Heat exchanger and indoor air conditioning unit

Abstract

It eliminates the need for cross-piping within the heat exchanger, has a rational space occupancy, is easy to install, and takes into account issues of heat exchange efficiency and pressure drop. [Solution] The present invention relates to a heat exchange device and an indoor unit of an air conditioner. A first heat exchange channel (11) is provided on the first heat exchange section (a), a second heat exchange channel (211) is provided on the second heat exchange section (b), a third heat exchange channel (212) is provided on the third heat exchange section (c), and a fourth heat exchange channel (221) is provided on the fourth heat exchange section (d). The flow area of ​​any first heat exchange channel (11) is larger than the flow area of ​​any third heat exchange channel (212) and larger than the flow area of ​​any fourth heat exchange channel (221). The flow area of ​​any second heat exchange channel (211) is larger than the flow area of ​​any third heat exchange channel (212) and larger than the flow area of ​​any fourth heat exchange channel (221).

Description

Technical Field

[0001] This application claims priority based on a patent filed in China on October 31, 2022 (the applicants are Handan Midea Cooling Equipment Co., Ltd. and Guangdong Midea Cooling Equipment Co., Ltd., the title is Heat Exchange Device and Air Conditioning Indoor Unit, and the application numbers are 202211351383.8 and 202222887796.X).

[0002] The present invention relates to the technical field of air conditioning equipment, and particularly to a heat exchange device and an air conditioning indoor unit.

Background Art

[0003] In related technologies, a heat exchange device exchanges heat with the surrounding environment, such as ambient air or ambient liquid, through a refrigerant flowing in a heat exchange tube. The refrigerant has a low dryness and a small flow velocity when entering the flow path, but the dryness gradually increases and the flow velocity gradually rises during the flow process. As a result, the flow velocity of the refrigerant in the heat exchange tube becomes fast, and the pressure drop in the heat exchange tube becomes large, making it difficult to consider the problems of heat exchange efficiency and pressure drop.

[0004] In addition to the above, the refrigerant needs to flow through a plurality of heat exchange tubes arranged in a cycle, and cross-piping may occur, which increases the difficulty of arrangement and worsens the space occupation of the heat exchange device.

Summary of the Invention

Problems to be Solved by the Invention

[0005] The present invention proposes a heat exchange device to solve at least one of the technical problems existing in the current technology, thereby eliminating the need for cross-piping in the heat exchange device, having a reasonable space occupation, a low degree of arrangement difficulty, and considering the problems of heat exchange efficiency and pressure drop.

Means for Solving the Problems

[0006] The present invention proposes an air conditioning indoor unit using the above heat exchange device.

[0007] The heat exchange apparatus according to the present invention comprises a rear heat exchanger and a front heat exchanger, wherein the rear heat exchanger is inclined downward from top to bottom and extends rearward, and the rear heat exchanger is the first heat exchange section, the front heat exchanger has a front upper heat exchange segment and a front lower heat exchange segment, the front upper heat exchange segment is inclined downward from top to bottom and extends forward, and the upper end of the front upper heat exchange segment is connected to the upper end of the rear heat exchanger, the front lower heat exchange segment is connected to the lower end of the front upper heat exchange segment and is inclined downward from top to bottom and extends rearward, the front upper heat exchange segment is divided into a second heat exchange section and a third heat exchange section located below the second heat exchange section, the front lower heat exchange segment is the fourth heat exchange section, and the first heat exchange section is provided with a plurality of first heat exchange channels, and the plurality of first heat exchange channels The total flow area of ​​the heat exchange channels is A1, the second heat exchange section is provided with a plurality of second heat exchange channels, the total flow area of ​​the plurality of second heat exchange channels is A2, the third heat exchange section is provided with a plurality of third heat exchange channels, the total flow area of ​​the plurality of third heat exchange channels is A3, the fourth heat exchange section is provided with a plurality of fourth heat exchange channels, the total flow area of ​​the plurality of fourth heat exchange channels is A4, the flow area of ​​any one of the first heat exchange channels is greater than the flow area of ​​any one of the third heat exchange channels and greater than the flow area of ​​any one of the fourth heat exchange channels, the flow area of ​​any one of the second heat exchange channels is greater than the flow area of ​​any one of the third heat exchange channels and greater than the flow area of ​​any one of the fourth heat exchange channels.

[0008] By making the flow area of ​​any one of the multiple first heat exchange channels larger than the flow area of ​​any one of the multiple third heat exchange channels and larger than the flow area of ​​any one of the multiple fourth heat exchange channels, and by making the flow area of ​​any one of the multiple second heat exchange channels larger than the flow area of ​​any one of the multiple third heat exchange channels and larger than the flow area of ​​any one of the multiple fourth heat exchange channels, on the one hand, the number of heat exchange tubes in each heat exchange section is determined, and there are possible to connect the channels using multiple connection methods, but no cross-piping occurs with each connection method. On the other hand, the number of heat exchange tubes is adapted to the dryness of the refrigerant, reducing the number of branch channels by placing fewer heat exchange tubes in areas with low dryness and increasing the number of branch channels by placing more heat exchange tubes in areas with high dryness, thereby taking into consideration the issues of heat exchange efficiency and pressure drop, ensuring that the pressure drop in each section of the heat exchange device does not become excessively large, and that the heat exchange efficiency is high and the heat exchange effect is good.

[0009] In some implementations, the values ​​are 2.17≦A1 / A2≦5.67, 2.5≦A3 / A2≦3.33, 0.75≦A3 / A4≦2, and 0.8≦(A1+A2) / (A3+A4)≦2.22.

[0010] In some implementations, the flow area of ​​any one of the first heat exchange channels is the same as the flow area of ​​any one of the second heat exchange channels, and / or the flow area of ​​any one of the third heat exchange channels is the same as the flow area of ​​any one of the fourth heat exchange channels.

[0011] In some implementations, the heat exchanger is a fin-tube type heat exchanger, and the heat exchange flow path is limited by the heat exchange tubes, with multiple first heat exchange flow paths having the same or different specifications and a diameter of 5 mm to 7 mm, multiple second heat exchange flow paths having the same or different specifications and a diameter of 5 mm to 7 mm, multiple third heat exchange flow paths having the same or different specifications and a diameter of 4 mm to 6.5 mm, and multiple fourth heat exchange flow paths having the same or different specifications and a diameter of 4 mm to 6.5 mm.

[0012] In some implementations, the third heat exchange section is smoothly connected to the fourth heat exchange section via a curved portion, and in the cross-section of the heat exchanger, the longitudinal direction of the first heat exchange section extends linearly with length L1, the longitudinal direction of the second heat exchange section extends linearly with length L2, the linearly extending length of the third heat exchange section is L31 and the curved extending length is L32, the linearly extending length of the fourth heat exchange section is L41 and the curved extending length is L42, and 1.85 ≤ L1 / L2 ≤ 3.56, 1.1 ≤ (L31 + L32) / L2 ≤ 2.2, and 0.7 ≤ (L31 + L32) / (L41 + L42) ≤ 1.9.

[0013] In some implementations, in the cross-section of the heat exchanger, the width of the first heat exchange section is B1, the width of the second heat exchange section is B2, the width of the third heat exchange section is B3, and the following inequalities hold: 2.85 ≤ L1 / B1 ≤ 5.14, 1.23 ≤ L2 / B2 ≤ 1.94, and 1.5 ≤ L41 / B3 ≤ 2.44.

[0014] In some implementation scenarios, B1=B2=B3.

[0015] In some implementations, the heat exchanger is a finned-tube heat exchanger, where the fins of the front upper heat exchange segment and the fins of the front lower heat exchange segment are different parts of the same fin, and the fins of the rear heat exchanger and the fins of the front heat exchanger are two separated parts of a single fin.

[0016] In some embodiments, the heat exchanger is a fin-tube heat exchanger, having multiple rows of tube assemblies arranged along the width direction of the fins in the first, second, third, and fourth heat exchange sections, respectively, and each row of tube assemblies includes multiple heat exchange tubes arranged along the longitudinal direction of the fins, the heat exchange tubes defining the corresponding heat exchange flow path, and gap assemblies are installed between each pair of adjacent heat exchange tubes along the longitudinal direction of the fins.

