JP3136534B2 - Automotive air conditioners - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner for a vehicle, and more particularly to an air conditioning unit for dividing an air passage into a first air passage and a second air passage.

[0002]

2. Description of the Related Art Conventionally, in an air conditioner for an automobile, an air passage of an air conditioning unit serving as an indoor unit is divided into a first air passage and a second air passage, and the temperatures of air flowing through both air passages are independently controlled. It is known that, by providing a temperature control mechanism for controlling, for example, the temperature of the face blown air blown upward in the vehicle compartment and the temperature of the foot blown air blown to the feet of the occupant in the vehicle compartment are independently controlled.

[0003] The inventors of the present invention have previously described Japanese Patent Application No.
Japanese Patent Application No. -264126 proposes a partition structure as shown in FIGS. 8 to 11 in order to partition the air passage of the air conditioning unit into a first air passage and a second air passage. In the configuration of this prior application, the air conditioning unit 1 is provided with a blower unit 2, a cooler unit 3, and a heater unit 4, and the blower unit 2 has inside air intake ports 6a, 6b, outside air intake port 7, and inside / outside air switching door 9a. , 9b, and two centrifugal fans 8a, 8
and an air blower 8 having a blower b, and the inside and outside air are switched into the air conditioning unit case 5 by the operation of the centrifugal fans 8a and 8b.

[0004] A cooler unit 3 disposed downstream of the blower unit 2 has an evaporator 11 of a refrigeration cycle.
The evaporator 11 cools the air. The cooling water (warm water) of the automobile engine flows into the heater unit 4 disposed downstream of the cooler unit 3 to heat the air.
The temperature control doors (air mix doors) 13a and 13b adjust the ratio between the air flow rate of the air (hot air) passing through the heater core 12 and the air flow rate of the air (cool air) not passing through (bypassing) the heater core 12. Then, the temperature of the blown air is controlled.

Further, at the downstream end of the air flow path of the heater unit 4, a foot outlet 14a for blowing air to the foot of the occupant in the vehicle compartment, a defroster outlet 14b for blowing air to the inner side of the vehicle front window, and a passenger in the vehicle cabin. A face outlet 14c for blowing air toward the head is provided, and these outlets 14a to 14c are connected to outlet mode doors 15a to 15c.
15c respectively open and close.

[0006] By disposing the partition plates 16, 17, 18, and 19 at the center of the air passage in the air conditioning unit case 5, the first air passage in the air conditioning unit case 5 communicating with the foot outlet 14a is formed. The air passage 10a and the second air passage 10b communicating with the defroster outlet 14b and the face outlet 14c are partitioned. The blown air of the two centrifugal fans 8a and 8b of the blower 8 is partitioned by partition plates 16 to 19, and the first and second blow paths 1 are mixed without being mixed.
Air is blown to 0a and 10b.

Therefore, by independently operating the temperature control doors 13a and 13b, the foot outlet 14a
And the outlet air temperature on the side of the defroster outlet 14b and face outlet 14c can be controlled independently. The downstream ends of the first air passage 10a and the second air passage 10b are provided with a communication port 14 for communicating the two.
d, and the communication port 14d is connected to the foot outlet door 1
It is opened in a face mode or the like in which the foot outlet 14a is closed by 5a.

By the way, in the device of the prior application, a structure for partitioning an air passage by the partition plates 16, 17, 18, and 19 is configured as shown in FIGS. 9 and 10 show a partition structure in the evaporator 11 portion. The evaporator 11 is provided with a large number of flat tubes 20 having a flat cross section through which the refrigerant of the refrigeration cycle flows. Are arranged in parallel with the direction of airflow of the conditioned air. And the partition plate 17,
The tubes 18 are arranged at both ends of the tube 20 on the upstream and downstream sides of the air so as to be located on the same line as the tube 20.

