JP7078375B2 - Outside air treatment machine and outside air treatment method using desiccant rotor - Google Patents

Description

The present invention relates to an outside air processing machine and an outside air processing method using a desiccant rotor.

As one of the devices for dehumidifying the outside air, there is a desiccant rotor provided with a dehumidifying agent that adsorbs the moisture in the outside air (for example, Patent Document 1-4).

Japanese Unexamined Patent Publication No. 2010-276317 Japanese Unexamined Patent Publication No. 2012-172880 Japanese Unexamined Patent Publication No. 2013-130389 Japanese Unexamined Patent Publication No. 2014-15309

When dehumidifying using a desiccant rotor, the outside air sent to the desiccant rotor is cooled (hereinafter referred to as precool) to increase the relative humidity in advance to improve the dehumidification efficiency. In addition, since the temperature of the outside air that has passed through the desiccant rotor has risen due to dehumidification by the desiccant rotor, the outside air that has passed through the desiccant rotor is recooled when cold air is supplied to the air-conditioned space. (Hereafter referred to as aftercool). Further, heated high-temperature air is sent to the adsorption surface of the desiccant rotor that has absorbed the moisture of the outside air to regenerate the adsorption surface, and the dehumidifying capacity of the desiccant rotor is maintained.

As one method of performing precooling, there is a method in which an evaporator is provided (hereinafter referred to as a precooling evaporator), and the outside air is cooled by exchanging heat with the precooling evaporator. Further, as one method of performing aftercooling, an evaporator different from the precooling evaporator (hereinafter referred to as an aftercooling evaporator) is provided, and the outside air is cooled by exchanging heat with the aftercooling evaporator. There is a way to be done. Further, as one method of heating the air used for regeneration, there is a method in which a condenser is provided and the outside air is heated by heat exchange with the condenser. Further, a heat pump unit that realizes a refrigeration cycle is also formed by connecting these two evaporators and one condenser. When such a heat pump unit is formed, the heat removed from the outside air in the precool evaporator and the aftercool evaporator is used for heating the air for regenerating the adsorption surface of the desiccant rotor, so that the outside air is used. The heat is used without waste.

However, in such a heat pump unit, the heat pump circuit becomes complicated, and it is difficult to control the capacity of the heat pump unit. That is, there is a possibility that the temperature of the outside air cannot be controlled to a desired value during precooling or aftercooling, and it is difficult to perform flexible operation such as controlling the capacity of the heat pump unit according to the outside air temperature.

Further, in the prior art, heated high-temperature air is sent to the suction surface of the desiccant rotor to regenerate the suction surface, but the degree of regeneration of the suction surface is not adjusted at that time. Therefore, for example, even when the outside air is low enough that it does not need to be recooled by the aftercool evaporator, dehumidification is performed by the desiccant rotor as in the case of other temperature and humidity conditions. As a result, the temperature rises, and recooling by an aftercool evaporator may be required. Further, for example, when the outside air has a low humidity, when the desiccant rotor dehumidifies the outside air as in the case of other temperature and humidity conditions, the outside air after passing through the desiccant rotor becomes an overhumidified state, which is lower than the desired humidity. There is a risk that air will be supplied to the air-conditioned space in this state.

That is, in the prior art, it is difficult to control the temperature and humidity of the outside air to a desired value when treating the outside air, and the outside air processing machine cannot be operated flexibly according to the outside air temperature and humidity, so that the outside air can be treated. It could not be treated favorably.

Therefore, in the present application, it is easy to control the temperature and humidity of the outside air to a desired value when treating the outside air, and the operation is flexibly performed according to the outside air temperature and humidity, so that the outside air can be treated appropriately. It is an object of the present invention to provide an outside air processing machine and an outside air processing method using a desiccant rotor that can be used.

In order to solve the above problems, in the present invention, the outside air processing machine using the desiccant rotor is provided with two heat pump units having independent refrigeration cycles.

Specifically, the present invention is provided across a supply air passage for supplying outside air to the air conditioning target space, an exhaust passage for discharging the return air from the air conditioning target space to the outside of the system, and an air supply passage and an exhaust passage. A first having a desiccant rotor, a first heat exchanger provided upstream of the desiccant rotor in the air supply path, and a second heat exchanger provided upstream of the desiccant rotor in the exhaust passage. It has a heat pump unit, a third heat exchanger provided on the downstream side of the desiccant rotor in the air supply passage, and a fourth heat exchanger provided on the upstream side of the desiccant rotor in the exhaust passage. The first heat pump unit includes a second heat pump unit having an independent refrigeration cycle, and a control means for controlling the capacity of the first heat pump unit and controlling the capacity of the second heat pump unit, and the second heat. The exchanger and the fourth heat exchanger are outside air treatment machines installed side by side in the vicinity of the desiccant rotor and in the direction of blocking the air flow.

In such an outside air processing machine, the first heat exchanger can be used as a precool evaporator, and the third heat exchanger can be used as an aftercool evaporator. The heat removed from the outside air in the precool evaporator and the aftercool evaporator is used to heat the air for regenerating the adsorption surface of the desiccant rotor in the second heat exchanger and the fourth heat exchanger. Therefore, the heat of the outside air is used without waste. Further, the first heat pump unit including the first heat exchanger and the second heat exchanger and the second heat pump unit including the third heat exchanger and the fourth heat exchanger are simple. Since each heat pump unit is formed by a heat pump circuit and the refrigeration cycle is realized independently, capacity control in each heat pump unit is easily performed. Therefore, it is easy to control the temperature and humidity of the outside air to a desired value during precooling and aftercooling. Further, since the second heat exchanger and the fourth heat exchanger are provided side by side in the vicinity of the desiccant rotor and in the direction of blocking the air flow, the air heated by heat exchange with the second heat exchanger and the second heat exchanger. The air heated by heat exchange with the heat exchanger of No. 4 flows into the suction surface of the desiccant rotor as it is, and the suction surface is regenerated.

