JP6719657B2 - Heat exchanger and refrigeration cycle device - Google Patents

Description

The present invention relates to a heat exchanger and a refrigeration cycle device.

A heat exchanger used for an air conditioner as an example of a refrigeration cycle device is disclosed in, for example, JP 2006-84078 A (Patent Document 1). The heat exchanger described in this publication is a small diameter multi-tube heat exchanger including a plurality of small diameter heat transfer tube units. Each of the plurality of small-diameter heat transfer tube units is configured by bonding two bilaterally symmetrical fin plates each having a groove portion for forming a tube body portion.

JP, 2006-84078, A

In the heat exchanger described in the above publication, if the two fin plates are not attached to each other so that the respective concave groove portions of the two fin plates are symmetrically aligned with each other, the fin plate is attached to the flow path formed of the concave groove portions. A brazing filler metal for joining penetrates. Therefore, the difficulty of assembling the fin plates is high. Therefore, there is a problem that it is difficult to manufacture the heat exchanger.

The present invention has been made in view of the above problems, and an object thereof is to provide a heat exchanger that can be easily manufactured and a refrigeration cycle apparatus including the heat exchanger.

The heat exchanger of the present invention includes a first heat transfer tube section, a second heat transfer tube section arranged so as to run in parallel with the first heat transfer tube section, and a corrugated fin having valleys and peaks. ing. The fin includes a first surface and a second surface opposite to the first surface. The troughs are configured such that the fins project in the direction from the first surface to the second surface. The ridges are configured such that the fins protrude in the direction from the second surface to the first surface. The first heat transfer tube portion is connected to the valley portion on the first surface of the fin. The second heat transfer tube portion is connected to the mountain portion on the second surface of the fin. The troughs and peaks are arranged side by side along the wind direction of the wind flowing into the fins. The fin includes a windward extension portion that extends straight upwind from any of the valley portion and the peak portion arranged on the most windward side of the wind in the direction in which the valley portion and the peak portion are arranged.

According to the heat exchanger of the present invention, the first heat transfer tube section is connected to the valley section of the fin, and the second heat transfer tube section is connected to the peak section of the fin. Therefore, it is easy to assemble the first heat transfer tube section and the second heat transfer tube section into the fins. Therefore, it is easy to manufacture the heat exchanger.

It is a perspective view which shows roughly the structure of the heat exchanger in one embodiment of this invention. It is a front view which shows roughly the structure of the heat exchanger in one embodiment of this invention. It is a side view which shows roughly the structure of the heat exchanger in one embodiment of this invention. It is sectional drawing which follows the IV-IV line of FIG. It is a side view which shows roughly the structure of the heat exchanger in the modification 1 of one embodiment of this invention. It is sectional drawing which follows the VI-VI line of FIG. It is a front view which shows roughly the structure of the heat exchanger in the modification 2 of one embodiment of this invention. It is a front view which shows roughly the structure of the heat exchanger in the modification 3 of one embodiment of this invention. It is sectional drawing which follows the IX-IX line of FIG. FIG. 9 is a cross sectional view schematically showing a configuration of a heat exchanger according to Modification 4 of the embodiment of the present invention at a cross sectional position corresponding to FIG. 2. It is a figure which shows the refrigerant circuit of the refrigerating-cycle apparatus in one embodiment of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
The configuration of the heat exchanger 1 according to the embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a perspective view of the heat exchanger 1 according to the present embodiment. FIG. 2 is a front view of the heat exchanger 1 according to the present embodiment. FIG. 3 is a side view of the heat exchanger 1 in this embodiment. FIG. 4 is a sectional view of the heat exchanger 1 according to the present embodiment.

As shown in FIGS. 1 and 2, the heat exchanger 1 in the present embodiment is a fin-tube heat exchanger. The heat exchanger 1 in the present embodiment is used, for example, in an air conditioner, an air conditioning refrigeration system, or the like. The heat exchanger 1 in the present embodiment includes a first heat transfer tube section 10, a second heat transfer tube section 20, fins 30, an inlet header 40, an outlet header 50, an inlet tube 60, and an outlet tube 70. Equipped with.

