JP6375904B2 - Air conditioner for vehicles - Google Patents

Description

  The present invention relates to an air conditioner used in a vehicle.

  Conventionally, in a general vehicle air conditioner, engine cooling water (hot water) for cooling a vehicle engine is used as a heat source for heating. In recent years, the temperature of engine cooling water has decreased as the efficiency of vehicle engines has increased, and thus there has been a problem that heating capacity is reduced due to insufficient heating heat sources.

  As a countermeasure, Patent Document 1 describes a vehicle air conditioner that performs heating efficiently by setting an inside / outside air two-layer flow mode.

  In this prior art, the air conditioning case internal passage is partitioned into a first air passage on the outside air side and a second air passage on the inside air side, and the first air passage on the outside air side is formed in the defroster opening and the face opening. The second air passage on the inside air side is communicated with the foot opening.

  Thereby, since the inside air having a temperature higher than the outside air is recirculated through the second air passage and blown out from the foot opening, the temperature of the air blown to the feet of the occupant can be increased to efficiently heat the inside air. Moreover, since the low temperature external temperature wind blows off from a defroster opening part, the anti-fogging property of a window glass is securable.

  In this prior art, a communication passage is provided in the air conditioning case to connect the first air passage on the outside air side and the second air passage on the inside air side. This communication path can be opened and closed by a communication door.

  Conventionally, in a general vehicle air conditioner, an evaporator is disposed in an air conditioning case. The evaporator absorbs the latent heat of evaporation of the refrigerant in the refrigeration cycle from the conditioned air and cools the conditioned air. The refrigerant in the refrigeration cycle is sucked and discharged by the compressor and supplied to the evaporator.

  When the compressor is operating, the conditioned air is cooled below the dew point temperature by the evaporator, so that condensed water is generated on the surface of the evaporator. When the compressor is stopped, the conditioned air is not cooled by the evaporator, so condensed water is not generated on the surface of the evaporator. When the compressor has been stopped for a long time, the condensed water on the evaporator surface evaporates, and the odorous component in the condensed water may be released into the air to generate odor.

  Therefore, conventionally, in a general vehicle air conditioner, when the surface of the evaporator is wet with condensed water, the compressor is operated so that the condensed water does not evaporate. This prevents the odor from coming off.

JP 2000-225826 A

  In the above-described prior art, in the inside / outside air two-layer flow mode, when it is desired to secure a large amount of blown air from the defroster opening and the face opening, it is necessary to open the communication path with the communication door. That is, by opening the communication path with the communication door, in addition to the outside air of the first air path, the internal air of the second air path can be blown out from the defroster opening and the face opening. The amount of blown air can be increased from the outside air flow rate of the first air passage.

  When the compressor is stopped at the time of heating in which the inside / outside air two-layer flow mode is set, the high-temperature inside air flowing through the second air passage is not cooled by the evaporator, so the evaporator surface condenses in the second air passage. Water evaporates and odor is likely to occur. At this time, if the communication door opens the communication passage, the odor in the second air passage is blown out to the upper side of the passenger compartment through the defroster opening and the face opening, so that the odor easily reaches the occupant's face. Become. As a result, there is a problem that the occupant tends to feel a bad odor.

  In view of the above points, an object of the present invention is to suppress a passenger from feeling a bad odor in a vehicle air conditioner capable of setting an inside / outside air two-layer flow mode.

In order to achieve the above object, in the invention described in claim 1,
A first air passage (31a) and a second air passage (31b) through which air blown into the vehicle interior space flows in parallel with each other, and a defroster outlet for blowing air from the first air passage (31a) toward the vehicle window and (2 6), a casing (31) forming a foot outlet (25) for blowing toward the air-ride membered feet of the second air passage (31b),
A blowing means (32) for blowing air to the first air passage (31a) and the second air passage (31b);
Inside / outside air switching means (23A, 23B) capable of setting an inside / outside air two-layer flow mode in which outside air is introduced into the first air passage (31a) and inside air is introduced into the second air passage (31b);
A compressor (11) for sucking and discharging refrigerant;
A radiator (12) for radiating the heat of the refrigerant discharged from the compressor (11);
Decompression means (14) for decompressing the refrigerant radiated by the radiator (12);
An evaporator (15) that evaporates the refrigerant and heats the air by exchanging heat between the refrigerant decompressed by the decompression means (14) and the air flowing through the first air passage (31a) and the second air passage (31b). )When,
Air heating means (36) for heating the air flowing through the first air passage (31a) and the second air passage (31b);
And the foot defroster mode where air and the second air passage air in the first air passage (31 a) is blown from the defroster outlet (2 6) (31b) is blown from the foot outlet (25), a second air Blowout switching means (24a, 25a, 26a, 38) for switching to a foot mode in which air in the passage (31b) is blown out from the foot blowout opening (25) ;
When the inside / outside air switching means (23A, 23B) is set to the inside / outside air two-layer flow mode and the compressor (11) is stopped, the window is likely to be cloudy and the surface of the evaporator (15) is condensed water. And control means (50) for performing switching prohibition control for switching to the foot mode by prohibiting the blowing switching means (24a, 25a, 26a, 38) from switching to the foot defroster mode. It is characterized by that.

According to this, when the condensed water on the surface of the evaporator (15) evaporates in the first air passage (31 a ) and the odor is likely to be generated, the control means (50) performs the switching prohibition control, whereby the first It is possible to suppress the odor of the air passage (31 a ) from being blown out to the defroster outlet (26) . Therefore, since it can suppress that the odor of a 1st air path (31a) reaches a passenger | crew's face part, it can suppress that a passenger | crew feels a bad smell.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

1 is an overall configuration diagram of a vehicle air conditioner according to an embodiment. It is a block diagram which shows the electric control part of the vehicle air conditioner of one Embodiment. It is a flowchart which shows the control processing of the vehicle air conditioner of one Embodiment. It is a flowchart which shows the principal part of the control processing of the vehicle air conditioner of one Embodiment. It is a flowchart which shows another principal part of the control processing of the vehicle air conditioner of one Embodiment. It is a flowchart which shows another principal part of the control processing of the vehicle air conditioner of one Embodiment. It is a flowchart which shows another principal part of the control processing of the vehicle air conditioner of one Embodiment. It is a control characteristic figure used for control processing of an air-conditioner for vehicles of one embodiment. It is a flowchart which shows another principal part of the control processing of the vehicle air conditioner of one Embodiment. It is a time chart which shows an example of the control result of the air-conditioner for vehicles of one embodiment.

  Hereinafter, embodiments will be described with reference to the drawings. FIG. 1 is an overall configuration diagram of a vehicle air conditioner 1 according to the present embodiment, and FIG. 2 is a block diagram illustrating a configuration of an electric control unit of the vehicle air conditioner 1. In the present embodiment, the vehicle air conditioner 1 is applied to a hybrid vehicle that obtains driving force for vehicle travel from an internal combustion engine (engine) EG and a travel electric motor.

  The hybrid vehicle of the present embodiment is configured as a plug-in hybrid vehicle capable of charging power supplied from an external power source (commercial power source) when the vehicle is stopped to a battery (vehicle battery) 81 mounted on the vehicle.

  This plug-in hybrid vehicle charges the battery 81 with electric power supplied from an external power source when the vehicle stops before the vehicle starts running, so that the remaining power SOC of the battery 81 is predetermined as when the vehicle starts running. When the reference remaining amount for traveling is greater than or equal to the traveling remaining amount, the operation mode is such that traveling is performed mainly by the driving force of the traveling electric motor. Hereinafter, this operation mode is referred to as an EV operation mode.

  On the other hand, when the remaining amount SOC of the battery 81 is lower than the reference remaining amount for traveling while the vehicle is traveling, the operation mode is set to travel mainly by the driving force of the engine EG. Hereinafter, this operation mode is referred to as an HV operation mode.

  More specifically, the EV operation mode is an operation mode in which the vehicle is driven mainly by the driving force output from the traveling electric motor. When the vehicle driving load becomes high, the engine EG is operated. Assist the electric motor for traveling. That is, this is an operation mode in which the driving force for driving (motor side driving force) output from the electric motor for driving is larger than the driving force for driving (internal combustion engine side driving force) output from the engine EG.

  In other words, it can also be expressed as an operation mode in which the driving force ratio of the motor side driving force to the internal combustion engine side driving force (motor side driving force / internal combustion engine side driving force) is at least greater than 0.5. .

  On the other hand, the HV operation mode is an operation mode in which the vehicle is driven mainly by the driving force output from the engine EG. When the vehicle driving load becomes high, the driving electric motor is operated to operate the engine EG. Assist. That is, this is an operation mode in which the internal combustion engine side driving force is larger than the motor side driving force. In other words, it can also be expressed as an operation mode in which the drive force ratio (motor side drive force / internal combustion engine side drive force) is at least smaller than 0.5.

  In the plug-in hybrid vehicle of the present embodiment, the fuel consumption amount of the engine EG with respect to a normal vehicle that obtains driving force for vehicle travel only from the engine EG by switching between the EV operation mode and the HV operation mode in this way. This suppresses vehicle fuel efficiency. The switching between the EV operation mode and the HV operation mode and the control of the driving force ratio are controlled by the driving force control device 70.

  Further, the driving force output from the engine EG is used not only for driving the vehicle but also for operating the generator 80. And the electric power generated with the generator 80 and the electric power supplied from the external power supply can be stored in the battery 81, and the electric power stored in the battery 81 is not only a traveling electric motor but also a vehicle air conditioner. 1 can be supplied to various in-vehicle devices including an electric component device that constitutes 1.

