JP4845943B2 - Finned tube heat exchanger and refrigeration cycle air conditioner - Google Patents

Description

  The present invention relates to a finned tube heat exchanger and a finned tube heat exchanger manufacturing method for performing heat exchange between a refrigerant and a fluid such as a gas, and a refrigeration cycle air conditioner using the same.

  As a conventional heat exchanger used in refrigeration cycle air conditioners, a flat tube is used for the heat transfer tube, the flat tube shape is generally a wing shape, and a fin tube type heat exchange constructed with many cuts on the fins. A vessel is disclosed (see, for example, Patent Document 1).

  In this conventional example, the use of a blade-shaped flat tube as the heat transfer tube of the main heat exchanger has an advantage that the ventilation resistance can be significantly reduced as compared with the circular tube. Moreover, the insertion property to a fin improves also by setting it as a wing | blade shape.

  When manufacturing a heat exchanger using flat heat transfer tubes, a large number of plate-like fins 1 stacked at appropriate intervals are fixed with a jig and inserted into the insertion holes of each plate-like fin to form a plate shape. The fin and the flat heat exchanger are brought into close contact with each other, and then brought into close contact with a brazing material or an adhesive.

  Another conventional heat exchanger is a fin that uses a flat tube as the heat transfer tube and improves the heat transfer performance of the condenser by changing the number of passes between the auxiliary heat exchanger part and the main heat exchanger part. A tube heat exchanger is disclosed (see, for example, Patent Document 2).

JP 2002-139282 A (page 4, FIGS. 1 to 3) Japanese Patent Laying-Open No. 2005-265263 (page 10, FIG. 10)

  However, in the conventional method disclosed in Patent Document 1, the heat exchanger of FIG. 15 has a problem in that a large number of cuts and protrusions on the fins are provided, so that ventilation resistance increases and a dead water area is generated. .

  In addition, the flat tube shape of the flat tube heat exchange is a wing shape, which makes it difficult to process.

  Further, when all the heat exchangers are flat tubes as shown in FIG. 16, when used as a condenser, there is a problem that the auxiliary heat exchanger cannot sufficiently hold the liquid when the refrigerant is supercooled. . In addition, when used as an evaporator, there is a problem in that the pressure loss in the tube in the auxiliary heat exchanger is large and the performance is reduced.

  The present invention has been made to solve the above-described problems, and reduces a dead water area in the wake of a flat tube, reduces a draft resistance, and has a high heat exchange efficiency, and a heat exchanger thereof. The main purpose is to provide a used refrigeration cycle air conditioner.

The heat exchanger according to the present invention includes a main heat exchanger and an auxiliary heat exchanger having a circular heat transfer tube, and a plurality of main heat exchangers are arranged in parallel in order to achieve the above-described goal. A plate-like fin having an opening through which air flows between the plate-like fin and a plate-like fin inserted perpendicularly to the plate-like fin, the working refrigerant passes through the inside, and a plurality of steps are provided in a step direction perpendicular to the air passage direction. A plurality of flat tubes provided in a plurality of rows in the row direction of the air passing direction, and a plurality of rows of raised portions provided in the plate fin for the air flow. The trailing edge of the cut-and-raised downstream side in the passing direction is arranged downstream of the downstream trailing edge of the flat tube, and the angle of attack on the downstream side is made larger than the angle of attack on the upstream side. Further, the leg cut and raised angle β1 of the upstream cut and the leg cut and raised angle of the downstream cut and raised The ratio .beta.1 / .beta.2 of .beta.2 is obtained as a 1.0 <β1 / β2 <2.0.

