JPH08219588A - Liquid receiver integration type refrigerant condenser - Google Patents

Abstract

PURPOSE: To provide a liquid receiver integration type condenser which facilitates setting in a narrow space. CONSTITUTION: A communication chamber 46 communicating with the downstream side of a condensing part 8 is provided in a header 16 and a gas/liquid separation chamber 48 on the side of the communication chamber 46 to separate a gas and a liquid of a refrigerant. The height of the part of the gas/liquid separation chamber 48 is made lower than the height of the communication chamber 46 to make the part of the gas/liquid separation chamber 48 hard to interfere with a surrounding equipment thereby facilitating the setting of a condenser 3.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention generally relates to a receiver-integrated refrigerant condenser used in a refrigeration cycle, and is used in, for example, a vehicle air conditioner in which the refrigerant circulation amount fluctuates greatly. It is suitable.

[0002]

2. Description of the Related Art Conventionally, in a refrigeration cycle of a vehicle air conditioner, a liquid receiver and a condenser are separately arranged. Therefore, it is difficult to reduce the cost by reducing the number of parts, and since the receiver and the condenser occupy the mounting space for each other, there is a problem that the demand for space saving cannot be met.

Therefore, in order to solve the above-mentioned problems, in Japanese Patent Laid-Open No. 4-320771, a part of an outlet header of a condenser is crushed to form a flat surface portion, and a flat surface portion is also provided. It has been proposed that the container is integrally brazed to the flat portion of the header.

[0004]

However, in all of these prior arts, the horizontal width dimension of the outlet-side header portion is increased by integrally providing the outlet-side header portion with the gas-liquid separation chamber. Will end up. As a result, when the condenser is installed in the extremely narrow engine room of the vehicle, the header portion may interfere with the vehicle body and other devices, which makes it difficult to install the condenser.

Therefore, in order to install the condenser in the limited space in the engine room, it may be necessary to reduce the width of the core for heat exchange between the refrigerant and the air in the condenser. There was a problem of down. In view of the above points, an object of the present invention is to provide a receiver-integrated refrigerant condenser in which interference between a header portion and peripheral devices does not easily occur even when installed in a narrow space.

Further, according to the present invention, even if the header part is integrally provided with the gas-liquid separation chamber, the liquid-receiver integrated refrigerant condenser having a good gas-liquid separation property of the refrigerant in the gas-liquid separation chamber is provided. The other purpose is to provide.

[0007]

In order to achieve the above object, according to the present invention, (a) a core having a condensing portion for condensing a horizontally flowing refrigerant, and (b) a vertical direction at one end of the core. A header to which the downstream end of the condenser is connected, and (c) is provided inside the header,
A communication chamber communicating with the downstream end of the condenser, (d) in the header, a gas-liquid separation chamber provided on a side of the communication chamber for separating a refrigerant into gas and liquid, and (e) in the header,
A refrigerant inflow means for allowing the refrigerant in the communication chamber to flow into the gas-liquid separation chamber; and (f) the header, which is positioned below the refrigerant inflow means, moves the liquid refrigerant in the gas-liquid separation chamber to the outside of the separation chamber. And a refrigerant outflow means for outflowing,
(G) The header is a liquid receiver integrated refrigerant condenser configured such that the vertical length of the gas-liquid separation chamber portion is shorter than the vertical length of the communication chamber portion. I am trying.

[0008]

According to the present invention, as shown in FIG. 2, the vertical length of the gas-liquid separation chamber 48 is made shorter than the vertical length of the communication chambers 46 and 47. Therefore, even with the structure in which the liquid receiving section 9 is integrally installed on the header 16 of the condenser 3, the degree of the liquid receiving section 9 interfering with surrounding devices is significantly reduced, and the liquid receiver integrated condenser Installation of 3 becomes easy. Therefore, there is no inconvenience that the width dimension of the core 14 having the condensing portion 8 has to be narrowed, and there is an effect that the condensing performance is easily ensured.

According to the invention described in claims 3, 6, 12, etc., as illustrated in FIG. 2, the refrigerant condensed in the condenser 8 is once collected in the upstream communication chamber 46 of the header 16, After that, it is sent out into the gas-liquid separation chamber 48 via the refrigerant inflow means 44. As a result, the fine bubble-like gas-phase refrigerant that comes out of the condenser 8 is collected in the upstream communication chamber 46 and becomes a bubble-like gas-phase refrigerant with a large diameter, which is greatly affected by buoyancy, and gas-liquid separation is performed. Gas-liquid separation is facilitated in the chamber 48.

Moreover, since the flow of the refrigerant is a U-turn flow from the refrigerant inflow means 44 to the refrigerant outflow means 45 through the gas-liquid separation chamber 48, the gas-liquid is separated by the centrifugal force to form a bubble. The more the vapor-phase refrigerant gathers, the larger the diameter of the bubble-like vapor-phase refrigerant becomes, and it is further affected by the buoyancy to facilitate the gas-liquid separation. And tentatively, the condensing part 8
Even if the lowermost part of the and the uppermost part of the supercooling part 10 are close to each other,
Due to the U-turn flow, the flow path length from the downstream end of the condensing section 8 to the upstream end of the subcooling section 10 becomes long, and the gas-liquid separation chamber 4
It is not necessary to send out the gas-phase vapor-phase refrigerant that has not been separated from the subcooler 8 to the subcooling unit 10.

Further, since the refrigerant is introduced from the refrigerant inflow means 44 into the liquid refrigerant in the lower part of the gas-liquid separation chamber 48, the liquid surface 9a in the gas-liquid separation chamber 48 is wavy even when the refrigerant flow rate is large. In other words, the gas-liquid separation of the refrigerant can be performed satisfactorily. Since the lower part of the gas-liquid separation chamber 48 communicates with the supercooling section 10 via the downstream side communication chamber 47, even if the gas-liquid separation in the gas-liquid separation chamber 48 is insufficient, The bubble-like vapor phase refrigerant disappears in the cooling unit 10.

By the combination of the above operations, it is possible to reduce the volume of the gas-liquid separation chamber 48, that is, the cross-sectional area of the gas-liquid separation chamber 48, and to secure the effective heat radiation area of the condenser section 8 and the supercooling section 10. It will be easier. Further, according to the invention described in claim 11, since the header plate 36 and the tank plate 362 are formed by bending one metal plate and integrally joining them as shown in FIG. 11, The cost can be reduced by reducing the number of parts.

According to the twelfth aspect of the invention, as illustrated in FIG. 9, the tank plate 362 and the cylindrical body 37 are provided.
Since and are integrally formed by extrusion, the cost can be reduced by reducing the number of parts, and the leakage defects can be reduced by reducing the number of joints. Further, according to the inventions of claims 15 and 16, in the header 16 as illustrated in FIGS. 18 and 19, the gas-liquid separation chamber 48 and the members 36 and 362 forming the communication chambers 46 and 47 are formed. Is composed of a separate cylindrical body 37, and this cylindrical body 37 is provided at two positions in the vertical direction of the communication chamber 46 and the constituent member 3 of the communication chamber 47.
Since the tubular body 37 and the constituent members 36 and 362 of the communication chambers 46 and 47 are integrally brazed after being fixed to the tubular body 37, the assembly position of the tubular body 37 is determined. Before attachment, the tubular body 37 is not displaced as shown in FIG.
6,362 can always be brazed well.

