JP4178472B2 - Heat exchanger and air conditioner - Google Patents

Description

  The present invention relates to a heat exchanger housed in an air conditioner and an air conditioner using the heat exchanger.

As a conventional heat exchanger, a heat exchanger configured in a multi-pass system by connecting a header to an end of a heat transfer tube group has been proposed (see, for example, Patent Documents 1 and 2).
Moreover, what equipped the auxiliary heat exchanger with the heat exchanger accommodated in an air conditioner is proposed (for example, refer patent document 3).

JP-A-4-268128 (Claim 1, FIG. 1, FIG. 4) JP-A-4-240364 (Claim 1, FIGS. 1 to 3) JP 2001-28761 A (paragraphs [0048] and [0072], FIGS. 7 to 9)

  As disclosed in Patent Document 1, a heat exchanger used in a conventional air conditioner is a multi-pass heat exchanger in which end portions of heat transfer tube groups are connected using a header in order to suppress pressure loss of the refrigerant. Is generally adopted. That is, the conventional heat exchanger includes a plurality of fins arranged in parallel along the airflow direction, a plurality of heat transfer tube groups arranged in a direction orthogonal to these fins and in which the refrigerant flows, Each header has a header connected to each end of the heat transfer tube group, and the inside of each header is partitioned by a flat partition plate parallel to the air flow direction so that each header in the vertical direction (stage direction) of the heat transfer tube group A plurality of refrigerant circuits through which the refrigerant passes through the header chamber are configured.

  In the heat exchanger of Patent Document 1, the refrigerant sequentially flows from the lower heat transfer tube group to the upper heat transfer tube group through the header chamber of each header during evaporation, and flows in the reverse order to the evaporation during condensation. In the course of this flow, heat exchange with air is performed through the fins. Further, since each header is partitioned by a flat partition plate parallel to the airflow direction, one refrigerant circuit does not overlap with other refrigerant circuits in the airflow direction. For this reason, when such a heat exchanger is used in an air conditioner, when the refrigerant evaporates, the dryness of the refrigerant increases in the heat transfer tube on the refrigerant outlet side, so that the air cannot be cooled sufficiently and the humidity is reduced. Since high air is allowed to pass through, moisture condenses on the surface of the fan installed behind the heat exchanger, and there is a problem that so-called dew is generated from the outlet of the air conditioner.

  On the other hand, Patent Document 2 adopts a diversion method that uses a header to reduce pipe resistance, while the refrigerant passes through a plurality of heat transfer tubes via a header formed so that the refrigerant moves in a direction orthogonal to the airflow direction. It shows what prevents dew spilling through a method of passing through and exchanging heat with air. However, in the heat exchanger disclosed in this document, after the refrigerant flows into the lowermost position (in the gravitational direction) of the header on the windward side of the airflow, the refrigerant moves down the windward side of the airflow in the header. Then, the refrigerant flows from the uppermost side to the lowermost side on the leeward side of the airflow, and then flows out from the lowermost position of the header on the leeward side to constitute a single refrigerant circuit. Further, in the header of this heat exchanger, a plurality of heat transfer tube groups in which a plurality of heat transfer tubes are integrally formed in the vertical direction are connected, and the number of heat transfer tubes included in these heat transfer tube groups is increased from below to above. A method of gradually increasing toward is adopted. Therefore, the piping structure of the header on the refrigerant inflow side and the outflow side is considerably complicated. Therefore, it is a header structure that is difficult to adopt for a multi-pass heat exchanger.

  In the air conditioner of Patent Document 3, since the heat exchange pipe has a circular cross section, the auxiliary heat exchanger is arranged in a plurality of rows, resulting in an increase in wind pressure loss, a reduction in air volume and noise. There was a problem that it increased.

  The present invention has been made in view of the above-described problems. The simple header structure reduces wind pressure loss and prevents dew escaping, and improves the refrigerant-side heat transfer coefficient and heat exchange between the refrigerants. An object is to obtain a highly efficient heat exchanger and air conditioner by preventing heat loss.

The heat exchanger of the present invention includes a plurality of fins arranged in parallel along the airflow direction, a plurality of heat transfer tube groups arranged in a direction orthogonal to the fins and in which a refrigerant flows, and the inside A heat exchanger having a first header and a second header each divided into a plurality of header chambers by a partition plate, wherein the header chamber of the second header is connected to a heat transfer tube group at a refrigerant inflow position of the second header. , A heat transfer tube group at the refrigerant inflow position of the second header, a heat transfer tube group at the refrigerant inflow position of the second header, a header chamber of the first header connected to the heat transfer tube group at the intermediate position, and a heat transfer tube group at the intermediate position Connected to the header chamber of the second header connected to the two heat transfer tube groups at the intermediate position, the heat transfer tube group at the intermediate position, the heat transfer tube group at the intermediate position, and the heat transfer tube group at the refrigerant outflow position of the second header first header header chamber, said second header Tube bank of the refrigerant outflow position, the second header of the second header of the header chamber connected to the tube bank of the refrigerant outflow position, capital sequentially plurality includes a refrigerant circuit constituted by connecting the first The header and the second header are provided so that each longitudinal direction thereof is orthogonal to the air flow direction, and the refrigerant transfer position of the second header is different from that of the heat transfer tube group at the refrigerant inflow position of the second header. The heat transfer tube group is configured to be adjacent to the airflow direction.

  According to the heat exchanger of the present invention, the first and second headers are connected to the end portions of the plurality of heat transfer tube groups, and the plurality of heat transfer tube groups are divided by the two types of partition plates of the first and second headers. The heat transfer tube group at the refrigerant inflow position of one refrigerant circuit divided into the refrigerant circuit and the heat transfer tube group at the refrigerant outflow position of another refrigerant circuit adjacent to the refrigerant circuit are Since it is arranged so as to overlap each other on the leeward side, air can be uniformly cooled and dehumidified, and dew can be prevented.

Embodiment 1 FIG.
FIG. 1 is a schematic configuration diagram of a heat exchanger showing a first embodiment of the present invention, FIG. 2 is an enlarged cross-sectional view taken along line BB in FIG. 1, and FIG. 3 is an enlarged cross-sectional view taken along line CC in FIG. FIG. 4 shows an enlarged view of the heat exchanger of FIG. 1 viewed from the right side.

  In FIG. 1, a large number of fins 5 are installed parallel to each other along the air flow direction, and a plurality of heat transfer tube groups 1a to 1c, 1d1 (1d2), 2a1 (in which the refrigerant flows in a direction orthogonal to the fins 5) 2a2), 2b-2c, 2d1 (2d2), 3a1 (3a2), 3b, 3c, 3d1 (3d2), 4a1 (4a2), 4b-4d, and each heat transfer tube of all the heat transfer tube groups Are connected and connected by a first header 12 and between the other ends by a second header 13. As shown in detail in FIG. 2, the first header 12 is provided with two types of partition plates 14 that are divided into a plurality of header chambers in the step direction (vertical direction) of the heat transfer tube group. As shown in detail in FIG. 3, two types of partition plates 15 are provided in the inside of 13, which are similarly divided into a plurality of header chambers in the step direction (vertical direction). Then, the flow direction of the refrigerant is regulated for each header chamber partitioned by these partition plates 14 and 15. All the heat transfer tube groups described above are joined to the fins 5 by the pipe expanding means.

