JP4939109B2 - Air conditioning unit and air conditioning apparatus - Google Patents

Description

  The present invention relates to an air conditioning unit and an air conditioning apparatus.

  2. Description of the Related Art Conventionally, an air conditioner for a vehicle that provides a comfortable vehicle interior environment by cooling and heating and dehumidifying the vehicle interior is known. Such a vehicle air conditioner condenses gas refrigerant by exchanging heat with a compressor that operates using a part of the output of an internal combustion engine for vehicle travel and air outside the vehicle compartment (outdoor air). A condenser (condenser), an expansion valve that depressurizes the liquid refrigerant, and an evaporator (evaporator) that vaporizes the liquid refrigerant by exchanging heat with air introduced from outside or inside the vehicle compartment are connected by refrigerant piping. It has a closed circuit refrigeration cycle.

The above-described evaporator has a function of depriving the heat of vaporization from air, and is usually installed in a HVAC (Heating, Ventilation, and Air-Conditioning) unit together with a heater core serving as a heating source for heating, and introduced air ( Cooling and dehumidification of indoor air or outdoor air (for example, refer to Patent Document 1).
JP 2006-15842 A

The above-described vehicle air conditioner includes three types of air outlets that supply conditioned air into the vehicle interior according to the selected air conditioning operation mode. That is, a defroster outlet for removing fog such as a windshield, a vent (face) outlet that opens to the front surface of the instrument panel in the passenger compartment, and a foot outlet that opens to the feet of the occupant are provided. .
In such a vehicle air conditioner, regarding the temperature of the air blown out from each outlet, from the function and comfort of each outlet, “air temperature of defrost outlet (Tdef)”> “foot outlet In some cases, a relationship of “air temperature (Tfoot)”> “air temperature of vent outlet (Tvent)” is required. In particular, in extremely cold regions, Tdef is required to be a sufficiently high temperature in order to melt a frozen windshield.
However, in the vehicle air conditioner described in Patent Document 1 described above, the temperature of Tdef is substantially the same as the temperature of Tfoot, and the temperature of Tdef is increased to a sufficient temperature to melt the frozen windshield. It was difficult. That is, it was difficult to satisfy the condition of Tdef> Tfoot.

The present invention was made to solve the above problems, in the heating operation, the air temperature definitive to defrost outlet, the air conditioning unit and air that may be higher than the air temperature of definitive to foot outlet It aims at providing a harmony device.

In order to achieve the above object, the present invention provides the following means.
The air conditioning unit of the present invention includes a housing, a cooling unit that cools the air introduced into the housing, a heating unit that heats the air introduced into the housing, and the air cooled by the cooling unit, A mixing region that mixes the air heated by the heating unit; the air that is provided downstream of the mixing region and is cooled by the cooling unit; and the air that is heated by the heating unit, and a defrost outlet and The conditioned air flow path leading to the foot outlet, and the conditioned air flow path, connected to the defrost outlet and connected to the defrost outlet, by the heating unit among the conditioned air mixed in the mix region a hot air passage ratio of the heated air has a higher hot conditioned air flows, leading to the foot outlet of of the conditioned air that is mixed in the mix area, the cooling Cold mixing suppressing portion is a partition plate for dividing the air flow path, it is provided, first and other said defrost outlet is the hot air flow ratio is higher cold conditioned air cooled air flows by The foot blower outlet is disposed opposite to the low-temperature air flow path, and the air flowing from the high-temperature and low-temperature air flow paths is allowed to flow through the one defrost blowout outlet and the foot blower. One damper that is controlled to be supplied to the outlet at a predetermined ratio is provided, and a portion facing the damper at the damper side end of the mixing suppression portion extends to a region near the damper, and the damper side The other part of the end part extends to the vicinity of the other defrost outlet .

According to the present invention, since the mixing suppression unit is provided, the air temperature at the defrost outlet can be made higher than the air temperature at the foot outlet.
The conditioned air flow path can guide the air cooled by the cooling unit and the air heated by the heating unit to the defrost and the foot outlet. Therefore, the conditioned air in which the cooled air and the heated air are mixed is blown out from the defrost outlet and the foot outlet. Here, the mixing suppression unit can suppress mixing of the heated and cooled air in the conditioned air flow path. Therefore, conditioned air having a high ratio of heated air and conditioned air having a high ratio of cooled air are formed in the conditioned air flow path. Air-conditioned air with a high ratio of heated air is blown out from the defrost outlet, and air-conditioned air with a high ratio of cooled air is blown out from the foot outlet.
Furthermore, since the mixing suppression unit is a partition plate that divides the conditioned air flow path into a high-temperature air flow path and a low-temperature air flow path, it suppresses mixing of heated and cooled air in the conditioned air flow path. it can.
The air cooled by the cooling unit and the air heated by the heating unit flow into the conditioned air flow path. The heated air and the cooled air are mixed while flowing through the conditioned air flow path to become conditioned air having a substantially uniform temperature. Here, the air-conditioning air flow path is divided into a high-temperature and low-temperature air flow path by a mixing suppression unit that is a partition plate, and the heated and cooled air flowing through the high-temperature air flow path, Do not mix with cooled air. Then, the temperature of the conditioned air in the high-temperature air channel having a high ratio of the heated air to the heated and cooled air is high, and the temperature of the conditioned air in the low-temperature air channel having a high ratio of the cooled air is decreased. That is, the conditioned air temperature blown out from the high-temperature air passage through the defrost outlet and the conditioned air temperature blown out from the low-temperature air passage through the foot outlet become different temperatures.

Furthermore , at the damper side end of the mixing suppression portion , the portion facing the damper extends to the vicinity of the damper, and the other portion extends to the vicinity of the other defrost outlet, so in one and other defrost outlets The air temperature can be higher than the air temperature at the foot outlet. Furthermore, the air temperature in another defrost blower outlet can be made higher than the air temperature in one defrost blower outlet.
The damper can control the inflow of air from the high-temperature and low-temperature air flow paths to the single defrost outlet and the foot outlet. Specifically, the damper performs the following three controls. The first control is control for causing the air in the high-temperature air flow path to flow into one and the other defrost outlets, and causing the air in the low-temperature air flow path to flow into the foot outlets. The second control is control for causing the air in the high-temperature and low-temperature air flow paths to flow into one and other defrost outlets.
The third control is control for causing the air in the high-temperature and low-temperature air flow paths to flow into the other defrost outlets and foot outlets. That is, at least air in the high-temperature air flow channel always flows into the other defrost hot air outlets.
Here, in the damper side end portion of the mixing suppressing portion , the portion facing the damper extends to the damper vicinity region, and the other portion extends to the vicinity of the other defrost outlet. Therefore, in the first control, the air in the high-temperature air channel flows into one and the other defrost outlets, and the air in the low-temperature air channel flows into the foot outlets. Therefore, the air temperature in one and other defrost outlets can be made higher than the air temperature in the foot outlet. In the second control, since the other part extends to the vicinity of another defrost outlet, the air in the low-temperature air flow path flows into one defrost outlet. Air in the hot air flow path flows into one and other defrost outlets. That is, the air in the low-temperature air flow path is less likely to flow into other defrost outlets by the mixing suppression unit . Therefore, the air temperature at the other defrost outlets is higher than the air temperature at one defrost outlet. In the third control, for the other part it extends to other defrost outlet near the part of the air of the hot air passage, and flows into the other defrost outlet. The air in the other hot air flow path flows into the foot outlet. The air in the low temperature air flow path flows into the foot outlet. For this reason, the air temperature at the other defrost outlets is higher than the air temperature at the foot outlets.

In the above invention, the heated air is through the mix area flows into the inlet of the hot and cold air passage from the hot air passage side, the cooled air is, via said mix region above flows from the cold air flow path to the inlet of the hot and cold air channel, wherein the mixing suppressing portion, the end portion of the mix region side inlet area and the cold air flow path of the hot air flow path It is desirable that an area control unit for controlling the area of the inlet is provided.

According to the present invention, since the area control unit is provided at the end of the mixing suppression unit on the mix region side, the conditioned air temperature at the defrost outlet and the conditioned air temperature at the foot outlet can be adjusted. .
Air that is heated from the high-temperature air flow path side flows into the high-temperature air flow path and the low-temperature air flow path, and cooled air flows from the low-temperature air flow path side. Therefore, the heated air is more likely to flow into the high-temperature air flow path as compared with the cooled air. On the other hand, the cooled air easily flows into the low temperature air flow path. Here, the area control unit is provided at the end of the mixing suppression unit on the mix region side, and the outer peripheral wall of the conditioned air flow path is fixed. Therefore, for example, when the area of the inlet of the high-temperature air channel is narrowed by the area control unit, the inlet is narrowed in the direction away from the low-temperature air channel. On the other hand, when the inlet area of the low temperature air channel is increased, the inlet becomes wider in the direction approaching the high temperature air channel side. Then, the flow rate of the cooled air flowing into the high temperature air flow path is reduced, and the ratio of the heated air to the conditioned air flowing through the high temperature air flow path is increased. On the other hand, the flow rate of the heated air flowing into the low temperature air flow path increases, and the ratio of the heated air to the conditioned air flowing through the low temperature air flow path increases.
As a result, the temperature of the conditioned air that is blown out from the high-temperature and low-temperature air passages through the defrost outlet and the foot outlet increases.
Conversely, if the area control unit increases the inlet area of the high-temperature air channel and reduces the inlet area of the low-temperature air channel, the high-temperature and low-temperature air channels are routed through the defrost outlet and foot outlet. The temperature of the conditioned air that is blown out is lowered.

In the above invention, the heated air flows from the high-temperature air flow path side into the inflow port of the high-temperature and low-temperature air flow paths through the mix area M, and the cooled air passes through the mix area. flows from the cold air flow path to the inlet of the hot and cold air channel, the mixing suppressing portion, the end portion of the mix region side, along the edge position of the mixed suppression section in the flow direction of the air It is desirable to provide an end moving part that is moved.

According to the present invention, since the end moving unit is provided at the end of the mixing suppression unit on the mix region side, the temperature difference between the air temperature at the defrost outlet and the air temperature at the foot outlet is adjusted. Can do.
Air that is heated from the high-temperature air flow path side flows into the high-temperature air flow path and the low-temperature air flow path, and cooled air flows from the low-temperature air flow path side. Therefore, the heated air is more likely to flow into the high-temperature air flow path as compared with the cooled air. On the other hand, the cooled air easily flows into the low temperature air flow path. Here, the position changing unit can move the end position on the air inflow side in the mixing suppressing unit along the air flow direction. For example, when the end position is moved to the upstream side of the air flow, the region where the heated air and the cooled air flowing into the high-temperature and low-temperature air flow channels are mixed is narrowed (the mixing distance is shortened). be able to. That is, the temperature difference of the conditioned air in the high temperature and low temperature air flow paths can be increased. On the other hand, when the end position is moved to the downstream side of the air flow, the region where the heated air and the cooled air flowing into the high-temperature and low-temperature air flow paths are mixed (the mixing distance is increased). be able to. That is, the temperature difference of the conditioned air in the high temperature and low temperature air flow paths can be reduced.

