JP3456021B2 - Vehicle air conditioner - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is equipped with a blower for driving two fans with one motor, and is capable of heating operation provided with an air passage that blows to the upper half of the occupant and the window glass and an air passage that blows to the feet of the occupant. Air conditioners for electric vehicles that consume energy to generate heat for heating, or hot water heaters that use engine cooling water, such as diesel vehicles and lean vehicles that have high engine thermal efficiency and low hot water temperatures. It is suitable for use in an air conditioner for a burn engine vehicle.

[0002]

BACKGROUND OF THE INVENTION When two fans are driven by one motor to generate an air flow in each of two passages, the two fans are generally formed in the same shape and the same size. Since the two fans are driven by one motor, they have the same blowing ability. However, when the two fans generate airflow in the passages having different ventilation resistances, or when the suction resistances that guide the air to the two fans are different, a difference in air flow amount occurs in the two passages. On the contrary, when the two passages have the same ventilation resistance, the two passages cannot have different air flow ratios.

As a technique for solving this problem, the applicant of the present application has proposed the technique of Japanese Patent Application No. 5-44133 (not a conventional technique). The technique proposed by the applicant of the present application changes the shapes and sizes of the two fans to realize the required air volume ratio in the two passages.

[0004]

However, since the technique proposed by the applicant fixes the air volume ratio of the two passages, it cannot be applied when there is a request to change the air volume ratio of the two passages. It was This will be specifically described by using a vehicle air conditioner capable of indoor heating using two passages. When heating, the air inside the vehicle (inside air) is sucked into the duct, reheated, and blown out again into the vehicle interior, so that the heating amount of the air is kept low, and it is possible to heat the vehicle interior with a small heating capacity. . However, the increase in humidity discharged by the passengers causes the window glass to become cloudy. Therefore, in the conventional air conditioner, in order to prevent fogging of the window glass (especially the windshield) during heating, the outdoor air (outside air)
Is sucked into the duct and heated, and is blown to the foot outlet and the defroster outlet. However, in this conventional technique, a large heating capacity is required because the indoor air is heated by heating the outside air having a low temperature and blowing it out into the room.

Therefore, the applicant of the present application has proposed the technique disclosed in Japanese Patent Application No. 5-41549 (not the conventional technique) and the technique disclosed in Japanese Patent Application Laid-Open No. 6-40236 in order to solve the above problems. . The technology proposed by the applicant is
At the time of heating, the outside air with low humidity is blown out from the defroster outlet and the face outlet, and the inside air with a high temperature and a small heating load is blown out from the foot outlet to prevent fogging of the window glass and reduce the heating capacity at the same time. This is a technology that was designed.

According to the technique proposed by the applicant of the present application, the amount of outside air blown from the defroster outlet and the face outlet during heating and the amount of inside air blown from the foot outlet are controlled at a predetermined ratio to prevent fogging of window glass. It is a technology that achieves both reduction of heating capacity. In this proposed technique, the window glass may be fogged due to a decrease in outside air temperature and an increase in indoor humidity. In this case, it is desirable to increase the amount of outside air with low humidity, suppress the amount of inside air with high humidity, and prevent fogging of the window glass. vice versa,
It is less likely that the window glass will be fogged due to an increase in outside air temperature and a decrease in indoor humidity. In this case, it is desired to suppress the amount of introduced outside air having a low temperature and a large heating load, and increase the amount of introduced indoor air having a high temperature and a small heating load to reduce the heating capacity.

However, in the prior art, as described above, the air flow rate ratio of the two passages is fixed, and therefore, when the air flow rate of one passage is increased or decreased, the air flow rate of the other passage is also increased or decreased. Therefore, the outside air amount cannot be increased to decrease the inside air amount, and conversely, the outside air amount cannot be decreased to increase the inside air amount, and thus the above-described demand cannot be satisfied.

[0008]

It is an object of the present invention to provide a blower for driving two first and second fans with one motor, and a first air passage and a first air passage to which an external air flow is mainly supplied from the first fan. Air quality (ratio of inside air and outside air) supplied to each of the second air passages to which the internal airflow is mainly supplied from the two fans
And an air conditioner for a vehicle capable of supplying the required air flow rates to the first air passage and the second air passage.

[0009]

[Means for Solving the Problems] [Means for Claim 1] An air conditioner for a vehicle according to the present invention is provided so as to be able to introduce outdoor air, and introduces a first fan for generating a first air flow and indoor air. A fan that is provided so as to include a second fan that generates a second air flow, and one motor that simultaneously drives the first fan and the second fan, and the first air flow that the first fan generates can be introduced. provided, toward the windshield first air passage comprising a defroster air outlet for blown air, provided to be introduced into the second air flow generated in the second fan, blown air toward the feet of the passenger A duct including a second air passage having a foot outlet, a first heating unit disposed in the first air passage for heating air passing through the first air passage, and a duct disposed in the second air passage. ,Previous The second heating means for heating the air passing through the second air passage.

The duct includes a first introduction passage for introducing the first air flow generated by the first fan, and the second introduction passage.
A second introduction passage for introducing the second air flow generated by the fan,
The first air flow passing through the first introduction passage is branched into the first air passage and the second air passage, and the second air flow passing through the second introduction passage is divided into the second air passage and the second air passage. The air quality variable door is provided so as to reduce the opening area of one of the first introduction passage and the second introduction passage that branches into one air passage. Further, the motor is controlled by a motor control unit that increases the rotation speed of the motor according to a decrease in the opening area of the first introduction passage or the second introduction passage by the air quality variable door.

[Means of Claim 2] In the vehicle air conditioner of Claim 1, the first fan is provided so as to be able to switch between outdoor air and indoor air and introduced, and the first air passage and the first air passage. When only indoor air is supplied to the two air passages, only the indoor air is introduced to the first fan, and the air quality variable door does not reduce the opening areas of the first introduction passage and the second introduction passage. Is characterized by.