The first heat transfer tube section 10, the second heat transfer tube section 20, and the fins 30 are arranged between the inlet header 40 and the outlet header 50. The first heat transfer pipe portion 10 and the second heat transfer pipe portion 20 are connected to the inlet header 40 and the outlet header 50 so that the refrigerant flows from the inlet header 40 to the outlet header 50, respectively. The inlet header 40 and the outlet header 50 are arranged to face each other. The inlet header 40 is arranged below the outlet header 50 in the gravity direction D2. Each of the inlet header 40 and the outlet header 50 has a refrigerant passage in which a refrigerant flows. An inlet pipe 60 is connected to the inlet header 40. An outlet pipe 70 is connected to the outlet header 50.

The first heat transfer tube section 10 and the second heat transfer tube section 20 are connected to the fins 30 to be integrally configured. The first heat transfer tube section 10, the second heat transfer tube section 20, and the fins 30 that are integrally configured constitute one heat transfer unit 100. In the present embodiment, the plurality of heat transfer units 100 are arranged side by side in the step direction D1.

As shown in FIGS. 2 and 3, the first heat transfer tube portion 10 extends in the gravity direction D2. The first heat transfer tube portion 10 is a cylindrical tube. The first heat transfer tube portion 10 is configured so that the refrigerant flows inside. The first heat transfer tube portion 10 is linearly configured. In the present embodiment, the first heat transfer tube section 10 has a plurality of first heat transfer tubes 11. The plurality of first heat transfer tubes 11 are arranged in parallel with each other. Specifically, the first heat transfer tube portion 10 has two first heat transfer tubes 11.

The second heat transfer tube section 20 is arranged so as to run parallel to the first heat transfer tube section 10. The second heat transfer tube section 20 is arranged in parallel with the first heat transfer tube section 10. The second heat transfer tube section 20 is arranged so as to be adjacent to the first heat transfer tube section 10 in the column direction D3. The second heat transfer tube portion 20 extends in the gravity direction D2. The second heat transfer tube 21 is a cylindrical tube. The second heat transfer tube portion 20 is configured so that the refrigerant flows inside. The second heat transfer tube portion 20 is linearly configured. In the present embodiment, the second heat transfer tube portion 20 has a plurality of second heat transfer tubes 21. The plurality of second heat transfer tubes 21 are arranged in parallel with each other. Each of the plurality of second heat transfer tubes 21 is arranged alternately with each of the plurality of first heat transfer tubes 11. Specifically, the second heat transfer tube section 20 has two first heat transfer tubes 11.

As shown in FIGS. 3 and 4, the fin 30 is configured to meander in a wavy shape. The fin 30 extends in the gravity direction. The fin 30 is composed of an integral plate. That is, the fin 30 has a flat surface extending in the direction of gravity.

The corrugated fin 30 has a valley portion 30a, a mountain portion 30b, a windward extending portion 30c, and a leeward extending portion 30d. The valley portion 30a and the mountain portion 30b are arranged so as to be adjacent to each other. That is, the valleys 30a and the peaks 30b are alternately arranged. The valleys 30a and the peaks 30b are arranged side by side along the wind direction A of the wind flowing into the fins 30.

The fin 30 has a first surface 31 and a second surface 32. The second surface 32 is located on the opposite side of the first surface 31. The valley portion 30 a is configured such that the fin 30 projects in the direction from the first surface 31 to the second surface 32. The ridges 30b are configured such that the fins 30 project in the direction from the second surface 32 to the first surface 31. That is, the valley portion 30a and the peak portion 30b are configured to project in opposite directions.