Further, the capacity control of the second heat pump unit may be executed according to the air condition on the upstream side of the first heat exchanger.

With such an outside air processing machine, the operation of the second heat pump unit can be stopped depending on the outside air temperature and humidity, for example, when the outside air is low temperature or low humidity. Therefore, the heating of air for regenerating the adsorption surface of the desiccant rotor is suppressed, the regeneration of the adsorption surface of the desiccant rotor is suppressed, and the dehumidifying capacity of the desiccant rotor can be reduced. Therefore, for example, when the outside air is at a low temperature, the temperature rise due to dehumidification of the desiccant rotor is suppressed, and recooling by the aftercool evaporator becomes unnecessary. Further, for example, when the outside air has a low humidity, over-dehumidification by the desiccant rotor is prevented. That is, the operation of the outside air processing machine is flexibly performed according to the outside air temperature and humidity, and the outside air can be appropriately treated. In addition, energy saving can be realized by stopping the operation of the second heat pump unit.

Further, in the exhaust passage, the outside air is taken in on the upstream side of the desiccant rotor, and the amount of the taken in outside air changes according to the state of the air on the downstream side of the second heat exchanger and on the upstream side of the desiccant rotor. May be done.

With such an outside air processing machine, it is possible to adjust the state of the air that regenerates the suction surface of the desiccant rotor. That is, the degree of regeneration of the suction surface of the desiccant rotor can be adjusted.

Further, the outside air processor may be provided with a total heat exchanger straddling the inlet of the supply air passage and the inlet of the exhaust passage.

With such an outside air processor, the heat of the air returned from the air-conditioned space can be used without waste, and the burden on the precool evaporator can be reduced.

The present invention can also be grasped from the aspect of the method. That is, in the present invention, for example, in the air supply process of supplying the outside air to the air conditioning target space through the air supply passage, the exhaust process of discharging the return air from the air conditioning target space to the outside of the system through the exhaust passage, and the air supply passage. It has a first heat exchanger provided on the upstream side of the desiccant rotor provided across the supply air passage and the exhaust passage, and a second heat exchanger provided on the upstream side of the desiccant rotor in the exhaust passage. A third heat exchanger that controls the capacity of the first heat pump unit and is installed on the downstream side of the desiccant rotor in the air supply passage, and a fourth heat exchanger that is installed on the upstream side of the desiccant rotor in the exhaust passage. The second heat exchanger and the fourth heat exchanger are provided with a control process for controlling the capacity of the second heat pump unit, which has and is independent of the refrigeration cycle from the first heat pump unit. It may be an outside air treatment method provided side by side in the vicinity of the desiccant rotor and in a direction of blocking the air flow.

The outside air treatment machine and the outside air treatment method using the desiccant rotor can easily control the temperature and humidity of the outside air to a desired value when treating the outside air, and can be operated flexibly according to the outside air temperature and humidity. Therefore, the outside air can be treated suitably.

FIG. 1 is a block diagram of an outside air processing machine according to an embodiment of the present invention. FIG. 2 is a schematic view of the desiccant rotor as viewed from the upstream side. FIG. 3 is an operation flow diagram of the outside air processing machine. FIG. 4 is an explanatory diagram of outside air treatment during the cooling / dehumidifying operation (pattern A). FIG. 5 is an air diagram showing changes in temperature and humidity during the cooling and dehumidifying operation (pattern A). FIG. 6 is an explanatory diagram of outside air treatment during the cooling / dehumidifying operation (pattern B). FIG. 7 is an air diagram showing changes in temperature and humidity during the cooling and dehumidifying operation (pattern B). FIG. 8 is an explanatory diagram of outside air treatment during the cooling / dehumidifying operation (pattern C). FIG. 9 is an air diagram showing changes in temperature and humidity during the cooling and dehumidifying operation (pattern C). FIG. 10 is an explanatory diagram of outside air treatment during the cooling / dehumidifying operation (pattern D). FIG. 11 is an air diagram showing changes in temperature and humidity during the cooling and dehumidifying operation (pattern D). FIG. 12 is an explanatory diagram of outside air processing during the heating / humidifying operation. FIG. 13 is an air diagram showing changes in temperature and humidity during heating and humidification operation.

Hereinafter, embodiments of the present invention will be described. The embodiments shown below are examples of embodiments of the present invention, and the technical scope of the present invention is not limited to the following embodiments.

FIG. 1 is a block diagram of an outside air processing machine according to an embodiment of the present invention. The outside air processor 100 shown in FIG. 1 has a supply air passage 1 through which air supplied to the air-conditioned space is passed, an exhaust passage 2 through which the return air from the air-conditioned space discharged to the outside of the system passes, and an air supply passage. A desiccant rotor 3 straddling 1 and an exhaust passage 2 is provided. Further, the outside air processor 100 includes a first heat exchanger 4 on the upstream side of the desiccant rotor 3 in the supply air passage 1, and a second heat exchanger on the upstream side and in the vicinity of the desiccant rotor 3 in the exhaust passage 2. A third heat exchanger 6 is provided on the downstream side of the desiccant rotor 3, and a fourth heat exchanger 7 is provided on the upstream side and in the vicinity of the desiccant rotor 3 in the exhaust passage 2. Further, the outside air processing machine 100 includes a compressor 8 and an expansion valve 9, and is a first heat pump unit 10 including a first heat exchanger 4, a second heat exchanger 5, a compressor 8, and an expansion valve 9. To prepare for. Further, the outside air processing machine 100 includes a compressor 11 and an expansion valve 12, and a second heat pump unit 13 including a third heat exchanger 6, a fourth heat exchanger 7, a compressor 11, and an expansion valve 12. To prepare for. Further, the cooling coil used in the first heat exchanger 4 can remove both latent heat and sensible heat of the passing air, for example, and the cooling coil used in the third heat exchanger 6 is, for example, the passing air. It may be one that can remove only the sensible heat of.

