US20220333833A1 - Multi-channel heat exchanger and air conditioning refrigeration system - Google Patents
Multi-channel heat exchanger and air conditioning refrigeration system Download PDFInfo
- Publication number
- US20220333833A1 US20220333833A1 US17/764,816 US202017764816A US2022333833A1 US 20220333833 A1 US20220333833 A1 US 20220333833A1 US 202017764816 A US202017764816 A US 202017764816A US 2022333833 A1 US2022333833 A1 US 2022333833A1
- Authority
- US
- United States
- Prior art keywords
- heat exchange
- exchange tube
- tube portion
- fins
- flow
- 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.)
- Pending
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
-
- 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
- F28D1/053—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 the conduits being straight
- F28D1/0535—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 the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
-
- 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
-
- 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
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
- F28F1/128—Fins with openings, e.g. louvered fins
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2210/00—Heat exchange conduits
- F28F2210/10—Particular layout, e.g. for uniform temperature distribution
Definitions
- the present disclosure relates to a field of heat exchange equipment, and more particularly, to a multi-channel heat exchanger and an air conditioning refrigeration system having the same.
- a multi-channel heat exchanger As an alternative technology of a copper tube fin heat exchanger, a multi-channel heat exchanger has attracted more and more attention in the field of an air conditioning technology, and has developed rapidly in recent years.
- the refrigerant evaporates or condenses at different positions in channels arranged side by side are, thus resulting in a mismatch between a flow distribution of the refrigerant in the channels and a heat-exchange temperature difference.
- An obvious temperature difference occurs between a windward side and a leeward side on a section of the heat exchange tube, and an obvious overcooling or overheating temperature gradient is formed on a section of the heat exchange tube adjacent to an outlet of the heat exchanger. A temperature difference on the windward side cannot be better utilized.
- a multi-channel heat exchanger includes a plurality of heat exchange tubes spaced apart along a thickness direction of the heat exchange tube.
- the heat exchange tube has a first longitudinal side face and a second longitudinal side face opposite to and parallel to each other along the thickness direction of the heat exchange tube, and a third longitudinal side face and a fourth longitudinal side face opposite to each other along a width direction of the heat exchange tube.
- a distance between the first longitudinal side face and the second longitudinal side face is less than a distance between the third longitudinal side face and the fourth longitudinal side face.
- the heat exchange tube is divided into four portions with an equal width along the width direction of the heat exchange tube, and the four portions includes a first heat exchange tube portion, a second heat exchange tube portion, a third heat exchange tube portion and a fourth heat exchange tube portion distributed along a direction from an inlet side of an airflow to an outlet side of the airflow.
- Each heat exchange tube portion includes at least two flow channels, and the flow channel extends in a length direction of the heat exchange tube.
- the respective flow channels of the four portions are spaced apart along the width direction of the heat exchange tube.
- the heat exchange tube has a cross section defined in the thickness direction of the heat exchange tube and the width direction of the heat exchange tube, and the cross section includes a flow section.
- a total area of a flow section of the first heat exchange tube portion is A1, a total area of a flow section of the second heat exchange tube portion being A2, a total area of a flow section of the third heat exchange tube portion being A3, a total area of a flow section of the fourth heat exchange tube portion is A4.
- the total area A1 of the flow section of the first heat exchange tube portion is 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion.
- An air conditioning refrigeration system includes a multi-channel heat exchanger, a second heat exchanger, a compressor and a throttle valve.
- One of a first header of the multi-channel heat exchanger and a first end of the second heat exchanger is connected to an inlet end of the compressor, and the other one of the first header of the multi-channel heat exchanger and the first end of the second heat exchanger is connected to an outlet end of the compressor.
- the throttle valve is connected between a second header of the multi-channel heat exchanger and a second end of the second heat exchanger.
- the multi-channel heat exchanger includes a plurality of heat exchange tubes spaced apart along a thickness direction of the heat exchange tube.
- the heat exchange tube has a first longitudinal side face and a second longitudinal side face opposite to and parallel to each other along the thickness direction of the heat exchange tube, and a third longitudinal side face and a fourth longitudinal side face opposite to each other along a width direction of the heat exchange tube.
- a distance between the first longitudinal side face and the second longitudinal side face is less than a distance between the third longitudinal side face and the fourth longitudinal side face.
- the heat exchange tube is divided into four portions with an equal width along the width direction of the heat exchange tube, and the four portions includes a first heat exchange tube portion, a second heat exchange tube portion, a third heat exchange tube portion and a fourth heat exchange tube portion distributed along a direction from an inlet side of an airflow to an outlet side of the airflow.
- Each heat exchange tube portion includes at least two flow channels, and the flow channel extends in a length direction of the heat exchange tube.
- the respective flow channels of the four portions are spaced apart along the width direction of the heat exchange tube.
- the heat exchange tube has a cross section defined in the thickness direction of the heat exchange tube and the width direction of the heat exchange tube, and the cross section includes a flow section.
- a total area of a flow section of the first heat exchange tube portion is A1
- a total area of a flow section of the second heat exchange tube portion being A2
- a total area of a flow section of the third heat exchange tube portion being A3
- a total area of a flow section of the fourth heat exchange tube portion is A4.
- the total area A1 of the flow section of the first heat exchange tube portion is 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion.
- FIG. 1 is a schematic view of a multi-channel heat exchanger according to an embodiment of the present disclosure
- FIG. 2 is a schematic side view of a multi-channel heat exchanger according to an embodiment of the present disclosure (an arrow direction is an air flow direction);
- FIG. 3 is a schematic view of a fin of a multi-channel heat exchanger according to an embodiment of the present disclosure from a perspective;
- FIG. 4 is a schematic view of a fin of a multi-channel heat exchanger according to an embodiment of the present disclosure from another perspective;
- FIG. 5 is a schematic view of a fin of a multi-channel heat exchanger according to an embodiment of the present disclosure
- FIG. 6 is a schematic view of a fin of a multi-channel heat exchanger according to an embodiment of the present disclosure
- FIG. 7 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure
- FIG. 8 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure
- FIG. 9 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure.
- FIG. 10 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure
- FIG. 11 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure
- FIG. 12 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure.
- a multi-channel heat exchanger 100 according to embodiments of the present disclosure will be described below with reference to FIGS. 1 to 12 .
- the multi-channel heat exchanger 100 includes a first header 10 , a second header 20 and a plurality of heat exchange tubes 30 .
- an axial direction of the first header 10 may be parallel to an axial direction of the second header 20
- the first header 10 and the second header 20 may be arranged in parallel to each other and spaced apart from each other, and the first header 10 and the second header 20 are distributed along a length direction of the heat exchange tube 30 .
- the first header 10 may be configured as an inlet header
- the second header 20 may be configured as an outlet header.
- the first header 10 may be configured as an outlet header
- the second header 20 may be configured as an inlet header.
- the plurality of heat exchange tubes 30 are spaced apart along a thickness direction of the heat exchange tube 30 , the thickness direction of the heat exchange tube 30 may be parallel to the axial direction of the first header 10 and the axial direction of the second header 20 , and the plurality of heat exchange tubes 30 may be spaced apart along the axial direction of the first header 10 and the axial direction of the second header 20 . As shown in FIG. 1 , the plurality of heat exchange tubes 30 are spaced apart along a thickness direction of the heat exchange tube 30 , the thickness direction of the heat exchange tube 30 may be parallel to the axial direction of the first header 10 and the axial direction of the second header 20 , and the plurality of heat exchange tubes 30 may be spaced apart along the axial direction of the first header 10 and the axial direction of the second header 20 . As shown in FIG.
- a first end of the heat exchange tube 30 is connected to the first header 10
- a second end of the heat exchange tube 30 is connected to the second header 20 , so as to communicate the first header 10 with the second header 20 , so that a heat exchange medium may flow in an order of the first header 10 , the heat exchange tube 30 and the second header 20 or in an order of the second header 20 , the heat exchange tube 30 and the first header 10 .
- the first header 10 may be provided with a first port
- the second header 20 may be provided with a second port.
- the first port and the second port are configured to be connected to an external pipeline, so as to connect the heat exchanger in a whole air conditioning system or other heat exchange systems.
- the heat exchange tube 30 has a first longitudinal side face 30 a , a second longitudinal side face 30 b , a third longitudinal side face 30 c and a fourth longitudinal side face 30 d.
- the first longitudinal side face 30 a and the second longitudinal side face 30 b are opposite to and parallel to each other along the thickness direction of the heat exchange tube 30
- the third longitudinal side face 30 c and the fourth longitudinal side face 30 d are opposite to each other along a width direction of the heat exchange tube 30
- a distance between the first longitudinal side face 30 a and the second longitudinal side face 30 b is less than a distance between the third longitudinal side face 30 c and the fourth longitudinal side face 30 d , i.e., a thickness of the heat exchange tube 30 is less than a width of the heat exchange tube 30 .
- an air flows through a gap between two heat exchange tubes 30 , i.e., the air passes by the first longitudinal side face 30 a and the second longitudinal side face 30 b .
- the first longitudinal side face 30 a and the second longitudinal side face 30 b are arranged in parallel, i.e., the thickness of the heat exchange tube 30 is constant along an air input direction. Therefore, the heat exchange tube 30 itself has little effect on the fluidity of the air.
- the heat exchange tube 30 is divided into four portions with an equal width along the width direction of the heat exchange tube 30 .
- the four portions include a first heat exchange tube portion, a second heat exchange tube portion, a third heat exchange tube portion and a fourth heat exchange tube portion distributed along a direction from an inlet side of an airflow to an outlet side of the airflow.
- Each heat exchange tube portion includes at least two flow channels 30 e , and the flow channel 30 e extends in the length direction of the heat exchange tube.
- the respective flow channels 30 e in the four heat exchange tube portions are spaced apart along the width direction of the heat exchange tube 30 .
- the heat exchange tube 30 has a cross section defined in the thickness direction of the heat exchange tube 30 and the width direction of the heat exchange tube 30 , and the cross section includes a flow section.
- a total area of a flow section of the first heat exchange tube portion is A1 and a total area of a flow section of the fourth heat exchange tube portion is A4.
- the total area A1 of the flow section of the first heat exchange tube portion is 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion.
