Heat exchanger and air conditioning device

Abstract

The heat exchanger includes a plurality of heat transfer tubes, each of which has a plurality of through holes formed therein. The plurality of heat transfer tubes have a plurality of connecting portions that directly connect the plurality of through holes of adjacent heat transfer tubes among the plurality of heat transfer tubes, or a plurality of header tubes that are inserted into the plurality of through holes and connect the plurality of through holes of adjacent heat transfer tubes among the plurality of heat transfer tubes. The plurality of connecting portions or the plurality of header tubes are a plurality of header sections formed to extend in a first direction, which communicate the refrigerant between each of the internal spaces of the plurality of heat transfer tubes and constitute a plurality of header sections that serve as inlets and outlets for the refrigerant of a heat transfer tube group formed by the plurality of heat transfer tubes, and the plurality of header portions are provided at positions that divide the plurality of heat transfer tubes into upper and lower sections in the direction of gravity.

Description

[Technical field]

[0001] The present disclosure relates to a heat exchanger and an air conditioner including the heat exchanger. [Background technology]

[0002] Conventionally, there has been a heat exchanger in which heat transfer tubes are installed vertically, the heat exchanger having a header portion and a plurality of heat transfer tubes connected to the header portion and formed to extend in the vertical direction (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] JP 2018-96638 A Summary of the Invention [Problem to be solved by the invention]

[0004] In a heat exchanger in which heat transfer tubes are installed vertically, such as the heat exchanger of Patent Document 1, if the vertical length of the heat transfer tubes becomes long, when the refrigerant flows in from the bottom of the heat exchanger during condensing operation, the refrigerant may not be able to rise to the top of the heat transfer tube due to the head difference (potential energy), resulting in liquid stagnation.

[0005] The present disclosure has been made to solve the above-mentioned problems, and has an object to provide a heat exchanger and an air conditioner that reduce head difference and suppress liquid retention. [Means for solving the problem]

[0006] A heat exchanger according to the present disclosure includes a plurality of heat transfer tubes arranged in a first direction, each extending in a second direction intersecting the first direction, both ends in the second direction sealed, and through which a refrigerant flows, each of the plurality of heat transfer tubes having a plurality of through holes formed inward from both ends and connecting an internal space of each of the plurality of heat transfer tubes to the outside, the plurality of heat transfer tubes having a plurality of connecting portions directly connecting the plurality of through holes of adjacent heat transfer tubes among the plurality of heat transfer tubes, or having a plurality of header tubes inserted into the plurality of through holes and connecting the plurality of through holes of adjacent heat transfer tubes among the plurality of heat transfer tubes, the plurality of connecting portions or the plurality of header tubes being a plurality of header portions formed to extend in the first direction, connecting the refrigerant between each of the internal spaces of the plurality of heat transfer tubes, and constituting a plurality of header portions which serve as inlets and outlets for the refrigerant of a heat transfer tube group constituted by the plurality of heat transfer tubes, the plurality of header portions being provided at positions dividing the plurality of heat transfer tubes into upper and lower portions in the gravity direction. The cross-sectional area a of each heat transfer tube is a [m 2 ], and the total flow area A of the multiple heat transfer tubes when the number of heat transfer tubes is N [tubes] is defined as A [m 2 ]=a×N[m 2 ], the length of the heat transfer tubes in the second direction is defined as H [m], the first direction is parallel to the horizontal plane, the inclination angle of the heat transfer tubes with respect to the horizontal plane is defined as θ [°], and the pressure difference in the refrigerant flow path is ΔP HEX and the liquid head is defined as ΔP HEAD When the above definition is made, ΔP HEX / ΔP HEAD =(5.94635×10-4×A-1.75030) / (8.4303HSinθ+0.8779)>1 It is something.

[0007] An air conditioner according to the present disclosure includes the above heat exchanger. Effect of the Invention

[0008] The heat exchanger and air conditioning apparatus according to the present disclosure have a plurality of header sections formed by connecting a plurality of through holes by a connecting section or a header pipe, and the plurality of header sections are provided at positions dividing the plurality of heat transfer tubes into upper and lower parts in the direction of gravity. The heat exchanger and air conditioning apparatus can shorten the distance that the refrigerant rises inside the heat transfer tubes, compared to a case where the plurality of header sections are not provided at positions dividing the plurality of heat transfer tubes into upper and lower parts in the direction of gravity. The heat exchanger and air conditioning apparatus can reduce the head difference and suppress liquid stagnation by shortening the distance that the refrigerant rises, compared to a case where the plurality of header sections are not provided at positions dividing the plurality of heat transfer tubes into upper and lower parts in the direction of gravity. [Brief description of the drawings]

[0009] [Figure 1] 1 is a perspective view showing a schematic configuration of a heat exchanger according to a first embodiment. [Diagram 2] 1 is a vertical cross-sectional view of a heat exchanger according to a first embodiment. [Diagram 3] 2 is a view of a heat transfer tube of the heat exchanger according to the first embodiment viewed in a first direction. [Figure 4] 4 is a conceptual diagram of a cross section of the heat transfer tube of FIG. 3 taken along line AA in the heat exchanger according to the first embodiment, viewed in the direction of the arrows. [Diagram 5] FIG. 4 is a vertical sectional view of a modified example of the heat exchanger according to the first embodiment. [Figure 6] FIG. 1 is a refrigerant circuit diagram during cooling operation of an air conditioner equipped with a heat exchanger according to a first embodiment. [Figure 7] FIG. 11 is a perspective view showing a heat transfer tube of a heat exchanger according to a second embodiment. [Figure 8] 5 is a conceptual diagram of a cross section of a heat transfer tube taken along line AA in FIG. 3, as viewed in the direction of the arrows, in a heat exchanger according to a second embodiment. [Figure 9] FIG. 11 is a perspective view showing a part of the inner surface of a heat transfer tube of a heat exchanger according to a third embodiment. [Figure 10] 11 is a conceptual diagram of a heat exchanger according to a fourth embodiment, viewed in a first direction. FIG. [Figure 11]13 is a conceptual diagram of a modified example of the heat exchanger according to the fourth embodiment, viewed in a first direction. FIG. [Figure 12] 4 is a conceptual diagram of a heat exchanger according to a comparative example viewed in a first direction. FIG. [Figure 13] FIG. 11 is a conceptual diagram of a heat exchanger according to a fifth embodiment, viewed in a first direction. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0010] Hereinafter, a heat exchanger according to the first embodiment and an air conditioner including this heat exchanger will be described with reference to the drawings. In the following drawings including FIG. 1, the relative dimensional relationship and shape of each component may differ from the actual one. In addition, in the following drawings, the same reference numerals are attached to the same or equivalent parts, and this is common throughout the entire specification. In addition, to facilitate understanding, terms indicating directions (e.g., "upper", "lower", "right", "left", "front", "rear", etc.) are used as appropriate, but these notations are only described in this way for the convenience of explanation and do not limit the arrangement and orientation of the device or parts. In the specification, the positional relationship between each component, the extension direction of each component, and the arrangement direction of each component are, in principle, those when the heat exchanger is installed in a usable state.

[0011] Embodiment 1 [Configuration of heat exchanger 100] FIG. 1 is a perspective view showing a schematic configuration of a heat exchanger 100 according to the first embodiment. The outline arrows in FIG. 1 indicate an example of the direction in which the refrigerant flows. The configuration of the heat exchanger 100 will be described with reference to FIG. 1. The refrigerant direction indicated by the outline arrows below is an example, and the refrigerant flow direction may be opposite to that shown in the figure depending on the case in which the heat exchanger 100 functions as an evaporator or a condenser. Also, in FIG. 1, a partition portion 70 provided inside the heat transfer tube 10 is indicated by a broken line.

[0012] The heat exchanger 100 is a device that exchanges heat between a refrigerant flowing inside the heat exchanger 100 and a fluid flowing outside the heat exchanger 100. In the case of an air-conditioning device, the heat exchanger 100 exchanges heat between the refrigerant flowing inside the heat exchanger 100 and the air flowing outside the heat exchanger 100. The heat exchanger 100 is connected to other heat exchangers and compressors, etc., by refrigerant piping, and constitutes a part of various devices that make up a refrigerant circuit.

[0013] FIG. 2 is a vertical cross-sectional view of the heat exchanger 100 according to the first embodiment. FIG. 3 is a view of the heat transfer tube 10 of the heat exchanger 100 according to the first embodiment as viewed in a first direction D1. FIG. 4 is a conceptual diagram of the cross section of the heat transfer tube 10 of FIG. 3 as viewed in the direction of the arrows in the heat exchanger 100 according to the first embodiment. The cross-sectional view shown in FIG. 2 shows the cross section of the heat exchanger 100 in a plane along the first direction D1 and the second direction D2. FIG. 2 also shows a part of the heat exchanger 100. In FIG. 3, the partition section 70 provided inside the heat transfer tube 10 is shown by a broken line. Hereinafter, the structure of the heat exchanger 100 will be described in detail with reference to FIGS. 1 to 4.

