JP7376654B2 - Heat exchanger and air conditioner - Google Patents

Description

The present invention relates to a heat exchanger.

The heat exchanger described in Patent Document 1 includes a plurality of flat tubes, a hollow cylindrical upper header, and a hollow cylindrical lower header. The plurality of flat tubes are arranged such that their longitudinal directions are inclined with respect to the vertical direction. An upper header and a lower header are connected to both ends of each flat tube. Each of the upper header and the lower header is arranged so that its longitudinal direction is parallel to the horizontal direction. The upper header is provided with two inlet tubes. The lower header is provided with one outlet pipe.

JP 2015-230129 Publication

However, in the structure of the heat exchanger described in Patent Document 1, when a plurality of heat exchangers are arranged in an air conditioner to increase the amount of heat exchange, the number of inlet pipes depends on the number of heat exchangers. and the number of outlet pipes increases. As a result, the refrigerant piping in the air conditioner becomes complicated.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a heat exchanger that can simplify refrigerant piping while increasing the amount of heat exchange.

According to one aspect of the present invention, the heat exchanger includes a first heat exchange unit that performs heat exchange. The first heat exchange unit includes a plurality of first flat tubes, a plurality of second flat tubes, a first header tube, a second header tube, and a third header tube. Each of the plurality of first flat tubes extends along the first direction, and the plurality of first flat tubes are lined up along the second direction orthogonal to the first direction. Each of the plurality of second flat tubes extends along the first direction, and the plurality of second flat tubes are lined up along the second direction. The first header tube is connected to one end of the plurality of first flat tubes in the first direction and extends along the second direction. The second header pipe is connected to the other end of the plurality of first flat tubes in the first direction and one end of the plurality of second flat tubes in the first direction, and extends along the second direction. . The third header tube is connected to the other ends of the plurality of second flat tubes in the first direction and extends along the second direction. The second header pipe includes at least one refrigerant inflow portion into which refrigerant flows from outside the first heat exchange unit, and at least one refrigerant outflow portion through which refrigerant flows out to the outside of the first heat exchange unit. .

According to the present invention, it is possible to provide a heat exchanger that can simplify refrigerant piping while increasing the amount of heat exchange.

1 is a perspective view showing an air conditioner according to Embodiment 1 of the present invention. 1 is a cross-sectional view schematically showing an air conditioner according to Embodiment 1. FIG. FIG. 3 is a diagram showing a first heat exchange unit of the air conditioner according to the first embodiment. FIG. 3 is a diagram showing a second heat exchange unit of the air conditioner according to the first embodiment. 1 is a diagram schematically showing piping in a heat exchanger of an air conditioner according to Embodiment 1. FIG. 1 is a diagram schematically showing the internal structure of a first heat exchange unit of an air conditioner according to Embodiment 1. FIG. FIG. 2 is a top view showing a heat exchanger and a fan unit of the air conditioner according to the first embodiment. It is a top view which shows the heat exchanger and fan unit of the air conditioner based on Embodiment 2 of this invention. FIG. 7 is a sectional view showing the inside of a second header pipe of the air conditioner according to the second embodiment. It is a figure which shows typically the internal structure of the 1st heat exchange unit of the air conditioner based on Embodiment 3 of this invention. It is a figure which shows typically the 1st heat exchange unit of the air conditioner based on Embodiment 4 of this invention. It is a figure which shows typically the internal structure of the 1st heat exchange unit of the air conditioner based on Embodiment 5 of this invention.

Embodiments of the present invention will be described below with reference to the drawings. In addition, in the drawings, the same or corresponding parts are given the same reference numerals and the description will not be repeated. Further, in the embodiment, the X-axis and the Y-axis are substantially parallel to the horizontal direction, the Z-axis is substantially parallel to the vertical direction, and the X-axis, Y-axis, and Z-axis are orthogonal to each other. A positive direction of the Z axis indicates an upward direction, and a negative direction of the Z axis indicates a downward direction.

(Embodiment 1)
An air conditioner 100 according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 7. First, the air conditioner 100 will be explained with reference to FIG. FIG. 1 is a perspective view showing an air conditioner 100. The air conditioner 100 performs air conditioning.

As shown in FIG. 1, the air conditioner 100 is an indoor unit. Therefore, the air conditioner 100 is installed indoors. Note that the air conditioner 100 is connected to an outdoor unit through piping. Then, the refrigerant circulates between the air conditioner 100 and the outdoor unit through the piping. The outdoor unit is installed outdoors. The outdoor unit includes various parts such as a fan, a compressor, a heat exchanger, and a four-way valve.

Air conditioner 100 includes a housing 1 and a panel 3. The panel 3 is supported by the casing 1 so that the attitude of the panel 3 can be changed with respect to the casing 1. The panel 3 has a substantially plate shape and is curved in a convex shape toward the housing 1.

Next, with reference to FIG. 2, the internal structure of the air conditioner 100 will be described. FIG. 2 is a cross-sectional view schematically showing the air conditioner 100. As shown in FIG. 2, the housing 1 of the air conditioner 100 has an inlet 10 and an outlet 13. The suction port 10 is located at the bottom of the housing 1 and opens toward the bottom of the housing 1. The air outlet 13 is open toward the panel 3.

The air conditioner 100 further includes a fan unit 5 and a heat exchanger 7. Heat exchanger 7 is located downstream of fan unit 5 in the air flow. The fan unit 5 and the heat exchanger 7 are housed in the housing 1. The fan unit 5 sucks air W1 through the suction port 10, and sends the sucked air W1 to the outside through the blowout port 13. Specifically, the fan unit 5 sends out the sucked air W1 toward the heat exchanger 7. As a result, the air W2 that has passed through the heat exchanger 7 passes through the air outlet 13 and is sent out toward the panel 3.

Heat exchanger 7 performs heat exchange. Specifically, the heat exchanger 7 includes a first heat exchange unit 9 and a second heat exchange unit 11. Each of the first heat exchange unit 9 and the second heat exchange unit 11 performs heat exchange. The first heat exchange unit 9 is located downstream of the second heat exchange unit 11 in the air flow.

Next, the first heat exchange unit 9 will be explained with reference to FIG. The first heat exchange unit 9 exchanges thermal energy between air and refrigerant. FIG. 3 is a diagram showing the first heat exchange unit 9. As shown in FIG. In FIG. 3, the first heat exchange unit 9 is viewed from the rear. In this specification, rear view refers to viewing the object from direction VD1 in FIG. 2 .

As shown in FIG. 3, the first heat exchange unit 9 is a parallel flow heat exchanger. Specifically, the first heat exchange unit 9 includes a first header pipe 21, a second header pipe 22, a third header pipe 23, a plurality of first flat tubes 31, and a plurality of second flat tubes 32. including.

Each of the plurality of first flat tubes 31 extends along the first direction D1 and is lined up along the second direction D2. The second direction D2 is orthogonal to the first direction D1. A refrigerant flows through the plurality of first flat tubes 31 . Specifically, each of the plurality of first flat tubes 31 has a plurality of refrigerant channels (not shown) arranged substantially parallel to each other.

Each of the plurality of second flat tubes 32 extends along the first direction D1 and is lined up along the second direction D2. A refrigerant flows through the plurality of second flat tubes 32 . Specifically, each of the plurality of second flat tubes 32 has a plurality of refrigerant flow paths (not shown) arranged substantially parallel to each other.

The first header pipe 21, the second header pipe 22, and the third header pipe 23 are arranged substantially parallel to each other.

