JP2006306146A - Heat pump type air-conditioner for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat pump type air-conditioner for a vehicle unlikely to have blur on the windshield glass when changing-over is made from the cooling or the dehumidifying operation into the heating operation and capable of shortening the waiting time after the changing-over till blowing-out of a hot wind. <P>SOLUTION: The heat pump type air-conditioner for the vehicle is equipped with a compressor 10, an intra-cabin heat exchanger 16, a decompressor 20, an extra-cabin heat exchanger 23, a four-way selector valve 13, an air exhaust duct 32 formed near the intra-cabin heat exchanger, an air exhaust damper 40 to open and close a passage 41 leading from the intra-cabin heat exchanger to the blowout hole in a casing, and a judging means to judge whether the condensate attached to the intra-cabin heat exchanger has evaporated at the time of changing over from the cooling into the heating operation. While judgement by the judging means is such that the condensate of the intra-cabin heat exchanger is not evaporated, the passage is closed by the air exhaust damper and moistened air is exhausted therefrom, and if it is judged otherwise, the passage is opened by the air exhaust damper and dry air is blown off the blowout hole into the cabin. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a heat pump type vehicle air conditioner, and more particularly to a device that prevents fogging of a windshield when switching from cooling operation to heating operation.

  In an engine-driven vehicle driven by an engine, when the engine is cooled with cooling water, the cooling water is warmed by the heat of the engine. Therefore, the heat of this cooling water (warm water) can be used as a heat source for heating in winter. In addition, a refrigeration cycle is used during cooling. However, when engine cooling water cannot be used as a heat source, or in a so-called electric vehicle driven by a battery and a motor, the refrigeration cycle is reversibly operated by a heat pump to heat the passenger compartment.

  A heat pump vehicle air conditioner includes a compressor that compresses a refrigerant, an indoor heat exchanger that exchanges heat between the refrigerant that is housed in a casing having a blower outlet and passes through the casing, and the air that flows in the casing. A decompressor that decompresses and expands the refrigerant, an outdoor heat exchanger that exchanges heat between the refrigerant that passes through the refrigerant and outside air, and a four-way switching valve that switches a flow direction of the refrigerant during cooling operation and heating operation. I have.

  In a heat pump type vehicle air conditioner, during cooling operation, an indoor heat exchanger is used as an evaporator (evaporator) to remove heat of vaporization from the air in the casing, and an outdoor heat exchanger is used as a condenser (condenser). . On the other hand, during heating operation, the indoor heat exchanger is used as a condenser to release condensed heat to the air in the casing, and the outdoor heat exchanger is used as an evaporator.

  By the way, at the turn of the season or when shifting from lowland travel to highland travel, it may be necessary to switch from cooling operation to heating operation. In this case, the indoor heat exchanger that functioned as an evaporator during the cooling operation functions as a condenser during the heating operation. As a result, the condensed water (condensate) adhering to the outer surface of the indoor heat exchanger during the cooling operation is warmed by the heat of the indoor heat exchanger due to switching to the heating operation, and rapidly evaporates. appear. When the humid air containing water vapor is blown out from the casing outlet into the passenger compartment, the windshield or the like may be fogged, which may hinder the driver's view. In particular, the windshield is more fogged as the passenger compartment is narrower, the outside air temperature is lower, and the humidity of the air in the passenger compartment is higher.

  In addition, since the indoor heat exchanger functions as an evaporator (evaporator) in the dehumidifying operation as well as in the cooling operation, there is a possibility that a problem of fogging of the windshield may occur when switching from the dehumidifying operation to the heating operation.

  In order to cope with the fogging of the windshield when the cooling operation is switched to the heating operation, the conventional automobile air conditioner (see Patent Document 1) is close to the portion of the casing in which the indoor heat exchanger is accommodated. An air discharge duct is formed to discharge moist air containing water vapor. Moreover, the air discharge damper which opens and closes the channel | path between an indoor heat exchanger and a blower outlet is arrange | positioned downstream of the indoor heat exchanger in a casing.

In this automotive air conditioner, when switching from cooling operation or the like to heating operation, the moist air is discharged from the air discharge duct near the indoor heat exchanger, and the passage is closed by the air discharge damper to moist air. Is not allowed to flow into the outlet. Then, after a predetermined time has elapsed, a passage is opened by an air discharge damper, and dry air is blown out from the outlet to the passenger compartment, thereby preventing the windshield from being fogged.
JP-A-4-252723

  However, in the conventional air conditioner described above, it is assumed that the maximum amount of condensed water always adheres (holds water) to the indoor heat exchanger when switching from the cooling operation or the like to the heating operation. Under this assumption, the air discharge damper is used until the predetermined time required for the maximum amount of condensed water to evaporate and dry, regardless of whether or not the actual amount of condensed water is attached and the amount of attached water (water holding amount). Is closed. Here, the amount of the condensed water varies depending on the driving state of the vehicle, and may be large or small.

  However, in the conventional example, even if the amount of condensed water adhering to the indoor heat exchanger is small, the air discharge damper does not open the passage unless the predetermined time has elapsed. As a result, the conventional air conditioner has poor warm-up performance, and after switching from the cooling operation to the heating operation, it takes a long time until the conditioned air (warm air) blows out from the air outlet into the vehicle interior. ing.

  The present invention has been made in view of the above problems, and when switching from cooling operation or dehumidifying operation to heating operation, the windshield is less likely to be fogged, and the heat pump type that can shorten the waiting time until warm air blows out after switching An object is to provide a vehicle air conditioner.

  The present inventor determines in real time the evaporation and drying timing of the condensed water, which changes depending on the presence or absence of the condensed water on the indoor heat exchanger and the amount of adhesion, by the determination means, and when the evaporation of the condensed water is considered to have ended The present invention was completed with the idea of opening the air discharge damper.

According to a first aspect of the present invention, there is provided a heat pump type vehicle air conditioner comprising: a compressor that compresses a refrigerant; a refrigerant that is housed in a casing having an outlet and passes through the interior; and air that flows through the casing. An indoor heat exchanger for exchanging heat between them, a decompressor for decompressing and expanding the refrigerant,
An outdoor heat exchanger for exchanging heat between the refrigerant passing through the inside and the outside air, a four-way switching valve for switching the flow direction of the refrigerant during cooling operation and heating operation, and the indoor heat exchange of the casing An air discharge duct formed near a cooler, an air discharge damper that opens and closes a passage between the indoor heat exchanger and the outlet of the casing, and when switching from the cooling operation to the heating operation, Determining means for determining whether or not the condensed water adhering to the indoor heat exchanger has evaporated.