The first heat transfer tube portion 10 is connected to the valley portion 30 a on the first surface 31 of the fin 30. The 1st heat transfer tube part 10 is arrange|positioned at the bottom of the valley part 30a. The second heat transfer tube portion 20 is connected to the crest portion 30b on the second surface 32 of the fin 30. The second heat transfer tube portion 20 is arranged on the top of the mountain portion 30b. In the present embodiment, the valley portion 30a has a plurality of valleys 30a1 and the mountain portion 30b has a plurality of mountains 30b1. Specifically, the valley portion 30a has two valleys 30a1 and the peak portion 30b has two peaks 30b1. Each of the two first heat transfer tubes 11 is connected to each of the two valleys 30a1. Each of the two second heat transfer tubes 21 is connected to each of the two crests 30b1. That is, the four heat transfer tube groups each including the first heat transfer tube 11 and the second heat transfer tube 21 are connected to one fin 30.

The windward extending portion 30c is configured to extend straight toward the windward from any one of the valley portion 30a and the mountain portion 30b arranged on the most windward side of the wind. To extend straight upwind means to extend upwind along the direction of the wind. That is, the upwind extending portion 30c may be inclined or curved as long as it extends in the wind direction toward the windward. The windward extending portion 30c extends along the column direction D3. The windward extending portion 30c is arranged at the center C in the direction in which the valley portion 30a and the mountain portion 30b project. The windward extending portion 30c has a dimension larger than the diameter of each of the first heat transfer tube portion 10 and the second heat transfer tube portion 20 in the column direction D3. The upwind extending portion 30c has a dimension smaller than the distance (row pitch) between the first heat transfer tube section 10 and the second heat transfer tube section 20 in the row direction D3.

The leeward extending portion 30d is configured to extend straight downward from any one of the valley portion 30a and the mountain portion 30b arranged at the most leeward side of the wind. To extend straight downwind means to extend downwind along the direction of the wind. That is, the leeward extending portion 30d may be inclined or curved as long as it extends in the windward direction toward the leeward side. The leeward extending portion 30d extends along the column direction D3. The leeward extending portion 30d is arranged at the center C in the direction in which the valley portion 30a and the mountain portion 30b project. The leeward extending portion 30d has a dimension larger than the diameter of each of the first heat transfer tube portion 10 and the second heat transfer tube portion 20 in the column direction D3. The leeward extending portion 30d has a dimension smaller than the distance (column pitch) between the first heat transfer tube portion 10 and the second heat transfer tube portion 20 in the row direction D3.

The first heat transfer tube section 10, the second heat transfer tube section 20, and the fins 30 are made of the same material. Each material of the 1st heat transfer tube part 10, the 2nd heat transfer tube part 20, and the fin 30 is copper, for example. Each of the first heat transfer tube section 10 and the second heat transfer tube section 20 and the fin 30 are connected by brazing. In this case, copper brazing may be used.

Then, operation|movement of the heat exchanger 1 of this Embodiment is demonstrated. Here, a case where the heat exchanger 1 is used as an evaporator will be described as an example.

When the heat exchanger 1 is used as an evaporator, the refrigerant flows into the inlet header 40 through the inlet pipe 60 connected to the inlet header 40 in a gas-liquid two-phase state. The refrigerant in the gas-liquid two-phase state is distributed from the inlet header 40 to each tube group of the first heat transfer tube section 10 and the second heat transfer tube section 20, and rises toward the outlet header 50. When the refrigerant in the gas-liquid two-phase state flows in the first heat transfer tube section 10 and the second heat transfer tube section 20, the heat and the air around the first heat transfer tube section, the second heat transfer tube section 20 and the fins 30 are generated. It becomes a gas state by exchanging it. The refrigerants in the gas state merge at the outlet header 50 and flow out from the outlet pipe 70 connected to the outlet header 50.

Next, the function and effect of the heat exchanger 1 in the present embodiment will be described.
According to the heat exchanger 1 in the present embodiment, the first heat transfer tube part 10 is connected to the valley part 30a of the fin 30, and the second heat transfer tube part 20 is connected to the crest part 30b of the fin 30. .. Therefore, it is easy to assemble the first heat transfer tube section 10 and the second heat transfer tube section 20 into the fin 30. Therefore, it is easy to manufacture the heat exchanger 1.