  In FIG. 2, the first header 12 is partitioned into eight header chambers 12 a to 12 h in the step direction by a partition plate 14 including partition plates 14 a and 14 b having two types of shapes. One partition plate 14a has a flat plate shape, and the other partition plate 14b has a step shape. These partition plates 14a and 14b are alternately provided in the step direction. Of the eight header chambers described above, 12b and 12c, 12d and 12e, and 12f and 12g are opposite to the L-shaped header chamber (for example, 12c) by the step-shaped partition plate 14b and the flat partition plate 14a. It is partitioned into an L-shaped header chamber (for example, 12b). In particular, heat transfer tube groups 1d1 and 2a1 connected to the header chamber 12b (these heat transfer tube groups are called heat transfer tube groups at the refrigerant inflow position), and heat transfer tube groups 1d2 and 2a2 connected to the header chamber 12c (these components) The heat transfer tube group is referred to as the heat transfer tube group at the refrigerant outflow position, and is separated into an upwind side and an leeward side of the airflow (the airflow direction is indicated by 11) and is arranged in two stages in the step direction. Similarly, heat transfer tube groups 2d1 and 3a1, 2d2 and 3a2, heat transfer tube groups 3d1 and 4a1, 3d2 and 4a2 are separated into two stages, each separated into the leeward side and leeward side of the airflow. Are arranged. Note that each of the above-described heat transfer tube groups is constituted by three heat transfer tubes arranged in the airflow direction. On the other hand, the heat transfer tube group other than these is composed of six heat transfer tubes arranged in the airflow direction.

  In FIG. 3, the second header 13 is divided into 12 header chambers 13a, 13b, 13c1, 13c2, 13d, 13e1, 13e2, 13f, 13g1, by a partition plate 15 composed of partition plates 15a and 15b having two types of shapes. It is divided into 13g2, 13h, and 13i. One partition plate 15a has a flat plate shape, and the other partition plate 15b has an I-shape. Every other I-shaped partition plate 15b is disposed. Among the 12 header chambers described above, 13c1, 13c2, 13e1, 13e2, 13g1, and 13g2 are partitioned into vertically long rectangular header chambers (for example, 13c1 and 13c2) by an I-shaped partition plate 15b. . In particular, heat transfer tube groups 1d1 and 2a1 connected to the header chamber 13c1 (these heat transfer tube groups are called heat transfer tube groups at the refrigerant inflow position) and heat transfer tube groups 1d2 and 2a2 connected to the header chamber 13c2 (these The heat transfer tube group is referred to as the heat transfer tube group at the refrigerant outflow position) and is divided into two stages each separated into the windward side and leeward side of the airflow. Similarly, heat transfer tube groups 2d1 and 3a1, 2d2 and 3a2, heat transfer tube groups 3d1 and 4a1, 3d2 and 4a2 are separated into two stages, each separated into the leeward side and leeward side of the airflow. Are arranged. Further, in FIGS. 1 and 4, 16 a, 16 b 1, 16 b 2, 16 c 1, 16 c 2, 16 d 1, 16 d 2, and 16 e are eight connecting pipes that serve as refrigerant inlets or outlets. Of these, 16b1, 16c1, 16d1, and 16e are refrigerant inlets during evaporation, and 16a, 16b2, 16c2, and 16d2 are refrigerant outlets during evaporation. At the time of condensation, the front four are the refrigerant inlet and the rear four are the refrigerant outlet.

  When the refrigerant evaporates, it passes through the connecting pipes 16b1, 16c1, 16d1, and 16e of one of the second headers 13 as indicated by solid arrows, and the dryness (the dryness is the mass flow rate of the refrigerant vapor. Is divided by the sum of the mass flow rate of the refrigerant liquid) and flows into the second header 13 in a state of about 0.2. First, the operation of the refrigerant flowing into the second header 13 through the connection pipe 16e will be described. The refrigerant that has flowed into the header chamber 13i from the connecting pipe 16e flows into the heat transfer tube group 4d in a state where the flow is restricted by the flat partition plate 15a. Since the refrigerant exchanges heat with the air flowing between the fins 5 while passing through the heat transfer tube group 4d, the dryness of the refrigerant increases. Thereafter, the refrigerant flows into the header chamber 12h on the first header 12 side from the heat transfer tube group 4d, and flows into the heat transfer tube group 4c again in a state where the flow is restricted by the flat partition plate 14a, and the air and heat Exchange. Thereafter, the refrigerant returns from the heat transfer tube group 4c to the header chamber 13h on the second header 13 side, passes through the heat transfer tube group 4b, and is partitioned by the flat partition plate 14a and the step-shaped partition plate 14b. It flows into the header chamber 12g on the 12th side. Thereafter, the refrigerant flowing into the header chamber 12g flows into the heat transfer tube groups 4a2 and 3d2 located downstream from the heat transfer tube group 4b, and exchanges heat with air. After that, the refrigerant that has passed through the heat transfer tube groups 4a2 and 3d2 merges in the header chamber 13g2 on the second header 13 side partitioned by the I-shaped partition plate 15b, and then the connection tube is in a state of dryness of 1. It flows out to external piping (not shown) through 16d2.

  The header chamber 13i, the heat transfer tube group 4d, the header chamber 12h, the heat transfer tube group 4c, the header chamber 13h, the heat transfer tube group 4b, the header chamber 12g, and the heat transfer tube groups 4a2 and 3d2, which are a series of refrigerant flow paths described above. The header chamber 13g2 forms one refrigerant circuit C1, in which the heat transfer tube group 4d is a heat transfer tube group located at the refrigerant inflow position, and the heat transfer tube groups 4a2 and 3d2 are located at the refrigerant outflow position. The heat tube group and heat transfer tube groups 4c and 4b are heat transfer tube groups at intermediate positions. Further, as shown in FIG. 2, the above-described heat transfer tube group 4 c is composed of one stage in the step direction (corresponding to the direction along gravity in this figure). For this reason, compared with the prior art example in which the heat transfer tube group 4c is composed of a plurality of stages, it is possible to prevent the refrigerant distribution to the individual heat transfer tubes from becoming uneven due to the influence of gravity. This also applies to the movement of the refrigerant from the heat transfer tube group 4c to 4b in the header chamber 13h, for example.

