JPH10220919A - Condenser - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent lubricant mixed in refrigerant from being accumulated in a condenser. SOLUTION: In a vertical flowing type condenser, a total flow passage area of first heat transfer pipes 19a, 19a where refrigerant flows down is made wider than a total flow passage area of second heat transfer pipes 20a, 20a where refrigerant is lifted up. Further, a total flow passage area of the second heat transfer pipes 21a, 21a is made less than a total flow passage area of third heat transfer pipes 21a, 21a where refrigerant is flowed down. Alternatively, inner fins becoming a relative large resistance against the flow of the refrigerant are arranged inside both third heat transfer pipes 19a, 21a. No such inner fins are arranged inside the second heat transfer pipe 20a.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to, for example, a liquid crystal device which is incorporated in series between a compressor and an evaporator of a vapor compression refrigerator constituting an air conditioner for an automobile, and radiates and condenses the refrigerant compressed by the compressor. The present invention relates to an improvement in a condenser to be sent to an evaporator through a tank.

[0002]

2. Description of the Related Art A vapor compression refrigerator is incorporated in an automotive air conditioner for cooling and dehumidifying the interior of an automobile.
FIG. 8 is a circuit diagram showing a basic configuration of a vapor compression refrigerator described in Japanese Patent Application Laid-Open No. 4-95522. The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 exchanges heat with air while passing through the condenser 2 to lower the temperature and condense and liquefy. The resulting liquid refrigerant is once stored in the liquid tank 3, sent to the evaporator 5 via the expansion valve 4, and evaporates in the evaporator 5. Since the temperature of the evaporator 5 decreases due to the deprivation of latent heat of vaporization, the flow of air for air-conditioning through the evaporator 5 reduces the temperature of the air and simultaneously removes the water vapor contained in the air. Can be. The refrigerant evaporated and vaporized in the evaporator 5 is sucked by the compressor 1 and compressed, and the cycle is repeated again.

FIG. 9 shows a capacitor 2 to which the present invention is applied. This condenser 2 is of a so-called vertical flow type, in which a refrigerant flows vertically between a pair of upper and lower headers 6a and 6b which are arranged in the horizontal direction at an interval vertically. Such a vertical flow type capacitor 2
Research has been conducted to share the fins with the core of a radiator (not shown) that is installed in the vicinity and to make the condenser 2 and the radiator compact. Inside each of the headers 6a and 6b constituting the capacitor 2,
Each of the headers 6a,
The inside of 6b is partitioned into a plurality of chambers while keeping the inside airtight and liquidtight. The partition includes an upper partition 13 that partitions the inside of the upper header 6a into two chambers, a first upper chamber 15 and a second upper chamber 16, and a first lower chamber 17 and a second lower chamber that partition the inside of the lower header 6b. 18 and a lower partition wall 14 for partitioning into two chambers.
The heat transfer tubes 7 constituting the condenser 2 sandwich fins 8 between the pair of headers 6a and 6b and the heat transfer tubes 7 adjacent to each other in the horizontal direction. In the state, they are arranged vertically. These heat transfer tubes 7, 7
And the fins 8 constitute a core portion 9. As shown in FIG. 9, each of the heat transfer tubes 7, 7 has a plurality of first heat transfer tubes 19, each having an upper end communicating with the first upper chamber 15 and a lower end communicating with the first lower chamber 17. , 19, a plurality of second heat transfer tubes 20, 20 having an upper end communicating with the second upper chamber 16, and a lower end communicating with the first lower chamber 17, respectively. 16, a plurality of third heat transfer tubes 21 each having a lower end portion connected to the second lower chamber 18,
21 and the upper and lower partitions 13 and 14. Among these, the first heat transfer tubes 19, 19 are a plurality of heat transfer tubes 7, 7 located at the most upstream side, and allow the refrigerant to flow downward. Each of the second heat transfer tubes 20, 20 is a plurality of heat transfer tubes 7, 7 existing in an intermediate portion, and allows the refrigerant to flow upward. Further, the third heat transfer tubes 21, 21 are a plurality of heat transfer tubes 7, 7 located at the most downstream side, and allow the refrigerant to flow downward. These first to third heat transfer tubes 19, 20, 2
1, and different from the number of heat transfer tubes 7, 7 corresponding to the respective total S of the sum S ₁₉ of the flow passage area of the first heat exchanger tube 19, 19 flow passage area of each of the second heat exchanger tube 20, 20 _{20 and} the sum S of the flow passage areas of the second heat transfer tubes 20, 20.
₂₀ is the total S ₂₁ of the flow passage areas of the third heat transfer tubes 21, _21.
Is wider than. That is, each of the first to third heat transfer tubes 19,
Total S ₁₉ of the flow passage area of 20 and 21, the S _20, S _21, S ₁₉
> S ₂₀ > S ₂₁ in this order. Also, FIG.
0, the sum S ₁₉ , S ₂₀ , S ₂₁ of the flow area of each of the first to third heat transfer tubes ₁₉ , ₂₀ , ₂₁ is represented by S ₁₉ = S ₂₀ = S _21.
In some cases, the number of heat transfer tubes 7 corresponding to the first to third heat transfer tubes 19, 20, 21 is the same. In any case, side plates 10a and 10b are provided at the left and right end edges of the core portion 9 including the heat transfer tubes 7 and fins 8 and 8, respectively.

