JP2003118358A - Air conditioner for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a drain structure for condensed water dropping into a blower from a cooling heat exchanger in an air conditioner for a vehicle having the cooling heat exchanger arranged above the blower. SOLUTION: The cooling heat exchanger 23 is arranged above the blower 11, a drain hole 44 for discharging water inside the blower 11 is arranged blow the blower 11, and condensed water from the cooling heat exchanger 23 is discharged to the outside the vehicle via a first drain passage 42 and a second drain passage 46. The drain hole 44 is communicated with the first drain passage 42, so that the condensed water inside the blower 11 can be discharged to the outside the vehicle via the drain hole 44, the first drain passage 42, and the second drain passage 46.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicle air conditioner in which a cooling heat exchanger is arranged above a blower so that the vehicle mounting space of an indoor unit can be reduced.
The present invention relates to a drainage structure of condensed water falling from a heat exchanger for cooling.

[0002]

2. Description of the Related Art The inventor of the present invention has previously proposed Japanese Patent Application No.
In the patent application of No. 2209, an air conditioner for a vehicle is proposed, which makes it possible to reduce the vehicle mounting space of the indoor unit part and to secure the drainage property in the horizontal cooling heat exchanger.

In this prior application, a cooling heat exchanger composed of an evaporator of a refrigeration cycle is arranged above the blower in a substantially horizontal direction, and air blown from the blower blows the cooling heat exchanger from below. In the vehicle air conditioner that passes upward, the heat exchange surface of the cooling heat exchanger is inclined at a predetermined angle from the horizontal plane, and the main flow of the blown air from the blower is at the higher part of the cooling heat exchanger. I'm trying to go.

According to this, the vehicle mounting space of the indoor unit can be reduced by the layout in which the cooling heat exchanger is arranged in the substantially horizontal direction above the blower, and at the same time, the main flow of the blown air is the cooling heat exchanger. Of the cooling heat exchanger, the condensed water that collects on the lower end side of the inclination of the cooling heat exchanger smoothly drops without being obstructed by the wind pressure of the main flow of blown air. Therefore, even if the cooling heat exchanger is placed horizontally above the blower, it is possible to ensure good drainage of the condensed water.

[0005]

However, according to the above-mentioned prior application, since there is no wind pressure from the lower side to the upper side of the cooling heat exchanger at the moment when the blower stops operating, that is, at the moment when the blower stops. Condensed water from the cooling heat exchanger falls into the blower. Further, even when the blower is operating, condensed water may temporarily drop into the blower due to vibration or the like when the vehicle is traveling.

In the latter case, the condensed water that has fallen into the blower is immediately blown up by the blown air and adheres to the cooling heat exchanger, so that the condensed water is cooled along the inclination of the cooling heat exchanger. By moving the lower surface of the exchanger downward, the condensate can be drained as usual from the lower inclined end of the cooling heat exchanger.
However, in the former case, the condensed water remains in the blower unless the ventilation is restarted or the evaporation of the condensed water in the blower is not completed. If the condensed water remains in the blower for a long time in this way, bacteria may grow in the residual condensed water and cause a bad odor, or the residual condensed water may shake due to vibration of the vehicle and generate a flow noise. .

In view of the above points, the present invention provides a drainage structure of condensed water that drops from a cooling heat exchanger into a blower in a vehicle air conditioner in which a cooling heat exchanger is arranged above the blower. With the goal.

Further, the present invention is directed to a vehicle air conditioner in which a cooling heat exchanger is arranged above a blower, and simplifies the drainage structure of condensed water that drops from the cooling heat exchanger into the blower. The purpose of.

Further, according to the present invention, in a vehicle air conditioner in which a cooling heat exchanger is arranged above a blower, drainage of condensed water that drops from the cooling heat exchanger into the blower and suppression of deterioration of the blowing performance. The other purpose is to achieve compatibility with.

[0010]

In order to achieve the above object, in the invention described in claim 1, a blower (11) for blowing air, and a cooling heat exchanger for cooling the blown air of the blower (11). (23), a cooling heat exchanger (23) is arranged above the blower (11), and a drain hole (44) for draining water in the blower (11) is provided below the blower (11). A drain hole (4) is provided in the main drain path (42, 46) that is provided and drains the condensed water from the cooling heat exchanger (23).
It is characterized in that 4) is communicated.

As a result, the condensed water that has entered the blower (11) is discharged from the drain hole (44) to the main drain paths (42, 4).
6) It can be drained to the outside of the car through. for that reason,
It is possible to prevent problems such as condensed water remaining in the blower (11) for a long time and causing a bad odor, and residual condensed water swaying due to vibration of the vehicle to generate a flowing sound.

Moreover, the condensed water from the cooling heat exchanger (23) and the condensed water that has entered the blower (11) can be discharged to the outside of the vehicle through the common drainage paths (42, 46), so that the condensed water is condensed. The water drainage structure can be simplified.

According to the invention described in claim 2, claim 1
In, the main drainage route is specifically the first drainage route (42) for draining the condensed water from the cooling heat exchanger (23).
And a second drainage path (46) which is connected to the downstream side of the first drainage path (42) and drains condensed water from the first drainage path (42) and water from the drainage hole (44) to the outside of the vehicle. Composed.

According to a third aspect of the invention, in the second aspect, the second drainage route (46) is inclined obliquely downward in the vehicle front-rear direction, and the inclination angle (θ1) of the second drainage route (46). Is 15 ° or more, and the upper end position (b) of the bottom inclined surface of the second drainage path (46) is set to the vertical line (L3) passing through the condensed water drop point (a) of the first drainage path (42). The angle (θ2) formed by the vertical line (L3) and the line (L4) connecting the upper end position (b) and the condensed water drop point (a) to the drain hole (44) side should be 15 ° or more. Is characterized by.