- a total area of a flow section of the second heat exchange tube portion is A2 and a total area of a flow section of the third heat exchange tube portion is A3.
- the heat exchange tube 30 of the present disclosure includes four portions divided equally along its width direction, and the distribution of the flow channels 30 e has no direct corresponding relationship with the division of the heat exchange tube. Therefore, at least part of the flow channel 30 e may be divided into a former heat exchange tube portion and a rest portion of the flow channel 30 e may be divided into a latter heat exchange tube portion in a specific division process. Therefore, the flow section of the heat exchange tube portion referred to in the present disclosure includes a cross section of the complete flow channel and a cross section of the incomplete flow channel located in the heat exchange tube portion.
- the multi-channel heat exchanger 100 Since the multi-channel heat exchanger 100 has a temperature difference on a windward side and a leeward side, when the total area A1 of the flow section of the first heat exchange tube portion is less than 1.05 times of the total area A4 of the flow section of the fourth heat exchange tube portion, the difference between the refrigerant in the flow channels of the first heat exchange tube portion and the refrigerant in the flow channels of the fourth heat exchange tube portion is small if the multi-channel heat exchanger 100 is used as an evaporator, which will result in that the refrigerant in the flow channels of the fourth heat exchange tube portion cannot have a sufficient heat exchange. For example, the liquid refrigerant in the flow channels at an outlet of the multi-channel heat exchanger 100 cannot be evaporated.
- the difference between the refrigerant in the flow channels of the first heat exchange tube portion and the refrigerant in the flow channels of the fourth heat exchange tube portion is large if the multi-channel heat exchanger 100 is used as the evaporator, which will result in that the refrigerant in the flow channels of the first heat exchange tube portion is evaporated too fully, thus causing a waste of space, and which will also have an impact on the structural safety of the multi-channel heat exchanger 100 , thus causing a decrease of burst pressure.
- the design of the flow channels can meet the safety of the multi-channel heat exchanger 100 so as not to cause a waste of excess space, and also can make full use of the temperature difference between the windward side and the leeward side of the multi-channel heat exchanger 100 , so as to allow the refrigerant in different flow channels to fully exchange heat, thus effectively reducing a temperature gradient on the cross section of the heat exchange tube of the multi-channel heat exchanger 100 , balancing the temperature difference between the refrigerant in the heat exchange tube on the windward side and the refrigerant in the heat exchange tube on the leeward side, achieving the optimal balanced state of outlet overheating, and hence improving the heat exchange performance of the multi-channel heat exchanger 100 .
- the total area A2 of the flow section of the second heat exchange tube portion may be 1.3 times of the total area A3 of the flow section of the third heat exchange tube portion, and the total area A3 of the flow section of the third heat exchange tube portion may be 1.2 times of the total area A4 of the flow section of the fourth heat exchange tube portion, i.e., flow sectional areas of the flow channels 30 e of the four heat exchange tube portions gradually decrease from the air inlet side to the air outlet side.
- the number of groups of the flow channels 30 e is not limited to four, but can also be more, such as six, seven or eight. Distances from any one of the flow channels 30 e in the four heat exchange tube portions to two flow channels 30 e adjacent to this flow channel 30 e can be set to be equal, so that each group of flow channels 30 e are evenly arranged.
- distances from at least one of the flow channels 30 e in the four heat exchange tube portions to two flow channels 30 e adjacent to the at least one flow channel 30 e may be different.
- a temperature difference between the airflow on a windward side of the multi-channel heat exchanger 100 and the heat exchange medium is large, and a temperature difference between the airflow on a leeward side of the multi-channel heat exchanger 100 and the heat exchange medium is small.
- a heat exchange demand of the airflow on the leeward side of the multi-channel heat exchanger 100 is less than a heat exchange demand of the airflow on the windward side of the multi-channel heat exchanger 100 .
- the windward side of the multi-channel heat exchanger 100 corresponds to the inlet side of the airflow and the leeward side of the multi-channel heat exchanger 100 corresponds to the outlet side of the airflow.
- the flow sectional areas of the plurality of flow channels 30 e of the multi-channel heat exchanger 100 from the windward side to the leeward side are the same. Due to the heat transfer between the airflow and the heat exchange medium, the temperatures of the heat exchange media in the respective flow channels 30 e arranged side by side along a wind direction (a transverse direction or the width direction of the heat exchange tube 30 ) are different. Therefore, the heat exchange medium in the flow channel adjacent to the windward side may have been evaporated or condensed, while the heat exchange medium in a latter flow channel (for example, the flow channel adjacent to the leeward side) along the transverse direction may have not been evaporated or condensed.
- a distance between any two adjacent flow channels 30 e in the first heat exchange tube portion is B1
- a distance between any two adjacent flow channels 30 e in the second heat exchange tube portion is B2.
- B1 is greater than or equal to B2, i.e., in multiple groups of flow channels 30 e , the distance between the flow channels in the respective groups of flow channels 30 e gradually decreases from the inlet side of the airflow to the outlet side of the airflow.
- a sum of the flow sectional areas of the flow channels 30 e completely located in the first heat exchange tube portion is C1
- a sum of the flow sectional areas of the flow channels 30 e completely located in the second heat exchange tube portion is C2.
- C2 is greater than or equal to C1.
- the heat exchange tube 30 of the present disclosure includes four portions divided equally along its width direction, and the distribution of the flow channels 30 e has no direct corresponding relationship with the division of the heat exchange tube. Therefore, at least part of the flow channel 30 e may be divided into a former heat exchange tube portion and a rest portion of the flow channel 30 e may be divided into a latter heat exchange tube portion in a specific division process.
- a sum of the flow sectional areas of the respective flow channels of the first heat exchange tube portion is greater than or equal to a sum of the flow sectional areas of the respective flow channels of the second heat exchange tube portion.
- the flow sectional areas of the corresponding flow channels 30 e in the plurality of heat exchange tube portions are configured to decrease sequentially from the air inlet side to the air outlet side, so that flow quantities of the heat exchange media in the plurality of heat exchange tube portions may be decreased sequentially from the air inlet side to the air outlet side, i.e., the heat exchange effect of the multi-channel heat exchanger 100 decreases gradually from the air inlet side to the air outlet side.
- the heat exchange amount on the windward side of the multi-channel heat exchanger 100 and the heat exchange amount on the leeward side of the multi-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, respectively, so that the heat exchange effects on two sides of the multi-channel heat exchanger 100 can better meet the actual requirements, a temperature difference between the windward side and the leeward side of the multi-channel heat exchanger 100 is balanced, and a situation in which one side of the multi-channel heat exchanger 100 is overcooled and the other side of the multi-channel heat exchanger 100 is overheated is prevented, thus ensuring the reasonable and safe use of the multi-channel heat exchanger 100 , and improving the heat exchange performance of the multi-channel heat exchanger 100 .
- the flow sectional areas of the flow channels in the four heat exchange tube portions are configured to decrease sequentially from the air inlet side to the air outlet side, so that the heat exchange amount on the windward side of the multi-channel heat exchanger 100 and the heat exchange amount on the leeward side of the multi-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, respectively, so as to effectively balance the temperature difference between the refrigerant in the heat exchange tube 30 on the windward side and the refrigerant in the heat exchange tube 30 on the leeward side, and to optimize the degree of outlet overcooling or overheating, thus improving the heat exchange performance of the multi-channel heat exchanger 100 .
- the multi-channel heat exchanger 100 further includes a fin 40 .
- the fin 40 is arranged between two heat exchange tubes 30 along the thickness direction of the heat exchange tube 30 , and the fin 40 is connected to the two heat exchange tubes 30 , respectively.
- the fin includes first to nth groups of fins 40 .
- each group includes at least one fin 40 .
- the first to nth groups of fins 40 are all mounted between the first longitudinal side face 30 a of one heat exchange tube 30 and the second longitudinal side face 30 b of an adjacent heat exchange tube 30 , and the first to nth groups of fins 40 are arranged sequentially along the width direction of the heat exchange tube 30 .
- the first group of fins 40 , . . . , the nth group of fins 40 are distributed along the direction from the air inlet side to the air outlet side, in which 1 ⁇ n, and n is an integer.
- the heat exchange tube 30 is provided with the plurality of flow channels 30 e in the width direction, so that the plurality of flow channels 30 e may correspond to the n groups of fins 40 . Therefore, the heat of the heat exchange medium in the multi-channel heat exchanger 100 may be diffused to the fin 40 , so as to exchange heat with the airflow. Moreover, the fin 40 has a large surface area, so that the airflow can fully exchange heat with the fin 40 . Thus, the heat dissipation effect of each portion of the multi-channel heat exchanger 100 can be maintained at a high level.
- An air-side heat transfer coefficient of the nth group of fins 40 is less than an air-side heat transfer coefficient of the first group of fins 40 .
- the air-side heat transfer coefficients of the n groups of fins 40 decrease sequentially from the first group of fins to the nth group of fins, and the heat transfer coefficient of the fin 40 adjacent to the air inlet side is greater than the heat transfer coefficient of the fin 40 adjacent to the air outlet side, so that the plurality of groups of fins 40 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, so as to effectively balance the temperature difference between the refrigerant in the heat exchange tube 30 on the windward side and the refrigerant in the heat exchange tube 30 on the leeward side, and to optimize the degree of outlet overcooling or overheating, thus improving the heat exchange performance of the multi-channel heat exchanger 100 .
- the first to nth groups of fins 40 each include a plurality of louvers 40 a arranged along the width direction of the heat exchange tube 30 .
- the number of the louvers 40 a of the first group of fins 40 is Q 1 , . . .
- the number of the louvers 40 a of a kth group of fins 40 is Q k , . . .
- the number of the louvers 40 a of the nth group of fins 40 is Q n , in which Q 1 is greater than Q n , and when n is greater than 1, Q k ⁇ 1 is greater than Q k .
- the number of the louvers 40 a decreases sequentially from the first group to the nth group, and the more the number of the louvers 40 a , the better the heat exchange effect, so that the heat exchange effect of the multi-channel heat exchanger 100 on the air inlet side is greater than the heat exchange effect of the multi-channel heat exchanger 100 on the air outlet side.
