Heat exchanger and air conditioning device having the same

Abstract

A heat exchanger and an air conditioning device having the heat exchanger can be provided, wherein even a heat exchanger having a heat transfer tube inserted therein can reduce the pressure loss of the refrigerant and have excellent heat exchange performance. The heat exchanger (100) comprises: a plurality of heat transfer tubes (2) arranged at intervals from each other in a first direction; a header (1) having an insertion hole (11a) for inserting the front end of each of the plurality of heat transfer tubes (2) from a second direction orthogonal to the first direction; and fins (3) mounted on the heat transfer tubes (2). The header (1) comprises a partition (13) which divides the interior of the header into a first space (15) on a side where the insertion hole (11a) is provided and a second space (16) to which the refrigerant pipe (4) is connected. The partition (14) is provided with an opening (14a) surrounding the outer periphery of the front end of the heat transfer tube (2) when viewed from the second direction. In addition, the air conditioning device (200) comprises the heat exchanger (100) as a condenser or an evaporator.

Description

Technical Field

[0001] The present disclosure relates to a heat exchanger including a header for collecting or distributing a refrigerant, and an air conditioning device including the heat exchanger. Background Art

[0002] Among heat exchangers having a header to which a plurality of heat transfer tubes are connected, there is known a heat exchanger in which the interior of the header is divided into a first space in which the plurality of heat transfer tubes are inserted and a second space in which the plurality of heat transfer tubes are not inserted by a partition plate, and a connecting hole is formed on the partition plate to connect the first space and the second space (for example, see Patent Document 1).

[0003] In Patent Document 1, in order to solve the problem caused by the passage resistance of the communicating hole of the partition plate, the communicating hole is inclined with respect to the refrigerant flow direction, and a guide for guiding the flow of the refrigerant is formed at the downstream edge portion in the refrigerant flow direction.

[0004] Prior art literature

[0005] Patent Literature

[0006] Patent Document 1: Japanese Patent Application Publication No. 2016-57036 Summary of the invention

[0007] Problems to be solved by the invention

[0008] In conventional heat exchangers, in order to connect the heat transfer tubes to the header and fix them by brazing, the heat transfer tubes need to protrude into the header. If the heat transfer tubes protrude into the header, the protruding portions form concavities and convexities, which may increase the pressure loss of the refrigerant flowing in the header. In addition, in Patent Document 1, the refrigerant flowing into the header from the heat transfer tubes collides with the partitions, which may cause pressure loss.

[0009] The present disclosure is made to solve the above-mentioned problems, and its purpose is to provide a heat exchanger and an air-conditioning device equipped with the heat exchanger. Even if the heat transfer tube is inserted into the inside of the header, the pressure loss of the refrigerant inside the header can be reduced and the heat exchange performance is excellent.

[0010] Solutions to Solve Problems

[0011] The heat exchanger involved in the present disclosure comprises: a plurality of heat transfer tubes, which are arranged at intervals from each other in a first direction; a header, which has an insertion hole for inserting the front ends of each of the plurality of heat transfer tubes from a second direction orthogonal to the first direction; and fins, which are installed on the heat transfer tubes, wherein the header comprises a partition, which divides the interior of the header into a first space on a side where the insertion hole is provided and a second space to which the refrigerant piping is connected, and an opening portion is provided on the partition for surrounding the outer periphery of the front ends of the heat transfer tubes when viewed from the second direction.

[0012] The air conditioner according to the present disclosure includes a refrigerant circuit in which a compressor, a condenser, an expansion valve, an evaporator, and a four-way valve are connected by pipes and a refrigerant flows, and the air conditioner includes the heat exchanger as a condenser or an evaporator.

[0013] Effects of the Invention

[0014] According to the present disclosure, a heat exchanger and an air-conditioning device equipped with the heat exchanger can be provided. The heat exchanger can reduce the pressure loss of the refrigerant and has excellent heat exchange performance by having a partition. The partition divides the interior of the collecting pipe into a first space on one side with an insertion hole and a second space connected to the refrigerant piping, and is provided with an opening portion surrounding the outer periphery of the front end of the heat transfer tube when viewed from a second direction. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 This is a schematic configuration diagram of the heat exchanger according to Embodiment 1.

[0016] Figure 2 It is a perspective view partially showing the structure of the collecting header according to the first embodiment.

[0017] Figure 3 This is a cross-sectional view of the collecting header according to Embodiment 1 as viewed from the second direction.

[0018] Figure 4 It is a diagram showing the width of the opening of the spacer according to the first embodiment.

[0019] Figure 5 This is a diagram showing the relationship between the width of the opening of the separator and the pressure loss in the first embodiment.

[0020] Figure 6 The heat exchanger of Embodiment 1 is Figure 1 Sectional view observed along the cutting line AA.

[0021] Figure 7 The heat exchanger of Embodiment 1 Figure 6 A partial enlarged view of .

[0022] Figure 8The heat exchanger of Embodiment 1 Figure 6 A partial enlarged view of .

[0023] Fig. 9 The heat exchanger of Embodiment 1 Figure 6 A partial enlarged view of .

[0024] Fig.10 This is a cross-sectional view of the heat exchanger according to Embodiment 1 cut along a plane parallel to the first direction.

[0025] Fig.11 This is a schematic diagram showing the flow of the refrigerant inside the collecting header according to Embodiment 1.

[0026] Fig.12 This is a schematic diagram showing the flow of the refrigerant inside the collecting header according to Embodiment 1.

[0027] Fig.13 It is a diagram showing changes in the flow rate and pressure loss of the refrigerant inside the collecting header according to Embodiment 1.

[0028] Fig.14 This is a schematic diagram showing the flow of the refrigerant in the distribution header according to Embodiment 1.

[0029] Fig.15 This is a cross-sectional view of the heat exchanger according to Embodiment 2 cut along a plane parallel to the first direction.

[0030] Fig.16 This is a perspective view of a partition plate according to the second embodiment.

[0031] Fig.17 This is a cross-sectional view of the heat exchanger according to Embodiment 3 cut along a plane parallel to the first direction.