[0017] In some implementations, in two adjacent rows of the heat exchanger assemblies, the number of gaps in at least one gap assembly in the upstream assemblies is equal to or greater than the number of gaps in any one gap assembly in the downstream assemblies of the heat exchanger, and the width of at least one gap assembly in the upstream assemblies is equal to or greater than the width of any one gap assembly in the downstream assemblies of the forward heat exchanger.

[0018] In some implementations, the rear heat exchanger has a rear upper heat exchange segment and a rear lower heat exchange segment, and the width of at least one gap assembly in the rear upper heat exchange segment is greater than or equal to the width of at least one gap assembly in the rear lower heat exchange segment.

[0019] In some implementations, the upper end of the rear heat exchanger has at least three types of gap assemblies, and / or the upper end of the front heat exchanger has at least three types of gap assemblies, wherein at least one parameter of the width, gap length, number of gaps and gap direction of the different types of gap assemblies is different.

[0020] In some implementations, a through-flow air passage is installed between the rear heat exchanger and the front heat exchanger, a groove is provided in a part of the front side of the rear heat exchanger, and at least a part of the groove faces the rear volute tongue of the through-flow air passage.

[0021] In some implementations, there are a plurality of gap assemblies at the connection point between the forward upper heat exchange segment and the forward lower heat exchange segment, the gap assembly located on the air injection side of the plurality of gap assemblies being the outer assembly, at least one of the outer assemblies forming a fixed assembly, the fixed assembly including one gap structure or a plurality of gap structures arranged along the direction of airflow passage, and in any two adjacent gap structures of the fixed assembly, the gap length of the downstream gap structure is greater than or equal to the gap length of the upstream gap structure.

[0022] The air conditioner indoor unit according to the present invention includes a housing, a blower device, and a heat exchange device. An air inlet is provided at the top of the housing. The blower device is installed inside the housing and has an air duct member and a cross-flow impeller. The cross-flow impeller is installed at the air duct inlet of the air duct member. The heat exchange device is installed inside the housing and is located between the air inlet and the blower device.

[0023] In some embodiments, the diameter of the cross-flow impeller is D, the maximum width of the housing in the front-rear direction is W, and 2.6 ≦ W / D ≦ 3.7.

[0024] Additional aspects and advantages of the present invention will be partially shown in the following description, or will become apparent from the following description, or will be found through the implementation of the present invention.

Effect of the Invention

[0025] The above and / or additional aspects and advantages of the present invention will become apparent and easy to understand in combination with the drawings and the description of the embodiments below.

Brief Description of the Drawings

[0026] [Figure 1] FIG. 1 is a schematic diagram of an air conditioner indoor unit according to an embodiment of the present invention. [Figure 2] FIG. 2 is a schematic diagram of a heat exchange device according to an embodiment of the present invention. [Figure 3] FIG. 3 is a schematic diagram of a first flow path arrangement method capable of executing a heat exchange device according to an embodiment of the present invention. [Figure 4] FIG. 4 is a schematic diagram of a second flow path arrangement method capable of executing a heat exchange device according to an embodiment of the present invention. [Figure 5] FIG. 5 is a schematic diagram of a third flow path arrangement method capable of executing a heat exchange device according to an embodiment of the present invention. [Figure 6] FIG. 6 is a schematic diagram of a fourth flow path arrangement method capable of executing a heat exchange device according to an embodiment of the present invention. [Figure 7]Figure 7 shows the energy efficiency diagrams of the first and second heat exchange tubes of different diameters in a heat exchange apparatus according to an embodiment of the present invention. [Figure 8] Figure 8 is an energy efficiency diagram of the third and fourth heat exchange tubes of different diameters in a heat exchanger according to an embodiment of the present invention. [Figure 9] Figure 9 is a schematic diagram of one type of gap structure according to the present invention. [Figure 10] Figure 10 is a schematic diagram from one viewpoint of another type of gap structure according to the present invention. [Figure 11] Figure 11 is a schematic diagram from another viewpoint of another type of gap structure according to the embodiment of the present invention. [Figure 12] Figure 12 is a schematic diagram of yet another gap structure according to the present invention. [Modes for carrying out the invention]

[0027] Embodiments of this application are described in detail below, and examples of such embodiments are shown in the drawings, where the same or similar reference numerals always indicate the same or similar elements or elements having the same or similar function. The embodiments described below with reference to the drawings are illustrative and are used only to interpret this application and should not be construed as limitations thereon.

[0028] In the description of this application, terms such as "center," "vertical," "horizontal," "length," "thickness," "width," "top," "bottom," "front," "back," "left," "right," "vertical," "horizontal," "top," "bottom," "inside," and "outside" represent directions or positional relationships based on the directions or positional relationships shown in the drawings. These terms are merely for convenience and simplification of the description of this application and do not explicitly or implicitly suggest that the mentioned devices or elements must be located in a particular direction or be made or operate according to a particular direction. It should be understood that these terms should not be interpreted as limitations on the scope of protection of the present invention.

[0029] Terms such as "first" and "second" are used solely for descriptive purposes and should not be understood as explicitly or implicitly indicating relative importance or suggesting the number of technical features. Therefore, technical features limited by "first" and "second" may explicitly or implicitly include one or more such features. In the description of this invention, unless otherwise specified, "multiple" means two or more.

[0030] Next, with reference to the drawings, the heat exchange device 100 and the air conditioning indoor unit 1000 according to the embodiment of the present invention will be described.

[0031] As shown in Figure 1-2, the heat exchange device 100 according to the first embodiment of the present invention comprises a front heat exchanger 20 and a rear heat exchanger 10.

[0032] The rear heat exchanger 10 extends backward in an inclination from top to bottom, and the rear heat exchanger 10 is the first heat exchange section a. The front heat exchanger 20 has a front upper heat exchange segment 21 and a front lower heat exchange segment 22. The front upper heat exchange segment 21 extends forward in an inclination from top to bottom, and the upper end of the front upper heat exchange segment 21 is connected to the upper end of the rear heat exchanger 10. The front lower heat exchange segment 22 is connected to the lower end of the front upper heat exchange segment 21 and extends backward in an inclination from top to bottom. The front upper heat exchange segment 21 is divided into a second heat exchange section b and a third heat exchange section c located below the second heat exchange section b, and the front lower heat exchange segment 22 is the fourth heat exchange section d.

[0033] The front heat exchanger 20 defines the contours of the second heat exchange section b, the third heat exchange section c, and the fourth heat exchange section d, and the rear heat exchanger 10 defines the contour of the first heat exchange section a. The upper ends of the first heat exchange section a and the second heat exchange section b (i.e., the front upper heat exchange segment 21) are connected in the front-rear direction (the connection according to the embodiment of the present invention may involve joining separating members or bending integrated members). The third heat exchange section c is located below the second heat exchange section b and extends inclined forward, and the fourth heat exchange section d is located below the third heat exchange section c and extends inclined backward. Thus, the encasing structure formed in the first heat exchange section a, the second heat exchange section b, the third heat exchange section c, and the fourth heat exchange section d encases the blower 200.

[0034] In some implementations, the pipe diameters of the second heat exchange channel 211 of the second heat exchange section b are all the same and are all larger than the pipe diameter of the third heat exchange channel 212 of the third heat exchange section c. The third heat exchange section c is connected to the fourth heat exchange section d, forming an angle between them in their respective extension directions.

[0035] In some implementations, as shown in Figure 2, the first row of heat exchange tubes on the upwind side of the forward heat exchanger 20 may be divided into three sections: the second heat exchange section b, the third heat exchange section c, the third heat exchange section c, and the section from the thirteenth heat exchange tube to the last heat exchange tube at the bottom, with specific restrictions on the extension direction and the number of heat exchange tubes in the second heat exchange section b, the third heat exchange section c, and the fourth heat exchange section d.

