JP7595441B2 - Heat exchanger and air conditioning device - Google Patents

Description

This disclosure relates to a heat exchanger and an air conditioning device.

Some heat exchangers have multiple heat transfer tubes arranged in one direction, and a reinforcing plate is provided along the end of the heat transfer tube.

For example, Patent Document 1 discloses a heat exchanger equipped with a reinforcing plate having bent portions formed at both ends and cutouts formed at each of the bent portions into which a heat transfer tube is fitted and to which the heat transfer tube is joined.

Patent document 2 discloses a heat exchanger in which both ends of a heat transfer tube are fixed to a tube plate inserted therein and a reinforcing plate is disposed along the heat transfer tube.

Japanese Unexamined Patent Publication No. 153691/1983 JP 2006-52866 A

When a heat exchanger is incorporated into an air conditioning system and the air conditioning system is operating in heating or cooling mode, the refrigerant flowing through the heat transfer tubes can become very hot. As a result, the heat transfer tubes can expand due to heat.

In this case, in the heat exchanger described in Patent Document 1, both ends of the heat transfer tube are joined to the notches on both ends of the reinforcing plate. This can cause thermal stress to occur in the heat transfer tube and the reinforcing plate. As a result, the heat exchanger can be destroyed by the thermal stress exceeding the yield point, or fatigue failure can occur in the heat exchanger due to repeated heating and cooling.

In addition, in the heat exchanger described in Patent Document 2, both ends of the heat transfer tubes are fixed to respective tube plates, and further, each tube plate is fixed to a reinforcing plate. For this reason, thermal stress occurs even in the heat exchanger described in Patent Document 2, and as a result, the heat exchanger may be destroyed.

This disclosure has been made to solve the above problems, and aims to provide a heat exchanger and air conditioner that are prevented from being destroyed by thermal stress.

In order to achieve the above object, the heat exchanger according to the present disclosure includes a first heat exchanger core, a first header, a second header, and a reinforcing member. The first heat exchanger core has a plurality of first heat transfer tubes arranged in one direction and a plurality of first fins connected to the plurality of first heat transfer tubes. The first header is connected to one end of each of the plurality of first heat transfer tubes, and causes a refrigerant to flow through each of the plurality of first heat transfer tubes. The second header is connected to the other end of each of the plurality of first heat transfer tubes, and the refrigerant flows into the second header from each of the plurality of first heat transfer tubes. Furthermore, the reinforcing member extends in the extension direction of the first heat transfer tube at the end of the arrangement direction among the plurality of first heat transfer tubes, and is arranged along the first heat transfer tube to reinforce the first heat transfer tube. At least one of the first header and the second header has a first protrusion. Furthermore, the reinforcing member has a flat portion with a plate surface facing in one direction and extending in the extension direction, and two upright walls that stand in one direction from both ends of the flat portion in the one direction and in a direction perpendicular to the extension direction. The ends of the two upright walls in the extension direction protrude further than the flat portion in the extension direction and sandwich at least one of the first header and the second header, and each of the two upright walls has a recess that is recessed inward from the end face in the extension direction and toward the opposite side of the extension direction, into which the first protrusion fits. At least one of the first header and the second header holds the reinforcing member slidably in the extension direction by the first protrusion being slidable within the recess in the extension direction .

According to the configuration of the present disclosure, the reinforcing member extends in the extension direction of the first heat transfer tube, and at least one of the first header and the second header holds the reinforcing member slidably in the direction in which the reinforcing member extends. Therefore, the reinforcing member does not restrain the first heat transfer tube in the extension direction. As a result, thermal stress is unlikely to occur in the joints between the first heat transfer tube and the first and second headers, and in the first heat transfer tube. As a result, it is possible to prevent destruction of the heat exchanger due to thermal stress.

FIG. 1 is a perspective view of an outdoor unit of an air conditioner including a heat exchanger according to a first embodiment of the present disclosure. FIG. 1 is a block diagram of an outdoor unit of an air conditioner including a heat exchanger according to a first embodiment of the present disclosure. FIG. 1 is a perspective view of a heat exchanger according to a first embodiment of the present disclosure; FIG. 1 is an enlarged perspective view of an upper portion of a heat exchanger according to a first embodiment of the present disclosure. FIG. 1 is a conceptual diagram of a heat exchanger core included in a heat exchanger according to a first embodiment of the present disclosure. FIG. 1 is an enlarged perspective view of a right side surface portion of a heat exchanger according to a first embodiment of the present disclosure. FIG. 1 is an enlarged perspective view of an upper end portion of a side plate included in a heat exchanger according to a first embodiment of the present disclosure. FIG. 11 is an enlarged perspective view of a lower portion of a heat exchanger according to a second embodiment of the present disclosure.