The first header pipe 21 has a substantially cylindrical shape. The first header pipe 21 is connected to one end 31a of the plurality of first flat pipes 31 in the first direction D1. The first header pipe 21 extends along the second direction D2. A refrigerant flows through the first header pipe 21 . The first header pipe 21 does not have a refrigerant inflow portion into which the refrigerant flows from outside the first heat exchange unit 9 and a refrigerant outflow portion through which the refrigerant flows out to the outside of the first heat exchange unit 9 .

The second header pipe 22 has a substantially cylindrical shape. The second header pipe 22 is connected to the other end 31b of the plurality of first flat tubes 31 in the first direction D1 and to one end 32a of the plurality of second flat tubes 32 in the first direction D1. The second header pipe 22 extends along the second direction D2. A refrigerant flows through the second header pipe 22 .

The second header pipe 22 includes at least one refrigerant inlet 25 and at least one refrigerant outlet 27 .

In the first embodiment, the second header pipe 22 includes a plurality of refrigerant inlets 25 (specifically, two refrigerant inlets 25). The refrigerant inflow portion 25 has a substantially cylindrical shape. A refrigerant flows into the refrigerant inflow portion 25 from outside the first heat exchange unit 9 . Further, the second header pipe 22 includes a plurality of refrigerant outflow portions 27 (specifically, two refrigerant outflow portions 27). The refrigerant outlet portion 27 has a substantially cylindrical shape. The refrigerant flows out from the refrigerant outflow portion 27 to the outside of the first heat exchange unit 9 . In the first embodiment, the number of refrigerant inlets 25 and the number of refrigerant outlets 27 are the same. Furthermore, the refrigerant inflow portions 25 and the refrigerant outflow portions 27 are arranged alternately.

The third header pipe 23 has a substantially cylindrical shape. The third header pipe 23 is connected to the other end 32b of the plurality of second flat pipes 32 in the first direction D1. The third header pipe 23 extends along the second direction D2. A refrigerant flows through the third header pipe 23 . The third header pipe 23 does not have a refrigerant inflow portion into which the refrigerant flows from outside the first heat exchange unit 9 and a refrigerant outflow portion through which the refrigerant flows out to the outside of the first heat exchange unit 9 .

As described above with reference to FIG. 3, according to the first embodiment, one heat exchange section 31X is configured by the first header pipe 21, the plurality of first flat pipes 31, and the second header pipes 22. Ru. In addition, the third header pipe 23, the plurality of second flat pipes 32, and the second header pipe 22 constitute one heat exchange section 32X. Therefore, compared to the case where the heat exchange unit has one heat exchange section, the first heat exchange unit 9 can increase the amount of heat exchange. In other words, the heat exchanger 7 can increase the amount of heat exchange. The heat exchange amount is the total amount of heat exchanged per unit time. Furthermore, in the first embodiment, by arranging both the refrigerant inflow part 25 and the refrigerant outflow part 27 in the second header pipe 22, the refrigerant inflow part 25 and the refrigerant outflow part are connected to the heat exchange part 31X and the heat exchange part 32X. It is shared with 27. Therefore, the refrigerant piping in the heat exchanger 7 can be simplified compared to the case where two parallel flow type heat exchangers are provided.

That is, according to the first embodiment, the heat exchanger 7 can simplify the refrigerant piping while increasing the amount of heat exchange.

Further, according to the first embodiment, both the refrigerant inlet 25 and the refrigerant outlet 27 are arranged in the second header pipe 22 . Therefore, the temperature distribution of the first heat exchange unit 9 can be more easily made uniform than when the refrigerant inlet and the refrigerant outlet are arranged in the first header pipe 21 (that is, at the end of the heat exchanger). Specifically, during heating operation, the refrigerant changes from a gas to a two-phase state, and further from a two-phase state to a liquid. In this case, the temperature of the gaseous refrigerant is high, and the temperature of the liquid refrigerant is relatively low. Therefore, when the refrigerant inlet is disposed at the end of the heat exchanger, the temperature of the flat tube near the refrigerant inlet becomes high, and the temperature of the flat tube in the center of the heat exchanger becomes relatively low. As a result, if there is a refrigerant inlet at the end of the heat exchanger, the refrigerant exchanges heat with the high temperature only at the end of the heat exchanger, which can result in uneven temperature distribution in the heat exchanger. In contrast, in the first embodiment, the refrigerant inflow section 25 is arranged in the second header pipe 22 located in the center of the first heat exchange unit 9, so that the temperature distribution of the first heat exchange unit 9 is uniform. easy to change.

Furthermore, generally speaking, when the shape of the indoor air passage is taken into account, the wind speed may differ between the ends and the center of the heat exchanger. Therefore, in the first embodiment, the amount of heat exchange can be increased by arranging the refrigerant inflow part 25 in the second header pipe 22 located in the center of the first heat exchange unit 9.

Further, according to the first embodiment, by flowing the refrigerant from the central part of the first heat exchange unit 9 (that is, the second header pipe 22) to the first header pipe 21 and the third header pipe 23, the refrigerant inflow section and Compared to the case where the refrigerant outflow part is arranged at the first header pipe 21 (that is, the end of the heat exchanger), pressure loss can be lowered. For example, in the first embodiment, the pressure loss can be reduced to the same extent as when the number of flat tubes through which the refrigerant flows at one time is doubled.

Here, "pressure loss" refers to a phenomenon in which the pressure of the refrigerant decreases due to flow path resistance when the refrigerant flows. The higher the flow rate or the narrower the flow path, the greater the pressure loss.

Further, according to the first embodiment, as shown in FIG. 2, the heat exchanger 7 (the first heat exchange unit 9 and the second heat exchange unit 11) is arranged between the fan unit 5 and the air outlet 13. Ru. That is, the heat exchanger 7 is arranged on the side of the air outlet 13 with respect to the fan unit 5. Therefore, in the first embodiment, the air sent out from the heat exchanger 7 is not agitated by the fan unit 5, unlike the case where the heat exchanger is disposed on the side of the suction port 10 with respect to the fan unit. As a result, the temperature of the air passed through the heat exchanger 7 and blown out from the outlet 13 becomes close to the temperature distribution of the heat exchanger 7. In other words, the temperature distribution of the heat exchanger 7 becomes close to the temperature distribution of the air outlet 13. In addition, by arranging the refrigerant inflow portion 25 in the second header pipe 22 located in the center of the first heat exchange unit 9, the temperature distribution of the first heat exchange unit 9 is made uniform. As a result, air with a uniform temperature distribution is sent out from the outlet 13, improving user comfort.

Further, in the first embodiment, the first direction D1 in which the first flat tube 31 and the second flat tube 32 extend is substantially parallel to the horizontal direction. That is, the first flat tube 31 and the second flat tube 32 extend in the horizontal direction. Therefore, the first heat exchange unit 9 functions as a side flow type parallel flow heat exchanger.

Note that the direction VD1 in FIG. 2 is perpendicular to the central axis AX1 of the first header pipe 21, the central axis AX2 of the second header pipe 22, and the central axis AX3 of the third header pipe 23. Further, the direction VD2 in FIG. 2 is parallel to the central axis AX1, the central axis AX2, and the central axis AX3.

Continuing to refer to FIG. 3, the first heat exchange unit 9 will be described. The first heat exchange unit 9 may further include a plurality of first corrugated fins 41 and a plurality of second corrugated fins 42. Each of the plurality of first corrugated fins 41 is arranged between the first flat tubes 31 that are adjacent to each other in the second direction D2. Each of the plurality of first corrugated fins 41 has a wave-shaped shape.

