KR100639176B1 - Air conditioner with one piece type heat exchanger for vehicle - Google Patents

Abstract

The present invention is an automobile air conditioner having an integrated heat exchanger, by which the integrated heat exchanger is built not only can improve the cooling and heating performance, but also can form a compact and lightweight air conditioner, it is possible to reduce cost and improve productivity It aims at improving air-conditioning performance.

According to the present invention, an air conditioner includes an evaporator (2) formed by a plurality of flat tubes (21) to which two L-shaped plates (23, 23) are joined, and an integral part of the evaporator and a heat transfer fin ( An integral heat exchanger (1) having a heater core (3) sharing 4) is built in the air path of the air conditioning case (5) such that the evaporator faces the blower (8); The air conditioning case has two temperature regulating doors 51 and 52 which are installed before and after the bent portion of the evaporator which does not overlap with the heater core; The air conditioning case has a drain hole 56 installed at a lower position of the integrated heat exchanger; The air conditioning case is characterized by having a lower vent door 54, an upper vent door 53, and a defrost vent door 55 along the circumference of the mixing chamber 57 on the air discharge side of the integrated heat exchanger.

Air Conditioning Unit, Integrated Heat Exchanger

Description

Automotive air conditioner with integrated heat exchanger {AIR CONDITIONER WITH ONE PIECE TYPE HEAT EXCHANGER FOR VEHICLE}

1 is a front view of main parts of an integrated heat exchanger constituting the air conditioner according to the present invention.

Figure 2a is a perspective view showing the operating state of the integrated heat exchanger constituting the air conditioner 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 shown by the central plate of the evaporator It is a perspective view which shows the partitioned latter part.

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

4 is a configuration diagram of a cooling cycle and a heating cycle by the air conditioner according to the present invention.

5 is a configuration diagram showing the action of the cooling water control valve constituting the air conditioner according to the present invention.

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

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

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

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

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

1: integral heat exchanger, 2: evaporator,

3: heater core, 4: heating fin,

5: air conditioning case, 21: flat tube of evaporator,

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

33: heater core plate, 51, 52: temperature control door,

53, 54, 55: vent door, 56: drain hole,

57: mixing chamber, 61: cooling water supply line,

62: coolant discharge line, 63: coolant control valve,

631: valve case, 633: valve plate,

231, 232, 233: euro ball, 235: block beads,

237: L turn euro, 245: connecting projection,

247: notch

The present invention relates to an air conditioner having an integrated heat exchanger, and in particular, an integral heat exchanger having an integrated evaporator and a heater core can be incorporated to improve cooling and heating performance, and to configure a compact and lightweight air conditioner. The present invention relates to an integrated heat exchanger capable of reducing cost and improving productivity and improving cooling and heating performance.

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 the 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 and an air conditioner in which the evaporator and the heater core are integrated have been proposed, which is disclosed in Japanese Patent Laid-Open No. 9-39553.

The heat exchanger, as shown in Figs. 6 to 9, is formed in an L shape, the first heat exchanger 101 through which the cooling medium flows, and is formed in the space of the L-shape to form a generally planar quadrangular shape. And a second heat exchanger 111 through which the heating medium flows, and heat transfer fins 121 shared by the first heat exchanger 101 and the second heat exchanger 111. A notch part (not shown) is installed to block heat transfer between the two heat exchangers 101 and 111, 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. The heat exchanger is installed in an air path through which air in the air conditioning case 131 flows, so that the first heat exchanger 101 is used as an evaporator of a cooling cycle, and the second heat exchanger 111 circulates engine coolant. Installed in and used as a heater core. In such an air conditioner, a door 133 is provided on the discharge side of the air of the first heat exchanger 101 to control the air passing through the first heat exchanger 101, and the second heat exchanger 111 is provided. ), A flow rate control valve 113 for controlling the amount of hot water flowing in the second heat exchanger 111 is provided.