[0004] One end of the upper header 6a (FIGS. 9 to 10).
An entrance block 11 is brazed and fixed to the upper surface of the right end portion of FIG. The inlet block 11 is provided with an inlet port 12 serving as a refrigerant inlet.
2 communicates with the inside of the first upper chamber 15. The refrigerant sent from the inlet port 12 is shown in FIGS.
As shown by the arrow in FIG. 3, the air flows in the vertical direction while folding back the portion between the pair of headers 6a and 6b.

Further, the other end of the lower header 6b (FIG. 9)
A discharge port (not shown) is provided in a part (a part corresponding to the second lower chamber 18 in the example of FIGS. 9 to 10) corresponding to the chamber located at the most downstream side in the (left end of the 10) portion. . It flows into the condenser 2 and the inside of the condenser 2 is shown in FIGS.
The refrigerant flowing as shown by the arrow in FIG.
Reaches the inside of the other end. The refrigerant is discharged from the discharge port, passes through the liquid tank 3 and the expansion valve 4,
It is sent to the evaporator 5 (see FIG. 8).

The capacitor 2 constructed and operates as described above
The refrigerant sent from the compressor 1 (see FIG. 8) passes through the inside of the inside while being condensed and liquefied. Further, the lubricating oil of the compressor, which is a mineral oil or a synthetic oil, is mixed in the liquid refrigerant passing through the inside of the condenser 2 as described above.

[0007]

In the above-mentioned conventional capacitor, the first lower chamber 17 is formed by a part of the upper header 6b.
The lubricating oil easily accumulates in the vicinity of the lower partition wall 14 that separates the lubricating oil from the second lower chamber 18 (see the hatched portions in FIGS. 9 to 10). This is because the refrigerant flowing in the first heat transfer tubes 19 and 19 and entering the first lower chamber 17 presses the lubricating oil against the lower partition wall 14 and enters the second heat transfer tubes 20 and 20. This is because the second heat transfer tubes 20, 20 flow upward. If the flow rate of the refrigerant flowing toward the lower partition wall 14 in the first lower chamber 17 is high, the lubricating oil can be pushed into the second heat transfer tubes 20, 20, but in the case of the conventional structure shown in FIGS. However, this flow rate is not sufficient. As a result, the lubricating oil mixed in the refrigerant does not rise in the second heat transfer tubes 20, 20 together with the refrigerant, and the lower header 6b
Will accumulate in a portion near the lower partition wall 14. As described above, the amount of the lubricating oil sent to the compressor tends to be insufficient for the amount of the lubricating oil remaining in the condenser 2. In particular, when the amount of refrigerant discharged from the compressor is small and the amount of refrigerant flowing through the condenser 2 is small, for example, at the time of idling or when the capacity of the variable capacity compressor is reduced, the above problem is likely to occur. The capacitor of the present invention has been invented in order to solve the above-mentioned problems.