Hereinafter, a heat exchanger and an air conditioning device according to an embodiment of the present disclosure will be described in detail with reference to the drawings. In the drawings, the same or equivalent parts are given the same reference numerals. In the Cartesian coordinate system XYZ shown in the drawings, when the extension direction of the heat transfer tubes of the heat exchanger is in the up-down direction and the extension direction of the header to which the heat transfer tubes are connected is in the left-right direction, the left-right direction is the X-axis, the front-rear direction is the Y-axis, and the direction perpendicular to the X-axis and Y-axis is the Z-axis. Below, this coordinate system will be referred to as appropriate in the explanation.

(Embodiment 1)
The heat exchanger according to the first embodiment is a heat exchanger used in an outdoor unit of an air conditioner. In this heat exchanger, in order to prevent thermal stress, a side plate is provided so as to be slidable in the extending direction of a heat transfer tube.

First, the configuration of the outdoor unit of the air conditioner will be explained with reference to Figures 1 and 2.

Figure 1 is a perspective view of an outdoor unit 100 of an air conditioner equipped with a heat exchanger 1A according to embodiment 1. Figure 2 is a block diagram of the outdoor unit 100.

As shown in FIG. 1, the outdoor unit 100 of the air conditioner is a so-called top-flow type outdoor unit. The outdoor unit 100 includes a housing 110 and a bellmouth 120 placed on the housing 110.

The housing 110 is formed in the shape of a rectangular box. Inside it, the components of the outdoor unit 100, such as the compressor 131, four-way valve 132, accumulator 133, and heat exchanger 1A shown in FIG. 2, are housed.

Here, the compressor 131 is a component that compresses the refrigerant. The four-way valve 132 is a component that switches the flow of the refrigerant. The accumulator 133 is a component that stores the liquid portion of the refrigerant and separates the gas portion. The heat exchanger 1A is a component that exchanges heat between the refrigerant and air.

These components housed in the outdoor unit 100 are connected to the indoor unit 200. These components are connected in the following order: compressor 131, four-way valve 132, heat exchanger 1A, indoor unit 200, and accumulator 133. As a result, these components form a refrigerant circuit that circulates the refrigerant. In this refrigerant circuit, the four-way valve 132 switches the flow of the refrigerant. As a result, the air conditioner cools or heats the air in the room.

In detail, when the four-way valve 132 is switched to one direction, the refrigerant flows in the direction indicated by the arrow A. The refrigerant is converted into a high-temperature, high-pressure gas by the compressor 131, and then supplied to the heat exchanger 1A. The refrigerant is then cooled by heat exchange with outdoor air in the heat exchanger 1A, and then expanded by an expansion valve (not shown) to reduce the pressure and change into a low-temperature liquid. The refrigerant then absorbs heat from the air inside the room in the heat exchanger of the indoor unit 200. As a result, the air conditioner cools the room. The refrigerant then returns to the compressor 131.

In contrast, when the four-way valve 132 is switched from this state, the refrigerant flows in the opposite direction. The refrigerant flows from the compressor 131 to the heat exchanger of the indoor unit 200, where it dissipates heat to the indoor air. As a result, the air conditioner heats the room. The refrigerant is then expanded by an expansion valve (not shown) and turns into a low-temperature liquid, after which it exchanges heat with the outdoor air in the heat exchanger 1A of the outdoor unit 100, and returns to the compressor 131.

In this way, in the components housed in the outdoor unit 100, the flow of refrigerant changes when the four-way valve 132 is switched. For ease of understanding, the following will be explained using as an example the flow of refrigerant when the air conditioner is in cooling operation.

Returning to FIG. 1, a bell mouth 120 is provided on the top surface 111 of the housing 110 to take in air for conditioning the above-mentioned components into the housing 110.

Although not shown, the bellmouth 120 is connected to an opening formed in the upper surface 111 of the housing 110. A blower 134 shown in FIG. 2 is disposed inside the bellmouth 120. When the blower 134 operates, the bellmouth 120 expels the air inside to the outside. In this way, the bellmouth 120 sucks in air inside the housing 110 shown in FIG. 1 and expels the air to the top of the housing 110.

On the other hand, an air vent (not shown) is opened in the front part 112 of the housing 110. This allows the blower 134 in the bell mouth 120 to draw air in from the front part 112. As shown in FIG. 1, a heat exchanger 1A is disposed in the front part 112 to exchange heat with the drawn-in air. Next, the configuration of the heat exchanger 1A will be described with reference to FIG. 3 and FIG. 4.

Figure 3 is a perspective view of heat exchanger 1A. Figure 4 is an enlarged perspective view of the upper part of heat exchanger 1A. Figure 5 is a conceptual diagram of heat exchanger cores 20, 30 provided in heat exchanger 1A. Note that in Figure 4, for ease of understanding, the heat exchanger 1A is illustrated with the upper right portion cut away.

As shown in FIG. 3, the heat exchanger 1A includes headers 11-13 through which the refrigerant flows in and out, heat exchanger cores 20, 30 joined to the headers 11-13, and side plates 40, 50 that reinforce the heat exchanger cores 20, 30.