[0012]

[Operation and Effect of the Invention] [Operation of Claim 1] When the first fan introduces the outside air to heat the interior of the vehicle, the first fan passes through the first air passage by the outside air of low humidity (first The airflow) is supplied, and the outside airflow (first airflow) heated by the first heating means is blown out from the defroster outlet of the first air passage, and the relatively warm outside airflow (first airflow) causes the windshield to move. Prevent fogging or give passengers a feeling of heating. A relatively warm internal airflow (second airflow) in the vehicle compartment is supplied to the second air passage by the second fan, and the internal airflow (second airflow) heated by the second heating unit (second airflow) is supplied.
Airflow) blows from the foot outlet of the second air passage to the feet of the occupant to heat the feet of the occupant. That is, at this time, the heating air is blown out from the low-humidity outside air from the first air passage to prevent fogging of the window glass, and the warm air inside the room is reheated from the second air passage. Can be kept low.

When the outside air temperature decreases, or when the indoor humidity rises due to an increase in the number of passengers, that is, the window glass is fogged (or easily fogged).
Then, by the air quality variable door, the internal air flow (second air flow)
Reduces the opening area of the second introduction passage through which Second
By reducing the opening area of the introduction passage, the proportion of the internal air flow (second air flow) introduced into the room is reduced. As a result, the proportion of the outside airflow (first airflow) in the total amount of air blown out into the room increases. However, if only the amount of the internal airflow (second air flow) introduced decreases, the total amount of air blown out into the room decreases and the flow rate of the external airflow (first air flow) introduced into the room does not increase. Therefore, the motor control means increases the rotation speed of the motor according to the amount of decrease in the opening area of the second introduction passage by the air quality variable door. As a result, the total amount of air blown out into the room can be kept constant, and the outside airflow (first airflow) supplied into the room can be increased.

When the outside air temperature rises or the indoor humidity decreases due to a decrease in the number of passengers, that is, when the window glass does not fog, the air quality variable door allows
The opening area of the first introduction passage through which the outside air flow (first air flow) passes is reduced. External airflow (first airflow) introduced into the room by reducing the opening area of the first introduction passage
The ratio of will decrease. As a result, the ratio of the internal air flow (second air flow) to the total amount of air blown out into the room increases. However, if only the amount of introduction of the outside airflow (first air flow) is decreased, the total amount of air blown out into the room is decreased, and the flow rate of the inside airflow (second air flow) introduced into the room is not increased. Therefore, the motor control means increases the rotation speed of the motor according to the amount of decrease in the opening area of the first introduction passage by the air quality variable door. As a result, it is possible to keep the total amount of air blown into the room constant and increase the internal airflow (second air flow) supplied to the room.

[Effect of Claim 1] As described in the above operation, when the window glass is fogged (or easily fogged), the air quality variable door is used. By decreasing the opening area of the second introduction passage and increasing the rotation speed of the motor by the motor control means, the outside air flow (first air flow) having a low humidity blown into the room is increased, and the inside air having a high humidity is increased. It is possible to reduce the air flow (second air flow) and suppress the occurrence of fogging on the window glass.

On the contrary, when the window glass does not fog, the temperature is lowered by reducing the opening area of the first introduction passage by the air quality variable door and increasing the rotation speed of the motor by the motor control means. It is possible to reduce the energy required for heating by reducing the external air flow (first air flow) having a large heating load and increasing the internal air flow (second air flow) having a high temperature and a small heating load.

[Operation of Claim 2] When the outside air temperature rises or the indoor humidity decreases due to a decrease in the number of passengers, that is, when the window glass does not fog, the first
Only the inside air with a small heating load is supplied to the air passage and the second air passage, and the energy required for heating is kept small.
At this time, only the inside air is supplied to the first fan. Then, both the first introduction passage and the second introduction passage guide the inside air to the first air passage and the second air passage. At this time, the air quality variable door does not reduce the opening area of the first introduction passage and the second introduction passage. Therefore, the internal airflow (first airflow) generated by the first fan and the internal airflow (second airflow) generated by the second fan are not affected by the flow of air by the air quality variable door. It is guided to the passage and the second introduction passage.

[Effect of Claim 2] As described in the above operation, the effect of claim 2 is that only the inside air is guided to the first fan, and the air quality variable door is provided in the first introduction passage and the second introduction passage. By not reducing the opening area, the internal airflow generated by the first fan (first air flow) and the internal airflow generated by the second fan (second air flow) are blocked by the air quality variable door. Absent. As a result, it is possible to suppress the drive energy of the blower to be small in the mode in which only the inside air is blown out into the room.

[0019]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, a vehicle air conditioner of the present invention will be described based on an embodiment shown in the drawings. [Configuration of Embodiment] FIG. 1 is a schematic configuration diagram of an entire vehicle air conditioner 1. (Description of Duct 2) The vehicle air conditioner 1 is installed in, for example, an electric vehicle, and includes a duct 2 that forms an air passage for sending air toward the interior of the vehicle. A blower 3 is connected to one end of the duct 2 to generate an air flow toward the room inside the duct 2. Further, the other end of the duct 2 is provided with a blowout passage through which the air passing through the duct 2 is blown toward each part in the room.

The blower 3 has a motor 4 whose rotational speed changes in accordance with the amount of electric power supplied thereto, a centrifugal first fan 5 and a second fan 6 mounted on both shafts of the motor 4 and driven, and the first fan 5. And a first scroll case 7 and a second scroll case 8 that house the second fan 6. The motor 4 is energized via the motor drive circuit 4a. In addition, the first scroll case 7
The suction port 9 is provided with an inside / outside air switching means 10 for switching between the inside air and the outside air for introduction into the first fan 5. The inside / outside air switching means 10 includes an inside air introduction port 11 that opens into the vehicle interior to introduce the inside air, and an outside air introduction port 12 that communicates with the outside of the vehicle interior to introduce the outside air. Then, the inside / outside air switching means 1
0 is provided with a plate-shaped inside / outside air switching door 13 capable of closing either the inside air inlet 11 or the outside air inlet 12. The inside / outside air switching door 13 is rotationally driven by a servomotor 14 with one side as an axis. Depending on the rotating position of the inside / outside air switching door 13, the air introduced by the first fan 5 is switched between the inside air and the outside air. Switch with. On the other hand, the second scroll case 8 is provided so that only the inside air is introduced from the second suction port 15.

The first fan 5 is provided on the upper side upstream of the duct 2.
A first introduction passage 21 that guides the generated first air flow into the duct 2 is provided. A second introduction passage 22 that guides the second air flow generated by the second fan 6 into the duct 2 is provided on the lower side of the upstream side of the duct 2.

