JP5171983B2 - Heat exchanger and refrigeration cycle apparatus - Google Patents

Description

  The present invention relates to a fin tube type heat exchanger and a refrigeration cycle apparatus using the same, for example.

  As a conventional heat exchanger, separators are installed in the headers provided at both ends of the flat tube so that the refrigerant flows in parallel to the plurality of flat tubes, the flow rate of the refrigerant is changed by the separator, and the performance of the heat exchanger is improved. Some have improved.

JP 2004-239598 A (page 6-7, FIG. 1)

  In the above-described conventional heat exchanger, it is difficult to locally control the drying of the refrigerant for an air conditioner, and the header interferes when the bent form of the heat exchanger is used like a room air conditioner. There is a problem that the heat exchanger itself must be made small.

  The present invention has been made to solve the above-described problems, and has optimized a heat exchanger path configuration using a flat tube and used a heat exchanger having a sufficiently balanced refrigerant path and the heat exchanger. An object is to provide a refrigeration cycle apparatus.

  The heat exchanger according to the present invention is configured by disposing an auxiliary heat exchanger and a main heat exchanger that are stacked in the fluid flow direction on the front upper side, the lower front side, and the rear side in the casing, respectively. The auxiliary heat exchanger and the main heat exchanger are inserted in the plate fins stacked in the direction perpendicular to the fluid flow direction, and the plate fin stacking direction. The auxiliary heat exchanger and the main heat exchanger arranged on the front upper side and the auxiliary heat exchanger arranged on the lower front side have one end as a heat transfer tube. Main heat is used in which a flat tube bent in a U-shape is used, and a U-shaped connecting tube is provided at the other end of one side of the flat tube adjacent to each other, and arranged on the lower front side and the back side. In the exchanger, a flat tube is used as the heat transfer tube, and one end of the flat tube is used. A first header having a partition plate is provided at the center of the part, a second header having a hollow structure is provided at the other end, and two pipe connection ports for entering and exiting the refrigerant with the partition plate as a boundary on the first header. Is provided.

  According to the present invention, one end of the auxiliary heat exchanger and the main heat exchanger arranged on the upper front side and the auxiliary heat exchanger arranged on the lower front side is bent into a U shape as a heat transfer tube. A flat tube is used, and a U-shaped connecting tube is provided at the other end of the flat tube adjacent to each other. In addition, a flat tube is used as a heat transfer tube in the main heat exchanger disposed on the lower front side and the rear side, and a first header having a partition plate in the center of the inside is provided at one end of the flat tube. A hollow second header is provided at the end, and two pipe connection ports for entering and exiting the refrigerant are provided in the first header with a partition plate as a boundary. Thereby, interference in the fluid flow direction of the heat exchanger is eliminated, and the space can be reduced without reducing the size of the heat exchanger. Moreover, since interference between headers can be eliminated, the heat transfer area can be increased, drying of the refrigerant can be suppressed, and heat exchange performance can be improved. In addition, since the main heat exchanger disposed on the lower front side and the rear side includes the first and second headers, variation in the flow rate of the liquid refrigerant can be suppressed.

FIG. 3 is a side view showing the configuration of the heat exchanger according to the first embodiment. Sectional drawing of the flat tube used for Embodiment 1. FIG. The top view of the hairpin of a flat tube which expands and shows a part of heat exchanger seen from the back surface in the side view of FIG. The side view of the hairpin shown in FIG. The external view and sectional drawing of the joint pipe | tube which couple | bond the flat pipe | tube shown in FIG. 1 and circular refrigerant | coolant piping. The side view which shows the structure of the bulge 3 way pipe shown in FIG. The front view and sectional drawing of one header which show the main heat exchanger of the front lower part side, and the main heat exchanger installed in the 2nd row of the back side. The front view and sectional drawing of the other header of the main heat exchanger shown in FIG. The top view which shows the whole main heat exchanger installed in the 2nd row | line | column on the lower surface side main heat exchanger and back side. The top view which shows the whole main heat exchanger installed in the 3rd row | line | column on the back side. FIG. 4 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to Embodiment 2.

