JP4049958B2 - Air conditioner for automobile - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a so-called integrated automobile air conditioner in which an evaporator and a heater core are housed in a single unit case so as to be arranged vertically, and in particular, the ventilation resistance of a bypass passage that bypasses the heater core is reduced. The present invention relates to an automotive air conditioner.
[0002]
[Prior art]
In a conventional automotive air conditioner, air inside and outside is selectively taken in by an intake unit, the air is guided to a cooling unit case (hereinafter simply referred to as a unit case), and the air is passed through an evaporator in the unit case. After cooling, the cooling 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. Here, the “evaporator” is, as is well known, a low-temperature and low-pressure refrigerant decompressed by an expansion valve or the like in a cooling cycle circulates inside, and cools the introduced air by heat exchange with the refrigerant. is there. The “heater core” is one in which high-temperature engine cooling water circulates inside and heats the air introduced therein by heat exchange with the high-temperature engine cooling water.
[0003]
Since such an air conditioner for automobiles is installed in a narrow vehicle compartment, there is a space restriction on the overall shape. Therefore, in recent cases, the evaporator and the heater core are placed substantially horizontally in one unit case. A so-called integrated type that is housed so as to be vertically arranged is known.
[0004]
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 a bypass air at a predetermined ratio is a door supported by one fulcrum. If the structure rotates around the center, the space becomes larger, so that the mix door is a flat plate-like door that can be slid in order to shorten the distance between the evaporator and the heater core and reduce the space. Has been proposed.
[0005]
FIG. 8 is a schematic cross-sectional view of an integrated automobile air conditioner that includes a plate-shaped mix door that is slidable and in which an evaporator and a heater core are placed substantially horizontally in a unit case.
[0006]
In the integrated automobile air conditioner shown in FIG. 8, the evaporator 2 is horizontally disposed below the unit case 1, and the heater core 4 is horizontally disposed above the evaporator 2. A plate-shaped mix door 5 having a circular arc cross section is provided between the evaporator 2 and the heater core 4 so as to be slidable in a substantially horizontal direction. By this mix door 5, the air (cold air) that has passed through the evaporator 2 is branched at a predetermined ratio between the warm air passage 3 side that passes through the heater core 4 and the bypass passage 6 side that bypasses the heater core 4, and from the evaporator 2 to 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 obtain air having a predetermined temperature.
[0007]
In the vent mode (cooling mode), cool air is blown out from a vent outlet Ov that is opened and closed by a vent door Dv provided above the unit case 1. In the case of the differential mode (mode to clear the cloudiness of the window), the air (mainly warm air) flowing into the upper passage 9 formed by the partition wall 7 and the unit case 1 from the differential foot opening Odf opened by the vent door Dv. ) Is blown out from a defrost outlet Od opened and closed by a differential-foot door Ddf. In the foot mode (heating mode), the air (mainly hot air) that flows 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]
[Problems to be solved by the invention]
However, in the integrated automobile air conditioner shown in FIG. 8, the air that passes through the evaporator 2 and travels toward the mix door 5 in the direction of arrow A <b> 0 in the drawing is guided to the surface of the mix door 5 during maximum cooling. In this way, it flows in the direction of arrow A0 'in the figure. For this reason, the flow of air (wind axis) F0 entering the cold 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.
[0009]
SUMMARY OF THE INVENTION An object of the present invention is to provide an automotive air conditioner that can reduce the ventilation resistance in a bypass passage while achieving compactness.
[0010]
[Means for Solving the Problems]
The object of the present invention is achieved by the following means.
[0011]
(1) A mixed door having a circular arc cross section is provided between the evaporator and the heater core arranged in the unit case, and the air passing through the evaporator passes through the heater core by sliding the mixed door. Branching into a predetermined ratio between the warm air passage side and the bypass passage side bypassing the heater core, mixing the cool air sent from the bypass passage and the hot air sent from the hot air passage in a mix zone, and a unit case In an automotive air conditioner that blows into the vehicle compartment from the air outlet provided in
The evaporator is disposed below the unit case so that air flowing through the air passage in the evaporator is directed to the bypass passage.
In the corrugated fin provided in the air passage in the evaporator, a louver that causes air to flow closer to the bypass passage is formed,
The heater core is an air conditioner for automobiles, which is disposed substantially horizontally above the evaporator.
[0012]
(2) The air passage of the evaporator is formed so that air flows orthogonally to the air inflow surface and the air outflow surface of the evaporator,
The evaporator is an air conditioner for an automobile according to (1) above, wherein the evaporator is disposed so as to be inclined such that the bypass passage side is positioned below the warm air passage side.