According to this invention, it is provided with a main heat exchanger and an auxiliary heat exchanger having a circular heat transfer tube, and the main heat exchangers are arranged in parallel and have openings through which air flows. Plate-shaped fins, inserted into the plate-shaped fins at right angles, through which the working refrigerant passes, are provided in a plurality of stages in a step direction perpendicular to the air passage direction, and a plurality of rows in the row direction of the air passage direction A flat tube provided on the plate-like fin, and a plurality of rows of cuts and raiseds for the air flow, and a trailing edge of the cut and raised downstream in the air passage direction among the plurality of cuts Is arranged downstream from the downstream trailing edge of the flat tube, the angle of attack on the downstream side is larger than the angle of attack on the upstream side, and the leg portion on the upstream side is further raised. The ratio β1 / β2 between the raising angle β1 and the lower leg raising angle β2 is 1.0 <β1 / β2. Since was set to be 2.0, it is possible to dead water of flat tube downstream is reduced, reducing the ventilation resistance. Further, since the auxiliary heat exchanger uses a circular heat transfer tube, high heat exchange performance can be ensured. In addition, it is possible to greatly suppress peeling of the back surface of the cut leg and contribute to the reduction of the ventilation resistance and the increase of the heat transfer coefficient. And heat exchange efficiency increases and the input of a fan can be reduced.

Embodiment 1 FIG.
1 is a side sectional view of a heat exchanger according to Embodiment 1 of the present invention. In the first embodiment, the heat exchanger is placed on the back of the main heat exchangers 9 and 10 using flat tubes placed on the upper front and the main heat exchangers 11 and 12 using flat tubes placed on the lower front. The main heat exchangers 7 and 8 using the flat tubes and the auxiliary heat exchangers 4, 5 and 6 arranged in the first row in the air flow direction.

  In the first embodiment, the main heat exchangers arranged in the second and third rows in the air flow direction indicated by arrows will be described. In the main heat exchangers 9 and 10 arranged at the upper front, the pitch Fp in the stacking direction of the plate-like fins 1 is Fp = 0.0011 m, the fin thickness Ft = 0.0001 m, and the fin width in the air flow direction Is L = 0.0142 m, the distance Dp between the heat transfer tubes adjacent in the stage direction of the heat exchanger is Dp = 0.0102 m, and the main heat exchangers 11 and 12 arranged at the lower part of the front face are Fp = 0.0011 m. Yes, fin thickness Ft = 0.0001m, fin width in the direction of air flow is L = 0.0137m, distance Dp of heat transfer tubes adjacent in the heat exchanger step direction is Dp = 0.0095m, and lower front part The main heat exchangers 7 and 8 arranged in the above are Fp = 0.0011 m, the fin thickness Ft = 0.0001 m, and the fin width in the air flow direction is L = 0.137m, in the step direction of the heat exchanger The distance Dp between adjacent heat transfer tubes is Dp = 0.09 m. The heat transfer tube has a flat shape, and the fin collar and the heat transfer tube are completely joined by brazing. Further, in the main heat exchanger, the flat tubes are arranged in a staggered manner, the plate-like fins are divided for each row, and a gap 19 is interposed between the rows. Further, in order to maintain a pressure resistance in the heat transfer tube, a partition wall is provided, and the inside of the tube is divided into a number of chambers. In addition, the major axis diameter of the heat transfer tube parallel to the air flow direction is db = 0.0105 m, and the minor axis diameter of the heat transfer tube at the leading edge with respect to the air flow direction is db = 0.0022 m. The number of columns is an example of two columns. Two slits are provided per row.

  The auxiliary heat exchangers 4, 5, and 6 using circular pipes have a pitch Fp in the stacking direction of the plate-like fins 1 of Fp = 0.0013 m, a fin thickness Ft = 0.0001 m, and fins in the direction of air flow. The width is L = 0.0127 m, the distance Dp between the centers of the heat transfer tubes adjacent in the direction of the heat exchanger is Dp = 0.0204, the heat transfer tubes are circular, and the fin collar 39 and the heat transfer tubes are connected to the fin front edge. Are pressure bonded by mechanical expansion.

  In the heat exchanger using the flat tube configured as described above, the flat tube 2 and the circular tube are formed of an extruded shape made of aluminum alloy, and the plate-like fins 1 are formed of a plate material made of aluminum alloy. . Thus, by making all the heat exchangers the same material, the proof stress of corrosion improves.

  Moreover, by arranging the flat tubes in a staggered manner in the main heat exchanger, the heat transfer coefficient of the leading edge of the flat tubes is improved, and the heat exchanger performance is improved.

  Further, in the main heat exchanger, by dividing the second and third plate fins, the arrangement of the heat exchanger can be variously accommodated in the indoor unit box, and the leading edge of the second plate fins An improvement in heat transfer coefficient due to the effect (air boundary layer separation effect) can also be expected.