Similarly, the heater core 12 shown in FIG.
As shown in FIG. 1, partition plates 18 and 19 are arranged at both ends of the tube 29 having a flat cross section on the upstream and downstream sides of the air so as to be located on the same line as the tube 29. In FIG. 11, reference numeral 30 denotes a corrugated fin joined to the tube 29, and 31 denotes an inlet-side tank for distributing hot water to the tube 29, and has an inlet pipe 32. An outlet side tank 33 for collecting warm water from the tube 29 has an outlet pipe 34.

[0010]

In the apparatus of the prior application, with the above configuration, the air blower in the air-conditioning unit case 5 is formed by the combination of the partition plates 16, 17, 18, 19 and the heat exchanger tubes 20, 29. Although it is possible to partition the path into a first ventilation path 10a and a second ventilation path 10b, when the present inventors actually make a prototype and study it, the partitioning of the ventilation path is surely performed due to the dimensional variation of each part. It cannot be performed, and it has been found that there is a problem that the air between the two air passages 10a and 10b is mixed.

That is, in FIG.
If the size of 18 becomes large due to manufacturing variations, the end faces of the partition plates 17 and 18 will hit the end face of the tube 20, and the air conditioning unit case (usually composed of upper and lower two-part cases) 5 cannot be assembled. Would. Conversely, if the dimensions of the partition plates 17 and 18 are reduced due to manufacturing variations, even if the air conditioning unit case 5 can be assembled, the end faces of the partition plates 17 and 18 and the tubes 20
A gap A is formed between the two air passages 10a and 10b as shown by the arrow B through the gap A, and the air is mixed.

The mixing of the air is performed by the two air passages 10a and 10a.
Inhibits independent temperature control at b. Further, the first air passage 1
This impairs the so-called two-layer flow of inside and outside air, that is, the inside air flows separately on the 0a side and the outside air separately flows on the second air passage 10a side. Therefore, the present invention has been made in view of the above points, without being affected by dimensional variations in manufacturing the partition plate and the like.
It is an object of the present invention to provide an air conditioner for a vehicle that can reliably partition an air passage in an air conditioning unit case into a first air passage and a second air passage.

[0013]

In order to achieve the above object, the present invention employs the following technical means. Claims 1 and 2
In the described invention, the pipe wall surfaces (20a) of the heat exchangers (11, 12) that perform heat exchange with the conditioned air are arranged in parallel with the direction of airflow of the conditioned air, and the heat exchangers (11, 1) are arranged in parallel.
Air conditioning unit case (5, 5a, 5b) for storing 2)
Inside the partition plate (1
6 to 19, 17a, 17b, 18a, 18b), and the partition plates (16 to 19, 17a, 17b, 18).
a, 18b) with at least a portion of a tube (20, 2,
It is a predetermined length in the tube wall (20a) of 9) and the blowing direction
The partition plates (16-19, 17
a, 17b, 18a, 18b) and tubes (20, 2,
The air flow path in the air conditioning unit case (5) is divided into a first air flow path (10a) and a second air flow path (10b) by the pipe wall surface (20a) of 9).

As a result, even if the dimensions of the partition plate and the like vary due to manufacturing reasons, the dimensional variation is absorbed by the overlapping portion, and a gap is generated between the partition plate and the tube. Can be prevented. As a result, mixing of air between the first air passage 10a and the second air passage 10b can be effectively suppressed. Therefore, the first and second air passages (10a, 10a,
It is possible to satisfactorily achieve functions such as flowing inside air to one side of b) and outside air to the other side, or adjusting the air in the first and second air passages (10a, 10b) to different temperatures.