[0014] The heat exchanger 100 includes a plurality of heat transfer tubes 10 arranged in a first direction D1, each extending in a second direction D2 intersecting the first direction D1, both ends of which are sealed in the second direction D2, and through which a refrigerant flows in the second direction D2.

[0015] (Heat transfer tube 10) 1, the heat exchanger 100 has a plurality of heat transfer tubes 10 arranged in a first direction D1 and connected to each other. As an example, the heat transfer tubes 10 are flat tubes that extend in a direction in which a tube axis Ax extends (hereinafter also referred to as a tube axis direction) and have a flat shape that is long in one direction in a cross section perpendicular to the tube axis Ax. Note that the heat transfer tubes 10 are preferably, but are not limited to, flat tubes.

[0016] In the following description, the first direction D1 in which the heat transfer tubes 10 are arranged may be referred to as the arrangement direction, the axial direction of the heat transfer tubes 10 may be referred to as the second direction D2 or the longitudinal direction of the heat transfer tubes 10, and the longitudinal direction of the cross section of the heat transfer tube 10 may be referred to as the third direction D3 or the short-side direction of the heat transfer tube 10. The third direction D3 is a direction perpendicular to the first direction D1 and the second direction D2.

[0017] 1, the heat exchanger 100 is defined as being installed such that the arrangement direction (first direction D1) of the heat transfer tubes 10 is the left-right direction. Each heat transfer tube 10 is defined as being disposed such that its tube axis Ax is the up-down direction perpendicular to the arrangement direction (first direction D1) and its short side direction (third direction D3) is the front-rear direction perpendicular to the tube axis direction and the arrangement direction.

[0018] The arrangement of the heat exchanger 100, or the angle between the arrangement direction (first direction D1) of the heat transfer tubes 10 in the heat exchanger 100 and the tube axis direction (second direction D2) of each heat transfer tube 10, is not limited to the above. For example, the heat exchanger 100 may be arranged at an angle such that the tube axis direction of each heat transfer tube 10 is inclined with respect to the up-down direction. Alternatively, when the heat exchanger 100 is installed such that the arrangement direction (first direction D1) of the heat transfer tubes 10 is the left-right direction, the heat exchanger 100 may be configured such that the tube axis direction of each heat transfer tube 10 is inclined with respect to the up-down direction.

[0019] Gaps that are air flow paths P2 are formed between the tube walls 11 of the heat transfer tubes 10 adjacent to each other in the arrangement direction of the heat transfer tubes 10 (first direction D1), and air flows through each gap in the heat exchanger 100 along the short side direction of the heat transfer tubes 10 (third direction D3). The fluid that flows through the heat transfer tubes 10 is a refrigerant. A heat transfer flow path P1a through which the refrigerant flows is provided inside the heat transfer tube 10. Note that the fluid that flows through the heat transfer tube 10 may be other fluids such as water or brine instead of a refrigerant.

[0020] Both ends of the heat transfer tube 10 in the longitudinal direction (second direction D2) are sealed. Specifically, the heat exchanger 100 includes tube sealing portions 20 that close each open end 10e of the heat transfer tube 10 on both sides in the longitudinal direction (second direction D2). In the example of Fig. 2, the tube sealing portions 20 are provided for each heat transfer tube 10 at two locations, one on the upper side and one on the lower side of the flat tube. The tube sealing portions 20 are joined to the open end 10e of the heat transfer tube 10 by joining means such as brazing or an adhesive, for example.

[0021] 2 to 4, each of the heat transfer tubes 10 has a tube wall 11 having a heat transfer flow path P1a through which a refrigerant flows in an internal space. The heat transfer tube 10 has a tube structure in which an internal space through which the refrigerant flows is maintained across the longitudinal direction (second direction D2) of the heat transfer tube 10, i.e., from the upper end to the lower end of the tube wall 11.

[0022] The tube wall 11 of the heat transfer tube 10 has substantially flat tube side wall portions 10a and 10b facing each other in the first direction D1. The tube wall 11 of the heat transfer tube 10 also has curved connecting wall portions 10c and 10d that connect the tube side wall portions 10a and 10b at both ends of the tube side wall portions 10a and 10b in the third direction D3. In the following description, the tube side wall portions 10a and 10b may be referred to as the tube side wall portions 10a, etc.

[0023] Each of the tube side wall portions 10a and 10b has a rectangular shape with a long side extending in the longitudinal direction (second direction D2) of the heat transfer tube 10 and a short side extending in the lateral direction (third direction D3) of the heat transfer tube 10. The tube side wall portions 10a and 10b are flat, but the "flat" in the present application does not have to be a completely flat surface, and may have a structure that appears to be flat as a whole. For example, the tube side wall portions 10a and 10b may have a depression, protrusion, or wave shape formed in a part of the flat area. In FIG. 2, the wall portion on the left side of the tube wall 11 is the tube side wall portion 10a, and the wall portion on the right side of the tube wall 11 is the tube side wall portion 10b. When the heat transfer tube 10 is a circular tube, the tube wall 11 is formed in a cylindrical shape.

[0024] As shown in Figures 2 and 3, each of the multiple heat transfer tubes 10 has multiple through holes 30 formed inward from both ends in the second direction D2, connecting the internal space of each of the multiple heat transfer tubes 10 to the outside.

[0025] 2 and 3, the tube side wall portion 10a and the tube side wall portion 10b are formed with a through hole 30. The left tube side wall portion 10a is formed with a through hole 30a penetrating in the first direction D1, and the right tube side wall portion 10b is formed with a through hole 30b penetrating in the first direction D1.

[0026] The through holes 30a and 30b are through holes constituting a first header portion 51 and a second header portion 52, which will be described later. The through holes 30a and 30b are formed at positions facing each other in the first direction D1. The through holes 30 are a general term for the through holes 30a and 30b. The through holes 30 are through holes constituting a header portion 50, which will be described later.

[0027] 2, adjacent heat transfer tubes 10 have connecting portions 12 for connecting their tube walls 11. Adjacent heat transfer tubes 10 have connecting portions 12 that connect their tube walls 11 and communicate with each other's heat transfer flow paths P1a inside the tube walls 11. Each heat transfer tube 10 has a tube wall 11, and connecting protrusions 12a and 12b that configure the connecting portion 12 and extend from the tube wall 11 outward in a first direction D1.

[0028] The connecting portion 12 between adjacent heat transfer tubes 10 has a tubular shape with a hollow portion Sg that penetrates in the first direction D1. The connecting portion 12 is formed by combining a connecting protrusion 12a and a connecting protrusion 12b. In the example of Fig. 2, the connecting portion 12 is formed by inserting the connecting protrusion 12b into the connecting protrusion 12a. The connecting protrusion 12a and the connecting protrusion 12b that constitute the connecting portion 12 are configured to fit together, for example.

[0029] The connecting portion 12 is composed of a connecting protrusion portion 12a and a connecting protrusion portion 12b formed on at least one of the opposing tube side wall portions 10a of adjacent heat transfer tubes 10, and protruding from the peripheral portion of the through hole 30 in the first direction D1.

[0030] In addition, the connecting portion 12 does not have to be configured such that the connecting protrusions 12a and 12b fit together. For example, the connecting portion 12 may be configured such that the connecting protrusions 12a and 12b are joined together by a joining means such as brazing or an adhesive.

[0031] The connecting portion 12 is composed of a connecting protrusion 12a or a connecting protrusion 12b provided on at least one of the opposing tube side wall portions 10a and 10b of the adjacent heat transfer tubes 10. The connecting protrusion 12a extends from the peripheral portion of the through hole 30a toward the opposing tube side wall portion 10b. The connecting protrusion 12b extends from the peripheral portion of the through hole 30b toward the opposing tube side wall portion 10a.

[0032] In FIG. 2, the connecting portion 12 is a cylindrical member formed on both of the tube side wall portions 10a and 10b of the adjacent heat transfer tubes 10. Concatenation The through holes 30a and 30b and the connecting protrusions 12a and 12b can be formed, for example, by a burring process in which a hole is drilled in the flat plate portion of the heat transfer tube 10 and the flat plate portion at the periphery is deformed so as to rise into a cylindrical shape.

[0033] 2, the connecting portion 12 connects the through holes 30a and 30b provided in the tube side wall portions 10a and 10b via the hollow portion Sg, thereby communicating the internal spaces of the adjacent tube walls 11. The connecting portion 12 also has a function of separating the inner hollow portion Sg from the air flow path P2, which is the space outside the connecting portion 12.