Therefore, in the air conditioner configured as described above, when the first heat exchanger 101 serving as the evaporator is connected to the cooling system and the second heat exchanger 111 serving as the heater core is connected to the heating system, the door The air blown by the blower 135 in the closed state 133 is heat-exchanged with the refrigerant flowing through the first heat exchanger 101 and cooled, and the cooled air passes through the second heat exchanger 111. When the heat exchanged with the hot water flowing through the second heat exchanger 111 is heated to the cold air through the upper vent 137 of the air conditioning case 131, and the warm air to the lower vent 139 of the air conditioning case 131 Through the discharge to the upper body of the passenger in the interior of the cabin is cooled or heated. In addition, when the door 133 is opened, a part of the air cooled by the first heat exchanger 101 (that is, the air discharged toward the door 133 through the first heat exchanger 101) is intact. 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 and an air conditioner using the same, a notch portion is formed between the first heat exchanger 101 and the second heat exchanger 111 to minimize heat transfer between them. Even if the heat transfer phenomenon between the first heat exchanger 101 and the second heat exchanger 111 cannot be completely prevented, and the cooling medium flowed into the first heat exchanger 101, the flow path is L-turn. Since the first heat exchanger 101 is discharged from the first heat exchanger 101 as it is, the heat exchange efficiency is poor. Therefore, the air, the first heat exchanger 101, and the second heat exchanger 111 that have passed through only a part of the first heat exchanger 101 are separated. The difference with rough air 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. Furthermore, in the conventional air conditioner, the door 133 for controlling the air that has passed through the first heat exchanger 101 is installed at the rear of the first heat exchanger 101 in the air discharge direction. Even when the air is closed, the air flows through the first heat exchanger 101 toward the second heat exchanger 111, so that temperature control cannot be effectively performed.

The present invention has been made in view of the conventional problems as described above, by integrating an integrated heat exchanger consisting of an evaporator and a heater core as well as to improve the heating and cooling performance as well as to form a compact and lightweight air conditioner, It aims to provide an air conditioner that can reduce costs, improve productivity, and improve cooling and heating performance.

In order to achieve the above object, the present invention, the evaporator is passed through the cooling medium formed by stacking a plurality of flat tubes are bonded to the two L-shaped plate, the L-shaped space is provided integrally with the evaporator A heat exchanger comprising a heater core in which a coolant flows, and a heat transfer fin shared between the evaporator and each flat tube of the heater core, which are generally rectangular in planar shape, the heat exchanger having the evaporator directed toward the blower. A first temperature regulating door and a second temperature regulating door for controlling the inflow air and the discharge air before and after the bent portion of the evaporator, the air conditioning case being embedded in the air path of the air conditioning case; A drain hole in the lower portion of the integrated heat exchanger; It is also characterized by having a lower vent door, an upper vent door and an upper defrost vent door along the circumference of the mixing chamber on the air discharge side of the integrated heat exchanger.

According to the present invention, 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 the bent portion of the upper end from the second euro hole in the center. By forming a partial bead up to a part, an L-turn flow path is formed on the inner surface of each plate, and is divided into the first half and the second half by a central plate in which the first flow path is blocked, and the first end plate at the end of the first flow path has a third flow hole. The second end plate of the second half end is blocked, and all the flow path holes are blocked, so that the first and second flow paths are formed by the first and third flow holes in each plate of the first half, and each plate of the second half plate. The third and fourth flow paths are formed by the first flow path and the third flow path in the first flow path, and the refrigerant introduced into the first flow path in the first half flows into the second flow path through the L-turn flow path. Flows, and this flow refrigerant flows through the third flow path of the central plate to the fourth flow path in the second half, and then flows through the L-turn flow path to the third flow path, and the second flow hole communicates in both the first and second parts. It is formed by the second end plate characterized in that the discharge through the fifth channel connected to the third channel.

According to the present invention, a cooling water control valve is installed over the cooling water supply line and the cooling water discharge line of the heater core, and the cooling water control valve includes: a valve case having a flow passage communicating with the cooling water supply line and the cooling water discharge line; It is rotatably installed in the flow path has a valve plate for controlling or blocking the supply and discharge of the cooling water in accordance with the amount of rotation.

According to the air conditioner of the present invention configured as described above, the evaporator is connected to the cooling system and the heater core is connected to the heating system.

In the heating mode, both thermostat doors are closed, so that the air blown through the blower is discharged to the mixing chamber through the heater core and the evaporator portion overlapping the heater core. On the other hand, the engine coolant is distributed to the inside of the heater core through the coolant supply line, so that the air discharged to the coolant and the mixing chamber is heat-exchanged and changed to a high temperature, thereby supplying warm air to the room. Temperature control can be performed by adjusting the rotation amount of a valve plate by operation of the temperature control switch of a control unit.

