CN114812014A - Heat exchanger and air conditioner - Google Patents
Heat exchanger and air conditioner Download PDFInfo
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- CN114812014A CN114812014A CN202210465056.9A CN202210465056A CN114812014A CN 114812014 A CN114812014 A CN 114812014A CN 202210465056 A CN202210465056 A CN 202210465056A CN 114812014 A CN114812014 A CN 114812014A
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- heat exchange
- 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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
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- 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
- F24F1/0003—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station characterised by a split arrangement, wherein parts of the air-conditioning system, e.g. evaporator and condenser, are in separately located units
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- 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
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The application discloses heat exchanger and air conditioner relates to air conditioner technical field for solve the lower problem of heat exchange efficiency of current heat exchanger. The heat exchanger comprises a gas collecting pipe, a heat exchanger main body and a flow dividing piece. Wherein, the inside formation gas collecting chamber of gas collecting pipe, the first blow vent and a plurality of second blow vent that communicate with gas collecting chamber are seted up to the gas collecting pipe. The heat exchanger main part includes a plurality of first heat transfer branch roads and at least one second heat transfer branch road, and the first end and the second vent intercommunication of every first heat transfer branch road, the first end and the second end intercommunication of at least two first heat transfer branch roads of every second heat transfer branch road. The interior of reposition of redundant personnel is formed into the reposition of redundant personnel chamber, and the reposition of redundant personnel piece is seted up with the confluence mouth and at least one branch opening that reposition of redundant personnel chamber communicates, and every branch opening communicates with the second end of a second heat transfer branch road. The heat exchanger is used for exchanging heat with the refrigerant.
Description
Technical Field
The application relates to the technical field of air conditioners, in particular to a heat exchanger and an air conditioner.
Background
In the context of the "two-carbon policy", higher demands are made on the capacity and energy efficiency of the air conditioner. The heat exchanger is a core component for heat exchange between the air conditioner and air, is used as an evaporator or a condenser, and can effectively control the temperature of the indoor environment. Therefore, the heat exchange performance of the heat exchanger is directly related to the operation efficiency of the air conditioner.
The existing heat exchanger has low heat exchange efficiency, so that the operation efficiency of the air conditioner is low, and the requirements of energy conservation and emission reduction cannot be met.
Disclosure of Invention
The application provides a heat exchanger and an air conditioner for solve the lower problem of heat exchange efficiency of current heat exchanger.
In order to achieve the purpose, the technical scheme is as follows:
on the one hand, this application embodiment provides a heat exchanger, and the heat exchanger includes discharge, heat exchanger main part and reposition of redundant personnel piece. Wherein, the inside formation gas collecting chamber of gas collecting pipe, the first blow vent and a plurality of second blow vent that communicate with gas collecting chamber are seted up to the gas collecting pipe. The heat exchanger main part includes a plurality of first heat transfer branch roads and at least one second heat transfer branch road, and the first end and the second vent intercommunication of every first heat transfer branch road, the first end and the second end intercommunication of at least two first heat transfer branch roads of every second heat transfer branch road. The interior of reposition of redundant personnel is formed into the reposition of redundant personnel chamber, and the reposition of redundant personnel piece is seted up with the confluence mouth and at least one branch opening that reposition of redundant personnel chamber communicates, and every branch opening communicates with the second end of a second heat transfer branch road.
Based on this, when the heat exchanger that this application embodiment provided was used as the condenser, the refrigerant enters into the gas collecting chamber of gas collecting inside through first air vent earlier, shunts in the gas collecting chamber, then enters into the heat exchanger main part through a plurality of second air vents. The refrigerants flowing out of the second vent holes firstly exchange heat for the first time through the first heat exchange branch circuits respectively, then the refrigerants in the at least two first heat exchange branch circuits exchange heat for the second time after being communicated with the second heat exchange branch circuit, finally converge into the flow dividing cavity through the flow dividing ports of the flow dividing pieces, and flow out through the convergence port. Therefore, the number of the first heat exchange branch circuits for performing the first heat exchange on the refrigerant is larger than that of the second heat exchange branch circuits for performing the second heat exchange on the refrigerant. When the refrigerant carries out the heat exchange for the first time, the dryness factor of the refrigerant is larger, the density is smaller, the refrigerant is firstly divided into more flow paths for heat exchange, the flow of each path can be reduced, the flow speed of each path of corresponding refrigerant can be reduced, and the heat exchange efficiency can be improved. When the second heat exchange is carried out, the dryness of the refrigerant becomes relatively smaller, and the density is relatively larger, at the moment, the refrigerant is divided into fewer flow paths for the second heat exchange, so that the heat exchange efficiency can be improved.
When the heat exchanger that this application embodiment provided was as the evaporimeter, the flow direction of refrigerant for the confluence mouth that passes through the reposition of redundant personnel earlier flows into the reposition of redundant personnel chamber, flows into in the heat exchanger main part from at least one reposition of redundant personnel mouth again. Then, the refrigerant flowing out of at least one of the branch ports firstly enters the heat exchanger main body through at least one second heat exchange branch to perform primary heat exchange, then the refrigerant in each second heat exchange branch is divided, the divided refrigerant enters the heat exchanger main body again through at least two first heat exchange branches to perform secondary heat exchange, finally converges in the gas collection cavity through a plurality of second vent ports, and flows out of the first vent ports. Therefore, the number of the second heat exchange branches for performing the first heat exchange on the refrigerant is less than that of the first heat exchange branches for performing the second heat exchange on the refrigerant. When the refrigerant carries out the first heat exchange, the dryness factor of the refrigerant is smaller, the density is larger, the refrigerant is firstly divided into fewer flow paths to enter the heat exchanger body for the first heat exchange, and the heat exchange performance of the heat exchanger can be improved. When the second heat exchange is carried out, the dryness of the refrigerant becomes relatively large, the density is relatively small, at the moment, the refrigerant is divided into more flow paths to enter the heat exchanger main body for the second heat exchange, the flow of each path can be reduced, the flow speed of each path of corresponding refrigerant is reduced, the pressure loss of the heat exchanger is small, and the heat exchange efficiency is improved. Therefore, when the heat exchanger is used as an evaporator and the flow dividing design scheme is adopted, the pressure loss of the heat exchanger can be reduced, and the heat exchange efficiency of the heat exchanger is improved.
