KR100639175B1 - One piece type heat exchanger - Google Patents

Abstract

The present invention relates to an integrated heat exchanger, by which the evaporator and the heater core are integrated to form a compact air conditioner, to reduce the cost and to improve the productivity, in particular to the integrated heat exchanger that can improve the cooling performance It is for the purpose of providing a flag.

The present invention provides an evaporator 2 through which a cooling medium formed by stacking a plurality of flat tubes 21 in which two L-shaped plates are laminated in turn, and an L-shaped space, which is generally formed in a rectangular planar shape. A heater core 3 through which the heating medium circulates, heat transfer fins 4 shared between the evaporator 2 and each flat tube of the heater core 3, and the evaporator 2 and the heater core. In the integral heat exchanger provided with a notch part to block heat transfer between (3), the first flow path 231 and the second flow path at the lower end of each plate so that each plate 23 constituting the evaporator 2 passes in turn. The ball 232 and the third flow path 233 are formed in turn, and a partition bead is formed from the central second flow hole 232 to a part of the bent portion of the upper end, so that the inner surface of each plate 23 has an L-turn flow path. 237 is formed, and the first euro hole 231 is formed. The first plate 211 ′ at the end of the first half portion 211 and the second half portion 212 are partitioned into the first half portion 211 and the second half portion 212 by the blocked central plate 213. The second end plate 212 ′ at the end of the second half 212 has all of the flow paths 231, 232, and 233 blocked, such that the first flow path 231 and the first flow path 231 in each plate 23 of the first half 211 are closed. First and second flow paths 231a and 233a are formed by the third flow hole 233, and the first flow path 231 and the third flow hole 233 in each plate 23 of the second half portion 212. The third and fourth flow paths (231b, 233b) are formed, and the refrigerant flowing into the first flow path 231a of the first half portion 211 flows through the L-turn flow path 237 to the second flow path 233a. The flow refrigerant flows through the third flow path 233 of the center plate 213 to the fourth flow path 233b of the second half portion 212, and then through the L-turn flow path 237, the third flow path 231b. And flows in both first and second parts 211 and 212. It is formed by the second flow path 232 is characterized in that the discharge through the fifth flow path (232a) connected to the third flow path (231b).

Integrated Heat Exchanger, Heat Exchanger

Description

Integrated Heat Exchanger {ONE PIECE TYPE HEAT EXCHANGER}

1 is a partial front view showing an integrated heat exchanger according to the present invention.

Figure 2a is a perspective view showing the operating state of the integrated heat exchanger according to the present invention, Figure 2b is a perspective view showing the first half partitioned by the central plate of the evaporator, Figure 2c is a perspective view showing the second half partitioned by the center plate of the evaporator to be.

3 is a configuration diagram showing an operating state of the air conditioner to which the integrated heat exchanger according to the present invention is applied.

4 is a perspective view showing a conventional integrated heat exchanger.

5 is a partial front view showing a conventional integrated heat exchanger.

6 is a partially exploded perspective view showing a conventional integrated heat exchanger.

7 is a configuration diagram showing an operating state of an air conditioner to which a conventional integrated heat exchanger is applied.

<Explanation of symbols for the main parts of the drawings>

2: evaporator, 3: heater core,

4: heating fin, 21: flat tube of evaporator,

23: evaporator plate, 31: flat tube of the heater core,

33: heater core plate, 231, 232, 233: euro ball,
231a, 233a: 1st, 2e euro, 231b, 233b: 3rd, 4euro,

235: compartment bead, 237: L turn euro,

245: connecting projection, 247: notch

The present invention relates to an integrated heat exchanger, and in particular, the evaporator and the heater core are integrated to form a compact air conditioner, to reduce cost and productivity, and to provide an integrated heat exchanger. It is about the flag.

The automotive air conditioner includes a cooling system for cooling the interior of a vehicle and a heating system for heating the interior of the vehicle. The cooling system is configured to cool the interior of a vehicle by heat exchange by an evaporator while the heat exchange medium discharged by the operation of the compressor is circulated back to the compressor via a condenser, a receiver drier, an expansion valve, and an evaporator. The coolant is configured to heat the room by introducing heat exchange into the heater core.

