JP2001213142A - Air conditioner unit for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air conditioner unit for a vehicle capable of making uniform the velocity of air passing through a cooling heat exchanger and preventing a back flow of condensed water. SOLUTION: A cooling heat exchanger 13 is disposed in a unit case 11 on the lower side and a heating heat exchanger 15 is disposed therein on the upper side. The cooling heat exchanger 13 is disposed in the unit case 11 with the air passing surface thereof inclined in either side of the longitudinal direction of a vehicle relative to the bottom surface 20 thereof, and an air inlet port 12 is formed in the side wall lower part of the unit case 11 positioned at one side of the vehicle in lateral direction so as to open the generally entire surface of the side surface of a space formed of the cooling heat exchanger 13 and the bottom surface 20. Air is blown through the air inlet port 12. A projected part 21 having an air direction changing wall surface 22 for changing the flow of air led from the area of the air inlet port 20 longer in opening height dimension to a direction aslant relative to the forward of the air leading direction is installed vertically on the side slightly forward of the center of the bottom surface 20 in the air leading direction so as to increase the velocity of air passing through the center of the cooling heat exchanger and, a plurality of projected ribs 32 are arranged so as to suppress the backflow of the condensed water.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioning unit for a vehicle, and more particularly, to a cooling heat exchanger and a heating heat exchanger, and air is blown from the intake unit to the cooling heat exchanger. The present invention relates to an air conditioning unit for a vehicle.

[0002]

2. Description of the Related Art Conventionally, as shown in FIG. 17, a cooling heat exchanger 1 and a heating heat exchanger 2 are connected to each other in order to increase a foot space in a vehicle compartment and to reduce materials, manufacturing and assembly costs. There is a vehicle air conditioner unit 3 arranged in the up-down direction. In the air conditioning unit 3 for a vehicle, air is sent to the cooling heat exchanger 1 from an intake unit (not shown) through an air inlet 4 having a substantially triangular shape formed in a lower part of the side surface of the unit. In the vehicle air conditioner unit 3 shown in FIG. 17, an opening / closing door 5 is disposed between the cooling heat exchanger 1 and the heating heat exchanger 2. This opening and closing door 5
The amount of air that passes through the heating heat exchanger 2 and the amount of air that is introduced directly downstream of the heating exchanger 2 are controlled. The cooling heat exchanger 1 is arranged in the unit case 6 in an inclined state as shown in FIG.
Supported. FIG. 18 is a perspective explanatory view showing the vehicle air-conditioning unit 3 that has been made more compact.
The vehicle air-conditioning unit 3 shown in FIG. 17 has a configuration in which the opening / closing door 5 of the vehicle air-conditioning unit 3 shown in FIG. 17 is replaced with a sliding door 7, and achieves space saving in the vertical direction.

[0003]

However, the air introduced from the air inlet 4 of the air conditioning unit 3 for a vehicle described above has a large air inlet 4 because the cooling heat exchanger 1 is inclined. Due to the action of the air blown from the part and the air blown from the narrow part, there is a problem that the pressure of the air blow to the lower surface of the cooling heat exchanger 1 becomes uneven.

That is, the unit case 6 shown in FIG.
When the air blowing state on the bottom surface 8 of the air inlet is viewed in a plan view, as shown in FIG. 19, the flow of the air introduced from the wide opening of the air inlet 4 and the flow of the air introduced from the narrow opening are changed. A counterclockwise swirling flow is generated in the figure due to the quantitative difference and the asymmetrical ventilation resistance between the engine room side and the vehicle room side of the space below the cooling heat exchanger 1. . For this reason, the center of the cooling heat exchanger 1 is a position corresponding to the center of the swirling flow, and the air pressure decreases at the center of the cooling heat exchanger 1 so that the wind does not easily pass through.

As shown in FIG. 19, the air introduced from the position A collides with the case side wall at the position B, and the pressure increases.

Further, at a position D shown in FIG. 19, the air introduced from the narrow opening of the air inlet 4 collides with the air introduced from the wide opening and swirled, so that the pressure is increased. In the figure, the stippling area indicates the area where the pressure has increased. FIG. 20 shows the relationship between each position A to E on the case bottom surface 8 and the height from the case bottom surface 8 to the lower surface of the cooling heat exchanger 1, and the cooling heat exchanger 1 at each position.
Shows the state of the wind passing through. As shown in the figure,
The area from position B to position C and the position D where the winds collide with each other
It can be seen that the amount of air passing through the cooling heat exchanger 1 increases.

[0007] As described above, if the air flow through the cooling heat exchanger 1 becomes non-uniform, adverse effects such as a decrease in the amount of heat exchange in the cooling heat exchanger 1 and a deterioration in space harmony characteristics are caused. There was a problem of giving.