  In this heat pump type vehicle air conditioner, while the determination means determines that the condensed water of the indoor heat exchanger has not evaporated, the air discharge damper closes the passage, and the air discharge damper Exhaust moist air. On the other hand, after it is determined that the condensed water has evaporated, the air discharge damper opens the passage and blows dry air from the outlet.

  The heat pump type vehicle air conditioner according to claim 2 includes a control unit having a storage unit that receives the determination result of the determination unit, controls the operation of the air exhaust damper, and stores the operation state of each time. It is characterized by. The heat pump type vehicle air conditioner according to claim 3, wherein the determination unit includes a humidity sensor that detects a humidity of air near the indoor heat exchanger, and the humidity of the air becomes a predetermined value or less. It is characterized by determining evaporation of condensed water.

  The heat pump type vehicle air conditioner according to claim 4, wherein the determination unit includes a first refrigerant temperature sensor that detects a temperature of the refrigerant in the first predetermined place, and a rate of increase in the temperature of the refrigerant changes from small to large. In this case, evaporation of the condensed water is determined. 6. The heat pump type vehicle air conditioner according to claim 5, wherein the determination means includes a first air temperature sensor that detects the temperature of air at a second predetermined location, and the rate of increase in the temperature of the air changes from small to large. In this case, evaporation of the condensed water is determined.

  The heat pump type vehicle air conditioner according to claim 6, wherein the determination means includes a first refrigerant temperature sensor that detects a temperature of the refrigerant in the first predetermined place and a second refrigerant that detects the temperature of the refrigerant in the third predetermined place. Including a temperature sensor, and determining evaporation of the condensed water when a temperature difference between the temperature of the refrigerant at the first predetermined location and the temperature of the refrigerant at the third predetermined location changes from large to small. To do.

  The heat pump type vehicle air conditioner according to claim 7, wherein the determination means includes a first air temperature sensor that detects a temperature of air at a second predetermined location and a second air that detects a temperature of air at a fourth predetermined location. Including a temperature sensor, and determining the evaporation of the condensed water when a temperature difference between the temperature of the air at the second predetermined location and the temperature of the air at the fourth predetermined location changes from small to large. To do.

  The heat pump type vehicle air conditioner according to claim 8 is a temperature between the temperature of the refrigerant at the first predetermined location and the temperature of the refrigerant at the third predetermined location immediately after switching from the cooling operation to the heating operation. The difference and the temperature difference between the temperature of the air at the second predetermined location and the temperature of the air at the fourth predetermined location are not considered. The heat pump type vehicle air conditioner according to claim 9 is disposed on the downstream side of the indoor heat exchanger in the casing, and overheats the air that has passed through the indoor heat exchanger, and on the upstream side of the heater core. It includes an air mix door arranged.

  Next, various aspects of the constituent elements of the heat pump type vehicle air conditioner (hereinafter referred to as “air conditioner” as necessary) described in claims 1 to 9 of the claims will be described. The vehicle air conditioner of the present invention is of a heat pump type and includes a compressor, an indoor heat exchanger, a decompressor, an outdoor heat exchanger, and a four-way switching valve. The refrigerant is circulated in one direction during the cooling operation in the refrigeration cycle, and the refrigerant is circulated in the other direction during the heating operation. Vehicles include both engine-driven vehicles and electric vehicles.

  The casing in which the indoor heat exchanger is accommodated has an air discharge duct for discharging moist air containing water vapor from which condensed water on the outer surface of the indoor heat exchanger has evaporated in the vicinity of the indoor heat exchanger. Moreover, the air drainage damper which opens and closes the channel | path connected to a blower outlet is provided in the vicinity of the indoor heat exchanger, or its downstream. The air discharge damper is temporarily closed when the cooling operation is switched to the heating operation, and then opened. The opening timing of the air discharge damper is determined by the relationship with the evaporation of the condensed water, and the end of the evaporation of the condensed water is determined by the determination means. This is the greatest feature of the present invention.

  On the downstream side of the indoor heat exchanger, a heater core that heats air that has passed through the indoor heat exchanger by using engine cooling water or the like as a heat source, and an air mix door on the upstream side thereof can be included. The opening and closing of the air mix door can be linked to the opening and closing of the air discharge damper. In addition, you may arrange | position the 2nd indoor heat exchanger different from the said indoor heat exchanger instead of a heater core. The heater core and the second indoor heat exchanger further heat the warm air that has passed through the indoor heat exchanger during the heating operation, and heat the cold air that has passed through the indoor heat exchanger during the dehumidifying operation.

  The air conditioner includes a control device that determines an operation state (heating, cooling, or dehumidification) based on signals from an outside air temperature sensor that detects an outside air temperature, an inside air temperature sensor that detects an inside air temperature, and the like. The operating state is determined by the rotational speed of the compressor, the direction of refrigerant circulation by switching the four-way switching valve, and the like. In addition, the control device has a storage unit that stores the operation state of each time, and the storage unit can be composed of, for example, a nonvolatile memory that does not lose the operation state even when the power is turned off. Thereby, switching between heating operation, cooling operation, and dehumidification operation, especially switching from cooling operation or dehumidification operation to heating operation can be reliably recognized.

  Furthermore, the determination result by the determination means for determining the evaporation of the condensed water on the outer surface of the indoor heat exchanger is input to the control device. The determination means includes a humidity sensor, a first refrigerant temperature sensor, an indoor unit air temperature sensor, a second refrigerant temperature sensor, an outside air temperature sensor, and the like. Detection results of these sensors (air humidity, refrigerant or air temperature) ) To control the operation of the air exhaust damper and the like.

  There are three types of determination means. Both types of determination means are common in that it is determined whether the condensed water has evaporated (vaporized) and the outer surface of the indoor heat exchanger has been dried, but what is determined is different.

  The first type determination means determines evaporation of condensed water based on the humidity of the air near the indoor heat exchanger. If the condensed water has not evaporated, the humidity of the air is high, and if it has evaporated, the humidity of the air is low. Therefore, the evaporation of the condensed water can be determined based on the detection value of the humidity sensor. The humidity sensor can be disposed in, for example, an air exhaust duct, and a general-purpose sensor such as an impedance change type humidity sensor or a capacitance change type humidity sensor that detects relative humidity can be used as the humidity sensor.

  When determining the evaporation, for example, while the humidity detected by the humidity sensor is higher than a predetermined value (for example, 5%), it is determined that the condensed water is before evaporation (during evaporation) and the outer surface is wet, and the air is discharged. The passage is closed with a damper and the moist air is discharged from the air discharge duct. On the other hand, if the detected humidity becomes lower than a predetermined value (for example, 5%), it is determined that the condensed water has been evaporated and the outer surface has been dried, and the passage is opened by the air discharge damper.