In addition, it is possible to prevent a brazing material for connecting the first heat transfer tube section 10 and the second heat transfer tube section 20 to the fins 30 from entering into each of the first heat transfer tube section 10 and the second heat transfer tube section 20. You can Therefore, also from this point, the heat exchanger 1 can be easily manufactured.

Further, since the valley portion 30a and the mountain portion 30b are arranged side by side along the wind direction A of the wind flowing into the fin 30, it is possible to reduce the ventilation resistance of the wind flowing along the fin 30. Therefore, the heat exchange efficiency can be improved.

Further, since the fins 30 have a corrugated shape, the fins 30 come into contact with the air between the end portion on the windward side and the end portion on the leeward side of the fin 30, as compared with the case where the fins 30 have a linear shape. The area increases. Therefore, the heat transfer area of the fin 30 can be increased. Further, since the fins 30 have a corrugated shape, the flow of air flowing along the fins 30 meanders. Therefore, the distance that the fins 30 come into contact with the air increases. Therefore, the heat exchange efficiency can be improved.

According to the heat exchanger 1 of the present embodiment, the first heat transfer tube section 10, the second heat transfer tube section 20 and the fins 30 extend in the gravity direction. When the heat exchanger 1 is used as an evaporator in an outdoor unit, condensed water adheres to the first heat transfer tube section 10, the second heat transfer tube section 20 and the fins 30. Since the first heat transfer tube section 10, the second heat transfer tube section 20 and the fins 30 extend in the direction of gravity D2, the condensed water is transmitted through the first heat transfer tube section 10, the second heat transfer tube section 20 and the fins 30 and discharged downward. can do. As a result, the condensed water is drained smoothly. Therefore, the drainage property during normal operation and during defrosting operation after frost formation is good, and the heat exchanger performance can be maintained high.

According to heat exchanger 1 in the present embodiment, fins 30 have windward extending portions 30c that extend straight toward windward from any of the valley portion 30a and the peak portion 30b that are arranged most upwind. Is included. Therefore, when the heat exchanger 1 is used as an evaporator, it is possible to suppress the generation of frost attached to the fins 30. Further, the heat transfer area of the fins 30 can be increased by the windward extending portion 30c.

According to heat exchanger 1 in the present embodiment, fin 30 includes leeward extending portion 30d that extends straight downwind from any of valley portion 30a and ridge portion 30b arranged most leeward. There is. Therefore, the air flowing downstream from the leeward extending portion 30d can be rectified. Further, the heat transfer area of the fin 30 can be increased by the leeward extending portion 30d.

Since the fins 30 in the present embodiment are formed of an integral plate, the first heat transfer tube section 10, the second heat transfer tube section 20 and the fins 30 can be integrated. Therefore, the fins 30 to which the first heat transfer tube section 10 and the second heat transfer tube section 20 are connected can be integrally handled like one heat transfer tube. Therefore, it becomes easy to handle the first heat transfer tube section 10, the second heat transfer tube section 20, and the fins 30 when manufacturing the heat exchanger 1. Therefore, the manufacturability of the heat exchanger 1 is increased.

According to heat exchanger 1 of the present embodiment, each of first heat transfer tube section 10, second heat transfer tube section 20 and fin 30 is made of the same material. Therefore, the heat transfer resistance between the fin 30 and each of the first heat transfer tube part 10 and the second heat transfer tube part 20 can be minimized. Thereby, the heat exchange efficiency can be improved. Further, the first heat transfer tube section 10, the second heat transfer tube section 20 and the fin 30 can be brazed with the same material. Therefore, as compared with the case where the first heat transfer tube section 10, the second heat transfer tube section 20 and the fin 30 are made of different materials, the first heat transfer tube section 10 and the second heat transfer tube section 20 respectively. The contact resistance between each and the fins 30 can be reduced. Thereby, the heat exchange efficiency can be improved.

