JP6622631B2 - Outside air treatment device - Google Patents

Description

  The present invention relates to an outside air processing apparatus that processes outdoor air and supplies dehumidified air or humidified air to a target room.

  Conventionally, an outside air processing system that combines an outside air processing device that takes in outside air and an internal circulation type high sensible heat air conditioner has been proposed (see, for example, Patent Document 1).

  A general air conditioner has both a function of reducing room temperature during cooling (sensible heat cooling) and a function of reducing humidity (latent heat cooling). However, since the high sensible heat air conditioner mainly performs only room temperature control (sensible heat cooling) and does not perform dehumidification (latent heat cooling), the target room humidity may not be adjusted to a desired humidity. Therefore, the humidity is adjusted by the outside air processing device. In the technique disclosed in Patent Document 1, the dehumidifying capacity of the outside air processing device is insufficient in a high-humidity situation in midsummer, resulting in poor indoor comfort.

JP 2011-80694 A

  As described above, in the technique disclosed in Patent Document 1, there is a case where the dehumidifying capacity of the outside air processing device is insufficient, and there is a problem that condensation occurs in the high sensible heat air conditioner and efficiency is lowered.

  The present invention has been made in order to solve such a conventional problem, and an object of the present invention is to provide an outside air treatment apparatus having sufficient dehumidifying ability and humidifying ability throughout the year and having excellent humidity controllability. Is to provide.

  In order to achieve the above object, the present invention relates to a flow path of air from the outdoor to the indoor in an outdoor air processing apparatus that supplies the dehumidified air or humidified air by processing the outdoor air into the room of the target room. The first air flow path, the second air flow path serving as a flow path of air from the room to the outside, the first air flow path, and the first air flow path. A moisture adsorbing means for adsorbing moisture in the air flowing through one of the channel and the second air channel and releasing moisture into the air flowing through the other channel, and a refrigerant circuit for circulating the refrigerant. The refrigerant circuit includes a compressor for compressing the refrigerant, a first heat exchanger disposed on the upstream side of the moisture adsorbing means in the second air flow path, and a third heat disposed on the downstream side. A second heat disposed upstream of the moisture adsorbing means in the exchanger and the first air flow path; In the dehumidification mode in which the dehumidified air is supplied indoors to the exchanger, the refrigerant output from the compressor is supplied to the first heat exchanger and the third heat exchanger, and the humidified air is supplied indoors. In the humidifying mode, the output switching means for switching to supply the refrigerant output from the compressor to the second heat exchanger, and a first provided between the first heat exchanger and the second heat exchanger. 1 expansion valve, a second expansion valve provided between the third heat exchanger and the second heat exchanger, the opening degree of the first expansion valve and the second expansion valve are controlled, and Control means for controlling the output switching means, a temperature detection unit for detecting the temperature of the air returned from the room, and a humidity detection unit for detecting the humidity of the air returned from the room. In the dehumidifying mode, output from the compressor The medium is joined from the output side of the first heat exchanger through the path through the first expansion valve and from the output side of the third heat exchanger through the path through the second expansion valve, and then In the humidification mode, the refrigerant that is output from the compressor is circulated from the output side of the second heat exchanger to the first expansion valve and the first heat. A refrigerant flow path is set so as to circulate the path passing through the exchanger and the path passing through the second expansion valve and the third heat exchanger, and the temperature detected by the temperature detection unit, The output of the compressor is controlled based on the humidity detected by the humidity detector so that the indoor humidity becomes a preset target humidity.

  In the outside air processing apparatus according to the present invention, it is possible to provide an outside air processing apparatus that has sufficient dehumidifying ability and humidifying ability throughout the year and is excellent in controllability of humidity in the target room.

It is a flowchart which shows roughly the flow of the air of the external air processing apparatus which concerns on one Embodiment of this invention, (a) shows dehumidification mode, (b) shows humidification mode. It is explanatory drawing which shows typically a mode that the external air processing apparatus which concerns on one Embodiment of this invention is connected to the object chamber. It is explanatory drawing which shows the structure of the refrigerant circuit of the external air processing apparatus which concerns on one Embodiment of this invention. It is a block diagram which shows the electrical connection relation of the external air processing apparatus which concerns on one Embodiment of this invention. It is a flowchart which shows the flow of the refrigerant | coolant of the refrigerant circuit at the time of dehumidification mode of the external air processing apparatus which concerns on one Embodiment of this invention. It is a flowchart which shows the flow of the refrigerant | coolant of the refrigerant circuit at the time of the humidification mode of the external air processing apparatus which concerns on one Embodiment of this invention. It is explanatory drawing which shows the transition of the operation mode of the external air processing apparatus which concerns on one Embodiment of this invention. It is explanatory drawing which shows the switching point of the operation mode of the external air processing apparatus which concerns on one Embodiment of this invention. It is a flowchart which shows the process sequence of the external air processing apparatus which concerns on one Embodiment of this invention. It is a flowchart which shows the control procedure of the compressor at the time of dehumidification mode concerning one Embodiment of this invention. It is a flowchart which shows the procedure of the expansion valve control in the dehumidification mode according to one embodiment of the present invention. It is a flowchart which shows the control procedure of the compressor at the time of humidification mode concerning one Embodiment of this invention. It is a flowchart which shows the procedure of the expansion valve control in the humidification mode according to one embodiment of the present invention. It is explanatory drawing which shows the example of the temperature in each site | part at the time of dehumidification mode, relative humidity, and absolute humidity concerning one Embodiment of this invention. It is explanatory drawing which shows the example of the temperature in each site | part at the time of humidification mode, relative humidity, and absolute humidity concerning one Embodiment of this invention. It is explanatory drawing which shows the example of the temperature in each part in the ventilation mode which changes from dehumidification mode, relative humidity, and absolute humidity concerning one Embodiment of this invention. It is explanatory drawing which shows the example of the temperature in each site | part in the ventilation mode which changes from humidification mode, and relative humidity concerning one Embodiment of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[Explanation of air flow]
FIG. 1 is a block diagram schematically showing an air flow of an outside air processing apparatus 100 according to an embodiment of the present invention, where (a) shows an air flow in a dehumidifying mode executed in summer, (B) has shown the flow of the air in the humidification mode performed in winter. FIG. 2 is an explanatory view schematically showing a state in which the outside air processing apparatus 100 shown in FIG. 1 is connected to a room to be dehumidified or humidified (hereinafter referred to as “target room”) by a duct or the like. is there. FIG. 2 shows the case where the inside of the target chamber 50 is humidified (that is, the case of FIG. 1B).

  As shown in FIG. 1 and FIG. 2, the outside air processing apparatus 100 includes a first air flow path 12 that goes from the outside of the target room 50 for air conditioning control to the room, a second air flow path 13 that goes from the room to the outside, It has.

