JP2007187386A - Dehumidification air conditioning system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce energy consumption of a dehumidification system using a desiccant dehumidifier. <P>SOLUTION: By heating air for regeneration of a desiccant dehumidifier by a gas cooler or a condenser of a heat pump, and supplying air, i.e., cooling dehumidification target air by an evaporator, energy is effectively used. A refrigerant after heating the air for the regeneration is further cooled by a cooling medium lead from the outside to improve cooling performance of the heat pump. After the air for the regeneration is heated by the heat pump, the air for the regeneration is further heated by an electric heater to increase regeneration capability, and it copes with the case that low humidity environment is necessary. A heat pump cycle is operated according to a heat reception amount of the regeneration air, and an auxiliary refrigerator is provided in preparation for the case that cooling capability becomes insufficient. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a dehumidifying air conditioning system based on a desiccant air conditioner and provided with a heat pump as its air heating / cooling means.

  As a dehumidification air-conditioning system concerning this invention, the technique of the following patent document 1 is mentioned, for example. This document includes a refrigerant circuit, that is, a heat pump and a desiccant rotor as a moisture absorption / release means, heats the air to be dehumidified by a heat radiator of the heat pump, humidifies the air in a moisture release area of the desiccant rotor, Is cooled by a heat absorber of the heat pump and further dehumidified in the moisture absorption region of the desiccant rotor. In this known example, the heat pump refrigerant radiates heat at a supercritical pressure in a radiator, and carbon dioxide is used as the refrigerant.

  Moreover, the following patent document 2 and nonpatent literature 1 are mentioned as background art regarding the heat pump cycle used by this invention. In these documents, there is an additional heat exchanger in which the low-pressure refrigerant is evaporated and heated by the heat of the high-pressure refrigerant, that is, a supercritical vapor compression cycle in which an internal heat exchanger is installed to increase the capacity. It is disclosed.

JP 2005-34838 A Japanese Patent Publication No. 7-18602 Figure 2 NEDO 2001 Survey Report 51401011-0-1 Survey on applied equipment using carbon dioxide refrigerant, etc. p. 105

  Since the conventional technology of Patent Document 1 is directed to a dehumidifying device used for general air conditioning, outside air is used as regeneration air heated by a heat pump. However, when a low humidity and low dew point environment is required, a so-called purge type desiccant dehumidifier with a purge zone provided in the desiccant rotor is used. In this case, the regeneration air heated by the heat pump is used to purge or cool the rotor. However, since the temperature of the air is higher than that of the outside air, heat radiation from the heat pump becomes insufficient, resulting in a problem that cooling COP is lowered and power consumption is increased.

  Furthermore, in the prior art of Patent Document 1 described above, air taken from outside is heated using the heat radiating portion of the heat pump to regenerate the desiccant rotor. However, since no consideration is given to fluctuations in outside air conditions, In addition, the humidity of the supplied air greatly fluctuates depending on the season, and the distribution of the heating amount and the cooling heat amount is determined by the heat pump cycle. In addition, since the regeneration air is heated only by the heat radiating portion of the heat pump, there is a problem that the upper limit of the regeneration air temperature is low and the dehumidifying capacity is limited to this.

  Further, in the prior art disclosed in Patent Document 1, carbon dioxide having a small global warming potential is used as a heat pump refrigerant, and regeneration air is heated at supercritical pressure. However, carbon dioxide is used as a heat pump refrigerant for regeneration. When performing high-temperature heating of industrial air, it is necessary to compress the refrigerant to a high pressure in the compressor in order to obtain a high temperature, and the heat insulation efficiency and volumetric efficiency of the compressor decrease, increasing the energy consumption and the capacity of the heat pump device However, the above-described prior art does not give consideration to this point.

  In addition, in the prior art of the above-mentioned Patent Document 2, mention is made of the improvement of the heat insulation efficiency of the compressor and the reduction of energy consumption caused by the reduction of the compression ratio, and the point that the installation of the internal heat exchanger plays a large role for this effect. Not done.

  An object of the present invention is to reduce power consumption of a desiccant dehumidification system using a heat pump used for a low dew point environment and to realize stable air supply against fluctuations in the outside air. Another object of the present invention is to reduce the refrigerant pressure and compression ratio at the compressor outlet when a heat pump in which the refrigerant in the heat radiating section using carbon dioxide or the like becomes supercritical pressure is used for air heating and cooling. The purpose is to improve the heat insulation efficiency of the compressor and reduce the power consumption of the dehumidifying air conditioning system.