Embodiment 1 FIG.
FIG. 1 is a side view showing the configuration of the heat exchanger according to the first embodiment.
In FIG. 1, the heat exchanger of this Embodiment is mounted in the indoor unit 100 attached to an indoor wall, for example. In the indoor unit 100, an air conditioner grill 102 for taking in indoor air is provided at the upper part of the casing 101, and a louver 105 for opening and closing the outlet 104 is provided at the lower front part of the casing 101. In the casing 101, heat exchange is performed by arranging an auxiliary heat exchanger and a main heat exchanger, which are stacked in the direction of the air flow, which is a fluid, on the front upper side, the lower front side, and the rear side, respectively. And a cross-flow fan 103 are provided. The cross-flow fan 103 sucks indoor air from the air conditioner grille 102 and sends cooling air or hot air passing through each of the heat exchangers described above into the room from the outlet 104.

  On the upper front side, an auxiliary heat exchanger 11b and main heat exchangers 11d and 11e are sequentially installed from the upstream side of the air flow. On the upper front side, an auxiliary heat exchanger 11c and main heat exchangers 11h and 11i are sequentially installed from the upstream side of the air flow. Further, on the back side, the auxiliary heat exchanger 11a and the main heat exchangers 11f and 11g are sequentially installed from the upstream side of the air flow in the same manner as described above.

  The auxiliary heat exchanger 11a on the back side includes a plate-like fin 2 laminated with a gap in a direction orthogonal to the air flow direction, and, for example, two U-shaped pieces inserted into the plate-like fin 2 in the lamination direction. The circular tube 1b has a shape and a U-shaped connecting circular tube 1c (solid line) that connects the ends of one side of each circular tube 1b adjacent to each other.

  The auxiliary heat exchanger 11b on the upper front side and the auxiliary heat exchanger 11c on the lower front side have a plate-like fin 2 laminated with a gap in the direction orthogonal to the air flow direction, and For example, four flat tubes 1a inserted into the fins 2 in the laminating direction and arranged in the longitudinal direction of the plate-like fins 2 and bent into a U shape by hairpins 5 (broken lines), and adjacent one side of each flat tube 1a An interstage U-bend 8 (solid line), which is a U-shaped connecting pipe that connects each end portion, is provided.

  The main heat exchangers 11d and 11e on the upper front side have plate-like fins 2 stacked in a direction perpendicular to the air flow direction, and are inserted in the plate-like fins 2 in the stacking direction and arranged in the longitudinal direction of the plate-like fins 2. For example, four flat tubes 1a bent into a U shape by hairpins 5 (broken lines) are provided. The main heat exchanger 11e in the third row is shifted in the longitudinal direction of the plate-like fins 2 with respect to the main heat exchanger 11d in the second row, and both flat tubes 1a are arranged in a staggered manner.

  When the two flat tubes 1a on the upper right side of the flat tubes 1a of the auxiliary heat exchanger 11b and the main heat exchangers 11d and 11e are the first, the first of the main heat exchangers 11d and 11e and The outer ends of the fourth flat tube 1a are connected by an inter-row U bend 4 and the one end portions of both the second and third flat tubes 1a are connected by an inter-row U bend 4. ing. Further, the one end of the third flat tube 1a of the auxiliary heat exchanger 11b, the first end of the second row main heat exchanger 11d, and the one end of each of the second flat tubes 1a are bulge three-way tubes 3. And the one end of the fourth flat tube 1a of the auxiliary heat exchanger 11b, the third end of the main heat exchanger 11d in the second row, and the one end of each of the fourth flat tubes 1a. They are connected by a bulge 3 way pipe 3.