The headers 11 and 13 are components that distribute refrigerant to the heat exchanger cores 20 and 30, or collect refrigerant from the heat exchanger cores 20 and 30. The headers 11 and 13 have rectangular tubular flow paths that extend horizontally. The headers 11 and 13 are arranged adjacent to each other in the front-to-rear direction.

The header 11 is connected to the compressor 131 shown in FIG. 2 by a refrigerant pipe (not shown). The header 11 receives a supply of refrigerant from the compressor 131. On the other hand, the heat exchanger core 20 includes a large number of heat transfer tubes 21 as shown in FIG. 4. The header 11 is connected to these heat transfer tubes 21. As a result, the header 11 distributes the refrigerant supplied from the compressor 131 to these heat transfer tubes 21.

As shown in FIG. 5, the heat exchanger core 20 includes a large number of heat transfer tubes 21 as described above. The heat exchanger core 20 also includes fins 22 connected to each of the heat transfer tubes 21.

As shown in FIG. 4, each heat transfer tube 21 extends in the vertical direction. They are arranged in the horizontal direction. The lower end of each heat transfer tube 21 is connected to the header 11, not shown. As a result, each heat transfer tube 21 receives the refrigerant from the header 11. Each heat transfer tube 21 transfers the heat of the refrigerant to the fins 22 shown in FIG. 5, and releases the heat when the fins 22 come into contact with the outside air. As a result, each heat transfer tube 21 cools the heat of the refrigerant. Meanwhile, the upper end of each heat transfer tube 21 is connected to the header 12, as shown in FIG. 4.

The header 12 is a part for circulating the refrigerant between the heat exchanger cores 20 and 30. As described above, the upper ends of the heat transfer tubes 21 of the heat exchanger core 20 are connected to the header 12. On the other hand, the heat exchanger core 30 also has a large number of heat transfer tubes 31 extending in the vertical direction, similar to the heat exchanger core 20. The upper ends of the heat transfer tubes 31 of the heat exchanger core 30 are connected to the header 12. The header 12 has a rectangular tube shape extending in the horizontal direction, and a flow path that functions as a return tube is provided inside the header 12, although not shown. The header 12 directs the refrigerant flowing from the heat transfer tubes 21 of the heat exchanger core 20 to the heat transfer tubes 31 of the heat exchanger core 30.

As shown in FIG. 4, the heat exchanger core 30 includes a large number of heat transfer tubes 31 that extend in the vertical direction and are arranged in the horizontal direction. As shown in FIG. 5, the heat exchanger core 30 also includes fins 32 provided on each of the heat transfer tubes 31.

As shown in FIG. 5, the heat transfer tubes 31 of the heat exchanger core 30 are arranged on the rear side of the heat transfer tubes 21 of the heat exchanger core 20. The fins 32 of the heat exchanger core 30 are also arranged on the rear side of the fins 22 of the heat exchanger core 20. In the outdoor unit 100 shown in FIG. 1, the front side is the side where air is sucked in, in other words, the upwind side. The heat transfer tubes 31 and fins 32 of the heat exchanger core 30 release heat transferred from the refrigerant to the outside air on the downwind side. This cools the refrigerant. The lower end of the heat transfer tubes 31 is connected to the header 13 shown in FIG. 3, and the cooled refrigerant is discharged to the header 13.

The header 13 is connected to the heat exchanger of the indoor unit 200 shown in FIG. 2. The header 13 collects refrigerant from each of the heat transfer tubes 31 of the heat exchanger core 30 and supplies the collected refrigerant to the heat exchanger of the indoor unit 200.

On the other hand, as shown in FIG. 3, a side plate 40 is provided on the right side of the heat exchanger cores 20, 30 to protect the heat transfer tubes 21, 31 arranged on the rightmost side of the heat exchanger cores 20, 30. Also, a side plate 50 is provided on the left side of the heat exchanger cores 20, 30 to protect the heat transfer tubes 21, 31 arranged on the leftmost side of the heat exchanger cores 20, 30.

As shown in FIG. 4, the side plate 40 has a plate shape bent into an inverted U shape when viewed from above. In detail, the side plate 40 has a flat portion 41 extending in the front-rear direction, and upright walls 42F, 42B at the front and rear ends of the flat portion 41, which are bent at right angles.

The flat surface 41 covers the right-most heat transfer tubes 21, 31 of the heat exchanger cores 20, 30 from the right side to protect those heat transfer tubes 21, 31. Meanwhile, the upright walls 42F, 42B are formed with through holes 43F, 43B for passing screws, as shown in FIG. 3. The through holes 43F, 43B are passed with screws to be attached to the housing 110 shown in FIG. 1. In this way, the upright walls 42F, 42B are fixed to the housing 110.

Although not shown, side plate 50 has the same configuration as side plate 40, except that it is symmetrical to side plate 40. For this reason, a description of the configuration of side plate 50 will be omitted.