According to the third aspect of the present invention, the tube walls (2, 29) of the heat exchangers (11, 12) are provided.
0a), the auxiliary partition plates (27, 28) are joined, and at least a part of the partition plates (16-19, 17a, 17b, 18a, 18b) is blown to the auxiliary partition plates (27, 28).
The partition plates (16-19, 17a, 17b, 18a, 18b) are arranged so as to overlap by a predetermined length in the direction.
And auxiliary partition plates (27, 28) and tubes (20, 2,
The air flow path in the air conditioning unit case (5) is divided into a first air flow path (10a) and a second air flow path (10b) by the pipe wall surface (20a) of 9). As in the invention described in the items 1 and 2, the first air passage 10
a and the air mixing between the second air passage 10b can be effectively suppressed.

In particular, according to the invention of claim 4, the inside / outside air switching mechanism (6a, 6b, 6b, 6b,
7, 9a, 9b) and the inside / outside air switching mechanism (6a, 6b).
b, 7, 9a, 9b) a blower (8) that separates the inside air and the outside air introduced from the inside air and blows the inside air to the first air passage (10a) and the outside air to the second air passage (10b). The inside air from the first air passage (10a) is blown to the foot outlet (14a) and the second air passage (10b).
Is blown to the defroster outlet (14b).

Thus, the mixing of air between the first air passage 10a and the second air passage 10b can be effectively suppressed, and at the same time, the low-humidity warm air is blown to the defroster side and the foot air outlet (14a). The hot air with a high temperature can be blown out by recirculating the inside air. Therefore, at the time of heating, both improvement of the heating capacity by reduction of the ventilation load and improvement of the effect of preventing fogging of the window glass can be realized well.

Further, according to the fifth aspect of the present invention, the length (L) of the overlapping portion of the partition plates (16-19, 17a, 17b, 18a, 18b) is set to 3 mm or more. As shown, the first air passage 10a and the second
Prevention of mixing of air between the air passages 10b can be more effectively achieved. In addition, the code | symbol in the parenthesis of each said means shows the correspondence with the concrete means of embodiment mentioned later.

[0019]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. (First Embodiment) The configuration of the air conditioning unit of the automotive air conditioner according to the first embodiment may be the same as that shown in FIG. The air passage partition structure in the air conditioning unit case will be mainly described.

FIG. 1 is an exploded perspective view of a cooler unit 3 of an air conditioning unit of an automotive air conditioner. FIG. 2 is an enlarged sectional view of a main part of FIG. The upper case and the lower case are divided, and both are formed of a molded article of a resin having a certain elasticity such as polypropylene. In this case 5a, 5
The evaporator 11 is stored in b. Also, the upper case 5a,
On the inner wall surface of the lower case 5b, partition plates 17a,
17b and partition plates 18a and 18b (the reference numeral 18b is shown only in FIG. 2) are integrally formed.

In this case, the partition plates 17a, 17b are
8 is a half-split portion obtained by dividing the partition plate 17 on the upstream side of the evaporator into upper and lower portions, and the partition plates 18a and 18b are shown in FIG.
This is a half-split portion obtained by dividing the partition plate 18 on the downstream side of the evaporator into upper and lower parts. On the other hand, the evaporator 11 has the same structure as that of FIG. 9 described above, and includes a tube 20 having a flat cross section formed by joining a pair of aluminum tube plates in a middle state. This is a so-called stacked evaporator in which many tubes 20 are stacked in parallel.

An aluminum tank 21 is disposed at one end (upper end) of the tube 20 having a flat cross section. The inside of the tank 21 is divided into two parts in parallel with the longitudinal direction of the tank, and one of the two parts is used as a refrigerant inlet side. The other is the refrigerant outlet side. Here, the illustration of the refrigerant inlet / outlet pipe to the tank 21 is omitted. Then, the refrigerant is distributed from the refrigerant inlet side portion in the tank 21 to the tubes 20, and the refrigerant is U-turned at the lower ends of the tubes 20, so that the tank 21
The refrigerant from the tube 20 is returned to the refrigerant outlet side portion in the inside,
Let them gather.