[0013]
(3) The air passage of the evaporator is formed such that air flows in an inclined manner with respect to an air inflow surface and an air outflow surface of the evaporator,
The evaporator is the air conditioning apparatus for automobiles according to (1) above, which is arranged substantially horizontally.
[0015]
( 4 ) The air intake port which is located below the evaporator and introduces air into the unit case is opened so that the warm air passage side becomes wider along the inclination of the evaporator. It is an air conditioner for automobiles according to (2) above.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[0017]
Embodiment 1
1 is a schematic cross-sectional view showing an automotive air conditioner according to Embodiment 1 of the present invention, FIG. 2 (A) is a view showing an evaporator along arrow B in FIG. 1, and FIG. 2 (B) is The perspective view for demonstrating the arrangement | positioning state of the corrugated fin of an evaporator, FIG. 3 is a schematic perspective view which shows a partially broken mix door. In addition, the same code | symbol is attached | subjected to the member which is common in the member shown in FIG.
[0018]
As shown in FIG. 1, the unit case 1 of the automotive air conditioner is disposed adjacent to a dash panel 40 that partitions the engine room E and the room R.
[0019]
An evaporator 2 is disposed at a lower position in the unit case 1. The evaporator 2 is inclined and arranged such that the rear end of the engine room E side is upward and the front end of the room R side is downward. Outside air (outside air) or inside air (inside air) taken 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 front side from the back side of the paper. Passes and flows upward. In the evaporator 2, a refrigerant circulates through 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. . The evaporator 2 constitutes a cooling cycle together with a compressor, a condenser, an expansion valve, and the like (not shown).
[0020]
The air intake 31 opens in a substantially trapezoidal shape so that the warm air passage 3 side becomes wider along the inclination of the evaporator 2. In the illustrated example, the side closer to the engine room E is wider. Thereby, the air intake 31 can be widened without enlarging the lower part of the unit case 1, the passage resistance can be reduced, and the air volume of the introduced air can be easily increased.
[0021]
A heater core 4 is disposed substantially horizontally above the evaporator 2. High-temperature engine cooling water circulates in the heater core 4 through a heater pipe 42 provided through the dash panel 40, and passes through heat exchange between the engine cooling water and air. Air is heated.
[0022]
By arranging the evaporator 2 and the heater core 4 vertically, a compact unit case 1 having a small height dimension and a small size in the left-right direction or the front-rear direction is obtained, and the installation space of the unit case 1 in the vehicle compartment is greatly reduced. As a result, surplus space generated in the passenger compartment can be used effectively.
[0023]
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 through the slide mechanism M, the air (cold air) that has passed through the evaporator 2 is heated and passed through the heater core 4, and the bypass passage 6 that bypasses the heater core 4. Branching at a predetermined ratio (including the case of selectively flowing to the warm air passage 3 side or the bypass passage 6 side). The cool air that has passed through the bypass passage 6 from the evaporator 2 and the warm air that has been 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 having a predetermined temperature.
[0024]
Here, the opening of the mix door 5 is adjusted by sliding it in the left-right direction in FIG. 1 according to the temperature set and desired by the occupant, so that the hot air passage 3 side is fully closed. It stops at an arbitrary position between the cool position (position shown in FIG. 1) and the full hot position where the bypass passage 6 side is fully closed. The ratio of the amount of air flowing to the hot air passage 3 and the amount of air flowing to the bypass passage 6 is adjusted depending on the position of the mix door 5, and the amount of cold air and the amount of hot air mixed in the mix zone 8 are adjusted.
[0025]
Above the unit case 1, there is provided a vent outlet Ov as a cold air outlet from which mainly cool air is discharged, and this vent outlet Ov is selectively opened and closed by a vent door Dv. In 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 differential-foot mode, the vent door Dv closes the vent outlet Ov.
[0026]
When the vent door Dv closes the vent outlet Ov, the airflow flows into the upper passage 9 from the differential-foot opening Odf. The upper passage 9 is provided with a defrost outlet Od that is opened and closed by a differential-foot door Ddf and mainly blows warm air at the upper part of the downstream side of the differential-foot opening Odf. A foot outlet Of opened and closed by a differential-foot door Ddf is provided on the downstream side of the defrost outlet Od.