As shown in FIG. 19, the unit case is provided with a drain pipe 9 at a lower position opposite to the space introduction port 4 and at the bottom of the engine room or at the lower part of the side wall. By this drain pipe 9, condensed water generated in the cooling heat exchanger 1 is discharged to the engine room side.

However, as shown in FIG.
Since the air introduced above generates a swirl flow, the condensed water W tends to stagnate at the position C due to the effect of the swirl flow, and there is a problem that the drainage efficiency to the drain pipe 9 is reduced. The condensed water W stagnated on the case bottom surface 8 may flow into the intake unit side depending on the running state of the vehicle, for example, a turning state in which centrifugal force acts, and it is feared that the condensed water W may impede the blower side. ing.

In view of the above, the present invention has been made in consideration of the above-described circumstances, and has a structure in which the pressure of air passing through the cooling heat exchanger is made uniform and the backflow of condensed water accumulated at the bottom of the unit case is reduced. It is an object of the present invention to provide an air conditioning unit for a vehicle that suppresses the drainage and has good drainage efficiency.

[0011]

According to the first aspect of the present invention,
In the unit case, the heat exchanger for cooling is arranged on the lower side, and the heat exchanger for heating is arranged on the upper side. And a substantially entire side surface of a space formed by the cooling heat exchanger and the bottom surface is opened at a lower portion of the side wall of the unit case located on one side in the vehicle width direction. An air conditioning unit for a vehicle in which an air inlet is formed so that air is blown through the air inlet, and a flow of air introduced from a region having a long opening height of the air inlet. The air flow direction changing wall that changes obliquely with respect to the front of the air introduction direction is erected at a position slightly forward of the center of the bottom surface in the air introduction direction, and the flow of the introduced air flowing around the back side of the wind direction changing wall surface. Equipped with road space A drain inlet is opened on the bottom surface located at the end of the flow passage in the flow passage space, and a plurality of low-height holes are provided on the bottom surface between the wind direction changing wall surface and the unit case side wall on the other side in the vehicle longitudinal direction. Are protrudingly provided.

According to the first aspect of the present invention, the air flow introduced from a region having a large opening height of the air inlet (a region having a wide opening) is provided upright on the bottom surface of the unit case. Since the air impinges on the wind direction changing wall surface and is guided obliquely with respect to the air introduction direction, the air pressure is increased at a position slightly in front of the wind direction changing wall surface, that is, in a region passing through the center of the bottom surface. As a result, the wind speed of the air passing through the center of the cooling heat exchanger can be increased.

According to the first aspect of the present invention, the air flow introduced from a region where the opening height of the air inlet is short (a region where the opening is narrow) is a wind direction changing wall provided on the bottom surface of the unit case. Without being hit by the wind direction changing wall, the wind merges with the wind whose direction is changed, meanders along the back side of the wind direction changing wall, and hits one case side wall in the vehicle front-rear direction to increase the pressure. As a result, it is possible to increase the pressure of the air from the region where the air joins to the region corresponding to the case side wall, and it is possible to increase the wind speed of the air passing through the region of the cooling heat exchanger corresponding to these regions. In addition, the wind speed of the air passing through the cooling heat exchanger can be made uniform. In particular, in the present invention, since the air flow flowing on the bottom surface meanders, condensed water is guided along the meandering, and the condensed water can be easily guided to the drain inlet.

Further, according to the first aspect of the present invention, the kinetic energy of the backflow can be reduced by diffusing the flow of the condensed water at the protruding ribs and joining them. Specifically, the backflow is divided at regular intervals by the protruding ribs in a direction perpendicular to the flow, and the width of each divided flow is narrowed by the opposing protruding rib surfaces to raise the water surface. In other words, the kinetic energy of the backflowing water is converted into potential energy for lifting the water surface to attenuate the flow velocity in the backflow direction and suppress the flow of condensed water toward the air inlet.

After the backflow has passed the first row of projecting ribs,
A plurality of water flows that flow out at equal intervals from between the protruding ribs in the first row, but the second rib row further divides these water flows into a pair of diffusion flows, and each of the separated flows flows in the adjacent rib. Similarly, it merges with the separated flow and is narrowed by the opposing protruding rib surfaces.

According to a second aspect of the present invention, in the air conditioning unit for a vehicle according to the first aspect, the protruding rib has a pyramid shape.

Further, the invention according to claim 3 is the invention according to claim 1.
The air conditioning unit for a vehicle according to claim 1, wherein the projecting rib has a hemispherical shape.