The evaporator 11 is positioned such that the flat tube wall 20a of the tube 20 is oriented substantially parallel to the flow of air.
Are arranged in the cases 5a and 5b. Further, by stacking a large number of tubes 20, the inside of the core portion of the evaporator 11 is partitioned by the tubes 20 into a large number of air passages. An aluminum corrugated fin 22 formed in a corrugated shape is disposed in the air flow path.
2 is joined to the tube wall surface 20a of the tube 20 by brazing. In this example, the width of the corrugated fin 22 is larger than the width of the tube 20 (the dimension in the left-right direction in FIG. 2). In addition, a well-known louver 22a for improving heat exchange efficiency is cut and raised obliquely on the corrugated fin 22.

In FIG. 1, upper and lower cases 5a, 5b
After the evaporator 11 is housed, it is assembled integrally by a fastening means such as a metal spring clip or screw (not shown). At this time, the partition plates 17a, 17b, the partition plates 18a, 18b
The molding position of the evaporator 11 is set so as to satisfy the following assembling position. That is, as shown in FIG. 2, the partition plates 17a, 17b and the partition plates 18a, 18b arranged on the leeward and leeward sides of the evaporator 11 have a predetermined length L, and one tube at the central portion of the evaporator 11. It is arranged so as to overlap with the leeward side portion and the leeward side portion of the pipe wall surface 20a.

In order to achieve this overlapping structure, the partition plates 17a, 17b and the end faces of the corrugated fins 22 corresponding to the partition plates 18a, 18b are provided with partition plates 17a, 17b.
b, slits 2 for inserting end portions of partition plates 18a, 18b
2b is provided. That is, when assembling the upper and lower cases 5a and 5b integrally, at the same time, the partition plates 17a and
17b, the ends of the partition plates 18a, 18b are slit 22
By inserting into b, the above-mentioned length L polymerization structure is achieved.

As shown in FIG. 3, the contact surfaces between the upper and lower partition plates 17a and 17b and the contact surfaces between the upper and lower partition plates 18a and 18b are fitted within the range of the plate thickness. A fitting structure between the projection 23 and the fitting groove 24 is provided, and this fitting structure prevents air leakage at the contact surface. Note that the fitting projection 23 is connected to the lower partition plate 17.
b, 18b, and the fitting groove 24 is formed in the upper partition plate 17
Needless to say, it may be provided in the a and 18a.

The above is the partition structure of the air passage in the cooler unit 3 and the above-described partition plate 17a,
17b, the partition plates 18a, 18b, and the tube 20 of the evaporator 11, the air passage in the cooler unit 3 is changed to the first air passage 10a and the second air passage 10b.
However, the partition structure of the air passage in the heater unit 4 is the same, and the tube 20 of the evaporator 11 in FIG. 2 only needs to be replaced with the tube 29 of the heater core 12 (see FIG. 11).

Next, the operation of the present embodiment in the above configuration will be described. In FIG. 8, when the blower 8 is operated,
Inside air or outside air is sucked from the inside / outside air suction ports 6a, 6b, 7 and flows into the evaporator 11 through the first air passage 10a and the second air passage 10b in the air conditioning unit case 5 by the blower fans 8a, 8b. I do. Then, the blown air is dehumidified and cooled by the evaporator 11, and then introduced into the heater core 12, where it is heated.

In the case of this embodiment, temperature control doors (air mix doors) 13a and 13b are used as air conditioning temperature control means.
The air passing through the heater core 12 and the heater core 1 are controlled by the opening of the temperature control doors 13a and 13b.
The flow rate of air bypassing 2 can be adjusted, thereby creating the desired blown air temperature. The conditioned air reheated to the desired temperature by the heater core 12 is distributed to a predetermined outlet by each of the doors 15a to 15c of the outlet mode switching unit located at the downstream end of the first air passage 10a and the second air passage 10b. Is done.