  Further, it has been found from the experimental results that the heat transfer coefficient is improved by making the length of the row direction of the cut and raised equal to the distance between the cut and raised.

  Moreover, in the main heat exchanger, the fin width Lp2 at the upper front is made larger than the fin widths Lp1 and Lp3 at the lower front and the rear, so that the heat exchanger outlet temperature at the front upper part where the wind speed is high approaches the air inlet temperature. The temperature efficiency can be made uniform throughout the heat exchanger. Further, by increasing the fin width at the front upper portion having a large inclination with respect to the gravitational direction, the distance between the flat tube and the fin rear edge is increased, thereby preventing dripping when used as an evaporator.

  FIG. 2 is a detailed view of a plate-like fin of a main heat exchanger using a flat tube. The plate shape is opened at the front edge portion in the air flow direction, and the front edge portion has no fin collar for regulating the pitch when the plate fins are stacked. A plate-like fin at a portion having no fin collar is provided with an arc-shaped notch, and two cuts and ridges are provided on the plate-like fin.

  With respect to the two cut-and-raised portions provided in a plate-like fin shape, the cut-and-raised leg portions in the upstream portion in the air flow direction are arranged substantially parallel to the row direction (air flow direction). On the other hand, the cut-and-raised portion in the downstream portion in the air flow direction is arranged so as to form an angle of attack θ with respect to the row direction. The upstream part of the air flow direction is sandwiched between flat tubes, and the air flow between the plate fins is almost the same as the row direction, so it is effective to be parallel to the air flow direction. Since the cut-and-raised portion of the downstream portion in the direction has advanced to the rear of the flat tube, it is possible to suppress the stagnation (dead water area) of the wake portion of the flat tube by forming the angle of attack θ. Further, the cut-and-raised angle β2 of the cut-and-raised leg portion in the downstream portion is formed smaller than the cut-and-raised angle β1 of the cut-and-raised leg portion in the upstream portion in the air flow direction. Since the cut-and-raft of the downstream portion forms an angle of attack θ, if β2 is increased, peeling occurs on the back side of the paper surface of the leg and the draft resistance is increased and the heat transfer rate is decreased, but from β1 By making β2 small, it is possible to greatly suppress the separation and peeling of the back surface of the leg portion, which can contribute to a reduction in ventilation resistance and an increase in heat transfer coefficient.

FIG. 3 shows the heat transfer coefficient outside the tube with respect to the ratio β1 / β2 of the cut-and-raft angle β1 of the upstream leg portion in the air flow direction and the cut-and-raft angle β2 of the downstream leg portion. FIG. 5 is a characteristic diagram showing the relationship between the ratio αo / ΔP of αo and ventilation resistance ΔP. When β1 / β2 is increased, αo / ΔP is improved, becomes maximum near β1 / β2 = 2.0, becomes equal to or larger than β1 / β2 = 2.3, and becomes less than αo / ΔP at β1 / β2 = 1.0. When the external heat transfer coefficient αo increases, the heat exchange efficiency increases, and when ΔP decreases, the input of the blower can be reduced. Therefore, it is better that αo / ΔP is larger, but an air conditioner with good performance can be configured particularly in the range of 1.0 <β1 / β2 <2.0.

  4 to 7 show a brazing material 23 arranged for joining plate-like fins and flat tubes in a furnace. FIG. 4 shows a case where two round bars are arranged in the cutout portion of the front edge of the flat tube and the plate fin in the air direction. By arranging the brazing material at the upper part in the gravity direction where the plate-like fin (fin collar) and the flat tube are in contact with each other, the brazing material spreads to the left and right of the flat tube, and the plate-like fin and the flat tube are sufficiently joined.

  FIG. 5 connects the two round brazing members of FIG. 4 and arranges them directly above the flat tube, so that the positional stability at the time of brazing material arrangement is improved. Also, the brazing material spreads to the left and right of the flat tube, and the fin and the flat tube are sufficiently joined.