The first introduction passage 21 is provided upstream of the duct 2.
By adjusting the flow rate of the first air flow (outside air flow or inward air flow) introduced from the and the flow rate of the second air flow (inner air flow) introduced from the second introduction passage 22. 31
Also, an air quality variable door 23 that leads to the second air passage 32 is provided. Details of the air quality variable door 23 will be described later.

The duct 2 downstream of the air quality variable door 23
A cooler 24 that cools the air flowing in the duct 2 is arranged inside, and a heater 25 that heats the air flowing in the duct 2 is arranged downstream of the cooler 24. The cooler 24 is provided over the entire surface of the duct 2 so that all the air flowing in the duct 2 passes through. Also,
A heating bypass passage 26 that bypasses the heater 25 is provided in the duct 2. The heating bypass passage 26 is opened and closed in the heating bypass passage 26.
A cool door 27 for changing the opening degree of 6 is provided. The cool door 27 is driven by a servo motor 28.

A first air passage 31 through which the first air flow (outer airflow or inner airflow) mainly passing through the first introduction passage 21 is guided is provided on the upper side in the duct 2, and the lower side in the duct 2 is provided. Is provided with a second air passage 32 through which the second air flow (inner airflow) that has mainly passed through the second introduction passage 22 is provided, and the first air passage 31 and the second air passage 32 are partitioned by the partition wall 33. Has been done.

The heater 25 is arranged in the duct 2 while penetrating the partition wall 33. Then, the first air passage 31
The heater 25 arranged inside serves as the first heating means of the present invention for heating the air passing through the first air passage 31, and the heater 25 arranged inside the second air passage 32 is Two
It serves as the second heating means of the present invention for heating the air passing through the air passage 32. That is, the first and second heating means of the present invention are constituted by the heater 25 in this embodiment.

The partition wall 33 downstream of the heater 25 has a first
A communication port 34 for communicating the air passage 31 and the second air passage 32 is provided. The communication port 34 is provided with a communication door 35 that opens and closes the communication port 34, and the communication door 35 is driven by a servomotor 36.

Next, at the downstream end of the duct 2, the air that has passed through the first air passage 31 is fed to the instrument panel 41.
(Refer to FIG. 2) Defroster outlet 42 provided on the upper part
A wide blower outlet 44 (an example of a face outlet) and a spot outlet 45 (an example of a face outlet) provided on the occupant side of the instrument panel 41 for passing air that has passed through the defroster outlet passage 43 and the first air passage 31 ) Is provided, and a foot outlet passage 48 that guides the air passing through the second air passage 32 to a foot outlet 47 provided at the foot of the occupant is provided. Then, the outlets 4 are provided in the openings leading to the outlet passages 43, 46, 48.
A defroster door 49, a face door 50, and a foot door 51 that control the air flow to 2, 44, 45, and 47 are provided. These doors 49, 50, and 51 are servo motors 52 and 53, respectively. Driven by 54.

Here, as shown in FIG. 2, the wide air outlets 44 are formed in a horizontally long shape at two locations, that is, the upper portion of the meter panel 55 on the driver's side and the instrument panel 41 on the passenger side. With the opening, these two wide outlets 44
To a small air volume (for example, 200 m ³ / h, wind speed 3 m / se
It is provided to gently blow out the wind of c). In addition, the spot outlet 45 is the instrument panel 4
There are two openings in the center of 1 and one in each of the left and right sides of the instrument panel 41, for a total of four openings, and a large air volume (for example, 400 m ³ /
h, a wind speed of 10 m / sec) is provided so as to gently blow out the wind. Small air volume (wide outlet 44)
And the large air volume (spot air outlet 45) are switched by driving the spot / wide switching door 56 provided in the face air outlet passage 46 by the servo motor 57.

The cool door 27, the communication door 35, and the spot / wide switching door 56 are operated as shown in Table 1 below according to each blowing mode.

[Table 1] In addition, * 1 shown in Table 1 is linearly controlled between open and closed during dehumidification. Further, * 2 is controlled to be opened during dehumidification.

Further, in Table 1, in the "FACE / spot" mode, the air is blown from the spot outlet 45, and in the "FACE / wide" mode, the wide outlet 4 is used.
4 blows the wind, and in the "B / L" mode, blows the wind from both the wide air outlet 44 and the foot air outlet 47,
In the "FOOT" mode, the air is blown from the foot outlet 47 and the defroster outlet 42 at a ratio of 80:20,
In the "FOOT / DEF" mode, air is blown from the foot outlet 47 and the defroster outlet 42 at a ratio of 50:50, and in the "DEF" mode, the defroster outlet 42.
The defroster door 49, the face door 50, and the foot door 51 are switched so that the wind blows from the.

The variable air quality door 23 is provided at the branch portion 61 upstream of the partition wall 33, and as shown in FIG. 1, the opening area of the first air passage 31 is set to 0 from the state of 100% opening. 2 Opening degree that makes the opening area of the air passage 32 zero -100%
It is possible to change continuously up to the state of
It is rotationally driven by 2. And the air quality variable door 23
Is the opening degree of 100% (the first introduction passage 21 is fully closed), the second air flow (internal air flow) that has passed through the second introduction passage 22.
Is supplied to both the first air passage 31 and the second air passage 32, and conversely, when the air quality variable door 23 has an opening degree of -100% (the second introduction passage 22 is fully closed), the first introduction passage 21
The first air flow (outside air flow or inward air flow) that has passed through is supplied to both the first air passage 31 and the second air passage 32. Further, when the variable air quality door 23 does not reduce the opening area of both the first air passage 31 and the second air passage 32 (see the solid line in FIG. 1), the opening degree is 0%. All of the first air flow (outer air flow or inner air flow) that has passed through the first introduction passage 21 is guided to the first air passage 31,
All the second air flow (internal airflow) that has passed through the introduction passage 22 is guided to the second air passage 32.

The branch portion 61 is a communication portion between the first air passage 31 and the second air passage 32, which is provided upstream of the partition wall 33. Airflow or internal airflow) is branched into the first air passage 31 and the second air passage 32, and the second airflow (internal airflow) passing through the second introduction passage 22 is divided into the second air passage 32 and the first air passage 32.
It branches to the air passage 31.