Returning to FIG. 3, the upper ends of the side plates 40, 50 are adjacent to the header 12. The lower ends of the side plates 40, 50 are adjacent to the headers 11, 13. Therefore, in order to increase the strength of the heat exchanger 1A, it is possible to join the side plates 40, 50 to the headers 11-13.

However, as mentioned above, when the air conditioner is in cooling operation, a high-temperature, high-pressure refrigerant is supplied to the heat exchanger 1A from the compressor 131. Therefore, the header 11 and the lower end portions of the heat transfer tubes 21 located in the vicinity thereof are prone to becoming hot, which can result in thermal expansion of the heat transfer tubes 21.

In such a case, if the lower and upper ends of the heat transfer tube 21 are joined to the headers 11 and 12, thermal stress will be generated in the heat transfer tube 21 and the side plates 40, 50 during cooling operation. As a result, if the generated thermal stress exceeds the yield point, the heat transfer tube 21 and the side plates 40, 50 will be damaged. In addition, repeated heating and cooling may cause fatigue failure in the heat transfer tube 21 and the side plates 40, 50.

To prevent damage due to thermal stress, the side plates 40, 50 are held in the headers 11-13 so that they can slide up and down in the direction in which the heat transfer tubes 21 extend. Next, the configuration of the side plates 40, 50 will be described with reference to Figures 6 and 7.

Figure 6 is an enlarged perspective view of the right side of heat exchanger 1A. Figure 7 is an enlarged perspective view of the upper end of side plate 40 of heat exchanger 1A.

As shown in FIG. 6, the side plate 40 has hooks 44F, 44B formed at the right ends of the upright walls 42F, 42B, and recesses 45F, 45B formed at the upper ends of the upright walls 42F, 42B.

As shown in FIG. 7, each of the hook portions 44F, 44B is formed in a flat rectangular shape perpendicular to the left-right direction. Each of the hook portions 44F, 44B is disposed on the upper end side of the right end of the standing wall 42F, 42B. Each of the hook portions 44F, 44B extends from the upper end side of the right end of the standing wall 42F, 42B toward between the standing walls 42F and 42B. More specifically, the hook portion 44F extends rearward from the standing wall 42F. The hook portion 44B extends forward from the standing wall 42B. Below the hook portions 44F, 44B, a horizontal wall 46 is provided that extends horizontally to the right from the flat portion 41.

In contrast, as shown in FIG. 6, the header 12 is formed in a rectangular tube shape, and its right end extends above the side plate 40. The right end of the header 12 is inserted between the upright walls 42F, 42B. The vertical position, i.e., the Z coordinate of the right end of the header 12, is determined by the bottom of the header 12 abutting against the horizontal wall 46 of the side plate 40.

In this state, the hook portions 44F and 44B abut against the right end face of the header 12. As a result, the hook portions 44F and 44B determine the left-right position of the header 12, i.e., the X coordinate of the header 12.

On the other hand, as shown in FIG. 7, the recesses 45F and 45B are formed at the upper ends of the upright walls 42F and 42B, respectively. They are shaped like rectangular recesses extending downward from the upper ends of the upright walls 42F and 42B, respectively.

In contrast, as shown in FIG. 6, protrusions 121F and 121B are formed on the right end side of the header 12. In detail, the header 12 is inserted between the upright walls 42F and 42B as described above. The width of the header 12 in the front-to-rear direction is the same as the distance between the upright walls 42F and 42B in the front-to-rear direction. As a result, the front wall 122F and the rear wall 122B of the header 12 abut against the upright walls 42F and 42B. A protrusion 121F is formed in the area of the front wall 122F that overlaps with the recess 45F in the front-to-rear direction. Also, a protrusion 121B is formed in the part of the rear wall 122B that overlaps with the recess 45B in the front-to-rear direction.

The protrusions 121F, 121B are formed in a rectangular parallelepiped shape. The rectangular tip surfaces face forward and backward. The left-right width of the tip surfaces of the protrusions 121F, 121B is substantially the same as the left-right width of the rectangular recesses 45F, 45B to an extent that they can be fitted into. In addition, the vertical length of the tip surfaces of the protrusions 121F, 121B is smaller than the vertical length of the recesses 45F, 45B. As a result, the protrusions 121F, 121B have a shape that can be fitted into the recesses 45F, 45B.

The length of the protrusions 121F, 121B in the front-rear direction is greater than the thickness of the upright walls 42F, 42B. The protrusions 121F, 121B are fitted into the recesses 45F, 45B. As a result, the protrusions 121F, 121B pass through the internal spaces of the recesses 45F, 45B and protrude to the outside of the recesses 45F, 45B. They hook onto the inner walls of the recesses 45F, 45B. This allows the header 12 to hold the side plate 40.