In a general air conditioner, an evaporator and a heater core are separately installed in an air conditioner case. In this case, mold development cost is high because the number of components of the evaporator and the heater core increases, and as the assembly line for the evaporator and the heater core is separately installed, the production line for the evaporator and the heater must be installed separately, thereby increasing the equipment cost. The cost of assembly and labor is high, resulting in higher costs and lower productivity. In addition, since the evaporator and heater core must be separately installed in the air conditioning case, additional installation of the temperature control door is required, which not only complicates the air conditioning case but also increases the size of the air conditioning case, thereby deteriorating the mountability of the vehicle. In addition, when the air conditioning system is complicated, the resistance increases in the flow of air blown from the blower into the air conditioning case, resulting in a decrease in system air volume, an increase in noise, and a decrease in air conditioning performance.

In consideration of this point, a heat exchanger in which an evaporator and a heater core are integrated has been proposed, which is disclosed in Japanese Patent Laid-Open No. 9-39553.

As shown in FIGS. 4 to 7, the heat exchanger is formed in an L shape, and is provided with a first heat exchanger 101 through which a cooling medium flows, and is installed in a space of the L shape to form a rectangular planar shape as a whole. A second heat exchanger 111 through which the medium flows, and a heat transfer fin 121 shared by the first heat exchanger 101 and the second heat exchanger 111. A notch part (not shown) is installed between the two heat exchangers 101 and 111 to block heat transfer, and the discharge side of the air is part of the discharge side of the first heat exchanger 101 and all of the discharge side of the second heat exchanger 111 ( It is comprised by the whole part.

Therefore, the integrated heat exchanger configured as described above is assembled to the air conditioning case 131 constituting the air conditioner as shown, and the first heat exchanger 101 serving as an evaporator is connected to the cooling system and the heater core. When the functioning second heat exchanger 111 is connected to the heating system, when the temperature control door 133 is closed, the air blown by the blower 135 flows through the first heat exchanger 101. Heat exchanged and cooled, and the cooled air is heat-exchanged with the hot water flowing through the second heat exchanger 111 when passing through the second heat exchanger 111, and the cold air passes through the upper vent 137, and The warm air is discharged through the lower vent 139 toward the upper body of the passenger in the cabin, thereby cooling or heating the interior of the cabin.

In addition, when the temperature control door 133 is opened, a part of the air cooled by the first heat exchanger 101 (that is, the temperature control door 133 side of the first heat exchanger 101) is directly vented. The remaining portion of the air discharged into the vehicle interior via the 137 and cooled by the first heat exchanger 101 is heat-exchanged with the second heat exchanger 111 to lower the lower body of the passenger in the vehicle interior through the lower vent 139. Discharged to the side. Therefore, in this case, the air discharged through only the first heat exchanger 101 without being heated by the second heat exchanger 111 is a low temperature and the air has passed through the first heat exchanger 101 and the second heat exchanger 111. Since the temperature is higher than the air above, the temperature difference is increased, so that the bi-lebel state makes the user feel comfortable.

However, in the conventional integrated heat exchanger as described above, although notches are formed between the first heat exchanger 101 and the second heat exchanger 111 to minimize heat transfer between the first heat exchanger as shown in FIG. In the case of the cooling medium introduced into the first heat exchanger 101 without the heat transfer phenomenon between the heat exchanger 101 and the second heat exchanger 111 completely, the flow path is L-turn As it is discharged from the first heat exchanger 101 as it is, the heat exchange efficiency is poor, so that the air passes through only a part of the first heat exchanger 101 and the air passes through the first heat exchanger 101 and the second heat exchanger 111. The difference is not big. Therefore, a good bi-level state cannot be obtained, and thus there is a problem in that the cooling performance is particularly low.

 The present invention has been made in view of the conventional problems as described above, by the evaporator and the heater core is formed integrally can form a compact air conditioning apparatus, it is possible to reduce the cost and productivity, especially cooling performance An object of the present invention is to provide an integrated heat exchanger capable of improving the temperature.

