JP5895788B2 - Air conditioner for vehicles - Google Patents

Description

  The present invention adjusts the temperature of the passenger compartment air and blows it out toward the lower side of the passenger compartment, and adjusts the temperature of the passenger compartment air to the upper side of the passenger compartment so that the inside / outside air two-layer mode can be executed. The present invention relates to a two-layer vehicle air conditioner.

  2. Description of the Related Art Conventionally, as a vehicle air conditioner, first and second air passages are formed in an air conditioning case, and the outside air sucked in by a first blower fan is blown upward through the first air passage to the second side. 2. Description of the Related Art A vehicle air conditioner of an inside / outside air two-layer type that can execute an inside / outside air two-layer mode that blows out the inside air sucked in by a blower fan to the lower side of the vehicle interior via a second air passage is known (for example, Patent Documents). 1).

  In this patent document 1, in order to prevent freezing at the time of the low outside temperature of the cooling heat exchanger that cools the air flowing through each air passage in the air conditioning case, and to prevent white fog in the vehicle interior at the time of the high outside temperature. In addition, a configuration is disclosed that switches to an outside air mode in which outside air is introduced into each air passage when the cooling heat exchanger operates. That is, the inside / outside air two-layer mode is executed only when the cooling heat exchanger is not operated.

  Moreover, in patent document 1, while the heat exchanger for heating which heats the air after passing through the heat exchanger for cooling is arrange | positioned in an air-conditioning case, to each air path in an air-conditioning case, to a heat exchanger for heating First and second air mix doors for adjusting the flow rate ratio between the flowing air and the air flowing around the heat exchanger for heating are provided, and an evaporator temperature sensor (post-evaporation temperature sensor) provided in the first air passage It is disclosed that each air mix door is controlled based on the detected value.

Japanese Patent No. 3812083

  By the way, in the above-described prior art, when the temperature difference between the outside air and the inside air is large, the temperature of the blown air blown upward in the vehicle interior and the temperature of the blown air blown downward in the inside / outside air two-layer mode greatly deviates. No consideration is given to the problem that would occur.

  Hereinafter, the factors that cause a difference in the temperature of the air blown up and down in the vehicle interior in the inside / outside air two-layer mode in the prior art will be described.

  In the prior art, since the cooling heat exchanger is not operating in the inside / outside air two-layer mode, the air after passing through the cooling heat exchanger in the first air passage has almost the same temperature as the outside air temperature, and the second air The air after passing through the cooling heat exchanger in the passage has almost the same temperature as the inside air temperature. For this reason, if the temperature difference between the inside air and the outside air is large, the temperature of the air after passing through the cooling heat exchanger in the first air passage and the temperature of the air after passing through the cooling heat exchanger in the second air passage are greatly different. Will be.

  At this time, as in the prior art, when each air mix door is controlled based on the detected value of the evaporator temperature sensor provided in one of the air passages, the air flowing into the heating heat exchanger and the heating heat exchanger The flow rate ratio with the air flowing around the air passage is the same in each air passage, and there is a possibility that the air flowing through each air passage after passing through the heat exchanger for heating is blown out into the vehicle compartment in a state of greatly deviating. If the difference between the blowout temperatures blown up and down in the vehicle interior is large, it becomes a factor that impairs the comfort of passengers in the vehicle interior.

  Even when the cooling heat exchanger is operating in the internal / external air two-layer mode, if the temperature difference between the external air and the internal air is large, the temperature of the air after passing through the cooling heat exchanger in each air passage Tends to deviate, and there is a possibility that the temperature of the air blown up and down in the passenger compartment deviates as in the case where the cooling heat exchanger is not operating.

  In contrast, an evaporator temperature sensor for detecting the temperature of the cooling heat exchanger is provided in each of the first and second air passages, and each air mix door is controlled based on the detection value of each temperature sensor. However, there is a problem that the number of parts arranged in the air conditioning case increases and the vehicle air conditioner becomes complicated.

  In view of the above points, it is a first object of the present invention to provide a vehicle air conditioner that can determine the difference between the upper and lower outlet temperatures into the vehicle interior in the inside / outside air two-layer mode with a simple configuration. .

  In addition, a second object of the present invention is to provide a vehicle air conditioner having a simple configuration and capable of ensuring passenger comfort in the inside / outside air two-layer mode.

In order to achieve the first object, according to the first to third aspects of the invention, the first and second blower fans (131, 132) for blowing air toward the vehicle interior and the first blower fan (131). ), The first air passage (112) through which the first blown air blown from, the second air passage (113) through which the second blown air blown from the second blower fan (132) flows, the upper part of the vehicle interior A casing (11) in which an upper opening (11a, 11b) for guiding air to the side and a lower opening (11c) for guiding air to the lower side of the passenger compartment are formed, and the casing is disposed in the casing The cooling heat exchanger (14) for cooling the first and second blown air, and the heating for heating the first and second blown air disposed on the downstream side of the air flow of the cooling heat exchanger in the casing. Heat exchanger (15) and first air passage Cooling heat exchanger and heating in the inside / outside air two-layer mode in which the introduced outside air is blown out through the upper opening and the inside air introduced into the second air passage is blown out through the lower opening. Temperature estimation means (50a) for estimating the temperatures of the first and second blown air immediately after passing through at least one of the heat exchangers, and the first and second estimated by the temperature estimation means. Based on the temperature of the blown air, it is determined whether or not there is a vertical temperature deviation state in which the blowing temperature of the air blown through the upper opening and the blowing temperature of the air blown through the lower opening are greatly deviated. And an upper and lower temperature deviation determination means (50b).
In the first aspect of the invention, the cooling temperature detecting means (54) disposed in one of the first air passage and the second air passage for detecting the temperature of the cooling heat exchanger, Provided, and the temperature estimating means exhibits the function of the cooling heat exchanger cooling the first and second blown air from the function exhibiting state of the cooling heat exchanger exhibiting the function of cooling the first and second blown air. At the time of transition to the function stop state, the temperature of the blown air immediately after passing through the heating heat exchanger in one air passage is estimated from the temperature of the heating heat exchanger and the detected value of the cooling temperature detecting means, and the heat exchange for heating Heat exchange in the other air passage from the correction value corrected by the temperature rise rate of the heat exchanger for cooling when the temperature of the cooling unit and the detected value of the cooling temperature detection means are shifted from the function exhibiting state to the function stopping state Of blown air just after passing And estimates the degree.
In order to achieve the second object, in the invention according to claim 2 or 3, the first blown air that is arranged in the first air passage and flows to the heat exchanger for heating, and the heat exchanger for heating are provided. The first air mix door (17) that changes the air volume ratio of the first blown air that flows in a detour, the second blown air that is arranged in the second air passage and flows to the heat exchanger for heating, and the heat exchanger for heating A second air mix door (18) that changes the flow rate ratio of the second blown air that flows around the door, and door control means (50c) that controls the operation of the first and second air mix doors, The control means, when the vertical temperature deviation determination means determines that the vertical temperature deviation state, the temperature difference between the blowout temperature of the air blown through the upper side opening and the blowout temperature of the air blown through the lower side opening The first and second so that And controlling the operation of Amikkusu door.
According to this, even if the vehicle interior temperature and the vehicle exterior temperature greatly deviate from each other, the control of the first and second air mix doors causes the difference between the upper and lower blowout temperatures into the vehicle interior in the inside / outside air two-layer mode. Can be suppressed. Therefore, it is possible to ensure the comfort of the occupant in the inside / outside air two-layer mode with a simple configuration.
Furthermore, in the invention according to claim 2, the door control means exhibits a function in which the heat exchanger for heating heats the first and second blown air, and the heat exchanger for cooling has the first and second blown air. In the heating state where the function of cooling the air is not exhibited, when it is determined that the vertical temperature deviation state is determined by the vertical temperature deviation determination unit, the first blown air flows into the heating heat exchanger so that all of the first blown air flows into the heating heat exchanger. The operation of the second air mix door is controlled so that a part of the second blown air flows into the heating heat exchanger and the remainder flows around the heating heat exchanger while controlling the operation of the first air mix door. It is characterized by controlling.
In the invention according to claim 3, the door control means exhibits a function in which the cooling heat exchanger cools the first and second blowing air, and the heating heat exchanger has the first and second blowing air. When it is determined that the vertical temperature divergence state is determined by the vertical temperature divergence determining means in the cooling state where the function of heating the air is not exhibited, all of the first blown air flows so as to bypass the heating heat exchanger. The second air mix door is controlled so that the operation of the first air mix door is controlled and a part of the second blown air flows into the heating heat exchanger and the remainder flows around the heating heat exchanger. It is characterized by controlling the operation of.

  Thus, if it is set as the structure which estimates the temperature of the 1st, 2nd ventilation air immediately after at least one heat exchanger passage among a heat exchanger for cooling and a heat exchanger for heating, the 1st, 2nd air Without providing dedicated temperature detection means on both sides of the passage, it is possible to determine the difference between the upper and lower blowing temperatures into the vehicle compartment in the inside / outside air two-layer mode with a simple configuration.

Specifically, in the invention described in claim 6, in the vehicle air conditioning system according to any one of claims 1 to 5, the temperature estimation means, the heating heat exchanger first, second blower Heating from the temperature of the heat exchanger for heating and the temperature of the outside air in the vehicle when the cooling heat exchanger is in a heating state that does not exhibit the function of cooling the first and second blown air. Estimating the temperature of the first blown air immediately after passing through the heat exchanger and estimating the temperature of the second blown air immediately after passing through the heat exchanger for heating from the temperature of the heat exchanger for heating and the temperature of the passenger compartment air. Features.

