone have the same specification and comprise a first supercooling heat exchange section B1 and a second supercooling heat exchange section B2 which are connected in parallel. The first common heat exchange section A1 and the second common heat exchange section A2 are connected in series with the first supercooling heat exchange section B1 after converging, and the third common heat exchange section A3 and the fourth common heat exchange section A4 are connected in series with the second supercooling heat exchange section B2 after converging.
Because each supercooling heat exchange zone is connected with two supercooling heat exchange sections of different flow paths in parallel, for example, the first supercooling heat exchange zone 210 comprises a first supercooling heat exchange section B1 and a second supercooling heat exchange section B2, the installation cost of the supercooling heat exchange sections can be reduced under the condition that the overall heat exchange effect is not affected.
In this embodiment, the heat exchanger is provided with a total liquid inlet pipeline 1 and a total liquid outlet pipeline 2, a liquid outlet of the total liquid inlet pipeline 1 is connected with liquid inlets of all the common heat exchange sections, a liquid inlet of the total liquid outlet pipeline 2 is connected with liquid outlets of all the supercooling heat exchange sections, and a liquid outlet of the total liquid outlet pipeline 2 is connected with the throttling device.
In order to improve the heat exchange capacity of the heat exchanger, two rows of common heat exchange sections are arranged in a staggered manner in the direction facing the heat exchange wind direction in each common heat exchange area, and two rows of supercooling heat exchange sections are arranged in a staggered manner in each supercooling heat exchange area in the direction facing the heat exchange wind direction.
Three rows of common heat exchange sections and supercooling heat exchange sections can be further arranged according to the requirements. Regardless of the increase and decrease of the number of the rows of the tubes, each common heat exchange area and each supercooling heat exchange area always keep expanding or reducing occupied space along the heat exchange wind direction, and the condition that the supercooling heat exchange sections and the common heat exchange sections mutually block heat exchange airflow is avoided.
When heat exchange is performed in the air conditioning refrigeration mode, heat exchange air passes through the heat exchanger from the right side to move to the left side, and the supercooling heat exchange area and the common heat exchange area are not blocked, so that uniform heat exchange can be realized, and the problem that heat exchange cannot be completely performed due to uneven air quantity of a heat exchanger fan can be effectively prevented.
When the air conditioner exchanges heat in a heating mode, the refrigerant is throttled and then shunted to enter a supercooling heat exchange section, so that the refrigerant enters a heat exchanger to exchange heat, the flow speed and pressure drop of the gaseous refrigerant are reduced when the gaseous refrigerant enters the heat exchanger, and the phenomenon that the heating performance of the air conditioner is affected by frosting due to lower side pressure of the heating low-pressure side is avoided.
In the embodiment, the split point and the confluence point of the heat exchange pipeline of the heat exchanger are connected by adopting the Y-shaped tee joint with uniform specification, so that the material cost can be reduced, and the difficulty of maintenance of a later product is reduced.
When the external environment is in the working condition of easy frosting, the supercooling heat exchange sections are distributed to different parts of the heat exchanger, so that the defrosting efficiency is improved, the uniform frosting of the air conditioning unit is facilitated, and the energy efficiency is improved while the heating quantity is improved.
Example 2
The invention provides an embodiment shown in fig. 5 for a specific tube arrangement mode of the heat exchanger.
In this embodiment, the heat exchangers are divided into 10 heat exchange areas from top to bottom, including a first general heat exchange area 110, a first supercooling heat exchange area 210, a second general heat exchange area 120, a second supercooling heat exchange area 220, a third general heat exchange area 130, a third supercooling heat exchange area 230, a fourth general heat exchange area 140, a fourth supercooling heat exchange area 240, a fifth general heat exchange area 150, and a fifth supercooling heat exchange area 250. The common heat exchange area is composed of common heat exchange section pipes, and the supercooling heat exchange area is composed of supercooling heat exchange section pipes.
In this embodiment, the common heat exchange sections of each common heat exchange area have the same specification, and each common heat exchange section includes a first common heat exchange section A1 and a second common heat exchange section A2 connected in parallel. The specification of the supercooling heat exchange section of each supercooling heat exchange zone is the same, and only the supercooling heat exchange section B is included. The first common heat exchange section A1 and the second common heat exchange section A2 are connected in series with the supercooling heat exchange section B after converging.
In this embodiment, the heat exchanger is provided with a total liquid inlet pipeline 1 and a total liquid outlet pipeline 2, a liquid outlet of the total liquid inlet pipeline 1 is connected with liquid inlets of all the common heat exchange sections, a liquid inlet of the total liquid outlet pipeline 2 is connected with liquid outlets of all the supercooling heat exchange sections, and a liquid outlet of the total liquid outlet pipeline 2 is connected with the throttling device.