  In FIG. 6, a plate-shaped brazing material is formed in a semicircular arc shape so as to cover the front edge arc of the flat tube, and the positional stability when the brazing material is arranged is improved. Also, the brazing material spreads to the left and right of the flat tube, and the fin and the flat tube are sufficiently joined.

  In FIG. 7, the plate-like brazing material is formed in a U-shape so as to be substantially in contact with the front edge arc of the flat tube, and the positional stability when the brazing material is arranged is improved. Also, the brazing material spreads to the left and right of the flat tube, and the fin and the flat tube are sufficiently joined.

  Next, the manufacturing process of the heat exchanger according to the first embodiment will be described. In the main heat exchanger, the flat tube is formed by extrusion processing, and then the outer peripheral shape is processed into a taper shape by press processing, inserted into a rectangular header that constitutes the flow path of the refrigerant, and fixed by a jig After inserting the lid into the square fin, adding a lid to the square header and adding refrigerant piping to the lid, brazing the brazing material to the upper part of the flat pipe, between the square header and flat pipe, between the square header and the header lid, header The heat exchanger assembly that is placed between the lid and the pipe, between the square header and the connection pipe, connected by the refrigerant pipe and combined in two rows is brazed in the furnace, washed, then coated with hydrophilic treatment material, and dried After that, a plurality of heat exchanger assemblies, distributors and reheat valves are joined by burner brazing, and then joined by pipes and burner brazing added to the circular tube auxiliary heat exchanger manufactured by expansion Manufactured in The

FIG. 8 is a simplified explanatory view showing the refrigerant flow path when used as the evaporator of the first embodiment, FIG. 9 (a) is a view showing the refrigerant flow path, and FIG. It is an enlarged view of the flow path of the refrigerant | coolant of a main heat exchanger. Next, the refrigerant path will be described with reference to FIG. 8, FIG. 9 (a) and FIG. 9 (b).
When used as an evaporator during cooling, the refrigerant passes through auxiliary heat exchangers 4, 5, 6 in the two-pass section, passes through a distributor that divides into three after joining, and uses a flat tube arranged at the upper part of the front surface. It is further branched into two in the corner header 25 added to the main heat exchanger, passed through the heat exchanger, merged by the distributor, passed through the throttle valve 26, passed through the distributor 26 divided into six branches, and the lower part of the front surface. Further, it is further branched into two in a square header added to the main heat exchanger using a flat tube arranged on the back, passes through the main heat exchanger, and passes through the cylindrical header 28. At this time, three refrigerant flow paths distributed by the three-branch pipe 24 or the six-branch pipe 27 are connected to the upstream (second row) main heat exchangers 7, 9, and 11, respectively. In each main heat exchanger, two rooms are arranged at symmetrical positions around three inlets arranged at regular intervals (here, a distance obtained by grouping flat tubes every four rooms), The three refrigerant flow paths are respectively connected to the three inlets. Therefore, in each flat tube group, the refrigerant is equally sent from the pipe to the four convenient rooms provided at two symmetrical positions via the inlet. Thereby, since heat exchange is uniform and uniform heat exchange is performed, heat exchange efficiency is improved. And the refrigerant | coolant which complete | finished heat exchange comes out from the exit provided in the room | chamber end of each flat tube group, and is sent to the main heat exchanger of a downstream (3rd row).
In the downstream main heat exchanger, two rooms are arranged at symmetrical positions around three outlets arranged at regular intervals (here, a distance obtained by grouping flat tubes every four rooms) as in the upstream. The three refrigerant flow paths are connected to the three outlets, respectively. Moreover, the refrigerant | coolant which came out of the room | chamber of the end of each flat tube group of an upstream heat exchanger is sent to the room | chamber of the end of each flat tube group of a downstream main heat exchanger. Accordingly, in each flat tube group of the downstream main heat exchanger, the refrigerant is sent evenly from the four convenient rooms provided by two rooms at symmetrical positions from the outlet, and exits to the outlet pipe through the outlet. come. Thereby, even in the downstream main heat exchange, there is no bias and uniform heat exchange is performed, so that the heat exchange efficiency is improved.