Therefore, according to the second and third aspects of the invention, in addition to the operation of the first aspect, for example, the inclination angle of the bottom surface, the width of the bottom surface, and the bottom surface and the lower surface of the cooling heat exchanger. It is possible to appropriately set the shape and structure of the protruding rib according to the distance between the ribs. Moreover, in the pyramid shape, by setting the angle of the side surface facing the air inlet, it is possible to slightly increase the pressure of the air introduced from the air inlet and increase the wind speed passing through the cooling heat exchanger. .

According to a fourth aspect of the present invention, in the air conditioning unit for a vehicle according to the first aspect, the projecting rib includes a splitter portion and a rib portion erected adjacent to the splitter portion. It is characterized by consisting of

According to a fourth aspect of the present invention, in addition to the operation of the first aspect, the condensed water is divided and dispersed by the splitter portion, and the condensed water is stored between the splitter portion and the rib portion. Has an action. Therefore, the backflow of the condensed water can be suppressed.

[0021] Further, the invention according to claim 5 is the invention according to claim 1.
5. The vehicle air conditioning unit according to claim 4, wherein the protruding rib includes a side surface that is gently inclined toward the air inlet.

Therefore, according to the fifth aspect of the present invention, in addition to the effects of the first to fourth aspects of the present invention, it is possible to prevent the condensed water from jumping upward when the backflow of the condensed water passes over the projecting rib. It has the effect of suppressing.

According to a sixth aspect of the present invention, there is provided the air conditioning unit for a vehicle according to any one of the first to fifth aspects, wherein the protruding ribs are arranged in a row along the longitudinal direction of the vehicle. A plurality of rows are arranged so that the rows are parallel to each other in the vehicle width direction, and the rows adjacent to each other are arranged in a staggered manner with a shift of a half pitch in the vehicle front-rear direction.

Therefore, according to the sixth aspect of the invention, in addition to the effects of the first to fifth aspects of the present invention, since the plurality of projecting ribs are arranged in a staggered manner, they are dispersed around the projecting ribs. The flow of condensed water hits the projecting ribs of the next row and is dispersed again, and at the same time, merges, so that kinetic energy is reduced more efficiently.

[0025]

According to the first aspect of the present invention, the pressure of the introduced air is increased by the wind direction changing wall surface, so that the wind speed of the air passing through the center of the cooling heat exchanger can be increased. This has the effect of equalizing the wind speed of the air passing through the heat exchanger. According to the first aspect of the present invention, since the airflow flowing on the bottom surface meanders, the condensed water is guided along the meandering, and the condensed water is guided to the drain inlet to improve drainage efficiency. . Furthermore, according to the first aspect of the present invention, there is an effect that the backward flow of the condensed water is reduced to prevent the condensed water from flowing toward the air inlet.

According to the second and third aspects of the present invention, in addition to the effect of the first aspect of the present invention, the degree of freedom in designing the projecting rib can be increased. That is, by selecting an appropriate projecting rib shape, it is possible to arbitrarily adjust the air resistance generated when air collides with the projecting rib. In particular, since the air that collides with each protruding rib passes through the gap between the ribs, the air resistance is small even if the height of the protruding rib is increased, and the rise in ventilation resistance due to countermeasures against water backflow can be reduced. . Conversely, when obtaining a pressure increase due to the protruding rib air resistance, the protruding rib shape may be set so that a surface orthogonal to the air flow is enlarged.

According to the fourth aspect of the invention, in addition to the effect of the first aspect of the invention, there is an effect of suppressing the backflow of the condensed water.

According to the invention described in claim 5, claims 1 to
In addition to the effect of the invention described in claim 4, there is an effect of suppressing the condensed water from jumping upward when the backflow of the condensed water gets over the projecting rib. In the plate-like ribs standing vertically from the bottom surface as seen in the prior art, when the backflow collides, water scatters upward along the surface of the colliding ribs. The dividing and narrowing positions rise gently and do not scatter.

According to the sixth aspect of the present invention, the first to fifth aspects are provided.
In addition to the effect of the invention according to claim 5, since the plurality of protruding ribs are arranged in a staggered manner, the flow of condensed water dispersed at the protruding ribs as a boundary hits the next row of protruding ribs and is again dispersed. At the same time, there is an effect that the kinetic energy is reduced more efficiently by merging.

[0030]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The details of an air conditioning unit for a vehicle according to the present invention will be described below based on an embodiment shown in the drawings.

Hereinafter, the details of the vehicle air conditioning unit according to the present invention will be described with reference to the embodiments shown in FIGS.