In some embodiments, adjacent at least two first heat exchange branches constitute a tube bank. The heat exchanger comprises at least one group of pipeline groups, and the second ends of at least two first heat exchange branches in the group of pipeline groups are communicated with the first end of one second heat exchange branch. And the at least one second heat exchange branch is positioned at one side of the at least one group of pipeline groups.
In some embodiments, the first heat exchange branch comprises at least two rows of sub-branches arranged side by side and at least one communicating pipe. At least one communicating pipe is positioned between two adjacent rows of sub-branches and communicated with the two adjacent rows of sub-branches.
In some embodiments, the sub-branch may include a plurality of first heat exchange tubes and a plurality of second heat exchange tubes. Wherein, a plurality of first heat exchange tubes interval and parallel arrangement, first heat exchange tube and communicating pipe cross arrangement. The second heat exchange tubes are arranged in parallel at intervals, one second heat exchange tube is positioned between two adjacent first heat exchange tubes and communicated with the two adjacent first heat exchange tubes, and the second heat exchange tubes and the first heat exchange tubes are arranged in a crossed mode.
In some embodiments, in the same first heat exchange branch, a refrigerant transmission path formed by two adjacent sub-branches and the communicating pipe is U-shaped. Or, in the same first heat exchange branch, a refrigerant transmission path formed by two adjacent sub-branches and the communicating pipe is Z-shaped.
In some embodiments, in the same tube bank, the refrigerant transmission paths formed by two adjacent sub-branches and the communicating tube in different first heat exchange branches are different in shape.
In some embodiments, the second heat exchange branch may include a plurality of third heat exchange tubes and a plurality of fourth heat exchange tubes. Wherein, a plurality of third heat exchange tubes interval and parallel arrangement. The plurality of fourth heat exchange tubes are arranged in parallel at intervals and are communicated with the two adjacent third heat exchange tubes, and one fourth heat exchange tube is positioned between the two adjacent third heat exchange tubes. The fourth heat exchange tube and the third heat exchange tube are arranged in a crossed mode.
In some embodiments, the heat exchanger may further comprise at least one pressure reducing pipe, one end of each pressure reducing pipe being in communication with the second end of one of the second heat exchanging branches, and the other end being in communication with one of the branch ports of the branch member.
On the other hand, the embodiment of the application also provides an air conditioner, which comprises a compressor, a four-way valve, an outdoor heat exchanger and an indoor heat exchanger. The four-way valve is provided with a first valve port, a second valve port, a third valve port and a fourth valve port. The compressor is provided with an air inlet and an air outlet, the air inlet is communicated with the first valve port, and the air outlet is communicated with the second valve port. One end of the outdoor heat exchanger is communicated with the third valve port. One end of the indoor heat exchanger is communicated with the fourth valve port, and the other end of the indoor heat exchanger is communicated with the other end of the outdoor heat exchanger. Wherein, at least one of the indoor heat exchanger and the outdoor heat exchanger is the heat exchanger.
Because the air conditioner that this application embodiment provided includes any kind of above-mentioned heat exchanger, consequently can solve the same problem with above-mentioned heat exchanger to reach the same technological effect, no longer repeated here.
In some embodiments, the outdoor heat exchanger may be the heat exchanger described above. At the moment, the first air vent of the air collecting pipe is communicated with the third valve port, and the confluence port of the flow dividing piece is communicated with the indoor heat exchanger.
In some embodiments, the indoor heat exchanger may be the heat exchanger described above. At the moment, the first air vent of the air collecting pipe is communicated with the fourth valve port, and the confluence port of the flow dividing piece is communicated with the outdoor heat exchanger.
Drawings
In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present application, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
Fig. 1 is a block diagram of an air conditioner according to an embodiment of the present disclosure;
fig. 2 is a block diagram illustrating a structure of an air conditioner in a cooling mode according to an embodiment of the present disclosure;
fig. 3 is a block diagram illustrating a structure of an air conditioner in a heating mode according to an embodiment of the present disclosure;
FIG. 4 is a schematic flow diagram of a heat exchanger used as a condenser according to an embodiment of the present disclosure;
fig. 5 is a pressure-enthalpy diagram of an air conditioner according to an embodiment of the present disclosure;
FIG. 6 is a schematic flow diagram of a heat exchanger according to an embodiment of the present disclosure as an evaporator;
fig. 7 is another pressure-enthalpy diagram of an air conditioner according to an embodiment of the present disclosure;
FIG. 8 is a schematic partial structural view of a heat exchanger according to an embodiment of the present disclosure;
FIG. 9 is an enlarged view of a portion of FIG. 4 at E;
FIG. 10 is a schematic connection diagram of a sub-branch of a heat exchanger according to an embodiment of the present disclosure;
fig. 11 is a partial enlarged view of F in fig. 4.
Reference numerals:
100-air conditioning; 1-a compressor; 2-a four-way valve; 3-a heat exchanger; 4-an oil separator; 5-a gas-liquid separator; 6-outdoor fan; 7-an indoor fan; 8-outdoor expansion valve; 9-indoor expansion valve; 10-oil return pressure reducing pipe; 11-a stop valve; 3 a-an outdoor heat exchanger; 3 b-indoor heat exchanger; 21-a first valve port; 22-a second valve port; 23-a third port; 24-fourth port; 31-a gas collecting pipe; 32-a heat exchanger body; 33-a splitter; 34-a pressure reducing tube; 101-an air inlet; 102-an air outlet; 311-gas collecting cavity; 312 — a first vent; 313-a second vent; 321-a first heat exchange branch; 322-a second heat exchange branch; 323-pipe set; 331-a shunting cavity; 332-a sink port; 333-shunt port; 3211-tributary; 3212-communicating tube; 3221-a third heat exchange tube; 3222-a fourth heat exchange tube; 32111-a first heat exchange tube; 32112-a second heat exchange tube.
Detailed Description
The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only a part of the embodiments of the present application, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
In the description of the present application, it is to be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience in describing the present application and simplifying the description, but do not indicate or imply that the referred device or element must have a particular orientation, be constructed in a particular orientation, and be operated, and thus should not be construed as limiting the present application.
In the description of the present application, the terms "first", "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implying any number of technical features indicated. Thus, features defined as "first" and "second" may be used to explicitly or implicitly include one or more of the features. In the description of the present application, "a plurality" means two or more unless otherwise specified.
