JPH0510633A - Condenser - Google Patents

Abstract

PURPOSE:To produce a condenser which is capable of forming a stabilized refrigeration cycle with improvement in refrigerating capacity and coefficient of performance by supercooling refrigerant in the condenser. CONSTITUTION:Refrigerant flowing through refrigerant tubes 10a, 10c undergoes condensation through release of heat through radiating fins 12a, 12c. Between the refrigerant tubes 10a placed upstream and the refrigerant tubes 10c placed downstream there is provided a receiver tube 26 which forms a passageway with a larger area than the passageway in the refrigerant tubes 10a, 10c. The passageway for refrigerant inside the receiver tube 26 is divided into two channels one channel 31 above the other channel 33 with a plate 32 used as a partition. Through the plate 32 holes 40 are opened by which the upper and lower channels 31, 33 communicate. By virtue of the condenser the receiver tube 26 in this condenser serves to separate the refrigerant into two phases of gas and liquid in the manner of a receiver and, moreover, has the function of a subcooler for supercooling liquid refrigerant at a subsidiary condensation part 8.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a condenser used for car air conditioners and the like.

[0002]

2. Description of the Related Art As a condenser for a car air conditioner, there is known a condenser in which a condenser and a liquid receiver are integrated, as disclosed in Japanese Utility Model Laid-Open No. 38055/1990. In this case, the degree of supercooling at the refrigerant outlet of the condenser is always controlled to zero.

[0003]

However, according to such a conventional condenser, the liquid refrigerant is heated in the middle of the pipe connected to the refrigerant outlet of the condenser due to heat from the inside of the engine room and the like. When air bubbles are generated in the expansion valve and the air bubbles enter the expansion valve, the refrigeration cycle becomes unstable, which causes a problem that not only a sufficient refrigeration capacity is not obtained but also noise is generated.

The present invention has been made in order to solve such a problem, and it is possible to improve the refrigerating capacity and the coefficient of performance by supercooling the refrigerant in the condenser and to form a stable refrigerating cycle. The purpose is to provide a condenser.

[0005]

A condenser according to a first aspect of the present invention for achieving the above object comprises a refrigerant passage pipe constituting a refrigerant passage, and a fin joined to the refrigerant passage pipe. A condenser that condenses by radiating heat through a flow of a refrigerant flowing through the refrigerant passage tube, the refrigerant passage having a passage area larger than the passage area of the refrigerant passage in the middle of the refrigerant passage, and the refrigerant. A receiver tube provided with a partition plate that divides the passage into upper and lower chambers and has a hole that communicates the upper chamber and the lower chamber, and the refrigerant flow separated into the lower chamber in the receiver tube. Further, it is characterized in that it is provided with a refrigerant passage pipe forming a refrigerant passage and an auxiliary condenser portion including fins joined to the refrigerant passage pipe so as to be supercooled.

The condenser according to the first aspect of the present invention is characterized in that the hole is formed downstream of the center of the partition plate in the refrigerant flow.

[0007]

According to the condenser of the present invention, not only has the receiver function of separating the refrigerant into gas-liquid two phases by the receiver tube, but also has the subcooler function of subcooling the liquid refrigerant in the auxiliary condenser section. Both the coefficient of performance can be improved.

[0008]

Embodiments of the present invention will be described below with reference to the drawings. As shown in FIG. 2, the refrigerant circuit that constitutes the refrigeration cycle includes a compressor 1, a condenser 2, an expansion valve 3 and an evaporator 4. Of these, the condenser 2 is a laminated condenser and has a condensing function, a liquid receiver function, and a supercooling function.

As shown in FIG. 1, the condenser 2 comprises a main condenser portion 6, a gas-liquid separation portion 7, and an auxiliary condenser portion 8. The main condenser portion 6 is configured as a header type, and includes the refrigerant tube 10a and the heat radiation fin 1
The core portion 13 is formed by alternately laminating 2a, and the header portions 15 and 17 connected to both left and right sides of the core portion 13.
The refrigerant tube 10a is formed of, for example, a single tube flat tube or a porous flat tube whose inside is divided into a plurality of passages, and the heat radiation fins 12a are formed of plate fins or corrugated fins. The heat radiation fin 12a is joined to the side surface of the refrigerant tube 10a by brazing, soldering or the like. Further, the refrigerant inlet pipe 16 is connected to the header portion 15, and the header portion 15
A partition wall 14 is provided inside. A partition wall 18 is provided inside the header portion 17.