  In order to achieve the above object, the dehumidifying air-conditioning system according to the present invention uses a heat pump for heating the regeneration air and cooling the supply air, and in addition to a heat radiator for heating the regeneration air, A heat dissipating means for cooling the high-pressure side refrigerant by the cooling medium is provided.

  According to the dehumidifying air-conditioning system of the present invention, the regeneration air is heated using a heat pump, so that power consumption is reduced as compared with the case where heating is performed using only an electric heater, and the cooling efficiency of the heat pump is reduced by heat radiation means to the outside. As the value rises, the power consumption can be further reduced.

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

  Example 1 will be described with reference to FIGS. 1, 2, and 3. 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 graph comparing the energy consumption and breakdown of the dehumidifying air conditioning system according to the present embodiment with a similar system.

  As shown in FIG. 1, the dehumidifying air conditioning system includes a desiccant dehumidifying rotor 10, a heat pump 30, an electric heater 70, a refrigerator 80, and ducts and fans that allow the processing air and the desiccant regeneration air to flow through them.

  The dehumidification rotor 10 is configured to treat a processing zone 11 that dehumidifies by adsorbing moisture from the processing air, a regeneration zone 12 that desorbs moisture from the rotor with high-temperature regeneration air, and a rotor whose temperature has increased in the regeneration zone. Dehumidification is performed by sequentially rotating a purge zone 13 that branches and cools a part of the gas. The dehumidifying rotor 10 holds a dehumidifying member such as silica gel or zeolite.

  The heat pump 30 compresses the refrigerant gas to a supercritical state and raises the temperature, and air heating that heats the rotor regeneration air 95 using the refrigerant 31 compressed to a supercritical pressure and heated to 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 for heat dissipation, and a pressure reducing valve 34 that depressurizes the refrigerant discharged from the outside air heater 33 from the supercritical state to the two-phase region. From the air coolers 35 and 36 for cooling the process air, that is, the return air 94 from the low dew point chamber (not shown) and the introduced outside air by evaporation of the refrigerant liquid of the two-phase refrigerant, and the refrigerant pipe 37 connecting them. It is configured.

  Further, in each part of the duct, a temperature sensor 39 for controlling the capacity of the heat pump 30, a temperature sensor 79 for detecting the temperature of the rotor regeneration air 95 for controlling the electric heater 70, and a generator 80 are provided. A temperature sensor 89 is provided for measuring the temperature of the introduced outside air 91 after passing through the direct expansion type cooling coil 81 provided in the refrigerator 80 in order to perform operation control including stopping.

  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 outside air 91 introduced for supply is first preliminarily cooled by a direct expansion type cooling coil 81 provided in the refrigerator 80. Further, after the precooled outside air is cooled by the air cooler 36 of the heat pump 30, the return air 94 from the low dew point chamber is combined with the air cooled by the air cooler 35 of the heat pump. A part of the merged air is branched and guided to the purge zone 13 as purge air 92, and the rest is guided to the processing zone 11 to reduce the humidity, and then is guided to a low dew point chamber (not shown) as supply air.

  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 in turn 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 outside 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 a saturation line.

  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 97 is heated to a state B while the temperature of the refrigerant drops, and is led to the outside air radiator 33. In the outside air radiator 33, the introduced outside air 99 for heat dissipation has a temperature lower than that of the regenerated air flowing into the air heater 32, so that the refrigerant further falls in temperature and enters the state C. Thereafter, the refrigerant is led to the expansion valve 34 to reduce the pressure, and a state D that is a two-phase state composed of the refrigerant liquid and the refrigerant vapor is obtained. Then, the introduced outside air 91 is cooled. In the air cooler 36, all the refrigerant liquid evaporates to a state E on the saturation line, and further enters a superheated steam state F by heat exchange with the outside air 91, and then is sucked into the compressor 31 and compressed again. .

  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 line 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.

  Next, operation control of the dehumidifying air conditioning system according to the present embodiment will be described. In the present embodiment, the heat pump 30 has an upper limit on the capacity and the refrigerant circulation amount based on the maximum amount of heat that can be recovered by the regenerated air 95 in the air heater 32. Accordingly, when the outside air temperature is high, the cooling capacity may be insufficient, and the refrigerator 80 is installed in preparation for this. The refrigerator 80 is controlled based on the output of the temperature sensor 89 that measures the temperature of the outside air cooled by the refrigerator.

