JP2006170503A - Air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air conditioner capable of reducing residual attachment of condensate on a fin of a heat exchanger in a cooling operation, reducing re-evaporation into a room, shortening a time to dry, and reducing return of moisture into the room. <P>SOLUTION: This air conditioner comprises a refrigerating cycle constituted of a compressor, an indoor heat exchanger, a throttle device and an outdoor heat exchanger connected by refrigerant pipes, and a control device for controlling rotational frequency of the compressor according to indoor temperature or indoor humidity, and indoor set temperature or indoor set humidity. The control device implements a water reducing operation for decelerating the compressor in comparison with the rotational frequency of the compressor controlled according to the indoor temperature or indoor humidity, and indoor set temperature or indoor set humidity, for a prescribed time, and then stops the operation or implements the other operation, when the operation applying the indoor heat exchanger as a cooling unit, is stopped, or the operation gives way to the other operation. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an air conditioner, and is particularly suitable for an air conditioner that controls the rotational speed of a compressor.

  When the cooling operation is performed by the air conditioner, the heat exchanger in the indoor unit is cooled because it acts as a cooler of the refrigeration cycle, and condenses moisture contained in the passing indoor air flow. As a result, condensed water adheres to the surface of the heat exchanger. Condensed water dripped from the heat exchanger is collected in a dew receiving tray and discharged to the outside through a drain hose. Further, during the cooling operation, the components such as the blower fan and the surface of the ventilation path, which are constituent members, are cooled by the cold indoor air flow and have a high relative humidity. Therefore, when the cooling operation is finished in such a state, the condensed water remains on the surface of the heat exchanger and the dew tray in the indoor unit, and the high humidity state is maintained until it naturally evaporates and dries. It will be.

  On the other hand, mold spores, bacteria, etc. floating in the indoor air will germinate at a fast position according to the temperature / humidity environment where the temperature / humidity environment can grow and if there is a substance to be used as food. , Start growing. Accordingly, if the amount of the condensed water that remains attached is large, it takes a long time to dry, and the time for maintaining the high humidity state becomes long. If such a viable environment is maintained for a long time, for example, mold spores form spores on the germinated mycelium, and the spores of the grown spores are scattered and reattached. To proliferate. As the growth process proceeds in sequence, odors, mold spores, wastes, etc. due to secretions produced by a large amount of fungi forming colonies are discharged into the room together with the discharged air current, causing discomfort to indoor residents. In addition, when the cooling operation is switched to the dehumidifying operation and the heat exchanger to which the condensed water is attached is heated, the condensed water is returned to the room, so that the indoor humidity rises. Gives you discomfort.

  As one simple solution for preventing such indoor unit contamination, there is a method of suppressing the growth of mold and the like by making the interior of the indoor unit dry because mold spores and bacteria are vulnerable to the dry state. In addition, reducing the condensed water remaining in the heat exchanger is also effective as a method of reducing the humidity returning to the room while keeping the interior of the indoor unit in a dry state to suppress the growth of mold and the like. As this kind of prior art, JP2003-143334A (Patent Document 1), JP2002-286278A (Patent Document 2), JP2003-322385A (Patent Document 3), JP2002-2002A, and the like. No. 221373 (Patent Document 4) is known.

  In Patent Document 1, the heat exchanger is dried by the cycle dry operation and the subsequent air blowing operation at the end of the cooling operation, and the heat exchanger is dried by the air blowing operation at the end of the dehumidifying operation.

  Patent Document 2 is for drying a heat exchanger in a dry mode dehumidifying operation at the end of a cooling operation.

  In Patent Document 3, the compressor is operated at the minimum number of revolutions for a predetermined time after the start of the dehumidifying operation, the temperature rise of the reheater is slowed down, and the condensation attached to the reheater part of the dehumidifying cycle during the cooling operation By restricting the rapid evaporation of water, the sprayed air is prevented from being oversaturated to prevent spraying into the room or splashing water.

  In Patent Document 4, the dehumidifying operation is started from low-speed heating-like dry at the time of switching from the cooling operation to the dehumidifying operation.

JP 2003-14334 A JP 2002-286278 A JP 2003-322385 A JP 2002-221373 A

  In Patent Document 1, although dehumidification is performed in the cycle dry operation, when viewed closely, the condensed water attached to the reheater part of the cycle dry during the cooling operation is once evaporated to return to the room to compensate for it. Thus, it is dehumidified by cycle dry operation. That is, all the condensed water attached to the reheater of the cycle dry during the cooling operation is re-evaporated and returned to the room, and is condensed again in the cycle dry operation and discharged to the outside. Further, the condensed water in the cooler portion of the cycle dry operation is re-evaporated and returned to the room in the subsequent blow drying operation.

  Even in Patent Document 2, all the condensed water attached to the reheater part of the dehumidification cycle is re-evaporated and returned to the room during the cooling operation, and is condensed again in the dry mode dehumidification operation and discharged to the outside. is there. Further, the condensed water attached to the cooler portion in the dry mode dehumidifying operation is left undried.