  Next, the detailed structure of the vehicle air conditioner 1 of this embodiment is demonstrated. The vehicle air conditioner 1 performs air conditioning (for example, pre-air conditioning) in the vehicle interior using electric power supplied from an external power source when the vehicle is stopped before traveling, in addition to air conditioning in the vehicle interior using electric power supplied from the battery 81. Configured to be executable.

  The vehicle air conditioner 1 of the present embodiment includes the refrigeration cycle 10 shown in FIG. 1, the indoor air conditioning unit 30, the air conditioning control device 50 shown in FIG.

  First, the indoor air conditioning unit 30 is arranged inside the instrument panel (instrument panel) at the foremost part of the vehicle interior, and the blower 32, the evaporator 15, the heater core 36, and the PTC heater 37 are disposed in a casing 31 that forms an outer shell thereof. Etc. are accommodated.

  The casing 31 forms an air passage for blown air that is blown into the vehicle interior, and is formed of a resin (for example, polypropylene) that has a certain degree of elasticity and is excellent in strength. A first air passage 31 a and a second air passage 31 b through which air flows in parallel with each other are formed in the casing 31.

  The first air passage 31a is an outside air passage through which outside air flows in the inside / outside air two-layer flow mode. The second air passage 31b is an inside air side passage through which the inside air flows in the inside / outside air two-layer flow mode. The outside air side passage 31a and the inside air side passage 31b are partitioned by a partition plate 31c (partition portion).

  An inside / outside air switching box 20 as an inside / outside air switching means for switching between the inside air (vehicle compartment air) and the outside air (vehicle compartment outside air) is arranged on the most upstream side of the blown air flow in the casing 31.

  More specifically, the inside / outside air switching box 20 is formed with a first inside air introduction port 21A, a second inside air introduction port 21B, a first outside air introduction port 22A, and a second outside air introduction port 22B. The first inside air introduction port 21 </ b> A and the second inside air introduction port 21 </ b> B introduce inside air into the casing 31. The first outside air introduction port 22A and the second outside air introduction port 22B introduce outside air into the casing 31.

  Furthermore, inside the inside / outside air switching box 20, a first inside / outside air switching door 23 </ b> A and a second inside / outside air switching door 23 </ b> B that change the air volume ratio between the volume of the inside air introduced into the casing 31 and the volume of the outside air are arranged. ing.

  The first inside / outside air switching door 23A continuously adjusts the opening areas of the first inside air introduction port 21A and the first outside air introduction port 22A. The second inside / outside air switching door 23B continuously adjusts the opening areas of the second inside air introduction port 21B and the second outside air introduction port 22B.

  Accordingly, the first inside / outside air switching door 23 </ b> A and the second inside / outside air switching door 23 </ b> B change the air volume ratio changing means (which changes the air volume ratio between the air volume of the inside air introduced into the casing 31 and the air volume of the outside air). (Inside / outside air switching means). More specifically, the first inside / outside air switching door 23A is driven by the electric actuator 62A, and the second inside / outside air switching door 23B is driven by the electric actuator 62B. The operation of the electric actuators 62A and 62B is controlled by a control signal output from the air conditioning control device 50.

  In addition, as the suction port mode, there are an all inside air mode, an all outside air mode, an inside / outside air mixing mode, and an inside / outside air two-layer flow mode.

  In the inside air mode, the first inside air introduction port 21A and the second inside air introduction port 21B are fully opened, the first outside air introduction port 22A and the second outside air introduction port 22B are fully closed, and the outside air side passage 31a and the inside air in the casing 31 are opened. Inside air is introduced into the side passage 31b.

  In the outside air mode, the first inside air introduction port 21A and the second inside air introduction port 21B are fully closed, and the first outside air introduction port 22A and the second outside air introduction port 22B are fully opened, and the outside air side passage 31a and the inside air in the casing 31 are opened. Outside air is introduced into the side passage 31b.

  In the inside / outside air mixing mode, the opening areas of the first inside air introduction port 21A, the second inside air introduction port 21B, the first outside air introduction port 22A, and the second outside air introduction port 22B are continuously set between the inside air mode and the outside air mode. By adjusting, the introduction ratio of the inside air and the outside air into the outside air side passage 31a and the inside air side passage 31b in the casing 31 is continuously changed.

  In the inside / outside air two-layer flow mode, the first inside air introduction port 21A and the second outside air introduction port 22B are fully opened, the first outside air introduction port 22A and the second inside air introduction port 21B are fully closed, and the outside air side in the casing 31 is opened. While introducing the outside air into the passage 31a, the inside air is introduced into the inside air passage 31b.

  A blower 32 (blower), which is a blowing means for blowing the air sucked through the inside / outside air switching box 20 toward the vehicle interior, is disposed on the downstream side of the inside / outside air switching box 20. The blower 32 is an electric blower that drives the first fan 32 a and the second fan 32 b by a common electric motor 32 c, and the number of rotations (blowing capacity) is controlled by a control voltage output from the air conditioning control device 50. The Therefore, the electric motor 32c constitutes a blowing capacity changing unit of the blower 32.

  The first fan 32a and the second fan 32b are centrifugal multiblade fans (sirocco fans). The first fan 32a is disposed in the outside air passage 31a, and blows the inside air from the first inside air introduction port 21A and the outside air from the first outside air introduction port 22A to the outside air passage 31a. The second fan 32b is disposed in the inside air passage 31b and blows the inside air from the second inside air introduction port 21B and the outside air from the second outside air introduction port 22B to the inside air passage 31b.

  An evaporator 15 is disposed on the downstream side of the air flow of the blower 32. The evaporator 15 is disposed over the entire area of the outside air side passage 31a and the inside air side passage 31b. The evaporator 15 functions as a cooling means (heat exchange means) that cools the blown air by exchanging heat between the refrigerant (heat medium) flowing through the evaporator 15 and the blown air blown from the blower 32. Specifically, the evaporator 15 constitutes a vapor compression refrigeration cycle 10 together with the compressor 11, the condenser 12, the gas-liquid separator 13, the expansion valve 14, and the like.

  Here, the main configuration of the refrigeration cycle 10 according to the present embodiment will be described. The compressor 11 is arranged in the engine room, sucks refrigerant in the refrigeration cycle 10, compresses and discharges the refrigerant, The fixed capacity type compression mechanism 11a having a fixed capacity is configured as an electric compressor that is driven by an electric motor 11b. The electric motor 11b is an AC motor whose operation (number of rotations) is controlled by an AC voltage output from the inverter 61 (FIG. 2).

  Further, the inverter 61 outputs an AC voltage having a frequency corresponding to the control signal output from the air conditioning control device 50. And the refrigerant | coolant discharge capability of the compressor 11 is changed by this rotation speed control. Therefore, the electric motor 11b constitutes a discharge capacity changing unit of the compressor 11.

  The condenser 12 is disposed in the engine room and dissipates the refrigerant discharged from the compressor 11 by exchanging heat between the refrigerant flowing through the inside and the outside air blown from the blower fan 12a as an outdoor blower. It is an outdoor heat exchanger (heat radiator) to be condensed. The blower fan 12a is an electric blower in which the operation rate, that is, the rotation speed (the amount of blown air) is controlled by a control voltage output from the air conditioning control device 50.

  The gas-liquid separator 13 is a receiver that gas-liquid separates the refrigerant condensed in the condenser 12 and stores excess refrigerant, and flows only the liquid-phase refrigerant downstream. The expansion valve 14 is a decompression unit that decompresses and expands the liquid-phase refrigerant that has flowed out of the gas-liquid separator 13. The evaporator 15 is an indoor heat exchanger that evaporates the refrigerant decompressed and expanded by the expansion valve 14 and exerts an endothermic effect on the refrigerant. Thereby, the evaporator 15 functions as a heat exchanger for cooling which cools blowing air.

  The above is the description of the main configuration of the refrigeration cycle 10 according to the present embodiment, and the description returns to the indoor air conditioning unit 30 below. In the outside air side passage 31a and the inside air side passage 31b in the casing 31, a cold air passage for heating and a cold air bypass passage for flowing air after passing through the evaporator 15 are formed in parallel on the downstream side of the air flow of the evaporator 15. . A heater core 36 and a PTC heater 37 for heating the air that has passed through the evaporator 15 are arranged in this order in the air flow direction in the cooling air passage for heating.

  In the outside air side passage 31a and the inside air side passage 31b, mixing spaces 35A and 35B for mixing the air flowing out of the heating cold air passage and the cold air bypass passage are formed on the downstream side of the air flow of the heating cold air passage and the cold air bypass passage. ing.

  The heater core 36 is a heat exchanger (air heating means) for heating the blown air that has passed through the evaporator 15 using engine cooling water (hereinafter simply referred to as cooling water) for cooling the engine EG as a heat medium. The engine EG is cooling water heating means (heat medium heating means) for heating the cooling water.

  Specifically, the heater core 36 and the engine EG are connected by a cooling water pipe, and the cooling water circuit 40 in which the cooling water circulates between the heater core 36 and the engine EG is configured. The cooling water circuit 40 is provided with a cooling water pump 40a for circulating the cooling water. The cooling water pump 40 a is an electric water pump whose rotational speed (cooling water circulation flow rate) is controlled by a control voltage output from the air conditioning control device 50.

  The PTC heater 37 has an PTC element (positive characteristic thermistor), and is an electric heater as auxiliary heating means that generates heat when electric power is supplied to the PTC element and heats the air after passing through the heater core 36. Note that the power consumption required to operate the PTC heater 37 of the present embodiment is less than the power consumption required to operate the compressor 11 of the refrigeration cycle 10.