[0034] 2 and 3, the through holes 30 and the connecting portions 12 are formed on the inside of the open ends 10e on both sides in the longitudinal direction (second direction D2) of the heat transfer tubes 10. Specifically, in the heat exchanger 100 arranged as shown in FIG. Concatenation The protrusion 12a and the connecting protrusion 12b are formed below the upper open end 10e of the heat transfer tube 10 and above the lower open end 10e of the heat transfer tube 10.

[0035] The through holes 30 and the connecting portions 12 are formed at positions that divide the heat transfer tubes 10 into upper and lower portions in the gravity direction. The through holes 30 and the connecting portions 12 are provided in the central portions 17 of the heat transfer tubes 10 in the second direction D2. The central portions 17 include not only the complete central portion of the heat transfer tubes 10 in the second direction D2, but also a portion near the central portion. The two through holes 30 are formed side by side in the third direction D3 of the heat transfer tube 10. The two connecting portions 12 are formed side by side in the third direction D3 of the heat transfer tube 10.

[0036] The heat transfer tube 10 can be manufactured, for example, by forming the through hole 30 and the connecting protrusions 12a and 12b in advance in a member that is to become the heat transfer tube 10, and then shaping the member by roll forming. The connecting protrusions 12a and 12b may also be formed by raising the periphery of the hole when forming the through hole 30 in the member that is to become the heat transfer tube 10. The heat transfer tube 10 is made of a metal material having high thermal conductivity, such as aluminum, copper, or brass.

[0037] Each of the heat transfer tubes 10 has a partition portion 70 disposed in the internal space of the tube wall 11, extending in the second direction D2, and dividing the internal space into a third direction D3 perpendicular to the first direction D1 and the second direction D2. Both ends of the partition portion 70 in the second direction D2 are located inside the both ends in the second direction D2 of the heat transfer flow path P1a of the heat transfer tube 10. An upper end 70a of the partition portion 70 is provided below an upper opening end 10e (see FIG. 2) of the heat transfer tube 10, and a lower end 70b of the partition portion 70 is provided above a lower opening end 10e (see FIG. 2) of the heat transfer tube 10.

[0038] The partition portion 70 is a plate-like or rod-like member extending in the first direction D1 and the second direction D2 in the internal space of the heat transfer tube 10. The partition portion 70 is provided so as to connect to the tube side wall portion 10a and the tube side wall portion 10b. The partition portion 70 is provided so as to extend between the tube side wall portion 10a and the tube side wall portion 10b. The partition portion 70 is a member that separates the internal space of the heat transfer tube 10 in the third direction D3, except for both ends of the heat transfer tube 10 in the second direction D2.

[0039] The partition portion 70 is provided, for example, in a central portion in the third direction D3 in the internal space of the heat transfer tube 10. Note that the installation position of the partition portion 70 is not limited to this portion, and the partition portion 70 may be provided biased toward either one side in the third direction D3.

[0040] The refrigerant flow path in the heat exchanger 100 is provided in the tube wall 11 of each heat transfer tube 10 and has a heat transfer flow path P1a extending in the longitudinal direction (second direction D2) of the heat transfer tube 10. The refrigerant flow path in the heat exchanger 100 also has a header flow path P1b extending in the arrangement direction (first direction D1) of the multiple heat transfer tubes 10 and connecting the heat transfer flow paths P1a of the multiple heat transfer tubes 10. The refrigerant flow path in the heat exchanger 100 also has a header flow path P1c extending in the arrangement direction (first direction D1) of the multiple heat transfer tubes 10 and connecting the heat transfer flow paths P1a of the multiple heat transfer tubes 10.

[0041] The heat transfer flow path P1a is divided into a first flow path P1a1 and a second flow path P1a2 by a partition 70. The first flow path P1a1 extends in the second direction D2 of the heat transfer tube 10, and is a flow path through which the refrigerant flowing in from a first header portion 51 (described later) branches from a central portion 17 of the heat transfer tube 10 toward the upper and lower ends. The second flow path P1a2 extends in the second direction D2 of the heat transfer tube 10, and is a flow path through which the refrigerant flowing in from the first flow path P1a1 flows from the upper and lower ends of the heat transfer tube 10 toward the central portion 17, and then merges and flows into the second header portion 52.

[0042] The first flow path P1a1 and the second flow path P1a2 communicate with each other at both upper and lower ends of the heat transfer tube 10. Therefore, the heat transfer flow path P1a for the refrigerant is formed in a substantially O-shape.

[0043] The refrigerant flow path of the heat exchanger 100 is composed of a plurality of heat transfer flow paths P1a, and a header flow path P1b and a header flow path P1c (see FIG. 3) provided in parallel in the front and rear directions in the central portion 17 of the heat exchanger 100. The header flow path P1b is composed of hollow portions Sg of a plurality of connecting portions 12 provided on the front side in the central portion 17 of the heat exchanger 100. The header flow path P1c is composed of hollow portions (not shown) of a plurality of connecting portions 12 provided on the rear side in the central portion 17 of the heat exchanger 100.

[0044] The heat transfer flow path P1a communicates with the header flow path P1b and the header flow path P1c at a central portion 17 of the heat transfer flow path P1a in the longitudinal direction (second direction D2) of the heat transfer tube 10. The header flow path P1b and the header flow path P1c each communicate with a plurality of heat transfer flow paths P1a. The above-mentioned through hole 30a, the through hole 30b, the hollow portion Sg of the connecting portion 12, etc. constitute the header flow path P1b and the header flow path P1c, and a refrigerant flows through the hollow portion Sg.

[0045] In the heat exchanger 100, the connecting portion 12 is formed of a part of the heat transfer tube 10, and the portion of the header flow passages P1b and P1c that is arranged between the tube walls 11 of the heat transfer tubes 10 is a hollow portion Sg inside the connecting portion 12. Therefore, in the heat exchanger 100, the header flow passages P1b and P1c are formed in the heat transfer tubes 10 that are heat exchange members, so that there is no need to provide a header portion on the outside of the multiple heat transfer tubes 10.

[0046] The heat transfer tubes 10 have a plurality of header sections 50 formed by connecting the through holes 30 of the adjacent heat transfer tubes 10 among the plurality of heat transfer tubes 10. The header section 50 is formed to extend in a horizontal direction, for example. The header section 50 is formed to be smaller than the width of the plurality of heat transfer tubes 10 in a third direction D3 perpendicular to the first direction D1 and the second direction D2. The header section 50 communicates the refrigerant with the internal spaces of the plurality of heat transfer tubes 10 as shown in FIG. 1, and serves as an inlet / outlet 51a and an inlet / outlet 52a for the refrigerant of the heat transfer tube group 15 formed by the plurality of heat transfer tubes 10. The end of the header section 50 opposite to the inlet / outlet 51a and the inlet / outlet 52a is closed by the tube wall 11 or the like.

[0047] The header section 50 functions as a distribution mechanism that distributes the refrigerant flowing into the heat transfer tube group 15 to the multiple heat transfer tubes 10. In addition, the header section 50 functions as a joining mechanism when the refrigerant flowing out from the multiple heat transfer tubes 10 joins when the refrigerant flows out from the heat transfer tube group 15.

[0048] The multiple header sections 50 include at least a first header section 51 and a second header section 52. The header section 50 is a general term for the first header section 51 and the second header section 52. As shown in FIG. 1 and FIG. 2, the multiple header sections 50 have the first header section 51 provided at one end side of the heat transfer tube 10 in the third direction D3, and the second header section 52 provided at the other end side of the heat transfer tube 10. The header section 50 is provided on the inside of the end of the heat transfer tube 10 in the second direction D2. The positions of the first header section 51 and the second header section 52 in the third direction D3 may be opposite to the positions shown in the drawings.

[0049] The multiple header portions 50 are formed at positions that divide the multiple heat transfer tubes 10 into upper and lower portions in the gravity direction. The multiple header portions 50 are also provided in central portions 17 of the multiple heat transfer tubes 10 in the second direction D2. The first header portion 51 and the second header portion 52 are also formed side by side in the third direction D3 of the heat transfer tube 10.

[0050] In the heat exchanger 100 of the first embodiment, when the heat exchanger 100 is either a condenser or an evaporator, the multiple header sections 50 include a first header section 51 serving as a refrigerant inlet and a second header section 52 serving as a refrigerant outlet. The first header section 51 and the second header section 52 are provided on both sides of the partition section 70 in the third direction D3, with the partition section 70 therebetween.

[0051] As described above, the heat transfer tubes 10 have a plurality of connecting portions 12 that directly connect the through holes 30 of the adjacent heat transfer tubes 10 among the plurality of heat transfer tubes 10, and each of the plurality of header portions 50 is composed of a plurality of connecting portions 12. That is, the plurality of connecting portions 12 form a plurality of header portions 50 formed to extend in the first direction D1. The plurality of connecting portions 12 communicate the refrigerant with the respective internal spaces of the plurality of heat transfer tubes 10, and constitute a plurality of header portions 50 that serve as inlets and outlets for the refrigerant of the heat transfer tube group 15 composed of the plurality of heat transfer tubes 10. In the heat exchanger 100, the through holes 30 are directly connected to each other by the connecting portions 12 provided in the through holes 30.