Air conditioner of the invention features in that it comprises an air-conditioning unit of the present invention.

According to this invention, since the air conditioning unit of the said invention is provided, the air conditioning apparatus can make the air temperature in a defrost blower outlet higher than the air temperature in a foot blower outlet.

According to the air conditioning unit and the air conditioning apparatus of the present invention, since the mixing suppression unit is provided, the air temperature at the defrost outlet can be made higher than the air temperature at the foot outlet.

[First Embodiment]
Hereinafter, a vehicle air conditioner according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 6.
FIG. 1 is a perspective view illustrating a schematic configuration of an HVAC unit in the vehicle air conditioner according to the present embodiment.
As shown in FIG. 1, an HVAC unit (air conditioning unit) 3 of a vehicle air conditioner (air conditioner) 1 includes an inside / outside air switching box 5 and a blower fan 7. The inside / outside air switching box 5 is provided with an inside / outside air switching damper 9. By operating the inside / outside air switching damper 9, the inside / outside air switching box 5 can selectively introduce air in the vehicle interior (indoor air) or air outside the vehicle interior (outdoor air).
In the following description, the indoor air and the outdoor air before air conditioning introduced from the inside / outside air switching box 5 are collectively referred to as “introduction air”, and warm air (heated) that has been air-conditioned after passing through the heat exchanger. Air whose temperature is adjusted by mixing air) and cold air (cooled air) will be referred to as “conditioned air”.

  The vehicle air conditioner 1 has a function of providing a comfortable vehicle interior environment by performing air conditioning and dehumidification by supplying conditioned air to the vehicle interior. The vehicle air conditioner 1 also includes a compressor (not shown) that is operated using a part of the output of the vehicle traveling internal combustion engine, and a condenser that condenses the gas refrigerant by exchanging heat with outdoor air. (Not shown), an expansion valve (not shown) that depressurizes the liquid refrigerant, and an evaporator 13 that exchanges heat with the introduced air to vaporize the liquid refrigerant, and is connected by refrigerant piping. Has a cycle. The evaporator 13 described above has a function of removing vaporization heat from the introduced air, and cooling and dehumidification of the introduced air as a cooling means installed in the HVAC unit 3 together with the heater core 15 serving as a heating source for normal heating. Is to do.

FIG. 2 is a cross-sectional view taken along the line AA for explaining the configuration of the HVAC unit of FIG.
As shown in FIG. 2, the HVAC unit 3 includes a casing (housing) 11, an evaporator (cooling unit) 13, and a heater core (heating unit) 15.
The casing 11 accommodates the evaporator 13 and the heater core 15 inside. The casing 11 has a half structure composed of a divided body 11A and a divided body 11B (see FIG. 1). The evaporator 13 is disposed on the vehicle front side (left side in FIG. 2), and the heater core 15 is disposed below the vehicle compartment side (right side in FIG. 2). If it demonstrates using the flow of the introduction air in the casing 11, the evaporator 13 will be arrange | positioned in the upstream (side near the blower fan 7) of the introduction air flow, and the heater core 15 will be arrange | positioned in the downstream of the introduction air flow. Yes.
As shown in FIG. 1, the casing 11 is provided with vent air outlets 17F and 17R, foot air outlets 19F and 19R, and defrost air outlets 21A and 21B in order from the upstream side in the flow direction of the conditioned air. (See FIG. 2). The vent air outlet 17F and the foot air outlet 19F blow air-conditioned air to the upper body side and the lower body side of the occupant seated in the front seat of the vehicle, respectively. The vent outlet 17R and the foot outlet 19R blow out conditioned air to the upper body side and the lower body side of the occupant seated in the rear seat of the vehicle, respectively. The defroster outlet 21A is a windshield defroster (W / S) outlet for fogging and defrosting in the windshield (windshield) in front of the vehicle, and the defroster outlet 21B is a side glass (side windshield) on the vehicle side. ) In the side windshield defroster (SWD) for clouding and defrosting.

As shown in FIG. 2, an air passage partition plate 23 is provided in the casing 11 at a position facing the air outflow surface of the heater core 15 with a predetermined interval. The air path partition plate 23 is provided upward from the lower end support surface of the heater core 15 and substantially parallel to the heater core 15 to the vicinity of the mix region M. The upper end portion of the airway partition plate 23 is formed in a curved surface that faces substantially forward, and is formed in a streamline shape.
On the back side (right side in FIG. 2) of the air passage partition plate 23 as viewed from the heater core 15 side, the temperature from the mixing region M formed on the downstream side of the evaporator 13 and on the upper portion of the heater core 15 between the casing 11 and the casing 11. Hot air passages (air-conditioned air passages) 25 communicating with the foot outlets 19F and 19R, which are wind outlets, and the defrost outlets 21A and 21B are formed. The mix region M is a space for mixing the cool air cooled by the evaporator 13 and the warm air heated by the heater core 15 to form conditioned air having a desired temperature.

An air mix damper 27 is provided between the evaporator 13 and the heater core 15 to selectively switch the flow path of the air that has passed through the evaporator 13. The air mix damper 27 is swingably provided with the shaft 27A as a fulcrum so that arbitrary damper positions such as a maximum heating position, a maximum cooling position, and an intermediate opening position can be appropriately selected according to an operation mode described later. It has become.
In the configuration example of this embodiment, the air passage area of the heater core 15 is set to be smaller than the air passage area of the evaporator 13 (about half). A space formed between the upper end portion of the heater core 15 and the upper casing 11 serves as a cold air bypass passage 29 for directly guiding the air that has passed through the evaporator 13 to the mix region M.
When the position of the air mix damper 27 is the maximum heating position, the cold air bypass passage 29 is fully closed, and the entire amount of air that has passed through the evaporator 13 is guided to the heater core 15. On the other hand, when the position of the air mix damper 27 is the maximum cooling position, the cold air bypass passage 29 is fully opened, and the entire amount of air that has passed through the evaporator 13 is guided to the mix region M.

  A vent damper 31 is provided at the vent outlets 17F and 17R. The vent damper 31 swings around a shaft 31A. The vent damper 31 swings between a position where the vent outlets 17F, 17R are fully closed and a position where the vent outlets 17F, 17R are fully opened and the inlet of the hot air passage 25 is fully closed. A desired blowing mode can be selected according to the position of the vent damper 31. In addition, also about this vent damper 31, arbitrary intermediate | middle opening can be suitably selected according to the operation mode mentioned later.

A foot / defrost switching damper (damper, hereinafter referred to as a “switching damper”) 33 that swings around the shaft 33A is provided at the branch portion of the hot air flow path 25. The switching damper 33 swings between three positions to be described later so that a desired blowing mode can be selected depending on the position of the switching damper 33.
The position of the first switching damper 33 is such that the switching damper 33 falls to the defrost outlets 21A and 21B, the foot outlets 19F and 19R are fully opened, and the defrost outlets 21A and 21B are fully closed. Position. The position of the second switching damper 33 is such that the switching damper 33 falls to the foot outlets 19F, 19R side, the foot outlets 19F, 19R are fully closed, and the defrost outlets 21A, 21B are fully opened. Position. As for the position of the third switching damper 33, the switching damper 33 is positioned between the foot outlets 19F, 19R and the defrost outlets 21A, 21B, and the foot outlets 19F, 19R and the defrost outlets 21A, 21B are opened. Position.

The hot air passage 25 is divided into a hot air passage 25 (high temperature hot air passage (high temperature air passage) 25H on the heater core 15 side (left side in FIG. 2)) and a low temperature hot air passage (low temperature) on the passenger compartment side (right side in FIG. 2). A guide vane (mixing suppression unit ) 35, which is a partition plate that is divided into (air flow path) 25L, is provided. The guide vane 35 is disposed substantially parallel to the air passage partition plate 23 and extends from the vicinity of the mix region M in the hot air passage 25 to the vicinity of the switching damper 33.
The guide vane 35 has a half structure similar to the casing 11. One and the other of the guide vanes 35 having a half structure are separated from each other by a predetermined interval (for example, an interval of 10 mm). By providing the predetermined interval in this way, when the divided bodies 11A and 11B are joined to form the casing 11, each of the divided bodies 11A and 11B may be connected due to poor coupling (see FIG. 1) or due to distortion of the casing 11. Problems such as malfunction of the damper can be prevented.

Next, the effect | action in the vehicle air conditioning apparatus 1 which consists of said structure is demonstrated.
First, the Defog operation mode that removes fogging of the windshield and side glass of the vehicle will be described.
In the defog operation mode, the air mix damper 27 is set to a position with a predetermined opening, the vent damper 31 is set to a position where the vent outlets 17F, 17R are fully closed, and the switching damper 33 is set to the defrost outlets 21A, 21B and The positions are set so that the foot outlets 19F and 19R are opened.
The opening degree of the air mix damper 27 is set based on the temperature of the conditioned air at the defrost outlets 21A and 21B and the foot outlets 19F and 19R. That is, when the temperature of the conditioned air at the defrost outlet 21A is increased, the opening degree of the air mix damper 27 is increased, and when the temperature of the conditioned air is decreased, the opening degree of the air mix damper 27 is decreased. To do.

  When the vehicle air conditioner 1 is operated in the above-described damper position setting, the air passes through the evaporator 13 through the inside / outside air switching box 5 by the blower fan 7 as shown in FIG. As shown in FIG. 2, the air is cooled and dehumidified as it passes through the evaporator 13. A part of the cooled and dehumidified air passes through the cold air bypass passage 29 and flows into the mix region M. The remaining air passes through the heater core 15 and is heated. The heated and dehumidified air flows along the air passage partition plate 23 and is mixed with the above-described cooled air in the mix region M to become conditioned air.

The conditioned air mixed in the mix region M flows into the high temperature hot air flow path 25H and the low temperature hot air flow path 25L with insufficient mixing. High-temperature conditioned air having a high ratio of heated air flows into the high-temperature hot-air channel 25H adjacent to the air passage partition plate 23. On the other hand, low-temperature conditioned air having a high ratio of cooled air flows into the low-temperature hot-air channel 25L away from the air channel partition plate 23.
The high-temperature conditioned air that has flowed into the high-temperature hot-air channel 25H is blown to the windshield and the side glass from the defrost outlets 21A and 21B, respectively. Since the high-temperature conditioned air is dehumidified, fogging of the windshield and the side glass can be easily removed. On the other hand, the low-temperature conditioned air that has flowed into the low-temperature hot-air channel 25L is blown out from the foot outlets 19F and 19R into the vehicle interior.
At this time, the switching damper 33, together with the guide vane 35, prevents mixing of the high-temperature conditioned air flowing through the high-temperature hot-air channel 25H and the low-temperature conditioned air flowing through the low-temperature hot-air channel 25L.