  More specifically, the PTC heater 37 is composed of a plurality of (in this embodiment, three) PTC elements. The positive side of each PTC element is connected to the battery 81 side, and the negative side is connected to the ground side via a switch element. The switch element switches between the energized state (ON state) and the non-energized state (OFF state) of each PTC element. The operation of the switch element is controlled by a control signal output from the air conditioning control device 50.

  The air-conditioning control device 50 controls the operation of the switch element so as to independently switch between the energized state and the non-energized state of each PTC element, thereby switching the number of PTC elements that are in the energized state and exhibit the heating capability. The heating capacity of the heater 37 as a whole can be changed.

  The cold air bypass passage is an air passage for guiding the air after passing through the evaporator 15 to the mixing spaces 35A and 35B without passing through the heater core 36 and the PTC heater 37. Accordingly, the temperature of the blown air mixed in the mixing spaces 35A and 35B varies depending on the air volume ratio of the air passing through the heating cold air passage and the air passing through the cold air bypass passage.

  Therefore, in the present embodiment, the heating cold air passage and the cold air bypass passage are provided on the downstream side of the air flow of the evaporator 15 in the outside air side passage 31a and the inside air side passage 31b and on the inlet side of the heating cold air passage and the cold air bypass passage. Air mix doors 39A and 39B that continuously change the air volume ratio of the cold air flowing into the air are arranged.

  The air mix doors 39A and 39B constitute temperature adjusting means for adjusting the air temperature in the mixing spaces 35A and 35B (the temperature of the blown air blown into the passenger compartment).

  More specifically, the air mix doors 39A and 39B are configured to have a common rotating shaft driven by a common electric actuator 63 and a plate-like door main body connected to the common rotating shaft. The so-called cantilever door. The operation of the electric actuator 63 for the air mix door is controlled by a control signal output from the air conditioning controller 50.

  A communication passage 31d for communicating the outside air passage 31a and the inside air passage 31b is formed at the most downstream portion of the blast air flow of the casing 31. A communication door 38 is disposed at the most downstream portion of the blast air flow of the casing 31. The communication door 38 is communication path opening / closing means for opening and closing the communication path 31d.

  The communication door 38 is driven by the electric actuator 65. The operation of the electric actuator 65 is controlled by a control signal output from the air conditioning controller 50.

  When the suction port mode is any of the all-in-air mode, all-outside-air mode, and inside / outside-air mixing mode, the communication door 38 opens the communication path 31d, so that the outside-air side path 31a and the inside-air side path 31b communicate with each other.

  When the suction port mode is the inside / outside air two-layer flow mode, the communication door 38 closes the communication path 31d, so that the outside air side path 31a and the inside air side path 31b are not communicated with each other.

  Furthermore, the blower outlets 24-26 which blow off the temperature-adjusted blown air from mixing space 35A, 35B to the vehicle interior which is an air-conditioning object space are arrange | positioned in the blower air flow most downstream part of the casing 31. FIG.

  Specifically, the air outlets 24 to 26 include a face air outlet 24 that blows air-conditioned air toward the upper body of an occupant in the vehicle interior, a foot air outlet 25 that blows air-conditioned air toward the feet of the occupant, and the front of the vehicle. A defroster outlet 26 that blows air-conditioned air toward the inner side surface of the window glass is provided.

  The face air outlet 24 and the defroster air outlet 26 are upper air outlets that blow out toward a space located above the upper body of the passenger in the vehicle interior space. The foot air outlet 25 is a lower air outlet that blows out toward a space located below the passenger's lower half of the passenger compartment space.

  The face air outlet 24 and the defroster air outlet 26 are disposed in the most downstream portion of the blown air flow in the outside air passage 31a. The foot outlet 25 is arranged in the most downstream part of the blown air flow in the inside air passage 31b.

On the upstream side of the air flow of the face air outlet 24, the foot air outlet 25, and the defroster air outlet 26, a face door 24a for adjusting the opening area of the face air outlet 24 and a foot door for adjusting the opening area of the foot air outlet 25, respectively. The defroster door 26a which adjusts the opening area of 25a and the defroster blower outlet 26 is arrange | positioned. The defroster door 26a is a defroster outlet opening / closing means.

  The face door 24a, the foot door 25a, and the defroster door 26a constitute an outlet mode switching means for switching the outlet mode, and an electric actuator 64 for driving the outlet mode door via a link mechanism (not shown). It is linked to and rotated in conjunction with it. The operation of the electric actuator 64 is also controlled by a control signal output from the air conditioning controller 50.

  Further, as the air outlet mode, the face air outlet 24 is fully opened and air is blown out from the face air outlet 24 toward the upper body of the passenger in the passenger compartment (FACE), and both the face air outlet 24 and the foot air outlet 25 are provided. Bi-level mode (B / L) that opens and blows air toward the upper body and feet of passengers in the passenger compartment, fully opens the foot outlet 25, opens the defroster outlet 26 by a small opening degree, and opens the foot outlet 25 Foot mode (FOOT) for mainly blowing air from the foot, and foot defroster mode (F / F) for opening air from both the foot outlet 25 and the defroster outlet 26 by opening the foot outlet 25 and the defroster outlet 26 to the same extent. D).

  Further, the defroster mode (DEF) in which the occupant manually operates the defroster switch 60c of the operation panel 60 shown in FIG. 2 to fully open the defroster outlet 26 and blow out air from the defroster outlet 26 to the inner surface of the vehicle front window glass. It can also be.

  When the suction port mode is the inside / outside air two-layer flow mode, when the total blown air volume from the face air outlet 24 and the defroster air outlet 26 is made larger than the blown air volume from the foot air outlet 25 (for example, face mode, foot defroster) Mode, defroster mode), the communication door 38 opens the communication path 31d. As a result, not only the air in the outside air passage 31 a but also the air in the inside air passage 31 b can be blown out from the face outlet 24 and the defroster outlet 26.

Face mode, the bi-level mode, a foot defroster mode and the defroster mode, the air outside air side passage 31 a is blown from at least one outlet of the face air outlet 24 and the defroster air outlet 26 (the upper side outlet) It is an upper side blowing mode.

  The face door 24a, the foot door 25a, and the defroster door 26a are blowing switching means for switching the blowing mode to the upper blowing mode. The face door 24a and the defroster door 26a are upper air outlet opening / closing means for opening and closing the face air outlet 24 and the defroster air outlet 26 (upper air outlet).

  When the suction port mode is the inside / outside air two-layer flow mode, when the amount of air blown from the foot outlet 25 is larger than the total amount of air blown from the face outlet 24 and the defroster outlet 26 (for example, foot mode), communication The door 38 opens the communication path 31d. Thereby, not only the air in the inside air side passage 31b but also the air in the outside air side passage 31a can be blown out from the foot outlet 25.

  The vehicle air conditioner 1 of this embodiment includes an electric heat defogger (not shown). The electric heat defogger is a heating wire arranged inside or on the surface of the vehicle interior window glass, and is a window glass heating means for preventing fogging or eliminating window fogging by heating the window glass. The operation of the electric heat defogger can be controlled by a control signal output from the air conditioning controller 50.

  Furthermore, the vehicle air conditioner 1 of the present embodiment includes a seat air conditioner 90 shown in FIG. The seat air conditioner 90 is auxiliary heating means for increasing the surface temperature of a seat on which a passenger is seated. Specifically, the seat air conditioner 90 is a seat heating unit that is configured by a heating wire embedded in the seat surface and generates heat when supplied with electric power.

  And when the heating of a vehicle interior may become inadequate with the conditioned wind which blows off from each blower outlet 24-26 of the indoor air conditioning unit 10, the function which supplements a passenger | crew's heating feeling by operating | operating is fulfill | performed. The operation of the seat air conditioner 90 is controlled by a control signal output from the air conditioner control apparatus 50, and is controlled so as to increase the surface temperature of the seat to about 40 ° C. during operation.

  Moreover, in the vehicle air conditioner 1 of this embodiment, you may provide the seat air blower, the steering heater, and the knee radiation heater. The seat blower is a blower that blows air from the inside of the seat toward the passenger. The steering heater is a steering heating means for heating the steering with an electric heater. The knee radiation heater is a heating means that radiates heat source light, which is a heat source of radiant heat, toward an occupant's knee. The operation of the seat blower, the steering heater, and the knee radiation heater can be controlled by a control signal output from the air conditioning controller 50.

  Next, the electric control unit of the present embodiment will be described with reference to FIG. The air-conditioning control device 50 (air-conditioning control means), the driving force control device 70 (driving force control means), and the power control device 71 (power control means) are composed of a well-known microcomputer including a CPU, ROM, RAM, etc. and its peripheral circuits. It is configured and performs various calculations and processing based on a control program stored in the ROM, and controls the operation of various devices connected to the output side.

  Connected to the output side of the driving force control device 70 are various engine components constituting the engine EG, a traveling inverter for supplying an alternating current to the traveling electric motor, and the like. Specifically, as various engine components, a starter for starting the engine EG, a fuel injection valve (injector) drive circuit (not shown) for supplying fuel to the engine EG, and the like are connected.

  Further, on the input side of the driving force control device 70, there are a voltmeter for detecting the voltage VB between the terminals of the battery 81, an ammeter for detecting the current ABin flowing into the battery 81 or the current ABout flowing from the battery 81, and the accelerator opening Acc. Various engine control sensors such as an accelerator opening sensor for detecting, an engine speed sensor for detecting the engine speed Ne, and a vehicle speed sensor (none of which is shown) for detecting the vehicle speed Vv are connected.