[0036] Multiple first heat exchange channels 11 are provided on the first heat exchange section a, and the total flow area of ​​the multiple first heat exchange channels 11 is A1. Multiple second heat exchange channels 211 are provided on the second heat exchange section b, and the total flow area of ​​the multiple second heat exchange channels 211 is A2. Multiple third heat exchange channels 212 are provided on the third heat exchange section c, and the total flow area of ​​the multiple third heat exchange channels 212 is A3. Multiple fourth heat exchange channels 221 are provided on the fourth heat exchange section d, and the total flow area of ​​the multiple fourth heat exchange channels 221 is A4. The flow area of ​​any one of the multiple first heat exchange channels 11 is greater than the flow area of ​​any one of the multiple third heat exchange channels 212, and also greater than the flow area of ​​any one of the multiple fourth heat exchange channels 221 (i.e., first heat exchange channel 11 > third heat exchange channel 212, first heat exchange channel 11 > fourth heat exchange channel 221). The flow area of ​​any one of the multiple fourth heat exchange channels 221 is greater than the flow area of ​​any one of the multiple third heat exchange channels 212, and also greater than the flow area of ​​any one of the multiple fourth heat exchange channels 221 (i.e., second heat exchange channel 211 > third heat exchange channel 212, second heat exchange channel 211 > fourth heat exchange channel 221).

[0037] For example, a first heat exchange tube may be installed in the first heat exchange section a, and multiple first heat exchange tubes may define the outline of the first heat exchange flow path 11; a second heat exchange tube may be installed in the second heat exchange section b, and multiple second heat exchange tubes may define the outline of the second heat exchange flow path 211; a third heat exchange tube may be installed in the third heat exchange section c, and multiple third heat exchange tubes may define the outline of the third heat exchange flow path 212; and a fourth heat exchange tube may be installed in the fourth heat exchange section d, and multiple fourth heat exchange tubes may define the outline of the fourth heat exchange flow path 221. On the cross-section of the heat exchanger 100 (referring to the cross-section of the heat exchanger 100 in a plane perpendicular to the axis of the cross-flow impeller 230 of the blower 200), the sum of the cross-sectional areas of the multiple first heat exchange tubes corresponds to the sum of the flow areas A1 of the first heat exchange flow channels 11, the sum of the cross-sectional areas of the multiple second heat exchange tubes corresponds to the sum of the flow areas A2 of the second heat exchange flow channels 211, the sum of the cross-sectional areas of the multiple third heat exchange tubes corresponds to the sum of the flow areas A3 of the third heat exchange flow channels 212, and the sum of the cross-sectional areas of the multiple fourth heat exchange tubes corresponds to the sum of the flow areas A4 of the fourth heat exchange flow channels 221.

[0038] At the inlet stage of the flow path, the degree of dryness of the refrigerant is low, and the mass of the liquid phase refrigerant is greater than the mass of the gaseous phase refrigerant. In either case, the flow area of ​​the second heat exchange flow path 211 is larger than the flow areas of the third heat exchange flow path 212 and the fourth heat exchange flow path 221. The refrigerant flow velocity in the pipe is low, and the heat exchange coefficient can be increased by increasing the refrigerant flow velocity at the inlet stage.

[0039] As the refrigerant flows through the intermediate stage, the degree of dryness of the refrigerant gradually increases, the mass of the refrigerant in the gas phase gradually becomes larger than the mass of the refrigerant in the liquid phase, the refrigerant flow velocity in the pipe gradually increases, and the flow area of ​​either the first heat exchange channel 11 is larger than the flow area of ​​either the third heat exchange channel 212 or either the flow area of ​​either the fourth heat exchange channel 221, thereby stabilizing the heat exchange and keeping the pressure drop within a reasonable range.

[0040] As the refrigerant flows to the outlet stage, the degree of dryness of the refrigerant increases, and the mass of the refrigerant in the gas phase becomes much larger than the mass of the refrigerant in the liquid phase. This reduces the flow area of ​​the third heat exchange channel 212 and the fourth heat exchange channel 221, significantly increasing the refrigerant flow velocity in the pipe. In response to this, more refrigerant branch channels are formed, increasing the number of channels and preventing excessive pressure drop of the refrigerant while ensuring heat exchange efficiency.

[0041] Based on the heat exchange apparatus 100 of the embodiment according to the present invention, the flow area of ​​any one of the plurality of first heat exchange channels 11 is made larger than the flow area of ​​any one of the plurality of third heat exchange channels 212 and larger than the flow area of ​​any one of the plurality of fourth heat exchange channels 221, and the flow area of ​​any one of the plurality of second heat exchange channels 211 is made larger than the flow area of ​​any one of the plurality of third heat exchange channels 212 and larger than the flow area of ​​any one of the plurality of fourth heat exchange channels 221, thereby, on the one hand, the number of heat exchange tubes in each heat exchange section is fixed To address this, it is possible to connect the flow paths using multiple connection methods, but without cross-piping occurring with each connection method, and on the other hand, the number of heat exchange tubes is appropriate to the dryness of the refrigerant, reducing the number of branched flow paths by placing fewer heat exchange tubes in areas with low dryness and increasing the number of branched flow paths by placing more heat exchange tubes in areas with high dryness, thereby taking into consideration the issues of heat exchange efficiency and pressure drop, ensuring that the pressure drop in each area of ​​the heat exchange device 100 does not become excessively large, and that the heat exchange efficiency is high and the heat exchange effect is good.

[0042] Based on several embodiments of the present invention, A1, A2, A3, and A4 further satisfy 2.17 ≤ A1 / A2 ≤ 5.67, 2.5 ≤ A3 / A2 ≤ 3.33, 0.75 ≤ A3 / A4 ≤ 2, and 0.8 ≤ (A1 A2) / (A3 A4) ≤ 2.22.

[0043] Referring to Tables 1-4, and according to the first to fourth test tables, different stages of the refrigerant flow path can be adapted to the number of heat exchange tubes, thereby improving heat exchange performance.

[0044] [Table 1]

[0045] Table 1 shows the energy efficiency table of the heat exchanger 100 for different A1 / A2 values, assuming that the A3 / A2 value is 2.8 and the A3 / A4 value is 1.5. Preferably, the energy efficiency of the heat exchanger 100 is higher when the A1 / A2 value is 2.5.

[0046] [Table 2]

[0047] Table 2 shows the energy efficiency of the heat exchanger 100 for different A3 / A2 values, assuming that the A1 / A2 value is 2.5 and the A3 / A4 value is 1.5. Preferably, the energy efficiency of the heat exchanger 100 is higher when the A3 / A2 value is 2.9.

[0048] [Table 3]

[0049] Table 3 shows the energy efficiency table of the heat exchanger 100 for different A3 / A4 values, assuming that the A1 / A2 value is 2.5 and the A3 / A2 value is 2.9. Preferably, the energy efficiency of the heat exchanger 100 is higher when the A3 / A4 value is 1.4.

[0050] [Table 4]

[0051] Table 4 shows the energy efficiency of the heat exchanger 100 for different values ​​of (A1+A2) / (A3+A4). Preferably, the energy efficiency of the heat exchanger 100 is higher when the value of (A1+A2) / (A3+A4) is 1.5.

[0052] As shown in Figure 1-4, the flow area of ​​the heat exchange tubes within each heat exchange section can affect the heat exchange performance of the heat exchange device 100. However, the limitations on the ratio relationship based on the present invention allow for a more rational number of heat exchange tubes in the inlet, intermediate, and outlet stages of the refrigerant flow path. By reducing the flow velocity and correspondingly decreasing the number of heat exchangers in areas with low dryness, and increasing the flow velocity and correspondingly increasing the number of heat exchangers in areas with high dryness, the energy efficiency of the heat exchange device 100 can be increased, and the heat exchange efficiency can be raised by up to 35%.

[0053] If the flow area of ​​each first heat exchange channel 11 is made larger than the flow area of ​​the third heat exchange channel 212 and the fourth heat exchange channel 221, the flow area of ​​each second heat exchange channel 211 is made larger than the flow area of ​​the third heat exchange channel 212 and the fourth heat exchange channel 221, the flow areas of the first heat exchange channel 11 and the second heat exchange channel 211 are made relatively larger, and the following conditions are met: 2.17≦A1 / A2≦5.67, 2.5≦A3 / A2≦3.33, 2.5≦A3 / A2≦3.33, 0.75≦A3 / A4≦2, and 0.8≦(A1 A2) / (A3 A4)≦2.22, then the number and arrangement of the first, second, third, and fourth heat exchange tubes are generally limited.