[0027]
A vent duct 43 is connected to the vent outlet Ov, and conditioned air is blown out through the vent duct 43 toward the upper body of the passenger in the passenger compartment. A defrost duct 44 is connected to the defrost outlet Od, and conditioned air is blown out toward the inner surfaces of the windshield 45 and the side glass via the defrost duct 44. A connection port 32 communicating with a foot duct (not shown) is provided on both sides (direction perpendicular to the paper surface) of the foot outlet Of. Conditioned air is blown out toward the feet of the passengers in the passenger compartment through the foot duct.
[0028]
The bottom of the unit case 1 is formed on a slope that slopes downward toward the dash panel 40. When the intake air is cooled in the evaporator 2, the moisture contained in the air is condensed and dripped onto the bottom of the unit case 1. This 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.
[0029]
As shown in FIG. 3, the mix door 5 has a door body 12 that extends between the evaporator 2 and the heater core 4 in a direction that blocks the air flow from the upstream side that has passed through the evaporator 2. The door body 12 generally has an outer peripheral flat portion 12a and an inner dome-shaped bulged portion 12b, and a seal member 15 made of foamed urethane or the like is attached to the outer surface side. In FIG. 3, the direction of the mix door is different from the direction shown in FIG.
[0030]
The bulging portion 12b has a circular arc shape in cross section, and is gently curved in a concave shape toward the upstream side of the air flow. The concave surface of the bulging portion 12 b serves as a guide when the air flow is guided to the heater core 4 or when the air flow is guided to the bypass passage 6. A rack 17 that meshes with the partial gear 20 (see FIG. 1) is formed on the inner surface side of the door body 12 continuously from end to end. Guide pins 18 that are slidably fitted in guide grooves 50a and 50b (see FIG. 1) formed on the side wall of the unit case 1 protrude from four side corners of the door body 12. Is formed.
[0031]
The slide mechanism M for operating the mix door 5 rotationally drives the guide grooves 50a and 50b in which the guide pins 18 are slidably fitted, the pair of partial gears 20 that mesh with the rack 17, and the pair of partial gears 20. Driving means. As the driving means, for example, an electric motor, a motor actuator in which a reduction gear is accommodated in a casing, or the like is used.
[0032]
Here, the guide grooves 50a and 50b support the four guide pins 18 so that the door main body 12 operates without rattling even if it receives wind pressure. As shown in FIG. 1, the guide grooves 50 a and 50 b are formed in an arc shape with a predetermined gap so as to have a curvature radius substantially the same as the curvature radius of the rack 17 of the mix door 5. The guide grooves 50 a and 50 b are formed on the left and right side walls of the unit case 1. The upper guide pin 18 in FIG. 3 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.
[0033]
In the automotive air conditioner of Embodiment 1, as shown in FIG. 1, the evaporator 2 is arranged so that the air flowing through the air passage 51 in the evaporator 2 is directed to the bypass passage 6 below the unit case 1. Is arranged.
[0034]
More specifically, the evaporator 2 is provided with a corrugated fin 53 in an air passage 51 between a plurality of flat tubes 52 and 52 each having a refrigerant passage formed therein, as shown in FIGS. It is a laminated evaporator. The corrugated fins 53 extend in a direction orthogonal 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 with respect to the air inflow surface 2a and the air outflow surface 2b. The evaporator 2 is disposed so as to be inclined at a predetermined angle θ with respect to the horizontal so that the bypass passage 6 side is positioned below the warm air passage 3 side.
[0035]
Although 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, for example, 5 to 45 degrees is preferable. Thereby, the condensed water flows along the inclination of the evaporator 2, and immediately drops from the lower portion of the evaporator 2 to the lower part of the unit case 1 and is discharged.
[0036]
Next, the operation of this embodiment will be described.
[0037]
Air from the intake unit is introduced into the unit case 1 from the air intake port 31 below the evaporator 2 and is cooled by passing through the evaporator 2. The opening area of the air intake port 31 changes in accordance with the inclination of the evaporator 2. Thereby, a large amount of air is introduced.
[0038]
The air that has passed through the evaporator 2 rises and reaches the mix door 5. The air that has passed through the evaporator 2 is branched into the hot air passage 3 and the bypass passage 6 by the mix door 5, and the air guided to the hot air passage 3 passes through the heater core 4 to become hot air, The air flows in the cold air, and both are mixed in the mixing zone 8 and adjusted to a desired temperature.
[0039]
The temperature-controlled air is blown out from the air outlets Ov, Od, Of corresponding to the air conditioning mode set by the passenger. The air conditioning mode is set by operating an air conditioning mode lever provided in the passenger compartment.