Further, the outside air processing machine 100 includes a total heat exchanger 14 straddling the inlet of the supply air passage 1 and the inlet of the exhaust passage 2. Further, the outside air processing machine 100 includes a duct for taking in outside air at a point downstream of the total heat exchanger 14 and upstream of the second heat exchanger 5 in the exhaust passage 2, and a motor damper 15 in the duct for taking in outside air. Further, the outside air processor 100 includes a humidifier 16 downstream of the third heat exchanger 6, an air supply fan 17 that supplies air to the air-conditioned space at the outlet of the air supply passage 1, and an outlet of the exhaust passage 2. Is equipped with an exhaust fan 18 that discharges return air from the air-conditioned space.

Further, the outside air processor 100 has a thermo-humidity meter 19A upstream of the first heat exchanger 4 and downstream of the total heat exchanger 14, and a thermo-humidity meter downstream of the first heat exchanger 4 and upstream of the desiccant rotor 3. A total of 19B, a thermo-humidity meter 19C downstream of the desiccant rotor 3 and upstream of the third heat exchanger 6, a thermo-humidifier 19D downstream of the third heat exchanger 6 and upstream of the humidifier 16, and a humidifier. A thermo-humidifier 19E is provided downstream of 16. Further, in the exhaust passage 2, a thermo-hygrometer 19F is provided downstream of the second heat exchanger 5 and upstream of the desiccant rotor 3. Although not shown, the thermo-hygrometer 19D has a control device that controls the capacity of the first heat pump unit 10 so that the enthalpy calculated from the temperature and humidity measured by the thermo-hygrometer 19B becomes a desired value. A control device that controls the capacity of the second heat pump unit 13 so that the temperature to be measured becomes a desired value, and a humidifier 16 that controls the humidity measured by the thermohygrometer 19E to a desired value. It is equipped with a control device. Further, hereinafter, a point outside the system of the outside air processing machine 100 is point A, a place where the thermo-hygrometer 19A is provided is point B, a place where the thermo-hygrometer 19B is provided is point C, and a thermo-hygrometer 19C. The place where is provided is point D, the place where the thermo-hygrometer 19D is provided is point E, the place where the thermo-hygrometer 19E is provided is point F, and the place where the thermo-hygrometer 19F is provided is G. Let it be a point.

Further, the second heat exchanger 5 and the fourth heat exchanger 7 are not provided side by side in the direction of the return air flow from the air-conditioned space in the exhaust passage 2, but in a direction of blocking the return air flow. It is installed side by side. Further, the second heat exchanger 5 is provided closer to the center of the desiccant rotor 3 than the fourth heat exchanger 7.

FIG. 2 is a schematic view of the desiccant rotor 3 as viewed from the upstream side. Air heated by heat exchange with the second heat exchanger 5 flows into the upper half portion 20 of the desiccant rotor 3 in the exhaust passage 2, and into the lower half portion 21 of the desiccant rotor 3 in the exhaust passage 2. , The heated air flows in by exchanging heat with the fourth heat exchanger 7. At this time, the area ratio of the portion 20 to the portion 21 is about 3: 2.

FIG. 3 shows an operation flow diagram of the outside air processing machine 100. The outside air processing machine 100 first measures the return air from the air-conditioned space and the absolute humidity of the outside air heat exchanged by the total heat exchanger 14 at point B (S101). Then, when the absolute humidity value at point B is 8.9 g / kg or more, the cooling / dehumidifying operation is performed (S104-S107), and when the absolute humidity value at point B is less than 8.9 g / kg, heating is performed. Humidification operation is performed (S103). In the cooling / dehumidifying operation, the heat medium circulates in the expansion valve 9, the first heat exchanger 4, the compressor 8, and the second heat exchanger 5 in this order in the first heat pump unit 10. Further, in the second heat pump unit 13, the heat medium circulates in the order of the expansion valve 12, the third heat exchanger 6, the compressor 11, and the fourth heat exchanger 7. On the other hand, in the case of heating / humidifying operation, the heat medium circulates in each heat pump unit in the reverse order of the above.

<Cooling and dehumidifying operation>
In the case of cooling and dehumidifying operation, the enthalpy is first calculated from the temperature and humidity of the outside air measured at point B (S104). Then, the operation method of the outside air processing machine changes depending on whether the enthalpy is 13.5 kcal / kg or more and less than 13.5 kcal / kg (S105). When the enthalpy is 13.5 kcal / kg or more, the control device of the outside air processor 100 calculates the enthalpy from the temperature and humidity of the air measured at the point C so that the enthalpy value becomes 12.0 kcal / kg. The capacity of the first heat pump unit 10 is controlled (S106). Further, the control device of the outside air processing machine 100 controls the capacity of the second heat pump unit 13 so that the temperature of the air measured at the point E becomes 19 ° C. (DB) (S106). On the other hand, when the enthalpy value calculated from the temperature and humidity measured at point B is less than 13.5 kcal / kg, the control device of the outside air processing machine 100 calculates the enthalpy from the temperature and humidity of the air measured at point C. Then, the capacity of the first heat pump unit 10 is controlled so that the enthalpy value is 9.7 kcal / kg (S107). Further, the operation of the second heat pump unit 13 is stopped (S107).