FIG. 1 is a side sectional view showing a state in which the vehicle air conditioning unit 10 of the present embodiment is cut along a plane passing through the vertical direction and the vehicle front-rear direction, and FIG.
FIG. 2 is a front sectional view showing a state where 0 is cut along a plane passing through a vertical direction and a vehicle width direction. 1 and 2, reference numeral 11 indicates a unit case. The unit case 11 is
It consists of a case lower half 11A and a case upper half 11B.
FIG. 3 is a perspective view of the lower case half 11A, and FIG. 4 is a plan view schematically showing the lower case half 11A. The case lower half 12 has an air inlet 12 formed on one side (side wall) in the vehicle width direction for introducing air sent from a blower (not shown).

The vehicle air conditioner unit 10 includes a cooling heat exchanger (evaporator) 13 disposed at a lower part in the unit case 11 so as to be inclined forward toward the cabin, and a downstream side of the cooling heat exchanger 13. Sliding door device 14 disposed on the side (upper side), and a heat exchanger (heater core) 1 for heating disposed downstream (upper side) of the sliding door device 14
5 and opening and closing doors 16 and 17 disposed downstream (upper side) of the cooling heat exchanger 13 and the heating heat exchanger 15.

The sliding door device 14 is configured such that the air passing through the cooling heat exchanger 13 passes through the heating heat exchanger 15 and the cross-sectional area of the flow path passes through the cooling heat exchanger 13. The cross-sectional area of the flow path directly guided to the downstream side of the vessel 15 is controlled. The cooling heat exchanger 13
Is composed of a refrigerant pipe through which a refrigerant flows and a number of fins (all are not shown).

As shown in FIG. 1, a front portion of the cooling heat exchanger 13 in the vehicle longitudinal direction is supported by a bracket 18 on an upper half portion 11B of the case, and a rear portion of the cooling heat exchanger 13 is a lower portion of the case. It is placed and fixed on the step 19 of the half 11A. As shown in FIG. 3, the structure of the step portion 19 is such that a plurality of ribs 28 are vertically arranged in the vehicle width direction in the vicinity of the air inlet 12 on the inner surface of the case wall portion 27 on the rear side in the vehicle front-rear direction. Are formed at predetermined intervals.

The space between the ribs 28 functions as a groove for flowing water. In the case wall portion 27, a portion between the rib 28 and the case wall portion 29 located on the opposite side to the air inlet 12 is provided along the vertical direction on the inner side surface of the step portion 19 </ b> A. Is formed at a predetermined pitch in the vehicle width direction. Therefore, the cooling heat exchanger 13 is placed on the step 19 having such a structure.
When the fixing is performed with the edge of the cooling heat exchanger 13 placed thereon, the condensed water generated at the edge of the cooling heat exchanger 13 falls to the below-described bottom surface 20 between the ribs 28 or through the slit 19B. It has become.

Further, at the rear of the cooling heat exchanger 13 and between the lower case half 11A and the cooling heat exchanger 13
The seal packing 13A is attached so as to be flush with the downstream surface in the air flow direction. In this case, the seal packing 13 is flush with the downstream surface in the air flow direction.
By attaching A, there is no generation of a water storage space in which condensed water discharged from the downstream side of the cooling heat exchanger 13 accumulates.

Also, in the unlikely event that the step portion 19 and the condensed water stored therein are extended in the vehicle width direction, the step portion 19 is provided at least on the side wall facing the air inlet. Since a gap or a notch directed toward the drain guide side is provided between the side wall and the side wall, drainage is possible. Further, in the structure shown in FIG.
The condensed water stored in 9A is passed through a slit 19B.
Drains smoothly.

The cooling heat exchanger 13 communicates with a compressor (not shown), a condenser, and an expansion valve, and the refrigerant discharged from the compressor passes through the condenser and the expansion valve, and becomes a cooling evaporator. A refrigeration cycle that returns from the heat exchanger 7 to the compressor again is configured.

As shown in FIG. 1, the heating heat exchanger 15 is supported on the case side wall on the engine room side and on both side walls in the width direction above the cooling heat exchanger 13 and the slide door device 14. Further, the heating heat exchanger 15 is configured so that heated water heated by an engine (not shown) flows, and heat is exchanged to heat the air when the air passes through the heat exchanger body. It has become.

As shown in FIG. 1, the air inlet 12 is formed in a substantially triangular shape with a high height on the front side and a low height on the rear side. The cooling heat exchanger 13 is disposed and fixed so as to face the bottom surface 20 of the lower case half 11A in a state of being inclined forward. In addition, the bottom surface 20 is formed so as to be gently inclined so as to gradually decrease from the air introduction port 12 toward the air introduction direction a.