  The first air flow path 12 is a flow path for supplying outdoor air into the room by an SA (Supply Air) fan 10 (see FIG. 1) provided on the downstream side thereof. 2 Air is supplied into the room via the heat exchanger 5, the rotary desiccant 8 (moisture adsorption means), and the SA fan 10. The desiccant 8 is disposed across the first air flow path 12 and the second air flow path 13, and is configured from a dehumidifying side that adsorbs moisture and dehumidifies air, and a regeneration side that releases and regenerates moisture. The

  The second air flow path 13 is a flow path for discharging indoor air to the outside by an EA (Exhaust Air) fan 9 (see FIG. 1) provided on the downstream side. The air is discharged to the outside through the 1 heat exchanger 4, the desiccant 8, the third heat exchanger 6, and the EA fan 9. As will be described later, a refrigerant circuit is connected to the first heat exchanger 4, the second heat exchanger 5, and the third heat exchanger 6, and each of the heat exchangers 4, 5, 6 is Acts as an evaporator or condenser. Note that “cooling” of the heat exchangers 4 and 6 shown in FIG. 2 indicates a case of acting as an evaporator, and “heating” of the heat exchanger 5 indicates a case of acting as a condenser.

  Here, it is desirable that the first heat exchanger 4 and the third heat exchanger 6 use heat exchangers having substantially the same heat capacity. Furthermore, the second heat exchanger 5 is desirably a heat exchanger having a smaller heat capacity than the first and third heat exchangers 4 and 6. Specifically, the first and third heat exchangers 4 and 6 use five rows and eight stages and one-pass heat exchangers, and the second heat exchanger 5 uses four rows and eight stages and two-pass heat exchangers. be able to.

  In the dehumidifying mode shown in FIG. 1A, the second heat exchanger 5 functions as an evaporator, and the first heat exchanger 4 and the third heat exchanger 6 function as a condenser. Further, the region (lower side in the figure) through which the first air flow path 12 passes in the desiccant 8 is the dehumidifying side, and the area (upper side in the figure) through which the second air flow path 13 passes is the regeneration side.

  And outdoor air (OA; Out Air) passes through the total heat exchanger 11, and temperature is lowered | hung, and it is further lowered | hung in the 2nd heat exchanger 5 which functions as an evaporator after that. Next, the moisture is removed by passing through the dehumidifying side of the desiccant 8 (that is, the humidity is lowered) and supplied into the target chamber 50. Therefore, air that has been dehumidified at a low temperature (dehumidified air) is supplied into the target chamber 50. As a result, low-humidity air can be supplied into the target room 50 in the summer.

  Further, the air (RA; Return Air) discharged from the target chamber 50 via the second air flow path 13 rises in temperature by passing through the total heat exchanger 11, and then as a condenser. By passing through the functioning first heat exchanger 4, the temperature further increases. Since the air whose temperature has risen can contain a large amount of moisture, it passes through the regeneration side of the desiccant 8 to absorb moisture adsorbed on the dehumidifying side of the desiccant 8 (that is, remove the moisture of the desiccant 8). In addition, it is discharged to the outside by the EA fan 9 via the third heat exchanger 6 that functions as a condenser.

  On the other hand, in the humidification mode shown in FIG. 1B, the operation is the opposite of the dehumidification mode described above. That is, the 1st heat exchanger 4 and the 3rd heat exchanger 6 function as an evaporator, and the 2nd heat exchanger 5 functions as a condenser. Moreover, the area | region where the 1st air flow path 12 of the desiccant 8 passes is made into the reproduction | regeneration side, and the area | region where the 2nd air flow path 13 passes is made into the dehumidification side.

  Then, the temperature of the room air (RA) is lowered by passing through the total heat exchanger 11, and then the temperature is further lowered by the first heat exchanger 4 functioning as an evaporator (reference numeral 4 in FIG. 2). "Cooling"). Next, moisture is removed by passing through the dehumidifying side of the desiccant 8, and the temperature is lowered by the third heat exchanger 6 functioning as an evaporator ("cooling" of reference numeral 6 in FIG. 2). Discharged.

  In addition, the temperature of the outdoor air (OA) rises by passing through the total heat exchanger 11, and then the temperature rises further by passing through the second heat exchanger 5 that functions as a condenser ( ("Heating" at 5 in FIG. 4). Since the air whose temperature has risen can contain a large amount of moisture, it passes through the regeneration side of the desiccant 8 to absorb moisture adsorbed on the dehumidifying side of the desiccant 8 (that is, remove the moisture of the desiccant 8). And supplied to the room by the SA fan 10. Therefore, air with increased temperature and increased humidity is supplied to the room. As a result, humid air can be supplied into the target chamber 50 with high humidity air in winter.

  Furthermore, in this embodiment, in addition to the humidification mode and the dehumidification mode described above, the operations of the first heat exchanger 4, the second heat exchanger 5, the third heat exchanger 6, and the desiccant 8 are all stopped. The air blowing mode (intermediate mode) in which the air sent out by the SA fan 10 is supplied indoors and the air is discharged by the EA fan 9 is set. The air blowing mode is a mode in which outdoor air passes through only the total heat exchanger 11 and is supplied into the target chamber 50. Details will be described later.

  As shown in FIG. 2, a high sensible heat air conditioner 51 and a humidity indicator 54 for setting the humidity are provided in the target room 50. The high sensible heat air conditioner 51 includes an indoor unit 53a and a remote controller 52 for setting the room temperature. Further, an outdoor unit 53 b of the high sensible heat air conditioner 51 is provided outside the target room 50.

[Configuration of refrigerant circuit]
Next, with reference to FIG. 3 and FIG. 4, the structure of the refrigerant circuit provided in the outside air processing apparatus 100 which concerns on this embodiment is demonstrated. FIG. 3 is a diagram schematically illustrating the configuration of the refrigerant circuit, and FIG. 4 is a block diagram illustrating an electrical connection relationship. As shown in FIG. 3, the outside air processing apparatus 100 according to the present embodiment includes a refrigerant circuit that circulates the refrigerant in each of the heat exchangers 4, 5, and 6 in addition to the configuration of FIG. 1 described above. The refrigerant circuit includes a compressor 1 that compresses and outputs a refrigerant under the control of an inverter 27 (see FIG. 4), and an accumulator 2 that is provided upstream of the compressor 1 and temporarily accumulates the refrigerant that is supplied to the compressor 1. And a four-way valve 3 (output switching means) for switching so that the compressed refrigerant delivered from the compressor 1 is output to either the first air flow path 12 side or the second air flow path 13 side heat exchanger, It has.

  The first heat exchanger 4 is provided on the upstream side of the desiccant 8 in the second air flow path 13, and the third heat exchanger 6 is provided on the downstream side of the desiccant 8. The second heat exchanger 5 is provided on the upstream side of the desiccant 8 in the first air flow path 12. The refrigerant circuit includes a first expansion valve 18, a second expansion valve 19, and various sensors.