  When the outside air temperature is high, the refrigerator 80 is controlled so that the air temperature measured by the temperature sensor 89 becomes a substantially constant value. The value of the air temperature is determined in accordance with the cooling capacity of the heat pump 30 in an operation state in which the heat pump 30 can supply the maximum amount of heat that can be recovered by the regeneration air 95 in the air heater 32.

  When the outside air temperature is low, the cooling load is reduced, and the operation of the refrigerator 80 is stopped because the outside air 91 and the indoor return air 94 can be sufficiently cooled only by the cooling capacity of the heat pump 30. In this case, it is not preferable to stop the operation of the heat pump 30 because the heating amount of the air heater 32 becomes zero and the power consumption of the electric heater 70 increases. In the present embodiment, when the air temperature measured by the temperature sensor 89 becomes lower than a predetermined value, the operation of the refrigerator 80 is stopped, and the air temperature rises again to maintain a predetermined operating gap (hysteresis). ), The operation of the refrigerator 80 is resumed.

  The heat pump 30 is controlled based on the output of the temperature sensor 39 that measures the processing air temperature after the indoor return air 94 and the outside air 91 that have been cooled by the air coolers 35 and 36 are mixed. At this time, the temperature of the indoor return air 94 at the inlet of the air cooler 35 is substantially constant, and the temperature of the outside air 91 at the inlet of the air cooler 36 is maintained below a certain temperature by the refrigerator 80 as described above. Therefore, the temperature of the processing air measured by the temperature sensor 39 is controlled to a substantially constant value within the capacity control range of the heat pump 30. This value is determined from the specifications of the supply air supplied from the dehumidifying air conditioning system to the low dew point chamber.

  In a state where the outside air temperature is low and the refrigerator 80 is stopped by the control operation, the temperature of the mixed air is maintained almost constant by controlling the capacity of the heat pump 30 as described above. The air heating amount in the heater 32 also changes. For this change, the amount of heat generated by the electric heater 70 is controlled based on the output of the temperature sensor 79 that detects the temperature of the regenerated air from the electric heater 70 toward the regeneration zone 12 of the dehumidifying rotor 10. The temperature is maintained at a predetermined value, and the dehumidifying capacity in the processing zone 11 is maintained.

  As described above, in this embodiment, the heat absorption part of the heat pump cycle, that is, the evaporator is used as a cooling source for processing air, and the heat radiation part is used as a heating source for regeneration air, thereby reducing the load on the electric heater 70. The energy consumption is reduced. In addition, by providing the outside air radiator 33, the carbon dioxide as the refrigerant heats the regeneration air 95 in the heat radiating part of the heat pump cycle to become the state B, and then further dissipates the heat in the outside air 99 for heat radiation until the state C. The temperature drops. That is, the cooling capacity in the air coolers 35 and 36 is QE which is an enthalpy difference between the state D and the state F in FIG. Compared with the case where the outside air radiator 33 is not used, the cooling capacity is reduced from the state B to the state D ′ when the outside air radiator 33 is not used, and the cooling capacity is between the state D ′ and the state F. QE ′, which is the enthalpy difference of. For this reason, it can be seen that the installation of the outside air radiator 33 increases the cooling capacity per unit refrigerant flow rate by (QE-QE '), and the electric energy input to the compressor 31 is reduced. Alternatively, the cooling load of the precooling refrigerator 80 is reduced by the increase in the cooling capacity, and energy saving of the entire dehumidifying air conditioning system can be achieved.

  Further, in this embodiment, by controlling the capacity of the heat pump 30 based on the temperature of the processing air cooled by the air coolers 35 and 36, the temperature of the air flowing into the processing zone 11 of the dehumidification rotor 10 is stabilized. As a result, it is possible to stably supply the low dew point air.

  In this embodiment, since the electric heater 70 is installed, the regeneration air 95 can be heated to a temperature higher than the highest temperature that can be heated by the heat pump. Thereby, since the moisture of the dehumidifying member is reduced during the rotor regeneration, it is possible to supply air having a low dew point such as −50 ° C. Further, a temperature sensor 79 for detecting the temperature of the regeneration air heated by the electric heater 70 is provided, and the heating amount of the electric heater 70 is controlled so that the temperature of the regeneration air becomes a constant value. Thereby, even when the operation state of the heat pump 30 is changed, the temperature of the regeneration air is stabilized to ensure the dehumidifying ability in the processing zone 11, and the low dew point air can be stably supplied.

