JP4848211B2 - Dehumidification air conditioning system - Google Patents

Description

  The present invention relates to a desiccant air conditioner and a dehumidifying air conditioning system including a heat pump as means for heating the regenerated air and cooling the treated air.

  As a dehumidification air-conditioning system concerning this invention, there exists a thing disclosed by patent document 1, for example. In Patent Document 1, the dehumidifying device is configured by an air supply path and an exhaust path, an adsorbent holding mechanism and a heat pump, and the low-temperature heat source and the high-temperature heat source of the heat pump are more than the adsorbent holding mechanism in the air supply path and the exhaust path, respectively. Arranged upstream. And energy saving is aimed at by using effectively the low temperature heat source and high temperature heat source of this heat pump.

  In addition, as another conventional technique according to the present invention, a known technique of Non-Patent Document 1 can be cited. In this known example, energy is saved by introducing a heat pump, and at the same time, an auxiliary heater is provided for the regeneration air of the dehumidification rotor, and the regeneration air is heated by the high-temperature heat source of the heat pump and further heated by this auxiliary heater to regenerate the dehumidification rotor. The structure leads to the zone.

Japanese Patent Laying-Open No. 2005-201624 (FIG. 1) Proceedings of the 2005 Air Conditioning and Sanitation Engineering Conference pp. FIG. 1

  In the prior art of Patent Document 1, the same refrigeration cycle is used to cool the supply air taken into the air supply path from outside, such as outdoors, and to regenerate the adsorbent from the exhaust air (regenerated air) taken into the exhaust path from the room. Heating is performed for use. By the way, the cooling heat quantity of the supply air supply varies greatly depending on the time variation and seasonal variation of the outside air temperature. For this reason, when the heat pump cycle is operated in accordance with this change, there is a problem that the heating amount of the exhaust air also fluctuates to change the regeneration state of the adsorbent and also the dehumidification performance of the supply air performed by this adsorbent. It was. Furthermore, as described above, the operation state of the heat pump largely fluctuates depending on the cooling load with respect to the outside air condition, and the condition that the heat pump equipment operates effectively is limited to the state where the cooling load is large, and the problem that the energy saving effect is small throughout the operation period. was there.

  In addition, when reheating the exhaust air by providing an auxiliary heater using electricity to compensate for fluctuations in the heating amount of the exhaust air, the load on the auxiliary heater increases due to fluctuations in the operating state of the heat pump. The problem of increased energy arises.

  With respect to these problems, in Non-Patent Document 1 described above, the regeneration air is heated with a high-temperature heat source of a heat pump and then further heated with an auxiliary heater, thereby stabilizing the temperature of the regeneration air supplied to the regeneration zone. The regeneration state and the dehumidifying performance of the supply air are stabilized.

  For fluctuations in the cooling load, a sensible heat rotor is provided for exchanging heat between the exhaust air from the room and the supply air dehumidified by the dehumidification rotor and having a temperature increased to about 65 ° C. The supply air that has exchanged heat with the air is cooled by the low-temperature heat source of the heat pump, thereby suppressing the influence of fluctuations in the outside air, effectively operating the heat pump equipment regardless of time fluctuations and seasonal fluctuations in the outside air conditions. . However, in this prior art, since a sensible heat rotor is required, there is a problem that the dehumidification system is enlarged.

  The object of the present invention is to provide a desiccant dehumidification air-conditioning system using a heat pump, supplying stable low-humidity air regardless of fluctuations in the outside air conditions, and simultaneously operating the heat pump stably to save energy, and to increase the size of the dehumidification system device. It is to suppress the conversion.

  In order to achieve the above object, a dehumidifying air conditioning system according to the present invention uses mixed air of outside air introduced from the outside and indoor return air to be recirculated through the air-conditioning target room, and the heat absorption part of the heat pump as a cooling source. The air cooler is provided in the flow path of the indoor return air to be recirculated.

