JPH09112942A - Heat exchanger and air conditioner having the heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a heat exchanging efficiency by a method wherein a turbulent flow which is high enough to break an air temperature interface layer is generated against air flowing at three mountain-shaped parts of a fin surface. SOLUTION: Two mountain-shaped parts 76, 76 projected along an air blowing direction and a flat part 78 arranged between these mountain-shaped parts are formed at a fin 71 of a heat exchanger, so that it is possible to generate a turbulent flow high enough to break an air temperature interface layer against air flowing at a surface of the fin and further it is also possible to improve a heat exchanging efficiency, resulting in that an air plowing resistance does not become excessive and so a heat exchanging efficiency of an entire heat exchanger can be improved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger having a plurality of laminated fins through which refrigerant tubes are inserted, or an air conditioner including the heat exchanger.

[0002]

2. Description of the Related Art For example, in a heat pump type air conditioner, during cooling operation, a refrigerant is circulated in the order of a compressor, a heat source side heat exchanger, a flow rate control valve, a utilization side heat exchanger, and a four-way switching valve to heat the air. While the refrigerant is circulated in the opposite direction to the cooling operation during the operation, the heat source side heat exchanger acts as an evaporator during the heating operation, and the heat source side evaporator acts as a condenser during the cooling operation.

In such a heat exchanger, various proposals regarding the shape of the fins have been made in order to improve the heat exchange efficiency. For example, as a fin having a concavo-convex shape on its surface, conventionally known is a fin having two chevron portions continuously protruding in the air blowing direction (width direction of the fin).

[0004]

However, in the fin in which two continuous chevron portions are formed as in the conventional case, sufficient turbulent flow cannot be generated in the air passing through the fin, and the temperature boundary of the air is not reached. There is a problem that the layer remains and the heat exchange rate is not sufficient.

On the other hand, it is conceivable that a large number of chevron portions are formed on the fin surface to form a sufficient turbulent flow for the wind passing through the fin surface. If the part is formed, the air flow resistance is too large,
On the contrary, there is a disadvantage that the heat exchange efficiency is lowered.

Further, as the refrigerant to be filled in the refrigerant circuit,
Conventionally, R-12 and R-50 having a chlorine group were used,
Because of the potential for depleting the ozone layer above the ground, R-22 (chlorodifluoromethane), which has a low chlorine group content, and R-32, which does not contain a chlorine group, are included for the purpose of environmental protection.
(Difluoromethane), R-125 (pentafluoroethane), R-134a (tetrafluoroethane), or a mixture thereof (hereinafter referred to as "HFC-based refrigerant") is used as an alternative refrigerant.

When such an HFC type refrigerant is used as the refrigerant, the property of the mixed refrigerant is high pressure and high temperature. Therefore, in order to prevent abnormal high pressure and high temperature in the refrigerant circuit, the heat exchanger is used. Therefore, it is desired to improve heat exchange efficiency higher than ever before.

Therefore, the present invention has been made to solve the above problems, and provides a heat exchanger capable of improving the heat exchange rate and an air conditioner equipped with the heat exchanger.

[0009]

According to a first aspect of the present invention, in a heat exchanger having a plurality of laminated fins through which refrigerant tubes are inserted, the fins are provided so as to project along the air blowing direction. Individual chevron portions and flat portions that are provided flat between the chevron portions are formed.

According to the heat exchanger of claim 1,
By forming two chevron portions on the fin surface and a flat portion between these chevron portions, the air flowing along the fin surface has sufficient turbulence to destroy the temperature boundary layer of the air. While the flow can be generated and the heat exchange rate can be improved, the ventilation resistance does not become excessive and the heat exchange rate can be improved for the entire heat exchanger.

Further, by forming the flat portion, water drainage becomes good, and frost is less likely to form. For example, in the defrosting operation, when the heat exchanger according to the present invention is used as an outdoor unit, the water is well drained during defrosting, the influence of the latent heat of the water is reduced, and then the heating operation is resumed. In addition, the effect on thermal efficiency is not small.