The gas-liquid separating section 7 is composed of a receiver tube 26 which is a rectangular tube having a diameter larger than that of the refrigerant tube 10a of the main condenser section 6, and sends the refrigerant from the main condenser section 6 to the auxiliary condenser section 8. . The receiver tube 26, as shown in FIGS. 3, 4 and 5,
A plate 32 for partitioning the inside of the rectangular tube 30 into upper and lower two stages is fitted in the longitudinal direction.
The upper cap 34 is fitted to the right end of the upper flow path 31 partitioned by the upper and lower parts, and the lower cap 36 is fitted to the left end of the lower flow path 33. In the downstream portion of the plate 32, four holes 40 having an inner diameter of about 5 mm are formed in the widthwise central portion at equal intervals in the longitudinal direction. These holes 40 are shown in FIG.
It is formed on the right side of the central part. This is because when the hole 40 is formed on the right side of the central portion, the liquid refrigerant can be passed through the upper channel 31 to the lower channel 33 in preference to the gas refrigerant. The number, the inner diameter, and the position of the holes formed in the plate 32 are not limited to those described above.

A method of manufacturing the receiver tube 26 will be described with reference to FIGS. A tube 30 made of an aluminum material and having a rectangular cross section shown in FIG. 6 is manufactured by extrusion molding. Further, as shown in FIG. 7, several holes 40 are formed after the central portion of the aluminum plate 32 in the longitudinal direction.
To form. This plate 32 is used as the groove portion 3 of the tube 30.
Insert into 0a. Then, a cap 34 made of an aluminum material is fitted and brazed to one passage side of the end surface of the tube 30 on one side. A cap 36 made of an aluminum material is fitted and brazed to the passage side opposite to the opposite end face. At this time, the hole 40 should come to the rear of the direction in which the refrigerant flows,
Further, the cap 34 is arranged so as to come to the upper stage side at the end surface on the hole 40 side.

Next, the structure of the header portion will be described with reference to FIGS. 9 and 10. Cylindrical header part 15, 1
Hole 52 into which the refrigerant tubes 10a and 10c can be inserted
And holes 54 into which the receiver tubes 26 can be inserted are formed, and the refrigerant tubes 10a, 10
c and the receiver tube 26 are inserted, and the header portions 15 and 17, the refrigerant tubes 10a and 10c, and the receiver tube 26 are integrally brazed and joined. The header portion can also have a flat shape.

The auxiliary condenser section 8 is of a header type like the main condenser section 6, and has a refrigerant tube 10c.
13 in which heat radiation fins 12c are alternately laminated
And left and right header parts 22 and 20. The auxiliary condenser section 8 has a function of further supercooling the liquid refrigerant in which the refrigerant flow from the gas-liquid separating section 7 is condensed. Next, how the refrigerant is condensed will be described in detail with reference to FIG.

A gas refrigerant is supplied to the inside of the header portion 15 of the main condenser portion 6 from a refrigerant inlet pipe 16. The supplied gas refrigerant flows through the refrigerant tube 10a that connects the header portion 15 and the header portion 17, and is cooled during this period to reach the header portion 17. The gas refrigerant exchanges heat with the outside air through the heat radiating fins 12a to radiate heat while passing through the refrigerant tube 10a of the main condenser unit 1, and is condensed to form a condensed liquid (liquid refrigerant) and a gas (gas refrigerant). It becomes a gas-liquid two-phase state.
Then, the proportion of the condensed liquid increases and the condensed liquid is sent to the gas-liquid separation unit 7.

