JP2012172880A - Outside air treatment device using desiccant rotor, and method for operating the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a water heat source outside air treatment device for using a compressor of small power and reducing a change in temperature of the air supplied inside a room by a change of outside air conditions.SOLUTION: The outside air treatment device 1 for performing dehumidification treatment of the outside air OA by using a desiccant rotor 15 and supplying an air-conditioned space with the air includes a heat pump circuit 12 which circulates refrigerant in order of an evaporator 30, a compressor 32, a condenser 27, and an expansion valve 26 to perform freezing cycle. The desiccant rotor 15 is freely rotatably placed across an exhaust duct 11 and an air supply duct 10, the evaporator 30 of the heat pump circuit 12 is placed on the downstream side of the desiccant rotor 15 in the air supply duct 10, the condenser 27 of the heat pump circuit 12 is placed on an upstream side of the desiccant rotor 15 in the exhaust duct 11, and a cooler 33 for after cool which uses a cold heat source water of a different system from the heat pump circuit 12 is placed between the desiccant rotor 15 and the evaporator 30 in the air supply duct 10.

Description

  The present invention relates to an outside air processing apparatus that dehumidifies outside air using a desiccant rotor and supplies air to an air-conditioned space, and an operation method thereof.

  In recent years, a low-temperature regenerated desiccant material of about 50 ° C has been developed, and an individual distributed air conditioning system equipped with this desiccant material and desiccant rotor, and an air conditioner (external air conditioner) for central air conditioning have been developed and launched. It was done. In addition, many inventions as disclosed in Patent Documents 1 to 15 have been disclosed for this technical field.

  The technology of Patent Document 1 relates to a heat pump circuit that maintains the regeneration air of a desiccant rotor at a high temperature to ensure a dehumidifying capacity. In the technique of Patent Document 1, the desiccant rotor regeneration unit is divided into two, and the regeneration air is maintained at a high temperature by the superheated steam refrigerant discharged from the compressor of the heat pump circuit. In the technique of Patent Document 2, as the heat source of the heat pump circuit that heats the desiccant rotor regeneration air, the exhaust air after passing through the rotor of the regeneration air together with the dehumidified air after passing through the desiccant rotor is used to secure the heat amount of the heat source. . In the technique of Patent Literature 3, a separate refrigerant is used as a heat source of a heat pump circuit that heats the desiccant rotor regeneration air, and the amount of heat of the heat source is secured. In the technique of Patent Document 4, the regenerated air is maintained at a high temperature by the superheated steam refrigerant discharged from the compressor of the heat pump circuit. The technology of Patent Document 5 is a packaged air conditioner system that uses a heat exchanger (indoor unit) that cools indoor air as a heat source of a heat pump circuit that heats the desiccant rotor regeneration air. Moreover, the technique of patent document 6 is a central system using the heat exchanger (air conditioner) which cools indoor air as a heat source of the heat pump circuit which heats desiccant rotor reproduction | regeneration air.

  The techniques of Patent Documents 7 to 10 and 13 relate to an individual dispersion system using an adsorbing element (a heat exchanger coated with an adsorbent). Furthermore, the technology of Patent Document 11 is a PAC system provided with a heat exchanger (indoor unit) that cools indoor air as a heat source of a heat pump circuit that heats the desiccant rotor regeneration air. Desiccant rotor regeneration air is heated. The technology of Patent Document 12 is a system that uses a heat exchanger that cools indoor air as well as a heat exchanger that cools and dehumidifies air before flowing into the desiccant rotor as a heat source of a heat pump circuit that heats the desiccant rotor regeneration air. is there. The technique of Patent Document 14 is a system having two heat pump paths as a heat pump circuit for heating the desiccant rotor regeneration air. The technique of patent document 15 is a system which heats desiccant rotor reproduction | regeneration air by heat-exchanging exhaust air and supply air with a sensible heat exchanger.

  In an external air conditioner using a desiccant rotor, the dehumidified air after passing through the rotor becomes high temperature. However, in the techniques of Patent Documents 1 to 15, for the purpose of supplying air into the room, (1) A method of cooling by replacement, (2) a method of cooling with water spray, or (3) a method of cooling with a heat pump circuit is shown. In the case of (1), a sensible heat rotor is required, and in the case of (2), a large desiccant rotor for sufficient dehumidification is required, so the external air conditioner becomes large. . In order to make the external air conditioner (ventilation unit) compact for an individual distributed air conditioning system, the method of cooling with the heat pump circuit of (3) is promising.