  In this embodiment, a refrigerator 80 for cooling the introduced outside air 91 is installed to compensate for the lack of cooling capacity by the heat pump 30. For this reason, it is possible to set the cycle capacity of the heat pump 30 corresponding to the amount of heat in the air heater 32, that is, the amount of heat that can be recovered when the temperature of the regeneration air 95 rises. Therefore, there is an effect that it is possible to prevent a decrease in energy use efficiency due to an excessive heating capacity of the heat pump 30 in the heat radiating portion.

  This effect will be described with reference to FIG. FIG. 3 compares the energy required for air heating and cooling in the dehumidifying air conditioning system according to the present embodiment with other methods. Each method of (1) to (3) has the following configuration. Configuration (1) represents a case in which the regeneration air in the dehumidification system is all heated by the electric heater 70, the processing air is all cooled by the refrigerator 80, and the heat pump 30 is not used. Next, in the configuration (2), the processing air is all cooled by the evaporator of the heat pump 30, and the regenerated air is heated by the heat radiating portion of the heat pump 30 and the electric heater 70, and the refrigerator 80 is not used.

  Configuration (3) is the configuration of the present embodiment, as described above, in which the heat pump 30 and the electric heater 70 are used for heating the regeneration air, and the heat pump 30 and the refrigerator 80 are used for cooling the processing air. In addition, it assumes that the external air cooler 33 is installed in the heat pump used by the configuration (2), and is within the scope of the present invention.

  In FIG. 3, the total energy consumption in the configuration (1) is 100%, and the energy consumption in each configuration is classified and compared for each element device. In the comparison of (1) and (2), the heat pump of (2) has greatly increased compared to the refrigerator of (1), which is required for cooling the processing air. This is because the refrigerant used in the heat pump 30 is carbon dioxide having a low coefficient of theoretical performance, whereas the refrigerant used is an alternative chlorofluorocarbon refrigerant.

  However, in (2), the regeneration air is heated by the heat pump 30, so that the energy consumption of the electric heater 70 is small as shown in the figure, and as a result, the energy consumption is reduced compared to (1). This indicates that even when the refrigerator 80 is not used, energy can be saved by employing the heat pump 30 provided with the outside air cooler 33.

  Next, in the comparison of (2) and (3), the power consumption of the refrigerator 30 is reduced because the capacity of the heat pump 30 is set in accordance with the amount of heat that can be recovered by the regenerative air. The power consumption of the refrigerator 80 that supplements the amount of cooling heat of the processed air is generated. The electric heater 70 is used for the purpose of heating the regenerated air from the highest temperature that can be heated by the heat pump 30 to a higher temperature, and therefore there is no difference between (2) and (3).

  In the comparison of total energy consumption, (3), which is the configuration of the present embodiment, is further reduced with respect to (2). This is because in (2) the capacity of the heat pump 30 is set in accordance with the cooling load, the heating capacity becomes excessive, the loss due to the release of the energy to the outside air, and a part of the air cooling of the coefficient of performance By doing with a high refrigerator 80. In addition, when the cooling load of the refrigerator 80 is increased in the configuration (3) and the capacity of the heat pump 30 is decreased, the energy consumption increases because the system configuration approaches (1).

  Furthermore, since the refrigerator 80 is installed, the load control of the refrigerator 80 can cope with the fluctuation of the outdoor air cooling load due to the season, so that the load of the heat pump 30 is stabilized and the heating by the air heater 32 is performed. There is an advantage that the amount can be secured. For example, when the outside air temperature is low and the cooling load is small, it can be dealt with by turning off the refrigerator 80.

  In addition, the start / stop and capacity control of the refrigerator 80 are performed based on the detected value of the temperature of the outside air 91 from the cooling coil 81 toward the air cooler 36 (the detected value of the temperature sensor 89). By providing only the portion exceeding the maximum capacity of 30 with the refrigerator 80, the operating capacity of the heat pump 30 is ensured to the maximum, the heating amount in the air heater 32 is maximized, and the input of the electric heater 70 is reduced. The energy saving effect shown in FIG. 3 can be exhibited.