Further, in the case of the main heat exchangers 11, 12, 7, and 8 in which the portion where the wind speed is high and the portion where the wind speed is low are conspicuous in the lower part of the front surface and the rear surface in the air flow direction, The heat exchange capacity may be reduced due to overheating at a large area. Therefore, in such a main heat exchanger, as shown in FIG. 9 (b), a flat tube group 40a of a heat exchanger having a high wind speed upstream and a flat tube group 41c of a heat exchanger having a low wind speed downstream are piped. The flat tube group 40c of the heat exchanger having a high wind speed upstream and the flat tube group 41a of the heat exchanger having a low wind speed downstream are connected in a pipe shape by a pipe. Further, the flat tube group 40b of the heat exchanger having an intermediate wind speed is connected to the flat tube group 41b of the heat exchanger having an intermediate wind speed.
In the main heat exchangers 11, 12, 7, and 8 using the flat tubes arranged on the lower front surface and the rear surface in this way, the second row and third row where the wind speed is high and the wind speed is low with respect to the air flow direction. By changing the refrigerant flow path of each part into a plow shape by the refrigerant piping for each row, the dryness of the outlet refrigerant can be kept uniform, the refrigerant wind speed is high, it is overheated at a place with a large heat load, and heat exchange performance is reduced Can be prevented.

  When used as an evaporator, the refrigerant flows through the main heat exchangers 9 and 10 at the front upper part in front of the throttle valve 26, so that the refrigerant is added to the front upper main heat exchanger where the inclination with respect to the direction of gravity is large and condensate can easily drip. The exit is not located. Therefore, a highly reliable heat exchanger can be formed. Moreover, in this Embodiment 1, the square header 25 is used for the both ends of a flat tube, and it branches into 2 at a refrigerant | coolant inlet part, and a refrigerant | coolant passes through a heat exchanger by the branch number double of the branch number in a divider | distributor. FIG. 10 is a diagram showing a refrigerant collision part provided inside the refrigerant inlet of the corner header 25, FIG. 10 (a) is an external view showing a schematic arrangement position of the refrigerant collision part, and FIG. 10 (b) is a refrigerant collision part. FIG. 10C is a cross-sectional view taken along the line AA of FIG. 10B. As shown in FIG. 10B, a refrigerant collision part 29 having a depression at the center inside the refrigerant inlet of the corner header 25 is provided, and the longitudinal direction of the corner header 25 from the refrigerant collision part 29 is substantially symmetrical. There are two flat tubes. Therefore, when the refrigerant that has passed through the flat tube and entered the corner header 25 collides with the refrigerant collision portion 29, the refrigerant is scattered substantially uniformly around 360 degrees in the vertical and horizontal directions by the depression of the refrigerant collision portion 29. After that, it enters the flat tube 2. At this time, since the refrigerant is scattered to the surroundings, gas and liquid are mixed here, and the refrigerant scattered almost uniformly to the surroundings enters the two flat tubes provided at substantially symmetrical positions. The amount of refrigerant that has entered the two flat tubes is distributed evenly with no bias. As described above, by equally distributing the amount of refrigerant mixed with the gas-liquid mixture of the refrigerant, variation in refrigerant branching can be suppressed. Thereby, the number of branches of the distributor can be reduced, and the distributor can be made compact and low in cost.

  FIG. 11 shows that in the main heat exchangers 11, 12, 7, and 8 at the front lower part and the rear part, the refrigerant pipe diameter for joining the six-branch distributor 27 and the heat exchanger is large at the part where the wind speed is large and the part where the wind speed is small. It is a small one. As a result, it is possible to increase the refrigerant flow rate at the part where the wind speed is high and the heat load is large, and to reduce the refrigerant flow rate at the part where the heat load is low and the part where the wind speed is low. I can do it.