- the heat exchange effect of the multi-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, thus optimizing the degree of outlet overcooling or overheating, avoiding the situation of overheating at one side and overcooling at the other side, and improving the rationality of the structural design of the multi-channel heat exchanger 100 .
- the multi-channel heat exchanger 100 has at least one of the following features.
- an opening width of the louver 40 a in the first group of fins 40 is W 1 , . . .
- an opening width of the louver 40 a in the kth group of fins 40 is W k , . . .
- an opening width of the louver 40 a in the nth group of fins 40 is W n , in which W 1 is greater than W n , and when n is greater than 1, W k ⁇ 1 is greater than W k .
- the opening width of the louver 40 a decreases sequentially from the first group to the nth group, and the larger the opening width of the louver 40 a , the better the heat exchange effect, so that the heat exchange effect of the multi-channel heat exchanger 100 on the air inlet side is greater than the heat exchange effect of the multi-channel heat exchanger 100 on the air outlet side. Therefore, the heat exchange effect of the multi-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, and the heat exchange performance of the multi-channel heat exchanger 100 is improved.
- an opening angle of the louver 40 a in the first group of fins 40 is R 1 , . . .
- an opening angle of the louver 40 a in the kth group of fins 40 is R k , . . .
- an opening angle of the louver 40 a in the nth group of fins 40 is R n , in which R 1 is greater than R n , and when n is greater than 1, R k ⁇ 1 is greater than R k .
- the opening angle of the louver 40 a decreases sequentially from the first group to the nth group, and the larger the opening angle of the louver 40 a , the better the heat exchange effect, so that the heat exchange effect of the multi-channel heat exchanger 100 on the air inlet side is greater than the heat exchange effect of the multi-channel heat exchanger 100 on the air outlet side. Therefore, the heat exchange effect of the multi-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, and the heat exchange performance of the multi-channel heat exchanger 100 is improved.
- an opening length of the louver 40 a in the first group of fins 40 is L 1 , . . .
- an opening length of the louver 40 a in the kth group of fins 40 is L k , . . .
- an opening length of the louver 40 a in the nth group of fins 40 is L n , in which L 1 is greater than L n , and when n is greater than 1, L k ⁇ 1 is greater than L k .
- the opening length of the louver 40 a decreases sequentially from the first group to the nth group, and the larger the opening length of the louver 40 a , the better the heat exchange effect, so that the heat exchange effect of the multi-channel heat exchanger 100 on the air inlet side is greater than the heat exchange effect of the multi-channel heat exchanger 100 on the air outlet side. Therefore, the heat exchange effect of the multi-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, and the heat exchange performance of the multi-channel heat exchanger 100 is improved.
- the air-side heat transfer coefficient or the heat dissipation performance of a former group of fins 40 is better than the air-side heat transfer coefficient of a latter group of fins 40 .
- the heat exchange between the fin 40 on the windward side and the air can be further increased, and the heat exchange from the refrigerant to the air is increased, so that the heat exchange medium on the leeward side can also have an effective heat exchange when exchanging heat on the leeward side, so as to balance the heat exchange effects on the two sides of the multi-channel heat exchanger 100 .
- a spacing between two adjacent fins 40 in the first group of fins 40 along the length direction of the heat exchange tube 30 is F p l , . . .
- a spacing between two adjacent fins 40 in the kth group of fins 40 along the length direction of the heat exchange tube 30 is F p k , . . .
- a spacing between two adjacent fins 40 in the nth group of fins 40 along the length direction of the heat exchange tube 30 is F p n , in which F p l , is less than F p n , and when n is greater than 1 , F p k k ⁇ 1 , is less than F p k .
- the spacing between the two adjacent fins 40 in the former group of fins 40 is less than the spacing between the two adjacent fins 40 in the latter group of fins 40 . Therefore, the air-side heat transfer coefficient or the heat dissipation performance of the former group of fins 40 is better than the air-side heat transfer coefficient of the latter group of fins 40 .
- the heat exchange between the fin 40 on the windward side and the air can be further increased, and the heat exchange from the refrigerant to the air is increased, so that the heat exchange medium on the leeward side can also have an effective heat exchange when exchanging heat on the leeward side, so as to balance the heat exchange effects on the two sides of the multi-channel heat exchanger 100 .
- relevant parameters of the flow sectional area of the flow channel 30 e in the heat exchange tube 30 and the fin 40 are designed cooperatively, so that a temperature gradient on the cross section of the heat exchange tube 30 of the multi-channel heat exchanger 100 can be effectively reduced, the temperature difference between the heat exchange medium on the windward side and the heat exchange medium on the leeward side can be balanced, and the degree of outlet overcooling or overheating can be optimized, thus improving the heat exchange performance of the multi-channel heat exchanger 100 .
- a boss may be arranged on the fin 40 , and a ratio of the number of the bosses of the fin 40 on the windward side to the number of the bosses of the fin 40 on the leeward side may be increased. Alternatively, a ratio of a contact area of the boss of the fin 40 on the windward side to a contact area of the boss of the fin 40 on the leeward side may be increased. Alternatively, a flanging height of a portion of the fin 40 on the windward side may be reduced and the number of openings on the fin 40 may be increased from the windward side to the leeward side.
- a distribution density of the fins 40 may be adjusted, for example, the density of the fins 40 on the windward side is greater than the density of the fins 40 on the leeward side, so as to balance the heat exchange effects on the two sides of the multi-channel heat exchanger 100 .
- each heat exchange tube portion includes a plurality of flow channels 30 e , and the flow sectional area of each flow channel 30 e in the same heat exchange tube portion is the same, so that the plurality of flow channels 30 e in each heat exchange tube portion may allow the heat exchange medium to flow, thus increasing the overall heat exchange efficiency of the multi-channel heat exchanger 100 .
- the multi-channel heat exchanger 100 has at least one of the following features.
- each flow channel 30 e in the same heat exchange tube portion is the same, so as to facilitate the extrusion of the heat exchange tube 30 .
- each heat exchange tube portion includes a plurality of flow channels 30 e , and the number of the flow channels 30 e in each heat exchange tube portion is the same, so as to make the overall structure of the multi-channel heat exchanger 100 more regular.
- any two flow channels 30 e along the width direction of the heat exchange tube 30 are the same, and sizes of the flow channels 30 e in different heat exchange tube portions along the thickness direction of the heat exchange tube 30 are different.
- the flow sectional areas of the flow channels 30 e in the plurality of heat exchange tube portions still decrease sequentially from the windward side to the leeward side.
- any two flow channels 30 e along the thickness direction of the heat exchange tube 30 are the same, and sizes of the flow channels 30 e in different heat exchange tube portions along the width direction of the heat exchange tube 30 are different.
- the flow sectional areas of the groups of flow channels 30 e still decrease sequentially from the windward side to the leeward side.
- each flow channel 30 e An outer profile of each flow channel 30 e is the same.
- the outer profile of each flow channel 30 e may be one of a rectangle, a circle, a hexagon and a triangle.
- at least part of the flow channels 30 e are provided with an inner rib 38 , and the inner rib is mainly arranged in the flow channel 30 e adjacent to the leeward side, so as to reduce the flow sectional area of the flow channel 30 e on the leeward side.
- At least one of the flow channels 30 e in the second heat exchange tube portion has a flow sectional area greater than or equal to any one of the flow channels 30 e in the third heat exchange tube portion. At least two of the flow channels 30 e in the first heat exchange tube portion, the flow channels 30 e in the second heat exchange tube portion and the flow channels 30 e in the third heat exchange tube portion have the same flow sectional area. Moreover, the number of the flow channels 30 e in the first heat exchange tube portion, the number of the flow channels 30 e in the second heat exchange tube portion and the number of the flow channels 30 e in the third heat exchange tube portion are configured to be the same, or are configured to decrease sequentially.
- an outer shape of the cross section of the heat exchange tube 30 is circular, a plurality of inner ribs 38 are arranged in the heat exchange tube 30 , and the number of the inner ribs 38 on the windward side is less than the number of the inner ribs 38 on the leeward side, so as to increase a flow resistance of the heat exchange medium on the leeward side and reduce a flow resistance of the heat exchange medium on the windward side.
- the plurality of inner ribs 38 extend radially outwards from a center of the heat exchange tube 30 , and divide the cross section of the heat exchange tube 30 into a plurality of flow channels 30 e .
- the number of the flow channels 30 e on the windward side is also less than the number of the flow channels 30 e on the leeward side.
- the inner rib 38 is arranged in a portion of the heat exchange tube 30 adjacent to the leeward side, and no inner rib 38 is arranged in a portion of the heat exchange tube 30 adjacent to the windward side.
- both the portions of the heat exchange tube 30 adjacent to the windward side and adjacent to the leeward side are provided with the inner rib 38 , while more inner ribs 38 are arranged in the portion of the heat exchange tube 30 adjacent to the leeward side than in the portion of the heat exchange tube 30 adjacent to the windward side.
- the heat exchange tube 30 sequentially includes a flow channel 31 in a first heat exchange tube portion, a flow channel 32 in a second heat exchange tube portion, a flow channel 33 in a third heat exchange tube portion, a flow channel 34 in a fourth heat exchange tube portion, a flow channel 35 in a fifth heat exchange tube portion, a flow channel 36 in a sixth heat exchange tube portion, and a flow channel 37 in a seventh heat exchange tube portion, and the inner rib 38 is arranged in the flow channels 30 e in multiple heat exchange tube portions adjacent to the leeward side.
- the outer shape of the cross section of the heat exchange tube 30 is configured to be oval or polygonal. As shown in FIGS. 7 to 12 , the outer shape of the heat exchange tube 30 is oval, and the number of the flow channels 30 e or the area of the flow channel 30 e on the windward side is larger than the number of the flow channels 30 e or the area of the flow channel 30 e on the leeward side.
- the heat exchange tube 30 adopts a wire tube, and along a direction from the windward side to the leeward side, the number of the wire tubes on the windward side is larger than the number of the wire tubes on the leeward side, or an inner section of the wire tube on the windward side is greater than an inner section of the wire tube on the leeward side.