  According to this, without providing dedicated temperature detection means in both the first and second air passages, it is possible to determine the difference between the upper and lower outlet temperatures into the vehicle compartment in the inside / outside air two-layer mode when the heating state is established. It becomes possible.

According to a seventh aspect of the present invention , in the vehicle air conditioner according to any one of the first to sixth aspects, the temperature estimating means is such that the cooling heat exchanger cools the first and second blown air. When the heating heat exchanger is in a cooling state that does not exhibit the function of heating the first and second blown air, the heat exchange for cooling is performed from the temperature of the cooling heat exchanger and the temperature of the outside air of the passenger compartment. The temperature of the 1st blowing air immediately after passing through the cooler is estimated, and the temperature of the second blown air immediately after passing through the cooling heat exchanger is estimated from the temperature of the cooling heat exchanger and the temperature of the passenger compartment air. .

  According to this, without providing dedicated temperature detection means in both the first and second air passages, it is possible to determine the difference between the upper and lower outlet temperatures into the vehicle compartment in the inside / outside air two-layer mode when the cooling state is established. It becomes possible.

  In addition, the code | symbol in the parenthesis of each means described in this column and the claim shows an example of a correspondence relationship with the specific means described in the embodiment described later.

It is a typical whole block diagram of the vehicle air conditioner which concerns on 1st Embodiment. It is a flowchart which shows the flow of a series of control processing by the control apparatus which concerns on 1st Embodiment. It is a flowchart which shows the flow of the determination process of the air mix door opening degree by the control apparatus which concerns on 1st Embodiment. It is explanatory drawing for demonstrating the temperature of the 1st, 2nd ventilation air immediately after the indoor condenser passage in the indoor air conditioning unit which concerns on 1st Embodiment. It is explanatory drawing for demonstrating the flow of the air at the time of the inside / outside air two-layer mode in the indoor air conditioning unit which concerns on 1st Embodiment. It is explanatory drawing for demonstrating the flow of the air at the time of the inside / outside air two-layer mode in the indoor air conditioning unit which concerns on 1st Embodiment. It is explanatory drawing for demonstrating the temperature change inside an indoor air-conditioning unit at the time of the operation mode transition of a refrigerating cycle. It is a flowchart which shows the flow of the temperature estimation process by the control apparatus which concerns on 2nd Embodiment. It is explanatory drawing for demonstrating the correction | amendment term of the temperature increase rate set according to the temperature difference of internal temperature and evaporator temperature. It is explanatory drawing for demonstrating the correction | amendment term of the temperature increase rate set according to the ventilation volume of an air blower. It is a flowchart which shows the flow of the determination process of the air mix door opening degree by the control apparatus which concerns on 3rd Embodiment. It is explanatory drawing for demonstrating the temperature of the 1st, 2nd ventilation air immediately after the evaporator passage in the indoor air conditioning unit which concerns on 3rd Embodiment. It is explanatory drawing for demonstrating the flow of the air at the time of the inside / outside air two-layer mode in the indoor air conditioning unit which concerns on 3rd Embodiment. It is explanatory drawing for demonstrating the flow of the air at the time of the inside / outside air two-layer mode in the indoor air conditioning unit which concerns on 3rd Embodiment. It is explanatory drawing for demonstrating the flow of the air at the time of the inside / outside air two-layer mode in the indoor air conditioning unit which concerns on 4th Embodiment. It is explanatory drawing for demonstrating the flow of the air at the time of the inside / outside air two-layer mode in the indoor air conditioning unit which concerns on 5th Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
First, the first embodiment will be described. As shown in FIG. 1, the vehicle air conditioner 1 of the present embodiment includes an indoor air conditioning unit 10 that adjusts the temperature and humidity of the blown air blown into the vehicle interior.

  The indoor air conditioning unit 10 is arranged inside the instrument panel (instrument panel) at the foremost part of the vehicle interior, and houses a blower 13, an evaporator 14, an indoor condenser 15 and the like in a casing 11 that forms an outer shell thereof. Is.

  The casing 11 forms an air passage for blown air that is blown into the vehicle interior. Inside the casing 11 of the present embodiment, a partition plate 111 that partitions an air passage formed therein into two air passages, an upper first air passage 112 and a lower second air passage 113, is disposed. ing.

  The blower 13 blows blown air toward the passenger compartment, and the first and second blower fans 131 and 131 formed of a centrifugal multiblade fan (sirocco fan) are connected by a common electric motor (not shown). The electric blower is driven, and the number of rotations (the amount of blown air) is controlled by a control voltage output from the control device 50 described later.

  More specifically, the first and second blower fans 131 and 132 are rotatably accommodated in first and second scroll casings (not shown) disposed in the first and second air passages 112 and 113, respectively. Yes.

  Accordingly, the first blown air blown by the first blower fan 131 flows through the first air passage 112, and the second blown air blown by the second blower fan 132 passes through the second air passage 113. .

  Further, in the present embodiment, the inside / outside air switching device 12 is disposed on the upstream side of the air flow of the blower 13 and on the most upstream side of the air flow of the casing 11. The inside / outside air switching device 12 is an inside / outside air switching means for switching the air to be introduced to the suction side of the first and second blower fans 131 and 132 between outside air (outside air) and inside air (inside air).

  The inside / outside air switching device 12 is formed with an outside air introduction port 121 for introducing outside air into each of the air passages 112 and 113 and an inside air introduction port 122 for introducing inside air. Furthermore, an inside / outside air switching door 123 that opens and closes the outside air introduction port 121 and the inside air introduction port 122 is disposed inside the inside / outside air switching device 12.

  The inside / outside air switching door 123 is constituted by a so-called cantilever door having a rotating shaft driven by an electric actuator (servo motor) (not shown) and a plate-like door main body connected to the one end of the rotating shaft. Yes. The operation of the electric actuator that drives the inside / outside air switching door 123 is controlled by a control signal output from the control device 50.

  In the vehicle air conditioner 1 of the present embodiment, the inside / outside air switching door 123 is rotationally displaced to a desired position, and the outside air introduction port 121 and the inside air introduction port 122 are opened and closed, thereby blowing either outside air or inside air. The suction port mode leading to the suction side of the fans 131 and 132 is switched. As the suction port mode, an outside air mode, an inside air mode, and an inside / outside air mode are provided.

  In the outside air mode, the inside / outside air switching door 123 is rotationally displaced to the closed position of the inside air introduction port 122 (the open position of the outside air introduction port 121), thereby introducing the outside air to the suction side of each of the blower fans 131 and 132. is there.

  The inside air mode is a suction port mode in which the inside / outside air switching door 123 is rotationally displaced to the closed position of the outside air introduction port 121 (the opening position of the inside air introduction port 122) to guide the inside air to the suction side of each of the blower fans 131 and 132. is there.

  In the inside / outside air mode, the inside / outside air switching door 123 is rotationally displaced to an open position where both the outside air introduction port 121 and the inside air introduction port 122 are opened, thereby introducing outside air to the suction side of the first blower fan 131 and This is a suction port mode that guides the inside air to the suction side of the two blower fans 132.

  Subsequently, an evaporator 14 is disposed on the downstream side of the air flow of the blower 13. The evaporator 14 according to the present embodiment is one of the components constituting the heat pump cycle 30 to be described later, and evaporates the low-pressure refrigerant in the heat pump cycle 30 to exert a heat absorbing action, thereby providing each of the blower fans 131 and 132. It is a heat exchanger for cooling which cools the ventilation air from.

  The evaporator 14 is disposed so as to pass through a through hole provided in the partition plate 111 disposed in the casing 11, and the upper heat exchange portion thereof is positioned in the first air passage 112, and the lower side A heat exchange part is positioned in the second air passage 113. Accordingly, the first blown air is cooled in the upper heat exchange section of the evaporator 14, and the second blown air is cooled in the lower heat exchange section of the evaporator 14.

  Further, an indoor condenser 15 is arranged on the downstream side of the air flow of the evaporator 14. The indoor condenser 15 is one of the components constituting the heat pump cycle 30 described later, and heat for heating the air that has passed through the evaporator 14 by radiating the heat of the high-pressure refrigerant in the heat pump cycle 30. It is an exchanger.

  The indoor condenser 15 is disposed so as to penetrate a through hole provided in the partition plate 111 disposed in the casing 11, and an upper heat exchange portion thereof is positioned in the first air passage 112, and the lower side A heat exchange part is positioned in the second air passage 113. Accordingly, the first blown air is heated in the upper heat exchange section of the indoor condenser 15, and the second blown air is heated in the lower heat exchange section of the indoor condenser 15.

  Here, on the upper side of the indoor condenser 15 in the first air passage 112, the first blown air that has passed through the upper heat exchange section of the evaporator 14 bypasses the upper heat exchange section of the indoor condenser 15. A first bypass passage 161 for flowing is formed. In the space on the downstream side of the air flow of the indoor condenser 15 in the first air passage 112, the first blown air that has passed through the first bypass passage 161 merges with the first blown air heated in the indoor condenser 15. It is supposed to be.

  Further, the second blown air that has passed through the lower heat exchange section of the evaporator 14 is caused to flow around the lower heat exchange section of the indoor condenser 15 on the lower side of the indoor condenser 15 in the second air passage 113. For this purpose, a second bypass passage 162 is formed. In the space on the downstream side of the air flow of the indoor condenser 15 in the second air passage 113, the second blown air that has passed through the second bypass passage 162 joins the second blown air heated in the indoor condenser 15. It is supposed to be.