[0054] As shown in Figure 3-6, in the present invention, the relationship between the flow area of ​​any one of the multiple first heat exchange channels 11, multiple second heat exchange channels 211, multiple third heat exchange channels 212, and multiple fourth heat exchange channels 221 is limited, and the ratio relationship of the total flow area between the first heat exchange channel 11 and the second heat exchange channel 211, the ratio relationship of the total flow area between the second heat exchange channel 211 and the third heat exchange channel 212, the ratio relationship of the total flow area between the third heat exchange channel and the fourth heat exchange channel 221, and the first heat exchange channel 11 and the second heat exchange channel 221 are limited, and the ratio relationship of the total flow area between third heat exchange channel and the fourth heat exchange channel 221, and the ratio relationship of the total flow area between the first heat exchange channel 11 and the second heat exchange channel 221 By further limiting the ratio between the total flow area of ​​the heat exchange channel 211 and the total flow area of ​​the third heat exchange channel 212 and the fourth heat exchange channel 221, it becomes possible to limit the number of heat exchange tubes in the first heat exchange section a, the second heat exchange section b, the third heat exchange section c, and the fourth heat exchange section d. Once the number of heat exchange tubes in each heat exchange section is determined, various heat exchange tube connection methods can be formed accordingly, and arrangements corresponding to each connection method ensure that no cross-piping exists.

[0055] Referring to Figure 3, this is a feasible first flow path arrangement according to the present invention.

[0056] On the air-blowing side of the second heat exchange section b, the first row of second heat exchange tubes forms the first set, the two second heat exchange tubes at the upper ends of the second and third rows form the second set, and the two second heat exchange tubes at the lower ends of the second and third rows form the third set.

[0057] On the air-blowing side of the first heat exchange section a, the six first heat exchange tubes at the upper end of the first row form the fourth set, the four first heat exchange tubes at the lower end of the first row on the air-blowing side and the two first heat exchange tubes at the lower ends of the second and third rows form the fifth set, the two first heat exchange tubes at the upper end of the second row and the six first heat exchange tubes at the upper end of the third row form the sixth set, and the six first heat exchange tubes in the middle of the second row and the two first heat exchange tubes in the middle of the third row form the seventh set.

[0058] On the air-blowing side of the third heat exchange section c, the eighth set is formed by the two third heat exchange tubes at the top of the first row, the three third heat exchange tubes at the top of the second row, and the three third heat exchange tubes at the top of the third row, and the ninth set is formed by the third and fourth third heat exchange tubes in the first row, the fourth and fifth third third heat exchange tubes in the second row, and the third to sixth third third heat exchange tubes in the third row.

[0059] The first three fourth heat exchange tubes at the top of the third row on the air-inlet side of the fourth heat exchange section d and the fifth and sixth third heat exchange tubes in the first row, sixth and seventh third row, and seventh third row of the third heat exchange section c form the tenth set. The first two fourth heat exchange tubes at the top of the first row on the air-inlet side of the fourth heat exchange section d, the first three in the second row, and the fourth fourth heat exchange tube in the third row and the two third heat exchange tubes at the bottom of the first row of the third heat exchange section c form the eleventh set. The fifth to seventh fourth heat exchange tubes in the first row, fourth to sixth fourth row, and fifth to sixth third row of the fourth heat exchange section form the twelfth set. The four heat exchangers at the bottom of the first row, two at the bottom of the second row, and two at the bottom of the third row form the thirteenth set. By sequentially connecting multiple heat exchangers within each set, one end of each set becomes a refrigerant inlet and the other end becomes a refrigerant outlet.

[0060] The specific flow path is as follows: The refrigerant flows in through the first set of refrigerant inlets and out through the first set of refrigerant outlets, and also flows in through the fourth set of refrigerant inlets and out through the fourth set of refrigerant outlets. Subsequently, it splits into two paths, each flowing into the second and third sets of refrigerant inlets and merging at the second and third sets of refrigerant outlets. The outflowing refrigerant then splits into three paths, each flowing into the fifth to seventh sets of refrigerant inlets. The refrigerant that merges at the fifth to seventh sets of refrigerant outlets then splits into six paths, each flowing into the eighth to thirteenth sets of refrigerant inlets. The refrigerant that flows out from the eighth to thirteenth sets of refrigerant outlets merges and returns to the compressor.

[0061] This allows for a rational arrangement of the flow path by determining the number and arrangement of heat exchange pipes from the first heat exchange section a to the fourth heat exchange section d, enabling the refrigerant to flow sequentially and eliminating the need for cross-piping.

[0062] Referring to Figures 4-6, Figure 4 shows the second flow path configuration, Figure 5 shows the third flow path configuration, and Figure 6 shows the fourth flow path configuration. These configurations differ from the first flow path configuration in that, even though the method of grouping the multiple heat exchange tubes is different, the refrigerant flows into the second heat exchange section b, merges inside the third heat exchange section c and the fourth heat exchange section d, and is discharged, thereby allowing the number of refrigerant branching flow paths to be adjusted at the inlet, intermediate, and outlet stages. For example, Figure 3 corresponds to the changing trend of refrigerant branching flow paths 1-2-3-6, and there are no crossing pipes in this configuration. No further description is provided in this invention.

[0063] In the inlet stage of the flow path (corresponding to the presence of the first and fourth sets of refrigerants), the degree of dryness of the refrigerant is low, the mass of the liquid phase refrigerant is greater than the mass of the gaseous phase refrigerant, the refrigerant flow velocity in the pipe is relatively low, the number of first and second heat exchange tubes is relatively small, and by forming only one refrigerant branch flow path, the refrigerant flow velocity in the inlet stage can be increased, thereby improving the heat exchange coefficient.

[0064] As the refrigerant flows through the intermediate stages (corresponding to the refrigerant being in sets 2-3 and 5-7), the degree of dryness of the refrigerant gradually increases, the mass of the refrigerant in the gas phase gradually becomes greater than the mass of the refrigerant in the liquid phase, the refrigerant flow velocity in the pipe gradually increases, and the number of refrigerant branching channels increases from two to three. This allows for stable heat exchange and keeps the pressure drop within a reasonable range.

[0065] When the refrigerant flows to the outlet stage (corresponding to the refrigerant being in sets 8-13), the degree of refrigerant dryness increases, the mass of the refrigerant in the gas phase becomes much larger than the mass of the refrigerant in the liquid phase, and the refrigerant flow velocity in the pipe increases significantly. In response to this, six branched refrigerant flow paths are formed, increasing the number of flow paths and preventing excessive pressure drop in the refrigerant while ensuring heat exchange efficiency.

[0066] Based on the heat exchange apparatus 100 of the embodiment according to the present invention, the flow area of ​​any one of the plurality of first heat exchange channels 11 is made larger than the flow area of ​​any one of the plurality of third heat exchange channels 212 and larger than the flow area of ​​any one of the plurality of fourth heat exchange channels 221, the flow area of ​​any one of the plurality of second heat exchange channels 211 is made larger than the flow area of ​​any one of the plurality of third heat exchange channels 212 and larger than the flow area of ​​any one of the plurality of fourth heat exchange channels 221, and 2.17≦A1 / A2≦5.67, 2.5≦A3 / A2≦3.33, 0.75≦A3 / A4≦2 and 0.8≦(A1+A2) / (A3+A4 By satisfying ) ≤ 2.22, on the one hand, the number of heat exchange tubes in each heat exchange section is determined, and correspondingly, there is a possibility of connecting the flow paths using multiple connection methods, but no cross-piping occurs with each connection method, and on the other hand, the number of heat exchange tubes is appropriate to the dryness of the refrigerant, reducing the number of branched flow paths by placing fewer heat exchange tubes in areas with low dryness and increasing the number of branched flow paths by placing more heat exchange tubes in areas with high dryness, thereby taking into consideration the issues of heat exchange efficiency and pressure drop, and ensuring that the pressure drop in each section of the heat exchange device 100 does not become excessively large, and that the heat exchange efficiency is high and the heat exchange effect is good.

[0067] In current technology, the heat exchange efficiency of the heat exchange device 100 is not sufficient to meet the usage requirements. Therefore, a rear pipe is usually installed on the air injection side of the front heat exchanger 20 and the rear heat exchanger 10 to increase heat dissipation via the rear. However, the heat exchange device 100 of the present invention has high heat exchange efficiency, and the usage requirements are met even without the installation of a rear pipe.