Next, each modification of the heat exchanger 1 of the present embodiment will be described. In addition, unless otherwise stated, since the heat exchanger 1 of each modified example has the same configuration as the heat exchanger 1 of the present embodiment described above, the same components are designated by the same reference numerals, and Do not repeat the explanation.

First, with reference to FIG. 5 and FIG. 6, the heat exchanger 1 in Modification 1 of the present embodiment will be described. FIG. 5 is a side view of the heat exchanger 1 in the first modification of the present embodiment. FIG. 6 is a cross-sectional view of the heat exchanger 1 according to the modified example 1 of the present embodiment.

As shown in FIG. 5 and FIG. 6, in the heat exchanger 1 according to the modified example 1 of the present embodiment, the plurality of heat transfer units 100 are arranged in two rows. Each of the plurality of heat transfer units 100 has a heat transfer unit 101 arranged in a windward row (windward row) and a heat transfer unit 102 arranged in a leeward row (leeward row). Each of the heat transfer units 101 in the upwind row and the heat transfer units 102 in the downwind row are connected to the row straddle header 80, and are connected to each other via the row straddle header 80.

The heat transfer units 101 in the leeward row and the heat transfer units 102 in the leeward row are arranged offset from each other in the step direction D1. Specifically, the first heat transfer tube portion 10 and the second heat transfer tube portion 20 of the heat transfer unit 101 in the upwind row, and the first heat transfer tube portion 10 and the second heat transfer tube portion 20 of the heat transfer unit 102 in the downwind row. Is arranged with a distance of a half of the pitch (step pitch) of the first heat transfer tube section 10 and the second heat transfer tube section 20 in the step direction D1 shifted.

When the heat exchanger 1 is used as the evaporator of the outdoor unit, the refrigerant flows into the inlet header 40 in a gas-liquid two-phase state from the inlet pipe 60 connected to the inlet header 40 of the heat transfer unit 101 in the upwind row. The refrigerant in the gas-liquid two-phase state is distributed from the inlet header 40 to each tube group of the first heat transfer tube section 10 and the second heat transfer tube section 20, rises toward the outlet header 50, and then at the row straddle header 80. It moves to the heat transfer unit 102 in the leeward row and is distributed to the first heat transfer tube portion 10 and the second heat transfer tube portion 20 of the heat transfer unit 101 in the leeward row. When the refrigerant in the gas-liquid two-phase state flows in the first heat transfer tube section 10 and the second heat transfer tube section 20 of the heat transfer unit 102 in the leeward row, the first heat transfer tube section 10 and the second heat transfer tube section 20 And heat exchange with the air around the fins 30 results in a gas state. The refrigerants in the gas state merge at the outlet header 50 and flow out from the outlet pipe 70 connected to the outlet header 50.

According to the heat exchanger 1 in the first modification of the present embodiment, in the heat transfer units 101 in the windward row and the heat transfer units 102 in the leeward row, from the first heat transfer pipe section 10 and the second heat transfer pipe section 20. Is arranged in the stage direction D1 with a displacement of half the stage pitch (half pitch). Therefore, a new temperature boundary layer is constructed at the front edge of the fin 30 of the heat transfer unit 102 in the leeward row. This improves the heat transfer coefficient. Further, in the heat exchanger 1 according to the modified example 1 of the present embodiment, the first heat transfer tube portion 10 and the second heat transfer tube portion 20 are not constrained in the step direction D1, so the step pitch adjustment in the step direction D1 is performed. Will be easier.

Then, with reference to FIG. 7, the heat exchanger 1 in the modification 2 of this Embodiment is demonstrated. FIG. 7 is a side view of the heat exchanger 1 according to the second modification of the present embodiment.

As shown in FIG. 7, in the heat transfer unit 101 in the upwind row in the second modification of the present embodiment, the heat exchanger 1 includes the first heat transfer tube section 10 and the second heat transfer tube section near the inlet header 40. 20 is bent. Specifically, the first heat transfer tube section 10 and the second heat transfer tube section 20 are bent inward in the column direction D3. The first heat transfer tube section 10 and the second heat transfer tube section 20 are bent between the fins 30 and the inlet header 40. The dimension of the inlet header 40 in the column direction D3 is smaller than the dimension of the outlet header 50 in the column direction.