  The first expansion valve 18 is provided between the first heat exchanger 4 and the second heat exchanger 5 and controls the flow rate while reducing the pressure of the refrigerant flowing between the first and second heat exchangers 4 and 5. To do. The second expansion valve 19 is provided between the third heat exchanger 6 and the second heat exchanger 5, and is transferred from the third heat exchanger 6 to the second heat exchanger 5 or the second heat exchanger. The flow rate of the refrigerant is controlled while lowering the pressure of the refrigerant flowing from 5 to the third heat exchanger 6. Note that the flow of refrigerant in the first expansion valve 18 and the second expansion valve 19 can be controlled in either direction.

  Furthermore, an air humidity sensor 23 (humidity detection unit) that measures air humidity and temperature on the air inlet side of the first heat exchanger 4, an air temperature sensor 24 (temperature detection unit), and a refrigerant pipe on the inlet side of the accumulator 2 Are provided with a refrigerant temperature sensor 20 for measuring refrigerant temperature and pressure, and a refrigerant pressure sensor 21. The air humidity sensor 23 and the air temperature sensor 24 are provided in a duct or the like for introducing exhaust air from the target chamber 50 into the outside air processing apparatus 100 as shown in FIG.

  Further, the compressor 1, the four-way valve 3, the first expansion valve 18, based on the detection signal obtained from the detection signal of each sensor described above and the setting signal input by the humidity indicator 54 (see FIG. 2), And the main control part 31 (control means) which controls the 2nd expansion valve 19 is provided. The main control unit 31 also controls the operations of the EA fan 9, the SA fan 10, and the desiccant 8 driving rotary motor 8a shown in FIG.

  Here, the main control unit 31 can be configured as an integrated computer including a central processing unit (CPU) and storage means such as a RAM, a ROM, and a hard disk, for example.

  FIG. 4 is a block diagram showing a detailed configuration of the main control unit 31 and other electrical configurations. As shown in FIG. 4, the main control unit 31 includes a sensor input unit 31a for inputting detection signals of various sensors and a humidity indicator 54, an EA fan 9, an SA fan 10, a rotary motor 8a for the desiccant 8, and four-way The opening degree of the 1st operation part 31b which controls the valve 3, the compressor output part 31c which controls the inverter 27 for driving the compressor 1, the 1st expansion valve 18, and the 2nd expansion valve 19 is adjusted. A second operation unit 31d.

[Explanation of refrigerant flow]
Next, the flow of the refrigerant in the dehumidifying mode, the humidifying mode, and the air blowing mode will be described. When the outside air processing apparatus 100 is set to the air blowing mode, the refrigerant circuit is stopped and the desiccant 8 is stopped under the control of the first operation unit 31b and the second operation unit 31d shown in FIG. That is, the heat exchangers 4, 5, 6 and the desiccant 8 shown in FIG. 3 do not operate, and only the air flowing through the first air flow path 12 and the second air flow path 13 passes.

  Hereinafter, the refrigerant flow in the dehumidifying mode and the humidifying mode will be described in detail with reference to FIGS. 5 and 6. FIG. 5 is a flowchart showing the flow of the refrigerant in the dehumidifying mode. In the dehumidifying mode, the main control unit 31 controls the four-way valve 3 so that the discharge side of the compressor 1 is connected to a pipe that goes to the first heat exchanger 4 and the third heat exchanger 6. That is, the refrigerant output from the compressor 1 is branched into two systems, one branch path is introduced into the first heat exchanger 4 functioning as a condenser, and the other branch path is also a third function also functioning as a condenser. It is introduced into the heat exchanger 6.

  The refrigerant that has passed through the first heat exchanger 4 is introduced into the second heat exchanger 5 that functions as an evaporator via the first expansion valve 18. The refrigerant that has passed through the third heat exchanger 6 is introduced into the second heat exchanger 5 via the second expansion valve 19. Then, the refrigerant that has passed through the second heat exchanger 5 is returned to the accumulator 2 via the four-way valve 3.

  The above flow will be described in more detail. In the dehumidifying mode, the compressed refrigerant output from the compressor 1 is high-temperature and high-pressure, so the first heat exchanger 4 and the third heat exchanger that function as a condenser. 6 to exchange heat with the air introduced into the second air flow path 13. Therefore, the temperature of the air flowing through the second air flow path 13 rises and the refrigerant condenses. That is, the refrigerant that has exited both heat exchangers 4 and 6 becomes a high-pressure liquid refrigerant. Thereafter, the refrigerant output from the first heat exchanger 4 is decompressed and expanded by passing through the first expansion valve 18, and becomes a low-temperature and low-pressure gas-liquid mixed refrigerant. This refrigerant is introduced into the second heat exchanger 5. Similarly, the refrigerant output from the third heat exchanger 6 is decompressed and expanded by passing through the second expansion valve 19, becomes a low-temperature low-pressure gas-liquid mixed refrigerant, and is introduced into the second heat exchanger 5. .

  The refrigerant introduced into the second heat exchanger 5 lowers the temperature of the air passing through the first air flow path 12 with evaporation (the temperature of the air before passing through the desiccant 8), and changes into a gas phase. This refrigerant is returned to the accumulator 2 via the four-way valve 3. That is, in the dehumidifying mode, the refrigerant output from the compressor 1 is routed from the output side of the first heat exchanger 4, the path passing through the first expansion valve 18, and the output side of the third heat exchanger 6. The path passing through the second expansion valve 19 is merged, and then the path passing through the second heat exchanger 5 is circulated.

  Thus, since the temperature of the air flowing through the first air flow path 12 can be lowered by the refrigerant introduced into the second heat exchanger 5, the cooled and dehumidified air can be supplied into the target chamber 50. Become. At this time, the first expansion valve 18 and the second expansion valve 19 have the same opening degree. Therefore, the refrigerant flow rate passing through the first expansion valve 18 and the refrigerant flow rate passing through the second expansion valve 19 can be distributed with good balance, and the refrigerant can be circulated stably.

  Next, the flow of the refrigerant in the humidification mode will be described with reference to FIG. In the humidification mode, the four-way valve 3 is connected to a pipe whose discharge side of the compressor 1 is directed to the second heat exchanger 5 under the control of the main control unit 31. In other words, the refrigerant output from the compressor 1 is introduced into the second heat exchanger 5 functioning as a condenser, and heat exchange with the air in the first air flow path 12 becomes high-pressure liquid refrigerant. Further, the refrigerant output from the second heat exchanger 5 is branched into two systems.

  Of these, the refrigerant flowing to one branch side is depressurized by the first expansion valve 18, becomes a low-temperature low-pressure gas-liquid mixed refrigerant, and is introduced into the first heat exchanger 4 functioning as an evaporator. The refrigerant output from the first heat exchanger 4 is returned to the accumulator 2 via the four-way valve 3.

  In parallel with this, the refrigerant flowing to the other branch side is decompressed by the second expansion valve 19, becomes a low-temperature and low-pressure gas-liquid mixed refrigerant, and is introduced into the third heat exchanger 6 that functions as an evaporator. The refrigerant output from the third heat exchanger 6 is returned to the accumulator 2 via the four-way valve 3. At this time, the piping from the compressor 1 through the second heat exchanger 5 to the upstream of the first expansion valve 18 and the second expansion valve 19 becomes a high-pressure refrigerant circuit, and the first expansion valve 18 and the second expansion valve 19 The piping from the downstream to the compressor 1 is a low-pressure refrigerant circuit.