[0068] Based on several embodiments of the present invention, the flow area of ​​any one of the plurality of first heat exchange channels 11 is the same as the flow area of ​​any one of the plurality of second heat exchange channels 211, and / or the flow area of ​​any one of the plurality of third heat exchange channels 212 is the same as the flow area of ​​any one of the plurality of fourth heat exchange channels 221.

[0069] In some implementations, the flow area of ​​any one of the multiple first heat exchange channels 11 is the same as the flow area of ​​any one of the multiple second heat exchange channels 211, and in some implementations, the flow area of ​​any one of the multiple third heat exchange channels 212 is the same as the flow area of ​​any one of the multiple fourth heat exchange channels 221. Preferably, the flow area of ​​any one of the multiple first heat exchange channels 11 is the same as the flow area of ​​any one of the multiple second heat exchange channels 211, and the flow area of ​​any one of the multiple third heat exchange channels 212 is the same as the flow area of ​​any one of the multiple fourth heat exchange channels 221.

[0070] Therefore, the first heat exchange tube forming the first heat exchange channel 11 and the second heat exchange tube forming the second heat exchange channel 211 can be selected as heat exchange tubes of the same standard size, and the third heat exchange tube forming the third heat exchange channel 212 and the fourth heat exchange tube forming the fourth heat exchange channel 221 can also be selected as heat exchange tubes of the same standard size. Using only two types of heat exchange tubes of the same standard (for example, copper tubes) is advantageous for standardization, and it is possible to reduce assembly costs and improve assembly efficiency.

[0071] As shown in Figure 2, in some implementations, the heat exchanger 100 is a fin-tube heat exchanger, where the heat exchange tubes define the contours of the corresponding heat exchange channels, with multiple first heat exchange channels 11 having the same or different specifications and diameters of 5mm to 7mm, multiple second heat exchange channels 211 having the same or different specifications and diameters of 5mm to 7mm, multiple third heat exchange channels 212 having the same or different specifications and diameters of 4mm to 6.5mm, and multiple fourth heat exchange channels 221 having the same or different specifications and diameters of 4mm to 6.5mm.

[0072] The first heat exchange tube in the first heat exchange section a and the second heat exchange tube in the second heat exchange section b correspond to diameters D1 and D2, respectively. The diameter of the first and second rows of heat exchange tubes on the air-blowing side of the third heat exchange section c and the fourth heat exchange section d is D3, and the diameter of the third row of heat exchange tubes on the air-blowing side of the third heat exchange section c and the fourth heat exchange section d is D4.

[0073] The first heat exchange channel 11 and the second heat exchange channel 211 are located at the inlet stage of the refrigerant flow path, where the degree of dryness of the refrigerant is low and the flow velocity is low. When the pipe diameter becomes small and the pressure drop changes significantly, the pipe diameter can be increased to balance the pressure drop. However, reducing the number of heat exchange tubes leads to a shortage of heat exchange surface area within the tubes, which is detrimental to improving heat exchange efficiency. Therefore, by using heat exchange tubes with a large pipe diameter and reducing the number of heat exchange tubes in this invention, the heat exchange surface area within the tubes is increased, and the number of refrigerant branch channels at the inlet stage is reduced, thereby achieving improved heat exchange.

[0074] Referring to Figure 7, which shows the effect of heat exchange tubes of different diameters at a dryness of 0.3 on the heat exchange efficiency of the heat exchange device 100, the optimal values ​​for D1 and D2 are 6.35 mm.

[0075] When the third heat exchange channel 212 and the fourth heat exchange channel 221 are in the intermediate and outlet stages of the refrigerant flow path, the degree of dryness gradually increases and the flow velocity gradually increases. If a large pipe diameter is used, the number of heat exchange tubes in the area decreases, which leads to a shortage of heat exchange area within the tubes. To ensure the stability of heat exchange within the area, it is necessary to use a larger number of heat exchange tubes with smaller pipe diameters, thereby increasing the heat exchange area. In addition, the heat exchange coefficient can be increased by using smaller pipe diameters, but the pressure drop is large, so the number of refrigerant branch channels is further increased to balance the pressure drop.

[0076] Referring to Figure 8, which shows the effect of heat exchange tubes of different diameters at a dryness of 0.6 on the heat exchange efficiency of the heat exchanger 100, the optimal values ​​for D3 and D4 are 5 mm according to Figure 8. This allows for the refrigerant flow path stages corresponding to different heat exchange sections to be matched with heat exchange tubes of appropriate diameters, taking into account both heat exchange efficiency and pressure loss.

[0077] As shown in Figure 2, in some embodiments of the present invention, the third heat exchange section c is smoothly connected to the fourth heat exchange section d via a curved portion, and in the cross-section of the heat exchange device 100, the longitudinal direction of the first heat exchange section a extends linearly and has a length L1, the longitudinal direction of the second heat exchange section b extends linearly and has a length L2, the linearly extending length of the third heat exchange section c in the longitudinal direction is L31 and the curved extending length is L32, the linearly extending length of the fourth heat exchange section d in the longitudinal direction is L41 and the curved extending length is L42, and each of the above lengths satisfies 1.85 ≤ L1 / L2 ≤ 3.56, 1.1 ≤ (L31 + L32) / L2 ≤ 2.2 and 0.7 ≤ (L31 + L32) / (L41 + L42) ≤ 1.9.

[0078] In this invention, the ratio relationship between the length of the first heat exchange section a and the length of the second heat exchange section b, the ratio relationship between the length of the second heat exchange section b and the length of the third heat exchange section c, and the ratio relationship between the length of the third heat exchange section c and the length of the fourth heat exchange section d are further defined.

[0079] Referring to Tables 5-7, and according to Test Tables 5 through 7, the different lengths of each heat exchange section can be adapted to different stages of the refrigerant flow path and to the number of heat exchange tubes, thereby improving heat exchange performance.

[0080] [Table 5]

[0081] Table 5 shows the energy efficiency of the heat exchanger 100 for different L1 / L2 values, assuming that the value of (L31 + L32) / L2 is 1.28 and the value of (L31 + L32) / (L41 + L42) is 1.08. Preferably, the energy efficiency of the heat exchanger 100 is higher when the L1 / L2 value is 2.8.

[0082] [Table 6]

[0083] Table 6 shows the energy efficiency of the heat exchanger 100 for different values ​​of (L31+L32) / L2, assuming that the value of L1 / L2 is 2.64 and the value of (L31+L32) / (L41+L42) is 1.08. Preferably, the energy efficiency of the heat exchanger 100 is higher when the value of (L31+L32) / L2 is 1.7.

[0084] [Table 7]

[0085] Table 7 shows the energy efficiency table of the heat exchanger 100 for different values ​​of (L31+L32) / (L41+L42), assuming that the value of L1 / L2 is 2.64 and the value of (L31+L32) / L2 is 1.36. Preferably, the energy efficiency of the heat exchanger 100 is higher when the value of ((L31+L32) / (L41+L42)) is 1.1.

[0086] According to Table 5-7, by rationally reducing the lengths of the first heat exchange section a, the second heat exchange section b, the third heat exchange section c, and the fourth heat exchange section d, the airflow distribution of the heat exchange device 100 can be improved, resulting in a more uniform airflow distribution, improved uniformity of flow velocity, and further enhancement of heat exchange efficiency and heat exchange effect.

[0087] In the embodiment shown in Figure 2, in the cross-section of the heat exchanger 100, the width of the first heat exchange section a is represented by B1, the width of the second heat exchange section b is represented by B2, and the width of the third heat exchange section c is represented by B3, and B1, B2, and B3 satisfy 2.85 ≤ L1 / B1 ≤ 5.14, 1.23 ≤ L2 / B2 ≤ 1.94, and 1.5 ≤ L41 / B3 ≤ 2.44.

[0088] The present invention further limits the aspect ratio of the first heat exchange section a, the aspect ratio of the second heat exchange section b, and the aspect ratio of the third heat exchange section c.

[0089] Referring to Tables 8-10, and according to Test Tables 8 through 10, by rationally controlling the aspect ratio of each heat exchange section, the airflow can be stabilized and the air velocity distribution can be improved.

[0090] [Table 8]

[0091] Table 8 shows the energy efficiency of the heat exchanger 100 at different L1 / B1 values, assuming that the L2 / B2 value is 1.6 and the L41 / B3 value is 2.08. Preferably, the energy efficiency of the heat exchanger 100 is higher when the L1 / B1 value is 4.4.