By the way, the vehicle inclines by about 15 ° in the front-rear direction as the vehicle travels uphill and downhill. In claim 3, paying attention to this point, the second drainage path (46) is inclined obliquely downward in the vehicle front-rear direction, and the inclination angle (θ
Since 1) is set to 15 ° or more, the second drainage route (46) can be maintained in the obliquely downward inclined state even when the vehicle inclines in the front-rear direction due to traveling uphill or downhill.

By setting the angle (θ2) to 15 ° or more, the condensed water in the first drainage path (42) is inclined at the bottom of the second drainage path (46) even if the vehicle is tilted in the front-rear direction. The state of falling on the surface can be maintained. As described above, it is possible to prevent condensed water in the first drainage path (42) and the second drainage path (46) from flowing back into the blower (11) through the drainage hole (44).

According to a fourth aspect of the present invention, in the second aspect, the second drainage path (46) is arranged substantially horizontally, and the drainage hole (44) is a predetermined amount larger than the second drainage path (46). It is characterized in that it is located at a high position, and the drainage hole (44) communicates with the second drainage path (46) via the step portion (55) for preventing backflow.

As a result, the water in the blower (11) flows from the drain hole (44) to the step portion (55) and the second drain path (46).
It can be discharged to the outside of the vehicle via. Moreover, the second drainage route (4
Even if 6) is arranged horizontally, the step portion (55) provided between the drainage hole (44) and the second drainage path (46) allows the second drainage path (46) to move to the drainage hole (44) side. The back flow of water can be prevented.

Further, when the length of the second drainage path (46) is long, if the second drainage path (46) is arranged in an inclined manner as in the third aspect, the second drainage path (46) can be arranged in an inclined manner. Although a lot of space is required in the vertical direction, according to claim 4, the second drainage route (46) is horizontally arranged even when the length of the second drainage route (46) is long, so that the second drainage route (46) is provided. The vertical space for arranging) is very small, which is practically advantageous.

According to a fifth aspect of the present invention, in any one of the first to fourth aspects, a maze for controlling the drainage path (44a) of the drainage hole (44) to prevent air leakage from the blower (11). It is characterized by having a structure.

As a result, even if the drain hole (44) is opened in the lower part of the blower (11), the pressure drop in the blower (11) can be suppressed to a small amount, and the decrease in the blower performance can be suppressed to a small extent.

According to a sixth aspect of the present invention, in any one of the first to fifth aspects, a drain hole for draining water in the duct (14) is provided at a lower portion of the suction duct (14) of the blower (11). (54) is provided, and the drainage hole (54) communicates with the main drainage path (42, 46).

By the way, rainwater or the like flows into the air suction duct (14) of the blower (11) through the outside air introduction port (20a), and the inflow moisture into this duct is also simple by using the drainage path of the condensed water. Can be drained with various configurations.

In the invention according to claim 7, the blower (11) for blowing air and the cooling heat exchanger (23) for cooling the blown air of the blower (11) are provided, and the blower (11) is provided.
A heat exchanger (23) for cooling is arranged above the
A drain hole (44) for draining water in the blower (11) is provided in the lower part of the blower (11), and a drainage path (44a) of the drain hole (44) is used to suppress air leakage from the inside of the blower (11). It is characterized by having a maze structure.

As a result, the water in the blower (11) can be drained through the drain hole (44) and the drain hole (4
Even if 4) is opened to the blower (11), air leakage from the inside of the blower (11) can be suppressed by the labyrinth structure to suppress deterioration of the blower performance.

[0026] In the invention according to claim 8, in claim 5 or 7, the maze structure is located substantially vertically downward with respect to the blowing direction in the blower (11) from the portion of the drain hole (44) on the front side of the blower. It is characterized by being constituted by an L-shaped bent plate member (45) which extends in the direction opposite to the air blowing direction in the blower (11) after facing.

According to this, the blown air is discharged through the drain hole (44).
When it tries to pass through, the bending plate member (45) first collides with a hanging portion substantially perpendicular to the air blowing direction to prevent the passage of air, so that the bending plate member (45) is simply bent in an L shape. Even with the shape, it is possible to favorably suppress the deterioration of the blowing performance.

The reference numerals in parentheses of the above means indicate the correspondence with the specific means described in the embodiments described later.

[0029]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment) FIGS. 1 to 3 show an indoor unit portion 10 of a vehicle air conditioner according to a first embodiment.
FIG. 1 is a vertical cross-sectional view of a main part (lower part) of the indoor unit section 10, and FIG. 2 is a front view of the indoor unit section 10 as viewed from the vehicle interior side. 3 is a right side view of the indoor unit section 10. The front, rear, up, down, left, and right arrows in each figure indicate the directions in which the indoor unit 10 is mounted on a vehicle.

The indoor unit portion 10 is arranged in the instrument panel (not shown) in the front portion of the vehicle compartment at a substantially central portion in the left-right direction. As shown in FIGS. 2 and 3, the indoor unit portion 10 is roughly divided into a blower 11 arranged in the lower step portion in the vertical direction, a heat exchange portion 12 arranged in the middle step portion in the vertical direction, and an upper step portion in the vertical direction. The blowout mode switching unit 13 is provided.
That is, the indoor unit section 10 is arranged so that the blower 11 moves vertically.
The heat exchange section 12 and the blowout mode switching section 13 are stacked to form a vertical layout.