Each of the plurality of second corrugated fins 42 is arranged between the second flat tubes 32 that are adjacent to each other in the second direction D2. Each of the plurality of second corrugated fins 42 has a wavy shape.

Next, the second heat exchange unit 11 will be explained with reference to FIG. FIG. 4 is a diagram showing the second heat exchange unit 11. The second heat exchange unit 11 exchanges thermal energy between air and refrigerant. In FIG. 4, the second heat exchange unit 11 is viewed from the back.

As shown in FIG. 4, the second heat exchange unit 11 includes a first heat exchange section 11A that performs heat exchange, and a second heat exchange section 11B that performs heat exchange. Each of the first heat exchange section 11A and the second heat exchange section 11B is a fin-and-tube type heat exchanger.

The first heat exchange section 11A includes a plurality of first fins 51 having a substantially flat plate shape and a first tube 61 having a substantially cylindrical shape.

Each of the plurality of first fins 51 extends along the third direction D3 and is lined up along the fourth direction D4. The fourth direction D4 is orthogonal to the third direction D3. The third direction D3 and the first direction D1 (FIG. 3) are substantially perpendicular to each other. The third direction D3 and the second direction D2 (FIG. 3) are substantially parallel to each other. The fourth direction D4 and the first direction D1 (FIG. 3) are substantially parallel to each other. Therefore, the fourth direction D4 is substantially parallel to the horizontal direction.

The first tube 61 penetrates the plurality of first fins 51 in the fourth direction D4 and meanderes. A refrigerant flows through the first pipe 61 . The first pipe 61 includes a first refrigerant inlet A1 and a first refrigerant outlet B1. A refrigerant flows into the first refrigerant inflow section A1 from outside the first heat exchange section 11A. From the first refrigerant outflow section B1, the refrigerant flows out to the outside of the first heat exchange section 11A.

The first heat exchange section 11A and the second heat exchange section 11B are lined up along the fourth direction D4 and face each other in the fourth direction D4.

The second heat exchange section 11B includes a plurality of second fins 52 having a substantially flat plate shape and a second pipe 62 having a substantially cylindrical shape. Each of the plurality of second fins 52 extends along the third direction D3 and is lined up along the fourth direction D4.

The second pipe 62 penetrates the plurality of second fins 52 in the fourth direction D4 and meanderes. A refrigerant flows through the second pipe 62 . The second pipe 62 includes a second refrigerant inlet A2 and a second refrigerant outlet B2. A refrigerant flows into the second refrigerant inflow section A2 from outside the second heat exchange section 11B. From the second refrigerant outflow section B2, the refrigerant flows out to the outside of the second heat exchange section 11B.

Next, with reference to FIG. 5, piping in the heat exchanger 7 will be explained. FIG. 5 is a diagram schematically showing piping in the heat exchanger 7. In addition, in FIG. 5, the first header pipe 21, the third header pipe 23, the first flat pipe 31, and the second flat pipe 32 are omitted for simplification of the drawing.

As shown in FIG. 5, the heat exchanger 7 further includes a confluence section 71, a branch section 72, a tube 73, a tube 74, a tube 75, a tube 76, and a tube 77.

The pipe 77 is connected to the flow dividing section 72 . The flow dividing section 72 divides the flow path of the pipe 77 and connects the pipe 77 to the pipes 78 and 79. The pipe 78 is connected to one of the two refrigerant inflow parts 25 of the second header pipe 22 , and the pipe 79 is connected to the other refrigerant inflow part 25 . One of the two refrigerant outflow parts 27 is connected to the pipe 76 , and the other refrigerant outflow part 27 is connected to the pipe 75 .

Pipe 75 and pipe 76 connect to merging section 71 . The confluence section 71 merges the flow paths of the tubes 75 and 76 and connects the tubes 75 and 76 to the tube 74 . The pipe 74 is connected to the second refrigerant inflow section A2 of the second heat exchange section 11B. The second refrigerant outlet B2 is connected to one end of the pipe 73. The other end of the pipe 73 is connected to the first refrigerant inflow section A1 of the first heat exchange section 11A. As a result, the second refrigerant outflow portion B2 and the first refrigerant inflow portion A1 are connected.

Continuing with reference to FIG. 5, the flow of refrigerant during heating operation will be described. As shown in FIG. 5, during heating operation, the refrigerant AR1 flows from the first heat exchange unit 9 to the second heat exchange unit 11.

Specifically, the refrigerant AR1 from the outside of the heat exchanger 7 flows into the branch part 72 from the pipe 77. Then, the refrigerant AR1 is divided by the flow dividing section 72 and flows into the refrigerant inflow section 25 of the first heat exchange unit 9. Then, the refrigerant AR1 flows out from the refrigerant outflow section 27 via the heat exchange section 31X and the heat exchange section 32X. Furthermore, the refrigerant AR1 is merged by the merge section 71 and flows into the second refrigerant inflow section A2 of the second heat exchange section 11B. Furthermore, the refrigerant AR1 flows out of the second refrigerant outlet B2 via the second pipe 62, and flows into the first refrigerant inlet A1 of the first heat exchange section 11A. Furthermore, the refrigerant AR1 flows out from the first refrigerant outlet B1 via the first pipe 61.

Continuing with reference to FIG. 5, the flow of refrigerant during cooling operation will be described. As shown in FIG. 5, during cooling operation, the refrigerant AR2 flows from the second heat exchange unit 11 to the first heat exchange unit 9.

Specifically, the refrigerant AR2 from the outside of the heat exchanger 7 flows into the first refrigerant outlet B1 of the first heat exchange section 11A. Therefore, the first refrigerant outflow section B1 functions as an "inflow section". Then, the refrigerant AR2 flows out from the first refrigerant inflow portion A1 via the first pipe 61. Therefore, the first refrigerant inlet A1 functions as an "outlet". Furthermore, the refrigerant AR2 flows into the second refrigerant outlet B2 of the second heat exchange section 11B via the pipe 73. Therefore, the second refrigerant outflow section B2 functions as an "inflow section". Furthermore, the refrigerant AR2 flows out from the second refrigerant inflow portion A2 via the second pipe 62. Therefore, the second refrigerant inlet A2 functions as an "outlet".

Then, the refrigerant AR2 is separated by the merging section 71 and flows into the refrigerant outlet section 27 of the first heat exchange unit 9. Therefore, the confluence section 71 functions as a "separation section" and the refrigerant outflow section 27 functions as an "inflow section." Furthermore, the refrigerant AR2 flows out from the refrigerant inflow section 25 via the heat exchange section 31X and the heat exchange section 32X. Therefore, the refrigerant inlet 25 functions as an "outlet". Furthermore, the refrigerant AR2 is combined by the flow dividing section 72 and flows out from the pipe 77. Therefore, the branching section 72 functions as a "merging section".

Next, the internal structure of the first heat exchange unit 9 will be explained with reference to FIG. FIG. 6 is a diagram schematically showing the internal structure of the first heat exchange unit 9. As shown in FIG. In FIG. 6, the flow of refrigerant in the first heat exchange unit 9 during heating operation is shown by "arrows". Moreover, for the sake of simplification of the drawing, the plurality of first flat tubes 31 are expressed as "block BL11 and block BL21". Similarly, the plurality of second flat tubes 32 are expressed as "block BL12 and block BL22".

As shown in FIG. 6, the first header pipe 21 of the first heat exchange unit 9 includes at least one partition plate 211. As shown in FIG. The partition plate 211 partitions the internal space of the first header pipe 21 and divides the internal space of the first header pipe 21 into two in the second direction D2.