  On the output side of the air conditioning controller 50, the blower 32, the inverter 61 for the electric motor 11b of the compressor 11, the blower fan 12a, various electric actuators 62A, 62B, 63, 64, 65, the PTC heater 37, and the cooling water pump 40a. The seat air conditioner 90 and the like are connected.

  On the input side of the air conditioning controller 50, an inside air sensor 51, an outside air sensor 52 (outside air temperature detecting means), a solar radiation sensor 53, a discharge temperature sensor 54 (discharge temperature detecting means), a discharge pressure sensor 55 (discharge pressure detecting means), For various air conditioning controls such as an evaporator temperature sensor 56 (evaporator temperature detection means), a cooling water temperature sensor 58, a window vicinity humidity sensor 59 (humidity detection means), a window glass vicinity air temperature sensor, and a window glass surface temperature sensor. Sensor groups are connected.

  The inside air sensor 51 detects a vehicle interior temperature Tr. The outside air sensor 52 detects the outside air temperature Tam. The solar radiation sensor 53 detects the solar radiation amount Ts in the passenger compartment. The discharge temperature sensor 54 detects the compressor 11 discharge refrigerant temperature Td. The discharge pressure sensor 55 detects the compressor 11 discharge refrigerant pressure Pd. The evaporator temperature sensor 56 detects the temperature of the air blown from the evaporator 15 (evaporator temperature) TE.

  The cooling water temperature sensor 58 detects the cooling water temperature Tw of the cooling water that has flowed out of the engine EG. The window vicinity humidity sensor 59 detects the relative humidity of the vehicle interior air in the vicinity of the window glass in the vehicle interior (hereinafter referred to as the window vicinity relative humidity). The window glass vicinity air temperature sensor detects the temperature of the passenger compartment air near the window glass. The window glass surface temperature sensor detects the window glass surface temperature.

  Note that the evaporator temperature sensor 56 of the present embodiment specifically detects the heat exchange fin temperature of the evaporator 15. Of course, as the evaporator temperature sensor 56, temperature detection means for detecting the temperature of other parts of the evaporator 15 may be adopted, or temperature detection means for directly detecting the temperature of the refrigerant itself flowing through the evaporator 15 may be used. It may be adopted. The detection values of the window vicinity humidity sensor 59, the temperature sensor, and the window glass surface temperature sensor are used to calculate the relative humidity RHW of the window glass surface.

  Further, operation signals from various air conditioning operation switches provided on the operation panel 60 disposed near the instrument panel in the front part of the vehicle interior are input to the input side of the air conditioning control device 50. Specifically, various air conditioning operation switches provided on the operation panel 60 include an air conditioner switch, an auto switch 60a, an outlet mode changeover switch 60b, a defroster switch 60c, an air volume setting switch of the blower 32, and a vehicle interior temperature setting switch 60d. A display unit or the like for displaying the current operating state of the vehicle air conditioner 1 is provided.

  The air conditioner switch is compressor operation setting means for switching between starting and stopping of the compressor 11 by the operation of the passenger. The air conditioner switch is provided with an air conditioner indicator that is turned on / off according to the operation status of the air conditioner switch.

  The auto switch 60a is automatic control setting means for setting or canceling automatic control of the vehicle air conditioner 1 by the operation of the occupant. The defroster switch 60c is defroster mode setting means for setting the defroster mode by the operation of the occupant. The vehicle interior temperature setting switch 60d is target temperature setting means for setting the vehicle interior target temperature Tset by the operation of the passenger.

  The air conditioner switch, auto switch 60a, outlet mode changeover switch 60b and defroster switch 60c are instruction means for instructing the air conditioning control device 50 to start and stop the compressor 11 by the operation of the occupant.

  Further, as various air conditioning operation switches provided on the operation panel 60, economy switches are provided. The economy switch is a switch that prioritizes the reduction of environmental load. By turning on the economy switch, the operation mode of the vehicle air conditioner 1 is set to an economy mode (economic mode for short) that prioritizes power saving of air conditioning. Therefore, the economy switch can also be expressed as power saving priority mode setting means.

  In addition, by turning on the economy switch, a signal for reducing the operating frequency of the engine EG that is operated to assist the electric motor for traveling is output to the driving force control device 70 in the EV operation mode.

  In addition, the air conditioning control device 50 and the driving force control device 70 are configured to be electrically connected to communicate with each other. Thereby, based on the detection signal or operation signal input into one control apparatus, the other control apparatus can also control the operation | movement of the various apparatuses connected to the output side. For example, the operation of the engine EG can be requested by the air conditioning control device 50 outputting a request signal for the engine EG to the driving force control device 70. When driving force control device 70 receives a request signal (operation request signal) for requesting operation of engine EG from air conditioning control device 50, it determines whether or not it is necessary to operate engine EG, and according to the determination result. Controls the operation of the engine EG.

  Further, the air conditioning control device 50 includes an electric power control device 71 that determines power to be distributed to various electric devices in the vehicle according to the power supplied from the power supply outside the vehicle or the power stored in the battery 81. It is connected to the. The air conditioning control device 50 of the present embodiment receives an output signal (such as data indicating air conditioning use permission power that is permitted to be used for air conditioning) output from the power control device 71.

  Here, the air-conditioning control device 50 and the driving force control device 70 are configured such that control means for controlling various control target devices connected to the output side are integrally configured. The structure to control (hardware and software) comprises the control means which controls the action | operation of each control object apparatus.

  For example, in the air-conditioning control device 50, the configuration that controls the operation of the blower 32, which is a blowing unit, and controls the blowing capability of the blower 32 constitutes the blowing capability control unit and is connected to the electric motor 11 b of the compressor 11. The configuration for controlling the frequency of the AC voltage output from the inverter 61 to control the refrigerant discharge capacity of the compressor 11 constitutes the compressor control means 50a, and the configuration for controlling the switching of the outlet mode is the outlet mode. The switching means 50b is comprised.

  Further, the configuration for controlling the cooling capacity of the evaporator 15 as the cooling means constitutes the cooling capacity control means 50c, and the configuration for controlling the heating capacity of the heater core 36 as the heating means constitutes the heating capacity control means. Moreover, the structure which controls the action | operation of the electric actuator 65 for the communication door 38 comprises the communication path opening / closing control means.

  Moreover, the structure which transmits / receives a control signal with the driving force control apparatus 70 in the air-conditioning control apparatus 50 comprises the request signal output means 50d. In addition, the driving force control device 70 transmits and receives control signals to and from the air conditioning control device 50, and determines whether or not the engine EG needs to be operated in accordance with an output signal from the request signal output means 50d or the like (determining whether or not the operation is necessary). Means) constitutes a signal communication means.

  Next, the operation of the vehicle air conditioner 1 of the present embodiment in the above configuration will be described with reference to FIGS. FIG. 3 is a flowchart showing a control process as a main routine of the vehicle air conditioner 1 of the present embodiment. In this control process, the operation switch of the vehicle air conditioner 1 is turned on while power is supplied from the battery 81 or an external power source to various in-vehicle devices including the electric components constituting the vehicle air conditioner 1. Will start. In addition, each control step in FIGS. 3-9 comprises the various function implementation | achievement means which the air-conditioning control apparatus 50 has.

  First, in step S1, initialization such as initialization of flags, timers, etc., and initial alignment of the stepping motor constituting the electric actuator described above is performed. In this initialization, some of the flags and calculation values that are stored at the end of the previous operation of the vehicle air conditioner 1 are maintained.

  Next, in step S2, an operation signal of the operation panel 60 is read and the process proceeds to step S3. Specific operation signals include a vehicle interior target temperature Tset set by a vehicle interior temperature setting switch, a suction port mode switch setting signal, and the like.

  Next, in step S3, a vehicle environmental state signal used for air conditioning control, that is, a detection signal of the above-described sensor groups 51 to 58, a power state signal indicating a power supply state from an external power source, and the like are read. When the power status signal indicates a state in which power can be supplied from the external power source to the vehicle (plug-in state), the external power source flag is turned on and power cannot be supplied from the external power source to the vehicle (plug-out state) ), The external power flag is turned off.

  In step S3, a part of the detection signal of the sensor group connected to the input side of the driving force control device 70 and the control signal output from the driving force control device 70 are also read from the driving force control device 70. It is out.

Next, in step S4, the target blowing temperature TAO of the vehicle compartment blowing air is calculated. Therefore, step S4 constitutes a target blowing temperature determining means. The target blowing temperature TAO is calculated by the following formula F1.
TAO = Kset × Tset−Kr × Tr−Kam × Tam−Ks × Ts + C (F1)
Here, Tset is the vehicle interior set temperature set by the vehicle interior temperature setting switch, Tr is the vehicle interior temperature (inside air temperature) detected by the inside air sensor 51, Tam is the outside air temperature detected by the outside air sensor 52, and Ts is This is the amount of solar radiation detected by the solar radiation sensor 53. Kset, Kr, Kam, Ks are control gains, and C is a correction constant.

  The target blowout temperature TAO corresponds to the amount of heat that the vehicle air conditioner 1 needs to generate in order to keep the passenger compartment at a desired temperature, and the air conditioning load required for the vehicle air conditioner 1 (air conditioning heat). Load).

  In subsequent steps S5 to S13, control states of various devices connected to the air conditioning control device 50 are determined. First, in step S5, the target opening degree SW of the air mix door 39 is calculated based on the target blowing temperature TAO, the blowing air temperature TE detected by the evaporator temperature sensor 56, and the cooling water temperature Tw.

Specifically, first, a temporary air mix opening degree SWdd is calculated by the following formula F2.
SWdd = [{TAO− (TE + 2)} / {MAX (10, Tw− (TE + 2))}] × 100 (%) (F2)
Note that {MAX (10, Tw− (TE + 2))} in Formula F2 means the larger value of 10 and Tw− (TE + 2).