FIG. 12 is an explanatory view showing the sealing plate, and FIG. 12 (a) is a view showing the refrigerant flow path, and at the same time, shows the arrangement position of the sealing plate 31 in the heat exchanger. FIG. 12B is a diagram showing a mounting state of a sealing plate that closes the hole (inlet) of the flat tube in the square header 25, and the filled portion in the drawing is the sealing plate 31. As shown in FIG. 12 (a), a plate that closes the hole of the flat tube is disposed in the square header 25 in the heat exchangers at the lower front portion and the rear surface, and the length of this plate in the row direction is shown in FIG. 12 (b). The number of holes in the flat tube is changed so as to increase at a portion where the wind speed is high and to decrease at a portion where the wind speed is low. As a result, the refrigerant flow rate at the part where the wind speed is large and the heat load is large can be increased, the refrigerant flow rate at the part where the wind speed is small and the heat load is small can be reduced, and the outlet refrigerant dryness can be kept uniform. .
In addition, in the example of FIG.10 (b), although the linear inclination is given so that the shape of the sealing board 31 may change continuously, it is not necessary to restrict to this. For example, the shape may be changed to a step shape, and any shape may be used as long as the number of holes in the flat tube is larger at a portion where the wind speed is high and smaller at a portion where the wind speed is low.
Further, without using a plate for closing the flat tube hole, the shape of the flat tube may be changed and the number of holes may be changed, and the same effect is obtained.

  FIG. 13 is an external view showing the square header and the ring-shaped plate. In the heat exchangers at the lower front and the rear, a ring-shaped plate 32 is provided between the square header and the refrigerant pipe, and the hole diameter of the ring-shaped plate 32 is shown. In this example, the hole diameter of the ring-shaped plate is made smaller as the part where the wind speed is large goes to the part where the wind speed is large and the wind speed is low. Thereby, the refrigerant | coolant flow rate of a part with a large wind speed and a large heat load can be enlarged, the refrigerant | coolant flow rate in a part with a small wind speed and a small heat load can be made small, and an exit refrigerant | coolant dryness can be kept uniform.

FIG. 14 is a refrigerant circuit diagram of the air conditioning refrigeration apparatus. The refrigerant circuit shown in the figure includes a compressor 33, a condensation heat exchanger 34, an expansion device 35, an evaporating heat exchanger 36, and a blower 37. By using the heat exchanger according to the first embodiment for the condensation heat exchanger 34, the evaporating heat exchanger 36, or both, an air-conditioning refrigeration apparatus with high energy efficiency can be realized.
Here, energy efficiency is constituted by the following equation.
Heating energy efficiency = indoor heat exchanger (condenser) capacity / all inputs Cooling energy efficiency = indoor heat exchanger (evaporator) capacity / all inputs

  In addition, about the heat exchanger described in Embodiment 1 and the air-conditioning refrigeration apparatus using the same, HCFC (R22) and HFC (R116, R125, R134a, R14, R143a, R152a, R227ea, R23, R236ea, R236fa, R245ca, R245fa, R32, R41, RC318, etc., and several mixed refrigerants R407A, R407B, R407C, R407D, R407E, R410A, R410B, R404A, R507A, R508A, R508B, etc.), HC (butane, etc.) Isobutane, ethane, propane, propylene, etc., and some mixed refrigerants of these refrigerants), natural refrigerant (air, carbon dioxide, ammonia, etc., some mixed refrigerants of these refrigerants), and some mixed refrigerants of these refrigerants Any kind of refrigerant Be used, it is possible to 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.

  In addition, heat transfer tubes and plate fins often use different materials. However, by using the same material such as copper for heat transfer tubes and plate fins and aluminum for heat transfer tubes and plate fins, plate fins are used. The heat transfer tube can be brazed, the contact heat transfer coefficient between the plate fin and the heat transfer tube is dramatically improved, and the heat exchange capacity is greatly improved. Moreover, recyclability can also be improved.

  In addition, as a method of closely attaching the heat transfer tube and the plate fin, when performing brazing in the furnace, by applying the hydrophilic material to the plate fin by post-processing, the hydrophilic material during brazing in the pre-treatment Burnout can be prevented.

  The heat exchanger described in the first embodiment and the air-conditioning refrigeration apparatus using the heat exchanger are soluble in refrigerant and oil such as mineral oil, alkylbenzene oil, ester oil, ether oil, and fluorine oil. The effect can be achieved with any refrigeration oil, whether or not it melts.