The second header pipe 22 includes a plurality of partition plates 220. In the first embodiment, the second header pipe 22 includes three partition plates 220. The three partition plates 220 partition the internal space of the second header pipe 22 and divide the internal space of the second header pipe 22 into four in the second direction D2.

The third header pipe 23 includes at least one partition plate 231 . The partition plate 231 partitions the internal space of the third header pipe 23 and divides the internal space of the third header pipe 23 into two in the second direction D2.

The refrigerant flowing from the refrigerant inlet 25 of the second header pipe 22 flows through the block BL11 of the heat exchange section 31X, turns at the first header pipe 21, and flows into the block BL21. The refrigerant then flows through the block BL21 and flows out from the refrigerant outflow portion 27. In addition, the refrigerant flowing from the refrigerant inflow section 25 flows through the block BL12 of the heat exchange section 32X, turns at the third header pipe 23, and flows into the block BL22. The refrigerant then flows through the block BL22 and flows out from the refrigerant outlet 27.

Note that during cooling operation, the refrigerant flows in the opposite direction to that during heating operation.

Next, with reference to FIG. 7, the heat exchanger 7 and fan unit 5 will be described in detail. FIG. 7 is a top view showing the heat exchanger 7 and the fan unit 5. In FIG. 7, the heat exchanger 7 and the fan unit 5 are viewed from above. In this specification, a top view indicates viewing the object from direction VD2 in FIG. 2 .

As shown in FIG. 7, in the first heat exchange unit 9, the first header pipe 21, the second header pipe 22, and the third header pipe 23 are arranged in a straight line. One end portion 31c of the first flat tube 31 in the first direction D1 protrudes into the internal space of the first header tube 21. The other end 31 d of the first flat tube 31 in the first direction D1 protrudes into the internal space of the second header tube 22 .

One end 32c of the second flat tube 32 in the first direction D1 protrudes into the internal space of the second header tube 22. The other end 32d of the second flat tube 32 in the first direction D1 protrudes into the internal space of the third header tube 23. A base end 25 a of the refrigerant inlet 25 and a base end 27 a of the refrigerant outlet 27 protrude into the internal space of the second header pipe 22 .

The number of heat exchange sections (first heat exchange section 11A and second heat exchange section 11B) of second heat exchange unit 11 is equal to the number of heat exchange sections (heat exchange section 31X and heat exchange section 32X) of first heat exchange unit 9. is the same as the number of The first heat exchange section 11A faces the heat exchange section 31X of the first heat exchange unit 9. Therefore, the first heat exchange section 11A faces the plurality of first flat tubes 31 connected to the first header tube 21 and the second header tube 22. Further, the second heat exchange section 11B faces the heat exchange section 32X of the first heat exchange unit 9. Therefore, the second heat exchange section 11B faces the plurality of second flat pipes 32 connected to the second header pipe 22 and the third header pipe 23.

Furthermore, in the second heat exchange unit 11, the first refrigerant inlet A1 and the first refrigerant outlet B1 are oriented in the direction from the first header pipe 21 to the second header pipe 22. That is, the first refrigerant inlet A1 and the first refrigerant outlet B1 are arranged on the second header pipe 22 side with respect to the first header pipe 21. In addition, the second refrigerant inlet A2 and the second refrigerant outlet B2 are oriented in the direction from the third header pipe 23 to the second header pipe 22. That is, the second refrigerant inlet A2 and the second refrigerant outlet B2 are arranged on the second header pipe 22 side with respect to the third header pipe 23.

That is, in a top view, the first refrigerant inflow part A1 and the first refrigerant outflow part B1, and the second refrigerant inflow part A2 and the second refrigerant outflow part B2 face each other. In addition, the first refrigerant inlet A1 and the first refrigerant outlet B1, and the second refrigerant inlet A2 and second refrigerant outlet B2 are located near the refrigerant inlet 25 and the refrigerant outlet 27.

Therefore, according to the first embodiment, compared to the case where the first refrigerant inflow part A1 and the first refrigerant outflow part B1 are located on the first header pipe 21 side, or the second refrigerant inflow part A2 and Compared to the case where the second refrigerant outflow portion B2 is located on the third header pipe 23 side, the piping in the heat exchanger 7 can be shortened and the piping can be simplified.

Furthermore, in the first embodiment, the inner diameter of the refrigerant inflow section 25 that functions as an "outflow section" of the refrigerant during cooling operation in the first heat exchange unit 9 is equal to the inner diameter of the first pipe 61 of the first heat exchange section 11A and the second pipe 61 of the first heat exchange section 11A. It is larger than each of the inner diameters of the second tubes 62 of the heat exchange section 11B. Therefore, the pressure loss of the refrigerant during cooling operation can be reduced.

Note that, in general, at the "outflow section" of the refrigerant during cooling operation, the refrigerant is in a gaseous state, so the flow rate of the refrigerant is high. The higher the flow rate or the narrower the flow path, the greater the pressure loss. As a result, the pressure loss of the refrigerant increases at the "outflow section" during cooling operation. Therefore, in the first embodiment, the pressure loss of the refrigerant is reduced by increasing the inner diameter of the refrigerant inflow section 25 that functions as the "outflow section" of the refrigerant during cooling operation. Note that as long as the refrigerant flows through the refrigerant inlet 25, the inner diameter of the refrigerant inlet 25 is not particularly limited.

Furthermore, in the first embodiment, in the first heat exchange unit 9, the inner diameter of the second header pipe 22 is larger than each of the inner diameters of the first header pipe 21 and the third header pipe 23. Therefore, according to the first embodiment, it is possible to increase the inner diameter of the refrigerant inflow portion 25 that functions as a refrigerant “outflow portion” during cooling operation. As a result, the pressure loss of the refrigerant during cooling operation can be reduced. In addition, in the second header pipe 22, a sufficient area for connecting both the first flat pipe 31 and the second flat pipe 32 can be easily secured. Note that the inner diameter of the second header tube 22 is not particularly limited as long as both the first flat tube 31 and the second flat tube 32 can be connected to the second header tube 22.

Continuing to refer to FIG. 7, the fan unit 5 will be described. As shown in FIG. 7, the fan unit 5 includes a fan 5A and a fan 5B. Each of the fan 5A and the fan 5B is, for example, a cross flow fan. The number of fans (fans 5A and fans 5B) of the fan unit 5 is the same as the number of heat exchange sections (first heat exchange section 11A and second heat exchange section 11B) of the second heat exchange unit 11.

The fan 5A faces the first heat exchange section 11A. The fan 5A sucks air W1 and sends the sucked air W1 toward the first heat exchange section 11A. As a result, the air W2 is sent out toward the air outlet 13 through the first heat exchange section 11A and the heat exchange section 31X.

Fan 5B faces second heat exchange section 11B. The fan 5B sucks in air W1 and sends out the sucked air W1 toward the second heat exchange section 11B. As a result, the air W2 is sent out toward the air outlet 13 through the second heat exchange section 11B and the heat exchange section 32X.

(Embodiment 2)
A heat exchanger 7 according to Embodiment 2 of the present invention will be described with reference to FIGS. 8 and 9. The second header pipe 22 of the heat exchanger 7 according to the second embodiment is arranged on the second heat exchange unit 11 side with respect to the first header pipe 21 and the third header pipe 23 in a top view. Embodiment 2 is mainly different from Embodiment 1. Hereinafter, the differences between the second embodiment and the first embodiment will be mainly explained.