A substantially triangular prism-shaped ridge 21 for meandering the air flow is provided on the bottom surface 20. As shown in FIG. 4, the jetty portion 21 forms a predetermined obtuse angle θ toward the rear side in the vehicle front-rear direction with respect to the direction a of the introduced airflow introduced from the air introduction port 12 side. 22. The wind direction changing wall surface 22 is disposed forward of the direction of the introduced airflow a from the center of the bottom surface 20, and the air introduced from the air inlet 12 collides with the wind direction changing wall surface 22 to change the wind direction in FIG. The direction is changed to the left (substantially the rearward direction of the vehicle).

A drain pipe 23 is provided on the bottom surface 20 near the front lower portion of the front wall 25 of the lower case half 11A in the direction a of the introduced air flow, and the drain pipe 23 is provided on the bottom surface 20 in the direction a of the introduced air flow. In the vicinity of the front side edge, there is formed a drain guide groove portion 24 that is gently inclined downward toward the drain pipe 23 side.

Further, as shown in FIGS.
In the vicinity of the zero air inlet 12, a dam portion 30 is formed to prevent condensed water from flowing back to a blower (not shown),
A groove 31 is formed at the center of the dam portion 30 for returning the water flowing back over the dam portion 30 to the bottom surface 20 side.

As shown in FIG. 1, the jetty 21 is formed such that its height is high on the front wall 25 side of the lower case half 11A and gradually decreases from the front wall 25 side to the vertex 26 located rearward. Have been. In addition, as shown in FIG. 4, the vertex 26 of the triangle on the rear side of the jetty 21 is set to be located slightly behind the center of the bottom surface 20. A gap 29 is formed between the front wall 25 and the ridge 21 so that the air inlet 12 side is narrowed. This gap 29
Is a passage through which condensed water flows to the drain pipe 23 side.

As shown in FIGS. 2 to 4, a plurality of protruding ribs 32 having a triangular pyramid shape are provided in a region between the ridge 21 on the bottom surface 20 and the case side wall located on the rear side in the vehicle longitudinal direction. They are arranged in a predetermined arrangement. This protruding rib 3
As shown in FIG. 4, two rows of the protruding ribs 32, 32 arranged in the vehicle front-rear direction are arranged in three rows in the vehicle width direction, and rows adjacent to each other are arranged by being shifted by a half pitch. ing. The projecting rib 32 is formed such that a side surface 32A facing the air inlet 12 is substantially perpendicular to the bottom surface 20.

The vehicle air-conditioning unit 10 having such a structure has the following operation. As shown in FIG. 5, in the space below the cooling heat exchanger 13, that is, in the lower case half 11 </ b> A, the space introduced from the space inlet 12 blows at a flow rate corresponding to the opening height of the space inlet 12. . Here, the air flow introduced from the position A2 where the height of the air inlet 12 is high goes straight in the vehicle width direction, hits the wind direction changing wall surface 22 of the jetty 21 at the position A3, and is obliquely along the wind direction changing wall surface 22. Flow backward. At this time, in the vicinity of the wind direction changing wall surface 22, the wind speed of the airflow passing through the cooling heat exchanger 13 arranged above and increasing is increased. Position A
The airflow that has proceeded from position 3 to position A4
It hits the rear side wall of the (case lower half 11A), merges with the air introduced from the low position A1 of the air inlet 12 and goes straight ahead, flows to the position A5, and hits the side wall of the case lower half 11A. It flows toward position A6.

Therefore, the air flow flowing from the position A 2 meanders around the jetty 21 and flows toward the drain pipe 23. Further, unlike the conventional case, the air flows do not collide with each other, energy loss is eliminated, and ventilation resistance can be reduced. Further, the wind speed of the airflow passing through the center of the cooling heat exchanger 13 can be increased, and as a result, the wind speed of the airflow passing through the cooling heat exchanger 13 can be made uniform.

FIG. 6 is a diagram showing the state of the airflow passing through the cooling heat exchanger 13 at the positions A2 to A6. The air introduced from the position A2 of the air inlet 12 is
Cooling heat exchanger 1 pressurizes against wind direction changing wall surface 22
The wind speed passing through the position 3 becomes faster between the position A3 and the position A4. At the positions A5 and A6, the air hits the side wall and the air hits the side surface 32A of the protruding rib 32 to increase the pressure. For this reason, the wind speed of the air passing through the portion of the cooling heat exchanger 13 corresponding to the position A4 to the position A5 increases. The air introduced from the position A1 is pressurized because the space between the air and the cooling heat exchanger 13 is narrow, and the wind speed in the space passing through the cooling heat exchanger 13 is increased. When these actions are combined, the wind speed in the space passing through the cooling heat exchanger 13 becomes uniform.