  Next, based on the provisional air mix opening SWdd, the air mix opening SW is determined with reference to a control map stored in the air conditioning control device 50 in advance. In this control map, the air mix opening SW is determined so as to be substantially proportional to the provisional air mix opening SWdd.

  In the next step S6, the blowing capacity of the blower 32 (specifically, the blower motor voltage applied to the electric motor) is determined. Details of step S6 will be described with reference to the flowchart of FIG.

  As shown in FIG. 4, first, in step S611, it is determined whether or not the auto switch 60a of the operation panel 60 is turned on. As a result, if it is determined that the auto switch 60a is not turned on, in step S612, the blower motor voltage that determines the passenger's desired air volume manually set by the air volume setting switch of the operation panel 60 is determined, and step S7 is performed. Proceed to

  Specifically, the air volume setting switch of the present embodiment can set five levels of air volume of Lo → M1 → M2 → M3 → Hi, and the blower motor voltage is set in the order of 4V → 6V → 8V → 10V → 12V. Determined to be higher.

  On the other hand, if it is determined in step S611 that the auto switch 60a is turned on, in step S613, the control map stored in the air conditioning controller 50 in advance based on the TAO determined in step S4 is referred to. The temporary blower level f1A (TAO) is then determined.

  As the temporary blower level f1A (TAO), a basic blower level corresponding to the air conditioning heat load is calculated. The temporary blower level f1A (TAO) is used as a blower level candidate value finally determined in step S6. The blower level is a value corresponding to the blower voltage applied to the electric motor in order to determine the blowing capacity of the blower 32.

  The control map for determining the temporary blower level f1A (TAO) in the present embodiment is configured such that the value of the temporary blower level f1A (TAO) for TAO draws a bathtub-like curve.

  That is, as shown in step S613 of FIG. 4, the air volume of the blower 32 is maximum in the extremely low temperature range of TAO (in this embodiment, −30 ° C. or lower) and the extremely high temperature range (in this embodiment, 80 ° C. or higher). The temporary blower level f1A (TAO) is raised to a high level so that the air volume is near.

  Further, when the TAO rises from the extremely low temperature range toward the intermediate temperature range, the temporary blower level f1A (TAO) is reduced so that the blown amount of the blower 32 is reduced as the TAO rises. Further, when the TAO decreases from the extremely high temperature range toward the intermediate temperature range, the temporary blower level f1A (TAO) is decreased according to the decrease in TAO so that the air volume of the blower 32 is decreased.

  When TAO enters a predetermined intermediate temperature range (10 ° C. to 40 ° C. in the present embodiment), the temporary blower level f1A (TAO) is lowered to a low level so that the air volume of the blower 32 becomes a low air volume. Thereby, the basic blower level corresponding to the air conditioning heat load is calculated.

  As is apparent from the above description, the temporary blower level f1A (TAO) is a value determined based on TAO, and is therefore based on the vehicle interior set temperature Tset, the internal temperature Tr, the external temperature Tam, and the solar radiation amount Ts. It is determined based on the value determined by

  In subsequent step S614, the warm-up upper limit blower level f2A (TW) is determined with reference to the control map stored in advance in the air conditioning controller 50 based on the coolant temperature Tw (water temperature) detected by the coolant temperature sensor 58. To do. The warm-up upper limit blower level f2A (TW) is an upper limit value of the blower level when the engine EG is warmed up (when the coolant temperature Tw is low).

  That is, as shown in step S614 of FIG. 4, the warm-up upper limit blower level f2A (TW) is raised in the range of 0 to 30 as the cooling water temperature Tw rises from the low temperature range to the high temperature range. In the control map shown in step S614 of FIG. 4, a hysteresis width for preventing control hunting is set.

  Thus, it is possible to prevent the occupant from feeling cold due to an increase in the amount of blown air when the cooling water temperature Tw is not sufficiently increased and the heater core 36 cannot sufficiently heat the air.

In subsequent step S615, the blower level is calculated by the following mathematical formula F3, and the process proceeds to step S616.
Blower level = MIN (f1A (TAO), f2A (TW)) (F3)
Note that MIN (f1A (TAO), f2A (TW)) in Formula F3 means the smaller value of f1A (TAO) and f2A (TW).

  In step S616, the blower voltage (blower motor voltage) is determined based on the determined blower level with reference to the control map stored in the air conditioning control device 50 in advance. That is, as shown in step S616 of FIG. 4, the blower voltage (blower motor voltage) is decreased as the blower level value is smaller.

  Thereby, the ventilation capability of the air blower 32 is appropriately adjusted according to the target blowing temperature TAO and the cooling water temperature Tw.

  In the next step S7, the inlet mode, that is, the switching state of the inside / outside air switching box 20 is determined. Details of step S7 will be described with reference to the flowchart of FIG. As shown in FIG. 5, first, in step S701, it is determined whether or not the auto switch 60a of the operation panel 60 is turned on. As a result, when it is determined that the auto switch 60a is not turned on, the outside air introduction rate corresponding to the manual mode is determined in steps S702 to S704, and the process proceeds to step S8.

  Specifically, when the manual inlet mode is the all-in-air mode (REC mode), the outside air rate is determined to be 0% (step S703), and when the manual inlet mode is the all-outside air mode (FRS mode), the outside air rate is determined. Is determined to be 100% (step S704). The outside air rate is a ratio of outside air in the introduced air (outside air and inside air) introduced into the casing 31 from the inside / outside air switching box 20.

  On the other hand, if it is determined in step S701 that the auto switch 60a has been turned on, the process proceeds to step S705, and based on the target outlet temperature TAO calculated in step S4, whether the air conditioning operation state is the cooling operation or the heating operation. Determine. In the example of FIG. 5, when the target blowing temperature TAO is higher than 25 ° C., it is determined that the heating operation is performed, and in other cases, the cooling operation is determined.

  When it determines with air_conditionaing | cooling operation, it progresses to step S706, refers to the control map previously memorize | stored in the air-conditioning control apparatus 50 based on the target blowing temperature TAO, determines an external air rate, and progresses to step S8.

  Specifically, the outside air rate is reduced when TAO is low, and the outside air rate is increased when TAO is high. In the example of FIG. 5, if TAO ≦ 0 ° C., the outside air rate is 0%, if TAO ≧ 15 ° C., the outside air rate is 100%, and if 0 ° C. <TAO <15 ° C., the outside air rate is higher as TAO is higher. Is increased in the range of 0 to 100%.

  When the outside air rate is set to 0%, the opening degree of the first inside / outside air switching door 23A and the second inside / outside air switching door 23B is controlled so that the suction port mode becomes the all inside air mode. When the outside air rate is set to 100%, the opening degree of the first inside / outside air switching door 23A and the second inside / outside air switching door 23B is controlled so that the suction port mode becomes the all outside air mode.

  When the outside air rate is set to be more than 0% and less than 100%, the opening degrees of the first inside / outside air switching door 23A and the second inside / outside air switching door 23B are controlled so that the suction port mode becomes the inside / outside air mixing mode. The opening degree of the first inside / outside air switching door 23A and the second inside / outside air switching door 23B is changed according to the set outside air rate.

  On the other hand, when it determines with heating operation in step S705, it progresses to step S707 and it is determined whether it is a compressor stop mode. In other words, it is determined whether or not the compressor 11 is stopped. Specifically, it is determined whether or not the rotational speed of the compressor 11 is determined to be 0 in the control process for determining the rotational speed of the compressor 11 in step S9.

  The compressor stop mode is an operation mode in which the compressor 11 is automatically stopped to improve fuel efficiency when the possibility of odor generation from the evaporator 15 during heating is low and the possibility of fogging of the window glass is low. It is.

  When it is determined that the compressor stop mode is not set, that is, when the compressor 11 is operating, the process proceeds to step S708, the outside air rate is determined as 100%, and the process proceeds to step S8. Thereby, since the outside air whose temperature is lower than that of the inside air is sucked into the evaporator 15, the power consumption of the compressor 11 can be reduced and the fuel efficiency can be improved.

  On the other hand, when it is determined that the compressor stop mode is set, that is, when the compressor 11 is stopped, the inside / outside air two-layer flow mode is determined and the process proceeds to step S8. Thereby, since the outside air flows into the evaporator 15 in the first air passage 31a, the temperature of the air flowing into the evaporator 15 can be lowered as compared with the case where the inside air flows into the evaporator 15. As a result, since the condensed water on the surface of the evaporator 15 can be suppressed from evaporating, the generation of odor from the evaporator 15 can be suppressed.

  Further, since the inside air is recirculated to the inside air side passage 31b, the temperature of the air flowing into the heater core 36 can be increased in the inside air side passage 31b. Therefore, since the amount of heat from which the hot water is taken away by the heater core 36 is reduced, it is possible to blow out hot air even if the operating frequency of the engine EG is lowered, and the practical fuel consumption of the vehicle can be improved.

  In this example, the outside air rate in the inside / outside air two-layer flow mode is 50%, but the outside air rate in the inside / outside air two-layer flow mode can be appropriately changed according to the specifications of the indoor air conditioning unit 30.

  In the next step S8, the outlet mode, that is, the switching state of the face door 24a, the foot door 25a, and the defroster door 26a is determined. Details of step S8 will be described with reference to the explanatory diagram of FIG.

  As shown in FIG. 6, first, in step S801, the time for drying the evaporator 15 (evaporator drying time) is calculated based on the outside air temperature.