(Explanation of Refrigeration Cycle 71) The cooler 24 of this embodiment is a refrigerant evaporator of the refrigeration cycle 71, and the heater 25 of this embodiment is a refrigerant condenser of the refrigeration cycle 71. An example of the refrigeration cycle 71 adopted in the present embodiment,
It is shown in the refrigerant circuit diagram of FIG. Refrigeration cycle 71 of the present embodiment
Is a refrigerant evaporator (cooler 2
4), in addition to the refrigerant condenser (heater 25), the outdoor heat exchanger 72, the refrigerant compressor 73, the heating decompression device 74, the cooling decompression device 75, the accumulator 76, and a flow path for switching the flow direction of the refrigerant. The switching means 77 is provided.

The outdoor heat exchanger 72 is provided outside the duct 2.
The outdoor fan 81 is provided for performing heat exchange between the outside air and the refrigerant, and forcibly exchanging heat between the outside air and the refrigerant. Refrigerant compressor 7
Reference numeral 3 is for sucking, compressing and discharging the refrigerant, and is driven by an electric motor 82. The refrigerant compressor 73 is arranged integrally with the electric motor 82 in the sealed case. The electric motor 82 that drives the refrigerant compressor 73 is the inverter 8
The rotation speed is variable under the control of the electric motor 82, and the refrigerant compressor 73 is changed by the change in the rotation speed of the electric motor 82.
The refrigerant discharge capacity of is changed. In this embodiment, the blowout temperature is controlled by changing the capacity of the refrigerant compressor 73 due to the change in the rotation speed.

The heating decompression device 74 is an expansion valve for decompressing and expanding the refrigerant flowing into the outdoor heat exchanger 72 during heating operation. The cooling decompression device 75 is a capillary tube that decompresses and expands the refrigerant flowing into the refrigerant evaporator (cooler 24) during the cooling operation.

The refrigerant flow path switching means 77 switches the flow direction of the refrigerant during the cooling operation, the heating operation, the cold dehumidifying operation, the high temperature dehumidifying operation, and the defrosting operation. Specifically, a four-way valve 85 that switches the discharge direction of the refrigerant compressor 73 between the outdoor heat exchanger 72 and the refrigerant condenser (heater 25), and an electromagnetic valve that bypasses the refrigerant evaporator (cooler 24) during heating operation. An on-off valve 86, an electromagnetic on-off valve 87 that bypasses the heating decompression device 74 during low-temperature dehumidifying operation, an electromagnetic on-off valve 88 that bypasses the cooling decompression device 75 during high-temperature dehumidifying operation, and a check valve 89 that regulates the flow direction of the refrigerant. Consists of.

The flow path switching means 77 (four-way valve 85,
The electromagnetic on-off valves 86, 87, 88) operate as shown in the following Table 2 depending on the cooling operation, the heating operation, the cold dehumidifying operation, the high temperature dehumidifying operation, and the defrosting operation.

[Table 2]

Next, the flow of the refrigerant in the refrigerating cycle 71 during the cooling operation, the heating operation, the cold temperature dehumidifying operation, the high temperature dehumidifying operation, and the defrosting operation will be shown. During cooling operation,
The refrigerant discharged from the refrigerant compressor 73 flows in the order of the four-way valve 85, the outdoor heat exchanger 72, the heating decompression device 74, the refrigerant evaporator (cooler 24), the accumulator 76, and the refrigerant compressor 73. As a result, the high-temperature refrigerant discharged from the refrigerant compressor 73 is radiated by the outdoor heat exchanger 72 to be liquefied and condensed, and the liquefied refrigerant is evaporated in the refrigerant evaporator (cooler 24) and the refrigerant evaporator (cooler 24). ) Is cooled.

During the heating operation, the refrigerant discharged from the refrigerant compressor 73 is supplied to the four-way valve 85 → refrigerant condenser (heater 25) → heating decompression device 74 → outdoor heat exchanger 72 → electromagnetic on-off valve 86.
(Refrigerant evaporator bypass)-> accumulator 76-> refrigerant compressor 73. As a result, the high temperature refrigerant discharged from the refrigerant compressor 73 radiates heat in the refrigerant condenser (heater 25), and the air passing through the refrigerant condenser (heater 25) is heated.

During the low temperature dehumidifying operation, the refrigerant discharged from the refrigerant compressor 73 is supplied to the four-way valve 85 → refrigerant condenser (heater 25) →
The electromagnetic on-off valve 87 (the heating decompression device 74 bypass) → the outdoor heat exchanger 72 → the cooling decompression device 75 → the refrigerant evaporator (cooler 24) → the accumulator 76 → the refrigerant compressor 73 in this order. As a result, the high-temperature refrigerant discharged from the refrigerant compressor 73 dissipates heat in the refrigerant condenser (heater 25) and the outdoor heat exchanger 72, and is liquefied and condensed. This reduces the amount of air heated by the refrigerant condenser (heater 25). On the other hand, the liquefied and condensed refrigerant is evaporated in the refrigerant evaporator (cooler 24) to cool the air passing through the refrigerant evaporator (cooler 24). As a result, a small amount of air that has passed through the refrigerant evaporator (cooler 24) and has been dehumidified is heated by the refrigerant condenser (heater 25), so that dehumidification tends to be at a low temperature.

During the high temperature dehumidifying operation, the refrigerant discharged from the refrigerant compressor 73 is supplied to the four-way valve 85 → refrigerant condenser (heater 25) →
Heating decompression device 74-> outdoor heat exchanger 72-> solenoid valve 8
8 (cooling decompression device 75 bypass) → refrigerant evaporator (cooler 24) → accumulator 76 → refrigerant compressor 73. As a result, the high-temperature refrigerant discharged from the refrigerant compressor 73 radiates heat in the refrigerant condenser (heater 25), and the amount of air heated by the refrigerant condenser (heater 25) increases. On the other hand, the liquefied and condensed refrigerant is evaporated in the outdoor heat exchanger 72 and the refrigerant evaporator (cooler 24). This reduces the amount of air cooled by the refrigerant evaporator (cooler 24). As a result, the degree of cooling of the air in the refrigerant evaporator (cooler 24) decreases, and the refrigerant condenser (heater 25) reheats the air, resulting in high temperature dehumidification.