It should be noted that in practical applications, due to the limitation of the precision of the device or the installation error, the absolute parallel or perpendicular effect is difficult to achieve. The vertical, parallel or same-directional descriptions in this application are not an absolute limiting condition, but rather indicate that the vertical or parallel structural arrangement can be realized within a preset error range and achieve a corresponding preset effect, so that the technical effect of limiting features can be realized maximally, the corresponding technical scheme is convenient to implement, and the feasibility is high.
In the description of the present application, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted" and "connected" are to be interpreted broadly, e.g., as being either fixedly connected, detachably connected, or integrally connected; may be a mechanical connection; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present application can be understood in a specific case by those of ordinary skill in the art.
Because the air conditioner can simply and quickly bring comfortable indoor temperature environment for people, the air conditioner becomes an indispensable household appliance in daily life with the increasing improvement of the living standard of people.
With the continuous deepening of the concept of energy conservation and emission reduction, better requirements are made on the operating efficiency of the air conditioner. In the related art, in order to improve the operation efficiency of the air conditioner, methods such as increasing the capacity of an air conditioner compressor, improving the efficiency of an air conditioner inverter, or reducing the pressure loss of an air conditioner gas-liquid separator may be adopted to improve the operation efficiency of the air conditioner. However, the above method improves the operation efficiency of the air conditioner and also increases the design cost of the air conditioner correspondingly.
The heat exchanger is used as an important component of the air conditioner, the heat exchange performance of the heat exchanger has important influence on the operation efficiency of the air conditioner, and how to improve the heat exchange efficiency of the heat exchanger becomes a key for improving the operation efficiency of the air conditioner.
In the related art, in order to improve the heat exchange performance of the heat exchanger and further realize the efficient operation of the air conditioner, the operating efficiency of the air conditioner is improved by adopting a scheme of increasing the area of the heat exchanger. However, the above scheme can increase the design cost of the air conditioner while improving the operation efficiency of the air conditioner.
Based on this, an embodiment of the present application provides an air conditioner, and referring to fig. 1, fig. 1 is a block diagram of a structure of the air conditioner provided in the embodiment of the present application, and the air conditioner 100 may include a compressor 1, a four-way valve 2, an outdoor heat exchanger 3a, and an indoor heat exchanger 3 b. The four-way valve 2 has a first port 21, a second port 22, a third port 23, and a fourth port 24. The compressor 1 has an inlet 101 and an outlet 102, the inlet 101 communicating with the first valve port 21, and the outlet 102 communicating with the second valve port 22. One end of the outdoor heat exchanger 3a communicates with the third port 23. One end of the indoor heat exchanger 3b is communicated with the fourth valve port 24, and the other end is communicated with the other end of the outdoor heat exchanger 3 a.
The compressor 1 may compress a refrigerant into a high-temperature and high-pressure gaseous refrigerant, and may discharge the compressed gaseous refrigerant. The outdoor heat exchanger 3a and the indoor heat exchanger 3b may function as a condenser or an evaporator. When the outdoor heat exchanger 3a or the indoor heat exchanger 3b serves as a condenser, the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 may be condensed into a high-pressure and medium-temperature liquid refrigerant, and heat may be released to the surrounding environment through the condensation process. When the outdoor heat exchanger 3a or the indoor heat exchanger 3b serves as an evaporator, the cooling effect can be achieved by evaporating the liquid refrigerant into the gaseous refrigerant by absorbing heat of the surrounding environment.
It is understood that when the air conditioner is in the heating mode, the outdoor heat exchanger 3a functions as an evaporator and the indoor heat exchanger 3b functions as a condenser. When the air conditioner 100 is in the cooling mode, the outdoor heat exchanger 3a functions as a condenser and the indoor heat exchanger 3b functions as an evaporator.
With continued reference to fig. 1, it is understood that the air conditioner 100 provided in the embodiment of the present application may further include an oil separator 4, a gas-liquid separator 5, an outdoor fan 6, an indoor fan 7, an outdoor expansion valve 8, an indoor expansion valve 9, an oil return decompression pipe 10, and a plurality of shutoff valves 11.
The oil separator 4 is connected between the air outlet 102 of the compressor 1 and the second valve port 22 of the four-way valve 2, and is used for separating lubricating oil mixed in high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1, so that safe and efficient operation of the air conditioning system can be ensured.
The gas-liquid separator 5 is connected between the air inlet 101 of the compressor 1 and the first valve port 21 of the four-way valve 2, and mainly functions to store part of the refrigerant in the air conditioning system and prevent the compressor oil from being diluted by liquid impact of the compressor 1 and excessive refrigerant.
The outdoor fan 6 is located at the outdoor heat exchanger 3a and is used for accelerating the flow of air around the outdoor heat exchanger 3a, so as to improve the heat exchange efficiency of the outdoor heat exchanger 3 a. The indoor fan 7 is located at the indoor heat exchanger 3b and used for accelerating the flow of air around the indoor heat exchanger 3b, and further improving the heat exchange efficiency of the indoor heat exchanger 3 b.
The outdoor expansion valve 8 and the indoor expansion valve 9 are both positioned between the indoor heat exchanger 3b and the outdoor heat exchanger 3a, wherein the outdoor expansion valve 8 is positioned at one side close to the outdoor heat exchanger 3a, the indoor expansion valve 9 is positioned at one side close to the indoor heat exchanger 3b, and the outdoor expansion valve and the indoor expansion valve both have the functions of throttling and depressurizing the high-pressure medium-temperature refrigerant condensed by the condenser to enable the refrigerant to become low-temperature low-pressure refrigerant easy to evaporate, and further achieve the purpose of improving the evaporation efficiency of the evaporator.
The oil return pressure reducing pipe 10 is connected between the oil separator 4 and the air inlet 101 of the compressor 1, and is used for reducing the pressure of the high-pressure lubricating oil discharged from the compressor 1, and preventing the high-pressure lubricating oil from directly entering the compressor 1 and further damaging the compressor 1.
The shutoff valves 11 are located between the outdoor expansion valve 8 and the indoor expansion valve 9, and between the indoor heat exchanger 3b and the fourth valve port 24, respectively.
Illustratively, two stop valves 11 are arranged between the outdoor expansion valve 8 and the indoor expansion valve 9, and a liquid pipe is connected between the two stop valves 11; two stop valves 11 are arranged between the indoor heat exchanger 3b and the fourth valve port 24, and an air pipe is connected between the two stop valves 11.