It is a figure which shows the side surface cross section of the heat exchanger of Embodiment 1 of this invention. It is the front view and side view which show the structure of the plate-shaped fin and flat tube of Embodiment 1 of this invention. It is a characteristic view which shows the heat exchanger performance of Embodiment 1 of this invention. It is sectional drawing which shows the arrangement position of the brazing material of Embodiment 1 of this invention. It is sectional drawing which shows the arrangement position of the brazing material of Embodiment 1 of this invention. It is sectional drawing which shows the arrangement position of the brazing material of Embodiment 1 of this invention. It is sectional drawing which shows the arrangement position of the brazing material of Embodiment 1 of this invention. It is a simplified explanatory drawing which shows the refrigerant | coolant flow path of Embodiment 1 of this invention. It is a figure which shows the refrigerant | coolant flow path of Embodiment 1 of this invention. It is an enlarged view of the flow path of the refrigerant | coolant of the main heat exchanger in Fig.9 (a). FIG. 5 is a diagram showing a refrigerant collision portion provided inside the refrigerant inlet of the corner header according to Embodiment 1 of the present invention. It is an external view showing the structure of the flat tube heat exchanger of this invention. It is a figure which shows the refrigerant | coolant flow path of Embodiment 1 of this invention. It is a figure which shows the attachment condition of the sealing board which plugs up the hole (inlet) of the flat tube in the square header. It is an external view which shows the square header and ring-shaped board of Embodiment 1 of this invention. It is a refrigerant circuit figure of the air-conditioning refrigerating device in which Embodiment 1 of this invention is used.

Explanation of symbols

  1 Plate-shaped fin, 2 flat tube, 3 circular tube, 4 auxiliary heat exchanger using circular tube, 5 auxiliary heat exchanger using circular tube, 6 auxiliary heat exchanger using circular tube, 7 flat tube Main heat exchanger used, 8 Main heat exchanger using flat tube, 9 Main heat exchanger using flat tube, 10 Main heat exchanger using flat tube, 11 Main heat exchanger using flat tube , 12 Main heat exchanger using a flat tube, 13 Blower, 14 Casing, 15 Front panel, 16 Cleaning box, 17 Filter, 18 Top panel, 19 Gap, 20 Notch on the front edge of the fin, 21 Plate fin Cut and raised on the top, 22 Cut and raised on the plate fin, 23 Brazing material, 24 Branch distributor, 25 Square header, 26 Throttle valve, 276 Branch distributor, 28 Cylindrical gas header, 29 Refrigerant collision part, 30 Connection piping, 31 sealing plate, 32 rings Plate, 33 compressor, 34 condenser heat exchanger, 35 expansion device, 36 evaporator heat exchanger, 37 blower, 38 blower motor, 39 fin collar, 40a-c flat tube group, 41a-c flat tube group .

Claims (19)