  In Patent Document 3, the condensed water adhering to the reheater portion of the dehumidification cycle during the cooling operation is slowly evaporated, and finally the entire amount of the condensed water in this portion is re-evaporated and returned to the room. This is condensed again in the dehumidifying operation and discharged outside the room.

  In Patent Document 4, the dehumidifying operation is started from low-speed heating-like dry when switching from the cooling operation to the dehumidifying operation, and the condensed water adhering to the reheater portion of the dehumidifying cycle during the cooling operation is finally The whole amount is re-evaporated and returned to the room, which is condensed again in the dehumidifying operation and discharged outside the room.

  The purpose of the present invention is to reduce the amount of residual condensed water condensed on the fins of the heat exchanger during the cooling operation, reduce re-evaporation into the room, shorten the time to drying, and reduce the moisture in the room. The object is to provide an air conditioner with reduced return.

  The first aspect of the present invention for achieving the above-described object includes a refrigeration cycle in which a compressor, an indoor heat exchanger, an expansion device, and an outdoor heat exchanger are connected by refrigerant piping, and an indoor temperature or an indoor temperature during operation. In an air conditioner comprising a control device that controls the number of revolutions of the compressor according to humidity and indoor set temperature or indoor set humidity, the control device performs an operation using the indoor heat exchanger as a cooler. When stopping or shifting to another operation, the water reducing operation is performed for a predetermined time to reduce the compressor speed by the number of rotations of the compressor controlled according to the room temperature or room humidity and the room set temperature or room set humidity. It is set as the structure controlled so that it may stop or transfer to another driving | operation after starting.

A more preferable specific configuration example in the first aspect of the present invention is as follows.
(1) The control device controls the throttle amount of the throttle device to be smaller than the throttle amount so far during the water reduction operation.
(2) The controller is configured to stop or operate the outdoor blower that ventilates the outdoor heat exchanger at a lower speed than the number of rotations until then during the water reduction operation.
(3) During the water reduction operation, the control device stops the indoor blower passing through the indoor heat exchanger or operates at a lower speed than the number of rotations up to that time.

  The second aspect of the present invention includes a refrigeration cycle in which a compressor, two indoor heat exchangers, a main throttle device, a dehumidifying throttle device, and an outdoor heat exchanger are connected by refrigerant piping, and an indoor temperature during operation. A control device that controls the number of revolutions of the compressor according to the indoor set temperature, and the refrigeration cycle includes a cooling cycle in which both the two indoor heat exchangers are coolers, and the two indoor heats. In the air conditioner that can be switched to a dehumidification cycle in which one of the exchangers is a cooler and the other is a heater, the control device switches from the cooling cycle to the dehumidification cycle after a stop time in the dehumidifying operation mode. The water reducing operation for reducing the speed of the compressor from the number of rotations of the compressor controlled in accordance with the indoor temperature and the indoor set temperature by the cooling cycle is controlled so as to reach a stop time after a predetermined time. It is obtained by a configuration in which.

A more preferable specific configuration example in the second aspect of the present invention is as follows.
(1) The said control apparatus made the predetermined time at the time of the said water reduction operation shorter than the stop time at the time of switching from the said cooling cycle to the said dehumidification cycle.
(2) During the water reduction operation, the control device causes the compressor to run at a lower speed than the number of rotations of the compressor controlled according to the indoor temperature and indoor humidity, the indoor set temperature and the indoor set humidity due to the cooling cycle. To control.

A more preferable specific configuration example in the first or second aspect of the present invention is as follows.
(3) An aluminum fin having a hydrophilic surface is used for the indoor heat exchanger.

  According to the present invention, the remaining amount of condensed water condensed on the fins of the heat exchanger during the cooling operation is reduced, the re-evaporation into the room is reduced, the time until drying is shortened, and the moisture inside the room is reduced. An air conditioner with reduced return can be provided.

  Hereinafter, an air conditioner according to an embodiment of the present invention will be described with reference to the drawings.

  FIG. 1 is a block diagram showing an air conditioner according to an embodiment of the present invention. Reference numeral 10 denotes an indoor unit of an air conditioner, and reference numeral 20 denotes an outdoor unit that performs air conditioning / dehumidification operation in cooperation with the indoor unit 10 to air-condition the room.

  The indoor unit control device 18 includes an indoor temperature detecting means 12 for detecting the indoor temperature, a humidity detecting means 13 for detecting the humidity, an indoor temperature setting means 14 for setting the indoor temperature, and a humidity setting means for setting the indoor humidity. 15. The indoor unit control device 18 creates a rotational speed command value for the compressor 29 based on signals output from the indoor temperature detecting means 12, the humidity detecting means 13, the indoor temperature setting means 14, and the humidity setting means 15, Control of the air blower 11, a wind direction board (not shown), the dehumidifying squeeze device 16, etc. is performed.