As described above, the vertical length of the tip surface of the protrusions 121F, 121B is smaller than the vertical length of the recesses 45F, 45B. Therefore, the protrusions 121F, 121B can slide vertically within the recesses 45F, 45B when fitted in the recesses 45F, 45B. Since the right and left surfaces of the protrusions 121F, 121B are in contact with the inner walls of the recesses 45F, 45B, respectively, they can slide when a force exceeding the static friction force or the kinetic friction force is applied. The sliding distance is the same as the vertical length of the recesses 45F, 45B because the upper side of the recesses 45F, 45B is open. As a result, even if the heat transfer tubes 21, 31 of the heat exchanger cores 20, 30 thermally expand and the position of the header 12 changes in the vertical direction, the protrusions 121F, 121B can slide vertically within the recesses 45F, 45B. As a result, the side plate 40 can absorb vertical movement of the header 12.

In this way, the header 12 is not restrained in the vertical direction by the side plate 40. This means that no thermal stress is applied to the header 12 and the heat transfer tubes 21, 31 joined to the header 12. In addition, no thermal stress is applied to these joints. As a result, damage to the header 12 and the heat transfer tubes 21, 31 due to thermal stress can be prevented.

In addition, since the protrusions 121F, 121B can slide vertically within the recesses 45F, 45B, the side plate 40 is not vertically constrained by the header 12. This means that the side plate 40 is not subjected to thermal stress. As a result, damage to the side plate 40 due to thermal stress can be prevented.

Although not shown, the lower end of the side plate 40 is joined to the right end of each of the headers 11 and 13. The joining means is, for example, brazing. However, as described above, the upper end of the side plate 40 is not vertically constrained by the header 12. Therefore, no thermal stress is applied to the heat transfer tubes 21 and 31 and the side plate 40, and destruction due to thermal stress is prevented.

The heat transfer tubes 21, 31 and fins 22, 32 of the heat exchanger cores 20, 30 are preferably made of an aluminum alloy and joined by brazing.

The protrusions 121F, 121B are preferably made of a material that is softer than the material that forms the side plates 40, 50, i.e., a soft material. This is because such a material can deform to follow the positional changes of the protrusions 121F, 121B due to thermal expansion. As a result, the side plates 40, 50 are not constrained, and thermal stress is less likely to occur. For example, the protrusions 121F, 121B are preferably made of a resin material. When the side plates 40, 50 are made of metal, the protrusions 121F, 121B are preferably made of a soft resin that is softer than the metal, such as a mixed resin exemplified by synthetic rubber, ABS (acrylonitrile butadiene styrene) resin, PS (polystyrene) resin, AS (acrylonitrile styrene copolymer) resin, and PC/ABS (polycarbonate/acrylonitrile butadiene styrene) alloy.

As described above, in the heat exchanger 1A according to the first embodiment, the side plates 40, 50 extend in the vertical direction, which is the extension direction of the heat transfer tubes 21, 31, and the header 12 holds the side plates 40, 50 so that they can slide in the vertical direction. Therefore, the side plates 40, 50 do not constrain the heat transfer tubes 21, 31 in the vertical direction. As a result, thermal stress is unlikely to occur at the joints between the heat transfer tubes 21, 31 and the header 12, and in the heat transfer tubes 21, 31 themselves. As a result, it is possible to prevent the heat exchanger 1A from being destroyed by thermal stress.

For example, during cooling operation when the outside temperature is low, the refrigerant becomes hot despite the low outside temperature. As a result, the heat transfer tubes 21 and 31 stretch due to thermal expansion. However, even in such a case, it is possible to prevent damage to the heat exchanger 1A due to thermal stress.

To give a more detailed example, in cooling operation when the outside air temperature is -10°C, the refrigerant temperature flowing into the header 11 may be 100°C. In this case, if the Z-direction length of the heat transfer tubes 21, 31 is 800 mm, the material of the heat transfer tubes 21, 31 is an aluminum alloy with alloy number A3003 standardized by the Japanese Standards Association and its linear expansion coefficient is 23.7, and the temperature of the refrigerant flowing in the portion of the heat transfer tube 21 up to 100 mm above the header 11 remains at 100°C, the heat transfer tubes 21, 31 will expand by 0.26 mm in the vertical direction due to thermal expansion. However, even in such a case, by setting the sliding distance of the above-mentioned protrusions 121F, 121B to be greater than 0.26 mm, it is possible to prevent the heat exchanger 1A from being destroyed by thermal stress.

In addition, if frost forms on the heat exchanger 1A during heating operation, a so-called hot gas defrosting process may be performed to melt the frost using latent heat and sensible heat. At that time, the temperature near the header 11 may rise suddenly, causing the heat transfer tubes 21 and 31 to thermally expand. However, even in such a case, it is possible to prevent damage to the heat exchanger 1A due to thermal stress.