  Since the second type determination means uses a part of the heat of the indoor heat exchanger as the latent heat of evaporation during the evaporation of the condensed water, the refrigerant in the first predetermined location of the air conditioner (for example, the outlet of the indoor heat exchanger) The temperature sensor is used to determine the evaporation rate of the condensed water by using a temporary decrease in the temperature of the air and the rate of increase in the temperature of the air at the second predetermined location of the air conditioner (for example, downstream of the indoor heat exchanger). That is, the temperature of the refrigerant inside the indoor heat exchanger rises at a substantially constant rate as time passes unless condensed water adheres. On the other hand, if condensed water adheres, the rate of increase in the temperature of the refrigerant becomes smaller during evaporation of condensed water than before and after evaporation due to the influence of the latent heat of evaporation. Therefore, if the rate of temperature rise of the refrigerant is detected by, for example, a first refrigerant temperature sensor (indoor unit refrigerant temperature sensor) disposed in a pipe extending from the outlet of the indoor heat exchanger, the evaporation of condensed water can be known.

  Similarly, the temperature of the air flowing downstream through the indoor heat exchanger rises at a substantially constant rate as time passes unless condensed water adheres, but if condensed water adheres, During the evaporation of the condensed water, the rate of increase in the refrigerant temperature is smaller than before and after the evaporation. If this small increase rate is detected by a first air temperature sensor (indoor unit air temperature sensor) disposed on the downstream side of the indoor heat exchanger in the casing, the evaporation of the condensed water can be determined. As the indoor unit refrigerant temperature sensor and the indoor unit air temperature sensor, general-purpose devices such as a thermistor, a thermocouple, or an IC temperature sensor can be used.

  The third type determination means is configured such that the temperature of the refrigerant or air that changes according to the evaporation of condensed water, such as the temperature of the refrigerant at the first predetermined location or the temperature of the air at the second predetermined location, and the temperature change thereof. The evaporation of the condensed water is determined using the temperature difference between the temperature of the refrigerant at the third predetermined location or the temperature of the air at the fourth predetermined location, which is not affected by the evaporation of the condensed water.

  That is, the temperature of the refrigerant at the third predetermined location (for example, the outlet of the compressor) of the air conditioner rises at a substantially constant rate with the passage of time after the start of the heating operation without being affected by the evaporation of the condensed water. Moreover, it is generally higher than the temperature of the refrigerant at the outlet of the indoor heat exchanger. As a result, the temperature difference between the temperature of the refrigerant discharged from the indoor heat exchanger and the temperature of the refrigerant discharged from the compressor increases during the evaporation of the condensed water and decreases after the evaporation. The change in the temperature difference is used to determine the evaporation of the condensed water.

  In addition, the change in the temperature of the fourth predetermined place (for example, outside air (outside air)) of the air conditioner is determined by the weather condition of the day, and does not change in a short time such as when the heating operation is started and is almost constant. Moreover, this temperature is between the temperature of the air on the downstream side of the indoor heat exchanger before evaporation of the condensed water and the temperature of the air after evaporation. As a result, the temperature difference between the temperature of the air on the downstream side of the indoor heat exchanger and the temperature of the outside air decreases during the evaporation of the condensed water and increases after the evaporation. The change in the temperature difference is used to determine the evaporation of the condensed water.

  According to the heat pump type vehicle air conditioner of the first aspect of the present invention, when the operating state of the air conditioner is switched from the cooling operation to the heating operation, the presence or absence of the adhering condensed water to the indoor heat exchanger and the amount of the adhering amount The length of the evaporation time of the condensed water that changes depending on the time is determined in real time by the determination means. As a result, firstly, the fogging of the windshield is reliably prevented. For example, even when the amount of condensed water attached is large and the time required for evaporation is long, the moist air before evaporation is discharged from the air discharge duct, so that the windshield is prevented from being fogged.

  Secondly, after switching from the cooling operation to the heating operation, it is possible to shorten the time during which the warm air blows out from the air outlet. For example, when the amount of condensed water adhering is small and the time required for evaporation is short, dry air immediately after evaporation is blown out from the outlet to the passenger compartment immediately after the evaporation is completed.

  According to the heat pump type vehicle air conditioner of the second aspect, the control device operates the air discharge damper at the optimum time based on the determination result from the determination means. In addition, since the operation state of each time is stored in the storage unit, switching from the cooling operation to the heating operation can be reliably detected. According to the heat pump type vehicle air conditioner of the third aspect, the evaporation can be determined easily based on the humidity detected by the temperature sensor disposed near the indoor heat exchanger.

  According to the heat pump type vehicle air conditioner of the fourth aspect, since evaporation of the condensed water is determined by a change in the rate of increase in the refrigerant temperature detected by the first refrigerant temperature sensor arranged at the first predetermined location, the determination of evaporation is performed. Become accurate. According to the heat pump type vehicle air conditioner of claim 5, since the evaporation of the condensed water is determined by the change in the rate of increase in the air temperature detected by the first air temperature sensor arranged at the second predetermined location, the determination of evaporation is performed. Become accurate.

  According to the heat pump type vehicle air conditioner of claim 6, the temperature of the refrigerant at the first predetermined location detected by the first refrigerant temperature sensor and the third predetermined location detected by the second refrigerant temperature sensor are detected. Judgment is made based on the temperature difference from the refrigerant temperature. Therefore, it is not necessary to detect the rate of increase in the temperature of the refrigerant at the first predetermined place and the third predetermined place, and the determination of evaporation is facilitated accordingly.

  According to the heat pump type vehicle air conditioner of claim 7, the temperature of the air at the second predetermined location detected by the first air temperature sensor and the fourth predetermined location detected by the second air temperature sensor are detected. Judged by the temperature difference from the air temperature. Therefore, it is not necessary to detect the rate of increase in the temperature of the air at the second predetermined place and the fourth predetermined place, and the determination of evaporation is facilitated accordingly.

  According to the heat pump type vehicle air conditioner of the eighth aspect, since the temperature difference immediately after the switching in which the refrigerant temperature and the air temperature are unstable is not taken into consideration, the determination of evaporation becomes more accurate. According to the heat pump type vehicle air conditioner of the ninth aspect, since the heater core on the downstream side of the indoor heat exchanger is included, rapid heating operation and dehumidifying operation are possible. In addition, the windshield can be prevented from being fogged even when switching from the dehumidifying operation to the heating operation, and the warm-up performance of the heating operation is improved.

  The best mode for carrying out the invention will be described below with reference to the accompanying drawings.