According to a second aspect of the present invention, in a heat exchanger in which a plurality of laminated fins are inserted with refrigerant pipes, the fins have two chevron portions projecting along the air blowing direction. And a flat portion provided between these chevron portions are formed, the width of the fin is 2 to 3 times the pipe diameter of the refrigerant pipe, and the width of the flat portion is the chevron portion. And the height of the chevron is 1/8 to 1/9 times the width of the chevron.

In the present specification, the "width" means the air blowing direction with respect to the fins.

According to the second aspect of the present invention, the width of the fins is set to be 2 to 3 times the width of the refrigerant pipe, so that the heat exchange efficiency based on the temperature difference between the air and the fins in heat exchange is maximized. The fin width can be minimized. That is, if the width of the fins is less than twice the width of the refrigerant pipe, a sufficient heat exchange area cannot be obtained, and if the width of the fins is more than three times, the fin width is too long and the temperature difference between the blown air and the fins is small. Nevertheless, it will grow unnecessarily.

The width of the flat portion interposed between the two chevron portions is half the width of the chevron portion, and the height of the chevron portion is 1/8 to 1/9 of the width of the chevron portion. By doubling it, the air flowing on the surface can be a turbulent flow to the extent that it destroys the temperature boundary layer, but the blast resistance can be minimized.

The invention according to claim 3 is an air conditioner configured to circulate a refrigerant in a refrigerant circuit having a compressor, a use side heat exchanger, a pressure reducing device, and a heat source side heat exchanger. At least one of the heat exchanger on the side and the heat exchanger on the heat source side is formed by inserting a refrigerant pipe into a large number of laminated fins, and the fins are provided so as to protrude along the air blowing direction. Two mountain-shaped portions and a flat portion that is provided flat between these mountain-shaped portions are formed.

According to the invention described in claim 3, claim 1
Since the heat exchanger described in (1) is used in an air conditioner, an air conditioner excellent in heat exchange efficiency can be obtained and the air conditioning operation capacity can be enhanced. In particular, in such an air conditioner, an HFC-based refrigerant having a high temperature during operation can be used as the refrigerant.

[0018]

Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.

FIG. 1 is a perspective view showing a general household air conditioner. This type of air conditioner is composed of a use side unit A arranged indoors and a heat source side unit B arranged outdoors, both of which are connected by a refrigerant pipe 300.

FIG. 2 is a refrigerant circuit diagram showing a refrigeration cycle of the air conditioner shown in FIG.

Reference numeral 1 denotes a compressor including a motor section and a compression section driven by the motor section. Reference numeral 2 is a muffler for suppressing vibration and noise due to pulsation of the refrigerant discharged from the compressor 1. Reference numeral 3 is a four-way switching valve for switching the flow of refrigerant during cooling / heating operation. 4 is a heat source side heat exchanger, 5 is a capillary tube unit, 6 is a screen filter, 7 is a use side heat exchanger, 8 is a muffler,
9 is an accumulator and 10 is an electromagnetic on-off valve.

The refrigerant discharged from the compressor 1 is indicated by a solid line arrow (cooling operation), a dotted line arrow (heating operation), and a solid line in accordance with the switching position of the four-way switching valve 3 and the opening / closing of the electromagnetic opening / closing valve 10. Like the dotted arrow (defrosting operation), the flow direction is determined according to the three modes. During cooling operation,
The heat source side heat exchanger 4 functions as a condenser, and the use side heat exchanger 7 functions as an evaporator. During the heating operation, the use side heat exchanger 7 functions as a condenser and the heat source side heat exchanger 4 functions as an evaporator. During the defrosting operation (during the heating operation), a part of the high-temperature refrigerant discharged from the compressor 1 is directly supplied to the heat source side heat exchanger 4 in order to raise the temperature of the heat source side heat exchanger 4. Is done. As a result, the temperature of the heat source side heat exchanger 4 rises and defrosting is performed. When the defrosting operation does not function sufficiently (especially when the outside air temperature is low), defrosting is forcibly performed by reverse cycle defrosting (flow indicated by a solid arrow).

