CN113785168B

CN113785168B - Heat exchanger and refrigeration cycle device

Info

Publication number: CN113785168B
Application number: CN201980095830.8A
Authority: CN
Inventors: 前田刚志; 东井上真哉
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2019-05-14
Filing date: 2019-05-14
Publication date: 2023-11-03
Anticipated expiration: 2039-05-14
Also published as: JP7170859B2; EP3971507A1; WO2020230267A1; CN113785168A; JPWO2020230267A1; EP3971507A4; EP3971507B1

Abstract

The object is to provide a heat exchanger and a refrigeration cycle device which are provided with a plurality of heat transfer tubes connected to each other at both ends in the tube axis direction and which can suppress deformation. The heat exchanger comprises: a plurality of heat transfer pipes arranged in a first direction at a distance from each other to circulate a refrigerant; a first header connected to one end of each of the plurality of heat transfer tubes; a second header connected to the other end of each of the plurality of heat transfer tubes; and a plurality of reinforcing members connected to the first header and the second header, the plurality of heat transfer tubes and the plurality of reinforcing members being disposed between the first header and the second header, the plurality of heat transfer tubes being connected to the first header and the second header without members connecting the side surfaces to each other.

Description

Heat exchanger and refrigeration cycle device

Technical Field

The present invention relates to a heat exchanger and a refrigeration cycle apparatus including the heat exchanger, and more particularly, to a structure for suppressing deformation of a heat transfer pipe.

Background

In recent years, heat exchangers of refrigeration and air conditioning apparatuses are known as follows: the corrugated fins disposed in the gaps formed between the heat transfer tubes are eliminated, the diameter of the heat transfer tubes is reduced, and the intervals between the heat transfer tubes are narrowed. In such a heat exchanger, since the plurality of heat transfer tubes are closely arranged and air passes between the heat transfer tubes, heat exchange performance is improved, and high performance and light weight of the refrigeration cycle apparatus are achieved. In recent years, reduction in the amount of refrigerant used, which has a high global warming potential, has become an important issue, and it has been demanded to develop a heat exchanger having a smaller volume in the tube of the heat transfer tube and higher performance than the conventional heat exchanger.

For example, the heat exchanger disclosed in patent document 1 has a flat tube made of aluminum instead of a round tube made of copper. The heat exchanger includes a plurality of flat tubes arranged at intervals and a pair of headers connected to both ends of the flat tubes in the tube axis direction.

The heat exchanger disclosed in patent document 2 has a heat transfer tube in which a plurality of round tubes having a reduced diameter are arranged in a ventilation direction, and fins are joined to the round tubes to connect the round tubes to each other. The heat exchanger includes a plurality of heat transfer tubes arranged in a direction orthogonal to the ventilation direction at intervals, and a pair of headers connected to both ends of a round tube constituting the heat transfer tubes.

Prior art literature

Patent literature

Patent document 1: international publication No. 2015/005352

Patent document 2: japanese patent laid-open No. 2018-155479

Disclosure of Invention

Problems to be solved by the invention

However, the heat transfer tubes of the heat exchangers of patent document 1 and patent document 2 have smaller cross-sectional areas perpendicular to the tube axis direction than conventional heat transfer tubes, and have low rigidity and strength. Further, since the heat exchanger does not have a heat transfer promoting member such as a corrugated fin between the plurality of heat transfer tubes, buckling in the tube axis direction of the heat transfer tubes and warping in the arrangement direction of the heat transfer tubes are difficult to suppress, and there is a possibility that the entire heat exchanger may be deformed.

The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a heat exchanger and a refrigeration cycle apparatus that include a plurality of heat transfer tubes connected to each other at both ends in a tube axis direction and that can suppress deformation.

Means for solving the problems

The heat exchanger of the present invention comprises: a plurality of heat transfer pipes arranged in a first direction at a distance from each other to circulate a refrigerant; a first header connected to one end of each of the plurality of heat transfer tubes; a second header connected to the other end of each of the plurality of heat transfer tubes; and a plurality of reinforcing members connected to the first header and the second header, the plurality of heat transfer tubes and the plurality of reinforcing members being disposed between the first header and the second header, the plurality of reinforcing members being connected by the first header and the second header without members connecting side surfaces to each other.

The refrigeration cycle device of the present invention includes the heat exchanger.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the present invention, the heat exchanger can suppress deformation of the heat exchanger in the direction in which the plurality of heat transfer tubes are arranged by the reinforcing member connected to the first header and the second header.

Drawings

Fig. 1 is a refrigerant circuit diagram showing a configuration of a refrigeration cycle apparatus including a heat exchanger 50 according to embodiment 1.

Fig. 2 is a front view showing a main part configuration of a heat exchanger 50 according to embodiment 1.

Fig. 3 is a top view of the heat exchanger 50 of fig. 2.

Fig. 4 is a side view of the heat exchanger 50 of fig. 2.

Fig. 5 is a cross-sectional view of the heat exchanger 50 of fig. 2.

Fig. 6 is a front view of a heat exchanger 150 as a comparative example of the heat exchanger 50 of embodiment 1.

Fig. 7 is a cross-sectional view of a heat exchanger 50A as a modification of the heat exchanger 50 of embodiment 1.