- the heat exchange amount on the windward side of the multi-channel heat exchanger 100 and the heat exchange amount on the leeward side of the multi-channel heat exchanger 100 can match with the actual heat exchange requirements, so as to effectively reduce the temperature gradient on the cross section of the heat exchange tube 30 of the multi-channel heat exchanger 100 , balance the temperature difference between the heat exchange medium on the windward side and the heat exchange medium on the leeward side, and optimize the degree of outlet overcooling or overheating, thus improving the heat exchange performance of the multi-channel heat exchanger 100 .
- the present disclosure further provides an air conditioning refrigeration system.
- the air conditioning refrigeration system includes a multi-channel heat exchanger 100 according to any one of the above embodiments, a second heat exchanger, a compressor and a throttle valve.
- a first header 10 of the multi-channel heat exchanger 100 and a first end of the second heat exchanger is connected to an inlet end of the compressor
- the other one of the first header 10 of the multi-channel heat exchanger 100 and the first end of the second heat exchanger is connected to an outlet end of the compressor
- the throttle valve is connected between a second header 20 of the multi-channel heat exchanger 100 and a second end of the second heat exchanger.
- the above multi-channel heat exchanger 100 is arranged in the air conditioning refrigeration system, so that the heat exchange medium in each heat exchange tube of the air conditioning refrigeration system can effectively exchange heat with the airflow, a local heat exchange will not have a lack or an excess, the rationality of the structural design of the air conditioning refrigeration system is improved and the practicability of the air conditioning refrigeration system is improved.
Abstract
A multi-channel heat exchanger includes a plurality of heat exchange tubes, each heat exchange tube includes first to fourth heat exchange tube portions which are distributed along a direction from an airflow inlet side to an airflow outlet side. Each heat exchange tube portion includes at least two flow channels. The heat exchange tube has a cross section defined in a thickness direction and a width direction of the heat exchange tubes, and the cross section includes a flow section. A total area of a flow section of the first heat exchange tube portion is A1, a total area of a flow section of the fourth heat exchange tube portion is A4, and the total area A1 of the flow section of the first heat exchange tube portion is 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion.
Description
- The present application is a national phase entry under 35 USC § 371 of International Application No. PCT/CN2020/115229, filed on Sep. 15, 2020, which claims the benefit of priority to Chinese Application No. 201921648808.5, filed on Sep. 29, 2019, both of which are incorporated by reference herein in their entireties for all purposes.
- The present disclosure relates to a field of heat exchange equipment, and more particularly, to a multi-channel heat exchanger and an air conditioning refrigeration system having the same.
- As an alternative technology of a copper tube fin heat exchanger, a multi-channel heat exchanger has attracted more and more attention in the field of an air conditioning technology, and has developed rapidly in recent years. Along a flow direction of a refrigerant, the refrigerant evaporates or condenses at different positions in channels arranged side by side are, thus resulting in a mismatch between a flow distribution of the refrigerant in the channels and a heat-exchange temperature difference. An obvious temperature difference occurs between a windward side and a leeward side on a section of the heat exchange tube, and an obvious overcooling or overheating temperature gradient is formed on a section of the heat exchange tube adjacent to an outlet of the heat exchanger. A temperature difference on the windward side cannot be better utilized.
- A multi-channel heat exchanger according to embodiments of the present disclosure includes a plurality of heat exchange tubes spaced apart along a thickness direction of the heat exchange tube. The heat exchange tube has a first longitudinal side face and a second longitudinal side face opposite to and parallel to each other along the thickness direction of the heat exchange tube, and a third longitudinal side face and a fourth longitudinal side face opposite to each other along a width direction of the heat exchange tube. A distance between the first longitudinal side face and the second longitudinal side face is less than a distance between the third longitudinal side face and the fourth longitudinal side face. The heat exchange tube is divided into four portions with an equal width along the width direction of the heat exchange tube, and the four portions includes a first heat exchange tube portion, a second heat exchange tube portion, a third heat exchange tube portion and a fourth heat exchange tube portion distributed along a direction from an inlet side of an airflow to an outlet side of the airflow. Each heat exchange tube portion includes at least two flow channels, and the flow channel extends in a length direction of the heat exchange tube. The respective flow channels of the four portions are spaced apart along the width direction of the heat exchange tube. The heat exchange tube has a cross section defined in the thickness direction of the heat exchange tube and the width direction of the heat exchange tube, and the cross section includes a flow section. A total area of a flow section of the first heat exchange tube portion is A1, a total area of a flow section of the second heat exchange tube portion being A2, a total area of a flow section of the third heat exchange tube portion being A3, a total area of a flow section of the fourth heat exchange tube portion is A4. The total area A1 of the flow section of the first heat exchange tube portion is 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion.
- An air conditioning refrigeration system according to embodiments of the present disclosure includes a multi-channel heat exchanger, a second heat exchanger, a compressor and a throttle valve. One of a first header of the multi-channel heat exchanger and a first end of the second heat exchanger is connected to an inlet end of the compressor, and the other one of the first header of the multi-channel heat exchanger and the first end of the second heat exchanger is connected to an outlet end of the compressor. The throttle valve is connected between a second header of the multi-channel heat exchanger and a second end of the second heat exchanger. The multi-channel heat exchanger includes a plurality of heat exchange tubes spaced apart along a thickness direction of the heat exchange tube. The heat exchange tube has a first longitudinal side face and a second longitudinal side face opposite to and parallel to each other along the thickness direction of the heat exchange tube, and a third longitudinal side face and a fourth longitudinal side face opposite to each other along a width direction of the heat exchange tube. A distance between the first longitudinal side face and the second longitudinal side face is less than a distance between the third longitudinal side face and the fourth longitudinal side face. The heat exchange tube is divided into four portions with an equal width along the width direction of the heat exchange tube, and the four portions includes a first heat exchange tube portion, a second heat exchange tube portion, a third heat exchange tube portion and a fourth heat exchange tube portion distributed along a direction from an inlet side of an airflow to an outlet side of the airflow. Each heat exchange tube portion includes at least two flow channels, and the flow channel extends in a length direction of the heat exchange tube. The respective flow channels of the four portions are spaced apart along the width direction of the heat exchange tube. The heat exchange tube has a cross section defined in the thickness direction of the heat exchange tube and the width direction of the heat exchange tube, and the cross section includes a flow section. A total area of a flow section of the first heat exchange tube portion is A1, a total area of a flow section of the second heat exchange tube portion being A2, a total area of a flow section of the third heat exchange tube portion being A3, a total area of a flow section of the fourth heat exchange tube portion is A4. The total area A1 of the flow section of the first heat exchange tube portion is 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion.
- Additional aspects and advantages of the present disclosure will be given in part in the following description, become apparent in part from the following description, or be learned from the practice of the present disclosure.
- The above and/or additional aspects and advantages of the present disclosure will become apparent and easy to understand from following descriptions of embodiments in combination with accompanying drawings, in which:
-
FIG. 1 is a schematic view of a multi-channel heat exchanger according to an embodiment of the present disclosure; -
FIG. 2 is a schematic side view of a multi-channel heat exchanger according to an embodiment of the present disclosure (an arrow direction is an air flow direction); -
FIG. 3 is a schematic view of a fin of a multi-channel heat exchanger according to an embodiment of the present disclosure from a perspective; -
FIG. 4 is a schematic view of a fin of a multi-channel heat exchanger according to an embodiment of the present disclosure from another perspective; -
FIG. 5 is a schematic view of a fin of a multi-channel heat exchanger according to an embodiment of the present disclosure; -
FIG. 6 is a schematic view of a fin of a multi-channel heat exchanger according to an embodiment of the present disclosure; -
FIG. 7 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure; -
FIG. 8 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure; -
FIG. 9 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure; -
FIG. 10 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure; -
FIG. 11 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure; -
FIG. 12 is a sectional view of a heat exchange tube of a multi-channel heat exchanger according to an embodiment of the present disclosure. - Embodiments of the present disclosure are described in detail below, and examples of the embodiments are shown in accompanying drawings. The same or similar elements or the elements having same or similar functions are denoted by the same or similar reference numerals throughout the descriptions. The following embodiments described with reference to the accompanying drawings are exemplary and are only intended to explain the present disclosure, rather than limit the present disclosure.