In order to achieve the above object, the present invention, the evaporator flows through the cooling medium is formed by stacking a plurality of flat tubes are bonded to each other L-shaped plate, and installed in the space of the L-shape the overall planar shape In an integrated heat exchanger provided with a heater core circulating through the heating medium, heat transfer fins shared between each flat tube of the evaporator and the heater core, and a notch portion to block heat transfer between the evaporator and the heater core. The first euro hole, the second euro hole and the third euro hole are sequentially formed at the lower end of each plate so that each plate constituting the evaporator passes in turn, and a partition bead is formed from the central second euro hole to a part of the bent portion of the upper end. As a result, an L-turn flow path is formed on the inner surface of each plate, and the central plate in which the first flow path is blocked. The first end plate of the first end end of the first end plate is blocked by a third flow hole, and the second end plate of the second end end of the second end plate is closed of all flow paths. First and second flow paths are formed by the flow path hole and the third flow path hole, and the third and fourth flow paths are formed by the first flow path hole and the third flow hole in each plate of the second half part, and the first and second flow paths are formed. The refrigerant flowing into the flow path flows through the L-turn flow path to the second flow path, and this flow refrigerant flows through the third flow hole of the central plate to the fourth flow path in the second half, and then passes through the L-turn flow path to the third flow path. It is characterized in that the flow is formed by the second passage hole communicated in both the first half and the second half is discharged through the fifth passage connected to the third passage from the second end plate side.

The integrated heat exchanger of the present invention configured as described above is assembled to the air conditioning case constituting the air conditioner, the evaporator is connected to the cooling system, and the heater core is connected to the heating system, and before and after the evaporator portion where the heater cores do not overlap. When the first temperature control door and the second temperature control door are installed, the air blown by the blower while the two temperature control doors are closed is cooled by heat exchange with the refrigerant flowing through the evaporator, and the cooled air cools the heater core. When passing, heat is exchanged with the hot water flowing through the heater core, and the cold air is discharged through the upper vent and the warm air is discharged toward the upper body of the passenger in the cabin, thereby cooling or heating the interior of the cabin.

In addition, when the two temperature control doors are opened, part of the air cooled by the evaporator (that is, the two temperature control doors) is discharged into the cabin through the upper vent as it is, and the remaining part of the air cooled by the evaporator is Heat exchanged with the heater core is discharged through the lower vent toward the lower body of the passenger in the cabin. Therefore, in this case, air that is not heated by the heater core and is discharged only through the evaporator is low temperature, and the air passing through both the evaporator and the heater core is higher than the air above, so the temperature difference becomes large, thereby making it bi-lebel. I can feel it.

Meanwhile, the refrigerant flows into the first end flat tube of the evaporator through the first channel hole of the first end plate, and the refrigerant introduced into the flat tube flows to the center blank plate through the first channel hole of each plate. L-turn inside the flat tube to flow into the second flow path formed by the third flow paths of each plate, and the refrigerant flowing through the third flow path again passes between the blank plate and the second end plates through the third flow paths. It flows into the fourth flow path formed by the flow path holes, turns L to flow toward the first flow hole, and then flows all into the third flow path located in the blocked first flow hole of the second end plate. As such, the refrigerant flowing into the third channel of the second end plate is connected to the fifth channel located in the blocked second channel hole of the second end plate, so that the refrigerant flows into the fifth channel and then the second channel hole of each plate. Through the second flow path toward the second flow path of the first end plate is discharged from the evaporator through the second flow hole. Therefore, since the refrigerant flowing inside the evaporator flows with two L turns and is finally discharged through the entire evaporator when discharged, the heat exchange efficiency is improved, thereby improving cooling performance.

Other features and advantages of the present invention will become more apparent from the following detailed description based on the accompanying drawings.

As shown in Fig. 1 and Figs. 2a to 2c, the integrated heat exchanger according to the present invention is connected to the evaporator 2 having an L shape and integrally connected to the evaporator 2 in the space of the L shape. It consists of the heater core 3 of a substantially rectangular parallelepiped shape, and therefore has a substantially hexahedral shape as a whole.

