JP2001130235A - Air conditioner for automobile - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide 'an air conditioner for an automobile' capable of realizing a compact and reducing a ventilation resistance in a bypass passage. SOLUTION: An air passage 51 of an evaporator 2 is formed such that an air flows in perpendicular to an air flowing-in surface 2a and an air flowing-out surface 2b. The evaporator 2 is so inclinedly disposed below a unit case 1 that a bypass passage 6 side is positioned below a warm air passage 3 side. By this arrangement, an air flowing in the air passage 51 in the evaporator 2 goes toward the bypass passage 6. A heater core 4 is approximately horizontally disposed above the evaporator 2. An air taking-in port 31 for introducing the air into the unit case 1 is opened such that a warm air passage side is enlarged along an inclination of the evaporator 2.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a so-called integrated type air conditioner for an automobile, in which an evaporator and a heater core are housed vertically in one unit case, and more particularly to a bypass for bypassing a heater core. TECHNICAL FIELD The present invention relates to an air conditioner for a vehicle in which ventilation resistance of a passage is reduced.

[0002]

2. Description of the Related Art In a conventional automobile air conditioner, inside and outside air are selectively taken in by an intake unit, and the air is guided to a cooling unit case (hereinafter simply referred to as a unit case), and an evaporator in the unit case is operated. The air is cooled by passing through, and the cooled air is heated by a heater core, or mixed with the heated air after bypassing the heater core to obtain hot air of a predetermined temperature, and then blown out from various outlets into the vehicle interior. ing. Here, the `` evaporator '' is, as is well known, a low-temperature low-pressure refrigerant whose pressure has been reduced by an expansion valve or the like in a cooling cycle flows through the inside, and cools the air introduced therein by heat exchange with the refrigerant. is there. Further, the "heater core" is one in which high-temperature engine cooling water flows inside, and heats the air introduced therein by heat exchange with the high-temperature engine cooling water.

[0003] Since such an air conditioner for an automobile is installed in a small cabin, there is a space limitation in the overall shape. Therefore, a recent air conditioner has an evaporator and a heater core arranged substantially horizontally to form one unit. There is known a so-called integrated type which is housed in a case so as to be vertically arranged.

Further, a mixed door provided between the evaporator and the heater core for branching the cooling air into the air passing through the heater core and the heater core into the bypass air at a predetermined ratio is supported by a single fulcrum. When the configuration is to rotate around the fulcrum, the space becomes large, so in order to further reduce the space between the evaporator and the heater core and to reduce the space, a flat plate-like door in which the mixing door can slide and move. What has been proposed.

FIG. 8 is a schematic cross-sectional view of an integrated air conditioner for a vehicle having a plate-shaped mix door slidably movable and having an evaporator and a heater core placed substantially horizontally in a unit case.

[0008] In the integrated air conditioner for a vehicle shown in FIG. 8, an evaporator 2 is horizontally arranged below a unit case 1, and a heater core 4 is horizontally arranged above the evaporator 2. A plate-shaped mix door 5 having an arc-shaped cross section is provided between the evaporator 2 and the heater core 4 so as to be slidable in a substantially horizontal direction. The mixed door 5 causes the air (cold air) that has passed through the evaporator 2 to branch at a predetermined ratio into the hot air passage 3 that passes through the heater core 4 and the bypass passage 6 that bypasses the heater core 4. The cool air passing through 6 and the warm air guided from the heater core 4 through the warm air passage 3 and guided by the partition wall 7 are mixed in a mix zone 8 to obtain air at a predetermined temperature.

In the vent mode (cooling mode), cool air is blown from a vent outlet Ov opened and closed by a vent door Dv provided above the unit case 1. In the differential mode (mode for clearing the fogging of windows), air (mainly hot air) flowing from the differential foot opening Odf opened by the vent door Dv into the upper passage 9 formed by the partition wall 7 and the unit case 1 )
Is blown out from a defrost outlet Od which is opened and closed by a differential foot door Ddf. In the case of the foot mode (heating mode), the air (mainly hot air) flowing into the upper passage 9 from the differential foot opening Odf is blown out from the foot outlet Of opened and closed by the differential foot door Ddf.

[0008]

However, in the integrated type air conditioner for an automobile shown in FIG. 8, the air passing through the evaporator 2 toward the mix door 5 in the direction of arrow A0 in the figure at the time of maximum cooling. Flows in the direction of arrow A0 'in the figure as guided by the surface of the mix door 5. Therefore, the flow (wind axis) F0 of the air entering the cool air passage 6 is narrowed. As a result, there is a problem that the wind speed becomes too high, the ventilation resistance in the bypass passage 6 increases, and the increase in the air volume is hindered.