- A
multi-channel heat exchanger 100 according to embodiments of the present disclosure will be described below with reference toFIGS. 1 to 12 . - As shown in
FIG. 1 andFIG. 2 , themulti-channel heat exchanger 100 according to the embodiments of the present disclosure includes afirst header 10, asecond header 20 and a plurality ofheat exchange tubes 30. - As shown in
FIG. 1 , an axial direction of thefirst header 10 may be parallel to an axial direction of thesecond header 20, thefirst header 10 and thesecond header 20 may be arranged in parallel to each other and spaced apart from each other, and thefirst header 10 and thesecond header 20 are distributed along a length direction of theheat exchange tube 30. Thefirst header 10 may be configured as an inlet header, and thesecond header 20 may be configured as an outlet header. Alternatively, thefirst header 10 may be configured as an outlet header, and thesecond header 20 may be configured as an inlet header. - As shown in
FIG. 1 , the plurality ofheat exchange tubes 30 are spaced apart along a thickness direction of theheat exchange tube 30, the thickness direction of theheat exchange tube 30 may be parallel to the axial direction of thefirst header 10 and the axial direction of thesecond header 20, and the plurality ofheat exchange tubes 30 may be spaced apart along the axial direction of thefirst header 10 and the axial direction of thesecond header 20. As shown inFIG. 2 , a first end of theheat exchange tube 30 is connected to thefirst header 10, and a second end of theheat exchange tube 30 is connected to thesecond header 20, so as to communicate thefirst header 10 with thesecond header 20, so that a heat exchange medium may flow in an order of thefirst header 10, theheat exchange tube 30 and thesecond header 20 or in an order of thesecond header 20, theheat exchange tube 30 and thefirst header 10. Thefirst header 10 may be provided with a first port, and thesecond header 20 may be provided with a second port. The first port and the second port are configured to be connected to an external pipeline, so as to connect the heat exchanger in a whole air conditioning system or other heat exchange systems. - As shown in
FIGS. 7 to 12 , theheat exchange tube 30 has a firstlongitudinal side face 30 a, a secondlongitudinal side face 30 b, a thirdlongitudinal side face 30 c and a fourthlongitudinal side face 30 d. - The first
longitudinal side face 30 a and the secondlongitudinal side face 30 b are opposite to and parallel to each other along the thickness direction of theheat exchange tube 30, and the thirdlongitudinal side face 30 c and the fourthlongitudinal side face 30 d are opposite to each other along a width direction of theheat exchange tube 30. A distance between the firstlongitudinal side face 30 a and the secondlongitudinal side face 30 b is less than a distance between the thirdlongitudinal side face 30 c and the fourthlongitudinal side face 30 d, i.e., a thickness of theheat exchange tube 30 is less than a width of theheat exchange tube 30. - In a practical application of the
multi-channel heat exchanger 100, an air flows through a gap between twoheat exchange tubes 30, i.e., the air passes by the firstlongitudinal side face 30 a and the secondlongitudinal side face 30 b. In theheat exchange tube 30 of the present disclosure, the firstlongitudinal side face 30 a and the secondlongitudinal side face 30 b are arranged in parallel, i.e., the thickness of theheat exchange tube 30 is constant along an air input direction. Therefore, theheat exchange tube 30 itself has little effect on the fluidity of the air. - As shown in
FIGS. 7 to 12 , theheat exchange tube 30 is divided into four portions with an equal width along the width direction of theheat exchange tube 30. The four portions include a first heat exchange tube portion, a second heat exchange tube portion, a third heat exchange tube portion and a fourth heat exchange tube portion distributed along a direction from an inlet side of an airflow to an outlet side of the airflow. Each heat exchange tube portion includes at least twoflow channels 30 e, and theflow channel 30 e extends in the length direction of the heat exchange tube. Moreover, therespective flow channels 30 e in the four heat exchange tube portions are spaced apart along the width direction of theheat exchange tube 30. Theheat exchange tube 30 has a cross section defined in the thickness direction of theheat exchange tube 30 and the width direction of theheat exchange tube 30, and the cross section includes a flow section. A total area of a flow section of the first heat exchange tube portion is A1 and a total area of a flow section of the fourth heat exchange tube portion is A4. The total area A1 of the flow section of the first heat exchange tube portion is 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion. A total area of a flow section of the second heat exchange tube portion is A2 and a total area of a flow section of the third heat exchange tube portion is A3. It should be noted that theheat exchange tube 30 of the present disclosure includes four portions divided equally along its width direction, and the distribution of theflow channels 30 e has no direct corresponding relationship with the division of the heat exchange tube. Therefore, at least part of theflow channel 30 e may be divided into a former heat exchange tube portion and a rest portion of theflow channel 30 e may be divided into a latter heat exchange tube portion in a specific division process. Therefore, the flow section of the heat exchange tube portion referred to in the present disclosure includes a cross section of the complete flow channel and a cross section of the incomplete flow channel located in the heat exchange tube portion. - Since the
multi-channel heat exchanger 100 has a temperature difference on a windward side and a leeward side, when the total area A1 of the flow section of the first heat exchange tube portion is less than 1.05 times of the total area A4 of the flow section of the fourth heat exchange tube portion, the difference between the refrigerant in the flow channels of the first heat exchange tube portion and the refrigerant in the flow channels of the fourth heat exchange tube portion is small if themulti-channel heat exchanger 100 is used as an evaporator, which will result in that the refrigerant in the flow channels of the fourth heat exchange tube portion cannot have a sufficient heat exchange. For example, the liquid refrigerant in the flow channels at an outlet of themulti-channel heat exchanger 100 cannot be evaporated. - When the total area A1 of the flow section of the first heat exchange tube portion is greater than 1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion, the difference between the refrigerant in the flow channels of the first heat exchange tube portion and the refrigerant in the flow channels of the fourth heat exchange tube portion is large if the
multi-channel heat exchanger 100 is used as the evaporator, which will result in that the refrigerant in the flow channels of the first heat exchange tube portion is evaporated too fully, thus causing a waste of space, and which will also have an impact on the structural safety of themulti-channel heat exchanger 100, thus causing a decrease of burst pressure. - Therefore, when the total area A1 of the flow section of the first heat exchange tube portion is 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion, the design of the flow channels can meet the safety of the
multi-channel heat exchanger 100 so as not to cause a waste of excess space, and also can make full use of the temperature difference between the windward side and the leeward side of themulti-channel heat exchanger 100, so as to allow the refrigerant in different flow channels to fully exchange heat, thus effectively reducing a temperature gradient on the cross section of the heat exchange tube of themulti-channel heat exchanger 100, balancing the temperature difference between the refrigerant in the heat exchange tube on the windward side and the refrigerant in the heat exchange tube on the leeward side, achieving the optimal balanced state of outlet overheating, and hence improving the heat exchange performance of themulti-channel heat exchanger 100. - Therefore, the total area A2 of the flow section of the second heat exchange tube portion may be 1.3 times of the total area A3 of the flow section of the third heat exchange tube portion, and the total area A3 of the flow section of the third heat exchange tube portion may be 1.2 times of the total area A4 of the flow section of the fourth heat exchange tube portion, i.e., flow sectional areas of the
flow channels 30 e of the four heat exchange tube portions gradually decrease from the air inlet side to the air outlet side. Of course, the number of groups of theflow channels 30 e is not limited to four, but can also be more, such as six, seven or eight. Distances from any one of theflow channels 30 e in the four heat exchange tube portions to twoflow channels 30 e adjacent to thisflow channel 30 e can be set to be equal, so that each group offlow channels 30 e are evenly arranged. - In some embodiments of the present disclosure, distances from at least one of the
flow channels 30 e in the four heat exchange tube portions to twoflow channels 30 e adjacent to the at least oneflow channel 30 e may be different. - It can be understood that in a process of the airflow flowing through the
multi-channel heat exchanger 100, a temperature difference between the airflow on a windward side of themulti-channel heat exchanger 100 and the heat exchange medium is large, and a temperature difference between the airflow on a leeward side of themulti-channel heat exchanger 100 and the heat exchange medium is small. In this way, a heat exchange demand of the airflow on the leeward side of themulti-channel heat exchanger 100 is less than a heat exchange demand of the airflow on the windward side of themulti-channel heat exchanger 100. The windward side of themulti-channel heat exchanger 100 corresponds to the inlet side of the airflow and the leeward side of themulti-channel heat exchanger 100 corresponds to the outlet side of the airflow. - In the related art, the flow sectional areas of the plurality of
flow channels 30 e of themulti-channel heat exchanger 100 from the windward side to the leeward side are the same. Due to the heat transfer between the airflow and the heat exchange medium, the temperatures of the heat exchange media in therespective flow channels 30 e arranged side by side along a wind direction (a transverse direction or the width direction of the heat exchange tube 30) are different. Therefore, the heat exchange medium in the flow channel adjacent to the windward side may have been evaporated or condensed, while the heat exchange medium in a latter flow channel (for example, the flow channel adjacent to the leeward side) along the transverse direction may have not been evaporated or condensed. - In some embodiments, a distance between any two
adjacent flow channels 30 e in the first heat exchange tube portion is B1, and a distance between any twoadjacent flow channels 30 e in the second heat exchange tube portion is B2. B1 is greater than or equal to B2, i.e., in multiple groups offlow channels 30 e, the distance between the flow channels in the respective groups offlow channels 30 e gradually decreases from the inlet side of the airflow to the outlet side of the airflow. - In some embodiments, in the
respective flow channels 30 e of the first heat exchange tube portion, a sum of the flow sectional areas of theflow channels 30 e completely located in the first heat exchange tube portion is C1, and in therespective flow channels 30 e of the second heat exchange tube portion, a sum of the flow sectional areas of theflow channels 30 e completely located in the second heat exchange tube portion is C2. C2 is greater than or equal to C1. In other words, the flow sectional areas of theflow channels 30 e in the respective heat exchange tube portions gradually decrease from the inlet side of the airflow to the outlet side of the airflow. It should be noted that theheat exchange tube 30 of the present disclosure includes four portions divided equally along its width direction, and the distribution of theflow channels 30 e has no direct corresponding relationship with the division of the heat exchange tube. Therefore, at least part of theflow channel 30 e may be divided into a former heat exchange tube portion and a rest portion of theflow channel 30 e may be divided into a latter heat exchange tube portion in a specific division process. - In some embodiments of the present disclosure, a sum of the flow sectional areas of the respective flow channels of the first heat exchange tube portion is greater than or equal to a sum of the flow sectional areas of the respective flow channels of the second heat exchange tube portion.