  The refrigerant flow described above will be described in more detail. In the humidification mode, the compressed refrigerant output from the compressor 1 is high-temperature and high-pressure, and is introduced into the second heat exchanger 5 acting as a condenser. The heat exchange with the air introduced into the first air flow path 12 is performed. Therefore, the temperature of the air flowing through the first air flow path 12 rises and the refrigerant condenses. And the refrigerant | coolant output from the 2nd heat exchanger 5 is branched into 2 systems, and the refrigerant | coolant which flows through one branch path is decompressed and expanded by passing the 1st expansion valve 18, and temperature falls. The refrigerant whose temperature has been reduced is introduced into the first heat exchanger 4 to reduce the temperature of the air passing through the second air flow path 13 with evaporation (the temperature of the air before passing through the desiccant 8). 3 is returned to the accumulator 2.

  On the other hand, the refrigerant that is output from the second heat exchanger 5 and flows through the other branch passage is decompressed and expanded by passing through the second expansion valve 19, and the temperature decreases. The refrigerant whose temperature has been lowered is introduced into the third heat exchanger 6 to reduce the temperature of the air passing through the second air flow path 13 with evaporation (the temperature of the air after passing through the desiccant 8). 3 is returned to the accumulator 2. That is, in the humidification mode, the refrigerant output from the compressor 1 is routed from the output side of the second heat exchanger 5 through the first expansion valve 18 and the first heat exchanger 4, and the second expansion valve. The flow path of the refrigerant is set so as to circulate through the path passing through 19 and the third heat exchanger 6. In this way, the temperature of the air flowing through the first air flow path 12 can be raised, so that heated and humidified air can be supplied into the target chamber 50.

  Here, in the present embodiment, the flow rate of the refrigerant supplied to the first heat exchanger 4 so that the moisture contained in the air passing through the first heat exchanger 4 in the humidification mode does not freeze due to a temperature drop due to the refrigerant. To control. Specifically, the flow rate of the refrigerant supplied to the first heat exchanger 4 is regulated by setting the opening of the first expansion valve 18 to a first lower limit opening Min1 (described later) or zero (fully closed). . At this time, the flow rate of the refrigerant flowing through the first expansion valve 18 is set in advance by calculation so that the moisture content of the air passing through the first heat exchanger 4 does not freeze. Further, the first lower limit opening degree Min1 is set so that the refrigerant flowing through the first heat exchanger 4 has the above flow rate. A detailed control method will be described later.

  Moreover, the outside air processing apparatus 100 is connected with the object chamber 50 by a duct etc. as shown in FIG. Then, air (RA) discharged from the target chamber 50 is introduced into the outside air processing device 100, and further, air (SA) output from the outside air processing device 100 is supplied into the target chamber 50.

  A high sensible heat air conditioner 51 is installed in the target room 50, and the temperature in the target room 50 can be controlled to a desired temperature by setting the desired temperature using the remote controller 52 of the high sensible heat air conditioner 51. . Further, the high sensible heat air conditioner 51 does not have a function of adjusting the humidity. Further, a humidity indicator 54 is provided in the target chamber 50, and the humidity indicator 54 is connected to the main control unit 31 shown in FIG. Therefore, when the operator in the target room 50 operates the humidity indicator 54 to set the humidity, the humidity setting signal is transmitted to the main control unit 31.

  In the present embodiment, the compressor 1 is controlled in accordance with a humidity setting signal when the humidity indicator 54 is operated in the target chamber 50, and the humidity of the air supplied to the target chamber 50 is set. To be.

[Explanation about compressor control]
Next, control of the compressor 1 by the main control unit 31 shown in FIG. 4 will be described. The main control unit 31 acquires the air temperature entering the first heat exchanger 4 detected by the air temperature sensor 24 and the air humidity entering the first heat exchanger 4 detected by the air humidity sensor 23. And the relative humidity Hc in the object room 50 is estimated based on these temperature data and humidity data. In this estimation calculation, it is possible to employ a calculation method of relative humidity → absolute humidity and a calculation method of absolute humidity → relative humidity, which are well-known calculation methods. That is, the air RA returned from the target chamber 50 via the duct has an air temperature different from the room temperature (because the air temperature changes by passing through the duct), and therefore an error occurs in the relative humidity. That is, the humidity data detected by the air humidity sensor 23 does not necessarily match the humidity in the target room 50. However, since the absolute humidity is the same, the absolute humidity is first calculated from the relative humidity of the air RA, and the relative humidity at the room temperature is calculated based on this result.

As a specific example, assuming that the temperature detected by the air temperature sensor 24 is T and the humidity detected by the air humidity sensor 23 is R (%), the assumed indoor temperature is 22 ° C., 24 ° C., 26 ° C., In the case of 28 ° C., the relative humidity (%) in the target chamber 50 is calculated by the arithmetic expressions shown in the following (1) to (4).
(1) When the assumed indoor temperature is 22 ° C. Hc = (0.1737 × T2-1.2631T + 43.355) × (R / 100)
(2) When the assumed indoor temperature is 24 ° C. Hc = (0.1539 × T2-1.192T + 38.411) × (R / 100)
(3) When the assumed indoor temperature is 26 ° C. Hc = (0.1366 × T2−0.9933T + 34.094) × (R / 100)
(4) When the indoor temperature is 28 ° C. Hc = (0.1215 × T2−0.8832T + 30.316) × (R / 100)
That is, when the assumed indoor temperature is selected, the relative humidity in the target room 50 can be estimated using the above equations (1) to (4).

  In addition, although said (1)-(4) type | formula has shown the general indoor temperature being 22 degreeC-28 degreeC, it has shown about the example which calculates relative humidity Hc in increments of 2 degreeC, This invention is not limited to this, You may make it obtain | require the relative humidity (%) in the target room 50 with another arithmetic expression based on the indoor temperature.

  In the present embodiment, the humidity threshold for switching to the air blowing mode when the dehumidifying mode is selected is the first threshold (target humidity in the dehumidifying mode) SPA, and the air blowing mode when the humidifying mode is selected is The humidity threshold for switching is set as a second threshold (target humidity in the humidification mode) SPB (SPA> SPB). Then, depending on the relationship between the humidity Hc in the target chamber 50 estimated by the calculations of the above formulas (1) to (4) and the first threshold SPA and the second threshold SPB, the dehumidifying mode, the humidifying mode, or the air blowing The mode is set automatically. At this time, a hysteresis Δh is set.

  Therefore, initially, the mode is set based on the relationship of Hc, “SPA + Δh”, and “SPB−Δh”, and the operation mode is changed as shown in FIGS. FIG. 7 shows the transition state of each operation mode, and FIG. 8 shows the humidity at which the operation mode is switched. In addition, the horizontal axis of FIG. 8 is high humidity in the left direction.