  According to the dehumidifying air-conditioning system of the present invention, the indoor return air is cooled by the heat absorption part of the heat pump. Therefore, when performing dehumidifying air-conditioning in offices, factory production sites, clean rooms, etc. where cooling loads occur throughout the year, A stable cooling load can be obtained. As a result, the heat pump equipment can be operated effectively, and an energy saving effect corresponding to the capacity can be obtained.

  Embodiments of the present invention will be described below with reference to the drawings.

  First, Example 1 will be described with reference to FIGS. FIG. 1 is an overall system diagram of a dehumidifying air conditioning system according to the present embodiment. FIG. 2 is a diagram showing the heat pump cycle used in this embodiment on a temperature-enthalpy diagram. FIG. 3 is a diagram showing a unit configuration of the present embodiment. FIG. 4 is a graph comparing the energy consumption and the breakdown of the dehumidifying air-conditioning system according to the present embodiment in the summer peak conditions with no heat pump. FIG. 5 is a graph comparing the monthly average energy consumption according to the present embodiment with the case where no heat pump is used as in FIG.

  As shown in FIG. 1, the dehumidifying air conditioning system includes a desiccant dehumidifying rotor 10 (hereinafter referred to as a dehumidifying rotor), a heat pump 30, an electric heater 70, a refrigerator 80, a duct for passing processing air and desiccant regenerating air through them, and a fan (not shown). Etc.

  The dehumidifying rotor 10 includes a processing zone 11 that adsorbs moisture from the processing air to dehumidify, a regeneration zone 12 that desorbs moisture from the dehumidifying rotor 10 with high-temperature regeneration air, and a dehumidification rotor that has increased in temperature in the regeneration zone 12. 10 is constituted by a purge zone 13 that cools by branching a part of the processing air. By rotating the dehumidifying rotor 10 and operating each zone, the process air is dehumidified. The dehumidifying rotor 10 holds a dehumidifying member such as silica gel or zeolite.

The heat pump 30 heats the rotor regeneration air 95 using a compressor 31 that compresses the refrigerant gas to a supercritical state and raises the temperature, and a refrigerant that has been compressed to a supercritical pressure by the compressor 31 and has reached a high temperature. An outside air radiator 33 that further cools the refrigerant whose temperature has been lowered by the air heater 32 with the outside air 99, and a pressure reducing valve 34 that decompresses the refrigerant that has come out of the outside air radiator 33 from a supercritical state to a two-phase region, The air cooler 35 cools the process air, that is, the indoor return air 94 from the air-conditioned room (not shown) by evaporating the refrigerant liquid of the two-phase refrigerant, the refrigerant pipe 37 connecting these, and the like. Furthermore, a temperature sensor 79 for controlling the electric heater 70 and a temperature sensor 89 for performing operation control including on / off of the refrigerator 80 are provided at various locations of the air duct.

  Next, the basic operation of the dehumidifying air conditioning system according to the present embodiment will be described. In the dehumidifying air conditioning system, the introduced outside air 91 is cooled by the first cooling coil 81 provided in the refrigerator 80, and the indoor return air 94 from the low dew point chamber is converted into the air cooler 35 of the heat pump 30 and the second of the refrigerator 80. It cools with the cooling coil 82, and joins these. As described above, a part of this merged air branches and is guided to the purge zone 13 as purge air 92, and the rest is guided to the processing zone 11 to lower the humidity, and then is supplied as air supply 93 to the air-conditioned room. Led. Note that an on-off valve 83 (solenoid valve) for controlling the refrigerant in the middle of the pipe from the refrigerator 80 to the first cooling coil 81 and an on-off valve 84 in the middle of the pipe from the refrigerator 80 to the second cooling coil. (Electromagnetic valve) is provided.