SUMMARY OF THE INVENTION It is an object of the present invention to provide an air conditioner for a vehicle which can reduce the ventilation resistance in a bypass passage while reducing the size.

[0010]

The object of the present invention is achieved by the following means.

(1) A mixing door having an arc-shaped cross section is provided between an evaporator and a heater core disposed in a unit case, and the air passing through the evaporator is slid by moving the mixing door, whereby the mixing door is moved. The hot air passage side passing through the heater core and the bypass passage side bypassing the heater core are branched at a predetermined ratio, and the cool air sent from the bypass passage and the hot air sent from the hot air passage are mixed in a mix zone. In an air conditioner for a vehicle which blows out into a vehicle interior from an outlet provided in a unit case, the evaporator is arranged such that air flowing through an air passage in the evaporator is provided below the unit case to the bypass passage. And the heater core is positioned above the evaporator, It is an automobile air conditioning system, characterized in that earnestly is located.

(2) The air passage of the evaporator is formed so that air flows orthogonally to an air inflow surface and an air outflow surface of the evaporator, and the evaporator has the hot air passage on the bypass passage side. The air conditioner for a vehicle according to (1), wherein the air conditioner is arranged to be inclined so as to be located below the side.

(3) The air passage of the evaporator is formed such that air flows obliquely with respect to an air inflow surface and an air outflow surface of the evaporator, and the evaporator is disposed substantially horizontally. The air conditioner for a vehicle according to the above (1), characterized in that:

(4) The vehicle according to (2) or (3), wherein a louver for flowing air toward the bypass passage is formed in a corrugated fin provided in the air passage of the evaporator. For air conditioners.

(5) The air intake port located below the evaporator and for introducing air into the unit case is opened so that the side of the hot air passage becomes wider along the inclination of the evaporator. An automotive air conditioner according to the above (2), which is characterized by the following.

[0016]

Embodiments of the present invention will be described below with reference to the drawings.

Embodiment 1 FIG. 1 is a schematic sectional view showing an air conditioner for a vehicle according to Embodiment 1 of the present invention, and FIG.
(A) is a diagram showing the evaporator along the arrow B in FIG. 1, FIG. 2 (B) is a perspective view for explaining the arrangement of the corrugated fins of the evaporator, and FIG. It is a schematic perspective view shown as. The members common to the members shown in FIG. 8 are denoted by the same reference numerals.

As shown in FIG. 1, the unit case 1 of the vehicle air conditioner is disposed adjacent to a dash panel 40 that separates an engine room E from a room R.

An evaporator 2 is disposed below the unit case 1. The evaporator 2 is disposed so as to be inclined such that the rear end of the engine room E side is upward and the front end of the indoor room R side is downward. Outside air (outside air) or inside air (inside air) taken in from an intake unit (not shown) is introduced into the unit case 1 from the air intake port 31 below the evaporator 2 toward the near side from the back side of the drawing, and the evaporator 2 is removed. Flows upward through. A refrigerant circulates through the evaporator 2 via a refrigerant pipe 41 provided through the dash panel 40, and the intake air is cooled by exchanging heat between the refrigerant and the intake air. . Evaporator 2
Constitutes a cooling cycle together with a compressor, a condenser, an expansion valve and the like (not shown).

The air intake 31 is open in a substantially trapezoidal shape so that the warm air passage 3 side is widened along the inclination of the evaporator 2. In the illustrated example, the side near the engine room E is wide. Thus, the air intake 31 can be widened without increasing the size of the lower part of the unit case 1, the passage resistance can be reduced, and the flow rate of the introduced air can be easily increased.

A heater core 4 is provided above the evaporator 2.
Are arranged substantially horizontally. High-temperature engine cooling water circulates through the heater core 4 through a heater pipe 42 provided through the dash panel 40, and passes by exchanging heat between the engine cooling water and air. The air is heated.

By arranging the evaporator 2 and the heater core 4 up and down, a compact unit case 1 having a small dimension in the height direction and a dimension in the left-right direction or the front-rear direction is obtained, and the installation space for the unit case 1 in the vehicle interior is greatly increased. , Thereby making it possible to effectively use the surplus space generated in the vehicle interior.