[0032] Fig.18 This is a perspective view of a partition plate according to the third embodiment.

[0033] Fig.19 This is a cross-sectional view of the heat exchanger according to Embodiment 4 cut along a plane parallel to the first direction.

[0034] Fig. 20 This is a perspective view of a partition plate according to a fourth embodiment.

[0035] Fig.21 This is a refrigerant circuit diagram showing an air-conditioning apparatus according to Embodiment 5. DETAILED DESCRIPTION

[0036] First, the embodiments of the present disclosure are described with reference to the accompanying drawings. In each figure, the parts marked with the same figure mark are the same or equivalent parts, which are common to the entire text of the specification. It should be noted that the forms of the constituent elements shown in the entire specification are only examples and are not limited to these records.

[0037] In addition, throughout the specification, mutually orthogonal directions are defined as the first direction, the second direction, and the third direction. Furthermore, as an example, a case where the first direction is defined as the horizontal direction, the second direction is defined as the vertical direction, and the third direction is defined as the width direction of the header is described, but this is not limited to the direction of the flow of the refrigerant, etc. It should be noted that in the drawings, the X direction corresponds to the first direction, the Y direction corresponds to the second direction, and the Z direction corresponds to the third direction.

[0038] In addition, in the following description, for easy understanding, terms indicating directions, such as "upper", "lower", "right", "left", etc., are appropriately used, but this is for explanation and these terms do not limit the present disclosure. It should be noted that "upper", "lower", "right", "left", etc. are used when the heat exchanger 100 is viewed from the side.

[0039] Implementation method 1.

[0040] Figure 1 It is a schematic structural diagram of the heat exchanger 100 which is Embodiment 1 of the present disclosure.

[0041] like Figure 1 As shown, the heat exchanger 100 according to Embodiment 1 includes a header 1 ( 1 a , 1 b ), a plurality of heat transfer tubes 2 , fins 3 , and refrigerant pipes 4 ( 4 a , 4 b ).

[0042] The header 1 (1a, 1b) is cylindrical in shape and is composed of a header upper plate 11, a header body 12, a side cover 13, and a partition plate 14 (not shown), and is arranged so that the long side direction of the header 1 (1a, 1b) is horizontal. Figure 1 In the figure, the long side direction of the header 1 (1a, 1b) is arranged to be perpendicular to the flow of air flowing from the front direction to the back side of the paper. Figure 1 In the vertical cross-sectional view of the header 1 (1a, 1b), a D-shaped example is shown, but a rectangular shape or a circular shape may also be used.

[0043] In addition, the header 1 (1a, 1b) is connected to the refrigerant distribution pipe 4 (4a, 4b) and a plurality of heat transfer tubes 2, and the refrigerant flows inside. The header 1 connected to the refrigerant inlet pipe 4a and distributing the refrigerant flowing in from the refrigerant inlet pipe 4a to each of the plurality of heat transfer tubes 2 is called a distribution header 1a. In addition, the header 1 connected to the refrigerant outflow pipe 4b and collecting the refrigerant in a manner that the refrigerant flowing out from the plurality of heat transfer tubes 2 can be discharged to the outside of the heat exchanger 100 through the refrigerant outflow pipe 4b is called a collection header 1b. It should be noted that a detailed description of the structure of the header 1 (1a, 1b) will be described later.

[0044] A plurality of heat transfer tubes 2 are arranged at intervals from each other in a first direction (X direction). One of the two ends of the heat transfer tube 2 is connected to the distribution header 1a, and the other end is connected to the collection header 1b. The heat transfer tubes 2 are metal tubes with a hollow interior, for example, flat tubes with a flat cross-section. Since they are made of metal, they have good thermal conductivity, and heat exchange between the refrigerant flowing inside the heat transfer tube 2 and the air outside the heat transfer tube 2 is easy. By exchanging heat between the refrigerant flowing inside the heat transfer tube 2 and the air outside the heat transfer tube 2, the refrigerant can be cooled to gasify it, or heated to liquefy it.

[0045] It should be noted that in Figure 1 In FIG. 1 , a flat tube is shown as an example of the heat transfer tube, but the shape of the heat transfer tube 2 is not limited thereto, and air may be another fluid.

[0046] The fin 3 is, for example, a corrugated metal plate, which is inserted between the plurality of heat transfer tubes 2 and joined to the surface of the adjacent heat transfer tubes 2, thereby being attached to the heat transfer tubes 2. Since the fin 3 is made of a heat-conducting material such as metal, it is possible to conduct heat from the joined heat transfer tubes 2 and perform heat exchange with the air or the like flowing in the gap. In addition, by forming the corrugated shape, the surface area in contact with the fluid such as the air for heat exchange is large, and heat exchange can be performed efficiently.

[0047] The refrigerant pipes 4 (4a, 4b) are connected to the side covers 13 of the side faces of the headers 1 (1a, 1b). As described above, the refrigerant pipes 4 connected to the distribution header 1a are the refrigerant inlet pipes 4a, and the refrigerant pipes 4 connected to the collection header 1b are the refrigerant outlet pipes 4b.

[0048] The refrigerant inflow pipe 4a allows the refrigerant to flow from the outside of the heat exchanger 100 into the distribution header 1a, and the refrigerant outflow pipe 4b allows the refrigerant collected in the collection header 1b to flow out of the heat exchanger 100. Figure 1 As shown, the refrigerant inflow pipe 4a and the refrigerant outflow pipe 4b are connected to, for example, different side surfaces.

[0049] The refrigerant flowing in the heat exchanger 100 is Figure 1 As shown by the solid arrows, the refrigerant flows from the refrigerant inlet pipe 4a into the distribution header 1a, and is distributed to each of the plurality of heat transfer tubes 2 through the distribution header 1a. The distributed refrigerant flows through the heat transfer tubes 2, is collected by the collection header 1b, and is discharged from the refrigerant outlet pipe 4b.