Similarly, the refrigerant that has flowed into the second header 13 through the connection pipe 16d1 at a dryness of about 0.2 flows into the header chamber 13g1 partitioned from the header chamber 13g2 by the I-shaped partition plate 15b, and the heat transfer tube Divide into groups 4a1 and 3d1. Since this refrigerant exchanges heat with air while passing through the heat transfer tube groups 4a1 and 3d1, the dryness of the refrigerant increases. Thereafter, the refrigerant flows from the heat transfer tube groups 4a1 and 3d1 into the header chamber 12f on the first header 12 side and joins, and the flow is regulated by the step-like partition plate 14b and the flat partition plate 14a. It flows into the heat transfer tube group 3c again and exchanges heat with air. After that, the refrigerant returns from the heat transfer tube group 3c to the header chamber 13f on the second header 13 side, passes through the heat transfer tube group 3b, and is partitioned by the flat partition plate 14a and the step-shaped partition plate 14b. Into the header chamber 12e. Thereafter, the refrigerant flowing into the header chamber 12e flows into the heat transfer tube groups 3a2 and 2d2 located on the leeward side and exchanges heat with the air. After that, the refrigerant that has passed through the heat transfer tube groups 3a2 and 2d2 is partitioned by the I-shaped partition plate 15b and merged in the header chamber 13e2 on the second header 13 side. Spill through.
The header chamber 13g1, the heat transfer tube groups 4a1 and 3d1, the header chamber 12f, the heat transfer tube group 3c, the header chamber 13f, the heat transfer tube group 3b, the header chamber 12e, and the heat transfer tube group 3a2 which are a series of refrigerant flow paths described above. 2d2 and the header chamber 13e2 form a refrigerant circuit C2 different from the above. In this refrigerant circuit C2, the heat transfer tube groups 4a1 and 3d1 are heat transfer tube groups located at the refrigerant inflow position, the heat transfer tube groups 3a2 and 2d2 are heat transfer tube groups located at the refrigerant outflow position, and the heat transfer tube groups 3c and 3b are intermediate positions. It is a heat transfer tube group.

In the above, heat transfer tube groups 4a2 and 3d2 at the refrigerant outflow position of refrigerant circuit C1, heat transfer tube groups 4a1 and 3d1 at the refrigerant inflow position of refrigerant circuit C2, 4a1 and 4a2, and 3d1 and 3d2 are adjacent to each other in the airflow direction. The windward side and the leeward side of the airflow are arranged so as to overlap each other (for example, as seen from the arrangement of 4a1 and 4a2, they are arranged at the same step position in the step direction). Further, when the main flow direction of the refrigerant in the first header 12 and the second header 13 in the step direction is evaporated, the refrigerant circuit C1 and other adjacent to the refrigerant circuit C1 as shown by solid line arrows in FIGS. C2 which is the refrigerant circuit of Fig. 2 is in the direction from bottom to top in the figure, while at the time of condensation, the refrigerant circuit C1 and other adjacent ones as shown by broken arrows in Figs. C2 which is a refrigerant circuit is also from the top to the bottom in the figure. Thus, in any case, the adjacent refrigerant circuits are in the same direction. Further, both refrigerant circuits are divided by a step-like partition plate 14 b in the first header 12 and by an I-shaped partition plate 15 b in the second header 13.
The operation of the refrigerant flowing from the connection pipe 16c1 to the second header 13 with a dryness of about 0.2 is the same as the operation of the refrigerant flowing from the connection pipe 16d1, and finally the dryness is 1 in each state. It flows out from the connecting pipes 16b2 and 16c2.

  Finally, the operation of the refrigerant that has flowed into the second header 13 through the connection pipe 16b1 at a dryness of about 0.2 will be described. The refrigerant that has flowed into the header chamber 13c1 on the second header 13 side partitioned by the I-shaped partition plate 15b from the connecting pipe 16b1 flows into the heat transfer tube groups 2a1 and 1d1, and passes through the heat transfer tube groups 2a1 and 1d1. In the meantime, heat exchange with air is performed, so the dryness of the refrigerant increases. Thereafter, the refrigerant flows into the header chamber 12b on the first header 12 side from the heat transfer tube groups 2a1 and 1d1 and merges, and the flow is regulated by the step-like partition plate 14b and the flat partition plate 14a. It again flows into the heat transfer tube group 1c and exchanges heat with air. The refrigerant returns from the heat transfer tube group 1c to the header chamber 13b on the second header 13 side, and flows into the header chamber 12a on the first header 12 side through the heat transfer tube group 1b. Thereafter, the refrigerant flowing into the header chamber 12a flows into the heat transfer tube group 1a and exchanges heat with air. Thereafter, the refrigerant that has passed through the heat transfer tube group 1a flows into the header chamber 13a on the second header 13 side, and flows out through the connection tube 16a with a dryness of 1.

  Also, during condensation, the refrigerant flows in the opposite direction to that during evaporation, as indicated by the dashed arrows. For example, the operation of the refrigerant flowing into the second header 13 through the connection pipe 16c2 will be described. The refrigerant flows into the connecting pipe 16c2 in the state of superheated gas having a dryness of 1. The refrigerant that has flowed into the header chamber 13e2 through the connection pipe 16c2 flows into the heat transfer pipe groups 2d2 and 3a2, and exchanges heat with air while passing through the heat transfer pipe groups 2d2 and 3a2. The degree becomes smaller. Thereafter, the refrigerant flows into and joins the header chamber 12e on the first header 12 side from the heat transfer tube groups 2d2 and 3a2, and the flow is regulated by the step-like partition plate 14b and the flat partition plate 14a. It again flows into the heat transfer tube group 3b and exchanges heat with air. Thereafter, the refrigerant returns from the heat transfer tube group 3b to the header chamber 13f on the second header 13 side, and flows into the header chamber 12f on the first header 12 side through the heat transfer tube group 3c. Thereafter, the refrigerant flowing into the header chamber 12f flows into the heat transfer tube groups 3d1 and 4a1 located on the windward side, and exchanges heat with air. Thereafter, the refrigerant that has passed through the heat transfer tube groups 3d1 and 4a1 merges in the header chamber 13g1 on the second header 13 side, and then flows out through the connection tube 16d1 in a supersaturated state with a dryness of 0. 2 and 3, the solid line arrows indicate the main flow direction of the refrigerant at the time of evaporation, and the broken line arrows indicate the main flow direction of the refrigerant at the time of condensation, both of which are stepwise.

  Thus, according to the first embodiment, when the refrigerant evaporates, the heat transfer tube groups 3d2, 4a2 having a dryness of 1 at the refrigerant outflow position of the refrigerant circuit C1, and the refrigerant at the refrigerant inflow position of the refrigerant circuit C2. The heat transfer tube groups 3d1, 4a1 having a low dryness, the heat transfer tube groups 2d2, 3a2 having a dryness of 1 at the refrigerant outflow position of the refrigerant circuit C2, and the refrigerant dryness at the refrigerant inflow position of the refrigerant circuit C3 are small. The heat transfer tube groups 2d1, 3a1 are further divided into heat transfer tube groups 1d2, 2a2 having a dryness of 1 at the refrigerant outflow position of the refrigerant circuit C3, and heat transfer tube groups 1d1 having a low dryness of the refrigerant at the refrigerant inflow position of the refrigerant circuit C4. 2a1 are overlapped at the same step position of the heat transfer tube group with respect to the airflow direction 11, respectively, so that the heat transfer tube groups 3d2, 4a2, 2d2, 3a2, 1d2, 2a2 at the refrigerant outflow position located on the leeward side of the airflow Even if the dryness of the refrigerant passing through becomes 1, air is uniformly distributed by the heat transfer tube groups 3d1, 4a1, 2d1, 3a1, 1d1, 2a1 positioned corresponding to these heat transfer tube groups on the windward side of the airflow. Since it can be cooled and dehumidified, it is possible to substantially prevent dew on the leeward side of the heat exchanger (hereinafter referred to as the rear of the heat exchanger). Here, among the heat transfer tube groups at the refrigerant outflow position arranged in the refrigerant circuit, the heat transfer tube group 1a arranged in only one step in the step direction overlaps with the heat transfer tube group having a small dryness in the air flow direction. However, in comparison with the conventional example, the ratio of the heat transfer tube group having a dryness of 1 corresponds to 1 in 16 in the step direction, and the conventional heat exchanger (the heat transfer tube group has 16 steps in the step direction, 6 in the direction of air flow, and the dampers at both ends are flat partition plates, 8 in the first header, 12 in the second header, and 12 in the header chamber. It is clear that the possibility of occurrence of dew is considerably reduced because it is much smaller than the proportion of heat transfer tubes.