Between the evaporator 2 and the heater core 4, a plate-shaped mix door 5 having a loose arc shape is provided so as to be slidable in a substantially horizontal direction. By sliding the mix door 5 via the slide mechanism M, the air (cool air) passing through the evaporator 2 is
A branch is made at a predetermined ratio between a side of the hot air passage 3 which is heated and flowed through the heater core 4 and a side of the bypass passage 6 which bypasses the heater core 4 (selectively to the side of the hot air passage 3 or the side of the bypass passage 6). Including when flowing). The cool air flowing from the evaporator 2 through the bypass passage 6 and the warm air guided from the heater core 4 through the warm air passage 3 and guided by the partition wall 7 are mixed in the mix zone 8 to be air at a predetermined temperature.

Here, the opening of the mix door 5 is adjusted by sliding in the left-right direction in FIG. 1 in accordance with the temperature set and desired by the occupant.
It stops at an arbitrary position between a full cool position (the position shown in FIG. 1) where the side is fully closed and a full hot position where the bypass passage 6 side is fully closed. Depending on the position of the mix door 5, the ratio of the amount of air flowing to the hot air passage 3 to the amount of air flowing to the bypass passage 6 is adjusted, and the amount of cold air and the amount of hot air mixed in the mix zone 8 are adjusted.

Above the unit case 1, there is provided a vent outlet Ov serving as a cool air outlet from which cool air is discharged, and the vent outlet Ov is selectively opened and closed by a vent door Dv. In the case of the vent mode, the vent door Dv opens the vent outlet Ov, and cool air is blown out from the vent outlet Ov. In the case of the differential-foot mode,
The vent door Dv closes the vent outlet Ov.

When the vent door Dv closes the vent outlet Ov, the air flow flows into the upper passage 9 from the differential foot port Odf. In the upper passage 9, the differential foot opening O
A defrost outlet Od which is opened and closed by a differential foot door Ddf at the upper part on the downstream side of df and mainly blows out hot air.
Is provided. On the downstream side of the defrost outlet Od, a foot outlet Of which is opened and closed by a differential foot door Ddf is provided.

A vent duct 43 is connected to the vent outlet Ov. Through this vent duct 43, conditioned air is blown toward the upper body of an occupant in the passenger compartment. A defrost duct 44 is connected to the defrost outlet Od, and a windshield 45 is connected through the defrost duct 44.
And conditioned air is blown toward the inner surface of the side glass.
On both sides (in the direction perpendicular to the paper) of the foot outlet Of,
A connection port 32 communicating with a foot duct (not shown) is provided. The conditioned air is blown out through the foot duct toward the feet of the occupant in the passenger compartment.

The bottom of the unit case 1 is formed on a slope inclined downward toward the dash panel 40. When the intake air is cooled in the evaporator 2, the water contained in the air is condensed and drops on the bottom of the unit case 1. The condensed water flows along the slope and is discharged to the engine room E from a drain pipe 46 provided through the dash panel 40.

As shown in FIG. 3, the mixing door 5 is provided between the evaporator 2 and the heater core 4.
Has a door body 12 extended in a direction of blocking an airflow from the upstream side that has passed through the door body 12. The door body 12 generally has a flat portion 12a on the outer periphery and a dome-shaped bulging portion 12 inside.
b, and a sealing member 15 made of urethane foam or the like is stuck on the outer surface side. In FIG. 3, the orientation of the mix door is different from the orientation shown in FIG. 1 for convenience of illustration.

The bulging portion 12b has an arcuate cross section and is gently curved concavely toward the upstream side of the air flow.
The concave surface of the bulging portion 12b serves as a guide when guiding the airflow to the heater core 4 and when guiding the airflow to the bypass passage 6. A partial gear 20 (see FIG. 1) is provided on the inner side of the door body 12.
Is formed continuously from end to end. Guide grooves 50a, 50b formed in the side wall of the unit case 1 are provided at four places at the side corners of the door body 12.
A guide pin 18 that is slidably fitted in the inside (see FIG. 1) is formed to protrude.

The slide mechanism M for operating the mix door 5 includes guide grooves 50a and 50b in which the guide pins 18 are slidably fitted, a pair of partial gears 20 meshing with the rack 17, and a pair of partial gears 20. And a driving means for rotationally driving the. As the driving unit, for example, an electric motor, a motor actuator having a reduction gear housed in a casing, or the like is used.