In this example, the indoor unit 10 is applied to a right-hand drive vehicle, and therefore, the air suction duct 14 for introducing the inside and outside air is provided on the left side (passenger side) of the indoor unit 10. It is arranged.

The blower 11 includes a blower fan 16 made of resin,
A fan driving motor 17 and a resin scroll casing 18 that houses the fan 16 are provided. The blower fan 16 is composed of a centrifugal multi-blade fan (sirocco fan) in which a large number of arcuate blades are arranged in the circumferential direction, and the central portion of the blower fan 16 is integrally fastened to a rotating shaft 19 of a motor 17. The rotating shaft 19 of the motor 17 is arranged in the left-right direction of the vehicle.

As shown in FIG. 1, the scroll casing 18 is arranged so that the winding start portion (nose portion) 18a of the scroll casing 18 is located on the vehicle rear side and the winding end portion 18b is located on the vehicle front side. is there. here,
The winding direction of the scroll casing 18 is a direction in which the diameter of the scroll shape gradually increases from the winding start portion (nose portion) 18a to the winding end portion 18b. The blower fan 16 rotates in the winding direction of the scroll casing 18 (the direction of arrow A in FIG. 1), and the air discharged from the blower fan 16 flows in the scroll casing 18 along the scroll winding direction.

Further, when the centrifugal blower fan 16 is viewed from above, the winding start portion (nose portion) 18a of the scroll casing 18 is prevented so that the centrifugal blower fan 16 is not exposed.
Thus, the scroll casing 18 is arranged so as to cover the upper part of the centrifugal blower fan 16. That is, in the horizontal direction of the blower fan 16, the winding start portion (nose portion) 1 is located on the outer side (front side of the vehicle) of the outer peripheral surface of the blower fan 16.
8a is located.

Here, since the vehicle normally tilts about 15 ° in the front-back direction due to traveling uphill and downhill, the arcuate shape of the outer peripheral surface of the blower fan 16 and the winding start portion (nose portion).
A tangent line L2 connecting the arcuate shape of 18a and this tangent line L2
Is a vertical line L passing through the point X where the outer peripheral surface of the blower fan 16 contacts
When the angle formed by 1 is θn, this angle θn is
15 ° considering the inclination angle (15 °) in the front-rear direction of the vehicle
It is preferable to set the above.

As shown in FIG. 2, in the scroll casing 18, the motor 17 of the blower 11 is arranged on the right side (driver's seat side) in the vehicle left-right direction, and the blower fan 16 is arranged on the left side (passenger seat side). The lower end of the air suction duct 14 is connected to the air intake port 18c (FIG. 2) provided on the left side (passenger seat side) of the scroll casing 18. The air suction duct 14 extends upward along the left side of the heat exchange unit 12, and the upper end portion thereof is at the blowout mode switching unit 1.
It is arranged at a portion of the vehicle 3 on the front side.

At the upper end of the air suction duct 14, an outside air introduction port 20a and an inside air introduction port 20b are provided, and
A plate-shaped inside / outside air switching door 21 is rotatably arranged around a rotation shaft 21a in the inner space of the upper end of the duct. By opening / closing the outside air introduction port 20a and the inside air introduction port 20b by the inside / outside air switching door 21, the blower 11 can switch and introduce the vehicle interior air (inside air) or the vehicle exterior air (outside air) through the duct 14. ing. A filter 22 for cleaning air is provided inside the air suction duct 14.
Has been placed.

On the other hand, the evaporator (cooling heat exchanger) 2 of the heat exchange section 12 is located above (just above) the blower 11 in the left-right direction of the vehicle.
3 are arranged in a substantially horizontal direction. More specifically, the dimension of the evaporator 23 in the vehicle left-right direction (tube stacking direction B in FIG. 4, which will be described later) is sufficiently larger than the dimension of the blower 11 in the vehicle left-right direction (axial dimension). Then, a substantially center portion of the evaporator 23 in the vehicle left-right direction is located substantially at a center portion of the blower 11 in the vehicle left-right direction (see FIG. 2). For this reason, the main flow of the blown air from the blower 11 is directed to the substantially central portion of the evaporator 23 in the vehicle left-right direction.

On the contrary, with respect to the front-rear direction of the vehicle, the rotary shaft 19 which is the central portion of the blower 11 is disposed so as to be biased toward the vehicle rear side (the upper end side of the inclination) of the evaporator 23 as shown in FIG. is there.

Here, the specific structure and layout of the evaporator 23 will be described in more detail. FIG.
In the evaporator 23, a plurality of flat tubes 24 forming a refrigerant passage, and corrugated fins 25 joined between the plurality of tubes 24 are exemplified.
A tank portion 2 formed integrally with both ends of the tube 24 in the longitudinal direction to communicate the refrigerant passages between the plurality of tubes 24.
6 and 27, and a refrigerant inlet / outlet joint 28.

Further, in the evaporator 23 of this example, the tube 2
The side plates 29 and 30 forming the side refrigerant passages are arranged on both side surfaces in the stacking direction B (vehicle left-right direction) B of FIG. Of the side plates 29, 30 at both ends in the vehicle left-right direction, the refrigerant inlet / outlet joint 28 is joined to the vehicle front side (tank portion 26 side) portion of the vehicle right side plate 29. The evaporator 2
Each member of 3 is formed of a metal material having good heat conduction such as aluminum, and assembled by integral brazing.