The conduction modes of the first valve port 21, the second valve port 22, the third valve port 23 and the fourth valve port 24 in the four-way valve 2 can be changed, and the functions of the outdoor heat exchanger 3a and the indoor heat exchanger 3b can be changed by changing the conduction modes of the first valve port 21, the second valve port 22, the third valve port 23 and the fourth valve port 24 in the four-way valve 2, so that the working mode of the air conditioner 100 can be changed. The conducting mode of the four-way valve and the flow direction of the refrigerant when the air conditioner is in different working modes will be further described with reference to the attached drawings.
Referring to fig. 2 and fig. 2 are block diagrams illustrating a configuration of an air conditioner in a cooling mode according to an embodiment of the present invention, when the air conditioner 100 operates in the cooling mode, first, the second port 22 and the third port 23 of the four-way valve 2 are communicated, and the first port 21 and the fourth port 24 are communicated. The low-temperature and low-pressure refrigerant is compressed by the compressor 1 to form a high-temperature and high-pressure superheated refrigerant gas, and then discharged from the compressor 1. The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 is deoiled by the oil separator 4 and then flows into the outdoor heat exchanger 3a through the four-way valve 2.
Then, the high-temperature and high-pressure gaseous refrigerant is condensed into a high-pressure medium-temperature liquid refrigerant in the outdoor heat exchanger 3a, and at the same time, the outdoor fan 6 operates to accelerate heat exchange between the refrigerant and air around the outdoor heat exchanger 3 a.
Then, the liquid refrigerant flowing out of the outdoor heat exchanger 3a passes through the outdoor expansion valve 8, the shutoff valve 11, and the indoor expansion valve 9 in this order. After the two times of throttling and pressure reduction by the outdoor expansion valve 8 and the indoor expansion valve 9, the high-pressure medium-temperature liquid refrigerant is changed into a low-temperature low-pressure gas-liquid two-phase mixed refrigerant.
Then, the low-temperature low-pressure gas-liquid two-phase mixed refrigerant enters the indoor heat exchanger 3b, is evaporated by the indoor heat exchanger 3b to become a low-temperature low-pressure gaseous refrigerant, and meanwhile, the indoor fan 7 operates to accelerate heat exchange between the refrigerant and air around the indoor heat exchanger 3 b. In this way, the refrigerant absorbs heat in the room in the indoor heat exchanger 3b, and the indoor temperature is reduced.
Finally, the refrigerant coming out of the indoor heat exchanger 3b passes through the shutoff valve 11, the four-way valve 2, and the gas-liquid separator 5 in this order, and further flows into the air inlet 101 of the compressor 1, thereby completing the entire refrigeration cycle.
Referring to fig. 3 and 3, which are block diagrams illustrating the air conditioner according to an embodiment of the present invention in a heating mode, when the air conditioner 100 operates in the heating mode, first, the second port 22 of the four-way valve 2 is communicated with the fourth port 24, and the first port 21 is communicated with the third port 23. The low-temperature and low-pressure refrigerant is compressed by the compressor 1 to form high-temperature and high-pressure superheated refrigerant gas, and then the superheated refrigerant gas is discharged from the compressor 1; the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 is deoiled by the oil separator 4, and then flows into the indoor heat exchanger 3b through the four-way valve 2 and the shutoff valve 11.
Then, the high-temperature high-pressure gaseous refrigerant exchanges heat with indoor air in the indoor heat exchanger 3b and is condensed into high-pressure medium-temperature liquid refrigerant, and heat released by the refrigerant in the condensation process is sent into the room, so that the purpose of increasing the indoor temperature is achieved. Meanwhile, the indoor fan 7 operates to accelerate the heat exchange speed between the indoor air and the refrigerant.
Then, the high-pressure medium-temperature liquid refrigerant flowing out of the indoor heat exchanger 3b sequentially flows through the indoor expansion valve 9, the stop valve 11, and the outdoor expansion valve 8, and after twice throttling and pressure reduction by the indoor expansion valve 9 and the outdoor expansion valve 8, the high-pressure medium-temperature liquid refrigerant becomes a low-temperature low-pressure gas-liquid two-phase mixed refrigerant. Then, the low-temperature low-pressure gas-liquid two-phase mixed refrigerant enters the outdoor heat exchanger 3a, and is evaporated by the outdoor heat exchanger 3a to become a low-temperature low-pressure gaseous refrigerant, and at the same time, the outdoor fan 6 operates to accelerate heat exchange between the refrigerant and the air around the outdoor heat exchanger 3 a.
Finally, the refrigerant coming out of the outdoor heat exchanger 3a passes through the four-way valve 2 and the gas-liquid separator 5 in order, and flows into the air inlet 101 of the compressor 1, thereby completing the entire heating cycle.
It is understood that in some embodiments, the outdoor heat exchanger 3a and the indoor heat exchanger 3b may be the same heat exchanger or may be two different heat exchangers. In order to improve the heat exchange efficiency of the outdoor heat exchanger 3a and the indoor heat exchanger 3b, the embodiment of the present application provides a heat exchanger, which can be used as the outdoor heat exchanger 3a or the indoor heat exchanger 3b in the air conditioner 100. The heat exchanger provided by the embodiment of the present application is further described below.
Referring to fig. 4 and fig. 4, which are schematic views of a flow path of a heat exchanger provided in an embodiment of the present application when the heat exchanger is used as a condenser, the heat exchanger 3 may include a gas collecting pipe 31, a heat exchanger main body 32, and a flow dividing member 33.
The gas collecting pipe 31 forms a gas collecting cavity 311, and the gas collecting pipe 31 is provided with a first vent 312 and a plurality of second vents 313 communicated with the gas collecting cavity 311. The heat exchanger body 32 comprises a plurality of first heat exchanging branches 321 and at least one second heat exchanging branch 322, a first end of each first heat exchanging branch 321 is communicated with one second vent 313, and a first end of each second heat exchanging branch 322 is communicated with second ends of at least two first heat exchanging branches 321. The flow dividing member 33 is internally provided with a flow dividing chamber 331, the flow dividing member 33 is provided with a confluence port 332 communicated with the flow dividing chamber 331 and at least one flow dividing port 333, and each flow dividing port 333 is communicated with the second end of one second heat exchange branch 322.