[0040]
Since this embodiment exhibits effectiveness during the vent mode, the vent mode will be described with reference to FIG.
[0041]
In general, in the vent mode, the mix door 5 is often positioned in the maximum cooling state. At the maximum cooling time, the vent door Dv fully closes the differential-foot opening Odf, while the vent outlet Ov is opened. The mix door 5 is positioned at the right end in FIG. 1 and the upstream front surface of the heater core 4 is fully closed.
[0042]
Thereby, the air cooled by passing through the evaporator 2 passes through the bypass passage 6 and enters the vent outlet Ov. And the cold wind which passed through the vent blower outlet Ov blows off toward the vehicle interior from the vent duct 43. FIG.
[0043]
In the first embodiment, since the evaporator 2 is arranged to be inclined at a predetermined angle θ with respect to the horizontal, the air flowing in the air passage 51 near the bypass passage 6 in the evaporator 2 directly flows down toward the bypass passage 6. . Further, the air flowing through 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 toward the upper left in the figure. Therefore, the speed component toward the bypass passage 6 is relatively large.
[0044]
For this reason, the air guided to the end of the mix door 5 flows as shown by the arrow A ′, and the air flow F directly entering the bypass passage 6 is not narrowed carelessly. As a result of the air flow F entering the bypass passage 6 being expanded more than in the case shown in FIG. 8, 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 during maximum cooling and reduce noise generation.
[0045]
Furthermore, since the evaporator 2 is inclined, the drainage of the condensed water becomes good. 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 port 31 is wide on the warm air passage 3 side, 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 is directed to the bypass passage 6, and it is possible to correct or suppress the increase of air flowing into the heater core 4. Temperature adjustment becomes easy. In this way, by inclining the evaporator 2, 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.
[0046]
During temperature control operation and maximum heating, the air that has passed through the evaporator 2 flows obliquely into the heater core 4, so that the airflow resistance in the passage from the evaporator 2 through the heater core 4 to the warm air passage 3 is slightly increased. Will increase. However, since the necessary air volume during these operations is smaller than that during the cooling operation, there is no problem that the air volume necessary for heating cannot be secured.
[0047]
4A and 4B are a perspective view and a cross-sectional view taken along line B-B, showing the corrugated fin of the evaporator according to the first embodiment.
[0048]
In the first embodiment , a louver 54 is formed on the corrugated fin 53 described above . The louver 54 is cut and raised so that the air flows down toward the bypass passage 6.
[0049]
According to the first embodiment, the air flowing into the air passage 51 near the heater core 4 in the evaporator 2 sequentially flows into the air passage 51 near the bypass passage 6 through the louver 54 while flowing through the evaporator 2. Flow down. For this reason, 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 in the air passage 51 passes through the louver 54, the velocity component toward the bypass passage 6 is increased, so that the evaporator 2 is disposed at a predetermined angle θ with respect to the horizontal. In combination with this, the velocity component of the air flowing out from the air outflow surface 2b toward the bypass passage 6 becomes larger, and the flow F of air directly entering the bypass passage 6 is further prevented from being narrowed. As a result, the airflow resistance in the bypass passage 6 is further reduced, and it is possible to easily achieve a high air volume at the maximum cooling time and to reduce the generation of noise.
[0050]
<< Embodiment 2 >>
FIG. 5 is a schematic cross-sectional view illustrating an automotive air conditioner according to Embodiment 2 of the present invention, and FIG. 6 is a perspective view for explaining an arrangement state of corrugated fins of an evaporator according to Embodiment 2.
[0051]
Similarly to the first embodiment, the evaporator 2 according to the second embodiment is arranged below the unit case 1 so that the air flowing through the air passage 55 in the evaporator 2 is directed toward the bypass passage 6.
[0052]
However, unlike Embodiment 1, the corrugated fins 56 extend in a direction inclined with respect to the air inflow surface 2a and the air outflow surface 2b. Thereby, the air passage 55 of the evaporator 2 is formed so that the air flows in an inclined manner with respect to the air inflow surface 2a and the air outflow surface 2b. The evaporator 2 is disposed substantially horizontally.
[0053]
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 toward the bypass passage 6. In addition, 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 air flow F directly entering the bypass passage 6 is careless. There is no narrowing. As a result, the ventilation resistance in the bypass passage 6 is reduced, and it is possible to easily achieve a high air volume at the maximum cooling time and to reduce the generation of noise.
[0054]
7A and 7B are a perspective view showing a corrugated fin of an evaporator according to Embodiment 2, and a cross-sectional view taken along line BB.