  The outdoor unit control device 28 inputs a signal sent from the indoor unit control device 18 and controls the compressor 29, the outdoor blower 21, the cooling / heating throttle device 26, the four-way valve 30, and the like. The indoor unit control device 18 and the outdoor unit control device 28 constitute a control device.

  Further, as shown in FIG. 4, the refrigeration cycle of the air conditioner according to the present embodiment includes a compressor 29, a four-way valve 30, an outdoor heat exchanger 31, an air conditioner / throttle device 26, and a first indoor heat exchanger 32a ( A reheater at the time of dehumidifying operation), a dehumidifying throttle device 16, and a second indoor heat exchanger 32b (cooler at the time of dehumidifying operation), and these components are connected by refrigerant piping in this order. . In addition, the 1st indoor heat exchanger 32a and the 2nd indoor heat exchanger 32b which comprise the indoor heat exchanger 32 (The code | symbol of 32 is abbreviate | omitted illustration) are the fin tube type heat exchange which has the fin hydrophilized. It is composed of a vessel. The cooling / heating throttle device 26 is constituted by an electric expansion valve. The dehumidifying throttle device 16 includes a dehumidifying expansion valve 16a and a dehumidifying on / off valve 16b.

  First, the operation of the refrigeration cycle during the cooling operation will be described. The high-temperature and high-pressure gas refrigerant compressed by the compressor 29 flows into the outdoor heat exchanger 31 via the four-way valve 30 switched to the cooling / dehumidifying operation side, and releases heat to the outside air by the outdoor heat exchanger 31. This condenses into a high-pressure liquid refrigerant.

  This refrigerant is reduced in pressure while passing through the air conditioning / throttle device 26 and becomes a low-temperature and low-pressure refrigerant and flows into the indoor unit 10. During the cooling operation, the expansion valve 16a of the dehumidifying expansion device 16 is fully opened and does not perform the throttling action, so both the first indoor heat exchanger 32a and the second indoor heat exchanger 32b function as coolers.

  On the other hand, indoor air is sucked in by the indoor blower 11 and is circulated through the first indoor heat exchanger 32a and the second indoor heat exchanger 32b, and heat is exchanged with the refrigerant to cool the circulating air. If the refrigerant temperature is low, moisture in the inflowing air is condensed and discharged to the outside as condensed water, and the cooled and dehumidified air is blown out into the room.

  Next, the operation of the refrigeration cycle during the dehumidifying operation will be described. The high-temperature and high-pressure gas refrigerant compressed by the compressor 29 flows into the outdoor heat exchanger 31 through the four-way valve 30 switched to the cooling / dehumidifying operation side.

  During the dehumidifying operation, the outdoor blower 21 rotates at a dehumidifying rotational speed that is lower than that during the cooling operation. Therefore, heat release from the outdoor heat exchanger 31 to the outside air is reduced, and part of the high-pressure refrigerant is not condensed. Will remain. Since the air conditioning and throttling device 26 is fully opened during the dehumidifying operation, the partially uncondensed high-pressure refrigerant flows into the first indoor heat exchanger 32a of the indoor unit 10 as it is.

  The high-pressure refrigerant partially uncondensed in the first indoor heat exchanger 32a radiates and liquefies the indoor air circulated by the indoor blower 11, and the first indoor heat exchanger 32a functions as a reheater. During the dehumidifying operation, the dehumidifying on-off valve 16b is closed and the dehumidifying expansion valve 16a performs a predetermined throttling action, so that the liquefied refrigerant that has entered the dehumidifying expansion valve 16a from the first indoor heat exchanger 32a is decompressed to become a low-temperature and low-pressure refrigerant. Then, the air enters the second indoor heat exchanger 32b and functions as a cooler to cool and dehumidify the indoor air circulated by the indoor blower 11.

  As a result, the indoor air sucked by the indoor blower 11 is heated by the first indoor heat exchanger 32a and cooled and dehumidified by the second indoor heat exchanger 32b. Is blown into the room as dry air.

  Next, the operation of the indoor unit control device 18 will be described with reference to FIGS. FIG. 2 shows changes over time in room temperature, humidity, and compressor rotation speed when switching from cooling operation to dehumidification operation when the air conditioner operation mode of the present embodiment is set to the dehumidification mode. FIG. 3 is a flowchart for explaining the operation details of FIG. The description will be made assuming that the condition of the air-conditioned room is high temperature and high humidity.

  When the air-conditioning operation mode is set to the dehumidifying mode, at the start of operation, if the room temperature is higher than the indoor set temperature, the cooling operation is performed, the indoor temperature is lower than the indoor set temperature, and the indoor humidity is higher than the indoor set humidity. If so, dehumidify. When the room temperature is lower than the indoor set temperature and the indoor humidity is lower than the indoor set humidity, the fan 11 and the compressor 29 are stopped and the room temperature and humidity are monitored.