[0014]

Next, a description will be given of an embodiment in which the liquid receiver integrated refrigerant condenser of the present invention is applied to an automobile air conditioner. 1 to 5 show a first embodiment of the present invention, and FIG. 1 is a view showing a refrigeration cycle of an automobile air conditioner. The refrigeration cycle 1 of this automobile air conditioner includes a refrigerant compressor 2, a receiver-integrated refrigerant condenser 3,
The sight glass 4, the expansion valve 5 and the refrigerant evaporator 6 are sequentially connected by a refrigerant pipe 7 made of a metal pipe or a rubber pipe.

The refrigerant compressor 2 is connected to an engine E installed in an engine room (not shown) of an automobile through a belt V and an electromagnetic clutch (power disconnecting means) C. When the rotational power of the engine E is transmitted, the refrigerant compressor 2 compresses the gas-phase (gas) refrigerant sucked into the inside of the refrigerant evaporator 6 to transfer the high-temperature and high-pressure gas-phase refrigerant to the receiver-integrated type. The refrigerant is discharged to the condenser 3.

The receiver-integrated refrigerant condenser 3 includes a condenser section 8,
The liquid receiving section 9 and the supercooling section 10 are integrally provided. The condenser 8 is connected to the discharge side of the refrigerant compressor 2 and causes the gas-phase refrigerant flowing into the refrigerant compressor 2 to exchange heat with the outdoor air sent by a cooling fan (not shown) or the like. Acts as a condensing means for condensing and liquefying. The liquid receiving unit 9 functions as a gas-liquid separating unit that separates the refrigerant flowing into the inside from the condensing unit 8 into a gas-phase refrigerant and a liquid-phase refrigerant, and supplies only the liquid-phase refrigerant to the subcooling unit 10. The supercooling unit 10 is provided below and adjacent to the condenser unit 8 arranged on the upper side,
It functions as a supercooling means for supercooling the liquid-phase refrigerant by exchanging heat between the liquid-phase refrigerant flowing in from the liquid receiving section 9 and the outdoor air sent by a cooling fan or the like.

The sight glass 4 is connected to the downstream side of the supercooling section 10 of the receiver-integrated refrigerant condenser 3 and observes the gas-liquid state of the refrigerant circulating in the refrigeration cycle 1 to enclose the refrigerant enclosed in the cycle. It serves as a refrigerant amount checking means for checking the excess and deficiency of the amount. The sight glass 4 is mounted independently in a place where it is easily visible to an inspector in the engine room of the automobile, for example, in the middle of the refrigerant pipe 7 adjacent to the receiver-integrated refrigerant condenser 3.

As shown in FIG. 1, the sight glass 4 is formed on a tubular metal body 11 whose both ends are connected to the refrigerant pipe 7 by means such as welding or fastening, and an upper surface of the metal body 11. It is composed of a welded glass 13 and the like fitted in the peep window 12. Generally, when bubbles are seen through the viewing window 12, the amount of refrigerant is insufficient, and when no bubbles are seen, the amount of refrigerant is appropriate.

The expansion valve 5 is connected to the refrigerant inlet side of the refrigerant evaporator 6 and adiabatically expands the high-temperature high-pressure liquid-phase refrigerant flowing from the sight glass 4 into a low-temperature low-pressure gas-liquid two-phase atomized refrigerant. Which serves as a pressure reducing means for operating the refrigerant evaporator 6 in this example.
A temperature-operated expansion valve that automatically adjusts the valve opening so as to maintain the refrigerant superheat degree at the refrigerant outlet portion at a predetermined value is used.

The refrigerant evaporator 6 is connected between the suction side of the refrigerant compressor 2 and the downstream side of the expansion valve 5, and blows the refrigerant in the gas-liquid two-phase state that has flowed into the inside from the expansion valve 5 (not shown). (2) heat-exchanges with the outdoor air or indoor air blown to evaporate the refrigerant, and the latent heat of evaporation serves as a cooling means for cooling the blown air. Next, the liquid receiver integrated refrigerant condenser 3 of this embodiment will be described in detail with reference to FIGS. The receiver-integrated refrigerant condenser 3 has, for example, a height of 300 mm to 400 mm and a width of 300 mm to 600 mm, and is a place in the engine room of an automobile that is susceptible to running wind, usually for cooling engine cooling water. It is attached to the vehicle body via a mounting bracket (not shown) so as to be located on the front side of the radiator.

The receiver-integrated refrigerant condenser 3 has a core 14 for heat exchange, a first header 15 arranged at one end of the core 14 in the horizontal direction, and the other end of the core 14 in the horizontal direction. It is composed of the second header 16 and the like arranged on the side, and all of these constituent parts are made of aluminum and are integrally brazed in a furnace to be manufactured. The core 14 is composed of a condensing part 8 and a subcooling part 10, and a side plate 17 for fixing a mounting bracket for mounting the liquid receiver integrated refrigerant condenser 3 to the vehicle body of an automobile at the upper end part and the lower end part thereof, 18 is joined by joining means such as brazing. The upper condensing part 8 is composed of a plurality of condensing tubes 19 and corrugated fins 20 extending in the horizontal direction, and these are joined by joining means such as brazing. The lower supercooling unit 10 is composed of a plurality of horizontally extending supercooling tubes 21 and corrugated fins 22, which are joined by joining means such as brazing.

The side plates 17 and 18 can be formed into a predetermined shape by pressing a metal plate obtained by clad a brazing material on aluminum or an aluminum alloy, and have the first shape at both ends in the horizontal direction.
Inserted pieces 171, 172, 181, 182 to be inserted into the header 15 and the second header 16 are formed. The plurality of condensing tubes 19 and the supercooling tubes 21 are refrigerant flow path forming means, and are formed into an oval shape having a flat cross section by extruding aluminum or aluminum alloy material having excellent corrosion resistance and thermal conductivity. In addition, it is formed in a shape having a plurality of refrigerant flow paths 19a therein (see FIG. 3). Also, the corrugated fins 20 and 22 are
It is a heat radiation promoting means for improving the heat radiation efficiency of the refrigerant, and is a corrugated metal plate such as aluminum or aluminum alloy whose both sides are clad with a brazing material.

From the first header 15 on the refrigerant inlet side, the refrigerant flows horizontally in the plurality of condensing tubes 19 and flows into the second header 16, while the refrigerant flowing in the plurality of supercooling tubes 21 is On the contrary, it flows horizontally from the second header 16 and flows into the first header 15. Further, in this embodiment, the number of the condensing tubes 19 is set to be larger than the number of the supercooling tubes 21, and according to experimental experience, the number of the supercooling tubes 21 is 15% of the entire core 14. ~
About 20% is preferable.