FIG. 3 is a control circuit diagram of the air conditioner.
The left side shows the control circuit of the utilization side unit A, and the right side shows the control circuit of the heat source side unit B with the dashed line in the center of FIG. 3 as the boundary. Both control circuits have power line 10
0 and the control line 200.

The user side unit A includes a rectifying circuit 11 and
A power supply circuit 12 for the motor, a power supply circuit 13 for the control, a motor drive circuit 15, a switch board 17,
The receiving circuit 18a, the display board 18, and the flap motor 1
9 and 9 are provided.

The rectifying circuit 11 rectifies the 100V AC voltage supplied by the plug 10a. The motor power supply circuit 12 adjusts the DC voltage supplied to the DC fan motor 16 to a voltage of 10 to 36V. The DC fan motor 16 is for blowing out conditioned air into the room to be conditioned according to a signal sent from the microcomputer 14.

The control power supply circuit 13 generates a DC voltage of 5V to be supplied to the microcomputer 14. The motor drive circuit 15 responds to a signal from the microcomputer 14 based on the rotational position information of the DC fan motor 16 to control the timing of energizing the stator winding of the DC fan motor 16. The switch board 17 is fixed to the operation panel of the utilization side unit A, and the switch board 17 is provided with an on / off switch, a trial run switch, and the like. The receiving circuit 18a receives a remote operation signal (for example, an on / off signal, a cooling / heating switching signal, a room temperature setting signal, or the like) from the wireless remote controller 60. The display board 18 displays the operating state of the air conditioner. The flap motor 19 functions to move a flap that changes the blowing direction of cold / warm air.

Further, the control circuit includes a room temperature sensor 20 for measuring the room temperature, a heat exchanger temperature sensor 21 for measuring the temperature of the utilization side heat exchanger, and a room humidity sensor. A humidity sensor 22 is provided. The measured values detected by these sensors are A / D converted and taken into the microcomputer 14. The control signal from the microcomputer 14 is sent to the heat source side unit B through the serial circuit 23 and the terminal board T ₃ . Further, the triac 26 and the heater relay 27 are controlled by the microcomputer 14 through the driver 24, thereby stepwise controlling the electric power supplied to the reheat heater 25 used during the dry operation.

Reference numeral 30 is an external ROM that stores specific data indicating the type and characteristics of the air conditioner. These specific data are taken out from the external ROM immediately after the power switch is input and the operation is stopped. When the power switch is input, commands are input from the wireless remote controller 60 or ON / OFF until the extraction of specific data from the external ROM 30 is completed.
The state of the switch or the trial run switch (operation will be described later) is not detected.

Next, the control circuit of the heat source side unit B will be described.

In the heat source side unit B, the terminal board T
_{'1, T'2, T'3} are connected to each use-side unit terminal plate T ₁ arranged in A, T _2, T _3.
Reference numeral 31 is a varistor connected in parallel terminal plate _T'1 and the _T'2, 32 is a noise filter, 34 is a reactor, 35 is voltage doubler for the voltage doubling, 36 noise filter 37 is 100V AC voltage to about 280V DC
It is a ripple filter for obtaining a voltage.