Here, the simulation result of the air-conditioning air temperature blown from the defrost outlet 21A, the defrost outlet 21B, and the foot outlets 19F and 19R in the defog operation mode in the present embodiment will be described. FIG. It is the graph which showed the air-conditioning air temperature which concerns on the air conditioning apparatus 1 for vehicles of this embodiment on the basis of the air-conditioning air temperature which blows off from the defrost blower outlet 21A etc. at the time of the Defog operation mode in an air conditioner. The vertical axis represents the temperature difference (ΔT (° C.)) of the conditioned air temperature according to the present embodiment with respect to the conditioned air temperature according to the conventional vehicle air conditioner. On the horizontal axis, the opening degree (M / A (%)) of the air mix damper 27 is shown. Here, when the air mix damper 27 falls to the heater core 15 side and the cold air bypass passage 29 is fully opened, the opening degree of the air mix damper 27 is set to 0 (%) (M / A = 0 (%)). When the cold air bypass passage 29 is fully closed, the opening degree of the air mix damper 27 is 100 (%) (M / A = 100 (%)). Moreover, in FIG. 3, the graph represented by the white square represents the difference in the conditioned air temperature at the defrost outlet 21A, and the graph represented by the white triangle represents the difference in the conditioned air temperature at the defrost outlet 21B. The graph represented by the white diamond is a graph representing the difference in the air-conditioning air temperature at the foot outlets 19F and 19R.

As shown in FIG. 3, when the opening degree of the air mix damper 27 is 90% or less, the conditioned air temperature at the defrost outlets 21A and 21B is higher than the conditioned air temperature at the foot outlets 19F and 19R. It is shown.
In the conventional vehicle air conditioner, the conditioned air temperature at the defrost outlets 21A and 21B and the conditioned air temperature at the foot outlets 19F and 19R are substantially equal. Under this premise, when the difference in the conditioned air temperature at the defroster outlets 21A and 21B in FIG. 3 is seen, the conditioned air temperature is high when the opening degree of the air mix damper 27 is 90% or less. I understand. On the other hand, when the difference in the air-conditioning air temperature at the foot outlets 19F and 19R in FIG. That is, it can be seen that the conditioned air temperature at the defrost outlets 21A and 21B is higher than the conditioned air temperature at the foot outlets 19F and 19R.
As a specific example, when the opening degree of the air mix damper 27 is 30%, the difference in air-conditioning air temperature between the foot outlets 19F, 19R and the defrost outlet 21A is about 9.3 ° C. The difference in the conditioned air temperature between the blowout ports 19F and 19R and the defrost blowout port 21B is about 6.8 ° C.

  Note that, as in the above-described Defog operation mode, the air mix damper 27 may be set at a predetermined opening position, or the air mix damper 27 may be set at the maximum heating position (M / A = 100%). Well, not particularly limited. Thus, when the air mix damper 27 is set to the maximum heating position, only the air heated by the heater core 15 flows into the mix region M. Therefore, the conditioned air temperatures at the defrost outlets 21A and 21B and the foot outlets 19F and 19R are equal.

Next, the Defrost operation mode for removing frost on the windshield and side glass of the vehicle will be described.
FIG. 4 is a schematic diagram illustrating the air flow in the Defrost operation mode.
As shown in FIG. 4, the position of each damper in the Defrost operation mode is set such that the switching damper 33 falls to the foot outlets 19F and 19R side and the foot outlets 19F and 19R are fully closed as compared to the Defog operation mode. The point to do is different. The setting positions of the air mix damper 27 and the vent damper 31 are the same as in the Defog operation mode.

The air flow in this operation mode is the same as that in the defog operation mode until the high-temperature and low-temperature conditioned air flows into the high-temperature and low-temperature hot-air flow paths 25H and 25L, respectively, and thus the description thereof is omitted.
The high-temperature conditioned air flowing through the high-temperature hot-air channel 25H flows along the guide vanes 35 and flows into the defrost outlets 21A and 21B. On the other hand, the low-temperature conditioned air flowing through the low-temperature hot-air channel 25L passes through the gap between the guide vane 35 and the switching damper 33 and flows into the defrost outlets 21A and 21B.
The high temperature and low temperature conditioned air that has flowed into the defrost outlets 21A and 21B are mixed and sprayed onto the windshield and the side glass, respectively. Since the conditioned air is dehumidified, frost on the windshield and the side glass can be easily removed.

Next, a description will be given of the Heater operation mode in which warm air is blown out to the feet of the front seat and rear seat of the vehicle.
FIG. 5 is a schematic diagram illustrating the air flow in the heater operation mode.
As shown in FIG. 5, the position of each damper in the heater operation mode is set such that the switching damper 33 falls to the defrost outlets 21A and 21B and the defrost outlets 21A and 21B are fully closed as compared with the defog operation mode. The point to do is different. The setting positions of the air mix damper 27 and the vent damper 31 are the same as in the Defog operation mode.

The air flow in this operation mode is the same as that in the defog operation mode until the high-temperature and low-temperature conditioned air flows into the high-temperature and low-temperature hot-air flow paths 25H and 25L, respectively, and thus the description thereof is omitted.
The high-temperature conditioned air flowing through the high-temperature hot-air channel 25H flows into the foot outlets 19F and 19R through the gap between the guide vane 35 and the switching damper 33. On the other hand, the low-temperature conditioned air flowing through the low-temperature hot-air channel 25L flows along the guide vane 35 and flows into the foot outlets 19F and 19R.
The high temperature and low temperature conditioned air flowing into the foot outlets 19F and 19R are mixed and blown out as warm air to the feet of the front and rear seats of the vehicle, respectively.

The vent damper 31 may be set to a position where the vent outlets 17F and 17R are fully closed, as in the above-described Defog operation mode, Defrost operation mode, and Heater operation mode, and the vent damper 31 has a predetermined opening degree. It may be set at the position, and is not particularly limited.
By setting the position as described above, it is possible to blow cool air to the front seat and the rear seat of the vehicle in each operation mode. That is, the conditioned air in the mix region M is divided into conditioned air having a high ratio of air cooled by the vent damper 31 and conditioned air having a high ratio of heated air. The former conditioned air flows into the vent outlets 17F and 17R and is blown out as cold air to the front seat and rear seat of the vehicle. The latter conditioned air is further divided into high-temperature conditioned air and low-temperature conditioned air by the guide vane 35, and flows into the high-temperature hot-air channel 25H and the low-temperature hot-air channel 25L, respectively. Thereafter, the high-temperature and low-temperature conditioned air is blown into the passenger compartment according to each operation mode.

Next, the cooling operation mode for blowing cool air to the front seat and the rear seat of the vehicle will be described.
FIG. 6 is a schematic diagram illustrating the air flow in the cooling operation mode.
In the cooling operation mode, the air mix damper 27 is set to a position (M / A = 0%) where the cold air bypass passage 29 is fully opened, and the vent damper 31 is set to a position where the vent outlets 17F, 17R are fully opened. The

When the vehicle air conditioner 1 is operated in the above-described damper position setting, the air passes through the evaporator 13 through the inside / outside air switching box 5 by the blower fan 7 as shown in FIG. As shown in FIG. 6, the air is cooled as it passes through the evaporator 13. The cooled air, that is, conditioned air, flows into the vent outlets 17F and 17R through the cold air bypass passage 29 and the mix region M.
The conditioned air that has flowed into the vent outlets 17F and 17R is blown out as cold air to the front and rear seats of the vehicle.

  Note that, as in the above-described cooling operation mode, the air mix damper 27 may be set at the maximum cooling position (M / A = 0%), or may be set at a predetermined opening position, and is particularly limited. It is not a thing. As described above, when the air mix damper 27 is set to the position of the predetermined opening, a part of the air cooled by the evaporator 13 is heated by the heater core 15. Therefore, the conditioned air in which the cooled air and the heated air are mixed in the mix region M is blown out from the vent outlets 17F and 17R. That is, the temperature of the blown air can be adjusted to a predetermined temperature.

According to said structure, since the guide vane 35 is provided, the air temperature in defrost outlet 21A, 21B can be made higher than the air temperature in foot outlet 19F, 19R.
The hot air flow path 25 can guide the air cooled by the evaporator 13 and the air heated by the heater core 15 to the defrost outlets 21A and 21B and the foot outlets 19F and 19R. Therefore, conditioned air in which cooled air and heated air are mixed is blown out from the defrost outlets 21A and 21B and the foot outlets 19F and 19R. Here, the guide vane 35 can suppress the mixing of heated and cooled air in the hot air flow path 25. Therefore, conditioned air having a high ratio of heated air and conditioned air having a high ratio of cooled air are formed in the hot air flow path 25. Air-conditioned air with a high ratio of heated air is blown out from the defrost outlets 21A and 21B, and air-conditioned air with a high ratio of cooled air is blown out from the foot outlets 19F and 19R.

Since the guide vane 35 is a partition plate that divides the hot air passage 25 into the high-temperature and low-temperature air passages, mixing of heated and cooled air in the hot-air passage 25 can be suppressed.
The air cooled by the evaporator 13 and the air heated by the heater core 15 flow into the hot air flow path 25. The heated air and the cooled air are mixed while flowing through the hot air flow path 25 to become conditioned air having a substantially uniform temperature. Here, the hot air flow path 25 is divided by the guide vane 35 into a high temperature hot air flow path 25H and a low temperature hot air flow path 25L. It does not mix with flowing heated and cooled air. Then, the temperature of the conditioned air in the high-temperature hot-air channel 25H having a high ratio of heated air is high, and the temperature of the conditioned air in the low-temperature hot-air channel 25L having a high ratio of cooled air is decreased. That is, the conditioned air temperature blown from the high temperature hot air flow path 25H via the defrost outlets 21A and 21B and the conditioned air temperature blown from the low temperature hot air flow path 25L via the foot blow outlets 19F and 19R become different temperatures.