The first header 15 is composed of a header plate 23 having a substantially U-shaped cross section and a tank plate 24 having a semi-circular cross section, and has a substantially cylindrical shape extending in the vertical direction. Both plates 23, 24 of the first header 15
Obtains the above-described predetermined shape by pressing a metal plate whose both sides are clad with a brazing material with aluminum or aluminum alloy having excellent corrosion resistance and thermal conductivity.

The upper part of the first header 15 is the condensing part 8
The upstream ends of the plurality of condensing tubes 19 constituting the above are connected, and the lower ends are connected to the downstream ends of the plurality of supercooling tubes 21 constituting the supercooling unit 10. Then, the cap 25 is fitted into the openings of the upper and lower ends of the first header 15 in the vertical direction (plate length direction). The cap 25 has the shape shown in FIG. 3 by pressing a metal plate clad with a brazing material of aluminum or an aluminum alloy, and is joined to the upper and lower ends of the first header 15 by a joining means such as brazing. It has a substantially annular joining piece 251 to be joined, and a substantially disc-shaped closing portion 252 that is recessed from the joining piece 251 and closes the openings at the upper and lower ends of the first header 15.

A large number of oval holes 26 are formed in the header plate 23 by press working, and through holes 27 are formed in the upper and lower ends, respectively. The upstream ends of the plurality of condensing tubes 19 and the downstream ends of the plurality of supercooling tubes 21 are joined to the numerous holes 26 by a joining means such as brazing. In addition, the side plate 1 is provided in the upper and lower two through holes 27.
The insertion pieces 171 and 181 of Nos. 7 and 18 are joined by a joining means such as brazing in the inserted state.

The tank plate 24 has a hole 29 for fixing the separator 28 that divides the interior into upper and lower parts by press working, and a circular refrigerant inlet 3 for fixing the inlet pipe 30.
Circular refrigerant discharge port 3 for fixing 1 and outlet pipe 32
3 are formed. The separator 28 is formed in a substantially disc shape, and the inside of the first header 15 communicates only with the upstream end of the condenser 8 at the inlet side communication chamber 34 and the outlet side that communicates only with the downstream end of the supercooling unit 10. It is divided into a communication chamber 35.

The inlet pipe 30 has a circular pipe shape, and is a pipe for allowing the high-temperature and high-pressure vapor-phase refrigerant discharged from the refrigerant compressor 2 to flow into the inlet-side communication chamber 34, by a joining means such as brazing. It is joined to the refrigerant suction port 31. Further, the outlet pipe 32 has a circular pipe shape and is a pipe for sending the liquid phase refrigerant in the outlet side communication chamber 35 to the side of the sight glass 4, and is joined to the refrigerant discharge port 33 by a joining means such as brazing.

The second header 16 has a header plate 36 having a substantially U-shaped cross section, a tank plate 362 having a substantially arc-shaped cross section, as shown in FIGS.
And a substantially cylindrical tubular body 37, and has a double tubular shape in which the three members 36, 362, 37 are combined to extend in the vertical direction. The second header 16 is made of aluminum or aluminum alloy having excellent corrosion resistance and thermal conductivity, and has the above-described predetermined shape.

The upper part of the second header 16 is the condensing part 8
The downstream ends of the plurality of condensing tubes 19 constituting the above are connected, and the lower ends are connected to the upstream ends of the plurality of supercooling tubes 21 constituting the supercooling unit 10. Then, in the second header 16, the vertical direction (plate length direction) of the cylindrical space formed by the header plate 36 and the tank plate 362.
A cap 38 is fitted in the openings at the upper and lower ends.

The cap 38 has a substantially annular joining piece 381 joined to the upper and lower end portions of the tubular space by means such as brazing, and is recessed from the joining piece 381, so that the cap 38 It has a substantially disk-shaped closing portion 382 that closes the inner openings of the upper and lower ends, and is formed into the shape shown by pressing an aluminum plate on which both sides of the brazing material are clad, like the cap 25. ing.

A large number of oval holes 39 are formed in the header plate 36 by pressing a metal plate made of aluminum whose both sides are clad with a brazing material, and through holes 40 are formed at the upper and lower ends, respectively. Has been formed. In the numerous holes 39, the downstream ends of the plurality of condensation tubes 19 and the plurality of supercooling tubes 21 are provided.
Is joined by means such as brazing with the upstream end of the plug inserted. Further, the insertion pieces 172 and 182 of the side plates 17 and 18 are joined to the two through holes 40 by means such as brazing while being inserted.

The tubular body 37 is formed by extruding an aluminum material into a tubular shape having a flat surface portion 371 on the surface facing the tank plate 362. Similarly, in the tank plate 362 as well, a flat surface portion 363 is formed on the surface facing the tubular body 37 by pressing. Where the tank plate 362
Is formed by pressing a metal plate made of aluminum whose both sides are clad with a brazing material. These flat portions 363 and 371 are provided to reduce the amount of protrusion of the second header 16 in the horizontal direction (horizontal direction) and to secure a brazing area between the tubular body 37 and the tank plate 362. There is.

FIGS. 4 and 5 show the brazing structure of both of them in detail. In this example, the flat surface projecting portions 37 projecting with a step at two positions above and below the flat surface portion 371 of the tubular body 37.
2 and 373 are formed by press work, and both protrusions 37
The tubular body 37 is brazed to the tank plate 362 with the brazing surfaces 2 and 373. The reason why the protrusions 372 and 373 are provided for brazing is to improve the brazing strength, and the detailed reason is as follows.

That is, it is conceivable that the flat portions 363 and 371 are brazed on their entire surfaces.
If brazing is performed on the entire surface, uneven application of the flux for brazing and the size of the gap on the joint surface may occur.
It becomes difficult to secure uniform brazing conditions over the entire flat surface, and brazing defects (voids) are likely to occur. However, as in the present example, by providing the flat surface projections 372 and 373 on the flat surface portion 371 of the tubular body 37, since the circumference of these flat projections is not brazed, the brazing filler metal does not come into contact with the brazing surface during brazing. Since it flows to a certain protruding portion 372, 373, and at the same time, the flux easily accumulates in the protruding portion, the brazing material in this portion is easily activated, and as a result, a reliable brazing surface is formed at the protruding portion 372, 373. Obtainable. Moreover, a plurality of protrusions (upper and lower 2 in this example)
By providing the individual pieces, the strength of the brazing surface can be further improved.

In the above example, the flat portions 371 of the tubular body 37 are provided with the projecting portions 372 and 373. However, the projecting portions are eliminated and a plurality of projecting portions are provided on the flat portion 363 of the tank plate 362. It may be provided to improve the strength of the brazing surface. On the other hand, the header plate 36 and the tank plate 36
The cylindrical space formed by 2 is divided by a disc-shaped separator 42 in the vertical direction into an upstream communication chamber 46 and a downstream communication chamber 47. The tubular body 37 is located on the side (outside) of both of the communication chambers 46 and 47, and the tubular body 37
A gas-liquid separation chamber 48 that constitutes the liquid receiving section 9 is formed inside.