Fig. 8 is a cross-sectional view of a heat exchanger 50B as a modification of the heat exchanger 50 of embodiment 1.

Fig. 9 is a single body perspective view of the reinforcing member 3B of fig. 8.

Fig. 10 is a cross-sectional view of a heat exchanger 50C as a modification of the heat exchanger 50 of embodiment 1.

Fig. 11 is a cross-sectional view of a heat exchanger 250 according to embodiment 2.

Fig. 12 is a cross-sectional view of a heat exchanger 350 according to embodiment 3.

Detailed Description

The heat exchanger and the refrigeration cycle apparatus according to embodiment 1 will be described below with reference to the drawings. In the following drawings including fig. 1, the relationship and shape of the relative sizes of the constituent members may be different from the actual ones. In the following drawings, the same reference numerals are used for the same or corresponding members, and are common throughout the specification. In addition, although terms indicating directions (e.g., "upper", "lower", "right", "left", "front", "rear", etc.) are used as appropriate for ease of understanding, these expressions are merely described for convenience of description and do not limit the arrangement and direction of the devices or components. In the specification, the positional relationship of the respective constituent members, the extending direction of the respective constituent members, and the arrangement direction of the respective constituent members are in principle the relationship and direction when the heat exchanger is provided in a usable state.

Embodiment 1

[ refrigeration cycle device 100]

Fig. 1 is a refrigerant circuit diagram showing a configuration of a refrigeration cycle apparatus 100 including a heat exchanger 50 according to embodiment 1. In fig. 1, the arrow shown by the broken line indicates the flow direction of the refrigerant during the cooling operation in the refrigerant circuit 110, and the arrow shown by the solid line indicates the flow direction of the refrigerant during the heating operation. First, a refrigeration cycle apparatus 100 including a heat exchanger 50 will be described with reference to fig. 1. In the embodiment, the air conditioning apparatus is exemplified as the refrigeration cycle apparatus 100, but the refrigeration cycle apparatus 100 is used for, for example, refrigeration applications or air conditioning applications such as a refrigerator, a freezer, a vending machine, an air conditioning apparatus, a refrigerating apparatus, a water heater, and the like. The illustrated refrigerant circuit 110 is an example, and the configuration of the circuit elements and the like are not limited to those described in the embodiments, and can be appropriately modified within the technical scope of the embodiments.

The refrigeration cycle apparatus 100 includes a refrigerant circuit 110, and the refrigerant circuit 110 connects a compressor 101, a flow path switching device 102, an indoor heat exchanger 103, a pressure reducing device 104, and an outdoor heat exchanger 105 in a loop shape via refrigerant pipes. At least one of the outdoor heat exchanger 105 and the indoor heat exchanger 103 uses a heat exchanger 50 described later. The refrigeration cycle apparatus 100 includes an outdoor unit 106 and an indoor unit 107. The outdoor unit 106 accommodates a compressor 101, a flow path switching device 102, an outdoor heat exchanger 105, a pressure reducing device 104, and an outdoor blower 108 for supplying outdoor air to the outdoor heat exchanger 105. The indoor unit 107 houses an indoor heat exchanger 103 and an indoor blower 109 that supplies air to the indoor heat exchanger 103. The outdoor unit 106 and the indoor unit 107 are connected to each other via two extension pipes 111 and 112, which are part of the refrigerant pipe.

The compressor 101 is a fluid machine that compresses and discharges a sucked refrigerant. The flow path switching device 102 is, for example, a four-way valve, and is a device that switches the flow path of the refrigerant between the cooling operation and the heating operation under the control of a control device (not shown).

The indoor heat exchanger 103 is a heat exchanger that exchanges heat between the refrigerant flowing inside and the indoor air supplied by the indoor blower 109. The indoor heat exchanger 103 functions as a condenser during a heating operation and functions as an evaporator during a cooling operation.

The pressure reducing device 104 is, for example, an expansion valve, and is a device for reducing the pressure of the refrigerant. As the pressure reducing device 104, an electronic expansion valve whose opening degree is adjusted by control of a control device can be used.

The outdoor heat exchanger 105 is a heat exchanger that exchanges heat between the refrigerant flowing inside and the air supplied by the outdoor fan 108. The outdoor heat exchanger 105 functions as an evaporator in the heating operation and functions as a condenser in the cooling operation.

[ operation of refrigeration cycle device ]

Next, an example of the operation of the refrigeration cycle apparatus 100 will be described with reference to fig. 1. During the heating operation of the refrigeration cycle apparatus 100, the high-pressure and high-temperature gas-state refrigerant discharged from the compressor 101 flows into the indoor heat exchanger 103 via the flow path switching device 102, exchanges heat with air supplied from the indoor fan 109, and condenses. The condensed refrigerant is in a high-pressure liquid state, flows out of the indoor heat exchanger 103, and is in a low-pressure gas-liquid two-phase state by the pressure reducing device 104. The low-pressure gas-liquid two-phase refrigerant flows into the outdoor heat exchanger 105, and evaporates by heat exchange with the air supplied from the outdoor blower 108. The evaporated refrigerant is in a low-pressure gas state and is sucked into the compressor 101.