In the cooling mode, both temperature control doors are opened. Therefore, the air blown through the blower is discharged to the mixing chamber via the entire area of the evaporator and the heater core. In this way, the air discharged into the mixing chamber is exchanged with the refrigerant flowing in the evaporator to be converted to low temperature so that cold air is supplied to the room. In this cooling mode, the flow path of the coolant supply line and the coolant discharge line is blocked by the valve plate, and the coolant supplied from the engine is bypassed from the coolant control valve to the engine so that no coolant flows to the heater core.

On the other hand, in the mixing mode, the two temperature control doors are opened at an appropriate angle for temperature control, and the flow path of the coolant control valve is also appropriately adjusted. In this state, the air blown from the blower passes through the appropriate area of the curved upper end of the evaporator and the entire lower part thereof according to the opening angle of the two temperature control doors, and the air passing through the evaporator area overlapped with the heater core is discharged through the heater core to the mixing chamber do. Therefore, low temperature air is discharged into the upper region of the mixing chamber, and air of an appropriate temperature higher than the air is discharged into the lower region of the mixing chamber and mixed through the vent door after mixing in the mixing chamber. In particular, since the upper part of the room is supplied with low-temperature air and the lower part of the room is supplied with air having a higher temperature than the air, a temperature difference occurs to form a bi-lebel, thereby making the room comfortable.

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 Fig. 2, reference numeral 1 denotes an evaporator 2 having an L shape as an integrated heat exchanger constituting the air conditioner according to the present invention, and an evaporator in the space of the L shape. It comprises the heater core 3 of the substantially rectangular parallelepiped shape integrally connected with (2), and has the substantially square planar shape as a whole.

The evaporator 2 is formed by stacking a plurality of flat tubes 21 which are formed by joining two L-shaped plates 23 and 23 to each other, and the heater core 3 is formed by two plates having a substantially rectangular shape ( A plurality of flat tubes 31 formed by joining 33 and 33 are laminated one by one. 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 2 of the evaporator 2 is inverted as shown in the drawing, the 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 the ball 233. In addition, the partition bead 235 is formed in an inverted L shape from the upper end of the second passage hole 232 to a portion of the upper bent portion, and the curved portion of the compartment bead 235 is curved in consideration of the fluidity of the refrigerant. Do.

The L-turn flow path 237 is formed on the plate 23 by the partition bead 235, and the L-turn flow path 237, the first flow path 231, and the third flow path 233 communicate with each other. It is preferable that the L-turn flow passage 237 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, and square, and the embossing beads 239 of various shapes may be formed to be mixed.

In addition, it is preferable that a slotted bead 241 in an oblique direction is formed at an inner edge portion of the plate 23 so that the flow of the coolant is guided well along the L-turn flow path 237 without biasing to one side. In addition, a flange 243 for brazing the two plates 23 and 23 is formed along the edge of each plate 23, and a portion of the flange 243 connected to the heater core 3 at predetermined intervals. As will be described later as a plurality of connecting protrusions 245 are formed, notches 247 are formed between the connecting protrusions 245 in order to minimize the transfer 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.
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.

delete

delete

On the other hand, as shown in FIGS. 1 and 2, the plates 33 forming each flat tube 31 of the heater core 3 are substantially rectangular, and each plate 33 of the heater core 3 is formed. Is connected to each plate 23 of the evaporator 2 in the state of being inserted into the L-shaped space of each plate 23 of the evaporator 2 corresponding thereto. 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 evaporator in the flange 343 of the heater core plate 33 is formed. In the portion corresponding to the plate 23, 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 has a fourth flow path 334 connected to a coolant inlet line 61 for circulating coolant, that is, an engine coolant, and a fifth connected to the coolant discharge line 62. The flow path hole 335 is 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 may be formed in various shapes such as circular, elliptical, or square, and such various types of embossing beads 339. ) May be mixed with each other. In addition, although not shown, diagonal slot-shaped 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, the refrigerant of the third end flat tube 31 at one end of the heater core 3 from the engine 7 (see FIG. 4) through the coolant inflow line 61, and through the fourth flow path 334. When the refrigerant flows through the U-turn flow passage 337 toward the fifth flow hole 335 of the third end flat tube 31, the refrigerant flows through the U-turn and the fourth flow holes 334 corresponding to each other. Refrigerant flows toward the fourth flow path 334 of the fourth end flat tube 31 at the other end of 3), and then each flat tube between the third end flat tube 31 and the fourth end flat tube 31 again. The U-flow flows through the U-turn flow paths 337 from the fourth flow path 334 of the 31 direction 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 transferred to the third end flat tube 31. Flow toward the fifth flow path 335 is finally discharged through the coolant discharge line 62 and returned to the engine (7).