Here, the guide grooves 50a and 50b support the four guide pins 18 so that the door body 12 operates without rattling even if it receives wind pressure. As shown in FIG. 1, the guide grooves 50a and 50b are formed in an arc shape with a predetermined gap therebetween so as to have a radius of curvature substantially equal to the radius of curvature of the rack 17 of the mix door 5. The guide grooves 50a and 50b are formed on the left and right side walls of the unit case 1, respectively. Guide pin 1 in the upper part of FIG.
8 is fitted in the left guide groove 50a in FIG. 1, and the lower guide pin 18 in FIG. 3 is fitted in the right guide groove 50b in FIG.

In the vehicle air conditioner according to the first embodiment, as shown in FIG. 1, the evaporator 2 is provided below the unit case 1 with an air passage 5 in the evaporator 2.
1 is arranged so as to flow toward the bypass passage 6.

More specifically, the evaporator 2 is provided in FIG.
(A) As shown in (B), an air passage 51 between a plurality of flat tubes 52, 52 having a refrigerant passage formed therein.
And a laminated evaporator provided with corrugated fins 53. The corrugated fins 53 extend in a direction perpendicular to the air inflow surface 2a and the air outflow surface 2b.
Thereby, the air passage 51 of the evaporator 2 is formed so that air flows orthogonally to the air inflow surface 2a and the air outflow surface 2b. And evaporator 2
Are arranged at a predetermined angle θ with respect to the horizontal so that the bypass passage 6 is located below the hot air passage 3.

The inclination angle θ of the evaporator 2 can be appropriately changed according to the size of the cross-sectional area of the evaporator 2 and the bypass passage 6, and is preferably, for example, 5 degrees to 45 degrees. As a result, the condensed water flows along the slope of the evaporator 2, and immediately drops from the lower part of the evaporator 2 to the lower part of the unit case 1 and is discharged.

Next, the operation of the present embodiment will be described.

The air from the intake unit is introduced into the unit case 1 from the air intake 31 below the evaporator 2, and is cooled by passing through the evaporator 2. The air intake 31 is connected to the evaporator 2
The opening area changes in accordance with the inclination of. Thereby, a large amount of air is introduced.

The air passing through the evaporator 2 rises,
It reaches mixed door 5. The air that has passed through the evaporator 2 is mixed by the mixing door 5 with the hot air passage 3 and the bypass passage 6.
The air guided to the hot air passage 3 passes through the heater core 4 to become hot air, and the air from the bypass passage 6 flows as cool air, and both are mixed in the mix zone 8 to obtain a desired temperature. Is adjusted to

The temperature-controlled air is blown out from outlets Ov, Od, Of corresponding to the air conditioning mode set by the occupant. The air conditioning mode is set by, for example, operating an air conditioning mode lever provided in the vehicle interior.

Since the present embodiment is effective in the vent mode, FIG.
This will be described with reference to FIG.

In general, in the vent mode, the mix door 5 is often positioned in the maximum cooling state. At the time of maximum cooling, the differential foot opening Odf is provided by the vent door Dv.
Is completely closed, while the vent outlet Ov is opened. The mix door 5 is located at the right end in FIG. 1, and the upstream front surface of the heater core 4 is fully closed.

Thus, the air cooled by passing through the evaporator 2 passes through the bypass passage 6 and enters the vent outlet Ov. Then, the cool air that has passed through the vent outlet Ov is blown out from the vent duct 43 toward the vehicle interior.

In the first embodiment, since the evaporator 2 is disposed at a predetermined angle θ with respect to the horizontal, the air passage 5 near the bypass passage 6 in the evaporator 2 is provided.
1 flows directly down to the bypass passage 6. The air flowing in the air passage 51 near the heater core 4 in the evaporator 2 flows while being guided along the surface of the mix door 5, but flows out from the air outflow surface 2b obliquely to the upper left in the figure. Therefore, the speed component toward the bypass passage 6 is relatively large.

Therefore, the air guided to the end of the mix door 5 flows as indicated by the arrow A ', and the flow F of the air directly entering the bypass passage 6 is not inadvertently narrowed. The flow F of air entering the bypass passage 6 is
As a result, the wind speed does not become too high, and the ventilation resistance in the bypass passage 6 is lower than in the case shown in FIG. Therefore, it is possible to easily achieve a high air volume at the time of maximum cooling, and to reduce the generation of noise.

