JP3993617B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner, and more particularly to an air conditioner having a dehumidifying throttle device.

  As a conventional air conditioner, when performing a dehumidifying operation for lowering the humidity, the air cooled mainly by an evaporator is reheated by an electric heater, or the method is reheated by the condensation heat of a refrigeration cycle. Things are known. When these two systems are compared particularly from the viewpoint of energy saving, the former system is superior to the latter system because it consumes much power.

  Examples of the refrigeration cycle in which the air cooled during the dehumidifying operation is reheated by the refrigeration cycle itself are disclosed in JP-A-60-181559, JP-A-2-183376, JP-A-3-31640, and There is one described in Japanese Utility Model Publication No. 51-18059.

  Among them, in JP-A-60-181559, a compressor, a four-way valve, an outdoor heat exchanger, an expansion device, an indoor heat exchanger, etc. are sequentially connected by refrigerant piping, and the indoor heat exchanger is further divided into two parts. A cycle configuration is disclosed in which a dehumidifying throttle device for dehumidifying operation and a two-way valve that bypasses the dehumidifying throttle device are provided in parallel between them. During the dehumidifying operation, the two-way valve is closed and the refrigerant is allowed to flow to the dehumidifying throttle device, so that the upstream side of the divided indoor heat exchanger is a condenser and the downstream side is an evaporator, and the indoor air flow is evaporated. The dehumidifying operation is performed by flowing from the condenser to the condenser, cooling and dehumidifying with the evaporator, and then heating again with the condenser to reduce the humidity without significantly reducing the temperature.

  JP-A-2-183377 further uses a two-way valve with a small hole as a dehumidifying throttle device, and has a cycle configuration in which the indoor heat exchanger is divided into two vertically, and the upper indoor heat exchanger is a condenser during dehumidifying operation. The lower indoor heat exchanger is an evaporator, and the indoor air flow is allowed to flow in parallel to these indoor heat exchangers. Cooling and dehumidification with an evaporator and heating with a condenser can prevent humidity from getting too cold. Enables dehumidifying operation to lower.

  In Japanese Patent Laid-Open No. 3-31640, in addition to the cycle configuration of the above-mentioned Japanese Patent Laid-Open No. 60-181559, even when a four-way valve is switched to a heating cycle by providing a flow path switching means comprising four check valves. The air flow is made to flow from the evaporator to the heater on the indoor side so that a powerful heating and dehumidifying operation can be performed. The amount of heat released from the outdoor heat exchanger is controlled by controlling the rotational speed of the outdoor fan, and the amount of air heated by the indoor heat exchanger is adjusted so that the room temperature becomes the set temperature. Moreover, it is described in a publicly known example that the outdoor fan is weakly operated when the outside air temperature is 22 ° C. or lower, and weakly operated when the outdoor temperature is 22 ° C. or higher.

  FIG. 30 shows a cycle configuration in Japanese Utility Model Publication No. 51-18059, and FIG. 31 shows an operation list of each part. The cycle configuration of FIG. 30 is provided with two compressors, but is basically the same as the cycle configuration described in Japanese Patent Laid-Open No. 60-181559. In the operation method shown in FIG. 31, the outdoor fan and the compressor perform control according to the operation function, but do not perform control according to the outdoor temperature or the like. For example, the outdoor fan is stopped at a low speed in the air-cooling dehumidifying operation and stopped in the air-warming dehumidifying operation. One compressor is operated during the dehumidifying operation.

  Recently, dehumidifying operation has been used for multiple purposes. For example, (1) Comfortable dehumidification operation that performs dehumidification while maintaining the set room temperature when the temperature is not so high in the rainy season or autumn rainy season, and (2) Low noise and no airflow in hot and humid nights and dawns , To reduce the humidity without reducing the temperature so that you can have a comfortable sleep, good night, laziness dehumidification, (3) keep relative humidity at around 50% to prevent mold and mite breeding, There are mite prevention dehumidification operation, and (4) laundry dehumidification operation that is used to dry laundry that dries in the house in the rainy season and autumn rainy season. However, the above four known publications do not consider the operation method for the purposes of use (1) to (4).

  In JP-A-3-31640, the rotational speed of the outdoor fan is controlled to adjust the air heating amount in the indoor heat exchanger in the dehumidifying operation. However, nothing is said about the operation of the compressor. In particular, it is insufficient for application to many purposes such as the above (1) to (4). Further, the outdoor fan is controlled in two stages, that is, a weak operation when the outdoor temperature is 22 ° C. or lower and a weak operation when the outdoor temperature is 22 ° C. or higher. However, this control is insufficient as a control for the outdoor temperature.

  In addition, air conditioners often perform cooling operation or heating operation in addition to dehumidifying operation. However, when two divided indoor heat exchangers are connected in series as described in the above four known publications, cooling operation is performed. In the heating operation, the refrigerant flow path of the indoor heat exchanger becomes long. Especially in the cooling operation using two indoor heat exchangers as the evaporator, the pressure loss of the refrigerant flow in the indoor heat exchanger increases, If the air flow and the refrigerant flow do not become opposite flows, or if a sufficient subcooling cannot be obtained during heating operation, the performance of the refrigeration cycle will deteriorate. In this case, in Japanese Patent Laid-Open No. 2-183776, at least one of the refrigerant flow paths in the indoor heat exchanger divided into two paths is used to reduce pressure loss, but this is still insufficient. Other known publications do not specifically address this problem.

  Furthermore, in a small air conditioner such as a room air conditioner, there is a limit to the size of an indoor unit (also referred to as an indoor unit). Under such limited conditions, the relationship between the piping configuration of the indoor heat exchanger and the air flow, etc. It is necessary to improve the heat transfer performance in the indoor heat exchanger as much as possible in each operation of dehumidification, cooling and heating, and keep the performance of the refrigeration cycle sufficiently high.

  Further, in Japanese Utility Model Publication No. 51-18059, the outdoor fan is stopped during the heating and dehumidifying operation, so that the temperature of the electrical components on the outdoor unit (also referred to as outdoor unit) side becomes high and the service life is shortened. Also, since the outdoor fan is not controlled by the outdoor temperature, the amount of heat dissipated from the outdoor heat exchanger (waste heat amount) changes depending on the outdoor temperature, and the indoor blowing air temperature and dehumidification amount cannot be controlled sufficiently, or the compressor operates at a constant speed. Since it is a single unit, it is not possible to sufficiently control the amount of dehumidification based on the difference between the set humidity and the room humidity.

  An object of the present invention is to provide an air conditioner capable of dehumidifying operation for various purposes.

In order to achieve the above object, the present invention provides a compressor, an outdoor heat exchanger, an outdoor fan, an indoor heat exchanger having a first indoor heat exchanger and a second indoor heat exchanger, and a dehumidifying operation. A dehumidifying and throttling device that functions as a throttling device, and an indoor fan, wherein the compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttling device, and the second indoor heat exchanger The compressor, the outdoor heat exchanger, the first indoor heat exchanger, and the second indoor heat exchanger are connected in this order during cooling operation, and the compressor and the second indoor heat exchange are connected during heating operation. In the air conditioner connected in the order of the heat exchanger, the first indoor heat exchanger, and the outdoor heat exchanger, the air volume of the indoor fan is variable, the operation mode during the dehumidifying operation, and the air volume of the indoor fan in There first air volume, wind the outdoor fan The is a variable, and laundry drying mode for drying the laundry, the A operation mode during dehumidifying operation, the second air volume air volume is less than the first flow rate of the indoor fan, the outdoor fan It is equipped with a comfortable dehumidifying operation mode in which the air volume is variable and the person feels comfortable .

  According to the present invention, an air conditioner capable of dehumidifying operation for various purposes can be provided.

  Hereinafter, each embodiment of the present invention will be described in detail with reference to the drawings by taking an air conditioner attached to a building as an example.

  An embodiment according to the present invention will be described with reference to FIGS. FIG. 1 is a diagram showing a refrigeration cycle and control system according to this embodiment, FIG. 2 is a flowchart of an operation mode, FIG. 3 is a flowchart of an operation method in a dehumidifying operation with a low air volume, and FIG. 4 is a dehumidifying operation method with a high air volume. It is a flowchart.

  The air conditioner of the present embodiment is configured as follows. In FIG. 1, 1 is a compressor, 2 is a four-way valve that is switched when switching between operating states such as cooling and heating, 3 is an outdoor heat exchanger, 4 is a main throttle device through which refrigerant flows during cooling and heating operations, 5 Is a two-way valve that is provided in parallel with the main throttle device 4 and allows the refrigerant to flow during the dehumidifying operation, 6a and 6b are divided into two indoor heat exchangers, and 7 is between the indoor heat exchangers 6a and 6b. A dehumidifying throttle device that is provided in series and through which refrigerant flows during dehumidifying operation, 8 is provided in parallel with the dehumidifying throttle device 7 between the indoor heat exchangers 6a and 6b, and a two-way valve for flowing the refrigerant during cooling and heating operations, 9 is an accumulator for preventing liquid return to the compressor, 10 is an outdoor fan, 11 is an outdoor fan motor, 12 is an indoor fan, 13 is an indoor fan motor, and 14 and 15 are arrows indicating the outdoor and indoor wind directions, respectively. , 16 is a control unit, 7 a temperature detecting means such as a temperature sensor for detecting the room temperature, 18 humidity detecting means, such as a humidity sensor for detecting a room humidity, shows respectively 21, 22, 23 wiring. The compressor 1 is capable of capacity control, and the outdoor fan 10 and the indoor fan 12 are capable of capacity control, that is, air flow control. In particular, recently, the compressor 1 and the fan motors 11 and 13 employ a rotational speed control method in which the rotational speed is continuously changed, and the ability can be finely controlled.

  In the above-described cycle configuration, during the cooling operation, the two-way valve 5 is closed and the two-way valve 8 is opened, whereby the refrigerant is circulated as indicated by the solid line arrow, and the outdoor heat exchanger 3 is connected to the condenser and the indoor heat. Indoor cooling is performed using the exchangers 6a and 6b as an evaporator. During heating operation, the four-way valve 2 is switched, the two-way valve 5 is closed, and the two-way valve 8 is opened, whereby the refrigerant is circulated as indicated by the dashed arrows, and the indoor heat exchangers 6a and 6b are condensers and outdoor heat exchanges. The room 3 is heated using the apparatus 3 as an evaporator.

  Further, during the dehumidifying operation, the four-way valve 2 is switched in the same manner as in the cooling operation, and the two-way valve 5 is opened and the two-way valve 8 is closed, so that the refrigerant is shown in the dashed line in the compressor 1, the four-way valve 2, and the outdoor. The heat exchanger 3, the two-way valve 5, the indoor heat exchanger 6a, the dehumidifying throttle device 7, the indoor heat exchanger 6b, the four-way valve 2, the accumulator 9, and the compressor 1 are circulated in this order, and the outdoor heat exchanger 3 is upstream. The indoor heat exchanger 6a is set as a downstream condenser, and the indoor heat exchanger 6b is set as an evaporator. Then, when the indoor air is flown by the indoor fan 12 as indicated by the arrow 15, the air is cooled and dehumidified by the indoor heat exchanger 6b that acts as an evaporator, and then the downstream condenser, that is, the indoor that becomes the heater. It is heated again by the heat exchanger 6a and blown into the room. In this case, by further controlling the capacity of the compressor 1 and the air blowing capacity of the indoor fan 12 and the outdoor fan 10, the capacity of the evaporator 6b and the heater 6a can be adjusted. The air temperature can be controlled according to the purpose of use.

  By the way, as described above, dehumidifying operation has recently been used for multiple purposes. For example, (1) The so-called comfortable dehumidification operation that dehumidifies while keeping the set temperature during the rainy season or autumnal rainy season, etc., (2) There is no sense of airflow in a sultry night or dawn, and low noise Low-humidity, low-humidity dehumidification operation that reduces humidity without significantly lowering the temperature in the state, (3) Keeping the relative humidity at about 50% to prevent mold and mite breeding, so-called There are dehumidifying operation to prevent mold and mites, and (4) so-called laundry dehumidifying operation that is used when drying laundry that is dried in the house in the rainy season or autumn rainy season.

  Considering the operating conditions of the compressor, indoor fan, and outdoor fan in the dehumidifying operation for various purposes described above, the good night / summer dehumidifying operation has a low noise and low dehumidification amount. The air volume dehumidifying operation is necessary, and the laundry dehumidifying operation particularly requires a high air volume dehumidifying operation in which the airflow reaches a wide range and has a high drying capacity. In the comfortable dehumidifying operation and the mold / tick prevention dehumidifying operation, it is necessary to appropriately use the dehumidifying operation with the low air flow and the dehumidifying operation with the high air flow. Further, it is necessary to perform a cooling, isothermal, or heating operation according to the room temperature for the low air volume dehumidifying operation and the high air volume dehumidifying operation.

  The dehumidifying operation methods for various purposes described above will be described below with reference to FIG. 2 which is a flowchart of the operation mode. As shown in FIG. 2, when an instruction to start the dehumidifying operation (200) is issued by forced operation or automatic operation that detects indoor and outdoor temperature and humidity, the use mode selection (201) in the dehumidifying operation is performed. Is selected from among a comfortable dehumidifying operation (210), a dehumidifying operation for preventing mold and mites (220), a good night / lazy dehumidifying operation (230), a laundry dehumidifying operation (240), and the like. At this time, when the selection mode is not designated, a comfortable dehumidifying operation (210) mode is automatically selected.