In the main condenser section 6, the condensed liquid and the gas-liquid 2
The refrigerant flow in the phase state is then introduced into the refrigerant passage of the gas-liquid separating section 7, that is, the receiver tube 26. The refrigerant in the receiver tube 26 has a gas-liquid two-phase flow rate ratio of gas-liquid, but the refrigerant flow flows in the receiver tube 26 in the right direction in FIG. 1 without changing the gas-liquid ratio. On the way, the gas and the liquid are separated vertically due to the influence of gravity, and the liquid refrigerant preferentially drops from the gas refrigerant from the upper flow passage 31 through the hole 40 to the lower flow passage 33. Is sent to the header section 20. This liquid refrigerant is the refrigerant tube 1
It is sent to the header section 22 through 0c. This liquid refrigerant is
While passing through the refrigerant tube 10c of the auxiliary condenser portion 8, heat is exchanged with the outside air through the heat radiating fins 12c to radiate heat.
The supercooled state is established and the supercooled liquid refrigerant is sent to the header portion 22.

Next, the refrigerating cycle of this refrigerant will be explained based on the Mollier diagram shown in FIG. The dry refrigerant vapor in the A state is compressed by the compressor 1 shown in FIG. 2 and becomes high temperature and high pressure in the B state. This high-temperature, high-pressure refrigerant vapor radiates heat in the main condenser portion 6 and is partly liquefied to be in a gas-liquid two-phase C state. Next, it enters the gas-liquid separation section 7 and separates into a gas phase and a liquid phase,
The liquid refrigerant enters the auxiliary condenser section 8. At this time, the degree of supercooling is zero, but further subcooling is performed in the auxiliary condenser unit 8 to reach the supercooling region in the E state. In the E state, the liquid refrigerant is supercooled. This liquid refrigerant passes through the expansion valve 3 and squeezes and expands into a low-temperature low-pressure gas-liquid mixed state and enters the evaporator 4 into the F state. In the evaporator 4, the refrigerant takes heat from the surrounding air to be vaporized, enters the overheated region A state, enters the compressor 1 again, and repeats the above refrigeration cycle.

In the conventional comparative example, the enthalpy difference (r ₁ ) of the refrigerating capacity in the evaporator 4 is small because it stops at the position of the D state where the degree of supercooling is zero and is not further cooled. . On the other hand, in the above embodiment, the enthalpy difference (r ₂ ) is relatively large. Note that W indicates the work of the compressor. In the high load condition, the curve of the refrigeration cycle is drawn in the upper right.

Next, experimental data according to the above embodiment of the present invention are shown in FIGS. The experimental load conditions were a condenser temperature of 35 ° C., a wind speed of 4.5 m / s, an evaporator temperature of 27 ° C., a humidity of 50%, a blower air volume of 300 m ³ / min, and a compressor rotation speed of 1800 rpm. Supercooling degree 0 ℃
As shown in FIG. 12, the power of the compressor does not change so much to a certain range. However, if it exceeds a certain degree of supercooling, the power of the compressor increases. Further, in FIG. 13, the refrigerating capacity is improved up to a certain range, but it is not improved any further. It can be understood from FIGS. 12 and 13 that the coefficient of performance is improved when the supercooling degree is 0 ° C. when the supercooling degree is excessive.

Next, a second embodiment in which the present invention is applied to a serpentine type condenser is shown in FIGS. 15 and 16. The second embodiment is a corrugated tube type condenser, in which a pipe-shaped refrigerant tube 60 is meandered and a receiver tube 62 is provided in the middle thereof.
Refrigerant tube 6 including an auxiliary condenser unit 70 at the downstream end of the
4 is an example in which No. 4 is formed. In FIG. 15, a main condenser unit 66, a gas-liquid separating unit 68, and a supplementary condenser unit 70 are configured. Radiating fins 72 are joined between the adjacent refrigerant tubes 60 of the refrigerant tubes 60 by brazing, soldering or the like. The receiver tube 62 has partition walls 74 formed in upper and lower two stages, and several holes 76 are formed on the downstream side of the partition walls 74. The refrigerant that has entered from the refrigerant inlet 78 radiates heat in the main condenser portion 66, becomes a gas-liquid mixed state, and enters the gas-liquid separation portion 68, and the liquid refrigerant thereof falls through the hole 76 into the lower flow path and the auxiliary condenser portion 70. Flowing through the refrigerant tube 64 to become a supercooled liquid refrigerant and is sent out from the refrigerant outlet 82.