Further, since the evaporator 2 is inclined, the drainage of the condensed water is improved. Then, in order to increase the air volume of the introduced air, the opening area of the air intake 31 can be increased by opening the air intake 31 in accordance with the inclination of the evaporator 2. Here, since the air intake 31 is widened on the side of the hot air passage 3, the amount of air flowing into the air passage 51 near the heater core 4 in the evaporator 2 tends to increase. However, since the evaporator 2 is inclined, the air that has passed through the evaporator 2 goes to the bypass passage 6, so that it is possible to correct or suppress an increase in the amount of air flowing into the heater core 4. Temperature adjustment becomes easy. By inclining the evaporator 2 in this manner, the ventilation resistance in the bypass passage 6 can be reduced, and the unbalanced air flow due to the shape of the air intake 31 can be corrected.

During the temperature control operation and the maximum heating, the air that has passed through the evaporator 2 flows obliquely into the heater core 4, so that the air flows from the evaporator 2 through the heater core 4 to the hot air passage 3. The resistance will increase slightly. However, since the required air volume during these operations is smaller than during the cooling operation, there is no problem that the air volume required for heating cannot be secured.

<< Modification of First Embodiment >> FIGS. 4A and 4B
FIG. 4 is a perspective view showing a corrugated fin of an evaporator according to a modification of the first embodiment, and a cross-sectional view taken along line BB.

In this modification, the louver 54 is formed on the corrugated fin 53 of the first embodiment.
The louver 54 is cut and raised so that air flows down toward the bypass passage 6.

According to this modification, the air that has flowed into the air passage 51 near the heater core 4 in the evaporator 2 passes through the louver 54 to the air passage 51 near the bypass passage 6 while flowing down in the evaporator 2. It flows down while flowing. Therefore, the amount of air flowing directly toward the bypass passage 6 is increased as compared with the case where the louver 54 is not formed. In addition, since the air flowing through the air passage 51 passes through the louver 54, the velocity component heading toward the bypass passage 6 is increased.
Along with the evaporator 2 being arranged at a predetermined angle θ with respect to the horizontal, the air flowing out of the air outflow surface 2b has a larger velocity component toward the bypass passage 6, and There is no longer any need to narrow the flow F of air that enters directly. As a result, the bypass passage 6
, The airflow resistance at the time of maximum cooling can be easily increased, and the generation of noise can be reduced.

Embodiment 2 FIG. 5 is a schematic sectional view showing an automotive air conditioner according to Embodiment 2 of the present invention, and FIG.
FIG. 9 is a perspective view for explaining an arrangement state of corrugated fins of the evaporator according to the second embodiment.

As in the first embodiment, the evaporator 2 of the second embodiment is arranged such that the air flowing through the air passage 55 in the evaporator 2 is provided below the unit case 1.
It is arranged to face.

However, unlike the first embodiment, the corrugated fins 56 extend in a direction inclined with respect to the air inflow surface 2a and the air outflow surface 2b. Thus, the air passage 55 of the evaporator 2 is formed such that air flows obliquely with respect to the air inflow surface 2a and the air outflow surface 2b. The evaporator 2 is disposed substantially horizontally.

Also in the second embodiment, the air flowing through the air passage 55 near the bypass passage 6 in the evaporator 2 directly flows down to the bypass passage 6. Further, the air flowing through the air passage 55 near the heater core 4 in the evaporator 2 has a relatively large velocity component toward the bypass passage 6 due to the inclination of the fins 56, and the flow F of the air directly entering the bypass passage 6 is inadvertently increased. There is no narrowing. As a result, the ventilation resistance in the bypass passage 6 is reduced, so that it is possible to easily achieve a high air volume at the time of maximum cooling, and to reduce the generation of noise.

<< Modification of Embodiment 2 >> FIGS. 7A and 7B
FIG. 9 is a perspective view showing a corrugated fin of an evaporator according to a modification of the second embodiment, and a cross-sectional view taken along line BB.

In this modification, the louver 57 is formed on the corrugated fin 56 of the second embodiment.
The louver 57 is cut and raised so that air flows down toward the bypass passage 6.

According to this modified example, the air that has flowed into the air passage 55 near the heater core 4 in the evaporator 2 passes through the louver 57 to the air passage 55 near the bypass passage 6 while flowing down in the evaporator 2. It flows down while flowing. Therefore, the amount of air flowing directly toward the bypass passage 6 is increased as compared with the case where the louver 57 is not formed. In addition, since the air flowing through the air passage 55 passes through the louver 57, the velocity component heading toward the bypass passage 6 is increased.
Combined with the corrugated fins 53 extending in the direction inclined with respect to the air inflow surface 2a and the air outflow surface 2b, the air flowing out of the air outflow surface 2b causes the velocity component traveling toward the bypass passage 6 to pass. Is further increased, and the flow F of the air that directly enters the bypass passage 6 is further reduced. As a result, the ventilation resistance in the bypass passage 6 is further reduced, the air volume can be easily increased at the time of maximum cooling, and the generation of noise can be reduced.