First, in the comfortable dehumidifying operation (210), the temperature sensor 17 and the humidity sensor 18 detect the temperature and humidity of the room air (211) and set the desired room temperature and humidity (212). Next, a setting (213) of the blowing state of the indoor fan 12 is performed to determine whether to perform the dehumidifying operation with a low air volume or to perform the dehumidifying operation with a high air volume. Alternatively, the high air volume dehumidifying operation (215) is selected.
In addition, when performing comfortable dehumidifying operation, it is necessary to set the indoor temperature and humidity so that people can feel comfortable, but it is used as a thermal environment evaluation index such as PMV (predicted mean vote). In the case of control based on this thermal environment evaluation index, the thermal sensation is taken into account not only the room temperature and humidity but also the radiation temperature, wind speed, amount of clothes, and amount of activity. It is possible to automatically set the temperature and humidity in consideration of the season, clothes, activity, etc.

  In the mold and mite prevention dehumidifying operation (220), as in the case of the comfortable dehumidifying operation (210), the temperature sensor 17 and the humidity sensor 18 detect the temperature and humidity of the room air (221) and set the desired room temperature and humidity ( 222) is performed. Next, a setting (223) of the ventilation state of the indoor fan 12 is performed to determine whether to perform the dehumidifying operation with a low air volume or to perform the dehumidifying operation with a high air volume. Based on this setting (223), the low air volume dehumidifying operation (224) is performed. Alternatively, the high air volume dehumidifying operation (225) is selected. It is known that the relative humidity should be about 40 to 60% to prevent mold and mite breeding. Therefore, in the dehumidifying operation to prevent mold and mites, for example, the humidity is automatically reduced to about 50%. It may be fixed and set. By performing such a dehumidifying operation, the dehumidifying operation can be performed in a state where the perceived temperature can be maintained well.

  In the night / azalea dehumidifying operation (230), the temperature sensor 17 and the humidity sensor 18 detect the temperature and humidity of the room air (231) and set the desired room temperature and humidity (232). Next, when sleeping, especially at the beginning of sleep or in the morning, if the feeling of airflow or noise is high, it is difficult to sleep, so a low air volume dehumidifying operation (233) with the air blowing capacity of the indoor fan 12 lowered is performed. In addition, the approximate value of comfortable indoor temperature and humidity during sleep is known. For example, during the rainy season or in the hot and humid summer, it is better to reduce the humidity sufficiently without lowering the room temperature. become. Therefore, in the night / summer dehumidification operation, the indoor temperature and humidity may be automatically fixed and set to such values. Furthermore, this operation mode can be used as an automatic operation mode programmed in accordance with a human sleep pattern such as at the beginning of sleep, deep sleep, or when waking up in the morning.

  In the laundry dehumidifying operation (240), the temperature sensor 17 and the humidity sensor 18 detect the temperature and humidity of the room air (241) and set the desired room temperature and humidity (242). Next, when the laundry is dried, it is necessary that the air flow is spread over a wide range and the dehumidifying capacity is sufficiently high. Therefore, the high air volume dehumidifying operation (243) in which the blowing capacity of the indoor fan 12 is increased is performed. Also, the temperature and humidity during drying of the laundry can be set to be approximately constant, unlike the human experience that changes slightly. Accordingly, the room temperature and humidity can be automatically fixed and set even in the laundry dehumidifying operation.

  In the operation modes for each purpose shown in FIG. 2, the indoor temperature / humidity detection (211), (221), (231), (241), the indoor temperature / humidity setting (212), (222), (232), (242), indoor air blowing state setting (213) and (223) are not necessarily performed in this order, and can be arbitrarily set.

  In each of the purposes of use described above, the operation modes are roughly divided into a low air volume dehumidifying operation and a high air volume dehumidifying operation. The air conditioner itself is suitable for each mode of use, such as comfortable dehumidification operation, mold / tick prevention dehumidification operation, good night / medicated dehumidification operation, laundry dehumidification operation, etc. Can be used.

  In the low air volume dehumidifying operation and the high air volume dehumidifying operation described above, when the detected value of the room temperature is different from the set value, detection is performed according to this temperature difference ΔT (ΔT = detected room temperature−set room temperature). When the room temperature is higher and ΔT is positive, the air-cooling taste is almost equal, when both are almost equal and ΔT is near zero, the temperature is isothermal, and when the detected temperature is lower and ΔT is negative, the heating-like dehumidifying operation is performed. There is a need. These operating methods are described below.

  As can be seen from FIG. 3 showing the operation method in the low air volume dehumidifying operation (300), the indoor fan is first set to the low air volume operation (301). Next, the detected room temperature detected by the temperature sensor 17 in the room is compared with the set room temperature (302). If the temperature difference ΔT is positive, a low air volume cooling and dehumidifying operation (310) is performed. In this case, since the compressor 1 can obtain a sufficient dehumidifying capacity even if the capacity is reduced, the outdoor heat exchanger 3 is set to the low capacity operation (311) and further to perform the cooling operation. It is necessary to increase the heat radiation capacity of the outdoor fan 10 and increase the air blowing capacity of the outdoor fan 10 (312).

  When the temperature difference ΔT is substantially zero, a low air volume isothermal dehumidifying operation (320) is performed. In this operation, since the compressor 1 can obtain a sufficient dehumidifying capacity even if the capacity is lowered, the heat dissipation capacity in the outdoor heat exchanger 3 can be used for the low capacity operation (321) and the isothermal operation. It is necessary to set the heating capacity of the indoor heat exchanger 6a used as a heater to the air flow 15 to a medium level. For this purpose, the blowing capacity of the outdoor fan 10 is set to a medium (322). .

  When the temperature difference ΔT is negative, the low air volume heating and dehumidifying operation (330) is performed. In this operation, it is necessary to increase the heating capacity for the air flow 15 by the indoor heat exchanger 6a used as a heater by reducing the heat radiation amount in the outdoor heat exchanger 3. For this purpose, the blowing capacity of the outdoor fan 10 is reduced as much as possible, and the outdoor fan is stopped (332) as necessary. In addition, the compressor 1 can obtain a sufficient dehumidifying ability even if the capacity is reduced, but the capacity of the heater 6a increases as the capacity of the compressor 1 increases, and the heater 1 can be more heated. Accordingly, the capacity of the compressor 1 increases (331) according to the degree of heating.

Here, as a specific operation example of the low air volume dehumidifying operation, for example, a room air conditioner having a standard cooling capacity of 2.8 kW is used under conditions of indoor temperature and humidity of 24 ° C. and 60%, outdoor temperature and humidity of 24 ° C. and 80%. When the outdoor air flow is sufficiently reduced and the indoor air flow is about 2 m ³ / min, the air temperature is about 21 ° C. and the compressor is operated with the theoretical pushing amount of 0.98 m ³ / h. When the amount of pushing is 1.5 m ³ / h, a heating-like operation with a blowing temperature of about 27 ° C. can be achieved. In other words, it is possible to perform a warming dehumidifying operation in which the temperature of the air blown from the indoor unit is from room temperature to 3 ° C to room temperature + 3 ° C.

  In the low air volume dehumidifying operation described above, the capacity of the compressor 1 is set low because the amount of dehumidification is sufficient, but the present invention is not limited to this, and the capacity of the compressor may be increased. In this case, the input increases greatly, but the dehumidifying capacity gradually increases.

  Next, the operation method of the high air volume dehumidifying operation (350) will be described with reference to FIG. First, the indoor fan 12 is set to high air volume operation (351). Next, the detected room temperature detected by the temperature sensor 17 in the room is compared with the set room temperature (352), and if the temperature difference ΔT is positive, a high air volume air-cooled dehumidifying operation (360) is performed. In this operation, since the indoor fan 12 is in a high air flow operation, the compressor 1 is operated at a high capacity in order to obtain a sufficient dehumidifying capacity by lowering the evaporation temperature of the indoor heat exchanger 6b acting as an evaporator (361). Further, in order to make the operation cooler, it is necessary to increase the heat radiation capacity in the outdoor heat exchanger 3 and lower the heating capacity for the air flow 15 by the indoor heat exchanger 6a acting as a heater. For this reason, the ventilation capacity of the outdoor fan 10 is increased (362).

  When the temperature difference ΔT is substantially zero, a high air volume isothermal dehumidification operation (370) is performed. In this operation, the compressor 1 is set to the high capacity operation (371) for the same reason as the above-described cooling operation. Further, in order to achieve an isothermal operation, it is necessary to set the heat dissipation capability of the outdoor heat exchanger 3 to a medium level and to the heating capability of the indoor heat exchanger 6a acting as a heater to the air flow 15 to a medium level. For this purpose, the blowing capacity of the outdoor fan 10 is set to the middle (372). When the temperature difference ΔT is negative, the high air volume heating and dehumidifying operation (380) is performed. In this operation, the compressor 1 is set to the high-capacity operation (381) for the same reason as the above-described cooling operation and isothermal operation. Furthermore, in order to perform a heating-like operation, it is necessary to increase the heating capacity for the air flow 15 by the indoor heat exchanger 6a that acts as a heater by reducing the heat radiation amount in the outdoor heat exchanger 3. For this purpose, the blowing capacity of the outdoor fan 10 is reduced as much as possible, and the outdoor fan 10 is stopped (382) as necessary.

Here, as a specific operation example of the high air volume dehumidifying operation, for example, a room air conditioner with a standard cooling capacity of 2.8 kW is used under conditions of indoor temperature and humidity of 24 ° C. and 60%, outdoor temperature and humidity of 24 ° C. and 80%, If the outdoor air flow is sufficiently reduced and the indoor air flow is about 6 m ³ / min, the heating temperature may be reduced to about 26.5 ° C when the theoretical pushing amount of the compressor is 1.9 m ³ / h. it can. In other words, it is possible to perform a heating operation in which the blown air temperature of the indoor unit is up to room temperature + 3 ° C.

  By the way, in the high air volume dehumidifying operation described above, the input becomes large because the compressor 1 is set to the high capacity operation. FIG. 5 is a side sectional view showing the structure of the indoor unit that can solve the problem that this input becomes large, and FIG. 6 is a flowchart of the high air volume dehumidifying operation method in this case.

  In FIG. 5, 6a, 6b, and 12 are respectively the same as the cycle configuration shown in FIG. 1, and are a leeward indoor heat exchanger, an leeward indoor heat exchanger, and an indoor fan, respectively. Further, 31 is a suction grille, 32 is a casing on the back side forming a ventilation path, 33 is a dew receiving tray for receiving condensed water, 34 is a damper that can be opened and closed, and 35 is a ventilation path provided in the upper part of the casing 32. . With such a configuration, during the dehumidifying operation, the indoor heat exchanger 6b serves as an evaporator and the indoor heat exchanger 6a serves as a heater, and the indoor fan 12 is operated so that the room air is shown from the air flow 36 as indicated by an arrow. By flowing like the air flow 37, the air flow 36 passes through the suction grille 31, is cooled and dehumidified by the evaporator 6 b, heated by the heater 6 a, and then passes through the indoor fan 12 in the direction of the arrow. Blown out. Further, the condensed water generated in the evaporator 6b is once received by the dew receiving tray 33 and then discharged to the outside.

  Next, the method of high air volume dehumidification operation when the indoor unit shown in FIG. 5 is used will be described with reference to the cycle configuration shown in FIG. 1 and the flowchart shown in FIG.

  When the high air volume dehumidifying operation mode is selected (400), the suction damper 34 is first opened (401) as indicated by 34a, and the indoor fan 12 is operated (402) in a high air volume state. Next, the detected room temperature detected by the temperature sensor 17 shown in FIG. 1 is compared with the set room temperature (403), and if the temperature difference ΔT is positive, a high air volume cooling and dehumidifying operation (410) is performed. In this operation, the indoor fan 12 is operated with a high airflow, but this airflow is the sum of the airflow passing through the ventilation path 35 and the airflow passing through the indoor heat exchangers 6b and 6a, and the indoor heat exchangers 6b and 6a are connected to each other. The amount of air passing through becomes small, and even if the compressor 1 is operated at a low capacity (411), the evaporation temperature of the evaporator 6b is lowered and a sufficient dehumidifying capacity is obtained. Further, in order to make the air-cooling operation, it is necessary to increase the heat dissipating ability in the outdoor heat exchanger 3 and lower the heating ability for the air flow 36 by the indoor heat exchanger 6a acting as a heater. For this reason, the ventilation capacity of the outdoor fan 10 is increased (412).

  When the temperature difference ΔT is substantially zero, a high air volume isothermal dehumidification operation (420) is performed. In this operation, the compressor 1 is set to the low capacity operation (421) for the same reason as the above-described cooling operation. Furthermore, in this isothermal operation, it is necessary to moderate the heat radiation capacity in the outdoor heat exchanger 3 and to moderate the heating capacity for the air flow 36 by the indoor heat exchanger 6a acting as a heater. For this purpose, the blowing capacity of the outdoor fan 10 is set to the middle level (422).