  When the compressor 1 is stopped in the dehumidifying mode and the humidity Hc falls below “SPA−Δh”, the mode is switched to the air blowing mode. On the other hand, when the compressor 1 is stopped in the humidification mode and the humidity Hc exceeds “SPB + Δh”, the mode is switched to the air blowing mode.

  In the air blowing mode, the dehumidifying mode is switched when the humidity Hc exceeds “SPA + Δh”, and the humidifying mode is switched when the humidity Hc falls below “SPB−Δh”. That is, the operation mode is automatically switched according to the magnitude of the humidity Hc.

  In the dehumidifying mode, the output of the inverter 27 is changed so that the humidity Hc in the target chamber 50 estimated by the above calculation becomes the first threshold SPA, and the output of the compressor 1 is controlled. That is, when the humidity Hc in the target chamber 50 is higher than the value “SPA + Δh” obtained by adding the hysteresis Δh to the first threshold SPA, the output of the inverter 27 is increased and the output of the compressor 1 is increased (humidity R → R + ΔR). When the humidity Hc in the target chamber 50 is lower than the value “SPA−Δh” obtained by subtracting the hysteresis Δh from the first threshold SPA, the output of the inverter 27 is decreased and the output of the compressor 1 is decreased (humidity R → R-ΔR). Then, control is performed so that the humidity Hc in the target chamber 50 is always within the range of “SPA−Δh” to “SPA + Δh”.

  In the humidification mode, the output of the inverter 27 is changed so that the humidity Hc in the target chamber 50 becomes the second threshold value SPB, and the output of the compressor 1 is controlled. That is, when the humidity Hc in the target chamber 50 is lower than the value “SPB−Δh”, the output of the inverter 27 is increased and the output of the compressor 1 is increased (humidity R → R + ΔR). When the humidity Hc in the target chamber 50 is higher than the value “SPB + Δh”, the output of the inverter 27 is decreased to decrease the output of the compressor 1 (humidity R → R−ΔR). Then, control is performed so that the humidity Hc in the target chamber 50 is always within the range of “SPB−Δh” to “SPB + Δh”.

  By performing the above control, in the dehumidifying mode, the humidity Hc in the target chamber 50 can be brought close to the first threshold SPA that is the target humidity. Further, in the humidification mode, the humidity Hc in the target chamber 50 can be brought close to the second threshold value SPB that is the target humidity. Further, by selecting the air blowing mode, unnecessary operation of the refrigerant circuit can be reduced, and the humidity Hc in the target chamber 50 can be controlled within the range of “SPB−Δh” to “SPA + Δh”.

[Description of control of first and second expansion valves]
(Dehumidification mode)
Based on the refrigerant temperature T1 measured by the refrigerant temperature sensor 20 and the refrigerant pressure P1 measured by the refrigerant pressure sensor 21, the refrigerant evaporation temperature Te is obtained. Then, the temperature difference between the refrigerant temperature T1 and the evaporation temperature Te, that is, “T1-Te” is set as the current superheat degree SH. The opening degrees Vst of the first expansion valve 18 and the second expansion valve 19 are determined so that the current superheat degree SH becomes the target superheat degree SSH. For example, a known control method such as PID control can be used as the determination method. Then, both the first expansion valve 18 and the second expansion valve 19 are set to the opening degree Vst. That is, the first expansion valve 18 and the second expansion valve 19 have the same opening. However, when the opening degree of the first and second expansion valves is equal to or lower than the preset lower limit value Min0, the lower limit value Min0 is set. That is, in the dehumidifying mode, the first expansion valve 18 and the second expansion valve 19 are set to the opening degree of the lower limit value Min0 at least.

(Humidification mode)
The current superheat degree SH is obtained by the same method as described above. Then, the opening degree Vst of the second expansion valve 19 is determined so that the current superheat degree SH becomes the target superheat degree SSH. For example, a known control method such as PID control can be used as the determination method. Then, the second expansion valve 19 is set to the opening degree Vst. On the other hand, the opening degree of the first expansion valve 18 is fixed to the first lower limit opening degree Min1 set in advance. That is, the second expansion valve 19 is controlled to have the opening Vst, and the first expansion valve 18 is set to the first lower limit opening Min1. At this time, the first lower limit opening Min1 is set to such an opening that the refrigerant flow rate supplied to the first heat exchanger 4 does not freeze the moisture contained in the air passing through the first heat exchanger 4. Is done. In other words, the moisture in the air passing through the first heat exchanger 4 is prevented from freezing by setting the first expansion valve 18 to the first lower limit opening Min1.

  When the opening Vst of the second expansion valve 19 is equal to or smaller than the second lower limit opening Min2 (however, Min2> Min1), the first expansion valve 18 is fully closed. Further, when the opening Vst of the second expansion valve 19 is smaller than the first lower limit opening Min1, the first lower limit opening Min1 is set. That is, at least the second expansion valve 19 is set to the first lower limit opening Min1.

[Description of action]
Next, a processing procedure of the outside air processing apparatus 100 according to the present embodiment configured as described above will be described with reference to flowcharts shown in FIGS.

  FIG. 9 is a flowchart showing the entire processing procedure. First, in step S1 of FIG. 9, the main control unit 31 activates the EA fan 9 and the SA fan 10 (see FIG. 1). The opening of the first expansion valve 18 is Vt1, and the opening of the second expansion valve 19 is Vt2.

In step S <b> 2, the main control unit 31 acquires temperature data and humidity data detected by the air humidity sensor 23 and the air temperature sensor 24.
In step S3, the main control unit 31 calculates the humidity Hc in the target chamber 50 using the arithmetic expressions shown in the above (1) to (4).

  In step S4, the main control unit 31 executes mode selection. Here, the operation mode of the outside air processing apparatus 100 is automatically set based on the current humidity Hc in the target chamber 50. For example, when the humidity Hc exceeds (SPA + Δh) under the condition of high humidity Hc in summer, the desiccant 8 and the refrigerant circuit are set to the dehumidifying mode and driven. Thereafter, the process proceeds to step S5.

  Further, when the humidity Hc is lower than (SPB-Δh) under the condition where the humidity Hc in winter is low, the desiccant 8 and the refrigerant circuit are set to the humidification mode and driven. Thereafter, the process proceeds to step S8.

  Further, for example, when the humidity Hc does not exceed (SPA + Δh) and the humidity Hc does not fall below (SPB−Δh) as in spring and autumn, for example, the ventilation mode (intermediate mode) is set. If the blower mode is set, the desiccant 8 and the compressor 1 are stopped in step S11.

  When the estimated value of the humidity Hc in the target chamber 50 exceeds (SPA + Δh) and the dehumidifying mode is set, the main control unit 31 controls the four-way valve 3 in step S5, and the output of the compressor 1 is the first. It sets so that it may become the heat exchanger 4 and the 3rd heat exchanger 6 side. That is, it sets like the four-way valve 3 shown in FIG.

  Next, in step S6, the compressor 1 is controlled in the dehumidifying mode. Details of the compressor control will be described later with reference to FIG. Thereafter, in step S7, expansion valve control in the dehumidifying mode is executed. Details of the expansion valve control will be described later with reference to FIG. Thereafter, the process proceeds to step S12.