- In the present disclosure, as shown in
FIGS. 7 to 12 , the flow sectional areas of thecorresponding flow channels 30 e in the plurality of heat exchange tube portions are configured to decrease sequentially from the air inlet side to the air outlet side, so that flow quantities of the heat exchange media in the plurality of heat exchange tube portions may be decreased sequentially from the air inlet side to the air outlet side, i.e., the heat exchange effect of themulti-channel heat exchanger 100 decreases gradually from the air inlet side to the air outlet side. Thus, the heat exchange amount on the windward side of themulti-channel heat exchanger 100 and the heat exchange amount on the leeward side of themulti-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, respectively, so that the heat exchange effects on two sides of themulti-channel heat exchanger 100 can better meet the actual requirements, a temperature difference between the windward side and the leeward side of themulti-channel heat exchanger 100 is balanced, and a situation in which one side of themulti-channel heat exchanger 100 is overcooled and the other side of themulti-channel heat exchanger 100 is overheated is prevented, thus ensuring the reasonable and safe use of themulti-channel heat exchanger 100, and improving the heat exchange performance of themulti-channel heat exchanger 100. - In the
heat exchange tube 30 according to the embodiments of the present disclosure, the flow sectional areas of the flow channels in the four heat exchange tube portions are configured to decrease sequentially from the air inlet side to the air outlet side, so that the heat exchange amount on the windward side of themulti-channel heat exchanger 100 and the heat exchange amount on the leeward side of themulti-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, respectively, so as to effectively balance the temperature difference between the refrigerant in theheat exchange tube 30 on the windward side and the refrigerant in theheat exchange tube 30 on the leeward side, and to optimize the degree of outlet overcooling or overheating, thus improving the heat exchange performance of themulti-channel heat exchanger 100. - In some embodiments, as shown in
FIG. 3 , themulti-channel heat exchanger 100 further includes afin 40. Thefin 40 is arranged between twoheat exchange tubes 30 along the thickness direction of theheat exchange tube 30, and thefin 40 is connected to the twoheat exchange tubes 30, respectively. The fin includes first to nth groups offins 40. - As shown in
FIG. 4 , each group includes at least onefin 40. The first to nth groups offins 40 are all mounted between the first longitudinal side face 30 a of oneheat exchange tube 30 and the second longitudinal side face 30 b of an adjacentheat exchange tube 30, and the first to nth groups offins 40 are arranged sequentially along the width direction of theheat exchange tube 30. The first group offins 40, . . . , the nth group offins 40 are distributed along the direction from the air inlet side to the air outlet side, in which 1≤n, and n is an integer. - The
heat exchange tube 30 is provided with the plurality offlow channels 30 e in the width direction, so that the plurality offlow channels 30 e may correspond to the n groups offins 40. Therefore, the heat of the heat exchange medium in themulti-channel heat exchanger 100 may be diffused to thefin 40, so as to exchange heat with the airflow. Moreover, thefin 40 has a large surface area, so that the airflow can fully exchange heat with thefin 40. Thus, the heat dissipation effect of each portion of themulti-channel heat exchanger 100 can be maintained at a high level. - An air-side heat transfer coefficient of the nth group of
fins 40 is less than an air-side heat transfer coefficient of the first group offins 40. The air-side heat transfer coefficients of the n groups offins 40 decrease sequentially from the first group of fins to the nth group of fins, and the heat transfer coefficient of thefin 40 adjacent to the air inlet side is greater than the heat transfer coefficient of thefin 40 adjacent to the air outlet side, so that the plurality of groups offins 40 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, so as to effectively balance the temperature difference between the refrigerant in theheat exchange tube 30 on the windward side and the refrigerant in theheat exchange tube 30 on the leeward side, and to optimize the degree of outlet overcooling or overheating, thus improving the heat exchange performance of themulti-channel heat exchanger 100. - In some embodiments, the first to nth groups of
fins 40 each include a plurality oflouvers 40 a arranged along the width direction of theheat exchange tube 30. The number of thelouvers 40 a of the first group offins 40 is Q1, . . . , the number of thelouvers 40 a of a kth group offins 40 is Qk, . . . , and the number of thelouvers 40 a of the nth group offins 40 is Qn, in which Q1 is greater than Qn, and when n is greater than 1, Qk−1 is greater than Qk. - That is, as shown in
FIG. 5 , in the n groups offins 40, the number of thelouvers 40 a decreases sequentially from the first group to the nth group, and the more the number of thelouvers 40 a, the better the heat exchange effect, so that the heat exchange effect of themulti-channel heat exchanger 100 on the air inlet side is greater than the heat exchange effect of themulti-channel heat exchanger 100 on the air outlet side. Therefore, the heat exchange effect of themulti-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, thus optimizing the degree of outlet overcooling or overheating, avoiding the situation of overheating at one side and overcooling at the other side, and improving the rationality of the structural design of themulti-channel heat exchanger 100. In some embodiments, themulti-channel heat exchanger 100 has at least one of the following features. - a. As shown in
FIG. 4 andFIG. 6 , an opening width of thelouver 40 a in the first group offins 40 is W1, . . . , an opening width of thelouver 40 a in the kth group offins 40 is Wk, . . . , and an opening width of thelouver 40 a in the nth group offins 40 is Wn, in which W1 is greater than Wn, and when n is greater than 1, Wk−1 is greater than Wk. Thus, in the n groups offins 40, the opening width of thelouver 40 a decreases sequentially from the first group to the nth group, and the larger the opening width of thelouver 40 a, the better the heat exchange effect, so that the heat exchange effect of themulti-channel heat exchanger 100 on the air inlet side is greater than the heat exchange effect of themulti-channel heat exchanger 100 on the air outlet side. Therefore, the heat exchange effect of themulti-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, and the heat exchange performance of themulti-channel heat exchanger 100 is improved. - b. As shown in
FIG. 4 , an opening angle of thelouver 40 a in the first group offins 40 is R1, . . . , an opening angle of thelouver 40 a in the kth group offins 40 is Rk, . . . , and an opening angle of thelouver 40 a in the nth group offins 40 is Rn, in which R1 is greater than Rn, and when n is greater than 1, Rk−1 is greater than Rk. Therefore, in the n groups of fins, the opening angle of thelouver 40 a decreases sequentially from the first group to the nth group, and the larger the opening angle of thelouver 40 a, the better the heat exchange effect, so that the heat exchange effect of themulti-channel heat exchanger 100 on the air inlet side is greater than the heat exchange effect of themulti-channel heat exchanger 100 on the air outlet side. Therefore, the heat exchange effect of themulti-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, and the heat exchange performance of themulti-channel heat exchanger 100 is improved. - c. As shown in
FIG. 4 , an opening length of thelouver 40 a in the first group offins 40 is L1, . . . , an opening length of thelouver 40 a in the kth group offins 40 is Lk, . . . , and an opening length of thelouver 40 a in the nth group offins 40 is Ln, in which L1 is greater than Ln, and when n is greater than 1, Lk−1 is greater than Lk. Therefore, in the n groups of fins, the opening length of thelouver 40 a decreases sequentially from the first group to the nth group, and the larger the opening length of thelouver 40 a, the better the heat exchange effect, so that the heat exchange effect of themulti-channel heat exchanger 100 on the air inlet side is greater than the heat exchange effect of themulti-channel heat exchanger 100 on the air outlet side. Therefore, the heat exchange effect of themulti-channel heat exchanger 100 can reasonably match with the heat exchange demand of the airflow on the air inlet side and the heat exchange demand of the airflow on the air outlet side, and the heat exchange performance of themulti-channel heat exchanger 100 is improved. - Therefore, when the
multi-channel heat exchanger 100 of the present disclosure meets at least one of the above features, the air-side heat transfer coefficient or the heat dissipation performance of a former group offins 40 is better than the air-side heat transfer coefficient of a latter group offins 40. In cooperation with a former group offlow channels 30 e with a large flow sectional area, the heat exchange between thefin 40 on the windward side and the air can be further increased, and the heat exchange from the refrigerant to the air is increased, so that the heat exchange medium on the leeward side can also have an effective heat exchange when exchanging heat on the leeward side, so as to balance the heat exchange effects on the two sides of themulti-channel heat exchanger 100. - In some embodiments, as shown in
FIG. 3 , a spacing between twoadjacent fins 40 in the first group offins 40 along the length direction of theheat exchange tube 30 is Fpl , . . . , a spacing between twoadjacent fins 40 in the kth group offins 40 along the length direction of theheat exchange tube 30 is Fpk , . . . , and a spacing between twoadjacent fins 40 in the nth group offins 40 along the length direction of theheat exchange tube 30 is Fpn , in which Fpl , is less than Fpn , and when n is greater than 1, Fpk k−1, is less than Fpk . In other words, the spacing between the twoadjacent fins 40 in the former group offins 40 is less than the spacing between the twoadjacent fins 40 in the latter group offins 40. Therefore, the air-side heat transfer coefficient or the heat dissipation performance of the former group offins 40 is better than the air-side heat transfer coefficient of the latter group offins 40. In cooperation with the former group offlow channels 30 e with the large flow sectional area, the heat exchange between thefin 40 on the windward side and the air can be further increased, and the heat exchange from the refrigerant to the air is increased, so that the heat exchange medium on the leeward side can also have an effective heat exchange when exchanging heat on the leeward side, so as to balance the heat exchange effects on the two sides of themulti-channel heat exchanger 100. - Therefore, relevant parameters of the flow sectional area of the
flow channel 30 e in theheat exchange tube 30 and thefin 40 are designed cooperatively, so that a temperature gradient on the cross section of theheat exchange tube 30 of themulti-channel heat exchanger 100 can be effectively reduced, the temperature difference between the heat exchange medium on the windward side and the heat exchange medium on the leeward side can be balanced, and the degree of outlet overcooling or overheating can be optimized, thus improving the heat exchange performance of themulti-channel heat exchanger 100. - A boss may be arranged on the
fin 40, and a ratio of the number of the bosses of thefin 40 on the windward side to the number of the bosses of thefin 40 on the leeward side may be increased. Alternatively, a ratio of a contact area of the boss of thefin 40 on the windward side to a contact area of the boss of thefin 40 on the leeward side may be increased. Alternatively, a flanging height of a portion of thefin 40 on the windward side may be reduced and the number of openings on thefin 40 may be increased from the windward side to the leeward side. A distribution density of thefins 40 may be adjusted, for example, the density of thefins 40 on the windward side is greater than the density of thefins 40 on the leeward side, so as to balance the heat exchange effects on the two sides of themulti-channel heat exchanger 100. - In some embodiments, as shown in
FIG. 8 andFIG. 9 , each heat exchange tube portion includes a plurality offlow channels 30 e, and the flow sectional area of eachflow channel 30 e in the same heat exchange tube portion is the same, so that the plurality offlow channels 30 e in each heat exchange tube portion may allow the heat exchange medium to flow, thus increasing the overall heat exchange efficiency of themulti-channel heat exchanger 100. - In some embodiments, the
multi-channel heat exchanger 100 has at least one of the following features. - a. As shown in
FIG. 8 andFIG. 9 , a shape of the cross section of eachflow channel 30 e in the same heat exchange tube portion is the same, so as to facilitate the extrusion of theheat exchange tube 30. - b. As shown in
FIG. 8 andFIG. 9 , each heat exchange tube portion includes a plurality offlow channels 30 e, and the number of theflow channels 30 e in each heat exchange tube portion is the same, so as to make the overall structure of themulti-channel heat exchanger 100 more regular. - c. As shown in