During cooling operation of the refrigeration cycle apparatus 100, the refrigerant flowing through the refrigerant circuit 110 flows in the opposite direction to that during heating operation. That is, during the cooling operation of the refrigeration cycle apparatus 100, the high-pressure and high-temperature gas-state refrigerant discharged from the compressor 101 flows into the outdoor heat exchanger 105 via the flow path switching device 102, exchanges heat with the air supplied from the outdoor fan 108, and condenses. The condensed refrigerant is in a high-pressure liquid state, flows out of the outdoor heat exchanger 105, and is in a low-pressure gas-liquid two-phase state by the pressure reducing device 104. The low-pressure gas-liquid two-phase refrigerant flows into the indoor heat exchanger 103, and evaporates by heat exchange with the air supplied by the indoor blower 109. The evaporated refrigerant is in a low-pressure gas state and is sucked into the compressor 101.

[ Heat exchanger 50]

Fig. 2 is a front view showing a main part configuration of a heat exchanger 50 according to embodiment 1. Fig. 3 is a top view of the heat exchanger 50 of fig. 2. Fig. 4 is a side view of the heat exchanger 50 of fig. 2. Fig. 5 is a cross-sectional view of the heat exchanger 50 of fig. 2. Fig. 5 is a cross section orthogonal to the tube axis of the flat tube 1, showing a cross section of the portion A-A of fig. 2. The cross section shown in fig. 5 is sometimes referred to as a first cross section. In fig. 2, arrow RF indicated by hatching indicates the flow of the refrigerant flowing into the heat exchanger 50 or flowing out of the heat exchanger 50. The heat exchanger 50 according to embodiment 1 will be described with reference to fig. 2 to 5.

The heat exchanger 50 according to embodiment 1 includes a plurality of flat tubes 1, a first header 2a and a second header 2b connected to ends of the plurality of flat tubes 1, and a plurality of reinforcing members 3 arranged in parallel with the plurality of flat tubes 1. The flat tubes 1 are arranged in plural in the x direction. The flat tubes 1 are arranged with the tube axes along the y-direction. In embodiment 1, the y direction is parallel to the gravity direction. However, the arrangement of the heat exchanger 50 is not limited to this, and may be arranged so that the y direction is inclined with respect to the gravity direction. The plurality of flat tubes 1 are arranged at equal intervals and have a width w1 in the x direction.

The first header 2a is connected to one end 12 of the plurality of flat tubes 1 in the tube axis direction. The second header 2b is connected to the other end 11 of the plurality of flat tubes 1 in the tube axis direction. The first header 2a and the second header 2b are arranged so that the longitudinal direction thereof faces the parallel direction of the plurality of flat tubes 1. The length directions of the first header 2a and the second header 2b are parallel to each other. In the following description, the first header 2a and the second header 2b are sometimes collectively referred to as a header 2.

The reinforcing member 3 is disposed outside the flat tubes 1 located at both ends among the plurality of flat tubes 1 arranged in the x-direction. In the heat exchanger 50 shown in fig. 2 to 5, two reinforcing members 3 are arranged, and one reinforcing member 3 is arranged at the end portion of the first header 2a and the second header 2b in the x direction. The other reinforcing member 3 is disposed at the end portion of the first header 2a and the second header 2b in the direction opposite to the x direction.

The ends 11 and 12 of the plurality of flat tubes 1 are inserted into the header 2, and the ends 31 and 32 of the plurality of reinforcing members 3 are also inserted into the header 2, respectively, and joined by a joining method such as brazing. The plurality of flat tubes 1 and the plurality of reinforcing members 3 are juxtaposed in the x-direction. The plurality of flat tubes 1 have heat transfer portions 13, which are portions other than the end portions 11 and 12, located between the lower surface of the first header 2a and the upper surface of the second header 2b. The reinforcing member 3 has a central portion 33, which is a portion other than the end portions 31 and 32, located between the lower surface of the first header 2a and the upper surface of the second header 2b.

(Flat tube 1)

The plurality of flat tubes 1 circulate the refrigerant therein. The plurality of flat tubes 1 extend between the first header 2a and the second header 2b, respectively. The plurality of flat tubes 1 are arranged with a space w1 therebetween in the x-direction, and are juxtaposed in the extending direction of the header 2. The plurality of flat tubes 1 are arranged so as to face each other. A gap that serves as a flow path for air is formed between two adjacent flat tubes 1 among the plurality of flat tubes 1. In embodiment 1, the direction in which the plurality of flat tubes 1 are arranged and the extending direction of the header 2, that is, the x direction, will be referred to as the first direction.

The heat exchanger 50 sets the arrangement direction of the plurality of flat tubes 1 as the first direction as the horizontal direction. However, the direction of arrangement of the plurality of flat tubes 1 in the first direction is not limited to the horizontal direction, and may be the vertical direction or may be a direction inclined with respect to the vertical direction. Similarly, the heat exchanger 50 sets the extending direction of the plurality of flat tubes 1 as the vertical direction. However, the extending direction of the plurality of flat tubes 1 is not limited to the vertical direction, and may be a horizontal direction or a direction inclined with respect to the vertical direction.