[0055]
In the second embodiment , a louver 57 is formed on the corrugated fin 56 described above . The louver 57 is cut and raised so that air flows down toward the bypass passage 6.
[0056]
According to the second embodiment, the air flowing into the air passage 55 near the heater core 4 in the evaporator 2 sequentially flows into the air passage 55 near the bypass passage 6 through the louver 57 while flowing through the evaporator 2. Flow down. For this reason, the amount of air flowing down directly toward the bypass passage 6 is increased as compared with the case where the louver 57 is not formed. Moreover, since the velocity component of the air flowing in the air passage 55 increases toward the bypass passage 6 by passing through the louver 57, the corrugated fins 53 are inclined with respect to the air inflow surface 2a and the air outflow surface 2b. The air flowing out from the air outflow surface 2b has a larger velocity component toward the bypass passage 6 and the air flow F directly entering the bypass passage 6 is narrowed together with the fact that the air flows out from the air outflow surface 2b. Things will disappear. As a result, the airflow resistance in the bypass passage 6 is further reduced, and it is possible to easily achieve a high air volume at the maximum cooling time and to reduce the generation of noise.
[0057]
【The invention's effect】
As described above, according to the air conditioning apparatus for automobiles according to claims 1 to 3 , the airflow resistance in the bypass passage can be reduced while achieving compactness, and a high air volume at the maximum cooling can be easily achieved. There is an effect that the generation of noise can be reduced.
[0058]
Further, according to the air conditioner for an automobile according to the fourth 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-sectional view showing an automotive air conditioner according to Embodiment 1 of the present invention.
2A is a view showing an evaporator along 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 Embodiment 1. FIG. It is.
FIG. 3 is a schematic perspective view showing a partially broken mix door.
4A and 4B are a perspective view showing a corrugated fin of the evaporator according to Embodiment 1, and a cross-sectional view taken along the line BB.
FIG. 5 is a schematic cross-sectional view showing an automotive air conditioner according to Embodiment 2 of the present invention.
FIG. 6 is a perspective view for explaining an arrangement state of corrugated fins of an evaporator according to a second embodiment.
7A and 7B are a perspective view showing a corrugated fin of an evaporator according to Embodiment 2, and a cross-sectional view taken along line BB.
FIG. 8 is a schematic cross-sectional view of an integrated automotive air conditioner that includes a plate-shaped mix door that can slide and that 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 ... Warm air passage 4 ... Heater core 5 ... Mix door 6 ... Bypass passage 8 ... Mix zone 31 ... Air intake port 51, 55 ... Air passage 52 ... tubes 53, 56 ... corrugated fins 54, 57 ... louver Ov ... vent outlet Od ... defrost outlet Of ... foot outlet

Claims (4)

A mix door (5) having a circular arc cross section is provided between the evaporator (2) and the heater core (4) disposed in the unit case (1), and the air that has passed through the evaporator (2) By sliding the door (5), it branches at a predetermined ratio between the warm air passage (3) passing through the heater core (4) and the bypass passage (6) bypassing the heater core (4), The cold air sent from the bypass passage (6) and the hot air sent from the hot air passage (3) are mixed in the mix zone (8), and the air outlets (Ov, Of, In an automotive air conditioner that is blown into the passenger compartment from Od),
The evaporator (2) is disposed below the unit case (1) so that air flowing through the air passages (51, 55) in the evaporator (2) is directed to the bypass passage (6).
In the corrugated fins (53, 56) provided in the air passages (51, 55) in the evaporator (2), louvers (54, 57) for allowing air to flow toward the bypass passage (6) are formed,
The automotive air conditioner, wherein the heater core (4) is disposed substantially horizontally above the evaporator (2). 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) of the evaporator (2),
The said evaporator (2) is inclined and arrange | positioned so that the said bypass channel (6) side may be located below rather than the said warm air channel | path (3) side, The object for motor vehicles of Claim 1 characterized by the above-mentioned. Air conditioner. The air passage (55) of the evaporator (2) is formed such that air flows in an inclined manner with respect to the air inflow surface (2a) and the air outflow surface (2b) of the evaporator (2),
The air conditioner for an automobile according to claim 1, wherein the evaporator (2) is arranged substantially horizontally. An air intake port (31) that is located below the evaporator (2) and that introduces air into the unit case (1) is wide on the warm air passage (3) side along the inclination of the evaporator (2). The automotive air conditioner according to claim 2 , wherein the air conditioner is open so as to be .

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