[0057]

As described above, according to the vehicle air conditioner according to the first to fourth aspects, the ventilation resistance in the bypass passage can be reduced while the size is reduced, and the air volume at the time of maximum cooling is increased. Can be easily achieved and the generation of noise can be reduced.

Further, according to the air conditioner for a vehicle according to the fifth aspect, it is possible to easily achieve a high air volume through the wide air intake.

[Brief description of the drawings]

FIG. 1 is a schematic cross section showing an automotive air conditioner according to Embodiment 1 of the present invention.

2A is a view showing an evaporator along an arrow B in FIG. 1, and FIG. 2B is a perspective view for explaining an arrangement state of corrugated fins of the evaporator according to the first embodiment. It is.

FIG. 3 is a schematic perspective view showing a mix door partially broken away.

FIGS. 4A and 4B are perspective views showing a corrugated fin of an evaporator according to a modification of the first embodiment, and FIG.
It is sectional drawing which follows the -B line.

FIG. 5 is a schematic sectional view showing an air conditioner for a vehicle according to a second embodiment of the present invention.

FIG. 6 is a perspective view for explaining an arrangement state of corrugated fins of the evaporator according to the second embodiment.

FIGS. 7A and 7B are perspective views showing a corrugated fin of an evaporator according to a modification of the second embodiment, and FIG.
It is sectional drawing which follows the -B line.

FIG. 8 is a schematic cross-sectional view of an integrated air conditioner for a vehicle that includes a plate-shaped mix door that is slidable and has an evaporator and a heater core placed substantially horizontally in a unit case.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Unit case 2 ... Evaporator 2a ... Evaporator air inflow surface 2b ... Evaporator air outflow surface 3 ... Hot air passage 4 ... Heater core 5 ... Mix door 6 ... Bypass passage 8 ... Mix zone 31 ... Air intake 51, 55 ... Air passage 52 ... Tubes 53, 56 ... Corrugated fins 54, 57 ... Louver Ov ... Vent outlet Od ... Defrost outlet Of ... Foot outlet

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Yoshiaki Namba, Inventor Calsonic, Inc. 5--24-15 Minamidai, Nakano-ku, Tokyo (72) Inventor Osamu Kato 5-24-15, Minamidai, Nakano-ku, Tokyo Calsonic F term in the company (reference) 3L011 BA01 BE00

Claims (5)

[Claims] 1. A mixing door (5) having an arc-shaped cross section is provided between an evaporator (2) disposed in a unit case (1) and a heater core (4) and passed through the evaporator (2). By sliding the air through the mix door (5), predetermined air flows into the hot air passage (3) passing through the heater core (4) and the bypass passage (6) bypassing the heater core (4). The air is branched at a ratio, and the cool air sent from the bypass passage (6) and the hot air sent from the hot air passage (3) are mixed in the mixing zone (8), and the outlet provided in the unit case (1) is provided. In the air conditioner for a vehicle which blows out from (Ov, Of, Od) into a vehicle interior, the evaporator (2) is provided with the unit case (1).
Below the air passage (5) in the evaporator (2).
1, the air flowing through the bypass passage (6) is disposed toward the bypass passage (6), and the heater core (4) is disposed substantially horizontally above the evaporator (2). For air conditioners. 2. The air passage (51) of the evaporator (2) is formed such that air flows orthogonally to an air inlet surface (2a) and an air outlet surface (2b) of the evaporator (2). The said evaporator (2) is inclinedly arrange | positioned so that the said bypass passage (6) side may be located lower than the said hot air passage (3) side, The said evaporator (2) is characterized by the above-mentioned. Automotive air conditioners. 3. The air passage (55) of the evaporator (2) is formed such that air flows obliquely with respect to an air inlet surface (2a) and an air outlet surface (2b) of the evaporator (2). The air conditioner according to claim 1, wherein the evaporator (2) is disposed substantially horizontally. 4. Corrugated fins (53, 5) provided in said air passages (51, 55) of said evaporator (2).
The vehicle air conditioner according to claim 2 or 3, wherein a louver (54, 57) for causing air to flow down toward the bypass passage (6) is formed in (6). 5. An air intake (31) located below the evaporator (2) and for introducing air into the unit case (1) is provided along the slope of the evaporator (2). (3) The air conditioner for a vehicle according to claim 2, wherein the side is open so as to be wider.