  In this embodiment, the desiccant dehumidifier used in the dehumidification system is a purge type. However, the same effect can be obtained by a standard desiccant dehumidifier having no purge zone as described in Patent Document 1. That is, the heat dissipation part of the heat pump is not limited to the air heater introduced as the processing air as in Patent Document 1, but the cooling air is introduced to further lower the temperature of the refrigerant after heating the processing air. By installing a proper outside air radiator, the cooling capacity can be increased and the energy of the entire apparatus can be saved.

  Next, another embodiment of the present invention will be described with reference to FIGS. 4 is an overall system diagram of the dehumidifying air conditioning system according to the present embodiment, FIG. 5 is a diagram showing the heat pump cycle used in the present embodiment on a temperature-enthalpy diagram, and FIG. 6 is an internal heat exchanger used in the present embodiment. FIG. 7 is a graph showing the relationship between the temperature efficiency and the power consumption of the dehumidifying air-conditioning system according to the present embodiment. FIG. 7 shows the energy consumption and the breakdown of the dehumidifying air-conditioning system according to the present embodiment. It is the graph compared. In each figure, the same components as those in the embodiment of FIG. In the following description, only the differences between the present embodiment and the embodiment of FIG. 1 will be described.

  As shown in FIG. 4, the dehumidifying air conditioning system according to the present embodiment is provided with a cycle of the heat pump 30 without providing the refrigerator 80, the cooling coil 81 attached thereto, and the temperature sensor 89 with respect to the embodiment of FIG. 1. An internal heat exchanger 38 for exchanging heat between the refrigerant in the supercritical state cooled by the outside air radiator 33 and the refrigerant cooled to the outside air by the air cooler 36 to become refrigerant vapor is provided. It is. The pressure reducing valve 34 is provided on the downstream side of the internal heat exchanger 38.

  In the dehumidifying air-conditioning system of the present embodiment, the outside air 91 introduced for supplying air is directly cooled by the air cooler 36 and merged with the indoor return air 94 cooled by the air cooler 35, and then the implementation of FIG. As in the example, part of the air becomes purge air 92 and the rest is dehumidified by the dehumidifying rotor 10 to become air supply 93. The system of purge air 92 and regeneration air 95 is the same as that of the embodiment of FIG.

  Operation | movement of the heat pump 30 in a present Example is shown by the thick line (4) in FIG. Symbols P to W represent the state of the refrigerant in the same manner as symbols A to F in FIG. The refrigerant whose pressure has been increased to the supercritical pressure by the compressor 31 rises to a state P, enters the state R through the air heater 32 and the outside air radiator 33, and then enters the internal heat exchanger 38 from the air cooler 36. Heat is applied to the refrigerant vapor directed to the compressor 31 to enter the state S. Then, after passing through the expansion valve 34, the two-phase state T is reached, and after becoming saturated steam U and superheated steam V in the air coolers 35 and 36, the internal heat exchanger 38 further heats and the temperature rises. After that, it is sucked into the suction side of the compressor 31.

  When the heat pump cycle in the present embodiment is compared with the cycle of the embodiment in FIG. 1 indicated by a dotted line in FIG. 5, the refrigerant is cooled from the state R to the state S in the internal heat exchanger 38 after the heat is radiated by the outside air radiator 33. As a result, the cooling capacity per unit refrigerant amount in the air coolers 35 and 36 is increased from QE to QE ″ shown in the figure. This effect is mainly obtained in a refrigeration cycle using carbon dioxide as a refrigerant. This is generally known as an increase in the refrigeration effect due to internal heat exchange.

  Furthermore, in this embodiment, the refrigerant vapor led to the compressor 31 is heated by the internal heat exchanger 38 and the temperature rises. Here, when the discharge pressure of the compressor is the same as that of the embodiment of FIG. 1, the discharge temperature of the compressor rises. In this embodiment, the discharge temperature is set to a low value by setting the discharge pressure of the compressor low. Same as example. Therefore, the compression ratio of the compressor 31 is smaller than that of the embodiment of FIG. Here, since it is generally better for the compressor to have a small compression ratio, in this embodiment, the efficiency of the compressor increases due to a decrease in the discharge pressure and the pressure ratio, and the power consumption is further reduced. Next, these relationships will be described with reference to FIG.