<First Embodiment>
(Constitution)
1, 2, 3, 4, 5, and 6 show a first embodiment. 1, the heat pump type vehicle air conditioner includes a compressor 10, a four-way switching valve 13, an indoor heat exchanger 16, a decompressor 20, an outdoor heat exchanger 23, an accumulator 26, a casing 30, and the like.

  The compressor 10 is a pump means that sucks in a low-temperature and low-pressure gas refrigerant, compresses it, and discharges the high-temperature and high-pressure gas refrigerant. Here, an inverter-controlled electric compressor is used, and its rotation speed is electronically controlled. Controlled by device 75. The four-way switching valve 13 switches between when the high-pressure refrigerant discharged from the compressor 10 and decompressed is circulated to the indoor heat exchanger 16 side and when circulated to the outdoor heat exchanger 23 side. Here, the electromagnetic four-way switching valve 13 controlled by the electronic control device 75 is employed.

  The indoor heat exchanger 16 is accommodated in a casing 30 to be described later, and performs heat exchange between a refrigerant flowing inside the casing 30 and air flowing in the casing 30 (hereinafter referred to as “casing inside air” as necessary). It is. During cooling, it functions as an evaporator (evaporator) that evaporates low-temperature and low-pressure liquid refrigerant and removes heat from the inside air. During heating, a condenser (condenser) that condenses and liquefies high-temperature and high-pressure gas refrigerant and releases heat to the inside air ).

  The decompressor 20 decompresses and expands the refrigerant flowing through the decompressor 20 into a cold / low pressure refrigerant. The throttle opening degree is controlled by the electronic control unit 75, and can be continuously changed from a fully open state in which almost no pressure loss occurs to a predetermined opening degree for decompressing and expanding the refrigerant. The outdoor heat exchanger 23 is a heat exchanger that exchanges heat between the refrigerant flowing inside the outdoor heat exchanger 23 and outdoor air (outside air). During cooling, it functions as a condenser (condenser) that condenses and liquefies high-temperature and high-pressure gas refrigerant and releases heat to the outside air, and during heating, an evaporator (evaporator) that evaporates and vaporizes low-temperature and low-pressure liquid refrigerant to remove heat from the outside air ).

  The accumulator 26 separates the refrigerant into a gas refrigerant and a liquid refrigerant, stores excess refrigerant as the liquid refrigerant, and supplies the gas refrigerant to the suction side of the compressor 10. The compressor 10, the four-way switching valve 13, the indoor heat exchanger 16, the decompressor 20, the outdoor heat exchanger 23, and the accumulator 26 are arranged in this order on the refrigerant circulation pipe 15.

  Next, the casing 30 will be described. The casing 30 forms a passage for conditioned air that blows out into the passenger compartment, and the indoor heat exchanger 16 is disposed in an intermediate portion in the length direction (vertical direction in FIG. 1). An air discharge duct 32 that also serves as a drain outlet branches off from the bottom of the portion where the indoor heat exchanger 16 is disposed, and the other end opens to the outside of the passenger compartment. A heater core 34 that heats the inside air of the casing during the heating operation and the dehumidifying operation is disposed downstream of the indoor heat exchanger 16 in the air flow direction (upward in FIG. 1). The heater core 34 is a heat exchanger that exchanges heat between the air flowing around the heater core 34 and the coolant supplied from the engine or the FC stack 36.

  An air mix door 38 is rotatably disposed on the upstream side of the heater core 34. The air mix door 38 is pivotally supported by the casing 30, and its operation is controlled by an electronic control device 75. Between the closed position where the upstream side of the heater core 34 is closed and retracted from the passage 41 (shown by a solid line) and the open position where the upstream side of the heater core 34 is opened and protruded into the passage 41 (shown by a broken line) Can take a moving angle. Of the air that has passed through the indoor heat exchanger 16 by adjusting the rotation angle, the air volume ratio between the warm air that is heated by passing through the heater core 34 and the cold air that bypasses the heater core 34 and flows through the passage 41 described below. Is adjusted. In this way, the temperature of the conditioned air blown out from the outlet to the passenger compartment is adjusted.

  A passage 41 is formed between the heater core 34 and the wall portion of the casing 30, and the passage 41 is opened and closed by an air discharge damper 40 that is pivotally supported by the casing 30. The air discharge damper 40 is controlled by an electronic control unit 75 and is rotated to a closed position (illustrated by a solid line) for closing the passage 41 or an open position (illustrated by a broken line) for opening the passage 41. It is rotated during the evaporation of the condensed water on the outer surface of the indoor heat exchanger 16 and is rotated after the evaporation of the condensed water. Details will be described later in the column of action.

  A blowing mode switching device (not shown) that selectively opens and closes a plurality of outlets that blow out the conditioned air that has passed through the indoor heat exchanger 16 and the heater core 34 to the passenger compartment is provided in the downstream portion of the casing 30. In addition, an upstream / outside air switching unit 42 that adjusts the amount of indoor air (inside air) and outdoor air (outside air) introduced into the casing 30, or a blower (fan) that blows air inside the casing 30, upstream of the casing 30. ) 44 and a motor 45 are provided.

  Note that the rotation angle of the air mix door 38 and the air discharge damper 40, the blowing mode switching device, the inside / outside air switching unit 42, and the operation of the motor 45 are controlled by the electronic control device 75.

  Next, various sensors will be described. First, as sensors disposed on the refrigerant circulation pipe 15, a discharge refrigerant temperature sensor 52 that detects the temperature of refrigerant discharged from the compressor 10, and a discharge refrigerant pressure sensor that detects the pressure of refrigerant discharged from the compressor 10. 54, an indoor unit refrigerant pressure sensor 56 that detects the pressure of the refrigerant that has flowed out of the indoor heat exchanger 16, an indoor unit refrigerant temperature sensor 58 that detects the temperature of the refrigerant that has flowed out of the indoor heat exchanger 16, and the outdoor heat exchanger 23. There is an outdoor refrigerant temperature sensor 60 that detects the temperature of the refrigerant flowing out of the refrigerant.

  Further, as sensors disposed inside and outside the casing 30, an indoor unit air temperature sensor 62 that detects the temperature of air immediately after passing through the indoor heat exchanger 16, and the humidity of air in the air discharge duct 32 are detected. A humidity sensor 64, a water temperature sensor 66 for detecting the temperature of the cooling water flowing into the heater core 34 from the engine or FC stack 36, an outside air temperature sensor 68 for detecting the outside air temperature, an inside air temperature sensor 70 for detecting the inside air temperature, and a vehicle interior There is a solar radiation sensor 72 that detects the solar radiation that is poured.