In the present embodiment, in a season requiring heating such as winter, air is blown into the air conditioning unit 1 while keeping the outside air and the inside air separated, and heat is exchanged with the evaporator 11 and the heater core 12. The defroster outlet 14b has a two-layer inner / outer air flow function in which warm air heated from low humidity outside air is blown out from the side of the defroster outlet 14b, while warm air heated inside air is blown out from the foot foot outlet 14a. It has the characteristic.

The operation and effect of this two-layer inside / outside air unit will be described below. In FIG. 8, when the first inside / outside air switching doors 9a and 9b are operated to the positions indicated by solid lines in FIG. The opening 6a is opened, and the first inside air introduction port 6a communicates with the suction port of the blower fan 8a. On the other hand, the second inside / outside air switching door 9b closes the second inside air introduction port 6b, and connects the outside air introduction port 7 to the suction port of the blower fan 8b.

Therefore, when the blower fans 8a and 8b rotate, the inside air from the first inside air inlet 6a is removed from the blower fan 8a.
a to the first air passage 10a, and the outside air from the outside air inlet 7 is passed through the blower fan 8b to the second air passage 10a.
The air is sent to the air passage 10b. Therefore, the first air passage 10a
And the second air passage 10b, the inside air and the outside air can be separately blown.

Further, in the air conditioning unit 1, the first and second air passages 10 on the leeward side of the heater core 12 are provided.
In the foot mode and the combined foot / diff mode, the communication ports 14d of the a and 10b are closed by the foot outlet door 15a (see the solid line position of the door 15a in FIG. 8). After the outside air flowing into the passage 10b passes through the evaporator 11 and the heater core 12, the defroster outlet 14b and the face outlet 1
4c (actually, of the face outlet 14c, only the left and right side face outlets disposed at the left and right ends of the vehicle instrument panel) and blows out toward the vehicle front window glass and the vehicle side window glass. Is done. Here, by heating the low-humidity outside air with the heater core 12 to generate hot air,
The fogging prevention effect of the vehicle window glass can be enhanced.

On the other hand, inside air is blown into the first air passage 10a, and the inside air is heated by the heater core 12 to generate warm air, which is blown out from the foot outlet 14a to the foot portion of the occupant. Therefore, the ventilation load due to the introduction of outside air does not occur during the heating of the feet in the passenger compartment, and therefore the temperature of the engine cooling water flowing into the heater core 12 is not sufficiently increased (for example, when the diesel engine vehicle is idling). Etc.), the heating effect can be enhanced by recirculation of inside air.

Accordingly, it is possible to achieve both the improvement of the fogging prevention effect of the vehicle window glass and the improvement of the heating effect. by the way,
In the air suction mode of the two-layer flow of the inside and outside air described above, since the amount of air blown on the side of the first air passage 10a is large and the amount of air blown on the side of the second air passage 10b is small, the pressure of the first air passage 10a is It is higher than the second air passage 10b. Therefore, as in the prior application shown in FIG. 10, the end of the tube 20 of the evaporator 11 and the partition plates 17 (17a, 17b) and the partition plate 18
(18a, 18b), when a gap A is generated due to a dimensional variation of the partition plate or the like, a part of the inside air of the first air passage 10a passes through the gap A, and the second air is blown as shown by an arrow B. There is a problem that the air enters the outside of the road 10b. Also in the heater core 12, the partition plate 18 (18a,
A similar problem occurs when the gap A is generated between the partition 18 and the partition 18.

As described above, when the inside air is mixed into the second air passage 10b on the outside air side, the humidity of the air blown out from the defroster outlet 14b increases, and the effect of preventing fogging of the window glass decreases. On the other hand, in the present embodiment, as described above, the partition plates 17a and 17b and the partition plates 18a and 18b disposed on the leeward and leeward sides of the evaporator 11 are separated from the center of the evaporator 11 by a predetermined length L. It is arranged so as to overlap with the tube wall surface 20a on the leeward and leeward side of one tube 20 of the part. Thereby, a part of the inside air of the first air passage 10a is mixed into the outside air of the second air passage 10b as shown by an arrow B.
The amount of inside air can be effectively suppressed.