Reference numeral 39 is a serial circuit for converting the control signal supplied from the user side unit A through the terminal board T'3, and the converted signal is transmitted to the microcomputer 41. 40 is the heat source side unit B
And a current detector that detects the current supplied to the load in the current transformer (CT) 33, rectifies the current into a DC voltage, and applies the DC voltage to the microcomputer 41.
41 is a microcomputer, 42 is a switching power supply circuit for generating power for operating the microcomputer 41, 38 is PW of power supplied to the compressor 1 based on a control signal from the microcomputer 41.
It is a motor driver that achieves M control. The six power transistors of the motor driver 38 are connected in the form of a three-phase bridge to form a so-called inverter unit. Reference numeral 43 is a compressor motor for operating the compressor 1 of the refrigeration cycle, and 44 is a supply temperature sensor for detecting the temperature of the refrigerant on the supply side of the compressor. Reference numeral 45 is a fan motor that controls the speed in three stages and sends air to the outdoor heat exchanger, and the four-way switching valve 3 and the solenoid valve 10 switch the refrigerant passage of the refrigeration cycle as described above. Further, the heat source side unit B has an outdoor temperature sensor 4 for detecting the outdoor temperature.
8 is arranged in the vicinity of the air intake port, and an outdoor heat exchanger temperature sensor 49 for detecting the temperature of the outdoor heat exchanger is arranged. The detected values obtained by these temperature sensors 48, 49 are A / D converted and are taken into the microcomputer 41.

Reference numeral 50 is an external ROM of the user side unit A.
It is an external ROM having the same function as 30. The specific data of the heat source side unit B is the same as that described for the external ROM 30, but is stored in the ROM 50.

The symbol F in each control circuit of the heat source side unit B and the use side unit A is a fuse.

Each of the microcomputers (control members) 14 and 41 is a ROM storing a program in advance,
A RAM that stores reference data and a CPU that calculates a program are stored in the same container (87C196MC (MC sold by Intel Corporation).
S-96 series)).

Next, the refrigerant will be described.

In the present embodiment, either a single refrigerant or a mixed refrigerant can be used, but in this embodiment, the mixed refrigerant will be described as an example. In the present specification, the "mixed refrigerant" means a refrigerant in which at least two kinds of refrigerants having different characteristics are mixed.

As the mixed refrigerant, for example, R-410A or R-410B is used. R-410A is a two-component mixed refrigerant, which contains R-32 at 50 wt% and R-125.
Is 50 Wt%, the boiling point is −52.2 ° C., and the dew point is −52.2 ° C. R-410B is R-32
Is 45 Wt% and R-125 is 55 Wt%.

In the mixed refrigerant having such a composition, HCFC
When compared with the conventional single refrigerant of -22, the discharge temperature of the compressor under the predetermined conditions is 66.0 ° C for HCFC-22 and 73.6 ° C for R-410A, and the condensing pressure is 17.35 bar for HCFC-22
In contrast, the R-410A has a characteristic of 27.30 bar, and the evaporation pressure of the HCFC-22 has a characteristic of 6.79 bar, whereas the R-410A has a characteristic of 10.86 bar. Conventional HCFC-
Higher temperature and higher pressure than when using 22 single refrigerants.

When an azeotropic mixed refrigerant such as R-410A and R-410B is used, the refrigerants of the respective components have almost the same boiling points, so that the refrigerant composition hardly changes and the refrigerant composition There is no need to consider problems such as temperature glide caused by changes. Therefore, control during driving becomes easy.

The brackets in the refrigerant circuit of FIG.
It shows the dimensions of the refrigerant line. That is, in the refrigerant circuit of FIG. 2, the dimension example of the refrigerant pipe between the four-way switching valve 3 and the use side heat exchanger 7 is 3/8 ″ (inch), and the use side heat exchanger 7 and the strainer 6 are The size of the refrigerant pipe between is 1 /
4 "(inch), the size of the refrigerant pipe between the decompressor 5 and the heat source side heat exchanger 4 is 1/4" (inch), and the size of the bypass pipe of the heat source side heat exchanger 4 is 1/8 " (Inch), the size of the refrigerant pipe between the four-way switching valve 2 and the accumulator 7 is
3/8 "or 1/2" (inch), and the size of the refrigerant pipe between the four-way switching valve and the heat source side heat exchanger 4 is 3/8 "(inch). Such a refrigerant pipe in a refrigerant circuit The size of is not particularly limited, but in relation to the refrigerant pipe inserted into the heat exchanger, according to the size of the refrigerant pipe of the refrigerant circuit according to the present embodiment, as a result, the most efficient air is obtained. I was able to obtain a harmony machine (heat exchanger).