[0008]

All the capacitors of the present invention are provided in the horizontal direction and are separated from each other in the vertical direction, similarly to the above-mentioned conventional capacitors. A pair of upper and lower headers arranged at least in one row, at least one upper partition partitioning the inside of the upper header into at least two chambers of a first upper chamber and a second upper chamber, and at least a first lower partition in the lower header. 2 of the room and the second lower room
At least one lower partition partitioning the chamber, a refrigerant inlet provided in a part of the upper header and communicating with the first upper chamber, provided between the upper header and the lower header, respectively The upper end of the first heat transfer tube, the lower end of each of the first heat transfer tube, the lower end of the first heat transfer tube, respectively, between the upper header and the lower header Provided, the upper end of each of the second upper chamber, the lower end of each of the first lower chamber, respectively, a plurality of second heat transfer tubes, the upper header and the lower header. A plurality of third heat transfer tubes, each having a plurality of third heat transfer tubes, each of which has an upper end portion connected to the second upper chamber and a lower end portion connected to the second lower chamber, respectively. And fins constituting a core together with the first to third heat transfer tubes. . The second lower chamber communicates with the refrigerant discharge port directly or via a flow path member provided downstream of the third heat transfer tube.

In the condenser according to the first aspect of the present invention, the refrigerant is present at the upstream end in the flow direction of the refrigerant, and the refrigerant flows downward from the first upper chamber toward the first lower chamber. The total of the flow area of the first heat transfer tube flowing in the middle direction with respect to the flow direction of the refrigerant, the second heat transfer tube of the flow of the refrigerant upward from the first lower chamber toward the second upper chamber While making it wider than the total flow area,
The sum of the flow area of the second heat transfer tube, the flow area of the third heat transfer tube which is present at the downstream end with respect to the flow direction of the refrigerant and flows the refrigerant downward from the second upper chamber toward the second lower chamber. Or less than the sum of

Further, in the condenser according to the present invention, the refrigerant exists at the upstream end and the downstream end in the flow direction of the refrigerant, and the refrigerant flows downward from the upper header toward the lower header. Inside the third heat transfer tubes, a resistance portion having a relatively large resistance to the flow of the refrigerant is provided, and is located at an intermediate portion with respect to the flow direction of the refrigerant, and the refrigerant flows from the lower header toward the upper header. Is not provided inside the second heat transfer tube through which heat flows upward.

[0011]

In any of the condensers of the present invention configured as described above, since the refrigerant flows vigorously from the lower header toward the upper header, the lubricating oil present in the lower header is removed by the refrigerant. In addition, it can be efficiently sent into the second heat transfer tube.

[0012]

FIG. 1 shows a first embodiment of the present invention corresponding to claim 1. The basic configuration of the capacitor 2 of the present example is the same as the conventional structure described above.
In particular, the capacitor 2 of the present invention is different from the conventional structure in that the horizontal position of the partition separating the headers 6a and 6b is different. Therefore, the description of the same parts as those of the conventional structure described above will be omitted or simplified, and the following description will focus on the characteristic parts of the present invention.

As shown in FIG.
A pair of upper and lower headers 6a, 6b, an upper partition 13 that partitions the inside of the upper header 6a into two chambers, a first upper chamber 15a and a second upper chamber 16a, and a first lower chamber 17 inside the lower header 6b.
a and a lower partition wall 14 that partitions the chamber into a second lower chamber 18a. Each of the heat transfer tubes 7, 7 is a plurality of heat transfer tubes 7, 7 located at the most upstream side. The first heat transfer tubes 19a, 19a through which the refrigerant flows downward, and the plurality of heat transfer tubes existing in an intermediate portion. The second heat transfer tube 20 which is a heat tube 7 and which allows the refrigerant to flow upward.
a, 20a and a plurality of heat transfer tubes 7, 7 which are present at the most downstream side, and are third heat transfer tubes 21a, 2
1a.