  On the other hand, when the estimated value of the humidity Hc in the target chamber 50 is less than (SPB−Δh) and the humidification mode is selected, the main control unit 31 controls the four-way valve 3 in step S8, and the compressor 1 Is set to be on the second heat exchanger 5 side. That is, it sets like the four-way valve 3 shown in FIG.

  Next, in step S9, the compressor 1 is controlled in the humidification mode. Details of the compressor control will be described later with reference to FIG. Thereafter, in step S10, the expansion valve control in the humidification mode is executed. Details of the expansion valve control will be described later with reference to FIG. Thereafter, the process proceeds to step S12.

  In step S12, the main control unit 31 determines whether or not an operation switch (not shown) indicating stop of the process has been operated. If the operation switch is turned off, in step S13, the main control unit 31 The fan 9 and the SA fan 10 are turned off. Further, the compressor 1 is stopped and the desiccant 8 is stopped. Thus, control of the outside air processing apparatus 100 in the humidification mode and the dehumidification mode is performed.

  Next, the control of the compressor 1 in the dehumidifying mode shown in step S6 of FIG. 9 will be described with reference to the flowchart shown in FIG. First, in step S <b> 31, the main control unit 31 operates the desiccant 8.

  In step S <b> 32, the main control unit 31 acquires temperature data and humidity data of the inlet side air of the first heat exchanger 4 detected by the air temperature sensor 24 and the air humidity sensor 23.

  In step S33, the main control unit 31 calculates the humidity Hc (relative humidity) in the target room 50 based on the temperature data and humidity data acquired in step S32. The calculation method of the relative humidity is as described above, and a known method can be used.

  In step S34, the main control unit 31 compares the first threshold SPA set in advance with the humidity Hc. And the output of the compressor 1 is controlled according to the magnitude relationship of both. Specifically, the hysteresis Δh is set, and when “Hc ≧ SPA + Δh”, the main control unit 31 increases the output of the compressor 1 by ΔR in step S35. That is, the output of the compressor 1 is changed from “R” to “R + ΔR”. However, when the compressor 1 is stopped, the compressor 1 is started.

  When “Hc ≦ SPA−Δh”, in step S36, the main control unit 31 decreases the output of the compressor 1 by ΔR. That is, the output of the compressor 1 is changed from “R” to “R−ΔR”. However, when R <0, the compressor 1 is stopped.

  On the other hand, when “SPA + Δh> Hc> SPA−Δh”, the output of the compressor 1 is not changed. In other words, the range of hysteresis ± Δh from the target humidity Hs is the dead zone. Thus, the output of the compressor 1 is adjusted so that the humidity Hc in the target chamber 50 falls within the range of “SPA ± Δh”.

  Next, the processing procedure of the expansion valve control shown in step S7 of FIG. 9 will be described with reference to the flowchart shown in FIG. First, in step S51, the main control unit 31 acquires the refrigerant pressure P1 detected by the refrigerant pressure sensor 21 and the refrigerant temperature T1 detected by the refrigerant temperature sensor 20.

  In step S52, the main controller 31 calculates the refrigerant evaporation temperature Te from the refrigerant pressure P1.

  In step S53, the main control unit 31 calculates a current superheat degree SH that is a difference between the refrigerant temperature T1 and the evaporation temperature Te. That is, SH = T1-Te is calculated.

  In step S54, the main control unit 31 calculates the opening degrees Vst of the first expansion valve 18 and the second expansion valve 19 for setting the current superheat degree SH to the target superheat degree SSH by using PID calculation or the like.

  In step S55, the main controller 31 compares the opening degree Vst calculated in step S54 with the lower limit value Min0. If Vst <Min0 is satisfied (YES in step S55), the process proceeds to step S57. If Vst <Min0 is not satisfied (NO in step S55), the process proceeds to step S56.

  In step S56, the main control unit 31 sets both the opening degrees Vt1 and Vt2 of the first expansion valve 18 and the second expansion valve 19 to Vst. That is, the first expansion valve 18 and the second expansion valve 19 are set to the same opening degree Vst.

  On the other hand, in step S57, the main controller 31 sets the opening degrees of the first expansion valve 18 and the second expansion valve 19 to the lower limit value Min0. That is, the lower limit Min0 indicates the minimum opening, and when the target opening Vst is smaller than the lower limit Min0, the lower limit Min0 is set.

  Thus, in the dehumidifying mode, the expansion valve opening degree Vst is set so that the current superheat degree SH becomes the target superheat degree SSH, and the first expansion valve 18 and the second expansion valve are set so as to become this opening degree Vst. 19 is adjusted. As a result, the current superheat degree SH can be brought close to the target superheat degree SSH. Moreover, since the opening degree of the first expansion valve 18 and the second expansion valve 19 is controlled to be the same, there is no bias between the first heat exchanger 4 and the second heat exchanger 5, and the balance is balanced. A good flow rate can be set. Furthermore, since the opening degree of the first expansion valve 18 and the second expansion valve 19 does not become the lower limit value Min0 or less, a minimum amount of refrigerant can flow.

  Next, the control of the compressor 1 in the humidification mode shown in step S9 of FIG. 9 will be described with reference to the flowchart shown in FIG.

  First, in step S61, the main control unit 31 operates the desiccant 8. In step S62, the main control unit 31 acquires temperature data and humidity data of the inlet side air of the first heat exchanger 4 detected by the air temperature sensor 24 and the air humidity sensor 23.

  In step S63, the main control unit 31 calculates the humidity Hc in the target room 50 based on the temperature data and humidity data acquired in step S31. The calculation method of the humidity Hc is as described above.

  In step S64, the main control unit 31 compares the preset second threshold value SPB with the humidity Hc. And the output of the compressor 1 is controlled according to the magnitude relationship of both. Specifically, the hysteresis Δh is set, and if “Hc ≦ SPB−Δh”, the main control unit 31 increases the output of the compressor 1 by ΔR in step S65. That is, the output is changed from “R” to “R + ΔR”.

  If “Hc ≧ SPB + Δh”, in step S66, the main control unit 31 decreases the output of the compressor 1 by ΔR. That is, the output of the compressor 1 is changed from “R” to “R−ΔR”.

  On the other hand, when “SPB + Δh> Hc> SPB−Δh”, the output of the compressor 1 is not changed. In other words, the range of hysteresis ± Δh from the target humidity Hs is the dead zone. Thus, the output of the compressor 1 is adjusted so that the humidity Hc in the target chamber 50 falls within the range of “SPB ± Δh”.

  Next, the processing procedure of the expansion valve control shown in step S10 of FIG. 9 will be described with reference to the flowchart shown in FIG.

  First, in step S81, the main control unit 31 acquires the refrigerant pressure P1 detected by the refrigerant pressure sensor 21 and the refrigerant temperature T1 detected by the refrigerant temperature sensor 20.

  In step S82, the main control unit 31 calculates the refrigerant evaporation temperature Te from the refrigerant pressure P1.