  In this case, since the room is assumed to be hot and humid, the air conditioner performs a cooling operation at the start of operation, and the rotation speed of the compressor 29 is a value corresponding to the temperature difference between the room temperature and the room set temperature. As the time elapses, the room temperature approaches the room set temperature and the humidity decreases, and the rotational speed of the compressor 29 also decreases from Nc1 to Nc4.

  When the indoor temperature reaches TS-Th obtained by subtracting the hysteresis (Th ° C.) determined so that the air conditioner does not respond sensitively from the indoor set temperature (TS ° C.), the indoor unit controller 18 is attached to the cooler. The condensed water that has flowed down is quickly flowed down, and the water reduction operation control is started to reduce the amount of condensed water remaining in the indoor heat exchanger 32 (cooler).

  In step S1, water reduction operation control is started. In step S2, the rotation speed of the compressor 29 is checked. If the rotation speed is low (Nps) suitable for the predetermined water reduction operation, the process proceeds to step S30. Otherwise, the process proceeds to step S10.

  Immediately after entering the water reduction operation control, since the rotation speed of the compressor 29 is controlled to a value corresponding to the temperature difference between the room temperature and the indoor set temperature and does not rotate at a low speed, the process proceeds to step S10 and a predetermined water reduction operation is performed. The operation time (t minutes) is set as a large interval, and the control interval determined so that the response of the refrigeration cycle does not become hypersensitive in step S11 is set as a small interval. Since the operation time of this water reduction operation causes an increase in power consumption if it is too long, it is set shorter than the stop time provided when switching from the cooling operation to the dehumidifying operation.

  Next, in step S12, the rotation speed of the compressor 29 is reduced to a low speed rotation speed (Nps) suitable for water reduction operation, and in step S13, the cooling / heating expansion device 26, which is the expansion device of the main refrigerant circuit at the time of cooling operation, is loosened to reduce water operation. In step S14, the outdoor unit 20 is instructed to control the outdoor blower 21 to a low speed suitable for water reduction operation. The low-speed rotation speed (Nps) suitable for the water reduction operation is set lower than the rotation speed of the compressor 29 controlled to a value corresponding to the temperature difference between the indoor temperature and the indoor set temperature.

  The reason why the rotation speed of the compressor 29 is reduced in this way is that the amount of refrigerant circulating in the refrigeration cycle during the water reduction operation decreases, the evaporation pressure of the indoor heat exchanger increases, and the evaporation temperature increases. Is intended. In addition, the air-conditioning expansion / contraction device 26 is loosened in order to increase the evaporation pressure of the indoor heat exchanger and increase the evaporation temperature. The reason why the outdoor fan 21 is set to a low speed is that the condensation pressure rises and the evaporation pressure rises and the evaporation temperature rises.

  The influence of each change amount on the evaporation temperature is not constant, and changes depending on the amount of other change amounts and the change amount of the rotational speed of the indoor blower described later. For this reason, detailed examination is performed in advance, and the above-described rotation speed of the compressor 29, the amount of restriction of the cooling / heating throttle device 26, the amount of change in the number of rotations of the outdoor fan 21, and the amount of change in the number of rotations of the indoor fan 11 to be described later are in an appropriate range. It is necessary to prescribe in

  Next, in step S15, the rotational speed of the indoor blower 11 is set to a predetermined initial designated rotational speed (NFps0). In step S25, the indoor blower 11 is operated at a low speed at this initial designated rotational speed (NFps0), and in step S40. finish.

  The reason why the rotational speed of the indoor blower is reduced in this way is to reduce the amount of indoor air moisture condensed into the fins when the temperature of the fins of the indoor heat exchanger is low during the water reduction operation, and the water reduction operation. Even when the temperature of the fins of the indoor heat exchanger rises excessively, the amount of reevaporation from the droplets is intended to be suppressed to a small amount.

  Thereafter, the indoor unit control device 18 leaves the water reduction operation control at one end, and after controlling other devices of the indoor unit 10, returns to the water reduction operation control again, and resumes the water reduction operation control in step S1.

  After restarting the water reduction operation control, the rotational speed of the compressor 29 is checked in step S2. The compressor 29 has a low speed rotational speed (Nps) suitable for the water reduction operation determined in advance in step S12. If it is within the operation time of the water reduction operation, the process proceeds to step S20, and if the operation time of the water reduction operation has elapsed, the process proceeds to step S31.

  The operation time of reduced water operation varies depending on the remaining amount of condensed water on the cooler, the room temperature, the degree of change in humidity, the type of air conditioning operation mode, and the structure of the cooler, and requires careful consideration in advance. If it progresses to step S20, if the small interval has not passed, it will progress to step S40, will be complete | finished, will wait for the appropriate response of a refrigerating cycle, and will repeat the same flow.