Next, the heat exchanger according to the present invention can be used for both the use side heat exchanger (indoor heat exchanger) 7 and the heat source side heat exchanger (outdoor heat exchanger) 4. Especially,
An example of use in the usage-side heat exchanger 7, which requires high heat exchange efficiency in relation to the air flow rate, will be described.

As shown in FIG. 4, the heat exchanger 7 is constructed by laminating a large number of fin bodies 71. A refrigerant pipe 82 is inserted through the laminated fin bodies 71, and the refrigerant pipe 82 meanders. Are arranged.

In this embodiment, the refrigerant pipe 82 has a diameter of 7 mm.
However, the pipe is not limited to this, and a pipe having another diameter such as 9 mm may be used. Note that, as shown in FIGS. 5 and 7, the pitch D of the refrigerant pipe 82 is not particularly limited, but as a result of the experiment, the heat exchange rate was the most excellent value, so in this embodiment, it is about 21 mm. And

In the present embodiment, the fin body 71 has two rows of fins 71a and 71b continuously formed in one plate in the air blowing direction to form one fin body 71. May be In other words, as shown in FIGS. 5 and 6, the fin body 71 has two fins 71a,
71b arranged in parallel are simultaneously formed.

As the material of the fin body 71, one having a good heat conduction characteristic is used, for example, aluminum is used.

The fin pitch FP, which is the distance between the stacked fin bodies 71 and 71, was the most excellent value of the heat exchange rate as a result of the experiment. Therefore, the fin pitch FP is preferably set to 1.2 to 1.6 mm. To be done. As shown in FIG. 5, the fin body 71 has fins 71a and 71b, and the through-holes 74 for the refrigerant pipes are formed in a row so that the refrigerant pipes 82 are alternately arranged in a staggered manner. Has been done. The pipe through hole 74 is defined by a protruding portion 75 as shown in FIG. 6, and the height H of the protruding portion 75 defines the fin pitch FP.

As shown in FIG. 6, each of the fins 71a and 71b is provided with two chevron portions 76 along the air blowing direction.
8 are formed in between to improve the heat exchange efficiency.

Here, the dimensions of each part of the fin body 71 will be described. The width of each of the fins 71a and 71b is determined in consideration of the heat exchange efficiency and the demand for miniaturization, but in the present embodiment, the value of the heat exchange rate is the most excellent as a result of the experiment, and therefore it is preferably 18 To 19 mm. Fin 71
The balance of heat exchange efficiency in determining a and 71b means, as shown in FIG. 9, the distance from the center of the refrigerant pipe to the edge portion in the width direction of the fin (half the fin width) is taken as the horizontal axis,
When the temperature of the wind passing through the fins is plotted on the vertical axis, the heat exchange efficiency decreases as the temperature difference between the fin surface and the wind decreases.

Therefore, in FIG. 9, since the temperature difference between the wind and the fins is small, it is preferable to set the distance to the T0 portion where the temperature decrease of the wind can hardly be expected to half S2 of the fin width. As shown by S1, if the distance (fin width) is shorter than the T0 portion, the temperature of the wind cannot be sufficiently lowered, and even if the distance (fin width) is made longer than the T0 portion, the temperature of the wind that has already passed through. Is sufficiently lowered, it is impossible to expect high heat exchange efficiency (temperature drop) even if the distance is made longer.

In this embodiment, T0 when the temperature is lowered by 6 ° C. is obtained and the distance S2 is adopted. This S2
The value obtained by doubling is adopted as the width S of the fin 71a (or the fin 71b) to be 18.19 mm.

Regarding the formation width W of each chevron portion 76 in the effective width S of the fins 71a and 71b, as shown in FIG. 6, a flat edge portion 77 is provided so as to guide the wind flow in the width direction.
As for the portion where is left, a chevron portion and a flat portion are formed, and the dimension S of the edge portion 77 is, for example, 0.8 mm,
The formation width W of each chevron portion 76 is 18.19−0.8 × 2 =
It will be 16.59 mm.