[0050] When the refrigerant flowing in is a gas-liquid two-phase state in which gas refrigerant and liquid refrigerant are mixed, and the gas-liquid two-phase refrigerant is evaporated by passing through the heat transfer tube 2, the heat exchanger 100 is called an evaporator. On the other hand, when the refrigerant flowing in is a gas and the refrigerant is condensed by passing through the heat transfer tube 2, the heat exchanger 100 is called a condenser. It should be noted that when the heat exchanger 100 is used as a condenser, the flow direction of the refrigerant is the same as that of the heat exchanger 100. Figure 1 The solid arrow points in the opposite direction.

[0051] Next, the detailed structure of the header 1 of the heat exchanger 100 of the present embodiment will be described. In the following description, the collecting header 1b is taken as an example, but the present disclosure is not limited to the collecting header 1b, and the distributing header 1a may also be used.

[0052] Figure 2 It is a perspective view partially showing the structure of the header according to the first embodiment. Figure 3 This is a cross-sectional view when the header of Embodiment 1 is viewed from the second direction, and shows the positional relationship between the heat transfer tubes 2 and the openings 14 a of the partition plates 14 . Figure 4 It is a diagram showing the width of the opening of the spacer according to the first embodiment. Figure 5 This is a diagram showing the relationship between the width of the opening 14 a of the separator 14 and the pressure loss according to the first embodiment.

[0053] like Figure 2 As shown, the header upper plate 11 of the collecting header 1b is provided with insertion holes 11a, which are arranged at intervals in the first direction (X direction) for inserting the front ends of the heat transfer tubes 2 from the second direction (Y direction). The heat transfer tubes 2 are inserted into the insertion holes 11a from the header upper plate 11 toward the header body 12, and the header upper plate 11 and the insertion holes 11a are fixed in a sealed manner without a gap by brazing or the like. That is, the vertical direction (second direction) of the heat transfer tubes 2 is the long side direction.

[0054] The partition 14 is a flat plate made of a metal such as aluminum, and is fixed to the manifold body 12 and the side cover 13 of the manifold 1b by brazing or the like. It should be noted that the partition 14 need not be fixed to the inner wall of the manifold body 12 around the entire periphery, and the refrigerant flowing inside the manifold may pass between the partition 14 and the inner wall of the manifold body 12. In addition, the partition 14 may be formed integrally with the manifold 1b. In addition, as Figure 2 As shown, the partition plate 14 is provided with a plurality of openings 14a into which the plurality of heat transfer tubes 2 are inserted respectively.

[0055] Figure 3 This is a diagram showing the interior of the collecting header 1b as viewed from the lower side in the second direction (Y direction), and is a schematic diagram showing the positional relationship between the heat transfer tube 2 and the opening 14a of the partition 14. The partition 14 is provided with an opening 14a surrounding the outer periphery of the front end of the heat transfer tube 2, that is, an opening 14a having an opening into which the heat transfer tube 2 can be inserted when viewed from the second direction.

[0056] In addition, if Figure 3 As shown, the opening 14a provided in the partition 14 is in a shape having a gap between the opening 14a and the outer periphery of the front end of the heat transfer tube 2 when viewed from the second direction (Y direction). That is, when the inside of the collecting header 1b is viewed from the second direction (Y direction), the opening 14a is in a shape surrounding the heat transfer tube 2 at a distance from the outer periphery of the front end of the heat transfer tube 2. The shape of the opening 14a is not limited to the same shape as the heat transfer tube 2 as long as there is a gap between the opening 14a and the outer periphery of the front end of the heat transfer tube 2 when viewed from the second direction (Y direction).

[0057] Figure 4 and Figure 3 Similarly, this is a diagram of the interior of the collection header 1b viewed from the lower side in the second direction (Y direction). Figure 4 As shown in FIG. 1 , the width of the opening 14 a in the first direction (X direction) is defined as K, and the distance between adjacent heat transfer tubes 2 among the plurality of heat transfer tubes 2 is defined as W.

[0058] Figure 5 : is a graph showing the relationship between the width K of the opening 14a and the pressure loss. The vertical axis is the pressure loss inside the collecting header, and the horizontal axis is the width K of the opening 14a in the first direction (X direction). Figure 5 It can be seen that the pressure loss varies according to the width K of the opening 14a. At a certain width K, the pressure loss shows a minimum value, and when the width K is smaller or larger than the width, the pressure loss increases. The opening 14a provided in the partition 14 has an opening area larger than the cross-sectional area of ​​the front end of the heat transfer tube 2, but as Figure 5As shown, if the width K of the opening 14a is too large, there is a tendency for the pressure loss to increase. Therefore, in the present Embodiment 1, the opening 14a provided in the partition 14 satisfies the relationship K < W. That is, the width K of the opening 14a in the first direction (X direction) is smaller than the distance W between adjacent heat transfer tubes 2 among the plurality of heat transfer tubes 2.

[0059] It should be noted that the width K at which the pressure loss shows the minimum value is about twice the width of the heat transfer tube 2. That is, as Figure 4 shown, when the shapes of the heat transfer tube 2 and the opening are flat, by making the width K of the opening 14a about twice the width of the heat transfer tube 2, the pressure loss can be minimized. Therefore, the width K of the opening 14a provided in the partition 14 is most preferably twice the width of the heat transfer tube 2 in size.

[0060] Next, the installation position of the partition 14 inside the header will be described.

[0061] Figure 6 is a cross-sectional view of the heat exchanger 100 of Embodiment 1 observed from the Figure 1 section line A-A. Figure 7 、 Figure 8 and Fig. 9 are partial enlarged views of the Figure 6 of the heat exchanger 100 of Embodiment 1. Figure 7 is an enlarged view of the header when the front end of the heat transfer tube 2 is located in the first space 15. Figure 8 is an enlarged view of the header when the front end of the heat transfer tube 2 is located in the second space 16. Fig. 9 is an enlarged view of the header when the front end of the heat transfer tube 2 is at the same height as the partition 14.