The evaporator 2 is formed by stacking a plurality of flat tubes 21 formed by joining two L-shaped plates 23 and 23 to each other, and the heater core 3 comprises two plates 33 having a substantially rectangular shape. , 33 are formed by stacking a plurality of flat tubes 31 which are formed by bonding. Then, the flat tubes 21 of the evaporator 2 and the flat tubes 31 of the heater core 3 are arranged to correspond to each other, and a single corgate type heat transfer fin 4 is stacked therebetween. Thus, the evaporator 2 and the heater core 3 share the heat transfer fins 4.

According to the present invention, when the L-shaped plate 23 forming the flat tube 21 of the evaporator 2 is inverted as shown in the drawing, a first flow path 231 is provided at the lower end of each plate 23. ), The second flow hole 232 and the third flow hole 233 are formed in sequence. As shown in the drawing, it is preferable that the arrangement heights of the first flow path 231 and the third flow path 233 are the same, and the placement height of the second flow path 232 in the center is the first flow path 231 and the third flow path. It is preferable that it is lower than the height of arrangement of the balls 233.

In addition, the partition bead 235 is formed in an inverted L shape from the upper end of the second flow path 232 to the bent portion of the upper end, and the curved portion of the partition bead 235 is preferably curved.

The L-turn flow path 237 is formed in the plate 23 by the partition beads 235. It is preferable that the L-turn flow passage, the first flow passage 231 and the third flow passage 233 communicate with each other, and the L-turn flow passage and the second flow passage 232 do not communicate with each other.

In addition, in order to increase the heat transfer area of the refrigerant on the inner surface of the plate 23, to promote turbulence of the refrigerant, and to increase the bonding strength of the two plates 23 and 23, a plurality of embossings are arranged on the L-turn flow path 237 in a predetermined arrangement. Bead 239 is formed entirely. That is, the embossed beads 239 and 239 of the two plates 23 and 23 are formed to correspond to each other so that the embossed beads 239 corresponding to each other when brazing are bonded to each other. The embossing beads 239 may be formed in various shapes such as circular, elliptical, square, and the like, and may be formed by mixing the various embossing beads.

In addition, it is preferable that a slotted bead 241 in an oblique direction is formed at an inner surface edge portion of the plate 23 so that the flow of the refrigerant is guided well along the L-turn flow passage 237 without biasing to one side. In addition, flanges 243 for brazing the two plates 23 and 23 are formed along the edges of the plates 23, and the flanges 243 connected to the heater cores 3 are formed at predetermined intervals. A plurality of connecting protrusions 245 are formed, and therefore, notches 247 are formed between the connecting protrusions 245 in order to minimize transmission between the evaporator 2 and the heater core 3.

The two plates 23 of the evaporator 2 made as described above are joined to each other to form a flat tube 21, and the flat tubes 21 are sequentially stacked to form the evaporator 2, thereby forming the inside of the evaporator 2. A predetermined flow path through which the refrigerant flows may be formed.

According to the present invention, the first end plate disposed at one end of both outermost sides of the plates 23 constituting the evaporator 2 so that the refrigerant flows through the evaporator 2 and exhibits an optimum heat exchange efficiency. For convenience, the third flow hole 233 of the flow path holes indicated by reference numeral 211 '(see FIG. 2) is blocked. In addition, the first flow path 231 of the center plate (referred to by reference numeral 213 for convenience) (see FIG. 2) disposed in the center of the plates 23 constituting the evaporator 2 is blocked, so that the center plate 213 is closed. It functions as a blank plate. Also, all of the flow path holes 231, 232, of the second end plate (referred to by reference numeral 212 ′ for convenience) (see FIG. 2) disposed at the other ends of both outermost sides of the plates 23 constituting the evaporator 2. 233 is blocked, and the first flow path 231 and the second flow path 232 of the second end plate 212 'communicate with each other.
In other words, the first flow path 231 is partitioned into a first half portion 211 and a second half portion 212 by the central plate 213 is blocked, the first end plate 211 ′ at the end of the first half portion 211 is The third flow path 233 is blocked, and all of the flow path holes 231, 232, and 233 are blocked in the second end plate 212 ′ at the end of the second half 212.
First and second flow paths 231a and 233a are formed by the first flow path 231 and the third flow path 233 in each plate 23 of the first half 211, and the second half 212 of the second half hole 212 is formed. The third and fourth flow paths 231b and 233b are formed by the first flow path 231 and the third flow path 233 in each plate 23.
A refrigerant inlet pipe (not shown) is connected to the first flow path 231 of the first end plate 211 ', and a refrigerant discharge pipe is connected to the second flow hole 232 of the first end plate 211'. (Not shown) are connected.