Thus, with continued reference to fig. 4, when the heat exchanger 3 is used as a condenser, the refrigerant first enters the gas collecting chamber 311 inside the gas collecting pipe 31 through the first air vent 312, is divided in the gas collecting chamber 311, and then enters the heat exchanger main body 32 through the plurality of second air vents 313. In this way, the refrigerant can be buffered before entering the heat exchanger body 32, and the heat exchanger body 32 is prevented from being damaged by the impact of the refrigerant.
Then, the refrigerants flowing out of the second vent holes 313 first exchange heat through the first heat exchange branches 321, and then the refrigerants in at least two first heat exchange branches 321 are communicated with one second heat exchange branch 322 and then exchange heat for the second time. In this way, the number of the first heat exchange branch passages 321 that perform the first heat exchange with respect to the refrigerant is greater than the number of the second heat exchange branch passages 322 that perform the second heat exchange with respect to the refrigerant. When the refrigerant carries out the heat exchange for the first time, the dryness factor of the refrigerant is larger, the density is smaller, the refrigerant is firstly divided into more flow paths for heat exchange, the flow of each path can be reduced, the flow speed of each path of corresponding refrigerant can be reduced, and the heat exchange efficiency can be improved. In the second heat exchange, the dryness of the refrigerant becomes relatively low and the density is relatively high, and at this time, the refrigerant is divided into a few flow paths to perform the second heat exchange, so that the heat exchange efficiency can be improved.
Therefore, when the heat exchanger 3 is used as a condenser and the flow dividing design scheme is adopted, the supercooling degree of the condensed refrigerant can be increased, and the heat exchange efficiency of the heat exchanger 3 is improved.
In addition, since the flow dividing chamber 331 is formed inside the flow dividing member 33, the flow dividing member 33 is opened with the confluence port 332 communicating with the flow dividing chamber 331 and at least one flow dividing port 333, and each flow dividing port 333 communicates with the second end of one second heat exchange branch 322. In this way, the refrigerant flowing out of the second heat exchange branch 322 after the second heat exchange can enter the branch chamber 331 of the branch member 33 through the branch port 333, and finally the refrigerant collected in the branch chamber 331 flows out of the confluence port 332.
When the heat exchanger provided in the embodiment of the present application is used as a condenser, the heat exchange efficiency improvement effect thereof can be referred to fig. 5, and fig. 5 is a pressure-enthalpy diagram of an air conditioner provided in the embodiment of the present application, where a-b-c-d are state points of each position when an outdoor heat exchanger in the air conditioner is a common outdoor heat exchanger, where a is an exhaust state point of a compressor 1 (fig. 2), b is a state point after condensation of an outdoor heat exchanger 3a, c is a state point after throttling by an expansion valve 8, and d is a state point after evaporation of an indoor heat exchanger 3 b. a-b '-c' -d are state points of each position when the outdoor heat exchanger in the air conditioner is the heat exchanger provided by the embodiment of the application, wherein b 'is a state point after being condensed by the outdoor heat exchanger 3a, and c' is a state point after being throttled by the expansion valve 8. It can be seen that, by applying the split-flow design scheme of the heat exchanger 3 provided by the embodiment of the present application, the temperature of the heat exchanger 3 after being condensed as a condenser is reduced by Δ h from b → b' to increase the supercooling degree of the refrigerant after being condensed, and the heat exchange efficiency of the heat exchanger 3 when being used as a condenser is improved.
In a second case, referring to fig. 6, fig. 6 is a schematic flow path diagram of a heat exchanger according to an embodiment of the present invention when the heat exchanger 3 is used as an evaporator, and when the heat exchanger is used as an evaporator, the refrigerant flows into the branch chamber 331 through the junction 332 of the branch member 33, and then flows into the heat exchanger main body 32 from at least one branch port 333.
Then, the refrigerant flowing out of the at least one tap 333 enters the heat exchanger main body 32 through the at least one second heat exchange branch 322 to perform first heat exchange, then the refrigerant in each second heat exchange branch 322 is further split, and the split refrigerant enters the heat exchanger main body 32 again through the at least two first heat exchange branches 321 to perform second heat exchange. In this way, the number of the second heat exchange branch passages 322 for performing the first heat exchange with respect to the refrigerant is smaller than the number of the first heat exchange branch passages 321 for performing the second heat exchange with respect to the refrigerant. When the refrigerant carries out the first heat exchange, the dryness factor of the refrigerant is smaller, the density is larger, the refrigerant is firstly divided into a few flow paths to enter the heat exchanger 3 body for the first heat exchange, and the heat exchange performance of the heat exchanger 3 can be improved. When the second heat exchange is performed, the dryness of the refrigerant becomes relatively large, the density is relatively small, at this time, the refrigerant is divided into more flow paths to enter the heat exchanger main body 32 for the second heat exchange, the flow of each path can be reduced, the flow rate of each path of corresponding refrigerant is reduced, the pressure loss of the heat exchanger 3 is small, and the heat exchange efficiency is improved.
Therefore, when the heat exchanger 3 is used as an evaporator and the flow dividing design scheme is adopted, the pressure loss of the heat exchanger 3 can be reduced, and the heat exchange efficiency of the heat exchanger 3 is improved.
Then, the refrigerant flowing out of the first heat exchange branches 321 may be collected into the gas collecting chamber 311 inside the gas collecting pipe 31 through the second air vents 313, and then may flow out through the first air vents 312.
When the heat exchanger provided in the embodiment of the present application is used as an evaporator, the effect of improving the heat exchange efficiency of the heat exchanger can be referred to fig. 7, and fig. 7 is another pressure-enthalpy diagram of an air conditioner provided in the embodiment of the present application, where a-B-C-D is a state point of each position when an outdoor heat exchanger in the air conditioner is a common outdoor heat exchanger, a is an exhaust state point of the compressor 1, B is a state point after condensation of the indoor heat exchanger 3B, C is a state point after throttling of the expansion valve, and D is a state point after evaporation of the outdoor heat exchanger. A '-B-C-D' is a state point of each position when an outdoor heat exchanger in the air conditioner is the heat exchanger provided by the embodiment of the application, A 'is a gas exhaust state point of the compressor 1, and D' is a state point after the outdoor heat exchanger is evaporated. It can be seen that, by the split flow design of the heat exchanger 3 provided in the embodiment of the present application, when the heat exchanger 3 is used as an outdoor heat exchanger, the state point after evaporation is from D → D ', and the discharge state point of the compressor 1 is from a → a', the pressure drop of the refrigerant after evaporation is reduced by Δ P, and the discharge temperature of the compressor 1 is also reduced. That is, the heat exchanger 3 provided by the embodiment of the present application is used as an evaporator, so that the pressure loss of the refrigerant in the evaporation process can be reduced, the exhaust temperature of the compressor 1 can be reduced, and the heat exchange efficiency of the heat exchanger 3 can be improved.