During the defrosting operation, the refrigerant discharged from the refrigerant compressor 73 is supplied with the four-way valve 85 → refrigerant condenser (heater 25) → electromagnetic on-off valve 87 (heating decompressor 74 bypass) → outdoor heat exchanger 72. → Cooling decompression device 75 → Refrigerant evaporator (cooler 2
4) Flow in the order of: accumulator 76, refrigerant compressor 73. As a result, the high-temperature refrigerant discharged from the refrigerant compressor 73 dissipates heat in the refrigerant condenser (heater 25) and the outdoor heat exchanger 72, and is liquefied and condensed. As a result, the frost attached to the outdoor heat exchanger 72 is melted and defrosted.

Next, the outdoor fan 81 of the outdoor heat exchanger 72.
The control of will be described. The outdoor fan 81 of this embodiment
As shown in FIG. 3, according to the operation mode of the refrigeration cycle 71 and the output data of each sensor described later, the high speed rotation “Hi”, the low speed rotation “Lo”, and the stop “OFF” are switched. Specifically, for example, in the cooling mode, the outside air temperature T
It becomes "Hi" when am is 25 ℃ or higher, and "Lo" when it is 22 ℃ or lower.
Becomes In the heating mode, when the outside air temperature Tam is 13 ° C. or lower, it becomes “Hi”, and when it is 16 ° C. or higher, it becomes “Lo”. In the low temperature dehumidification mode, the refrigerant discharge pressure Pr of the refrigerant compressor 73, the after-condensing temperature Tc, the target outlet temperature TAO-the after-condensing temperature Tc are determined in the priority order of Hi>Lo> OFF. For example, if the refrigerant discharge pressure Pr is 19 kgf / cm ² G or more,
Whatever the value of Tc, TAO-Tc,
i ”. Similarly, if TAO-Tc is −2 ° C. or less, it is always “Hi” even if the refrigerant discharge pressure Pr is lower than 19 kgf / cm ² G. In the high temperature dehumidification mode, when the refrigerant discharge pressure Pr of the refrigerant compressor 73, the after-condensing temperature Tc, the target outlet temperature TAO-the after-condensing temperature Tc is 0 ° C. or less, “OFF”
It becomes "Hi" at 2 ℃ or more. And 1 ℃ →
It becomes "Lo" in the range of 2 ℃ and 1 ℃ → 0 ℃.

(Explanation of the control device 91) The motor 4 of the blower 3, the inverter 84 of the electric motor 82 for driving the refrigerant compressor 73, the outdoor fan 81, the four-way valve 85, the electromagnetic opening / closing valves 86, 87, 88, the inside and outside The controller 91 controls the energization of electric components such as the servo motor 14 that drives the air switching door 13, the servo motor 62 that drives the variable air quality door 23, and the servo motors that drive the other doors. The control device 91 is mainly composed of a microcomputer, and includes a CPU 92, a RAM 93 for temporarily storing each data, a ROM 94 for storing each control program and control numerical values, and an A / D for digitally converting an input signal.
A converter 95, an I / O port 96, a crystal oscillator 97 that generates a reference signal, and the like are provided, and power is supplied from a battery 98, which is a vehicle-mounted power source, through an ignition switch 99.

The control device 91 measures the environmental conditions for controlling the operation of the vehicular air conditioner 1 by measuring the inside air temperature Tr and the outside air temperature T.
The outside air temperature sensor 102 that detects am, the solar radiation sensor 103 that detects the solar radiation amount Ts, the after-evaporation sensor 104 that detects the cold air temperature (after-evaporation temperature) Te immediately after the refrigerant evaporator (cooler 24), the refrigerant condenser ( A post-conversion sensor 105 for detecting a warm air temperature (post-conversion temperature) Tc immediately after the heater 25),
A discharge pressure sensor 106 for detecting the discharge pressure Pr of the refrigerant compressor 73 is provided.

The control device 91 controls the energization of each electric component based on the operation signal of the operation panel 111 (see FIG. 4) operated by the occupant and the output data of each of the sensors 101 to 106. As shown in FIG. 2, the operation panel 111 is installed in a room where the operability is good, such as the center of the instrument panel 41. The operation panel 111 is provided with a temperature setter 112 that sets the temperature inside the room. The temperature setter 112 includes a temperature decrease key 113 for decreasing the set temperature and a temperature increase key 114 for increasing the set temperature. Then, the temperature down key 113
And the set temperature sensation Sset set by the temperature increase key 114 is the display unit 11 in which a plurality of light emitting elements are arranged in a line.
It is displayed in 5. On the operation panel 111, the temperature setter 1
12, an ON-OFF switch 116 for instructing start and stop of the air conditioner, a dehumidifying switch 117 for giving a dehumidifying instruction,
A defroster switch 118 that blows air from the defroster outlet, a rear defogger switch 119 that gives an instruction to energize the rear heating wire, and an air quality adjusting lever 120 that adjusts the air quality (ratio of inside air to outside air) into the vehicle interior are provided. .

The air quality adjusting lever 120 is moved to the first inside air indicating position N of outside air amount: inside air amount = 15: 85 from the left end inside air circulation indicating position N0 (outside air amount: inside air amount = 0: 100).
1, 2nd inside air indication position N of outside air amount: inside air amount = 25: 75
2, central auto instruction position AUTO, outside air amount: inside air amount =
50:50 second outside air indicating position G2, outside air amount: inside air amount =
It is a lever that can be set to the outside air introduction instruction position G0 (outside air amount: inside air amount = 100: 0) at the right end via the first outside air instruction position G1 at 75:25, depending on the setting position of the air quality adjusting lever 120. The opening degree of the air quality variable door 23 is controlled by the control device 9
By the operation of the air quality control means provided in No. 1, it is controlled as shown in Table 3 below. Further, the applied voltage of the motor 4 of the blower 3 is controlled according to the set position of the air quality adjusting lever 120 by the operation of the motor control means provided in the control device 91 as shown in Table 3 below.

[0048]

[Table 3] In Table 3, * 1 indicates that the inside / outside air switching means is automatically adjusted at this designated position. Also, * 2 shows the ratio in this position in the heating mode.

Next, an example of the operation of the control program for air conditioning will be described with reference to the flowchart of FIG. First, in step S100, initial values of counters, flags, etc. used for the subsequent arithmetic processing are set. Then, the process proceeds to step S110, where the set temperature sensation Sset input by operating the temperature setting device 112 is read, and each sensor 1
Output data 01 to 106 (inside air temperature Tr, outside air temperature T
am, solar radiation Ts, post-evaporation temperature Te, post-condensation temperature Tc)
Read.