  Further, first and second air mix doors 17 and 18 are disposed between the evaporator 14 and the indoor condenser 15 in the first and second air passages 112 and 113. The first air mix door 17 is a flow rate ratio between the amount of blown air passing through the upper heat exchange part of the indoor condenser 15 and the amount of blown air passing through the first bypass passage 161 in the air after passing through the evaporator 14. It is a member for adjusting. The second air mix door 18 is a flow rate ratio between the amount of blown air passing through the lower heat exchange section of the indoor condenser 15 and the amount of blown air passing through the second bypass passage 162 in the air after passing through the evaporator 14. It is a member for adjusting.

  In the present embodiment, as each air mix door 17, 18, a flat plate member is slid and displaced by an electric actuator (servo motor) (not shown), and the air inflow area in each heat exchange part of the indoor condenser 15, and 1. The sliding door which changes the opening area of the entrance side of the 2nd bypass passages 161 and 162 is employ | adopted.

  In this embodiment, the electric actuator is provided corresponding to each air mix door 17 and 18 so that each air mix door 17 and 18 can be controlled independently. The operation of the electric actuator that drives each air mix door 17, 18 is controlled by a control signal output from the control device 50.

  In the present embodiment, a communication hole penetrating the front and back is formed in a part of the partition plate 111 on the downstream side of the air flow of the indoor condenser 15, and an opening / closing door 111a for opening and closing the communication hole is disposed.

  The operation of the open / close door 111a is controlled by a control signal output from the control device 50. The open / close door 111a of the present embodiment closes the communication hole when the air outlet mode is a mode in which air is blown up and down in the vehicle interior such as the foot mode and the bi-level mode, and opens the communication hole when other air outlet modes are used. To be controlled.

  A defroster opening 11a, a face opening 11b, and a foot opening 11c are formed at the most downstream portion of the air flow of the casing 11 to allow the blown air blown into the vehicle interior to flow out of the casing 11.

  The defroster opening 11 a is an opening hole for guiding the blown air flowing in the casing 11 to the vehicle window glass W. The defroster opening 11a is connected to a defroster outlet 19a disposed in the vehicle compartment via a blowout duct, and air whose temperature is adjusted toward the inner surface of the vehicle window glass W is blown out from the defroster outlet 19a. .

  The face opening 11b is an opening hole for guiding the blown air flowing in the casing 11 to the upper body of the occupant. The face opening portion 11b is connected to a face air outlet 19b disposed in the vehicle compartment via an air outlet duct, and air whose temperature is adjusted is blown out from the face air outlet 19b toward the upper body of the occupant.

  The foot opening 11c is an opening hole for guiding the blown air flowing in the casing 11 to the lower body (foot) of the occupant. The foot opening 11c is connected to a foot outlet 19c through an outlet duct, and air whose temperature is adjusted is blown out from the foot outlet 19c toward the lower body (foot) of the occupant.

  In the present embodiment, the defroster opening 11a and the face opening 11b constitute an upper opening that blows the first blown air toward the upper side of the vehicle interior, and the foot opening 11c is the lower side of the vehicle interior. The lower side opening part which blows off 2nd ventilation air toward the side is comprised.

  A defroster door 20a, a face door 20b, and a foot door 20c are rotatably disposed at upstream portions of the openings 11a to 11c. Each of these doors 20a to 20c constitutes an outlet mode switching means for switching an outlet mode of the conditioned air blown into the passenger compartment. Each of the doors 20a to 20c includes a rotary shaft driven by an electric actuator (servo motor), It is comprised with what is called a butterfly door which has the plate-shaped door main-body part by which the rotating shaft was connected to the approximate center part of the plate surface.

  Furthermore, the rotation shafts of the doors 20a to 20c are connected via a link mechanism (not shown), and the doors 20a to 20c are opened and closed by a common electric actuator. The operation of the electric actuator for the air outlet mode switching means is controlled by a control signal output from the control device 50.

  Further, as the air outlet mode that is switched by the doors 20a to 20c constituting the air outlet mode switching means, a face mode in which the face opening 11b is fully opened and air is blown out from the face air outlet 19b toward the upper body of the occupant. A bi-level mode in which both the opening 11b and the foot opening 11c are opened to blow air toward the upper and lower bodies of the passengers in the passenger compartment, the foot opening 11c is fully opened and the defroster opening 11a is opened by a small opening. In addition, there is a foot differential mode in which air is mainly blown from the foot outlet 19c.

  In addition, it can also be set as the defroster mode which blows off air-conditioning wind from the defroster blower outlet 19a to the vehicle windshield W inner surface by fully opening the defroster opening part 11a by a passenger | crew's manual operation of the switch of an operation panel.

  Here, when the suction port mode is set to the inside / outside air mode and the outlet mode is set to the foot differential mode or the bi-level mode, the outside air introduced into the first air passage 112 is defroster opening 11a. Or the inside air introduced into the second air passage 113 is blown out to the lower side of the vehicle interior via the foot opening 11c through the face opening 11b. That is, a state in which the suction port mode is set to the inside / outside air mode and the outlet mode is set to either the foot differential mode or the bi-level mode is the inside / outside air two-layer mode described in the claims.

  Next, the heat pump cycle 30 will be described. In the heat pump cycle 30 of the present embodiment, by changing the refrigerant flow path, the operation mode is a cooling mode for cooling the vehicle interior, a normal heating mode for heating the vehicle interior, a dehumidification for dehumidifying and heating the vehicle interior It is configured to be switchable to the heating mode. The cooling mode is a mode (cooling state) in which the evaporator 14 basically exhibits the function of cooling the blown air and the indoor condenser 15 does not perform the function of heating the blown air. In this mode, the evaporator 14 basically does not exhibit the function of cooling the blown air, and the indoor condenser 15 exhibits the function of heating the blown air (heating state).

  The heat pump cycle 30 includes a compressor 31, an evaporator 14, an indoor condenser 15, an outdoor heat exchanger 33, first and second electromagnetic valves 32 and 35 as decompression means for decompressing and expanding the refrigerant, an accumulator 36, and the like. Yes.

  The compressor 31 compresses and discharges the refrigerant, and is composed of an electric compressor that drives a compression mechanism (not shown) having a fixed discharge capacity by an electric motor (not shown). The electric motor is controlled according to a control signal output from the control device 50.

  The refrigerant discharge side of the compressor 31 is connected to the refrigerant inlet side of the indoor condenser 15 that functions as a heat exchanger for heating that heats the blown air. A first solenoid valve 32 is connected to the refrigerant outlet side of the indoor condenser 15.

  The first solenoid valve 32 functions as a decompression unit that decompresses the refrigerant that has flowed out of the indoor condenser 15 in the normal heating mode and the dehumidifying heating mode, and remains as it is without decompressing the refrigerant that has flowed out of the indoor condenser 15 in the cooling mode. It consists of a variable aperture mechanism with a fully open function that allows it to pass through. The first electromagnetic valve 32 has its throttle opening controlled in accordance with a control signal output from the control device 50.

  The refrigerant inlet side of the outdoor heat exchanger 33 is connected to the refrigerant outlet side of the first electromagnetic valve 32. The outdoor heat exchanger 33 exchanges heat between the refrigerant circulating inside and the outside air blown from an outdoor fan (not shown).

  A second electromagnetic valve 35 is connected to the refrigerant outlet side of the outdoor heat exchanger 33 via a check valve 34. The second electromagnetic valve 35 functions as a pressure reducing means for reducing the pressure of the refrigerant flowing out of the outdoor heat exchanger 33 during the cooling mode and the dehumidifying heating mode, and is a refrigerant between the outdoor heat exchanger 33 and the evaporator 14 during the normal heating mode. It is composed of a variable throttle mechanism with a fully closing function that closes the passage. In addition, the throttle opening degree of the second electromagnetic valve 35 is controlled in accordance with a control signal output from the control device 50.

  The refrigerant outlet side of the second electromagnetic valve 35 is connected to the refrigerant inlet side of the evaporator 14 that functions as a cooling heat exchanger for cooling the blown air. An accumulator 36 is connected to the refrigerant outlet side of the evaporator 14.

  The accumulator 36 is a gas-liquid separator that separates the gas-liquid of the refrigerant flowing into the interior and stores the separated liquid-phase refrigerant as surplus refrigerant. The outlet of the separated gas-phase refrigerant is connected to the suction side of the compressor 31. It is connected.

  Further, between the outdoor heat exchanger 33 and the accumulator 36, the refrigerant that has flowed out of the outdoor heat exchanger 33 bypasses the check valve 34, the second electromagnetic valve 35, and the evaporator 14 and flows to the accumulator 36. A refrigerant bypass passage 37 is provided.

  A passage opening / closing valve 38 for opening and closing the refrigerant bypass passage 37 is disposed in the refrigerant bypass passage 37. The passage opening / closing valve 38 is configured to open the refrigerant bypass passage 37 in the normal heating mode and close the refrigerant bypass passage 37 in the cooling mode and the dehumidifying heating mode.

  Thereby, in the normal heating mode, the refrigerant that has flowed out of the outdoor heat exchanger 33 flows into the accumulator 36 by bypassing the check valve 34, the second electromagnetic valve 35, and the evaporator 14. The throttle opening degree of the passage opening / closing valve 38 is controlled in accordance with a control signal output from the control device 50.

  Next, the electric control part of the vehicle air conditioner of this embodiment will be described. The control device 50 includes a well-known microcomputer including a CPU, a memory constituting a storage means, and its peripheral circuits.

  Various devices 13, 123, 17, 18, 20 a to 20 c constituting the indoor air conditioning unit 10, various devices 31, 32, 35, 38 constituting the heat pump cycle 30 are connected to the output side of the control device 50. The operation of each device is controlled based on a control program stored in the memory.