In the condenser 2 of this embodiment, the number of the first to third heat transfer tubes 19a, 20a and 21a is different from that of the conventional structure described above. That is, the first upper chamber 1
The total S _19a of the flow passage areas of the first heat transfer tubes 19a, 19a through which the refrigerant flows downward from 5a toward the first lower chamber 17a,
The flow path area of the second heat transfer tubes 20a, 20a through which the refrigerant flows upward from the first lower chamber 17a toward the second upper chamber 16a is wider than the total flow area _S20a . With this,
The total heat transfer area S _20a of the second heat transfer tubes 20a, 20a through which the refrigerant flows upward, the third heat transfer tubes 21a, through which the refrigerant flows downward from the second upper chamber 16a toward the second lower chamber 18a, The sum of the flow path areas _{21a is not} more than _S21a . That is, each of the first to third heat transfer tubes 19a, 20a, 21a
_S19a , _S20a , and _{S21a have} a relationship of _S19a > _S20a ≦ _S21a .

As described above, the total flow area S _20a of the second heat transfer tubes 20a, 20a through which the refrigerant flows upward is determined by the respective flow paths of the first and third heat transfer tubes 19a, 21a through which the refrigerant flows downward. Since the total area is equal to or smaller than S _19a and S _21a , the flow velocity of the refrigerant rising in the second heat transfer tubes 20a and 20a increases. Then, the lubricating oil that has reached the vicinity of the lower partition wall 14 in the lower header 6b is efficiently pushed into the second heat transfer tubes 20a, 20a together with the refrigerant. As a result, the amount of lubricating oil sent to the compressor together with the refrigerant is secured, and the durability of the compressor can be improved.

FIG. 2 shows a second embodiment of the present invention, which also corresponds to claim 1. In the condenser 2 of this example, two upper partition walls 13 are provided, and the heat transfer tubes 7 are provided with first to fourth heat transfer tubes 19b, 20b, 21.
b, 23. In the case of this example, the flow path area of the first heat transfer tubes 19b, 19b, which is present at the upstream end in the flow direction of the refrigerant and flows the refrigerant downward, is S.
The _19b, present in the intermediate portion with respect to the flow direction of the refrigerant, the flowing coolant upwardly second heat exchanger tube 20b, are wider than the sum S _20b of the flow path area of 20b. At the same time, the total heat transfer area S _20b of the second heat transfer tubes 20b, 20b through which the refrigerant flows upward is reduced by the third heat transfer tubes 21 through which the refrigerant flows downward.
The sum of the flow path areas b and 21b is set to S _21b or less.
In addition, as described in the claims, corresponds to a flow path member provided downstream from the third heat transfer pipe, the total flow area S23 of the fourth heat transfer pipe ₂₃ , ₂₃ for flowing the refrigerant upward, The flow path area of the third heat transfer tubes 21b, 21b, which is present on the upstream side of the fourth heat transfer tubes 23, 23 and allows the refrigerant to flow downward, is made smaller than the total _S21b . That is, each of the first to fourth heat transfer tubes 19
b, 20b, 21b, the sum of the flow channel areas S _19b , S
_20b, S _21b, the relationship between _{S 23, S 19b> S 20b} ≦ S
_21b> is restricted to S _23.