Japanese Patent Laid-Open No. 10-267576 Japanese Patent Laid-Open No. 10-288486 Japanese Unexamined Patent Publication No. 2000-171058 JP 2001-263732 A JP 2002-22205 A JP 2002-303433 A JP2003-232538 JP 2005-114291 A JP 2005-114294 A JP 2005-164165 A JP 2005-180885 JP JP 2005-195285 A JP 2006-275409 A Japanese Patent No. 2968224 JP 2010-112633 A

In response to recent global warming prevention issues, in addition to reducing CO ₂ emissions through energy conservation, do not release CFC refrigerants with a global warming potential GWP of several thousand (a greenhouse effect several thousand times that of CO ₂ ) to the atmosphere. is important. To that end, it is necessary to develop equipment and construction technology that have no refrigerant leakage, but it will soon be possible to adopt equipment and systems with a minimum amount of refrigerant. If the power of the compressor included in the outside air processing device is small, the refrigerant charge amount can be reduced accordingly.

  Moreover, in the water heat source outside air processing apparatus mounted on the desiccant rotor, it has been desired to minimize the change in the supply air temperature to the room due to the change in the outside air condition.

  The present invention has been made in view of the above points, and provides a water heat source outside air treatment device that can use a compressor with small power and can reduce a change in supply air temperature to the room due to a change in outside air conditions. Objective.

In order to achieve the above object, according to the present invention, there is provided an outside air processing device for dehumidifying outside air using a desiccant rotor and supplying the air to an air-conditioned space, wherein the refrigerant is an evaporator, a compressor, a condenser, and an expansion. A heat pump circuit that circulates in the order of the valves to perform a refrigeration cycle, the desiccant rotor is rotatably disposed across an exhaust path and an air supply path, and an evaporator of the heat pump circuit is connected to the desiccant rotor in the air supply path The cooler for aftercooling which is arranged on the downstream side of the heat pump circuit and which is arranged on the upstream side of the desiccant rotor in the exhaust passage and cools using a cold source water different from the refrigeration cycle Is provided between the desiccant rotor and the evaporator in the air supply path. Note that the refrigerant, for example as fluorocarbon refrigerant and CO ₂ refrigerant is subjected to compression and expansion by the heat exchange object and cooled by evaporation (vaporization), refers to those which heat the heat exchange object by condensation (liquefaction) . The cold heat source water includes brine or water mixed with brine, and is used for heat exchange without phase change like the above-described refrigerant.

  According to the present invention, the outside air dehumidified by the desiccant rotor is cooled by the aftercool cooler using the cold source water different from the heat pump circuit, and further cooled by the evaporator of the heat pump circuit. Is supplied to the air-conditioned space.

  In the outside air processing apparatus of the present invention, the heat pump circuit may further include a precooling evaporator, and the precooling evaporator may be disposed on the upstream side of the desiccant rotor in the air supply path. Further, in the heat pump circuit, a regenerative heat source evaporator that evaporates the refrigerant by using heat source water of a system different from the heat pump circuit may be disposed between the evaporator and the compressor. Further, in the heat pump circuit, another condenser that cools the refrigerant by using cold source water that is different from the heat pump circuit may be disposed between the expansion valve and the condenser.

  According to the present invention, after the heat of the outside air dehumidified by the desiccant rotor is removed and cooled by the cooler for aftercooling using the cold source water different from the heat pump circuit, the evaporation of the heat pump circuit is performed. Since it is further cooled by the cooler and supplied to the air-conditioned space, the cooling load of the evaporator of the heat pump circuit is reduced. For this reason, the power of the compressor provided in the heat pump circuit is small, and the amount of refrigerant charged in the heat pump circuit can be reduced accordingly. In addition, since heat from the outside air is removed using a cold source water that is separate from the heat pump circuit, the evaporator of the heat pump circuit can perform stable cooling, and the supply air temperature to the room due to changes in the outside air conditions It will be possible to reduce the change of.