Further, during the cooling / dehumidifying operation, the desiccant rotor 3 is rotationally controlled so that the absolute humidity measured at point D is 8.9 g / kg. Further, the rotation speed control of the exhaust fan 18 and the open / close control of the motor damper 15 are performed so that the temperature value measured at the G point is from 40 ° C. to 55 ° C. (DB).

4 to 11 are views showing a process in which the outside air having various temperatures and humidity at the point A is controlled to a desired value by the cooling / dehumidifying operation of the outside air processing machine 100 and is supplied to the air-conditioned space. The temperature and humidity conditions of the outside air at point A are, for example, the values shown in Table 1, and the outside air is cooled and dehumidified and supplied to the air-conditioned space at a temperature of 19 ° C. and a humidity of 65%. The temperature of the air-conditioned space is, for example, 26 ° C., and the humidity is 50%. Further, the first heat exchanger 4 has a cooling capacity of, for example, 5.3 kW, the third heat exchanger 6 has a cooling capacity of, for example, 4.0 kW, and the compressor 8 has an output of, for example, 1. It is assumed that the compressor 11 has an output of, for example, 0.7 kW. Further, it is assumed that the desiccant rotor 3 has an outer diameter of 660 mm, for example.

<< Pattern A >>
FIG. 4 is an explanatory diagram of outside air treatment when the outside air temperature is 34.4 ° C. and the humidity is 56% at point A. FIG. 5 is an psychrometric chart showing changes in temperature and humidity during the outside air treatment process. The outside air is first taken into the total heat exchanger 14 with an air volume of 1000 CMH, and is heat-exchanged with the return air also taken in from the air-conditioned space in the total heat exchanger 14 with an air volume of 1000 CMH. The outside air that has passed through the total heat exchanger 14 has a temperature of 28.5 ° C. and a humidity of 54% at point B. When the enthalpy is calculated from this temperature and humidity, it is about 14.9 kcal / kg. Therefore, as shown in the operation flow chart of FIG. 3, the capacity of the first heat pump unit 10 is controlled so that the enthalpy value at point C is 12.0 kcal / kg (temperature 18.3 ° C., humidity 95%). .. After that, the outside air passes through the desiccant rotor 3 and is dehumidified, and at point D, the temperature becomes 31.1 ° C. and the humidity becomes 32%. After that, the outside air is recooled to a temperature of 19 ° C. by the third heat exchanger 6 of the second heat pump unit 13 (humidity 65%). Then, air is supplied to the air-conditioned space by the air supply fan 17 with an air volume of 1000 CMH.

On the other hand, the return air from the air-conditioned space is exchanged with the outside air in the total heat exchanger 14, and then heated by the second heat exchanger 5 and the fourth heat exchanger 7. At this time, the temperature of the air at the G point is 55 ° C. or higher. Therefore, the opening degree of the motor damper 15 is adjusted, the outside air is taken into the exhaust passage 2 at 350 CMH, and the air at the G point is adjusted to a temperature of 50.4 ° C. and a humidity of 22%. Then, the air heated by the second heat exchangers 5 and 7 flows to the desiccant rotor 3, and the adsorption surface of the desiccant rotor 3 is regenerated. Then, the air used for regenerating the adsorption surface of the desiccant rotor 3 is discharged to the outside of the system by the exhaust fan 18 with an air volume of 1350 CMH after passing through the desiccant rotor 3.

<< Pattern B >>
FIG. 6 is an explanatory diagram of outside air treatment when the outside air temperature is 31 ° C. and the humidity is 50% at point A. FIG. 7 is a psychrometric chart showing changes in temperature and humidity during the outside air treatment process. The outside air is taken into the total heat exchanger 14 with an air volume of 1000 CMH, and is heat-exchanged with the return air also taken in from the air-conditioned space in the total heat exchanger 14 with an air volume of 1000 CMH. The outside air that has passed through the total heat exchanger 14 has a temperature of 27.5 ° C. and a humidity of 50% at point B. When the enthalpy is calculated from this temperature and humidity, it is about 13.6 kcal / kg. Therefore, as shown in the operation flow chart of FIG. 3, the capacity of the first heat pump unit 10 is controlled so that the enthalpy value at point C is 12.0 kcal / kg (temperature 20.9 ° C., humidity 74%). .. After that, the outside air passes through the desiccant rotor 3 and is dehumidified, and at point D, the temperature becomes 30.2 ° C. and the humidity becomes 33%. After that, the outside air is recooled to a temperature of 19 ° C. by the third heat exchanger 6 of the second heat pump unit 13 (humidity 65%). Then, air is supplied to the air-conditioned space by the air supply fan 17 with an air volume of 1000 CMH.

On the other hand, the return air from the air-conditioned space is exchanged with the outside air in the total heat exchanger 14, and then heated by the second heat exchanger 5 and the fourth heat exchanger 7. At this time, at point G, the temperature of the air heated by the second heat exchanger 5 is 42.8 ° C., and the humidity is 24%. Further, the temperature of the air heated by the fourth heat exchanger 7 is 52 ° C., and the humidity is 15%. Therefore, since the temperature does not exceed 55 ° C. at the G point, the motor damper 15 remains in the closed state. Then, the air heated by the second heat exchanger 5 and the fourth heat exchanger 7 flows to the desiccant rotor 3, and the adsorption surface of the desiccant rotor 3 is regenerated. Then, the air used to regenerate the adsorption surface of the desiccant rotor 3 is discharged to the outside of the system by the exhaust fan 18 with an air volume of 1000 CMH after passing through the desiccant rotor 3.