The heat exchanger cores 20 and 30 are examples of the first heat exchanger core and the second heat exchanger core as defined in this specification. The heat transfer tubes 21 and the fins 22 are examples of the first heat transfer tube and the first fin as defined in this specification. The heat transfer tubes 31 and the fins 32 are examples of the second heat transfer tube and the second fin as defined in this specification. The lower end and the upper end of the heat transfer tube 21 are examples of one end and the other end of the first heat transfer tube as defined in this specification, and the upper end and the lower end of the heat transfer tube 31 are examples of one end and the other end of the second heat transfer tube as defined in this specification. The left or right direction in which the heat transfer tubes 21 are lined up is an example of one direction in which the first heat transfer tubes are arranged as defined in this specification. It is also an example of the arrangement direction of the first heat transfer tubes. The headers 11-13 are examples of the first header, the second header, and the third header as defined in this specification. The side plates 40 and 50 are examples of the reinforcing members as defined in this specification. Protrusions 121F and 121B are an example of the first protrusion as defined in this specification.

In addition, the recesses 45F, 45B function as hooks or locks because they hook onto the protrusions 121F, 121B from below. For this reason, in this specification, the recesses 45F, 45B are also referred to as hooks or locks. Note that the recesses 45F, 45B are an example of the first hook-shaped portion as defined in this specification.

(Embodiment 2)
Although not shown in the drawings, in the heat exchanger 1A according to the first embodiment, the side plates 40, 50 are joined to the headers 11, 13. However, the side plates 40, 50 do not have to be joined to the headers 11, 13. In other words, the side plates 40, 50 do not have to be fixed to the headers 11, 13.

In the heat exchanger 1B according to embodiment 2, the side plate 60 is fixed to the header 13 but not to the header 11.

Hereinafter, the heat exchanger 1B according to the second embodiment will be described with reference to FIG. 8. In the second embodiment, the configuration different from the first embodiment will be mainly described.

Figure 8 is an enlarged perspective view of the lower part of heat exchanger 1B according to embodiment 2. Note that in Figure 8, only the right end of heat exchanger 1B is shown because the configuration of the left end of heat exchanger 1B is the same as that of the right end of heat exchanger 1B except that it is symmetrical.

As shown in FIG. 8, the side plate 60 of the heat exchanger 1B has a horizontal wall 66 at its lower end.

In detail, like the side plate 40 described in the first embodiment, the side plate 60 has a flat surface 61 extending in the front-rear direction, and upright walls 62F, 62B formed by bending the plate at right angles at the front and rear ends of the flat surface 61. Between the upright walls 62F, 62B, a horizontal wall 66 is provided that is bent to the right from the bottom end of the flat surface 61.

In contrast, each of the headers 11 and 13 is formed in the shape of a rectangular tube. The headers 11 and 13 are adjacent to each other in the front-to-rear direction. However, the headers 11 and 13 are not joined to each other, but are merely adjacent to each other in the front-to-rear direction.

The headers 11 and 13 are adjacent to each other in the front-rear direction and extend in the left-right direction. Their right ends are inserted between the upright walls 62F and 62B, with their vertical positions determined by the horizontal wall 66 of the side plate 60. Of the right ends of the inserted headers 11 and 13, the right end of the header 13 has a folded portion 14 that extends to the right, bends upward, and then bends back to the left. The horizontal wall 66 is sandwiched between the folded portion 14. As a result, the header 13 holds the side plate 60. Furthermore, although not shown, the folded portion 14 and the horizontal wall 66 are brazed. As a result, the header 13 and the side plate 60 are joined together. As a result, the side plate 60 is fixed to the header 13.

On the other hand, the header 11 is not joined to the plate 60. Although not shown, the header 11 is joined to the heat transfer tube 21 connected to the header 12 described in the first embodiment. As a result, the header 11 is suspended from the header 12 via the heat transfer tube 21. Therefore, when the heat transfer tube 21 thermally expands, the position of the header 11 moves up and down in response to the thermal expansion.

In this way, the header 11 is not restrained by the plate 60. As a result, even if the heat transfer tubes 21 and 31 thermally expand, the header 11 is not subjected to thermal stress. As a result, damage to the header 11 due to thermal stress is prevented.

As described above, in the heat exchanger 1B according to the second embodiment, the header 11 is not joined to the plate 60 and is not constrained by the plate 60. As a result, the heat exchanger 1B can be prevented from being destroyed by thermal stress.

The header 11 is supplied with high-temperature refrigerant during cooling operation and is prone to high temperatures. As a result, the heat transfer tube 21 connected to the header 11 is prone to thermal expansion. In addition, the heat transfer tube 21 is arranged on the upwind side. This places the heat transfer tube 21 in an environment where temperature changes are large and fatigue failure is likely to occur. In the heat exchanger 1B, the header 11 is not restrained by the plate 60, so fatigue failure can be prevented more effectively.

In the heat exchanger 1B, although not shown, the header 12 holds the side plate 60 so that it can slide up and down in the direction in which the heat transfer tubes 21 and 31 extend. As a result, no thermal stress is generated in the side plate 60, and no thermal stress is generated in the heat transfer tubes 21 and 31. This prevents the heat exchanger 1B from being destroyed by thermal stress.

The above describes the heat exchangers 1A, 1B and air conditioning devices according to the embodiments of the present disclosure, but the heat exchangers 1A, 1B and air conditioning devices are not limited to this.