[0092] [Table 9]

[0093] Table 9 shows the energy efficiency table of the heat exchanger 100 at different L2 / B2 values, assuming that the L1 / L2 value is 4.4 and the L41 / B3 value is 2.08. Preferably, the energy efficiency of the heat exchanger 100 is higher when the L2 / B2 value is 1.6.

[0094] [Table 10]

[0095] Table 10 shows the energy efficiency table of the heat exchanger 100 for different values ​​of (L31+L32) / (L41+L42), assuming that the value of L1 / L2 is 2.64 and the value of (L31+L32) / L2 is 1.36. Preferably, the energy efficiency of the heat exchanger 100 is higher when the value of (L31+L32) / (L41+L42) is 1.1.

[0096] As shown in Figure 8-10, by appropriately limiting the aspect ratio of the first heat exchange section a, the second heat exchange section b, the third heat exchange section c, and the fourth heat exchange section d, the airflow distribution of the heat exchange device 100 can be improved, the airflow rate and wind speed distribution can be stabilized, and the overall structure of the device can be optimized, further enhancing the heat exchange efficiency and heat exchange effect.

[0097] In some implementations, B1=B2=B3, meaning the widths of the first heat exchange section a, the second heat exchange section b, the third heat exchange section c, and the fourth heat exchange section d are the same, which is convenient for connecting the front heat exchanger 20 to the rear heat exchanger 10.

[0098] As shown in Figure 2, in some embodiments of the present invention, the heat exchanger 100 is a finned tube heat exchanger, where the fins of the front upper heat exchange segment 21 and the fins of the front lower heat exchange segment 22 are different parts of the same fin, and the fins of the rear heat exchanger 10 and the fins of the front heat exchanger 20 are two divided parts of a single fin.

[0099] The fins of the forward heat exchanger 20 are defined as the first stage, and the fins of the rear heat exchanger 10 are defined as the second stage. Multiple first stages and multiple second stages are integrated, and through a single cut (cutting off the excess portion between the first and second stages), multiple first parts having the same shape as the outer contour of the first stage and multiple second parts having the same shape as the outer contour of the second stage are obtained. The first parts can be connected to or separated from the second parts. Multiple first parts are arranged sequentially, multiple second parts are arranged sequentially, and then two cuts are performed (separating adjacent first stages and adjacent second stages) to obtain multiple first and second stages that are either separated or connected. The first stages are connected to the second stages by connection methods such as angle adjustment or overlapping joints, and the heat exchanger 100 can be directly obtained by overlapping the connected multiple first and second stages along the overlapping direction.

[0100] By integrally molding the forward heat exchanger 20 and the rear heat exchanger 10, and cutting and slicing a single large fin plate, it becomes possible to obtain multiple heat exchange fins, including the first and second stages. By stacking these multiple heat exchange fins and passing them through the heat exchange tube, the heat exchange device 100 can be obtained, reducing the difficulty of processing and increasing processing efficiency.

[0101] Furthermore, when multiple heat exchange sections of the same width are cut from a single large fin sheet, the utilization rate of flat surfaces increases, reducing waste and lowering material costs.

[0102] As shown in Figure 2, in some implementations, the heat exchanger 100 is a fin-tube type heat exchanger, with multiple rows of tube assemblies arranged along the width direction of the fins on the first heat exchange section a, the second heat exchange section b, the third heat exchange section c, and the fourth heat exchange section d, respectively, and each row of tube assemblies includes multiple heat exchange tubes arranged along the longitudinal direction of the fins, the heat exchange tubes defining the contour of a corresponding heat exchange flow path, and a gap assembly e is installed between each pair of adjacent heat exchange tubes along the longitudinal direction of the fins.

[0103] By providing a gap assembly e on the fins, the heat exchange area of ​​the fins can be increased, thereby improving heat exchange efficiency. Furthermore, by positioning the gap assembly e close to the heat exchange tube, it is possible to guide a portion of the airflow into the heat exchange tube, thereby further improving heat exchange efficiency.

[0104] As shown in Figures 9-12, Figure 9 shows a bridge-type gap structure, specifically, a bridge piece a1 is installed in the perforation area, with both ends connected to the perforation b1 in the longitudinal direction, and a gap structure with spaced fins is installed in other areas. Figures 10-11 show a single-window type gap structure, specifically, a single-window type gap structure is installed in the perforation area, with one end connected to the perforation b1 and the other end extending away from the perforation b1. Figure 12 shows a bidirectional louver gap structure, specifically, two sets of louvers facing each other are arranged in the perforation area, and the shield pieces c1 (i.e., leaf pieces) of the two sets of louvers are installed facing each other. The modified structure in Figure 12 may also include a unidirectional louver gap structure with only one set of louvers. In any case, the heat exchange area of ​​the fins can be effectively increased. Of course, the gap structures of the present invention are not limited to these, and it is possible to install further gap structures such as protruding rectangular blocks, and the present invention does not impose any specific limitations on this.

[0105] As shown in Figure 2, multiple sets of heat exchange tubes are arranged, and these sets of heat exchange tubes are sequentially stacked in the thickness direction of the front heat exchanger 20 and the thickness direction of the rear heat exchanger 10, but the airflow flows from one side to the other of the width of the front heat exchanger 20. One side corresponding to the front heat exchanger 20 is the air inlet surface, and the other side is the air outlet surface. The upstream pipe assembly refers to the pipe assembly that approaches the air inlet surface, and the downstream pipe assembly refers to the pipe assembly that approaches the air outlet surface.

[0106] In two adjacent rows of heat exchange tube assemblies within the forward heat exchanger 20, the number of gaps in at least one gap assembly e within the upstream tube assembly is not less than the number of gaps in any one gap assembly e within the downstream tube assembly within the forward heat exchanger 20. In addition, the width of at least one gap assembly e within the upstream tube assembly is not less than the width of any one gap assembly e within the downstream tube assembly within the forward heat exchanger 20. In the airflow direction, a high gas flow velocity and a large number of gaps on the air inlet side can increase heat exchange efficiency, while a low gas flow velocity on the air outlet side and a larger gap structure width in the downstream tube assembly can reduce wind resistance and increase airflow, thereby also increasing heat exchange efficiency.

[0107] Similarly, the rear heat exchanger 10 has a rear upper heat exchange segment 12 and a rear lower heat exchange segment 13, and the width of at least one gap assembly e in the rear upper heat exchange segment 12 is smaller than the width of at least one gap assembly e in the rear lower heat exchange segment 13, thereby increasing the heat exchange efficiency and heat exchange effect.

[0108] For example, the gap assembly e on the rear upper heat exchange segment 12 has 2-4 gaps, and the gap assembly e on the rear lower heat exchange segment 13 has 2-3 gaps, with the widths of the gaps being H1 and H2 respectively, satisfying the ratio relationship 1 ≤ H1 / H2 ≤ 1.2. This arrangement increases the number of temporary cuts between the gap assemblies e corresponding to the heat exchange tube assemblies in each row, thereby reducing reverse heat conduction through the fins.

[0109] As shown in Figure 2, in some implementations, at least three types of gap assemblies e are installed at the upper end of the rear heat exchanger 10 and / or at least three types of gap assemblies e are installed at the upper end of the front heat exchanger 20, and at least one parameter of the width, gap length, number of gaps, and gap direction of the different types of gap assemblies e is different.

[0110] Specifically, the rear heat exchanger 10 and / or the front heat exchanger 20 may be equipped with multiple gap assemblies e as shown in Figure 9-12. The width, number of gaps, gap length, and gap direction of the multiple gap assemblies e may differ, thereby enhancing heat exchange in different areas. In addition, the gap structure can improve airflow uniformity and guide the airflow to the heat exchange tubes through a guided gap structure. This allows airflow from areas with fewer heat exchange tubes to areas with more heat exchange tubes, further enhancing heat exchange and improving heat exchange efficiency.

[0111] Because there are few heat exchange tubes in the area connecting the front heat exchanger 20 to the rear heat exchanger 10, a gap structure can be installed to increase the heat exchange area, and a gap assembly e that guides the airflow can be provided to enhance heat dissipation.