[0062] As Figure 6 shown, the header 1b is separated by the partition 14 into a first space 15 on the side of the header upper plate 11 and provided with insertion holes 11a for the heat transfer tubes 2, and a second space 16 connected to a refrigerant outflow pipe 4b (not shown). The first space 15 and the second space 16 are different spaces, and the partition 14 is provided in such a manner that the first space 15 and the second space 16 are arranged in the vertical direction. In addition, as Figure 6 shown, it is preferable to provide the partition 14 in such a manner that the second space 16 is larger than the first space 15. It should be noted that the first space 15 and the second space 16 are refrigerant flow paths that communicate in the Figure 6 paper depth direction, that is, the long side direction of the header 1b.

[0063] Since the partition plate 14 is provided with an opening 14a that surrounds the outer periphery of the front end of the heat transfer tube 2 when viewed from the second direction (Y direction), the partition plate 14 is arranged such that the front end of the heat transfer tube 2 is located in the first space 15, or at the same position as the partition plate 14, or in the second space 16. Here, in Figure 6 、 Figure 7 、 Figure 8 and Fig. 9 in the second direction (Y direction), the distance between the insertion hole 11a and the front end of the heat transfer tube 2 is defined as the "insertion length D", the distance between the insertion hole 11a and the partition plate 14 is defined as the "first space height H", the distance between the partition plate 14 and the front end of the heat transfer tube 2 is defined as the "gap distance L", and the thickness of the partition plate 14 is defined as "t".

[0064] As Figure 7 、 Figure 8 and Fig. 9 shown, the partition plate 14 of Embodiment 1 of the present disclosure is arranged such that the gap distance L is smaller than the insertion length D and smaller than the first space height H. That is, the partition plate 14 is arranged in a manner that satisfies the relationship L < D and L < H. In this case, the front end of the heat transfer tube 2 is located in the first space 15 or the second space 16.

[0065] In addition, as Figure 7 shown, when the partition plate 14 is arranged such that the front end of the heat transfer tube 2 is located in the first space 15, it is more preferable to arrange the partition plate 14 such that the gap distance L is smaller than half of the first space height H. That is, it is more preferable to arrange the partition plate 14 in a manner that satisfies L < D / 2.

[0066] In addition, as Figure 8 shown, when the partition plate 14 is arranged such that the front end of the heat transfer tube 2 is located in the second space 16, it is more preferable to arrange the partition plate 14 such that the gap distance L is smaller than half of the second space height H. That is, it is more preferable to arrange the partition plate 14 in a manner that satisfies L < H / 2.

[0067] It should be noted that regarding the setting position of the partition plate 14, when comparing the case where the partition plate 14 is arranged such that the front end of the heat transfer tube 2 is located in the first space 15 ( Figure 7 ) and the case where the partition plate 14 is arranged such that the front end of the heat transfer tube 2 is located in the second space 16 ( Figure 8 ), it is preferable to arrange the partition plate 14 such that the front end of the heat transfer tube 2 is located in the second space 16 ( Figure 8 ). That is, it is preferable to arrange the partition plate 14 such that the front end of the heat transfer tube 2 is located in the second space 16.

[0068] And, as Fig. 9As shown, it is more preferable to arrange the spacer 14 so that the gap distance L is less than the thickness t of the spacer 14. That is, it is most preferable to arrange the spacer 14 so as to satisfy L≤t.

[0069] Next, the flow and pressure loss of the refrigerant inside the collecting header will be described.

[0070] Fig.10 This is a cross-sectional view of the heat exchanger 100 according to Embodiment 1 cut along a plane parallel to the first direction (X direction). Fig.11 as well as Fig.12 It is a diagram showing the flow of the refrigerant inside the collecting header according to Embodiment 1. Fig.11 is a diagram showing the flow of the refrigerant when the partition plate 14 is not provided. Fig.12 1 is a diagram showing the flow of the refrigerant when the partition plate 14 is provided. Fig.10 , Fig.11 as well as Fig.12 In FIG. 1 , the solid arrows schematically indicate the flow of the refrigerant.

[0071] like Fig.10 As shown, the refrigerant flowing through the heat transfer tube 2 flows into the second space 16 through the opening 14a provided in the partition 14. At this time, since the opening area of ​​the opening 14a is larger than the cross-sectional area of ​​the front end of the heat transfer tube 2, the refrigerant flowing out of the heat transfer tube 2 flows into the second space 16 without colliding with the partition 14. The refrigerant flowing out of the heat transfer tube 2 merges in the second space 16 and is discharged to the outside of the heat exchanger 100 from the refrigerant outflow pipe 4b provided on the side of the second space 16.

[0072] like Fig.11 As shown, in order to fix the heat transfer tube 2 to the header upper plate 11, the heat transfer tube 2 needs to be inserted into the collecting header 1b with a certain length. However, if the heat transfer tube 2 is inserted to the length required for fixing the heat transfer tube 2, a concave-convex portion is formed inside the collecting header 1b due to the inserted heat transfer tube 2. Hereinafter, it is sometimes referred to as a concave-convex portion for explanation. The front end of the heat transfer tube 2 becomes a convex portion, and the portion of the collecting header 1b where the heat transfer tube 2 is not inserted becomes a concave portion. Since the refrigerant inside the collecting header flows toward the refrigerant outflow pipe, the expansion and contraction of the refrigerant flow path occurs due to the concave-convex portion of the heat transfer tube 2. Due to the expansion and contraction of the refrigerant flow path, the refrigerant is subjected to pressure loss. In addition, when multiple heat transfer tubes 2 are inserted, the expansion and contraction of the refrigerant flow path occur repeatedly, and the pressure loss of the refrigerant flowing inside the collecting header 1b is further increased.

[0073] In addition, inside the collecting pipe, there is also pressure loss caused by the friction between the inner wall surface inside the collecting pipe and the refrigerant, and pressure loss caused when the refrigerant flowing in the collecting pipe 1b merges with the refrigerant flowing in from the heat transfer tube 2 when the refrigerant flows from the heat transfer tube 2 to the collecting pipe 1b. However, the pressure loss caused by the uneven parts of the heat transfer tube 2 in particular has a great impact on the performance degradation of the heat exchanger 100.