As shown in FIGS. 1 and 3, the evaporator 23 is tilted by a predetermined angle θe from the horizontal plane so that the front side is lower than the rear side in the vehicle front-rear direction. Here, the larger the inclination angle θe of the evaporator 23, the better the drainage of the condensed water, but on the other hand, since the vertical arrangement space of the evaporator 23 increases, the drainage of the condensed water and the evaporator 23 are increased. The inclination angle θe of the evaporator 23 is set to an angle in the vicinity of 20 ° from the viewpoint of suppressing the arrangement space for Also,
As shown in FIG. 4, the longitudinal direction C of the tube 24 faces the vehicle front-rear direction, so that the evaporator 23 inclines along the longitudinal direction of the tube 24.

By the way, the scroll casing 18 and the case 31 located above the scroll casing 18 are separated from each other by a dividing line 32 (FIG. 2) located substantially in the center of the indoor unit 10 in the vehicle left-right direction.
Is divided into two in the left-right direction of the vehicle. The left and right split cases are integrally molded with resin, and a metal spring clip,
The left and right split cases are integrally fastened by fastening means such as screws.

As shown in FIG. 3, a heater core 33 is installed in the case 31 on the downstream side of the evaporator 23 (upper side of the vehicle) and on the front side of the vehicle. here,
The heater core 33 is arranged in a substantially horizontal state with an inclination along the inclination of the evaporator 23. The heater core 33 is a heating heat exchanger that heats blown air using engine cooling water (warm water) as a heat source.

In the case 31, a bypass passage 34 is formed in the portion of the heater core 33 on the vehicle rear side. A plate-like slide type air mix door 35 is disposed in a portion immediately below the heater core 33 and the bypass passage 34 (upper portion of the evaporator 23) so as to be slidable in the vehicle front-rear direction.

The slide type air mix door 35 plays a role of a temperature adjusting means. The slide type air mix door 35 has a warm air heated by passing through the heater core 33 and a cool air passing by the bypass passage 34 by sliding in the vehicle longitudinal direction. The temperature of the air blown into the passenger compartment is adjusted by adjusting the air flow rate. By using the air mix door 35 that is slidable in the vehicle front-rear direction in this manner, the vertical door arrangement space can be significantly reduced compared to the case where a rotary plate door is used.

At the upper part of the heater core 33, there is formed a hot air passage 36 through which the warm air after passing through the heater core 33 flows from the front side of the vehicle toward the rear side of the vehicle as shown by an arrow D. The warm air from the hot air passage 36 (arrow D) and the cold air from the bypass passage 34 (arrow E) are mixed in the working space inside the blowout mode switching rotary door 37 to become air at a predetermined temperature. That is, the working space of the rotary door 37 also serves as an air mixing chamber.

Here, the rotary door 37 for switching the blowing mode has a known structure and has a semi-cylindrical shape or a cylindrical shape extending in the left-right direction of the vehicle, and has both ends in the axial direction (left-right direction of the vehicle). The rotating shaft is integrally molded with resin.

The rotary door 37 has a surface (semi-cylindrical or cylindrical circumferential surface) distant from the rotary shaft by a predetermined distance in the radial direction as a door surface. The openings 38, 39, 40 of the face, foot, and defroster are opened and closed by one door surface. The openings 38, 39, 40 are provided in the rotary door 37.
Are arranged at predetermined intervals in the circumferential direction of the door surface.

The face opening 38 is opened at a portion on the rear side of the vehicle on the upper surface of the working space of the rotary door 37.
The face opening 38 communicates with a face outlet (not shown) for blowing air toward the upper side (passenger's head side) in the vehicle compartment. Further, the foot openings 39 are opened at the left and right sides of the lower surface of the working space of the rotary door 37, and foot outlet ducts (not shown) extending downward are provided at the left and right sides of the case 31 in the foot openings 39. The air is blown toward the occupant's feet in the passenger compartment from the foot outlets provided at the lower ends of the left and right foot outlet ducts.

The defroster opening 40 has a rotary door 37.
The defroster opening 40 is opened at a portion on the front side of the vehicle in the upper surface of the working space of the defroster outlet 40 that blows air toward the inner surface of the windshield of the vehicle (not shown).
Communicate with.

By rotating one rotary door 37, it is possible to switch and open a plurality of blowout openings 38 to 40 arranged in the circumferential direction of the door. It can be reduced compared to the mode switching unit.

Next, the drainage path of the condensed water from the evaporator 23 will be described. As shown in FIGS. 1 and 3, an auxiliary drainage member 41 is attached to the outside of the scroll casing 18 and the case 31 (vehicle front side) on the lower inclined side of the evaporator 23 (vehicle front side). A first drainage path 42 is formed in 41. The auxiliary drainage member 41 is a resin plate member, and is formed to extend over the entire length of the evaporator 23 in the vehicle left-right direction in the vicinity of the inclined lower end portion (vehicle front end portion) of the evaporator 23. Thus, the first drainage path 42 is also formed over the entire length of the evaporator 23 in the vehicle left-right direction in the vicinity of the inclined lower end of the evaporator 23.

Further, in the case 31, a plate-shaped drainage promotion guide 4 that abuts on the lower side surface of the heat exchange core portion of the evaporator 23 near the inclined lower end portion (a portion on the extension of the arrow F in FIG. 4).
3 is integrally formed over the entire length of the evaporator 23 in the vehicle left-right direction. At the upper end of the drainage promotion guide 43, notch-shaped drainage ports 43a (see FIGS. 1 and 5) are formed near both ends in the vehicle left-right direction. Condensed water generated in the evaporator 23 does not fall directly downward due to the surface tension between the surface of the evaporator 23 and the upward wind pressure of the blower 11, and as shown in G of FIG. It moves diagonally downward along the lower surface of the replacement core. Then, the condensed water adheres to the upper end portion of the drainage promotion guide 43.