  Specifically, when the outside air temperature is high, the evaporator drying time is set longer. That is, as the outside air temperature is higher, the amount of condensed water generated in the evaporator 15 during the operation of the refrigeration cycle 10 is increased, so that it takes time for the evaporator 15 to dry. In the example of FIG. 6, the outside air temperature is 0 ° C. for 30 seconds, the outside air temperature is 10 ° C., and 20 ° C. is 120 seconds.

  When the humidity of the outside air is low, the evaporator drying time may be set short. This is because the lower the outside air humidity, the faster the evaporator 15 is dried by introducing the outside air. The larger the air volume of the blower 32, the shorter the evaporator drying time may be set. This is because the evaporator 15 dries faster as the air volume of the blower 32 increases.

  Next, in step S802, it is determined whether or not the auto switch 60b of the operation panel 60 is turned on. As a result, if it is determined that the auto switch 60b is not turned on, the process proceeds to step S803, the air outlet mode corresponding to the manual mode is determined, and the process proceeds to step S9.

  Specifically, one of the face mode, the bi-level mode, the foot mode, and the foot defroster mode is determined according to the operation of the air outlet mode changeover switch 60b by the occupant.

  On the other hand, if it is determined in step S802 that the auto switch 60b is turned on, the process proceeds to step S804, and based on the target outlet temperature TAO calculated in step S4, the base outlet mode (temporary outlet mode). To decide.

  In the example of FIG. 6, the base outlet mode is determined to be the face mode in the low temperature range of the target outlet temperature TAO, the base outlet mode is determined to be the bi-level mode in the middle temperature range of the target outlet temperature TAO, and the target outlet temperature TAO In high temperature range, base outlet mode is determined to be foot mode. In the control map shown in step S804 of FIG. 6, a hysteresis width for preventing control hunting is set.

  In the subsequent step S805, it is determined whether or not the outside air temperature is less than 0 ° C. and the relative humidity RHW of the window glass surface exceeds 95%. If the outside air temperature is not less than 0 ° C. or the relative humidity RHW of the window glass surface does not exceed 95%, it can be determined that the window glass is not easily fogged, so the process proceeds to step S806, and the outlet mode is determined in step S804. The base air outlet mode (temporary air outlet mode) is determined, and the process proceeds to step S9. Thereby, blower outlet mode is switched appropriately according to target blow temperature TAO.

  On the other hand, if it is determined that the outside air temperature is less than 0 ° C. and the relative humidity RHW of the window glass surface exceeds 95%, it can be determined that the window glass is likely to be fogged. Determine whether or not. The compressor stop mode is an operation mode in which the compressor 11 is automatically stopped to improve fuel efficiency when the possibility of odor generation from the evaporator 15 during heating is low and the possibility of fogging of the window glass is low. It is.

When it is determined that it is not the compressor stop mode, that is, when the compressor 11 is operating, the process proceeds to step S808, the blower outlet mode is determined as the foot defroster mode, and the process proceeds to step S9. Accordingly, the conditioned air heated by the heater core 36 can be blown out from the foot outlet 25 and heated, and the conditioned air dehumidified by the evaporator 15 can be blown out from the defroster outlet 26 to prevent fogging of the window glass.

  On the other hand, when it determines with it being a compressor stop mode by step S807, it progresses to step S809 and it is determined whether the suction inlet mode determined by step S7 is inside / outside air two-layer flow mode.

When it determines with it not being inside / outside air two-layer flow mode, it progresses to step S810, determines a blower outlet mode to foot defroster mode, and progresses to step S9. Thus, fogging can be prevented in the window glass by blowing air-conditioned air heated by the heater core 36 with the conditioned air heated by the heater core 36 can be heated by blowing a foot air outlet 25 from de Furosuta outlet 26.

  On the other hand, if it is determined that the inside / outside air two-layer flow mode is selected, the process proceeds to step S811, and it is determined whether the blower 32 is operating (ON). When it determines with the air blower 32 operating, it progresses to step S812, an evaporator drying timer is counted, and it progresses to step S814.

  On the other hand, when it determines with the air blower 32 having stopped (OFF), it progresses to step S813, an evaporator drying timer is stopped, and it progresses to step S814. That is, when the blower 32 is stopped, air is not blown to the evaporator 15 and drying of the evaporator 15 is delayed, so the evaporator drying timer is not counted.

In step S814, it is determined whether or not the count time of the evaporator drying timer is equal to or longer than the evaporator drying time set in step S801. When it is determined that the count time of the evaporator drying timer is equal to or longer than the evaporator drying time, it is determined that the evaporator 15 is dry to the extent that no odor is generated from the evaporator 15, so the process proceeds to step S815, and the outlet The mode is determined to be the foot defroster mode, and the process proceeds to step S9. Thus, the conditioned air heated by the heater core 36 can be blown out from the foot outlet 25 for heating, and the conditioned air heated by the heater core 36 can be blown out from the defroster outlet 26 to prevent fogging of the window glass.

  On the other hand, if it is determined in step S814 that the count time of the evaporator drying timer is not equal to or longer than the evaporator drying time, it is determined that the evaporator 15 is wet and odor may be generated from the evaporator 15. Then, the process proceeds to step S816, the outlet mode is determined to be the foot mode, and the process proceeds to step S9.

  That is, in step S816, switching prohibition control is performed to prohibit switching to the foot defroster mode.

Thereby, the conditioned air heated by the heater core 36 can be blown out from the foot outlet 25 and heated. In addition, since the conditioned air in the inside air passage 31b is not blown out from the defroster outlet 26 , even if the condensed water on the surface of the evaporator 15 evaporates in the inside air passage 31b through which the high-temperature inside air flows, the occupant smells. It becomes difficult to feel.

  In the next step S9, the refrigerant discharge capacity of the compressor 11 (specifically, the rotational speed of the compressor 11) is determined. The determination of the compressor speed in step S9 is not performed every control cycle τ in which the main routine of FIG. 3 is repeated, but is performed every predetermined control interval (1 second in the present embodiment).

  Details of step S9 will be described with reference to the flowchart of FIG. As shown in FIG. 7, first, in step S901, a rotational speed change amount Δf with respect to the previous compressor rotational speed fn−1 is obtained. Specifically, based on the TAO determined in step S4 or the like, a target of the blown air temperature TE from the indoor evaporator 26 is referred to with reference to a control map (for example, FIG. 8) stored in advance in the air conditioning control device 50. The blowing temperature TEO is determined.

  Then, a deviation En (TEO-TE) between the target blowing temperature TEO and the blowing air temperature TE is calculated, and a deviation change rate Edot (En− (En− ()) obtained by subtracting the previously calculated deviation En−1 from the currently calculated deviation En. En-1)) is calculated, and the previous compressor rotation is calculated based on the fuzzy inference based on the membership function and the rule stored in advance in the air conditioning controller 50 using the deviation En and the deviation rate of change Edot. A rotational speed change amount Δf with respect to the number fn−1 is obtained.

  In the next step S902, it is determined whether or not the economy switch of the operation panel 60 is turned on (whether or not the eco mode is set).

  If it is determined in step S902 that the economy switch has not been turned on, the process proceeds to step S903, where the upper limit value (MAX speed) of the compressor 11 is set to 10,000 rpm, and the process proceeds to step S905.

  If it is determined that the economy switch is turned on, the process proceeds to step S904, where the upper limit value (MAX speed) of the compressor 11 is set to 7000 rpm, and the process proceeds to step S905.

  That is, when the economy switch is turned on, the energy (electric energy) consumed for air conditioning the vehicle interior is reduced by lowering the upper limit value of the rotation speed of the compressor 11 than when the economy switch is not turned on. I am letting.

  In step S905, on the basis of the value obtained by subtracting the compressor power consumption from the air conditioning use permission power, that is, the air conditioning use permission power-compressor power consumption value, the control map stored in the air conditioning control device 50 in advance is referred to. The upper limit value f (the air-conditioning use permission power-compressor power consumption) of the rotation speed variation is determined.

  The air-conditioning use permission power is “power permitted to be used for air-conditioning out of the power usable in the entire vehicle” and is output from the power control device 71 to the air-conditioning control device 50.

  In the present embodiment, the power control device 71 calculates the air conditioning use permission power as follows. First, the temporary air conditioning use permission power and the air conditioning usable power are calculated, and the smaller value of the temporary air conditioning use permission power and the air conditioning usable power is set as the air conditioning use permission power.

  Temporary air-conditioning use permission electric power is calculated as follows. When it is not in the eco mode and the remaining power SOC of the battery 81 is not less than 20%, the provisional air-conditioning use permission power is determined to be 8000 W. When it is in the eco mode, or when the remaining power SOC of the battery 81 is lower than 20%, the provisional air conditioning use permission power is determined to be 4000 W.

The air conditioning usable power is calculated by the following formula F4.
Air conditioning usable power = Maximum supply power-Power consumption other than air conditioning ... (F4)
The maximum power supply is the maximum power that can be supplied by the battery 81, and the power consumption other than air conditioning is the power consumed in applications other than air conditioning.

  Specifically, in step S905, the upper limit f of the amount of rotation speed change (air-conditioning use permission power-compressor power consumption) is determined as follows. As shown in step S905 of FIG. 7, the upper limit f of the amount of change in the rotational speed (air-conditioning use permission power−compressor) in the minimum region of air-conditioning use permission power−compressor power consumption (in this embodiment, −1000 W or less) (Power consumption) is determined to be a negative value (-300 rpm in the present embodiment).

  Further, in the maximum region of air conditioning use permission power-compressor power consumption (1000 W or more in the present embodiment), the upper limit f of the amount of change in rotation speed (air conditioning use permission power-compressor power consumption) is a positive value (this In the embodiment, it is determined to be +300 rpm.