  Further, one end of each of the first and second flat tubes 1a of the main heat exchanger 11e in the third row is connected by a bulge three-way tube 3 and each of the third and fourth flat tubes 1a is connected. One end is connected by a bulge three-way pipe 3. These two bulge three-way pipes 3 are connected to the three-way pipe 6 via refrigerant pipes 25 and 26. Further, the three-way pipe 6 is connected to a reheat valve 10 via a refrigerant pipe, and the reheat valve 10 is connected to a distributor 9.

  The main heat exchangers 11h, 11i on the lower front side and the main heat exchangers 11f, 11g on the rear side are formed of a plate-like fin 2 laminated with a gap in a direction orthogonal to the air flow direction, For example, eight flat tubes 1a inserted into the fins 2 in the stacking direction and arranged in the longitudinal direction of the plate-like fins 2, and headers 7 and 14 (first and second headers) connected to both ends of each flat tube 1a ). The header 7 on one side is provided with a partition plate 13 which will be described later.

  The main heat exchangers 11i in the third row on the lower front side are arranged so as to be arranged in a staggered manner with the flat tubes 1a of the main heat exchanger 11h in the second row. The main heat exchanger 11g in the third row on the back side is arranged so as to be arranged in a staggered manner with the flat tubes 1a of the main heat exchanger 11f in the second row. Each header 7 of the main heat exchanger 11h in the second row on the lower front side and the main heat exchanger 11f in the second row on the rear side is connected to the distributor 9 via the refrigerant pipes 28 and 29. .

  The pitch Fp in the stacking direction of the plate-like fins 2 of the main heat exchangers 11f, 11g · 11d, 11e · 11h, and 11i is Fp = 0.0012m, the fin thickness Ft is Ft = 0.0001m, and the fin width L in the airflow direction L = 0.0127 m. The distance Dp between the centers of the flat tubes 1a arranged in the longitudinal direction is Dp = 0.01425m. The main heat exchangers 11f, 11g · 11d, 11e · 11h, 11i are arranged in two rows in the direction of the air flow, and the fins are divided for each row.

  The auxiliary heat exchanger 11a on the back side has a pitch Fp in the stacking direction of the plate-like fins 2 of Fp = 0.0013 m, a fin thickness Ft of Ft = 0.0001 m, and a fin width L in the direction of air flow is L = 0.0127 m. is there. The distance Dp between the centers of the circular tubes 1b arranged in the longitudinal direction of the plate-like fins 2 is Dp = 0.0204m. In the circular tube 1b, the fin collar and the circular tube 1b are brought into pressure contact with each other up to the fin front edge portion by mechanical expansion.

  Further, the auxiliary heat exchanger 11b on the front upper side and the auxiliary heat exchanger 11c on the lower front side have a pitch Fp in the stacking direction of the plate-like fins 2 of Fp = 0.0012 m, a fin thickness Ft of Ft = 0.0001 m, and air The fin width L in the flow direction is L = 0.0127 m. The distance Dp between the centers of the flats 1a arranged in the longitudinal direction of the plate-like fins 2 is Dp = 0.01425 m 2.

  The flat tube 1a and the circular tube 1b described above are formed by extrusion processing made of aluminum alloy, and the plate-like fins 2 are formed of a plate material made of aluminum alloy. Thus, the proof stress of corrosion improves by making all the heat exchangers into the same material. Further, by arranging the flat tubes 1a in a staggered manner in the main heat exchangers 11f, 11g, 11d, 11e, 11h, and 11i, the heat transfer coefficient on the front edge side (windward side) of the flat tubes 1a is improved and heat exchange is performed. The performance of the vessel is improved.

  Moreover, the main heat exchangers 11f, 11g, 11d, 11e, 11h, and 11i are divided into two rows to divide the plate-like fins 2, so that the arrangement of the heat exchangers can be variously accommodated in the casing 101, and the air flow An improvement in the heat transfer coefficient due to the leading edge effect (the effect of dividing the air boundary layer) in the plate-like fins 2 of the third row of main heat exchangers 11g, 11e, 11i located on the downstream side can be expected.