In the vicinity of the drainage promotion guide 43, as shown in FIG.
As indicated by arrows H and I, the blown air of the blower 11 flows from the blowout passage portion of the scroll casing 18 so as to spread to both left and right sides of the vehicle. Due to this air flow, the condensed water moves to the left and right sides of the vehicle at the upper end of the drainage promotion guide 43,
It reaches the drain ports 43a on both the left and right sides. Then, the condensed water passes through both drainage ports 43 a and flows into the first drainage path 42.

As shown in FIG. 1, the first drainage path 42 slopes obliquely downward along the scroll casing 18 of the blower 11 from the front side of the vehicle toward the rear side of the vehicle and reaches the lowermost portion of the scroll casing 18. Has been formed. A drainage hole 44 is provided at the bottom of the scroll casing 18.
Is open. The drainage hole 44 has a slit-like shape elongated in the lateral direction of the vehicle with a minute width dimension of about mm, and a bent plate member 45 bent in an L shape (key shape) is provided below the drainage hole 44. is there. The bent plate member 45 may be integrally formed with the scroll casing 18 or may be separately formed and fixed to the scroll casing 18.

This bent plate member 45 prevents the drainage hole 44 from being deteriorated due to the opening of the drainage hole 44 as much as possible.
A drainage path 44a having a maze (labyrinth) structure is formed immediately below. Therefore, in this example, the bent plate member 45 hangs downward from a front portion of the drainage hole 44 in the air blowing direction A in a direction perpendicular to the air blowing direction A (for example, about 5 mm), and the hanging portion In the direction opposite to the air blowing direction A from the lower end of the predetermined dimension (for example,
It has an L-shape extending about 10 mm).

The first drainage path 42 communicates with a second drainage path 46 that is inclined downwardly from the vehicle rear side toward the vehicle front side at a lower portion of the scroll casing 18. The drainage path 44a downstream of the drainage hole 44 of the scroll casing 18 also communicates with the upper end of the second drainage path 46.

More specifically, the auxiliary drainage member 4
1, in the lower part of the scroll casing 18,
A bent wall surface 47 that vertically hangs downward from the bottom surface of the scroll casing 18 and that bends horizontally in an L-shape is formed below the bent plate member 45. This curved wall 4
The lower end tip of the bending plate member 45 faces the vertical wall surface of 7 at a predetermined interval. Therefore, in this example, by combining the bent plate member 45 bent in an L shape (key shape) and the bent wall surface 47, the drainage path 44a of the labyrinth structure is formed.
Is formed.

The second drainage path 46 protrudes into the engine room 49 through a through hole 51 of a partition plate (fire wall) 50 on the vehicle body side that separates the interior of the vehicle room 48 from the interior of the engine room 49. The tip end opening of the second drainage path 46 forms a drain hole 46a.
Drain the condensed water from 6a. The pipe member 46b forming the second drainage path 46 may be integrally molded with the auxiliary drainage member 41 or may be molded separately and fixed to the auxiliary drainage member 41.

By the way, the vehicle normally inclines about 15 ° in the front-rear direction due to traveling uphill and traveling downhill. When this vehicle tilts in the front-rear direction, the condensed water in the second drainage path 46 passes through the drainage hole 44 and passes through the scroll casing 18.
There is a risk of backflow. Therefore, in the present embodiment, the inclination angle θ1 of the second drainage path 46 obliquely downward is set to 1.
The angle θ2 defining the upstream end position of the bottom surface portion of the second drainage path 46 is set to 5 ° or more and 15 ° or more.

Here, the angle θ2 is defined as follows. L3 is a vertical line passing through the condensed water drop point a of the first drainage path 42, and point b is a corner portion at the upstream end position of the inclined bottom surface portion of the second drainage path 46, and this corner portion b is It is located on the drain hole 44 side by an angle θ2 with respect to the vertical line L3.
That is, the line L4 is the condensed water drop point a of the first drainage path 42.
And a corner portion b, and the angle formed by the line L4 and the vertical line L3 is θ2.

As a result, even when the vehicle is tilted in the front-rear direction, the condensed water from the first drainage path 42 always drops onto the inclined bottom surface portion of the second drainage path 46. Condensed water is drained out of the vehicle along the slope of the second drainage path 46 without flowing back into the scroll casing 18.

Next, the function and effect of this embodiment will be described. When the blower 11 is operating normally, the blower 11
Since the wind pressure in the upward direction acts on the evaporator 23, the condensed water generated in the evaporator 23 does not drop directly downward due to the surface tension between the evaporator surface and the wind pressure in the upward direction.
As shown in G of FIG. 1, the lower surface of the heat exchange core of the evaporator 23 travels diagonally downward and the condensed water adheres to the upper end of the drainage promotion guide 43.

The condensed water at the upper end of the drainage promotion guide 43 moves to both ends in the left and right direction of the vehicle by the air flow to the left and right sides of the vehicle shown by arrows H and I in FIG. Condensed water from the drain port 43a is the first drainage path 42.
Flows in. The condensed water further passes through the first drainage path 42 and the second drainage path 46 and is drained to the outside of the vehicle through the drain hole 46a at the tip. Since the pressure inside the scroll casing 18 is high during the operation of the blower 11, the first
The condensed water in the drainage path 42 does not flow back into the scroll casing 18 through the drainage hole 44.