  When the temperature difference ΔT is negative, the high air volume heating and dehumidifying operation (430) is performed. Even in this operation, the compressor 1 is set to the low-capacity operation (431) for the same reason as the above-described cooling operation and isothermal operation. Furthermore, in order to perform this heating-like operation, it is necessary to increase the heating capacity for the air flow 36 by the indoor heat exchanger 6a acting as a heater by reducing the heat radiation amount in the outdoor heat exchanger 3. For this purpose, the blowing capacity of the outdoor fan 10 is reduced as much as possible, and the outdoor fan 10 is stopped (432) as necessary.

  In FIG. 5, the low air volume dehumidifying operation can be performed in the same manner as the operation method shown in FIG. 3 by closing the damper 34. In FIG. 5, 34 is a damper that can be rotated and opened, but the damper is not limited to this, and any structure that can be opened and closed may be used. In the above description, the indoor temperature / humidity is detected by the procedure described with reference to FIG. 2. However, the present invention is not limited to this, and the comparison between the detected room temperature and the set room temperature in FIGS. 3, 4, and 6 ( 302), (352), and (403).

  Another embodiment according to the present invention is shown in FIGS. FIG. 7 is a configuration diagram showing the outdoor portion of the cycle of this embodiment, and FIG. 8 is a diagram showing a method of adjusting the heat radiation amount of the outdoor heat exchanger 3.

  The outdoor portion of the cycle shown in FIG. 7 corresponds to a portion 40 surrounded by a two-dot chain line in FIG. 1. In the cycle configuration shown in FIG. 1, the outdoor heat exchanger 3 is bypassed via the two-way valve 41. A bypass pipe 42 is provided. In FIG. 7, the same reference numerals as those in FIG. 1 denote the same parts.

  In the air conditioner of the present embodiment having the cycle configuration shown in FIG. 7, the operation method is almost the same as that in the cycle configuration shown in FIG. 1, but the low-air-volume heating-like dehumidification operation (330) shown in FIG. 3. Step 332 in FIG. 4, step 382 in the high air volume heating flavor dehumidification operation (380) shown in FIG. 4 and step 432 in the high air volume heating flavor dehumidification operation (430) shown in FIG. 6 corresponding to the structure of the indoor unit shown in FIG. The method of adjusting the heat radiation capacity of the outdoor heat exchanger 3 is different as follows.

  In the heating mode dehumidifying operation, in order to increase the heating capacity of the indoor heat exchanger 6a acting as a heater in the embodiment shown in FIG. 1 by the method of adjusting the heat radiation amount of the outdoor heat exchanger 3 shown in FIG. The ventilation capacity of the outdoor fan 10 is reduced as much as possible, or the outdoor fan 10 is stopped (501). Next, the room temperature is detected again and compared with the set room temperature (502). If the detected room temperature is lower than the set room temperature, the two-way valve 41 is opened (503). If the detected room temperature is not lower than the set room temperature, the setting is terminated (504). As a result, when the two-way valve 41 is opened in step 503, the indoor heat exchanger 6a in which most of the high-temperature and high-pressure refrigerant flow discharged from the compressor 1 acts as a heater without passing through the outdoor heat exchanger 3. Therefore, when the two-way valve 41 is closed and the outdoor fan 10 is stopped, the amount of heat radiated to the outside air by natural convection is also transferred to the indoor heat exchanger 6a acting as a heater, and the indoor heat exchanger 6a. As a result, the amount of heating is further increased, and the dehumidifying operation can be performed more like heating.

  In the cycle configuration of the embodiment shown in FIG. 1, the case of the dehumidifying operation has been described so far, but the cycle performance and the heat exchange performance in the indoor heat exchangers 6a and 6b are ensured for each operation of cooling and heating. It is necessary to operate efficiently. Hereinafter, this method will be described.

  First, in the embodiment shown in FIG. 1, since the indoor heat exchanger is divided into 6a and 6b and these are connected in series via the two-way valve 8, in the cooling operation and the heating operation, particularly in the cooling operation. Is an evaporator in which both the indoor heat exchangers 6a and 6b have a low pressure and the specific volume of the gas refrigerant is large and the volumetric flow rate is large, so that the pressure loss in the indoor heat exchanger increases and the cycle performance decreases. .

  An embodiment capable of solving this problem is shown in FIGS. The embodiment shown in FIGS. 9 and 10 corresponds to the heat exchanger portion of the indoor portion 90 surrounded by the one-dot chain line in the embodiment shown in FIG. 1, and FIG. 10 is viewed from the direction of the arrow P in FIG. It is a front view. 9 and 10, reference numerals 51a and 51b denote two-divided indoor heat exchangers corresponding to 6a and 6b shown in FIG. 1, respectively. The indoor heat exchanger 51a has a refrigerant pipe 52 and a refrigerant pipe at point A. 53. After having been divided into 53 refrigerant pipes, the pipe has a pipe configuration that merges again into one line at point B. Similarly, the indoor heat exchanger 51b has two lines of refrigerant pipe 54 and refrigerant pipe 55 at point C. After dividing into refrigerant piping, it is set as the piping structure which joins again in one system at D point. Reference numeral 56 denotes a radiation fin. The other parts having the same numbers as those in FIG. 1 indicate the same parts.

  In the air conditioner configured as described above, the refrigerant flows in two systems in the indoor heat exchangers 51a and 51b by opening the two-way valve 8 during cooling operation and heating operation. The refrigerant flow rate flowing through the refrigerant is halved, and the refrigerant flow pressure loss in the indoor heat exchangers 51a and 51b is reduced.

  9 and 10 show the case where the refrigerant pipes of the indoor heat exchangers 51a and 51b are divided into two systems. However, the present invention is not limited to this, and can be divided into more systems. In this case as well, the refrigerant flow pressure loss in the indoor heat exchangers 51a and 51b can be reduced, and the deterioration of the performance can be prevented. However, if there are too many refrigerant flows, the pressure loss of the refrigerant flow will decrease, but the heat transfer coefficient will decrease significantly, and the overall performance of the air conditioner, such as cooling capacity and operating coefficient, will decrease. It is necessary to set the number of systems, and the number of systems is determined by the inner diameter of the refrigerant pipe.

  Next, in the heating operation, in order to improve the performance such as the heating capacity and the operation coefficient, in the indoor heat exchanger that acts as a condenser, the heat exchanger portion through which the high-temperature gas refrigerant flow at the inlet flows, Heat exchange with the air flow at a position where there is no heat exchanger part to exchange heat on the leeward side, and the heat exchanger part at the outlet of the refrigerant flow is sufficiently subcooled so that the air flow on the leeward side at a relatively low temperature can be taken. It is necessary to exchange heat with. An example of such a configuration is shown in FIG. In FIG. 11, 60a is an indoor heat exchanger composed of two refrigerant pipes 61 and 62 coupled at points E and F, and 60b is an indoor heat exchanger composed of two refrigerant pipes 63 and 64 coupled at point G. 60c is a two-line refrigerant pipe connected at point H provided at a position where the refrigerant flow is upstream of the indoor heat exchanger 60b and the air flow 15 is leeward after passing through the indoor heat exchanger 60b during heating operation. An indoor heat exchanger composed of 66 and 67, 60d is a refrigerant provided at a position where the refrigerant flow is downstream of the indoor heat exchanger 60a and the air flow 15 directly hits and is above the indoor heat exchanger 60b during heating operation. This is an indoor heat exchanger having a refrigerant pipe 65 with a single flow, and basically has a configuration in which indoor heat exchangers 60c and 60d are further provided in the embodiment shown in FIG. .

  In what is configured as described above, during the heating operation, the refrigerant flows through the indoor heat exchanger through the two-way valve 8 in the order of 60c, 60b, 60a, 60d, and the high-temperature gas as indicated by the broken arrows. The refrigerant flow exchanges heat with the air flow 15a after heat exchange with the indoor heat exchanger 60b in the indoor heat exchanger 60c, and further exchanges heat with the air flow 15 having a relatively low temperature in the indoor heat exchanger 60b. Heat is exchanged with the air flow 15a after heat exchange with the indoor heat exchanger 60b in the indoor heat exchanger 60a, thereby being radiated and cooled, and sufficiently condensed at the outlet of the indoor heat exchanger 60a. Next, this condensed liquid refrigerant flow flows into the indoor heat exchanger 60d of one system and becomes high speed, the heat transfer coefficient in the pipe becomes sufficiently high, and heat exchange with the relatively low temperature air flow 15 is performed, so that the subcool Is fully removed. In this case, the refrigerant flow from the indoor heat exchangers 60c to 60b is opposite to the air flow 15 and the air flow 15a, and the refrigerant flow flowing from the indoor heat exchanger 60a to the indoor heat exchanger 60d is also the air flow 15. 15a and 15a, and in both cases, the heat exchange is efficient.

  In the cooling operation, the refrigerant flows in the order of the indoor heat exchanger 60d, the indoor heat exchanger 60a, the two-way valve 8, the indoor heat exchanger 60b, and the indoor heat exchanger 60c as indicated by solid arrows. The indoor heat exchanger acts as an evaporator.

  During the dehumidifying operation, the refrigerant flows in the order of the indoor heat exchanger 60d, the indoor heat exchanger 60a, the dehumidifying / humidifying squeezing device 7, the indoor heat exchanger 60b, and the indoor heat exchanger 60c, as indicated by the one-dot chain line arrow, The exchanger 60d and the indoor heat exchanger 60a function as a heater, and the indoor heat exchanger 60b and the indoor heat exchanger 60c function as a cooling / dehumidifying device. In this case, since the indoor heat exchanger 60c acting as a cooling / dehumidifying device is located below the indoor heat exchanger 60a acting as a heater, the dehumidified water generated in the indoor heat exchanger 60c is converted into the indoor heat exchanger. It does not evaporate again when heated at 60a. Further, since the indoor heat exchanger 60d acting as a heater is located above the indoor heat exchanger 60b serving as a cooling / dehumidifying device, the dehumidified water generated in the indoor heat exchanger 60b is transferred to the indoor heat exchanger 60d. It does not evaporate again when heated.

As can be understood from what has been described so far, in FIG. 11, the indoor heat exchanger 60 c does not necessarily have to be under the indoor heat exchanger 60 a, and is a position indicated by a dashed line 68 and the indoor heat exchanger 60 b. Of the indoor heat exchanger 60c at the time of dehumidifying operation at a position indicated by a one-dot chain line below or at a position 68a, including the leeward side of the indoor heat exchanger 60a, such that there is no indoor heat exchanger portion on the leeward side. If the dehumidified water is not hung on the indoor heat exchanger as a heater, it can be placed at any position. Moreover, the indoor heat exchanger 60d does not necessarily have to be above the indoor heat exchanger 60b, and is a position indicated by a two-dot chain line 69, and a position indicated by a two-dot chain line above the indoor heat exchanger 60a or 69a. In addition, any position including the front of the indoor heat exchanger 60b, etc., where the dehumidifying water is not applied at the time of the dehumidifying operation can be placed at any position including the direct contact with the relatively low temperature air flow 15.

  In FIG. 11, both the indoor heat exchanger 60c and the indoor heat exchanger 60d are provided on the inlet hot gas region side and the outlet subcool region side of the refrigerant flow during the heating operation. In this case, the effects of the actions of the indoor heat exchangers 60c and 60d can be obtained.

  More specifically, in FIG. 9, the indoor heat exchangers 51a and 51b are two refrigerant flow paths, or in FIG. 11, the indoor heat exchangers 60a, 60b and 60c are two refrigerant flow paths and indoor heat. Although the exchanger 60d is a single-system refrigerant flow path, the present invention is not limited to this, and the refrigerant flow paths of the indoor heat exchangers 51a and 51b or 60a, 60b, 60c, and 60d are used in terms of the refrigerant flow rate and the simplicity of the configuration. Judgment can be made into one system or multiple systems. For example, when the refrigerant flow rate is relatively high, 51a and 51b in FIG. 9 or 60a, 60b and 60c in FIG. 11 which are indoor heat exchangers in which gas flows are mixed are used in order to reduce the pressure loss. In the indoor heat exchanger 60d in FIG. 11, which is almost in a liquid flow state during heating operation, it is better to use a single refrigerant flow path in order to increase the flow rate in the pipe and improve the heat transfer performance. . When the refrigerant flow rate is relatively small, 51a in FIG. 9 and 60a in FIG. 11 that serve as indoor heat exchangers having relatively low refrigerant dryness on the upstream side during cooling operation are made into a single refrigerant flow path (illustrated). (Omitted), pressure loss is relatively small here, and performance degradation hardly poses a problem, and the piping configuration is simplified. Further, when the refrigerant flow rate is small, all the indoor heat exchangers (51a, 51b in FIG. 9 or 60a, 60b, 60c, 60d in FIG. 11) can be made into a single refrigerant pipe (not shown). The drop does not become a problem, and the piping configuration is further simplified.

  By the way, in a room air conditioner or the like that is a small air conditioner, the structure of the indoor heat exchanger is almost limited and the degree of freedom of the piping configuration and the like is small, so this point needs to be considered. Hereinafter, a specific example of such a case will be described with reference to an example of an indoor heat exchanger in a case where the number of piping rows is two in the embodiment shown in FIG.