On the other hand, as shown in Figure 3, reference numeral 5 is an air conditioning case constituting the air conditioner according to the present invention, the inlet side is connected to the blower 8, the air is blown into the internal air path by the blower (8) Can be. The air conditioning case 5 includes the integrated heat exchanger 1 so that the evaporator 2 faces the blower 8, so that the air blown by the blower passes through the integrated heat exchanger 1. It heat-exchanges and is discharged to the rear side of the integrated heat exchanger 1.

According to the present invention, in order to effectively control the temperature of the air by heat exchange, the air conditioning case (5) is the first temperature door installed before and after the upper bent portion of the evaporator (3) that does not overlap with the heater core (3) And a second temperature regulating door 52. That is, the temperature control doors (51, 52) is the upper end is rotatably coupled to the air conditioning case (5) to adjust the opening angle to the upper bent portion of the evaporator (2). In addition, the lower part of the integrated heat exchanger 1 and the corresponding air conditioner case 5 are recessed downward, and the drain hole 56 is provided in the lowest end of this recessed part. Therefore, the water that flows down on the surface of the evaporator 2 may be discharged to the outside through the drain hole 56.

The inner space of the air conditioner case 5 located at the rear side of the integrated heat exchanger 1 through which the heat-exchanged air is discharged serves as the mixing chamber 57. A bottom vent door 54 for supplying heat-exchanged air toward the lower body of the passenger is rotatably installed at the bottom of the outer wall of the air conditioning case 5 forming the mixing chamber 57. In addition, the upper end portion of the outer wall forming the mixing chamber 57 is formed to be inclined, and the inclined portion is rotatably provided with an upper vent door 53 for supplying heat-exchanged air toward the upper body of the passenger. In addition, a defrost vent door 55 is rotatably provided at a portion of the outer wall forming the mixing chamber 57 to form a ceiling.

On the other hand, as shown in Fig. 4 and 5, by connecting the engine 7 and the heater core 3, the cooling water supply line 61 for supplying the engine coolant to the heater core 3, and the heater core 3 The coolant control valve 63 is installed over the coolant discharge line 62 for returning the engine coolant to the engine 7. The coolant control valve 63 rotates in a valve case 631 having a flow path 632 communicating with the coolant supply line 61 and the coolant discharge line 62, and a flow path 632 of the valve case 631. It is possible to have a valve plate 633 installed to adjust the degree of opening of the flow path 632 of the cooling water supply line 61 and the cooling water discharge line 62 according to the amount of rotation. That is, when the valve plate 633 is rotated to a position that blocks the flow path of the coolant supply line 61 and the coolant discharge line 62, the coolant discharged from the engine 7 is the coolant supply line 61, the valve case. By passing through the flow path 632 and the coolant discharge line 62 of the 631 to the engine 7, the coolant is not supplied to the heater core 3, and the valve plate 633 is provided with the coolant supply line 61 and When rotating to a position where the flow path of the coolant discharge line 62 is not blocked, the coolant discharged from the engine 7 is supplied to the coolant supply line 61, the flow path 632 of the valve case 631, and the coolant supply line 61. ), The heater core 3, the coolant discharge line 62, the flow path 632 of the valve case 631, and the coolant discharge line 62 are sequentially returned to the engine 7. In this case, the amount of coolant flow is determined according to the opening degree of the coolant supply line 61 and the coolant discharge line 62 according to the amount of rotation of the valve plate 633, and the amount of rotation of the valve plate 633 is the instrument panel of the vehicle interior. It can be adjusted by a control unit (not shown) installed in.

Next, the operation of the air conditioner of the present invention will be described in detail.