On the other hand, at the moment when the blower 11 is stopped from the operating state (the moment when the blower is stopped), there is no upward wind pressure acting on the evaporator 23, so that the evaporator 23 as shown by the water droplet J in FIG. Condensed water falls from the lower surface of the, and the condensed water tries to collect at the bottom of the scroll casing 18. Figure 1
The broken line K indicates the condensed water accumulated at the bottom of the scroll casing 18. Even if the blower 11 is operating, when the vehicle vibrates in the vertical direction, the condensed water causes the condensed water to flow from the lower surface of the evaporator 23 due to the vibration.
The phenomenon of falling into 8 occurs.

However, according to this embodiment, since the drain hole 44 is opened at the bottom of the scroll casing 18 and the drain hole 44 communicates with the second drain path 46, the condensed water in the scroll casing 18 is removed. The water can be quickly drained to the outside of the vehicle from the drain hole 44 through the second drain path 46. Therefore, it is possible to prevent a problem that condensed water stays in the scroll casing 18 for a long time and causes an offensive odor, or that the condensed water stayed in the scroll casing 18 shakes due to vehicle vibration to generate an abnormal noise. .

Moreover, drainage of condensed water in the blower 11
Second drainage path 46 for drainage of condensed water at regular times
Therefore, the drainage structure of the condensed water in the blower 11 can be simply configured at low cost.

Further, since the drainage hole 44 is opened in the scroll casing 18, there is a concern that the pressure in the scroll casing 18 may be reduced due to air leakage from the drainage hole 44 and the ventilation performance may be reduced. According to the form,
Since the drainage path 44a of the labyrinth structure is formed by the bent plate member 45 in the lower portion of the drainage hole 44, air leakage from the drainage hole 44 can be favorably suppressed and the ventilation performance can be suppressed from being deteriorated.

In particular, in the present embodiment, the bent plate member 45 hangs downward from the front portion of the drainage hole 44 in the air blowing direction A in the direction perpendicular to the air blowing direction A, and from the lower end of this hanging portion, the air blowing direction. Since it has an L-shape extending in the direction opposite to A, when the blown air tries to pass through the drain hole 44, the air first collides with the hanging portion of the bending plate member 45 in the direction perpendicular to the blown direction A. Since it is possible to prevent the passage of air, even if the bending plate member 45 has a simple L-shaped bent shape, it is possible to reliably suppress the deterioration of the blowing performance.

When the blower 11 is stopped, the blower 1
Since the pressure in 1 has fallen to the atmospheric pressure, when the vehicle inclines in the front-back direction due to traveling uphill or downhill, the condensed water that has flowed into the second drainage path 46 from the first drainage path 42 is drained. To flow back into the scroll casing 18. However, according to the present embodiment, both the inclination angle θ1 of the second drainage path 46 and the angle θ2 that defines the upstream end position b of the bottom surface portion of the second drainage path 46 correspond to the inclination angle in the vehicle front-rear direction. Since it is set to 15 ° or more, the condensed water from the first drainage path 42 always drops onto the inclined bottom surface portion of the second drainage path 46 even when the vehicle is tilted in the front-rear direction. Condensed water from the route 42 can be discharged to the outside of the vehicle along the slope of the second drainage route 46. Therefore, the first drainage path 42 and the second drainage path 4
It is possible to reliably prevent the condensed water in 6 from flowing back into the scroll casing 18.

If the condensed water falls at the moment when the blower 11 stops operating (the moment when the blower stops), or if the condensed water falls due to the vibration of the vehicle and hits the rotating blower fan 16. An abnormal noise is generated in the blower fan 16. However, according to the present embodiment, the centrifugal blower fan 16 is covered with the winding start portion (nose portion) 18a of the scroll casing 18 to cover the upper portion of the centrifugal blower fan 16 and the centrifugal blower fan 16 is Since it is not exposed, it is possible to prevent the condensed water from hitting the rotating blower fan 16 even if the condensed water falls, and it is possible to prevent the generation of abnormal noise.

(Second Embodiment) In the first embodiment, the evaporator 23 is inclined so that the front side becomes lower and the rear side becomes higher in the vehicle front-rear direction, but in the second embodiment,
As shown in FIG. 6, the evaporator 23 is inclined so that the front side becomes higher and the rear side becomes lower in the vehicle front-rear direction.

Therefore, in the second embodiment, the first drainage path 42 into which condensed water flows from the inclined lower end portion of the evaporator 23 located on the vehicle rear side is provided along the scroll outer peripheral shape on the vehicle rear side of the scroll casing 18. It is formed from top to bottom. The lowermost drainage hole 44 of the scroll casing 18, the bent plate member 45, the second drainage path 46, and the like are provided in the second embodiment as in the first embodiment.

(Third Embodiment) FIGS. 7 and 8 show a third embodiment. In the first and second embodiments, the evaporator 23 is inclined in the vehicle front-rear direction, but in the third embodiment, the evaporator 23 is inclined in the vehicle left-right direction as shown in FIG. 7.

More specifically, in the third embodiment, the evaporator 23 is inclined in the lateral direction of the vehicle so that the vehicle right side of the evaporator 23 becomes higher and the vehicle left side of the evaporator 23 becomes lower.

Therefore, in the third embodiment, both the direction of the rotary shaft 19 of the blower 11 and the inclination direction of the evaporator 23 are arranged so as to be directed in the vehicle left-right direction. In the third embodiment, since the inclination direction of the evaporator 23 is the vehicle left-right direction, the evaporator 23 is arranged so that the tube longitudinal direction C (see FIG. 4) of the evaporator 23 faces the vehicle left-right direction. It

Since the third embodiment is applied to the right-hand drive vehicle, the air suction duct 14 is arranged on the left side (passenger seat side) of the indoor unit 10.