It is explanatory drawing of the external air processing apparatus concerning this Embodiment, and has shown the state of the air_conditioning | cooling dehumidification driving | operation. It is explanatory drawing of the external air processing apparatus concerning this Embodiment, and has shown the state of heating humidification driving | operation. It is a graph which shows the change of the driving | running state on the ph diagram by the rotation speed control of a compressor. It is an air line figure which shows the driving | running state (the driving | running state of Tables 2-4) at the time of supplying cold source water to the cooler for aftercooling. It is an air line figure which shows the driving | running state (operating state of Tables 5-7) when not supplying cold-heat source water to the cooler for aftercooling. It is the graph which showed collectively the case where the cold source water is supplied to the cooler for aftercool, and the case where it does not supply the influence which the change of the outside air condition (change of the outside temperature) in the range of Table 1 has on the supply air temperature. (A). (B) is a graph which shows the capability of a precooling evaporator, and the change of evaporation temperature. FIG. 9 is an air line diagram showing an operating state when cold source water is supplied to an aftercool cooler under the outside air condition (No. 2) in Table 8. It is an air line figure which shows the driving | running state in the case of not supplying cold-heat source water to the cooler for aftercooling in external air conditions (the 2). Table 8 summarizes the effects of changes in the outside air conditions (changes in the outside air temperature) on the supply air temperature in the range shown in Table 8 with and without supply of cold source water to the aftercool cooler. It is a graph (a). (B) is a graph which shows the capability of a precooling evaporator, and the change of evaporation temperature. It is an air line figure which shows the driving | running state at the time of supplying cold-heat source water to the cooler for aftercooling in the external air conditions (the 3) of Table 9. It is an air line figure which shows the driving | running state in the case of not supplying cold-heat source water to the cooler for aftercooling in the external air conditions (the 3) of Table 9. The effect of changes in the outside air conditions (changes in the outside air temperature) on the supply air temperature in the range of Table 9 is a graph that summarizes the cases of supplying and not supplying the cold source water to the aftercool cooler. Yes (a). (B) is a graph which shows the capability of a precooling evaporator, and the change of evaporation temperature. It is explanatory drawing of the external air processing apparatus which provided another condenser between the expansion valve and the condenser in the 1st flow path of a heat pump circuit, and has shown the state of the air_conditioning | cooling dehumidification driving | operation. It is explanatory drawing of the external air processing apparatus which abbreviate | omitted the regeneration heat source evaporator from the 2nd flow path, and has shown the state of the air_conditioning | cooling dehumidification driving | operation. It is explanatory drawing of the air-conditioning system which distribute | distributed multiple water heat source small heat pump units with a built-in compressor in a building, and has arrange | positioned the external air processing apparatus concerning embodiment of this invention in part.

  Embodiments of the present invention will be described below. In addition, in this specification and drawing, about the component which has the substantially same function structure, duplication description is abbreviate | omitted by attaching | subjecting the same code | symbol.

  As shown in FIGS. 1 and 2, in the outside air processing apparatus 1 according to the embodiment of the present invention, the outside air OA is dehumidified and supplied to the air-conditioned space (not shown) as the air supply SA. 10 and an exhaust passage 11 for exhausting the return air RA exhausted from the air-conditioned space (not shown) to the outside as exhaust EA. A heat pump circuit 12 is provided inside the outside air processing apparatus 1.

  An air-permeable cylindrical desiccant rotor 15 in which a desiccant is held is disposed across the air supply path 10 and the exhaust path 11. Half of the desiccant rotor 15 is disposed in the exhaust path 11, and the other half of the desiccant rotor 15 is disposed in the air supply path 10. The desiccant rotor 15 is rotating, and the side surface of the desiccant rotor 15 is alternately moved through the air supply path 10 and the exhaust path 11 along with the rotation.

  The heat pump circuit 12 includes a four-way valve 20 having four entrances P1, P2, P3, and P4. As shown in FIG. 1, in the cooling and dehumidifying operation state, the four-way valve 20 is connected to the inlet / outlet P1 and the inlet / outlet P2 and is connected to the inlet / outlet P3 and the inlet / outlet P4. As shown in FIG. 2, in the heating and humidifying operation state, the four-way valve 20 is connected to the entrance P1 and the entrance P4, and is connected to the entrance P2 and the entrance P3. A first flow path 21 for circulating the refrigerant of the heat pump circuit 12 is connected to the inlet / outlet P1 and the inlet / outlet P3 of the four-way valve 20, and a second flow for circulating the refrigerant of the heat pump circuit 12 is connected to the inlet / outlet P2 and the inlet / outlet P4. A path 22 is connected.