FIG. 8 , sizes of any twoflow channels 30 e along the width direction of theheat exchange tube 30 are the same, and sizes of theflow channels 30 e in different heat exchange tube portions along the thickness direction of theheat exchange tube 30 are different. However, the flow sectional areas of theflow channels 30 e in the plurality of heat exchange tube portions still decrease sequentially from the windward side to the leeward side. - d. As shown in
FIG. 7 andFIG. 9 , sizes of any twoflow channels 30 e along the thickness direction of theheat exchange tube 30 are the same, and sizes of theflow channels 30 e in different heat exchange tube portions along the width direction of theheat exchange tube 30 are different. However, the flow sectional areas of the groups offlow channels 30 e still decrease sequentially from the windward side to the leeward side. - e. An outer profile of each
flow channel 30 e is the same. For example, the outer profile of eachflow channel 30 e may be one of a rectangle, a circle, a hexagon and a triangle. Moreover, at least part of theflow channels 30 e are provided with aninner rib 38, and the inner rib is mainly arranged in theflow channel 30 e adjacent to the leeward side, so as to reduce the flow sectional area of theflow channel 30 e on the leeward side. - In some embodiments, at least one of the
flow channels 30 e in the second heat exchange tube portion has a flow sectional area greater than or equal to any one of theflow channels 30 e in the third heat exchange tube portion. At least two of theflow channels 30 e in the first heat exchange tube portion, theflow channels 30 e in the second heat exchange tube portion and theflow channels 30 e in the third heat exchange tube portion have the same flow sectional area. Moreover, the number of theflow channels 30 e in the first heat exchange tube portion, the number of theflow channels 30 e in the second heat exchange tube portion and the number of theflow channels 30 e in the third heat exchange tube portion are configured to be the same, or are configured to decrease sequentially. - In some embodiments, an outer shape of the cross section of the
heat exchange tube 30 is circular, a plurality ofinner ribs 38 are arranged in theheat exchange tube 30, and the number of theinner ribs 38 on the windward side is less than the number of theinner ribs 38 on the leeward side, so as to increase a flow resistance of the heat exchange medium on the leeward side and reduce a flow resistance of the heat exchange medium on the windward side. The plurality ofinner ribs 38 extend radially outwards from a center of theheat exchange tube 30, and divide the cross section of theheat exchange tube 30 into a plurality offlow channels 30 e. Since the number of theinner ribs 38 on the windward side is less than the number of theinner ribs 38 on the leeward side, the number of theflow channels 30 e on the windward side is also less than the number of theflow channels 30 e on the leeward side. - As shown in
FIG. 10 , in some other embodiments, theinner rib 38 is arranged in a portion of theheat exchange tube 30 adjacent to the leeward side, and noinner rib 38 is arranged in a portion of theheat exchange tube 30 adjacent to the windward side. Alternatively, both the portions of theheat exchange tube 30 adjacent to the windward side and adjacent to the leeward side are provided with theinner rib 38, while moreinner ribs 38 are arranged in the portion of theheat exchange tube 30 adjacent to the leeward side than in the portion of theheat exchange tube 30 adjacent to the windward side. - As shown in
FIG. 10 , theheat exchange tube 30 sequentially includes aflow channel 31 in a first heat exchange tube portion, aflow channel 32 in a second heat exchange tube portion, aflow channel 33 in a third heat exchange tube portion, aflow channel 34 in a fourth heat exchange tube portion, aflow channel 35 in a fifth heat exchange tube portion, aflow channel 36 in a sixth heat exchange tube portion, and aflow channel 37 in a seventh heat exchange tube portion, and theinner rib 38 is arranged in theflow channels 30 e in multiple heat exchange tube portions adjacent to the leeward side. - Alternatively, the outer shape of the cross section of the
heat exchange tube 30 is configured to be oval or polygonal. As shown inFIGS. 7 to 12 , the outer shape of theheat exchange tube 30 is oval, and the number of theflow channels 30 e or the area of theflow channel 30 e on the windward side is larger than the number of theflow channels 30 e or the area of theflow channel 30 e on the leeward side. Alternatively, theheat exchange tube 30 adopts a wire tube, and along a direction from the windward side to the leeward side, the number of the wire tubes on the windward side is larger than the number of the wire tubes on the leeward side, or an inner section of the wire tube on the windward side is greater than an inner section of the wire tube on the leeward side. - Therefore, through the shape of the
heat exchange tube 30 as well as the shape and arrangement of theflow channels 30 e, the heat exchange amount on the windward side of themulti-channel heat exchanger 100 and the heat exchange amount on the leeward side of themulti-channel heat exchanger 100 can match with the actual heat exchange requirements, so as to effectively reduce the temperature gradient on the cross section of theheat exchange tube 30 of themulti-channel heat exchanger 100, balance the temperature difference between the heat exchange medium on the windward side and the heat exchange medium on the leeward side, and optimize the degree of outlet overcooling or overheating, thus improving the heat exchange performance of themulti-channel heat exchanger 100. - The present disclosure further provides an air conditioning refrigeration system.
- The air conditioning refrigeration system according to embodiments of the present disclosure includes a
multi-channel heat exchanger 100 according to any one of the above embodiments, a second heat exchanger, a compressor and a throttle valve. One of afirst header 10 of themulti-channel heat exchanger 100 and a first end of the second heat exchanger is connected to an inlet end of the compressor, the other one of thefirst header 10 of themulti-channel heat exchanger 100 and the first end of the second heat exchanger is connected to an outlet end of the compressor, and the throttle valve is connected between asecond header 20 of themulti-channel heat exchanger 100 and a second end of the second heat exchanger. - Therefore, the above
multi-channel heat exchanger 100 is arranged in the air conditioning refrigeration system, so that the heat exchange medium in each heat exchange tube of the air conditioning refrigeration system can effectively exchange heat with the airflow, a local heat exchange will not have a lack or an excess, the rationality of the structural design of the air conditioning refrigeration system is improved and the practicability of the air conditioning refrigeration system is improved. - Reference throughout this specification to “an embodiment,” “some embodiments,” “an exemplary embodiment,” “an example,” “a specific example,” or “some examples,” means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present disclosure. Thus, the exemplary descriptions of the above terms throughout this specification are not necessarily referring to the same embodiment or example. Moreover the particular features, structures, materials or characteristic described may be combined in a suitable manner in any one or more embodiments or examples.
- Although embodiments of the present disclosure have been shown and described, it would be appreciated by those skilled in the art that various changes, modifications, alternatives and variations may be made in the embodiments without departing from principles and purposes of the present disclosure. The scope of the present disclosure is defined by the claims and their equivalents.
Claims (20)
1. A multi-channel heat exchanger, comprising:
a plurality of heat exchange tubes spaced apart along a thickness direction of the heat exchange tube,
the heat exchange tube having a first longitudinal side face and a second longitudinal side face opposite to and parallel to each other along the thickness direction of the heat exchange tube, and a third longitudinal side face and a fourth longitudinal side face opposite to each other along a width direction of the heat exchange tube, a distance between the first longitudinal side face and the second longitudinal side face being less than a distance between the third longitudinal side face and the fourth longitudinal side face,
the heat exchange tube being divided into four portions with an equal width along the width direction of the heat exchange tube, the four portions comprising a first heat exchange tube portion, a second heat exchange tube portion, a third heat exchange tube portion and a fourth heat exchange tube portion distributed along a direction from an inlet side of an airflow to an outlet side of the airflow, each heat exchange tube portion comprising at least two flow channels, the flow channel extending in a length direction of the heat exchange tube, the respective flow channels of the four portions being spaced apart along the width direction of the heat exchange tube,
the heat exchange tube having a cross section defined in the thickness direction of the heat exchange tube and the width direction of the heat exchange tube, the cross section comprising a flow section, a total area of a flow section of the first heat exchange tube portion being A1, a total area of a flow section of the second heat exchange tube portion being A2, a total area of a flow section of the third heat exchange tube portion being A3, a total area of a flow section of the fourth heat exchange tube portion being A4, and the total area A1 of the flow section of the first heat exchange tube portion being 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion.
2. The multi-channel heat exchanger according to claim 1 , wherein distances from at least one of the flow channels in the four heat exchange tube portions to two flow channels adjacent to the at least one of the flow channels are different.
3. The multi-channel heat exchanger according to claim 1 , wherein a distance between any two adjacent flow channels in the first heat exchange tube portion is greater than or equal to a distance between any two adjacent flow channels in the second heat exchange tube portion.
4. The multi-channel heat exchanger according to claim 1 , wherein a sum of flow sectional areas of the flow channels completely located in the first heat exchange tube portion in the respective flow channels of the first heat exchange tube portion is greater than or equal to a sum of flow sectional areas of the flow channels completely located in the second heat exchange tube portion in the respective flow channels of the second heat exchange tube portion.
5. The multi-channel heat exchanger according to claim 1 , further comprising a fin, the fin being arranged between two heat exchange tubes along the thickness direction of the heat exchange tube and connected to the two heat exchange tubes, respectively, the fin comprising first to nth groups of fins, the first to groups of fins being distributed along the direction from the inlet side of the airflow to the outlet side of the airflow, wherein 1≤n, n is an integer, and an air-side heat transfer coefficient of the nth group of fins is less than an air-side heat transfer coefficient of the first group of fins.
6. The multi-channel heat exchanger according to claim 5 , wherein the first to nth groups of fins comprise a plurality of louvers arranged along the width direction of the heat exchange tube, and the number of the louvers of the first group of fins is greater than the number of the louvers of the nth group of fins.
7. The multi-channel heat exchanger according to claim 6 , wherein the multi-channel heat exchanger comprises at least one of following features:
a. an opening width of the louver of the first group of fins is greater than an opening width of the louver of the nth group of fins;
b. an opening angle of the louver of the first group of fins is greater than an opening angle of the louver of the nth group of fins; and
c. an opening length of the louver of the first group of fins is greater than an opening length of the louver of the nth group of fins.
8. The multi-channel heat exchanger according to claim 6 , wherein a spacing between two adjacent fins in the first group of fins along the length direction of the heat exchange tube is less than a spacing between two adjacent fins in the nth group of fins along the length direction of the heat exchange tube.
9. The multi-channel heat exchanger according to claim 1 , wherein a flow sectional area of each flow channel in each the same heat exchange tube portion is the same.
10. The multi-channel heat exchanger according to claim 9 , wherein the multi-channel heat exchanger comprises at least one of following features:
a. a shape of a cross sectional of each flow channel in the same heat exchange tube portion is the same;
b. each heat exchange tube portion comprises a same number of flow channels;
c. sizes of any two flow channels along the width direction of the heat exchange tube are the same, and sizes of the flow channels in different heat exchange tube portions along the thickness direction of the heat exchange tube are different;
d. sizes of any two flow channels along the thickness direction of the heat exchange tube are the same, and sizes of the flow channels in different heat exchange tube portions along the width direction of the heat exchange tube are different; and
e. at least part of the flow channels are provided with an inner rib.