  In addition, the step-like partition plate 14b allows the number of heat transfer tubes (three) in the heat transfer tube group of one refrigerant circuit to have a dryness of 1 at the same step position in the step direction with respect to the airflow and at the refrigerant outflow position. The sum of the number of heat transfer tubes (3) in the heat transfer tube group of another refrigerant circuit where the dryness of the refrigerant is small at the refrigerant inflow position is arranged in the same number as the total number (6) of heat transfer tubes in each adjacent stage. In addition, the main flow directions of the refrigerants in both refrigerant circuits at the header position can be the same direction. For this reason, it is also possible to adopt a configuration in which the connection with the external piping is concentrated on one second header 13.

  Further, for example, even if the refrigerant flowing into the header chamber 13g1 through the connection pipe 16d1 is non-uniformly distributed in the heat transfer tube groups 3d1 and 4a1, it is merged again in the other header chamber 12f, so that the non-uniform distribution Can be eliminated once and heat transfer performance can be secured. Further, the fact that the number of stages of the heat transfer tubes is one in the intermediate path of the refrigerant circuit is useful for eliminating uneven distribution.

  In addition, the boundary lines (partition plates) of the header chambers of the conventional example, all of which are formed in parallel, as shown in FIG. 2, for example, with the heat transfer tube group (for example, 2d2, 3a2) at the refrigerant outflow position, At the boundary where the heat transfer tube group (for example, 2d1, 3a1) at the refrigerant inflow position is adjacent, one of the heat transfer tubes is arranged in two stages (the number of heat transfer tubes is half that of the conventional case) By simply changing the boundary line of the header chamber in the first header 12 to a step shape (in the other second header 13 shown in FIG. 3, the boundary line of the header chamber is changed to an I-shape), it is possible to substantially prevent exposure. The heat exchanger which can be obtained can be obtained easily.

On the other hand, the refrigerant that flows in at the time of condensation is adjacent to the heat transfer tube group (for example, 3d2, 4a2) at the refrigerant inflow position and the heat transfer tube group (for example, 3d1, 4a1) at the refrigerant outflow position, and has a large amount of refrigerant liquid on the windward side. Since the heat tube group is arranged, an efficient heat exchanger can be realized.
Moreover, since the connection pipes 16b1, 16c1, and 16d1 that are the refrigerant outlets of the refrigerant circuit are positioned on the windward side of the air flow during condensation, the temperature of the refrigerant can be sufficiently lowered, and the efficiency of the system can be improved. .

2 and 3, in one refrigerant circuit, the number of heat transfer tube groups is 5 or 6 in the stage direction, and in the airflow direction, for example, 6 rows for 4d, 4c, and 4b, 4a2 and 3d2 show the case where there are three rows, but the number of stages and the number of rows of the heat transfer tube group are arbitrary.
Moreover, although each connection part of the inflow port and outflow port of one refrigerant circuit and external piping (not shown) was provided in the same header here, you may provide these connection parts in a different header, You may provide so that the connection part of the inflow port and outflow port of a certain one refrigerant circuit and external piping (not shown) may exist in the same header, and the thing in a different header may coexist.

Embodiment 2. FIG.
Next, a heat exchanger according to a second embodiment of the present invention is shown in FIGS. 5 is a schematic configuration diagram of the heat exchanger according to this embodiment, FIG. 6 is a DD enlarged sectional view of FIG. 5, FIG. 7 is an EE enlarged sectional view of FIG. 5, and FIG. It is the enlarged view which looked at the vessel from the right side.
The heat exchanger of this embodiment is a heat transfer tube group 1A, 2B, 3C, 4D, 2A, 2B, 2C, 2D, 3A, 3B, 3C, 3D, 4A, 4B, 4C, 4D having a flat cross section. It is composed. That is, each heat transfer tube has a plurality of (for example, six) refrigerant channels arranged in the airflow direction 11. These flat heat transfer tube groups are inserted and joined in a direction orthogonal to a large number of fins 5 arranged in parallel along the airflow direction and so that the major axis direction of the cross section is parallel to the airflow direction 11. And the 1st header 12 and the 2nd header 13 of the same structure as 1st Embodiment are connected to the edge part of each heat exchanger tube group. In addition, when referring to a flat heat transfer tube, the cross section of the heat transfer tube includes an ellipse, an ellipse, or a streamline shape, and a plurality of independent flow paths through which the refrigerant flows are integrally formed. It is what. In addition, the cross-sectional shape of the refrigerant flow path is not particularly limited, and may be any shape such as a square or a circle.

Here, assuming that the refrigerant flow path of each flat heat transfer tube is represented by the same reference numeral as that of the heat transfer tube group described in the first embodiment, the refrigerant flow path of the flat heat transfer tube group is as shown in FIG. It becomes like 6. In the first header 12, the flat heat transfer tube groups 1D and 2A are divided into refrigerant flow paths 1d1 and 2a1 at the refrigerant inflow position and refrigerant flow path 1d2 at the refrigerant outflow position by the step-like partition plate 14b when the refrigerant evaporates. And 2a2 are arranged at the same step position so as to overlap each other on the windward side and the leeward side of the airflow.
Similarly, the flat heat transfer tube groups 2D and 3A are arranged so that the refrigerant flow paths 2d1 and 3a1 at the refrigerant inflow position and the refrigerant flow paths 2d2 and 3a2 at the refrigerant outflow position overlap each other on the windward side and the leeward side of the airflow. The flat heat transfer tube groups 3D and 4A are arranged at the same stage position. The refrigerant flow paths 3d1 and 4a1 at the refrigerant inflow position and the refrigerant flow paths 3d2 and 4a2 at the refrigerant outflow position are on the windward side and leeward side of the airflow. They are arranged at the same step position so as to overlap each other.

  Further, in the second header 13, when the refrigerant evaporates, the flat heat transfer tube groups 1D and 2A are separated from the refrigerant flow paths 1d1 and 2a1 at the refrigerant inflow position and the refrigerant flow at the refrigerant outflow position by the I-shaped partition plate 15b. The channels 1d2 and 2a2 are arranged at the same step position so that they overlap each other on the windward side and leeward side of the airflow, and the flat heat transfer tube groups 2D and 3A are connected to the refrigerant flow paths 2d1 and 3a1 at the refrigerant inflow position and the refrigerant outflow, respectively. The refrigerant flow paths 2d2 and 3a2 at the positions are arranged at the same step position so that they overlap each other on the windward side and the leeward side of the air flow, and the flat heat transfer tube groups 3D and 4A are arranged at the refrigerant flow positions 3d1 and 4a. 4a1 and the refrigerant flow paths 3d2 and 4a2 at the refrigerant outflow position are arranged at the same step position so as to overlap each other on the windward side and leeward side of the airflow.