According to the heat exchanger 1 in the second modification of the present embodiment, the volume of the inlet header 40 is small, so that the inlet header 40 can be downsized. In addition, since the distance between the tubes of the first heat transfer tube portion 10 and the second heat transfer tube portion 20 in the portion inserted into the inlet header 40 becomes small, when the refrigerant is distributed to the tube group. It is possible to reduce the variation in the refrigerant flow rate. Therefore, when the heat exchanger 1 is used as an evaporator, it is possible to prevent the region of superheat from varying due to uneven distribution of the liquid refrigerant in the heat exchanger 1. This can prevent the heat exchange efficiency from decreasing.

Next, with reference to FIG. 8 and FIG. 9, the heat exchanger 1 in Modification 3 of the present embodiment will be described. FIG. 8 is a side view of the heat exchanger 1 in Modification 3 of the present embodiment. FIG. 9 is a cross-sectional view of the heat exchanger 1 in Modification 3 of the present embodiment.

As shown in FIGS. 8 and 9, in heat exchanger 1 of Modification 3 of the embodiment of the present invention, fins 30 include first fin portions 301 and second fin portions 302. The second fin portion 302 is arranged side by side with the first fin portion 301 in the direction in which the first heat transfer pipe portion 10 and the second heat transfer pipe portion 20 extend. That is, the first fin portion 301 and the second fin portion 302 are arranged side by side in the gravity direction D2. The first fin portion 301 and the second fin portion 302 include a valley portion 30a and a mountain portion 30b, respectively. The troughs 30a and the peaks 30b of the first fin portion 301 are opposite to the troughs 30a and the peaks 30b of the second fin portion 302 with respect to the first heat transfer tube 10 and the second heat transfer tube 20, respectively. It is located in. That is, the first fin portion 301 and the second fin portion 302 are alternately joined to the first heat transfer tube portion 10 and the second heat transfer tube portion 20 in the opposite directions. In the first fin portion 301 and the second fin portion 302, the respective arrangements of the first surface 31 and the second surface 32 are reversed.

According to the heat exchanger 1 in the third modification of the present embodiment, the valley portion 30a and the peak portion 30b of the first fin portion 301 are provided with respect to the first heat transfer pipe portion 10 and the second heat transfer pipe portion 20, respectively. The second fin portion is arranged on the opposite side of the valley portion 30a and the mountain portion 30b. Therefore, the first fin portion 301 and the second fin portion 302 are arranged in directions opposite to each other with respect to the first heat transfer tube portion 10 and the second heat transfer tube portion 20. Therefore, it is possible to prevent the forces acting on the first heat transfer tube section 10 and the second heat transfer tube section 20 from being biased in one direction. This makes it easy to vertically install the first heat transfer tube section 10 and the second heat transfer tube section 20, respectively.

Then, the manufacturing method of the heat exchanger 1 in the modification 3 of this Embodiment is demonstrated. The method for manufacturing the heat exchanger 1 according to Modification 3 of the present embodiment has the following configuration.

First, the fin 30 and the tube group including the first heat transfer tube section 10 and the second heat transfer tube section 20 are combined. Next, the fins 30 are pulled from both sides in the column direction D3 (width direction). As a result, the fins 30 are pulled in the column direction D3 (width direction). Subsequently, a tube group including the first heat transfer tube section 10 and the second heat transfer tube section 20 is inserted into the inlet header 40, the outlet header 50, and the row straddle header 80, respectively. Then, a brazing material is arranged at the joint between each tube group and each header, and brazing in the furnace is performed. By doing so, it is possible to provide the heat exchanger 1 which is easy to manufacture and has high jointability between the fin and the tube.

Next, with reference to FIG. 10, the heat exchanger 1 in Modification 4 of the present embodiment will be described. FIG. 10 is a cross-sectional view of the heat exchanger 1 in Modification 4 of the present embodiment.