A main heat exchanger;
An auxiliary heat exchanger having a circular heat transfer tube, and
The main heat exchanger is a plurality of plate-like fins arranged in parallel and having openings through which air flows.
The plate-like fins are inserted at right angles, the working refrigerant passes through them, and is provided in a plurality of stages in a step direction perpendicular to the air passage direction and in a plurality of rows in the row direction of the air passage direction. Flat tube,
The plate-like fins are provided with a plurality of rows and raised portions for the air flow,
Of the plurality of cuts and raised portions, the rear edge of the cut and raised downstream in the air passage direction is arranged on the downstream side of the downstream downstream edge of the flat tube, and from the angle of attack of the upstream cut and raised The angle of attack of the cut and raised on the downstream side is increased , and the ratio β1 / β2 between the leg cut and raised angle β1 of the upstream cut and the cut and raised leg β2 of the downstream cut is 1 0.0 <β1 / β2 <2.0 . A finned tube heat exchanger characterized by the above .   The fin tube type heat exchanger according to claim 1, wherein the flat tube, the circular tube, and the plate-like fin are made of the same material.   The finned tube heat exchanger according to claim 1 or 2, wherein the plate-like fins of the main heat exchanger are divided for each row.   4. The finned tube heat exchanger according to claim 3, wherein the flat tubes are arranged in a staggered pattern.   The fin tube type heat exchanger according to any one of claims 1 to 4, wherein a length in the row direction of the cut and raised is equal to a distance between the cut and raised. The main heat exchanger is provided with a cut on a circular arc at a portion where the front edge of the plate fin in the air flow direction and the flat tube are in contact, and a brazing material is disposed at the cut and joined by brazing in a furnace. The finned tube heat exchanger according to any one of claims 1 to 5 , wherein The finned tube heat exchanger according to claim 6 , wherein two round bar-shaped brazing members are arranged at the time of brazing in the furnace. The finned tube heat exchanger according to claim 6 , wherein the brazing material is formed by connecting two round shapes when brazing in the furnace. The fin according to claim 6 , wherein when brazing in the furnace, the shape of the brazing material is arranged as a semicircular arc plate shape so as to substantially contact the circumferential portion of the front edge portion of the flat tube in the air flow direction. Tube heat exchanger. At the time of brazing in the furnace, the shape of the brazing material is generally a U-shape on the windward side of the circumferential portion of the front edge of the flat tube, and the top of the U-shape and the top of the flat tube coincide The finned tube heat exchanger according to claim 6 , wherein the finned tube heat exchanger is arranged as described above. Said auxiliary heat exchanger has a fin collar, claim 1-10, characterized in that it comprises a heat transfer tube of the fin collar and the mechanical tube expansion by circular tube formed by pressure bonding to the leading edge of the plate-like fin The finned tube heat exchanger according to any one of the above. The main heat exchanger is
A first main heat exchanger disposed on the front upper portion of the indoor unit and having a first flat tube;
Wherein arranged in the lower front and rear portions of the indoor unit, it includes a second main heat exchanger having a second flat tube, and
When used as an evaporator, the auxiliary heat exchanger is provided at one or two first refrigerant flow paths for inputting refrigerant from an outdoor unit to the circular pipe and at the refrigerant outlet of the circular pipe. A first rectangular header that merges the refrigerant that has passed through,
A first distributor for branching the refrigerant merged by the first square header into a plurality of flow paths;
The first main heat exchanger is provided at an end portion of the first flat tube, and has a second square shape that further doubles each of the plurality of flow paths branched by the first distributor. With a header,
A second distributor for joining a plurality of flow paths connected to the outlet of the first flat tube;
A throttle valve that throttles the refrigerant output from the second distributor;
A third distributor for branching the outlet side flow path of the throttle valve to twice the number of branches of the first distributor;
The second heat exchanger is provided at an end portion of the second flat tube, and the flow path branched by the third distributor is further branched to double the refrigerant to the second flat tube. The finned tube heat exchanger according to claim 1 , further comprising a third rectangular header to be input and a columnar header provided at an outlet of the second flat tube. The fin tube type heat exchanger according to claim 12, wherein the first to third square headers have a mechanism for bifurcating the refrigerant. 13. The second main heat exchanger according to claim 12, wherein the refrigerant flow paths of a portion having a relatively high wind speed and a portion having a relatively low wind speed are replaced by a refrigerant pipe for each row. Item 14. The finned tube heat exchanger according to item 13 . In the second main heat exchanger, the diameter of the refrigerant pipe joining the distributor and the heat exchanger is relatively large at a portion where the wind speed is relatively large and relatively small at a portion where the wind speed is relatively small. The finned tube heat exchanger according to claim 12 or 13 , wherein the finned tube heat exchanger is characterized by the above. The second main heat exchanger is configured such that the number of holes in the second flat tube is relatively large at a portion where the wind speed is relatively large and relatively small at a portion where the wind speed is relatively small. The finned tube heat exchanger according to claim 12 or 13 , characterized in that In the main heat exchanger at the lower part of the front face and the rear face, the length in the row direction of the plate that seals the hole in the flat tube provided in the first to third square headers is changed from the portion where the wind speed is relatively large to the wind speed. finned tube heat exchanger according to claim 12 or claim 13, characterized in that to increase toward the smaller sites. In the second main heat exchanger, a ring-shaped plate is provided between the first to third square headers and the refrigerant pipe, and the ring-shaped plate has a lower wind speed from a portion having a relatively high wind speed. toward the site, finned tube heat exchanger according to claim 12 or claim 13, characterized in that to reduce the hole diameter of the ring-shaped plate. A refrigeration cycle air conditioner comprising a compressor, a throttle valve, and the finned tube heat exchanger according to any one of claims 1 to 18 .

Images