  FIG. 12 is a side view of the indoor heat exchanger 70 in which two rows of pipes are arranged and the number of stages of the pipes is nine, and also shows a configuration example of pipes around the indoor heat exchanger 7. . In FIG. 12, what is indicated by a circle is a heat transfer pipe 73 provided so as to pass through a plurality of radiation fins 71, those indicated by broken lines and solid lines are connection pipes, and 7 and 8 are those shown in FIG. Similarly to the above, a dehumidifying throttle device and a two-way valve are shown. In addition, the indoor heat exchanger 70 is separated into two L-shaped heat exchangers 70a and 70b by cutting the radiating fins 71 at a portion indicated by a line 72, and the heat transfer tubes 73a and 73b are a single refrigerant. The other heat transfer tubes are piped so as to form a two-system refrigerant flow with the dehumidifying throttle device 7 and the two-way valve 8 interposed therebetween.

  With the configuration described above, the refrigerant flow flows in the directions indicated by the solid line arrow, the broken line arrow, and the alternate long and short dash line in the cooling, heating, and dehumidifying operations. For this reason, during the cooling operation, all the heat transfer tubes become low-pressure evaporators, but since all the heat transfer tubes except 73a and 73b have two refrigerant flows, the pressure loss is small and there is no problem. Further, during the heating operation, the high-temperature gas refrigerant flow flows from the heat transfer tubes 73c and 73d on the inlet side of the indoor heat exchanger 70 to the heat transfer tubes 73e and 73f on the downstream side, respectively, and is opposed to the air flow 15. An efficient heat exchange state can be realized, and in the heat transfer tubes 73b and 73a which are the heat transfer tubes on the outlet side, heat exchange is performed between the air flow 15 having a relatively low temperature and the upwind side, and the refrigerant flow is one system. Because the speed is increased and the heat transfer performance in the pipe is improved, a sufficient subcooling can be achieved. During the dehumidifying operation, the indoor heat exchanger 70b serves as an upwind side cooling / dehumidifier (ie, an evaporator) and the indoor heat exchanger 70a serves as a downwind side heater (ie, a condenser) with respect to the air flow 15, 15 is cooled, dehumidified and then heated again. In this case, since it is separated into the indoor heat exchanger 70a having a high temperature and the indoor heat exchanger 70b having a low temperature with the cut 72 as a boundary, there is no heat loss because the mutual heat exchangers do not directly interfere with each other, Efficient dehumidifying operation can be performed. Also, the indoor heat exchanger 70a that acts as a heater is above the indoor heat exchanger 70b that acts as a cooling / dehumidifier, and the dehumidified water flowing downward is not heated and evaporated again.

FIG. 13 is a modification of the embodiment of the indoor heat exchanger shown in FIG. 12 in which the heat transfer tubes are arranged in 9 rows in two rows. Compared with the embodiment shown in FIG. In order to take a subcooling at the outlet side of the flow, the heat transfer tubes 74a and 74b in which the refrigerant flow is made in one system are shifted one stage upward, and the inlet heat transfer tube into which the high-temperature gas refrigerant flow flows is A pipe structure having a heat transfer tube 74c on the leeward side and a heat transfer tube 74d on the leeward side is divided into two by a cutting line indicated by 96. In this piping configuration, the heat transfer tube 74c in the high temperature gas region and the heat transfer tubes 74e and 74f in the condensing region on the leeward side are not opposed to the air flow 15 during the heating operation, but after cooling and dehumidifying during the dehumidifying operation. The height h ₂ of the heat exchanger portion to be heated again is longer than h ₁ shown in FIG. 12, and a larger amount of dehumidification than the embodiment shown in FIG. 12 can be obtained.

FIG. 14 shows still another modification of the indoor heat exchanger shown in FIG. 12 in which the heat transfer tubes are arranged in nine rows in two rows. In the heating operation, the refrigerant flow is used to take a subcool at the outlet side of the refrigerant flow. The heat transfer tubes 75a and 75b in one line are arranged in the uppermost two rows, and the inlet heat transfer tubes into which the refrigerant flow of the high-temperature gas flows are piped so that both of them become the heat transfer tubes 75c and 75d on the windward side with respect to the air flow 15. The indoor heat exchanger 88 is divided into two parts 88a and 88b at a position indicated by 89. In this piping configuration, the inlet heat transfer tubes 75c and 75d in the hot gas region and the lower temperature heat transfer tubes 75b, 75e, 75f and 75g on the leeward side do not face the air flow 15 during the heating operation, but during the dehumidifying operation. cooling, the height h ₃ of the heat exchanger portion after reheating dehumidified be longer than the embodiment shown in FIG. 13, it is possible to take more dehumidification amount.

  FIG. 15 is a side view of an embodiment of the indoor heat exchanger 80 in which the heat transfer tubes are piped in 10 rows in two rows, and the piping configuration around the indoor heat exchanger 80 is also shown. As in the embodiment shown in FIG. 12, those indicated by ◯ in FIG. 15 are the heat transfer tubes provided so as to penetrate through the plurality of radiation fins 81, those indicated by broken lines and solid lines are connection pipes, Each is a dehumidifying throttle device and a two-way valve. The indoor heat exchanger 80 is separated into two L-shaped heat exchangers 80a and 80b by cutting the radiating fins 81 at the portion indicated by the separation line 82, and the heat transfer tubes 83a and 83b are separated from each other. The refrigerant flow and the other heat transfer tubes are piped so as to form a two-system refrigerant flow with the dehumidifying throttle device 7 and the two-way valve 8 interposed therebetween. The L-shaped heat exchanger 80b has a refrigerant piping configuration of two systems, a system indicated by an arrow 84 and a system indicated by an arrow 85, between the branching I point and J point. Since the number of heat transfer tubes (in this case, two) is smaller than the piping of the system indicated by 85, the heat transfer tubes 83c and J in the piping of the system indicated by 84 are the same so that the flow resistance of the refrigerant flow is the same. A resistance tube 86 is provided between the points.

  With the above configuration, the refrigerant flow flows in the directions indicated by the solid line arrow, the broken line arrow, and the alternate long and short dash line in the cooling, heating, and dehumidifying operations, respectively, and the low pressure loss refrigerant flow state in the cooling operation In the heating operation, the heat exchange state by the countercurrent flow of the high temperature gas refrigerant flow and the air flow at the inlet and the subcooling sufficient by one refrigerant flow at the outlet, cooling to the air flow 15 in the dehumidification operation, dehumidification and reheating As in the embodiment shown in FIG. 12, this function can be performed efficiently and without problems.

  The resistance tube 86 may be provided anywhere between points I and J in the piping of the system indicated by 84. Furthermore, it is also possible to apply a resistance pipe to each refrigerant flow path having a plurality of systems in which the flow resistance is smaller to equalize the flow resistance of each flow path. For example, in the embodiment shown in FIG. 9 or FIG. 11, a resistance tube is provided in a flow path having a low flow resistance for each refrigerant flow path in a plurality of systems so that the flow resistance is equalized and the refrigerant flows in a balanced manner. Sometimes applicable.

FIG. 16 is a modification of the indoor heat exchanger shown in FIG. 15 in which the heat transfer tubes are arranged in 10 rows in two rows. In the heating operation, the refrigerant flow is integrated into one system in order to take a subcooling at the outlet side of the refrigerant flow. The three heat transfer tubes 87a, 87b, 87i are arranged so that the inlet heat transfer tubes into which the refrigerant flow of the high-temperature gas flows are both heat transfer tubes 87c, 87d on the windward side with respect to the air flow 15. It is constructed and similarly cut at 97. In this piping configuration, the inlet heat transfer tubes 87c and 87d in the high temperature gas region and the lower temperature heat transfer tubes 87e, 87f, 87g and 87h on the leeward side do not face the air flow 15 during the heating operation. but during the dehumidifying operation, cooling, the height h ₅ of the heat exchanger portion after reheating dehumidified longer than h ₅ in FIG. 15, it is possible to take more dehumidification amount. Further, the refrigerant flow between the point K and the point L is a two-system flow, but the length of the heat transfer tube of each system is set to be the same, and the resistance tube 86 as in the embodiment shown in FIG. Need not be provided.

  In addition, in the Example shown in FIG.12, FIG.13, FIG.14, FIG.16, although the number of the heat exchanger tubes used as a heater at the time of a dehumidification operation is made larger than the number of the heat exchanger tubes used as a cooling / dehumidifier, This is because it is effective in performing the heating-like dehumidifying operation described in the embodiments shown in FIGS. 3, 4, 6, and 8. That is, in the dehumidifying operation, the capacity of the cooling / dehumidifying device can be lowered, and the ability of the heater can be increased, so that the dehumidifying operation with a heating effect is facilitated.

  Here, in the indoor heat exchangers shown in FIGS. 12 to 16, both of the heat exchangers divided into two form a two-system refrigerant flow path, which has been described in the embodiment shown in FIG. Thus, it is suitable as a piping configuration of an air conditioner having a relatively large refrigerant flow rate. When the refrigerant flow rate is relatively small, in the embodiment shown in FIGS. 12 to 16, the indoor heat becomes an upstream evaporator (for example, 70a in FIG. 12 and 80a in FIG. 15) during the cooling operation. The exchanger can be a single refrigerant flow path, and when the refrigerant flow rate is small, an indoor heat exchanger that acts as an evaporator on the downstream side during cooling operation (for example, 70b in FIG. 12, In FIG. 15, indicated by 80b can also be a single refrigerant flow path.

  As an example, FIG. 17 will be used to explain an embodiment in which a piping configuration is used when the refrigerant flow rate is relatively small, corresponding to the embodiment shown in FIG. Here, FIG. 17 shows the heat exchanger 70a shown in FIG. In FIG. 17, reference numeral 98 denotes a heat exchanger 98 a that is divided into two by a cutting line 72 and has a refrigerant flow path that serves as an upstream evaporator during cooling operation, and a refrigerant that serves as a downstream evaporator during cooling operation. This is an indoor heat exchanger composed of a heat exchanger 98b (same as 70b shown in FIG. 12) having two flow paths. In FIG. 17, the same reference numerals as those in FIG. 12 denote the same parts.

  When configured as described above, the refrigerant flows in the directions indicated by solid arrows, broken lines, and dashed lines in cooling, heating, and dehumidifying operations. During the cooling operation, both the indoor heat exchangers 98a and 98b are low-pressure evaporators. However, since the refrigerant flow rate is relatively small, the upstream evaporator 98a having a low dryness has a pressure loss even with one refrigerant flow path. Relatively few and conversely the refrigerant flow rate is faster than in the embodiment shown in FIG. Moreover, in the evaporator 73b on the downstream side, the degree of dryness is increased, but since the refrigerant flow path has two systems, the refrigerant flow rate is sufficiently low and the pressure loss is small.

  Further, during the heating operation, in the indoor heat exchanger 98, since the refrigerant flow is high pressure, the specific volume of the gas refrigerant is reduced and the flow velocity is slowed down. After entering the heat exchanger 98b to condense and the refrigerant dryness becomes sufficiently low, the refrigerant flow path enters the one-system indoor heat exchanger 98a, so that no problematic pressure loss occurs. Accordingly, when the refrigerant flow rate is relatively small, in the embodiment shown in FIG. 17, there is no problem in performance in both cooling and heating operation, and the refrigerant flow path of the indoor heat exchanger 98a is integrated into one system. The configuration is simple. The heat exchange state between the indoor heat exchanger 98 and the air flow 15 during the cooling operation, the heating operation, and further during the dehumidifying operation is the same as that in the embodiment shown in FIG.

  Here, in the embodiment shown in FIGS. 12 to 16, the indoor heat exchanger is completely divided into two parts by, for example, the cutting line 72 shown in FIG. 12 or the cutting line 89 shown in FIG. The heat transfer is sufficiently blocked, and sufficient cooling, dehumidification and heating are possible during the dehumidifying operation. However, on the other hand, there is a problem that the assembly of the heat exchanger becomes complicated, and in order to solve this, the heat dissipating fins before incorporating the heat transfer tubes are preferably configured as shown in FIGS.

  The heat dissipating fin 91 shown in FIG. 18 has a structure in which an intermittent slit 92 is provided at a position corresponding to the cutting line 72 shown in FIG. As a result of this configuration, the heat insulation performance is somewhat inferior to the cutting line 72 shown in FIG. 12 due to the slit 92, but the heat transfer between the 91a side and the 91b side of the radiating fin 91 can be blocked, and further, Since the 91a side and the 91b side are connected, this assembly can be facilitated when the heat exchanger is assembled.

  Further, the radiating fin 93 shown in FIG. 19 has a structure in which an intermittent slit 94 is provided at a position corresponding to the cutting line 89 shown in FIG. In this case as well, as in the embodiment shown in FIG. 18, the heat transfer between the 93a side and the 93b side of the radiating fin 93 can be blocked by the slit 94, and the 93a side and the 93b side of the radiating fin are connected. This assembly can be facilitated when the heat exchanger is assembled.

  In the embodiment described above, the case where a single refrigerant such as HCFC22 (abbreviation of hydrochlorofluorocarbon 22) often used in an air conditioner has been described. Recently, however, research on alternative refrigerants to replace HCFC22 has been actively conducted from the viewpoint of ozone layer destruction and global warming. Further, as an alternative refrigerant, use of not only a single refrigerant but also a mixed refrigerant is being studied. Among these, the single refrigerant has a difference in pressure level, but the refrigeration cycle and its characteristics are the same as those of HCFC22. In the case of a mixed refrigerant, the examples shown in FIGS. The cycle configuration, indoor unit structure, operation control method, indoor heat exchanger piping configuration, and the like that have been described can be applied, and similar effects can be obtained.