In the embodiment, the number of the supercooling heat exchange areas is more, the number of supercooling heat exchange sections in each supercooling heat exchange area is correspondingly reduced, the influence of uneven heat exchange air quantity on supercooling heat exchange is further reduced, and the liquid separation heat exchange of each flow path of the heat exchanger is more balanced.
Example 3
The invention proposes an embodiment as shown in fig. 6 for a specific tube arrangement of the heat exchanger.
In this embodiment, the heat exchangers are divided into 10 heat exchange areas from top to bottom, including a first general heat exchange area 110, a first supercooling heat exchange area 210, a second general heat exchange area 120, a second supercooling heat exchange area 220, a third general heat exchange area 130, a third supercooling heat exchange area 230, a fourth general heat exchange area 140, a fourth supercooling heat exchange area 240, a fifth general heat exchange area 150, and a fifth supercooling heat exchange area 250. The common heat exchange area is composed of common heat exchange section pipes, and the supercooling heat exchange area is composed of supercooling heat exchange section pipes.
In this embodiment, the common heat exchange sections of each common heat exchange area have the same specification, and each common heat exchange section includes a first common heat exchange section A1 and a second common heat exchange section A2 connected in parallel. The specification of the supercooling heat exchange section of each supercooling heat exchange zone is the same, and only the supercooling heat exchange section B is included. The first common heat exchange section A1 and the second common heat exchange section A2 are connected in series with the supercooling heat exchange section B after converging.
In this embodiment, the heat exchanger is provided with a total liquid inlet pipeline 1 and a total liquid outlet pipeline 2, a liquid outlet of the total liquid inlet pipeline 1 is connected with liquid inlets of all the common heat exchange sections, a liquid inlet of the total liquid outlet pipeline 2 is connected with liquid outlets of all the supercooling heat exchange sections, and a liquid outlet of the total liquid outlet pipeline 2 is connected with the throttling device. After the number of the tube arrangement is increased, the heat exchange capacity of the heat exchanger can be further improved.
Examples 1 and 2 set forth a2 gauntlet arrangement and example 3 set forth a3 gauntlet arrangement. The specific scheme can be determined according to factors such as actually required heat exchange power, heat exchange area and production cost.
In addition, the invention also provides an air conditioner which adopts the heat exchanger described in any one of the embodiments.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the invention.
Claims (6)
1. A heat exchanger is characterized in that a common heat exchange area and a supercooling heat exchange area are alternately distributed on a main body of the heat exchanger perpendicular to the heat exchange wind direction;
the general heat exchange area is composed of at least one section of general heat exchange section, and the supercooling heat exchange area is composed of at least one section of supercooling heat exchange section;
each supercooling heat exchange area is connected in parallel;
Each common heat exchange area is connected in parallel;
each supercooling heat exchange section is connected with at least one common heat exchange section in series;
The heat exchanger is provided with a total liquid inlet pipeline and a total liquid outlet pipeline;
The liquid outlet of the total liquid inlet pipeline is connected with the common heat exchange sections of the common heat exchange areas;
the liquid inlet of the total liquid outlet pipeline is connected with the supercooling heat exchange sections of the supercooling heat exchange areas, and the liquid outlet of the total liquid outlet pipeline is connected with the throttling device;
At least one row of common heat exchange sections are arranged in the direction facing the heat exchange wind direction, and at least one row of supercooling heat exchange sections are arranged in the direction facing the heat exchange wind direction.
2. The heat exchanger of claim 1, wherein the subcooling heat exchange zone comprises a first subcooling heat exchange section and a second subcooling heat exchange section connected in parallel.
3. The heat exchanger of claim 1, wherein the common heat transfer zone comprises a first common heat transfer section and a second common heat transfer section connected in parallel.
4. The heat exchanger of claim 1, wherein the common heat exchange section tube layout of each common heat exchange zone is the same in specification, or the subcooling heat exchange section tube layout of each subcooling heat exchange zone is the same in specification.
5. The heat exchanger of claim 1, wherein the split point and the sink point of the heat exchange tube of the heat exchanger are connected by a Y-tee.