Therefore, in the evaporator 2 employing the two end plates 211 'and 212' and the center plate 213, the center plate (1) through the first flow hole 231 of the first end plate 211 ' The refrigerant flows through the first flow path 231a connected to each plate 23 to the first flow path 231 of the 213, and the first flow path 231 of the first end plate 211 ′. Center plate 213 through the second flow path 233a located in the third flow path 233 of the first end plate 211 'via the L-turn flow path 237 inside each flat tube 21). Flow toward the third flow path 233.
The refrigerant flowing through the third channel hole 233 of the center plate 213 flows to the third channel hole 233 of the second end plate 212 'through the fourth channel 233b. The first flow path 231 of the second end plate 212 'is passed through the L-turn flow passage 237 inside each of the flat tubes 21 between the center plate 213 and the second end plate 212'. Flows to the third flow path 231b located at
The refrigerant flowing into the third flow path 231b passes through the fifth flow path 232a located in the second flow path hole 232 of the second end plate 212 ', and thus, the second flow path of the first end plate 211'. It is discharged from the evaporator 2 through the refrigerant discharge pipe connected to the flow path hole 232.

delete

Therefore, since the refrigerant flowing inside the evaporator 2 flows while turning L, and is finally discharged through the entire evaporator 2 through the fifth channel 232a passing through the second channel holes 232, heat exchange efficiency. This improves the cooling performance.

On the other hand, the plates 33 forming each flat tube 31 of the heater core 3 are made substantially rectangular, and each plate 23 of the heater core 3 corresponds to each plate 23 of the evaporator 2 corresponding thereto. It is connected to each plate 23 of the evaporator 2 in the state of being inserted in the L-shaped space of. That is, a flange 343 for brazing the two plates 33 and 33 is formed at the edge of the plate 33 of the heater core 3, and the flange 343 of the plate 33 of the heater core 3 is formed. At the portion corresponding to the plate 23 of the evaporator 2, a plurality of connecting protrusions 345 corresponding to the connecting protrusions 245 of the evaporator plate 23 are formed at predetermined intervals. Therefore, the connection protrusion 245 of the evaporator plate 23 and the connection protrusion 345 of the heater core plate 33 are joined to each other so that the evaporator plate 23 and the heater core plate 33 may be connected to each other. Since the evaporator plate 23 and the heater core plate 33 are connected to each other, notches 247 may be formed between the evaporator 2 and the heater core 3 to prevent mutual transfer. The size and spacing of the connecting protrusions 245 and 345 may be set to minimize the heat transfer rate by experiment.

The lower end of the heater core plate 33 is connected to a fourth flow path 334 connected to a cooling water inlet pipe (not shown) for circulating a heating medium, that is, an engine cold water, and a cooling water discharge pipe (not shown). Five euro holes 335 are formed. The partition ribs 336 are formed between the two flow path holes 334 and 335 to a predetermined height at the upper end, thereby forming a U-turn flow path 337 as a whole, and the U-turn flow path 337 includes the two flow path holes 334 and 335. It is preferable to communicate with each other. In addition, a plurality of embossing beads 339 are formed in a predetermined arrangement on the inner surface of the heater core plate 33, and the embossing beads 339 may be formed in various shapes such as circular, elliptical, or square, and such various types of embossing Beads 339 may be formed to be mixed with each other. In addition, diagonal edge-type beads may be formed at both edges of the upper end of the heater core plate 33 so that the coolant may flow smoothly without biasing to one side.