  If the small interval has elapsed in step S20, the process proceeds to step S21, the small interval is set again, and the process proceeds to step S22. In step S22, the dew point temperature (Td) of the intake air is calculated based on the data from the room temperature detecting means 12 and the humidity detecting means 13, and in step S23, the first air functioning as a cooler during the cooling operation and serving as the heater during the dehumidifying operation. The temperature (Tc) of the indoor heat exchanger 32a is detected.

  Next, in step S24, it is proportional to the difference (Td-Tc) between the dew point temperature (Td) and the temperature (Tc) of the first indoor heat exchanger 32a and the commanded rotational speed (NFps) to the indoor blower 11 so far. The amount of increase ΔNFps of the rotational speed to be calculated is calculated, and in addition to the commanded rotational speed (NFps) to the indoor blower 11 until that time, a new commanded rotational speed (NFps) is set. In step S25, the indoor blower 11 is set to a new commanded rotational speed (NFps). ) And finishes in step S40.

  The rotational speed of the indoor blower 11 is controlled in this manner by setting the temperature of the fins of the first indoor heat exchanger 32a close to the dew point temperature of the indoor air and suppressing further condensation of the indoor air moisture. It is intended to suppress the re-evaporation of the condensed water attached to the fins into the room air.

  Here, as a method for controlling the rotation speed of the indoor blower 11, in the embodiment, the difference (Td−Tc) between the dew point temperature (Td) and the temperature (Tc) of the first indoor heat exchanger 32a and the indoor blower up to that point. 11, a method of adding the amount of increase ΔNFps in proportion to the indicated rotational speed (NFps) to 11 to the previous indicated rotational speed (NFps) to the indoor blower 11 is employed, but the present invention is not limited to this. The method is not limited as long as the temperature (Tc) of the first indoor heat exchanger 32a is brought close to the dew point temperature (Td) in the room.

  Further, when the large interval that is the water reduction operation time has elapsed in step S30, the process proceeds to step S31, where the compressor 29 is stopped, and in step S32, the cooling / heating expansion device 26, which is the expansion device of the main refrigerant circuit during the cooling operation, is fully opened. In step S33, the outdoor unit 20 is instructed to stop the outdoor blower 21. Next, the water reduction operation flag is set to “end” in step S34, and the water reduction operation control is ended in step S40.

  Thereafter, the control of the indoor unit control device 18 shifts to the control of other devices of the indoor unit 11 and the control of the dehumidifying operation, and the restart prohibition time for balancing the refrigerant pressure on the high pressure side and the refrigerant pressure on the low pressure side of the refrigeration cycle. After the (stop time), the dehumidifying throttle device 16 is adjusted to an appropriate throttle amount, and the compressor 29 is dehumidified at the dehumidifying start rotation speed (Nd0) with the indoor blower 11 and the outdoor blower 21 set to rotation speeds suitable for dehumidification operation. After operating for the start-up holding time, the dehumidifying operation is continued by operating at the room temperature and the indoor set temperature and / or the rotational speed (Nd1) corresponding to the indoor humidity and the indoor set humidity.

  By doing in this way, the evaporation pressure of the indoor heat exchanger 32 of the refrigeration cycle increases during the water reduction operation that is the operation for a predetermined time, and the evaporation temperature increases. For this reason, the temperature of the fin of the indoor heat exchanger 32 also rises, and the temperature of the condensed water adhering to the indoor heat exchanger 32 as a droplet does not flow down but also rises.

  As the temperature of the dew condensation water rises, the surface tension of the dew condensation water decreases, the surface of the droplet is broken and the dew condensation water flows down, and the viscosity also decreases, and the flow of the dew condensation water becomes even smoother. For this reason, before the water reduction operation, a large amount of the condensed water remaining in the fins of the heat exchanger without flowing down flows down as the water reduction operation is performed and falls to the dew pan provided at the lower part of the heat exchanger. It is discharged to the outside through a drain pipe connected to. In addition, when the temperature of the fins of the indoor heat exchanger 32 is low during the water reduction operation, it is possible to suppress the amount of moisture in the indoor air condensed to the fins, and also when the temperature of the fins of the indoor heat exchanger 32 is high. It is possible to suppress the amount of condensed water attached to the fins of the indoor heat exchanger and re-evaporating into the room.

  In addition, although a present Example demonstrates the case where it transfers to cooling dehumidification operation from cooling operation, this invention is not limited to this, the transfer from cooling operation to heating operation or ventilation operation, cycle dehumidification operation The same effect can be obtained by switching from air conditioning to heating operation or air blowing operation, even in the same cycle dehumidifying operation, from cooling air dehumidifying operation to heating air dehumidifying operation, cooling operation stop, and similar water draining operation even when dehumidifying operation is stopped. Can be obtained.

  Although the present embodiment describes the case where the rotation speed of the compressor 29 is controlled in accordance with the room temperature and the room set temperature, the present invention is not limited to this, and the room humidity and the room setting are controlled. When controlling the rotation speed of the compressor 29 according to the humidity, also when controlling the rotation speed of the compressor 29 according to the indoor temperature and humidity, the indoor set temperature and the indoor set humidity, by performing the same draining operation, Similar effects can be obtained.