<< Pattern C >>
FIG. 8 is an explanatory diagram of outside air treatment when the outside air temperature is 31 ° C. and the humidity is 46% at point A. FIG. 9 is a psychrometric chart showing changes in temperature and humidity during the outside air treatment process. The outside air is taken into the total heat exchanger 14 with an air volume of 1000 CMH, and is heat-exchanged with the return air taken in from the air-conditioned space in the total heat exchanger 14 with an air volume of 1000 CMH. The outside air that has passed through the total heat exchanger 14 has a temperature of 27.5 ° C. and a humidity of 49% at point B. When the enthalpy is calculated from this temperature and humidity, it is less than 13.5 kcal / kg. Therefore, as shown in the operation flow chart of FIG. 3, the capacity of the first heat pump unit 10 is controlled so that the enthalpy value at point C is 9.7 kcal / kg (temperature 15 ° C., humidity 95%). After that, the outside air passes through the desiccant rotor 3 and is dehumidified. However, here, as shown in the operation flow chart of FIG. 3, the operation of the second heat pump unit 13 is stopped when the enthalpy at the point B is less than 13.5 kcal / kg. Therefore, the air that has passed through the fourth heat exchanger 7 in the exhaust passage 2 is not heated. Therefore, the degree of regeneration of the suction surface of the desiccant rotor 3 is lower than that when the second heat pump unit 13 is in operation. Therefore, the temperature rise of the outside air passing through the desiccant rotor 3 in the air supply passage 1 is suppressed, and the temperature becomes 19 ° C. and the humidity becomes 65% at the point D. Since the operation of the second heat pump unit 13 is stopped, the outside air is supplied to the air-conditioned space by the air supply fan 17 with an air volume of 1000 CMH while maintaining the temperature and humidity at the point D.

On the other hand, the return air from the air-conditioned space is heated by the second heat exchanger 5 after being heat-exchanged with the outside air in the total heat exchanger 14. At this time, the temperature of the air heated by the second heat exchanger 5 at the G point becomes 55 ° C. or higher. Therefore, the opening degree of the motor damper 15 is adjusted, the outside air is taken into the exhaust passage 2 at 350 CMH, and the temperature of the air heated by the second heat exchanger 5 at the G point is adjusted to 53.3 ° C. and the humidity 14%. Will be done. Further, the air that has passed through the desiccant rotor 3 is discharged to the outside of the system by the exhaust fan 18 with an air volume of 1350 CMH.

<< Pattern D >>
FIG. 10 is an explanatory diagram of outside air treatment when the outside air temperature is 19 ° C. and the humidity is 90% at point A. FIG. 11 is a psychrometric chart showing changes in temperature and humidity during the outside air treatment process. The outside air is taken into the total heat exchanger 14 with an air volume of 1000 CMH, and is heat-exchanged with the return air taken in from the air-conditioned space in the total heat exchanger 14 with an air volume of 1000 CMH. The outside air that has passed through the total heat exchanger 14 has a temperature of 23.9 ° C. and a humidity of 60% at point B. When the enthalpy is calculated from this temperature and humidity, it is less than 13.5 kcal / kg. Therefore, as shown in the operation flow chart of FIG. 3, the capacity of the first heat pump unit 10 is controlled so that the enthalpy value at point C is 9.7 kcal / kg (temperature 15 ° C., humidity 95%). After that, the outside air passes through the desiccant rotor 3 and is dehumidified. However, here, as in the pattern C, the operation of the second heat pump unit 13 is stopped because the enthalpy at the point B is less than 13.5 kcal / kg. Therefore, the air that has passed through the fourth heat exchanger 7 in the exhaust passage 2 is not heated. Therefore, the degree of regeneration of the suction surface of the desiccant rotor 3 is lower than that when the second heat pump unit 13 is in operation. Therefore, the temperature rise of the outside air passing through the desiccant rotor 3 in the air supply passage 1 is suppressed, and the temperature becomes 19 ° C. and the humidity becomes 65% at the point D. Since the operation of the second heat pump unit 13 is stopped, the outside air is supplied to the air-conditioned space by the air supply fan 17 with an air volume of 1000 CMH while maintaining the temperature and humidity at the point D.

On the other hand, the return air from the air-conditioned space is heated by the second heat exchanger 5 after being heat-exchanged with the outside air in the total heat exchanger 14. At this time, at point G, the temperature of the air heated by the second heat exchanger 5 is 44.4 ° C., and the humidity is 20%. Therefore, since the temperature does not exceed 55 ° C. at the G point, the motor damper 15 remains in the closed state. Further, after passing through the desiccant rotor 3, the return air is discharged to the outside of the system by the exhaust fan 18 with an air volume of 1000 CMH.

<Effect>
In such an outside air processing machine 100, the first heat exchanger 4 can be used as a precooling evaporator, and the third heat exchanger 6 can be used as an aftercooling evaporator. Then, the heat of the outside air removed by the precool evaporator and the aftercool evaporator is used to regenerate the adsorption surface of the desiccant rotor 3 in the second heat exchanger 5 and the fourth heat exchanger 7. Since it is used for heating, the heat of the outside air is used without waste.

Further, the first heat pump unit 10 and the second heat pump unit 13 are each formed by a simple heat pump circuit, and the refrigeration cycle is realized independently. Therefore, capacity control in each heat pump unit can be easily performed. Therefore, even if the temperature and humidity of the outside air at point A are various, it is easy to control the outside air temperature to a desired value during precooling (point C) and aftercooling (point E), and the space to be air-conditioned. Suitable outside air can be supplied to the air. Further, since the first heat pump unit 10 and the second heat pump unit 13 are independent of each other, for example, both latent heat and sensible heat of the air passing through the cooling coil used in the first heat exchanger 4 are available. For pre-cooling evaporators and after-cooling evaporators, such as using a cooling coil used in the third heat exchanger 6 that can remove only the sensible heat of the passing air. Different types of cooling coils can be used for each.