[0052] [Modifications of the heat exchanger 100] Fig. 5 is a vertical cross-sectional view of a modified example of the heat exchanger 100 according to the embodiment 1. Fig. 5 shows a part of the heat exchanger 100. The modified example of the heat exchanger 100 will be described with reference to Fig. 5.

[0053] The heat exchanger 100 may have a header pipe 80 in the header section 50 without using the connecting portion 12. That is, the heat exchanger 100 may use the header pipe 80 instead of the connecting portion 12 to connect the through holes 30. The heat exchanger 100 may connect the through holes 30 to each other using the header pipe 80, which is a member separate from the heat transfer tube 10.

[0054] The heat transfer tubes 10 are inserted into the through holes 30, and include a plurality of header tubes 80 that connect the through holes 30 of adjacent heat transfer tubes 10 among the plurality of heat transfer tubes 10. Each of the plurality of header sections 50 is formed of the header tube 80 inserted into the through hole 30. The header tube 80 has a plurality of holes 82 formed therein that communicate with the internal spaces of each of the plurality of heat transfer tubes 10.

[0055] Each of the heat transfer tubes 10 has a tube wall 11 provided with a heat transfer flow path P1a through which a fluid flows in an internal space. The tube wall 11 has tube side wall portions 10a etc. facing each other in a first direction D1, and the tube side wall portions 10a etc. have through holes 30 formed therein into which header tubes 80 are inserted. In the heat exchanger 100, the header tubes 80 indirectly connect the through holes 30 to each other.

[0056] As described above, the header pipe 80 penetrates the heat transfer pipes 10 in the first direction D1, and the refrigerant flows through the header pipe 80. The header pipe 80 is, for example, a circular pipe having a cylindrical cross-sectional shape. Note that the header pipe 80 is not limited to a circular pipe, and may be a pipe having a cross-sectional shape other than a cylindrical shape.

[0057] A header flow path P1b or a header flow path P1c is formed inside the header pipe 80 or the connecting portion 12. For example, the header pipe 80 or the connecting portion 12 constituting the first header portion 51 constitutes the header flow path P1b, and the header pipe 80 or the connecting portion 12 constituting the second header portion 52 constitutes the header flow path P1c.

[0058] The multiple header sections 50 are formed to extend in the first direction D1, and communicate the refrigerant between the internal spaces of each of the multiple heat transfer tubes 10, constituting the multiple header sections 50 that serve as refrigerant inlets and outlets for the heat transfer tube group 15 formed by the multiple heat transfer tubes 10.

[0059] Next, an example of the operation of the heat exchanger 100 will be described with reference to Figs. 1 and 2. As shown in Fig. 1, the refrigerant that flows from the first header portion 51 into the heat transfer tube group 15 flows inside the heat transfer tube group 15 and flows out from the second header portion 52. More specifically, as shown by the outline arrow in Fig. 1, the refrigerant flows into the heat exchanger 100 from the refrigerant inlet / outlet 51a of the first header portion 51. As shown in Fig. 2, in the heat exchanger 100, the refrigerant first flows into the header flow path P1b of the first header portion 51 that penetrates the center portion 17 of the plurality of heat transfer tubes 10 in the left-right direction, and flows through the header flow path P1b. In the process, the refrigerant is distributed and flows into the heat transfer flow paths P1a provided in the respective tube walls 11 of the plurality of heat transfer tubes 10.

[0060] As shown in FIG. 3, inside each heat transfer tube 10, the refrigerant that has flowed into each heat transfer flow path P1a from the first header portion 51 branches into upper and lower paths in the first flow path P1a1, merges from the first flow path P1a1 into the second flow path P1a2, and flows out of the second header portion 52. At this time, the refrigerant exchanges heat with air flowing through the gaps between the tube walls 11 of the heat transfer tubes 10 (i.e., the air flow path P2) via the tube walls 11. The refrigerant flows from the multiple heat transfer flow paths P1a into the header flow paths P1c of the second header portion 52 that penetrates the central portions 17 of the multiple heat transfer tubes 10, and merges in the header flow path P1c. The refrigerant that has merged in the header flow path P1c flows through the header flow path P1c, and flows out of the heat exchanger 100 from the refrigerant inlet / outlet 52a (see FIG. 1) of the second header portion 52.

[0061] 1 to 5 is an example of the heat exchanger 100 of the present disclosure, and the number and shapes of the heat transfer tubes 10, the heat transfer flow paths P1a, the header flow paths P1b, and the header flow paths P1c can be changed as appropriate. For example, the heat transfer tubes 10 may be provided with fins that serve as heat transfer promotion members. In addition, the heat transfer tubes 10 may have protrusions such as dimples that protrude into the air flow path P2.

[0062] [Air conditioner 200] Fig. 6 is a refrigerant circuit diagram during cooling operation of the air conditioner 200 equipped with the heat exchanger 100 of the first embodiment. As shown in Fig. 6, the heat exchanger 100 constitutes a part of a refrigerant circuit 250 through which the refrigerant circulates in the air conditioner 200. The heat exchanger 100 is applied to either or both of an outdoor heat exchanger 203 or an indoor heat exchanger 205 described below.

[0063] The air conditioning apparatus 200 has a compressor 201, a flow path switching device 202 that switches the flow path of the refrigerant, and an outdoor heat exchanger 203 that exchanges heat between the outdoor air and the refrigerant flowing inside. The air conditioning apparatus 200 also has an expansion valve 204 that reduces the pressure of the refrigerant flowing inside, and an indoor heat exchanger 205 that exchanges heat between the indoor air and the refrigerant flowing inside. Note that the air conditioning apparatus 200 does not necessarily have to have the flow path switching device 202.

[0064] 6, in the air conditioning device 200, a compressor 201, a flow path switching device 202, an outdoor heat exchanger 203, and an expansion valve 204 are provided in an outdoor unit 231, and an indoor heat exchanger 205 is provided in an indoor unit 232. A header section 50 (see FIG. 2), which serves as an inlet and outlet for the refrigerant of the heat exchanger 100, is connected to the flow path switching device 202 and the expansion valve 204 of the refrigerant circuit 250.

[0065] In the air conditioner 200, a compressor 201, a flow path switching device 202, an outdoor heat exchanger 203, an expansion valve 204, and an indoor heat exchanger 205 are connected by refrigerant piping 255 to form a refrigerant circuit 250 in which the refrigerant circulates. The air conditioner 200 shown in Fig. 6 is capable of both cooling operation and heating operation by switching the flow path switching device 202.

[0066] The compressor 201 draws in a low-temperature, low-pressure refrigerant, compresses the drawn refrigerant, and discharges a high-temperature, high-pressure refrigerant. The flow path switching device 202 is, for example, a four-way valve, and switches between cooling operation and heating operation by switching the direction in which the refrigerant flows. The flow path switching device 202 connects the discharge side of the compressor 201 to the indoor heat exchanger 205 during heating operation, and connects the discharge side of the compressor 201 to the outdoor heat exchanger 203 during cooling operation.

[0067] The outdoor heat exchanger 203 exchanges heat between the outdoor air and the refrigerant flowing inside the outdoor heat exchanger 203. As shown in Fig. 6, during cooling operation, the outdoor heat exchanger 203 functions as a condenser 221 that radiates heat of the refrigerant to the outdoor air and condenses the refrigerant. During heating operation, the outdoor heat exchanger 203 also functions as an evaporator that evaporates the refrigerant and cools the outdoor air with the heat of vaporization.

[0068] The expansion valve 204 is, for example, an electronic expansion valve capable of adjusting the throttle opening, and by adjusting the opening, the pressure of the refrigerant flowing into the outdoor heat exchanger 203 or the indoor heat exchanger 205 is controlled. Note that, in the embodiment, the expansion valve 204 is provided in the outdoor unit 231, but it may be provided in the indoor unit 232, and the installation location is not limited.

[0069] The indoor heat exchanger 205 exchanges heat between the indoor air and the refrigerant flowing inside the indoor heat exchanger 205. As shown in Fig. 6, the indoor heat exchanger 205 functions as an evaporator 222 that evaporates the refrigerant during cooling operation and cools the outdoor air with the heat of evaporation at that time. Also, the indoor heat exchanger 205 functions as a condenser that releases heat of the refrigerant to the outdoor air and condenses the refrigerant during heating operation.

[0070] The air conditioning device 200 may have an outdoor fan 203a and an indoor fan 205a for blowing air to the outdoor heat exchanger 203 and the indoor heat exchanger 205. The outdoor fan 203a and the indoor fan 205a form a flow of air that flows through a flow path P2 (see FIG. 2) between adjacent heat transfer tubes 10.