Therefore, through the analysis of the two situations, the heat exchanger 3 provided by the embodiment of the application can improve the heat exchange performance of the heat exchanger 3 by changing the shunting mode of the refrigerant in the heat exchanger, and the heat exchanger 3 is used as a condenser or an evaporator, so that the efficient operation of the air conditioner can be realized. In addition, the heat exchanger 3 that this application embodiment provided can be under the prerequisite that does not increase the cost of heat exchanger 3, through changing the reposition of redundant personnel mode of refrigerant in the heat exchanger, can promote the heat transfer performance of heat exchanger 3, and then can improve the operating efficiency of air conditioner 100, reduces the cost of air conditioner.
It is understood that both the outdoor heat exchanger 3a and the indoor heat exchanger 3b of the air conditioner 100 shown in fig. 1 may be selected from the heat exchangers 3 provided in the embodiments of the present application.
When the outdoor heat exchanger 3a is the heat exchanger 3 described above, the first air port 312 of the gas header 31 communicates with the third valve port 23, and the junction port 332 of the flow divider 33 communicates with the indoor heat exchanger 3 b.
When the indoor heat exchanger 3b is the heat exchanger 3 described above, the first air port 312 of the air collector 31 communicates with the fourth valve port 24, and the flow collecting port 332 of the flow divider communicates with the outdoor heat exchanger 3 a.
Of course, both the outdoor heat exchanger 3a and the indoor heat exchanger 3b may be the heat exchanger 3 described above. At this time, the first air port 312 of the header 31 of the heat exchanger 3, which is the outdoor heat exchanger 3a, communicates with the third valve port 23, and the junction 332 of the flow divider 33 communicates with the indoor heat exchanger 3 b. The first air port 312 of the header 31 of the heat exchanger 3 serving as the indoor heat exchanger 3b communicates with the fourth valve port 24, and the junction 332 of the flow divider communicates with the outdoor heat exchanger 3 a.
Continuing with the description of the heat exchanger 3, referring to fig. 8, fig. 8 is a partial schematic structural diagram of a heat exchanger provided in an embodiment of the present application, and in some embodiments, at least two adjacent first heat exchange branches 321 form a pipe group 323. The heat exchanger 3 comprises at least one group of pipe sets 323, and the second ends of at least two first heat exchange branches 321 in the group of pipe sets 323 are communicated with the first end of one second heat exchange branch 322, that is, the second ends of all first heat exchange branches 321 in the group of pipe sets 323 are connected with the first end of one second heat exchange branch 322. At least one second heat exchange branch 322 is located on one side of at least one set of tube banks 323, i.e., all second heat exchange branches 322 in heat exchanger body 32 are located on one side of all tube banks 323.
Therefore, by making at least two adjacent first heat exchange branches 321 form a pipe group 323, and making the second ends of all first heat exchange branches 321 in the pipe group 323 communicate with the first end of one second heat exchange branch 322, it is more convenient to connect a plurality of first heat exchange branches 321 with one second heat exchange branch 322.
Illustratively, as shown in fig. 8, the heat exchanger body 32 may include three tube banks 323, and each tube bank 323 may be formed by two first heat exchange branches 321. Correspondingly, the heat exchanger body 32 may further include three second heat exchange branches 322. Of course, the heat exchanger main body 32 may also include other numbers of the pipe sets 323, for example, two or four pipe sets 323, and each pipe set 323 may also include other numbers of the first heat exchange branches 321, for example, each pipe set 323 includes three first heat exchange branches 321 or four first heat exchange branches 321, which may be specifically designed according to the size of the heat exchanger and is not further limited herein.
All second heat exchange branches 322 in heat exchanger 3 are located on one side of all tube banks 323. Therefore, the first heat exchange branch 321 and the second heat exchange branch 322 can exchange heat at one side respectively, so that the mutual influence between the first heat exchange branch 321 and the second heat exchange branch 322 is small, and further the heat exchange efficiency of the heat exchanger 3 can be further improved.
Of course, in other embodiments, the tube group 323 may also be disposed at an interval with the second heat exchange branch 322, that is, one side of each tube group 323 is disposed with one second heat exchange branch 322, so that each tube group 323 is relatively close to the second heat exchange branch, and the connection is more convenient.
Referring to fig. 9, fig. 9 is a partial enlarged view of fig. 4 at E, and in some embodiments, the first heat exchange branch 321 may include at least two rows of sub-branches 3211 and at least one communicating pipe 3212 arranged side by side. At least one communicating pipe 3212 is located between two adjacent rows of sub-branches 3211 and is communicated with the two adjacent rows of sub-branches 3211.
In this way, because at least two rows of sub-branches 3211 of the first heat exchange branch 321 are arranged side by side, the length of the heat exchanger along the arrangement direction of the sub-branches 3211 is not too long. Each first heat exchange branch 321 includes at least two rows of sub-branches 3211 communicated by the communicating pipe 3212, so that the length of the flow path of each first heat exchange branch 321 is longer, the heat exchange area of the first heat exchange branch 321 can be effectively increased, and the heat exchange capacity of the first heat exchange branch 321 is improved.
For example, with continued reference to fig. 9, the first heat exchanging branch 321 includes two rows of sub-branches 3211 and a communicating pipe 3212 arranged side by side. Or, the first heat exchanging branch 321 may also include three rows of sub-branches 3211 and two communicating pipes 3212 arranged side by side, and the two communicating pipes 3212 communicate the three rows of sub-branches 3211 with each other. It is understood that the number of sub-branches included in the first heat exchange branch 321 may be designed according to practical situations, and is only used as an example here.