As shown in the above embodiment, according to the present invention,
Integrate the condenser, receiver and auxiliary condenser,
The receiver tube has a special shape and is divided into two stages to effectively separate the liquid refrigerant and the gas refrigerant.

[0021]

As described above, according to the condenser of the present invention, the condenser portion, the gas-liquid separating portion, and the auxiliary condenser portion having a supercooling function are integrated into each other without connecting them by piping. With this configuration, the refrigerating capacity and the coefficient of performance of the refrigerating cycle can be improved, and there is an effect that space saving and compactness can be achieved by eliminating the piping of the refrigerant circuit.

[Brief description of drawings]

FIG. 1 is a schematic configuration diagram showing a condenser according to a first embodiment of the present invention.

FIG. 2 is a refrigerant circuit diagram showing a refrigeration cycle to which the condenser according to the first embodiment of the present invention is applied.

FIG. 3 is a vertical sectional view showing a receiver tube according to the first embodiment of the present invention.

FIG. 4A is a view on arrow A shown in FIG. (B) is a view on arrow B shown in FIG. 3.

5 is a view on arrow C of the plate shown in FIG. 3. FIG.

FIG. 6 is a partial side view of a receiver tube.

FIG. 7 is an explanatory diagram showing a step of attaching a plate to a tube of a receiver tube.

FIG. 8 is an explanatory diagram showing a state in which a cap is attached to the tube of the receiver tube.

FIG. 9 is a partial perspective view showing a header portion.

FIG. 10 is a plan view showing a header section.

FIG. 11 is a Mollier diagram comparing the refrigeration cycle according to the first embodiment of the present invention with the refrigeration cycle according to the conventional comparative example.

FIG. 12 is a characteristic diagram showing the relationship between the degree of supercooling and the required power of the compressor according to the experimental data of the first embodiment of the present invention.

FIG. 13 is a characteristic diagram showing the relationship between the degree of supercooling and the refrigerating capacity according to the experimental data of the first embodiment of the present invention.

FIG. 14 is a characteristic diagram showing the relationship between the degree of supercooling and the coefficient of performance according to the experimental data of the first embodiment of the present invention.

FIG. 15 is a schematic configuration diagram showing a condenser according to a second embodiment of the present invention.

FIG. 16 is a partial perspective view showing a mounted state of a refrigerant tube and a receiver tube according to a second embodiment of the present invention.

[Explanation of symbols]

6 Main capacitor section 7 Gas-liquid separation section 8 Auxiliary capacitor section 10a, 10c Refrigerant tube (refrigerant passage tube) 12a, 12c Heat dissipation fin 26 receiver tube 31, 33 Channel (room) 32 plates (partition plate) 40 holes

Continued front page    (72) Inventor Toshio Ohara             Nihonden, 1-1, Showa-cho, Kariya city, Aichi prefecture             Sozo Co., Ltd.

Claims (2)

[Claims] 1. A condenser comprising a refrigerant passage pipe forming a refrigerant passage and fins joined to the refrigerant passage pipe, wherein the refrigerant flow flowing in the refrigerant passage pipe is radiated through the fins to condense to condense. And a hole having a passage area larger than the passage area of the refrigerant passage in the middle of the refrigerant passage and partitioning the refrigerant passage into upper and lower two-stage chambers and connecting the upper chamber and the lower chamber. A receiver tube provided with a partition plate having, a refrigerant passage tube that constitutes a refrigerant passage and a refrigerant passage tube that constitutes a refrigerant passage so as to further subcool the refrigerant flow separated into the lower chamber in the receiver tube. A condenser, comprising: an auxiliary condenser section including joined fins. 2. The condenser according to claim 1, wherein the hole is formed on the downstream side of the refrigerant flow from the central portion of the partition plate.