[0071] In the air conditioner 200, as a result of the compressor 201 operating, a refrigeration cycle is performed in which the refrigerant circulates through the compressor 201, the outdoor heat exchanger 203, the expansion valve 204, and the indoor heat exchanger 205 while undergoing a phase change.

[0072] During cooling operation of the air conditioner 200 shown in FIG. 7, the refrigerant compressed by the compressor 201 is sent to the outdoor heat exchanger 203. In the outdoor heat exchanger 203, the refrigerant releases heat to the outdoor air and is condensed. The refrigerant is then sent to the expansion valve 204, where it is decompressed, and then sent to the indoor heat exchanger 205. The refrigerant then takes in heat from the indoor air in the indoor heat exchanger 205 and evaporates, before returning to the compressor 201. Therefore, during cooling operation of the air conditioner 200, the outdoor heat exchanger 203 functions as a condenser 221, and the indoor heat exchanger 205 functions as an evaporator 222.

[0073] During heating operation of the air conditioner 200, the refrigerant compressed by the compressor 201 is sent to the indoor heat exchanger 205. In the indoor heat exchanger 205, the refrigerant releases heat to the indoor air and is condensed. The refrigerant is then sent to the expansion valve 204, where it is decompressed, and then sent to the outdoor heat exchanger 203. The refrigerant then absorbs heat from the outdoor air in the outdoor heat exchanger 203 and evaporates, before returning to the compressor 201. Therefore, during heating operation of the air conditioner 200, the outdoor heat exchanger 203 functions as an evaporator, and the indoor heat exchanger 205 functions as a condenser.

[0074] [Effects of the heat exchanger 100] The heat exchanger 100 includes a plurality of heat transfer tubes 10 arranged in a first direction D1, each extending in a second direction D2 intersecting the first direction D1, with both ends in the second direction D2 sealed and through which a refrigerant flows. Each of the plurality of heat transfer tubes 10 has a plurality of through holes 30 formed on the inside of the both ends and communicating the internal space of each of the plurality of heat transfer tubes 10 with the outside. The plurality of heat transfer tubes 10 have a plurality of connecting portions 12 that directly connect the plurality of through holes 30 of the heat transfer tubes 10 adjacent to each other among the plurality of heat transfer tubes 10. Alternatively, the plurality of heat transfer tubes 10 have a plurality of header tubes 80 that are inserted into the plurality of through holes 30 and connect the plurality of through holes 30 of the heat transfer tubes 10 adjacent to each other among the plurality of heat transfer tubes 10. The plurality of connecting portions 12 or the plurality of header tubes 80 constitute a plurality of header portions 50 formed to extend in the first direction D1. The multiple header sections 50 communicate the refrigerant with the internal spaces of the multiple heat transfer tubes 10, and serve as refrigerant inlets and outlets for the heat transfer tube group 15 formed by the multiple heat transfer tubes 10. The multiple header sections 50 are provided at positions that divide the multiple heat transfer tubes 10 into upper and lower sections in the gravity direction.

[0075] The heat exchanger 100 has a plurality of header sections 50 formed by connecting a plurality of through holes 30 by a connecting section 12 or a header pipe 80, and the plurality of header sections 50 are provided at positions that divide the plurality of heat transfer tubes 10 into upper and lower sections in the direction of gravity. The heat exchanger 100 can shorten the distance that the refrigerant rises inside the heat transfer tubes 10, compared to a case in which the plurality of header sections 50 are not provided at positions that divide the plurality of heat transfer tubes 10 into upper and lower sections in the direction of gravity. By shortening the distance that the refrigerant rises, the heat exchanger 100 can reduce the head difference and suppress liquid stagnation, compared to a case in which the plurality of header sections 50 are not provided at positions that divide the plurality of heat transfer tubes 10 into upper and lower sections in the direction of gravity.

[0076] Moreover, the header portions 50 are provided in the central portions 17 of the heat transfer tubes 10 in the second direction D2. Compared to a case where the header portions 50 are not provided in the central portions 17 of the heat transfer tubes 10, the heat exchanger 100 can shorten the distance that the refrigerant flows out of the header portions 50 or flows into the header portions 50 rises inside the heat transfer tubes 10. By shortening the distance that the refrigerant rises, the heat exchanger 100 can reduce the head difference and suppress liquid stagnation, compared to a case where the header portions 50 are not provided at positions that divide the heat transfer tubes 10 into upper and lower portions in the gravity direction. Also, since the header portions 50 are provided in the central portions 17 of the heat transfer tubes 10, the heat exchanger 100 can gather the inlets and outlets of the refrigerant in the central portion, making it easier to handle the piping.

[0077] Each of the heat transfer tubes 10 has a partition portion 70 disposed in the internal space of the tube wall 11, extending in the second direction D2, and dividing the internal space into a third direction D3 perpendicular to the first direction D1 and the second direction D2. Both ends of the partition portion 70 in the second direction D2 are located inside the ends of both sides of the heat transfer flow path P1a of the heat transfer tube 10 in the second direction D2. The header portions 50 include a first header portion 51 serving as a refrigerant inlet and a second header portion 52 serving as a refrigerant outlet. The first header portion 51 and the second header portion 52 are provided on both sides of the partition portion 70 in the third direction D3, with the partition portion 70 sandwiched therebetween. The heat exchanger 100 has the partition portion 70, which makes it easier to branch the refrigerant flowing in from the first header portion 51 into upper and lower portions, and the flow rate of the rising refrigerant can be increased by narrowing the flow path inside the heat transfer tube 10. Therefore, in the heat exchanger 100, the refrigerant can rise more easily than in a case where the partition portion 70 is not provided, and therefore the head difference can be reduced and liquid retention can be suppressed.

[0078] Furthermore, the air conditioning device 200 is equipped with the heat exchanger 100. Because the air conditioning device 200 is equipped with the heat exchanger 100, it is able to achieve the effects of the heat exchanger 100 described above.

[0079] Embodiment 2 Fig. 7 is a perspective view showing a heat transfer tube 10 of a heat exchanger 100 according to embodiment 2. Fig. 8 is a conceptual diagram of a cross section of the heat transfer tube 10 at line AA in Fig. 3 in the heat exchanger 100 according to embodiment 2, viewed in the direction of the arrow. The heat exchanger 100 of embodiment 2 is a modified version of the heat transfer tube 10 in the heat exchanger 100 of embodiment 1. Note that components having the same functions and actions as those in embodiment 1 are denoted by the same reference numerals, and description thereof will be omitted.

[0080] 7 and 8, the partition portion 70 of the heat exchanger 100 according to the second embodiment is biased toward one side in the third direction D3. The partition portion 70 is provided at a position closer to the first header portion 51 than to the central portion in the third direction D3.

[0081] In the heat exchanger 100, the flow path cross-sectional area of ​​the internal space on the first header section 51 side is smaller than the flow path cross-sectional area of ​​the internal space on the second header section 52 side. That is, in the heat exchanger 100, the flow path cross-sectional area of ​​the first flow path P1a1 is smaller than the flow path cross-sectional area of ​​the second flow path P1a2.

[0082] The heat exchanger 100 is a header section 50 in which a refrigerant having a larger liquid component than a gas component flows through the first header section 51 than through the second header section 52. In the heat exchanger 100, a refrigerant having a larger liquid component than a gas component flows through the internal space on the first header section 51 side than through the internal space on the second header section 52 side. In the heat exchanger 100, a refrigerant having a larger liquid component than a gas component flows through the first flow path P1a1 than through the second flow path P1a2. In the heat exchanger 100, a refrigerant having a higher ratio of liquid component to gas component flows through the internal space on the first header section 51 side than through the internal space on the second header section 52 side.

[0083] The first header section 51 is, for example, the header section 50 on the side into which the refrigerant flows when the heat exchanger 100 is an evaporator, and is the header section 50 on the side from which the refrigerant flows out when the heat exchanger 100 is an evaporator. In the example shown in FIG. 6, the heat exchanger 100 according to the second embodiment is applied to an indoor heat exchanger 205.

[0084] [Effects of the heat exchanger 100] The partition section 70 in the heat exchanger 100 of the second embodiment is provided at a position closer to the first header section 51 than to the central portion in the third direction D3. Therefore, the heat transfer tubes 10 of the heat exchanger 100 are formed so that the flow path cross-sectional area of ​​the internal space on the first header section 51 side is smaller than the flow path cross-sectional area of ​​the internal space on the second header section 52 side. In the heat transfer tubes 10 of the heat exchanger 100, a refrigerant with a larger liquid component than a gas component flows in the internal space on the first header section 51 side than in the internal space on the second header section 52 side.