  On the other hand, the purge air 92 cools the dehumidifying rotor 10 in the purge zone 13. Thus, as is well known as a feature of the purge type desiccant dehumidifier, air is supplied from only a sufficiently cooled region, and as a result, air supply with very low humidity can be obtained. The purge air 92 that has risen in temperature by cooling the dehumidifying rotor 10 merges with the recirculation regenerated air 96 to become regenerated air, and is further heated sequentially by the air heater 32 and the electric heater 70 of the heat pump 30 and then into the regeneration zone 12. It is guided and regenerated, that is, desorbs and removes moisture from the dehumidifying rotor 10.

A part of the regeneration air 95 from the regeneration zone 12 is branched as described above and merged with the purge air 92 as the recirculation regeneration air 96, and the rest is discharged out of the apparatus as the exhaust 97 together with the water removed from the dehumidification rotor 10. Is done.

  Next, the operation of the heat pump 30 at this time will be described with reference to FIG. In the present embodiment, carbon dioxide is used as the working medium of the heat pump 30. Symbols A to F in FIG. 2 indicate the state of the refrigerant on the temperature-enthalpy diagram shown in FIG. Represents.

  The refrigerant compressed to the supercritical pressure by the compressor 31 rises in temperature to the state A and is led to the air heater 32. In the air heater 32, the regenerative air 95 is heated while the refrigerant is lowered in temperature to be in the state B, and is led to the outside air radiator 33. In the outside air radiator 33, the introduced outside air 99 for heat radiation has a temperature lower than that of the regenerated air flowing into the air heater 32. Therefore, the refrigerant further falls in temperature and enters the state C. Thereafter, the refrigerant is led to the pressure reducing valve 34 to reduce the pressure, and the state D is a two-phase state composed of the refrigerant liquid and the refrigerant vapor, and the indoor cooler 94 is cooled by the latent heat of evaporation of the refrigerant liquid in the air cooler 35. To do. In the air cooler 35, all the refrigerant liquid is evaporated to become the state E on the saturation line, and further to the superheated steam state F by heat exchange with the indoor return air 94, and then sucked into the compressor 31 and compressed again. Is done.

  Actually, there is a pressure loss in each heat exchanger, but in FIG. 2, the influence is omitted, and states A, B, and C are shown on the isobaric lines in the supercritical region, and states D, E, and F are two. It is shown on the isobaric lines of the phase region and gas region.

  FIG. 3 shows the unit configuration of the dehumidifying air conditioning system in this embodiment and the installation status of each component of the heat pump cycle. The dehumidifying air conditioning system is mainly composed of a heat exhaust unit 101 and a dehumidifier unit 102. The exhaust heat unit 101 includes a compressor 31, an outside air radiator 33, a fan 38 that allows the outside air radiator 33 to vent outside air, a pressure reducing valve 34, and the like.

The dehumidifier unit 102 is provided with an air heater 32 and an air cooler 35 among the components of the heat pump cycle. Although not shown in FIG. 3, the dehumidification rotor 10, the electric heater 70, the first cooling coil 81 and the second cooling coil of the refrigerator 80 shown in FIG. A fan or the like is built in the dehumidifier unit 102. And the refrigerant | coolant piping 37 which forms a heat pump cycle has connected the exhaust heat unit 101 and the dehumidifier unit 102. FIG.

  Next, operation control of the dehumidifying air conditioning system of the present embodiment will be described. With respect to changes in the outside air temperature, the temperature of the processing air supplied to the processing zone 11 of the dehumidifying rotor 10 is maintained substantially constant by controlling the capacity of the refrigerator 80. This treated air is a mixture of air obtained by cooling the outside air 91 using the first cooling coil 81 and air obtained by cooling the indoor return air 94 using the air cooler 35 of the heat pump 30 and the second cooling coil 82 of the refrigerator 80. It is a thing. Therefore, even when the cooling load in the air-conditioned room or the temperature of the indoor return air 94 changes, the capacity control of the refrigerator 80 can cope with it.