For adjacent flat tubes 1 among the plurality of flat tubes 1, the flat tubes 1 are not connected to each other by the heat transfer promoting member 130. The heat transfer promoting member 130 is, for example, a plate fin, a corrugated fin, or the like. That is, the plurality of flat tubes 1 are connected to each other only by the header 2, respectively.

As shown in fig. 5, the flat tube 1 has a cross-sectional shape flattened in one direction such as an oblong shape. The flat tube 1 has first and second side end portions 60a and 60b, and a pair of flat surfaces 60c and 60d. In the cross section shown in fig. 5, the first side end 60a may be formed to protrude outward between one end of the flat surface 60c and one end of the flat surface 60d. In this cross section, the second side end 60b may be formed to protrude outward between the other end of the flat surface 60c and the other end of the flat surface 60d. That is, the flat tube 1 may have fins extending from the end portions 60a and 60b in the longitudinal direction of the cross section in the z direction or in the direction opposite to the z direction. The fins provided from the first side end 60a and the second side end 60b of the flat tubes 1 are provided to improve the heat exchange performance of the flat tubes 1 in the heat exchanger 50 having no heat transfer promoting member 130 (see fig. 6) between the plurality of flat tubes 1.

When the heat exchanger 50 functions as an evaporator of the refrigeration cycle apparatus 100, the refrigerant flows from one end to the other end in the extending direction in each of the plurality of flat tubes 1. In addition, when the heat exchanger 50 functions as a condenser of the refrigeration cycle apparatus 100, the refrigerant flows from the other end to one end in the extending direction in each of the plurality of flat tubes 1.

(header 2)

The first header 2a and the second header 2b extend in the x-direction, respectively, and are configured to allow the refrigerant to circulate therein. As shown in fig. 2, for example, the refrigerant flows in from one end of the second header 2b and is distributed to each of the plurality of flat tubes 1. The refrigerant passing through the plurality of flat tubes 1 merges in the first header 2a and flows out from one end of the first header 2a.

In fig. 2 to 5, the header 2 has a rectangular parallelepiped shape, but the shape is not limited thereto. The external shape of the header 2 may be, for example, a cylinder, an elliptic cylinder, or the like, and the cross-sectional shape may be appropriately changed. The header 2 may be formed, for example, by a cylindrical body with both ends closed, or by a structure in which plate-like bodies having slits formed therein are stacked. The first header 2a and the second header 2b are respectively formed with a refrigerant inflow port into and out of which a refrigerant can flow.

(reinforcing member 3)

As shown in fig. 5, in the heat exchanger 50, the reinforcing member 3 is juxtaposed with the plurality of flat tubes 1. That is, the reinforcing member 3 is disposed such that the longitudinal direction thereof is parallel to the tube axes of the plurality of flat tubes 1. In embodiment 1, the reinforcing members 3 are disposed at both ends of the array of the plurality of flat tubes 1. That is, the reinforcing member 3 is provided at two places in the heat exchanger 50, and one reinforcing member 3 is disposed adjacent to the flat tube 1a located at the end portion on the opposite side in the x direction, and is located outside the arrangement of the plurality of flat tubes 1. The other reinforcing member 3 is disposed adjacent to the flat tube 1b located at the end in the x direction, and is located outside the arrangement of the plurality of flat tubes 1.

In embodiment 1, the reinforcing members 3 are cylindrical and are arranged in a group of two at both ends of the array of the plurality of flat tubes 1. When focusing on one reinforcing member 3a or 3b, two cylinders are aligned in the z direction. The two cylinders are arranged at an interval equal to the width of the plurality of flat tubes 1 in the z direction.

The reinforcing member 3 is made of a material having a higher strength than the material constituting the flat tube 1. Since the flat tube 1 is made of aluminum, the reinforcing member 3 may be made of a material having higher rigidity and strength than aluminum, such as stainless steel.

(action of reinforcing member 3)

Fig. 6 is a front view of a heat exchanger 150 as a comparative example of the heat exchanger 50 of embodiment 1. The heat exchanger 150 of the comparative example has the same structure as that of embodiment 1, but differs in that corrugated fins as the heat transfer promoting members 130 are provided between the plurality of flat tubes 1 and the reinforcing members 3 are not provided. In addition, the heat transfer promoting member 130 connects the side surfaces of the adjacent plurality of flat tubes 1. The heat transfer promoting member 130 is joined to the side surfaces of the plurality of flat tubes 1x by brazing or the like.

The heat exchanger 50 according to embodiment 1 narrows the intervals w1 between the plurality of flat tubes 1, and increases the number of flat tubes 1 to be arranged. Thus, the heat exchanger 50 can improve the heat exchange performance between the refrigerant and the fluid passing through the heat exchanger while reducing the volume without providing the heat transfer promoting member 130 which is disposed between the plurality of flat tubes 1 and connects the side surfaces of the flat tubes 1 to each other. The plurality of flat tubes 1 of embodiment 1 have a smaller width dimension in the x direction than the flat tube 1x of the heat exchanger 150 of the comparative example in which the heat transfer promoting member 130 is provided. Therefore, for example, when the ends 11 and 12 are fixed ends and a load in the x direction is applied to the heat transfer portion 13, the flat tube 1 of the heat exchanger 50 of embodiment 1 has lower strength and rigidity against bending than those of the flat tube 1x of the comparative example. On the other hand, the heat exchanger 150 of the comparative example has a structure in which the heat transfer promoting member 130 is provided between the plurality of flat tubes 1x, and therefore, the heat exchanger is joined to the heat transfer promoting member 130 and the adjacent flat tubes 1x so as not to be deformed easily even when a load is applied to the heat transfer portions 113 of the plurality of flat tubes 1 x.