As shown in FIG. 10, in the heat exchanger 1 according to Modification 4 of the embodiment of the present invention, the heat transfer units 100 adjacent to each other in the step direction D1 are displaced from each other in the column direction D3. Specifically, the heat transfer units 100 adjacent to each other in the step direction D1 have a dimension (half pitch) that is half the pitch (row pitch) between the first heat transfer tube portion 10 and the second heat transfer tube portion 20 in the row direction D3. Deviated.

According to the heat exchanger 1 in the fourth modification of the present embodiment, the first heat transfer tube portion 10 and the second heat transfer tube portion 20 of the heat transfer unit 100 that are adjacent to each other in the step direction D1 are displaced in the column direction D3. Therefore, as compared with the case where the first heat transfer tube portion 10 and the second heat transfer tube portion 20 of the heat transfer unit 100 that are adjacent to each other in the step direction D1 are not displaced in the column direction D3, the first heat transfer tube portions 10 and the second heat transfer tube portion 10 are not moved. Since the space between the heat transfer tube portions 20 can be increased, the ventilation resistance can be reduced. Therefore, the heat exchange efficiency can be improved. Further, the distance between the heat transfer units 100 can be reduced in the step direction D1.

Next, with reference to FIG. 6, a refrigerant circuit of the refrigeration cycle device 300 in the present embodiment will be described. FIG. 6 is a refrigerant circuit diagram of an air conditioning refrigeration apparatus as an example of refrigeration cycle apparatus 300 in the present embodiment.

As shown in FIG. 6, the air-conditioning refrigerating apparatus as an example of the refrigerating cycle apparatus 300 of the present embodiment has a compressor 33, a condensing heat exchanger 34, a throttle device 35, an evaporative heat exchanger 36, It is provided with a first blower 37 and a second blower 38. The compressor 33, the condensing heat exchanger 34, the expansion device 35, and the evaporative heat exchanger 36 are connected to each other via a pipe to form a refrigerant circuit. The refrigerant circulates through the refrigerant circuit in the order of the compressor 33, the condensation heat exchanger 34, the expansion device 35, and the evaporation heat exchanger 36, as shown by the arrow in the figure.

The compressor 33 is configured to compress the refrigerant. The compressor 33 is configured to circulate a refrigerant with the heat exchanger. The condensation heat exchanger 34 functions as a condenser and is configured to condense the refrigerant compressed by the compressor 33. The condensing heat exchanger 34 is provided with a first blower 37. The first blower 37 is configured to adjust the heat exchange amount between the refrigerant and the air in the condensation heat exchanger 34.

The expansion device 35 is configured to reduce the pressure of the refrigerant condensed by the condensation heat exchanger 34. The evaporation heat exchanger 36 functions as an evaporator, and is configured to evaporate the refrigerant decompressed by the expansion device 35. A second blower 38 is attached to the evaporation heat exchanger 36. The second blower 38 is configured to adjust the amount of heat exchange between the refrigerant and the air in the evaporation heat exchanger 36.

The heat exchanger 1 in the present embodiment described above can be used as either or both of the condensation heat exchanger 34 and the evaporation heat exchanger 36. Accordingly, it is possible to realize an air conditioning refrigeration system as an example of the refrigeration cycle system 300 having high energy efficiency. Here, the energy efficiency is defined by the following equation.

Heating energy efficiency=indoor heat exchanger (condenser) capacity/total input Cooling energy efficiency=indoor heat exchanger (evaporator) capacity/total input In addition, the heat exchanger 1 of the above-described present embodiment and the same are used. For an air conditioning refrigeration system as an example of the refrigeration cycle system, the effect can be achieved by using a refrigerant such as R410A, R32, HFO1234yf.

Further, although the example of air and refrigerant has been shown as the working fluid, the same effect can be obtained by using other gas, liquid, or gas-liquid mixed fluid.