  Next, the structure of the flat tube 1a, the hairpin 5, the joint tube 12, and the bulge three-way tube 3 will be described.

FIG. 2 is a cross-sectional view of a flat tube used in the first embodiment.
The flat tube 1a has, for example, a length a1 in the major axis direction of 11 mm and a length a2 in the minor axis direction of 4 mm, and a groove a3 extending in the axial direction is provided on the inner surface of the flat tube 1a. This is to promote heat transfer.

3 is a plan view of a hairpin of a flat tube showing a part of the heat exchanger as seen from the back side in the side view of FIG. 1, and FIG. 4 is a side view of the hairpin shown in FIG.
The hairpin 5 is obtained by bending the flat tubes 1a of the auxiliary heat exchangers 11b and 11c arranged on the upper front side and the lower front side and the main heat exchangers 11d and 11e arranged on the upper front side into a U shape. It is. Thereby, since a refrigerant | coolant flow path can be comprised without using refrigerant | coolant piping, the width | variety of the fin lamination direction of each heat exchanger can be made small.

FIG. 5 is an external view and a cross-sectional view of a joint pipe connecting the flat pipe and the circular refrigerant pipe shown in FIG.
The joint pipe 12 includes a flat tube portion 2a that is coupled to the flat tube 1a (see FIG. 2), and a circular tube portion 12b that is coupled to a refrigerant pipe having a diameter of φ6, for example. When the refrigerant flows from the joint tube 12 to the flat tube 1a, the refrigerant is divided into four holes formed in the flat tube 1a.

  When connecting each end of the adjacent flat tube 1a with the interstage U-bend 8, the joint tube 12 is coupled to each end of the flat tube 1a, and both the joint tubes 12 are connected to the interstage U-bend 8 with each other. Join with. Moreover, when connecting each end part of the flat tube 1a of the main heat exchangers 11d and 11e by the inter-row U-bend 4, a joint tube 12 is connected to each end part of the flat tube 1a, and both joints are connected. Tubes 12 are joined with inter-row U-bends 4.

FIG. 6 is a side view showing the configuration of the bulge 3-way pipe shown in FIG.
The bulge three-way tube 3 includes a flat U-shaped tube 3a bent in a U-shape and a flat horizontal tube 3b extending at right angles from a tube on one side of the U-shaped tube 3a. When connecting the three flat tubes 1a using the bulge three-way tube 3, each of the two flat tubes 1a arranged in the longitudinal direction of the U-shaped tube 3a of the bulge three-way tube 3 and the plate-like fins 2 is provided. The ends are connected, the horizontal pipe 3b of the bulge three-way pipe 3 and the joint pipe 12 are connected, and one end of the refrigerant pipe 24 is connected to the joint pipe 12 and the other end of the refrigerant pipe 24 is connected. It connects with the 3rd flat tube 1a through another joint pipe 12 couple | bonded with the part.

Next, configurations of the main heat exchangers 11h and 11i on the lower front side and the main heat exchangers 11f and 11g on the rear side will be described.
FIG. 7 is a front view and a cross-sectional view of one header showing a main heat exchanger on the lower front side and a main heat exchanger installed in the second row on the back side, and FIG. 8 is a view of the main heat exchanger shown in FIG. FIG. 9 is a plan view showing the entire main heat exchanger installed in the second row on the rear side and the main heat exchanger on the lower side on the front side, and FIG. It is a top view which shows the whole main heat exchanger installed in the row | line | column.

  Each header 7 of the main heat exchangers 11h, 11i on the lower front side and the main heat exchanger 11f on the rear side is composed of a rectangular box extending in the arrangement direction of the flat tubes 1a, as shown in FIG. A partition plate 13 for separating the inflow and outflow of the refrigerant is provided inside. For example, eight flat tubes 1 a connected to the header 7 are divided into four pieces each by the partition plate 13. In addition, a pipe connection port 16 serving as a refrigerant inlet and a pipe connection port 17 serving as a refrigerant outlet are provided on one side of the header 7 with the partition plate 13 as a boundary.