  Further, on the input side of the control device 50, an inside air temperature sensor (inside air temperature detecting means) 51 for detecting the temperature of inside air, an outside air temperature sensor (outside air temperature detecting means) 52 for detecting the temperature of outside air, and the amount of solar radiation are detected. A solar radiation sensor 53, an evaporator temperature sensor (cooling temperature detecting means) 54 for detecting the surface temperature (fin temperature) of the evaporator 14, and a heating temperature sensor (for example, a refrigerant temperature) for detecting the condenser temperature (for example, the refrigerant temperature) of the indoor condenser 15. Various air conditioning sensor groups (not shown) such as a heating temperature detecting means 55 and an operation panel (not shown) are connected. The control device 50 receives detection signals from various air conditioning sensor groups and operation signals from various operation switches on the operation panel.

  Specifically, the evaporator temperature sensor 54 of the present embodiment detects the fin temperature of the lower heat exchange part (second air passage 113 side) of the evaporator 14. Of course, as the evaporator temperature sensor 54, a cooling temperature detecting means for directly detecting the temperature of the refrigerant flowing through the lower heat exchange section of the evaporator 14 may be employed.

  Here, when the temperature difference between the outside air temperature and the inside air temperature is large in the inside / outside air two-layer mode, there is a possibility that the blowing temperature of the air blown up and down in the passenger compartment greatly deviates.

  Therefore, the control device 50 of the present embodiment estimates the temperatures of the first and second blown air immediately after passing through at least one of the evaporator 14 and the indoor condenser 15 in the inside / outside air two-layer mode. Based on the estimated temperature, it is determined whether or not the blowing temperature of the air blown up and down in the passenger compartment greatly deviates.

  Note that immediately after passing through the indoor condenser 15 means a section from passing through the indoor condenser 15 to the merging portion where the air flowing through the bypass passages 161 and 162 is joined. It means a section from the passage through the condenser 14 to the indoor condenser 15 and the bypass passages 161 and 162.

  Further, the control device 50 according to the present embodiment determines the opening degrees of the first and second air mix doors 17 and 18 according to the determination result obtained by determining the difference in the temperature of the air blown up and down in the passenger compartment. I have to.

  In addition, the structure which estimates the temperature of the 1st, 2nd ventilation air immediately after at least one heat exchanger among the evaporator 14 and the indoor condenser 15 in the control apparatus 50 comprises the temperature estimation means 50a, and temperature estimation The structure for determining whether or not the blowing temperature of the air blown up and down in the passenger compartment greatly deviates according to the estimation result of the means 50a constitutes the up-and-down temperature deviation judging means 50b. Moreover, the structure which controls the action | operation of the 1st, 2nd air mix doors 17 and 18 in the control apparatus 50 comprises the door control means 50c.

  Next, the operation of this embodiment in the above configuration will be described. In the vehicle air conditioner 1 of the present embodiment, when an operation signal of the vehicle air conditioner 1 is input from the operation panel in the vehicle operating state, the control device 50 executes the control program stored in the memory.

  Hereinafter, the control processing executed by the control device 50 will be described with reference to the flowchart of FIG. First, initialization processing of various flags and settings is performed (S10). The initialization process is a process performed at the start of execution of the control process. Once the process is completed, the process is skipped and the process proceeds to the next process.

  Subsequently, the detection signal detected by the air conditioning sensor group and the operation signal of the operation panel are read (S20), and the target blowing temperature TAO of the air blown into the vehicle interior is calculated based on these signals (S30). .

Specifically, 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 temperature setting switch on the operation panel, Tr is the inside air temperature detected by the inside air temperature sensor 51, Tam is the outside air temperature detected by the outside air temperature sensor 52, and Ts is the solar radiation sensor. The solar radiation amount detected by 53, Kset, Kr, Kam, and Ks are control gains, and C is a correction constant.

  Subsequently, the operation mode of the heat pump cycle 30 is determined based on the target outlet temperature TAO and the operation mode switch on the operation panel (S40), and the control state of the cycle component device is determined according to the determined operation mode. .

  For example, when the operation mode is determined to be the cooling mode, the closed state in which the passage opening / closing valve 38 is closed in the refrigerant bypass passage 37, the first electromagnetic valve 32 is in the fully open state, and the second electromagnetic valve 35 is in the throttle state in which the pressure reducing action is exerted. To decide. As for the refrigerant discharge capacity of the compressor 31 (specifically, the frequency of the alternating current supplied to the electric motor of the compressor 31), the evaporator temperature Te detected by the evaporator temperature sensor 54 is the target refrigerant evaporation. The temperature TEO is determined using a feedback control method or the like.

  Thus, in the cooling mode, the refrigerant discharged from the compressor 31 flows in the order of the first electromagnetic valve 32 → the outdoor heat exchanger 33 → the check valve 34 → the second electromagnetic valve 35 → the accumulator 36, and the compressor 31 again. Inhaled.

  Further, when the operation mode is determined to be the normal heating mode, the passage opening / closing valve 38 is opened, the refrigerant bypass passage 37 is opened, the first solenoid valve 32 is throttled to exert a pressure reducing action, and the second solenoid valve 35 is fully opened. Determine the closed state. The refrigerant discharge capacity of the compressor 31 is determined using a feedback control method or the like so that the condenser temperature TC detected by the heating temperature sensor 55 becomes the target heating temperature TCO.

  As a result, in the heat pump cycle 30, the refrigerant discharged from the compressor 31 flows in the order of the first electromagnetic valve 32 → the outdoor heat exchanger 33 → the refrigerant bypass passage 37 → the accumulator 36 and is sucked into the compressor 31 again.

  Further, when the operation mode is determined to be the dehumidifying / heating mode, the passage opening / closing valve 38 is determined to be closed, and the first and second electromagnetic valves 32, 35 are determined to be in the throttle state. The refrigerant discharge capacity of the compressor 31 is determined using a feedback control method or the like so that the condenser temperature TC detected by the heating temperature sensor 55 becomes the target heating temperature TCO.

  Thereby, at the time of dehumidification heating mode, the refrigerant | coolant discharged from the compressor 31 is the 1st solenoid valve 32-> outdoor heat exchanger 33-> check valve 34-> 2nd solenoid valve 35-> accumulator 36 similarly to the time of cooling mode. In this order, and is sucked into the compressor 31 again.

  Then, based on the target blowing temperature TAO, the air volume of the air blower 13 is determined with reference to the control map previously memorize | stored in memory (S50). In this control map, for example, the maximum air volume is obtained in the extremely low temperature range and the very high temperature range of the target blowing temperature TAO, and the air flow decreases as it goes from the extremely low temperature range to the intermediate temperature range, and from the extremely high temperature range to the intermediate temperature range. The relationship between the air flow rate of the blower 13 and the target blowing temperature TAO is defined so that the air flow rate decreases as it goes.

  Subsequently, the air outlet mode is determined based on the target air temperature TAO (S60). That is, based on the target blowing temperature TAO, the opening / closing states of the openings 11a to 11c by the defroster door 20a, the face door 20b, and the foot door 20c are determined. The air outlet mode is determined so that, for example, the face mode → bilevel mode → foot mode is changed from a low temperature to a high target air temperature TAO.

  Subsequently, the inlet mode is determined (S70). That is, the open / closed state of the outside air introduction port 121 and the inside air introduction port 122 by the inside / outside air switching door 123 is determined. The determination of the suction port mode is, for example, basically determined as the outside air mode, and is determined as the inside air mode when the temperature difference between the inside air and the outside air is large and the ventilation loss due to the introduction of the outside air becomes large. Further, when the ventilation loss due to the introduction of the outside air is large and fogging of the window glass of the passenger compartment is predicted, the inside / outside air mode is determined.

  Then, the opening degree of the 1st, 2nd air mix doors 17 and 18 is determined (S80), and a control signal is output to various apparatuses so that the control state determined in each step can be obtained (S90). Each step excluding the initialization process is periodically executed.

  Here, the determination processing of the opening degree of the first and second air mix doors 17 and 18 of the present embodiment will be described with reference to the flowchart of FIG.

  As shown in FIG. 3, first, it is determined whether or not the inside / outside air two-layer mode is set (S81). Specifically, it is determined whether or not the blowing mode is determined to be either the foot differential mode or the bi-level mode in step S60, and whether or not the suction port mode is determined to be the inside / outside air mode in step S70.

As a result, when it is determined that it is not the inside / outside air two-layer mode (S81: NO), the opening degree SW of the first and second air mix doors 17 and 18 is expressed by the following formula F2 based on each sensor value. Determined by
SW = [(TAO−Te) / (TC−Te)] × 100 (%) (F2)
However, Te in Formula F2 indicates the evaporator temperature detected by the evaporator temperature sensor 54, and TC indicates the condenser temperature detected by the heating temperature sensor 55.

  SW = 0 (%) is the maximum cooling position (MAXCOOL) of the air mix doors 17 and 18, the inlet side of the first and second bypass passages 161 and 162 is fully opened, and the indoor condenser 15 side is Fully closed. SW = 100 (%) is the maximum heating position (MAXHOT) of the air mix doors 17 and 18, the inlet side of the first and second bypass passages 161 and 162 is fully closed, and the indoor condenser 15 side Is fully open.

  When it is determined in step S81 that the internal / external air two-layer mode is selected (S81: YES), it is further determined whether or not the operation mode of the heat pump cycle 30 is the normal heating mode (S83).

  As a result, when it is determined that the operation mode of the heat pump cycle 30 is not the normal heating mode (S83: NO), the process proceeds to step S82 and the opening SW of each air mix door 17, 18 is determined.

  On the other hand, when it is determined that the operation mode of the heat pump cycle 30 is the normal heating mode (S83: YES), the first and second air immediately after passing through the indoor condenser 15 in the first and second air passages 112 and 113. The temperature of the blown air is estimated (S84).