First, with reference to FIG. 8, a heat exchanger 7 according to a second embodiment will be described. FIG. 8 is a top view showing the heat exchanger 7 and fan unit 5 according to the second embodiment. In FIG. 8, the heat exchanger 7 and the fan unit 5 are viewed from above.

As shown in FIG. 8, in the heat exchanger 7, the central axis AX2 of the second header pipe 22 of the first heat exchange unit 9A is the same as the central axis AX1 of the first header pipe 21 and the central axis AX3 of the third header pipe 23. In contrast, the first header pipe 21, the second header pipe 22, and the third header pipe 23 are arranged so as to be located on the second heat exchange unit 11 side.

Therefore, according to the second embodiment, even if the outer diameter of the second header pipe 22 is larger than each of the outer diameters of the first header pipe 21 and the third header pipe 23, the second header pipe 22 can be suppressed from protruding downstream of the air flow with respect to the first header pipe 21 and the third header pipe 23. In other words, the second header pipe 22 can be prevented from protruding further downstream of the air flow than the line LN. Line LN is a line segment connecting the most downstream end of the first header pipe 21 and the most downstream end of the third header pipe 23.

Specifically, the central axis AX2 of the second header pipe 22 is connected to the first heat exchange section 11A with respect to the central axis AX1 of the first header pipe 21 and the central axis AX3 of the third header pipe 23. The first header pipe 21, the second header pipe 22, and the third header pipe 23 are arranged so as to be located on the space SP side between the first header pipe 21 and the portion 11B.

Next, the inside of the second header pipe 22 will be explained with reference to FIG. FIG. 9 is a sectional view showing the inside of the second header pipe 22. As shown in FIG. In FIG. 9 , in order to facilitate understanding, the first flat tube 31 and the second flat tube 32 are shown to have a larger inclination than the first flat tube 31 and the second flat tube 32 in FIG. 8 .

As shown in FIG. 9, the first flat tube 31 has a refrigerant flow path 311, a refrigerant flow path 312, a refrigerant flow path 313, a refrigerant flow path 314, and a refrigerant flow path 315. The second flat tube 32 has a refrigerant flow path 321 , a refrigerant flow path 322 , a refrigerant flow path 323 , a refrigerant flow path 324 , and a refrigerant flow path 325 .

The refrigerant CM that has flowed into the second header pipe 22 from the refrigerant inflow portion 25 flows into the refrigerant flow path 311 to refrigerant flow path 315 of the first flat tube 31 . Similarly, the refrigerant CM flows into the refrigerant passages 321 to 325 of the second flat tube 32.

Here, as described with reference to FIG. 8, the central axis AX2 of the second header pipe 22 is located on the second heat exchange unit 11 side with respect to the central axis AX1 and the central axis AX3. Therefore, each of the end surface 316 of the first flat tube 31 and the end surface 326 of the second flat tube 32 is inclined with respect to the inflow direction of the refrigerant CM so as to widen toward the refrigerant inflow portion 25.

As a result, according to the second embodiment, the refrigerant flow path 321 The refrigerant CM can effectively flow into the refrigerant flow path 325 and the refrigerant flow path 321 to the refrigerant flow path 325.

(Embodiment 3)
With reference to FIG. 10, a heat exchanger 7 according to Embodiment 3 of the present invention will be described. Embodiment 3 differs from Embodiment 1 mainly in that the number of refrigerant inlets 25 and the number of refrigerant outlets 27 of second header pipe 22 of heat exchanger 7 according to Embodiment 3 are different. Hereinafter, the differences between the third embodiment and the first embodiment will be mainly explained.

FIG. 10 is a diagram schematically showing the internal structure of the first heat exchange unit 9B of the heat exchanger 7 according to the third embodiment. In FIG. 10, the flow of refrigerant in the first heat exchange unit 9B during heating operation is shown by "arrows". Further, for the sake of simplification of the drawing, the plurality of first flat tubes 31 are expressed as "block BL11a, block BL21a, block BL11b, and block BL21b". Similarly, the plurality of second flat tubes 32 are expressed as "block BL12a, block BL22a, block BL12b, and block BL22b."

As shown in FIG. 10, in the first heat exchange unit 9B of the heat exchanger 7, the number of refrigerant inflow portions 25 and the number of refrigerant outflow portions 27 of the second header pipe 22 are different. Therefore, compared to the case where the number of refrigerant inflow parts 25 and the number of refrigerant outflow parts 27 are the same, the number of pipes connected to the refrigerant inflow part 25 or the number of pipes connected to the refrigerant outflow part 27 is reduced. It can be reduced. As a result, the piping can be further simplified.

In the third embodiment, the number of refrigerant outflow sections 27 is smaller than the number of refrigerant inflow sections 25. Specifically, the second header pipe 22 has two refrigerant inlets 25 and one refrigerant outlet 27. Therefore, the number of pipes connected to the refrigerant outlet 27 can be reduced. For example, in FIG. 5, it is sufficient to provide either one of the pipe 75 and the pipe 76, and furthermore, the merging portion 71 does not need to be provided. Note that when the number of refrigerant inlets 25 is smaller than the number of refrigerant outlets 27, the number of pipes connected to the refrigerant inlets 25 can be reduced.

Further, in the third embodiment, since the number of refrigerant inflow parts 25 and the number of refrigerant outflow parts 27 of the second header pipe 22 are different, when the number of refrigerant inflow parts 25 and the number of refrigerant outflow parts 27 are the same, Compared to this, the distance in the second direction D2 between the refrigerant inlet 25 and the refrigerant outlet 27 is larger. As a result, heat exchange loss can be suppressed and heat exchange by the first heat exchange unit 9 can be effectively performed.

Specifically, during heating operation, the refrigerant in the refrigerant inlet portion 25 of the second header pipe 22 is in a superheated state. On the other hand, during heating operation, the refrigerant is in a gas-liquid two-phase state at the refrigerant outlet portion 27 of the second header pipe 22. Therefore, by increasing the distance in the second direction D2 between the refrigerant inlet 25 and the refrigerant outlet 27, heat exchange between the refrigerant in the refrigerant inlet 25 and the refrigerant in the refrigerant outlet 27 can be suppressed. The heat exchange between the refrigerant in the refrigerant inflow section 25 and the refrigerant in the refrigerant outflow section 27 is not a heat exchange that should be performed by the first heat exchange unit 9, but is a heat exchange loss for the first heat exchange unit 9. In the third embodiment, heat exchange by the first heat exchange unit 9 can be effectively performed by suppressing heat exchange loss.

Continuing to refer to FIG. 10, the flow of the refrigerant will be described. As shown in FIG. 10, the second header pipe 22 includes a plurality of partition plates 220. In the first embodiment, the second header pipe 22 includes two partition plates 220. The two partition plates 220 partition the internal space of the second header pipe 22 and divide the internal space of the second header pipe 22 into three in the second direction D2.

The refrigerant flowing from one of the two refrigerant inflow parts 25 flows through the block BL11a of the heat exchange part 31X, turns at the first header pipe 21, and flows into the block BL21a. The refrigerant then flows through the block BL21a and flows out from one refrigerant outlet 27. On the other hand, the refrigerant flowing from the other refrigerant inflow section 25 flows through the block BL11b of the heat exchange section 31X, turns at the first header pipe 21, and flows into the block BL21b. Then, the refrigerant flows through the block BL21b and flows out from one refrigerant outlet 27. Therefore, the refrigerants flowing from the two refrigerant inlets 25 and flowing through the heat exchanger 31X share one refrigerant outlet 27.