[0074] like Fig.12 As shown, when a partition 14 having an opening 14a surrounding the outer periphery of the front end of the heat transfer tube 2 as viewed from the second direction (Y direction) is provided inside the collecting header 1b, the refrigerant flowing out from the front end of the heat transfer tube 2 flows into the collecting header 1b through the opening 14a without colliding with the partition 14. The refrigerant flowing into the collecting header 1b mainly flows in the second space 16 toward the refrigerant outflow pipe 4b. That is, the refrigerant uses the second space 16, which is the space between the partition 14 and the main body of the collecting header, as the main flow path. In addition, since the opening 14a provided in the partition 14 is larger than the cross-sectional area of ​​the front end of the heat transfer tube 2, a part of the refrigerant flowing inside the collecting header 1b flows in the first space 15.

[0075] In such Fig.12 When the partition 14 is provided in this way, the front end of the heat transfer tube 2 becomes a convex portion, and the surface of the partition 14 facing the second space 16 becomes a concave portion. That is, the concave-convex portion caused by the insertion of the heat transfer tube 2 becomes smaller than when the partition 14 is not provided. By reducing the concave-convex portion, the expansion and contraction of the refrigerant flow path are also reduced, and the pressure loss of the refrigerant flowing inside the collecting header can be reduced. In addition, inside the collecting header, the refrigerant mainly flows in the second space. Therefore, even when the partition 14 is provided in such a manner that the front end of the heat transfer tube is located in the first space 15, the influence of the concave-convex portion caused by the insertion of the heat transfer tube on the pressure loss of the refrigerant can be reduced.

[0076] Furthermore, the refrigerant flowing out from the front end of the heat transfer tube 2 flows into the second space 16 without colliding with the partition 14, thereby reducing the pressure loss caused by the collision of the refrigerant with the partition 14. This reduces the pressure loss of the refrigerant flowing inside the collecting header.

[0077] Next, the effects of the heat exchanger 100 according to the present embodiment will be described.

[0078] In the heat exchanger 100 of the first embodiment, by arranging the partition plate 14 having the opening 14a that surrounds the outer periphery of the front end of the heat transfer tube 2 when viewed from the second direction (Y direction) so as to divide the header interior into a first space 15 on the side where the insertion hole 11a of the heat transfer tube 2 is provided and a second space 16 connected to the refrigerant pipe 4, the unevenness generated due to the insertion of the heat transfer tube 2 into the collecting header 1b becomes smaller. Therefore, the expansion and contraction of the refrigerant flow path inside the collecting header can be reduced. Thus, by providing the partition plate 14, the expansion and contraction of the refrigerant flow path can be reduced. Therefore, the change in the cross-sectional area of the refrigerant flow path inside the collecting header becomes smaller, and the pressure loss received by the refrigerant flowing inside can be reduced.

[0079] In addition, by providing the partition plate 14, the refrigerant flowing out from the front end of the heat transfer tube 2 inserted into the header interior can flow into the second space 16, which is the main flow path, without colliding with the partition plate 14. In the existing example, since the communication hole is inclined, the structure has a portion where the heat transfer tube 2 and the communication hole do not overlap, and the refrigerant flowing out from the front end of the heat transfer tube 2 collides with the partition plate 14, which may cause pressure loss. However, like the heat exchanger 100 of the first embodiment, by providing the partition plate 14 with the above structure inside the collecting header 1b, the pressure loss caused by the collision between the refrigerant flowing out from the front end of the heat transfer tube 2 and the partition plate 14 can be suppressed. Thereby, a heat exchanger 100 with excellent heat exchange performance can be provided.

[0080] In addition, since the opening 14a has a shape with a gap between the opening 14a and the outer periphery of the front end of the heat transfer tube 2 when viewed from the second direction, the refrigerant flowing out from the front end of the heat transfer tube 2 can more easily avoid colliding with the partition plate 14, and the pressure loss can be reduced. It should be noted that when the partition plate 14 is arranged such that the front end of the heat transfer tube 2 is located in the second space 16, the refrigerant can flow through the gap formed between the opening 14a and the outer periphery of the heat transfer tube 2 at the opening 14a, and there is no need to provide a communication hole separately, which can also reduce costs.

[0081] In addition, the opening 14a has a structure in which the width K of the opening 14a is smaller than the distance W between adjacent heat transfer tubes 2. The opening area of the opening 14a is larger than the cross-sectional area of the front end of the heat transfer tube 2, but if the opening area is too large, most of the refrigerant flowing in the second space 16 flows into the first space through the opening 14a. That is, if the opening area of the opening 14a is too large, it approaches the unevenness in the case where the partition plate 14 is not provided, so the expansion and contraction of the refrigerant flow path may occur, increasing the pressure loss. Therefore, by adopting a structure in which the opening 14a satisfies the relationship of K < W, the pressure loss inside the collecting header 1b can be further reduced.

[0082] In addition, by arranging the partition plate 14 in such a manner that the relationship of L < D and L < H is satisfied, the unevenness generated due to the insertion of the heat transfer tubes 2 is further reduced, and the expansion and contraction of the refrigerant flow path are also further alleviated. That is, by making the distance L in the second direction (Y direction) between the front ends of the plurality of heat transfer tubes 2 inserted into the header smaller than the distance D in the second direction (Y direction) between the front ends of the plurality of heat transfer tubes 2 and the insertion holes, and smaller than the distance H in the second direction (Y direction) between the partition plate and the insertion holes, the change in the flow path cross-sectional area of the refrigerant inside the collective header 1b becomes smaller, and the pressure loss suffered by the refrigerant flowing inside the collective header can be further reduced.

[0083] In addition, when the front ends of the heat transfer tubes 2 are located in the first space 15, by arranging the partition plate 14 in such a manner that the relationship of L < D / 2 is satisfied, the distance between the front ends of the heat transfer tubes 2 and the second space 16 becomes closer, and the refrigerant easily flows into the second space 16. Therefore, the pressure loss can be reduced. That is, by making the distance L in the second direction (Y direction) between the front ends of the plurality of heat transfer tubes 2 inserted into the header smaller than half of the insertion length D, the distance between the front ends of the heat transfer tubes 2 and the opening 14a of the partition plate 14 becomes closer, and the refrigerant easily flows from the heat transfer tubes 2 into the second space 16, thereby suppressing an increase in the pressure loss. On the other hand, when the front ends of the heat transfer tubes 2 are located in the second space 16, by arranging the partition plate 14 in such a manner that the relationship of L < H / 2 is satisfied, the distance between the front ends of the heat transfer tubes 2 and the partition plate 14 becomes closer, and the unevenness caused by the insertion of the heat transfer tubes 2 can be further reduced. Therefore, the pressure loss can be further reduced.