Further, with continued reference to fig. 9, in some embodiments, the sub-branch 3211 may include a first plurality of heat exchange tubes 32111 and a second plurality of heat exchange tubes 32112. The plurality of first heat exchange tubes 32111 are arranged in parallel at intervals, and the first heat exchange tubes 32111 are arranged in a cross manner with the communication tube 3212. A plurality of second heat exchange pipes 32112 are arranged in parallel at intervals, one second heat exchange pipe 32112 is located between two adjacent first heat exchange pipes 32111 and is communicated with the two adjacent first heat exchange pipes 32111, and the second heat exchange pipes 32112 and the first heat exchange pipes 32111 are arranged in a crossing manner.
In this way, since the first heat exchange pipe 32111 is disposed to intersect the communication pipe 3212, and the second heat exchange pipe 32112 is disposed to intersect the first heat exchange pipe 32111. Therefore, referring to fig. 10, fig. 10 is a schematic connection diagram of a sub-branch of a heat exchanger provided in an embodiment of the present application, and the first heat exchange tube 32111, the second heat exchange tube 32112 and the communication tube 3212 (fig. 9) have a repeatedly bent flow path design, which further increases the length of the first heat exchange branch 321 (fig. 9), thereby increasing the heat exchange area of the first heat exchange branch 321 and improving the heat exchange capacity of the first heat exchange branch 321.
Meanwhile, as the plurality of first heat exchange tubes 32111 are arranged at intervals and in parallel, the contact area between the first heat exchange tubes 32111 and air can be increased, and the heat exchange efficiency of the first heat exchange tubes 32111 is further improved. Because the second heat exchange tubes 32112 are located between two adjacent first heat exchange tubes 32111 and are in communication with the two adjacent first heat exchange tubes 32111, the second heat exchange tubes 32112 can serve as a connecting tube for connecting the two adjacent first heat exchange tubes 32111, which facilitates the connection of the two adjacent first heat exchange tubes 32111, so that the plurality of first heat exchange tubes 32111 can more easily form a complete flow path. The second heat exchange tube 32112 may also increase the length of the sub-branch 3211 to a certain extent, so as to improve the heat exchange effect.
For example, with continued reference to fig. 10, the first heat exchange pipe 32111 may be a straight pipe, the second heat exchange pipe 32112 may be a U-shaped pipe, and the second heat exchange pipe 32112 is connected to ends of two adjacent first heat exchange pipes 32111. It is understood that a communication pipe 3212 (fig. 9) communicating the two sub-branches may be a hose, both ends of which are connected to the end of one first heat exchange pipe 32111 of the two sub-branches, respectively.
It can be understood that a plurality of first heat exchange tubes 32111 in one row of the sub-branches 3211 may be arranged in a staggered manner with a plurality of first heat exchange tubes 32111 in another row of the sub-branches 3211, that is, as shown in fig. 9, the plurality of first heat exchange tubes 32111 in the right side sub-branch 3211 are respectively located at positions corresponding to the intervals between two adjacent first heat exchange tubes 32111 in the left side sub-branch 3211. In this way, the air can reach the first heat exchange tubes 32111 in the other row of the sub-branches 3211 from the space, so that both rows of the sub-branches 3211 can exchange heat with the air sufficiently.
Of course, the first heat exchange tubes 32111 in one row of the sub-branches 3211 may also be disposed opposite to the first heat exchange tubes 32111 in another row of the sub-branches 3211.
With reference to fig. 9, in some embodiments, in the same first heat exchanging branch 321, a refrigerant transmission path formed by two adjacent sub-branches 3211 and the communicating pipe 3212 is U-shaped. That is, in the upper first heat exchange branch 321, two ends of the communicating pipe 3212 are connected to the ends of the two adjacent sub-branches 3211 that are close to each other. Or, in the same first heat exchange branch 321, a refrigerant transmission path formed by two adjacent sub-branches 3211 and the communication pipe 3212 is Z-shaped. That is, in the lower first heat exchange branch 321, two ends of the communicating pipe 3212 are connected to the ends of the two adjacent sub-branches 3211 that are far away from each other.
From this, when the transmission path that two adjacent sub-branches 3211 and communicating pipe 3212 constitute is the U type, communicating pipe 3212 is connected with the one end that is close to each other in two adjacent sub-branches, and it is comparatively convenient to connect, and required communicating pipe 3212's length is shorter, can material saving, and then practice thrift the cost. When transmission path is the Z type, communicating pipe 3212's length is longer, can play certain heat transfer effect, promotes the heat transfer effect.
With reference to fig. 9, in some embodiments, in the same pipe group 323, the refrigerant transmission paths formed by two adjacent sub-branches 3211 and the communicating pipe 3212 in different first heat exchange branches 321 are different in shape. That is, the refrigerant carrying paths of the plurality of first heat exchange branches 321 in the same tube group 323 are different in shape. Therefore, the influence of heat exchange between two adjacent first heat exchange branches 321 in the adjacent pipe group 323 can be further reduced, and the heat exchange efficiency of the first heat exchange branches 321 can be further improved.
Referring to fig. 11, fig. 11 is a partial enlarged view of fig. 4 at F, and in some embodiments, the second heat exchange branch 322 may include a plurality of third heat exchange tubes 3221 and a plurality of fourth heat exchange tubes 3222. Wherein, a plurality of third heat exchanging pipes 3221 are arranged in parallel and spaced. A plurality of fourth heat exchange tubes 3222 are arranged in parallel at intervals, and one fourth heat exchange tube 3222 is located between two adjacent third heat exchange tubes 3221 and is communicated with two adjacent third heat exchange tubes 3211. The fourth heat exchanging pipe 3222 is arranged to cross the third heat exchanging pipe 3221. In this way, the fourth heat exchanging pipe 3222 is arranged to cross the third heat exchanging pipe 3221. Therefore, the design of the flow path with the third heat exchange tube 3221 and the fourth heat exchange tube 3222 being repeatedly bent further increases the length of the second heat exchange branch 322, thereby increasing the heat exchange area of the second heat exchange branch 322, and further improving the heat exchange capability of the second heat exchange branch 322.
Meanwhile, since the plurality of third heat exchange tubes 3221 are arranged in parallel at intervals, the contact area between the third heat exchange tubes 3221 and air can be increased, and the heat exchange efficiency of the third heat exchange tubes 3221 is further improved. Since the fourth heat exchange tubes 3222 are located between two adjacent third heat exchange tubes 3221 and are communicated with the two adjacent third heat exchange tubes 3221, the fourth heat exchange tubes 3222 can serve as a connecting tube for connecting the two adjacent third heat exchange tubes 3221, which is convenient for connecting the two adjacent third heat exchange tubes 3221, so that the plurality of third heat exchange tubes 3221 can more easily form a complete flow path.