These flat heat transfer tube groups 1D, 2A, 2D, 3A, 3D, and 4A are joined to the first header 12 across the vertical plate of the step-like partition plate 14b in the first header 12, and in the second header 13, The I-shaped partition plate 15b is joined to the second header 13 with the vertical plate interposed therebetween. Therefore, it is not always necessary to divide these flat heat transfer tube groups into a refrigerant channel group at the refrigerant inflow position and a refrigerant channel group at the refrigerant outflow position.
Further, all the above flat heat transfer tube groups are joined to the fins 5 by brazing means.

  The heat exchanger according to the second embodiment is configured as described above. The heat exchanger according to the first embodiment is different in that a plurality of refrigerant flow paths are integrally formed in one heat transfer tube. Since it is different from the heat exchanger, the action and effect at the time of refrigerant evaporation and condensation are basically the same as those of the first embodiment. However, the flat heat transfer tube group has the advantages of higher heat exchange efficiency and lower noise than the heat transfer tube group having a circular cross section.

Embodiment 3 FIG.
FIG. 9 schematically shows a cross section of an air conditioner according to a third embodiment to which the above-described heat exchanger of the present invention is applied. In the figure, 21 is an indoor unit body of an air conditioner, 22 is an upper air inlet, 23 is a front side air inlet, 24 is an air outlet, 25 is an outlet vane, 26 is a heat exchanger, 27 is a blower, 28 Is a front drain pan, 29 is a back drain pan, and 30 is a scroll casing. Further, a movable panel (not shown) that opens during operation may be provided in front of the front air inlet 23.

  A heat exchanger 26 is disposed in the indoor unit main body 21, and a blower 27 is disposed so as to be covered by the heat exchanger 26. The blower 27 has an axial dimension substantially the same as the width dimension of the heat exchanger 26, and includes a cross-flow fan disposed to face the heat exchanger 26 and a fan motor that rotationally drives the cross-flow fan. The

  The lower end portion on the front side of the heat exchanger 26 is placed on the front drain pan 28, and the lower end portion on the rear side is placed on the rear drain pan 29. The drain water generated in the heat exchanger flows down to these drain pans, is collected in the front drain pan 28, and can be drained to the outside through a drain hose (not shown).

  In addition, the outer surface of a part of the side walls of the front and rear drain pans 28 and 29 is provided at a position close to the blower 27, and these constitute a nose for the blower 27. A scroll casing 30 connects the side walls of the drain pans 28 and 29 and the air outlet 24. A space surrounded by the scroll casing 30 serves as an air passage that communicates the nose and the air outlet 24.

Next, the heat exchanger 26 will be described in detail. This heat exchanger 26 is a combination of a main heat exchanger 40 formed in a substantially inverted V shape in a side view and an auxiliary heat exchanger 44 arranged along the air suction side of the main heat exchanger 40. Consists of the body. Since such a main heat exchanger 40 is incorporated in the indoor unit main body 21, it is positioned in a generally U shape opposite to the front air inlet 23, so that this portion is designated as a front upper heat exchanger. 41 and the front lower heat exchanger 42, and the one that is inclined to the upper air inlet 22 and the oblique rear side is called the rear heat exchanger 43.
Here, the main heat exchanger 40 is an application of the above-described heat exchanger of the present invention, and the header portion connected to the end portion is not shown. The main heat exchanger 40 includes a large number of fins 45 provided side by side with a narrow space, and a heat exchange pipe 46 having a flat cross section through the fins 45 and joined by brazing means. The heat exchange pipe 46 corresponds to the flat heat transfer tube in the second embodiment, and a plurality of refrigerant flow paths are integrally formed therein.

  On the other hand, the auxiliary heat exchanger 44 is disposed in a substantially triangular space above the rear heat exchanger 43 and has a width direction dimension substantially the same as the width direction dimension of the rear heat exchanger 43. The auxiliary heat exchanger 44 includes a large number of fins 47 provided with a small interval, and a heat exchange pipe 48 having a flat cross section that penetrates the fins 47 and is joined by brazing means. Become.

  FIG. 10 schematically shows a piping system in the heat exchanger 26. The main heat exchanger 40 includes two rows of heat exchange pipes 46 having a flat cross section in the longitudinal direction of the front upper heat exchanger 41, the front lower heat exchanger 42, and the rear heat exchanger 43 in the longitudinal direction. Are arranged at a certain distance and arranged in a grid pattern.

  The heat exchange pipe 46 having a flat cross-sectional shape in the main heat exchanger 40 has a straight portion whose length is substantially the same as the width direction of the parallel fins 45, and both ends project from the parallel fins 45. Each end is connected to a header (not shown) to form a plurality of refrigerant circuits.

  The heat exchange pipes 48 having a flat cross section in the auxiliary heat exchanger 44 are arranged in a line along the longitudinal direction of the fins 47. A solid line and a broken line shown above and below between the heat exchange pipes 48 having a flat cross section indicate one end of a portion protruding from the fins 47 at both ends, and the cross section flat heat exchange pipe 48 of the protrusion portion is bent in a U shape, or A flow path is configured by connecting a header (not shown).

  The auxiliary heat exchanger 44 is formed with two refrigerant channels, each of which is further connected to four systems, and the main heat exchanger 40 is formed with eight refrigerant channels.

  The arrows in FIG. 10 indicate the flow of the refrigerant in the cooling operation. That is, at the time of cooling, the refrigerant is introduced from the outside into the auxiliary heat exchanger 44, exits the auxiliary heat exchanger 44, is divided into a plurality of systems at the branching portion 51, and then led to the main heat exchanger 40. Further, the refrigerant merges after leaving the main heat exchanger 40 and is guided to the outside. The refrigerant flow during heating is the reverse of that during cooling. That is, after heating, the refrigerant is divided into a plurality of systems from the outside and then introduced into the main heat exchanger 40. After leaving the main heat exchanger 40, the refrigerant is merged and led to the auxiliary heat exchanger 44.

  According to the third embodiment, as the heat exchanger 26, in addition to the front upper heat exchanger 41, the front lower heat exchanger 42, and the rear heat exchanger 43, auxiliary heat is added to the upper dead space of the indoor unit body 21. Since the exchanger 44 is provided, the capacity of the indoor unit body 21 can be maintained as it is, and the heat exchange capacity can be increased, so that the heat exchange capacity can be increased. Further, since the main heat exchanger 40 is provided with a heat exchange pipe 46 having a flat cross section that penetrates the fin 45 and is joined by brazing means, the wind pressure loss can be reduced, and the efficiency is increased and the noise is reduced by increasing the air volume. Can be realized.