  The other header 14 is formed of a rectangular box similar to the header 7 described above, and is connected with eight flat tubes 1 a connected to the header 7. The inside of the header 14 has a hollow structure. As shown in FIG. 10, the main heat exchanger 11g on the back side has a pipe connection port 17 serving as a refrigerant outlet at a position close to the partition plate 13 of the header 7. The same as the exchanger 11h and the like.

  As described above, the pipe connection port 16 of the main heat exchanger 11h on the lower front side is connected to the distributor 9 via the refrigerant pipe 28, and the pipe connection port 17 is connected via the U-bend 4 between the rows of circular tubes. It is connected to the pipe connection port 16 of the main heat exchanger 11i in the third row. The pipe connection port 16 of the main heat exchanger 11f on the back side is connected to the distributor 9 via the refrigerant pipe 29, and the pipe connection port 17 is connected to the third row via the U-bend 4 between the rows of circular tubes. Is connected to the pipe connection port 16 of the main heat exchanger 11g.

The flow of the refrigerant when used as an evaporator in the heat exchanger configured as described above will be described with reference to FIG.
When the heat exchanger of the present embodiment is used as an evaporator, the refrigerant flows into the refrigerant pipe 21 through the circular pipe 1b of the back side auxiliary heat exchanger 11a, and is divided into two directions by the three-way pipe 6. Is done. One refrigerant from the three-way pipe 6 flows into the auxiliary heat exchanger 11b on the upper front side from the direction of gravity, and passes from the sixth flat pipe 1a to the second row main heat exchanger 11d through the refrigerant pipe 24. It flows to one bulge 3 way pipe 3.

  The other refrigerant from the three-way pipe 6 flows into the auxiliary heat exchanger 11c on the lower front side from below in the gravitational direction, passes through the flat tube 1a and enters the auxiliary heat exchanger 11b on the upper front side in the lower gravitational direction. From the 7th stage flat tube 1a and flows to the other bulge 3 way tube 3 on the second row main heat exchanger 11d.

  The refrigerant that has flowed into one of the bulge three-way pipes 3 on the main heat exchanger 11d flows from the first flat pipe 1a into the third row main heat exchanger 11e through the inter-row U-bend 4 from the direction of gravity. At the same time, the fourth flat tube 1a flows into the fourth flat tube 1a of the same main heat exchanger 11e via the inter-row U-bend 4. In addition, the refrigerant that has flowed to the other bulge three-way pipe 3 on the main heat exchanger 11d passes through the inter-row U-bend 4 from the fifth flat pipe 1a to the fifth main heat exchanger 11e. While flowing into the flat tube 1a, it flows into the eighth flat tube 1a of the same main heat exchanger 11e via the inter-row U-bend 4 from the eighth flat tube 1a.

  The respective refrigerants flowing into the first and fourth flat tubes 1a of the third row of main heat exchangers 11e join together through the bulge three-way tube 3 and flow to the three-way tube 6 through the refrigerant pipe 25. Further, the respective refrigerants flowing into the fifth and eighth flat tubes 1a of the same main heat exchanger 11e are joined by the bulge three-way tube 3 and flow to the three-way tube 6 through the refrigerant pipe 26, Merge with the previous refrigerant. The refrigerant from the three-way pipe 6 flows into the reheat valve 10 through the refrigerant pipe 27, flows into the distributor 9 installed with the refrigerant flow direction perpendicular to the direction of gravity, and is distributed in two directions.