[First Modification of First Embodiment]
Next, a first modification of the first embodiment of the present invention will be described with reference to FIGS.
The basic configuration of the vehicle air conditioner of this modification is the same as that of the first embodiment, but the shape of the guide vane is different from that of the first embodiment. Therefore, in this modification, only the periphery of the shape of the guide vane will be described with reference to FIGS.
FIG. 7 is a schematic diagram for explaining the arrangement relationship between guide vanes and switching dampers in the HVAC unit according to the vehicle air conditioner of the present modification.
In addition, about the component same as 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 2, the HVAC unit (air conditioning unit) 103 according to the vehicle air conditioner (air conditioner) 101 includes a switching damper (damper) 133 and a guide vane (mixing suppression unit ) 135 that is a partition plate. And.
The switching damper 133 controls opening / closing of the defrost outlet 21A and the foot outlets 19F and 19R.
The switching damper 133 is disposed so as to be swingable between the following three positions around the shaft 133A. The first position is a position where both the defrost outlets 21A and 21B and the foot outlets 19F and 19R are opened, and prevents mixing of the conditioned air flowing through the high temperature hot air passage 25H and the low temperature hot air passage 25L. Position. The second position is a position where the foot outlets 19F and 19R are fully closed, and is a position where the conditioned air flowing through the high temperature hot air passage 25H and the low temperature hot air passage 25L flows into the defrost outlets 21A and 21B. . The third position is a position where the defrost outlet 21A is fully closed, and the conditioned air flowing through the high temperature hot air passage 25H and the low temperature hot air passage 25L is caused to flow into the defrost outlet 21B and the foot outlets 19F, 19R. Position.
The switching damper 133 is provided with a hole 134 at a position corresponding to the foot outlets 19F and 19R. When the switching damper 133 fully closes the defrost outlet 21A or the foot outlets 19F and 19R, a part of the conditioned air flowing through the hot air flow path 25 passes through the hole 134, and the defrost outlet 21A or the foot outlet 19F. , 19R.

FIG. 8 is a schematic diagram illustrating the shape of the guide vane in FIG.
The guide vane 135 is a partition plate that divides the hot air passage 25 into a high temperature hot air passage 25H and a low temperature hot air passage 25L. As shown in FIGS. 7 and 8, the end portion on the defrost outlet 21 </ b> A side of the guide vane 135 has a portion (central portion) facing the switching damper 33 extending to the vicinity of the switching damper 33, and the other portions. (Both ends) extend to the vicinity of the defrost outlet 21B.

Next, the effect | action in the air conditioning apparatus 101 for vehicles which consists of said structure is demonstrated.
First, the Defog operation mode that removes fogging of the windshield and side glass of the vehicle will be described.
Since the setting positions of the dampers in the defog operation mode in the present modification are the same as those in the first embodiment, the description thereof is omitted. The air flow during operation of the vehicle air conditioner 101 is the same as that in the first embodiment until the conditioned air flows into the high temperature hot air flow path 25H and the low temperature hot air flow path 25L. Omitted.

As shown in FIG. 7, the switching damper 133 is a position where both the defrost outlet 21A and the foot outlets 19F and 19R are opened, and the mixing of the conditioned air flowing through the high temperature hot air passage 25H and the low temperature hot air passage 25L. The position is set to prevent
The high-temperature conditioned air flowing through the high-temperature hot-air channel 25H flows along the guide vane 135 and the switching damper 133, and flows into the defrost outlets 21A and 21B. The high-temperature conditioned air that has flowed into the defrost outlets 21A and 21B is blown to the windshield and the side glass, respectively.
On the other hand, the low-temperature conditioned air flowing through the low-temperature hot-air channel 25L flows along the guide vane 135 and the switching damper 133 and flows into the foot outlets 19F and 19R. The low-temperature conditioned air that has flowed into the foot outlets 19F and 19R is blown out to the front and rear seats of the vehicle, respectively.
Here, the defrost outlet 21A is isolated from the low temperature hot air flow path 25L by the guide vane 135 and the switching damper 133, and the defrost outlet 21B is isolated from the low temperature hot air flow path 25L by the guide vane 135.

Here, the simulation result of the air-conditioning air temperature blown out from the defroster outlet 21A, the defroster outlet 21B, and the foot outlets 19F and 19R in the defog operation mode in the present modification will be described. It is the graph which showed the air-conditioning air temperature which concerns on the air conditioning apparatus 101 for vehicles of this modification on the basis of the air-conditioning air temperature which blows off from defrost outlet 21A etc. at the time of the Defog operation mode in an air conditioner. The vertical axis represents the temperature difference (ΔT (° C.)) of the air-conditioning air temperature according to this modification with respect to the air-conditioning air temperature according to the conventional vehicle air conditioner. On the horizontal axis, the opening degree (M / A (%)) of the air mix damper 27 is shown.
In addition, since description of the opening degree of the air mix damper 27, the symbol of a graph, etc. is the same as that of the case of the said FIG. 3, the description is abbreviate | omitted.

As shown in FIG. 9, when the opening degree of the air mix damper 27 is 90% or less, the conditioned air temperature at the defrost outlets 21A and 21B is higher than the conditioned air temperature at the foot outlets 19F and 19R. It is shown.
In the conventional vehicle air conditioner, the conditioned air temperature at the defrost outlets 21A and 21B and the conditioned air temperature at the foot outlets 19F and 19R are substantially equal. Under this assumption, when the difference in the air-conditioning air temperature at the defrost outlets 21A and 21B in FIG. 9 is seen, the air-conditioning air temperature is high when the opening degree of the air mix damper 27 is 90% or less. I understand. On the other hand, when the difference of the air-conditioning air temperature in the foot outlets 19F and 19R of FIG. 9 is seen, it turns out that the air-conditioning air temperature is low when the opening degree of the air mix damper 27 is 90% or less. That is, it can be seen that the conditioned air temperature at the defrost outlets 21A and 21B is higher than the conditioned air temperature at the foot outlets 19F and 19R.
As a specific example, when the opening degree of the air mix damper 27 is 30%, the difference in the air-conditioning air temperature between the foot outlets 19F, 19R and the defrost outlet 21A is about 10.6 ° C. The difference in the air-conditioning air temperature between the air outlets 19F and 19R and the defrost air outlet 21B is about 12.8 ° C. That is, it is shown that the air conditioner 101 of the present modification can raise the air-conditioning air temperature at the defrost outlets 21A and 21B, compared to the air conditioner 1 of the first embodiment described above. In particular, it is shown that the air-conditioning air temperature at the defrost outlet 21B can be increased.

  Even when the opening degree of the air mix damper 27 is 80%, the temperature increase of the air-conditioning air temperature at the defrost outlets 21A and 21B (6 ° C.) is the temperature increase of the air-conditioning air temperature at the foot outlets 19F and 19R. Greater than minutes (2 ° C). That is, even when the opening degree of the air mix damper 27 is 80%, it can be seen that the air-conditioning air temperature at the defrost outlets 21A and 21B is higher than the air-conditioning air temperature at the foot outlets 19F and 19R.

Next, the Defrost operation mode for removing frost on the windshield and side glass of the vehicle will be described.
FIG. 10 is a schematic diagram for explaining the air flow around the switching damper in the Defrost operation mode.
Since the setting positions of the respective dampers in the Defrost operation mode in the present modification are the same as those in the first embodiment, the description thereof is omitted. The air flow during operation of the vehicle air conditioner 101 is the same as that in the first embodiment until the conditioned air flows into the high temperature hot air flow path 25H and the low temperature hot air flow path 25L. Omitted.

As shown in FIG. 7, the switching damper 133 is in a position where the foot outlets 19F and 19R are fully closed, and the conditioned air flowing through the high temperature hot air passage 25H and the low temperature hot air passage 25L is defrosted from the outlets 21A and 21B. It is a position to flow into.
The high-temperature conditioned air flowing through the high-temperature hot-air channel 25H flows along the guide vane 135 and flows into the defrost outlets 21A and 21B. On the other hand, the low-temperature conditioned air flowing through the low-temperature hot-air channel 25L passes between the guide vane 135 and the switching damper 133 and flows into the defrost outlet 21A.
Here, since the guide vane 135 extends to the vicinity of the defrost outlet 21B, it is difficult for low-temperature conditioned air to flow in.
The high-temperature and low-temperature conditioned air that has flowed into the defrost outlet 21A is mixed and blown onto the windshield. On the other hand, the high-temperature conditioned air that has flowed into the defrost outlet 21B is blown onto the side glass.

Next, a description will be given of the Heater operation mode in which warm air is blown out to the feet of the front seat and rear seat of the vehicle.
FIG. 11 is a schematic diagram illustrating the air flow around the switching damper in the heater operation mode.
Since the setting positions of the respective dampers in the heater operation mode in the present modification are the same as those in the first embodiment, the description thereof is omitted. The air flow during operation of the vehicle air conditioner 101 is the same as that in the first embodiment until the conditioned air flows into the high temperature hot air flow path 25H and the low temperature hot air flow path 25L. Omitted.

As shown in FIG. 11, the switching damper 133 is a position where the defrost outlet 21 </ b> A is fully closed, and the conditioned air flowing through the high temperature hot air passage 25 </ b> H and the low temperature hot air passage 25 </ b> L is transferred to the defrost outlet 21 </ b> B and the foot outlet. This is the position that flows into 19F and 19R.
Part of the high-temperature conditioned air flowing through the high-temperature hot-air channel 25H flows along the guide vane 135 and flows into the defrost outlet 21B. The remaining high-temperature conditioned air passes between the guide vane 135 and the switching damper 133 and flows into the foot outlets 19F and 19R. On the other hand, the low-temperature conditioned air flowing through the low-temperature hot-air channel 25L flows along the guide vanes 135 and flows into the foot outlets 19F and 19R.
Here, since the defrost outlet 21B is not closed by the switching damper 133 and the guide vane 135 extends to the vicinity, the remaining high-temperature conditioned air flows into the defrost outlet 21B.
The high-temperature conditioned air that has flowed into the defrost outlet 21B is blown to the side glass. On the other hand, the high-temperature and low-temperature conditioned air flowing into the foot outlets 19F and 19R are mixed and blown out to the feet of the front seat and the rear seat of the vehicle, respectively.

  In addition, since the air flow in other operation modes is the same as that of 1st Embodiment, the description is abbreviate | omitted.

According to the above configuration, at the end portion of the guide vane 135 on the switching damper 133 side, the portion facing the switching damper 133 extends to the vicinity of the switching damper 133, and the other portion extends to the vicinity of the defrost outlet 21B. Therefore, the air temperature at the defrost outlets 21A and 21B can be made higher than the air temperature at the foot outlets 19F and 19R. Furthermore, the air temperature at the defrost outlet 21B can be made higher than the air temperature at the defrost outlet 21A.
The switching damper 133 can control the inflow of air from the high temperature and low temperature hot air flow paths 25H, 25L to the defrost outlet 21A and the foot outlets 19F, 19R. Specifically, the switching damper 133 is set at the following three positions. The first setting position is a position where the air in the high temperature hot air flow path 25H flows into the defrost outlets 21A and 21B and the air in the low temperature hot air flow path 25L flows into the foot outlets 19F and 19R. The second setting position is a position where the air in the high temperature and low temperature hot air flow paths 25H and 25L is allowed to flow into the defrost outlets 21A and 21B. The third setting position is a position where the air in the high temperature and low temperature hot air flow paths 25H, 25L is allowed to flow into the defrost outlet 21B and the foot outlets 19F, 19R. That is, at least air in the hot air flow path 25H always flows into the defrost outlet 21B.
Here, at the end portion of the guide vane 135 on the switching damper 133 side, the portion facing the switching damper 133 extends to the region near the switching damper 133, and the other portion extends to the vicinity of the defrost outlet 21B. Therefore, in the first setting position, the air in the high temperature hot air passage 25H flows into the defrost outlets 21A and 21B, and the air in the low temperature hot air passage 25L flows into the foot outlets 19F and 19R. Therefore, the air temperature at the defrost outlets 21A and 21B can be made higher than the air temperature at the foot outlets 19F and 19R. Since the other portion extends to the vicinity of the defrost outlet 21B at the second setting position, the air in the low temperature hot air flow path 25L flows into the defrost outlet 21A. The air in the high temperature hot air passage 25H flows into the defrost outlets 21A and 21B. That is, the air in the low temperature hot air flow path 25L is less likely to flow into the defrost outlet 21B by the guide vane 135. Therefore, the air temperature at the defrost outlet 21B is higher than the air temperature at the defrost outlet 21A. Since the other portion extends to the vicinity of the defrost outlet 21B at the third set position, a part of the air in the high temperature hot air flow path 25H flows into the defrost outlet 21B. The remaining air in the high-temperature hot-air channel 25H flows into the foot outlets 19F and 19R. The air in the low-temperature hot-air channel 25L flows into the foot outlets 19F and 19R. Therefore, the air temperature at the defrost outlet 21B is higher than the air temperature at the foot outlets 19F and 19R.