The above operation has been described only for the case where the outside air and the inside air are simultaneously introduced. However, the operation positions of the two inside / outside air switching doors 6a and 6b are selected between the solid line position and the two-dot chain line position in FIG. By doing, the first and second air passages 10
a and 10b, and an inside air mode in which inside air is introduced into both the first and second air passages 10a and 10b.

According to the examination of the trial production by the present inventors, it was found that the relationship between the overlap length L of the partition plates 17a, 17b, 18a, 18b and the inside air mixing ratio is as shown in the graph of FIG. In FIG. 4, the inside air mixing ratio on the vertical axis is
In a two-layer internal / external air suction mode in which inside air flows through the first air passage 10a and outside air flows through the second air passage 10b, the ratio of inside air mixed into the outside air flow of the second air passage 10b. A region where the overlap length L on the horizontal axis is negative means that the gap A is generated.

As understood from FIG. 4, by setting the polymerization length L to 3 mm or more, the inside air mixing
%. (Second Embodiment) FIG. 5 shows a second embodiment. In this example, the width of the tube 20 of the evaporator 11 is made larger than the width of the corrugated fin 22, and the evaporator is provided outside the corrugated fin 22. 11 tubes 20 and partition plate 1
7a, 17b, 18a and 18b are polymerized.

In this way, the corrugated fin 22
It is not necessary to provide the partition plates 17a, 17b and the slits 22b for inserting the ends of the partition plates 18a, 18b in the first embodiment. Therefore, the processing of the corrugated fins 22 can be simplified, and the assembly of the corrugated fins 22 and the partition plate can be simplified. However, there is a disadvantage in that the heat exchange performance is reduced due to the reduction in the area of the corrugated fins 22. (Third Embodiment) FIG. 6 shows a third embodiment. In this example, the partition plates 17a, 17a in the first embodiment are used.
b, 18a, 18b, two forked protrusions 25, 2
6 and slits 22b on both sides of the tube wall surface 20a of the tube 20 in the corrugated fin 22 for fitting the forked protruding portions 25 and 26.

According to the structure of the present embodiment, the length of the flow path through which the inside air is mixed with the outside air is increased, and the mixing ratio of the inside air can be reduced more effectively. (Fourth Embodiment) FIG. 7 shows a fourth embodiment. In this example, metal (aluminum) auxiliary partitioning plates 27 and 28 are provided in a tube 20 of an evaporator 11.
The auxiliary partitioning plates 27, 28 and the ends of the partitioning plates 17a, 17b and the partitioning plates 18a, 18b are overlapped by a predetermined length L at the time of assembling. is there.

According to the structure of this embodiment, the auxiliary partition plates 27 and 28 are previously joined to the tube 20 of the evaporator 11 so as to protrude outside the corrugated fins 22. And the partition plates 17a, 17
b, 18a and 18b are polymerized with the ends thereof, so that the first,
Partition plates 17a, 17b, 18 as in the third embodiment
a, 18b, or a bifurcated protruding portion 25, 26, which is fitted to the slit 22b.
Assembling of 7a, 17b, 18a, 18b becomes easy.

In the second to fourth embodiments, the evaporator 11
The partition structure of the air passages 10a and 10b in the portion has been described.
The configurations of the second to fourth embodiments can be similarly adopted in the partition structures a and 10b. (Other Embodiments) In each of the above embodiments, as shown in FIG. 1, the case where the upper and lower partition plates 17a, 17b, 18a, 18b are integrally formed on the upper case 5a and the lower case 5b, respectively, has been described. However, if the partition plate is formed separately from the upper and lower cases 5a and 5b, the partition plate can be formed of a single plate material without being divided into upper and lower portions.