For example, in the first and second embodiments, the heat exchangers 1A and 1B are provided with side plates 40, 50, and 60 that reinforce the heat exchanger cores 20 and 30. However, the heat exchangers 1A and 1B are not limited to this. The side plates 40, 50, and 60 may be reinforcing members that extend in the direction in which the heat transfer tubes 21 and 31 of the heat exchanger cores 20 and 30 extend and reinforce the heat transfer tubes 21 and 31. The side plates 40, 50, and 60 may be columnar members having a shape such as a rectangular column or a cylinder. In this case, the columnar members may be formed of metal, synthetic resin, or the like.

In addition, in the first and second embodiments, the side plates 40, 50, and 60 are in the shape of plates bent into a U-shape when viewed from above, but they may be in the shape of flat plates that are not bent. The side plates 40, 50, and 60 may simply be called plates.

In the first and second embodiments, the header 12 has protrusions 121F, 121B, and the side plates 40, 50, 60 have recesses 45F, 45B. However, the header 12 and the side plates 40, 50, 60 are not limited to this. In the heat exchangers 1A, 1B, the side plates 40, 50, 60 may have protrusions 121F, 121B, and the header 12 may have recesses 45F, 45B. In this case, it is preferable that the protrusions of the side plates 40, 50, 60 fit into the recesses 45F, 45B of the header 12 and be able to slide in the extension direction of the heat transfer tubes 21, 31 within the recesses 45F, 45B.

In addition, in the first and second embodiments, the header 12 has the protrusions 121F, 121B, and the headers 11, 13 do not have the protrusions 121F, 121B, but the headers 11, 13 may have the protrusions 121F, 121B. In this case, the side plates 40, 50, 60 may have recesses 45F, 45B into which the protrusions 121F, 121B on the headers 11, 13 fit. In this case, the protrusions 121F, 121B on the headers 11, 13 may be slidable within the recesses 45F, 45B in the extension direction of the heat transfer tubes 21, 31.

Furthermore, the headers 11 and 13 may have recesses 45F and 45B, and the side plates 40, 50 and 60 may have protrusions 121F and 121B. In this case, the protrusions 121F and 121B of the side plates 40, 50 and 60 may fit into the recesses 45F and 45B of the headers 11 and 13, and may be slidable within the recesses 45F and 45B in the extension direction of the heat transfer tubes 21 and 31.

In this way, in the heat exchangers 1A and 1B, it is preferable that either the header 11-13 or the side plate 40, 50, or 60 has the protrusions 121F and 121B, and the other of the header 11-13 and the side plate 40, 50, or 60 has the recesses 45F and 45B.

The recesses 45F, 45B may be called hook-shaped portions because they hook onto the protrusions 121F, 121B. Also, if the header 11-13 has the protrusions 121F, 121B and the side plates 40, 50, 60 have the recesses 45F, 45B, the protrusions 121F, 121B in that case may be called first protrusions, and the recesses 45F, 45B in that case may be called first hook-shaped portions. Furthermore, if the side plates 40, 50, 60 have the protrusions 121F, 121B and the header 11-13 has the recesses 45F, 45B, the protrusions 121F, 121B in that case may be called second protrusions, and the recesses 45F, 45B in that case may be called second hook-shaped portions.

In addition, in the heat exchangers 1A and 1B in the first and second embodiments, the recesses 45F and 45B are recessed from the end faces of the side plates 40, 50, and 60 toward the inside of the plates. However, the recesses 45F and 45B are not limited to this. In the heat exchangers 1A and 1B, it is sufficient that at least one of the headers 11-13 holds the side plates 40, 50, and 60 slidably in the extension direction of the heat transfer tubes 21 and 31. For this reason, the recesses 45F and 45B may be replaced with elongated holes whose longitudinal direction is the extension direction of the heat transfer tubes 21 and 31.

In addition, in the first and second embodiments, the recesses 45F and 45B penetrate the side plates 40, 50, and 60, but they may simply be recessed in the thickness direction of the side plates 40, 50, and 60.

In the first and second embodiments, the side plates 40, 50, 60 are provided with the hook portions 44F, 44B arranged on the upright walls 42F, 42B. The side plates 40, 50, 60 are also provided with the horizontal walls 46, 66. However, the side plates 40, 50, 60 are not limited to this. The upright walls 42F, 42B, the hook portions 44F, 44B, and the horizontal walls 46, 66 are of any configuration. For example, the side plates 40, 50, 60 may not have the hook portions 44F, 44B. As with the lower end of the side plate 60 described in the second embodiment, only the upright walls 42F, 42B may be provided. Since the configuration is arbitrary, the number of the upright walls 42F, 42B, the hook portions 44F, 44B, and the horizontal walls 46, 66 is also arbitrary. These may be provided only on the side plate 40 of the heat exchangers 1A and 1B, or on both the side plates 40 and 50.