In the integrated heat exchanger 1 embedded in the air conditioning case 5, the evaporator 2 constitutes a cooling cycle and faces the blower 8, and the heater core 3 constitutes a heating cycle and the engine 7 Is connected to the side.

According to the present invention, in the heating mode, the first bent temperature control door 51 and the second temperature control door 52 of the air conditioning case 5 are pivoted so that the upper bent part of the evaporator 2 does not overlap with the heater core 3. By being in close contact with the front and rear, the front and rear portions of the upper bent portion of the evaporator 2 are blocked off from the air passage 8 side of the air conditioner 5 and the mixing chamber 57. Therefore, the air blown through the blower 8 is discharged to the mixing chamber 57 through the evaporator portion 2 and the heater core 3 which overlap with the heater core 3 in sequence without passing through the upper bent portion of the evaporator 2. . Meanwhile, in the heating mode, the operation of the cooling cycle is stopped and the engine coolant is supplied into the heater core 3 through the coolant supply line 61. Thus, the coolant flows into the heater core 3 so that the heater core 3 is heated. In the process of passing through the interior, the coolant and the air passing through the heater core 3 exchange heat with each other. The heat-exchanged coolant returns to the engine 7 in a state where the temperature is lowered to cool the engine 7 again, and the heat-exchanged air is discharged to the mixing chamber 57 in a state where the temperature is increased to vent valves 53, 54, and 55. It is supplied to the room through). The temperature control of the air can be achieved by adjusting the amount of rotation of the valve plate 633 incorporated in the coolant control valve 63 by the operation of the control unit in the vehicle interior. That is, when the valve plate 633 is rotated in parallel with them between the cooling water supply line 61 and the cooling water discharge line 62, the cooling water supply amount to the heater core 3 is maximized and the temperature of the heat-exchanged air is increased. The highest. When the valve plate 633 is obliquely rotated between the coolant supply line 61 and the coolant discharge line 62, the valve plate 633 blocks the flow path between the coolant supply line 61 and the coolant discharge line 62. Since the amount of cooling water supplied to the heater core 3 is smaller than that of the case, the temperature of the heat-exchanged air is low. The temperature of the air at this time is increased or decreased by the difference in the amount of cooling water flow to the heater core 3 according to the opening degree of the flow path of the lines (61, 62).

On the other hand, in the cooling mode, the two temperature regulating doors 51 and 52 of the air conditioner case 5 are opened. Therefore, the air blown through the blower 8 also passes through the two temperature control doors 51 and 52 side areas of the evaporator 2, so that the mixing chamber 57 passes through the entire area of the evaporator 2 and the heater core 3. To be discharged. As such, the air discharged through the entire area of the evaporator 2 to the mixing chamber 57 is exchanged with the refrigerant flowing in the evaporator 2 to be converted to a low temperature and discharged to the mixing chamber 57 so that the upper vent door 53 may be discharged. The cold air is supplied to the room through the lower vent door 54 and the defrost vent door 55. In this cooling mode, the flow paths of the coolant supply line 61 and the coolant discharge line 62 are blocked by the valve plate 633 so that the coolant supplied from the engine 7 moves from the coolant control valve 63 to the engine 7. By-pass, no coolant flows to the heater core 3, and the temperature of the cold wind can be determined by the opening degree of the vent doors 53, 54, 55.

On the other hand, in the mixing mode, the two temperature regulating doors 51 and 52 are opened at appropriate angles for temperature control, and the cooling water supply line 61 and the cooling water according to the rotation of the valve plate 633 of the cooling water regulating valve 63. The opening degree of the discharge line 62 is also adjusted appropriately. That is, in this state, the air blown from the blower 8 is heat-exchanged through the appropriate area of the curved upper end part of the evaporator 2 according to the opening angle of the two temperature control doors 51 and 52. And the air passing through the area | region of the evaporator 2 which overlapped with the heater core 3 is discharged to the mixing chamber 57 via the heater core 3 also. Accordingly, low temperature air is discharged to the upper region of the mixing chamber 57, and air of a higher temperature than the air is discharged to the lower region of the mixing chamber 57 and mixed in the mixing chamber 57. Through 53,54,55. Although low temperature air and hot air having a higher temperature are mixed in the mixing chamber 57, the low temperature air is discharged to the upper region of the mixing chamber 57 close to the upper vent door 53, and the high temperature air is lowered. Since it is discharged to the lower area of the mixing chamber near the vent door 54, relatively low-temperature air is supplied to the upper part of the room, and air having a higher temperature than the air is supplied to the lower part of the room. It achieves a bi-lebel, so convection can be effectively induced to make the room comfortable.