Here, it is assumed that the heat exchanger 50x as a comparative example is a heat exchanger 50 in which the reinforcing member 3 is not provided in the heat exchanger 50 of embodiment 1, and the flat tubes 1 are arranged at the positions of the reinforcing member 3. Then, for example, when the second header 2b is fixed and a load in the x direction is applied to the first header 2a, the heat exchanger 50x is easily deformed from the initial shape F0 shown by the two-dot chain line in fig. 2 to the shape F1. The shapes F0 and F1 are rectangles formed by connecting the center line of the header 2 in the x direction and the center line of the reinforcing member 3 in the y direction when the heat exchanger 50x is viewed from the front, and are schematic shapes of the heat exchanger 50 when viewed from the front. As described above, in the case of eliminating the heat exchanger 50x of the heat transfer promoting member 130 of the heat exchanger 150, there is a problem that strength against deformation is reduced in the arrangement direction of the plurality of flat tubes 1.

That is, in the case of the heat exchanger 50x of the comparative example in which the reinforcing member 3 is not provided as described above, there are the following problems: each of the plurality of flat tubes 1 has a low strength against bending in the x-direction, and when a load in the x-direction is applied to the first header 2a, the plurality of flat tubes 1 are likely to deform, and as a result, the shape of the entire heat exchanger 50x is likely to deform. In addition, the following problems exist: when a load is applied to the heat exchanger 50x in the y direction, each of the plurality of flat tubes 1 is also deformed by buckling, and the heat exchanger 50x is easily deformed in the direction in which the distance between the first header 2a and the second header 2b is shortened.

However, the heat exchanger 50 of embodiment 1 includes reinforcing members 3 at both ends of the array of the plurality of flat tubes 1. Therefore, by adding the reinforcing member 3 to the arrangement of the plurality of flat tubes 1, the load applied to the heat exchanger 50 can be shared by the reinforcing member 3, and therefore, the strength of the heat exchanger 50 is improved, and deformation of the heat exchanger 50 can be suppressed. Further, by further making the strength and rigidity against bending in the x-direction higher than those of the flat tubes 1, the reinforcing member 3 can enhance the effect of suppressing deformation of the entire heat exchanger 50. Further, since the strength and rigidity of the reinforcing member 3 against buckling are also higher than those of the flat tube 1, deformation such as shortening of the heat exchanger 50 in the y direction can be suppressed.

Further, since the reinforcing member 3 is disposed along the tube axes of the plurality of flat tubes 1 in the longitudinal direction, the strength and rigidity of the heat exchanger 50 can be improved and deformation can be suppressed without inhibiting the flow of moisture due to dew condensation or frost melting of the plurality of flat tubes 1.

(modification of the reinforcing member 3)

In the above description, the reinforcing member 3 is cylindrical, but is not limited to this embodiment. A modified example of the reinforcing member 3 will be described below.

Fig. 7 is a cross-sectional view of a heat exchanger 50A as a modification of the heat exchanger 50 of embodiment 1. Fig. 7 shows a section A-A of fig. 2. The heat exchanger 50A is a heat exchanger in which the reinforcing member 3 of the heat exchanger 50 is replaced with a reinforcing member 3A having the same outer shape as the plurality of flat tubes 1 in cross-sectional shape. The cross-sectional shape of the reinforcing member 3A has the same outer shape as the flat tube 1 in the cross-section shown in fig. 7, and is solid inside. On the other hand, the flat tube 1 has a refrigerant flow path formed therein. Therefore, when the neutral axis N along the z-direction is assumed in the cross section shown in fig. 7, the section modulus of the reinforcing member 3A about the neutral axis N is a value larger than the section modulus of the flat tube 1 about the neutral axis N. Therefore, even if the reinforcing member 3A is made of the same material as the flat tube 1, the strength and rigidity of the reinforcing member 3A are higher than those of the flat tube 1. In embodiment 1, since the reinforcing member 3A is made of a material having higher strength and rigidity than the flat tube 1, the strength and rigidity are further higher than those of the flat tube 1.

In the heat exchanger 50A according to the modification, the cross-sectional shapes of the plurality of flat tubes 1 and the reinforcing member 3A connected to the header 2 are all the same. Therefore, when the header 2 and the plurality of flat tubes 1 are joined by brazing at the time of manufacture, the reinforcing member 3A can also be joined using a positioning jig common to the plurality of flat tubes 1. Therefore, the reinforcing member 3A and the positioning jigs of the plurality of flat tubes 1 at the time of manufacture can be simplified. The header 2 is provided with insertion portions into which the end portions 11, 12, 31, 32 of the plurality of flat tubes 1 and the reinforcing members 3A are inserted, and the insertion portions may all be of a common shape. Therefore, the manufacturing cost of the header 2 can also be reduced.