  6, the horizontal axis represents the temperature efficiency ε of the internal heat exchanger 38, the vertical axis represents the power consumption, the ratio of the compression ratio and the compressor efficiency that varies with the compression ratio, and the discharge temperature of the compressor 31 is a constant value. This shows the relationship. The point of the temperature efficiency ε = 0 represents the same configuration as (2) in FIG. 3 when the internal heat exchanger 38 is not installed in FIG. 4, and the heat pump cycle is shown in FIG. Similar to the embodiment, the cycle is indicated by a broken line in FIG. 2 or FIG. The internal heat exchanger 38 of the heat pump 30 in this embodiment operates at a temperature efficiency indicated by (4) on the horizontal axis during rated operation.

  First, considering only the increase in the refrigeration effect, that is, the compressor efficiency is a constant value, the result of calculating the power consumption of the entire dehumidifying air conditioning system is indicated by a thin line. When the temperature efficiency of the internal heat exchanger increases, the work of the compressor is reduced by the effect of increasing the cooling capacity per unit refrigerant amount, and the power consumption of the entire system is reduced.

  Next, the change in the compression ratio at this time is indicated by a broken line. As a result of increasing the temperature efficiency ε and increasing the compressor inlet temperature, the discharge pressure is determined so that the discharge temperature becomes constant. As a result, the discharge pressure and the compression ratio decrease as shown in FIG. Yes. The result of deriving the compressor efficiency η from this compression ratio is shown by a dotted line in FIG. The relationship between the compression ratio and the compressor efficiency is, for example, p. 106 (5.1-4) and the like. As shown in the figure, the compressor efficiency increases as the temperature efficiency of the internal heat exchanger 38 increases.

  The result of recalculating the power consumption of the entire dehumidifying air-conditioning system in consideration of this increase in compressor efficiency is shown by a thick line in FIG. By installing the internal heat exchanger 38, the compressor efficiency is increased, and the power consumption is further reduced as compared with the power consumption reduction effect due to the increase in the cooling capacity indicated by the thin line. In the operation condition (4) of the present embodiment, a power consumption reduction effect of about 15% is obtained as compared with the case without the internal heat exchanger.

  FIG. 7 shows the energy required for air heating and cooling by the dehumidifying air conditioning system according to the present embodiment compared to the three types of systems compared in FIG. It can be seen that the power consumption is further reduced as compared with the embodiment of FIG.

  As described above, in this embodiment, by adding the internal heat exchanger 38 to the heat pump 30, in addition to the generally known effect of increasing the cooling capacity, the compressor efficiency can be improved by reducing the compression ratio. As a result, the power consumption can be reduced. That is, the feature of the present embodiment is that the compressor discharge pressure and the compression ratio are lower than those of the embodiment of FIG. 1, but the same compressor discharge temperature is obtained, and the heat pump cycle is used in the dehumidifying air conditioning system. This is a unique effect when applied.

  Although the refrigerator 80 is not used in this embodiment, the same effect can be obtained by adding the internal heat exchanger 38 to the heat pump of the dehumidifying air conditioning system using the refrigerator 80 as in the embodiment of FIG. It is clear that is obtained. Further, when the refrigerator 80 is not used as in the present embodiment, the system is simplified, and it is necessary to use a refrigerant such as an alternative CFC having a high global warming potential by using carbon dioxide as the refrigerant of the heat pump 30. Therefore, it is possible to obtain a dehumidifying air conditioning system that is extremely advantageous in terms of environmental conservation in combination with the effect of reducing energy consumption.

  In each of the embodiments described above, the refrigerant of the heat pump 30 dissipates heat at the supercritical pressure in the air heater 32, so that the regeneration air 95 can be heated to a high temperature, as shown in FIG. 3 or FIG. As shown in the comparison between the configuration (1) and (2), (3), and (4) according to the implementation of the present invention, the power consumption of the electric heater 70 is reduced and the energy saving effect of the entire dehumidifying air conditioning system is obtained.

  Further, in each of the embodiments described above, 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, The effect of heat dissipation 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 the external air radiator 33 was installed as a cooling means of the refrigerant | coolant after leaving the air heater 32, and it was set as the structure cooled with the external air 99 for thermal radiation, the installation of a cooling water system | strain is carried out. There is an advantage that it 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. It is obvious that this cooling water may be river water or seawater.