[0084] In addition, by arranging the partition plate 14 in such a manner that the relationship of L ≤ t is satisfied, there is almost no expansion and contraction of the refrigerant flow path generated due to the insertion of the heat transfer tubes 2. That is, by making the distance L in the second direction (Y direction) between the front ends of the heat transfer tubes 2 inserted into the header less than or equal to the thickness t of the partition plate 14, the front ends of the heat transfer tubes 2 become substantially the same height as the partition plate 14, and there is almost no unevenness. That is, the flow path cross-sectional area of the refrigerant inside the collective header 1b is almost constant. Thus, the refrigerant flowing in the first direction (X direction) in the second space 16 is not affected by the expansion and contraction of the flow path, and the pressure loss suffered by the refrigerant flowing inside the collective header can be further reduced.

[0085] In addition, by arranging the partition plate 14 in such a manner that the second space 16 is larger than the first space, the refrigerant easily flows in the second space 16 which is the main flow path, contributing to improving the heat exchange performance.

[0086] In addition, by arranging the partition plate 14 such that the front end of the heat transfer tube 2 is located in the second space 16, the refrigerant flowing out from the front end of the heat transfer tube 2 can directly flow into the second space 16. Therefore, the pressure loss caused by the collision with the partition plate 14 can be suppressed.

[0087] Fig.13 It is a diagram showing the changes in the refrigerant flow rate and pressure loss inside the header in the case where the partition plate 14 is provided in the header 1b of the first embodiment 1 and the case where the partition plate 14 is not provided. The vertical axis represents the pressure loss inside the header, and the horizontal axis represents the amount of refrigerant flowing into the header 1b. The pressure loss in the case where the partition plate 14 is provided inside the header is represented by a square diagram, and the pressure loss in the case where the partition plate 14 is not provided inside the header is represented by a circular diagram. It should be noted that the installation position of the partition plate 14 is set to satisfy the relationship of L < D and L < H and the front end of the heat transfer tube 2 is located in the second space 16.

[0088] From Fig.13 it can be seen that at each refrigerant flow rate, the pressure loss in the case where the partition plate 14 is provided (square diagram) is smaller than that in the case where the partition plate 14 is not provided (circular diagram). That is, by providing the partition plate 14 of the first embodiment 1 in the header 1b, the pressure loss can be reduced. In particular, as the refrigerant flow rate increases, the pressure loss in the case where the partition plate 14 is provided (square diagram) is smaller than that in the case where the partition plate 14 is not provided (circular diagram). That is, it can be seen that the greater the refrigerant flow rate, the greater the effect of reducing the pressure loss brought by the installation of the partition plate 14.

[0089] Thus, the heat exchanger 100 of the first embodiment 1 includes: a plurality of heat transfer tubes 2 arranged at intervals in the first direction (X direction); a header 1 having insertion holes 11a for inserting the front ends of the respective heat transfer tubes of the plurality of heat transfer tubes 2 from the second direction (Y direction) orthogonal to the first direction (X direction); and fins 3 mounted on the heat transfer tubes 2. The header 1 includes a partition plate 14 that divides the inside of the header into a first space 15 on the side where the insertion holes 11a are provided and a second space 16 connected to the refrigerant pipe 4. An opening 14a that surrounds the outer periphery of the front end of the heat transfer tube is provided on the partition plate 14. With this structure, a heat exchanger 100 can be provided that can reduce the pressure loss of the refrigerant and has excellent heat exchange performance even for the heat exchanger 100 into which the heat transfer tubes 2 are inserted.

[0090] Here, in the heat exchanger 100 of the first embodiment 1, the header 1b where the gas refrigerant is gathered is taken as an example for description, but it can also be a distribution header 1a as Fig.14 shown in which the gas-liquid two-phase refrigerant flows. Fig.14 It is a diagram showing the flow of the refrigerant in the distribution header of the heat exchanger 100 of the first embodiment.

[0091] In addition, the refrigerant flowing in the heat exchanger 100 of the first embodiment is, for example, propane refrigerant, HFO refrigerant, ammonia refrigerant, dimethyl ether refrigerant, etc. When a refrigerant having a density lower than that of the commonly used R32 under the condition of working as an evaporator in the air-conditioning device 200 like these refrigerants, or a mixed refrigerant obtained by adding any of these refrigerants as one of the components is used, the effect of reducing the pressure loss can be particularly increased.

[0092] In the first embodiment, the heat transfer tubes are arranged in one row. However, the arrangement is not limited to one row, and the heat transfer tubes may be arranged in two or more rows.

[0093] Implementation method 2.

[0094] use Fig.15 as well as Fig.16 The heat exchanger 100 in Embodiment 2 of the present disclosure is described. The heat exchanger 100 in Embodiment 2 is different from the heat exchanger 100 in Embodiment 1 in the number of openings 14a of the partition 14. It should be noted that the description of the structure repeated in Embodiment 1 is omitted, and the same or corresponding parts as in Embodiment 1 are marked with the same reference numerals.

[0095] Fig.15 This is a cross-sectional view of the collecting header 1b according to the second embodiment cut along a plane parallel to the first direction (X direction). Fig.16 It is a perspective view showing the partition plate 14 according to the second embodiment, and the position of the heat transfer tube 2 is indicated by a dotted line.

[0096] In the first embodiment, the case where the number of heat transfer tubes 2 inserted into the collecting header 1b is equal to the number of openings 14a of the partition plate 14 is described as an example, but in the second embodiment, Fig.16 As shown, the number of openings 14a is less than the number of heat transfer tubes 2. Fig.16 As shown, the opening 14 a of the second embodiment is provided at a position where two adjacent heat transfer tubes 2 can be inserted into one opening 14 a when viewed from the second direction.