Next, in step S120, a target indoor set temperature Tset is obtained from the set temperature sensation Sset, the outside air temperature Tam, and the amount of solar radiation Ts by the following equation (1). Tset = f (Sset, Tam, Ts) = Tset '+ ΔTam + ΔTs (1) where Tset' = 25 + 0.4Sset ...
(A) of ΔTam = (10−Tam) / 20 (FIG. 6B)
Reference ΔTs = −Ts / 1000 ... (c) of FIG.
reference

After calculating the set temperature Tset in step S120, the process proceeds to step S130 to set temperature Tse in the passenger compartment.
The amount QAO of blown heat required to maintain at t
Calculate by formula. QAO = K1 * Tset-K2 * Tr-K3 * Tam-K4 * Ts + C (2) Here, K1, K2, K3, and K4 are coefficients, and C is a constant.

After calculating the heat quantity of blow-out QAO in step S130, the process proceeds to step S140, and it is determined whether the air-conditioning state at this time is a steady state or a transient state as follows. First, the temperature difference | Tset-Tr | between the set temperature Tset and the inside air temperature Tr is calculated, and this | Tset-Tr |
Is determined to be equal to or smaller than a predetermined value δ (eg, δ = 3 °). Then, if | Tset−Tr | ≦ δ, it is determined to be a steady state, and if | Tset−Tr |> δ, it is determined to be a transient state.

When it is determined in step S140 that the engine is in the steady state, the process proceeds to step S141, and as shown in FIG. 7, the blowout air volume VB of the motor 4 of the blower 3 is obtained from the required blowout heat quantity QAO in the steady state. Target air flow rate VAO
And Next, the process proceeds to step S142, and as shown in FIG. 7, the target outlet temperature TAO is obtained from the required outlet heat amount QAO in the steady state.

On the other hand, if it is determined in step S140 that the engine is in the transient state, the process proceeds to step S143, and the target blown air volume VAO of the motor 4 of the blower 3 during the transition is calculated based on the following equation (3). VAO = VB + ΔV (3) Here, VB is the required blow-out heat quantity Q in the steady state shown in FIG. 7.
This is obtained from the blown air volume characteristic of the motor 4 of the blower 3 with respect to AO. Further, ΔV is a corrected air volume, which is obtained from the corrected air volume characteristic set for Tr-Tset shown in FIG.

Next, the routine proceeds to step S144, where the target blowout temperature TAO at the time of transition is obtained from the following equation (4). TAO = QAO / (Cp · γ · V2) + Tr = 3.57 × QAO / V2 + Tr (4) where Cp is the specific heat of air and γ is the specific gravity of air (2
5 ° C.).

When the process of step S142 or step S144 is completed, the process proceeds to step S150, and it is determined whether or not the operation in the dehumidifying mode is performed. The condition for performing this dehumidification mode is that the dehumidification switch 117 is ON,
This means that the two conditions of TAO> T0 (T0 is, for example, 5 ° C.) are satisfied. If these two conditions are satisfied, the determination at step S150 becomes YES and the process proceeds to step S161. The condition is that TAO is at a predetermined temperature T0 (5
This is because dehumidification can be sufficiently performed in the cooling mode when the temperature is lower than (° C).

If the determination in step S150 is no, the process moves to step S160. In this step S160, it is first determined whether or not the air quality adjusting lever 120 is set to the automatic instruction position.

When it is determined that the automatic instruction position is set, it is determined whether or not the target outlet temperature TAO ≦ inside air temperature Tr. i) The result of this determination is that the target outlet temperature TAO ≤ inside air temperature Tr
In this case, the inside / outside air switching door 13 sets the inside / outside air switching means 10 to the inside air mode, and the opening degree of the air quality variable door 23 is set to 0%. ii) When the determination result is the target outlet temperature TAO> inside air temperature Tr, the inside / outside air switching means 1 is operated by the inside / outside air switching door 13.
0 is set to the outside air mode and the air quality variable door 2
Set the opening of 3 to 0%.

When it is determined that the air quality adjusting lever 120 is not set to the automatic instructed position, as shown in Table 3, the opening is set according to the instructed position of the air quality adjusting lever 120. The inside / outside air switching door 13 and the air quality variable door 23 are operated.

When the process of step S160 is completed, the process proceeds to step S170 and the operation mode of the refrigeration cycle 71 is determined as follows. First, the intake air temperature Tin introduced from the inside air inlet 11 and the outside air inlet 12 is calculated by the following equation (5). Tin = α · Tam + (1−α / 100) · Tr (5) Here, α / 100 represents the introduction ratio of outside air. Also, α
Is a value set as shown in Table 3, and α = 0 in the inside air mode.

Next, the target outlet temperature TAO and the intake air temperature Ti
The temperature difference Tm from n is calculated by the following equation (6). Tm = TAO-Tin (6) Then, when Tm ≧ + θ (for example, θ = 2 °), the heating mode is set, when Tm ≦ −θ, the cooling mode is set, and −θ <Tm
When <+ θ, the refrigerant compressor 73 is stopped.

After determining the operation mode in step S170, the process proceeds to step S180, in which the blowing mode is "FACE (spot)" or "FACE (wide)" based on the target blowing temperature TAO and the target blowing air amount VAO of the blower 4. ,
"B / L", "FOOT", "FOOT / DEF",
It is determined to be either "DEF".

After determining the blowout mode in step S180, the process proceeds to step S190, and the various control values determined as described above are output to each electric device. Then, the process returns to step S110 to repeat the above process. Here, in order to realize the target blown air volume VAO obtained in steps S141 and S143, the applied voltage V of the motor 4 of the blower 3 is set as shown in FIG.
Of the air quality variable door 23 (the opening of the air quality variable door 23 is 0%) and the applied voltage V according to the opening of the air quality variable door 23 by the operation of the motor control means. Are the constants (a1, a2, a3,
a4). Note that a1> 1, a4> a
3>a2> 1.

Here, in order to produce the target outlet temperature TAO required to maintain the vehicle interior at the set temperature Tset, the refrigerant compressor 73 is driven by inverter control, and the refrigeration cycle 71 is operated in the operation mode determined in step S160. To drive. At this time, in the cooling mode, the capacity of the refrigerant compressor 73 is feedback-controlled by PI control or fuzzy control for the post-evaporator temperature Te, and in the heating mode, PI control is performed for the post-conversion temperature Tc. Alternatively, the capacity of the refrigerant compressor 73 is feedback-controlled by fuzzy control.