The reinforcing member 3A shown in fig. 7 has flat side surfaces 35 in the cross section shown in fig. 7, and the side surfaces 35 are arranged so as to face the flat surfaces 15 of the flat tubes 1. As a result, the reinforcing member 3A can flow fluid between the side surfaces 35 and the flat surfaces 15, similarly to the plurality of flat tubes 1, without blocking the flow of fluid.

Fig. 8 is a cross-sectional view of a heat exchanger 50B as a modification of the heat exchanger 50 of embodiment 1. Fig. 8 corresponds to section A-A of fig. 2. The heat exchanger 50B includes a reinforcing member 3B having an I-shaped cross section in fig. 8. The reinforcing member 3B includes flange portions extending in the x direction and the opposite direction to the x direction at both end portions in the z direction. The reinforcing member 3B can have a section modulus about the neutral axis N larger than that of the flat tube 1 by appropriately setting the width of the flange portion in the x-direction.

Fig. 9 is a single body perspective view of the reinforcing member 3B of fig. 8. The outer shape of the cross-sectional shapes of the end portions 31 and 32 of the reinforcing member 3B is the same shape as the outer shape of the cross-sectional shape of the flat tube 1. With this structure, the strength and rigidity of the central portion 33 of the reinforcing member 3B are higher than those of the heat transfer portion 13 of the flat tube 1. However, the end portions 31 and 32 of the reinforcing member 3B inserted into the insertion portion of the header 2 have the same shape as the flat tube 1. Therefore, the insertion portion of the header 2 into which the reinforcing member 3B is inserted can be formed in the same shape as the insertion portion into which the flat tube 1 is inserted. Therefore, the reinforcing member 3B can be inserted into the header 2 in the same manner as the flat tubes 1 while having a shape with higher strength and rigidity than the flat tubes 1, and therefore, the heat exchanger 50A can be easily manufactured.

The reinforcing member 3B includes end surfaces 34 and 35 at both ends in the longitudinal direction. The end faces 34 and 35 are abutted against the lower surface of the first header 2a and the upper surface of the second header 2B in a state where the end portions 31 and 32 of the reinforcing member 3B are inserted into the header 2. Therefore, when a load is applied in the direction in which the reinforcing member 3B of the heat exchanger 50B is bent, the lower surface of the first header 2a and the upper surface of the second header 2B come into contact with the end surfaces 34 and 35 of the reinforcing member 3B, and the load can be received, so that the strength and rigidity of the heat exchanger 50B are further improved. Further, by joining the end surfaces 34 and 35 of the reinforcing member 3B to the header 2, the joint area between the reinforcing member 3B and the header 2 increases, and the strength and rigidity of the heat exchanger 50B can be further improved.

Fig. 10 is a cross-sectional view of a heat exchanger 50C as a modification of the heat exchanger 50 of embodiment 1. Fig. 10 corresponds to section A-A of fig. 2. The cross-sectional shape of the reinforcing member 3C of the heat exchanger 50C is a shape bent at the center. The width of the reinforcing member 3C in the z direction is set to be the same as that of the flat tube 1. The width of the reinforcing member 3C in the x-direction is a width from both ends of the reinforcing member 3C in the z-direction to the curved central portion. In embodiment 1, the width of the reinforcing member 3C in the x direction is larger than that of the flat tube 1. Thereby, the reinforcing member 3C can have a section modulus about the neutral axis N larger than that of the flat tube 1.

In addition, the reinforcing member 3C located at the end of the heat exchanger 50C in the x direction and the reinforcing member 3C located at the end opposite to the x direction are symmetrically arranged with respect to the center of the heat exchanger 50C in fig. 10. With this configuration, the heat exchanger 50C can have stable strength by having the same strength and rigidity in deformation in the x direction as in deformation in the opposite direction.

Further, since the reinforcing member 3C is formed to open outward with respect to the arrangement of the plurality of flat tubes 1 of the heat exchanger 50C as going from the center toward both ends in the z direction, it is easy to introduce fluid to both ends of the arrangement of the plurality of flat tubes 1.

Embodiment 2

The heat exchanger 250 of embodiment 2 will be described. The heat exchanger 250 is a heat exchanger in which the position of the reinforcing member 3A of the heat exchanger 50A of embodiment 1 is changed. The same reference numerals are given to constituent elements having the same functions and actions as those of embodiment 1, and the description thereof will be omitted.

Fig. 11 is a cross-sectional view of a heat exchanger 250 according to embodiment 2. Fig. 11 corresponds to section A-A of fig. 2. The heat exchanger 250 includes reinforcing members 3Aa and 3Ab at both ends of the arrangement of the plurality of flat tubes 1, and also includes reinforcing members 3Ac and 3Ad in the arrangement of the plurality of flat tubes 1, as in the heat exchanger 50A of embodiment 1. That is, the reinforcing members 3Ac and 3Ad are disposed adjacent to two flat tubes 1 among the plurality of flat tubes 1. In embodiment 2, the reinforcing members 3Aa, 3Ab, 3Ac, and 3Ad are arranged at equal intervals. The reinforcing members 3Aa and 3Ab and the reinforcing members 3Ac and 3Ad are arranged symmetrically with respect to the center of the arrangement of the plurality of flat tubes 1. In addition, the reinforcing members 3Ac and 3Ad are sometimes referred to as first reinforcing members, and the reinforcing members 3Aa and 3Ab are sometimes referred to as second reinforcing members.