In the first and second embodiments, the heat exchangers 1A and 1B are incorporated in the outdoor unit 100 of the air conditioning system. However, the heat exchangers 1A and 1B are not limited to this. The heat exchangers 1A and 1B can be applied to any device that requires heat exchange. In addition, since the heat exchangers 1A and 1B have reinforcing members and are highly rigid, they are preferably incorporated and used in devices that require a certain degree of rigidity.

In addition, because the heat exchangers 1A and 1B are incorporated into the top-flow type outdoor unit 100, the headers 11-13 extend in the left-right direction. In addition, the side plates 40, 50, and 60 extend in the up-down direction. However, these orientations are arbitrary as long as the side plates 40, 50, and 60 extend in the same direction as the heat transfer tubes 21 and 31. The headers 11-13 and side plates 40, 50, and 60 may be oriented in a manner that corresponds to the orientation of the heat exchangers 1A and 1B themselves.

1A, 1B Heat exchanger, 11-13 Header, 14 Folded portion, 20, 30 Heat exchanger core, 21, 31 Heat transfer tube, 22, 32 Fin, 40, 50, 60 Side plate, 41, 61 Plane portion, 42F, 42B, 62F, 62B Standing wall, 43F, 43B Through hole, 44F, 44B Hanging portion, 45F, 45B Recess, 46, 66 Horizontal wall, 100 Outdoor unit, 110 Housing, 111 Top portion, 112 Front portion, 120 Bell mouth, 121F, 121B Protrusion, 122F Front wall, 122B Rear wall, 131 Compressor, 132 Four-way valve, 133 Accumulator, 134 Blower, 200 Indoor unit, A Arrow.

Claims (6)

a first heat exchanger core including a plurality of first heat transfer tubes arranged in one direction and a plurality of first fins connected to the plurality of first heat transfer tubes;
a first header connected to one end of each of the first heat transfer tubes and allowing a refrigerant to flow through each of the first heat transfer tubes;
a second header connected to the other end of each of the first heat transfer tubes and into which the refrigerant flows from each of the first heat transfer tubes;
a reinforcing member extending in an extension direction of a first heat transfer tube at an end of the arrangement direction among the plurality of first heat transfer tubes and disposed along the first heat transfer tube to reinforce the first heat transfer tube;
Equipped with
At least one of the first header and the second header has a first protrusion;
The reinforcing member has a plate surface facing the one direction, a flat portion extending in the extension direction, and two upright walls standing in the one direction from both ends of the flat portion in a direction perpendicular to the one direction and the extension direction,
The end portions of the two upright walls in the extension direction protrude beyond the flat portion in the extension direction, sandwiching at least one of the first header and the second header, and each of the two upright walls has a recess recessed inward from the end surface in the extension direction and toward the opposite side in the extension direction, into which the first protrusion fits,
At least one of the first header and the second header holds the reinforcing member slidably in the extension direction by the first protrusion being slidable in the extension direction within the recess. The two upright walls each have a hook portion extending toward a space between the upright walls and hooked to at least one end of the first header and the second header,
the reinforcing member has a wall portion extending from an end of the planar portion in the extending direction in a direction in which the two upright walls stand, and abutting against an end of at least one of the first header and the second header;
2. The heat exchanger of claim 1. The reinforcing member has a second projection,
At least one of the first header and the second header has a tip extending parallel to an extension direction of the first heat transfer tube, and the tip has a second hook-shaped portion that is hooked onto the second protrusion.
2. The heat exchanger of claim 1. the first header and the second header extend in an arrangement direction of the first heat transfer tubes,
The second hook-shaped portion is formed on an end surface of at least one of the first header and the second header in an extension direction, and has a recessed shape recessed inward from the end surface.
4. The heat exchanger of claim 3 . a first heat exchanger core including a plurality of first heat transfer tubes arranged in one direction and a plurality of first fins connected to the plurality of first heat transfer tubes;
a first header connected to one end of each of the first heat transfer tubes and allowing a refrigerant to flow through each of the first heat transfer tubes;
a second header connected to the other end of each of the first heat transfer tubes and into which the refrigerant flows from each of the first heat transfer tubes;
a reinforcing member extending in an extension direction of a first heat transfer tube at an end of the arrangement direction among the plurality of first heat transfer tubes and disposed along the first heat transfer tube to reinforce the first heat transfer tube;
a second heat exchanger core arranged on the leeward side of the first heat exchanger core, the second heat exchanger core including a plurality of second heat transfer tubes arranged in the one direction, the second header connected to one end thereof and into which a refrigerant flows from the second header, and a plurality of second fins connected to the plurality of second heat transfer tubes;
a third header connected to the other end of each of the second heat transfer tubes and into which the refrigerant flows from each of the second heat transfer tubes;
Equipped with
At least one of the first header and the second header holds the reinforcing member slidably in a direction in which the reinforcing member extends,
The reinforcing member is joined to the second header and the third header. An air conditioner comprising the heat exchanger according to any one of claims 1 to 5 .

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