Similarly, the refrigerant flowing from one refrigerant inflow B25 of the two refrigerant inflow sections 25 flows through the block BL12a of the heat exchange section 32X, turns at the third header pipe 23, and flows into the block BL22a. The refrigerant then flows through the block BL22a and flows out from one refrigerant outlet 27. On the other hand, the refrigerant flowing from the other refrigerant inlet 25 flows through the block BL12b of the heat exchanger 32X, turns at the third header pipe 23, and flows into the block BL22b. Then, the refrigerant flows through the block BL22b and flows out from one refrigerant outlet 27. Therefore, the refrigerants flowing from the two refrigerant inlets 25 and flowing through the heat exchanger 32X share one refrigerant outlet 27.

As described above with reference to FIG. 10, in the first heat exchange unit 9B, the refrigerant flowing from the two refrigerant inlets 25 flows into the refrigerant outlet 27 located between the two refrigerant inlets 25. are shared.

Note that during cooling operation, the refrigerant flows in the opposite direction to that during heating operation.

(Embodiment 4)
With reference to FIG. 11, a heat exchanger 7 according to Embodiment 4 of the present invention will be described. Embodiment 4 is different from Embodiment 3 in that the first heat exchange unit 9C of the heat exchanger 7 according to Embodiment 4 includes a first plate member 81 and a second plate member 82 extending in the first direction D1. Mainly different. Hereinafter, the differences between the fourth embodiment and the third embodiment will be mainly explained.

FIG. 11 is a diagram schematically showing the first heat exchange unit 9C of the heat exchanger 7 according to the fourth embodiment. In FIG. 11, the first heat exchange unit 9C is viewed from the back. Furthermore, for the sake of simplification of the drawing, the first corrugated fins 41 and the second corrugated fins 42 are omitted.

As shown in FIG. 11, the first heat exchange unit 9C of the heat exchanger 7 further includes a first plate member 81 and a second plate member 82. The first plate member 81 extends from the second header pipe 22 to the first header pipe 21 along the first direction D1. For example, instead of the first flat tube 31 close to the refrigerant outlet 27, the first plate member 81 is arranged. Therefore, the first plate member 81 is arranged between the two first flat tubes 31. The first plate member 81 does not have a refrigerant flow path. The second plate member 82 extends from the second header pipe 22 to the third header pipe 23 along the first direction D1. For example, instead of the second flat tube 32 close to the refrigerant outlet 27, the second plate member 82 is arranged. Therefore, the second plate member 82 is arranged between the two second flat tubes 32. The second plate member 82 does not have a refrigerant flow path.

According to the fourth embodiment, by providing the first plate member 81, the interval d1 between the two first flat tubes 31 sandwiching the first plate member 81 can be made larger than the pitch p1 of the other first flat tubes 31. can do. In addition, by providing the second plate member 82, the interval d2 between the two second flat tubes 32 sandwiching the second plate member 82 can be made larger than the pitch p2 of the other second flat tubes 32. can.

Therefore, inside the second header pipe 22, the base end 27a (FIG. 7) of the refrigerant outlet 27 is connected to the end 31d (FIG. 7) of the first flat tube 31 and the end 32c (FIG. 7) of the second flat tube 32. (Fig. 7) can be easily suppressed. As a result, the outer diameter and inner diameter of the refrigerant outlet portion 27 can be easily increased.

Further, according to the fourth embodiment, by providing the first plate-like member 81, during cooling operation, among the plurality of first flat tubes 31, the side closer to the refrigerant outlet portion 27 that functions as an “inflow portion” It is possible to prevent the flow rate of the refrigerant flowing into the first flat tube 31 from becoming non-uniform between the first flat tube 31 and the first flat tube 31 on the far side. Similarly, by providing the second plate member 82, during cooling operation, the second flat tube 32 on the side closer to the refrigerant outlet 27 functioning as an "inflow section" among the plurality of second flat tubes 32 It is possible to prevent the flow rate of the refrigerant flowing into the second flat tube 32 from becoming non-uniform with the second flat tube 32 on the far side.

Note that, for example, if the first flat tube 31 (hereinafter referred to as "first flat tube 31Q") is arranged at the position of the first plate member 81, the first flat tube 31Q is located at the refrigerant outlet. Close to 27. Therefore, during cooling operation, there is a possibility that a larger amount of refrigerant will flow into the first flat tube 31Q from the refrigerant outflow section 27 that functions as an "inflow section" than the refrigerant that flows into the other first flat tubes 31. There is.

Specifically, the first plate member 81, the second plate member 82, and the refrigerant outlet portion 27 of the second header pipe 22 are arranged as follows. That is, the refrigerant outflow portion 27 is close to the end 81a of the first plate member 81 and the end 82a of the second plate member 82. The end 81a of the first plate member 81 is the end on the second header pipe 22 side of both ends of the first plate member 81 in the first direction D1. The end 82a of the second plate member 82 is the end on the second header pipe 22 side of both ends of the second plate member 82 in the first direction D1.

More specifically, the refrigerant outflow portion 27, the first plate member 81, and the second plate member 82 are arranged in a straight line when viewed from the rear. That is, the position of the refrigerant outlet portion 27 in the second direction D2 is approximately equal to the position of the first plate member 81 in the second direction D2, and is approximately equal to the position of the second plate member 82 in the second direction D2. . For example, the refrigerant outlet 27, the end 81a of the first plate member 81, and the end 82a of the second plate member 82 are arranged on the same circumference in the second header pipe 22.

Here, as long as the first plate member 81 is arranged in the heat exchange section 31X, the position and number of the first plate member 81 are not particularly limited. Further, as long as the second plate member 82 is disposed in the heat exchange section 32X, the position and number of the second plate member 82 are not particularly limited.

For example, by arranging the two first plate members 81 and the two second plate members 82 at positions different from those shown in FIG. It may be close to the end 81a of the first plate-like member 81 and the end 82a of the second plate-like member 82. In this case, the outer diameter and inner diameter of the refrigerant inflow portion 25 can be easily increased. Also, during heating operation, among the plurality of first flat tubes 31, the first flat tube 31 on the side closer to the refrigerant inflow part 25 and the first flat tube 31 on the far side are used to flow into the first flat tube 31. It is possible to prevent the flow rate of the refrigerant from becoming non-uniform. Similarly, during heating operation, among the plurality of second flat tubes 32, the second flat tube 32 on the side closer to the refrigerant inflow part 25 and the second flat tube 32 on the far side are used to flow into the second flat tube 32. It is possible to prevent the flow rate of the refrigerant from becoming non-uniform.

That is, at least one of the refrigerant inlet 25 and the refrigerant outlet 27 of the second header pipe 22 is close to the end 81a of the first plate member 81 and the end 82a of the second plate member 82. That's fine.

Further, according to the first embodiment, by providing the first plate member 81 and the second plate member 82, the strength of the first heat exchange unit 9C can be improved.

(Embodiment 5)
With reference to FIG. 12, a heat exchanger 7 according to Embodiment 5 of the present invention will be described. Embodiment 5 differs from Embodiment 3 mainly in that the partition plate 220 of the first heat exchange unit 9D of the heat exchanger 7 according to Embodiment 5 is inclined. Hereinafter, the differences between the fifth embodiment and the third embodiment will be mainly explained.

FIG. 12 is a diagram schematically showing the internal structure of the first heat exchange unit 9D of the heat exchanger 7 according to the fifth embodiment. In FIG. 12, the flow of refrigerant in the first heat exchange unit 9D during heating operation is shown by "arrows".