Since the heat exchanger 250 of embodiment 2 further includes the reinforcing member 3Ac and the reinforcing member 3Ad, strength and rigidity are further improved as compared with the heat exchanger 50 of embodiment 1. In addition, in the case where the header 2 is long in the x-direction, the strength of the central portion of the heat exchanger 250 in the x-direction becomes weak. For example, in the case where the reinforcing members 3A are disposed at both ends as in the heat exchanger 50A of embodiment 1, when a load is applied to the central portion of the first header 2a in the direction opposite to the y direction, the first header 2a deflects and the flat tubes 1 disposed at the central portion are forced in the buckling direction. Therefore, the heat exchanger 250 of embodiment 2 can improve the strength of the central portion of the heat exchanger 250 by providing the reinforcing members 3Aa and 3Ab at both ends of the plurality of flat tubes 1 and providing the reinforcing members 3Ac and 3Ad in the aligned interior. Therefore, the heat exchanger 250 is advantageous in the case of having a structure long in the x-direction.

The arrangement of the reinforcing member 3 is not limited to the one shown in fig. 11. For example, the reinforcing member 3 may be disposed only in the arrangement of the plurality of flat tubes 1. The disposition of the reinforcing member 3 can be appropriately set according to the length of the heat exchanger 250 in the x direction, and is preferably located at a position symmetrical with respect to the center of the arrangement of the plurality of flat tubes 1.

The disposition of the reinforcing member 3 may be set according to the flow rate distribution of the fluid flowing into the heat exchanger 250. For example, when air is fed into the heat exchanger 250 by the blower, the flow rate of air at each position of the heat exchanger 250 based on the arrangement of the blower may be considered, and the reinforcing member 3 may be arranged at a position where the flow rate of air is small.

The heat exchanger 250 may change the cross-sectional shape of the reinforcing member 3. For example, the cross-sectional shape may be changed according to the position in the heat exchanger 250. The heat exchanger 250 of embodiment 2 has the reinforcing members 3Ac and 3Ad without the heat transfer promoting members 130 disposed between the adjacent flat tubes 1. Therefore, the cross-sectional shapes of the reinforcing members 3Ac and 3Ad can be appropriately changed. The heat exchanger 250 can employ, for example, a reinforcing member 3 having a cross section of the I-shape described above, or a reinforcing member 3 having a curved shape, such as a reinforcing member 3C, which has a high cross section modulus and an uneven side surface shape.

Embodiment 3

The heat exchanger 350 of embodiment 3 will be described. The heat exchanger 350 is a heat exchanger in which the plurality of flat tubes 1 of the heat exchanger 50 of embodiment 1 are modified to have heat transfer tubes of different structures. The same reference numerals are given to constituent elements having the same functions and actions as those of embodiment 1, and the description thereof will be omitted.

Fig. 12 is a cross-sectional view of a heat exchanger 350 according to embodiment 3. Fig. 12 corresponds to section A-A of fig. 2. The heat exchanger 350 includes a plurality of heat transfer tubes 1A. The plurality of heat transfer tubes 1A are formed by arranging two round tubes 301 in parallel with tube axes and connecting the tubes with each other by the fins 4. The plurality of heat transfer tubes 1A further include fins 5 and fins 6 extending in the opposite z direction from the end of the circular tube 301. In embodiment 3, the heat transfer tube 1A is configured by connecting two round tubes 301, but may be configured by connecting a larger number of round tubes 301. Although the refrigerant flows through the circular tube 301, the cross-sectional shape of the circular tube 301 may be not only a circle but also an ellipse or other shape.

The heat exchanger 350 includes a reinforcing member 303 in an arrangement of a plurality of heat transfer tubes 1A. In the cross section shown in fig. 12, the reinforcing member 303 has the same outer shape as the plurality of heat transfer pipes 1A. The reinforcing member 303 3D arranges two cylindrical bars and connects them with a plate 304. Further, the reinforcing member 303 is provided with a plate material 305 and a plate material 306 extending from the ends in the z direction and the direction opposite to the z direction. Since the reinforcing member 303 is formed by connecting solid bars 3D with the plate material 304, the section modulus about the neutral axis N along the z-direction is larger than that of the plurality of heat transfer tubes 1A.

The heat exchanger 350 may change the arrangement of the reinforcing member 303. For example, the heat exchanger 50 of embodiment 1 may be disposed at the end of the array of the plurality of heat transfer tubes 1A. In addition, the heat exchanger 350 may further increase the number of the reinforcing members 303.

According to the heat exchanger 350 of embodiment 3, the strength and rigidity of the reinforcing member 303 are higher than those of the heat transfer tube 1A. The end 31 and the end 32 of the reinforcing member 303 inserted into the insertion portion of the header 2 have the same shape as the heat transfer tube 1A. Therefore, the insertion portion of the header 2 into which the reinforcing member 303 is inserted can be formed in the same shape as the insertion portion into which the heat transfer tube 1A is inserted. Therefore, the reinforcing member 303 can be inserted into the header 2 in the same manner as the heat transfer tubes 1A while having a shape with higher strength and rigidity than the heat transfer tubes 1A. Therefore, the heat exchanger 350 is easily manufactured.