  The first flow path 21 connecting the entrance P1 and the entrance P3 of the four-way valve 20 is provided with a precooling evaporator 25, an expansion valve 26, and a condenser 27 in order from the entrance P1 to the entrance P3. Yes. The precooling evaporator 25 is arranged on the upstream side of the desiccant rotor 15 in the air supply path 10. The condenser 27 is disposed upstream of the desiccant rotor 15 in the exhaust passage 11.

  In the second flow path 22 connecting the entrance P2 and the entrance P4 of the four-way valve 20, an evaporator 30, a regeneration heat source evaporator 31, and a compressor 32 are provided in this order from the entrance P2 to the entrance P4. ing. The evaporator 30 is disposed on the downstream side of the desiccant rotor 15 in the air supply path 10. The regenerative heat source evaporator 31 is supplied with hot heat source water heated by a heat source device (for example, a boiler, etc.) different from the refrigeration cycle of the heat pump circuit 12, and the regenerative heat source evaporator 31 has a heat pump. The refrigerant in the circuit 12 is heated and evaporated. The regeneration heat source evaporator 31 is disposed between the evaporator 30 and the compressor 32.

  An aftercool cooler 33 is disposed between the desiccant rotor 15 and the evaporator 30 in the air supply path 10. The aftercool cooler 33 is supplied with cold source water cooled by a cooling source device (for example, a cooling tower, etc.) that is separate from the refrigeration cycle of the heat pump circuit 12. The heat of the outside air OA flowing through the air supply path 10 is removed.

  When the cooling / dehumidifying operation is performed in the outside air processing apparatus 1 configured as described above, the entrance / exit P1 and the entrance / exit P2 of the four-way valve 20 are connected, and the entrance / exit P3 and the entrance / exit P4 are connected as shown in FIG. In the heat pump circuit 12, the refrigerant is supplied in the order of the precooling evaporator 25, the evaporator 30, and the regeneration heat source evaporator 31. Then, after the refrigerant which has absorbed heat in the precooling evaporator 25, the evaporator 30 and the regeneration heat source evaporator 31 and is sequentially evaporated into a gas is compressed by the compressor 32, the inlet / outlet is opened through the inlet / outlet P4 of the four-way valve 20. It passes to P3 and is supplied to the condenser 27. Then, the refrigerant that has radiated heat in the condenser 27 and becomes liquid is supplied again in the order of the precooling evaporator 25, the evaporator 30, and the regeneration heat source evaporator 31 through the expansion valve 26. Thus, in the heat pump circuit 12, the refrigerant is circulated in the order of the precooling evaporator 25, the evaporator 30, the regeneration heat source evaporator 31, the compressor 32, the condenser 27, and the expansion valve 26, and the precooling evaporator 25, the evaporator A refrigerating cycle is performed in which heat is absorbed by the evaporator 30 and the regenerative heat source evaporator 31 and is radiated by the condenser 27.

  In addition, outside air OA is taken into the air supply path 10 of the outside air processing apparatus 1 from the outside and passes through the precooling evaporator 25, the desiccant rotor 15, the aftercooling cooler 33, and the evaporator 30 in this order, and is cooled and dehumidified. The treated air is supplied as air supply SA and is supplied into the room from the air supply path 10. First, in the precooling evaporator 25, the outside air OA is cooled and dehumidified by the evaporation of the refrigerant in the heat pump circuit 12, and then moisture is adsorbed by the desiccant rotor 15 to perform the dehumidifying process. Further, the high-temperature dehumidified air after passing through the desiccant rotor 15 is cooled by the cold heat source water supplied to the aftercool cooler 33 from the cold heat source device of a system different from the heat pump circuit 12, and the heat is removed. Then, the outside air OA from which heat has been removed is further cooled by the evaporation of the refrigerant in the heat pump circuit 12 in the evaporator 30, and supplied to the room as a cooled and dehumidified supply air SA.