  Signals from the various sensors 52, 54, 56, 68, 60, 62, 64, 66, 68, 70 and 72 are input to the electronic control device 75. As described above, the electronic control unit 75 controls the rotation speed of the compressor 10, the switching of the four-way switching valve 13, the rotation of the air mix door 38, the operation of the air discharge damper 40, the inside / outside air switching unit 42, and the like. To do. Moreover, the memory | storage part 77 which memorize | stores the operating state of every time of an air conditioner is incorporated.

(Function)
Next, the operation of the first embodiment will be described in detail with reference to FIGS. 1 to 5. Signals from the various sensors 52, 54, 56, 68, 60, 62, 64, 66, 68, 70 and 72 are read in step S10 of the flowchart of FIG. For example, the target blowing temperature TAO is calculated from information such as the outside air temperature sensor 68 that detects the outside air temperature and the inside air temperature sensor 70 that detects the inside air temperature. Next, it progresses to step S11, and the necessity of heating is judged by whether TAO is higher than a predetermined value, for example.

  If the determination in step S11 is YES, the process proceeds to step S12 to start the heating operation. In the heating operation, the refrigerant is circulated in the refrigerant circulation pipe 15 as shown by arrows in FIGS. 3 (a) and 3 (b). FIG. 3A shows a state during evaporation of condensed water, and FIG. 3B shows a state after evaporation of condensed water. The electronic control unit 75 switches the four-way switching valve 13 so that the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 is directed to the indoor heat exchanger 16 side. The refrigerant dissipates heat to the air in the casing by the indoor heat exchanger 16 and is condensed and liquefied. Thereby, the inside air of the casing is heated by the indoor heat exchanger 16. The rotation of the air mix door 38 and the air discharge damper 40 will be described later.

  The refrigerant condensed in the indoor heat exchanger 16 expands in the decompressor 20 to become a low-temperature and low-pressure mist state, and flows into the outdoor heat exchanger 23. The refrigerant absorbs heat from the outside air in the outdoor heat exchanger 23 and evaporates to become a gas refrigerant. Next, the refrigerant flows into the accumulator 26 through the four-way switching valve 13, and after separating the liquid refrigerant, only the gas refrigerant is sucked into the compressor 10.

  In step S13, it is determined whether the previous operation of the air conditioner is cooling or dehumidifying. This determination is necessary in order to discharge moist air from the air discharge duct 32 when the previous operation is cooling or the like. The previous operation state is stored in the storage unit 77. When the previous operation is cooling or dehumidifying, the process proceeds to step S14 and damper closing control is performed. Incidentally, in the case of cooling, as shown in FIG. 4 described later, the air mix door 38 is closed and the air discharge damper 40 is opened. In the damper closing control, as shown in FIG. 3A, the air mix door 38 is rotated to the closed position indicated by the solid line, and the air discharge damper 40 is rotated to the closed position indicated by the solid line to close the passage 41.

  As a result, moist air containing water vapor cannot flow downstream from the indoor heat exchanger 16 and is discharged from the air drain duct 32 to the outside of the vehicle compartment as indicated by an arrow x in FIG. . The closing of the passage 41 by the air discharge damper 40 and the discharge of the wet air from the air discharge duct 32 are continued until the humidity detection value by the humidity sensor 64 described below becomes below the reference value. By preventing the moist air from being blown into the passenger compartment, the windshield is prevented from fogging. If the determination in step S13 is NO, the previous operation is heating, and there is no problem with fogging of the windshield, so the process returns.

  Then, it progresses to step S15 and it is judged whether the condensed water of the outer surface of the indoor heat exchanger 16 evaporated. This determination is made to determine how long the air mix door 38 and the air discharge damper 40 are to be closed, that is, when to open. The evaporation of the condensed water is determined based on whether or not the detection value Hin of the humidity sensor 64 is equal to or less than a reference value Hbase (for example, 5%). If the detection value Hin is equal to or less than the reference value Hbase, it is determined that the condensed water is evaporated.

  In FIG. 5 showing the evaluation results in the first embodiment, the detection value of the humidity sensor 64 in the process of evaporating attached condensed water is shown by a curve b. The detected value of the humidity sensor 64 when the condensed water is not attached is indicated by a curve c. As can be seen, the humidity remains constant for a while after the start of the heating operation, and is constant, but thereafter decreases at a substantially constant rate. Then, it is determined that the condensed water has evaporated when the detected humidity value becomes 5% close to the level of the curve c. Details will be described later.

  Proceeding to step S16, damper opening control is performed, and as shown in FIG. 3B, the air mix door 38 is rotated to a predetermined intermediate position determined by TAO, and the air discharge damper 40 is rotated to the open position by a broken line. 41 is released. As a result, the normal heating operation is restored, and a part of the casing air heated by the indoor heat exchanger 16 is further heated when passing through the heater core 34, and as shown by the arrow y in FIG. The remainder of the flow around the heater core 38 flows through the passage 41. Both casing internal airs merge on the downstream side of the heater core 38, and then blow out into the vehicle compartment from the air outlet. If the determination in step S15 is NO, the condensed water on the indoor heat exchanger 16 has not evaporated, and the process returns.

  Next, cooling and dehumidification will be described. If the determination in step S11 is NO, the process proceeds to step S17, and the necessity of cooling is determined based on whether the target blowing temperature TAO is low. If it is determined that cooling is necessary, the process proceeds to the cooling operation in step S18. In the cooling operation, the refrigerant is circulated in the refrigerant circulation pipe 15 as indicated by an arrow in FIG. For this purpose, the electronic control unit 75 switches the four-way switching valve 13 so that the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 is directed to the outdoor heat exchanger (condenser) 23. The refrigerant dissipates heat to the outside air in the outdoor heat exchanger 23 to condense and liquefy, expands in the decompressor 20, enters a low-temperature low-pressure mist state, and flows into the indoor heat exchanger (evaporator) 16. The indoor heat exchanger 16 exchanges heat between the refrigerant and the casing inner air, and the refrigerant takes the heat of vaporization from the casing inner air and evaporates. Thus, the inside air of the casing is cooled by the indoor heat exchanger 16.