Next, the drainage path of the condensed water according to the third embodiment will be described. In the case 31, a plate-shaped drainage which abuts on the lower side surface of the heat exchange core portion of the evaporator 23 in the vicinity of the inclined lower end portion. The promotion guide 43 is integrally provided so as to extend in the vehicle front-rear direction. Since the drainage promotion guide 43 extends in the vehicle front-rear direction, a drainage port 43a corresponding to the drainage port 43a of FIG. 5 is formed at both ends in the vehicle front-rear direction of the upper end portion of the drainage promotion guide 43 in this example.

On the lower inclined side of the evaporator 23 (left side of the vehicle), the drainage path 5 extending in the vehicle front-rear direction is located outside the drainage promotion guide 43 (left side of the vehicle) as shown in FIG.
Forming 2. The condensed water attached to the upper end of the drainage promotion guide 43 flows into the drainage path 52 from the drainage ports 43a at both ends in the vehicle front-rear direction.

As shown by the broken line in FIG. 8, the drainage path 52 is inclined so that the vehicle rear side is high and the vehicle front side is low. The lowermost portion of the drainage path 52 on the vehicle front side communicates with the first drainage path 42 through a communication hole 53. Therefore, the condensed water in the drainage path 52 flows into the first drainage path 42 from the communication hole 53.

The first drainage path 42 is the same as in the first and second embodiments, and the condensed water in the first drainage path 42 passes through the second drainage path 46 and is discharged outside the vehicle in the engine room 49. Be drained. Condensed water on the bottom of the scroll casing 18 of the blower 11 is drained through the drain hole 44 and the bent plate member 45.
Is drained from the drainage route 44a through the second drainage route 46.

By the way, the air suction duct 14 has
Rainwater from the outside air inlet 20a at the upper end, water for car washing,
Since snow or the like in the winter may invade, it is necessary to discharge the invading water. Therefore, in the third embodiment, the drain hole 54 is provided at the lowermost portion of the air suction duct 14, and the drain hole 54 is communicated with the lower portion of the first drainage path 42.

Therefore, even if water such as rainwater enters the air suction duct 14 through the outside air introduction port 20a, the water M accumulated at the bottom of the air suction duct 14 is discharged from the drain hole 54 to the first drainage path 42, and then to the first drainage path 42. 2 The water can be quickly discharged to the outside of the vehicle through the drainage route 46.

(Fourth Embodiment) FIG. 9 shows a fourth embodiment, which is a modification of the first embodiment. In the fourth embodiment,
The bending plate member 45 of the first embodiment is eliminated. By eliminating the bent plate member 45, air leakage from the scroll casing 18 through the drainage hole 44 is likely to occur and the air blowing performance is deteriorated. However, by eliminating the bent plate member 45, the vertical dimension of the indoor unit 10 can be reduced.

Further, in the fourth embodiment, the second drainage path 46
10 is longer than that of FIG. 10 (fifth embodiment) described later, and when the second drainage path 46 is long in this way, if the second drainage path 46 is inclined at a predetermined angle θ1. The vertical space for disposing the second drainage path 46 is increased, and thus the vertical space of the indoor unit 10 is increased. Therefore, in the fourth embodiment, the second drainage route 46 is arranged in the horizontal direction without setting the inclination of the predetermined angle θ1 in the second drainage route 46.

Then, the drainage hole 44 is set at a position higher than the second drainage path 46 by a predetermined amount h, and the downstream path of the drainage hole 44 is connected to the tapered step portion 55 so as to be horizontally directed to the vehicle front side. The tapered step portion 55 communicates with the second drainage path 46. Here, the tapered step portion 55 forms an inclined surface directed obliquely downward toward the vehicle front side at a predetermined angle,
In addition, the step portion 55 is the condensed water drop point a of the first drainage path 42.
Is connected to the second drainage path 46 at a portion c on the drainage hole 44 side (a portion on the vehicle rear side) with respect to a vertical line L3 passing through. A line L5 is a line connecting the points c and a, and an angle θ3 is an angle formed by the line L5 and the vertical line L3.

As described above, when the vehicle is not inclined in the front-rear direction, the condensed water directly drops from the lower part of the first drainage path 42 into the second drainage path 46 on the downstream side of the step portion 55,
Even if the vehicle leans in the front-rear direction, the first drainage path 42
Condensed water falls on the step portion 55 from below. Therefore, even if the second drainage path 46 is arranged in the horizontal direction,
The step portion 55 can reliably prevent the water in the first drainage path 42 and the second drainage path 46 from flowing back into the scroll casing 18.

(Fifth Embodiment) FIG. 10 shows a fifth embodiment, which is a modification of the fourth embodiment. In the fifth embodiment, the length of the second drainage route 46 is shorter than that in FIG. 9 (the fourth embodiment), and therefore the second drainage route 46 is used.
Is set to a predetermined angle θ1. That is, when the length of the second drainage path 46 is short, even if the second drainage path 46 itself is inclined at a predetermined angle θ2, the indoor unit 10
Since the increase in the vertical dimension of the can be reduced, it is not a problem. The angle θ2 is the angle θ in FIG. 1 (first embodiment).
It is set in the same way as in 2. Both the angles θ1 and θ2 are set to 15 ° or more in consideration of the inclination (15 °) in the front-rear direction of the vehicle.