In this formation width W, two chevron portions 76 and
The flat portion 78 is formed between the two chevron portions, and as a result of the experiment, the width W3 of the flat portion is half the width W2 of one chevron portion, that is, (W2) / 2. The heat exchange efficiency was the best.

Specifically, the width W2 of one chevron is 6.
It is 636 mm and the width W3 of the flat portion is 3.318 mm.

Height H1 of chevron portion 76 formed on the fin
May be increased so as to provide a resistance that causes turbulent flow to the extent that the passing wind destroys the temperature boundary layer.
When 6 is too high, the pressure loss becomes too large, and the heat exchange efficiency is rather lowered. The height H1 of the chevron portion 76 is determined from this relationship, but the height H1 of the chevron portion 76 is determined.
The dimensional ratio (H1 / W
In the case of 2), the width of the chevron portion 76 was ⅛ to 1/9 times as large as the turbulent flow to destroy the temperature boundary layer, and the blast resistance could be minimized. Specifically, Yamagata 7
The dimension of the height H1 of 6 was the most excellent value of the heat exchange rate in the result of the experiment, and therefore, it is preferably 0.5 to 1.0.
mm, and the most excellent value among them is 0.8 mm in the present embodiment. The dimensional ratio (H1 / W2) of the height H1 of the chevron portion 76 to the formation width W2 of the chevron portion 76 is about 1/8.

It should be noted that each of the peaks and valleys of the Yamagata part is R.
(R) is formed, which facilitates manufacturing.

Next, the operation of the embodiment will be described.

During the cooling operation, as shown by the solid arrow in FIG. 2, the refrigerant discharged from the compressor 1 includes a muffler 2, a four-way switching valve 3, a heat source side heat exchanger (outdoor heat exchanger) 4, a capillary tube. 5, the screen filter 6, the use side heat exchanger (indoor heat exchanger) 7, the muffler 8, the four-way switching valve 3, and the accumulator 9 circulate through the refrigerant circuit in this order, and the use side heat exchanger 7 functions as an evaporator. The pressure is reduced by the capillary tube 5. During the heating operation, the refrigerant discharged from the compressor 1 is
Four-way switching valve 3, muffler 8, utilization side heat exchanger (indoor heat exchanger) 7, screen filter 6, capillary tube 5, heat source side heat exchanger (outdoor heat exchanger) 4, four-way switching valve 3, accumulator 9 The heat source side heat exchanger 4 circulates in the refrigerant circuit in order, functions as an evaporator, and is decompressed by the electric expansion valve 5.

During the cooling operation or the heating operation, the fan is blown to the use side heat exchanger (indoor heat exchanger) 7 to exchange heat between the refrigerant passing through the refrigerant pipe and the air.
In the present embodiment, the air blown to the heat exchanger 7 passes between the stacked fin bodies 71, 71 for heat exchange.

When air passes between the fin bodies 71, 71, the air passing through the two chevron portions 76 and the flat portion 78 between these chevron portions 76 is turbulent enough to break the temperature boundary layer of the air. In addition, since the pressure loss is not too large, a high heat exchange rate can be obtained. As a result, the air conditioning operation capacity of the air conditioner can be improved.

Particularly, when an HFC type refrigerant is used as the refrigerant, the refrigerant circuit is in a high pressure and temperature state, but even in that case, sufficient heat exchange with the indoor air or the outdoor air is performed in the heat exchanger. Can be planned.

Further, by forming the flat portion, drainage becomes good and frost is less likely to form.

The present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the scope of the claims. For example, in the above-described embodiment, the air conditioner has been described as an example. However, the heat exchanger according to the present invention is not limited to this, and can be used in a refrigerator such as a refrigerator.