Furthermore, the refrigerator is also used in the case where the outside air temperature fluctuates and the refrigerant outlet temperature of the outside air radiator 33 changes, and the amount of cooling heat of the air cooler 35 and the outlet temperature of the indoor return air 94 fluctuate due to the influence. 80 capacity control can cope with this. Moreover, the heating amount of the regeneration air 95 in the air heater 32 changes with the change of the heat pump cycle. This change is dealt with by keeping the regeneration air temperature measured by the temperature sensor 79 constant by controlling the capacity of the electric heater 70.

  Accordingly, the influence of fluctuations in the outside air temperature and the indoor load on the heat pump cycle is small, and the heat pump is operated at a substantially constant output during operation of this system. The capacity of the heat pump is set so that the cooling capacity of the indoor return air 94 determined by the set temperature of the air-conditioned room set at the time of planning is lower than the cooling capacity of the air cooler 35.

  Next, FIGS. 4 and 5 will be described with respect to the energy saving effect according to the present embodiment. FIG. 4 shows the calculation result of the power consumption of the dehumidifying air conditioning system in the summer peak period when the heat pump 30 is not used (use of the heat pump: none), that is, the outside air 91 and the indoor return air 94 are cooled only by the refrigerator 80. This compares the case where the regeneration air 95 is heated only by the electric heater 70 and the case where the heat pump 30 is used. As shown in FIG. 4, the power consumption is reduced by about 10% by the introduction of the heat pump.

  FIG. 5 shows the result of calculating the power consumption for each month of the year using the monthly average temperature in a certain region. The comparison at the summer peak shown in FIG. 4 is also shown in FIG. As shown in FIG. 5, a substantially constant reduction amount is obtained regardless of the season. This is because the heating and cooling loads by the heat pump are almost constant throughout the year, so that the heat pump can always be operated at the rated capacity.

  As described above, in this embodiment, since the air cooler 35 of the heat pump 30 is provided in the flow path of the indoor return air 94 having a cooling load throughout the year, the annual operation state of the heat pump is stabilized, and FIG. As shown, it is possible to obtain energy saving effects throughout the year. In the present embodiment, the power consumption reduction amount shown in FIG. 4 is obtained throughout the year, and the total power consumption value decreases in the intermediate period and winter season, so the reduction rate exceeds 10%. As a result, the power consumption reduction rate throughout the year is also 10% or more.

  In addition, according to the present embodiment, the capacity of the heat pump 30 is set to a value that does not exceed the cooling load of the indoor return air, so the scale of the apparatus is small compared to the case where the cooling load of the outside air is borne, and the initial cost is reduced. It is possible to suppress the rise of Further, since the operation state of the heat pump 30 is stabilized, the operation state, that is, the heating amount of the electric heater 70 is also stable throughout the year as shown in the case of “use” of the heat pump in FIG. 5, and the capacity of the electric heater 70 is reduced. Thus, it is possible to reduce the size.

  Furthermore, since these devices operate effectively throughout the year, the energy saving effect on the increase in initial cost is increased.

  In this embodiment, the refrigerator 80 for cooling the introduced outside air 91 is provided, and the refrigerator 80 is controlled so that the temperature of the processing air supplied to the processing zone 11 of the dehumidification rotor 10 is constant. Regardless of fluctuations in the outside air temperature, it is possible to supply stable low-humidity air to the air-conditioned material and to stabilize the operation state of the heat pump 30.

  Furthermore, in this embodiment, the indoor return air 94 cooled by the air cooler 35 of the heat pump 30 is re-cooled by providing a second cooling coil 82 that re-cools using a part of the cooling capacity of the heat pump 30. In addition to fluctuations in the outside air temperature, fluctuations in the indoor load can be handled without changing the operating state of the heat pump 30.