When the PI control is performed, the temperature deviation En is first calculated by the following equation (7). En = TAOn-Tn (7) Here, the subscript n of each variable indicates the n-th sample value,
TAOn represents the target outlet temperature determined in steps S142 and S144, Tn represents the post-evaporation temperature Te in the cooling mode, and Tn represents the post-conversion temperature Tc in the heating mode.

Next, the frequency change amount Df of the inverter 84
n is calculated by the following equation (8). Dfn = Kp {(En-En- ₁ ) + t / TI * En} (8) where Kp is a proportional gain, t is a sample time, and TI is
Is the integration time. From the frequency change amount Dfn, the target frequency fn of the inverter 84 is calculated by the following equation (9). fn = f _n-1 + Dfn (9) Then, the target frequency fn is output to the inverter 84 to control the rotation speed of the refrigerant compressor 73.

On the other hand, if it is determined in step S150 that the operation in the dehumidifying mode is to be performed, that is, if the dehumidifying switch 117 is on and the two conditions of TAO> T0 are satisfied, the process proceeds to step S161. This step S16
At 1, first, it is determined whether or not the air quality adjusting lever 120 is set to the automatic instructed position.

When it is determined that the automatic instruction position is set, the inside / outside air switching door 13 sets the inside / outside air switching means 10 to the inside air mode, and the opening degree of the air quality variable door 23 is set to 0%. . When it is determined that the air quality adjusting lever 120 is not set to the automatic instruction position, as shown in Table 3, the inside / outside air switching is performed so that the opening degree is set according to the instruction position of the air quality adjusting lever 120. The opening degree of the door 13 and the air quality variable door 23 are operated.

When the process of step S161 is completed, the process proceeds to step S210, and the intake air temperature Tin is changed to the next (10)
Calculate by formula. Tin = α · Tam + (1-α / 100) · Tr (10)

Next, in step S220, it is determined whether the dehumidification mode should be switched to the low temperature dehumidification mode or the high temperature dehumidification mode, as shown in FIG. 10, based on the intake air temperature Tin and the target outlet temperature TAO. . In both of these dehumidification modes, the post-evaporation temperature Te = Thc (for example, Thc =
The rotation speed of the refrigerant compressor 73 is controlled by the inverter 84 so that it becomes 5 ° C.).

After the dehumidifying mode is determined in step S220, the process proceeds to step S230, and the blowing mode is "FACE (spot)" or "FACE (wide)" based on the target blowing temperature TAO and the target blowing air amount VAO of the blower 3. ,
"B / L", "FOOT", "FOOT / DEF",
It is determined to be either "DEF".

After the blowout mode is determined in step S230, the process proceeds to step S240 and the opening degrees of the cool door 27 and the communication door 35 are determined as follows. The opening degrees of the cool door 27 and the communication door 35 are different in the FACE mode and other modes.

When not in the FACE mode, the communication door 35
And the opening SWc of the cool door 27
Is calculated based on the following equation (11).

[Equation 1] The opening degree SW of the cool door 27 calculated by the equation (11)
As shown in FIG. 11, the opening degree of c increases as the target outlet temperature TAO decreases.

On the other hand, in the FACE mode, the opening degree of the communication door 35 and the opening degree SWc of the cool door 27 are as follows.
Is controlled as follows. i) In the case of TAO ≧ (ψ1 · Te + Tc) / (ψ1 + 1), as in the case of FACE mode and below, the communication door 3
5 is fully opened and the opening degree SWc of the cool door 27
Is calculated by the above equation (11). Therefore, as shown in FIG. 11, the opening degree SWc of the cool door 27 increases as the target outlet temperature TAO decreases.

I) TAO <(ψ 1 · Te + Tc) / (ψ
In the case of (1 +1), the opening degree SWc of the cool door 27 is fully opened, and the opening degree SWs of the communication door is set to (1)
2) Calculate based on the equation.

[Equation 2] The opening degree SWs of the communication door 35 calculated by the equation (12)
As shown in FIG. 12, the opening degree decreases as the target outlet temperature TAO decreases.

Then, the process proceeds to step S250, and the various control values determined as described above are output to each electric device. Then, the process returns to step S110 to repeat the above process. In this process as well, like step S190, step S
141, the applied voltage V of the motor 4 of the blower 3 is determined according to the voltage characteristic and the blowing mode of FIG. 9 (the opening of the air quality variable door 23) in order to realize the target blowing air amount VAO. 0%), and the applied voltage V is constant (a1, a2, a3, a4) shown in Table 3 according to the opening degree of the air quality variable door 23 by the operation of the motor control means.
Is corrected by. Note that a1> 1, a4>a3> a
2> 1 relationship.

[Effects of Embodiment] In the vehicle air conditioner 1 of this embodiment, the blower 3 that drives the first fan 5 and the second fan 6 by the single motor 4 allows the defroster outlet 42 and the wide outlet to be discharged. 44 (an example of a face air outlet), a first air passage 31 leading to a spot air outlet 45 (an example of a face air outlet), and a second air passage 32 leading to a foot air outlet 47 are each provided with a predetermined air volume. By generating and adjusting the opening degree of the air quality variable door 23, it is possible to adjust the air quality (ratio of inside air and outside air) supplied to each of the first air passage 31 and the second air passage 32. it can. Further, since the applied voltage of the motor 4 is corrected based on the opening degree of the air quality variable door 23, the air volume required for each of the first air passage 31 and the second air passage 32 does not decrease, and the first air passage 31 And a required air volume can be obtained from the second air passage 32 into the room.

Specifically, when the window glass is fogged (or easily fogged), the occupant operates the air quality adjusting lever 120 to the outside air introduction instruction position G0 side (fresh side). The air quality variable door 23 reduces the opening area of the second introduction passage 22 and increases the rotation speed of the motor by the motor control means. As a result, the low-humidity external airflow (first air flow) blown into the room increases and the high-humidity internal airflow (second air flow) decreases, so that it is possible to suppress the occurrence of fogging on the window glass.