The upstream side communication chamber 46 communicates only with the downstream end of the condenser section 8, the downstream side communication chamber 47 communicates only with the upstream end of the subcooling section 10, and the upstream side communication chamber 46 thereof. At the substantially rectangular refrigerant inlet 44 provided near the bottom (the bottom of the condenser 8), the refrigerant liquid level 9a of the gas-liquid separation chamber 48.
(This liquid surface 9a is a liquid surface when the amount of the refrigerant enclosed in the cycle is a normal appropriate amount), that is, it communicates with the liquid refrigerant storage portion in the chamber 48. Further, the gas-liquid separation chamber 48 is close to its bottom (in other words, the refrigerant inlet port 4
4 is a lower position) and is provided with a substantially rectangular refrigerant outlet port 45.
And communicates with the downstream communication chamber 47.

The separator 42 is formed by pressing an aluminum plate clad with a brazing material into a disk shape, press-fitted into a hole 43 provided in the tank plate 362 and temporarily fixed, and then the header plate 36. To the tank plate 362 by brazing. The refrigerant inlet 44 and the refrigerant outlet 45 are holes 44a and 44b formed in the tank plate 362 and the tubular body 37, respectively.
It is formed by holes 45a and 45b. Further, a plurality of (four in this example) claw pieces 44c, 45c are integrally formed on the peripheral portions of the holes 44a, 45a of the tank plate 362, and these claw pieces 44c, 45c are formed on the inner circumferences of the holes 44b, 45b. The tank plate 362 and the tubular body 37 are temporarily fixed to each other by press fitting, and then joined by brazing.

The openings at the upper and lower ends of the tubular body 37 are
The cap 50 is closed by a cap 50. The cap 50 is similar to the caps 25 and 38, and is a substantially annular joining piece joined to the upper and lower ends of the tubular body 37 by means such as brazing. 501 and a substantially disk-shaped closing portion 502 which is recessed from the joining piece 501 and closes the inner opening of the upper and lower end portions of the tubular body 37, and is aluminum clad with a brazing material on both sides. The plate is pressed into a shape as shown.

The refrigerant inlet 44 is connected to the upstream communication chamber 46.
Is opened at the lower part (the lowermost part of the condensation part 8) of the upstream communication chamber 4
It forms a refrigerant inflow means for injecting the refrigerant in 6 into the liquid refrigerant reservoir below the liquid surface 9a in the gas-liquid separation chamber 48, and the refrigerant outlet port 45 opens below the refrigerant inlet port 44, It constitutes a refrigerant outflow means for outflowing the liquid refrigerant in the separation chamber 48 into the downstream communication chamber 47. Further, the gas-liquid separation chamber 48 plays a role of separating the refrigerant flowing into the upstream communication chamber 46 into a gas-phase refrigerant and a liquid-phase refrigerant, and sending only the liquid-phase refrigerant to the downstream communication chamber 47. In addition, in this example, the flat surface portion 363 of the tank plate 362 and the flat surface portion 373 of the tubular body 37.
By these, the partition part which divides both communication chambers 46 and 47 and the gas-liquid separation chamber 48 is comprised.

In the present embodiment, as clearly shown in FIGS. 1, 2 and 5, the upper end of the gas-liquid separation chamber 48 is located at the upper end of both communication chambers 46 and 47.
The lower end of the gas-liquid separation chamber 48 is made higher than the lower ends of the two communication chambers 46, 47, and the vertical length of the gas-liquid separation chamber 48 is made lower than the upper end of the two communication chambers 46, 47. It is shorter than the vertical length of the part. Next, the operation of the refrigeration cycle 1 of the vehicle air conditioner of the first embodiment will be described based on FIGS. 1 and 2. When the operation of the vehicle air conditioner is started, the electromagnetic clutch C is energized, and the refrigerant compressor 2 is rotationally driven by the engine E via the belt V and the electromagnetic clutch C.

Therefore, the high-temperature and high-pressure vapor-phase refrigerant compressed and discharged in the refrigerant compressor 2 flows into the inlet-side communication chamber 34 of the first header 15 through the inlet pipe 30. The gas-phase refrigerant that has flowed into the inlet-side communication chamber 34 is stored in the inlet-side communication chamber 3
It is distributed to a plurality of condensing tubes 19 that constitute the condensing part 8 in the condenser 4. Then, the vapor-phase refrigerant distributed to the plurality of condensing tubes 19 is heat-exchanged with the outdoor air via the corrugated fins 20 when passing through these condensing tubes 19 to be condensed and liquefied, and a part of the vapor phase Almost liquid phase refrigerant, leaving the refrigerant. This refrigerant is a plurality of condensing tubes 1
9 flows into the upper communication chamber 46 of the second header 16 and is once collected in the upstream communication chamber 46, and thereafter, via the refrigerant inlet 44 opening at the lower part of the upstream communication chamber 46, the liquid receiving portion. It is sent to the inside of 9. As a result, the fine bubble-like vapor-phase refrigerant that emerges from the downstream ends of the plurality of condensing tubes 19 is collected in the upstream side communication chamber 46 and becomes a bubble-like vapor-phase refrigerant with a large diameter, which is greatly affected by buoyancy. Like

Next, the refrigerant that has flowed into the upper communication chamber 46 passes through the refrigerant inlet 44 and the liquid receiving portion 9 (the gas-liquid separation chamber 4).
8) The refrigerant flows into the liquid refrigerant below the liquid surface 9a.
In the liquid receiving section 9 (gas-liquid separation chamber 48), the cross-sectional area is made relatively large (for example, 500 mm ² ) to reduce the speed of the refrigerant and utilize the buoyancy of the bubble-like gas-phase refrigerant,
The refrigerant is separated into gas and liquid.

Further, since the refrigerant flows from the chamber 46 through the inflow port 44 into the liquid refrigerant in the lower part of the gas-liquid separation chamber 48, the liquid surface 9a is wavy in the chamber 48 due to the refrigerant inflow. Is not generated, and the gas-liquid separation of the refrigerant is further improved. In particular, even when the refrigerant circulation amount is large, such as when the refrigerant compressor 2 is operated at high speed, the liquid surface 9a does not swell, so that the gas-liquid separation can be performed without increasing the cross-sectional area of the liquid receiving section 9. Is performed well, and a stable gas-liquid interface is formed in the liquid receiving section 9.

Further, by the second separator 42, from the downstream end of the lowermost condensing tube 19 of the plurality of condensing tubes 19 to the uppermost supercooling tube 21 of the plurality of supercooling tubes 21. The flow path length to the upstream end is long to facilitate gas-liquid separation by buoyancy. In addition, the second separator 42 causes the refrigerant flowing from the plurality of condensation tubes 19 into the second header 16 to make a U-turn and flow out to the plurality of supercooling tubes 21. As described above, the fine bubble-like gas-phase refrigerant that emerges from the downstream end of the is once gathered in the upstream communication chamber 46, becomes a bubble with a large diameter here, and is easily subjected to buoyancy, and then centrifugal force causes gas-liquid The separated and bubble-like vapor-phase refrigerant is collected in one place (inner side).