As shown in FIG. 12, in the first heat exchange unit 9D of the heat exchanger 7, the second header pipe 22 includes at least two partition plates 220 that partition the internal space of the second header pipe 22. At least two partition plates 220 are inclined away from each other from the third header pipe 23 side toward the first header pipe 21 side.

Therefore, the number N of first flat tubes 31 included in block BL21a and block BL21b of heat exchange section 31X is different from the number M of second flat tubes 32 included in block BL22a and block BL22b of heat exchange section 32X. can be set. In other words, the number N of first flat tubes 31 through which refrigerant flows from the first header pipe 21 toward the refrigerant outlet 27 is the number M of the second flat tubes 32 through which refrigerant flows from the third header tube 23 toward the refrigerant outlet 27. It can be made different.

Therefore, even if the flow path resistance of the air passing through the heat exchange section 31X and the flow path resistance of the air passing through the heat exchange section 32X are different, that is, the air flow between the heat exchange section 31X and the heat exchange section 32X is Even if the flow path resistance is asymmetric, the number N of first flat tubes 31 and the number M of second flat tubes 32 can be set according to the flow path resistance of air. As a result, the heat exchange efficiency in the first heat exchange unit 9D can be improved.

For example, in the area Q1 of the heat exchanger 31X, air with a strong airflow passes through, so the flow resistance is large, and in the area Q2 of the heat exchanger 32X, air with a weak airflow passes, so the flow resistance is small. The number N of flat tubes 31 is made larger than the number M of second flat tubes 32. As a result, the heat exchange efficiency in the first heat exchange unit 9D can be improved.

In the fifth embodiment, at least two partition plates 220 are inclined away from each other from the first header pipe 21 side to the third header pipe 23 side, so that the first flat pipe 31 The number N is greater than the number M of the second flat tubes 32. However, at least two partition plates 220 may be inclined away from each other from the first header pipe 21 side toward the third header pipe 23 side. In this case, the number M of second flat tubes 32 is greater than the number N of first flat tubes 31.

The embodiments of the present invention have been described above with reference to the drawings. However, the present invention is not limited to the above-described embodiments, and can be implemented in various embodiments without departing from the spirit thereof (for example, (1) to (4) shown below). Moreover, various inventions can be formed by appropriately combining the plurality of components disclosed in the above embodiments. For example, some components may be deleted from all the components shown in the embodiments. Furthermore, components of different embodiments may be combined as appropriate. For ease of understanding, the drawing mainly shows each component schematically, and the thickness, length, number, spacing, etc. of each component shown in the diagram may differ from the actual one for convenience of drawing. may be different. Furthermore, the materials, shapes, dimensions, etc. of each component shown in the above embodiments are merely examples, and are not particularly limited, and various changes can be made without substantially departing from the effects of the present invention. be.

(1) In Embodiments 1 to 5 described with reference to FIGS. 1 to 12, the heat exchanger 7 has the second heat exchange unit 11, but the heat exchanger 7 has the first heat exchange unit 11. As long as the heat exchanger 7 includes any one of the units 9 to 9D, the heat exchanger 7 does not need to include the second heat exchange unit 11. In this case, the heat exchanger 7 may have, for example, one first heat exchange unit 9 or a plurality of first heat exchange units 9.

Further, the first heat exchange units 9 to 9D may be located upstream of the second heat exchange unit 11 in the air flow.

(2) In Embodiments 1 to 5 described with reference to FIGS. 1 to 12, during heating operation, the refrigerant flows from the first heat exchange units 9 to 9D to the second heat exchange unit 11 to cool the air conditioner. During operation, the refrigerant flowed from the second heat exchange unit 11 to the first heat exchange units 9-9D. However, during heating operation, the refrigerant flows from the second heat exchange unit 11 to the first heat exchange units 9 to 9D, and during cooling operation, the refrigerant flows from the first heat exchange units 9 to 9D to the second heat exchange unit. It may flow to 11.

Further, although the refrigerant inflow portion 25, the first refrigerant inflow portion A1, and the second refrigerant inflow portion A2 are “inflow portions” during heating operation, they may also be “inflow portions” during cooling operation. In addition, although the refrigerant outflow portion 27, the first refrigerant outflow portion B1, and the second refrigerant outflow portion B2 are “outflow portions” during heating operation, they may also be “outflow portions” during cooling operation. .

(3) In Embodiment 1 and Embodiment 2 described with reference to FIGS. 1 to 9, as long as the number of refrigerant inflow portions 25 and the number of refrigerant outflow portions 27 are the same, the number of refrigerant inflow portions 25 The number of refrigerant outlet portions 27 is not particularly limited. Furthermore, in the third to fifth embodiments described with reference to FIGS. 10 to 12, as long as the number of refrigerant inflow parts 25 and the number of refrigerant outflow parts 27 are different, the number of refrigerant inflow parts 25 and the number of refrigerant outflow parts 27 are different. The number of outflow portions 27 is not particularly limited. Further, plate members such as the first plate member 81 and the second plate member according to the fourth embodiment described with reference to FIG. It may be provided in the heat exchange units 9, 9A, 9B, and 9D. Furthermore, in Embodiments 1 to 4, the partition plate 220 may be tilted as in Embodiment 5 described with reference to FIG. Furthermore, in the first heat exchange unit 9A according to the second embodiment described with reference to FIG. You can also let

(4) In the first embodiment described with reference to FIG. 5, during heating operation, the refrigerant flows through the second heat exchange section 11B and then through the first heat exchange section 11A, and during cooling operation, the refrigerant flows through the first heat exchange section 11A. Although the refrigerant flows through the second heat exchange section 11B after flowing through the section 11A, there is no particular limitation on how the refrigerant flows.

For example, during heating operation or cooling operation, refrigerant can flow in parallel to the first heat exchange section 11A and the second heat exchange section 11B. In this case, the comparison is made with one second heat exchange unit (hereinafter referred to as "second heat exchange unit EX") whose size is the combined size of the first heat exchange section 11A and the second heat exchange section 11B. In the fourth direction D4 (FIG. 4) of the second heat exchange units (second heat exchange unit 11, second heat exchange unit EX), one region (first heat exchange section 11A) and the other region (second Temperature drift between the heat exchanger 11B and the heat exchanger 11B can be suppressed. Temperature drift is a phenomenon in which the temperature of the refrigerant is uneven between one region and the other region in the fourth direction D4 of the second heat exchange unit, and the refrigerant flows between one region and the other region.

In addition, in the second heat exchange unit EX, since the distance from one end to the other end in the fourth direction D4 of the second heat exchange unit EX is long, one area in the fourth direction D4 of the second heat exchange unit EX There is a possibility that temperature drift between one region and the other region will become large.

Specifically, in FIG. 4, during heating operation, the refrigerant flows into the first refrigerant inflow part A1 of the first heat exchange part 11A, and the refrigerant flows into the second refrigerant inflow part A2 of the second heat exchange part 11B. do. As a result, during heating operation, the refrigerant flows in parallel to the first heat exchange section 11A and the second heat exchange section 11B. That is, the refrigerant flows from the first refrigerant inlet A1 along the fourth direction D4 toward one end of the second heat exchange unit 11 in the fourth direction D4, and meanderingly flows from the first refrigerant outlet B1. leak. On the other hand, the refrigerant flows from the second refrigerant inlet A2 along the fourth direction D4 toward the other end of the second heat exchange unit 11 in the fourth direction D4, and meanderingly flows from the second refrigerant outlet B2. leak.