  In the present embodiment, the temperature of the first blown air immediately after passing through the indoor condenser 15 is estimated from the heating temperature TC of the indoor condenser 15 and the outside air temperature, and the indoor condensation is calculated from the heating temperature TC of the indoor condenser 15 and the inside air temperature. The temperature of the second blown air immediately after passing through the container 15 is estimated.

Specifically, the temperature of the first blown air immediately after passing through the indoor condenser 15 is estimated by the following formula F3, and the temperature of the second blown air immediately after passing through the indoor condenser 15 is estimated by the following formula F4.
TCH_OUT = φc × (TC−TCH_IN) + TCH_IN (F3)
TCL_OUT = φc × (TC−TCL_IN) + TCL_IN (F4)
As shown in FIG. 4, TCH_OUT in Formulas F3 and F4 is the estimated temperature of the first blown air immediately after passing through the indoor condenser 15, and TCH_IN is the inflow of the first blown air that flows into the upper heat exchange section of the indoor condenser 15. The temperature, TCL_OUT indicates the estimated temperature of the second blown air immediately after passing through the indoor condenser 15, and TCL_IN indicates the inflow temperature of the second blown air flowing into the lower heat exchange section of the indoor condenser 15. Note that φc indicates the heat exchange efficiency in the indoor condenser 15 and is calculated based on the air flow rate of the blower 13 and the inflow temperatures TCH_IN and TCL_IN of each blown air flowing into the indoor condenser 15.

  Here, in the inside / outside air two-layer mode, when the normal heating mode is set, the air introduced into the air passages 112 and 113 flows into the indoor condenser 15 as it is without being cooled by the evaporator 14. .

  Therefore, the inflow temperature of the 1st ventilation air which flows into the upper side heat exchange part of the indoor condenser 15 becomes comparable as external temperature, and the inflow of the 2nd ventilation air which flows into the lower side heat exchange part of the indoor condenser 15 The temperature is about the same as the internal temperature.

  Therefore, in the present embodiment, the detected value of the outside air temperature sensor 52 is substituted into the mathematical formula F3 as the inflow temperature TCH_IN of the first blown air flowing into the upper heat exchanging portion of the indoor condenser 15, whereby the indoor condenser 15 An estimated temperature TCH_OUT of the first blown air immediately after passing is calculated.

  Similarly, by substituting the detected value of the inside air temperature sensor 51 into Formula F4 as the inflow temperature TCL_IN of the second blown air flowing into the lower heat exchange part of the indoor condenser 15, the first value immediately after passing through the indoor condenser 15 is obtained. 2 Estimated temperature TCL_OUT of the blown air is calculated. Since the detected value of the evaporator temperature sensor 54 is almost the same value as the inside air temperature, the detected value of the evaporator temperature sensor 54 is the second blown air flowing into the lower heat exchange section of the indoor condenser 15. The inflow temperature TCL_IN may be substituted into the formula F4.

  Subsequently, based on the estimated temperature of the first and second blown air immediately after passing through the indoor condenser 15 estimated in step S84, the air blown upward in the vehicle interior via the defroster opening 11a or the face opening 11b. It is determined whether or not there is an up-and-down temperature deviation state in which the blowing temperature of the air and the blowing temperature of the air blown down to the lower side of the vehicle interior via the foot opening 11c are greatly deviated (S85).

  Specifically, when the difference between the estimated temperatures of the first and second blown air exceeds a predetermined temperature, it is determined that the temperature is in a vertical deviation state, and the estimated temperatures of the first and second blown air are determined. When the difference is equal to or lower than the predetermined temperature, it is determined that there is no vertical temperature deviation state.

  Here, when the difference between the estimated temperatures of the first and second blown air is equal to or lower than the predetermined temperature, the air blowing temperature of the air blown up and down in the vehicle interior is large even if the air mix doors 17 and 18 have the same opening degree. Judgment is difficult.

  On the other hand, when the difference between the estimated temperatures of the first and second blown air exceeds a predetermined temperature, if the air mix doors 17 and 18 have the same opening degree, the air blown up and down in the vehicle interior There is a high possibility that the temperature will deviate greatly.

  For this reason, as a result of the determination process in step S85, when it is determined that the temperature is not in the up / down temperature deviation state (S85: NO), the air mix doors 17 and 18 are determined to have the same opening (for example, the maximum heating position). (S86).

  As a result, the first blown air blown from the first blower fan 131 to the first air passage 112 is heated by the indoor condenser 15 and blown upward in the vehicle interior, as shown by the thick arrow in FIG. Is done. Further, the second blown air blown from the second blower fan 132 to the second air passage 113 is heated by the indoor condenser 15 and blown downward in the vehicle interior, as shown by the thick broken line arrows in FIG. Is done. FIG. 5 shows the flow of the first and second blown air when the air outlet mode is set to the foot differential mode.

  On the other hand, as a result of the determination process in step S85, when it is determined that the temperature is in the up / down temperature divergence state (S85: YES), the blowing temperature of the air blown through the defroster opening 11a or the face opening 11b and the foot opening The opening degree of each air mix door 17 and 18 is determined so that the temperature difference of the blowing temperature of the air which blows off via the part 11c becomes small.

  In the present embodiment, the opening degree of the first air mix door 17 is determined as the maximum heating position (MAXHOT) at which all of the first blown air flows into the indoor condenser 15, and the opening degree of the second air mix door 17 is changed to the first opening degree. The intermediate opening position is determined so that a part of the 2 blown air flows into the indoor condenser 15 and the remaining part flows into the second bypass passage 162.

Specifically, the opening degree SW2 of the second air mix door 17 may be determined to an opening degree that satisfies the following formula F5.
SW2 = [(TAO-TCL_IN) / (TC-TCL_IN)] × 100 (%) (F5)
As a result, the first blown air blown from the first blower fan 131 to the first air passage 112 is heated by the indoor condenser 15 and blown upward in the vehicle interior, as indicated by the thick arrow in FIG. Is done.

  In addition, as shown by the thick broken line arrow in FIG. 6, a part of the second blown air blown from the second blower fan 132 to the second air passage 113 is heated by the indoor condenser 15, so that It blows out downward. That is, on the lower side of the vehicle compartment, the second blown air having a lower temperature is blown out to the lower side of the vehicle cabin than when all of the second blown air is heated by the indoor condenser 15. FIG. 6 shows the flow of first and second blown air when the outlet mode is set to the foot differential mode.

  Therefore, the temperature difference between the blowing temperature of the air blown out through the defroster opening 11a and the blowing temperature of the air blown out through the foot opening 11c becomes small.

  In the vehicle air conditioner 1 of the present embodiment described above, the first and second immediately after passing through the indoor condenser 15 functioning as a heat exchanger for heating when in the normal heating mode in the inside / outside air two-layer mode. The temperature of the blown air is estimated, and the difference between the upper and lower blowing temperatures into the passenger compartment is determined according to the estimated temperature.

  According to this, the difference between the upper and lower outlet temperatures into the vehicle interior in the inside / outside air two-layer mode is achieved with a simple configuration without providing dedicated temperature detection means in both the first and second air passages 112 and 113. Can be determined.

  Furthermore, according to the vehicle air conditioner 1 of the present embodiment, even when the outside air temperature and the inside air temperature greatly deviate from each other, the control of the first and second air mix doors 17 and 18 controls the inside and outside air two-layer mode. The gap between the upper and lower blowing temperatures into the passenger compartment can be suppressed. Therefore, it is possible to ensure the comfort of the occupant in the inside / outside air two-layer mode with a simple configuration.

(Second Embodiment)
In the first embodiment described above, in the temperature estimation process (step S84 in FIG. 3) performed when the opening degree of the first and second air mix doors 17 and 18 is determined, the first air temperature flows into the indoor condenser 15. The example in which the inflow temperature of the blown air is used and the inside air temperature is the inflow temperature of the second blown air flowing into the indoor condenser 15 has been described.

  However, at the time of transition from a function exhibiting state in which the evaporator 14 functions to cool the blown air to a function stopped state in which the function of cooling the blown air is not performed, the detected values of the outside air temperature sensor 52 and the inside air temperature sensor 51 are actually There is a possibility that the temperature will be different from the inflow temperature of the first and second blown air flowing into the indoor condenser 15.

  For example, as shown in FIG. 7, at the time of transition from the dehumidifying heating mode to the normal heating mode (immediately after switching), the detected values of the outside air temperature sensor 52 and the inside air temperature sensor 51 flow into the indoor condenser 15. This is different from the inflow temperature of the second blown air.

  Therefore, in the second embodiment, at the time of transition from the dehumidifying heating mode to the normal heating mode, the temperature change of the evaporator 14 after the mode switching is taken into account, and the first and second blown air flowing into the indoor condenser 15 are taken into account. The inflow temperature is calculated, and the temperatures of the first and second blown air immediately after passing through the indoor condenser 15 are estimated based on the calculated value.

  Hereinafter, the temperature estimation process in the present embodiment will be described with reference to the flowchart of FIG. In the present embodiment, description of the same or equivalent parts as in the first embodiment will be omitted or simplified.

  In the dehumidifying and heating mode, a low-temperature low-pressure refrigerant flows through the evaporator 14, and therefore the difference between the detected value of the evaporator temperature sensor 54 (evaporator temperature Te) and the detected value of the internal air temperature sensor 51 (internal air temperature Tr) is large.

  On the other hand, immediately after switching from the dehumidifying heating mode to the normal heating mode, the difference between the detected value of the evaporator temperature sensor 54 and the detected value of the internal air temperature sensor 51 is large, but gradually increases with time. It approaches and eventually becomes almost the same value.

  Therefore, in the temperature estimation process of the present embodiment, first, in order to determine whether or not the transition from the dehumidifying heating mode to the normal heating mode is in progress, the temperature difference between the evaporator temperature Te and the internal temperature Tr is a predetermined value or more. It is determined whether or not (S841).