[Second Modification of First Embodiment]
Next, a second modification of the first embodiment of the present invention will be described with reference to FIG.
The basic configuration of the vehicle air conditioner of this modification is the same as that of the first embodiment, but the configuration of the guide vane is different from that of the first embodiment. Therefore, in this modified example, only the periphery of the configuration of the guide vane will be described with reference to FIG.
FIG. 12 is a schematic diagram illustrating the configuration of guide vanes in the HVAC unit according to the vehicle air conditioner of the present modification.
In addition, about the component same as 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 12, a HVAC unit (air conditioning unit) 203 according to a vehicle air conditioner (air conditioner) 201 includes a guide vane (mixing suppression unit ) 235 that is a partition plate, and a hinge (area control unit). 237.
The guide vane 235 is a partition plate that divides the hot air flow path 25 into a high temperature hot air flow path 25H and a low temperature hot air flow path 25L. A hinge 237 is provided at the end of the guide vane 235 on the mix region M side.
The hinge 237 controls the area of the inflow portion of the high temperature hot air flow path 25 and the area of the inflow portion of the low temperature hot air flow path 25L. The hinge 237 is swingably supported on the high temperature hot air flow path 25H side and the low temperature hot air flow path 25L side around the connection portion with the guide vane 235.

Next, the effect | action in the vehicle air conditioner 201 which consists of said structure is demonstrated.
First, the Defog operation mode that removes fogging of the windshield and side glass of the vehicle will be described.
Since the setting positions of the dampers in the defog operation mode in the present modification are the same as those in the first embodiment, the description thereof is omitted. Moreover, since the air flow at the time of driving the vehicle air conditioner 201 is the same as that of the first embodiment in which heated air and cooled air are mixed in the mixing region M, description thereof is omitted. .

Here, as shown in FIG. 12, the case where the hinge 237 has fallen to the low temperature hot air flow path 25L side is demonstrated.
The conditioned air mixed in the mix region M flows into the high temperature hot air flow path 25H and the low temperature hot air flow path 25L with insufficient mixing. Therefore, the ratio of the heated air in the mixed conditioned air increases as it goes from the low temperature hot air flow path 25L side to the high temperature hot air flow path 25H side. On the contrary, the ratio of the cooled air becomes higher as it goes from the high temperature hot air flow path 25H to the low temperature hot air flow path 25L.
In this state, when the hinge 237 falls to the low temperature hot air flow path 25L side, the inlet of the high temperature hot air flow path 25H expands in a direction approaching the low temperature hot air flow path 25L side, and the area thereof increases. Then, compared with the case where the hinge 237 is not tilted, the conditioned air on the low-temperature hot air flow path 25L side easily flows into the high-temperature hot air flow path 25H. Therefore, the cooled air in the conditioned air flowing through the high-temperature hot air flow path 25H The ratio of becomes higher. That is, the temperature of the conditioned air flowing through the high temperature hot air flow path 25H is lowered.
On the other hand, the inlet of the low temperature hot air flow path 25L becomes narrower in the direction away from the high temperature hot air flow path 25H, and the area becomes narrower. Then, compared to the case where the hinge 237 is not tilted, the conditioned air on the high temperature hot air flow path 25H side is less likely to flow into the low temperature hot air flow path 25L, so the heated air in the conditioned air flowing through the low temperature hot air flow path 25L. The ratio of becomes lower. That is, the temperature of the conditioned air flowing through the low temperature hot air flow path 25L is lowered.
As a result, the temperature of the conditioned air at the defrost outlets 21A and 21B and the foot outlets 19F and 19R can be lowered.

On the contrary, the case where the hinge 237 has fallen to the high temperature hot air flow path 25H side is demonstrated.
When the hinge 237 falls to the high temperature hot air flow path 25H side, the inlet of the high temperature hot air flow path 25H becomes narrower in the direction away from the low temperature hot air flow path 25L, and the area becomes narrow. Then, compared with the case where the hinge 237 is not tilted, the conditioned air on the low-temperature hot air flow path 25L side is less likely to flow into the high-temperature hot air flow path 25H. The ratio of becomes lower. That is, the temperature of the conditioned air flowing through the high temperature hot air flow path 25H increases.
On the other hand, the inlet of the low temperature hot air flow path 25L spreads in the direction approaching the high temperature hot air flow path 25H side, and the area becomes large. Compared with the case where the hinge 237 is not tilted, the conditioned air on the high temperature hot air flow path 25H side easily flows into the low temperature hot air flow path 25L, so the ratio of the heated air in the conditioned air flowing through the low temperature hot air flow path 25L Becomes higher. That is, the temperature of the conditioned air flowing through the low temperature hot air flow path 25L increases.
As a result, the temperature of the conditioned air at the defrost outlets 21A and 21B and the foot outlets 19F and 19R can be increased.

The air flow in the vicinity of the hinge 237 in the other operation modes is the same as the air flow in the above-described Defog operation mode, and thus the description thereof is omitted.
In addition, the air flow in the other operation modes is the same as that in the first embodiment, and thus the description thereof is omitted.

According to the above configuration, since the hinge 237 is provided, the conditioned air temperature at the defrost outlets 21A and 21B and the conditioned air temperature at the foot outlets 19F and 19R can be adjusted.
Air heated from the high temperature hot air flow path 25H flows into the high temperature hot air flow path 25L and air cooled from the low temperature hot air flow path 25L flows into the high temperature hot air flow path 25L. Therefore, the heated air is more likely to flow into the high-temperature hot air flow path 25H as compared with the cooled air. On the other hand, the cooled air easily flows into the low-temperature hot air flow path 25L. Here, the hinge 237 is provided at the end of the guide vane 235, and the outer peripheral wall of the hot / warm air flow path 25 is fixed. Therefore, when the inlet area of the high temperature hot air passage 25H is narrowed by the hinge 237, the inlet becomes narrower in the direction away from the low temperature hot air passage 25L. On the other hand, when the inlet area of the low temperature hot air channel 25L is increased, the inlet becomes wider in the direction approaching the high temperature hot air channel 25H. Then, the flow rate of the cooled air flowing into the high temperature hot air flow path 25H decreases, and the ratio of the heated air to the conditioned air flowing through the high temperature hot air flow path 25H increases. On the other hand, the flow rate of the heated air flowing into the low temperature hot air flow path 25L increases, and the ratio of the heated air to the conditioned air flowing through the low temperature hot air flow path 25L increases.
As a result, the temperature of the conditioned air blown out from the high temperature hot air passage 25H and the low temperature hot air passage 25L through the defrost outlets 21A and 21B and the foot outlets 19F and 19R increases.
On the contrary, when the inlet area of the high temperature hot air flow path 25H is widened by the hinge 237 and the inlet area of the low temperature hot air flow path 25L is narrowed, the defrost outlet from the high temperature hot air flow path 25H and the low temperature hot air flow path 25L. The temperature of the conditioned air blown out through 21A, 21B and the foot outlets 19F, 19R is lowered.

[Third Modification of First Embodiment]
Next, a third modification of the first embodiment of the present invention will be described with reference to FIG.
The basic configuration of the vehicle air conditioner of this modification is the same as that of the first embodiment, but the configuration of the guide vane is different from that of the first embodiment. Therefore, in this modification, only the periphery of the configuration of the guide vane will be described with reference to FIG.
FIG. 13 is a schematic diagram illustrating the configuration of guide vanes in the HVAC unit according to the vehicle air conditioner of the present modification.
In addition, about the component same as 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 13, a HVAC unit (air conditioning unit) 303 according to a vehicle air conditioner (air conditioner) 301 includes a guide vane (mixing suppression unit ) 335 that is a partition plate, and a slide door (area control unit). 337).
The guide vane 335 is a partition plate that divides the hot air passage 25 into a high temperature hot air passage 25H and a low temperature hot air passage 25L. A slide door 337 is provided at the end of the guide vane 335 on the mix region M side.
The slide door 337 controls the area of the inflow portion of the high temperature hot air flow path 25 and the area of the inflow portion of the low temperature hot air flow path 25L. The slide door 337 is a plate member that extends in a direction intersecting the guide vane 235, and is supported so as to be slidable on the high temperature hot air flow path 25H side and the low temperature hot air flow path 25L side.

Next, the effect | action in the vehicle air conditioner 301 which consists of said structure is demonstrated.
First, the Defog operation mode that removes fogging of the windshield and side glass of the vehicle will be described.
Since the setting positions of the dampers in the defog operation mode in the present modification are the same as those in the first embodiment, the description thereof is omitted. Moreover, since the air flow at the time of driving the vehicle air conditioner 301 is the same as that of the first embodiment in which heated air and cooled air are mixed in the mixing region M, description thereof is omitted. .

Here, as shown in FIG. 13, the case where the slide door 337 is slid to the low temperature hot air flow path 25L side is demonstrated.
The conditioned air mixed in the mix region M flows into the high temperature hot air flow path 25H and the low temperature hot air flow path 25L with insufficient mixing. Therefore, the ratio of the heated air in the mixed conditioned air increases as it goes from the low temperature hot air flow path 25L side to the high temperature hot air flow path 25H side. On the contrary, the ratio of the cooled air becomes higher as it goes from the high temperature hot air flow path 25H to the low temperature hot air flow path 25L.
In this state, when the slide door 337 slides to the low temperature hot air flow path 25L side, the inlet of the high temperature hot air flow path 25H expands in a direction approaching the low temperature hot air flow path 25L side, and its area increases. Then, compared with the case where the slide door 337 is not slid, the conditioned air on the low temperature hot air flow path 25L side easily flows into the high temperature hot air flow path 25H. Increased air ratio. That is, the temperature of the conditioned air flowing through the high temperature hot air flow path 25H is lowered.
On the other hand, the inlet of the low temperature hot air flow path 25L becomes narrower in the direction away from the high temperature hot air flow path 25H, and the area becomes narrower. Then, compared with the case where the slide door 337 is not slid, the conditioned air on the high temperature hot air flow path 25H side is less likely to flow into the low temperature hot air flow path 25L. The air ratio becomes lower. That is, the temperature of the conditioned air flowing through the low temperature hot air flow path 25L is lowered.
As a result, the temperature of the conditioned air at the defrost outlets 21A and 21B and the foot outlets 19F and 19R can be lowered.