  At this time, the air mix door 38 is in a closed position indicated by a solid line, and the air discharge damper 40 is in an open position indicated by a broken line and opens the passage 41. Accordingly, as indicated by an arrow z in FIG. 4, the cold air flows through the passage 41 to the outlet. The refrigerant evaporates by heat exchange in the indoor heat exchanger 16, flows into the accumulator 26 through the four-way switching valve 13, is separated into gas refrigerant and liquid refrigerant by the accumulator 26, and only the gas refrigerant is sucked into the compressor 10. The

  If the determination in step S17 is NO, the process proceeds to step S19 to determine the necessity for dehumidification. If it is determined that dehumidification is necessary, the process proceeds to step S20 and a dehumidifying operation is performed. During the dehumidifying operation, the refrigerant is circulated in the same direction as in the cooling operation, the indoor heat exchanger 16 functions as an evaporator to cool the casing inner air, and the heater core 34 heats the casing inner air. For this purpose, the air mix door 38 is rotated to a predetermined intermediate position determined by TAO, and the air discharge door 40 is rotated to a closed position indicated by a solid line. Then, after the moisture in the casing is removed by the indoor heat exchanger 16, the air in the casing is heated by the heater core 34, and the conditioned air whose temperature is adjusted to a temperature between the cold air and the warm air blows out from the outlet. If it is determined in step 19 that dehumidification is unnecessary, the process proceeds to step S21 and the air conditioner is stopped.

  Next, determination of evaporation of condensed water in step S15 will be described with reference to FIG. In FIG. 5, the horizontal axis represents the elapsed time after the start of the heating operation, and the vertical axis represents the amount of condensed water adhering (water retention amount) in the indoor heat exchanger 16 or the value detected by the humidity sensor 64. Curve a indicates the amount of condensed water adhering to the indoor heat exchanger 16 (water retention amount), and the water retention amount was determined by actual measurement. A curve b indicates a detection value by the humidity sensor 64 when condensed water adheres to the indoor heat exchanger 16, and a curve c indicates a detection value by the humidity sensor 64 when no condensed water adheres.

  As can be seen from the curve a, the water retention amount has a high and constant value immediately after the start of the heating operation, but thereafter gradually decreases with the passage of time. The reason why the water retention amount does not decrease immediately after the switching is that the temperature of the condensed water is rising due to the heat of the indoor heat exchanger 16 during this period. Thereafter, as the condensed water evaporates, the water retention amount decreases with time.

  As can be seen from the curve b, the value detected by the humidity sensor 64 is high and constant immediately after the start of the heating operation, but thereafter gradually decreases with the passage of time, and the decreasing tendency is the same as the decreasing tendency of the water retention amount. It is. When there is no condensed water adhering to the indoor heat exchanger 16, the detected value remains low as shown by the curve c. Theoretically, the evaporation of condensed water is completed at time t1 when the curve b intersects the curvature c. However, as can be seen from the curve a, the condensed water is actually evaporated at a time t2 earlier than the time t1, and the water retention amount is zero.

(effect)
According to the first embodiment, the following effects can be obtained. First, it is possible to prevent fogging of the windshield when the air conditioner is switched from the cooling operation or the dehumidifying operation to the heating operation. This is because when the condensed water on the outer surface of the indoor heat exchanger 16 is not evaporated and dried, the air discharge damper 40 closes the passage 41 and discharges moist air from the air discharge duct 32 to the outside of the vehicle. Achieved.

  Second, after the air conditioner is switched from the cooling operation or the dehumidifying operation to the heating operation, the waiting time until the warm air blows out from the outlet of the casing 30 to the vehicle compartment can be shortened. This is achieved by determining the evaporation of the condensed water in the indoor heat exchanger 16 in real time based on the detection value of the humidity sensor 64 and determining the length of time for closing the passage 41 by the air discharge damper 40 according to the determination result. It was done. That is, as can be seen from the curve a in FIG. 5, the curve b reaches the level of 5% humidity slightly higher than the level of the curvature c (humidity 0%) at a time t3 earlier than the time t2. Therefore, if the damper opening control in step S16 is performed at time t3, the waiting time until the warm air blows out becomes shorter than when waiting until time t2 or time t1. The reason why the condensed water is evaporated at a humidity level of 5% is because the response delay of the humidity sensor 64 is taken into consideration.

  Further, a curve a in FIG. 5 shows a process in which a certain amount of water retention evaporates, and a curve b similarly shows a detected humidity value in a process in which a certain amount of water retention evaporates. As described above, the water retention amount may be large or small depending on the operation state. Therefore, for example, when the actual water retention amount is smaller, the value detected by the humidity sensor 64 becomes smaller as indicated by the two-dot difference line d, and the time until the level reaches 5% is a time t4 earlier than the time t3. become. If the damper opening control is performed at time t4, the waiting time can be further shortened.

  Third, since the humidity sensor 64 is used as a means for determining the evaporation of the condensed water, the evaporation of the condensed water can be easily determined based on the detected value. Moreover, since the humidity sensor 64 is disposed in the air discharge duct 32 branched from the casing 30, the humidity of the humid air discharged from the air discharge duct 32 can be accurately detected.

Second Embodiment
6 and 7 show a second embodiment. In the second embodiment, the condensed water of the indoor heat exchanger 16 is based on the detected value of the indoor refrigerant temperature sensor 58 (see FIG. 1) that detects the temperature of the refrigerant discharged from the indoor heat exchanger 16 during the heating operation. Determine evaporation. More specifically, as indicated by a curve e in FIG. 6, when no condensed water adheres to the indoor heat exchanger 16 (no water retention), the indoor heat exchanger 16 discharges the indoor heat exchanger temperature sensor 58. The temperature of the refrigerant detected at 1 rises at a substantially constant rate as time elapses after the heating operation is started.

  On the other hand, a change in the temperature of the refrigerant detected by the indoor unit refrigerant temperature sensor 58 when condensed water adheres (holds water) is shown by a curve f. As indicated by f1, the refrigerant temperature suddenly rises for a while after the heating operation is started. During this time, the temperature of the condensed water on the outer surface of the indoor heat exchanger 16 is rising. Thereafter, as shown by f2, a shelf portion where the temperature of the refrigerant rises gradually appears. During this time, the condensed water is evaporated and a part of the heat is consumed as latent heat of evaporation, so the rate of increase in the refrigerant temperature is small. The reason why the refrigerant temperature suddenly increases as indicated by f3 is that all condensed water has evaporated. The second embodiment uses a change in the rate of increase in the refrigerant temperature (f2 to f3) that changes in relation to the evaporation of the condensed water.

  Hereinafter, determination of evaporation of condensed water will be described with reference to the flowchart of FIG. However, Steps S30 to S34 and S42 to S46 are the same as Steps S10 to S14 and S17 to S21 of the first embodiment, and thus description thereof is omitted. In step S34, damper closing control is performed, and the air discharge damper 40 is rotated to the closed position to close the passage 41. And the moist air containing water vapor | steam is discharged | emitted from the air drain duct 32 out of a vehicle interior.

  Next, in step S35, it is determined whether or not the latent heat shelf detection flag TEflag is 1, that is, whether or not the refrigerant temperature detected by the indoor unit refrigerant temperature sensor 58 is in the shelf portion f2 of the curve f in FIG. If it is in the shelf portion f2 (TEflag = 1), the process proceeds to step S36, and if not (TEflag = 0), the process proceeds to step S40.