  Moreover, since the refrigerant | coolant subcooling part at the time of heating is arrange | positioned in the auxiliary heat exchanger 44 thermally interrupted with the main heat exchanger 40, it arises by the heat exchange of the refrigerant | coolants by the temperature difference with a refrigerant | coolant two phase part. It becomes possible to prevent heat loss. Further, since the number of refrigerant flow paths of the auxiliary heat exchanger 44 is smaller than the number of refrigerant flow paths of the main heat exchanger 40, the heat transfer performance is increased by increasing the flow rate of the liquid refrigerant (supercooling portion) having a low heat transfer coefficient. Can be improved.

In addition, as the degree of supercooling Sc (deg) during heating operation increases, the enthalpy difference at the entrance and exit of the heat exchanger increases and the heat exchange amount Q increases, but the total heat exchange of the supercooling section with poor heat transfer. The ratio to the vessel area increases, and the ratio of the refrigerant two-phase part with good heat transfer decreases.
The coefficient of performance COP of the cycle is expressed by COP = Q / W (W is the compressor input), and the compressor input becomes smaller as the heat transfer rate K of the heat exchanger increases. The heat transfer rate K is determined by the heat transfer coefficient in the heat transfer tube and the heat transfer coefficient on the air side. Therefore, the coefficient of performance COP is generally the highest in the air conditioner when the degree of supercooling Sc is about Sc = 5-15.

  FIG. 13 shows a flat-shaped heat exchange pipe 46 without an auxiliary heat exchanger, as opposed to a circular heat exchanger without an auxiliary heat exchanger (see FIG. 11), which is composed of a circular heat exchange pipe 46a. The ratio of the heat transfer rate K with respect to the degree of supercooling Sc (deg) of the flat tube heat exchanger (refer FIG. 12) is shown. In the flat tube heat exchanger without an auxiliary heat exchanger in this example, the degree of decrease in K when Sc increases is large compared to a circular tube heat exchanger without an auxiliary heat exchanger, and when Sc is small, K of the flat tube heat exchanger is larger than that of the circular tube heat exchanger, but as Sc is increased, K is lower than that of the circular tube heat exchanger. This is due to the fact that the ratio of the heat transfer coefficient in the tube between the two-phase region and the supercooling region of the flat tube heat exchanger is very large compared to the circular tube.

  On the other hand, FIG. 15 shows a flat tube heat exchanger having an auxiliary heat exchanger 44 according to the present embodiment, as opposed to a circular tube heat exchanger (see FIG. 14) having an auxiliary heat exchanger 44a composed of a circular tube. The ratio of the heat passage rate K to the degree of supercooling Sc (deg) is shown. In the flat tube heat exchanger in the present embodiment, the degree of decrease in K when Sc is larger than that of the circular tube heat exchanger is substantially equal to that of the circular tube. Further, in the flat tube heat exchanger of the present embodiment, K does not fall below the circular tube heat exchanger even if Sc increases. This is because the auxiliary heat exchanger (supercooling section) 44 of the flat tube heat exchanger has two passes and a smaller number of passes than the number of passes of the main heat exchanger 40, and the flow velocity in the pipe has increased. This is because the heat transfer coefficient in the tube has been greatly improved. Therefore, the effect of adding the auxiliary heat exchanger is greater than that of the circular tube heat exchanger.

  In the present embodiment, the case of the air-conditioning indoor unit has been shown, but the same effect can be obtained by the same configuration in the outdoor unit. In addition, the case where the heat exchange pipes 46 having a flat cross section are arranged in a grid arrangement is shown, but the same effect can be obtained even in a staggered arrangement.

Embodiment 4 FIG.
FIG. 16 schematically shows a cross section of an air conditioner according to a fourth embodiment of the present invention. This is an example in which the auxiliary heat exchanger 44 is arranged in the space on the suction side of the front upper heat exchanger 41. Others are the same as the structure of 3rd Embodiment, and the same effect is acquired.

Embodiment 5 FIG.
FIG. 17 schematically shows a cross section of an air conditioner according to a fifth embodiment of the present invention. The auxiliary heat exchanger 44a of the present embodiment includes a large number of fins 47 arranged in parallel with a narrow interval, and a heat exchange pipe having a circular cross section that penetrates the fins 47 and is joined by a pipe expanding means. 49. Others are the same as the structure of 3rd Embodiment, and the same effect is acquired.

Embodiment 6 FIG.
FIG. 18 schematically shows a cross section of an air conditioner according to a sixth embodiment of the present invention. The auxiliary heat exchanger 44a of the present embodiment includes a large number of fins 47 arranged in parallel with a narrow interval, and a heat exchange pipe having a circular cross section that penetrates the fins 47 and is joined by a pipe expanding means. 49, and is arranged in the space on the suction side upper portion of the front upper heat exchanger 41. Others are the same as the structure of 3rd Embodiment, and the same effect is acquired.

Embodiment 7 FIG.
FIG. 19 is a seventh embodiment of the present invention schematically showing the refrigerant piping system in the heat exchanger 26 of the air conditioner shown in FIG. The auxiliary heat exchanger 44 is formed with a single refrigerant flow path, and includes a bypass circuit 53 via a check valve 52 between the inlet and outlet. The main heat exchanger 40 in which the eight refrigerant paths are formed is connected to the auxiliary heat exchanger 44 through the refrigerant branching portion 51.

  The arrows in FIG. 19 indicate the flow of the refrigerant in the cooling operation. That is, during cooling, the refrigerant bypasses the auxiliary heat exchanger 44 from the outside, is introduced into the refrigerant branching portion 51 via the check valve 52, and is divided into a plurality of systems in the refrigerant branching portion 51 before main heat exchange. It is led to the container 40 (41, 42, 43). And after leaving the main heat exchanger 40, it joins and is guide | induced to the exterior. The refrigerant flow during heating is the reverse of that during cooling. That is, the refrigerant is divided into a plurality of systems from the outside during heating, and then introduced into the main heat exchanger 40. After leaving the main heat exchanger 40, the refrigerant is merged at the refrigerant branching portion 51 to the auxiliary heat exchanger 44. Led. At this time, the refrigerant does not flow into the bypass circuit 53 by the check valve 52.

  According to the present embodiment, the auxiliary heat exchanger 44 that is thermally shut off from the main heat exchanger 40 is provided with the refrigerant subcooling section during heating, and therefore the refrigerant due to the temperature difference from the refrigerant two-phase section. It is possible to prevent heat loss caused by heat exchange between the two. Moreover, since the refrigerant flow path of the auxiliary heat exchanger 44 is made into one system, the heat transfer performance can be improved by increasing the flow rate of the liquid refrigerant (supercooling part) having a low heat transfer coefficient.

  Further, during cooling, by bypassing the auxiliary heat exchanger 44 composed of one system of refrigerant flow path, it is possible to suppress an increase in refrigerant pressure loss in the heat exchange pipe. In addition, since the refrigerant can be equally distributed to a plurality of refrigerant flow paths in a state where the refrigerant dryness is small, uniform refrigerant distribution is possible. As a result, the heat exchange performance can be improved.