  Further, as an example of operating the indoor heat exchanger 32 as a cooler, the present embodiment describes the case of the cooling operation. However, the present invention is not limited to this, and the indoor heat exchanger includes a cooler and a cooler. Even in the case of the cycle dehumidifying operation having the reheater, the same effect can be obtained by performing the same draining operation.

  In addition, the present embodiment describes the case of using an electric expansion valve for air conditioning that is placed in an outdoor unit as a main refrigerant circuit throttle device, but the present invention is not limited to this, and a two-way valve and A combination of a capillary tube or two-way valve and a mechanical expansion valve may be used, and in the case of stopping or shifting from cycle dehumidification operation, the dehumidifying throttling device placed in the indoor unit becomes the main refrigerant circuit throttling device, and similarly The same effect can be obtained by performing the same draining operation even with an electric expansion valve, a two-way valve and a capillary tube, or a combination of a two-way valve and a mechanical expansion valve.

  Moreover, although the present Example demonstrates the case where the superhydrophilized fin is used for a cooler, this invention is not limited to this, When the hydrophilized fin is used for a cooler Although the effect is slightly reduced compared to the use of fins that have been subjected to superhydrophilic treatment, the amount of retained water is reduced compared to fins that have not been hydrophilized, and the amount of reevaporation into the room is suppressed. By performing the draining operation, a useful result can be obtained although the effect is slightly reduced as compared with the case of using the superhydrophilic fin.

  Note that there are many techniques such as JP 2003-336986 A, JP 2002-90084 A, and JP 2002-71298 A as fins subjected to superhydrophilic treatment, so that the balance between cost and performance is balanced. An appropriate method may be selected in consideration of the above.

  Further, in this embodiment, the room temperature and the room humidity are detected, and the dew point temperature is obtained by calculation from the detection result, but the present invention is not limited to this, only the room temperature is detected, and the humidity is, for example, Even if the calculation is performed assuming 55 to 65% for the cooling operation and 45 to 55% for the dehumidifying operation, the error slightly increases, but a practically useful result can be obtained.

  In addition, the correlation between the room temperature during cooling and dehumidifying operation, the temperature of the cooler, and the dew point temperature is experimentally obtained to obtain a correlation formula or correlation table. The dew point temperature may be calculated or read from the above correlation equation or correlation table, and any of them can provide useful results.

  In this embodiment, the compressor speed and the outdoor fan speed are reduced, the main refrigerant circuit throttle device 26 is loosened, and the speed of the indoor fan 11 is changed to control the cooler temperature. However, the present invention is not limited to this, and the rotational speed of the indoor blower 11 is reduced, and the rotational speed of the compressor 29, the rotational speed of the outdoor blower 21 or the throttle amount of the main refrigerant circuit 26 is changed. The cooler temperature may be controlled, and a similar effect can be obtained by performing a similar draining operation.

  Further, in this embodiment, the rotational speed of the indoor blower 11 is obtained by calculation from the correlation obtained experimentally, but the present invention is not limited to this, for example, the temperature and dew point of the cooler. The correlation is experimentally obtained from the temperature and the rotational speed of the indoor blower 11 to obtain a correlation formula or a correlation table, and the rotational speed of the indoor blower 11 at which the cooler temperature and the dew point temperature coincide with each other is calculated using the above-described correlation formula or correlation. Calculations or readings from the table may be used, both of which can yield useful results.

  As described above, according to the present embodiment, the refrigeration cycle in which the compressor, the indoor heat exchanger, the expansion device, and the outdoor heat exchanger are connected by the refrigerant pipe, the room temperature or the room humidity and the room setting during operation. An air conditioner including a control device that controls the rotation speed of the compressor according to temperature or indoor set humidity, wherein the control device stops the operation using the indoor heat exchanger as a cooler or other When shifting to operation, the water-reducing operation is performed for a predetermined time to reduce the speed of the compressor based on the rotation speed of the compressor controlled according to the room temperature or room humidity and the room set temperature or room set humidity, and then stopped. Alternatively, since the control is performed so as to shift to another operation, the circulation amount of the refrigerant circulating in the refrigeration cycle during the water reduction operation is decreased, the evaporation pressure of the indoor heat exchanger is increased, and the evaporation temperature is increased. For this reason, the temperature of the fin of the heat exchanger also rises, and the temperature of the condensed water adhering as droplets without flowing down also rises.

  As the temperature of the dew condensation water rises, the surface tension of the dew condensation water decreases, the surface of the droplet breaks, and the dew condensation water flows down. For this reason, before operating the compressor at low speed, a large amount of condensed water that has not flowed down and remains on the fins of the heat exchanger flows down as the compressor operates at low speed. It falls to the dew receiving tray provided in and is discharged to the outside through a drain pipe connected to the dew receiving tray.