Accordingly, when the refrigerant of the third end flat tube 31 at one end of the heater core 3 flows from the engine through the fourth flow hole 334 through the cooling water inlet pipe, the refrigerant flows through the U-turn flow path 337. The fourth end of the other end of the heater core 3 through the fourth flow holes 334 corresponding to each other while the U flow flows toward the fifth flow hole 335 of the three-end flat tube 31. The coolant flows toward the fourth flow hole 334 of the flat tube 31 and flows back to the fourth flow hole 334 of each flat tube 31 between the third end flat tube 31 and the fourth end flat tube 31. The U flow flows through the U-turn flow paths 337 toward the fifth flow path hole 335. As such, the refrigerant flowing toward the fifth flow path 335 of each flat tube 31 between the third end flat tube 31 and the fourth end flat tube 31 is again flowed into the fifth flow path of the third end flat tube 31. Flow toward the ball 335 may be finally discharged through the coolant discharge pipe and returned to the engine.

Next, the operation of the integrated heat exchanger of the present invention will be described in detail.

The integrated heat exchanger according to the present invention is embedded in the air conditioning case 5 constituting the air conditioner as shown in FIG. 3, and the evaporator 2 is embedded to face the blower 6. The evaporator 2 embedded in the air conditioning case 5 is connected to the cooling system through the refrigerant inlet pipe and the refrigerant discharge pipe, and the heater core 3 is connected to the engine side cooling water line through the cooling water inlet pipe and the cooling water discharge pipe. . Since the evaporator plate 23 is longer than the heater core plate 33, the evaporator 2 has a portion which does not overlap with the heater core 3, which corresponds to the bent portion of the evaporator plate 23. When the first temperature regulating door 51 and the second temperature regulating door 52 are sequentially installed in the air conditioning case 5 in correspondence with the front and rear of the portion of the evaporator 2 in which the heater core 3 does not overlap, When the temperature control doors 51 and 52 are closed, the air blown by the blower 6 is cooled by heat exchange with the refrigerant flowing through the evaporator 2, and the cooled air is heated by the heater core 3 while the heater is in operation. When passing through the heat exchange with the hot water flowing through the heater core (3). The heat exchanged cold or warm air is discharged into the interior of the cabin through the upper vent 53, the lower vent 54, and the upper defrost vent 55 of the air conditioner case 5, thereby cooling or heating the interior of the interior of the cabin. That is, the air blown by the blower 6 passes only the portion overlapping with the heater core 3 of the evaporator 2 and the heater core 3 but does not pass through the portion not overlapping with the heater core 3 of the evaporator 2. Do not.

On the other hand, in the state in which the two temperature control doors 51 and 52 are in the mode-opened state, part of the air blown from the blower 6 (that is, the two temperature control doors 51 and 52 side) is the heater core of the evaporator 2 ( 3) is cooled to low temperature while not overlapping with the part 3 and is discharged into the vehicle interior through the upper vent 53 of the air conditioning case 5, and the remaining part of the air blown from the blower 6 is evaporator 2 After being cooled through the overlapping portion of the heater core 3, the heat exchanger passes through the heater core 3, and is discharged through the lower vent 54 of the air conditioner case 5 toward the lower half of the passenger in the cabin. Therefore, in this case, the air discharged through only the evaporator 2 without being heated by the heater core 3 is a low temperature, and the air passing through both the evaporator 2 and the heater core 3 is higher than the air above, so the temperature difference It becomes bigger and becomes bi-lebel state, and can make a room comfortable. The heat conduction phenomenon between the evaporator 2 and the heater core 3 can be prevented to a minimum by the notches 247 provided between the evaporator 2 and the heater core 3.

Meanwhile, in the integrated heat exchanger according to the present invention, the refrigerant flow path flowing into the evaporator 2 through the expansion valve (not shown) and discharged to the compressor (not shown) is performed as follows.