  Further, in the case of using a mixed refrigerant, generally, the indoor heat exchanger having the piping configuration shown in FIGS. 11 to 17 can be obtained in the cooling operation, which cannot be obtained when a single refrigerant is used. Such an effect is obtained.

  FIG. 21 shows a modeled temperature-entropy diagram for the refrigeration cycle when a single refrigerant and a mixed refrigerant are used. In this temperature-entropy diagram, for example, when cooling operation is performed in the piping configuration shown in FIG. 11, in the indoor heat exchanger acting as an evaporator, in the case of a single refrigerant, the refrigerant flow evaporates due to pressure loss. As shown in FIG. 21 from the Ta point to the Pa point, the temperature decreases from the inlet toward the outlet, and the indoor heat exchanger 60a becomes a high-temperature side evaporator and 60b becomes a low-temperature side evaporator. The flow and the air flow 15 are not counterflows. On the other hand, in the case of the mixed refrigerant, the composition ratio of the mixed refrigerant in the gas phase and the liquid phase generally changes during the evaporation process, and accordingly, as shown from the T point to the P point in FIG. The evaporation temperature rises from the inlet to the outlet of the heat exchanger. As a result, in the embodiment shown in FIG. 11, the evaporating temperature of the indoor heat exchanger 60a is lower than the evaporating temperature of the indoor heat exchanger 60b. Compared to the case, the heat exchange state is more efficient.

  In the heating operation, on the condensing side, both the single refrigerant and the mixed refrigerant at the inlet of the indoor heat exchanger are shown in FIG. 21 as Q point to Ra point, then Sa point, Q point to R point and S point, respectively. Since the refrigerant temperature decreases from the outlet toward the outlet, the temperature relationship between the refrigerant flow and the air flow in the indoor heat exchanger is the same as that between the single refrigerant and the mixed refrigerant.

  Heretofore, as shown in FIG. 1, the explanation has been made assuming a structure in which the indoor heat exchangers 6 a and 6 b divided into two are arranged in series (front and rear) with respect to the air flow 15. Even if the divided indoor heat exchangers are arranged in parallel (up and down) with respect to the air flow, the same action and effect can be obtained during the dehumidifying operation. A diagram showing a refrigeration cycle and a control system according to this embodiment is shown in FIG. In FIG. 22, 110 a and 110 b are divided into two indoor heat exchangers, which are arranged in parallel (up and down) with respect to the air flow 15. Other than that, it is the same as FIG. 1, the same reference numerals as those in FIG. 1 denote the same parts, the compressor 1 is capable of capacity control, and the outdoor fan 10 and the indoor fan 12 are capacity control, that is, air flow control. Is possible.

  Here, the indoor fan 12 is illustrated in the case where air flows through the indoor heat exchangers 6a and 6b in parallel, but the indoor heat exchangers 6a and 6b are bent into a dogleg shape, First, the indoor fan 12 can be arranged so that air flows through the indoor heat exchanger 6b and then the air flows through the indoor heat exchanger 6a. With this configuration, a passage for inflow and outflow of air is formed. It's easy to do.

  Also in the cycle configuration of FIG. 22, as in the cycle configuration of FIG. 1, during the cooling operation, the two-way valve 5 is closed and the two-way valve 8 is opened, whereby the refrigerant is circulated as indicated by the solid line arrows, The room is cooled using the exchanger 3 as a condenser and the indoor heat exchangers 6a and 6b as evaporators. During heating operation, the four-way valve 2 is switched, the two-way valve 5 is closed, and the two-way valve 8 is opened, whereby the refrigerant is circulated as shown by the broken line arrows, and the indoor heat exchangers 6a and 6b are condensers and outdoor heat exchangers. The room is heated using 10 as an evaporator.

In the dehumidifying operation, the four-way valve 2 is switched in the same manner as in the cooling operation, and the two-way valve 5 is opened and the two-way valve 8 is closed, so that the refrigerant is supplied to the compressor 1, the four-way valve 2, and the outdoor as shown by the one-dot chain line. The heat exchanger 3, the two-way valve 5, the indoor heat exchanger 110a, the dehumidifying throttle device 7, the indoor heat exchanger 110b, the four-way valve 2, the accumulator 9, and the compressor 1 are circulated in this order, and the outdoor heat exchanger 3 is upstream. The indoor heat exchanger 6a is a downstream condenser, and the indoor heat exchanger 6b is an evaporator. When the indoor air is caused to flow as indicated by the arrow 15 by the indoor fan 12, a part of the air flow is cooled and dehumidified by the indoor heat exchanger 110b serving as an evaporator, and the remaining air flow is converted into a heater by a condenser. The indoor heat exchanger 110a is heated and blown into the room. In this case, the ability of the evaporator 110b and the heater 110a can be adjusted by controlling the ability of the compressor 1 and the blowing ability of the indoor fan 12 and the outdoor fan 10, and finally the dehumidification amount and the blown air temperature. Can be controlled according to the purpose of use.

  Therefore, in the dehumidifying operation, even when the indoor heat exchangers 110a and 110b divided into two with respect to the air flow 15 as shown in FIG. 22 are arranged in parallel (up and down), the air flow 15 as shown in FIG. Various operations similar to the case where the indoor heat exchangers 6a and 6b divided in two are arranged in series (front and rear) are possible, the same operation method as in FIGS. 2 to 4 can be performed, and similar effects can be obtained. I can get it. That is, the dehumidifying operation according to various usage purposes, such as the comfortable dehumidifying operation, the night / azame dehumidifying operation, the mold / tick prevention dehumidifying operation, the laundry dehumidifying operation, etc. described in the embodiment of FIG. It is possible to perform a dehumidifying operation with a cooling, isothermal or heating depending on the use of the low air volume dehumidifying operation and the high air volume dehumidifying operation according to the operation and the room temperature.

  By the way, in the above-described high air volume dehumidifying operation, the input is increased because the compressor is operated at a high capacity. An embodiment capable of solving this problem is shown in FIG. FIG. 23 is a diagram showing a side cross section of the indoor unit when the indoor heat exchanger is divided into two parts in the vertical direction as compared with the previous embodiment of FIG. 5, and 110a, 110b, and 12 are the cycle configurations of FIG. These are the same as those described above, respectively, the upper indoor heat exchanger, the lower indoor heat exchanger, and the indoor fan. Moreover, what attached the same number as FIG. 5 shows the same part.

  With the above configuration, during the dehumidifying operation, the indoor heat exchanger 6b serves as an evaporator and the indoor heat exchanger 6a serves as a heater, and the indoor fan 12 is operated to flow the indoor air as indicated by arrows 36 to 37. A portion 36 passes through the suction grill 31 and is partially cooled and dehumidified by the evaporator 6 b and partially heated by the heater 6 a, and further blown out in the direction of the arrow 37 through the indoor fan 12. The condensed water generated in the evaporator 6b is once received by the dew receiving tray 33 and then discharged outside the room.

  Note that the various operation methods when the indoor unit shown in FIG. 23 is used are the same as those of the indoor unit shown in FIG. 5 described above, and the method of the high air volume dehumidifying operation is the flowchart shown in FIG. The same effect as in the embodiment of FIG. 5 can be obtained.

  Also, in the case of FIG. 22, it is obvious that the same effect can be obtained by applying the embodiment of FIG. 7 as in the case of FIG. That is, the portion 40 surrounded by the two-dot chain line in FIG. 22 is configured as shown in FIG. 7, and the amount of heat released from the outdoor heat exchanger 3 is adjusted by the heating-like dehumidifying operation method shown in FIG. It is possible to perform a dehumidifying operation more like a heating than the case.

  The operation method during the dehumidifying operation shown in FIGS. 2, 3, 4, 6, and 8 has been described assuming the cycle configuration shown in FIG. 1, FIG. 7 or FIG. Not limited to this, the indoor heat exchanger is divided into two and a dehumidifying throttle device is provided between them. During the dehumidifying operation, the upstream side of the refrigerant flow in the divided indoor heat exchanger is a heater, and the downstream side is cooled and dehumidified. For an air conditioner having a cycle configuration as a heat exchanger, as described above, the indoor heat exchangers are arranged one after the other and the air flow is caused to flow sequentially through these indoor heat exchangers, or the air flows are arranged one above the other. It can be applied in common, including the case of flowing in parallel to the heat exchanger, and the same effect can be obtained.

  By the way, although the case of the dehumidifying operation has been described with respect to the cycle configuration of the embodiment shown in FIG. 22, the cycle performance and the indoor heat exchange are also applied to the cooling and heating operations as in the case of the cycle configuration of FIG. 1. It is necessary to ensure efficient heat exchange performance in the units 110a and 110b and to operate efficiently. This method will be described below. First, in the embodiment shown in FIG. 22, the indoor heat exchanger is divided into two parts 110a and 110b, and in the cooling operation and the heating operation, these are connected in series via the two-way valve 8, so that the cooling operation is particularly preferable. , The indoor heat exchangers 110a and 110b are both low pressure evaporators having a large specific volume of gas refrigerant and a large volume flow rate, and the pressure loss in the indoor heat exchanger is increased, resulting in a reduction in cycle performance.

  An embodiment capable of solving this problem is shown in FIG. This embodiment corresponds to the heat exchanger portion of the indoor portion 111 surrounded by the one-dot chain line in the embodiment shown in FIG. In FIG. 24, 100a and 100b are two-divided indoor heat exchangers corresponding to 110a and 110b in FIG. 22, respectively. Furthermore, the indoor heat exchanger 100a is connected to two refrigerant pipes 101 and 102 at point P. After splitting, the piping configuration is to join again into one system at point Q. Similarly, the indoor heat exchanger 100b is split into two systems of refrigerant pipes 103 and 104 at point R and then joined back to the system at point S. It has a piping configuration. Moreover, what attached the same number as FIG. 22 shows the same part.

  In the above configuration, during cooling operation and heating operation, by opening the two-way valve 8, the refrigerant flows in the indoor heat exchangers 100a and 100b separately in two systems, so the refrigerant flow rate flowing through each system is halved. The refrigerant flow pressure loss in the indoor heat exchangers 100a and 100b can be reduced, and the deterioration of the performance can be prevented.

  In the embodiment shown in FIG. 24, the refrigerant pipes of the indoor heat exchangers 100a and 100b are divided into two systems. However, the present invention is not limited to this, and can be divided into more systems. The refrigerant flow pressure loss in the vessels 100a and 100b can be reduced, and the performance can be prevented from deteriorating. However, if there are too many refrigerant flows, the pressure loss of the refrigerant flow will be reduced, but the heat transfer rate will be too low and the overall performance such as cooling capacity and operating coefficient will be reduced. And this value varies depending on the inner diameter of the refrigerant pipe.

  Furthermore, in the heating operation, in order to improve the performance such as the heating capacity and the operation coefficient, it is necessary to take a sufficient subcooling in the heat exchanger portion corresponding to the refrigerant outlet in the indoor heat exchanger serving as the condenser. An embodiment capable of realizing this is shown in FIG. In FIG. 25, reference numeral 100c denotes an indoor heat exchanger which is a downstream side of the refrigerant flow during heating operation, which is composed of two refrigerant pipes 106 and 107 coupled to one refrigerant pipe 105 at point T, and is the same as FIG. Numbered parts indicate the same parts. That is, the embodiment of FIG. 25 is obtained by replacing the indoor heat exchanger 100a having two refrigerant pipes with an indoor heat exchanger 100c having a combination of one refrigerant pipe and two refrigerant pipes in FIG.

  In the above configuration, during the heating operation, the refrigerant flows in the order of the indoor heat exchanger 100b, the two-way valve 8, and the indoor heat exchanger 100c. In this case, the high-temperature gas refrigerant flow that has entered as indicated by the broken line arrow is Heat exchange with the air flow 15 causes the refrigerant piping to be sufficiently condensed in the two systems 106 and 107 of the refrigerant piping of the indoor heat exchanger 100c from the two systems indoor heat exchanger 100b of 103 and 104. Next, this condensed liquid refrigerant flow enters the one-line refrigerant pipe 105 of the indoor heat exchanger 100c and becomes high speed, and the heat transfer coefficient in the pipe becomes sufficiently high, so that the subcool is sufficiently removed. As a result, an efficient heat exchange state is obtained.

  Further, during the cooling operation, as indicated by solid arrows, the refrigerant flows from one refrigerant pipe 105 of the indoor heat exchanger 100c to two refrigerant pipes 106 and 107, the two-way valve 8, and the indoor heat exchanger 100b. Although the refrigerant pipes 103 and 104 of the system flow in this order, in this case, the pressure loss does not increase so much in the refrigerant pipe 105 of one system because the dryness of the refrigerant flow is low. Furthermore, in the single line of the refrigerant pipe 105, the flow rate of the refrigerant flow is increased, so that the heat transfer rate in the pipe is increased and the heat transfer performance is improved.