[0017] As described above, the flowing coolant upwardly second heat exchanger tube 20b, and the sum S _20b of the flow path area of 20b, the first flow of coolant to lower, third heat exchanger tube 19b, 21b flow path of The total area S23 of the fourth heat transfer tubes ₂₃ , _23, which is smaller than the total area _S19b , _{S21b and} which also allows the refrigerant to flow upward, is present upstream of the fourth heat transfer tubes ₂₃ , _23. , The third heat transfer tubes 21b, 21b through which the refrigerant flows downward.
Since the flow area of the refrigerant ascending in the second and fourth heat transfer tubes 20b and 23 is increased by making the total flow area S _21b smaller than that of It can be efficiently fed into the four heat transfer tubes 20b and 23. Other configurations and operations are the same as those of the first example described above,
Equivalent portions are denoted by the same reference numerals, and redundant description will be omitted. In the case where the number of the partition walls is further increased and the heat transfer tubes 7 constituting the core portion 9 are further finely divided, similarly,
The sum of the flow passage areas of the heat transfer tubes for raising the refrigerant is equal to or less than the sum of the flow passage areas of the heat transfer tubes for lowering the refrigerant.

Next, FIGS. 3 and 4 correspond to claim 2.
13 shows a third example of the embodiment of the present invention. In the condenser of this example, as the first and third heat transfer tubes through which the refrigerant flows, heat transfer tubes 7b called so-called combined tubes as shown in FIG. 4 are used for the purpose of cost reduction. This heat transfer tube 7b is formed by connecting a width direction intermediate portion of a plate material made of aluminum alloy to U
It is folded back into a letter shape, and a folded portion 28 and a pair of parallel flat plate portions 2 continuous from both end edges of the folded portion 28 are formed.
9, 29 are provided. Then, these two flat plate portions 29,
Bent portions 30 and 30 are respectively provided at the tip edges of 29,
They are formed in a direction approaching each other, and these bent portions 30,
The 30 tips are overlapped with each other. The overlapping portions of the distal ends of the two bent portions 30, 30 are brazed and joined together with the other components at the same time.

Further, an inner fin 22a constituting a resistance portion having a relatively large resistance to the flow of the refrigerant is inserted into the inside of the heat transfer tube 7b, and the inner fin 22a and each of the flat plate portions 29 are formed. , 29 are brazed to each other. The inner fins 22a disturb the flow of the fluid (refrigerant) flowing in the heat transfer tube 7b, improve the heat exchange efficiency between the fluid and the heat transfer tube 7b, and form a pair of the heat transfer tube 7b. The distance between the flat plate portions 29 is prevented from being widened, and the pressure resistance of the heat transfer tube 7b is improved. In addition, such an inner fin 22a is formed by bending a band-shaped plate made of an aluminum alloy. On the other hand, the heat transfer tube 7a serving as the second heat transfer tube for raising the refrigerant is formed by, for example, extruding an aluminum alloy, and as shown in FIG. It is provided integrally. Since the heat transfer tube 7a has a wall that partitions the inside formed straight along the length of the heat transfer tube 7a, the heat transfer tube 7a does not have a large resistance to the flow of the refrigerant in the heat transfer tube 7a. Therefore, the passage resistance is smaller than that of the heat transfer tube 7b having the inner fins 22a as shown in FIG.

As described above, by changing the structure of the heat transfer tube 7b serving as the first and third heat transfer tubes for flowing the refrigerant and the heat transfer tube 7a serving as the second heat transfer tube for raising the refrigerant, the second heat transfer tube is formed. The resistance of the heat transfer tube 7a is reduced.
The lubricating oil in the refrigerant can be efficiently sent together with the refrigerant into the heat transfer tube 7a serving as the second heat transfer tube by increasing the flow velocity of the refrigerant rising inside. It should be noted that the structure of this example is used alone, that is, in combination with the capacitor having the conventional structure shown in FIGS. Can also be implemented.