[0097] By adopting such a structure, the refrigerant flowing out from the front end of the heat transfer tube 2 can flow into the second space 16 without colliding with the partition plate 14, and the pressure loss can be reduced. Therefore, the heat exchanger 100 with excellent heat exchange performance can be provided.

[0098] Implementation method 3.

[0099] use Fig.17 as well as Fig.18A heat exchanger 100 in Embodiment 3 of the present disclosure will be described. Embodiment 3 differs from Embodiment 1 in the shape of the opening 14a of the partition plate 14. It should be noted that the description of the same structure as Embodiment 1 is omitted, and the same or corresponding parts as those in Embodiment 1 are denoted by the same reference numerals.

[0100] Fig.17 This is a cross-sectional view of the collecting header 1b according to the third embodiment cut along a plane parallel to the first direction (X direction). Fig.18 It is a perspective view showing the partition plate 14 according to the third embodiment.

[0101] like Fig.17 As shown, the opening 14a of the partition wall of the third embodiment is in the shape of a tapered portion having an opening area of ​​the opening 14a gradually expanding from the first space toward the second space 16. That is, the opening 14a gradually expands from the first space toward the second space 16. For example, Fig.17 As shown, the heat transfer tube 2 has an inclined shape extending toward the terminal end.

[0102] By adopting such a structure, not only can the same effect as that of Embodiment 1 be obtained, but also the concavity and convexity caused by the insertion of the heat transfer tube 2 can be further reduced by the tapered portion, and the expansion and contraction of the refrigerant flow path inside the collecting header 1b can be made more gradual. As a result, the pressure loss of the refrigerant flowing in the second space 16 of the header can be further reduced, and a heat exchanger 100 with excellent heat exchange performance can be provided. In addition, by providing the tapered portion, when the front end of the heat transfer tube 2 is inserted into the opening 14a, it is also possible to prevent the front end of the heat transfer tube 2 from colliding with the edge of the opening 14a of the partition 14 and being damaged.

[0103] Implementation method 4.

[0104] use Fig.19 as well as Fig. 20 A heat exchanger 100 in Embodiment 4 of the present disclosure will be described. Embodiment 4 differs from Embodiment 1 in the shape of the partition plate 14. It should be noted that description of the same configuration as Embodiment 1 will be omitted, and the same or corresponding parts as those in Embodiment 1 are denoted by the same reference numerals.

[0105] Fig.19 This is a cross-sectional view of the collecting header 1b according to the fourth embodiment cut along a plane parallel to the first direction (X direction). Fig. 20 It is a perspective view showing the partition plate 14 according to the fourth embodiment.

[0106] like Fig.19As shown, the partition wall 14 of the fourth embodiment is in the shape of a corrugated shape having concave and convex portions at intervals smaller than the width of the adjacent heat transfer tubes 2. That is, the concave and convex portions of the corrugated shape are smaller than the intervals between the heat transfer tubes 2. Fig. 20 As shown, it is preferred that an opening 14a is provided at the top of the corrugated convex portion, and the concave portion has a flat bottom. The corrugated convex portion of the partition plate 14 is in contact with the header upper plate 11 and fixed.

[0107] It should be noted that, in the present embodiment 4, the first space 15 is divided in the first direction for each heat transfer tube 2. In addition, the gap between the heat transfer tube 2 and the opening 14a is closed by the header upper plate 11. Therefore, it is preferred that the width of the partition 14 in the third direction (Z direction) is smaller than the width inside the header, or a cutout is partially formed at the end of the partition 14 in the third direction (Z direction), so that the first space 15 and the second space 16 are connected. By adopting such a structure, not only can the same effect as in the embodiment 1 be obtained, but also the fixing cost of the partition 14 can be reduced.

[0108] Implementation method 5.

[0109] use Fig.21 The air conditioning device 200 in Embodiment 5 of the present disclosure is described. Embodiment 5 is an air conditioning device 200 having the heat exchanger 100 of any one of Embodiments 1 to 4 as a condenser or an evaporator. It should be noted that the description of the structure repeated in Embodiment 1 is omitted, and the same or corresponding parts as those in Embodiment 1 are marked with the same reference numerals.

[0110] Fig.21 1 is a refrigerant circuit diagram showing an air conditioning device 200 equipped with the heat exchanger 100 (100a, 100b) according to any one of Embodiments 1 to 4. Fig.21 The solid arrows indicate the flow of the refrigerant during the heating operation, and the heating operation is taken as an example for description.

[0111] like Fig.21 As shown, in the air conditioning device 200 of the fifth embodiment, the heat exchanger 100 (100a, 100b) described in the first to fourth embodiments is mounted as a condenser or an evaporator in the indoor unit or the outdoor unit. In the heating operation, the heat exchanger 100a becomes a condenser, and the heat exchanger 100b becomes a condenser. The refrigerant circuit of the air conditioning device 200 is as follows: Fig.21 As shown, the compressor 22, the condenser, the expansion valve 21, the evaporator, and the four-way valve 23 are connected by pipes.

[0112] The refrigerant is compressed by the compressor 22 and becomes a high-temperature and high-pressure gas refrigerant. Then, the gas refrigerant flows into the condenser. The gas refrigerant exchanges heat with a fluid such as air in the heat exchanger 100b that functions as a condenser and condenses to become a high-pressure liquid refrigerant. Then, the liquid refrigerant is decompressed by the expansion valve 21 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant, and flows into the evaporator. The gas-liquid two-phase refrigerant exchanges heat with a fluid such as air in the heat exchanger 100a that functions as an evaporator and evaporates to become a gas refrigerant. The refrigerant that has become a gas refrigerant returns to the compressor 22.

[0113] In addition, the flow of the refrigerant is reversed by switching the circuit with the four-way valve 23, so that cooling operation can be performed. During cooling operation, the heat exchanger 100a serves as a condenser, and the heat exchanger 100b serves as an evaporator.