  For this reason, the amount of condensed water remaining in the heat exchanger due to re-evaporation or other air-conditioning operation can be reduced to a small amount and return to the room, so it is condensed on the heat exchanger fins during cooling operation. Thus, it is possible to obtain an air conditioner that reduces the amount of residual condensed water remaining, reduces re-evaporation into the room, shortens the time until drying, and suppresses the return of moisture to the room.

  In addition, the air conditioner according to the present embodiment is configured such that, during the predetermined time operation, the main refrigerant circuit throttle device has the throttle amount smaller than the throttle amount so far, so that the high temperature side pressure and the low temperature of the refrigeration cycle can be reduced during the predetermined time operation. The difference in side pressure decreases, the evaporation pressure of the indoor heat exchanger increases, and the evaporation temperature increases. For this reason, the temperature of the fin of the heat exchanger also rises, and the temperature of the condensed water adhering as droplets without flowing down also rises.

  As the temperature of the dew condensation water rises, the surface tension of the dew condensation water decreases, the surface of the droplet breaks, and the dew condensation water flows down. For this reason, before operating the compressor at low speed, a large amount of condensed water that has not flowed down and remains on the fins of the heat exchanger flows down as the compressor operates at low speed. It falls to the dew receiving tray provided in and is discharged to the outside through a drain pipe connected to the dew receiving tray.

  For this reason, the amount of condensed water remaining in the heat exchanger due to re-evaporation or other air-conditioning operation can be reduced to a small amount and return to the room, so it is condensed on the heat exchanger fins during cooling operation. Thus, it is possible to obtain an air conditioner that reduces the amount of residual condensed water remaining, reduces re-evaporation into the room, shortens the time until drying, and suppresses the return of moisture to the room.

  Further, the air conditioner according to the present embodiment stops the outdoor blower during the predetermined time operation or operates at a lower speed than the rotation speed up to that time, thereby exchanging heat of the high-temperature side heat exchanger of the refrigeration cycle during the predetermined time operation. Since the capacity decreases, the high temperature side pressure rises, and accordingly, the low temperature side pressure also rises, so that the evaporation temperature of the indoor heat exchanger rises.

  For this reason, the temperature of the fin of the heat exchanger also rises, and the temperature of the condensed water adhering as droplets without flowing down also rises. As the temperature of the dew condensation water rises, the surface tension of the dew condensation water decreases, the surface of the droplet breaks, and the dew condensation water flows down.

  For this reason, before operating the compressor at low speed, a large amount of condensed water that has not flowed down and remains on the fins of the heat exchanger flows down as the compressor operates at low speed. It falls to the dew receiving tray provided in and is discharged to the outside through a drain pipe connected to the dew receiving tray.

  For this reason, the amount of condensed water remaining in the heat exchanger due to re-evaporation or other air-conditioning operation can be reduced to a small amount and return to the room, so it is condensed on the heat exchanger fins during cooling operation. Thus, it is possible to obtain an air conditioner that reduces the amount of residual condensed water remaining, reduces re-evaporation into the room, shortens the time until drying, and suppresses the return of moisture to the room.

  Further, the air conditioner according to the invention of the present embodiment stops the indoor blower during the predetermined time operation or operates at a lower speed than the rotation speed until then, so that the temperature of the fins of the indoor heat exchanger can be increased during the predetermined time operation. Reduces the amount of indoor air moisture condensing into the fins when the temperature is low, and the temperature of the condensed water adhering as liquid droplets increases too much during the specified time operation due to the temperature of the fins of the indoor heat exchanger rising too high Even if the temperature rises above the dew point temperature, the indoor blower is stopped or operated at a lower speed than the rotation speed so far, so the amount of reevaporation during operation for a predetermined time from the droplets can be suppressed to a small amount. It is possible to obtain an air conditioner that reduces the re-evaporation of the condensed water condensed on the fins of the indoor heat exchanger and suppresses the return of moisture to the room.

  In addition, the air conditioner according to this embodiment uses aluminum fins having a hydrophilic surface on the heat exchanger used as a cooler, so that the air conditioner remains as droplets without flowing down to the fins of the heat exchanger. This reduces the amount of condensed water that is re-evaporated and returns to the room indoors, so that the amount of condensed water that has condensed on the fins of the heat exchanger during cooling operation can be reduced and It is possible to obtain an air conditioner that reduces evaporation, shortens the time until drying, and suppresses the return of moisture to the room.

  In addition, the air conditioner according to the present embodiment has the temperature of the indoor heat exchanger that has been cooled until that time is lower than the indoor dew point temperature at the time of the predetermined time operation, and is higher than that at the time of the previous cooling operation. By operating as described above, the evaporation pressure of the indoor heat exchanger increases during the predetermined time operation, and the evaporation temperature increases. For this reason, the temperature of the fin of the heat exchanger also rises, and the temperature of the condensed water adhering as droplets without flowing down also rises.