That is, even though the refrigerant inlet 44 opens at the lower part of the upstream communication chamber 46 and the refrigerant inlet 44 and the refrigerant outlet 45 are relatively close to each other, the refrigerant containing bubbles still flows into the refrigerant. When passing through the inlet 44 → the liquid receiving portion 9 → the refrigerant outlet 45, the liquid phase refrigerant having a large specific gravity is transferred to the outer side portion of the tubular body 37 due to the centrifugal force based on the U-turn flow (vector in the opposite direction). Then, the gaseous vapor-phase refrigerant having a small specific gravity gathers at the protruding portion of the second separator 42 into the liquid receiving portion 9.

Therefore, the gas-liquid is separated by the centrifugal force, and the bubble-like gas-phase refrigerant is more gathered, so that the diameter of the bubble-like gas-phase refrigerant becomes larger and the influence of the buoyancy force is exerted more and the gas-liquid separation is caused. It will be easy. Therefore, when the refrigerant flows into the liquid receiving section 9 through the refrigerant inlet port 44, the refrigerant is easily separated into gas and liquid, and in the liquid receiving section 9, the vapor phase refrigerant stays upward and the liquid phase refrigerant stays downward.

As a result, the unseparated gaseous refrigerant in the vapor phase does not flow out from the liquid receiving section 9 to the plurality of supercooling tubes 21, and the supercooling section 10 can be effectively operated. Further, since the subcooling unit 10 is provided on the downstream side of the liquid receiving unit 9, even if the gas-liquid separation in the liquid receiving unit 9 is not complete, the subcooling unit 10 forms a bubble-like vapor phase refrigerant. Completely disappears, the volume of the liquid receiving portion 9, that is, the cross-sectional area of the liquid receiving portion 9 can be reduced, and the effective heat radiation area of the condensing portion 8 of the core 14 and the supercooling portion 10 can be reduced. Can be prevented.

By summing up the above, the gas-liquid two-phase state refrigerant in the liquid receiving section 9 is efficiently separated into gas and liquid, so that the gas phase refrigerant is in the upper part of the liquid receiving section 9 and the liquid phase refrigerant is in the lower part. Will be accumulated. Therefore, if the refrigeration cycle 1 is filled with a sufficient amount of refrigerant to form a gas-liquid interface in the liquid receiving section 9, there is no supercooling degree from the refrigerant outlet port 45 at the bottom of the liquid receiving section 9. Only the liquid-phase refrigerant flows into the downstream communication chamber 47. The liquid-phase refrigerant that has flowed into the downstream side communication chamber 47 has a plurality of supercooling tubes 2 that constitute the supercooling unit 10 here.
Distributed to 1.

The liquid-phase refrigerant distributed to the plurality of supercooling tubes 21 is supercooled by exchanging heat with the outdoor air via the corrugated fins 22 when passing through these supercooling tubes 21. It becomes a liquid-phase refrigerant having a supercooling degree and flows into the outlet side communication chamber 35 of the first header 15.

The liquid-phase refrigerant flowing into the outlet side communication chamber 35 flows into the expansion valve 5 through the outlet pipe 32 and the sight glass 4. Since the supercooled liquid-phase refrigerant is supplied into the expansion valve 5, the degree of dryness of the refrigerant after being decompressed by the expansion valve 5 becomes small, which causes the refrigerant between the inlet and the outlet of the refrigerant evaporator 6. The enthalpy difference becomes large, and the cooling capacity of the automobile air conditioner can be improved.

Further, since the vertical length of the gas-liquid separation chamber 48 is shorter than the vertical length of both the communication chambers 46 and 47, the condenser 3 is placed in the narrow engine room of the automobile. It is extremely advantageous in practice when installed in front of the radiator. That is, because the vehicle body in front of the radiator of an automobile is often designed with curved surfaces in both left and right and up and down directions of the automobile for design reasons, the width dimension (horizontal dimension) of the condenser 3 should be minimized. Therefore, it is desired that the condenser 3 does not interfere with peripheral devices such as the vehicle body. In consideration of this point, the vertical length of the chamber 48 is set to the chambers 46, 4
Since it is shorter than the vertical length of the seven parts, even if the width of the condenser is increased by the amount of the chamber 48, it is possible to effectively prevent the chamber 48 from interfering with the vehicle body, etc. Installation in the room can be facilitated.

Further, in this embodiment, since the receiver-integrated refrigerant condenser 3 is connected between the refrigerant compressor 2 and the sight glass 4, compared to the case where the receiver is installed independently. The cost can be reduced by reducing the number of parts. In addition, the space for installing the receiver in the engine room of the automobile can be eliminated, saving space. In addition, in this embodiment, since the sight glass 4 is connected to the downstream side of the supercooling unit 10, it is not necessary to ensure the gas-liquid separability in the liquid receiving unit 9, and the volume of the liquid receiving unit 9 That is, the cross-sectional area of the liquid receiving section 9 may be estimated by the amount of refrigerant fluctuation due to load fluctuation of the refrigeration cycle 1 and the amount of margin for refrigerant leakage.

[Second Embodiment] FIG. 6 shows a second embodiment of the present invention, and is a cross-sectional view of an essential part corresponding to FIG. 4. In this example, the tubular body 37 is not extruded but is placed on both front and back surfaces. A metal plate such as an aluminum plate clad with a material is bent to form a tubular shape having a flat surface portion 371, and the flat bent end portion 37a of the metal plate is joined by brazing. . The other points are the same as in the first embodiment.

[Third Embodiment] FIG. 7 shows a third embodiment. In the above-described second embodiment, flat portions 363 and 3 are formed by pressing both the tank plate 362 and the tubular body 37.
71 is formed, and both are brazed on this flat surface portion, but in the example of FIG. 7, only one of them is used, for example, the cylindrical body 3
7 is formed by pressing a concave portion 37b having an arcuate cross section, and the concave portion 37b is brazed to the arcuate outer peripheral surface of the tank plate 362 in close contact with each other.

Of course, in the example of FIG. 7, a recess having an arcuate cross section may be formed on the side of the tank plate 362, and the arcuate outer peripheral surface of the tubular body 37 may be brought into close contact with this recess for brazing. In the example of FIG. 6 described above,
Instead of brazing at the flat surface portion, a recess having an arcuate cross section may be formed in the tubular body 37 or the tank plate 362, and brazing at this arcuate portion may be performed.

[Fourth Embodiment] FIGS. 8 to 10 show a fourth embodiment, in which a tank plate 362 and a tubular body 37 are integrated into one tubular part 376 by extruding an aluminum material. After molding, the upper and lower ends of the tubular body 37 are scraped off to form the tubular body 37 in a desired height as shown in FIG. The holes that form the refrigerant passages 44 and 45 are formed by performing additional processing such as press working and drilling.

[Fifth Embodiment] FIGS. 11A and 11B show a fifth embodiment.
In this embodiment, the tubular body 37 is the same as that shown in FIG. 5B, but the header plate 36 and the tank plate 362 are made of metal plates such as aluminum with brazing material clad on both sides. It is formed by bending and integrally forming one tubular component 365 formed into a tubular shape, and the flat bent end portions 365a of the metal plates are joined by brazing. A flat surface portion 363 is formed on the tank plate 362, and the flat surface portion 363 communicates with the holes 44b and 45b of the cylindrical body 37 and the refrigerant passages 44 and 45.
There is a hole (not shown) that forms the. The other points are the same as in the first embodiment.