  As a result, when it is determined that the temperature difference between the evaporator temperature Te and the internal temperature Tr is smaller than the predetermined value (S841: NO), it is considered that the normal heating mode is completely shifted. For this reason, as in the first embodiment, the outside air temperature is set as the inflow temperature to the first blowing air flowing into the indoor condenser 15, and the inside temperature is set as the inflow temperature to the second blowing air flowing into the indoor condenser 15. The temperatures of the first and second blown air immediately after passing through the condenser 15 are estimated (S842).

  On the other hand, when it is determined that the temperature difference between the evaporator temperature Te and the internal temperature Tr is equal to or greater than the predetermined value (S841: YES), the transition from the dehumidifying heating mode to the normal heating mode is in progress, and the outside temperature and the internal temperature are indoors. This is considered to be different from the inflow temperature of the first and second blown air flowing into the condenser 15.

  For this reason, when it is determined that the temperature difference between the evaporator temperature Te and the internal temperature Tr is equal to or greater than a predetermined value (S841: YES), the temperature increase rate α per unit time in the evaporator 14 when the refrigerant flow is stopped. Is calculated (S843).

  This temperature increase rate α varies depending on the temperature difference between the outside air temperature Tam and the evaporator temperature Te and the amount of air blown to the evaporator 14. For this reason, in this embodiment, the temperature increase rate α is calculated based on the air flow rate of the blower 13 and the temperature difference between the outside air temperature Tam and the evaporator temperature Te.

Specifically, the temperature increase rate α is calculated with reference to the following formulas F6 and F7 and the control maps shown in FIGS.
α = f (temperature difference) × g (air flow) F6
Temperature difference = | Tam−Te |… F7
However, “f (temperature difference)”, as shown in FIG. 9, is a correction term for the rate of temperature increase that increases as the temperature difference between the outside air temperature Tam and the evaporator temperature Te increases. ")" Is a correction term for the rate of temperature increase that increases with an increase in the air flow rate of the blower 13.

  Subsequently, the temperature of the first and second blown air flowing into the indoor condenser 15 is estimated (S844), and the temperature of the first and second blown air after passing through the indoor condenser 15 is estimated (S845). .

  Specifically, since the inflow temperature TCL_IN of the second blown air flowing into the indoor condenser 15 is almost the same value as the detected value of the evaporator temperature sensor 54, it is set as the evaporator temperature Te (TCL_IN = Te). The temperature of the second blown air after passing through the indoor condenser 15 is estimated by the above-described formula F4.

  On the other hand, the inflow temperature TCH_IN of the first blown air flowing into the indoor condenser 15 is a smaller value among the correction value obtained by correcting the evaporator temperature Te_ex at the time of operation mode switching with the temperature increase rate α and the outside air temperature Tam. The temperature of the first blown air after passing through the indoor condenser 15 is estimated by the above-described mathematical formula F3.

The correction value is calculated by the following formula F8.
Correction value = Te_ex + α × t... F8
However, t has shown the elapsed time after switching of the operation mode.

  Other configurations and operations are the same as those in the first embodiment. Therefore, according to the present embodiment, with a simple configuration, it is possible to determine the difference between the upper and lower blowing temperatures into the vehicle interior during the inside / outside air two-layer mode, and to ensure passenger comfort in the inside / outside air two-layer mode. be able to.

  In addition to this, according to the present embodiment, the detected values of the outside air temperature sensor 52 and the inside air temperature sensor 51 flow into the indoor condenser 15 as in the transition from the dehumidifying heating mode to the normal heating mode. Even if it differs from the inflow temperature of the second blown air, the vehicle interior in the inside / outside air two-layer mode is provided without providing dedicated temperature detection means in both the first and second air passages 112 and 113. The difference between the upper and lower outlet temperatures can be determined.

  In the present embodiment, the example in which the evaporator temperature sensor 54 is disposed on the lower heat exchange part (on the second air passage 113 side) of the evaporator 14 has been described. You may arrange | position to a heat exchange part (1st air passage 112 side).

  In this case, in the temperature estimation process, first, it is determined whether or not the temperature difference between the evaporator temperature Te and the outside air temperature Tam is a predetermined value or more. As a result, when the temperature difference between the evaporator temperature Te and the outside air temperature Tam is determined to be a predetermined value or more, the temperature increase rate α per unit time in the evaporator 14 when the refrigerant flow is stopped is calculated, The temperature of the 1st, 2nd ventilation air which flows in into the indoor condenser 15 will be estimated.

  Note that the inflow temperature TCH_IN of the first blown air flowing into the indoor condenser 15 is almost the same value as the detected value of the evaporator temperature sensor 54. Therefore, the evaporator temperature Te (TCH_IN = Te) is used. What is necessary is just to estimate the temperature of the 1st ventilation air after indoor condenser 15 passage by numerical formula F3.

  Further, the inflow temperature TCH_IN of the second blown air flowing into the indoor condenser 15 is a small value among the correction value obtained by correcting the evaporator temperature Te_ex at the time of operation mode switching with the temperature increase rate α and the internal temperature Tr. What is necessary is just to estimate the temperature of the 2nd ventilation air after passing the indoor condenser 15 by above-mentioned numerical formula F4. At this time, the temperature increase rate α changes according to the temperature difference between the internal air temperature Tr and the evaporator temperature Te and the amount of air blown to the evaporator 14. Alternatively, it may be calculated based on the temperature difference between the internal temperature Tr and the evaporator temperature Te.

(Third embodiment)
Next, a third embodiment will be described. In the present embodiment, an example of determining the difference between the upper and lower outlet temperatures into the passenger compartment when the cooling mode is set in the inside / outside air two-layer mode in the determination processing of the opening degrees of the air mix doors 17 and 18 will be described. . In the present embodiment, description of the same or equivalent parts as in the first embodiment will be omitted or simplified.

  The opening determination process of the first and second air mix doors 17 and 18 of the present embodiment will be described with reference to the flowchart of FIG.

  As shown in FIG. 11, when it is determined in step S81 that the inside / outside air two-layer mode is selected (S81: YES), it is further determined whether or not the operation mode of the heat pump cycle 30 is the cooling mode (S88). ).

  As a result, when it is determined that the operation mode of the heat pump cycle 30 is not the cooling mode (S88: NO), the process proceeds to step S82, and the opening SW of each air mix door 17, 18 is determined.

  On the other hand, when it is determined that the operation mode of the heat pump cycle 30 is the cooling mode (S88: YES), the first and second blown air immediately after passing through the evaporator 14 in the first and second air passages 112 and 113. Is estimated (S89).

  In the present embodiment, the temperature of the first blown air immediately after passing through the evaporator is estimated from the evaporator temperature Te of the evaporator 14 and the outside air temperature Tam, and the evaporator is obtained from the evaporator temperature Te of the evaporator 14 and the inside air temperature Tr. The temperature of the 2nd ventilation air just after 14 passage is estimated.

Specifically, the temperature of the first blown air immediately after passing through the evaporator 14 is estimated by the following formula F9, and the temperature of the second blown air just after passing through the evaporator 14 is estimated by the following formula F10.
TeH_OUT = φe × (Te−TeH_IN) + TeH_IN (F9)
TeL_OUT = φe × (Te−TeL_IN) + TeL_IN (F10)
12, TeH_OUT in Formulas F9 and F10 is the estimated temperature of the first blown air immediately after passing through the evaporator 14, TeH_IN is the inflow temperature of the first blown air flowing into the upper heat exchange section of the evaporator 14, TeL_OUT indicates the estimated temperature of the second blown air immediately after passing through the evaporator 14, and TeL_IN indicates the inflow temperature of the second blown air that flows into the lower heat exchange section of the evaporator 14. Note that φe indicates the heat exchange efficiency in the evaporator 14, and is calculated based on the amount of air blown by the blower 13 and the inflow temperatures TeH_IN and TeL_IN of each blown air flowing into the evaporator 14.

  Here, in the case of the cooling mode in the inside / outside air two-layer mode, the inflow temperature of the first blown air flowing into the evaporator 14 is approximately the same as the outside air temperature, and the inflow of the second blown air flowing into the evaporator 14 The temperature is about the same as the internal temperature.

  Therefore, in the present embodiment, the detected value of the outside air temperature sensor 52 is substituted into Formula F9 as the inflow temperature TeH_IN of the first blown air flowing into the evaporator 14, so that the first blown air immediately after passing through the evaporator 14 is substituted. Estimated temperature TeH_OUT is calculated.

  Similarly, by substituting the detected value of the inside air temperature sensor 51 into Formula F10 as the inflow temperature TeL_IN of the second blowing air flowing into the evaporator 14, the estimated temperature TeL_OUT of the second blowing air immediately after passing through the evaporator 14 is obtained. calculate. Since the detected value of the evaporator temperature sensor 54 is almost the same as the temperature of the second blown air immediately after passing through the evaporator 14, the detected value of the evaporator temperature sensor 54 is used as the second blower immediately after passing through the evaporator 14. The estimated temperature TeL_OUT of air may be used.

  Subsequently, based on the estimated temperatures of the first and second blown air immediately after passing through the evaporator 14 estimated in step S89, it is determined whether or not there is a vertical temperature deviation state (S90). Specifically, when the difference between the estimated temperatures of the first and second blown air exceeds a predetermined temperature, it is determined that there is a vertical temperature deviation state. It is determined that it is not in a state.

  As a result of the determination process in step S90, when it is determined that the temperature is not in the up / down temperature divergence state (S90: NO), each air mix door 17, 18 is determined to have the same opening (for example, the maximum cooling position) (S91). ).