  However, since the temperature of the heat exchanger is set to the dew point temperature or less, the temperature of the dew condensation water becomes the dew point or less, and the amount of re-evaporation during the draining operation is reduced. Although the dew point temperature is below the dew point temperature, the condensed water temperature rises during the cooling operation, the surface tension of the condensed water decreases, the surface of the droplet breaks and the condensed water flows down. The flow becomes even smoother.

  For this reason, before operating the compressor at low speed, a large amount of condensed water that has not flowed down and remains on the fins of the heat exchanger flows down as the compressor operates at low speed. It falls to the dew receiving tray provided in and is discharged to the outside through a drain pipe connected to the dew receiving tray.

  For this reason, the amount of condensed water remaining in the heat exchanger due to re-evaporation or other air-conditioning operation can be reduced to a small amount and return to the room, so it is condensed on the heat exchanger fins during cooling operation. Thus, it is possible to obtain an air conditioner that reduces the amount of residual condensed water remaining, reduces re-evaporation into the room, shortens the time until drying, and suppresses the return of moisture to the room.

It is a block diagram which shows the air conditioner which concerns on one Example of this invention. It is the graph which showed the time change of room temperature, humidity, and compressor rotation speed when switching from the cooling operation of the air conditioner of FIG. 1 to a dehumidification operation. It is a flowchart explaining the operation | movement detail of FIG. It is a figure which shows the refrigerating cycle of the air conditioner of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Indoor unit of air conditioner, 11 ... Indoor blower, 12 ... Room temperature detection means, 13 ... Humidity detection means, 14 ... Room temperature setting means, 15 ... Humidity setting means, 16 ... Dehumidification throttle device, 16a ... Dehumidification expansion valve, 16b ... dehumidifying on-off valve, 17 ... cooler temperature detecting means, 18 ... indoor control device, 20 ... outdoor unit of air conditioner, 21 ... outdoor blower, 26 ... air conditioning and throttling device, 28 ... outdoor control device, 29 ... compressor 30 ... Four-way valve, 31 ... Outdoor heat exchanger, 32 ... Indoor heat exchanger, 32a ... First indoor heat exchanger, 32b ... Second indoor heat exchanger.

Claims (8)

The compressor, the indoor heat exchanger, the expansion device, and the outdoor heat exchanger are connected by refrigerant piping, and the compressor is operated according to the indoor temperature or humidity and the indoor set temperature or indoor set humidity during operation. In an air conditioner equipped with a control device for controlling the rotational speed,
The control device is configured such that when the operation using the indoor heat exchanger as a cooler is stopped or shifted to another operation, the compression is controlled according to an indoor temperature or an indoor humidity and an indoor set temperature or an indoor set humidity. An air conditioner that is controlled so as to stop or shift to another operation after performing a water-reducing operation in which the compressor is driven at a lower speed than the number of rotations of the machine.   2. The air conditioner according to claim 1, wherein the control device controls a throttle amount of the throttle device to be smaller than a throttle amount so far during the water reduction operation.   2. The air conditioner according to claim 1, wherein the control device is configured to stop or operate an outdoor blower that ventilates the outdoor heat exchanger at a speed lower than a rotational speed until then during the water reduction operation. Machine.   2. The air conditioner according to claim 1, wherein the control device is configured to stop or operate the indoor blower that ventilates the indoor heat exchanger at a lower speed than the number of rotations until then during the water reduction operation. Machine. A compressor, two indoor heat exchangers, a main throttle device, a dehumidifying throttle device, and an outdoor heat exchanger connected by refrigerant piping, and the compressor according to the indoor temperature and the indoor set temperature during operation. A control device that controls the number of revolutions, and the refrigeration cycle includes a cooling cycle in which both of the two indoor heat exchangers are coolers, and one of the two indoor heat exchangers is used as a cooler and the other is heated. In an air conditioner that can be switched to a dehumidification cycle
In the dehumidifying operation mode, when the controller switches from the cooling cycle to the dehumidifying cycle after a stop time, the control device controls the rotation speed of the compressor controlled according to the indoor temperature and the indoor set temperature by the cooling cycle. An air conditioner characterized by controlling the water reduction operation at a low speed of the compressor so as to reach a stop time after a predetermined time.   6. The air conditioner according to claim 5, wherein the control device makes a predetermined time during the water reduction operation shorter than a stop time when switching from the cooling cycle to the dehumidification cycle.   6. The air conditioner according to claim 5, wherein the control device controls the number of revolutions of the compressor controlled in accordance with an indoor temperature, an indoor humidity, an indoor set temperature, and an indoor set humidity by the cooling cycle during the water reduction operation. The air conditioner is characterized in that the compressor is controlled at a low speed. 6. The air conditioner according to claim 1, wherein aluminum fins having a hydrophilic surface are used for the indoor heat exchanger.

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