That is, when the refrigerant flows into the first end flat tube 21 of the evaporator 2 through the first flow path 231 of the first end plate 211 ′, the introduced refrigerant is introduced into each plate 23. The first flow path 231a formed by the first flow path 231a flows to the blank plate 213 in the center, and the L-turn flow path 237 inside each flat tube 21 flows L-turn. In order to flow toward the second channel 233a formed by the third channel hole 233 of each plate 23. In this way, the refrigerant flowing from the first end plate 211 ′ to the second flow path 233a from the blank plate 213 again passes through the third flow hole 233 from the blank plate 213 to the second end plate ( 2 L 'flows toward the fourth flow path 233b formed by the third flow path 233 between the two flow paths 233b, and each L-turn flow path 237 of the plates 23 flows L-turns to the blank plate 213. ) Flows toward the third flow path 231b formed by each of the first flow path holes 231 between the second end plates 212 '. The refrigerant flowing in this way includes a third flow path 231b formed at a position of the closed first flow path 231 of the second end plate 212 ', and a blocked second flow hole of the second end plate 212'. It is formed at the position 232 and flows through the fifth channel 232a connected to the third channel 231b. Subsequently, it is discharged from the evaporator 2 through a refrigerant discharge pipe connected to the second flow path 232 of the first end plate 211 ′ and supplied to the compressor. Therefore, since the refrigerant flowing in the evaporator 2 is finally discharged through the entire evaporator 2 through two second flow holes 232 and then flows into the compressor, the heat exchange efficiency is improved as well as the compressor. Liquid refrigerant flow can be prevented.

In the integrated heat exchanger of the present invention configured as described above, the evaporator 2 is formed by the first flow path 231, the second flow path 232, and the third flow path 233 formed in the evaporator plate 23. Heat exchange efficiency is improved because the refrigerant flowing through the inside of the evaporator 2 when the refrigerant flows through two L-turns is finally discharged, thereby improving heat exchange efficiency, and thus the low temperature discharged through the evaporator 2 only. The temperature difference between the air and the hot air passing through both the evaporator 2 and the heater core 3 becomes larger than before, so that a bi-lebel state can be effectively obtained, thereby making the room comfortable. In addition, since the heat exchange efficiency of the evaporator 2 is improved, not only the compaction of the air conditioner is possible but also the liquid refrigerant inflow into the compressor is prevented, thereby protecting the compressor.

Claims (1)

An evaporator 2 through which a cooling medium formed by stacking a plurality of flat tubes 21 in which two L-shaped plates are laminated in sequence and a heating medium installed in the L-shaped space part to form a generally rectangular planar shape are provided. A heater core 3 which is circulated, heat transfer fins 4 shared between the evaporator 2 and each flat tube of the heater core 3, and between the evaporator 2 and the heater core 3. In an integrated heat exchanger provided with a notch to block heat transfer to the The first euro hole 231, the second euro hole 232, and the third euro hole 233 are sequentially formed at the lower end of each plate so that each plate 23 constituting the evaporator 2 passes in turn. The partition bead is formed from the central second flow hole 232 to a part of the bent portion of the upper end, whereby an L-turn flow path 237 is formed on the inner surface of each plate 23, and the first flow hole 231 is blocked. It is partitioned into the first half portion 211 and the second half portion 212 by the central plate 213, The first end plate 211 ′ at the end of the first half 211 is blocked by a third flow path 233, and the second end plate 212 ′ at the end of the second half 212 is formed at all flow paths 231 and 232. , 233) First and second flow paths 231a and 233a are formed by the first flow path 231 and the third flow path 233 in each plate 23 of the first half 211, and the second half 212 of the second half hole 212 is formed. Third and fourth flow paths 231b and 233b are formed by the first flow path 231 and the third flow path 233 in each plate 23. The refrigerant introduced into the first flow path 231a of the first half portion 211 flows into the second flow path 233a through the L-turn flow path 237, and the flow refrigerant flows through the third flow path of the central plate 213 ( 233 is flowed into the fourth flow path 233b of the second half portion 212, and then flows into the third flow path 231b through the L-turn flow passage 237, and both in the first half portion 211 and the second half portion 212. The integrated heat exchanger is formed by the second passage hole (232) communicated to be discharged through the fifth passage (232a) connected to the third passage (231b) from the second end plate (212 ') side.

Images