Next, FIGS. 5 to 7 show a fourth embodiment of the present invention, which also corresponds to claim 2. FIG. In the condenser of the present example, the heat transfer tubes 7c serving as the first and third heat transfer tubes through which the refrigerant flows down are shaped as shown in FIG. The heat transfer tube 7c is formed by roll-forming a band-shaped plate member 24 made of an aluminum alloy. That is, the joining portions 25a, 25b are formed at both ends in the width direction of the plate material 24 with the roll forming.
Is formed over the entire length of the plate member 24, and the widthwise intermediate portion of the plate member 24 is folded back in a U-shape by 180 degrees.
The heat transfer tube 7c is obtained by brazing the two joint portions 25a and 25b against each other. The above-described roll forming is performed on the plate member 24 on the opposing portions on both surfaces of the pair of flat plate portions 26 constituting the heat transfer tube 7c, and at the same time, each protrudes toward the inner surface side of the heat transfer tube 7c. A large number of projections 27 are formed. These projections 27, 27 are formed on the flat plate portion 26 so that a parallel flow path extending in the axial direction is not formed inside the heat transfer tube 7c.
Are arranged in a zigzag pattern. Therefore, each of the protrusions 27, 2
7 disturbs the flow of the refrigerant in the heat transfer tube 7c in a direction different from the length direction of the heat transfer tube 7c, and has a relatively large resistance to the flow of the refrigerant. On the other hand, as shown in FIGS. 6 to 7, the heat transfer tube 7 d serving as the second heat transfer tube for raising the refrigerant is made of an aluminum alloy plate and has a corrugated inner fin 22.
b is inserted. The heat transfer tube 7d does not disturb the flow of the refrigerant, and has a lower resistance than the above-described heat transfer tube 7c.

With the above configuration, the resistance of the heat transfer tube 7d serving as the second heat transfer tube through which the refrigerant flows upward can be reduced.
By increasing the flow velocity of the refrigerant rising in the heat transfer tube 7d,
The lubricating oil in the refrigerant can be efficiently sent into the heat transfer tube 7d together with the refrigerant. Other configurations and operations are the same as those of the third embodiment.
This is the same as in the example. The heat transfer tubes 7a, 7
The combination of b, 7c, 7d constitutes a second heat transfer tube for raising the refrigerant by the heat transfer tubes 7a, 7d having a small passage resistance, and the heat transfer tube 7 having a relatively large resistance to the flow of the refrigerant.
Any combination other than the above-described third and fourth examples may be used as long as it constitutes the first and third heat transfer tubes through which the refrigerant flows down by b and 7c.

[0023]

The condenser of the present invention is constructed and operated as described above, and therefore, of the lubricating oil mixed in the refrigerant,
The amount of lubricating oil accumulated near the lower partition of the lower header can be reduced. As a result, the amount of lubricating oil sent to the compressor can be secured, and the durability of an air conditioner for an automobile incorporating the compressor can be improved.

[Brief description of the drawings]

FIG. 1 is a schematic perspective view of a capacitor showing a first example of an embodiment of the present invention.

FIG. 2 is a schematic perspective view of a capacitor showing the second example.

FIG. 3 is a partially cut perspective view showing a heat transfer tube incorporated as a second heat transfer tube in the third example.

FIG. 4 is an end perspective view showing heat transfer tubes incorporated as first and third heat transfer tubes in the third example.

FIG. 5 is a partially cutaway perspective view showing heat transfer tubes incorporated as first and third heat transfer tubes in the fourth example.

FIG. 6 is a partially cut perspective view showing a heat transfer tube incorporated as a second heat transfer tube in the fourth example.

FIG. 7 is a sectional view taken along the line AA of FIG. 6, which is shown in an assembled state.

FIG. 8 is a circuit diagram of a vapor compression refrigerator in which a condenser is incorporated.

FIG. 9 is a schematic perspective view showing a first example of a conventional capacitor.