[0085] With the above configuration, the heat exchanger 100 has a faster flow rate on the side with a larger liquid component than on the side with a larger gas component, making it easier to raise the refrigerant and further reducing the head difference and suppressing liquid stagnation compared to a case where the heat exchanger 100 does not have the above configuration. With the above configuration, the heat exchanger 100 has a faster flow rate on the side with a larger liquid component, where heat transfer is more easily performed, than on the side with a larger gas component, improving the heat transfer coefficient and improving the heat exchanger performance.

[0086] Furthermore, the air conditioning device 200 is equipped with the heat exchanger 100. Because the air conditioning device 200 is equipped with the heat exchanger 100, it is able to achieve the effects of the heat exchanger 100 described above.

[0087] Embodiment 3 9 is a perspective view showing a part of the inner surface of the heat transfer tube 10 of the heat exchanger 100 according to the embodiment 3. The heat exchanger 100 of the embodiment 3 is obtained by modifying the configuration of the heat transfer tube 10 in the heat exchanger 100 of the embodiment 1. Note that components having the same functions and actions as those in the embodiments 1 and 2 are denoted by the same reference numerals and the description thereof will be omitted.

[0088] Each of the multiple heat transfer tubes 10 has at least one or more protruding portions 60 protruding into the internal space of the heat transfer tube 10. The protruding portions 60 are formed in a protruding shape. There may be one or more protruding portions 60. In the heat exchanger 100, the protruding portions 60 can narrow the heat transfer flow path P1a inside the heat transfer tube 10. The flow speed of the refrigerant is faster when flowing through a narrowed space than when flowing through an unnarrowed space.

[0089] The protrusions 60 are desirably provided at positions closer to the through holes 30 than to both ends in the second direction D2 of the heat transfer tube 10. The protrusions 60 are desirably provided at positions closer to the header section 50 than to both ends in the second direction D2 of the heat transfer tube 10. By providing the protrusions 60 at positions closer to the through holes 30 or the header section 50, the heat exchanger 100 can increase the flow rate of the refrigerant that has flowed into the header section 50.

[0090] It is particularly preferable that the protrusions 60 are provided above the through holes 30 or the header portion 50. By providing the protrusions 60 above the through holes 30 or the header portion 50, the protrusions 60 can impart momentum to the refrigerant flowing upward.

[0091] [Effects of the heat exchanger 100] Each of the heat transfer tubes 10 in the heat exchanger 100 according to the third embodiment has at least one or more convex portions 60 protruding into the internal space of the heat transfer tube 10. By providing the convex portions 60 in the heat transfer tube 10, the flow rate of the liquid refrigerant increases because the convex portions 60 act as a fluid resistance and narrow the internal space of the heat transfer tube 10. The heat exchanger 100 can increase the flow rate of the refrigerant in the heat transfer tube 10 compared to a case where the convex portions 60 are not provided, so that the refrigerant can be easily raised, the head difference can be alleviated, and liquid stagnation can be suppressed. The heat exchanger 100 can also control the uneven flow of the liquid refrigerant depending on the position of the convex portions 60, and can adjust the refrigerant distribution in the heat transfer tube 10 while suppressing liquid stagnation, thereby improving the heat exchanger performance.

[0092] Furthermore, the air conditioning device 200 is equipped with the heat exchanger 100. Because the air conditioning device 200 is equipped with the heat exchanger 100, it is able to achieve the effects of the heat exchanger 100 described above.

[0093] Embodiment 4 Fig. 10 is a conceptual diagram of the heat exchanger 100 according to the fourth embodiment, viewed in the first direction D1. Fig. 11 is a conceptual diagram of a modified example of the heat exchanger 100 according to the fourth embodiment, viewed in the first direction D1. The heat exchanger 100 according to the fourth embodiment is obtained by modifying the configuration of the heat transfer tube 10 in the heat exchanger 100 according to the first embodiment. Note that in Fig. 10, the upper and lower partitions 90 provided inside the heat transfer tube 10 are indicated by dashed lines. Components having the same functions and actions as those in the first to third embodiments are denoted by the same reference numerals, and their description will be omitted.

[0094] As shown in Figures 10 and 11, each of the multiple heat transfer tubes 10 is arranged in the internal space of the tube wall 11 and has at least one upper and lower partition portions 90 extending through the internal space in a third direction D3 perpendicular to the first direction D1 and the second direction D2, respectively.

[0095] 10 and 11, the upper and lower partitions 90 separate two of the multiple header sections 50 arranged in parallel in the second direction D2, thereby dividing the internal space of the heat transfer tube 10 into upper and lower parts. Alternatively, as shown in Fig. 11, the upper and lower partitions 90 separate two of the multiple end side header sections 55 arranged in parallel in the second direction D2, thereby dividing the internal space of the heat transfer tube 10 into upper and lower parts.

[0096] In the heat exchanger 100, two or more refrigerant paths are formed by the upper and lower partitions 90, the multiple header sections 50, and the end header sections 55. Fig. 10 shows, as an example, a heat exchanger 100 having two refrigerant paths. Fig. 11 shows, as an example, a heat exchanger 100 having four refrigerant paths.

[0097] 10, each of the multiple heat transfer tubes 10 is disposed in the internal space of the tube wall 11 and has an upper and lower partition portion 90 that separates the first header portion 51 and the second header portion 52. The upper and lower partition portion 90 extends through the internal space of the heat transfer tube 10 in a third direction D3 that is perpendicular to the first direction D1 and the second direction D2, respectively, and divides the internal space of the heat transfer tube 10 into upper and lower spaces. The internal space of the heat transfer tube 10 is separated by the upper and lower partition portion 90 into an upper space 10f and a lower space 10g.

[0098] The upper and lower partitions 90 are plate- or rod-shaped members extending in the third direction D3 in the internal space of the heat transfer tube 10. The upper and lower partitions 90 shown in Fig. 10 are formed in a substantially Z-shape when viewed in the first direction D1, but are not limited to this shape. For example, the upper and lower partitions 90 may be formed in an inclined straight line when viewed in the first direction D1 so that the height positions of both ends in the third direction D3 are different.

[0099] The upper and lower partition portion 90 is provided so as to connect with the tube side wall portion 10a and the tube side wall portion 10b (see FIG. 4). The upper and lower partition portion 90 is provided so as to extend between the tube side wall portion 10a and the tube side wall portion 10b.

[0100] The multiple header sections 50 include a first header section 51 serving as an inlet for the refrigerant, and a second header section 52 serving as an outlet for the refrigerant.

[0101] The multiple connection portions 12 or the multiple header tubes 80 constitute multiple end side header sections 55 formed to extend in the first direction D1. The end side header sections 55 communicate the refrigerant with the internal spaces of the multiple heat transfer tubes 10, and serve as refrigerant inlets and outlets for the heat transfer tube group 15 constituted by the multiple heat transfer tubes 10. The multiple end side header sections 55 are formed closer to the ends of the multiple heat transfer tubes 10 than the multiple header sections 50 in the second direction D2.

[0102] The end side header section 55 has a similar structure to the header section 50. That is, the end side header section 55 is configured by directly or indirectly connecting the through holes 30 of the heat transfer tubes 10 to each other. The end side header section 55 is configured by the connecting section 12 or the header tube 80. The end side header section 55 is provided closer to the end of the heat transfer tube 10 than the header section 50 provided in the central section 17.

[0103] The multiple end side header sections 55 include a third header section 56 serving as an inlet for the refrigerant, and a fourth header section 57 serving as an outlet for the refrigerant.

[0104] The third header section 56 is formed below the first header section 51 and the second header section 52, and forms a refrigerant inlet through which the refrigerant flowing out from the second header section 52 flows in. The fourth header section 57 is formed above the first header section 51 and the second header section 52, and forms a refrigerant outlet through which the refrigerant flowing in from the first header section 51 flows out.

[0105] A header flow path P1e or a header flow path P1f is formed inside the header pipe 80 or the connecting portion 12. For example, the header pipe 80 or the connecting portion 12 constituting the third header section 56 constitutes the header flow path P1e, and the header pipe 80 or the connecting portion 12 constituting the fourth header section 57 constitutes the header flow path P1f.

[0106] The refrigerant flow path of the heat exchanger 100 of the fourth embodiment is composed of a plurality of heat transfer flow paths P1a, and header flow paths P1b and P1c (see FIG. 3) provided in parallel in the front and rear directions in a central portion 17 of the heat exchanger 100. The refrigerant flow path of the heat exchanger 100 is also composed of header flow paths P1e and P1f provided on the end side in the second direction D2 relative to the central portion 17 of the heat exchanger 100.

[0107] The heat transfer flow path P1a communicates with the header flow path P1e and the header flow path P1f at the end side of the heat transfer flow path P1a in the longitudinal direction (second direction D2) of the heat transfer tube 10. The header flow path P1e and the header flow path P1f each communicate with a plurality of heat transfer flow paths P1a. When the heat transfer tube 10 has a connecting portion 12 (see FIG. 2), the above-mentioned through hole 30a, the through hole 30b, the hollow portion Sg of the connecting portion 12, etc. constitute the header flow path P1e and the header flow path P1f, and the refrigerant flows through the hollow portion Sg.