  In step S40, it is determined whether or not the refrigerant temperature discharged from the indoor heat exchanger 16 and detected by the indoor unit refrigerant temperature sensor 58 has entered the shelf portion f2. Specifically, whether or not the difference between the current value TEnow (for example, an average value for 5 seconds) of the refrigerant temperature and the previous value TEpre (for example, the average value for 5 seconds) of the refrigerant temperature is equal to or less than a reference value TEbase (for example, 1 ° C.). Determine whether. If it is less than or equal to the reference value TEbase, it is determined that the shelf portion f2 has been entered, and the latent heat shelf detection flag Tflag is set to 1 in step S41.

  On the other hand, in step S36, it is determined whether or not the refrigerant temperature detected by the indoor unit refrigerant temperature sensor 58 has passed through the shelf portion f2, that is, whether or not the condensed water in the indoor heat exchanger 16 has evaporated. Specifically, the difference between the current value TEnow (for example, the average value for 5 seconds) of the refrigerant temperature detected by the indoor unit refrigerant temperature sensor 58 and the previous value TEpre (for example, the average value for 5 seconds) of the refrigerant temperature is the reference value TEbase. It is judged whether it is above (for example, 1 degreeC). If the difference between the two is equal to or greater than the reference value TEbase, it is determined that the condensed water in the indoor heat exchanger 16 has evaporated and the outer surface has dried. In step S37, damper opening control is performed, the air discharge damper 40 is rotated to the open position, the passage 41 is opened, and warm air is blown into the vehicle interior from the outlet. Thereafter, TEflag is reset to 0 in step S38, and TEpre is updated in step S39.

  According to the second embodiment, the same effects as the first effect and the second effect of the first embodiment can be obtained. In addition to these effects, the evaporation of condensed water is determined based on the change rate of the temperature of the refrigerant discharged from the indoor heat exchanger 16 and detected by the indoor refrigerant temperature sensor 58. Therefore, even if an instantaneous temperature rise occurs for some reason, the damper opening control is not performed, and the determination of evaporation of condensed water becomes more accurate.

<Modification>
As a modification of the second embodiment, the evaporation of the condensed water may be determined based on the temperature of the casing inside air on the downstream side of the indoor heat exchanger 16. The temperature of the air on the downstream side of the indoor heat exchanger 16 detected by the indoor unit air temperature sensor 62 (see FIG. 1) changes at the same rate of increase as the refrigerant temperature detected by the indoor unit refrigerant temperature sensor 58. Therefore, it is determined that the condensed water has evaporated when the detected value of the indoor unit air temperature sensor 62 passes through the shelf portion (see f2 in FIG. 6).

<Third Embodiment>
8 and 9 show a third embodiment. In the third embodiment, the refrigerant temperature discharged from the indoor heat exchanger 16 and detected by the indoor unit refrigerant temperature sensor 58 (see FIG. 1) and the refrigerant temperature sensor 52 discharged from the compressor 10 and discharged (see FIG. 1). The evaporation of the condensed water in the indoor heat exchanger 16 is determined on the basis of the temperature difference from the refrigerant temperature detected by.

  That is, as indicated by a curve i in FIG. 8, the refrigerant temperature TE detected by the indoor unit refrigerant temperature sensor 58 when the condensed water adheres to the indoor heat exchanger 16 is a steep portion after the heating operation is started. It includes a gentle portion (shelf portion) indicated by i1, and then i2, and a sharp portion i3 thereafter. The upward trend of the curve i is basically the same as the upward trend of the curve f of the second embodiment.

  On the other hand, the refrigerant temperature TD detected by the discharged refrigerant temperature sensor 52 increases rapidly immediately after the start of heating as shown by a curve h, and then gradually increases at a substantially constant rate. It is higher than the refrigerant temperature TE. The rapid rise immediately after the start of heating is because the refrigerant is compressed from the low temperature and low pressure state by the compressor 10 when the air conditioner is started, and is changed to the high temperature and high pressure state within a short time.

  As a result of the difference between the two refrigerant temperature rise rates described above, the refrigerant temperature discharged from the indoor heat exchanger 16 and detected by the indoor refrigerant temperature sensor 58 and the refrigerant temperature discharged from the compressor 10 and detected by the discharged refrigerant temperature sensor 52 are detected. The temperature difference from the refrigerant temperature increases rapidly immediately after the start of the heating operation. Thereafter, since there is a shelf portion i2 in the refrigerant temperature TE, the temperature difference between the two becomes large, and at the steep portion i3, the temperature difference between both becomes small. In the third embodiment, a change in temperature difference between the two refrigerant temperatures is used.

  Hereinafter, determination of evaporation of condensed water will be described with reference to the flowchart of FIG. However, Steps S50 to S54 and S61 to S65 are the same as Steps S10 to S14 and S17 to S21 of the first embodiment, and thus description thereof is omitted.

  In step S54, damper closing control is performed, and the air discharge damper 40 is turned to the closed position to close the passage 41. And the moist air containing water vapor | steam is discharged | emitted from the air drain duct 32 out of a vehicle interior. Next, in step S55, it is determined whether or not the discharge temperature detection flag TDflag is 1. This is because a place where there is no temperature difference between the refrigerant temperature TD and the refrigerant temperature TE immediately after the start of heating is not considered. If the reference value is exceeded (TDflag = 1), the process proceeds to step S56, and if not exceeded (TDflag = 0), the process proceeds to step S59.

  In step S59, it is determined whether or not the refrigerant temperature TD discharged from the compressor 10 and detected by the discharged refrigerant temperature sensor 52 exceeds a reference value. If the value of the refrigerant temperature exceeds 50 ° C., the shelf portion i2 has been entered, so the latent heat shelf detection flag TDflag is set to 1 in step S60.

  In step S56, the condensation of the indoor heat exchanger 16 is performed based on the refrigerant temperature TD detected by the discharged refrigerant temperature sensor 52 and the refrigerant temperature TE discharged from the indoor heat exchanger 16 and detected by the indoor refrigerant temperature sensor 58. Determine water evaporation. Specifically, when the temperature difference between the refrigerant temperature TD and the refrigerant temperature TE becomes equal to or less than the reference value TDbase (for example, 50 ° C.), it is determined that the shelf portion i2 of the refrigerant temperature ends and the condensed water in the indoor heat exchanger 16 has evaporated. To do. Then, damper opening control is performed in step S57, and the air discharge damper 40 is rotated to the open position to open the passage 41. In this way, warm air is blown out from the air outlet into the passenger compartment, and TDflag is reset to 0 in step S58.