  One refrigerant that has flowed out of the distributor 9 flows into the header 7 of the main heat exchanger 11h on the lower front side through the refrigerant pipe 28, and the other refrigerant passes through the refrigerant pipe 29 and passes through the main pipe on the rear side. It flows into the header 7 of the heat exchanger 11f. The refrigerant that has flowed into the header 7 of the main heat exchanger 11h on the lower front side flows into the four flat tubes 1a by the partition plate 13 in the header 7 as shown by an arrow 15 in FIG. It flows in the direction opposite to the direction of gravity in the header 14 having a hollow structure, passes through the remaining four flat tubes 1a, and returns to the header 7 (see FIG. 8). Then, the refrigerant flows into the main heat exchanger 11i in the third row via the inter-row U-bend 4 as indicated by an arrow 15 in FIG. 9, and four flat tubes are formed by the partition plate 13 in the header 7. It flows into la, flows in the direction of gravity by a header 14 having a hollow structure arranged opposite to it, passes through the remaining four flat tubes 1a, returns to the header 7, and reaches the pipe connection port 17 of the refrigerant outlet.

  The refrigerant that has flowed into the header 7 of the main heat exchanger 11f on the back side flows into the four flat tubes 1a by the partition plate 13 in the header 7 as shown by the arrow 15 in FIG. It flows in the direction opposite to the direction of gravity in the header 14 of the structure, passes through the remaining four flat tubes 1a, and returns to the header 7. Then, as indicated by an arrow 15 shown in FIG. 10, the refrigerant flows into the main heat exchanger 11 g in the third row through the inter-row U bend 4, and four flat tubes are formed by the partition plate 13 in the header 7. It flows into la, flows in the direction of gravity by a header 14 having a hollow structure arranged opposite to it, passes through the remaining four flat tubes 1a, returns to the header 7, and reaches the pipe connection port 17 of the refrigerant outlet.

  When the heat exchanger according to the present embodiment is used as a condenser, the refrigerant flows in the opposite direction, and the main heat exchanger in the third row on the back side and the lower front side where the pipe connection port 16 is installed. 11g and 11i are overheated and saturated, and the main heat exchangers 11f and 11h in the second row on the rear side and the lower front side and the main heat exchangers 11d and 11e on the upper front side are saturated and three rear auxiliary The heat exchangers 11a, 11b, and 11c are supercooled.

As described above, in the present embodiment, the following effects are obtained.
(1) In the main heat exchangers 11d, 11e, 11h, 11i, 11f, and 11g having the headers 7 and 14 on both sides, the refrigerant flows into the flat tube 1a between the headers by the partition plate 13 provided on the header 7. Can be performed in half, and variations in the flow rate of the liquid refrigerant can be suppressed. Moreover, the management in manufacture can be made easy by making the branch number (4) of the flat tube 1a into half of the whole number (8).

(2) In the main heat exchanger 11g in the third row on the back side, the wind speed is small and the thermal load is small compared to the direction opposite to the direction of gravity. By setting the position of the refrigerant outlet as high as possible with respect to the direction of gravity as much as possible, the amount of refrigerant circulation above the direction of gravity can be increased, the amount of refrigerant circulation below can be reduced, and the drying of the refrigerant can be balanced.

(3) In the main heat exchangers 11d and 11e on the upper front side, piping is performed using the bulge three-way pipe 3 and the inter-row U bend 4, the inter-stage U bend 8 and the joint pipe 12. Since the headers 7 and 14 are used for the main heat exchangers 11h, 11i, 11f, and 11g on the side, there is no interference in the direction of the air flow, and the space can be reduced.

(4) When used as an evaporator, on the downstream side of the reheat valve 10 where the dryness of the refrigerant is large, the pressure loss in the pipe is large and it is necessary to increase the number of passes. The piping space can be reduced by flowing in parallel. Moreover, since the header chamber is made small by using the partition plate 13 in the header 7, the behavior of the liquid refrigerant in the header 7 can be reduced, and the heat exchangers 11i and 11g in the third row on the lower front side and the rear side are arranged. The refrigerant distribution inside can be improved.