  As a result, the first blown air blown from the first blower fan 131 to the first air passage 112 is cooled by the evaporator 14 and blown upward in the vehicle interior, as indicated by the thick arrow in FIG. The Further, the second blown air blown from the second blower fan 132 to the second air passage 113 is cooled by the evaporator 14 and blown out downward in the vehicle interior as shown by the thick broken line arrows in FIG. The In addition, in FIG. 13, the flow of the 1st, 2nd ventilation air when the blower outlet mode is set to bilevel mode is shown.

  On the other hand, as a result of the determination process in step S90, when it is determined that the temperature is in the up / down temperature divergence state (S90: YES), the blowing temperature of the air blown through the defroster opening 11a or the face opening 11b and the foot opening The opening degree of each air mix door 17 and 18 is determined so that the temperature difference of the blowing temperature of the air which blows off via the part 11c becomes small.

  In the present embodiment, the opening degree of the first air mix door 17 is determined as the maximum cooling position (MAXCOOL) at which all of the first blown air flows into the first bypass passage 161, and the opening degree of the second air mix door 17 is determined. The intermediate opening position is determined so that a part of the second blown air flows into the indoor condenser 15 and the remaining part flows into the second bypass passage 162.

Specifically, the opening degree SW2 of the second air mix door 17 may be determined to an opening degree that satisfies the following formula F11.
SW2 = [(TAO−TeL_IN) / (TC−TeL_IN)] × 100 (%) (F11)
As a result, the first blown air blown from the first blower fan 131 to the first air passage 112 is sent from the air cooled by the evaporator 14 in the indoor condenser 15 as indicated by the thick arrow in FIG. It is blown out upward in the passenger compartment without being heated.

  Further, the second blown air blown from the second blower fan 132 to the second air passage 113 is a part of the air cooled by the evaporator 14 as indicated by the thick broken line arrow in FIG. 15 is heated and blown out to the lower side of the passenger compartment. That is, on the lower side of the vehicle interior, the second blown air having a higher temperature is blown out to the lower side of the vehicle interior than when the second air is not heated by the indoor condenser 15 at all.

  Therefore, the temperature difference between the blowing temperature of the air blown through the defroster opening 11a or the face opening 11b and the blowing temperature of the air blown through the foot opening 11c becomes small.

  In the vehicle air conditioner 1 of the present embodiment described above, the first and second blown air immediately after passing through the evaporator 14 functioning as a cooling heat exchanger when in the cooling mode in the inside / outside air two-layer mode. The temperature is estimated, and the difference between the upper and lower blowing temperatures into the passenger compartment is determined according to the estimated temperature.

  According to this, the difference between the upper and lower outlet temperatures into the vehicle interior in the inside / outside air two-layer mode is achieved with a simple configuration without providing dedicated temperature detection means in both the first and second air passages 112 and 113. Can be determined.

  Furthermore, according to the vehicle air conditioner 1 of the present embodiment, even when the outside air temperature and the inside air temperature greatly deviate from each other, the control of the first and second air mix doors 17 and 18 controls the inside and outside air two-layer mode. A passenger's comfort can be secured by suppressing the difference between the upper and lower outlet temperatures into the passenger compartment.

(Fourth embodiment)
Next, a fourth embodiment will be described. In the present embodiment, an example will be described in which the blower outlet mode is changed when it is determined that the upper and lower temperatures are in a state of difference in the opening degree determination process of the air mix doors 17 and 18. In the present embodiment, description of the same or equivalent parts as in the first to third embodiments will be omitted or simplified.

  In the present embodiment, when it is determined in the determination process of step S85 of FIG. 3 or step S90 of FIG. ) And the lower side opening (foot opening 11c), the mode is determined to blow out air from one of the openings. Further, the open / close door 111a is set to a position where the communication hole provided in the partition plate 111 is opened.

  For example, when it is determined in the determination process of step S85 of FIG. 3 that the temperature difference is in the vertical direction, as shown in FIG. 15, the defroster opening 11a and the face opening 11b are fully closed and the foot opening 11c is opened. Thus, the foot mode for blowing air from the foot outlet 19c is determined. Furthermore, the opening / closing door 111a is set to a position where the communication hole provided in the partition plate 111 is opened. In addition, about the opening degree of each air mix door 17 and 18, similarly to the process of step S82, it determines with above-mentioned numerical formula F2 based on each sensor value.

  As a result, the first blown air blown from the first blower fan 131 to the first air passage 112 is heated by the indoor condenser 15 and blown downward in the vehicle interior, as shown by the thick arrow in FIG. Is done. Similarly, the second blown air blown from the second blower fan 132 to the second air passage 113 is heated by the indoor condenser 15 and moved downward in the vehicle interior as shown by the thick broken line arrows in FIG. Blown out.

  Other configurations and operations are the same as those in the first embodiment. Therefore, according to the present embodiment, it is possible to determine the difference between the upper and lower outlet temperatures into the vehicle compartment in the inside / outside air two-layer mode with a simple configuration.

  Further, according to the present embodiment, in the inside / outside air two-layer mode, the air outlet mode is changed from one of the upper side opening and the lower side opening when it is determined that the upper and lower temperature divergence state occurs. It is set as the structure determined to the mode which blows off air. According to this, air having different temperature zones is not blown out toward the top and bottom of the passenger compartment, so that it is possible to appropriately ensure the comfort of the passenger.

(Fifth embodiment)
Next, a fifth embodiment will be described. In the present embodiment, an example will be described in which the suction port mode is changed when it is determined that the upper and lower temperature is in a state of deviation in the opening determination process of the air mix doors 17 and 18. In the present embodiment, description of the same or equivalent parts as in the first to third embodiments will be omitted or simplified.

  In the present embodiment, when it is determined in the determination process of step S85 of FIG. 3 or step S90 of FIG. 11 that the temperature difference is in the vertical direction, the suction port mode is changed to a mode other than the inside / outside air mode (outside air mode and inside air mode). decide.

  For example, when it is determined in the determination process in step S85 of FIG. 3 that the temperature difference is in the vertical direction, as shown in FIG. 16, the suction port mode is changed to the outside air mode in which the inside / outside air switching door 123 closes the inside air introduction port 122. To decide. In addition, about the opening degree of each air mix door 17 and 18, similarly to the process of step S82, it determines with above-mentioned numerical formula F2 based on each sensor value.

  As a result, as shown by the thick arrows in FIG. 16, outside air is introduced to the suction side of the first and second blower fans 131 and 132, and the blown air blown from the blower fans 131 and 132 is converted into the indoor condenser 15. And is blown out upward and downward in the vehicle compartment.

  Other configurations and operations are the same as those in the first embodiment. Therefore, according to the present embodiment, it is possible to determine the difference between the upper and lower outlet temperatures into the vehicle compartment in the inside / outside air two-layer mode with a simple configuration.

  In addition, according to the present embodiment, in the inside / outside air two-layer mode, when it is determined that the upper and lower temperature divergence state, the suction port mode is determined as a mode other than the inside / outside air mode (outside air mode and inside air mode). It is said. According to this, air having different temperature zones is not blown out toward the top and bottom of the passenger compartment, so that it is possible to appropriately ensure the comfort of the passenger.

(Other embodiments)
The embodiment of the present invention has been described above, but the present invention is not limited to this, and elements constituting the embodiment can be appropriately changed or possible without departing from the scope described in each claim. The embodiments can be appropriately combined within a range. For example, it can be changed as follows.

  (1) In each of the above-described embodiments, the example has been described in which the difference between the upper and lower outlet temperatures into the passenger compartment is determined when either the heating mode or the cooling mode is set in the inside / outside air two-layer mode. Instead, for example, when the dehumidifying and heating mode is set in the inside / outside air two-layer mode, the difference between the upper and lower blowing temperatures into the vehicle compartment may be determined.

  In this case, first, the temperatures TeH_OUT and TeL_OUT of each blown air immediately after passing through the evaporator 14 are estimated by the formulas F9 and F10. Thereafter, the temperatures TeH_OUT and TeL_OUT of each blown air immediately after passing through the evaporator 14 are substituted into the mathematical expressions F3 and F4 as the temperatures TCH_IN and TCL_IN of each blown air flowing into the indoor condenser 15, so that immediately after passing through the indoor condenser 15. The temperature TCH_OUT and TCL_OUT of each of the blast air may be estimated, and it may be determined whether or not there is a vertical temperature deviation state based on the estimated values TCH_OUT and TCL_OUT. In this determination, when it is determined that there is a vertical temperature deviation state, the opening degree of the first air mix door 17 is determined as the maximum heating position (MAXHOT) and the second air mix door 17 is opened as in the first embodiment. The degree SW2 may be determined using Formula F5.

  (2) In each of the above-described embodiments, the example in which the heat exchanger for heating is configured by the indoor condenser 15 of the heat pump cycle 30 has been described, but the present invention is not limited to this. For example, the heat exchanger for heating may be composed of a heater core that exchanges heat between the high-temperature engine coolant and the blown air that has passed through the evaporator 14, or an electric heater that generates heat when energized.

  (3) In each of the above-described embodiments, the example in which the heat exchanger for cooling is configured by the evaporator 14 of the heat pump cycle 30 has been described, but the present invention is not limited to this. For example, the cooling heat exchanger may be a heat exchanger that incorporates an air cooling component such as a Peltier element.

  (4) In each of the above-described embodiments, the estimated temperature of the first and second blown air after passing through at least one of the heat exchangers of the evaporator 14 and the indoor condenser 15 is set to the air mix doors 17 and 18. Although the example used for opening degree control was demonstrated, it is not restricted to this, For example, the estimated temperature of the 1st, 2nd ventilation air after passing a heat exchanger is used as the component (for example, compressor 31 and 1st, etc.) of heat pump cycle 30 , And may be used for controlling the second electromagnetic valves 32 and 35).