  Further, in this embodiment, since the outside air radiator 33 is installed as the heat radiating portion of the heat pump 30 in addition to the air heater 32 that heats the regeneration air 95, the air cooler 35, that is, the evaporator inlet as shown in FIG. The enthalpy of the refrigerant decreases from the value of the state B in FIG. As a result, the cooling capacity of the air cooler increases from the enthalpy difference between the state B and the state F to the QE shown in FIG. 2 from the enthalpy difference between the state D and the state F when the outside air radiator 33 is not installed. . Therefore, the refrigeration load of the refrigerator 80 is reduced, and the effect of reducing the size of the refrigerator 80 and saving energy can be obtained.

Furthermore, in this embodiment, the entire dehumidifying air conditioning system is divided into a heat removal unit 101 including a compressor 31, an outside air radiator 33, a fan 38, and a dehumidifier including a dehumidification rotor 10, an air heater 32, an air cooler 35, and the like. Since it comprises the unit 102, the exhaust heat unit 101 can be installed outdoors, and the dehumidifier unit 102 can be installed outdoors.

Since the dehumidifier unit 102 circulates the processing air, there is an advantage that a waterproof construction or the like becomes unnecessary by installing the dehumidifier unit 102 indoors such as a machine room. On the other hand, in the exhaust heat unit 101, as the refrigerant outlet temperature from the outside air radiator 33 is lower, the cooling capacity QE of the air cooler shown in FIG. 2 is increased and the load of the heat pump 30 is reduced to save energy. Therefore, the energy saving effect is increased by installing the exhaust heat unit 101 outdoors and dissipating heat to the outside air whose temperature is lower than that in the machine room. In this embodiment, these advantages can be obtained simultaneously.

  Further, in the present embodiment, the refrigerant of the heat pump 30 radiates heat at the supercritical pressure in the air heater 32, so that the refrigerant radiates heat to the regeneration air 95 while the temperature continuously decreases in the air heater 32. Therefore, the counter-flow type heat exchange with the regenerated air 95 is possible, and the power consumption of the electric heater 70 is reduced and dehumidification as shown in the comparison of the use “present” and “none” of the heat pump in FIGS. The energy saving effect of the entire air conditioning system is obtained.

  Further, in this embodiment, carbon dioxide having a relatively low critical temperature of 31.1 ° C. is used as the refrigerant of the heat pump 30, so that the high pressure side of the cycle easily enters a supercritical state, and is due to heat dissipation in the supercritical state. An effect is obtained. Moreover, since carbon dioxide has a very low global warming coefficient as is well known, it is not necessary to recover the refrigerant, and a dehumidifying air conditioning system corresponding to environmental problems can be obtained.

  Furthermore, in each Example shown above, since it was set as the structure which installs the external air heat radiator 33 as a cooling means of the refrigerant | coolant after leaving the air heater 32, and cools with the external air 99 for heat radiation, it is the equipment of a cooling water system | strain. There is an advantage that is unnecessary.

  On the other hand, when the present system is introduced into a factory or the like where a cooling water system has been prepared in advance, a water-cooled refrigerant cooler may be installed in place of the outside air radiator 33 and cooled by the cooling water. In this case, instead of requiring a cooling water system, cooling can be performed with a smaller heat transfer area compared to the air-cooled outside air radiator 33, so that the refrigerant cooler and the dehumidifying air conditioning system can be reduced in size. is there. Obviously, this cooling water may be river water or seawater.

  Next, a second embodiment of the present invention will be described with reference to FIG. The dehumidifying air-conditioning system in FIG. 6 has substantially the same configuration as that in FIG. 1, but the following points are different. In the embodiment of FIG. 1, the indoor return air 94 to be recirculated from the room is cooled by the second cooling coil 82, whereas in this embodiment, the indoor return air 94 and the outside air 91 introduced from the outside merge. The subsequent processing air is cooled by the second cooling coil 82.