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 graph which shows the energy consumption of the dehumidification air conditioning system in the Example of FIG. The whole system diagram of the dehumidification air-conditioning system concerning other examples of the present invention. The Th diagram of the heat pump cycle in the Example of FIG. The graph which showed the power consumption of the dehumidification air conditioning system in the Example of FIG. 4, and the compression ratio of a compressor with the relationship with the temperature efficiency of an internal heat exchanger. The graph which shows the energy consumption of the dehumidification air conditioning system in the Example of FIG.

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 ... Expansion valve, 35 ... Indoor return Air cooler for air 36, Air cooler for treating outside air, 37. Refrigerant piping, 38. Internal heat exchanger, 39. Temperature sensor for heat pump control, 70... Electric heater, 79. Refrigerator 81 Direct expansion cooling coil 89 Refrigerator control temperature sensor 91 Air supply outside air 92 Purge air 93 Air supply 95 Regeneration air 96 Recirculation regenerative air 97 ... exhaust, 99 ... outside air for heat dissipation, A to F, P to W, refrigerant state on Th graph, H ... saturation line, QE, QE ', QE "... cooling capacity.

Claims (12)

A dehumidification rotor having a treatment zone that absorbs moisture from the treatment air, a regeneration zone that releases this moisture to high-temperature regeneration air, and a purge zone that cools the area where the moisture has been released by raising the temperature in the regeneration zone with cooling air A purge type desiccant dehumidifier that sequentially passes by rotating, a heat pump having a heat absorption part and a heat dissipation part, a cooler that cools the processing air using the heat absorption part as a cooling source, and the regeneration using the heat dissipation part as a heating source In a dehumidifying air conditioning system having a heater for heating air at the regeneration zone inlet side,
The dehumidifying air conditioning system is characterized in that the heat dissipating section includes a first heat radiator that releases heat to the regeneration air and a second heat radiator that releases heat to an external cooling medium. A desiccant dehumidifier that passes through a processing zone that absorbs moisture of the processing air, a dehumidification rotor that includes a regeneration zone that discharges the moisture to high-temperature regeneration air, and a heat pump that includes a heat absorption unit and a heat radiation unit, In a dehumidification air conditioning system having a cooler that cools the processing air using the heat absorption part as a cooling source, and a heater that heats the regeneration air on the regeneration zone inlet side using the heat dissipation part as a heating source,
The dehumidifying air-conditioning system is characterized in that the heat radiating unit includes a first radiator that releases heat to the regeneration air and a second radiator that releases heat to an external cooling medium. In the dehumidification air-conditioning system according to claim 1 or 2,
The dehumidifying air conditioning system, wherein the heat pump is provided with an internal heat exchanger for exchanging heat between the refrigerant radiated by the second radiator and the refrigerant absorbed by the heat absorbing section. In the dehumidification air conditioning system in any one of Claim 1 to 3,
A dehumidifying air-conditioning system comprising a control device that detects the temperature of the processing air cooled in a cooler and controls the capacity of the heat pump. In the dehumidification air conditioning system in any one of Claim 1 to 4,
Dehumidification characterized by comprising reheating means for heating the regenerated air after being heated in the first radiator, and leading the regenerated air from the reheat means to the regeneration zone of the desiccant dehumidifier. Air conditioning system. In the dehumidification air-conditioning system according to claim 5,
A dehumidifying air-conditioning system comprising a controller for detecting the temperature of the regenerated air heated by the reheating means and adjusting the heating amount of the reheating means. In the dehumidification air conditioning system in any one of Claim 1 to 6,
A dehumidifying air conditioning system comprising auxiliary cooling means for cooling the processing air. In the dehumidification air-conditioning system according to claim 7,
A temperature sensor for detecting the temperature of the processing air cooled by the auxiliary cooling means is provided, and a control device for starting and stopping or controlling the capacity of the auxiliary cooling means using an output from the temperature sensor is provided. Dehumidifying air conditioning system. In the dehumidification air conditioning system in any one of Claim 1 to 8,
The dehumidifying air conditioning system, wherein the external cooling medium is air. In the dehumidification air conditioning system in any one of Claim 1 to 8,
The dehumidifying air conditioning system, wherein the external cooling medium is cooling water. In the dehumidification air conditioning system in any one of Claim 1 to 10,
The dehumidifying air conditioning system characterized in that the refrigerant of the heat pump radiates heat at a supercritical pressure in the heat radiating section. In the dehumidification air-conditioning system according to claim 11,
The dehumidifying air conditioning system, wherein the refrigerant of the heat pump is carbon dioxide.

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