  More specifically, in FIG. 24, the indoor heat exchangers 100a and 100b are two refrigerant channels, or in FIG. 25, the indoor heat exchanger 100b is two refrigerant channels and the indoor heat exchanger. Although 100c is made into the flow path structure which combined one refrigerant flow path and two refrigerant flow paths, it is not restricted to this, The refrigerant flow path of each indoor heat exchanger 100a, 100b or 100c is made into refrigerant | coolant flow volume or structure. Judging from the simplicity of the system, it is possible to make one system or multiple systems. For example, when the refrigerant flow rate is relatively large, 100a and 100b in FIG. 24 or 100c and 100b in FIG. 25, which are indoor heat exchangers with mixed gas flows, are connected to a plurality of refrigerant flow paths in order to reduce pressure loss. (The indoor heat exchanger 100c in FIG. 25 may be a combination of one system and a plurality of systems). When the refrigerant flow rate is relatively small, 100a in FIG. 24 and 100c in FIG. 25, which are indoor heat exchangers having a relatively low refrigerant dryness on the upstream side during the cooling operation, are made into one system refrigerant flow path (illustrated). (Omitted), pressure loss is relatively small here, and performance degradation hardly poses a problem, and the piping configuration is simplified. If the refrigerant flow rate is even smaller, all indoor heat exchangers (100a, 100b in FIG. 24 or 100c, 100b in FIG. 25) can be made into one system of refrigerant piping (not shown), and the performance degradation becomes a problem. Therefore, the piping configuration is further simplified.

  As for the type of refrigerant flowing in the refrigeration cycle of FIG. 22, as in the case of the embodiment of FIG. 1, the cycle configuration described so far for a single refrigerant such as HCFC 22 or various mixed refrigerants, It is obvious that the same effect can be obtained by applying the indoor unit structure, the operation control method, the piping configuration of the indoor heat exchanger, and the like.

  By the way, as a method for controlling the capacity of the compressor, the indoor fan, and the outdoor fan in the cycle configuration shown in FIGS. 1 and 22 and the like described so far, a method of controlling the rotational speed using a typical inverter or DC motor has been described. Various other methods can be considered. For example, various methods such as a method of mechanically controlling the capacity for the compressor, a method of switching the tap of the AC motor, a method of narrowing the ventilation path, and a method of increasing the ventilation resistance can be used for the blower. Moreover, generally the high air volume of the indoor fan in the dehumidifying operation used until now is generally equal to or less than the air volume during the cooling operation or the heating operation.

  In the embodiments shown in FIGS. 1, 9, 11, 12, 13, 14, 15, 15, 16, 17, 22, 24, and 25, as described above, The main throttle device 4 or the dehumidifying throttle device 7 is not limited to a fixed throttle device such as a capillary tube, and a variable throttle device such as an expansion valve or an electric expansion valve can be used. It can be carried out. In particular, when an electric expansion valve that can be fully opened with low flow resistance is used, the two-way valve 5 or the two-way valve 8 is not necessary. For example, as shown in FIG. 1 and FIG. In addition, the portions 45 and 46 of the throttle device 4 and the two-way valve 5 and the throttle device 7 and the two-way valve 8 provided in parallel can be replaced by the fully openable electric expansion valve 95 as shown in FIG.

Further, the refrigeration cycle capable of three operation states of cooling, heating, and dehumidification has been described so far, but the present invention is not limited to this, and the operation method described so far for other refrigeration cycles. And the configuration of the indoor heat exchanger can be applied. For example, in the embodiment shown in FIG. 1 or FIG. 22, the four-way valve 2 is removed, and the compressor 1 and the accumulator 9 are connected to the indoor heat exchanger 6b or 110b, the accumulator 9, the compressor 1, and the outdoor heat exchanger 3 in series. When connected in such a manner (not shown), a refrigeration cycle in which the cooling operation of the refrigerant flow indicated by the solid line arrow and the dehumidifying operation of the refrigerant flow indicated by the alternate long and short dash line are possible. In the dehumidifying operation of such a refrigeration cycle, the operating method shown in FIG. 2, FIG. 3, FIG. 4, the operating method shown in FIG. 6 in the indoor unit structure shown in FIG. 5 or FIG. A similar effect can be obtained by performing the driving method shown in FIG.

  Furthermore, in the refrigeration cycle configuration shown in FIGS. 1 and 22, an accumulator is not always necessary, and depending on the type of compressor used, the type of main throttle device, and the control method, a refrigeration cycle configuration without an accumulator can be obtained. .

  Next, an example of a more specific operation method centering on the dehumidifying operation according to the present invention will be described with reference to FIGS. 26, 27, 28 and 29. FIG.

  FIG. 26 shows a cycle system diagram and temperature sensors (typically a thermistor) and humidity detection means (typically a humidity sensor, which may be estimated from the temperature by calculation) of each part. It is a figure which shows a position. During the dehumidifying operation, the refrigerant discharged from the compressor 201 passes through the four-way valve 202, the outdoor heat exchanger 203, and the bypass two-way valve (typically, an electromagnetic valve) 206 to the indoor heat exchanger 208 serving as a heater. Then, the pressure is further reduced by the dehumidifying expansion device 219, passes through the indoor heat exchanger 209 serving as an evaporator, and returns to the compressor 201 again. The outdoor unit includes an outdoor air temperature sensor 215 that detects an outside air temperature, the indoor unit includes a humidity sensor 216 that detects humidity, an indoor air intake temperature sensor 217 that detects an intake air temperature, and an indoor air temperature that detects a blown air temperature. A blowing temperature sensor 218 is provided. These temperature sensor and humidity sensor are connected to a control unit (not shown).

An embodiment of the control method of the present invention will be described with reference to FIGS.
FIG. 27 shows a method for controlling the outdoor fan 211 with respect to the temperature detected by the outside air temperature sensor 215. When the outdoor temperature decreases, the amount of heat radiated by the outdoor heat exchanger 203 increases, the amount of heat during the dehumidifying operation decreases, and the indoor blown air temperature decreases, so that the outdoor fan decreases when the outdoor temperature decreases. The rotational speed of 211 is reduced to prevent the indoor blown air temperature from being lowered. Further, in the outdoor unit having an electrical unit on the outdoor unit side and configured to prevent the temperature increase of the outdoor unit side electrical product by operating the outdoor fan 211, when the outdoor temperature rises, the outdoor unit side Since the temperature rise of the electrical product also increases, the rotational speed of the outdoor fan 211 is increased to decrease the temperature rise of the electrical product as the outdoor temperature rises.

  The control method of the outdoor temperature and the rotational speed of the outdoor fan 211 is patterned or stored in the control unit as an arithmetic expression, and stored in the control unit in advance based on the outdoor temperature detected by the outdoor temperature sensor 215. The outdoor fan 211 is controlled using the calculated pattern and calculation formula. At this time, not only the rotation speed of the outdoor fan 211 is changed depending on the outdoor temperature, but also the ON-OFF intermittent operation is performed, and the ratio of the ON-OFF time is changed according to the outdoor temperature. can get.

  According to this control method, even when the outdoor temperature decreases, the indoor blown air temperature does not decrease and the comfort is improved, and when the outdoor temperature increases, the rotational speed of the outdoor fan 211 is increased. As a result, the temperature rise of the electrical component provided on the outdoor unit side can be suppressed, and the reliability of the electrical component can be ensured.

  FIG. 28 shows a control method of the compressor 1 with respect to the humidity detected by the humidity sensor 216. When the indoor humidity is high, the number of rotations of the compressor 201 is increased to increase the refrigerant circulation amount in the refrigeration cycle, and the operation with a large dehumidification amount is performed to quickly reduce the indoor humidity. Further, when the indoor humidity is low, the operation is performed by reducing the number of revolutions of the compressor 201 to achieve an efficient operation. The control method of the indoor humidity and the compressor 201 is stored in the control unit as a pattern or an arithmetic expression, and the rotation speed of the compressor 201 is controlled with respect to the indoor humidity detected by the humidity sensor 216.

  As described above, a comfortable and efficient dehumidifying operation is performed by controlling the operation patterns of the rotational speeds of the outdoor fan 211 and the compressor 201 according to the detected outdoor temperature and indoor humidity.

  According to this control method, when the indoor humidity is high, for example, at the start of operation, the rotation speed of the compressor 201 is maximized, the dehumidifying operation is performed with a large dehumidifying capacity, and the room humidity is quickly reduced to an arbitrary humidity. . Further, when the indoor humidity decreases to an arbitrary humidity, the rotational speed of the compressor 201 is decreased, and the operation is performed with a relatively low dehumidification amount and high efficiency. These control methods enable more comfortable and efficient dehumidifying operation.

  Another control method of the present invention will be described with reference to FIG.

  One is a method of controlling the rotational speed of the outdoor fan 211 and the compressor 201 based on the difference between the temperatures detected by the indoor outlet temperature sensor 218 and the indoor inlet temperature sensor 217. When the indoor outlet air temperature is lower than the indoor inlet air temperature By reducing the rotational speed of the outdoor fan 211 and reducing the amount of heat released on the outdoor unit side, the temperature of the indoor blown air is increased. Further, the temperature of the indoor blown air can be changed by changing (increasing or decreasing) the rotational speed of the compressor 201. The increase or decrease in the rotation speed of the compressor 201 varies depending on the size ratio of the indoor heat exchanger 209, the heating heat exchanger 208, and the outdoor heat exchanger 203 in the refrigeration cycle. (The control method of the rotation speed of the compressor 201 is like a solid line or a one-dot chain line.) Also, depending on the difference between the room temperature and the arbitrarily set temperature (desired temperature of the occupant), the room blown air temperature and the room suction When determining the temperature difference from the air temperature, for example, when the indoor temperature is higher than the arbitrarily set temperature, control is performed such that the indoor blown air temperature−the indoor intake air temperature ≦ 0, and the outdoor fan 211 , And the compressor 201 is operated with appropriate control. When the indoor temperature is lower than the arbitrarily set temperature, the indoor blown air temperature−the indoor intake air temperature> 0 is controlled, the outdoor fan 211 is operated at a low rotation speed, and the compressor 201 is appropriately controlled and operated. To do.

  In these cases, not only the outdoor fan 211 is continuously operated, but also ON / OFF intermittent operation is performed, and the ON / OFF time ratio is determined from the difference between the indoor blown air temperature and the indoor intake air temperature. More effective. The difference between the indoor blow-out air temperature and the indoor intake air temperature and the operation patterns of the outdoor fan 211 and the compressor 201 are previously patterned or calculated and stored in the control unit.

  With these control methods, it is possible to further improve the comfort during the dehumidifying operation.

  FIG. 32 shows an example of an operation pattern in the case of patterning the outdoor fan 211 and the compressor 201 stored in the control unit in the case of controlling by the temperature difference between the room temperature and the set temperature. Each block of FIG. 32 describes not only the dehumidifying operation mode but also the cooling operation and heating operation modes, and the cooling operation, the dehumidifying operation, and the heating operation mode are also appropriate according to the outdoor temperature and indoor temperature ranges. Therefore, comfortable operation can be performed over a wider range of outdoor temperature and room temperature.

  In FIG. 32, the horizontal axis represents the outdoor temperature, the vertical axis represents the room temperature (the room intake air temperature can be used), the outdoor temperature range is divided into four, and the indoor temperature range is divided into five (1) to (5 ) In a grid pattern with constant operating conditions for each block. The constant operating conditions include cooling / dehumidification / heating operation modes, outdoor fan operation patterns, compressor operation patterns, and the like. Among these, the operation pattern of the outdoor fan 211 includes continuous operation at a certain rotational speed in the stepwise rotational speeds shown in FIG. 27 and FIG. 29, intermittent operation with the ON / OFF time ratio appropriately changed, and further There are various operation patterns such as a combination of continuous operation and intermittent operation. The operation pattern of the compressor 201 also includes continuous operation at the rotational speed at the stepwise rotational speed shown in FIGS. 28 and 29, intermittent operation with the ON / OFF time ratio appropriately changed, and these continuous operation. There are various operation patterns such as combined intermittent operation. Even when the number of rotations can be changed only by an outdoor fan or compressor, many operation patterns can be set by changing the time ratio between continuous operation and ON-OFF in various ways. it can.

  And the operation pattern in these outdoor fans or compressors and the operation mode of cooling / dehumidification / heating are set for each block in FIG. 32 according to the outdoor temperature and the indoor temperature corresponding to this block. As a result, in actual operation, when the outside air temperature or the room temperature is detected by the temperature sensor, the operation mode (for cooling / dehumidification / heating) corresponding to the block of FIG. The fan is operated in accordance with the fan operation pattern and the compressor operation pattern. For example, in the block (7), the air-cooling dehumidification operation is performed. As a result, comfortable driving can be performed.

  The division of the outdoor temperature and the indoor temperature is not necessarily performed as shown in FIG. 32, and one or more can be appropriately divided as necessary.

  Further, the relationship between the temperature difference between the room temperature and the set temperature or the temperature difference between the room blown air temperature and the room intake air temperature and the operation pattern of the outdoor fan 211 and the compressor 201 is calculated and stored in the control unit. In this case, finer control becomes possible, and this control method is effective particularly when the capacity of the outdoor fan or the compressor can be continuously controlled.

  In addition, the set value of the room temperature or the room humidity can be determined based on the thermal environment evaluation method such as PMV described above. In this case, more comfortable driving can be automatically performed. it can. By performing such a dehumidifying operation, a dehumidifying operation with a good sensible temperature can be performed.