  On the other hand, the return air RA is taken into the exhaust passage 11 of the outside air processing apparatus 1 from the room, passes through the condenser 27 and the desiccant rotor 15 in this order, and becomes exhaust EA and is discharged from the exhaust passage 11 to the outside of the room. In the exhaust path 11, the return air RA is first heated to, for example, about 50 ° C. by the condensation of the refrigerant in the heat pump circuit 12 in the condenser 27. Then, the return air RA that has reached a high temperature is sent to the desiccant rotor 15, and moisture is removed and released to regenerate the desiccant rotor 15. And the return air RA which became high temperature and humidity is exhausted outside as exhaust EA.

  Further, as the desiccant rotor 15 rotates, the side surface of the desiccant rotor 15 alternately moves in the air supply path 10 and the exhaust path 11. In the exhaust passage 11, the moisture attached to the desiccant rotor 15 is removed and released, and the desiccant rotor 15 is regenerated. On the other hand, in the air supply path 10, moisture of the outside air OA is adsorbed by the regenerated desiccant rotor 15 to perform dehumidification processing.

  According to the outside air processing apparatus 1, the heat of the outside air OA dehumidified by the desiccant rotor 15 is removed by the aftercool cooler 33 using the cooling source water that is different from the refrigeration cycle of the heat pump circuit 12. After being cooled, the evaporator 30 is further cooled and supplied to the air-conditioned space. Therefore, in the heat pump circuit 12, the cooling load of the evaporator 30 is reduced, and power consumption is reduced (high efficiency). For this reason, the power of the compressor 32 included in the heat pump circuit 12 is small, and the amount of refrigerant charged in the heat pump circuit 12 can be reduced accordingly. Moreover, since the heat of the outside air is removed using a cold source water of a system different from that of the heat pump circuit 12, the evaporator 30 of the heat pump circuit 12 can perform stable cooling, and the indoor air due to changes in the outside air conditions can be achieved. The temperature change of the supply air SA can be reduced, and the controllability of temperature can be improved.

  In the heat pump circuit 12, a precooling evaporator 25, an evaporator 30, and a regeneration heat source evaporator 31 are connected in series. It is also conceivable that these evaporators 25, 30, and 31 are connected in parallel and each is multi-controlled. However, since the first purpose of the heat pump circuit 12 is to regenerate the desiccant rotor 15 by heating the return air RA to about 50 ° C. in the condenser 27, the evaporator 25 on the heat source side of the heat pump circuit 12. A simple circuit (simple circuit) in which the three evaporators 25, 30, and 31 are connected in series is employed so that the heat collecting ability on the 30 and 31 side can be easily maintained.

  The cold heat source water supplied to the aftercool cooler 33 is cooled by a cold heat source device such as a cooling tower, for example. In the cooling tower, the power for cooling the cold heat source water is only the pump and the fan, so that cold heat can be produced with a minimum of power compared to a refrigerator or the like. In the aftercooling cooler 33, the “cooling heat” is processed by this cooling heat source water, so that the cooling load in the heat pump circuit 12 is reduced and the power consumption is reduced (high efficiency).

  The air supplied to the evaporator 30 is not high-temperature dehumidified air immediately after passing through the desiccant rotor 15, but cold source water cooled by a cooling tower or the like (cold source water having a temperature corresponding to the wet bulb temperature of the outside air OA). ). On the other hand, the air cooled by the precooling evaporator 25 is the outside air OA. By processing “other heat” with the cold source water in the aftercool cooler 33, the inlet air of both the precool evaporator 25 and the evaporator 30 is simultaneously affected by the outside air OA. This leads to an increase in the controllability (controllability of the supply air temperature) of the ability of the heat pump circuit 12 in which the evaporators 25, 30, 31 are arranged in series as shown in FIG. Details will be described below.

  In the cooling and dehumidifying operation (operation for reducing the enthalpy of air) in the outside air processing device 1, the desiccant rotor 15 converts the latent heat of the outside air OA into sensible heat, and does not reduce the enthalpy of the air (exactly Enthalpy is not constant, and enthalpy increases slightly due to exchange efficiency of 1 or less). The outlet air of the desiccant rotor 15 is in a high temperature and low humidity state. Therefore, the operation of reducing the enthalpy of air is performed by the aftercool cooler 33 and the evaporator 30 downstream of the desiccant rotor 15. The higher the moisture concentration (relative humidity) of the supply air to the desiccant rotor 15, the greater the dehumidification amount (moisture concentration transfer amount) in the desiccant rotor 15. Therefore, the precooling evaporator 25 sets the relative humidity to 100% RH ( Saturated air).