[0112] A through-flow air passage is installed between the rear heat exchanger 10 and the front heat exchanger 20. A groove 14 is provided in a portion of the front side of the rear heat exchanger 10, and at least a portion of the groove 14 faces the rear volute tongue 210 of the through-flow air passage. The rear volute tongue 210 and the front and rear volute tongues 220 define the contour of the air passage inlet of the through-flow air passage.

[0113] By providing grooves 14 on the rear heat exchanger 10, and having the grooves 14 face at least a portion of the rear volute tongues 210, wind resistance is effectively reduced, increasing the intake volume of the rear heat exchanger 10, improving the heat exchange effect and heat exchange efficiency, and making the overall blown air more uniform and the wind speed distribution more uniform.

[0114] In some embodiments of the present invention, a plurality of gap assemblies e are arranged at the connection portion between the forward upper heat exchange segment 21 and the forward lower heat exchange segment 22, the gap assembly located on the air injection side among the plurality of gap assemblies e is the outer assembly, at least one of the outer assemblies forms a fixed assembly, the fixed assembly has one gap structure or a plurality of gap structures arranged along the airflow direction, and in any two adjacent gap structures of the fixed assembly, the gap length of the downstream gap structure is not smaller than the gap length of the upstream gap structure.

[0115] Multiple gap assemblies e are arranged at the connection point between the forward upper heat exchange segment 21 and the forward lower heat exchange segment 22. Among the multiple gap assemblies e, the gap assembly located on the air injection side of the fin 10 is the outer assembly, and at least one of the outer assemblies forms a fixed assembly. The fixed assembly has one gap structure or multiple gap structures arranged along the airflow direction, and in any two adjacent gap structures of the fixed assembly, the gap length of the downstream gap structure is not smaller than the gap length of the upstream gap structure.

[0116] The upper heat exchange segment and the lower heat exchange segment are at an acute angle, and one end of the front upper heat exchange segment 21 is connected to one end of the front lower heat exchange segment 22. The connected area (i.e., the connection part) forms an arc shape, and a gap assembly e is installed in the arc shape, thereby increasing the heat exchange area of ​​the connection part via the gap assembly e and enhancing the heat exchange effect.

[0117] The airflow flows from one side of the heat exchanger 100 to the other side, and a gap assembly e corresponding to the air injection side is installed on the corresponding fin. These gap assemblies e are defined as outer assemblies, and there is a possibility of arranging multiple outer assemblies, and each outer assembly may contain multiple gap structures. The gap structures of the multiple outer assemblies may be the same or different (for example, a bridge-type gap structure or a louver gap structure). At least one of the multiple outer assemblies is a fixed assembly, and the fixed assembly utilizes a gap structure, and the structures of the other outer assemblies not defined as fixed assemblies in the gap structure area may be the same or different.

[0118] The anchoring assembly may include multiple gap structures arranged along the direction of airflow, and these gap structures, for example, two, three, or four gap structures, are arranged sequentially from the air inlet side to the air outlet side. Among the multiple gap structures, the gap structures on the air inlet side that are relatively close are upstream gap structures, and the gap structures on the air inlet side that are relatively far apart are downstream gap structures, so that the gap length of the downstream gap structures is not smaller than the gap length of the upstream gap structures. In the airflow direction, the gap length increases as the substrate flow velocity decreases, thereby reducing wind resistance, increasing airflow, and improving heat exchange efficiency.

[0119] In any two adjacent gap structures, the gap length of the downstream gap structure is not smaller than the gap length of the upstream gap structure, which means that the anchoring assembly may contain two gap structures, where the gap length of the upstream gap structure is not larger than the gap length of the downstream gap structure; or the anchoring assembly may contain three gap structures, where the gap lengths of the two upstream gap structures are equal, but the gap length of the one downstream gap structure is larger than the gap lengths of the two upstream gap structures; or the anchoring assembly may contain three gap structures, where the gap lengths of the two downstream gap structures are equal, but the gap length of the one upstream gap structure is smaller than the gap lengths of the two downstream gap structures; or the anchoring assembly may contain three gap structures, where the gap lengths of the three gap structures gradually increase along the airflow direction.

[0120] By installing a fixed assembly and ensuring that the gap length of the downstream gap structure is not smaller than the gap length of the upstream gap structure in two adjacent gap structures within the fixed assembly, and by reducing the number of gap structures at the connection point in the airflow direction or increasing the gap length of the gap structures, the wind resistance at the connection point is improved, the airflow rate is increased, and the heat exchange effect is enhanced.

[0121] As shown in Figure 1, the air conditioning indoor unit 1000 according to the second embodiment of the present invention comprises a housing 300, a blower 200, and a heat exchanger 100, with an air inlet provided at the top of the housing 300, the blower 200 installed inside the housing 300, and having an air passage member and a cross-flow impeller 230, the cross-flow impeller 230 installed at the air passage inlet of the air passage member, and the heat exchanger 100 arranged inside the housing 300 and located between the air inlet and the blower 200.

[0122] When an air conditioning indoor unit 1000 according to an embodiment of the present invention is placed in the corner of a wall or mounted on a wall inside a room, in the horizontal direction, the direction approaching the wall is defined as the rear, and the direction away from the wall is defined as the front. In the vertical direction, the direction towards the top of the housing 300 is defined as the up, and the direction towards the bottom of the housing 300 is defined as the down. When the cross-flow impeller 230 is used as a wind turbine structure, the heat exchanger 100 is arranged around the cross-flow impeller 230, and the negative pressure generated by the rotation of the cross-flow impeller 230 disrupts the airflow and is drawn into the housing 300. The airflow then passes through the heat exchanger 100, performs sufficient heat exchange with the heat exchanger 100, and is discharged from the air passage outlet, thereby performing heat exchange in the indoor space (for example, cooling or heating).

[0123] In the embodiment of the present invention, the indoor air conditioning unit 1000 utilizes the above-mentioned heat exchanger, reducing wind resistance in the curved portion of the heat exchanger surrounding the blower 200. This increases the heat exchange efficiency and heat exchange effect, potentially raising the overall heat exchange efficiency by 35%, and improving the energy efficiency of the indoor air conditioning unit 1000.

[0124] The diameter of the cross-flow impeller 230 is D, and the maximum width of the housing 300 in the front-to-back direction is W. By satisfying 2.6 ≤ W / D ≤ 3.7, the airflow effect of the cross-flow impeller 230 is improved, the amount of air blown in is increased, and the heat exchange effect is enhanced.

[0125] In the description of this application, terms such as "center," "vertical," "horizontal," "length," "thickness," "width," "top," "bottom," "front," "back," "left," "right," "vertical," "horizontal," "top," "bottom," "inside," "outside," "axial direction," "radial direction," and "circumferential direction" represent directions or positional relationships based on the directions or positional relationships shown in the drawings. These terms are merely for convenience and simplification of the description of this application and do not explicitly or implicitly suggest that the mentioned devices or elements must be located in a particular direction or be made up or operate according to a particular direction. It is important to understand that these terms should not be interpreted as limitations on the scope of protection of the present invention.

[0126] Terms such as "first" and "second" are used solely for descriptive purposes and should not be understood as explicitly or implicitly indicating relative importance or suggesting the number of technical features. Therefore, technical features limited by "first" and "second" may explicitly or implicitly include one or more such features. In the description of this invention, unless otherwise specified, "multiple" means two or more.

[0127] In this application, unless otherwise specified or limited, terms such as “attach,” “connect,” and “fix” should be interpreted broadly, including, for example, fixing permanently, removably, integrally, directly, indirectly through an intermediate medium, or referring to internal communication between two elements or the interrelationship between two elements. A person skilled in the art will be able to understand the specific meaning of the above terms in this application depending on the particular circumstances.

[0128] In this invention, unless otherwise specified, if the first feature is located "above" or "below" the second feature, the first feature may directly contact the second feature, or the first feature may indirectly contact the second feature via an intermediate medium. Furthermore, if the first feature is located "above," "above," and "above" the second feature, the first feature may be located directly above or diagonally above the second feature, or the height of the first feature may be greater than that of the second feature. If the first feature is located "above," "below," and "below" the second feature, the first feature may be located directly below or diagonally below the second feature, or the height of the first feature may be lower than that of the second feature.