[0108] In the heat exchanger 100, header flow paths P1b, P1c, P1e, and P1f are formed in the heat transfer tubes 10, which are heat exchange members, so that there is no need to provide a header portion on the outside of the multiple heat transfer tubes 10.

[0109] [Effects of the heat exchanger 100] 12 is a conceptual diagram of a heat exchanger 100L according to a comparative example viewed in a first direction D1. The heat exchanger 100L according to the comparative example is a conventional heat exchanger having header portions 50L at both ends of a heat transfer tube 10L in the second direction D2. Since the heat exchanger 100 according to the comparative example has the header portions 50L at both ends of the heat transfer tube 10L in the second direction D2, the effective area E for heat exchange by the heat transfer tube 10L is reduced compared to a case where the header portions 50 are not provided.

[0110] The multiple connection parts 12 or the multiple header tubes 80 in the heat exchanger 100 according to the fourth embodiment constitute multiple end-side header sections 55 formed to extend in the first direction D1. The end-side header section 55 communicates the refrigerant with the internal space of each of the multiple heat transfer tubes 10, and serves as an inlet and outlet for the refrigerant of the heat transfer tube group 15 constituted by the multiple heat transfer tubes 10. The multiple end-side header sections 55 are formed on the end side of the multiple heat transfer tubes 10 relative to the multiple header sections 50 in the second direction D2. Each of the multiple heat transfer tubes 10 is disposed in the internal space of the tube wall 11, extends through the internal space in a third direction D3 perpendicular to the first direction D1 and the second direction D2, and has at least one or more upper and lower partition sections 90 that divide the internal space of the heat transfer tube 10 into upper and lower parts. The upper and lower partition sections 90 separate two header sections 50 arranged in parallel in the second direction D2 among the multiple header sections 50. Alternatively, the upper and lower partitions 90 separate two end side header sections 55 that are arranged in parallel in the second direction D2 among the multiple end side header sections 55. In the heat exchanger 100, the upper and lower partitions 90, the multiple header sections 50, and the end side header sections 55 form two or more refrigerant paths.

[0111] In the heat exchanger 100 according to the fourth embodiment, a header portion is provided directly on the heat transfer tube 10 by a plurality of header portions 50 and a plurality of end side header portions 55. Therefore, in the heat exchanger 100 according to the fourth embodiment, the effective area E for heat exchange is not reduced by the header portion as in the heat exchanger 100L of the comparative example shown in FIG.

[0112] When the heat exchanger 100 according to the fourth embodiment and the heat exchanger 100L according to the comparative example have the same height, the effective area E for heat exchange in the heat exchanger 100 is larger than the effective area E for heat exchange in the heat exchanger 100L of the comparative example shown in Fig. 12. That is, in the conventional heat exchanger 100L such as the comparative example, the effective area for heat exchange, which is reduced when the header section 50L is disposed above and below the heat transfer tube 10L, is increased in the heat exchanger 100 according to the fourth embodiment. Therefore, the effective area for heat exchange in the heat exchanger 100 according to the fourth embodiment is larger than that in the heat exchanger 100L not having the above configuration, and the heat exchange efficiency can be improved.

[0113] The heat exchanger 100 according to the fourth embodiment has at least one or more upper and lower partitions 90 that divide the internal space of the heat transfer tube 10 into upper and lower spaces. The heat exchanger 100 shortens the distance that the refrigerant rises compared to a case in which the heat exchanger 100 does not have the upper and lower partitions 90. Therefore, the heat exchanger 100 can reduce the head difference and suppress liquid retention compared to a case in which the heat exchanger 100 does not have the upper and lower partitions 90, thereby improving the heat exchange efficiency.

[0114] The upper and lower partitions 90 are disposed in the internal space of the pipe wall 11 and separate the first header section 51 and the second header section 52. The third header section 56 is formed below the first header section 51 and the second header section 52, and forms a refrigerant inlet through which the refrigerant flowing out from the second header section 52 flows. The fourth header section 57 is formed above the first header section 51 and the second header section 52, and forms a refrigerant outlet through which the refrigerant flowing in from the first header section 51 flows out. Compared to a case not having this configuration, the heat exchanger 100 does not have an effective area E for heat exchange that is reduced by the header section as in the heat exchanger 100L of the comparative example shown in FIG. 12. Therefore, the heat exchanger 100 according to the fourth embodiment has a wider effective area for heat exchange and can improve the heat exchange efficiency compared to the heat exchanger 100L not having this configuration.

[0115] Furthermore, the air conditioning device 200 is equipped with the heat exchanger 100. Because the air conditioning device 200 is equipped with the heat exchanger 100, it is able to achieve the effects of the heat exchanger 100 described above.

[0116] Embodiment 5. 13 is a conceptual diagram of a heat exchanger 100 according to embodiment 5 as viewed in a first direction D1. Note that components having the same functions and actions as those in embodiments 1 to 4 are given the same reference numerals and descriptions thereof will be omitted.

[0117] When the number of heat transfer tubes 10 is N, the total flow path cross-sectional area A of the heat transfer tubes 10 is calculated by the following formula (1). A = a × N [m 2 ]·····(1) a: Flow passage cross-sectional area [m 2 ] N: Number of heat transfer tubes (10) The pressure difference in the refrigerant flow path (hereinafter referred to as the flow path pressure difference) is ΔP HEX , liquid head ΔP HEAD If we define ΔP HEX / ΔP HEAD can be calculated using the following formula (2). HEX is the pressure difference between the upper and lower ends of the heat transfer tube 10 in the heat transfer tube group 15. ΔP HEX / ΔP HEAD =(5.94635×10-4×A-1.75030) / (8.4303HSinθ+0.8779)>1····(2) A: total flow cross-sectional area of ​​the heat transfer tubes 10 [m 2 ] H: Length of the heat transfer tube 10 in the second direction D2 [m] θ: the inclination angle [°] of the multiple heat transfer tubes 10 with respect to the horizontal plane F when the first direction D1 is parallel to the horizontal plane F

[0118] The length H [m] of the heat transfer tube 10 in the second direction D2 is particularly effective when it is longer than 0.420 [m] (length H>0.420). Many heat exchangers using corrugated fins used in outdoor units of car air conditioners and the like have a heat transfer tube length of about 0.300 [m], whereas many heat exchangers used in outdoor units of buildings and the like have a heat transfer tube length of 0.420 [m] or more.

[0119] According to the research of the inventors, for example, when the length H of the heat transfer tube 10 is increased to about 0.420 [m], ΔP HEX / ΔP HEAD It was found that the head difference decreases. The inventors also found that when the length H of the heat transfer tube in the heat exchanger is 0.420 [m] or more, a head difference occurs, and liquid stagnation occurs in a part of the heat exchanger, making it difficult for the liquid refrigerant to flow. The heat exchanger 100 according to the fifth embodiment can suppress liquid stagnation by satisfying the above formula (2) even when the length H [m] of the heat transfer tube in the second direction D2 is longer than 0.420 [m], and can improve the heat exchanger performance.

[0120] The above formula (2) is an empirical formula obtained by the inventors through numerical analysis and experimental results. Formula (2) expresses the flow path differential pressure ΔP HEX is the total flow cross-sectional area A [m 2 ] and liquid head ΔP HEAD and the length H [m] of the heat transfer tube 10, which is a dominant geometric parameter of the heat exchanger 100. Equation (2) is formulated within a range of conditions in which the heat exchanger 100 is used in an outdoor unit 231 (see FIG. 6) for buildings, stores, homes, etc.

[0121] [Effects of the heat exchanger 100] If the heat exchanger is mounted on the outdoor unit with the header installed horizontally and the heat transfer tubes extending in the direction of gravity, the distance in the length H direction of the heat transfer tube will become long, and the liquid refrigerant may not be able to rise all the way up the heat transfer tube and may become stagnant.

[0122] The heat exchanger 100 according to the fifth embodiment has a ΔP HEX / ΔP HEAD =(5.94635×10-4×A-1.75030) / (8.4303HSinθ+0.8779)>1. When the heat exchanger 100 is used within the range of this formula, it is possible to suppress the occurrence of liquid stagnation, in which the refrigerant that has liquefied due to the influence of gravity cannot rise and remains when the refrigerant flows as an upward current inside the heat transfer tube 100, and it is possible to improve the heat exchanger performance.

[0123] Furthermore, the air conditioning device 200 is equipped with the heat exchanger 100. Because the air conditioning device 200 is equipped with the heat exchanger 100, it is able to achieve the effects of the heat exchanger 100 described above.