[Sixth Embodiment] FIG. 12 shows a sixth embodiment. Unlike the first embodiment shown in FIG. 1, the position of the refrigerant inlet 44 is above the gas-liquid separation chamber 9, that is, the refrigerant. The refrigerant that is provided above the liquid surface 9a and is condensed in the condensing section 8 is supplied to the inlet 44
From the above into the gas-phase refrigerant inside the gas-liquid separation chamber 9. The other points are the same as in the first embodiment.

[Seventh Embodiment] FIG. 13 shows a seventh embodiment in which the supercooling section 10 in the first embodiment shown in FIG. 1 is eliminated. In this example, the entire heat exchange part of the condenser 3 is configured as the condensing part 8, and the refrigerant condensed in the condensing part 8 is discharged from the refrigerant inlet 44 provided below the refrigerant liquid surface 9a of the gas-liquid separation chamber 9, It is made to flow into the liquid refrigerant in the chamber 9, and the outlet pipe 32 is placed at a position below the refrigerant inlet 44,
The tubular body 37 forming the gas-liquid separation chamber 9 is joined by brazing, and the inlet tip of the outlet pipe 32 is opened into the chamber 9 to serve as a refrigerant outlet 45, and the liquid refrigerant in the chamber 9 is discharged from the outlet pipe 32. To the outside and then to the sight glass 4 side.

[Eighth Embodiment] FIG. 14 shows an eighth embodiment of the present invention and is a view showing a liquid receiver integrated refrigerant condenser. In this embodiment, the first header 15 and the second header 15
A chamber communicating with the plurality of condensing tubes 19 constituting the condensing unit 8 is provided in the header 16 with the third and fourth separators 6
The intermediate communication chamber 34a and the upstream communication chamber 46a are divided into two by 1 and 62, and the way of flowing the refrigerant in the condensing section 8 is S-turn.

The number of turns may be increased by increasing the number of separators in the way of flowing the refrigerant in the condenser section 8. [Ninth Embodiment] FIG. 15 shows a ninth embodiment.
This is a modification of the inlet and outlet pipes 30, 32 in the embodiment. In this embodiment, both pipes 30, 32 are integrally molded with aluminum pipe joints 30a, 32a, and the joints 30a, 32a are the first header. 15 by brazing, and the joints 30a, 32a
1 is connected to the refrigerant pipe 7.
In this case, the opening direction of the pipes 30 and 32 is set so that the pipe connection is made in the condenser depth direction (the front and rear direction of the vehicle) to further reduce the installation space in the engine room.

[Tenth Embodiment] FIG. 16 shows a tenth embodiment. An inlet pipe 30 is provided in the second header 16 on the side where the liquid receiving section 9 is provided, and the inlet pipe 30 is provided in the same manner as in the ninth embodiment. The pipe 30 is integrally formed with the pipe joint 30a and brazed to the second header 16. From the viewpoint of increasing the degree of freedom in mounting on various vehicles, it is desirable that the inlet pipe 30 and the outlet pipe 32 of the condenser 3 can be attached to different headers. Therefore, there are two types of cases where the inlet pipe 30 is attached to the first header 15 and the outlet pipe 32 is attached to the second header 16, and the inlet pipe 30 is attached to the second header 16 and the outlet pipe 32 is attached to the first header 15. Although it may be attached, as described above, it is preferable that the number of the supercooling tubes 21 is about 15% to 20% of the entire core 14, so that the inlet pipe 30 is temporarily connected to the first header 15 and the outlet is connected to the outlet. When trying to attach the pipe 32 to the second header 16 on the liquid receiving section 9 side, the supercooling section 10 has to make a U-turn flow, and since the supercooling section 10 has a small number of tubes 21, the refrigerant pressure loss. Will become bigger.

Therefore, the inlet pipe 30 is connected to the second side of the liquid receiving section 9 side.
It is preferable to attach the header 16 to the header 16. Therefore, in the tenth embodiment shown in FIG. 16, by adding a separator 62 in the second header 16, the condensing section 8 is made to have an S-turn flow, and the inlet pipe 3 is provided in the second header 16.
No pipe joint 30a was attached, and as a result, the inlet pipe 30 and the outlet pipe 32 could be attached to different headers.

[Eleventh Embodiment] As shown in the sectional views of FIGS. 4, 6 and 7, the cylindrical body 37 constituting the liquid receiving portion 9 is formed.
Is formed separately from the tank plate 362 of the header 16, and when these both 37 and 362 are brazed together, it is necessary to temporarily fix them before brazing. For this temporary fixing, in the first embodiment, the holes 4 of the tank plate 362 are
A plurality of claw pieces 44c, 45c projecting to the tubular body 37 side are integrally formed on the peripheral edge portions of 4a, 45a.
45c is press-fitted into the inner peripheral portions of the holes 44b and 45b to temporarily fix the tank plate 362 and the tubular body 37.

However, when the present inventors actually made a prototype and examined it, as shown in FIG.
The holes 44a, 45a of the one end side (lower end side) in the longitudinal direction
When it is provided at a position biased to, there is no means for supporting and fixing the other end side of the tubular body 37, so that the tubular body 37 can be removed before the condenser assembly is transported into the brazing furnace. The other end is shown in FIG.
It was found that the normal assembling position in (a) is shifted to the position in FIG. 17 (b), resulting in brazing failure.

Therefore, in the eleventh embodiment, an improvement is made in order to eliminate the problem that the tubular body 37 is displaced from the regular assembling position. It is designed to be fixed with. That is, FIGS. 18 to 20 show a specific structure of the eleventh embodiment. In this embodiment, one of the tank plate 362 and the tubular body 37 is shown.
As in the case of the first embodiment, the plurality of claw pieces 44c and 45c integrally formed on the peripheral edge of the holes 44a and 45a of the tank plate 362 are fixed to the cylindrical body 3 as in the first embodiment.
The holes 44b and 45b of No. 7 are press-fitted into the inner peripheral portions of the holes.

Here, in the eleventh embodiment, the holes 44a and 45a of the tank plate 362 and the hole 44 of the tubular body 37 are provided.
Different from the first embodiment, each of b and 45b is formed with one hole, and the separator 42 is arranged at the center of the one hole, so that the upper communication chamber 46 and the lower communication chamber 47 are formed.
And the refrigerant inlet 44 and the refrigerant outlet 45.
Are partitioned.

Then, the tank plate 362 and the cylindrical body 3
The other one of the positions of 7 is fixed (the upper side of the vertical direction is fixed) by using another separator 62. This separator 62 is used in the eighth embodiment (FIG. 14) and the tenth embodiment (FIG. 1).
This is used to partition the upper communication chamber into two chambers 46 and 46a in order to make the refrigerant flow in the condensation section 8 described in 6) an S-turn.

When the separator 62 is press-molded into a substantially disc shape in order to fix the tank plate 362 and the tubular body 37 using this separator 62, the outer peripheral portion of the substantially disc shape is removed. Projecting portion 62a projecting toward the tubular body 37 side
Are integrally molded. Here, the separator 62 is formed from an aluminum plate in which a brazing material is clad on both sides.