(5) In the main heat exchangers 11d and 11e on the front upper side, in the upstream heat exchange with a small number of passes and a low dryness, the refrigerant is distributed using the joint pipe 12 and the three-way pipe 6; And the interference of the headers 7 and 14 due to the bent heat exchange mode of the main heat exchangers 11h, 11i, 11f, and 11g on the back side can be suppressed.

(6) The flat tubes 1a are used for the auxiliary heat exchangers 11b and 11c on the front upper side and the lower front side, and the circular tube 1b is used for the auxiliary heat exchanger 11a on the rear side. By increasing the in-pipe cross-sectional area of the auxiliary heat exchanger 11a on the back side used as a variation in the degree of supercooling due to the change in the refrigerant amount. In addition, since the wind speed on the back side is lower than that on the front side, the temperature efficiency can be made uniform by using a circular tube having a small heat exchange capacity on the back side.

(7) In the main heat exchangers 11h, 11i, 11f, and 11g on the lower front side and the rear side, the headers in the second row and the third row are connected by the U bend 4, but the fluctuation of the liquid refrigerant and the wind speed Since the position of the U-bend 4 can be changed according to the heat addition caused by the distribution, the refrigerant distribution characteristics can be made appropriate.

Embodiment 2. FIG.
FIG. 11 is a refrigerant circuit diagram of the refrigeration cycle apparatus according to Embodiment 2.
The refrigerant circuit shown in the figure includes a compressor 33, a condensing heat exchanger 34, an expansion device 35, an evaporating heat exchanger 36, a blower 37, a blower motor 38, and the like. By using the heat exchanger according to the first embodiment for the condensation heat exchanger 34 or the evaporating heat exchanger 36 or both in the above-described embodiment, a highly efficient refrigeration cycle apparatus can be realized.

Here, energy efficiency is comprised by following Formula.
Heating energy efficiency = indoor heat exchanger (condenser) capacity / total input Cooling energy efficiency = indoor heat exchanger (evaporator) capacity / total input

  Note that the HCFC (R22) and HFC (R116, R125, R134a, R14, R143a, R152a, R227ea, R23, R236ea, R236fa, and the HCFC (R22) and the refrigeration cycle apparatus using the heat exchanger described in Embodiment 1 are described. R245ca, R245fa, R32, R41, RC318, etc., and mixed refrigerants R407A, R407B, R407C, R407D, R407E, R410A, R410B, R404A, R507A, R508A, R508B, etc.), HC (butane, isobutane, etc.) Ethane, propane, propylene, etc., several mixed refrigerants of these refrigerants), natural refrigerants (air, carbon dioxide, ammonia, etc., several mixed refrigerants of these refrigerants), low GWP refrigerants such as HF01234yf, and these refrigerants Number of Such refrigerant mixing, even with any type of refrigerant, can achieve its effect.

  Moreover, although the example of air and a refrigerant | coolant was shown as a working fluid, even if it uses other gas, liquid, and gas-liquid mixed fluid, there exists the same effect.

  The heat transfer tubes (flat tubes 1a, circular tubes 1b) and the plate-like fins 2 often use different materials, but the heat transfer tubes 1a, 1b and the plate-like fins 2 are made of copper, and the heat transfer tubes 1a, 1b. By using the same material such as aluminum for the plate-like fin 2, the plate-like fin 2 and the heat transfer tubes 1 a and 1 b can be brazed, and the contact heat transfer coefficient between the fin portion and the heat transfer tubes 1 a and 1 b is dramatically increased. And heat exchange capacity is greatly improved. Moreover, recyclability can also be improved.

  In addition, as a method of closely attaching the heat transfer tubes 1a and 1b and the plate-like fins 2, for example, when brazing in a furnace, by performing post-processing to apply a hydrophilic material to the plate-like fins 2, In this case, the burning of the hydrophilic material during brazing can be prevented.

  Further, the same effect can be obtained when the heat exchanger described in the first embodiment is used in an outdoor unit.