By the way, the description has been made assuming that a humidity sensor is used as the humidity detection means. However, since the humidity sensor is relatively expensive, it is possible to simply estimate the humidity using an inexpensive temperature sensor such as a thermistor. . In particular, there is a correlation between the room temperature, the evaporation temperature of the heat exchanger, and the room humidity. This relationship is experimentally obtained in advance, and the humidity can be obtained from the room temperature and the evaporation temperature (although the accuracy is reduced). it can. In addition, this relationship can be used effectively when the operation is stopped when the humidity falls to the target value. From experience so far, for example, there is the following relationship between the indoor temperature T ₁ and the evaporation temperature T ₂ when the indoor humidity is about 50%, with A and B being constants.

T ₂ = A × T ₁ -B
Therefore, by detecting the room temperature and the evaporation temperature by the temperature sensor, the evaporation temperature Once made the temperature T ₂ when the indoor humidity of 50% corresponding to the indoor temperature T1, it is possible to perform the humidity control such as stopping the operation . In this case, the appropriate humidity is said to be around 50%, and since it is not as sensitive as the temperature, such humidity control is sufficiently practical. In addition, it can be realized at a lower cost than when using a humidity sensor.

  In addition, although all the examples described so far have been described assuming an air conditioner used in a general building, the present invention is not limited to this, and the present invention is not limited to this. Is also applicable. In such a case, generally, the indoor heat exchanger can be referred to as a utilization side heat exchanger, the outdoor heat exchanger as a heat source side heat exchanger, the indoor fan as a utilization side fan, and the outdoor fan as a heat source side fan.

  The following is a summary of each of the embodiments described above.

  The objective in the said Example is to provide the air conditioner which can perform the dehumidification driving | operation for various uses.

  Another object is to provide an air conditioner that can perform a dehumidifying operation and maintain a sufficiently high performance in a cooling operation and a heating operation.

  Another object of the present invention is to provide an air conditioner that can ensure the indoor air temperature and dehumidification amount at a predetermined temperature and dehumidification amount even when the outdoor temperature changes, and can quickly set the indoor humidity to the set humidity.

  Another object is to provide an air conditioner in which the temperature of the electric components on the outdoor unit side is not excessively high and can maintain a sufficient life.

  In order to achieve the first object, the air conditioner of the above embodiment is an air conditioner including at least a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger, wherein the indoor heat exchanger is Heating capacity of the heating part by controlling the capacity of the compressor, the air volume of the fan of the indoor heat exchanger, and the air volume of the fan of the outdoor heat exchanger during the dehumidifying operation. The heat dissipation amount of the outdoor heat exchanger is controlled.

  Further, in an air conditioner including at least a compressor, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger, the indoor heat exchanger is divided into a cooling / dehumidifying portion, a heating portion, and the cooling / dehumidifying portion that are thermally divided. Having a second throttle device provided between the part and the heating part, and having a control circuit for inputting the temperature detected by the indoor temperature sensor, and the ability of the compressor by the control circuit, The air volume of the fan of the indoor heat exchanger and the air volume of the fan of the outdoor heat exchanger are controlled to control each dehumidifying operation such as cooling, isothermal, and heating.

  Also, in air conditioners equipped with at least a compressor, indoor heat exchanger, expansion device and outdoor heat exchanger, comfortable dehumidification operation, good night / mezama dehumidification operation, mold / tick prevention dehumidification operation, laundry dehumidification operation as dehumidification operation The air flow of the indoor heat exchanger fan is reduced during the night and laziness dehumidifying operation, and the air flow of the indoor heat exchanger fan is increased during the laundry operation. Is.

  Further, in an air conditioner having at least a compressor, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger, the indoor heat exchanger inputs the humidity detected by the indoor humidity detecting means and the indoor humidity detecting means. A control circuit and a mite / mold prevention dehumidifying operation mode at the time of dehumidifying operation, and when the operation mode is set, the humidity detected by the humidity detecting means is in the range of 40% to 60%. In this way, the control circuit controls the capacity of the compressor, the air volume of the fan of the indoor heat exchanger, and the air volume of the fan of the outdoor heat exchanger.

  Further, the control circuit controls the compressor capacity, the air flow rate of the indoor heat exchanger fan, and the air flow rate of the outdoor heat exchanger fan so that the humidity detected by the humidity detecting means is about 50%. Is what you do.

  Further, in an air conditioner having at least a compressor, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger, the indoor heat exchanger has a cooling / dehumidifying portion and a heating portion, and is detected by an indoor temperature sensor. When the difference between the detected room temperature and the set temperature is determined to be negative, the control circuit reduces the heat radiation amount of the outdoor heat exchanger, and Operation control is performed so as to increase the heating capacity.

  Further, in an air conditioner including at least a compressor, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger, a ventilation path is provided for the indoor unit including the indoor heat exchanger to flow in indoor air, And a damper-like opening / closing opening for opening and closing the ventilation path, and the air flow passing through the indoor unit passes through the ventilation path without passing through the indoor heat exchanger and the indoor heat exchanger. In the dehumidifying operation, when the indoor fan has a low air volume, the compressor is controlled from a low capacity to a high capacity and the outdoor fan is controlled from a high air volume to a low air volume. When the indoor fan has a high air flow, the air flow passing through the indoor heat exchanger and the air flow passing through the ventilation path without opening the indoor heat exchanger by opening the opening / closing port provided in the ventilation path are combined. And high air flow, and Low air volume dehumidification operation or high temperature over a wide range of cooling, isothermal, and heating flavors by controlling from low capacity to high capacity while reducing the compression function and controlling the outdoor fan from high air volume to low air volume. Air volume dehumidification operation is performed.

  Further, in an air conditioner including at least a compressor, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger, a ventilation path is provided for the indoor unit including the indoor heat exchanger to flow in indoor air, When the difference between the room temperature detected by the room temperature sensor and the set temperature is almost zero, the opening is opened and the air temperature is detected by the room temperature sensor. When the difference between the room temperature and the set temperature is negative, the opening / closing port is controlled to be closed.

  Further, in an air conditioner including at least a compressor, an indoor heat exchanger, a throttle device, and an outdoor heat exchanger, the indoor heat exchanger has a cooling / dehumidifying portion and a heating portion, and the outdoor heat exchanger is A bypass pipe having a two-way valve is provided, and when the room temperature detected by the room temperature sensor is determined to be lower than the set temperature, the two-way valve is controlled to open during the dehumidifying operation. It is.

  Further, in an air conditioner including at least a compressor, an indoor heat exchanger, a throttle device, and an outdoor heat exchanger, the indoor heat exchanger has a cooling / dehumidifying portion and a heating portion that are thermally divided, and A control circuit for inputting the temperature detected by the indoor temperature sensor, and when the difference between the temperature detected by the indoor temperature sensor and the set temperature is determined to be positive, the control circuit While controlling so that the air volume of the fan of an exchanger may be increased, the rotation speed of a compressor is controlled according to the air volume of the fan of an indoor heat exchanger.

  Further, in an air conditioner including at least a compressor, an indoor heat exchanger, a throttle device, and an outdoor heat exchanger, the indoor heat exchanger has a cooling / dehumidifying portion and a heating portion that are thermally divided, and A control circuit for inputting the temperature detected by the indoor temperature sensor, and when the difference between the temperature detected by the indoor temperature sensor and the set temperature is determined to be substantially zero, the control circuit While controlling the air volume of the fan of a heat exchanger to a medium range, the rotation speed of a compressor is controlled according to the air volume of the fan of an indoor heat exchanger.

  Further, in an air conditioner including at least a compressor, an indoor heat exchanger, a throttle device, and an outdoor heat exchanger, the indoor heat exchanger has a cooling / dehumidifying portion and a heating portion that are thermally divided, and A control circuit for inputting the temperature detected by the indoor temperature sensor, and when the difference between the temperature detected by the indoor temperature sensor and the set temperature is determined to be negative, the control circuit While controlling so that the air volume of the fan of an exchanger may be reduced, the rotation speed of a compressor is controlled according to the air volume of the fan of an indoor heat exchanger.

  Further, in an air conditioner including at least a compressor, an indoor heat exchanger, a throttle device, and an outdoor heat exchanger, the indoor heat exchanger has a cooling / dehumidifying portion and a heating portion that are thermally divided, and It has a control circuit for inputting the temperature detected by the room temperature sensor, and when it is determined that the difference between the temperature detected by the room temperature sensor and the set temperature is negative, the set temperature is set. While controlling the capacity | capacitance of a heater, the rotation speed of a compressor is controlled according to the air volume of the fan of an indoor heat exchanger.

  Further, when the air volume of the fan of the indoor heat exchanger is set to a low air volume, control is performed so as to reduce the capacity of the compressor. Further, when the air volume of the fan of the indoor heat exchanger is set to a high air volume, control is performed so as to increase the capacity of the compressor.

  Further, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger, a detecting means for detecting an outdoor temperature, and the number of rotations of the outdoor fan motor in accordance with a signal from the detecting means And a means for controlling the number of revolutions of the compressor in accordance with a signal from the means for detecting the room temperature to control the room temperature and the dehumidifying capacity.

  An air conditioner having a dehumidifying function in which the indoor heat exchanger is composed of a cooler and a heater is provided with means for controlling the rotational speed of the outdoor fan motor and means for controlling the rotational speed of the compressor. The room temperature and the dehumidifying capacity are controlled by controlling the number of rotations and the number of rotations of the compressor.

  Further, in an air conditioner having a dehumidifying function in which the indoor heat exchanger is composed of a cooler and a heater, a means for controlling the dehumidifying capacity of the indoor heat exchanger while maintaining the temperature of the experience substantially constant independently of the indoor temperature control. It is what has.

  Further, in the air conditioner provided with at least a compressor, an indoor heat exchanger, a throttle device, and an outdoor heat exchanger, the dehumidifying operation has each operation mode of sleep operation, mold, and tick prevention operation, The room temperature and the dehumidifying capacity are controlled by controlling the air volume of the fan of the outdoor heat exchanger and the rotational speed of the compressor in stages.

  Further, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger, a detecting means for detecting an outdoor temperature, and a rotation speed of the compressor according to a signal from the detecting means. And a means for controlling the number of revolutions of the compressor in accordance with a signal from the means for detecting the room temperature and a means for detecting the room temperature, the temperature is controlled to be close to the set temperature, and the humidity is 40 to 60%. The dehumidifying ability is controlled so as to be in the range.

  In addition, in the operation mode of any one of the comfortable dehumidifying operation, mold / tick-preventing dehumidifying operation, good night / lazy dehumidifying operation, and laundry dehumidifying operation, the temperature and humidity suitable for the operation mode are stored in advance, and the temperature sensor The temperature and humidity are detected by a humidity sensor, and the controller performs a dehumidifying operation so that the detected temperature and humidity matches the stored temperature and humidity.

  The cooling / dehumidifying part of the indoor heat exchanger is provided on the windward side of the heating part.

  The heating part of the indoor heat exchanger is provided above the cooling / dehumidifying part.

  The comfortable dehumidifying operation is controlled based on a PMV thermal environment evaluation method, and the dehumidifying operation is performed so that the PMV becomes substantially zero.

  The compressor or blower controls the rotational speed.

  The main expansion device or the dehumidifying expansion device is an electric expansion valve that can be fully opened.

  Further, the refrigerant sealed in the air conditioner is a mixed refrigerant.

  Further, the temperature detecting means is converted by the temperatures detected by the two temperature sensors. Further, the temperature of air blown from the indoor heat exchanger is controlled to be within 3 degrees higher than the set temperature.

  The cooler and the heater of the indoor heat exchanger are arranged in the vertical direction.

  In order to achieve the second object, an air conditioner according to the present invention is an air conditioner including at least a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger, wherein the indoor heat exchanger is a heat exchanger. A cooling / dehumidifying portion and a heating portion that are divided into parts, and a dehumidifying squeezing device used during dehumidifying operation is provided between the cooling / dehumidifying portion and the heating portion, and the cooling / dehumidifying portion and the heating portion of the refrigerant Each of the flow paths is composed of two or more systems.

  In addition, a resistance tube is provided in one of the refrigerant flow paths so that the flow resistances of the respective refrigerant flow paths configured in two or more systems are equal.

  Moreover, the refrigerant flow path of the heat exchanger which becomes an upstream side at the time of air_conditionaing | cooling operation is made into one system among the said indoor heat exchangers.

  Moreover, the refrigerant | coolant outflow part at the time of heating operation is made into one system | strain refrigerant | coolant flow path among the said indoor heat exchangers.

  Further, the indoor heat exchanger has a structure in which a heat transfer tube is brought into close contact with a hole formed in the radiating fin and is divided into two by inserting a cutting line into the radiating fin. The indoor heat exchanger has a structure in which a heat transfer tube is brought into close contact with a hole formed in the radiating fin, and a slit is provided in the radiating fin to thermally divide into two.

  Also, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger, the indoor heat exchanger is divided into two parts by being divided into two parts for use during a dehumidifying operation. While providing a dehumidifying throttle device, the refrigerant | coolant outflow port part at the time of the heating operation of this indoor heat exchanger is provided in the air stream most upstream.