[0063]

According to the invention described in claim 1, two fins are formed in the fin of the heat exchanger along the air blowing direction,
Since the flat portion is formed between these chevron portions, it is possible to generate sufficient turbulence for the air flowing through the three chevron portions on the fin surface to the extent that the temperature boundary layer of air is destroyed. While the heat exchange rate can be improved, the ventilation resistance does not become excessive, and the heat exchange rate of the heat exchanger as a whole can be improved. Further, by forming the flat portion, drainage becomes good, and frost does not easily form.

According to the invention described in claim 2, according to claim 1
In the fin, the width of the fin is 2 to 3 times the diameter of the refrigerant pipe, the width of the flat portion is half the width of the chevron portion, and the height of the chevron portion is the width of the chevron portion. Since it is 1/8 to 1/9 times, the fin width can be minimized while maximizing the heat exchange efficiency based on the temperature difference between the air and the fins in heat exchange.

According to the invention of claim 3, claim 1
Since the heat exchanger described in (1) is used in an air conditioner, an air conditioner excellent in heat exchange efficiency can be obtained and the air conditioning operation capacity can be enhanced. In particular, in such an air conditioner, an HFC-based refrigerant having a high temperature can be used as the refrigerant.

[Brief description of the drawings]

FIG. 1 is a diagram showing an outline of an air conditioner of the present invention.

FIG. 2 is a diagram showing a refrigerant circuit of the air conditioner of the present invention.

FIG. 3 is a control circuit diagram of the refrigerant circuit of FIG.

FIG. 4 is a perspective view showing an example of a heat exchanger of a refrigerant circuit.

FIG. 5 is a plan view showing an example of fins of the heat exchanger of the refrigerant circuit.

6 is an enlarged cross-sectional view taken along line A1-A1 of the fin body shown in FIG.

FIG. 7 is a plan view showing a part of the fin body of FIG.

FIG. 8 is a cross-sectional view showing an outline of a fin.

FIG. 9 is a graph showing the relationship between the fin width and the temperature of blown air.

[Explanation of symbols]

 1 Compressor 4 Outdoor Heat Exchanger (Heat Exchanger) 5 Capillary Tube (Decompression Device) 7 Indoor Heat Exchanger (Heat Exchanger) 71a, 71b Fins 76 Angle Section 78 Flat Section

 ─────────────────────────────────────────────────── ─── Continued Front Page (72) Inventor Yoshinori Toya 2-5-5 Keihanhondori, Moriguchi-shi, Osaka Sanyo Denki Co., Ltd. (72) Inventor Masahiro Kobayashi 2-chome, Keihanhondori, Moriguchi-shi, Osaka 5 Sanyo Electric Co., Ltd. (72) Inventor Atsumi Ishikawa 2-5-5 Keihan Hondori, Moriguchi City, Osaka Prefecture 5-5 Sanyo Electric Co., Ltd. (72) Inventor Yoshitaka Hara 2-5 Keihan Hondori, Moriguchi City, Osaka Prefecture Address No. 5 Sanyo Electric Co., Ltd.

Claims (3)

[Claims] 1. A heat exchanger in which a plurality of laminated fins are inserted with refrigerant pipes, wherein the fins are provided with two chevron portions projecting along the air-blowing direction and these chevron portions. A heat exchanger characterized in that a flat portion provided flat is formed therebetween. 2. In a heat exchanger having a plurality of laminated fins through which refrigerant pipes are inserted, the fins are provided with two chevron portions projecting along the air-blowing direction, and these chevron portions. And the width of the fin is 2 to 3 times the diameter of the refrigerant pipe, and the width of the flat portion is half the width of the chevron portion. And the height of the chevron is 1/8 to 1/9 times the width of the chevron. 3. An air conditioner configured to circulate a refrigerant in a refrigerant circuit having a compressor, a use side heat exchanger, a pressure reducing device, and a heat source side heat exchanger, wherein the use side heat exchanger and the heat source. At least one of the side heat exchangers has a refrigerant pipe inserted through a large number of laminated fins, and the fins have two chevron portions projecting along the air blowing direction. An air conditioner characterized in that a flat portion that is provided flat is formed between these chevron portions.