11. An air conditioning refrigeration system, comprising a multi-channel heat exchanger, a second heat exchanger, a compressor and a throttle valve, one of a first header of the multi-channel heat exchanger and a first end of the second heat exchanger being connected to an inlet end of the compressor, the other one of the first header of the multi-channel heat exchanger and the first end of the second heat exchanger being connected to an outlet end of the compressor, and the throttle valve being connected between a second header of the multi-channel heat exchanger and a second end of the second heat exchanger,
the multi-channel heat exchanger, comprising a plurality of heat exchange tubes spaced apart along a thickness direction of the heat exchange tube,
the heat exchange tube having a first longitudinal side face and a second longitudinal side face opposite to and parallel to each other along the thickness direction of the heat exchange tube, and a third longitudinal side face and a fourth longitudinal side face opposite to each other along a width direction of the heat exchange tube, a distance between the first longitudinal side face and the second longitudinal side face being less than a distance between the third longitudinal side face and the fourth longitudinal side face,
the heat exchange tube being divided into four portions with an equal width along the width direction of the heat exchange tube, the four portions comprising a first heat exchange tube portion, a second heat exchange tube portion, a third heat exchange tube portion and a fourth heat exchange tube portion distributed along a direction from an inlet side of an airflow to an outlet side of the airflow, each heat exchange tube portion comprising at least two flow channels, the flow channel extending in a length direction of the heat exchange tube, the respective flow channels of the four portions being spaced apart along the width direction of the heat exchange tube,
the heat exchange tube having a cross section defined in the thickness direction of the heat exchange tube and the width direction of the heat exchange tube, the cross section comprising a flow section, a total area of a flow section of the first heat exchange tube portion being A1, a total area of a flow section of the second heat exchange tube portion being A2, a total area of a flow section of the third heat exchange tube portion being A3, a total area of a flow section of the fourth heat exchange tube portion being A4, and the total area A1 of the flow section of the first heat exchange tube portion being 1.05-1.4 times of the total area A4 of the flow section of the fourth heat exchange tube portion.
12. The air conditioning refrigeration system according to claim 11 , wherein distances from at least one of the flow channels in the four heat exchange tube portions to two flow channels adjacent to the at least one of the flow channels are different.
13. The air conditioning refrigeration system according to claim 11 , wherein a distance between any two adjacent flow channels in the first heat exchange tube portion is greater than or equal to a distance between any two adjacent flow channels in the second heat exchange tube portion.
14. The air conditioning refrigeration system according to claim 11 , wherein a sum of flow sectional areas of the flow channels completely located in the first heat exchange tube portion in the respective flow channels of the first heat exchange tube portion is greater than or equal to a sum of flow sectional areas of the flow channels completely located in the second heat exchange tube portion in the respective flow channels of the second heat exchange tube portion.
15. The air conditioning refrigeration system according to claim 11 , wherein the multi-channel heat exchanger further comprises a fin, the fin is arranged between two heat exchange tubes along the thickness direction of the heat exchange tube and connected to the two heat exchange tubes, respectively, the fin comprises first to nth groups of fins, the first to nth groups of fins are distributed along the direction from the inlet side of the airflow to the outlet side of the airflow, wherein 1≤n, n is an integer, and an air-side heat transfer coefficient of the nth group of fins is less than an air-side heat transfer coefficient of the first group of fins.
16. The air conditioning refrigeration system according to claim 15 , wherein the first to nth groups of fins comprise a plurality of louvers arranged along the width direction of the heat exchange tube, and the number of the louvers of the first group of fins is greater than the number of the louvers of the nth group of fins.
17. The air conditioning refrigeration system according to claim 16 , wherein the multi-channel heat exchanger comprises at least one of following features:
a. an opening width of the louver of the first group of fins is greater than an opening width of the louver of the nth group of fins;
b. an opening angle of the louver of the first group of fins is greater than an opening angle of the louver of the nth group of fins; and
c. an opening length of the louver of the first group of fins is greater than an opening length of the louver of the nth group of fins.
18. The air conditioning refrigeration system according to claim 16 , wherein a spacing between two adjacent fins in the first group of fins along the length direction of the heat exchange tube is less than a spacing between two adjacent fins in the nth group of fins along the length direction of the heat exchange tube.
19. The air conditioning refrigeration system according to claim 11 , wherein a flow sectional area of each flow channel in the same heat exchange tube portion is the same.
20. The air conditioning refrigeration system according to claim 19 , wherein the multi-channel heat exchanger comprises at least one of following features:
a. a shape of a cross section of each flow channel in the same heat exchange tube portion is the same;
b. each heat exchange tube portion comprises a same number of flow channels;
c. sizes of any two flow channels along the width direction of the heat exchange tube are the same, and sizes of the flow channels in different heat exchange tube portions along the thickness direction of the heat exchange tube are different;
d. sizes of any two flow channels along the thickness direction of the heat exchange tube are the same, and sizes of the flow channels in different heat exchange tube portions along the width direction of the heat exchange tube are different; and
e. at least part of the flow channels are provided with an inner rib.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201921648808.5U CN210689278U (en) | 2019-09-29 | 2019-09-29 | Multichannel heat exchanger and air conditioner refrigerating system |
CN201921648808.5 | 2019-09-29 | ||
PCT/CN2020/115229 WO2021057543A1 (en) | 2019-09-29 | 2020-09-15 | Multi-channel heat exchanger and air conditioning refrigeration system |
Publications (1)
Publication Number | Publication Date |
---|---|
US20220333833A1 true US20220333833A1 (en) | 2022-10-20 |
Family
ID=70899278
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US17/764,816 Pending US20220333833A1 (en) | 2019-09-29 | 2020-09-15 | Multi-channel heat exchanger and air conditioning refrigeration system |
Country Status (3)
Country | Link |
---|---|
US (1) | US20220333833A1 (en) |
CN (1) | CN210689278U (en) |
WO (1) | WO2021057543A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN210689278U (en) * | 2019-09-29 | 2020-06-05 | 杭州三花微通道换热器有限公司 | Multichannel heat exchanger and air conditioner refrigerating system |
EP4184084A4 (en) * | 2020-07-14 | 2024-03-13 | Sanhua Hangzhou Micro Channel Heat Exchanger Co Ltd | Heat exchanger |
CN114608352A (en) * | 2020-12-08 | 2022-06-10 | 杭州三花微通道换热器有限公司 | Heat exchanger |
CN114322105B (en) * | 2021-03-29 | 2023-07-25 | 杭州三花微通道换热器有限公司 | Heat exchanger and air conditioning system |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101526322A (en) * | 2009-04-13 | 2009-09-09 | 三花丹佛斯(杭州)微通道换热器有限公司 | Flat pipe and heat exchanger |
CN102297547B (en) * | 2011-06-27 | 2013-04-10 | 三花控股集团有限公司 | Heat exchanger |
JP6062164B2 (en) * | 2012-06-13 | 2017-01-18 | 西谷 均 | Hinge device |
CN109974484B (en) * | 2019-04-15 | 2021-08-24 | 合肥华凌股份有限公司 | Heat exchanger and refrigeration equipment with same |
CN210689278U (en) * | 2019-09-29 | 2020-06-05 | 杭州三花微通道换热器有限公司 | Multichannel heat exchanger and air conditioner refrigerating system |
-
2019
- 2019-09-29 CN CN201921648808.5U patent/CN210689278U/en active Active
-
2020
- 2020-09-15 US US17/764,816 patent/US20220333833A1/en active Pending
- 2020-09-15 WO PCT/CN2020/115229 patent/WO2021057543A1/en active Application Filing
Also Published As
Publication number | Publication date |
---|---|
WO2021057543A1 (en) | 2021-04-01 |
CN210689278U (en) | 2020-06-05 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20220333833A1 (en) | Multi-channel heat exchanger and air conditioning refrigeration system | |
US4328861A (en) | Louvred fins for heat exchangers | |
US7913750B2 (en) | Louvered air center with vortex generating extensions for compact heat exchanger | |
US10767937B2 (en) | Flattened tube finned heat exchanger and fabrication method | |
US8276652B2 (en) | High performance louvered fin for heat exchanger | |
US20130240186A1 (en) | Multiple Tube Bank Flattened Tube Finned Heat Exchanger | |
US10508862B2 (en) | Heat exchanger for air-cooled chiller | |
US9714794B2 (en) | Heat exchanger tube having fins with varying louver inclination angle | |
US20160054038A1 (en) | Heat exchanger and refrigeration cycle apparatus | |
US20090173477A1 (en) | Heat exchanger fin | |
WO2015004720A1 (en) | Heat exchanger, and air conditioner | |
EP1519133A2 (en) | Heat exchanging apparatus | |
US6672376B2 (en) | Twisted-louver high performance heat exchanger fin | |
CN210128650U (en) | Flat pipe, multichannel heat exchanger and air conditioner refrigerating system | |
US5170842A (en) | Fin-tube type heat exchanger | |
US5975200A (en) | Plate-fin type heat exchanger | |
JP2010216718A (en) | Heat exchanger with fin | |
CN210268332U (en) | Multichannel heat exchanger and air conditioner refrigerating system | |
US20220236015A1 (en) | Flat tube, multi-channel heat exchanger, and air conditioning and refrigeration system | |
CN210128651U (en) | Flat pipe, multichannel heat exchanger and air conditioner refrigerating system | |
CN209960732U (en) | Heat exchanger and air conditioning system | |
EP0803695A2 (en) | Plate-fin type heat exchanger | |
JP2001133076A (en) | Heat exchanger | |
JP2003222436A (en) | Heat exchanger for heat pump type air conditioner | |
US20220034593A1 (en) | Heat exchanger devices and systems and associated methods |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: SANHUA (HANGZHOU) MICRO CHANNEL HEAT EXCHANGER CO., LTD., CHINA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:ZHAO, LEI;JIANG, JIANLONG;GAO, QIANG;AND OTHERS;SIGNING DATES FROM 20220303 TO 20220308;REEL/FRAME:059428/0077 |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION |