JP4507460B2 - Air conditioner for vehicles - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a vehicle air conditioner that controls the evaporator temperature by intermittently operating the compressor of the refrigeration cycle.
[0002]
[Prior art]
Conventionally, in Japanese Patent Application Laid-Open No. 11-198644, in a vehicle air conditioner, the target evaporator temperature is set to a low temperature of about 3 to 4 ° C. in the normal mode, while the power saving (fuel consumption priority) mode by the economy switch is set. At the time of setting, the target evaporator temperature is set to a high temperature of about 12 to 13 ° C., thereby lowering the operating rate of the intermittent compressor operation (compressor operating time / (compressor operating time + compressor stop time)). Thus, there is described a vehicle air conditioner that reduces the power of a vehicle engine that drives a compressor.
[0003]
Also, in vehicles (hybrid vehicles, eco-run vehicles, etc.) that automatically stop the vehicle engine when the vehicle stops, such as when waiting for a signal, the condensed water on the surface of the evaporator rises when the compressor temperature rises when the compressor stops when the vehicle stops. When the vehicle is completely dried, the odor component dissolved in the condensed water is released from the evaporator and blown out into the passenger compartment together with the blown air, giving the passengers an uncomfortable feeling.
[0004]
Therefore, in the above prior art, when the vehicle engine is stopped (when the compressor is stopped), the compressor stop time that can suppress the generation of odor is calculated based on the condition of the intake air of the evaporator, and the elapsed time after the compressor stops is calculated as follows. When the calculation time is exceeded, it has been proposed to restart the vehicle engine and return the compressor to the operating state even when the vehicle is stopped.
[0005]
[Problems to be solved by the invention]
By the way, in the vehicle air conditioner, the evaporator temperature may be determined in terms of air conditioning function from the viewpoints of control of the passenger compartment temperature (cooling) and dehumidification performance (ensuring the antifogging performance of the window glass, control of the passenger compartment humidity) However, in practice, there is a problem that the upper limit of the evaporator temperature is restricted in order to suppress the odor from the evaporator.
[0006]
More specifically, in the middle season of spring and autumn, from the viewpoint of vehicle interior temperature control and dehumidifying performance, the evaporator temperature may increase to about 18 to 20 ° C. Even below, the evaporator temperature is suppressed to a temperature of about 12 to 13 ° C. in order to suppress odor from the evaporator.
[0007]
The upper limit value of the evaporator temperature (12 to 13 ° C.) is set so as to be always lower than the dew point temperature of the intake air of the evaporator under normal use conditions of the vehicle air conditioner. It will be in the state wet with water, and, thereby, detachment | desorption of an odor component can be prevented and odor generation can be suppressed. However, with such evaporator temperature control (ie, compressor intermittent control), there is room for the air conditioning function to raise the evaporator temperature to a higher temperature. The upper limit of the vessel temperature is kept low, hindering the power saving effect.
[0008]
The present invention has been made in view of the above points. In a vehicle air conditioner that controls the evaporator temperature by intermittently operating the compressor of the refrigeration cycle, the odor generation from the evaporator is suppressed and the compressor is driven. The purpose is to balance the improvement of the power saving effect of the source.
[0009]
[Means for Solving the Problems]
The present invention has devised technical means for achieving the above object based on experimental findings described below.
[0010]
FIG. 25 is a view similar to FIG. 17 of Japanese Patent Application Laid-Open No. 11-198644, and shows the mechanism of odor generation associated with intermittent (ON-OFF) control of the compressor. FIG. 25 (a) shows the odor intensity of the air in the passenger compartment sensed by the passenger in the passenger compartment, FIG. 25 (b) shows the change in the evaporator outlet temperature due to the intermittent operation of the compressor, and FIG. FIG. 25 (d) shows the behavior of the condensed water on the evaporator surface due to the intermittent operation of the compressor.
[0011]
As shown in FIG. 25 (c), the compressor stops when the evaporator outlet temperature drops to the target temperature TEO-α (α is the hysteresis width of the ON-OFF control), and the evaporator stops when the compressor stops. When the temperature rises to the target temperature TEO, the compressor returns to the operating state.
[0012]
During operation of the compressor, the evaporator blowout temperature is lowered to a temperature lower than the dew point temperature of the intake air of the evaporator due to the endothermic effect of the refrigerant in the evaporator, so that condensed water is generated on the surface of the evaporator. Dissolves odorous components. In the period (1) immediately after the compressor is stopped, the endothermic action of the refrigerant is stopped, so that the evaporator outlet temperature rises rapidly, and thereafter the evaporator outlet temperature rises gradually.
[0013]
In the next period (2), the evaporator outlet temperature is gradually stabilized at a substantially constant temperature. This is because the temperature of the evaporator suction air drops to a temperature that matches the endothermic amount (latent heat) due to evaporation of condensed water on the evaporator surface, and the balance between the latent heat of evaporation of condensed water and the temperature drop of the evaporator suction air is almost balanced. It is to do.
[0014]
The evaporator blowout temperature (constant temperature) in period (2) is the wet bulb temperature Twet of the evaporator suction air. This wet bulb temperature Twe is determined based on the wet air diagram of FIG. Sphere temperature) and relative humidity. That is, in the wet air diagram of FIG. 26, the wet bulb temperature Twe is obtained at the point where the isoenthalpy line Q that passes through the intersection point P between the evaporator suction air temperature (dry bulb temperature) and the relative humidity intersects the saturation curve. be able to. For example, when the temperature of the evaporator suction air (dry bulb temperature) = 35 ° C. and the relative humidity = 35%, the wet bulb temperature Twet = 23 ° C. At this time, the dew point temperature Trt is a temperature at which the humid air at the intersection P becomes saturated with the absolute humidity being constant, and in the above example, the dew point temperature Trt = 17.5 ° C.
[0015]
The relationship of the dew point temperature Trt <the wet bulb temperature Twe is always satisfied by the characteristics of the wet air diagram of FIG. The dew point temperature Trt is a temperature at which condensed water begins to adhere to the evaporator surface, and the wet bulb temperature Twe is a temperature at which the evaporator surface is held at a predetermined temperature by evaporation of the condensed water.
[0016]
In the period {circle around (2)}, odorous components are concentrated in the condensed water as the condensed water evaporates. Furthermore, when the time passes and the next period {circle around (3)} is reached, the condensed water film becomes thin and the thermal resistance of the condensed water decreases immediately before the condensed water on the evaporator surface dries out. The amount increases and the amount of heat absorbed by the evaporation of condensed water increases. As a result, the evaporator outlet temperature decreases by a predetermined amount. Thereafter, the condensed water on the surface of the evaporator is completely dried, and heat absorption due to evaporation of the condensed water is eliminated, so that the evaporator outlet temperature rises again.
[0017]
Odor generation in the evaporator blowing air is started during the period {circle around (3)}, i.e., immediately after the condensed water on the evaporator surface is completely dried, and the adhering odor component is released from the fin surface of the evaporator, and The odor intensity gradually increases with time.
[0018]
According to the odor generation mechanism of FIG. 25, in the behavior of the evaporator outlet temperature during the compressor stop period, the period during which the condensed water evaporates, that is, the evaporator outlet temperature rises to the wet bulb temperature of the evaporator suction air. It can be seen that after the elapse of period (2), period (3) in which the odor intensity increases is reached.
[0019]
  Therefore, paying attention to the above points, in the first aspect of the invention, in the vehicle air conditioner for controlling the evaporator temperature by intermittently operating the compressor (1) of the refrigeration cycle,
  The compressor (1) is stopped during the first predetermined time (t1) when the condition for generating odor from the evaporator (9) is satisfied, and is a time sufficiently shorter than the first predetermined time (t1). During the second predetermined time (t2), the intermittent operation mode for operating the compressor (1) is executed,
  When the number of executions of the intermittent operation mode is a predetermined number or more, it is determined whether the evaporator temperature is equal to or lower than the wet bulb temperature of the intake air of the evaporator (9),
  When the evaporator temperature is lower than the wet bulb temperature, the operation of the compressor (1) is intermittently controlled so that the evaporator temperature is lower than the wet bulb temperature and higher than the dew point temperature of the suction air. And
  When it is determined that the evaporator temperature is higher than the wet bulb temperature, the operation of the compressor (1) is intermittently controlled so that the evaporator temperature is maintained at the normal target evaporator temperature.It is characterized by that.
  According to this, since the intermittent operation mode in which the compressor (1) is operated intermittently for a short time (t2) when the condition for generating odor from the evaporator (9) is satisfied, the compression in the intermittent operation mode is performed. During the machine stop period (t1), the condensed water on the surface of the evaporator (9) is gradually evaporated, and the surface of the evaporator (9) is partially dried little by little. Thereby, since the odor component is gradually dispersed and desorbed from the surface of the evaporator (9), the odor level can be kept low, and the odor level does not rise to a level at which it feels uncomfortable.
  Moreover, in the intermittent operation mode, the operation of the compressor (1) is forcibly limited to intermittent operation for a short time (t2), and the compressor (1) is stopped for a time sufficiently longer than the time (t2). The operating rate of the machine (1) can be further lowered to further improve the power saving effect.
  As in the second aspect of the present invention, in the first aspect, the target evaporator temperature in the normal state is determined based on at least a temperature necessary for controlling the temperature of the air blown into the passenger compartment. .
  As in the third aspect of the invention, in the first or second aspect, the generation of condensed water and the drying of the condensed water are repeated on the surface of the evaporator (9) with the intermittent operation of the compressor (1). By determining the condition, it can be determined that the condition for generating an odor from the evaporator (9) is satisfied.
  As in the invention described in claim 4, in claim 3, the evaporation is performed based on the state of the intake air of the evaporator (9) and the target evaporator temperature for intermittently controlling the operation of the compressor (1). The conditions under which the generation of condensed water and the drying of condensed water are repeated on the surface of the vessel (9) may be determined.
  As in the invention described in claim 5, when the target evaporator temperature is in the vicinity of the wet-bulb temperature and dew point temperature of the intake air of the evaporator (9) in the fourth aspect, the surface of the evaporator (9) You may make it determine with it corresponding to the conditions where generation | occurrence | production of condensed water and drying of condensed water are repeated.
  As in the invention described in claim 6, in any one of claims 1 to 5, the temperature sensor (39) for detecting the temperature of the intake air of the evaporator (9) and the humidity for detecting the humidity of the intake air A sensor (40) may be provided, and the wet bulb temperature may be calculated based on the intake air temperature and the intake air humidity detected by both the sensors (39, 40).
  According to a seventh aspect of the present invention, in any one of the first to fifth aspects, in the interior air mode in which the interior air is sucked into the evaporator (9), the humidity is determined based on the interior temperature and the interior humidity. The sphere temperature may be calculated.
  As in the eighth aspect of the invention, in any one of the first to fifth aspects, the compressor (1) is stopped from the operating state in the outside air mode in which outside air is sucked into the evaporator (9). The evaporator temperature after the stop state has passed for a predetermined time may be the wet bulb temperature.
  According to the seventh and eighth aspects of the present invention, a dedicated sensor for detecting the state of the intake air of the evaporator becomes unnecessary.
[0020]
  In the invention according to claim 9, in the vehicle air conditioner including compressor control means (S9) for intermittently controlling the operation of the compressor (1) of the refrigeration cycle according to the evaporator temperature,
  The compressor control means (S9) has first calculation means (S160) for calculating the wet bulb temperature of the intake air of the evaporator (9), and second calculation for calculating the dew point temperature of the intake air of the evaporator (9). Means (S170) and determination means (S180) for determining whether or not a condition for generating odor from the evaporator (9) is satisfied,
  When it is determined by the determination means (S180) that the odor is generated from the evaporator (9), the evaporator temperature is equal to or lower than the wet bulb temperature calculated by the first calculation means (S160), and (2) The operation of the compressor (1) is intermittently controlled so that the temperature is higher than the dew point temperature calculated by the calculating means (S170).
  According to this, even after the evaporator temperature is once lowered to a temperature lower than the dew point temperature Trt and condensed water adheres to the evaporator (9), the upper limit of the evaporator temperature is controlled by the above control. By limiting to below the bulb temperature Twet, the evaporator temperature can be lowered again before the condensed water has dried. Therefore, since the surface of the evaporator can be kept wet with the condensed water, the generation of odor from the evaporator (9) can be suppressed.
[0021]
In addition, by maintaining the evaporator temperature in the vicinity of the wet bulb temperature that is higher than the dew point temperature of the intake air of the evaporator, the operating rate of the compressor (1) can be reduced and the power saving effect of the compressor drive source can be improved.
[0022]
Therefore, it is possible to achieve both suppression of odor generation from the evaporator (9) and improvement of the power saving effect of the compressor drive source.
[0023]
  ClaimTo 10Like the claimed invention, the claims9After the compressor (1) is stopped, the evaporator temperature isCalculated by the first calculating means (S160)When the wet bulb temperature or a temperature lower than the wet bulb temperature by a predetermined temperature is raised, the compressor (1) is returned to the operating state.ifGood.
[0035]
  Claim11Like the claimed invention, the claims9 or 10InThe judging means (S180)Conditions for generating odor from the evaporator (9) by determining the conditions under which the condensed water is repeatedly generated and dried on the surface of the evaporator (9) with the intermittent operation of the compressor (1) Can be determined.
[0036]
  ClaimTo 12Like the claimed invention, the claims11InThe judging means (S180)Based on the state of the intake air of the evaporator (9) and the target evaporator temperature for intermittently controlling the operation of the compressor (1), generation of condensed water and drying of condensed water on the surface of the evaporator (9) It is also possible to determine a condition for repeating the above.
[0037]
  Claim13Like the claimed invention, the claims12InThe judging means (S180)The target evaporator temperature isCalculated by the first calculating means (S160)Wet bulb temperature andCalculated by the second calculating means (S170)When the temperature is near the dew point temperature, it may be determined that the condition that the generation of condensed water and the drying of condensed water are repeated on the surface of the evaporator (9) is satisfied.
[0040]
  Claim14Like the described invention,In any one of claims 9 to 13,A temperature sensor (39) for detecting the temperature of the intake air of the evaporator (9) and a humidity sensor (40) for detecting the humidity of the intake air;
  The first calculation means (S160)The wet bulb temperature may be calculated based on the intake air temperature and the intake air humidity detected by both sensors (39, 40).
[0041]
  Claim15Like the described invention,In any one of Claims 9 thru | or 13, 1st calculation means (S160)The wet bulb temperature may be calculated based on the vehicle interior temperature and the vehicle interior humidity in the inside air mode in which the vehicle interior air is sucked into the evaporator (9).
[0042]
  Claim16Like the described invention,In any one of Claims 9 thru | or 13, 1st calculation means (S160)In the outside air mode in which the outside air of the passenger compartment is sucked into the evaporator (9), the compressor (1) is stopped from the operating state, and the evaporator temperature after the predetermined time has passed is the wet bulb temperature.Calculate asYou may do it.
[0043]
  Claim15 and 16According to the described invention, a dedicated sensor for detecting the state of the intake air of the evaporator becomes unnecessary.
[0044]
  ClaimTo 17In the described invention, the claims1 to 8 and claims 12, 13In any one of these, the 1st determination means (S120) which determines the 1st target evaporator temperature required in order to control the blowing temperature to a vehicle interior,
  A second determining means (S130) for determining a second target evaporator temperature necessary for maintaining the humidity in the passenger compartment within a comfortable range;
  Third determining means (S140) for determining a third target evaporator temperature required for defrosting the window glass;
  And fourth determining means (S150) for finally determining the lowest temperature among the first to third target evaporator temperatures as the target evaporator temperature.
[0045]
  ClaimInvention described in Item 17According to the above, the temperature of the evaporator (9) is controlled to the lowest temperature among the temperatures required for controlling the blowout temperature into the passenger compartment, controlling the humidity in the passenger compartment, and preventing fogging of the window glass.
[0046]
By the way, if the humidity in the air-conditioned space is maintained within a comfortable range, the user can feel comfort without cooling. Therefore, in the season when the outside air is in a low humidity atmosphere, such as in the middle of spring and autumn, the second target evaporator temperature for humidity control by the second determining means (S130) is maintained at a higher temperature. Also, in such an intermediate period, the outside air temperature is in the intermediate temperature range, and the other first and third target evaporator temperatures can both be increased, so that the final target evaporator temperature is eventually reached. Becomes a higher temperature, and the power saving effect of the compressor drive source can be improved by reducing the operating rate of the compressor (1).
[0051]
In addition, the code | symbol in the bracket | parenthesis of each said means shows the correspondence with the specific means as described in embodiment mentioned later.
[0052]
DETAILED DESCRIPTION OF THE INVENTION
(First embodiment)
FIG. 1 is an overall configuration diagram of the first embodiment, and a refrigeration cycle R of a vehicle air conditioner includes a compressor 1 that sucks, compresses, and discharges refrigerant. The compressor 1 has an electromagnetic clutch 2 for power interruption, and the power of the vehicle engine 4 is transmitted to the compressor 1 via the electromagnetic clutch 2 and the belt 3. The energization of the electromagnetic clutch 2 is intermittently performed by the air conditioning electronic control device 5, and the operation of the compressor 1 is intermittently activated by the intermittent energization of the electromagnetic clutch 2.
[0053]
The high-temperature and high-pressure superheated gas refrigerant discharged from the compressor 1 flows into the condenser 6, where the refrigerant is cooled and condensed by exchanging heat with outside air blown from a cooling fan (not shown). The refrigerant condensed in the condenser 6 then flows into the liquid receiver 7 where the gas-liquid refrigerant is separated inside the liquid receiver 7, and surplus refrigerant (liquid refrigerant) in the refrigeration cycle R is received by the liquid receiver 7. Stored in.
[0054]
The liquid refrigerant from the liquid receiver 7 is decompressed to a low pressure by an expansion valve (decompression means) 8 to be in a low-pressure gas-liquid two-phase state. The expansion valve 8 is a temperature type expansion valve having a temperature sensing part 8a that senses the temperature of the outlet refrigerant of the evaporator 9. The low-pressure refrigerant from the expansion valve 8 flows into the evaporator (cooling heat exchanger) 9. The evaporator 9 is installed in the air conditioning case 10 of the air conditioning unit 15 of the vehicle air conditioner, and the low-pressure refrigerant flowing into the evaporator 9 absorbs heat from the air in the air conditioning case 10 and evaporates. The outlet of the evaporator 9 is coupled to the suction side of the compressor 1 and forms a closed circuit with the above-described cycle components.
[0055]
In the air conditioning case 10, a blower 11 is disposed upstream of the evaporator 9, and the blower 11 is provided with a centrifugal blower fan 12 and a drive motor 13. An inside / outside air switching box 14 is disposed on the suction side of the blower fan 12, and the inside / outside air switching door 14 a in the inside / outside air switching box 14 opens and closes the outside air introduction port 14 b and the inside air introduction port 14 c. Thereby, outside air (vehicle compartment outside air) or inside air (vehicle compartment air) is switched and introduced into the inside / outside air switching box 14. The inside / outside air switching door 14a is driven by an electric drive device 14e made of a servo motor.
[0056]
The air blown by the blower 11 flows into the upstream portion of the evaporator 9 in the air conditioning case 10. An air mix door 19 is disposed in the air conditioning case 10 on the downstream side of the evaporator 9. A hot water heater core (heating heat exchanger) 20 that heats air using hot water (cooling water) of the vehicle engine 4 as a heat source is installed on the downstream side of the air mix door 19. A bypass passage 21 that bypasses the hot water heater core 20 and flows air is formed on the side (upper part) of the hot water heater core 20.
[0057]
The air mix door 19 is a rotatable plate-like door, and is driven by an electric drive device 22 composed of a servo motor. The air mix door 19 adjusts the air volume ratio between the hot air passing through the hot water heater core 20 and the cool air passing through the bypass passage 21, and the air blown into the vehicle interior by adjusting the air volume ratio of the cold / hot air. Adjust the temperature. Therefore, in this example, the air mix door 19 constitutes a temperature adjusting means for the air blown into the passenger compartment.
[0058]
A hot air passage 23 extending upward from the lower side is formed on the downstream side of the hot water heater core 20, and the hot air from the hot air passage 23 and the cold air from the bypass passage 21 are mixed by the air mixing unit 24 to be desired. Can produce temperature air.
[0059]
Further, in the air conditioning case 10, a blowing mode switching unit is configured on the downstream side of the air mixing unit 24. That is, a defroster opening 25 for blowing air to the inner surface of the vehicle windshield is formed on the upper surface of the air conditioning case 10, and the defroster opening 25 is opened and closed by a rotatable plate-like defroster door 26.
[0060]
In addition, a face opening 27 that blows air toward the upper body of the passenger in the passenger compartment is formed on the upper surface of the air conditioning case 10 at a position on the rear side of the vehicle from the defroster opening 25. The face opening 27 is rotatable. It is opened and closed by a flat plate-like face door 28.
[0061]
In the air conditioning case 10, a foot opening 29 for blowing air toward the feet of passengers in the passenger compartment is formed in the lower part of the face opening 27, and the foot opening 29 is a rotatable plate-like foot door 30. It is opened and closed by.
[0062]
The blowing mode doors 26, 28, and 30 are connected to a common link mechanism (not shown), and are driven by an electric drive device 31 including a servo motor via the link mechanism.
[0063]
Next, the outline of the electric control unit in the present embodiment will be described. The air-conditioning electronic control device 5 includes a well-known microcomputer including a CPU, a ROM, a RAM, and the like, and its peripheral circuits. As a temperature sensor of the evaporator 9, a temperature sensor 32 composed of a thermistor is provided. More specifically, the temperature sensor 32 is disposed in a portion of the air conditioning case 10 immediately after the air is blown from the evaporator 9, and detects the evaporator blowing temperature Te.
[0064]
In this embodiment, the humidity sensor 33 that detects the relative humidity RRH in the vehicle interior, the temperature sensor 39 that detects the intake air temperature Tin of the evaporator 9, and the humidity sensor that detects the relative humidity RHi of the intake air of the evaporator 9. 40.
[0065]
In addition to the sensors 32, 33, 39, and 40 described above, the air-conditioning electronic control device 5 detects the inside air temperature Tr, the outside air temperature Tam, the solar radiation amount Ts, the hot water temperature Tw, and the like for air conditioning control. Detection signals are input from the sensors 34 to 37.
[0066]
The air conditioning control panel 38 installed near the vehicle interior instrument panel is provided with operation switches 38a to 38e that are manually operated by passengers, and operation signals of the operation switches 38a to 38e are also input to the air conditioning electronic control device 5. Is done.
[0067]
Specifically, as this operation switch, a temperature setting switch 38a for generating a temperature setting signal Tset, an air volume switch 38b for generating an air volume switching signal, an air blowing mode switch 38c for generating an air blowing mode signal, and an inside / outside air switching signal are generated. An inside / outside air changeover switch 38d, an air conditioner switch 38e, and the like are provided.
[0068]
The blowout mode switch 38c is used to manually switch between the face mode, foot mode, bilevel mode, foot differential mode, and defroster mode. The air conditioner switch 38e generates an on / off signal for the compressor 1.
[0069]
Next, the operation of this embodiment in the above configuration will be described. The flowchart of FIG. 2 shows an outline of the control processing executed by the microcomputer of the air-conditioning electronic control device 5. The control routine of FIG. 2 is such that the ignition switch of the vehicle engine 4 is turned on and power is supplied to the control device 5. And start.
[0070]
First, in step S1, flags and timers are initialized, and in the next step S2, operation signals such as operation switches 38a to 38e of the air conditioning control panel 38 are read. In the next step S3, a vehicle environmental condition detection signal is read from the sensors 32 to 37 and the like.
[0071]
Subsequently, in step S4, a target blowing temperature TAO of the conditioned air blown into the vehicle interior is calculated. This target blowing temperature TAO is a blowing temperature necessary for maintaining the passenger compartment at the set temperature Tset of the temperature setting switch 38a, and is calculated based on the following Equation 1.
[0072]
[Expression 1]
TAO = Kset × Tset−Kr × Tr−Kam × Tam−Ks × Ts + C
However, Tr: The inside air temperature detected by the inside air sensor 33
Tam: outside air temperature detected by outside air sensor 34
Ts: amount of solar radiation detected by the solar radiation sensor 35
Kset, Kr, Kam, Ks: Control gain
C: Constant for correction
Next, in step S5, a target air flow rate of air blown by the blower 11, specifically, a blower voltage Ve that is an applied voltage of the blower drive motor 13 is determined based on the TAO. The method for determining the blower voltage Ve is well known. The blower voltage (target air volume) Ve is increased on the high temperature side (maximum heating side) and the low temperature side (maximum cooling side) of the TAO, and the blower voltage is increased in the intermediate temperature range of the TAO. Reduce the voltage (target air volume) Ve.
[0073]
Next, in step S6, the inside / outside air mode is determined. In this inside / outside air mode, for example, the inside air mode is set when the inside temperature Tr is significantly higher than the set temperature Tset by a predetermined temperature or higher (during cooling high load), and the outside air mode is set at other times. Alternatively, as the TAO rises from the low temperature side to the high temperature side, the setting may be switched from the all-inside air mode → the inside / outside air mixing mode → the all outside air mode.
[0074]
Next, in step S7, the blowing mode is determined according to the TAO. As is well known, the blowing mode is switched from face mode to bi-level mode to foot mode as TAO rises from the low temperature side to the high temperature side.
[0075]
Next, in step S8, the target opening degree SW of the air mix door 19 is calculated by the following formula 2 based on the TAO, the evaporator outlet temperature Te, and the hot water temperature Tw.
[0076]
[Expression 2]
SW = [(TAO−Te) / (Tw−Te)] × 100 (%)
Here, the target opening degree SW of the air mix door 19 sets the maximum cooling position of the air mix door 19 (solid line position in FIG. 1) to 0%, and the maximum heating position of the air mix door 19 (dotted line position in FIG. 1). Is expressed as a percentage with 100%.
[0077]
Next, it progresses to step S9 and the interruption (ON-OFF) of a compressor action | operation is determined. That is, the target evaporator temperature TEO and the evaporator outlet temperature Te detected by the temperature sensor 32 are compared to determine the applied voltage Vc to the electromagnetic clutch 2 and determine the intermittent operation (ON-OFF) of the compressor. To do. Details of step S9 will be described later with reference to FIG.
[0078]
Next, it progresses to step S10 and a control signal is output to various actuator parts (2, 13, 14e, 22, 31) so that the control state determined by said step S5-S9 may be obtained. When it is determined in the next step S11 that the control cycle τ has elapsed, the process returns to step S2.
[0079]
FIG. 3 shows a specific example of the method for determining the intermittent (ON-OFF) operation of the compressor in step S9. First, in step S100, it is determined whether or not the air conditioner switch 38e is turned on. When 38e is OFF, the OFF signal of the compressor 1 is output in step S110.
[0080]
When the air conditioner switch 38e is ON, the process proceeds to step S120, and a target evaporator temperature TEO1 for room temperature control determined from the target blowing temperature TAO calculated in step S4 of FIG. 2 is calculated. This TEO1 is determined in order to obtain an evaporator temperature necessary for controlling the passenger compartment temperature. Therefore, TEO4 is determined to decrease with a decrease in TAO as illustrated in the map of FIG.
[0081]
Next, in step S130, a target evaporator temperature TEO2 for controlling the passenger compartment to a comfortable humidity range is calculated. The humidity control TEO2 is determined so that the vehicle interior relative humidity RHr detected by the humidity sensor 33 is maintained near the target relative humidity (for example, around 60%), and more specifically. As illustrated in the map of FIG. 5, when the vehicle interior relative humidity exceeds 60%, TEO2 becomes a lower temperature T1 (for example, 11 ° C.), and the vehicle interior relative humidity is less than 50%. A higher temperature T2 (for example, 18 ° C.) is set. In this way, by switching TEO2 between the high and low levels according to the actual vehicle interior relative humidity, the vehicle interior relative humidity can be maintained near the target relative humidity (for example, around 60%).
[0082]
Next, in step S140, the target evaporator temperature TEO3 for antifogging control of the vehicle window glass is calculated. Here, the fogging factor of the vehicle window glass is roughly divided into the temperature of the window glass and the relative humidity of the air in the passenger compartment. That is, as the temperature of the window glass decreases and the relative humidity of the air in the passenger compartment increases, the window glass becomes more easily fogged.
[0083]
Therefore, in step S140, as illustrated in the map of FIG. 6, it is determined that TEO3 decreases as the temperature of the window glass decreases and as the relative humidity of the cabin air increases. More specifically, TEO3 is determined based on the temperature of the window glass and the relative humidity of the passenger compartment air so that the relative humidity in the vicinity of the inner surface of the window glass is maintained near 90%.
[0084]
The temperature of the window glass can be calculated (estimated) based on the outside air temperature Tam, the vehicle speed, the defroster blowing temperature, the inside air temperature Tr, etc., in addition to being directly detected by the temperature sensor.
[0085]
Next, in step S150, the lowest temperature among the three target evaporator temperatures TEO1 to TEO3 is finally determined as the target evaporator temperature TEO. Note that the ON / OFF control of the compressor 1 is provided with a predetermined hysteresis width (usually about 1 ° C.) between the temperature at which the compressor 1 is turned on and the temperature at which the compressor 1 is turned off in order to prevent hunting. In this specification, the temperature at which the compressor 1 is turned ON is defined as the target evaporator temperature TEO.
[0086]
In the next step S160, the wet bulb temperature Twet of the evaporator suction air is calculated. Specifically, the wet air diagram of FIG. 26 is stored in the ROM of the electronic control unit 5 for air conditioning, and this humid air diagram and the temperature Tin of the evaporator intake air detected by the sensors 39 and 40 and Based on the relative humidity RHi, the wet bulb temperature Twet of the evaporator suction air can be calculated.
[0087]
Next, the process proceeds to step S170, and the dew point temperature Trt of the intake air is calculated based on the wet air diagram, the temperature Tin of the evaporator intake air, and the relative humidity RHi.
[0088]
Next, it progresses to step S180 and it is determined whether the target evaporator temperature TEO corresponds to the conditions which generate | occur | produce an odor from the evaporator 9. FIG. Specifically, it is determined whether the target evaporator temperature TEO is set to a temperature near the wet bulb temperature Twet and the dew point temperature Trt.
[0089]
For this reason, in step S180, it is determined whether TEO is in a temperature range higher than (Trt + 2 ° C.) and lower than (Twet + 2 ° C.). Here, the determination ranges of Trt + 2 ° C. and Twet + 2 ° C. are set in consideration of response delay of the evaporator blowout temperature sensor 32, variation in detected temperature, and the like. This determination range is based on the characteristics of the temperature sensor 32, the compressor It is preferable to set an appropriate value for each target product in consideration of the refrigeration cycle responsiveness (responsibility of change in evaporator blowout temperature) and the like with respect to 1 operation interruption.
[0090]
When TEO is within the above determination range, generation of condensed water on the surface of the evaporator 9 (wet surface of the evaporator) and evaporation and drying of the condensed water due to intermittent operation of the compressor 1 (surface of the evaporator) It is determined that the condition in which the odor is generated from the evaporator is satisfied.
[0091]
When the determination in step S180 is NO, the target evaporator temperature TEO does not correspond to the condition for generating odor from the evaporator 9, so the process proceeds to step S190, and normal compressor control is performed. That is, when the actual evaporator outlet temperature Te detected by the temperature sensor 32 rises to the target evaporator temperature TEO, an ON signal of the compressor 1 is output, and the actual evaporator outlet temperature Te becomes the target evaporator temperature TEO−. When the temperature falls to 1 ° C., an OFF signal of the compressor 1 is output. That is, during normal compressor control, the evaporator outlet temperature Teon = TEO at which the compressor 1 is turned on, and the evaporator outlet temperature Teoff = TEO-1 at which the compressor 1 is turned off.
[0092]
Here, during normal compressor control in step S170, since there is no upper limit of the target evaporator temperature TEO for odor suppression, the viewpoint of TEO is room temperature control, vehicle interior humidity control, and window glass antifogging control. Can be raised to the minimum temperature required. In particular, in the season in which the outside air is in a low humidity atmosphere such as in the middle of spring and autumn, the minimum temperature can be raised to a temperature of around 20 ° C., thereby reducing the operating rate of the compressor 1 and reducing the vehicle engine 4. The power saving effect can be greatly improved.
[0093]
If the relative humidity is in a comfortable range (usually a wide range of about 25 to 65% RH), the user of the air-conditioned space can operate without cooling (dehumidification / dehumidification) by the evaporator 9, that is, without operating the compressor 1. It is known to feel comfort over a relatively wide temperature range.
[0094]
Therefore, in the first embodiment, a humidity sensor 33 that detects the relative humidity RHr in the vehicle interior is added as an air conditioning control sensor, and the relative humidity RHr in the vehicle interior is near the upper limit (for example, about 60%) of the comfort area. By determining the target evaporator temperature TEO so as to be maintained, the operating rate of the compressor 1 can be further reduced, and the power saving of the vehicle engine 4 can be realized particularly effectively.
[0095]
On the other hand, when the target evaporator temperature TEO satisfies the condition for generating odor from the evaporator 9, the determination in step S180 is YES, and odor suppression compressor control is performed in step S200. Specifically, the evaporator outlet temperature Teon when the compressor 1 is turned on is limited to the wet bulb temperature Twet of the evaporator suction air. For this reason, in step S200, the evaporator outlet temperature Teon when the compressor 1 is turned on is set to the lower one of the target evaporator temperature TEO and the wet bulb temperature Twet. That is, Teon = MIN (Twet, TEO).
[0096]
And the evaporator blowing temperature Teoff when the compressor 1 is turned off is a temperature lower than Teon by a predetermined hysteresis width (for example, 1 ° C.). That is, Teoff = MIN (Twet, TEO) −1 ° C.
[0097]
FIG. 7 shows compressor control for odor suppression in step S200. When the evaporator blowout temperature Te rises to the wet bulb temperature Twe, the compressor 1 is always turned on, so the evaporator blowout temperature Te is shown in FIG. While the wet bulb temperature Twe of the period (2) of b) is reached, the compressor 1 is turned on to lower the evaporator outlet temperature Te again. For this reason, it is possible to prevent the condensed water on the surface of the evaporator from drying out and to prevent the shift to the period {circle around (3)}, that is, the generation of odor.
[0098]
Moreover, even when the compressor is controlled to suppress odor, the evaporator blowout temperature Teon when the compressor 1 is turned on is increased to the wet bulb temperature Twe of the evaporator suction air, so that Teon is less than the dew point temperature Trt of the evaporator suction air. Compared with the case where the temperature is set to a low temperature, the OFF period of the compressor 1 becomes longer, the operation rate is lowered, and the power saving effect of the vehicle engine 4 can be improved.
[0099]
(Second Embodiment)
FIG. 8 is a flowchart showing the control according to the second embodiment, and since steps S100 to S170 of FIG. 3 of the first embodiment are the same, illustration is omitted. In the second embodiment, steps S210 and S220 are added between step S180 and step S200 in FIG.
[0100]
That is, in the OFF period of the compressor 1, the period {circle around (2)} in which the evaporator outlet temperature Te is the wet bulb temperature Twet continues for a certain period of time as shown in FIG. Since no odor occurs, paying attention to this point, in the second embodiment, after the evaporator outlet temperature Te reaches the wet bulb temperature Twe during the OFF period of the compressor 1 by adding steps S210 and S220, a predetermined time After t0 (for example, 5 seconds) has passed, the process proceeds to step S200, where the compressor 1 is turned on to prevent the generation of odor.
[0101]
According to the second embodiment, the ON-OFF operation of the compressor 1 is as shown in FIG. 9, and the OFF period of the compressor 1 is lengthened by a predetermined time t0 compared to the first embodiment (FIG. 7). be able to. Thereby, a compressor operation rate can be lowered | hung and the power saving effect of the vehicle engine 4 can be improved further.
[0102]
In the second embodiment, in the above description, the predetermined time t0 is set to a fixed value of 5 seconds. However, after the evaporator outlet temperature Te reaches the wet bulb temperature Twe during the OFF period of the compressor 1, the evaporator The time until the condensed water on the surface is completely dried (period (2) in FIG. 25) varies depending on the amount of condensed water on the evaporator surface and the condensed water evaporation rate, and the amount of condensed water on the evaporator surface The condensed water evaporation rate can be estimated from the temperature of the evaporator intake air, the relative humidity, the dew point temperature, the evaporator outlet temperature, and the like. Therefore, the predetermined time t0 may be a variable time calculated from the temperature of the evaporator intake air, the relative humidity, the dew point temperature, the evaporator outlet temperature, and the like.
[0103]
(Third embodiment)
FIG. 10 is a flowchart showing the control according to the third embodiment. In the first embodiment, the evaporator outlet temperature Teon = MIN (Twet, TEO) when the compressor 1 is turned on in step S200 is set. In the embodiment, in step S200a, the evaporator outlet temperature Teon = MIN (Twet-2, TEO).
[0104]
That is, as shown in FIG. 11, the compressor 1 is turned on at a temperature lower than the wet bulb temperature Twe by a predetermined temperature T0 (2 ° C. in this example).
[0105]
In order to calculate the wet bulb temperature Twe, it is necessary to detect the temperature Tin of the evaporator suction air and the relative humidity RHi. However, the response delay of the sensors 39 and 40 for detecting the temperature and relative humidity, and the variation of the detection signal. In some cases, calculation errors may occur due to the above. In addition, a response delay, a variation in detected temperature, or the like may also occur in the evaporator outlet temperature sensor 32. Therefore, in consideration of these points, in the third embodiment, the compressor 1 is turned on at a temperature lower than the wet bulb temperature Twe by a predetermined temperature T0 (2 ° C. in this example), thereby further improving the effect of suppressing odor. Can be demonstrated reliably.
[0106]
(Fourth embodiment)
FIG. 12 is a flowchart showing the control according to the fourth embodiment, which is a combination of the second embodiment and the third embodiment. That is, in the fourth embodiment, the evaporator outlet temperature Teon for turning on the compressor 1 in the second embodiment is changed to Twe-2 ° C. in the third embodiment.
[0107]
Therefore, according to the fourth embodiment, as shown in FIG. 13, when a predetermined time t0 (for example, 5 seconds) elapses after the evaporator outlet temperature Te reaches Twe-T0 (for example, 2 ° C.), the step Proceeding to S200, the compressor 1 is turned on to prevent the generation of odor. For this reason, it is possible to improve the power saving effect of the vehicle engine 4 by reducing the compressor operation rate by extending the compressor OFF period by the predetermined time t0 while exhibiting the effect of preventing the generation of odor.
[0108]
(Fifth embodiment)
In the first to fourth embodiments, basically, the upper limit of the evaporator outlet temperature Te is limited to the vicinity of the wet bulb temperature Twet of the evaporator suction air, so that from the evaporator 9 accompanying the intermittent control of the compressor 1. Although the odor generation is suppressed, the fifth embodiment pays attention to the hysteresis width of the intermittent control of the compressor 1, and when the odor is generated from the evaporator 9, by reducing the hysteresis width, Odor generation from the evaporator 9 is suppressed.
[0109]
Therefore, in the fifth embodiment, the target evaporator temperature for intermittent control of the compressor 1, specifically, the evaporator outlet temperature Teon for turning on the compressor 1 and the evaporator outlet temperature Teoff for turning off the compressor 1 are set. This is determined based on a different concept from the first to fourth embodiments.
[0110]
FIG. 14 is a flowchart showing the control according to the fifth embodiment, and steps S100 and S110 are the same processes as those in the first to fourth embodiments. In step S150, the target evaporator temperature TEO is calculated based on the target outlet temperature TAO (see S4 in FIG. 2). The target evaporator temperature TEO in this example is determined so that TAO-C> TEO from the viewpoint of room temperature control. That is, TEO is determined to be lower by a predetermined value C than TAO.
[0111]
This is due to the following reason. When the compressor 1 is turned on and off, the evaporator outlet temperature Te changes, but if the target evaporator temperature TEO is determined to be lower than the target outlet temperature TAO by a predetermined value C as described above, the air mix door 19 This is because fluctuations in the temperature of the air blown into the passenger compartment can be eliminated by adjusting the opening degree (adjusting the heating amount of the heater core 20).
[0112]
The next step S170 is the same process as in the first to fourth embodiments, and calculates the dew point temperature Trt based on the wet air diagram of FIG. 26, the temperature Tin of the evaporator intake air, and the relative humidity RHi. The next step S183 is to determine whether or not the condition for generating odor from the evaporator 9 is satisfied, as in step S180 in FIG. 3 and the like. In this example, the specific process is as follows. Do.
[0113]
That is, whether the dew point temperature Trt is within the shaded area in FIG. 16, that is, is in the range between the target evaporator temperature (TEO-1) = Teoff for turning off the compressor 1 and (Teoff-3 ° C.). If Trt is within this range, the wetting state of the evaporator surface (Te <Trt) and the drying state of the evaporator surface (Te> Twet) are repeated with the ON-OFF behavior of the compressor 1. It is determined that it falls under the condition of generating odor.
[0114]
When the determination in step S183 is NO, it is a time when the condition for generating an odor is not satisfied, and therefore normal compressor control is performed. That is, the evaporator outlet temperature Teon = TEO at which the compressor 1 is turned on in step S300, and the evaporator outlet temperature Teoff = TEO-1 ° C. at which the compressor 1 is turned off in step S310.
[0115]
On the other hand, when the determination in step S183 is YES, it corresponds to the condition for generating odor, the hysteresis width of the compressor ON-OFF control is reduced for odor suppression control. That is, since the evaporator outlet temperature Teon = TEO at which the compressor 1 is turned on at step S320 and the evaporator outlet temperature Teoff = TEO−0.3 ° C. at which the compressor 1 is turned off at step S330 are increased, the Teoff is increased. Compared to the case of compressor control, the hysteresis width (Teon-Teoff) of ON-OFF control is reduced from 1 ° C to 0.3 ° C.
[0116]
In the next step S340, ON / OFF of the compressor 1 is determined by comparing the actual evaporator outlet temperature Te detected by the sensor 32 with the above-described Teon and Teoff.
[0117]
Next, the operational effects of the fifth embodiment will be described in detail by comparison with the prior art. FIG. 15 shows compressor control according to the prior art in which the hysteresis width (Teon-Teooff) is always 1 ° C. FIG. 15 shows an example in which the target evaporator temperature TEO (evaporator outlet temperature Teon at which the compressor 1 is turned on) is increased to 19 ° C. for power saving of the vehicle engine.
[0118]
As environmental conditions for air conditioning, for example, when the outside air temperature is 35 ° C. and the outside air humidity is 50%, and the suction mode of the air conditioner is the outside air mode, the suction air temperature Tin of the evaporator 9 is 35 ° C. and the suction air humidity is 50. 26, and the dew point temperature Trt = 23 ° C. of the sucked air and the wet bulb temperature Twet = 26 ° C. from the wet air diagram of FIG. Therefore, even if TEO = 19 ° C., TEO is sufficiently lower than the dew point temperature Trt, so that the evaporator surface always remains wet. For this reason, as shown on the left side of FIG. 15, the odor intensity felt by the passenger in the passenger compartment is at a low level without any problem.
[0119]
However, as the environmental conditions of air conditioning, for example, when the intake air temperature Tin of the evaporator 9 is 21.5 ° C. and the intake air humidity is 80%, the dew point temperature Trt of the intake air Trt = 18 from the wet air diagram of FIG. ° C, wet bulb temperature Twet = 19 ° C. That is, as shown on the right side of FIG. 15, both the dew point temperature Trt and the wet bulb temperature Twe are close to the target evaporator temperature TEO.
[0120]
Also in this case, the compressor 1 is turned on at the target evaporator temperature TEO (Teon) = 19 ° C., and the compressor 1 is turned off at 18 ° C. of TEO-1 (= Teoff). When the compressor 1 is OFF due to delay, refrigeration cycle response, etc., an undershoot of the evaporator outlet temperature Te occurs, the evaporator outlet temperature Te falls below the dew point temperature Trt, and condensed water adheres to the evaporator surface. When the compressor 1 is turned on, an overshoot of the evaporator blowout temperature Te occurs, and the evaporator blowout temperature Te exceeds the wet bulb temperature Twe. Therefore, a phenomenon occurs in which condensed water evaporates and dries out.
[0121]
For this reason, an odor is generated by the mechanism of FIG. 25 and the odor intensity increases to a level of 1.5. Therefore, in the case of ON-OFF control with a constant hysteresis width according to the prior art, it is practically impossible to switch TEO to a high temperature of 19 ° C. (improve power saving effect) due to the problem of odor generation.
[0122]
On the other hand, in the fifth embodiment, when the dew point temperature Trt is close to the target evaporator temperature TEO, such as the dew point temperature Trt = 18 ° C. of the intake air and the wet bulb temperature Twet = 19 ° C. 14, it is determined that the condition for generating the odor from the evaporator 9 is satisfied in step S183 in FIG. 14, and in step S330, the temperature Teoff at which the compressor 1 is turned off is raised to (TEO−0.3 ° C.), and the hysteresis width Is reduced to 0.3 ° C.
[0123]
As a result, as shown in FIG. 16, since the compressor 1 is turned off at a temperature level at which the evaporator outlet temperature Te is sufficiently higher than the dew point temperature Trt, the evaporator outlet temperature Te even if an undershoot of the evaporator outlet temperature Te occurs. Does not drop to the dew point temperature Trt and the condensed water does not adhere to the evaporator surface. Therefore, since the evaporator surface is kept dry, the odor intensity can be suppressed to a problem-free level of 0.5.
[0124]
Thereby, suppression of generation | occurrence | production of odor and the demonstration of the power saving effect by switching to the high temperature side of TEO can be made compatible.
[0125]
As apparent from the comparison between FIG. 15 and FIG. 16, when the compressor control of the fifth embodiment corresponds to the condition that odor is generated from the evaporator 9, the cycle of the compressor ON-OFF control is set at the time of normal control. It can be said that the control is smaller than the above.
[0126]
In addition, the compressor ON-OFF control cycle is reduced only under conditions where odors occur, and during normal control, the cycle is increased as usual, so the adverse effect on the durable life of the electromagnetic clutch 2 is small. it can.
[0127]
In the evaporator 9, it is inevitable that a certain temperature distribution is generated due to non-uniform distribution of the gas-liquid distribution in the refrigerant passage, non-uniformity of the wind speed distribution on the air side, and the like. On the other hand, since the temperature sensor 32 detects a typical air blowing temperature Te of the evaporator 9, in the control of FIG. 16 according to the fifth embodiment, the evaporator blowing temperature is partially determined by the temperature distribution in the evaporator 9. There may be a location where Te falls below the dew point temperature Trt. Even in this case, since the cycle of the compressor ON-OFF control is small, the time during which the evaporator outlet temperature Te falls below the dew point temperature Trt is shortened, and the amount of condensed water generated is small, so the amount of odorous components dissolved is small, Odor generation can be effectively suppressed.
[0128]
(Sixth embodiment)
Since the sixth embodiment is a modification of the fifth embodiment, only the difference will be described with reference to FIG. In the sixth embodiment, the wet bulb temperature Twet of the evaporator suction air is calculated in step S160 based on the wet air diagram, the suction air temperature Tin, and the suction air humidity RHi.
[0129]
In the next step S185, it is determined whether or not the wet bulb temperature Twe is within the behavior range of the evaporator outlet temperature Te by the compressor ON-OFF control, and whether or not the condition for generating an odor from the evaporator 9 is satisfied. Determine. More specifically, it is determined whether the wet bulb temperature Twe is higher than the temperature Teoff-3 ° C. at which the compressor 1 is turned off and lower than the temperature Teon + 1 ° C. at which the compressor 1 is turned on.
[0130]
Here, the lower limit value of the behavior range of the evaporator outlet temperature Te is set to (Teoff-3 ° C.) in this example. Even if the compressor 1 is turned off at Teoff (= TEO−1 ° C.), the actual evaporator This is because the fin surface temperature causes an undershoot of about 3 ° C. due to the responsiveness of the temperature sensor 32 and the cycle. In addition, the upper limit value of the behavior range of the evaporator outlet temperature Te is set to (Teon + 1 ° C.) in this example because an overshoot of about 1 ° C. occurs due to the problem of responsiveness.
[0131]
As described above, when the wet bulb temperature Twe is within the behavior range of the evaporator outlet temperature Te by the compressor ON-OFF control, the actual evaporator outlet temperature Te is lower than the dew point temperature Trt and condensed water is generated. Since the state in which the evaporator 9 gets wet and the state in which the actual evaporator blowing temperature Te exceeds the wet bulb temperature Twe and the condensed water is dried are repeated, it can be determined that the condition for generating odor from the evaporator 9 is satisfied. .
[0132]
Accordingly, when the determination in step S185 is YES, the process proceeds to the next steps S320 and S330 as in the fifth embodiment, and in step S330, the OFF temperature Teoff of the compressor 1 is set to (TEO−0.3 ° C.). Pull up to reduce the hysteresis width to 0.3 ° C. Thereby, the effect similar to the said 5th Embodiment can be exhibited.
[0133]
(Seventh embodiment)
FIG. 18 shows a seventh embodiment, which is a combination of the dew point temperature Trt calculation step S170 and determination step S183 according to the fifth embodiment and the wet bulb temperature Twet calculation step S160 and determination step S185 according to the sixth embodiment. It is a thing.
[0134]
According to the seventh embodiment, in step S183 and step S185, it is confirmed that both the wet bulb temperature Twet and the dew point temperature Trt are within a predetermined range of the behavior of the evaporator outlet temperature Te by the compressor ON-OFF control. Thus, since the condition for generating odor from the evaporator 9 is determined, the determination accuracy of the odor generating condition is improved.
[0135]
(Eighth embodiment)
In the fifth to seventh embodiments described above, when it is determined in steps S183 and S185 that the odor generation condition is satisfied, the OFF temperature Teoff of the compressor 1 is increased to (TEO-0.3 ° C.) in step S330. However, in the eighth embodiment, on the contrary, the ON temperature Teon of the compressor 1 is lowered from TEO to reduce the hysteresis width.
[0136]
The eighth embodiment will be specifically described with reference to FIG. 19. Steps S100 to S185 are the same as those in FIG. If it is determined in step S185 that the odor generation condition is satisfied based on the wet bulb temperature Twet, the ON temperature Teon of the compressor 1 is lowered to (TEO-0.65 ° C.) in the next step S325. On the other hand, the OFF temperature Teoff of the compressor 1 is set to (TEO-1 ° C.) in step S335. Accordingly, the OFF temperature Teoff has the same value as that in step S310 during normal control.
[0137]
FIG. 20 shows the control of the eighth embodiment. During the control of odor countermeasures, the hysteresis width of the compressor ON-OFF control is reduced to 0.35 ° C. by lowering the ON temperature Teon. As a result, the upper limit value of the evaporator outlet temperature Te becomes lower than the wet bulb temperature Twet, and the condensed water does not dry out. In other words, since the surface of the evaporator 9 is always kept wet by the condensed water, the generation of odor from the evaporator 9 can be suppressed.
[0138]
(Ninth embodiment)
In the fifth to eighth embodiments described above, when controlling the odor countermeasure, the hysteresis width of the compressor ON-OFF control is reduced, and as a result, the cycle of the compressor ON-OFF control is reduced. In the ninth embodiment, the ON time of the compressor 1 is directly limited to a predetermined time by a timer means, thereby reducing the cycle of the compressor ON-OFF control and suppressing the generation of odor.
[0139]
First, the problem of the ninth embodiment will be described with reference to FIG. 21. FIG. 21 shows a case where TEO is raised to a considerably high temperature level of 26 ° C. The solid line in the figure indicates the evaporator outlet temperature detected by the temperature sensor 32. This is the behavior of Te, and the alternate long and short dash line is the behavior of the fin surface temperature of the evaporator 9. In this case, TEO is at a high temperature of 26 ° C. Therefore, the evaporator blowout temperature Te and the fin surface when the compressor 1 is turned on The amount of temperature undershoot tends to increase. FIG. 21 shows a case where the hysteresis width of the compressor ON-OFF control is always set to 1 ° C. as a result. As a result, the compressor ON time is 6 seconds, the ON-OFF cycle is 90 seconds, and the fin surface temperature is under. The fin surface temperature drops below the dew point temperature Trt as shown in part A by the chute to generate condensed water.
[0140]
And by the compressor OFF, the evaporator blowing temperature Te and the fin surface temperature rise to a temperature sufficiently higher than the wet bulb temperature Twet. Thereby, since condensed water dries, the state where the surface of the evaporator 9 was wet with the condensed water and the dried state are repeated, and an odor is generated from the evaporator 9.
[0141]
In particular, in the TEO high temperature range, the evaporator fin surface temperature rapidly decreases when the compressor 1 is turned on, but the evaporator outlet temperature Te detected by the temperature sensor 32 is lower than the decrease in fin surface temperature due to sensor response delay. Decline with a delay. For this reason, the phenomenon that the ON period of the compressor 1 is excessively long occurs with respect to the actual decrease in the evaporator fin surface temperature, which further promotes the undershoot of the fin surface temperature.
[0142]
In view of the above points, in the ninth embodiment, the high temperature region of TEO is determined, and the ON time of the compressor 1 is forcibly limited to a predetermined time by the timer means.
[0143]
The ninth embodiment will be described with reference to FIG. 22. Steps S100, S110, and S150 are the same as those in the above embodiments. In step S187, it is determined whether TEO is in a high temperature range. As a specific example, TEO> 20 ° C. is determined, and when TEO is higher than 20 ° C., it is determined as a high temperature range.
[0144]
If the determination in step S187 is YES, it is next determined in step S350 that the evaporator outlet temperature Te has passed the point (1) in FIG. That is, it is determined whether the state where Te is higher than TEO (Te ≧ TEO) from the state where the evaporator outlet temperature Te is lower than TEO (Te <TEO). If the determination in step S350 is YES, then in step S360, the compressor 1 is turned on for a predetermined time (one second as a specific example), and then the compressor 1 is turned off.
[0145]
Here, since the ON time of the compressor 1 is as short as 1 second, the evaporator outlet temperature Te continues to rise slightly after the compressor 1 is turned ON for the cycle side and the sensor response. 23, the evaporator outlet temperature Te starts to decrease from the point (2) in FIG. 23 (time point after the compressor 1 is turned off), and after a certain period of time, the evaporator outlet temperature Te increases again at the point (3). .
[0146]
If it is not determined in step S350 that the evaporator outlet temperature Te has passed the point (1) in FIG. 23, the process proceeds to step S370, and the compressor 1 is turned on (1) for a predetermined time (a time sufficiently longer than the compressor ON time). Thus, it is determined whether or not the evaporator outlet temperature Te is not lowered even after 10 seconds as a specific example.
[0147]
Normally, when the compressor 1 is turned on, the evaporator outlet temperature Te decreases from the point (2) to the point (3) in FIG. 23. Therefore, the determination in step S370 is NO, and the compressor 1 is turned off in step S380. maintain.
[0148]
If Te continues to rise as indicated by the alternate long and short dash line B in FIG. 23 from the time point {circle around (1)} when the compressor is turned on for some reason, the determination in step S370 is YES, and the process proceeds to step S360, and the compressor 1 is ON only for seconds.
[0149]
By the above control, the compressor 1 is turned on for 1 second every time the point (1) in FIG. 23 passes. For this reason, according to the ninth embodiment, as shown in FIG. 24, when TEO = 26 ° C., the lower limit value of the evaporator outlet temperature Te is set to a temperature higher than the wet bulb temperature Twe due to the compulsory limitation of the compressor ON time. Can be maintained. This can always keep the surface of the evaporator 9 dry and suppress the generation of odor from the evaporator 9.
[0150]
In addition, according to the ninth embodiment, since it is possible to control odor suppression from the evaporator 9 without detecting the temperature and humidity of the air sucked into the evaporator, the cost of the entire apparatus can be reduced by reducing the number of sensors. This is extremely advantageous in practical use.
[0151]
(10th Embodiment)
In the ninth embodiment, the case where the compressor ON time is fixed to a value of 1 second has been described. However, in the tenth embodiment, the compressor ON time is varied so as to be increased by increasing the heat load of the evaporator 9. Here, the target evaporator temperature TEO is calculated so as to decrease as the heat load of the evaporator 9 increases.
[0152]
Therefore, in the tenth embodiment, for example, when TEO = 25 ° C., the compressor ON time = 1 second, when TEO = 20 ° C., the compressor ON time = 1.5 seconds, and when TEO = 15 ° C., the compressor Determine ON time = 2 seconds.
[0153]
In the tenth embodiment, for example, TEO> 13 ° C. may be determined, and the time when TEO is higher than 13 ° C. may be determined as the high temperature range.
[0154]
The high temperature range of TEO in the ninth and tenth embodiments is that the evaporator blow-off temperature rises above the wet bulb temperature Twe of the evaporator suction air when the compressor 1 is turned off, and the condensed water is completely dried. It is a temperature range that satisfies Therefore, it is preferable that the determination temperature in the high temperature region varies depending on the use region, and further, the determination temperature in the high temperature region may be varied depending on the season of use of the air conditioning.
[0155]
(Eleventh embodiment)
The eleventh embodiment is configured to execute an intermittent operation mode in which the compressor 1 is intermittently operated at a predetermined time interval for a short time, thereby suppressing the generation of odor from the evaporator 9. The power saving effect of the compressor drive source (vehicle engine 4) is further enhanced.
[0156]
FIG. 27 is a flowchart of compressor control according to the eleventh embodiment, and the control processes in steps S100, S110, and S150 to S190 are the same as those in the above embodiments.
[0157]
When the air conditioner switch 38e (FIG. 1) is turned on, the processes in steps S150 to S180 are performed in the same manner as in the first embodiment. The calculation of the target evaporator temperature TEO in step S150 may be determined based only on the target evaporator temperature TEO1 for room temperature control calculated from TAO (see step S120 in FIG. 3). Similarly to the embodiment, in addition to the target evaporator temperature TEO1 for room temperature control, the target evaporator temperature TEO2 for vehicle interior humidity control (see step S130 in FIG. 3), and the target evaporator for antifogging control of vehicle window glass The temperature TEO3 (see step S140 in FIG. 3) may be calculated, and the lowest temperature among these may be finally calculated as the target evaporator temperature TEO.
[0158]
In step S180, it is determined whether or not the target evaporator temperature TEO is set to a temperature in the vicinity of the wet bulb temperature Twet and the dew point temperature Trt, thereby determining whether or not the condition for generating an odor from the evaporator 9 is satisfied. To do. If the determination in step S180 is YES, the process proceeds to step S400, and an intermittent operation mode in which the compressor 1 is intermittently operated at a predetermined time interval for a short time is executed.
[0159]
Specifically, in step S400, the compressor 1 is stopped for the first predetermined time t1 by the first timer means, and the compressor 1 is operated only for the second predetermined time t2 by the second timer means. repeat. Here, during the second predetermined time t2, the compressor 1 is operated for a short time, and the rate at which the ratio of the wet state by the condensed water on the surface of the evaporator 9 decreases (in other words, the surface of the evaporator 9 dries out). For example, 1 second.
[0160]
On the other hand, the first predetermined time t1 is much longer than the second predetermined time t2, for example, 30 seconds, thereby reducing the operating rate of the compressor 1 and maximizing the power saving effect.
[0161]
In this intermittent operation mode, odor generation from the evaporator 9 can also be suppressed for the following reason. That is, under normal cooling operation conditions, by setting the compressor stop period (period T2) in the intermittent operation mode, the condensed water gradually evaporates on the surface of the evaporator 9, and the evaporator 9 The surface wetting ratio is gradually reduced, and the surface of the evaporator 9 is gradually dried.
[0162]
At this time, since the temperature distribution due to the non-uniform refrigerant evaporation amount unavoidably occurs on the surface of the evaporator 9, the portion where the condensed water is completely dried gradually increases on the surface of the evaporator 9. For this reason, the odor component is gradually dispersed and separated from the surface of the evaporator 9. As a result, according to the intermittent operation mode, the odor level can be kept low, and the odor level does not rise to a level at which it feels uncomfortable.
[0163]
In the next step 410, the number of executions of the intermittent operation mode in step S400 is counted. This count is made by counting either the number of operations of the compressor 1 during the first predetermined time t1, the number of stops of the compressor 1 during the second predetermined time t2, or the number of executions of one cycle (t1 + t2) in the intermittent operation mode. Also good.
[0164]
In the next step 420, it is determined whether or not the number of executions of the intermittent operation mode has reached a predetermined value, for example, 10 times or more, and when the number of executions of the intermittent operation mode becomes a predetermined value or more, the process proceeds to step S430. It is determined whether the evaporator outlet temperature Te after executing the mode a predetermined number of times is equal to or lower than the wet bulb temperature Twet.
[0165]
Under normal cooling operation conditions, the surface of the evaporator 9 is gradually dried by executing the intermittent operation mode as described above. Therefore, after the intermittent operation mode is executed a predetermined number of times (for example, 10 times) or more, the evaporator The condensed water on the surface of 9 is completely dried, and the evaporator outlet temperature Te rises to a temperature higher than the wet bulb temperature Twe as indicated by a point X in FIG.
[0166]
Thus, in the state where the condensed water on the surface of the evaporator 9 is completely dried and the evaporator blowing temperature Te exceeds the wet bulb temperature Twe, no odor is generated from the surface of the evaporator 9, so the process proceeds from step S430 to step S190. Proceed and perform normal compressor control.
[0167]
On the other hand, when the intake air temperature of the evaporator 9 is very low, the evaporation of the condensed water on the surface of the evaporator 9 becomes small, and therefore, after the intermittent operation mode is executed a predetermined number of times (10 times). In some cases, the surface of the evaporator 9 is kept wet with condensed water, and the relationship of the evaporator blowing temperature Te ≦ the wet bulb temperature Twe is maintained. In this case, since the determination in step S430 is YES, the process proceeds to step S440 to perform compressor control for odor suppression.
[0168]
That is, in the compressor control in step S440, the compressor 1 is turned on at the evaporator outlet temperature Te ′ when the intermittent operation mode is executed a predetermined number of times (10 times) (when the determination in step S420 is YES). The target temperature Teon is set to Te′−1 ° C., and the operation of the compressor 1 is intermittently controlled. That is, in the compressor control in step S440, the evaporator outlet temperature Te 'when the intermittent operation mode is executed a predetermined number of times is set to the target evaporator temperature TEO, and thereafter the operation of the compressor 1 is intermittently controlled.
[0169]
Since the evaporator outlet temperature Te is controlled to be equal to or lower than the wet bulb temperature Twe by the compressor control in step S440, the generation of odor from the evaporator 9 can be suppressed.
[0170]
Further, since the compressor 1 is turned off at a temperature higher than the dew point temperature Trt, which is Te′-1 ° C., the operating rate of the compressor 1 is kept lower than when the compressor 1 is turned off at the dew point temperature Trt or lower. And power saving effect can be demonstrated.
[0171]
By the way, since the intermittent operation mode of step S400 repeats a special intermittent operation of the compressor operation at a very short time t2, it is not preferable to continue for a long time in view of the operation mode of the vehicle engine 4. However, in the present embodiment, when the number of intermittent operation modes reaches a predetermined number or more, the intermittent operation mode in step S400 is stopped, and the routine proceeds to normal compressor control in step S190 or compressor control for odor suppression in step S440. From this, the compressor operation time and the compressor stop time extend to the time based on the hysteresis widths of the target temperatures Teon and Teoff, which is a preferable operation mode for the vehicle engine 4.
[0172]
Even when the determination in step S180 is NO, since no odor is generated from the surface of the evaporator 9, the process proceeds to step S190, and normal compressor control is performed.
[0173]
In the compressor control in step S440 described above, the target temperature Teon = Te ′ is set. However, the compressor 1 is intermittently controlled by setting Teon = wet bulb temperature Twe and Toff = Twet−1 ° C. The same effect can be exhibited.
[0174]
(Other embodiments)
In the first to eighth embodiments, the temperature sensor 39 and the humidity sensor 40 arranged on the suction side of the evaporator 9 detect the temperature Tin and humidity RHi of the evaporator suction air. Is in the inside air mode, the temperature and humidity of the evaporator intake air are substantially the same as the vehicle interior temperature Tr detected by the internal air sensor 34 and the vehicle interior humidity RHr detected by the vehicle interior humidity sensor 33. The detection values of the sensor 34 and the vehicle interior humidity sensor 33 may be used as the temperature and humidity of the evaporator intake air to perform compressor control of each embodiment.
[0175]
Further, the wet bulb temperature Twe of the evaporator suction air is the evaporator outlet temperature Te in the period (2) in FIG. 25B, and the evaporator outlet temperature Te in the period (2) is from the compressor 1 in the ON state. Since the temperature reaches after a predetermined time (for example, 30 seconds) has elapsed after switching to the OFF state, instead of calculating the wet bulb temperature Twe based on the temperature Tin and the humidity RHi of the evaporator suction air, the compressor 1 After switching from the ON state to the OFF state, the evaporator outlet temperature Te after a lapse of a predetermined time may be estimated as the wet bulb temperature Twet. According to this, it is possible to cope with a case where the inside / outside air suction mode is the outside air mode and no outside air humidity sensor is provided.
[0176]
In the above-described embodiment, the case where the temperature sensor 32 that detects the evaporator blown air temperature Te is used as the temperature sensor that detects the evaporator temperature has been described. However, as the temperature sensor that detects the evaporator temperature, the evaporator It is possible to use a temperature sensor that detects the fin temperature or the like.
[0177]
Moreover, in said embodiment, although ON-OFF control of the compressor 1 at the time of operation | movement of the vehicle engine 4 (at the time of vehicle travel) was demonstrated, the eco-run vehicle which stops the vehicle engine 4 automatically at the time of a stop, or vehicle In a hybrid vehicle equipped with both an engine and an electric motor for traveling and stopping the vehicle engine when the vehicle is stopped, the present invention may be applied to compressor ON-OFF control when the vehicle is stopped. In this case, the control of the present invention can satisfactorily balance extending the compressor OFF period when the vehicle is stopped and suppressing the generation of odor.
[Brief description of the drawings]
FIG. 1 is an overall system diagram of a first embodiment of the present invention.
FIG. 2 is a flowchart showing an overall outline of air conditioning control according to the first embodiment;
FIG. 3 is a flowchart showing compressor control according to the first embodiment.
FIG. 4 is a characteristic diagram of a target evaporator temperature for room temperature control according to the first embodiment.
FIG. 5 is a characteristic diagram of a target evaporator temperature for humidity control according to the first embodiment.
FIG. 6 is a characteristic diagram of a target evaporator temperature for window glass antifogging according to the first embodiment.
FIG. 7 is an operation explanatory diagram of compressor control according to the first embodiment.
FIG. 8 is a flowchart showing compressor control according to a second embodiment.
FIG. 9 is an operation explanatory diagram of compressor control according to the second embodiment.
FIG. 10 is a flowchart showing compressor control according to a third embodiment.
FIG. 11 is an operation explanatory diagram of compressor control according to the third embodiment.
FIG. 12 is a flowchart showing compressor control according to a fourth embodiment.
FIG. 13 is an operation explanatory diagram of compressor control according to the fourth embodiment.
FIG. 14 is a flowchart showing compressor control according to a fifth embodiment.
FIG. 15 is an operation explanatory diagram of conventional compressor control corresponding to the fifth embodiment.
FIG. 16 is an operation explanatory diagram of compressor control according to the fifth embodiment.
FIG. 17 is a flowchart showing compressor control according to a sixth embodiment.
FIG. 18 is a flowchart showing compressor control according to a seventh embodiment.
FIG. 19 is a flowchart showing compressor control according to an eighth embodiment.
FIG. 20 is an operation explanatory diagram of compressor control according to an eighth embodiment.
FIG. 21 is an operation explanatory diagram of conventional compressor control corresponding to the eighth embodiment.
FIG. 22 is a flowchart showing compressor control according to a ninth embodiment.
FIG. 23 is an operation explanatory diagram of compressor control according to the ninth embodiment.
FIG. 24 is an operation explanatory diagram of compressor control according to the ninth embodiment.
FIG. 25 is an explanatory diagram showing the relationship between compressor intermittent control, evaporator blowing temperature behavior, and odor generation mechanism in the prior art.
FIG. 26 is a moist air diagram used for explaining the prior art and the present invention.
FIG. 27 is a flowchart showing compressor control according to an eleventh embodiment.
FIG. 28 is a characteristic diagram showing the behavior of the evaporator outlet temperature during the intermittent operation mode of the eleventh embodiment.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Compressor, 4 ... Vehicle engine, 9 ... Evaporator, 32 ... Evaporator blowing temperature sensor, 39 ... Evaporator suction air temperature sensor, 40 ... Evaporator suction air humidity sensor.

Claims (17)

An evaporator (9) for cooling the air blown into the passenger compartment;
A compressor (1) for compressing and discharging the refrigerant that has passed through the evaporator (9);
Temperature detecting means (32) for detecting the temperature of the evaporator (9);
In a vehicle air conditioner comprising compressor control means (S9) for intermittently controlling the operation of the compressor (1) according to the evaporator temperature detected by the temperature detection means (32).
The compressor (1) is stopped for a first predetermined time (t1) when the condition for generating odor from the evaporator (9) is satisfied, and is sufficiently shorter than the first predetermined time (t1). During the second predetermined time (t2) which is time, the intermittent operation mode for operating the compressor (1) is executed,
When the number of executions of the intermittent operation mode is equal to or greater than a predetermined number of times, it is determined whether the evaporator temperature is equal to or lower than the wet bulb temperature of the intake air of the evaporator (9),
When the evaporator temperature is lower than the wet bulb temperature, the compressor (1) is operated so that the evaporator temperature is lower than the wet bulb temperature and higher than the dew point temperature of the suction air. Control intermittently,
Further, when it is determined that the evaporator temperature is higher than the wet bulb temperature, the operation of the compressor (1) is intermittently controlled so that the evaporator temperature is maintained at the target evaporator temperature at the normal time. vehicle air conditioner, wherein the to Turkey. 2. The vehicle air conditioner according to claim 1 , wherein the normal target evaporator temperature is determined based on at least a temperature necessary for controlling a temperature of air blown into the passenger compartment. 3. By determining the conditions under which the generation of condensed water and the drying of condensed water are repeated on the surface of the evaporator (9) with the intermittent operation of the compressor (1), the odor is emitted from the evaporator (9). air-conditioning system according to claim 1 or 2, characterized in that to determine that corresponding to the generated condition. Based on the state of the intake air of the evaporator (9) and the target evaporator temperature for intermittently controlling the operation of the compressor (1), the generation of condensed water on the surface of the evaporator (9) air-conditioning system according to claim 3, characterized in that to determine the conditions under which drying of the condensed water is repeated. Conditions under which the generation of condensed water and the drying of condensed water are repeated on the surface of the evaporator (9) when the target evaporator temperature is in the vicinity of the wet bulb temperature and dew point temperature of the suction air of the evaporator (9) The vehicle air conditioner according to claim 4 , wherein the vehicle air conditioner is determined to correspond to the above. A temperature sensor (39) for detecting the temperature of the intake air of the evaporator (9) and a humidity sensor (40) for detecting the humidity of the intake air are provided, and the intake air detected by both sensors (39, 40) The vehicle air conditioner according to any one of claims 1 to 5 , wherein the wet bulb temperature is calculated based on temperature and suction air humidity. The inside air mode in which room air is sucked into the evaporator (9), to any one of claims 1 to 5, characterized in that to calculate the wet bulb temperature on the basis of the vehicle interior temperature and vehicle compartment humidity The vehicle air conditioner described. In the outside air mode where outside air is sucked into the evaporator (9), the compressor (1) is stopped from the operating state, and the evaporator temperature after the stop state has passed for a predetermined time is referred to as the wet bulb temperature. The vehicle air conditioner according to any one of claims 1 to 5 , characterized in that: An evaporator (9) for cooling the air blown into the passenger compartment;
A compressor (1) for compressing and discharging the refrigerant that has passed through the evaporator (9);
Temperature detecting means (32) for detecting the temperature of the evaporator (9);
In a vehicle air conditioner comprising compressor control means (S9) for intermittently controlling the operation of the compressor (1) according to the evaporator temperature detected by the temperature detection means (32).
The compressor control means (S9) calculates a first calculation means (S160) for calculating the wet bulb temperature of the intake air of the evaporator (9), and calculates a dew point temperature of the intake air of the evaporator (9). A second calculating means (S170) and a determining means (S180) for determining whether or not a condition for generating odor from the evaporator (9) is satisfied,
The determination means (S180) the evaporator (9) when the odor is determined to meet the conditions arising from the can, the wet-bulb temperature of the evaporator temperature is calculated by the first calculating means (S160) The vehicle air conditioner is characterized in that the operation of the compressor (1) is intermittently controlled below so that the temperature is higher than the dew point temperature calculated by the second calculation means (S170) . After the compressor (1) is stopped, when the evaporator temperature rises to the wet bulb temperature calculated by the first calculation means (S160) or a temperature lower than the wet bulb temperature by a predetermined temperature, the compressor (1 The vehicle air conditioner according to claim 9 , wherein the vehicle air conditioner is returned to an operating state. The determination means (S180) determines the conditions under which the generation of condensed water and the drying of condensed water are repeated on the surface of the evaporator (9) with the intermittent operation of the compressor (1). The vehicle air conditioner according to claim 9 or 10 , wherein it is determined that a condition for generating odor from the evaporator (9) is satisfied. The determination means (S180) is based on the state of the intake air of the evaporator (9) and the target evaporator temperature for intermittently controlling the operation of the compressor (1). air-conditioning system according to claim 11, characterized in that to determine the conditions under which drying occurs when condensed water condensed water is repeated at the surface of the. The determination means (S180) is when the target evaporator temperature is near the wet bulb temperature calculated by the first calculation means (S160) and the dew point temperature calculated by the second calculation means (S170). and the evaporator (9) air-conditioning system according to determined that the drying of the condensed water and the generation of condensed water will meet the conditions repeated in claim 12, wherein the surface of the. A temperature sensor (39) for detecting the temperature of the intake air of the evaporator (9) and a humidity sensor (40) for detecting the humidity of the intake air;
Said first calculating means (S160), the two sensors (39, 40) based on the detected intake air temperature and intake air humidity of claims 9 to 13, characterized in that to calculate the wet bulb temperature by The vehicle air conditioner as described in any one. The said 1st calculation means (S160) calculates the said wet bulb temperature based on vehicle interior temperature and vehicle interior humidity at the time of the inside air mode in which vehicle interior air is suck | inhaled by the said evaporator (9). Item 14. The vehicle air conditioner according to any one of Items 9 to 13 . The first calculating means (S160) is configured to stop the compressor (1) from an operating state in an outside air mode in which outside air is sucked into the evaporator (9), and after the predetermined time has passed. The vehicle air conditioner according to any one of claims 9 to 13 , wherein the evaporator temperature is calculated as the wet bulb temperature. First determining means (S120) for determining a first target evaporator temperature necessary for controlling the temperature of the air blown into the passenger compartment;
Second determining means (S130) for determining a second target evaporator temperature necessary for maintaining the humidity in the passenger compartment within a comfortable range;
A third determining means (S140) for determining a third target evaporator temperature required for defrosting the window glass;
Finally the fourth determining means (S150) claims 1 and having a to 8 and claims is determined as the target evaporator temperature the lowest temperature among the first to third target evaporator temperature The vehicle air conditioner according to any one of 12 and 13 .

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