  In this embodiment, the processing air immediately before flowing into the processing zone 11 of the dehumidifying rotor 10 is cooled by the second cooling coil 82. Thereby, as compared with the first embodiment, the rotor inlet air temperature detected by the temperature sensor 89 can be stably controlled near the target value by the capacity control of the refrigerator 80. As described above, in the dehumidifying rotor holding the dehumidifying member, the dehumidifying performance is affected by the inlet temperature of the processing air. Therefore, in this embodiment, the inlet temperature is stabilized, so that the temperature of the rotor outlet air, that is, the supply air 93 is increased. There is an advantage that the humidity can be controlled near the target value and stably. This is particularly important from the viewpoint of improving production quality in applications where a low-humidity environment is required, such as manufacturing processes for semiconductors and displays.

  The annual variation of the heat pump cycle, power consumption, and power consumption in this embodiment is shown in FIGS. 2, 4, and 5 as in the first embodiment, and the same effect can be obtained. Further, it is possible to adopt a unit configuration similar to that in FIG. 3, and the same effect as in the first embodiment can be obtained.

1 is an overall system diagram of a dehumidifying air conditioning system according to an embodiment of the present invention. The Th diagram of the heat pump cycle in the Example of FIG. The figure showing the unit structure in the Example of FIG. The graph which shows the power consumption of the dehumidification air conditioning system in the Example of FIG. The graph which shows the annual fluctuation | variation of the power consumption of the dehumidification air conditioning system in the Example of FIG. The whole system chart of the dehumidification air-conditioning system concerning the 2nd example of the present invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Dehumidification rotor, 11 ... Processing zone, 12 ... Regeneration zone, 13 ... Purge zone, 30 ... Heat pump, 31 ... Compressor, 32 ... Air heater, 33 ... Outside air radiator, 34 ... Pressure reducing valve, 35 ... Air cooling 37 ... refrigerant pipe, 38 ... fan, 70 ... electric heater, 79 ... temperature sensor for electric heater control, 80 ... refrigerator, 81 ... first cooling coil, 82 ... second cooling coil,
89 ... Temperature sensor for refrigerator control, 91 ... Outside air for air supply, 92 ... Purge air, 93 ... Air supply,
95 ... Regenerative air, 96 ... Recirculation regenerated air, 97 ... Exhaust, 99 ... Outside air for heat dissipation, 101 ... Exhaust heat unit, 102 ... Dehumidifier unit, A to F ... Refrigerant state on Th diagram, H ... saturation line, QE ... cooling capacity.

Claims (3)

A treatment zone for absorbing moisture treatment air dehumidification rotor, the purge zone and the regeneration zone to release the water in hot regeneration air, the area to release moisture and temperature rise in the regeneration zone is cooled by cooling air with the door, the dehumidifying rotor cooling and purging type desiccant dehumidifier each zone sequentially passes by to rotate, and a heat pump having a heat radiating portion and the heat absorbing portion, the process air the heat absorbing section as a cooling source In a dehumidifying air conditioning system having an air cooler and an air heater that heats the regeneration air at the regeneration zone inlet side using the heat radiating portion as a heating source,
The treated air is a mixed air of introduced outside air introduced from the outside and indoor return air that is guided from the room to be air-conditioned and recirculated,
The pre Kisora air cooler, with kicking set in the flow path of the indoor return air, the introduction outside air is dehumidified, characterized in that said digits set the refrigerator to cool the upstream side of the mixing portion of the indoor return air Air conditioning system. In the dehumidification air-conditioning system according to claim 1,
The refrigerator cools the introduced outside air on the upstream side of the mixing portion with the indoor return air, and introduces the indoor return air cooled by the air cooler using the heat absorption portion of the heat pump as a cooling source. A dehumidifying air-conditioning system that re-cools before or after merging with outside air. In the dehumidification air-conditioning system according to claim 1 or 2,
The heat dissipation part of the heat pump includes an air heater that radiates heat to the regeneration air as a heating source of the regeneration air, and an outside air radiator that releases heat to an external cooling medium, and the outside air radiator is the air heater. A dehumidifying air-conditioning system connected to the downstream side of the refrigerant flow path .

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