On the other hand, the plane portion 36 of the tank plate 362
3 and the flat surface portion 371 of the tubular body 37, the slit-shaped hole 363 into which the protruding portion 62a of the separator 62 can be fitted.
a and 371a are formed. Therefore, after the protruding portion 62a of the separator 62 is fitted into the holes 363a and 371a, the protruding portion 62a is bent in the direction of arrow Z in FIG. Can be fixed.

Bending of the protruding portion 62a of the separator 62 can be performed by inserting an appropriate jig inside the tubular body 37 and applying a pressing force to the protruding portion 62a.
Moreover, the direction of bending is not limited to the arrow Z direction in FIG. 19, and it is needless to say that it may be the direction opposite to the arrow Z direction (right direction in FIG. 19). As described above, the tubular body 37
Is a fixing portion formed by press-fitting a plurality of claw pieces 44c, 45c integrally formed on the peripheral portions of the holes 44a, 45a, and the separator 6
Since the two protruding portions 62a can be fixed to the tank plate 362 at two positions on the fixing portion by bending, the fixing position of the tubular body 37 is set to the position shown in FIG.
As shown in (b), the regular assembly position of FIG. 17 (a) can be reliably held during brazing without being distorted.

Therefore, the cylindrical body 37 is attached to the tank plate 3
62 can always be brazed well. The advantage of the eleventh embodiment is that the tubular body 37 and the tank plate 36 are
This is achieved when the structure of 2 and the structure of 2 are formed separately and are joined (brazed) to each other.
The structure of the eleventh embodiment (two-point fixing structure of the tubular body 37) is obtained by integrally molding the header plate 36 and the tank plate 362 with one tubular component 365 as in the fifth embodiment.
May be combined.

Also in the eleventh embodiment, as in the first embodiment, the two holes 44a in the tank plate 362,
A plurality of claw pieces 44c, 45c projecting to the tubular body 37 side are integrally formed on the peripheral edge of 45a.
It goes without saying that the tank plate 362 and the tubular body 37 may be temporarily fixed by press-fitting into the inner peripheral portions of the two holes 44b and 45b of the tubular body 37.

In this case, the claw pieces 44c and 45c may be formed only on the peripheral portion of one of the holes 44a and 45a of the tank plate 362. [Modifications] In each of the above-described embodiments, the present invention is applied to the air conditioner for automobiles, but the present invention is applied to any air conditioner in which the fluctuation of the refrigerant circulation amount is large, such as railroad vehicles, ships and aircrafts. You may.

In each of the above embodiments, the second header 1
Although various specific examples have been described for No. 6, the first header 15
As with the second header 16, various modifications are possible.

[Brief description of drawings]

FIG. 1 is a configuration diagram showing a refrigeration cycle of an automobile air conditioner used in a first embodiment of the present invention.

FIG. 2 is a sectional view showing a liquid receiver integrated refrigerant condenser used in the first embodiment of the present invention.

3 is a partial exploded perspective view of the liquid receiver integrated refrigerant condenser of FIG. 2. FIG.

4 is a cross-sectional view showing the second header of FIG. 2, taken along line A of FIG.
-A cross section is shown.

5A is a front view of a tank plate of a second header in the first embodiment, and FIG. 5B is a front view of a tubular body of the second header.

6 is a sectional view showing a second embodiment of the present invention, and FIG.
A cross section corresponding to is shown.

FIG. 7 is a sectional view showing a third embodiment, showing a section corresponding to FIG.

FIG. 8 is a front view of a condenser showing a fourth embodiment.

9 is a sectional view taken along line BB of FIG.

10 is a perspective view of the tubular part 376 shown in FIGS. 8 and 9. FIG.

FIG. 11A is a perspective view of a tubular body 37 showing a fifth embodiment, and FIG. 11B is a sectional view of an essential part showing an assembled state of the tubular body 37 and the tubular component 365. .

FIG. 12 is a front view of a condenser showing a sixth embodiment.

FIG. 13 is a front view of a condenser showing a seventh embodiment.

FIG. 14 is a sectional view of a condenser showing an eighth embodiment.

FIG. 15 is a front view of a condenser showing a ninth embodiment.

FIG. 16 is a front view of a condenser showing a tenth embodiment.

FIG. 17 is a side view of a condenser header section showing a technical problem of the eleventh embodiment.

FIG. 18 is an exploded perspective view of a condenser header portion of an eleventh embodiment.

FIG. 19 is a partial cross-sectional view of the condenser header portion of the eleventh embodiment.

FIG. 20 is a partial cross-sectional view of another portion of the condenser header portion of the eleventh embodiment.

[Explanation of symbols]

 1 Refrigeration cycle 3 Refrigerant condenser with integrated receiver 4 Sight glass 8 Condensing part 9 Liquid receiving part 10 Supercooling part 14 Core 15 1st header 16 2nd header 19 Condensing tube 21 Supercooling tube 42 Separator (partitioning part) ) 44 refrigerant inlet 45 refrigerant outlet 46 upstream communication chamber 47 downstream communication chamber 48 gas-liquid separation chamber

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor, Michiyasu Yamamoto, 1-1, Showa-cho, Kariya city, Aichi Prefecture, Nihon Denso Co., Ltd. (72) Inventor, Koji Yamanaka, 1-1, Showa-cho, Kariya city, Aichi prefecture Co., Ltd. (72) Inventor Kaoru Tsuzuki 1-1, Showa-cho, Kariya city, Aichi Prefecture Nihondenso Co., Ltd.

Claims (17)