In this embodiment, the case lower half 11
A jetty 2 so that the air pressure becomes high at the center of the bottom surface 20 of A
By forming 1 and meandering the air flow, the wind flows toward the drain pipe 23 side, and thus has an effect of guiding condensed water accumulated on the bottom surface 20 to the drain pipe 23. Therefore, the condensed water can be efficiently discharged to the drain pipe 23 side.

Further, in this embodiment, a plurality of triangular pyramid-shaped projecting ribs 32 are arranged in a staggered manner in a region between the jetty 21 on the bottom surface 20 and the case side wall located on the rear side in the vehicle longitudinal direction. For example, when condensed water in the drain guide groove portion 24 is going to flow backward toward the air inlet 12 when the vehicle performs a centrifugal force operation such as a turning operation, FIG. As shown, the protruding ribs 32 scatter the flow of the condensed water and combine them to reduce the kinetic energy of the condensed water. At the same time, as shown in FIG. 8, in the present embodiment, the condensed water passes over the protruding ribs 32, converting kinetic energy into potential energy, reducing the backflow momentum, and the air inlet 1.
Backflow to the second side can be suppressed.

(Modification 1 of Projecting Rib) Next, FIG. 9 shows Modification 1 of the projecting rib formed on the bottom surface 20 of the lower case half 11A of the air conditioning unit 10 for a vehicle according to the above-described embodiment. Will be explained.

In the first modification, the area between the ridge 21 on the bottom surface 20 of the lower case half 11A and the case side wall located on the rear side in the vehicle front-rear direction, or the entire area except the drain guide groove 24 on the bottom surface 20A. A plurality of protruding ribs 33 each having a quadrangular pyramid shape as shown in FIG. A plurality of rows of these quadrangular pyramid-shaped projecting ribs 33 are arranged at substantially equal intervals, and the projecting ribs 33 of mutually adjacent rows are arranged so as to be shifted by a half pitch. The bottom surface of the protruding rib 33 is substantially square, and two diagonal lines thereof are set so as to substantially coincide with a vehicle width direction receiving centrifugal force when the vehicle turns and a vehicle front-rear direction. By forming such a protruding rib 33, similarly to the protruding rib 32 of the above-described embodiment, the condensed water flows are scattered and merged to reduce the kinetic energy of the condensed water. In the first modification, the condensed water passes over the protruding ribs 33, thereby converting the kinetic energy into potential energy and reducing the backflow momentum.
Backflow to the side can be suppressed.

(Modification 2) FIG. 10 is a plan view showing Modification 2 of the projecting rib according to the above-described embodiment. In this modified example 2, the area between the jetty 21 on the bottom surface 20 of the lower case half 11A and the case side wall located on the rear side in the vehicle front-rear direction or the entire area except the drain guide groove 24 on the bottom surface 20 is illustrated in FIG. A plurality of hemispherical projecting ribs 34 as shown in FIG. A plurality of rows of these hemispherical protruding ribs 34 are arranged at substantially equal intervals, and the protruding ribs 33 of rows adjacent to each other are arranged so as to be shifted by a half pitch. In the modified example 2 as well, similarly to the protruding ribs 32 of the above-described embodiment, there is an effect that the flow of the condensed water is scattered and merged to reduce the kinetic energy of the condensed water. Also in the second modification, the condensed water passes over the protruding ribs 34, thereby converting the kinetic energy into potential energy, reducing the backflow momentum, and suppressing the backflow to the air inlet 12 side. it can.

(Modification 3) FIG. 11 is a perspective view showing Modification 3 of the protruding rib according to the above-described embodiment. The protruding rib 35 is disposed in a region between the ridge 21 on the bottom surface 20 of the lower case half 11A and a case side wall located on the rear side in the vehicle front-rear direction, or in the entire region except for the drain guide groove 24 on the bottom surface 20. You. This projecting rib 35
It comprises a quadrangular pyramid-shaped splitter portion 35A having a low height, and a rib portion 35B having a substantially V-shaped planar shape erected along two adjacent side edges of the splitter portion 35A.
In the third modification, the height of the rib 35B is set higher than the height of the splitter 35A. And
One of the diagonal lines on the bottom surface of the splitter portion 35A is in the vehicle width direction X.
Is located downstream of the direction of the introduced air (indicated by the thick arrow in FIG. 11), and the rib 35B is located upstream of the direction of the air. Note that, as shown in FIG. 11, the rib portion 35B is formed so as to expand toward the downstream side in the air direction. Further, the height of the rib 35B and the height of the splitter 35A may be the same.

FIG. 12 is an arrangement example of the protruding rib 35 according to the third modification. In this arrangement example, the protruding ribs 35 are densely arranged so that the edges are adjacent to each other so as to face in the same direction.