Further, the air heated by heat exchange with the second heat exchanger 5 and the air heated by heat exchange with the fourth heat exchanger 7 flow into the suction surface of the desiccant rotor 3 as they are, respectively. Regenerate the suction surface. Therefore, as shown in the operation flow diagram of FIG. 3, if the operation of the second heat pump unit 13 is stopped when the enthalpy value at point B is low (pattern C, pattern D), the fourth heat exchanger 7 and The heat is not exchanged with the air, and the air that has passed through the fourth heat exchanger 7 is sent to the suction surface of the desiccant rotor 3 without being heated. Therefore, the regeneration of the adsorption surface of the desiccant rotor 3 is suppressed, and the dehumidifying capacity of the desiccant rotor 3 is reduced. Therefore, when the outside air is low temperature as in pattern C and pattern D, the temperature rise due to dehumidification of the desiccant rotor 3 is suppressed, and recooling by the aftercool evaporator becomes unnecessary. Further, although not illustrated here, when the outside air has a low humidity, over-dehumidification by the desiccant rotor 3 is prevented. That is, the outside air processing machine 100 can be flexibly operated according to the outside air temperature and humidity, and can appropriately treat the outside air. In addition, energy saving can be realized by stopping the operation of the second heat pump unit 13.

Further, in the exhaust passage 2, the second heat exchanger 5 and the fourth heat exchanger 7 are not provided side by side in the direction of the air flow of the return air from the air-conditioned space in the vicinity of and upstream of the desiccant rotor 3. , They are installed side by side in a direction that blocks the air flow of the return air. Then, the second heat exchanger 5 is positioned closer to the center of the desiccant rotor 3 than the fourth heat exchanger 7, and the air heated by exchanging heat with the second heat exchanger 5 in the desiccant rotor 3. The ratio of the portion 20 into which the heat flows and the portion 21 into which the heated air flows by exchanging heat with the fourth heat exchanger 7 is about 3: 2. Therefore, even when the operation of the second heat pump unit 13 is stopped and the fourth heat exchanger 7 does not operate (pattern C, pattern D), the air heated by the second heat exchanger 5 is used. The ratio of the flowing portion 20 is relatively large. Therefore, even when the operation of the second heat pump unit 13 is stopped, the suction surface of the desiccant rotor 3 is not abruptly regenerated, and the dehumidifying capacity of the desiccant rotor 3 is prevented from being abruptly reduced. ..

However, the arrangement of the second heat exchanger 5 and the fourth heat exchanger 7 may be appropriately changed according to the embodiment. For example, the fourth heat exchanger 7 may be provided closer to the center of the desiccant rotor 3 than the second heat exchanger 5, and the second heat exchanger 5 and the fourth heat exchanger 7 may be desiccanted. It may be provided equidistant from the center of the rotor 3. Further, in order to change the area ratio between the portion 20 and the portion 21, the arrangement of the second heat exchanger 5 and the fourth heat exchanger 7 may be appropriately changed.

Further, since the outside air processing machine 100 can adjust the temperature and humidity of the air at the G point by opening and closing the motor damper 15, the degree of regeneration of the suction surface of the desiccant rotor 3 can be adjusted.

Further, since the total heat exchanger 14 is provided straddling the inlet of the air supply passage 1 and the inlet of the exhaust passage 2, the heat of the air returned from the air-conditioned space is used without waste, and the first heat is used. The temperature of the outside air flowing into the exchanger 4 can be lowered, and the burden on the first heat exchanger 4 can be reduced.

<Heating and humidifying operation>
FIG. 12 is an explanatory diagram of outside air processing during the heating / humidifying operation. FIG. 13 is an psychrometric chart showing changes in temperature and humidity during the outside air treatment process. Here, the outside air temperature is, for example, 6.6 ° C. and the humidity is 63%, and the temperature of the air-conditioned space is, for example, 26 ° C. and the humidity is 50%. Further, the humidifier 16 may have a humidifying capacity of, for example, 2.5 kg / h.

The outside air first enters the total heat exchanger 14, and is exchanged with the return air from the air-conditioned space in the total heat exchanger 14. The outside air that has passed through the total heat exchanger 14 has a temperature of 15.4 ° C. and a humidity of 58% at point B. After that, as shown in the operation flow chart of FIG. 3, the capacity of the first heat pump unit 10 is controlled so that the enthalpy value at point C becomes 10.3 kcal / kg (temperature 26.9 ° C., humidity 29%). ). After that, since the operation of the desiccant rotor 3 and the second heat pump unit 13 is stopped, the outside air is sent to the humidifier 16 with the temperature and humidity as they are. Then, the humidifier 16 humidifies the humidity so that the absolute humidity at the point F is 8.2 g / kg (for example, 22 ° C., 50%). After that, the outside air is supplied to the air-conditioned space by the air supply fan 17 with an air volume of 1000 CMH.

As described above, the outside air processing machine 100 can perform not only the cooling / dehumidifying operation but also the heating / humidifying operation according to the temperature and humidity of the outside air, and can supply suitable outside air to the air-conditioned space.