[Claims] 1. A core having a condensing portion for condensing a horizontally flowing refrigerant, and (b) a vertically extending portion at one end of the core,
A header to which the downstream end of the condensing part is connected, (c) a communication chamber provided inside the header and communicating with the downstream end of the condensing part, and (d) a side of the communication chamber in the header. A gas-liquid separation chamber for separating the refrigerant into a liquid and a gas; and (e) in the header, a refrigerant inflow means for causing the refrigerant in the communication chamber to flow into the gas-liquid separation chamber; and (f) in the header, A refrigerant outflow means located below the refrigerant inflow means for outflowing the liquid refrigerant in the gas-liquid separation chamber to the outside of the separation chamber; and (g) the header has a length in the vertical direction of the communication chamber portion. The receiver-integrated refrigerant condenser is characterized in that the vertical length of the gas-liquid separation chamber portion is shortened. 2. A core having a condensing section for condensing a horizontally flowing refrigerant, and (b) a core extending vertically in one end of the core,
A header to which the downstream end of the condensing part is connected, (c) a communication chamber provided inside the header and communicating with the downstream end of the condensing part, and (d) a side of the communication chamber in the header. A gas-liquid separation chamber for separating the refrigerant into a gas and a liquid, and (e) the header, which is provided at a portion corresponding to a liquid refrigerant storage section below the gas-liquid separation chamber, and stores the refrigerant in the communication chamber into the gas. Refrigerant inflow means for inflowing into the liquid refrigerant in the liquid separation chamber, and (f) The liquid refrigerant in the gas-liquid separation chamber is provided at a position lower than the refrigerant inflow means, and the liquid refrigerant in the gas-liquid separation chamber directly flows out of the condenser. (G) the header is configured such that the vertical length of the gas-liquid separation chamber portion is shorter than the vertical length of the communication chamber portion. Characteristic liquid receiver integrated refrigerant condenser. 3. (a) A condensing section for condensing a horizontally flowing refrigerant is arranged on the upper side, and a supercooling section for horizontally cooling the refrigerant condensed by this condensing section to supercool is arranged on the lower side. (B) vertically extending at one end of the core,
A header to which the downstream end of the condensing part is connected to the upper side part and to which the upstream end of the supercooling part is connected to the lower side part; and (c) which is provided inside the header and communicates with the downstream end of the condensing part. And (d) a downstream communication chamber that is provided inside the header below the upstream communication chamber and is partitioned from the upstream communication chamber, and that communicates with an upstream end of the supercooling unit. (E) a gas-liquid separation chamber that is provided on the side of the both communication chambers in the header and that separates the refrigerant into a gas and a liquid; and (f) is disposed in a lower portion of the upstream communication chamber, and from the upstream communication chamber. Refrigerant inflow means for injecting the refrigerant into the liquid refrigerant storage portion below the gas-liquid separation chamber; and (g) Disposing the liquid refrigerant from the gas-liquid separation chamber into the downstream communication chamber, which is arranged below the refrigerant inflow means. (H) the header comprises: Integrated type condenser-receiver, wherein the vertical length of the gas-liquid separation chamber portion than the vertical length of the communication chamber portion is configured to be shorter. 4. (a) A condensing section for condensing a horizontally flowing refrigerant is arranged on the upper side, and a supercooling section for horizontally cooling the refrigerant condensed by the condensing section is arranged on the lower side. (B) vertically extending at one end of the core,
A header to which the downstream end of the condensing part is connected to the upper side part and to which the upstream end of the supercooling part is connected to the lower side part; and (c) which is provided inside the header and communicates with the downstream end of the condensing part. And (d) a downstream communication chamber that is provided inside the header below the upstream communication chamber and is partitioned from the upstream communication chamber, and that communicates with an upstream end of the supercooling unit. (E) a gas-liquid separation chamber, which is provided at a side of the both communication chambers in the header, and separates the refrigerant into a gas and a liquid; (f) an upper opening of the gas-liquid separation chamber to the upstream communication chamber; Refrigerant inflow means for allowing a refrigerant to flow into the gas refrigerant in the upper part of the gas-liquid separation chamber from the upstream communication chamber, and (g) an opening to the downstream communication chamber below the gas-liquid separation chamber, the gas-liquid separation chamber And a refrigerant outflow means for outflowing the liquid refrigerant into the downstream side communication chamber, ) The header is integrated type condenser-receiver, wherein the heights of the gas-liquid separation chamber portion than to the two communicating chamber portion is configured to be lower. 5. The upper end of the gas-liquid separation chamber portion is lower than the upper ends of both communication chamber portions, and the lower end of the gas-liquid separation chamber portion is higher than the lower ends of both communication chamber portions. The liquid receiver integrated refrigerant condenser according to any one of claims 1 to 4. 6. The header is inserted with tube ends of a condenser part and a supercooling part of the core, and is joined to the header plate, and the header plate is joined to the header plate. A tank plate that forms the upstream communication chamber and the downstream communication chamber, a partition that separates the space formed by the header plate and the tank plate into the two communication chambers, and a side surface that is joined to the outer surface of the header tank. A cylindrical body having a height lower than that of the header plate and the tank plate and forming the gas-liquid separation chamber therein; Refrigerant inflow means for inflowing into the liquid refrigerant, and refrigerant outflow located below the refrigerant inflow means for outflowing the liquid refrigerant in the gas-liquid separation chamber into the downstream communication chamber. Integrated type condenser-receiver according to any one of claims 3 to 5, characterized in that a stage. 7. The receiver-integrated refrigerant condenser according to claim 6, wherein a joint portion between the tank plate and the cylindrical body is formed into a flat shape. 8. The liquid receiver-integrated refrigerant condenser according to claim 6, wherein a joint portion between the tank plate and the cylindrical body has a curved shape. 9. The liquid receiver integrated refrigerant condenser according to claim 6, wherein the tubular body is integrally formed by extrusion. 10. The liquid receiver integrated refrigerant condenser according to claim 6, wherein the tubular body is formed by bending a metal plate into a tubular shape. 11. The structure according to claim 6, wherein the header plate and the tank plate have a structure in which one metal plate is bent into a tubular shape and integrally joined.
A receiver-integrated refrigerant condenser according to item 6. 12. The header is inserted with the tube ends of the condensing part and the supercooling part of the core, and the header plate is joined with the tube ends, and the header plate is joined with the header plate. A header tank that forms the upstream communication chamber and the downstream communication chamber, a partition that separates the space formed by the header plate and the header tank into the two communication chambers, and extrudes to the outer surface side of the header tank. A cylindrical body integrally formed with the header tank by processing, having a height lower than the heights of the header plate and the header tank, and forming the gas-liquid separation chamber therein; Refrigerant inflow means for inflowing the indoor refrigerant into the liquid refrigerant in the gas-liquid separation chamber, and a liquid refrigerant in the gas-liquid separation chamber located below the refrigerant inflow means. Integrated type condenser-receiver according to claim 3, characterized in that and a refrigerant outflow means for flowing downstream communication chamber. 13. A sight glass for observing a state of a refrigerant is connected in the middle of a refrigerant pipe downstream of the supercooling section, according to any one of claims 3, 4, 7, and 12. The receiver-integrated refrigerant condenser according to [4]. 14. The liquid receiver-integrated refrigerant condenser according to claim 7, wherein the joint portion is formed by a plane protrusion that protrudes from a part of the plane shape with a step. 15. In the header, the gas-liquid separation chamber is composed of a tubular body that is separate from the member that constitutes the communication chamber, and the tubular body is provided at two positions in the vertical direction. After being fixed to the member forming the communication chamber, the tubular body and the member forming the communication chamber are integrally brazed to each other. The receiver-integrated refrigerant condenser according to [4]. 16. A claw piece projecting toward the tubular body is formed at a peripheral edge of at least one of the refrigerant inflow means and the refrigerant outflow means, and the claw piece connects the tubular body and the communication chamber. One of the fixing points with the constituent members is configured, and the communication chamber is provided with a partition member that partitions the inside thereof in the vertical direction. The partition member is integrally formed with a protruding portion that protrudes toward the tubular body side. 16. The liquid receiver according to claim 15, wherein the protruding portion of the partition member configures the other of the fixing points of the tubular body and the member forming the communication chamber. Body type refrigerant condenser. 17. The receiver-integrated refrigerant condenser according to claim 1, wherein the constituent parts of the condenser are made of aluminum and temporarily assembled into a predetermined structure,
A method for manufacturing a refrigerant condenser integrated with a liquid receiver, which comprises integrally joining by brazing.