On the contrary, the case where the slide door 337 is slid to the high temperature hot air flow path 25H side is demonstrated.
When the slide door 337 slides toward the high temperature hot air flow path 25H, the inlet of the high temperature hot air flow path 25H becomes narrower in the direction away from the low temperature hot air flow path 25L, and the area thereof becomes narrow. Then, compared with the case where the slide door 337 is not slid, the conditioned air on the low-temperature hot air flow path 25L side is less likely to flow into the high-temperature hot air flow path 25H, so that the conditioned air flowing through the high-temperature hot air flow path 25H is cooled. The air ratio becomes lower. That is, the temperature of the conditioned air flowing through the high temperature hot air flow path 25H increases.
On the other hand, the inlet of the low temperature hot air flow path 25L spreads in the direction approaching the high temperature hot air flow path 25H side, and the area becomes large. Compared with the case where the slide door 337 is not slid, the conditioned air on the high temperature hot air flow path 25H side easily flows into the low temperature hot air flow path 25L, so the heated air in the conditioned air flowing through the low temperature hot air flow path 25L The ratio of becomes higher. That is, the temperature of the conditioned air flowing through the low temperature hot air flow path 25L increases.
As a result, the temperature of the conditioned air at the defrost outlets 21A and 21B and the foot outlets 19F and 19R can be increased.

  The air flow in the vicinity of the slide door 337 in the other operation modes is the same as the air flow in the above-described Defog operation mode, and thus the description thereof is omitted.

According to the above configuration, since the slide door 337 is provided, the conditioned air temperature at the defrost outlets 21A and 21B and the conditioned air temperature at the foot outlets 19F and 19R can be adjusted.
Air heated from the high temperature hot air flow path 25H flows into the high temperature hot air flow path 25L and air cooled from the low temperature hot air flow path 25L flows into the high temperature hot air flow path 25L. Therefore, the heated air is more likely to flow into the high-temperature hot air flow path 25H as compared with the cooled air. On the other hand, the cooled air easily flows into the low-temperature hot air flow path 25L. Here, the slide door 337 is provided at the end of the guide vane 235, and the outer peripheral wall of the hot / warm air flow path 25 is fixed. Therefore, if the inlet area of the high temperature hot air passage 25H is narrowed by the slide door 337, the inlet becomes narrower in the direction away from the low temperature hot air passage 25L. On the other hand, when the inlet area of the low temperature hot air channel 25L is increased, the inlet becomes wider in the direction approaching the high temperature hot air channel 25H. Then, the flow rate of the cooled air flowing into the high temperature hot air flow path 25H decreases, and the ratio of the heated air to the conditioned air flowing through the high temperature hot air flow path 25H increases. On the other hand, the flow rate of the heated air flowing into the low temperature hot air flow path 25L increases, and the ratio of the heated air to the conditioned air flowing through the low temperature hot air flow path 25L increases.
As a result, the temperature of the conditioned air blown out from the high temperature hot air passage 25H and the low temperature hot air passage 25L through the defrost outlets 21A and 21B and the foot outlets 19F and 19R increases.
Conversely, when the inlet area of the high temperature hot air passage 25H is widened by the slide door 337 and the inlet area of the low temperature hot air passage 25L is narrowed, the defrost blow from the high temperature hot air passage 25H and the low temperature hot air passage 25L. The temperature of the conditioned air blown out through the outlets 21A and 21B and the foot outlets 19F and 19R is lowered.

[Fourth Modification of First Embodiment]
Next, a fourth modification of the first embodiment of the present invention will be described with reference to FIG.
The basic configuration of the vehicle air conditioner of this modification is the same as that of the first embodiment, but the configuration of the guide vane is different from that of the first embodiment. Therefore, in this modification, only the periphery of the configuration of the guide vane will be described with reference to FIG. 14, and description of other components will be omitted.
FIG. 14 is a schematic diagram illustrating the configuration of guide vanes in the HVAC unit according to the vehicle air conditioner of the present modification.
In addition, about the component same as 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 14, a HVAC unit (air conditioning unit) 403 according to a vehicle air conditioner (air conditioner) 401 includes a guide vane (mixing suppression unit ) 435 that is a partition plate, and a vane length variable unit (end). Part moving part) 437.
The guide vane 435 is a partition plate that divides the hot air passage 25 into a high temperature hot air passage 25H and a low temperature hot air passage 25L. The guide vane 435 has a shorter overall length than the guide vane of the first embodiment, and the end position on the mix area M side is a position away from the mix area M. A vane length variable portion 437 is provided at an end portion of the guide vane 435 on the mix region M side.
The vane length variable unit 437 controls the entire length of the guide vane 435. The vane length variable portion 437 is a plate member extending in a direction along the surface of the guide vane 435 and is slidably supported so as to be able to approach and separate from the mix region M.

Next, the effect | action in the vehicle air conditioner 401 which consists of said structure is demonstrated.
First, the Defog operation mode that removes fogging of the windshield and side glass of the vehicle will be described.
Since the setting positions of the dampers in the defog operation mode in the present modification are the same as those in the first embodiment, the description thereof is omitted. Moreover, since the air flow at the time of driving | running the vehicle air conditioner 401 is the same as that of 1st Embodiment with which the heated air and the cooled air are mixed in the mixing area | region M, the description is abbreviate | omitted. .

Here, as shown in FIG. 14, the case where the vane length variable portion 437 slides in the direction away from the mix region M, that is, the case where the total length of the guide vane 435 is shortened will be described.
In this state, the hot air flow path 25 is divided by the guide vane 435 and the vane length variable portion 437 into an area divided into the high temperature and low temperature hot air flow paths 25H and 25L and an area where the hot air flow path 25 remains.
The conditioned air mixed in the mix region M flows into the hot air flow path 25 in a state where mixing is insufficient. That is, the air flows into the hot air channel 25 in a state where there is a temperature difference between the conditioned air on the high temperature hot air channel 25H side and the conditioned air on the low temperature hot air channel 25L side. The conditioned air is mixed while flowing through the hot air flow path 25, and the temperature difference is reduced. The conditioned air flows into the high-temperature hot-air channel 25H and the low-temperature hot-air channel 25L in a state where the temperature difference is small.
As a result, the temperature difference between the conditioned air at the defrost outlets 21A and 21B and the conditioned air at the foot outlets 19F and 19R can be reduced.

On the contrary, the case where the vane length variable part 437 slides in the direction approaching the mix region M, that is, the case where the total length of the guide vane 435 is increased will be described.
In this state, the hot air flow path 25 is substantially divided into high temperature and low temperature hot air flow paths 25H and 25L by the guide vane 435 and the vane length variable portion 437.
The conditioned air mixed in the mix region M flows into the high-temperature and low-temperature hot air flow paths 25H and 25L with insufficient mixing. That is, it flows into the high temperature and low temperature hot air flow paths 25H and 25L in a state where there is a temperature difference between the conditioned air on the high temperature hot air flow path 25H side and the conditioned air on the low temperature hot air flow path 25L side. Therefore, high-temperature conditioned air flows into the high-temperature hot-air channel 25H, and low-temperature conditioned air flows into the low-temperature hot-air channel 25L.
As a result, the temperature difference between the conditioned air at the defrost outlets 21A and 21B and the conditioned air at the foot outlets 19F and 19R can be increased.

  The air flow in the vicinity of the vane length variable portion 437 in the other operation modes is the same as the air flow in the above-described Defog operation mode, and thus the description thereof is omitted.

According to said structure, since the vane length variable part 437 is provided, the temperature difference of the air temperature in defrost outlet 21A, 21B and the air temperature in foot outlet 19F, 19R can be adjusted.
Air heated from the high temperature hot air flow path 25H flows into the high temperature and low temperature hot air flow paths 25H and 25L, and cooled air flows from the low temperature hot air flow path 25L. Therefore, the heated air is more likely to flow into the high-temperature hot air flow path 25H as compared with the cooled air. On the other hand, the cooled air easily flows into the low-temperature hot air flow path 25L. Here, the vane length variable unit 437 can move the end position of the guide vane 435 on the side of the mix region M (air-conditioned air inflow) along the direction along the surface of the guide vane 435 (the flow direction of air-conditioned air). it can.
For example, when the end position of the vane length variable portion 437 is moved in a direction approaching the mix region M (upstream side of the air flow), the heated air flowing into the high temperature and low temperature hot air flow paths 25H and 25L and the cooled air are cooled. The area where the air is mixed can be narrowed (the mixing distance is shortened). That is, the temperature difference of the conditioned air in the high temperature and low temperature hot air flow paths 25H and 25L can be increased. On the other hand, when the end position of the vane length variable portion 437 is moved in the direction away from the mix region M (downstream side of the air flow), the heated air flowing into the high temperature and low temperature hot air flow paths 25H and 25L and the cooled air are cooled. The area where the air is mixed can be widened (the mixing distance is increased). That is, the temperature difference of the conditioned air in the high temperature and low temperature hot air flow paths 25H and 25L can be reduced.

[Fifth Modification of First Embodiment]
Next, a fifth modification of the first embodiment of the present invention will be described with reference to FIG.
The basic configuration of the vehicle air conditioner of this modification is the same as that of the first embodiment, but the configuration of the guide vane is different from that of the first embodiment. Therefore, in this modification, only the periphery of the configuration of the guide vane will be described with reference to FIG. 15, and description of other components will be omitted.
FIG. 15 is a schematic diagram illustrating the configuration of guide vanes in the HVAC unit according to the vehicle air conditioner of the present modification.
In addition, about the component same as 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 15, the HVAC unit (air conditioning unit) 503 according to the vehicle air conditioner (air conditioner) 501 includes a guide vane (mixing suppression unit ) 535 that is a partition plate, and a vane length extension portion (end). Part moving part) 537.
The guide vane 535 is a partition plate that divides the hot air flow path 25 into a high temperature hot air flow path 25H and a low temperature hot air flow path 25L. The guide vane 535 has a shorter overall length than the guide vane of the first embodiment, and the end position on the mix area M side is a position away from the mix area M. A vane length extension 537 is provided at the end of the guide vane 535 on the side of the mix region M.
The vane length extension 537 extends the entire length of the guide vane 535. The vane length extension part 537 is a plate member arranged in a direction along the surface of the guide vane 535. The vane length extension part 537 is formed in a predetermined length according to a customer's request, for example, and is disposed at the end of the guide vane 535.