  In step S83, the main control unit 31 calculates the current superheat degree SH that is the difference between the refrigerant temperature T1 and the evaporation temperature Te. That is, SH = T1-Te is calculated.

  In step S84, the main control unit 31 calculates the opening degrees Vst of the first expansion valve 18 and the second expansion valve 19 for setting the current superheat degree SH to the target superheat degree SSH by using PID calculation or the like.

  In step S85, the main control unit 31 compares the opening degree Vst calculated in step S84 with the second lower limit opening degree Min2, and if Vst <Min2 is satisfied (YES in step S85), the process proceeds to step S87. If the process shifts to Vst <Min2 (NO in step S85), the process shifts to step S86.

  In step S86, the main control unit 31 compares the opening degree Vst with the first lower limit opening degree Min1, and if Vst <Min1 (YES in step S86), the main control unit 31 proceeds to step S89, and Vst <Min1 If not (NO in step S86), the process proceeds to step S88.

  In step S87, the main control unit 31 sets the opening of the first expansion valve 18 to the first lower limit opening Min1, and sets the opening of the second expansion valve 19 to the opening Vst. That is, by restricting the opening degree of the first expansion valve 18 to the first lower limit opening degree Min1 (by not setting it to Min1 or more), the flow rate of the refrigerant flowing into the first heat exchanger 4 is limited, and the first heat The moisture in the air passing through the exchanger 4 is prevented from freezing.

  In step S88, the main control unit 31 sets the opening of the first expansion valve 18 to zero and sets the opening of the second expansion valve to the opening Vst. That is, since the expansion valve opening degree Vst is between the first lower limit opening degree Min1 and the second lower limit opening degree Min2, the opening degree of the first expansion valve 18 is set to zero (that is, fully closed state). That is, in the humidification mode, if excessive refrigerant is supplied to the first heat exchanger 4, moisture in the air passing through the first heat exchanger may freeze, so that the first expansion valve 18 is opened as much as possible. The refrigerant flow rate to be supplied to the first heat exchanger 4 is reduced by decreasing the degree.

  In step S89, the main control unit 31 sets the opening of the first expansion valve 18 to zero, and sets the second expansion valve opening to the first lower limit opening Min1. That is, since the opening degree of the second expansion valve 19 does not become equal to or less than the first lower limit opening degree Min1, it is possible to flow a minimum amount of refrigerant.

[Explanation of changes in temperature and humidity in each operation mode]
Next, specific examples of temperature and humidity at each position in the dehumidifying mode, the humidifying mode, and the air blowing mode will be described with reference to FIGS.

  FIG. 14 is an explanatory diagram illustrating an example of temperature and humidity at each position of the outside air processing apparatus 100 when the dehumidifying mode is set. Note that the numerical values shown at each position in FIG. 14 indicate “temperature ° C.”, “relative humidity%”, and “absolute humidity g / kg” from the top. For example, the inside of the target room 50 indicates that the temperature is 26.0 ° C., the relative humidity is 49%, and the relative humidity is 10.2 g / kg.

  As shown in FIG. 14, when the temperature set value in the target chamber 50 is 26.0 ° C. and the humidity set value is 50%, the outside air (OA) introduced from the first air flow path 12 is By passing through the total heat exchanger 11, the temperature is lowered, and further, the air is cooled in the second heat exchanger 5, moisture is removed (adsorbed) in the desiccant 8, and the humidity is lowered in the target chamber 50. To be supplied. Specifically, outside air of 35.3 ° C., 59%, 21.3 g / kg becomes air at 29.4 ° C., 33%, 8.4 g / kg, and is supplied into the target chamber 50. As a result, the air in the target room 50 is controlled to 26.0 ° C., 49%, 10.2 g / kg by the combined use effect with the sensible heat cooling of the high sensible heat air conditioner 51 in the target room 50.

  More specifically, the temperature entering the first heat exchanger 4 is 32.8 ° C., and the temperature entering the third heat exchanger 6 is 33.0 ° C., which are substantially the same temperature. The first heat exchanger 4 and the third heat exchanger 6 use heat exchangers having substantially the same heat capacity and are provided in the same second air flow path 13, and therefore perform heat exchange with the same air volume. Furthermore, since the first expansion valve 18 and the second expansion valve 19 are controlled at the same opening degree, the refrigerant exiting the compressor 1 is distributed almost evenly to the first heat exchanger 4 and the third heat exchanger 6. It is estimated that it will flow. Therefore, since the two heat exchangers functioning as the condenser can be efficiently used, the cooling capacity of the second heat exchanger 5 is increased, and the dehumidifying capacity of the outside air processor 100 is improved.

  FIG. 15 is an explanatory diagram illustrating an example of temperature and humidity at each position of the outside air processing apparatus 100 when the humidifying mode is set. For example, when the set temperature in the target chamber 50 is 22.0 ° C. and the set humidity is 50%, the outside air (OA) introduced from the first air flow path 12 passes through the total heat exchanger 11. As a result, the temperature rises, and the air is heated in the second heat exchanger 5, added with moisture in the desiccant 8 (regeneration), and air with increased humidity is supplied into the target chamber 50. Specifically, outside air of 0.3 ° C., 47%, 1.8 g / kg becomes 26.7 ° C., 38 percent, 8.2 g / kg of air, and is supplied into the target chamber 50. As a result, the air in the target room 50 is controlled to 22.6 ° C., 48%, and 8.2 g / kg by the combined use effect with the sensible heat heating of the high sensible heat air conditioner 51 in the target room 50.

  More specifically, the temperature entering the first heat exchanger 4 is 8.9 ° C., and the same temperature is 8.1 ° C. Since the air entering the first heat exchanger 4 is low in temperature, the heat exchanger may freeze. However, since the opening of the first expansion valve 18 is controlled to Min1 or zero (fully closed), freezing can be prevented.

  In addition, the temperature entering the third heat exchanger is 13.5 ° C., and the same temperature is 6.1 ° C. Since the air entering the third heat exchanger is not low temperature, there is no risk of freezing. Further, it can be seen that the exhaust heat released when moisture is adsorbed (dehumidified) by the desiccant 8 is recovered and released by the second heat exchanger 5.

  FIG. 16 is an explanatory diagram showing an example of temperature and humidity in the air blowing mode that is switched in the dehumidifying mode, that is, in the air blowing mode when transition is made in the loop L2 in FIG. In the air blowing mode, the outside air supplied from the first air flow path 12 passes through the total heat exchanger 11 and the temperature and humidity of the air are lowered, and then supplied into the target chamber 50. That is, since the second heat exchanger 5 and the desiccant 8 are stopped, the air that has passed through the total heat exchanger 11 is supplied into the target chamber 50 as it is.

  FIG. 17 is an explanatory diagram showing an example of the temperature and humidity when transition is made in the air blowing mode that is switched in the humidifying mode, that is, the loop L4 in FIG. In the air blowing mode, the outside air supplied from the first air flow path 12 passes through the total heat exchanger 11 to increase the temperature and humidity of the air, and then is supplied into the target chamber 50. That is, since the second heat exchanger 5 and the desiccant 8 are stopped, the air that has passed through the total heat exchanger 11 is supplied into the target chamber 50 as it is.