  Also, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger, the indoor heat exchanger is divided into two parts and used during dehumidification operation between the two parts. The dehumidifying throttle device is provided, and the refrigerant outlet portion during the heating operation of the indoor heat exchanger is configured such that no other portion of the indoor heat exchanger is disposed below the refrigerant outlet portion. is there.

  Also, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttle device, and an outdoor heat exchanger, the indoor heat exchanger is divided into two parts and used during the dehumidifying operation between the two parts. In addition to providing a dehumidifying throttle device, the refrigerant inlet portion at the time of heating operation of the indoor heat exchanger is configured such that other portions of the indoor heat exchanger are not disposed on the leeward side of the inlet portion.

  Also, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger, the indoor heat exchanger is divided into two, and the dehumidifying throttling device used during the dehumidifying operation between the two divided And the refrigerant inlet portion during heating operation of the indoor heat exchanger is configured such that no other portion of the indoor heat exchanger is disposed below the inlet portion.

  Also, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger, the indoor heat exchanger is divided into two parts and used during dehumidification operation between the two parts. The dehumidifying squeezing device is provided, and the indoor heat exchanger is built in such a manner that a heat transfer tube is brought into close contact with a hole formed in the radiating fin and a cutting wire is inserted into the radiating fin to divide it into two.

  Also, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger, the indoor heat exchanger is divided into two parts by being divided into two parts for use during a dehumidifying operation. In addition to providing a dehumidifying squeezing device, an indoor heat exchanger is built in such a manner that a heat transfer tube is brought into close contact with a hole formed in the radiating fin, and a slit is provided in the radiating fin to thermally divide into two. .

  In order to achieve the third or fourth object, an air conditioner of the present invention is an air conditioner including at least a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger. The indoor heat exchanger has a cooling / dehumidifying portion and a heating portion that are thermally divided, and the indoor unit includes a humidity detection means for detecting the indoor humidity and a temperature sensor for detecting the outdoor temperature. The control pattern of the compressor rotational speed is put in the control pattern of the outdoor temperature and the outdoor fan motor, the difference between the indoor blowout air temperature and the outdoor fan motor control pattern, and the indoor humidity and the set humidity. The control is to perform optimum operation corresponding to the humidity state and outdoor temperature.

  In the above-described configuration, in the dehumidifying operation for various purposes described above, for example, in the night and laziness dehumidifying operation, a low air volume dehumidifying operation with no airflow feeling and low noise and a large dehumidifying amount is necessary. In particular, high air volume dehumidification operation with a high drying capacity is required because the airflow reaches a wide range. In comfortable dehumidifying operation and mold / tick dehumidifying operation, it is necessary to properly use low air volume dehumidifying operation and high air volume dehumidifying operation. In addition, in addition to the low air volume dehumidifying operation and the high air volume dehumidifying operation, it is necessary to perform a cooling, isothermal or heating operation according to the room temperature.

  Low air volume dehumidification operation can be realized by reducing the air volume of the indoor fan. Furthermore, by controlling the compressor from low capacity to high capacity, or by controlling the outdoor fan from high air volume to low air volume, the air conditioner can be kept warm. Furthermore, the low air volume dehumidifying operation can be performed over a wide temperature range from isothermal to heating.

  In order to perform the high air volume dehumidifying operation, the air volume of the indoor fan is increased and the compressor is operated with the capacity equal to or higher than that in the low air volume dehumidifying operation. On the other hand, when the indoor unit is provided with the opening / closing port and a ventilation path that does not pass through the indoor heat exchanger is provided, the compressor is set to a low capacity state as in the case of the low air volume dehumidifying operation, and the opening / closing port is further opened. A high air volume dehumidifying operation can be performed in a more energy-saving state by adding an air flow that does not pass through the indoor heat exchanger and is increased in air volume. Furthermore, in these high air volume dehumidification operations, the compression function is controlled to a high capacity, or the outdoor fan is controlled from a high air volume to a low air volume, so that the air conditioner has a wide range of air quality from the air condition to the air condition. High air volume dehumidification operation can be performed over a temperature range.

  In addition, by dividing the refrigerant flow path of each indoor heat exchanger divided into two, the refrigerant flow rate in each flow path is reduced in each operation of dehumidification, cooling, and heating, so that the usage-side heat exchanger divided into two It is possible to prevent an increase in pressure loss due to the connection in series, and to prevent a decrease in performance. This effect is particularly great in a cooling operation in which both indoor heat exchangers serve as evaporators. Furthermore, since the outlet channel portion in the heating operation in the indoor heat exchanger is made into one system, an appropriate subcooling of the refrigerant can be taken during the heating operation, and the performance can be secured. Still further, in the indoor heat exchanger, the heat transfer performance is maintained and the performance is ensured by making the refrigerant flow and the air flow as opposite flows as possible.

  In addition, the controller uses the outdoor temperature detected by the temperature sensor to operate the outdoor fan that matches the outdoor temperature by using a data table or an arithmetic expression in which the outdoor fan motor operation pattern and rotation speed are stored in advance. Furthermore, using the indoor humidity detected by the humidity detecting means, the number of rotations of the compressor corresponding to the humidity is determined by a data table stored in advance according to the difference from the set humidity or an arithmetic expression.

  In addition, using the temperature of the indoor blown air detected by the temperature sensor, the operation pattern and the number of revolutions are determined by a data table in which the number of revolutions of the outdoor fan motor and the compressor is stored in advance, or an arithmetic expression.

  According to the air conditioner of the embodiment described above, the use side heat exchanger such as the indoor heat exchanger is divided into two parts, and a dehumidifying throttle device is provided between the use side during the dehumidifying operation. In the refrigeration cycle that cools, dehumidifies, and heats air using one of the heat exchangers as an evaporator and the other as a condenser, capacity control of the use side fans such as indoor fans, heat source side fans such as outdoor fans, and compressors As possible, by appropriately controlling the capacity of these devices, low air volume dehumidification operation and high air volume dehumidification operation can be performed in a state where sufficient dehumidification amount can be obtained. It is possible to perform operation with a slight taste, an isothermal taste, and a cool feeling.

  As a result, dehumidifying operation has been expanded to a wide range of operating modes, such as comfortable dehumidifying operation, good night / medicated dehumidifying operation, mold / tick prevention dehumidifying operation, laundry dehumidifying operation, etc. It is possible to provide an air conditioner that can be used, can satisfy the recently increasing needs for comfort and health, and can be used for purposes other than air conditioning.

  Also, in summer when it is not so hot, instead of cooling operation, it is possible to perform dehumidification operation with the same sensory temperature by lowering the humidity without lowering the room temperature so much, and furthermore, high air volume dehumidification operation can be performed with low input. Energy can be achieved.

  In addition, the refrigerant flow path of each use side heat exchanger divided into two or more systems is prevented to prevent an increase in refrigerant flow resistance in the use side heat exchanger, or heating operation in the refrigerant flow path of the use side heat exchanger Performance by making the outlet part of the hour into a single system so that sufficient refrigerant subcooling can be obtained during heating operation, and the refrigerant flow and air flow in the user-side heat exchanger are made as opposed to each other as much as possible. Can be prevented.

  In addition, the refrigerant flow path of each of the usage-side heat exchangers divided into two systems is changed from one system to a plurality of systems according to the refrigerant flow rate to prevent an increase in refrigerant flow resistance in the usage-side heat exchanger, By making the outlet part during heating operation a single system so that sufficient refrigerant subcooling can be obtained during heating operation, and further, the refrigerant flow and air flow in the use side heat exchanger are made to be as opposed to each other as possible. , Can prevent performance degradation.

  Further, by providing a blow-out temperature sensor and humidity detecting means on the indoor unit side and providing an outside air temperature sensor on the outdoor unit side, it is possible to perform a comfortable dehumidifying operation that meets the conditions during the dehumidifying operation. For example, the lower the outdoor temperature, the higher the rotational speed of the outdoor fan to control the amount of air heating in the room, or the higher the humidity, the higher the rotational speed of the indoor fan or compressor. It is possible to perform a dehumidifying operation in which the room is quickly brought to a predetermined humidity by performing an operation with a large amount of dehumidification, and further, when the room temperature is low, the blowout air temperature of the indoor unit is made higher than the intake air temperature.

  Furthermore, the dehumidifying operation method and the piping configuration of the use side heat exchanger as described above can be applied regardless of a single refrigerant or a mixed refrigerant, and the same effect can be obtained.

It is a figure which shows the structure of the air conditioner which is one Example of this invention. It is a flowchart which shows the driving | operation method of the dehumidification driving | operation for various uses. It is a flowchart which shows the operating method of the compressor in a low air volume dehumidification driving | operation, and a fan. It is a flowchart which shows the operation method of the compressor in a high air volume dehumidification driving | operation, and a fan. It is a sectional side view which shows the indoor unit structure of an air conditioner. It is a flowchart which shows the operation method of the compressor in a high air volume dehumidification driving | operation, and a fan. It is a figure which shows the heat-source side part of the air conditioner which is the other Example of this invention. It is a flowchart which shows the operation method of the heat-source side part corresponding to a heating-like dehumidification operation. It is a figure which shows the piping system of a utilization side heat exchanger. It is a front view of a use side heat exchanger. It is a figure which shows the piping system of a utilization side heat exchanger. It is a side view which shows the piping structure of a utilization side heat exchanger. It is a side view which shows the piping structure of a utilization side heat exchanger. It is a side view which shows the piping structure of a utilization side heat exchanger. It is a side view which shows the piping structure of a utilization side heat exchanger. It is a side view which shows the piping structure of a utilization side heat exchanger. It is a side view which shows the piping structure of a utilization side heat exchanger. It is a side view of the radiation fin of a use side heat exchanger. It is a side view of the radiation fin of a use side heat exchanger. It is a block diagram of an aperture device part. It is a temperature entropy diagram of a refrigerating cycle. It is a figure which shows the structure of the air conditioner which is further another Example of this invention. It is side sectional drawing which shows the other indoor unit structure of an air conditioner. It is a figure which shows the piping system of a utilization side heat exchanger. It is a figure which shows the piping system of a utilization side heat exchanger. It is a figure which shows the structure of the air conditioner of this invention. It is a figure which shows the control method of an outdoor fan. It is a figure which shows the control method of a compressor. It is a figure which shows the control method of an outdoor fan-compressor. It is a figure which shows the structure of the air conditioner by a prior art. It is a figure which shows the control method of a prior art. It is a figure which shows one Example of the driving | running pattern by this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1,201 ... Compressor, 2,202 ... 4-way valve, 3,203 ... Outdoor heat exchanger, 4 ... Main throttle device, 5, 8, 41 ... 2-way valve, 6a, 6b, 51a, 51b, 60a, 60b 60c, 60d, 68, 68 ', 69, 69', 70, 70a, 70b, 80, 80a, 80b, 88, 88a, 88b98, 98a, 98b, 100a, 100b, 100c, 110a, 110b, 208, 209 ... indoor heat exchanger, 7, 210 ... dehumidifying throttle device, 10, 211 ... outdoor fan, 11, 212 ... outdoor fan motor, 12, 213 ... indoor fan, 13, 214 ... indoor fan motor, 16 ... control unit, 17 216 ... temperature sensor 18, 216 ... humidity detection means, 34 ... opening / closing damper, 35 ... ventilation path, 52, 53, 54, 55, 61, 62, 63, 64, 65, 66, 67, 01, 102, 103, 104, 105, 106, 10 ... refrigerant piping, 56, 71, 81, 91, 91a, 91b, 93, 93a, 93b ... radiating fins, 72, 82, 89, 96, 97 ... cut lines 73a, 73b, 73c, 73d, 73e, 73f, 74a, 74b, 74c, 74d, 74e, 74f, 75a, 75b, 75c, 75d, 75e, 75f, 75g, 83a, 83b, 83c, 87a, 87b, 87c 87d, 87e, 87f, 87g, 87h ... Heat transfer tube, 86 ... Resistance tube, 92, 94 ... Slit, 95 ... Electric expansion valve, 204 ... Heating throttle device, 205 ... Heating / cooling throttle device, 206 ... Bypass electromagnetic Valve 207 check valve 210 dehumidifying throttling device 215 outside temperature sensor 217 indoor suction temperature sensor 218 indoor blowout temperature sensor Support.

Claims (1)

Compressor, outdoor heat exchanger, outdoor fan, indoor heat exchanger having a first indoor heat exchanger and a second indoor heat exchanger, a dehumidifying throttle device functioning as a throttling device during dehumidifying operation, and an indoor fan The compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttle device, and the second indoor heat exchanger are connected in this order during the dehumidifying operation, and the compressor, An outdoor heat exchanger, the first indoor heat exchanger, and the second indoor heat exchanger are connected in this order. During the heating operation, the compressor, the second indoor heat exchanger, the first indoor heat exchanger, and the outdoor In the air conditioner connected in the order of the heat exchanger,
The air volume of the indoor fan is variable,
Wherein a mode of operation during the dehumidifying operation, the air volume of the indoor fan is the first air volume, and variable air volume of the outdoor fan, and laundry drying mode for drying the laundry,
Wherein a mode of operation during the dehumidifying operation, the second air volume air volume is less than the first flow rate of the indoor fan, and variable air volume of the outdoor fan, and comfort drying mode humans feel comfortable Air conditioner equipped with .

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