  According to the third embodiment, the same effects as the first effect and the second effect of the first embodiment can be obtained. In addition to these, the temperature difference between the refrigerant temperature TD discharged from the compressor 10 and detected by the discharged refrigerant temperature sensor 52 and the refrigerant temperature TE discharged from the indoor heat exchanger 16 and detected by the indoor unit refrigerant temperature sensor 58. Since the evaporation of the condensed water is determined based on the change of the refrigerant temperature, it is not necessary to detect the rising rate of the refrigerant temperature TD and the refrigerant temperature TE.

<Modification>
As a modification of the third embodiment, based on the temperature difference between the temperature of the indoor unit air temperature sensor 62 that detects the air temperature downstream of the indoor heat exchanger 16 and the temperature of the outside air temperature sensor 68 that detects the outside air temperature. The evaporation of condensed water can also be determined. That is, as shown by a curve k in FIG. 10, the air temperature downstream of the indoor heat exchanger 16 detected by the indoor air temperature sensor 62 is a steep portion k1 after switching to the heating operation, and the subsequent shelf. It includes a part k2 and a subsequent sharp part k3. This temperature increasing tendency is the same as the temperature increasing tendency of the refrigerant at the outlet of the indoor heat exchanger 16 detected by the indoor refrigerant temperature sensor 58 shown by the curve f in FIG.

  On the other hand, the temperature of the outside air detected by the outside air temperature sensor 68 does not change at the start of the heating operation, as indicated by the straight line l, and is substantially constant, and this constant value is the shelf portion of the curve k. It passes near the boundary between k2 and the steep part k3. As a result, the temperature difference between the temperature of the air on the downstream side of the indoor heat exchanger 16 and the temperature of the outside air becomes small during the evaporation of the condensed water, that is, the shelf portion k2, and becomes large after the evaporation, that is, the steep portion k3. Therefore, the evaporation of the condensed water can be determined using this change in temperature difference.

1 is an overall explanatory diagram of a first embodiment of the best mode of the present invention. It is a flowchart explaining the action | operation of 1st Embodiment. It is explanatory drawing which shows the flow of the refrigerant | coolant at the time of heating operation of 1st Embodiment, (a) is during the evaporation of condensed water, (b) shows the state after evaporation similarly. It is explanatory drawing which shows the flow of the refrigerant | coolant at the time of the air_conditionaing | cooling operation of 1st Embodiment. It is a graph which shows the effect of a 1st embodiment. It is a graph explaining the principle of 2nd Embodiment. It is a flowchart explaining the action | operation of 2nd Embodiment. It is a graph explaining the principle of 3rd Embodiment. It is a flowchart explaining the action | operation of 3rd Embodiment. It is a graph which shows the principle of the modification of 3rd Embodiment.

Explanation of symbols

10: Compressor 13: Four-way switching valve 16: Indoor heat exchanger 20: Pressure reducer 23: Outdoor heat exchanger 30: Casing 32: Air exhaust duct 34: Heater core 38: Air mix door 40: Air exhaust bumper 41: Passage 75: Control device 77: Storage unit

Claims (9)

A compressor (10) for compressing the refrigerant;
An indoor heat exchanger (16) that is accommodated in a casing (30) having an outlet and exchanges heat between the refrigerant passing through the inside and air flowing in the casing;
A decompressor (20) for decompressing and expanding the refrigerant;
An outdoor heat exchanger (23) for exchanging heat between the refrigerant passing through the interior and the outside air;
A four-way switching valve (13) for switching the flow direction of the refrigerant during cooling operation and heating operation;
An air discharge duct (32) formed in the casing near the indoor heat exchanger;
An air discharge damper (40) for opening and closing a passage (41) between the indoor heat exchanger and the outlet of the casing;
Determination means for determining whether or not the condensed water adhering to the indoor heat exchanger has evaporated at the time of switching from the cooling operation to the heating operation,
While it is determined by the determination means that the condensed water of the indoor heat exchanger has not evaporated, the air discharge damper closes the passage and discharges moist air from the air discharge damper.
After determining that the condensed water has evaporated, the heat pump vehicle air conditioner is characterized in that the air discharge damper opens the passage and blows dry air from the outlet.   The control device (75) having a storage unit (77) that receives the determination result of the determination means, controls the operation of the air exhaust damper, and stores the operation state of each time. The heat pump type vehicle air conditioner as described.   The determination means includes a humidity sensor (64) for detecting the humidity of the air near the indoor heat exchanger, and determines the evaporation of the condensed water when the humidity of the air falls below a predetermined value. The heat pump type vehicle air conditioner according to claim 2.   The determination means includes a first refrigerant temperature sensor (58) for detecting the temperature of the refrigerant in the first predetermined place, and determines the evaporation of the condensed water when the rate of increase in the temperature of the refrigerant changes from small to large. The heat pump type vehicle air conditioner according to claim 2.   The determination means includes a first air temperature sensor (62) for detecting the temperature of air at a second predetermined location, and determines evaporation of the condensed water when the rate of increase in the temperature of the air changes from small to large. The heat pump type vehicle air conditioner according to claim 2.   The determination means includes a first refrigerant temperature sensor (58) for detecting the temperature of the refrigerant at the first predetermined place and a second refrigerant temperature sensor (52) for detecting the temperature of the refrigerant at the third predetermined place. The heat pump according to claim 2, wherein evaporation of the condensed water is determined when a temperature difference between the temperature of the refrigerant at a predetermined location and the temperature of the refrigerant at the third predetermined location changes from large to small. Type vehicle air conditioner.   The determination means includes a first air temperature sensor (62) for detecting the temperature of the air at the second predetermined place and a second air temperature sensor (68) for detecting the temperature of the air at the fourth predetermined place. The heat pump according to claim 2, wherein evaporation of the condensed water is determined when a temperature difference between the temperature of the air at a predetermined location and the temperature of the air at the fourth predetermined location changes from small to large. Type vehicle air conditioner.   A temperature difference between the temperature of the refrigerant at the first predetermined location and the temperature of the refrigerant at the third predetermined location immediately after switching from the cooling operation to the heating operation, and the temperature of the air at the second predetermined location The heat pump vehicle air conditioner according to claim 6 or 7, wherein a temperature difference from the temperature of the air at the fourth predetermined place is not taken into consideration.   A heater core (34) disposed on the downstream side of the indoor heat exchanger in the casing for heating the air passing through the indoor heat exchanger; and an air mix door (38) disposed on the upstream side of the heater core. The heat pump type vehicle air conditioner according to claim 3, 4, 5, 6 or 8.

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