1 ... air supply passage; 2 ... exhaust passage; 3 ... desiccant rotor; 4 ... first heat exchanger; 5 ... second heat exchanger; 6 ... third heat exchanger; 7・ ・ Fourth heat exchanger; 8 ・ ・ Compressor; 9 ・ ・ Expansion valve; 10 ・ ・ First heat pump unit; 11 ・ ・ Compressor; 12 ・ ・ Expansion valve; 13 ・ ・ Second heat pump unit 14 ... Total heat exchanger; 15 ... Motor damper; 16 ... Humidifier; 17 ... Air supply fan; 18 ... Exhaust fan; 19A, 19B, 19C, 19D, 19E, 19F ... Thermo-hygrometer; 20 ... The part where the heated air flows in after exchanging heat with the second heat exchanger 5; 21 ... The part where the heated air flows in after exchanging heat with the fourth heat exchanger 7; 100 ... Outside air Processing machine

Claims (11)

The air supply path that supplies the outside air to the air-conditioned space,
An exhaust passage that exhausts the return air from the air-conditioned space to the outside of the system,
A desiccant rotor provided across the air supply passage and the exhaust passage, and
A first having a first heat exchanger provided upstream of the desiccant rotor in the air supply passage and a second heat exchanger provided upstream of the desiccant rotor in the exhaust passage. With the heat pump unit,
It has a third heat exchanger provided on the downstream side of the desiccant rotor in the air supply passage and a fourth heat exchanger provided on the upstream side of the desiccant rotor in the exhaust passage. The second heat pump unit, which has an independent refrigeration cycle from the first heat pump unit,
A control means for controlling the capacity of the first heat pump unit and controlling the capacity of the second heat pump unit is provided.
The second heat exchanger and the fourth heat exchanger are provided side by side in the vicinity of the desiccant rotor and in a direction of blocking the air flow.
In the exhaust passage, outside air is taken in on the upstream side of the desiccant rotor, and the outside air is taken in.
The amount of outside air taken in is changed according to the state of air downstream of the second heat exchanger and upstream of the desiccant rotor.
Outside air processing machine. The capacity control of the second heat pump unit is executed according to the air condition on the upstream side of the first heat exchanger.
The outside air processing machine according to claim 1. The outside air processor comprises a total heat exchanger straddling the inlet of the air supply passage and the inlet of the exhaust passage.
The outside air processing machine according to claim 1 or 2. The air supply path that supplies the outside air to the air-conditioned space,
An exhaust passage that exhausts the return air from the air-conditioned space to the outside of the system,
A desiccant rotor provided across the air supply passage and the exhaust passage, and
A first having a first heat exchanger provided upstream of the desiccant rotor in the air supply passage and a second heat exchanger provided upstream of the desiccant rotor in the exhaust passage. With the heat pump unit,
It has a third heat exchanger provided on the downstream side of the desiccant rotor in the air supply passage and a fourth heat exchanger provided on the upstream side of the desiccant rotor in the exhaust passage. The second heat pump unit, which has an independent refrigeration cycle from the first heat pump unit,
A control means for controlling the capacity of the first heat pump unit and controlling the capacity of the second heat pump unit is provided.
The second heat exchanger and the fourth heat exchanger are provided side by side in the vicinity of the desiccant rotor and in a direction of blocking the air flow, and the second heat exchanger is the fourth heat exchange. It is located closer to the center of the desiccant rotor than the vessel.
Outside air processing machine. The air supply path that supplies the outside air to the air-conditioned space,
An exhaust passage that exhausts the return air from the air-conditioned space to the outside of the system,
A desiccant rotor provided across the air supply passage and the exhaust passage, and
A first heat exchanger provided upstream of the desiccant rotor in the air supply passage, a second heat exchanger provided upstream of the desiccant rotor in the exhaust passage, and the first heat. A first heat pump unit having a first compressor provided in the middle of a pipe connecting the exchanger and the second heat exchanger, and a first heat pump unit.
It has a third heat exchanger provided on the downstream side of the desiccant rotor in the air supply passage and a fourth heat exchanger provided on the upstream side of the desiccant rotor in the exhaust passage. The second heat pump unit, which has an independent refrigeration cycle from the first heat pump unit,
A control means for controlling the capacity of the first heat pump unit and controlling the capacity of the second heat pump unit.
Equipped with a total heat exchanger that exchanges heat between the outside air and the return air,
The air supply passage and the exhaust passage are arranged in parallel so that the direction of the air flow in the air supply passage and the direction of the air flow in the exhaust passage are in the same direction.
The total heat exchanger is provided so as to straddle the inlets of the air supply passage and the exhaust passage.
The first compressor is provided in the exhaust passage on the upstream side of the second heat exchanger and the fourth heat exchanger.
Outside air processing machine. The second heat pump unit further comprises a second compressor provided in the exhaust passage on the downstream side of the desiccant rotor.
The outside air processing machine according to claim 5. The air supply path that supplies the outside air to the air-conditioned space,
An exhaust passage that exhausts the return air from the air-conditioned space to the outside of the system,
A desiccant rotor provided across the air supply passage and the exhaust passage, and
A first having a first heat exchanger provided upstream of the desiccant rotor in the air supply passage and a second heat exchanger provided upstream of the desiccant rotor in the exhaust passage. With the heat pump unit,
It has a third heat exchanger provided on the downstream side of the desiccant rotor in the air supply passage and a fourth heat exchanger provided on the upstream side of the desiccant rotor in the exhaust passage. The second heat pump unit, which has an independent refrigeration cycle from the first heat pump unit,
A control means for controlling the capacity of the first heat pump unit and controlling the capacity of the second heat pump unit.
Equipped with a total heat exchanger that exchanges heat between the outside air and the return air,
The air supply passage and the exhaust passage are arranged in parallel so that the direction of the air flow in the air supply passage and the direction of the air flow in the exhaust passage are in the same direction.
The total heat exchanger is provided so as to straddle the inlets of the air supply passage and the exhaust passage.
The enthalpy at the position is calculated from the temperature and humidity at the position between the total heat exchanger and the first heat exchanger.