[0114] In the air-conditioning device 200, by mounting a heat exchanger 100 of any one of embodiments 1 to 4 on an evaporator or a condenser, not only can the same effect as embodiments 1 to 4 be obtained, but also an air-conditioning device 200 having a heat exchanger 100 (100a, 100b) with excellent heat exchange performance can be provided.

[0115] Thus, the air conditioner 200 of the fifth embodiment includes a refrigerant circuit in which the compressor 22, the condenser, the expansion valve 21, the evaporator, and the four-way valve 23 are connected by piping and the refrigerant flows, and includes the heat exchanger 100 of any one of the first to fourth embodiments as a condenser or an evaporator. Thus, the air conditioner 200 including the heat exchanger 100 having excellent heat exchange performance can be provided.

[0116] Here, in the fifth embodiment, the example in which the heat exchanger 100 described in the first to fourth embodiments is applied to a condenser or an evaporator is described. However, in particular, it is most preferable to apply the structure of the heat exchanger 100 described in the first to fourth embodiments to an evaporator having a collection header 1b for collecting gas refrigerant from a plurality of heat transfer tubes 2 or a condenser having a distribution header for distributing gas refrigerant to a plurality of heat transfer tubes 2. This is because the speed of the refrigerant flowing out or flowing in from the front end of the heat transfer tube 2 in the header 1 where the gas refrigerant flows is greater than that in the header 1 where the gas-liquid two-phase refrigerant flows, and therefore, the influence of the pressure loss caused by the collision of the refrigerant flowing out from the front end of the heat transfer tube 2 with the partition 14 is also likely to become large. However, according to the above-mentioned heat exchanger 100, the pressure loss caused by the collision with the partition 14 can be reduced, and the pressure loss caused by the expansion and contraction caused by the convex and concave insertion of the heat transfer tube 2 is reduced, so that the heat exchanger 100 with excellent heat exchange performance can be provided.

[0117] It should be noted that the structure of the heat exchanger 100 of the first embodiment can also be applied to an evaporator having a distribution header 1a that distributes the refrigerant to a plurality of heat transfer tubes 2, or a condenser having a collection header 1b that collects the refrigerant from a plurality of heat transfer tubes 2. In this case, the pressure loss caused by the collision with the partition 14 and the pressure loss caused by the expansion and contraction due to the convex and concave insertion of the heat transfer tube 2 can be reduced, so that the heat exchanger 100 with excellent heat exchange performance can be provided. In addition, since the pressure loss can be reduced, it is also effective when the size of the header 1 is miniaturized.

[0118] It should be noted that appropriate combination, modification, or omission of the embodiments is also included in the scope of the technical concept shown in the embodiments.

[0119] Description of Reference Numerals

[0120] 1 header, 1a distribution header, 1b collection header, 2 heat transfer tube, 3 fin, 4 refrigerant pipe, 4a refrigerant inlet pipe, 4b refrigerant outlet pipe, 11 header upper plate, 11a insertion hole, 12 header body, 13 side cover, 14 partition, 14a opening, 15 first space, 16 second space, 21 expansion valve, 22 compressor, 23 four-way valve, 100, 100a, 100b heat exchanger, 200 air conditioning device.

Claims

1. A heat exchanger, comprising: A plurality of heat transfer tubes, wherein the plurality of heat transfer tubes are arranged at intervals from each other in a first direction; a header having an insertion hole into which a front end of each of the plurality of heat transfer tubes is inserted from a second direction orthogonal to the first direction; and fins, the fins being installed between adjacent heat transfer tubes among the plurality of heat transfer tubes, The heat exchanger is characterized in that The header includes a partition plate that partitions the interior of the header into a first space on a side where the insertion hole is provided and a second space to which the refrigerant pipe is connected. The partition plate is provided with an opening portion surrounding the outer periphery of the front end of the heat transfer tube when viewed from the second direction. The opening has a shape having a gap between the opening and the outer periphery of the front end of the heat transfer tube when viewed from the second direction.

2. The heat exchanger according to claim 1, characterized in that A width of the opening in the first direction is smaller than a distance between the adjacent heat transfer tubes.

3. The heat exchanger according to claim 2, characterized in that The distance between the front end of the heat transfer tube inserted into the header and the opening in the second direction is smaller than the distance between the front end of the heat transfer tube and the insertion hole in the second direction, and smaller than the distance between the opening and the insertion hole in the second direction.

4. The heat exchanger according to claim 3, characterized in that When the front end of the heat transfer tube is located in the first space, the distance between the front end of the heat transfer tube inserted into the header and the opening in the second direction is smaller than half of the distance between the front end of the heat transfer tube and the insertion hole in the second direction. When the front end of the heat transfer tube is located in the second space, the distance between the front end of the heat transfer tube inserted into the header and the opening in the second direction is smaller than half of the distance between the opening and the insertion hole in the second direction.

5. The heat exchanger according to claim 3 or 4, characterized in that: The distance between the front end of the heat transfer tube and the opening in the second direction is less than or equal to the thickness of the partition plate in the second direction.

6. The heat exchanger according to claim 3 or 4, characterized in that: The front end of the heat transfer tube is located in the second space.

7. The heat exchanger according to claim 1, characterized in that The number of the openings is less than the number of the heat transfer tubes.

8. The heat exchanger according to any one of claims 1 to 4, characterized in that: The opening portion includes a tapered portion that gradually increases an opening area of ​​the opening portion from the first space toward the second space.

9. The heat exchanger according to any one of claims 1 to 4, characterized in that: The partition plate has a corrugated shape having concave and convex portions at intervals smaller than the widths of the adjacent heat transfer tubes.

10. The heat exchanger according to any one of claims 1 to 4, characterized in that: The refrigerant flowing through the heat exchanger is propane refrigerant, HFO refrigerant, ammonia refrigerant, dimethyl ether refrigerant, or a mixed refrigerant in which any of these refrigerants is added as one of the components.

11. An air conditioning device, characterized in that: The air conditioner is provided with a refrigerant circuit in which a compressor, a condenser, an expansion valve, an evaporator, and a four-way valve are connected by piping and a refrigerant flows, and the air conditioner is provided with the heat exchanger according to any one of claims 1 to 10 as the condenser or the evaporator.

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