In addition, in the reinforcing member 303, not only the bar stock 3D but also the plates 304, 305, and 306 can be joined to the header 2. Thus, the plates 304, 305, and 306 can also contribute to the strength and rigidity of the heat exchanger 350.

The embodiments are described above, but are not limited to the above embodiments. For example, the embodiments may be combined. In short, it is to be noted that various modifications, applications, and application ranges, which are required by those skilled in the art, are also included in the technical scope for the sake of brevity. The flat tubes 1, 1A, 1b of embodiments 1 to 2 and the heat transfer tube 1A of embodiment 3 are all included in some cases, and are referred to as heat transfer tubes.

Description of the reference numerals

1 flat tube, 1A heat transfer tube, 1A flat tube, 1B flat tube, 1x flat tube, 2 header, 2a first header, 2B second header, 3 reinforcing member, 3A reinforcing member, 3Aa reinforcing member, 3Ab reinforcing member, 3Ac reinforcing member, 3B reinforcing member, 3C reinforcing member, 3D rod, 3A reinforcing member, 3B reinforcing member, 4 fin, 5 fin, 11 end, 12 end, 13 heat transfer portion, 31 end, 32 end, 33 center portion, 34 end, 50 heat exchanger, 50A heat exchanger, 50B heat exchanger, 50C heat exchanger, 50x heat exchanger, 60A first side end, 60B second side end, 60C flat surface, 60D flat surface, 100 refrigeration cycle device, 101 compressor, 102 flow switching device, 103 indoor heat exchanger, 104 pressure reducing device, 105 outdoor heat exchanger, 106 outdoor unit, 107 indoor unit, 108 outdoor unit, 109 indoor unit, 110 refrigerant circuit, 111 extension piping, 112 extension, 113 center portion, 130 fan heat transfer promoting member, 150 heat exchanger, 250 heat exchanger, 301, 305 heat exchanger, 305, 350 x heat exchanger, 350, F plate shape, F, 1, N, and RF plate shape, and the like.

Claims

1. A heat exchanger, comprising:

a plurality of heat transfer pipes arranged in a first direction at a distance from each other to circulate a refrigerant;

a first header connected to one end of each of the plurality of heat transfer tubes;

a second header connected to the other end of each of the plurality of heat transfer tubes; and

a plurality of reinforcing members connected to the first header and the second header,

the plurality of heat transfer tubes and the plurality of reinforcing members are disposed between the first header and the second header, are connected by the first header and the second header, have no heat transfer promoting members connecting the side surfaces to each other,

each of the plurality of reinforcing members has:

two insertion portions inserted into the first header or the second header at both ends of the reinforcing member; and

a central portion located between the two insertion portions,

the two insertion portions have the same outer shape as the plurality of heat transfer tubes in a first section orthogonal to tube axes of the plurality of heat transfer tubes,

the central portion having an outer shape different from the two insertion portions in the first cross section, the central portion having flange portions extending in the first direction and in a direction opposite to the first direction at both ends in a second direction orthogonal to the first direction and to tube axes of the plurality of heat transfer tubes,

an end surface of the central portion abuts at least one of the first header and the second header.

2. The heat exchanger of claim 1, wherein,

the plurality of reinforcing members are provided with a first reinforcing member that is disposed adjacent to two heat transfer tubes among the plurality of heat transfer tubes in the first direction.

3. A heat exchanger according to claim 1 or 2, wherein,

the plurality of reinforcing members include second reinforcing members disposed outside heat transfer tubes located at both ends in the first direction among the plurality of heat transfer tubes.

4. A heat exchanger according to claim 1 or 2, wherein,

the plurality of reinforcing members are arranged in the first direction together with the plurality of heat transfer tubes, and are arranged at positions symmetrical with respect to a center of the arrangement of the plurality of heat transfer tubes.

5. A heat exchanger according to claim 1 or 2, wherein,

the plurality of reinforcing members and the plurality of heat transfer pipes are arranged at equal intervals in the first direction.

6. A heat exchanger according to claim 1 or 2, wherein,

each of the plurality of reinforcing members has a section modulus about a neutral axis intersecting the first direction that is greater than a section modulus of the plurality of heat transfer tubes in the first section.

7. A heat exchanger according to claim 1 or 2, wherein,

the plurality of reinforcing members are composed of a material having a higher strength than the plurality of heat transfer tubes.

8. A heat exchanger according to claim 1 or 2, wherein,

each of the plurality of heat transfer tubes is a flat tube,

each of the plurality of reinforcing members has a flat side surface, and the side surface is disposed so as to face a flat surface of the flat tube in a longitudinal direction of the cross-sectional shape in a cross-section perpendicular to a tube axis of the flat tube.

9. A heat exchanger according to claim 1 or 2, wherein,

the plurality of reinforcing members are disposed outside of the heat transfer tubes located at both ends in the first direction among the plurality of heat transfer tubes.

10. A refrigeration cycle apparatus comprising the heat exchanger according to any one of claims 1 to 9.