  Note that the heat exchanger described in Embodiment 1 and the refrigeration cycle apparatus using the heat exchanger, such as mineral oil-based, alkylbenzene oil-based, ester oil-based, ether oil-based, fluorine oil-based, etc., are not soluble. Regardless, any refrigeration oil can achieve its effect.

  As an application example of the present invention, it can be used for a heat pump device that requires improved heat exchange performance and improved energy saving performance.

  1a flat tube, 1b circular tube, 1c connecting circular tube, 2 plate-like fins, 3 bulge 3-way tube, 4 row U-bend, 5 hairpin, 6 3-way tube, 7 header with partition plate, 8-stage U-bend , 9 Distributor, 10 Reheat valve, 11a, 11b, 11c Auxiliary heat exchanger, 11d, 11e, 11f, 11g, 11h, 11i Main heat exchanger, 12 Joint pipe, 13 Partition plate, 14 Hollow structure header, 15 Refrigerant flow, 16 Pipe connection port as refrigerant inlet, 17 Pipe connection port as refrigerant outlet, 21-29 Refrigerant piping, 33 Compressor, 34 Condensing heat exchanger, 35 Throttle device, 36 Evaporating heat exchanger, 37 Blower, 38 Blower Motor, 100 Indoor Unit, 101 Casing, 102 Air Conditioner Grill, 103 Cross-flow Blower, 104 Outlet, 105 Louver.

Claims (7)

A heat exchanger configured by arranging an auxiliary heat exchanger and a main heat exchanger, which are stacked in the fluid flow direction, on the front upper side, the lower front side and the back side in the casing, respectively.
The auxiliary heat exchanger and the main heat exchanger are inserted into a plate-like fin laminated in a direction orthogonal to the fluid flow direction, and the plate-like fin is laminated, and a plurality of the plate-like fins are arranged in the longitudinal direction of the plate-like fin. A heat transfer tube provided;
The auxiliary heat exchanger and the main heat exchanger arranged on the upper front side, and the auxiliary heat exchanger arranged on the lower front side are flattened with one end bent as a U-shape as the heat transfer tube. A pipe is used, and further, a U-shaped connecting pipe is provided at the other end of one side of the flat tube adjacent to each other,
A flat tube is used as the heat transfer tube in the main heat exchanger disposed on the lower front side and the rear side, and a first header having a partition plate in the center of the inside is provided at one end of the flat tube. A heat exchanger, wherein a second header having a hollow structure is provided at an end, and further, two pipe connection ports for entering and exiting the refrigerant are provided at the first header with a partition plate as a boundary.   The heat exchanger according to claim 1, wherein a circular pipe is used as the heat transfer pipe in the auxiliary heat exchanger arranged on the back side. The main heat exchanger is arranged in the second and third rows with the auxiliary heat exchanger installed upstream of the fluid as the first row,
The heat exchange according to claim 1 or 2, wherein a U-bend pipe is used for connection between headers of the second and third rows of main heat exchangers arranged on the lower front side and the rear side. vessel.   In the main heat exchangers arranged on the lower front side and the rear side, when used as an evaporator, the refrigerant flows in the direction opposite to the direction of gravity in the second header of the second row main heat exchanger. In addition, the refrigerant pipes are connected to either one of the two pipe connection ports provided in both the first headers so as to flow in the direction of gravity in the second headers of the main heat exchangers in the third row. The heat exchanger according to claim 3.   One of the two pipe connection ports provided in the first header of the third row main heat exchanger arranged on the back side is provided in the vicinity of the partition plate for refrigerant outflow. The heat exchanger according to claim 4.   Of the main heat exchangers in the second row and the third row, the main heat exchanger in the third row is displaced in the longitudinal direction of the plate fins, and both the flat tubes are arranged in a staggered manner. The heat exchanger according to any one of claims 3 to 5.   A refrigeration cycle apparatus using the heat exchanger according to any one of claims 1 to 6.

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