(Sixth Embodiment) FIG. 11 shows a sixth embodiment, which is a modification of the fifth embodiment. In the sixth embodiment, the lower part of the first drainage path 42 is bent from the surface of the scroll casing 18 on the vehicle front side toward the vehicle front side, and is connected to the upstream end of the second drainage path 46. .
In addition, the drainage hole 44 at the bottom of the scroll casing 18
Is connected to the upstream end of the second drainage path 46 via a drainage path 44b that extends horizontally from the vehicle rear side toward the vehicle front side.

Here, the upstream end of the bottom slope of the second drainage path 46, that is, the coupling angle between the bottom of the drainage path 44b from the scroll casing 18 and the upstream end of the bottom slope of the second drainage path 46. The portion b is formed at a portion on the drain hole 44 side (a portion on the vehicle rear side) at an angle θ2 with respect to the vertical line L3 passing through the condensed water drop point a of the first drainage path 42. The inclination angle θ1 of the second drainage route 46 and the second drainage route 46
The angle θ2 that determines the upstream end position of the bottom inclined surface of
It is set to 15 ° or more in consideration of the inclination (15 °) in the front-rear direction of the vehicle.

As described above, also in the sixth embodiment, the water in the first drainage path 42 and the second drainage path 46 is transferred to the scroll casing 1 in the same way as in the first and fifth embodiments.
It is possible to surely prevent the backflow into the inside.

[Brief description of drawings]

FIG. 1 is a side sectional view of a main part of an indoor unit section according to a first embodiment of the present invention.

FIG. 2 is a front view of the indoor unit section according to the first embodiment as viewed from the vehicle interior side.

FIG. 3 is a side view of the indoor unit section according to the first embodiment.

FIG. 4 is a front view illustrating the evaporator according to the first embodiment.

FIG. 5 is an upper front view of the drainage promotion guide according to the first embodiment.

FIG. 6 is a side sectional view of a main part of an indoor unit section according to a second embodiment.

FIG. 7 is a front sectional view of a main part of an indoor unit section according to a third embodiment.

FIG. 8 is a side sectional view of a main part of an indoor unit section according to a third embodiment.

FIG. 9 is a side sectional view of a main part of an indoor unit section according to a fourth embodiment.

FIG. 10 is a side sectional view of a main part of an indoor unit section according to a fifth embodiment.

FIG. 11 is a side sectional view of an essential part of an indoor unit section according to a sixth embodiment.

[Explanation of symbols]

10 ... Indoor unit part, 11 ... Blower, 14 ... Air suction duct, 16 ... Blower fan, 17 ... Drive motor,
18 ... Scroll casing, 23 ... Evaporator (cooling heat exchanger), 42 ... First drainage path, 44 ... Drainage hole, 46 ...
Second drainage route.

Claims (8)

[Claims] 1. A blower (11) for blowing air, and a cooling heat exchanger (23) for cooling blown air of the blower (11), wherein the cooling heat is provided above the blower (11). Exchanger (2
3) is arranged and a drain hole (44) for draining water in the blower (11) is provided in the lower part of the blower (11) to drain condensed water from the cooling heat exchanger (23). A vehicle air conditioner characterized in that the drainage hole (44) is communicated with a main drainage path (42, 46). 2. The first drainage path (42) for draining condensed water from the cooling heat exchanger (23) as the main drainage path.
And a second drainage path (4) which is connected to the downstream side of the first drainage path (42) and drains condensed water from the first drainage path (42) and water from the drainage hole (44) to the outside of the vehicle.
The vehicle air conditioner according to claim 1, wherein the vehicle air conditioner comprises: 3. The second drainage path (46) is inclined obliquely downward in the vehicle front-rear direction, and the inclination angle (θ1) of the second drainage path (46) is 15 °.
As described above, the second drainage path (46) is provided with respect to the vertical line (L3) passing through the condensed water drop point (a) of the first drainage path (42).
The upper end position (b) of the bottom inclined surface of the is located on the drain hole (44) side, the line (L4) connecting the upper end position (b) and the condensed water drop point (a), and the vertical line (L3). ) And the angle (θ2)
3. The vehicle air conditioner according to claim 2, wherein the angle is 15 ° or more. 4. The second drainage path (46) is disposed substantially horizontally, the drainage hole (44) is located at a position higher than the second drainage path (46) by a predetermined amount, and the drainage hole ( 44) is the second drainage path (46) via the step portion (55) for preventing backflow.
The air conditioner for a vehicle according to claim 2, which is in communication with the air conditioner. 5. A drainage path (44) for the drainage hole (44).
The vehicle air conditioner according to any one of claims 1 to 4, wherein a) has a maze structure for suppressing air leakage from the blower (11). 6. A drain hole (54) for draining water in the duct (14) is provided in a lower portion of a suction duct (14) of the blower (11), and the drain hole (54) is provided in the main drain path. The vehicle air conditioner according to any one of claims 1 to 5, which communicates with (42, 46). 7. A blower (11) for blowing air, and a cooling heat exchanger (23) for cooling blown air of the blower (11), wherein the cooling heat is provided above the blower (11). Exchanger (2
3) is arranged, a drain hole (44) for draining water in the blower (11) is provided in the lower part of the blower (11), and a drainage path (44a) of the drain hole (44) is provided in the blower. (11) A vehicular air conditioner having a maze structure that suppresses air leakage from the inside. 8. The blower (11) is configured such that the maze structure is directed downward from a portion of the drain hole (44) on the blower front side in a direction substantially perpendicular to a blower direction in the blower (11).
L-shaped bent plate member (4
5) The vehicle air conditioner according to claim 5 or 7, characterized in that