6. An air conditioner, characterized in that the heat exchanger according to any one of claims 1 to 5 is used.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210239120.1A CN114459080B (en) | 2022-03-11 | 2022-03-11 | Heat exchanger and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210239120.1A CN114459080B (en) | 2022-03-11 | 2022-03-11 | Heat exchanger and air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114459080A CN114459080A (en) | 2022-05-10 |
| CN114459080B true CN114459080B (en) | 2024-09-24 |
Family
ID=81418160
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210239120.1A Active CN114459080B (en) | 2022-03-11 | 2022-03-11 | Heat exchanger and air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114459080B (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201285195Y (en) * | 2008-10-13 | 2009-08-05 | 海信（山东）空调有限公司 | Heat exchanger of air conditioner and air conditioner mounted with the same |
| CN216953290U (en) * | 2022-03-11 | 2022-07-12 | 珠海格力电器股份有限公司 | Heat exchanger and air conditioner |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100225628B1 (en) * | 1997-01-20 | 1999-10-15 | 윤종용 | Refrigerant distribution structure of multi type airconditioner |
| JP4073850B2 (en) * | 2003-09-11 | 2008-04-09 | シャープ株式会社 | Heat exchanger |
| JP4715963B1 (en) * | 2010-02-15 | 2011-07-06 | ダイキン工業株式会社 | Air conditioner heat exchanger |
| CN201715782U (en) * | 2010-06-09 | 2011-01-19 | 广东美的电器股份有限公司 | Channel variable liquid-gas separation type heat exchanger |
| JP2012202636A (en) * | 2011-03-25 | 2012-10-22 | Toshiba Corp | Air conditioner outdoor unit |
| US20120291478A1 (en) * | 2011-05-20 | 2012-11-22 | Kia Motors Corporation | Condenser for vehicle and air conditioning system for vehicle |
| JP2013029257A (en) * | 2011-07-29 | 2013-02-07 | Keihin Thermal Technology Corp | Condenser |
| CN203928497U (en) * | 2014-05-29 | 2014-11-05 | 美的集团股份有限公司 | Heat exchanger and air-conditioning |
| CN109751752B (en) * | 2019-01-10 | 2023-04-07 | 青岛海尔空调器有限总公司 | Heat exchanger and air conditioner |
| CN209978343U (en) * | 2019-04-09 | 2020-01-21 | 苏州三星电子有限公司 | Heat exchanger and air conditioner for reducing noise of refrigerant fluid |
| CN112178795A (en) * | 2020-11-02 | 2021-01-05 | 珠海格力电器股份有限公司 | Outdoor heat exchanger and air conditioning device |
-
2022
- 2022-03-11 CN CN202210239120.1A patent/CN114459080B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201285195Y (en) * | 2008-10-13 | 2009-08-05 | 海信（山东）空调有限公司 | Heat exchanger of air conditioner and air conditioner mounted with the same |
| CN216953290U (en) * | 2022-03-11 | 2022-07-12 | 珠海格力电器股份有限公司 | Heat exchanger and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114459080A (en) | 2022-05-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106233077B (en) | Air-conditioning device | |
| CN203323459U (en) | Heat exchanger | |
| CN214581751U (en) | Heat exchanger and air conditioner | |
| US10670311B2 (en) | Heat exchanger | |
| CN214276219U (en) | Heat exchanger and air conditioner | |
| CN102445100A (en) | Heat exchange tube unit, finned tube air-cooled condenser and cooling air evaporator | |
| CN214275958U (en) | Heat exchanger and air conditioner | |
| CN104764256A (en) | Heat exchanger and multi-split system with the same | |
| CN203758089U (en) | Micro-channel heat exchanger and air conditioner with micro-channel heat exchanger | |
| CN105352225A (en) | Air conditioner | |
| CN216953290U (en) | Heat exchanger and air conditioner | |
| CN108351188A (en) | Heat exchanger and air-conditioning | |
| CN110220296A (en) | A kind of heat exchanger and air conditioner | |
| CN114459080B (en) | Heat exchanger and air conditioner | |
| CN102635984B (en) | Outdoor condenser and air-conditioner | |
| WO2020019386A1 (en) | High-efficiency evaporative condenser with hot and cold complementary variable function | |
| CN111512099B (en) | Heat exchanger and refrigeration cycle device | |
| CN202581953U (en) | Condenser of outdoor machine and air-conditioner | |
| CN106871496B (en) | Indoor heat exchanger and air conditioner | |
| CN109654597A (en) | A kind of air-conditioning system that can adjust heat exchange amount | |
| CN105180307B (en) | A kind of air-conditioner outdoor unit and its condenser | |
| CN201476415U (en) | Heat exchanger of outdoor unit of air-cooled heat pump air conditioner | |
| CN202281365U (en) | Air conditioner heat exchanger and air conditioner with same | |
| CN210374186U (en) | Condenser, heat exchange system and air conditioner | |
| CN207247642U (en) | A kind of straight-expansion type air conditioner device of the balanced liquid separation of energy |
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 |