  (5) In each of the above-described embodiments, the elements constituting the embodiment are not essential elements unless explicitly stated as essential or clearly considered essential in principle. Needless to say. In addition, even when details of elements constituting the embodiment (for example, quantity, numerical value, position, shape) are mentioned, it is clearly indispensable when clearly indicated as essential or in principle. It is not limited to that except where it is conceivable.

11 casing 112 first air passage 113 second air passage 11a defroster opening (upper side opening)
11b Face opening (upper side opening)
11c Foot opening (lower opening)
131 1st ventilation fan 132 2nd ventilation fan 14 Evaporator (heat exchanger for cooling)
15 Indoor condenser (heat exchanger for heating)
50a Temperature estimation means 50b Vertical temperature deviation determination means

Claims (7)

First and second blower fans (131, 132) for blowing air toward the passenger compartment;
A first air passage (112) through which the first blown air blown from the first blower fan (131) flows, and a second air passage through which the second blown air blown from the second blower fan (132) flows. (113), upper openings (11a, 11b) for guiding air to the upper side of the passenger compartment, and lower openings (11c) for guiding air to the lower side of the passenger compartment are formed. A casing (11);
A cooling heat exchanger (14) disposed in the casing for cooling the first and second blown air;
A heating heat exchanger (15) that is disposed on the downstream side of the air flow of the cooling heat exchanger in the casing and heats the first and second blown air;
Inside / outside air two-layer mode in which outside air from the passenger compartment introduced into the first air passage is blown out through the upper opening, and air in the passenger compartment introduced into the second air passage is blown out through the lower opening. Sometimes, the temperature estimation means (50a) for estimating the temperature of each of the first and second blown air immediately after passing through at least one of the cooling heat exchanger and the heating heat exchanger,
Based on the temperature of the first and second blown air estimated by the temperature estimating means, the blowing temperature of the air blown through the upper side opening and the blowing of air blown through the lower side opening An upper and lower temperature deviation determining means (50b) for determining whether or not the temperature is in a state of an upper and lower temperature deviation that greatly deviates;
Cooling temperature detection means (54) disposed in one of the first air passage and the second air passage and detecting the temperature of the cooling heat exchanger,
The temperature estimating means includes
Stopping the function that the cooling heat exchanger does not exhibit the function of cooling the first and second blown air from the function exhibiting state where the cooling heat exchanger exhibits the function of cooling the first and second blown air When transitioning to a state,
Estimating the temperature of the blown air immediately after passing through the heating heat exchanger in the one air passage from the temperature of the heating heat exchanger and the detected value of the cooling temperature detecting means,
From the correction value obtained by correcting the temperature of the heat exchanger for heating and the detection value of the cooling temperature detecting means by the rate of temperature increase of the cooling heat exchanger at the time of transition from the function exhibiting state to the function stop state, A vehicle air conditioner that estimates the temperature of blown air immediately after passing through the heating heat exchanger in the other air passage . First and second blower fans (131, 132) for blowing air toward the passenger compartment;
A first air passage (112) through which the first blown air blown from the first blower fan (131) flows, and a second air passage through which the second blown air blown from the second blower fan (132) flows. (113), upper openings (11a, 11b) for guiding air to the upper side of the passenger compartment, and lower openings (11c) for guiding air to the lower side of the passenger compartment are formed. A casing (11);
A cooling heat exchanger (14) disposed in the casing for cooling the first and second blown air;
A heating heat exchanger (15) that is disposed on the downstream side of the air flow of the cooling heat exchanger in the casing and heats the first and second blown air;
Inside / outside air two-layer mode in which outside air from the passenger compartment introduced into the first air passage is blown out through the upper opening, and air in the passenger compartment introduced into the second air passage is blown out through the lower opening. Sometimes, the temperature estimation means (50a) for estimating the temperature of each of the first and second blown air immediately after passing through at least one of the cooling heat exchanger and the heating heat exchanger,
Based on the temperature of the first and second blown air estimated by the temperature estimating means, the blowing temperature of the air blown through the upper side opening and the blowing of air blown through the lower side opening An upper and lower temperature deviation determining means (50b) for determining whether or not the temperature is in a state of an upper and lower temperature deviation that greatly deviates;
A first air mix that is disposed in the first air passage and that changes an air volume ratio of the first blown air that flows to the heat exchanger for heating and the first blown air that flows around the heat exchanger for heating. A door (17);
A second air mix that is arranged in the second air passage and changes a flow rate ratio of the second blown air that flows to the heat exchanger for heating and the second blown air that flows around the heat exchanger for heating. A door (18);
Door control means (50c) for controlling the operation of the first and second air mix doors,
The door control means includes
When the heating heat exchanger exhibits a function of heating the first and second blown air, and the cooling heat exchanger is in a heating state in which the function of cooling the first and second blown air is not exhibited. In addition, when the vertical temperature deviation determination means determines that the vertical temperature deviation state,
While controlling the operation of the first air mix door so that all of the first blown air flows into the heat exchanger for heating,
The operation of the second air mix door is controlled such that a part of the second blown air flows into the heating heat exchanger and the remainder flows around the heating heat exchanger. A vehicle air conditioner. First and second blower fans (131, 132) for blowing air toward the passenger compartment;
A first air passage (112) through which the first blown air blown from the first blower fan (131) flows, and a second air passage through which the second blown air blown from the second blower fan (132) flows. (113), upper openings (11a, 11b) for guiding air to the upper side of the passenger compartment, and lower openings (11c) for guiding air to the lower side of the passenger compartment are formed. A casing (11);
A cooling heat exchanger (14) disposed in the casing for cooling the first and second blown air;
A heating heat exchanger (15) that is disposed on the downstream side of the air flow of the cooling heat exchanger in the casing and heats the first and second blown air;
Inside / outside air two-layer mode in which outside air from the passenger compartment introduced into the first air passage is blown out through the upper opening, and air in the passenger compartment introduced into the second air passage is blown out through the lower opening. Sometimes, the temperature estimation means (50a) for estimating the temperature of each of the first and second blown air immediately after passing through at least one of the cooling heat exchanger and the heating heat exchanger,
Based on the temperature of the first and second blown air estimated by the temperature estimating means, the blowing temperature of the air blown through the upper side opening and the blowing of air blown through the lower side opening An upper and lower temperature deviation determining means (50b) for determining whether or not the temperature is in a state of an upper and lower temperature deviation that greatly deviates;
A first air mix that is disposed in the first air passage and that changes an air volume ratio of the first blown air that flows to the heat exchanger for heating and the first blown air that flows around the heat exchanger for heating. A door (17);
A second air mix that is arranged in the second air passage and changes a flow rate ratio of the second blown air that flows to the heat exchanger for heating and the second blown air that flows around the heat exchanger for heating. A door (18);
Door control means (50c) for controlling the operation of the first and second air mix doors,
The door control means includes
When the cooling heat exchanger exhibits a function of cooling the first and second blown air, and the heating heat exchanger enters a cooling state in which the function of heating the first and second blown air is not exhibited. In addition, when the vertical temperature deviation determination means determines that the vertical temperature deviation state,
While controlling the operation of the first air mix door so that all of the first blown air flows around the heat exchanger for heating,
The operation of the second air mix door is controlled such that a part of the second blown air flows into the heating heat exchanger and the remainder flows around the heating heat exchanger. A vehicle air conditioner. The door control means includes
When the heating heat exchanger exhibits a function of heating the first and second blown air, and the cooling heat exchanger is in a heating state in which the function of cooling the first and second blown air is not exhibited. In addition, when the vertical temperature deviation determination means determines that the vertical temperature deviation state,
While controlling the operation of the first air mix door so that all of the first blown air flows into the heat exchanger for heating,
The operation of the second air mix door is controlled such that a part of the second blown air flows into the heating heat exchanger and the remainder flows around the heating heat exchanger. The vehicle air conditioner according to claim 1 or 3 . The door control means includes
When the cooling heat exchanger exhibits a function of cooling the first and second blown air, and the heating heat exchanger enters a cooling state in which the function of heating the first and second blown air is not exhibited. In addition, when the vertical temperature deviation determination means determines that the vertical temperature deviation state,
While controlling the operation of the first air mix door so that all of the first blown air flows around the heat exchanger for heating,
The operation of the second air mix door is controlled such that a part of the second blown air flows into the heating heat exchanger and the remainder flows around the heating heat exchanger. The vehicle air conditioner according to claim 1 . The temperature estimating means includes
The heating heat exchanger exhibits a function of heating the first and second blown air, and the cooling heat exchanger is in a heating state in which the function of cooling the first and second blown air is not exhibited. ,
Estimating the temperature of the first blown air immediately after passing through the heating heat exchanger from the temperature of the heating heat exchanger and the temperature of the outside air of the passenger compartment,
Any one of claims 1 to 5, characterized in that estimating the second temperature of air blown immediately after the heating heat exchanger passes the temperature of the temperature and the vehicle interior air in the heating heat exchanger The vehicle air conditioner described in 1. The temperature estimating means includes
The cooling heat exchanger exhibits a function of cooling the first and second blown air, and the heating heat exchanger is in a cooling state in which the function of heating the first and second blown air is not exhibited. ,
Estimating the temperature of the first blown air immediately after passing through the cooling heat exchanger from the temperature of the cooling heat exchanger and the temperature of the outside air of the passenger compartment,
Any one of claims 1 to 6, characterized in that to estimate the temperature of the second blowing air immediately after the cooling heat exchanger passes the temperature of the temperature and the vehicle interior air in the cooling heat exchanger The vehicle air conditioner described in 1.

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