In the first and third embodiments, the partition plates 17a, 17b, the partition plate 1
Although slits 22b for inserting the end portions of 8a and 18b are provided, the slits 22b are eliminated and the partition plates 17a and 1b are inserted.
7b, by forcibly pressing the end portions of the partition plates 18a and 18b against the end surfaces of the corrugated fins 22, and partially deforming the end surfaces of the corrugated fins 22 into a concave shape,
A predetermined overlap length L may be ensured.

The corrugated fins 22 are made of a thin metal plate having excellent thermal conductivity such as aluminum, and can be pressed and deformed relatively easily. In addition, the evaporator 11 is not limited to the above-described laminated type, and other types such as a so-called serpentine type in which a multi-hole flat tube is formed in a meandering shape and corrugated fins are combined with the meandering tube. It may be.

In the above-described embodiment, an air mix system for adjusting the mixing ratio of cold and hot air is adopted as a temperature control system for air conditioning, but instead of the temperature control doors (air mix doors) 13a and 13b, A hot water control valve for controlling the flow rate of hot water to the heater core 12 is provided, and the flow rate of hot water to the heater core 12 is controlled by the hot water control valve. You may make it control.

In the above embodiment, the air conditioning unit 1
Inside air and outside air are blown independently to improve the anti-fogging effect of the window glass during heating and improve the heating effect, but the ventilation path partition structure according to the present invention is limited to this. It is not something to be done. For example, the ventilation path partition structure of the present invention can be applied to a so-called left and right independent temperature control type automotive air conditioner that independently controls the temperature of air blown to the driver's seat side and the passenger's seat side of the vehicle compartment.

As in the bilevel mode, in the mode in which air is blown out from both the upper air outlet (face air outlet) and the lower air outlet (foot air outlet) at the same time, the upper air outlet is used. The ventilation path partition structure of the present invention may be applied to an automotive air conditioner having a so-called vertical independent temperature control function for independently controlling the temperature of air blown from an outlet and a lower outlet.

Further, even if the ventilation path partition structure of the present invention is applied to an automotive air conditioner of a so-called front and rear independent temperature control system for independently controlling the temperature of air blown to the front seat side and the rear seat side of the passenger compartment. Good. In such a left-right, up-down, or front-rear independent temperature control system, the air temperature of the first and second air passages 10a and 10b separated by the partition plates 16 to 19 is controlled by the mixing doors 13a and 13b and the like. The temperature control means may be independently controlled to select a predetermined outlet and blow out the conditioned air into the vehicle interior.

[Brief description of the drawings]

FIG. 1 is an exploded perspective view of a cooler unit according to a first embodiment of the present invention.

FIG. 2 is a sectional view of a main part of FIG.

FIG. 3 is an enlarged sectional view of a contact surface portion of upper and lower partition plates in FIG. 1;

FIG. 4 is a graph showing the effect of the present invention.

FIG. 5 is a sectional view of a main part showing a second embodiment of the present invention.

FIG. 6 is a sectional view of a main part showing a third embodiment of the present invention.

FIG. 7 is a sectional view of a main part showing a fourth embodiment of the present invention.

FIG. 8 is a schematic sectional view of a ventilation system of an air conditioning unit of a vehicle air conditioner used for describing the present invention and the prior application.

FIG. 9 is a perspective view of the evaporator part of FIG.

FIG. 10 is a sectional view taken along line XX of FIG. 9;

FIG. 11 is a perspective view of a heater core part of FIG. 8;

[Explanation of symbols]

5 ... air-conditioning unit case, 6a, 6 ... inside air inlet, 7 ...
Outside air inlet, 8… Blower, 9a, 9b… Inside / outside switching door,
10a, 10b: first and second air passages, 11: evaporator, 1
2: heater core, 14a: foot outlet, 14b: defroster outlet, 14c: face outlet, 16 to 19,
17a, 17b, 18a, 18b ... partition plates, 20, 2
9 ... Tube, 22, 30 ... Corrugated fin, 27,
28 ... Auxiliary partition plate.