Further, in FIG. 4, during cooling operation, the refrigerant flows into the first refrigerant outlet B1 of the first heat exchange section 11A, and the refrigerant flows into the second refrigerant outlet B2 of the second heat exchange section 11B. As a result, during cooling operation, the refrigerant flows in parallel to the first heat exchange section 11A and the second heat exchange section 11B. That is, the refrigerant flows from the first refrigerant outflow portion B1 along the fourth direction D4 toward one end of the second heat exchange unit 11 in the fourth direction D4, and meanderingly flows from the first refrigerant inflow portion A1. leak. On the other hand, the refrigerant flows from the second refrigerant outflow portion B2 along the fourth direction D4 toward the other end of the second heat exchange unit 11 in the fourth direction D4, and meanderingly flows from the second refrigerant inflow portion A2. leak.

The present invention provides a heat exchanger and has industrial applicability.

7 Heat exchanger 9, 9A to 9D First heat exchange unit 11 Second heat exchange unit 11A First heat exchange section 11B Second heat exchange section 21 First header pipe 22 Second header pipe 23 Third header pipe 25 Refrigerant inflow Part 27 Refrigerant outlet 31 First flat tube 32 Second flat tube 51 First fin 52 Second fin 61 First tube 62 Second tube 81 First plate member 82 Second plate member 220 Partition plate A1 First refrigerant Inflow part A2 Second refrigerant inflow part B1 First refrigerant outflow part B2 Second refrigerant outflow part

Claims (8)

Comprising a first heat exchange unit and a second heat exchange unit that perform heat exchange,
The first heat exchange unit includes:
a plurality of first flat tubes each extending in a first direction and lined up in a second direction perpendicular to the first direction;
a plurality of second flat tubes each extending in an extension direction perpendicular to the second direction and lined up in the second direction;
a first header pipe connected to one end of the plurality of first flat tubes in the first direction and extending in the second direction;
a second header pipe connected to the other end of the plurality of first flat tubes in the first direction and one end of the plurality of second flat tubes in the extension direction and extending in the second direction;
a third header pipe connected to the other end of the plurality of second flat tubes in the extension direction and extending in the second direction;
The second heat exchange unit has a first heat exchange section and a second heat exchange section,
The first heat exchange part faces the plurality of first flat tubes, and the second heat exchange part faces the plurality of second flat tubes ,
The second header pipe is
at least one refrigerant inlet into which refrigerant flows from outside the first heat exchange unit;
at least one refrigerant outlet through which refrigerant flows out of the first heat exchange unit;
including;
A heat exchanger in which the number of refrigerant inflow portions and the number of refrigerant outflow portions of the second header pipe are different . Comprising a first heat exchange unit and a second heat exchange unit that perform heat exchange,
The first heat exchange unit includes:
a plurality of first flat tubes each extending in a first direction and lined up in a second direction perpendicular to the first direction;
a plurality of second flat tubes each extending in an extension direction perpendicular to the second direction and lined up in the second direction;
a first header pipe connected to one end of the plurality of first flat tubes in the first direction and extending in the second direction;
a second header pipe connected to the other end of the plurality of first flat tubes in the first direction and one end of the plurality of second flat tubes in the extension direction and extending in the second direction;
a third header pipe connected to the other end of the plurality of second flat tubes in the extension direction and extending in the second direction;
has
The second heat exchange unit has a first heat exchange section and a second heat exchange section,
The first heat exchange section faces the plurality of first flat tubes.
The second heat exchange section faces the plurality of second flat tubes,
The first heat exchange unit includes:
a first plate member extending in the first direction from the first header pipe to the second header pipe;
A heat exchanger further comprising: a second plate member extending in the extension direction from the third header pipe to the second header pipe. Comprising a first heat exchange unit and a second heat exchange unit that perform heat exchange,
The first heat exchange unit includes:
a plurality of first flat tubes each extending in a first direction and lined up in a second direction perpendicular to the first direction;
a plurality of second flat tubes each extending in an extension direction perpendicular to the second direction and lined up in the second direction;
a first header pipe connected to one end of the plurality of first flat tubes in the first direction and extending in the second direction;
a second header pipe connected to the other end of the plurality of first flat tubes in the first direction and one end of the plurality of second flat tubes in the extension direction and extending in the second direction;
a third header pipe connected to the other end of the plurality of second flat tubes in the extension direction and extending in the second direction;
has
The second heat exchange unit has a first heat exchange section and a second heat exchange section,
The first heat exchange section faces the plurality of first flat tubes.
The second heat exchange section faces the plurality of second flat tubes,
The second header pipe includes at least two partition plates that partition an internal space of the second header pipe,
In the heat exchanger, the at least two partition plates are inclined away from each other from the third header pipe side toward the first header pipe side. The second header pipe is
at least one refrigerant inlet into which refrigerant flows from outside the first heat exchange unit;
at least one refrigerant outlet through which refrigerant flows out of the first heat exchange unit;
The heat exchanger according to claim 2 or 3, comprising: The first heat exchange section includes:
a first refrigerant inflow section into which a refrigerant flows from outside the first heat exchange section;
a first refrigerant outflow portion through which the refrigerant flows out;
The heat exchanger according to claim 1 or 4, wherein the first refrigerant inlet and the first refrigerant outlet are arranged on the second header pipe side with respect to the first header pipe. The first header pipe is arranged such that the central axis of the second header pipe is located on the second heat exchange unit side with respect to the central axis of the first header pipe and the central axis of the third header pipe. , the second header pipe, and the third header pipe are arranged, the heat exchanger according to any one of claims 1 to 5. Comprising a first heat exchange unit and a second heat exchange unit that perform heat exchange,
The first heat exchange unit includes:
a plurality of first flat tubes each extending in a first direction and lined up in a second direction perpendicular to the first direction;
a plurality of second flat tubes each extending in the first direction and lined up in the second direction;
a first header pipe connected to one end of the plurality of first flat tubes in the first direction and extending in the second direction;
a second header pipe connected to the other end of the plurality of first flat tubes in the first direction and one end of the plurality of second flat tubes in the first direction and extending in the second direction;
a third header pipe connected to the other end of the plurality of second flat tubes in the first direction and extending in the second direction;
The second header pipe is
at least one refrigerant inlet into which refrigerant flows from outside the first heat exchange unit;
at least one refrigerant outlet through which the refrigerant flows out of the first heat exchange unit;
The second heat exchange unit includes a first heat exchange section and a second heat exchange section,
The first heat exchange section includes a plurality of flat first fins and a meandering first pipe passing through the plurality of first fins,
The second heat exchange part includes a plurality of flat second fins and a meandering second pipe passing through the plurality of second fins,
The first pipe includes a first refrigerant inflow portion into which the refrigerant flows, and a first refrigerant outflow portion through which the refrigerant flows out;
The second pipe includes a second refrigerant inflow portion into which the refrigerant flows and a second refrigerant outflow portion through which the refrigerant flows out;
The first heat exchange part faces the plurality of first flat tubes connected to the first header pipe and the second header pipe,
The first refrigerant inflow part and the first refrigerant outflow part are arranged on the second header pipe side with respect to the first header pipe,
The second heat exchange section faces the plurality of second flat tubes connected to the second header pipe and the third header pipe,
The second refrigerant inflow part and the second refrigerant outflow part are arranged on a side of the second header pipe with respect to the third header pipe. An air conditioner comprising the heat exchanger according to any one of claims 1 to 7.

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