Meanwhile, in the integrated heat exchanger 1 applied to the air conditioner according to the present invention, the refrigerant flow path flowing into the evaporator 2 through the expansion valve 91 and discharged to the compressor 92 is performed as follows.

That is, when the refrigerant flows from the expansion valve 91 to 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 The L flow path flows through the first flow path 231a formed by the first flow path 231 of each plate 23 to the blank plate 213 in the center, and at the same time, the L-turn flow path inside the flat tube 21 ( 237 flows L turns to flow toward the second flow path 233a formed by the third flow 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, the refrigerant is discharged from the evaporator 2 through the refrigerant discharge pipe connected to the second flow path 232 of the first end plate 211 ′ and supplied to the compressor 92. Therefore, since the refrigerant flowing in the evaporator 2 is discharged through the entire evaporator 2 through the second flow holes 232 after the second L-turn flow, not only the heat exchange efficiency is improved but also the compressor ( 92 can be prevented.

In the automotive air conditioner having the integrated heat exchanger of the present invention configured as described above, the first temperature control door 51 and the second temperature control before and after the region of the evaporator 2 which does not overlap with the heater core 3. Since the door 52 is installed, not only can the heat transfer between the evaporator 2 and the heater core 3 be minimized, but also the temperature control can be finely adjusted, thereby improving cooling and heating performance. Furthermore, two L-turn flows of the refrigerant flowing inside the evaporator 2 by the first flow path 231, the second flow path 232, and the third flow paths 233 formed in the evaporator plate 23. Since the heat exchange efficiency is improved, the temperature difference between the low temperature air discharged only through the evaporator 2 and the high temperature air passing through both the evaporator 2 and the heater core 3 increases. The bi-lebel state can be obtained effectively, making the room comfortable. In addition, the compaction of the air conditioner according to the compactness of the heat exchanger, productivity and cost reduction can be achieved, and the heat exchange efficiency of the evaporator is improved to prevent the introduction of liquid refrigerant into the compressor 92, thereby preventing the compressor 92. Can protect.

Claims (3)

An evaporator 2 through which a cooling medium formed by stacking a plurality of flat tubes 21 joined together with two L-shaped plates 23 and 23 is sequentially stacked, and integrated with the evaporator 2 in the space of the L-shape. Heated fins (4) shared between the heater core (3) through which the coolant flows, and the flat fins (21) of the evaporator (2) and the heater core (3), which are installed to form a rectangular planar shape as a whole. In the heat exchanger provided with, The integrated heat exchanger is embedded in the air path of the air conditioning case 5 so that the evaporator 2 faces the blower 8, The air conditioning case 5 includes a first temperature regulating door 51 and a second temperature regulating door 52 for controlling inlet and outlet air before and after the bent portion of the evaporator 2 which does not overlap with the heater core 3. Has; In addition, the air conditioning case (5) has a drain hole 56 which is installed in the lower position of the integral heat exchanger; The air conditioning case 5 also has a lower vent door 54, an upper vent door 53, and an upper defrost vent door 53 along the circumference of the mixing chamber 57 on the air discharge side of the integrated heat exchanger. Automotive air conditioner having an integrated heat exchanger, characterized in that. The method of claim 1, 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. It is formed by the second passage hole 232 communicated with the integrated heat exchanger, characterized in that the discharge through the fifth passage 232a connected to the third passage 231b from the second end plate 212 'side Automotive air conditioner. The method of claim 1, Cooling water control valve 63 is installed across the cooling water supply line 61 and the cooling water discharge line 62 of the heater core (3), The coolant control valve 63 is a valve case 631 having a flow path 632 communicating with the coolant supply line 61 and the coolant discharge line 62, and rotatably installed in the flow path 632. The air conditioner for automobiles with an integrated heat exchanger, characterized in that it comprises a valve plate (633) for controlling or blocking the supply and discharge of the cooling water.

Images