Further, although the heat exchanger 1 in the above-described present embodiment is preferably used in an outdoor unit, the same effect can be obtained even when the heat exchanger 1 in the above-described present embodiment is used in an indoor unit. it can.

Regarding the heat exchanger 1 of the present embodiment and the air conditioning refrigeration apparatus as an example of the refrigeration cycle apparatus 300 using the heat exchanger 1, a mineral oil type, an alkylbenzene oil type, an ester oil type, an ether oil type, a fluorine oil type is used. The effect of any refrigerating machine oil can be achieved regardless of whether or not the refrigerant and the oil melt.

According to refrigeration cycle apparatus 300 in the present embodiment, at least one of condensation heat exchanger 34 and evaporation heat exchanger 36 as heat exchanger 1, and condensation heat exchanger 34 and evaporation as heat exchanger 1 described above. A compressor 33 that circulates a refrigerant with at least one of the heat exchangers 36 is provided. Therefore, it is possible to provide the refrigeration cycle apparatus 300 in which the heat exchanger 1 can be easily manufactured.

The embodiment disclosed this time is an example, and the present invention is not limited to this. The present invention is shown not by the scope described above but by the claims, and is intended to include all modifications within the meaning and range equivalent to the claims.

DESCRIPTION OF SYMBOLS 1 heat exchanger, 10 1st heat transfer tube part, 11 1st heat transfer tube, 20 2nd heat transfer tube part, 21 2nd heat transfer tube, 30 fins, 30a valley part, 30a1 valley, 30b mountain part, 30b1 mountain, 30c wind Upper extension part, 30d Downward extension part, 31 1st surface, 32 2nd surface, 33 Compressor, 34 Condensation heat exchanger, 35 Throttling device, 36 Evaporation heat exchanger, 37 1st blower, 38 2nd Blower, 40 inlet header, 50 outlet header, 60 inlet pipe, 70 outlet pipe, 80 header, 100, 101, 102 heat transfer unit, 300 refrigeration cycle device, 301 first fin portion, 302 second fin portion, D1 stage Direction, D2 gravity direction, D3 row direction.

Claims (7)

A first heat transfer tube section,
A second heat transfer tube section arranged so as to run parallel to the first heat transfer tube section;
And a corrugated fin having valleys and peaks,
The fin includes a first surface and a second surface opposite to the first surface,
The valley portion is configured such that the fin protrudes in a direction from the first surface toward the second surface,
The mountain portion is configured such that the fins protrude in a direction from the second surface toward the first surface,
The first heat transfer tube portion is connected to the valley portion on the first surface of the fin,
The second heat transfer tube portion is connected to the mountain portion on the second surface of the fin,
The valley portion and the mountain portion are arranged side by side along the wind direction of the wind flowing into the fin ,
The fin is a windward extension portion that extends straight upwind from any one of the valley portion and the mountain portion arranged on the most windward side of the wind in the direction in which the valley portion and the mountain portion are arranged. Including a heat exchanger. The heat exchanger according to claim 1, wherein each of the first heat transfer tube section, the second heat transfer tube section, and the fin extends in the direction of gravity. The fin comprises a downwind extending portion extending immediately repaired toward the downwind from any of the valleys and the ridges are arranged closest downwind of the wind, in any one of claims 1 or 2 The heat exchanger described. The fin is integrally configured of a plate heat exchanger according to any one of claims 1-3. It said first heat transfer tube portion, said second respective heat transfer tube portion and the fins are made of the same material, the heat exchanger according to any one of claims 1-4. The fin includes a first fin portion and a second fin portion arranged side by side with the first fin portion in a direction in which the first heat transfer pipe portion and the second heat transfer pipe portion extend,
The troughs and peaks of the first fin section are opposite to the troughs and peaks of the second fin section with respect to the first heat transfer tube section and the second heat transfer tube section, respectively. is arranged, the heat exchanger according to any one of claims 1-5. A heat exchanger according to any one of claims 1 to 6
A refrigeration cycle apparatus comprising: a compressor that circulates a refrigerant between the heat exchanger and the heat exchanger.

Images