It is understood that the third heat exchanging pipe 3221 may also be a straight pipe, and the fourth heat exchanging pipe 3222 may also be a U-shaped pipe, and is connected to the end portions of two adjacent third heat exchanging pipes 3221.
With continued reference to fig. 11, in some embodiments, the heat exchanger 3 may further comprise at least one pressure reducing tube 34, each pressure reducing tube 34 having one end in communication with the second end of one of the second heat exchanging branches 322 and another end in communication with one of the tap openings 333 of the tap member 33.
Therefore, the decompression tube 34 is arranged between the flow dividing part 33 and the second end of the second heat exchange branch 322, when the heat exchanger 3 is used as a condenser, the decompression tube 34 can reduce the pressure of the refrigerant discharged from the second end of the second heat exchange branch 322, and the high-pressure refrigerant is prevented from directly impacting the flow dividing part, so that the connection between the second heat exchange branch 322 and the flow dividing port 333 is damaged. When the heat exchanger 3 is used as an evaporator, the decompression pipe 34 can further throttle and decompress the refrigerant flowing into the heat exchanger main body 32, and thus can improve the evaporation efficiency when the heat exchanger 3 is used as an evaporator.
The above description is only for the specific embodiments of the present application, but the scope of the present application is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present application should be covered within the scope of the present application. Therefore, the protection scope of the present application shall be subject to the protection scope of the claims.
Claims (10)
1. A heat exchanger, comprising:
the gas collecting pipe is internally provided with a gas collecting cavity; the gas collecting pipe is provided with a first vent and a plurality of second vents which are communicated with the gas collecting cavity;
the heat exchanger comprises a heat exchanger body, a heat exchanger body and a heat exchanger, wherein the heat exchanger body comprises a plurality of first heat exchange branches and at least one second heat exchange branch; the first end of each first heat exchange branch is communicated with one second vent; the first end of each second heat exchange branch is communicated with the second ends of at least two first heat exchange branches; and the number of the first and second groups,
the inner part of the flow dividing piece is provided with a flow dividing cavity; the flow dividing piece is provided with a confluence port communicated with the flow dividing cavity and at least one flow dividing port; each branch flow port is communicated with the second end of one second heat exchange branch.
2. The heat exchanger of claim 1,
at least two adjacent first heat exchange branches form a pipeline group; the heat exchanger comprises at least one group of the pipeline groups; the second ends of at least two first heat exchange branches in one group of the pipeline groups are communicated with the first end of one second heat exchange branch;
the at least one second heat exchange branch is positioned at one side of the at least one group of pipeline groups.
3. The heat exchanger of claim 2,
the first heat exchange branch comprises:
at least two rows of sub-branches arranged side by side; and the number of the first and second groups,
and the at least one communicating pipe is positioned between the two adjacent rows of the sub-branches and is communicated with the two adjacent rows of the sub-branches.
4. The heat exchanger of claim 3,
the sub-branch includes:
the first heat exchange tubes are arranged at intervals and in parallel; the first heat exchange tube and the communicating tube are arranged in a crossed manner;
the plurality of second heat exchange tubes are arranged at intervals and in parallel; one second heat exchange tube is positioned between two adjacent first heat exchange tubes and communicated with the two adjacent first heat exchange tubes; the second heat exchange tube and the first heat exchange tube are arranged in a crossed mode.
5. The heat exchanger of claim 3,
in the same first heat exchange branch, a refrigerant transmission path formed by two adjacent sub-branches and the communicating pipe is U-shaped;
or, in the same first heat exchange branch, a refrigerant transmission path formed by two adjacent sub-branches and the communicating pipe is in a Z shape.
6. The heat exchanger of claim 5,
in the same pipeline group, in different first heat exchange branches, the refrigerant transmission paths formed by two adjacent sub-branches and the communicating pipe are different in shape.
7. The heat exchanger according to any one of claims 1 to 6,
the second heat exchange branch comprises:
the plurality of third heat exchange tubes are arranged at intervals and in parallel;
the plurality of fourth heat exchange tubes are arranged at intervals and in parallel; one fourth heat exchange tube is positioned between two adjacent third heat exchange tubes and is communicated with the two adjacent third heat exchange tubes; the fourth heat exchange tube and the third heat exchange tube are arranged in a crossed mode.
8. The heat exchanger of claim 1, further comprising:
and one end of each pressure reducing pipe is communicated with the second end of one second heat exchange branch, and the other end of each pressure reducing pipe is communicated with one shunt port of the shunt piece.
9. An air conditioner, comprising:
a four-way valve having a first port, a second port, a third port, and a fourth port;
a compressor having a gas inlet and a gas outlet; the air inlet is communicated with the first valve port, and the air outlet is communicated with the second valve port;
one end of the outdoor heat exchanger is communicated with the third valve port; and the number of the first and second groups,
one end of the indoor heat exchanger is communicated with the fourth valve port, and the other end of the indoor heat exchanger is communicated with the other end of the outdoor heat exchanger;
wherein at least one of the indoor heat exchanger and the outdoor heat exchanger is the heat exchanger of any one of claims 1 to 8.
10. The air conditioner according to claim 9, wherein the outdoor heat exchanger is the heat exchanger; the first air vent of the gas collecting pipe is communicated with the third air vent; the confluence port of the flow dividing piece is communicated with the indoor heat exchanger; and/or the presence of a gas in the gas,
the indoor heat exchanger is the heat exchanger; the first air vent of the gas collecting pipe is communicated with the fourth valve port; and the confluence port of the flow dividing piece is communicated with the outdoor heat exchanger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210465056.9A CN114812014A (en) | 2022-04-29 | 2022-04-29 | Heat exchanger and air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202210465056.9A CN114812014A (en) | 2022-04-29 | 2022-04-29 | Heat exchanger and air conditioner |
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| CN114812014A true CN114812014A (en) | 2022-07-29 |
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| CN202210465056.9A Withdrawn CN114812014A (en) | 2022-04-29 | 2022-04-29 | Heat exchanger and air conditioner |
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| EP0723121A2 (en) * | 1995-01-20 | 1996-07-24 | MKS S.r.l. | A heat exchanger particularly for air-conditioning a cabinet for containing electrical apparatus |
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Application publication date: 20220729 |