  Further, in the intermediate range of air conditioning use permission power-compressor power consumption (in this embodiment, -1000 W or more and 1000 W or less), the upper limit value of the rotation speed change amount according to the increase in air conditioning use permission power-compressor power consumption. f (Air-conditioning use permission power-compressor power consumption) is increased.

In the next step S906, the rotational speed change amount Δf of the compressor 11 is calculated by the following mathematical formula F5, and the process proceeds to step S907.
Δf = MIN (Δf, f (air-conditioning use permission power-compressor power consumption)) (F5)
Note that MIN (Δf, f (air-conditioning use permission power-compressor power consumption)) in Formula F5 means a smaller value of Δf and f (air-conditioning use permission power-compressor power consumption). .

  In subsequent steps S907 to S910, it is determined whether or not to perform compressor automatic stop control for automatically stopping the compressor 11. First, in step S907, it is determined whether or not the outside air temperature is less than 15 ° C. If it is determined that the outside air temperature is less than 15 ° C., it can be determined that if the outside air is introduced even if the compressor 11 is stopped, the evaporator 15 is slow to dry and hardly smells, so the process proceeds to step S908, and the suction port It is determined whether or not the mode is the manual full air mode (manual REC mode).

  If it is determined that the suction port mode is not the manual all-air mode (manual REC mode), it can be determined that even if the compressor 11 is stopped, the drying of the evaporator 15 is slow due to the introduction of the outside air, and it is difficult for odor to occur. To determine whether the relative humidity RHW of the window glass surface is less than 100%.

  When it is determined that the relative humidity RHW of the window glass surface is less than 100%, it can be determined that the window glass is not easily fogged even when the compressor 11 is stopped. Therefore, the process proceeds to step S910, and the target blowing temperature TAO of the vehicle interior blowing air It is determined whether or not the temperature exceeds 25 ° C.

  If it is determined that the target outlet temperature TAO of the vehicle compartment outlet air is higher than 25 ° C., it can be determined that the cooling operation is not necessary, so that the process proceeds to step S911 and the current compressor speed is determined to be zero. In other words, it is determined to execute the compressor stop mode. Thus, the compressor automatic stop control can be performed to reduce the compressor power consumption, and consequently the air conditioning power can be reduced. That is, energy can be saved.

On the other hand, if it is determined in step S907 that the outside air temperature is not less than 15 ° C., if it is determined in step S908 that the suction port mode is the manual all-air mode (manual REC mode), the relative humidity RHW of the window glass surface is determined in step S909. Is determined to be less than 100%, or when it is determined in step S910 that the target outlet temperature TAO of the vehicle compartment outlet air does not exceed 25 ° C., the compressor 11 is operated to cool the air with the evaporator 15. Since it can be determined that it is necessary to dehumidify, the process proceeds to step S912, and the current rotational speed of the compressor is calculated by the following equation F6.
Current compressor speed = MIN {(previous compressor speed + Δf), MAX speed}} (F6)
Note that MIN {(previous compressor rotation speed + Δf), MAX rotation speed} in Formula F6 means the smaller value of the previous compressor rotation speed + Δf and MAX rotation speed.

  As a result, even when the compressor 11 needs to be operated, the refrigerant discharge capacity of the compressor 11 can be reduced in the eco mode or when the compressor power consumption is large, that is, when the air conditioning power needs to be reduced. The power consumption of the compressor can be reduced by lowering, and thus the power for air conditioning can be reduced.

  In the next step S10, the number of operating PTC heaters 37 and the operating state of the electric heat defogger are determined. First, the determination of the number of operating PTC heaters 37 will be described. In step S10, the number of operating PTC heaters 37 is determined according to the outside air temperature Tam, the temporary air mix opening SWdd determined in step S51, and the cooling water temperature Tw. To decide.

  Specifically, when it is determined that the outside air temperature is higher than 26 ° C., it is determined that the blowing temperature assist by the PTC heater 37 is not necessary, and the number of operation of the PTC heater 37 is determined to be zero. On the other hand, when it is determined that the outside air temperature is lower than 26 ° C., it is determined whether or not the PTC heater 37 needs to be operated based on the temporary air mix opening degree SWdd.

  That is, the provisional air mix opening SWdd is reduced, which means that the necessity of heating the blown air in the cold air passage for heating is reduced. Therefore, as the air mix opening SW is reduced. Therefore, the necessity of operating the PTC heater 37 is also reduced.

  Therefore, when the temporary air mix opening degree SWdd is compared with a predetermined reference opening degree and the temporary air mix opening degree SWdd is equal to or less than the first reference opening degree (100% in the present embodiment), the PTC heater Assuming that there is no need to operate 37, the number of operating PTC heaters 37 is determined to be zero.

  On the other hand, if the temporary air mix opening degree SWdd is equal to or larger than the second reference opening degree (110% in the present embodiment), it is necessary to operate the PTC heater 37 and the PTC heater according to the cooling water temperature Tw. The operation number of 37 is determined.

  Specifically, when the cooling water temperature Tw is high enough to sufficiently heat the air with the heater core 36, the number of operation of the PTC heater 37 is determined to be 0, and the number of operation of the PTC heater 37 is decreased as the cooling water temperature Tw is lower. Increase.

  As for the electric heat defogger, the electric heat defogger is operated when the window glass is highly likely to be fogged due to the humidity and temperature in the passenger compartment or when the window glass is fogged.

  In the next step S11, a request signal output from the air conditioning control device 50 to the driving force control device 70 is determined. Examples of the request signal include an engine EG operation request signal (engine ON request signal), an EV / HV operation mode request signal, and the like.

  Here, in a normal vehicle that obtains driving force for driving the vehicle only from the engine EG, the engine is always operated during driving, so that the cooling water is always at a high temperature. Therefore, in a normal vehicle, sufficient heating capacity can be exhibited by circulating cooling water through the heater core 36.

  On the other hand, in the plug-in hybrid vehicle of the present embodiment, the driving force for traveling the vehicle can also be obtained from the traveling electric motor. Therefore, the operation of the engine EG may be stopped, and the vehicle air conditioner 1 When heating the vehicle interior at, the temperature of the cooling water may not rise to a sufficient temperature as a heat source for heating.

  Therefore, the vehicle air conditioner 1 according to the present embodiment does not require the engine EG to operate in order to output the driving force for traveling. A request signal (operation request signal) for requesting the operation of the engine EG is output to the driving force control device 70 that controls the driving force so that the cooling water temperature is raised to a temperature sufficient as a heat source for heating. I have to.

  Next, in Step S12, it is determined whether or not to operate the cooling water pump 40a for circulating the cooling water between the heater core 36 and the engine EG in the cooling water circuit 40. Details of step S12 will be described with reference to the flowchart of FIG. First, in step S121, it is determined whether or not the coolant temperature Tw is higher than the blown air temperature TE.

  In step S121, when the cooling water temperature Tw is equal to or lower than the blown air temperature TE, the process proceeds to step S124, and it is determined to stop (OFF) the cooling water pump 40a. The reason is that if the cooling water flows to the heater core 36 when the cooling water temperature Tw is equal to or lower than the blown air temperature TE, the cooling water flowing through the heater core 36 cools the air after passing through the evaporator 15. Therefore, the temperature of the air blown from the outlet is lowered.

  On the other hand, when the cooling water temperature Tw is higher than the blown air temperature TE in step S121, the process proceeds to step S122. In step S122, it is determined whether the blower 32 is operating. When it is determined in step S122 that the blower 32 is not operating, the process proceeds to step S124, and it is determined to stop (OFF) the cooling water pump 40a for power saving.

  On the other hand, when it determines with the air blower 32 operating in step S122, it progresses to step S123 and determines operating the cooling water pump 40a (ON). As a result, the cooling water pump 40a operates and the cooling water circulates in the refrigerant circuit, so that the cooling air flowing through the heater core 36 and the air passing through the heater core 36 can be heat-exchanged to heat the blown air. .

  Next, in step S13, it is determined whether or not the seat air conditioner 90 needs to be operated. The operating state of the seat air conditioner 90 is a control stored in the air conditioning controller 50 in advance based on the target air temperature TAO determined in step S5, the provisional air mix opening degree Sdd, and the outside air temperature Tam read in step S2. Determined with reference to the map.

  Next, in step S14, various devices 32, 12a, 61, 62, 63, 64, 65, 12a, 37, 37 are provided from the air conditioning control device 50 so that the control state determined in steps S5 to S13 described above is obtained. Control signals and control voltages are output to 40a and 80. Further, the request signal determined in step S11 is transmitted from the request signal output means 50c to the driving force control apparatus 70.

  Next, in step S15, the system waits for the control period τ, and returns to step S2 when it is determined that the control period τ has elapsed. In the present embodiment, the control cycle τ is 250 ms. This is because the air conditioning control in the passenger compartment does not adversely affect the controllability even if the control period is slower than the engine control or the like. As a result, it is possible to suppress a communication amount for air conditioning control in the vehicle and sufficiently secure a communication amount of a control system that needs to perform high-speed control such as engine control.

  Since the vehicle air conditioner 1 of this embodiment operates as described above, the blown air blown from the blower 32 is cooled by the evaporator 15. The cold air cooled by the evaporator 15 flows into the heating cold air passage and the cold air bypass passage according to the opening degree of the air mix door 39.

  The cold air that has flowed into the heating cold air passage is heated when passing through the heater core 36 and the PTC heater 37, and is mixed with the cold air that has passed through the cold air bypass passage in the mixing spaces 35A and 35B. Then, the conditioned air whose temperature is adjusted in the mixing spaces 35A and 35B is blown out from the mixing spaces 35A and 35B into the vehicle interior via the respective outlets.