FIG. 10 is a schematic perspective view showing the second example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Compressor 2 Condenser 3 Liquid tank 4 Expansion valve 5 Evaporator 6a, 6b Header 7, 7a, 7b, 7c Heat transfer tube 8 Fin 9 Core part 10a, 10b Side plate 11 Inlet block 12 Inlet port 13 Upper partition 14 Lower partition 15, 15a First upper chamber 16, 16a Second upper chamber 17, 17a First lower chamber 18, 18a Second lower chamber 19, 19a, 19b First heat transfer tube 20, 20a, 20b Second heat transfer tube 21, 21a, 21b Third Heat transfer tubes 22a, 22b Inner fins 23 Fourth heat transfer tube 24 Plates 25a, 25b Joined portions 26 Flat plate portions 27 Projections 28 Folded portions 29 Flat plate portions 30 Bent portions

Claims (2)

[Claims] 1. Each is provided in a horizontal direction,
A pair of upper and lower headers spaced apart from each other in the vertical direction, at least one upper partition partitioning the interior of the upper header into at least a first upper chamber and a second upper chamber; At least one lower partition partitioning the inside of the header into at least two chambers of a first lower chamber and a second lower chamber, and a refrigerant inlet provided in a part of the upper header and communicating with the first upper chamber. , Provided between the upper header and the lower header, each upper end in the first upper chamber,
Each lower end is connected to the first lower chamber, respectively, a plurality of first heat transfer tubes, provided between the upper header and the lower header, each upper end of the second header In the upper chamber, the lower end of each is connected to the first lower chamber, respectively, a plurality of second heat transfer tubes, provided between the upper header and the lower header, each upper end The second upper chamber, the lower end of each of the second lower chamber, respectively, a plurality of third heat transfer tubes, and a plurality of first to third heat transfer tubes each with a core portion. In the condenser, the second lower chamber is connected to the refrigerant discharge port directly or through a flow path member provided downstream of the third heat transfer tube. Exists at the upstream end with respect to the first upper chamber toward the first lower chamber. The total of the flow area of the first heat transfer tube for flowing the medium downward is present at an intermediate portion with respect to the flow direction of the refrigerant, and the second for flowing the refrigerant upward from the first lower chamber toward the second upper chamber. Along with the passage area of the heat transfer tubes being wider than the sum of the passage areas of the second heat transfer tubes, the sum of the passage areas of the second heat transfer tubes is located at the downstream end with respect to the flow direction of the refrigerant and is directed from the second upper chamber to the second lower chamber. A condenser characterized in that the total flow passage area of the third heat transfer tube through which a refrigerant flows downward is equal to or less than the total. 2. Each is provided in a horizontal direction,
A pair of upper and lower headers spaced apart from each other in the vertical direction, at least one upper partition partitioning the interior of the upper header into at least a first upper chamber and a second upper chamber; At least one lower partition partitioning the inside of the header into at least two chambers of a first lower chamber and a second lower chamber, and a refrigerant inlet provided in a part of the upper header and communicating with the first upper chamber. , Provided between the upper header and the lower header, each upper end in the first upper chamber,
Each lower end is connected to the first lower chamber, respectively, a plurality of first heat transfer tubes, provided between the upper header and the lower header, each upper end of the second header In the upper chamber, the lower end of each is connected to the first lower chamber, respectively, a plurality of second heat transfer tubes, provided between the upper header and the lower header, each upper end The second upper chamber, the lower end of each of the second lower chamber, respectively, a plurality of third heat transfer tubes, and a plurality of first to third heat transfer tubes each with a core portion. In the condenser, the second lower chamber is connected to the refrigerant discharge port directly or through a flow path member provided downstream of the third heat transfer tube. Exists at the upstream end and the downstream end with respect to Inside the first and third heat transfer tubes for flowing the refrigerant downward toward the header, a resistance portion having a relatively large resistance to the flow of the refrigerant is provided, and the resistance portion is present at an intermediate portion with respect to the flow direction of the refrigerant, A capacitor characterized by not having a resistance portion that has a large resistance to the flow of a refrigerant inside a second heat transfer tube through which a refrigerant flows upward from a lower header toward an upper header.