The control means controls the capacity of the first heat pump unit so that the enthalpy at the position between the first heat exchanger and the desiccant rotor becomes the first predetermined value according to the value of the enthalpy. And
The control means controls the capacity of the second heat pump unit so that the temperature at a position on the downstream side of the third heat exchanger becomes a second predetermined value, or operates the second heat pump unit. Will be stopped,
Outside air processing machine. The air supply process that supplies outside air to the air-conditioned space through the air supply path,
The exhaust process that exhausts the return air from the air-conditioned space to the outside of the system through the exhaust passage,
A first heat exchanger provided in the air supply passage on the upstream side of the desiccant rotor provided across the air supply passage and the exhaust passage, and a first heat exchanger provided on the upstream side of the desiccant rotor in the exhaust passage. The capacity of the first heat pump unit having the second heat exchanger is controlled, and the third heat exchanger provided downstream of the desiccant rotor in the air supply passage and the desiccant rotor in the exhaust passage. It includes a fourth heat exchanger provided on the upstream side of the heat exchanger, and a control step of controlling the capacity of the second heat pump unit having a refrigerating cycle independent of the first heat pump unit.
The second heat exchanger and the fourth heat exchanger are provided side by side in the vicinity of the desiccant rotor and in a direction of blocking the air flow.
In the exhaust passage, outside air is taken in on the upstream side of the desiccant rotor, and the outside air is taken in.
The amount of outside air taken in is changed according to the state of air downstream of the second heat exchanger and upstream of the desiccant rotor.
Outside air treatment method. The air supply process that supplies outside air to the air-conditioned space through the air supply path,
The exhaust process that exhausts the return air from the air-conditioned space to the outside of the system through the exhaust passage,
A first heat exchanger provided in the air supply passage on the upstream side of the desiccant rotor provided across the air supply passage and the exhaust passage, and a first heat exchanger provided on the upstream side of the desiccant rotor in the exhaust passage. The capacity of the first heat pump unit having the second heat exchanger is controlled, and the third heat exchanger provided downstream of the desiccant rotor in the air supply passage and the desiccant rotor in the exhaust passage. It includes a fourth heat exchanger provided on the upstream side of the heat exchanger, and a control step of controlling the capacity of the second heat pump unit having a refrigerating cycle independent of the first heat pump unit.
The second heat exchanger and the fourth heat exchanger are provided side by side in the vicinity of the desiccant rotor and in a direction of blocking the air flow, and the second heat exchanger is the fourth heat exchange. It is located closer to the center of the desiccant rotor than the vessel.
Outside air treatment method. The air supply process that supplies outside air to the air-conditioned space through the air supply path,
The exhaust process that exhausts the return air from the air-conditioned space to the outside of the system through the exhaust passage,
A first heat exchanger provided in the air supply passage on the upstream side of the desiccant rotor provided across the air supply passage and the exhaust passage, and a first heat exchanger provided on the upstream side of the desiccant rotor in the exhaust passage. The second heat exchanger, the first heat exchanger and the second heat exchanger
A first compressor provided in the middle of the connecting pipe, and a third heat exchanger provided on the downstream side of the desiccant rotor in the air supply path by controlling the capacity of the first heat pump unit having the first compressor. , A fourth heat exchanger provided upstream of the desiccant rotor in the exhaust passage, and capacity control of the second heat pump unit having a refrigeration cycle independent of the first heat pump unit. Control process and
The air supply passage and the exhaust passage are arranged in parallel so that the direction of the air flow in the air supply passage and the direction of the air flow in the exhaust passage are in the same direction, and the air supply passage and the exhaust passage are arranged in parallel. Including a heat exchange process in which a total heat exchanger provided across each inlet exchanges heat between the outside air and the return air.
The first compressor is provided in the exhaust passage on the upstream side of the second heat exchanger and the fourth heat exchanger.
Outside air treatment method. The air supply process that supplies outside air to the air-conditioned space through the air supply path,
The exhaust process that exhausts the return air from the air-conditioned space to the outside of the system through the exhaust passage,
A first heat exchanger provided in the air supply passage on the upstream side of the desiccant rotor provided across the air supply passage and the exhaust passage, and a first heat exchanger provided on the upstream side of the desiccant rotor in the exhaust passage. The capacity of the first heat pump unit having the second heat exchanger is controlled, and the third heat exchanger provided downstream of the desiccant rotor in the air supply passage and the desiccant rotor in the exhaust passage. A control step of controlling the capacity of a second heat pump unit having a fourth heat exchanger provided on the upstream side and having a refrigerating cycle independent of the first heat pump unit.
The air supply passage and the exhaust passage are arranged in parallel so that the direction of the air flow in the air supply passage and the direction of the air flow in the exhaust passage are in the same direction, and the air supply passage and the exhaust passage are arranged in parallel. Including a heat exchange process in which a total heat exchanger provided across each inlet exchanges heat between the outside air and the return air.
The enthalpy at the position is calculated from the temperature and humidity at the position between the total heat exchanger and the first heat exchanger.
In the control step, the capacity of the first heat pump unit is controlled so that the enthalpy at the position between the first heat exchanger and the desiccant rotor becomes the first predetermined value according to the value of the enthalpy. Made,
In the control step, the capacity of the second heat pump unit is controlled so that the temperature at the position downstream of the third heat exchanger becomes the second predetermined value, or the operation of the second heat pump unit is performed. Will be stopped,
Outside air treatment method.

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