Embodiment 8 FIG.
FIG. 20 shows the arrangement of the air conditioner heat exchanger 26 (the main heat exchanger 40 and the auxiliary heat exchanger 44) and the blower 27 according to the eighth embodiment of the present invention. This is an example of a four-way blowout ceiling cassette type of a packaged air conditioner. FIG. 4A is a schematic top view, and FIG. 4B is a schematic side view.
In the figure, the heat exchanger 26 includes a main heat exchanger 40 and an auxiliary heat exchanger 44. The main heat exchanger 40 has a heat exchange pipe 46 with a flat cross section, and is arranged so as to surround the blower 27 via the header 31. The auxiliary heat exchanger 44 is disposed between the main heat exchanger 40 and the blower 27, that is, the whole or a part of the suction side of the main heat exchanger 40. The auxiliary heat exchanger 44 has the flat cross-section heat exchange pipe 46 or the circular cross-section heat exchange pipe 49 as in the first to fifth embodiments, so that the refrigerant becomes a refrigerant supercooling section during heating. A flow path is arranged.

  Also. This heat exchanger 26 is arranged so as to surround the blowout side of the blower 27 of the turbofan. The blower 27 sucks room air from below through a suction grille / prefilter (both not shown), and blows it out toward the heat exchanger 26 in the radial direction. The air that has passed through the heat exchanger 26 is blown into the room through a blowout air passage (not shown).

  Since it comprised in this way, the effect similar to the said Embodiment 1-7 is acquired also in this Embodiment.

The schematic block diagram of the heat exchanger which shows Embodiment 1 of this invention. The BB expanded sectional view of FIG. CC expanded sectional view of FIG. The right enlarged side view of the heat exchanger shown in FIG. The schematic block diagram of the heat exchanger which shows Embodiment 2 of this invention. The DD expanded sectional view of FIG. EE expanded sectional view of FIG. The right expanded side view of the heat exchanger shown in FIG. Sectional drawing of the air conditioner which shows Embodiment 3 of this invention. The refrigerant | coolant piping system diagram of the heat exchanger in Embodiment 3 of this invention. Sectional drawing of the air conditioner by the circular pipe heat exchanger without an auxiliary heat exchanger. Sectional drawing of the air conditioner by the flat tube heat exchanger without an auxiliary heat exchanger. The characteristic comparison figure of the said circular tube heat exchanger and a flat tube heat exchanger. Sectional drawing of the air conditioner which comprises the circular pipe heat exchanger with an auxiliary heat exchanger. The characteristic comparison figure of the heat exchanger of Embodiment 3 of this invention and the circular tube heat exchanger of FIG. Sectional drawing of the air conditioner which shows Embodiment 4 of this invention. Sectional drawing of the air conditioner which shows Embodiment 5 of this invention. Sectional drawing of the air conditioner which shows Embodiment 6 of this invention. The refrigerant | coolant piping system diagram of the heat exchanger which shows Embodiment 7 of this invention. The top view and side view of an air conditioner which show Embodiment 8 of this invention.

Explanation of symbols

1a, 1b, 1c, 1d1, 1d2, 2a1, 2a2, 2b, 2c, 2d1, 2d2, 3a1, 3a2, 3b, 3c, 3d1, 3d2, 4a1, 4a2, 4b, 4c, 4d Heat transfer tube group or refrigerant flow path Group, 1A, 1B, 1C, 1D, 2A, 2B, 2C, 2D, 3A, 3B, 3C, 3D, 4A, 4B, 4C, 4D flat heat transfer tube group, 5 fin, 11 airflow direction, 12 first header , 12a to 12h Header chamber, 13 Second header, 13a, 13b, 13c1, 13c2, 13d, 13e1, 13e2, 13f, 13g1, 13g2, 13h, 13i Header chamber, 14 Partition plate, 14a Flat partition plate, 14b Step-like partition plate, 15 partition plate, 15a flat plate-like partition plate, 15b I-shaped partition plate, 21 air conditioner body, 40 main heat exchanger, 41 Upper surface heat exchanger, 42 Front lower heat exchanger, 43 Back heat exchanger, 44 Auxiliary heat exchanger, 45 fins, 46 cross section flat heat exchange pipe, 47 fins, 48 cross section flat heat exchange pipe, 49 cross section circle Shape heat exchange pipe, 51 refrigerant branch, 52 check valve, 53 bypass circuit.

Claims (10)