Next, the operation when the condensed water flows in the direction of the thick arrow by the turn G will be described with reference to FIG. The condensed water flowing backward in the direction of the air is divided by the splitter section 35A, and is flowed obliquely rearward of the splitter section 35A. The condensed water that has flowed obliquely rearward in this manner is collected in a V-groove formed between the slopes of the splitter portion 35A and the rib portion 35B, as shown in FIG. 14 (a cross-sectional view taken along the line AA in FIG. 13). Can be The condensed water that is not stored in the protruding ribs 35 further moves to the protruding ribs 35 located diagonally rearward of the protruding ribs 35 and is stored between the slopes of the splitter portions 35A and the rib portions 35B of the protruding ribs 35. Can be By repeating such an operation, the condensed water W is dispersed while being stored in the entire projecting rib 35.

In the third modification, the splitter section 35A has a function of dividing and dispersing the condensed water, and the rib section 35B
Has a function as a dam for storing condensed water. Further, as shown in FIGS. 14 (a) and 14 (b), even when the rib portion 35B is inclined at α ° to the blower side in the vehicle width direction, the condensed water flows to the blower side because the rib portion 35B is higher than the splitter portion 35A. Does not flow easily and acts to increase the amount of water stored, and if it is inclined to the drain guide groove 24 side opposite to the blower side,
Drains smoothly.

The protruding rib 35 has the function of scattering the flow of the condensed water and merging it to reduce the kinetic energy of the condensed water. Also in this modified example 3, the condensed water is projected from the ribs (the splitter portion 35A and the rib portion 35B) 3
By moving over 4, the kinetic energy is converted into potential energy, the backflow momentum is reduced, and backflow toward the air inlet 12 can be suppressed. Also, the projecting rib 3
Even if the overall height of the plurality of projecting ribs 35 is set low.
As a whole, the functions of dispersing, merging, and storing the condensed water can be achieved. For this reason, there is almost no adverse effect on the air flow due to the provision of the protruding ribs 35. Such a protruding rib 35 can be easily formed by a mold that is die-cut in the vertical direction with respect to the bottom surface 20 when the case lower half 11A is molded. Note that such a protruding rib 35 may be separately formed and fixed to the bottom surface 20. Further, it is possible to integrally form the protruding rib 35 on a heat insulating material (insulator) incorporated in the lower case half 11A.

Although the embodiment has been described above, the present invention is not limited to this, and various changes accompanying the gist of the configuration are possible.

For example, in the above embodiment, the jetty 2
Although 1 has a substantially triangular prism shape, a rib-shaped plate having a wind direction changing wall surface 22 may be provided upright. Further, the protruding ribs 32, 33, 3 of the above-described embodiment and the first to third modifications.
In addition to the ribs 4 and 35, for example, as shown in FIG.
A protruding rib 36 made of 7B may be used. Further, as shown in FIG. 16, a protruding rib 37 composed of a quadrangular pyramid-shaped splitter 37A and a substantially V-shaped rib 37B may be used. Even when the protruding ribs 36 and 37 shown in FIGS. 15 and 16 are used, the same operation and effect as those of the above-described embodiment and Modifications 1 to 3 can be obtained. In addition, as the shape of the splitter portion, in addition to the above-described quadrangular pyramid shape, a shape such as a conical shape, a triangular pyramid shape, a prism shape, a cylindrical shape, or the like can be adopted. The planar shape of the rib portion may be a U-shape in addition to the above-described V-shape and U-shape, and the cross-sectional shape may be various shapes such as a rectangular cross-section in addition to a triangular cross-section. It is possible.

In the above-described embodiment, an example is shown in which a gap is provided between the adjacent protruding ribs 32, but this gap may be “0”.

Further, the projecting ribs 32 to 37 are
Or the entire area excluding the drain guide groove 24 or the entire area from the vertex 26 of the jetty 21 to the rear side in the vehicle front-rear direction and the bottom surface 20 on the air inlet side. In this case, the size of the protruding ribs 32, 33, and 34 may be easily affected by the introduction wind, and it is a matter of course that a smaller protruding rib may be provided.

[Brief description of the drawings]

FIG. 1 is a side sectional view showing an embodiment of a vehicle air conditioning unit according to the present invention.

FIG. 2 is a front sectional view of the vehicle air conditioning unit of the embodiment.

FIG. 3 is a perspective view showing a lower half of a case of the vehicle air conditioning unit of the embodiment.

FIG. 4 is a plan view of a lower half of a case of the air conditioning unit for a vehicle according to the embodiment.

FIG. 5 is an explanatory diagram showing a wind direction state and a moving direction of condensed water in the embodiment.