  And in the ventilation mode shown in FIG. 16, FIG. 17, since the temperature and humidity in the target chamber 50 are hold | maintained to a desired numerical value in the state which stopped the compressor 1 and the desiccant 8, power consumption can be reduced. . In addition, the aging life of the apparatus can be extended.

[Description of effects]
As described above, in the outside air processing apparatus 100 according to the present embodiment, the output of the compressor 1 is controlled according to the humidity in the target chamber 50, and the dehumidifying capacity or the humidifying capacity is controlled. It becomes possible to control the humidity in the target chamber 50 with high accuracy.

  When the dehumidifying mode is selected, the first expansion valve 18 and the second expansion valve 19 are set to the same opening degree, and the degree of superheat is controlled, so that the refrigerant exchanges with the first heat exchanger 4 and the third heat exchange. Since the heat is condensed in both heat exchangers and the heat of condensation is released in both heat exchangers, the cooling capacity of the second heat exchanger 5 is improved. For this reason, by combining with the control of the compressor 1, the control range of the dehumidifying capacity is expanded, and the temperature controllability in the target chamber 50 can be improved.

  Further, when the humidification mode is selected, the opening degree of the first expansion valve 18 is substantially fixed and the opening degree of the second expansion valve 19 is controlled according to the degree of heating, so that the refrigerant mainly performs the third heat exchange. It will evaporate in the vessel 6. Therefore, the first heat exchanger 4 is prevented from freezing, and the exhaust heat released from the desiccant 8 is recovered by the third heat exchanger 6, and the amount of heat is passed through the refrigerant circuit in the second heat exchanger. Since it discharges | emits, the humidification capability of a 2nd heat exchanger improves, The control range of a humidification capability spreads by combining with the compressor 1, and the humidity control property in the object chamber 50 can be improved.

  Further, since the outside air processing apparatus of the present invention controls the humidity in the target room 50 and the high sensible heat air conditioner controls the room temperature, for example, in the dehumidifying mode, the high sensible heat air conditioner increases the evaporation temperature (pressure) of the refrigerant. The coefficient of performance of the refrigeration cycle can be increased. Furthermore, even if it evaluates combining with the external air processing apparatus 100 of this application, it becomes a system excellent in energy-saving property.

  In addition, since the mode setting (dehumidification, humidification, and ventilation) can be automatically changed throughout the summer, intermediate, and winter seasons, it is possible to save management work.

  As mentioned above, although the outside air processing apparatus of this invention was demonstrated based on embodiment of illustration, this invention is not limited to this, The structure of each part is replaced with the thing of the arbitrary structures which have the same function. Can do.

1 Compressor 2 Accumulator 3 Four-way valve (output switching means)
4 1st heat exchanger 5 2nd heat exchanger 6 3rd heat exchanger 8 Desiccant (moisture adsorption means)
8a Rotating motor 9 EA fan 10 SA fan 11 Total heat exchanger 12 1st air flow path 13 2nd air flow path 18 1st expansion valve 19 2nd expansion valve 20 Refrigerant temperature sensor 21 Refrigerant pressure sensor 23 Air humidity sensor (humidity) Detection unit)
24 Air temperature sensor (temperature detector)
27 Inverter 31 Main control unit (control means)
31a Sensor input unit 31b First operation unit 31c Compressor output unit 31d Second operation unit 50 Target room (target room)
51 High Sensible Air Conditioner 52 Remote Controller 53a Indoor Unit 53b Outdoor Unit 100 Outside Air Treatment Device

Claims (5)

In the outside air processing apparatus that supplies the dehumidified air or humidified air by processing the outside air into the room of the target room,
A first air flow path serving as an air flow path from the outdoor to the indoor;
A second air flow path serving as a flow path of air from the room toward the outside;
It is disposed across the first air flow path and the second air flow path, adsorbs moisture of the air flowing through one of the first air flow path and the second air flow path, and the other flow Moisture adsorption means for releasing moisture into the air flowing through the road;
A refrigerant circuit for circulating the refrigerant,
The refrigerant circuit is
A compressor for compressing the refrigerant;
A first heat exchanger disposed upstream of the moisture adsorbing means in the second air flow path, and a third heat exchanger disposed downstream.
A second heat exchanger disposed upstream of the moisture adsorbing means in the first air flow path;
In the dehumidifying mode for supplying dehumidified air to the room, the refrigerant output from the compressor is supplied to the first heat exchanger and the third heat exchanger, and in the humidifying mode for supplying the humidified air to the room. Output switching means for switching to supply the refrigerant output from the compressor to the second heat exchanger;
A first expansion valve provided between the first heat exchanger and the second heat exchanger; and a second expansion valve provided between the third heat exchanger and the second heat exchanger;
Control means for controlling the opening degree of the first expansion valve and the second expansion valve, and for controlling the output switching means;
A temperature detection unit for detecting the temperature of air returned from the room; and a humidity detection unit for detecting humidity of air returned from the room;
Furthermore, the control means includes
In the dehumidifying mode, the refrigerant output from the compressor is transferred from the output side of the first heat exchanger to the path passing through the first expansion valve and from the output side of the third heat exchanger. 2 join the path through the expansion valve, then circulate the path through the second heat exchanger,
In the humidification mode, the refrigerant output from the compressor is routed from the output side of the second heat exchanger to the path through the first expansion valve and the first heat exchanger, and the second expansion valve. Set the flow path of the refrigerant so as to circulate the path through the third heat exchanger,
Further, based on the temperature detected by the temperature detector and the humidity detected by the humidity detector, the output of the compressor is controlled so that the indoor humidity becomes a preset target humidity. A featured outside air treatment device. The control means includes
In the dehumidifying mode, the first heat exchanger and the third heat exchanger condense the refrigerant, the first expansion valve and the second expansion valve have the same opening degree, and the degree of superheat of the refrigerant is It controls so that it may become target superheat degree. The external air processing apparatus of Claim 1 characterized by the above-mentioned. The control means includes
In the humidification mode, the opening of the first expansion valve is set so that more refrigerant is evaporated in the third heat exchanger than in the first heat exchanger, and the degree of superheat of the refrigerant is further increased. The outside air processing apparatus according to claim 1, wherein the opening degree of the second expansion valve is controlled so as to achieve a target superheat degree. The said control means performs switching of an intermediate period mode in addition to a dehumidification mode and a humidification mode, and stops the said compressor and the said water | moisture-content adsorption | suction means in the said intermediate period mode. The outside air processing apparatus according to any one of the above. A total heat exchanger provided upstream of the first heat exchanger and the second heat exchanger and exchanging heat between the first air flow path and the second air flow path; 5. The outside air processing apparatus according to claim 4, wherein in the interim mode, moisture in the air in the first air flow path and the second air flow path is exchanged by the total heat exchanger.

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