A plurality of fins arranged in parallel along the airflow direction;
A plurality of heat transfer tube groups that are arranged in a direction orthogonal to the fins and in which the refrigerant flows; and a first header and a second header that are each divided into a plurality of header chambers by partition plates. In the heat exchanger,
The header chamber of the second header to which the heat transfer tube group at the refrigerant inflow position of the second header is connected, the heat transfer tube group at the refrigerant inflow position of the second header, the heat transfer tube group at the refrigerant inflow position of the second header, and the middle first header header chamber connected to the tube bank position, tube bank of intermediate positions, two second header header chamber connected to the tube bank of the middle position, tube bank of the intermediate position, the intermediate position first header header chamber connected to the tube bank of the refrigerant outflow position of the heat transfer tube group and the second header, the tube bank of the refrigerant outflow position of the second header, a refrigerant outflow position of the second header A plurality of refrigerant circuits configured by sequentially connecting the header chambers of the second header connected to the heat transfer tube group;
The first header and the second header are provided such that each longitudinal direction is orthogonal to the airflow direction,
The heat exchanger is configured such that the heat transfer tube group at the refrigerant inflow position of the second header and the heat transfer tube group at the refrigerant outflow position of the second header having different refrigerant circuits are adjacent to each other in the airflow direction. A plurality of fins arranged in parallel along the airflow direction;
A plurality of heat transfer tube groups that are arranged in a direction orthogonal to the fins and in which the refrigerant flows, and are connected to one end of the plurality of heat transfer tube groups and partitioned by two types of partition plates, a flat plate shape and a step shape A first header having a plurality of header chambers,
A second header having a plurality of header chambers connected to the other ends of the plurality of heat transfer tube groups and partitioned by a flat plate shape and an I-shaped partition plate;
The first header includes a portion to which a heat transfer tube group partitioned in the step direction and the windward side of the airflow is connected by the stepped partition plate, and a heat transfer tube partitioned only in the step direction by the flat partition plate. A first header chamber composed of a portion to which a group is connected, a portion to which a heat transfer tube group partitioned in the step direction and the leeward side of the airflow is connected by the step-like partition plate, and the flat partition plate And a second header chamber composed of a portion to which a heat transfer tube group partitioned only in the step direction is connected,
The second header includes a third header chamber partitioned only by the flat partition plate, and the heat transfer tube group on the windward side and leeward side of the airflow by the flat plate shape and the I-shaped partition plate. Two divided header chambers, a fourth header chamber which is a leeward header chamber, and a fifth header chamber which is a leeward header chamber;
The first header and the second header are heat exchangers provided such that each longitudinal direction is orthogonal to the air flow direction,
When the heat exchanger is used as a condenser, the fifth header chamber, a portion where the leeward heat transfer tube group of the second header chamber is connected, and the compartment in only the step direction of the second header chamber A portion to which the heat transfer tube group is connected, a third header chamber, a portion to which the heat transfer tube group partitioned only in the step direction of the first header chamber is connected, and the windward side of the first header chamber The refrigerant flows sequentially through the heat transfer tube group to the portion where the heat transfer tube group is connected to the fourth header chamber,
Or, when used as an evaporator, the fourth header chamber, the portion to which the upwind heat transfer tube group of the first header chamber is connected, and is partitioned only in the step direction of the first header chamber. The portion to which the heat transfer tube group is connected, the third header chamber, the portion to which the heat transfer tube group partitioned only in the step direction of the second header chamber is connected, and the windward transfer of the second header chamber. A plurality of refrigerant circuits configured such that the refrigerant flows sequentially through the heat transfer tube group to the portion to which the heat tube group is connected, to the fifth header chamber;
The heat exchanger, wherein the fifth header chamber of one refrigerant circuit and the fourth header chamber of another refrigerant circuit are arranged adjacent to each other in the airflow direction. A plurality of fins arranged in parallel along the airflow direction;
A flat heat transfer tube group having a flat cross section having a plurality of refrigerant flow paths arranged in a direction orthogonal to the fins and through which the refrigerant flows;
In a heat exchanger having a first header and a second header that are each divided into a plurality of header chambers by a partition plate,
A header chamber of the second header to which a flat heat transfer tube at the refrigerant inflow position of the second header is connected, a flat heat transfer tube at the refrigerant inflow position of the second header, and a flatness of the refrigerant inflow position of the second header -Shaped heat transfer tube and a header chamber of a first header connected to a flat heat transfer tube at an intermediate position, a flat heat transfer tube at an intermediate position, and a second header connected to two flat heat transfer tubes at an intermediate position the header chamber, flat heat transfer tubes of the intermediate position, the first header of the header chamber connected to the flat shape flat heat exchanger tube of the outflow position of the heat transfer tube and the second header of the intermediate position, the second flat heat transfer tube of the outflow position of the header, the second header of the flat of the second header of the header chamber connected to the heat transfer tubes of the refrigerant outflow position, a refrigerant circuit constituted by successively connecting the city Multiple
The first header and the second header are provided such that each longitudinal direction is orthogonal to the airflow direction,
The flat heat transfer tube at the refrigerant inflow position of the second header and the flat heat transfer tube at the refrigerant outflow position of the second header having different refrigerant circuits are adjacent to each other in the airflow direction. Heat exchanger. A plurality of fins arranged in parallel along the airflow direction;
A flat heat transfer tube group having a flat cross section having a plurality of refrigerant flow paths arranged in a direction orthogonal to the fins and through which the refrigerant flows;
A first header having a plurality of header chambers connected to one end of the flat heat transfer tube group and partitioned by two types of flat plate and step-like partition plates, and connected to the other end of the flat heat transfer tube group A second header having a plurality of header chambers partitioned in a step direction by a flat plate shape and an I-shaped partition plate;
The header chamber of the first header is formed in the step direction by the step-like partition plate to which the flat heat transfer tube group partitioned in the step direction and the windward side of the airflow is connected, and the flat partition plate. A first header chamber composed of a portion to which the flat heat transfer tube group partitioned only is connected, and the flat heat transfer tube group partitioned in the step direction and the leeward side of the airflow by the step-shaped partition plate. A second header chamber comprising a connected portion and a portion to which the flat heat transfer tube group partitioned only in the step direction by the flat partition plate is connected;
The second header includes a third header chamber partitioned only by the flat partition plate, and the flat heat transfer tube group by the flat plate and the I-shaped partition plate. Two header chambers divided into a fourth header chamber, which is a leeward header chamber, and a fifth header chamber, which is a leeward header chamber,
The first header and the second header are heat exchangers provided such that each longitudinal direction is orthogonal to the air flow direction,
When used as a condenser, the fifth header chamber, a portion to which a flat heat transfer tube group on the leeward side of the second header chamber is connected, a flat section partitioned only in the step direction of the second header chamber A portion to which the heat transfer tube group is connected, a third header chamber, a portion to which the flat heat transfer tube group partitioned only in the step direction of the first header chamber is connected, and the wind of the first header chamber The refrigerant flows sequentially through the flat heat transfer tube group to the portion where the upper flat heat transfer tube group is connected, to the fourth header chamber,
Alternatively, when used as an evaporator, the fourth header chamber, a portion to which the windward flat heat transfer tube group of the first header chamber is connected, and only the step direction of the first header chamber is partitioned. A portion to which the flat heat transfer tube group formed is connected, a third header chamber, a portion to which the flat heat transfer tube group partitioned only in the step direction of the second header chamber is connected, and the second header chamber A portion to which the flat heat transfer tube group on the windward side is connected, a plurality of refrigerant circuits through which the refrigerant flows sequentially through the flat heat transfer tube group to the fifth header chamber,
A heat exchanger, wherein a fifth header chamber of one refrigerant circuit and a fourth header chamber of another refrigerant circuit are arranged adjacent to each other in the airflow direction. A plurality of fins arranged in parallel along the airflow direction;
A plurality of heat transfer tube groups that are arranged in a direction orthogonal to the fins and in which the refrigerant flows; and a first header and a second header that are each divided into a plurality of header chambers by partition plates. In the heat exchanger,
The header chamber of the second header to which the heat transfer tube group at the refrigerant inflow position of the second header is connected, the heat transfer tube group at the refrigerant inflow position of the second header, the heat transfer tube group at the refrigerant inflow position of the second header, and the middle first header header chamber connected to the tube bank position, tube bank of intermediate positions, two second header header chamber connected to the tube bank of the middle position, tube bank of the intermediate position, the intermediate position first header header chamber connected to the tube bank of the refrigerant outflow position of the heat transfer tube group and the second header, the tube bank of the refrigerant outflow position of the second header, a refrigerant outflow position of the second header A plurality of refrigerant circuits configured by sequentially connecting the header chambers of the second header connected to the heat transfer tube group;
The first header and the second header are provided such that each longitudinal direction is orthogonal to the airflow direction,
The second header connected to the heat transfer tube group at the refrigerant outflow position of the second header, the refrigerant circuit of which is different from the header chamber of the second header to which the heat transfer tube group at the refrigerant inflow position of the second header is connected. A heat exchanger configured to be adjacent to the header chamber in the airflow direction.   The heat exchanger according to claim 3 or 4, wherein the flat heat transfer tube group is joined to the fins by brazing means.   An air conditioner, wherein the heat exchanger according to any one of claims 1 to 6 is a main heat exchanger, and an auxiliary heat exchanger is disposed on the air suction side of the main heat exchanger.   The auxiliary heat exchanger includes a plurality of fins arranged side by side with a narrow interval, and a heat passing through these fins and joined by brazing means, and has a flat cross section and a plurality of refrigerant flow paths. The air conditioner according to claim 7, comprising an exchange pipe.   The auxiliary heat exchanger is composed of a large number of fins arranged in parallel with a narrow interval, and a heat exchange pipe having a circular cross section that is penetrated through these fins and joined by a pipe expanding means. The air conditioner according to claim 7.   The air conditioner according to any one of claims 7 to 9, wherein the number of refrigerant channels of the auxiliary heat exchanger is smaller than the number of refrigerant channels of the main heat exchanger.

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