FIG. 6 is a diagram showing a wind direction state in the embodiment.

FIG. 7 is an explanatory plan view showing the operation of the protruding rib according to the embodiment.

FIG. 8 is an explanatory diagram showing a kinetic energy reducing action of the projecting rib of the embodiment.

FIG. 9 is a plan view showing Modification Example 1 of the protruding rib of the embodiment.

FIG. 10 is a plan view showing a modified example 2 of the protruding rib of the embodiment.

FIG. 11 is a perspective view showing a modified example 3 of the protruding rib of the embodiment.

FIG. 12 is a plan view showing an example of the arrangement of projecting ribs according to a third modification.

FIG. 13 is an explanatory plan view showing an operation of a protruding rib according to a third modification.

FIG. 14 is an explanatory cross-sectional view illustrating an operation of a protruding rib according to a second modification.

FIG. 15 is a plan view showing a modification of the protruding rib of the embodiment.

FIG. 16 is a plan view showing a modification of the protruding rib of the embodiment.

FIG. 17 is an explanatory view of a conventional air conditioning unit for a vehicle.

FIG. 18 is an explanatory perspective view of another conventional air conditioning unit for a vehicle.

FIG. 19 is an explanatory diagram showing a wind direction state of a conventional air conditioning unit for a vehicle.

FIG. 20 is a diagram showing a wind direction state of a conventional vehicle air conditioning unit.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Air conditioning unit for vehicles 11 Unit case 12 Air inlet 13 Heat exchanger for cooling 15 Heat exchanger for heating 20 Bottom (case bottom) 21 Jetty part 22 Wind direction changing wall surface 23 Drain pipe 32, 33, 34, 35, 36 , 37 Protruding rib W Condensate

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Osamu Kato 5-24-15 Minamidai, Nakano-ku, Tokyo Inside Calsonic Nick Kansei Corporation (72) Inventor Yoshitoshi Noda 5-24-15 Minamidai, Nakano-ku, Tokyo F term in Calsonic Kansei Corporation (reference) 3L011 BA02 BP02

Claims (6)

[Claims] 1. A cooling heat exchanger (13) is disposed on a lower side in a unit case (11), and a heating heat exchanger (15) is disposed on an upper side, and a bottom surface (2) of the unit case (11) is provided.
0), the cooling heat exchanger (13) is arranged so that the air passage surface is inclined in one direction in the vehicle front-rear direction, and the unit case (11) located on one side in the vehicle width direction. ), On the lower side wall of the cooling heat exchanger (13)
An air inlet (12) is formed so as to open substantially the entire side surface of a space formed by the base and the bottom surface (20), and the vehicle air to which air is blown through the air inlet (12). The air conditioning unit (10), wherein a wind direction changing wall surface (22) for changing a flow of air introduced from a region having a long opening height of the air introduction port (12) in an oblique direction with respect to a front of the air introduction direction. ) Is provided upright at a position slightly forward of the center of the bottom surface (20) in the air introduction direction, and a flow passage space is provided on the back side of the wind direction changing wall surface (22), where the introduced air flows around, and the flow passage space is provided. A drain inlet is opened at the bottom surface (20) located at the end of the flow path of the vehicle, and the bottom surface (2) between the wind direction changing wall surface (22) and the unit case side wall on the other side in the vehicle front-rear direction.
0) An air conditioning unit for a vehicle, wherein a plurality of protruding ribs (32) having a low height are provided on the upper surface thereof. 2. The air conditioning unit for a vehicle according to claim 1, wherein the protruding rib has a pyramid shape. 3. The air conditioning unit for a vehicle according to claim 1, wherein the projecting rib has a hemispherical shape. 4. The vehicle air conditioner unit (10) according to claim 1, wherein the projecting ribs (35, 36, 37) include a splitter portion (35A, 36A, 37A) and the splitter portion (3).
5A, 36A, 37A) and a rib portion (35B, 36B, 37B) erected adjacent to the vehicle air conditioning unit. 5. The air conditioning unit (10) for a vehicle according to claim 1, wherein the protruding ribs (32, 33, 34, 35, 36, 37).
The air inlet (1
2) An air conditioning unit for a vehicle, comprising a side surface that is gently inclined toward the side. 6. The air conditioning unit (10) according to claim 1, wherein the protruding ribs (32, 33, 34, 35, 36, 37).
Are arranged in a row along the vehicle front-rear direction, a plurality of rows are arranged so that the rows are parallel to each other in the vehicle width direction, and the adjacent rows are staggered by a half pitch in the vehicle front-rear direction. An air conditioning unit for vehicles, which is arranged in a shape.