Next, the operation of the vehicle air conditioner 501 having the above configuration will be described.
First, the Defog operation mode that removes fogging of the windshield and side glass of the vehicle will be described.
Since the setting positions of the dampers in the defog operation mode in the present modification are the same as those in the first embodiment, the description thereof is omitted. Moreover, since the air flow at the time of driving | running | working the air conditioning apparatus 501 for vehicles is the same as that of 1st Embodiment with which the heated air and the cooled air are mixed in the mixing area | region M, the description is abbreviate | omitted. .

Here, as shown in FIG. 15, the case where the vane length extension part 537 is short, that is, the case where the total length of the guide vane 535 is shortened will be described.
In this state, the hot air channel 25 is divided into a region divided into the high temperature and low temperature hot air channels 25H and 25L by the guide vane 535 and the vane length extension 537, and a region where the hot air channel 25 remains.
The conditioned air mixed in the mix region M flows into the hot air flow path 25 in a state where mixing is insufficient. That is, the air flows into the hot air channel 25 in a state where there is a temperature difference between the conditioned air on the high temperature hot air channel 25H side and the conditioned air on the low temperature hot air channel 25L side. The conditioned air is mixed while flowing through the hot air flow path 25, and the temperature difference is reduced. The conditioned air flows into the high-temperature hot-air channel 25H and the low-temperature hot-air channel 25L in a state where the temperature difference is small.
As a result, the temperature difference between the conditioned air at the defrost outlets 21A and 21B and the conditioned air at the foot outlets 19F and 19R can be reduced.

On the contrary, the case where the vane length extension part 537 is long, that is, the case where the total length of the guide vane 535 becomes long will be described.
In this state, the warm air flow path 25 is divided into a high temperature and a low temperature warm air flow path 25H, 25L by a guide vane 535 and a vane length extension 537.
The conditioned air mixed in the mix region M flows into the high-temperature and low-temperature hot air flow paths 25H and 25L with insufficient mixing. That is, it flows into the high temperature and low temperature hot air flow paths 25H and 25L in a state where there is a temperature difference between the conditioned air on the high temperature hot air flow path 25H side and the conditioned air on the low temperature hot air flow path 25L side. Therefore, high-temperature conditioned air flows into the high-temperature hot-air channel 25H, and low-temperature conditioned air flows into the low-temperature hot-air channel 25L.
As a result, the temperature difference between the conditioned air at the defrost outlets 21A and 21B and the conditioned air at the foot outlets 19F and 19R can be increased.

  Since the air flow in the vicinity of the vane length extension portion 537 in the other operation modes is the same as the air flow in the above-described Defog operation mode, description thereof is omitted.

According to said structure, since the vane length extension part 537 is provided, the temperature difference of the air temperature in defrost outlet 21A, 21B and the air temperature in foot outlet 19F, 19R can be adjusted.
Air heated from the high temperature hot air flow path 25H flows into the high temperature and low temperature hot air flow paths 25H and 25L, and cooled air flows from the low temperature hot air flow path 25L. Therefore, the heated air is more likely to flow into the high-temperature hot air flow path 25H as compared with the cooled air. On the other hand, the cooled air easily flows into the low-temperature hot air flow path 25L. Here, the vane length extension part 537 can move the end position of the guide vane 535 on the side of the mix region M (air-conditioned air inflow) along the direction along the surface of the guide vane 535 (the flow direction of air-conditioned air). it can.
For example, when the end position of the vane length extension 537 is moved in a direction approaching the mix region M (upstream side of the air flow), the heated air flowing into the high temperature and low temperature hot air flow paths 25H and 25L and the cooled air are cooled. The area where the air is mixed can be narrowed (the mixing distance is shortened). That is, the temperature difference of the conditioned air in the high temperature and low temperature hot air flow paths 25H and 25L can be increased. On the other hand, when the end position of the vane length extension 537 is moved in the direction away from the mix region M (downstream side of the air flow), the heated air flowing into the high temperature and low temperature hot air flow paths 25H and 25L and the cooled air The area where the air is mixed can be widened (the mixing distance is increased). That is, the temperature difference of the conditioned air in the high temperature and low temperature hot air flow paths 25H and 25L can be reduced.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG.
The basic configuration of the vehicle air conditioner of the present embodiment is the same as that of the first embodiment, but the configuration of the hot air flow path is different from that of the first embodiment. Therefore, in this embodiment, only the periphery of the configuration of the hot air flow path will be described with reference to FIG. 16, and description of other components and the like will be omitted.
FIG. 16 is a schematic diagram illustrating the configuration of the HVAC unit according to the vehicle air conditioner of the present embodiment.
In addition, about the component same as 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 16, the HVAC unit (air conditioning unit) 603 according to the vehicle air conditioning apparatus (air conditioning apparatus) 601 includes a casing (housing) 611, an evaporator 13, and a heater core 15.
The casing 611 accommodates the evaporator 13 and the heater core 15 inside. The casing 611, in the flow direction of the conditioned air, the vent outlet 17F in this order from the upstream side, and 617R, the foot outlet 6 19F, 619R and defrost outlet 21A, 21B are provided. The foot outlets 619F and 619R are arranged above (on the vent outlet 17F side) as compared to the first embodiment. The vent air outlet 17F and the foot air outlet 619F blow out conditioned air to the upper body side and the lower body side of the occupant seated in the front seat of the vehicle, respectively. The vent outlet 617R and the foot outlet 619R blow out conditioned air to the upper body side and the lower body side of the occupant seated in the rear seat of the vehicle, respectively.

In the casing 611, as shown in FIG. 2, an air passage partition plate 23 is provided at a position facing the air outflow surface of the heater core 15 with a predetermined interval. On the back side (right side in FIG. 16) of the air passage partition plate 23 as viewed from the heater core 15 side, the temperature from the mixing region M formed on the downstream side of the evaporator 13 and on the upper portion of the heater core 15 between the casing 611. Hot air passages (air conditioning air passages) 625 that are in communication with the foot air outlets 619F and 619R and the defrost air outlets 21A and 21B are formed. The hot air flow path 625 has a shorter overall length compared to the first embodiment.
A switching damper 33 that swings about the shaft 33A as a fulcrum is provided at a branch portion of the hot air flow path 625.

Next, the operation of the vehicle air conditioner 601 having the above configuration will be described.
First, the Defog operation mode that removes fogging of the windshield and side glass of the vehicle will be described.
Since the setting position of each damper at the time of the Defrost operation mode in this embodiment is the same as that of the first embodiment, the description thereof is omitted. The air flow during operation of the vehicle air conditioner 601 is the same as in the first embodiment until the heated and cooled air flows into the mix region M, and a description thereof will be omitted.

The conditioned air mixed in the mix region M flows into the hot air flow path 625 with insufficient mixing. That is, the air flows into the hot air flow path 625 in a state where there is a temperature difference between the conditioned air on the air passage partition plate 23 side and the conditioned air on the casing 611 side. Since the hot air flow path 625 has a short overall length compared to the first embodiment, the temperature difference remains until a part of the conditioned air flows into the foot outlets 619F and 619R. Therefore, conditioned air with a large ratio of cooled air flows into the foot outlets 619F and 619R. The remaining conditioned air with a large proportion of heated air flows into the defrost outlets 21 </ b> A and 21 </ b> B through the hot air flow path 625.
As a result, the temperature of the conditioned air at the defrost outlets 21A and 21B can be made higher than the temperature of the conditioned air at the foot outlets 619F and 619R.

  The air flow in the vicinity of the hot air flow path 625 in the other operation modes is the same as the air flow in the above-described Defog operation mode, and thus the description thereof is omitted.

According to said structure, while the air heated from the side in which the air-path partition plate 23 (defrost blower outlet 21A, 21B) was provided flows into the warm air flow path 625, the casing 611 (foot blower outlet 619F, 619R) is supplied from the side where the air is cooled, foot outlets 619F and 619R are provided on the air inflow side (on the air mix region M side) in the hot air flow path 625, and the defrost outlets 21A and 21B are provided. Since it is provided on the air outflow side, the air temperature at the defrost outlets 21A and 21B can be made higher than the air temperature at the foot outlets 619F and 619R.
Heated air flows into the hot air flow path 625 from the side where the defrost outlets 21A and 21B are provided, and cooled air flows from the side where the foot outlets 619F and 619R are provided. Therefore, on the air inflow side of the hot air flow path 625, the ratio of heated air is high on the side where heated air flows, and the ratio of cooled air is high on the side where cooled air flows. Become. In other words, the temperature of the conditioned air on the side where the heated air flows in the hot air flow path 625 becomes higher than the temperature of the conditioned air on the side where the cooled air flows. Here, the foot outlets 619F and 619R are provided on the air inflow side in the warm air flow path 625. On the other hand, the defrost outlets 21 </ b> A and 21 </ b> B are provided on the air outflow side in the warm air flow path 625. Therefore, the conditioned air having a low temperature flows out from the hot air channel 625 on the air inflow side of the hot air channel 625. That is, the conditioned air having a high temperature and the conditioned air having a low temperature are separated on the air inflow side in the warm air flow path 625. After separation, since the mixing of the conditioned air having a high temperature and the conditioned air having a low temperature does not proceed, the air temperature at the defrost outlets 21A and 21B can be made higher than the air temperature at the foot outlets 619F and 619R. .

[Third Embodiment]
Next, a third embodiment of the present invention will be described with reference to FIG.
The basic configuration of the vehicle air conditioner of the present embodiment is the same as that of the first embodiment, but is different from the first embodiment in the vicinity of the hot air flow path. Therefore, in this embodiment, only the vicinity of the vicinity of the hot air flow path will be described with reference to FIG.
FIG. 17 is a schematic diagram illustrating the configuration of the HVAC unit according to the vehicle air conditioner of this embodiment.
In addition, about the component same as 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 17, the HVAC unit (air conditioning unit) 703 according to the vehicle air conditioner (air conditioner) 701 includes a casing (housing) 711, an evaporator 13, and a heater core 15.
The casing 711 is provided with an air passage partition plate 723 at a position facing the air outflow surface of the heater core 15 with a predetermined interval. The air passage partition plate 723 is provided upward from the lower end support surface of the heater core 15 to the vicinity of the mix region M substantially parallel to the heater core 15. The upper end portion of the air passage partition plate 723 is formed in a curved surface that faces substantially forward, and is formed in a streamline shape. In addition, an opening 725 through which air heated by the heater core 15 flows into the hot air flow path 25 is provided in the vicinity of the lower end of the air path partition plate 723. The air path partition plate 723 on the lower end side from the opening 725 is disposed so as to protrude from the air path partition plate 723 above the opening 725 toward the warm air flow path 25.