  When the inside air temperature Tr in the passenger compartment is cooled below the outside air temperature Tam by the conditioned air blown into the inside of the passenger compartment, cooling of the inside of the passenger compartment is realized, while the inside air temperature Tr is heated higher than the outside air temperature Tam. In such a case, heating of the passenger compartment is realized.

  An example of the operation according to this embodiment is shown in FIG. In the example of FIG. 10, when the ignition switch of the vehicle is turned on (IG ON), compressor automatic stop control is started in step S9. That is, the compressor 11 is automatically stopped (step S911). In other words, the automatic dehumidification OFF control is started. That is, the dehumidification by the evaporator 15 is automatically stopped.

  Since the compressor 11 is stopped, in step S7, the suction port mode is determined to be the inside / outside air two-layer flow mode (step S709). In step S6, the blower voltage is determined to be 2V. In other words, the air blower 32 operates and air is blown.

  In this example, since the outside air temperature is 10 ° C., the evaporator drying time is determined to be 120 seconds in step S8 (step S801).

  Therefore, while the count time of the evaporator drying timer is less than the evaporator drying time (120 seconds in this example), the air outlet mode is determined to be the foot mode (step S816). Thereby, since conditioned air is not blown out from the face outlet 24 and the defroster outlet 26, even if the condensed water on the surface of the evaporator 15 evaporates in the inside air passage 31b where the high-temperature inside air is recirculated, odor is generated. Since it can suppress that the air-conditioning wind containing arriving at a passenger | crew's face part, it can suppress that a passenger | crew feels a bad smell.

  Thereafter, when the count time of the evaporator drying timer reaches the evaporator drying time (120 seconds in this example), the air outlet mode is switched to the foot defroster mode (step S815).

  Thereby, the conditioned air dehumidified by the evaporator 15 can be blown out from the defroster outlet 26 to prevent fogging of the window glass. At this time, since the evaporator 15 is dry to such an extent that no odor is generated from the evaporator 15, even if the conditioned air after passing through the evaporator 15 is blown from the defroster outlet 26, the occupant does not feel the odor.

  In the example of FIG. 10, after the ignition switch of the vehicle is turned on (IG ON), the blower voltage (in other words, the blowing capacity of the blower 32) increases as the cooling water temperature Tw rises.

  In the present embodiment, as described in step S8, the air-conditioning control device 50 is configured so that the surface of the evaporator 15 is condensed water in a state where the inside / outside air two-layer flow mode is set and the compressor 11 is stopped. When it is determined that the product is wet, switching prohibition control is performed to prohibit switching to the upper blowing mode. The upper air outlet mode is an air outlet mode in which air in the inside air passage 31b is blown out from the face air outlet 24 and the defroster air outlet 26 (upper air outlet).

According to this, that the air in the first air passage 31 a is prevented blown from the upper side outlet 24 and 26 when and compressor 11 and outside air 2-layer flow mode is set is stopped it can.

Therefore, even when odors condensed water of the evaporator 15 surface in the first air passage 31 a evaporates occurs, it is possible to suppress the odor of the first air passage 31a reaches the face of the occupant, occupant It is possible to suppress a bad odor.

  In the present embodiment, as described in steps S814 and S815, the air conditioning control device 50 ends the switching prohibition control when it is determined that the surface of the evaporator 15 is dry in the case where the switching prohibition control is being performed.

  Thereby, when the surface of the evaporator 15 is dried and no odor is generated, the air in the inside air passage 31b can be blown out from the face outlet 24 or the defroster outlet 26. That is, it is possible to suppress the switching prohibition control from being performed more than necessary.

  In the present embodiment, the air conditioning control device 50 controls the operation of the face door 24a and the defroster door 26a so that the face outlet 24 and the defroster outlet 26 are closed in the switching prohibition control.

  Thereby, at the time of switching prohibition control, the air in the inside air side passage 31b is not reliably blown out from the face air outlet 24 and the defroster air outlet 26.

(Other embodiments)
The above embodiment can be variously modified as follows, for example.

  (1) In the above-described embodiment, in step S816, by determining the air outlet mode as the foot mode, the conditioned air in the inside air passage 31b is prevented from being blown out from the face air outlet 24 and the defroster air outlet 26. In S816, the communication door 38 may close the communication passage 31d so that the conditioned air in the inside air-side passage 31b is not blown out from the face outlet 24 and the defroster outlet 26.

  That is, the air conditioning control device 50 may control the operation of the communication door 38 so that the communication path 31d is closed in the above-described switching prohibition control. Even in this case, the air in the inside air passage 31b is not reliably blown out from the face outlet 24 and the defroster outlet 26 during the switching prohibition control as in the above embodiment.

  In this embodiment, the communication door 38 functions as a blowing switching unit that switches to the upper blowing mode.

  (2) In the above embodiment, when it is determined in steps S814 and S816 that the evaporator 15 is moist and odor may be generated from the evaporator 15, the foot defroster mode is prohibited and the foot mode is disabled. Even if it is determined that the evaporator 15 is moist and there is a possibility that odors may be generated from the evaporator 15, the window may be displayed when it is determined that the window glass is very likely to be fogged. The foot defroster mode or the defroster mode may be set giving priority to prevention of fogging of the glass.

  Whether the window glass is very likely to be fogged may be determined, for example, based on the relative humidity RHW of the window glass surface.

  (3) Although the details of the driving force for driving the hybrid vehicle are not described in the above embodiment, a so-called parallel type hybrid that can travel by directly obtaining driving force from both the engine EG and the driving electric motor. The vehicle air conditioner 1 may be applied to the vehicle, or the engine EG is used as a drive source of the generator 80, the generated power is stored in the battery 81, and further, the power stored in the battery 81 is supplied. The vehicle air conditioner 1 may be applied to a so-called serial-type hybrid vehicle that travels by obtaining a driving force from the traveling electric motor that operates by the above.

  Moreover, you may apply the vehicle air conditioner 1 to the electric vehicle which obtains the driving force for vehicle travel only from a travel electric motor, without providing the engine EG. In this case, for example, an electric heater such as a PTC heater can be used as the cooling water heating means for heating the cooling water.

  Moreover, you may apply the vehicle air conditioner 1 to the motor vehicle which obtains the driving force for vehicle travel only from the engine EG, without providing the travel electric motor. In this case, the compressor 11 can be a belt-driven compressor that is driven by an engine belt by the driving force of the engine EG.

11 Compressor 15 Evaporator 23A First inside / outside air switching door (inside / outside air switching means)
23B Second inside / outside air switching door (inside / outside air switching means)
24 Face outlet (upper side outlet)
24a Face door (outlet switching means)
25 Foot outlet (upper side outlet)
25a Foot door (outlet switching means)
26 Defroster outlet (lower outlet)
26a Defroster door (outlet switching means)
31 Casing 31a Outside air passage (first air passage)
31b Inside air side passage (second air passage)
32 Blower (Blower means)
36 Heater core (air heating means)
50 Air-conditioning control device (control means)

Claims (4)

A first air passage (31a) and a second air passage (31b) through which air blown into the vehicle interior space flows in parallel with each other, and a defroster that blows out the air in the first air passage (31a) toward the vehicle window outlet and (2 6), and the second said foot outlet (25) for blowing toward air to the power-membered feet of the air passage (31b) a casing to form a (31),
A blowing means (32) for blowing air to the first air passage (31a) and the second air passage (31b);
Inside / outside air switching means (23A, 23B) capable of setting an inside / outside air two-layer flow mode in which outside air is introduced into the first air passage (31a) and inside air is introduced into the second air passage (31b);
A compressor (11) for sucking and discharging refrigerant;
A radiator (12) for radiating the heat of the refrigerant discharged from the compressor (11);
Decompression means (14) for decompressing the refrigerant radiated by the radiator (12);
The refrigerant is evaporated by heat exchange between the refrigerant decompressed by the decompression means (14) and the air flowing through the first air passage (31a) and the second air passage (31b). An evaporator (15) for cooling the
Air heating means (36) for heating the air flowing through the first air passage (31a) and the second air passage (31b);
The foot defroster said air air the defroster outlet (2 6) are blown out and the second air passage (31b) is blown from the foot outlet (25) of said first air passage (31 a) Blowing switching means (24a, 25a, 26a, 38) for switching between a mode and a foot mode in which the air in the second air passage (31b) is blown from the foot outlet (25) ;
When the inside / outside air switching means (23A, 23B) sets the inside / outside air two-layer flow mode and the compressor (11) is stopped, the window is likely to be cloudy and the evaporator (15). When it is determined that the surface of the water is wet with condensed water, the blow switching means (24a, 25a, 26a, 38) prohibits switching to the foot defroster mode and performs switching prohibition control to switch to the foot mode. A vehicle air conditioner comprising control means (50).   The said control means (50) ends the said switch prohibition control, when it is judged that the surface of the said evaporator (15) has dried in the said switch prohibition control being performed. The vehicle air conditioner described. It said outlet switching means has a defroster outlet closing means (26a) for opening and closing the defroster outlet (26),
The said control means (50) controls the action | operation of the said defroster blower outlet opening-and-closing means ( 26a) so that the said defroster blower outlet ( 26) may be closed in the said switching prohibition control. The vehicle air conditioner described in 1. The casing (31) forms a communication passage (31d) that connects the first air passage (31a) and the second air passage (31b),
The blowing switching means has communication path opening / closing means (38) for opening and closing the communication path (31d),
The said control means (50) controls the action | operation of the said communication path opening / closing means (38) so that the said communication path (31d) may be closed in the said switching prohibition control. Vehicle air conditioner.

Images