On the contrary, when the window glass does not fog, the occupant operates the air quality adjusting lever 120 to the inside air circulation instructing position N0 side (return side) so that the air quality variable door 23 is moved to the first introduction passage 21. The opening area of the motor is reduced and the rotation speed of the motor is increased by the motor control means. As a result, the outside airflow (first airflow) having a low temperature and a large heating load decreases, and the internal airflow (second airflow) having a high temperature and a small heating load increases, so that the energy required for heating can be kept small. You can

On the other hand, in this embodiment, the air quality adjusting lever 1
When the occupant has set 20 to the inside air circulation instruction position N0 (when only 100% inside air is introduced into the room), the inside / outside air switching means 1
0 is set to the inside air mode, the opening degree of the air quality variable door 23 is set to 0%, and the opening areas of the first introduction passage 21 and the second introduction passage 22 are not reduced. As a result, the internal airflow (first airflow) generated by the first fan 5 and the internal airflow (second airflow) generated by the second fan 6 are not obstructed by the air quality variable door 23. As a result, when only the inside air is blown into the room, the voltage applied to the blower 3 is suppressed,
It is possible to reduce power consumption in an electric vehicle.

[Second Embodiment] FIG. 13 shows a second embodiment of the present invention, and is a schematic diagram of the vehicle air conditioner 1. The vehicle air conditioner 1 of this embodiment includes a first fan 5 and a second fan 5.
The fan 6, the first scroll case 7, and the second scroll case 8 are integrated.

[Modification] In the above embodiment, a plate-shaped door in which one opening area of the first introduction passage or the second introduction passage is reduced by rotation is shown as an example of the air quality variable door. Other door means such as a film door or a tubular door may be used. Although the example in which the outside air and the inside air are selected and taken in by the first fan has been shown, it may be provided so that only the outside air is introduced. In this case, when only the inside air is introduced into both the first air passage and the second air passage, it can be achieved by setting the opening area of the first introduction passage to 0 by the air quality variable door. Further, although an example in which the air quality variable door and the inside / outside air switching door are operated independently has been shown, they may be provided so as to be interlocked.

Although an example in which the air conditioner is mounted on an electric vehicle has been shown, it may be mounted on an automobile driven by an internal combustion engine, particularly a diesel engine or a lean burn engine. The configuration is not limited to the refrigeration cycle shown in the present embodiment, and other refrigeration cycle configurations may be appropriately changed and used. Although the refrigerant condenser is shown as an example of the heater, other heaters such as a hot water heater core, an electric heater, and a combustion heater may be used. Further, although the example in which the first heater and the second heater are integrally provided is shown, they may be provided separately.

The first air passage is provided above the duct, and the second air passage is provided.
Although the example in which the air passage is provided on the lower side of the duct is shown, the positional relationship and the like are not limited. For example, the first air passage is provided on the lower side of the duct, and the second air passage is provided on the upper side of the duct. Alternatively, the first air passage and the second air passage may be provided in parallel in the horizontal direction. In the above embodiment, the blowing temperature, the blowing mode, and an example of automatically adjusting the blowing air amount have been shown, but instead of the temperature setting device, an operating means such as a lever or a photographing device for manually changing the blowing temperature is provided, and the operating means The rotation speed of the refrigerant compressor can be changed according to the operating state, the operation means for manually setting the blowout mode is provided to change the blowout mode, and the operation means for manually setting the airflow is provided to change the airflow. It may be provided to do so.

[Brief description of drawings]

FIG. 1 is a schematic configuration diagram of an air conditioner (first embodiment).

FIG. 2 is a front view of an instrument panel.

FIG. 3 is a table showing the operation of an outside air fan.

FIG. 4 is a front view of an operation panel.

FIG. 5 is a flowchart illustrating the operation of a control program.

FIG. 6 is a graph used for air conditioning control.

FIG. 7 is a graph for determining a blown air volume and a target blown temperature.

FIG. 8 is a graph for determining a corrected air volume.

FIG. 9 is a graph for determining an applied voltage of a blower.

FIG. 10 is a graph for determining a dehumidification mode.

FIG. 11 is a graph for determining the opening degree of the cool door.

FIG. 12 is a graph for determining the opening degree of a communication door.

FIG. 13 is a schematic configuration diagram of an air conditioner (second embodiment).

[Explanation of symbols]

1 Air conditioner for vehicle 2 ducts 3 blower 4 motor 5 First fan 6 second fan 21 first introduction passage 22 2nd introduction passage 23 Air quality variable door 25 Heater (first heating means, second heating means) 31 First air passage 32 Second air passage 42 Defroster outlet 44 Wide outlet (face outlet) 45 Spot outlet (face outlet) 47 foot outlet 61 Branch

─────────────────────────────────────────────────── ─── Continuation of the front page (58) Fields surveyed (Int.Cl. ⁷ , DB name) B60H 1/00-3/06

Claims (2)

(57) [Claims] 1. A first fan capable of introducing outdoor air to generate a first air flow, a second fan capable of introducing indoor air to generate a second air flow, the first fan, and A blower composed of one motor that drives the second fan at the same time, and provided so that the first air flow generated by the first fan can be introduced.
A first air passage having a defroster outlet for blowing air toward the windshield, a second air flow provided by the second fan, and a foot for blowing air toward the feet of an occupant. Second with outlet
A duct having an air passage, a first heating means arranged in the first air passage and heating air passing through the first air passage, and a duct arranged in the second air passage and passing through the second air passage In a vehicle air conditioner including a second heating unit that heats air, the duct includes a first introduction passage for introducing a first air flow generated by the first fan, and a duct generated by the second fan. 2nd introduction passage which introduces 2 air flows, 1st air passage which passed the 1st introduction passage branches to the 1st air passage and the 2nd air passage, and 2nd which passed the 2nd introduction passage A branching portion for branching an air flow into the second air passage and the first air passage, and an air quality variable door provided so as to reduce an opening area of one of the first introduction passage and the second introduction passage, The motor is Serial with decreasing the opening area of the air quality variable door by said first introduction passage and the second introduction passage, the air conditioner for a vehicle, characterized in that it is controlled by a motor control means for increasing the rotational speed of the motor. 2. The vehicle air conditioner according to claim 1, wherein the first fan is provided so as to be able to switch between outdoor air and indoor air and introduced into the first air passage and the second air passage. A vehicle characterized in that when only air is supplied, only indoor air is introduced into the first fan, and the air quality variable door does not reduce the opening areas of the first introduction passage and the second introduction passage. Air conditioner.