[0129] In this specification, descriptions such as “one embodiment,” “several embodiments,” “exemplary embodiments,” “examples,” “specific examples,” and “several examples” mean that the specific features, structures, materials, or properties described in the embodiment or example are grouped together in at least one embodiment or example of the present application. In this specification, the exemplary descriptions using the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or properties described may be combined in any one or more embodiments or examples through appropriate means.

[0130] Notwithstanding the descriptions and representations of embodiments of this application, those skilled in the art will understand that various modifications, alterations, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of this application, and that the scope of this application is limited by the claims and their equivalents.

Claims

1. It is equipped with a rear heat exchanger and a front heat exchanger, The rear heat exchanger is inclined from top to bottom and extends to the rear, and the rear heat exchanger is the first heat exchange section. The forward heat exchanger has a forward upper heat exchange segment and a forward lower heat exchange segment, the forward upper heat exchange segment extends forward inclined from top to bottom and the upper end of the forward upper heat exchange segment is connected to the upper end of the rear heat exchanger, the forward lower heat exchange segment is connected to the lower end of the forward upper heat exchange segment and extends rearward inclined from top to bottom, the forward upper heat exchange segment is divided into a second heat exchange section and a third heat exchange section located below the second heat exchange section, and the forward lower heat exchange segment is a fourth heat exchange section. The first heat exchange section is provided with a plurality of first heat exchange channels, the sum of the flow areas of the plurality of first heat exchange channels is A1; the second heat exchange section is provided with a plurality of second heat exchange channels, the sum of the flow areas of the plurality of second heat exchange channels is A2; the third heat exchange section is provided with a plurality of third heat exchange channels, the sum of the flow areas of the plurality of third heat exchange channels is A3; the fourth heat exchange section is provided with a plurality of fourth heat exchange channels, the sum of the flow areas of the plurality of fourth heat exchange channels is A4; the flow area of ​​any one of the first heat exchange channels is greater than the flow area of ​​any one of the third heat exchange channels and greater than the flow area of ​​any one of the fourth heat exchange channels; the flow area of ​​any one of the second heat exchange channels is greater than the flow area of ​​any one of the third heat exchange channels and greater than the flow area of ​​any one of the fourth heat exchange channels; A heat exchange device characterized by the following features.

2. 2.17 ≤ A1 / A2 ≤ 5.67, 2.5 ≤ A3 / A2 ≤ 3.33, 0.75 ≤ A3 / A4 ≤ 2, 0.8 ≤ (A1 + A2) / (A3 + A4) ≤ 2.

22. The heat exchange apparatus according to feature 1.

3. The flow area of ​​any one of the first heat exchange channels is the same as the flow area of ​​any one of the second heat exchange channels, and / or the flow area of ​​any one of the third heat exchange channels is the same as the flow area of ​​any one of the fourth heat exchange channels. The heat exchange apparatus according to claim 1 or 2.

4. The heat exchange device is a fin-tube type heat exchanger, and the heat exchange flow path is limited by the heat exchange tube, with the specifications of the multiple first heat exchange flow paths being the same or different and having a diameter of 5 mm to 7 mm, the specifications of the multiple second heat exchange flow paths being the same or different and having a diameter of 5 mm to 7 mm, the specifications of the multiple third heat exchange flow paths being the same or different and having a diameter of 4 mm to 6.5 mm, and the specifications of the multiple fourth heat exchange flow paths being the same or different and having a diameter of 4 mm to 6.5 mm. A heat exchange apparatus according to any one of claims 1 to 3, characterized by the features described herein.

5. The third heat exchange section is smoothly connected to the fourth heat exchange section via a curved portion, and in the cross-section of the heat exchange apparatus, the longitudinal direction of the first heat exchange section extends linearly and has a length L1, the longitudinal direction of the second heat exchange section extends linearly and has a length L2, the length of the linearly extending longitudinal section of the third heat exchange section is L31 and the length of the curved extension is L32, the length of the linearly extending longitudinal section of the fourth heat exchange section is L41 and the length of the curved extension is L42, and 1.85 ≤ L1 / L2 ≤ 3.56, 1.1 ≤ (L31 + L32) / L2 ≤ 2.2, 0.7 ≤ (L31 + L32) / (L41 + L42) ≤ 1.

9. A heat exchange apparatus according to any one of claims 1 to 4, characterized by the present invention.

6. In the cross-section of the heat exchanger, the width of the first heat exchange section is B1, the width of the second heat exchange section is B2, the width of the third heat exchange section is B3, and 2.85 ≤ L1 / B1 ≤ 5.14, 1.23 ≤ L2 / B2 ≤ 1.94, and 1.5 ≤ L41 / B3 ≤ 2.

44. The heat exchange apparatus according to feature 5.

7. The heat exchange apparatus according to claim 6, characterized in that B1 = B2 = B3.

8. The heat exchange device is a fin-tube type heat exchanger, where the fins of the front upper heat exchange segment and the fins of the front lower heat exchange segment are different parts of the same fin, and the fins of the rear heat exchanger and the fins of the front heat exchanger are two separate parts of a single fin. A heat exchange apparatus according to any one of claims 1 to 7, characterized by the features described herein.

9. The heat exchange device is a fin-tube type heat exchanger, and the first heat exchange section, the second heat exchange section, the third heat exchange section, and the fourth heat exchange section each have a plurality of rows of tube assemblies arranged along the width direction of the fins, and each row of tube assemblies includes a plurality of heat exchange tubes arranged along the longitudinal direction of the fins, the heat exchange tubes define the corresponding heat exchange flow path, and a gap assembly is installed between each pair of adjacent heat exchange tubes along the longitudinal direction of the fins. A heat exchange apparatus according to any one of claims 1 to 8, characterized by the present invention.

10. In the forward heat exchanger, in two adjacent rows of the heat exchange tube assemblies, the number of gaps in at least one of the gap assemblies in the upstream tube assembly is equal to or greater than the number of gaps in any one of the gap assemblies in the downstream tube assembly of the forward heat exchanger, and the width of at least one of the gap assemblies in the upstream tube assembly is equal to or greater than the width of any one of the gap assemblies in the downstream tube assembly of the forward heat exchanger. The heat exchange apparatus according to feature 9.

11. The rear heat exchanger has a rear upper heat exchange segment and a rear lower heat exchange segment, and the width of at least one gap assembly in the rear upper heat exchange segment is greater than or equal to the width of at least one gap assembly in the rear lower heat exchange segment. The heat exchange apparatus according to feature 9.

12. The upper end of the rear heat exchanger has at least three types of gap assemblies, and / or the upper end of the front heat exchanger has at least three types of gap assemblies, wherein at least one parameter of the width, gap length, number of gaps and gap direction of the different types of gap assemblies is different. A heat exchange apparatus according to any one of claims 1 to 11, characterized by the features described herein.

13. A through-flow air passage is installed between the rear heat exchanger and the front heat exchanger, a groove is provided in a part of the front side of the rear heat exchanger, and at least a part of the groove faces the rear volute tongue of the through-flow air passage. A heat exchange apparatus according to any one of claims 1 to 11, characterized by the features described herein.

14. The connection point between the forward upper heat exchange segment and the forward lower heat exchange segment has a plurality of gap assemblies, the gap assembly located on the air injection side of the plurality of gap assemblies is the outer assembly, at least one of the outer assemblies forms a fixing assembly, the fixing assembly includes a plurality of gap structures arranged along the direction through which one airflow passes, and in any two adjacent gap structures of the fixing assembly, the gap length of the downstream gap structure is greater than or equal to the gap length of the upstream gap structure. A heat exchange apparatus according to any one of claims 1 to 11, characterized by the features described herein.

15. It comprises a housing, a blower, and a heat exchanger. An air intake is provided at the top of the housing, The blower is installed inside the housing and has an air passage member and a cross-flow impeller, and the cross-flow impeller is installed at the air passage inlet of the air passage member. The heat exchanger is installed inside the housing and is located between the air inlet and the blower, and the heat exchanger is the heat exchanger described in any one of claims 1 to 14. An indoor air conditioning unit characterized by the following features.

16. The diameter of the cross-flow impeller is D, the maximum width of the housing in the front-to-back direction is W, and 2.6 ≤ W / D ≤ 3.

7. The indoor air conditioning unit according to feature 15.

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