[0124] Although the embodiments have been described above, the present disclosure is not limited to the above-described embodiments. For example, the present disclosure may be configured by combining the respective embodiments. [Explanation of symbols]

[0125] 10 heat transfer tube, 10L heat transfer tube, 10a tube side wall portion, 10b tube side wall portion, 10c connection wall portion, 10d connection wall portion, 10e opening end, 10f upper space, 10g lower space, 11 tube wall, 12 connection portion, 12a connection protrusion portion, 12b connection protrusion portion, 15 heat transfer tube group, 17 center portion, 20 tube sealing portion, 30 through hole, 30a through hole, 30b through hole, 50 header portion, 50L header portion, 51 first header portion, 51a inlet / outlet, 52 second header portion, 52a inlet / outlet, 55 end side header portion, 56 third header portion, 57 fourth header portion, 60 convex portion, 70 partition portion, 70a upper end, 70b lower end, 80 header tube, 82 hole, 90 Upper and lower partitions, 100 heat exchanger, 100L heat exchanger, 200 air conditioning device, 201 compressor, 202 flow path switching device, 203 outdoor heat exchanger, 203a outdoor fan, 204 expansion valve, 205 indoor heat exchanger, 205a indoor fan, 221 condenser, 222 evaporator, 231 outdoor unit, 232 indoor unit, 250 refrigerant circuit, 255 refrigerant piping, P1a heat transfer flow path, P1a1 first flow path, P1a2 second flow path, P1b header flow path, P1c header flow path, P1e header flow path, P1f header flow path, P2 flow path, Sg hollow portion.

Claims

1. a plurality of heat transfer tubes arranged in a first direction, each extending in a second direction intersecting the first direction, both ends of which are sealed in the second direction, through which a refrigerant flows; Each of the plurality of heat transfer tubes has a plurality of through holes are formed inside the both end portions and communicating the internal space of each of the plurality of heat transfer tubes with the outside; The plurality of heat transfer tubes include Among the plurality of heat transfer tubes, a plurality of connection portions directly connecting the plurality of through holes of adjacent heat transfer tubes are provided, or a plurality of header tubes are inserted into the plurality of through holes and connecting the plurality of through holes of adjacent heat transfer tubes among the plurality of heat transfer tubes are provided, The plurality of connection portions or the plurality of header pipes are a plurality of header sections formed to extend in the first direction, the header sections communicating a refrigerant between the internal spaces of the plurality of heat transfer tubes and serving as inlets and outlets for the refrigerant of a heat transfer tube group formed by the plurality of heat transfer tubes; The plurality of header portions include a pressure adjusting portion for dividing the heat transfer tubes into upper and lower portions in the gravity direction; The flow passage cross-sectional area a of each of the plurality of heat transfer tubes is defined as a [m 2 ]; When the number of the heat transfer tubes is N, a total flow passage cross-sectional area A of the plurality of heat transfer tubes is defined as A [m 2 ] = a × N [m 2 ]; The length of the plurality of heat transfer tubes in the second direction is defined as H [m], When the first direction is a direction parallel to a horizontal plane, an inclination angle of the plurality of heat transfer tubes with respect to the horizontal plane is defined as θ [°]; The pressure difference in the refrigerant flow path is defined as ΔP HEX , If the liquid head is defined as ΔP HEAD , then A heat exchanger which satisfies the relationship: ΔP HEX / ΔP HEAD = (5.94635 × 10 -4 × A - 1.75030) / (8.4303 H Sin θ + 0.8779) > 1.

2. The plurality of header portions include The heat exchanger according to claim 1 , wherein the first heat transfer tube is provided at a central portion of the plurality of heat transfer tubes in the second direction.

3. Each of the plurality of heat transfer tubes is The internal space has a pipe wall provided with a heat transfer flow path through which a refrigerant flows, The pipe wall has pipe side wall portions facing each other in the first direction, and the through hole is formed in the pipe side wall portions, Each of the plurality of heat transfer tubes is a partition portion disposed in the internal space of the pipe wall, extending in the second direction, and dividing the internal space into a third direction perpendicular to the first direction and the second direction, both ends of the partition portion in the second direction are located inside of both ends of the heat transfer flow path of the heat transfer tube in the second direction, The plurality of header portions include A first header portion serving as an inlet for a refrigerant; A second header portion serving as an outlet for the refrigerant; Including, The first header portion and the second header portion are The heat exchanger according to claim 1 or 2, wherein the first and second heat exchangers are provided on both sides of the partition portion with the partition portion therebetween in the third direction.

4. a refrigerant having a liquid component greater than a gas component flows in the internal space on the first header portion side than in the internal space on the second header portion side, The partition portion is the first header portion is provided at a position closer to the first header portion than the central portion in the third direction, 4. The heat exchanger according to claim 3, wherein a flow passage cross-sectional area of ​​the internal space on the first header side is smaller than a flow passage cross-sectional area of ​​the internal space on the second header side.

5. A heat transfer tube arranged in a first direction, each extending in a second direction intersecting the first direction, both ends of which are sealed in the second direction and through which a refrigerant flows; Each of the plurality of heat transfer tubes has a plurality of through holes are formed inside the both end portions and communicating the internal space of each of the plurality of heat transfer tubes with the outside; The plurality of heat transfer tubes include Among the plurality of heat transfer tubes, a plurality of connection portions directly connecting the plurality of through holes of adjacent heat transfer tubes are provided, or a plurality of header tubes are inserted into the plurality of through holes and connecting the plurality of through holes of adjacent heat transfer tubes among the plurality of heat transfer tubes are provided, The plurality of connection portions or the plurality of header pipes are a plurality of header sections formed to extend in the first direction, the header sections communicating a refrigerant between the internal spaces of the plurality of heat transfer tubes and serving as inlets and outlets for the refrigerant of a heat transfer tube group formed by the plurality of heat transfer tubes; The plurality of header portions include a pressure adjusting portion for dividing the heat transfer tubes into upper and lower portions in the gravity direction; Each of the plurality of heat transfer tubes is The internal space has a pipe wall provided with a heat transfer flow path through which a refrigerant flows, The pipe wall has pipe side wall portions facing each other in the first direction, and the through hole is formed in the pipe side wall portions, The plurality of connection portions or the plurality of header pipes are a plurality of end side header sections formed to extend in the first direction, the end side header sections communicating a refrigerant between the internal spaces of the plurality of heat transfer tubes and serving as inlets and outlets for the refrigerant of the heat transfer tube group constituted by the plurality of heat transfer tubes; The plurality of end side header portions include the heat transfer tubes are arranged closer to the ends of the heat transfer tubes than the header portions are arranged in the second direction, Each of the plurality of heat transfer tubes is at least one upper and lower partition section is disposed in the internal space of the pipe wall, extends through the internal space in a third direction perpendicular to the first direction and the second direction, separates two of the plurality of header sections arranged in parallel in the second direction, or separates two of the plurality of end side header sections arranged in parallel in the second direction, and divides the internal space into upper and lower parts; A heat exchanger in which two or more refrigerant paths are formed by the upper and lower partitions, the plurality of header sections, and the end side header section.

6. The plurality of header portions include A first header portion serving as an inlet for a refrigerant; A second header portion serving as an outlet for the refrigerant; Including, The upper and lower partitions are a first header portion and a second header portion disposed in the internal space of the pipe wall, the first header portion and the second header portion being separated from each other; The plurality of end side header portions include a third header portion serving as an inlet for the refrigerant; a fourth header portion serving as an outlet for the refrigerant; Including, The third header portion is a refrigerant inlet for receiving the refrigerant flowing out from the second header portion; The fourth header portion is The heat exchanger according to claim 5 , further comprising a refrigerant outlet formed above the first header portion and the second header portion and through which the refrigerant flowing in from the first header portion flows out.

7. Each of the plurality of heat transfer tubes is The heat exchanger according to claim 1 or 5, further comprising at least one protrusion protruding into the internal space of the heat transfer tube.

8. The flow passage cross-sectional area a of each of the plurality of heat transfer tubes is a [m ２ ], When the number of the heat transfer tubes is N [tubes], the total flow passage cross-sectional area A of the plurality of heat transfer tubes is A [m ２ ] = a × N [m ２ ], The length of the plurality of heat transfer tubes in the second direction is defined as H [m], When the first direction is a direction parallel to a horizontal plane, an inclination angle of the plurality of heat transfer tubes with respect to the horizontal plane is defined as θ [°]; The pressure difference in the refrigerant flow path is ΔP ＨＥＸ Define it as: Liquid head ΔP ＨＥＡＤ If we define ΔP ＨＥＸ / ΔP ＨＥＡＤ The heat exchanger according to claim 5 or 6, which satisfies the relationship: = (5.94635 × 10-4 × A-1.75030) / (8.4303HSinθ + 0.8779) > 1.

9. An air conditioner comprising the heat exchanger according to claim 1 or 5.

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