──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Kenji Suwa 1-1-1, Showa-cho, Kariya-shi, Aichi Japan Inside Denso Co., Ltd. (72) Inventor Yuji Kato 1-Toyota-cho, Toyota-shi, Aichi Toyota Motor Corporation (72) Inventor Goro Uchida 1 Toyota Town, Toyota City, Aichi Prefecture Inside Toyota Motor Corporation (58) Field surveyed (Int. Cl. ⁷ , DB name) B60H 1/32 613

Claims (5)

(57) [Claims] 1. A heat exchanger (11, 12) for exchanging heat with conditioned air; an air conditioning unit case (5, 5a, 5b) for accommodating the heat exchanger (11, 12); In the air-conditioning unit case (5, 5a, 5b), a partition plate (16 to 19, 17a, 17b, 18a, 18b) arranged in parallel with the direction of the air-conditioned air is provided, and the heat exchanger (11) is provided. , 12) are provided in parallel with a number of tubes (20, 29) having a flat cross section through which a heat exchange fluid flows. The tube wall surface (20a) of the tubes (20, 29) The partition plates (16 to 19, 17a, 17b, 18a,
18b) comprises at least a portion of the tube (20, 2
9) A predetermined length in the pipe wall surface (20a) and the blowing direction
The partition plates (16 to 19, 17a, 17b, 18a,
18b) and the tube wall (20, 29) of the tubes (20, 29).
(a) The air conditioner for a vehicle, wherein the air passage in the air conditioning unit case (5) is divided into a first air passage (10a) and a second air passage (10b). 2. A corrugated fin (22, 30) is joined to a tube wall (20a) of the tube (20, 29) of the heat exchanger (11, 12). The width in the air flow direction is equal to or less than the width of the corrugated fin, and the end of the partition plate (16 to 19, 17a, 17b, 18a, 18b) is inserted into the corrugated fin (22, 30). The air conditioner for a vehicle according to claim 1, wherein a slit (22b) is formed. 3. A heat exchanger (11, 12) for exchanging heat with air-conditioned air; an air-conditioning unit case (5, 5a, 5b) accommodating the heat exchanger (11, 12); In the air-conditioning unit case (5, 5a, 5b), a partition plate (16 to 19, 17a, 17b, 18a, 18b) arranged in parallel with the direction of the air-conditioned air is provided, and the heat exchanger (11) is provided. , 12) are provided in parallel with a number of tubes (20, 29) having a flat cross section through which a heat exchange fluid flows. The tube wall surface (20a) of the tubes (20, 29) The auxiliary partition plates (27, 28) are joined to the tube wall surface (20a) of the tubes (20, 29), and the partition plates (16 to 19, 17a, 17b) , 18a,
18b) is at least partially provided by the auxiliary partition plate (2).
7 and 28) and a predetermined length in the blowing direction, and are arranged so as to overlap with each other, and the partition plates (16 to 19, 17a, 17b, 18a,
18b), the auxiliary partitioning plates (27, 28), and the tube wall surface (20a) of the tubes (20, 29), the air passage in the air conditioning unit case (5) is changed to a first air passage (1).
0a) and a second air passage (10b). 4. An internal / external air switching mechanism (6a, 6b, 7, 9a, 9b) configured to switch and introduce internal air and external air and to simultaneously introduce internal air and external air; 6b, 7, 9a, and 9b), a blower (8) that separates inside air and outside air from each other, blows inside air to the first air passage (10a), and blows outside air to the second air passage (10b). ), The inside air from the first air passage (10a) is blown to the foot outlet (14a), and the second air passage (10a) is blown.
4. A vehicle air conditioner according to claim 1, wherein the outside air from b) is blown to a defroster outlet (14b). 5. The partition plate (16 to 19, 17a, 1
7b, 18a, 18b) has a length (L) of 3 m
The air conditioner for a vehicle according to any one of claims 1 to 4, wherein m is not less than m.