A switching damper (damper) 733 that swings around the shaft 733A is provided at a branch portion of the hot air flow path 25. As in the first embodiment, the switching damper 733 swings between three positions so that a desired blowing mode can be selected depending on the position of the switching damper 733. At the same time, the switching damper 733 controls opening / closing of the opening 725 of the air passage partition plate 723.
That is, the position of the first switching damper 733 is such that the switching damper 733 falls to the defrost outlets 21A and 21B, the foot outlets 19F and 19R are fully opened, and the defrost outlet 21A is fully closed. Position. At this time, the opening 725 of the air passage partition plate 723 is closed by the tip of the switching damper 733 and is fully closed. The position of the second switching damper 733 is such that the switching damper 733 falls to the foot outlets 19F and 19R, the foot outlets 19F and 19R are fully closed, and the defrost outlets 21A and 21B are fully opened. Position. At this time, the opening 725 of the air passage partition plate 723 is fully opened. The position of the third switching damper 733 is such that the switching damper 733 is positioned between the foot outlets 19F and 19R and the defrost outlets 21A and 21B, and the foot outlets 19F and 19R and the defrost outlets 21A and 21B are opened. Position. At this time, the opening 725 of the air passage partition plate 723 is fully opened.

Next, the effect | action in the air conditioning apparatus 701 for vehicles which consists of said structure is demonstrated.
First, the Defog operation mode that removes fogging of the windshield and side glass of the vehicle will be described.
Since the setting positions of the respective dampers in the defog operation mode in the present embodiment are the same as those in the first embodiment, the description thereof is omitted. The air flow during operation of the vehicle air conditioner 701 is the same as that in the first embodiment until the introduced air is cooled and heated by the evaporator 13 and the heater core 15, and thus the description thereof is omitted.
Most of the air heated through the heater core 15 flows along the air passage partition plate 723 and is mixed with the air cooled by the evaporator 13 in the mix region M to become conditioned air. On the other hand, a part of the heated air described above flows into the hot air flow path 25 from the opening 725 of the air passage partition plate 723 as described later.

  The conditioned air mixed in the mix region M flows into the hot air flow path 25, and part of the conditioned air flows into the foot outlets 19F and 19R by the switching damper 733. On the other hand, the remaining conditioned air is mixed with the heated air flowing in from the opening 725 described above, and flows into the defrost outlets 21A and 21B. Therefore, conditioned air having a temperature higher than the conditioned air at the foot outlets 19F and 19R is blown from the defrost outlets 21A and 21B to the windshield and the side glass, respectively. From the foot outlets 19F and 19R, conditioned air having a temperature lower than that of the conditioned air at the defrost outlets 21A and 21B is blown out to the feet of the front seat and the rear seat of the passenger compartment, respectively.

Next, the Defrost operation mode for removing frost on the windshield and side glass of the vehicle will be described.
Since the setting position of each damper at the time of the Defrost operation mode in this embodiment is the same as that of the first embodiment, the description thereof is omitted.
Most of the air heated through the heater core 15 flows along the air passage partition plate 723 and is mixed with the air cooled by the evaporator 13 in the mix region M to become conditioned air. On the other hand, a part of the heated air described above flows into the hot air flow path 25 from the opening 725 of the air passage partition plate 723 as described later.
The conditioned air mixed in the mix region M flows into the warm air flow path 25, and all flows into the defrost outlets 21 </ b> A and 21 </ b> B by the switching damper 733. On the other hand, the heated air that has flowed into the warm air passage 25 from the opening 725 described above also flows into the defrost outlets 21A and 21B. Therefore, air in which the conditioned air mixed in the mix region M and the heated air flowing in from the opening 725 are mixed is blown out from the defrost outlets 21A and 21B.

Next, a description will be given of the Heater operation mode in which warm air is blown out to the feet of the front seat and rear seat of the vehicle.
Since the setting positions of the respective dampers in the heater operation mode in the present embodiment are the same as those in the first embodiment, the description thereof is omitted.
The total amount of the air heated through the heater core 15 flows along the air passage partition plate 723 and flows into the mix region M because the opening 725 is closed by the switching damper 733. The heated air that has flowed into the mixing region M is mixed with the air cooled by the evaporator 13 to become conditioned air.
The conditioned air mixed in the mix region M flows into the hot air flow path 25, and all flows into the foot outlets 19F and 19R and the defrost outlet 21B by the switching damper 733. Therefore, the conditioned air mixed in the mix region M is blown out from the foot outlets 19F and 19R and the defrost outlet 21B.

  In addition, since the air flow in other operation modes is the same as that of 1st Embodiment, the description is abbreviate | omitted.

According to said structure, since the opening part 725 provided in the air-path partition plate 723 and the switching damper 733 are provided, the air temperature in defrost blower outlet 21A, 21B is made into foot blower outlet 19F, 19R. It can be higher than the air temperature.
The hot air flow path 25 can guide the air cooled by the cooling unit and the air heated by the heating unit to the defrost outlets 21A and 21B and the foot outlets 19F and 19R. In the hot air flow path 25, the conditioned air is a mixture of cooled air and heated air. Here, the switching damper 733 can perform opening / closing control of the opening 725 provided in the air passage partition plate 723. Part of the air heated in the heating unit through the open opening 725 flows into the hot air flow path 25. Since the switching damper 733 controls the inflow of air from the hot air flow path 25 to the defrost outlets 21A and 21B and the foot outlets 19F and 19R, some heated air flows only into the defrost outlets 21A and 21B. To do. As a result, the ratio of the heated air in the conditioned air blown out from the defrost outlets 21A and 21B is increased, and the conditioned air blown out from the defrost outlets 21A and 21B is compared with the conditioned air blown out from the foot outlets 19F and 19R. The temperature rises.

It is a perspective view explaining the schematic structure of the HVAC unit in the air harmony device for vehicles concerning a 1st embodiment of the present invention. It is AA sectional drawing explaining the structure of the HVAC unit of FIG. It is a graph which concerns on the air-conditioning air temperature which blows off from the air conditioning apparatus for vehicles of FIG. It is a schematic diagram explaining the flow of the air at the time of the Defrost operation mode in the HVAC unit of FIG. It is a schematic diagram explaining the flow of the air at the time of the Heater operation mode in the HVAC unit of FIG. It is a schematic diagram explaining the flow of the air at the time of the cooling operation mode in the HVAC unit of FIG. It is a schematic diagram explaining the arrangement | positioning relationship of the guide vane and the switching damper in the HVAC unit which concerns on the vehicle air conditioner of the 1st modification of the 1st Embodiment of this invention. It is a schematic diagram explaining the shape of the guide vane of FIG. It is a graph which concerns on the air-conditioning air temperature which blows off from the air conditioning apparatus for vehicles of FIG. It is a schematic diagram explaining the air flow around the switching damper in the Defrost operation mode. It is a schematic diagram explaining the air flow around the switching damper in the Heater operation mode. It is a schematic diagram explaining the structure of the guide vane in the HVAC unit which concerns on the air conditioning apparatus for vehicles of the 2nd modification of the 1st Embodiment of this invention. It is a schematic diagram explaining the structure of the guide vane in the HVAC unit which concerns on the air conditioning apparatus for vehicles of the 3rd modification of the 1st Embodiment of this invention. It is a schematic diagram explaining the structure of the guide vane in the HVAC unit which concerns on the air conditioning apparatus for vehicles of the 4th modification of the 1st Embodiment of this invention. It is a schematic diagram explaining the structure of the guide vane in the HVAC unit which concerns on the vehicle air conditioner of the 5th modification of the 1st Embodiment of this invention. It is a schematic diagram explaining the structure of the HVAC unit which concerns on the vehicle air conditioner of 2nd Embodiment of this invention. It is a schematic diagram explaining the structure of the HVAC unit which concerns on the air conditioning apparatus for vehicles of 3rd Embodiment of this invention.

Explanation of symbols

1, 101, 201, 301, 401, 501, 601, 701 Vehicle air conditioner (air conditioner)
3,103,203,303,403,503,603,703 HVAC unit (air conditioning unit)
11,611,711 Casing (housing)
13 Evaporator (cooling part)
15 Heater core (heating part)
19F, 19R, 619F, 619R foot outlet 21A, 21B defrost outlet 25,625 warm air passage (air-conditioned air flow path)
33,133,733 Foot / defrost switching damper (damper)
25H high temperature hot air flow path (high temperature air flow path)
25L Low temperature hot air flow path (low temperature air flow path)
35, 235, 335, 435, 535 Guide vane (mixing suppression part)
237 Hinge (Area Control Unit)
337 Sliding door (area control unit)
437 Vane length variable part (end moving part)
5 37 Vane length extension (end moving part)
723 Airway partition 725 Opening

Claims (4)

A housing,
A cooling unit for cooling the air introduced into the housing;
A heating unit for heating the air introduced into the housing;
A mix region for mixing the air cooled by the cooling unit and the air heated by the heating unit;
An air-conditioning air flow path that is provided on the downstream side of the mixing region and that is cooled by the cooling unit, and that is heated by the heating unit, to guide the defrost outlet and the foot outlet.
Provided in the conditioned air flow path, the conditioned air flow path,
High-temperature air flow path into which high-temperature conditioned air that is connected to the defrost outlet and mixed in the mix region has a high ratio of air heated by the heating unit,
Mixing that is a partition plate that is connected to the foot outlet and is divided into a low-temperature air passage into which low-temperature conditioned air that has a high ratio of air cooled by the cooling unit flows out of the conditioned air mixed in the mix region A suppression unit ,
One and the other defrost outlets are arranged opposite the hot air flow path ;
The foot outlet is disposed opposite the low temperature air flow path;
There is provided one damper for controlling the air flowing from the high temperature and low temperature air flow paths to be supplied to the one defrost outlet and the foot outlet at a predetermined ratio,
The portion facing the damper at the damper side end of the mixing suppression portion extends to a region near the damper,
The other part of the end portion on the damper side extends to the vicinity of the other defrost outlet . The heated air flows into the inlet of the high temperature and low temperature air flow path from the high temperature air flow path side through the mix region ,
The cooled air flows into the inlet of the high temperature and low temperature air flow path from the low temperature air flow path side through the mix region ,
An area control unit for controlling the inlet area of the high-temperature air channel and the inlet area of the low-temperature air channel is provided at an end of the mixing suppression unit on the mix region side. The air conditioning unit according to claim 1 . The heated air flows into the inlet of the high temperature and low temperature air flow path from the high temperature air flow path side through the mix region ,
The cooled air flows into the inlet of the high temperature and low temperature air flow path from the low temperature air flow path side through the mix region ,
Of the mixing suppressing portion, the end portion of the mix region side, claims, characterized in that the end portion moving portion that moves the end position of the mixing suppressing portion in the flow direction of the air is provided The air conditioning unit according to 1 or 2. An air conditioning apparatus comprising the air conditioning unit according to any one of claims 1 to 3 .

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