  In addition, the performance of the low temperature regeneration desiccant rotor that is currently on the market is the dehumidification amount generally required for air conditioning (dehumidification amount of the introduced outside air) with regenerated air of about 50 ° C obtained with a general-purpose refrigerant heat pump circuit such as R410A. Is not enough to achieve. Therefore, in the precooling evaporator 25, in order to secure the dehumidification amount in the desiccant rotor 15, it is necessary to use the saturated air as the supply air to the desiccant rotor 15 and to cool and dehumidify the insufficient amount of dehumidification in the desiccant rotor 15. is there.

  Therefore, the operation for reducing the enthalpy of air in the outside air processing apparatus 1 is directly performed by the precooling evaporator 25, the evaporator 30, and further the aftercooling cooler 33.

  However, in order to reliably perform the above operation, first, the desiccant rotor 15 is regenerated (regenerative air (return air RA supplied to the desiccant rotor 15) is maintained at a temperature of about 50 ° C. Therefore, maintaining the capacity of the condenser 27 will be described as a first object.

  As a control method of the humidity temperature and humidity of the supply air SA (indoor) of the outside air processing device 1, first, “heat compressor speed control” by an inverter is employed in the heat pump circuit 12. In the heat pump circuit 12, the supply temperature and flow rate of the fluid to be heated (return air RA) on the condenser 27 side and the fluid to be cooled (outside air OA) on the evaporators 25, 30, and 31 side are constant, and FIG. As the number of rotations of the compressor increases, the evaporation temperature (evaporation pressure) decreases, the condensation temperature (condensation pressure) increases, and the capacities of the evaporators 25, 30, 31 and the condenser 27 increase.

  The heat pump circuit 12 of the outside air processing apparatus 1 here is the main operation (first purpose) of regeneration of the desiccant rotor 15, and the compressor rotation speed (refrigerant flow rate) by the inverter depending on the humidity of the supply air SA (indoor). Adjust. At this time, the capabilities of the evaporators 25, 30, and 31 change along with the capabilities of the condenser 27.

  For example, when the humidity of the outside air OA increases and the temperature increases (when the latent heat load increases and the sensible heat load also increases), the compressor rotational speed is increased (the refrigerant flow rate is increased), and the condenser 27 Thus, the desiccant rotor 15 can be sufficiently regenerated and the dehumidifying performance of the desiccant rotor 15 can be increased (the humidity of the supply air SA can be reduced). At the same time, the cooling dehumidification capability of the precooling evaporator 25 can be increased to lower the supply air humidity, and the capability of the evaporator 30 can be increased at the same time to lower the temperature of the supply air SA.

  However, when the humidity of the supply air SA is increased and the temperature is a predetermined value (only the latent heat load is increased), the temperature of the supply air SA is overcooled only by increasing the compressor speed. Therefore, flow rate control (two-way valve control or the like) of the hot heat source water supplied to the regeneration heat source evaporator 31 is employed. For example, when the heat source water is not being supplied to the regeneration heat source evaporator 31 now, the humidity of the supply air SA is increased, and thus the rotational speed of the compressor is increased as described above. At the same time, if the heat source water is supplied to the regeneration heat source evaporator 31 (the flow rate of the heat source water is controlled), the total heat transfer area of the evaporators 25, 30, and 31 is increased. As in (b), a decrease in evaporation pressure (evaporation temperature) can be suppressed.

  Next, in order to describe the controllability of the temperature of the outside air processing apparatus 1, the influence of changes in outside air conditions on the supply air temperature when the heat source water is supplied to the regeneration heat source evaporator 31 will be considered. The conditions of this outside air OA are as shown in Table 1. Dry bulb temperature 30.0 ° C DB / absolute humidity 16.6g / kgDA (Case (1)), 32.5 ° C DB / 17.7g / kgDA (Case (2)), and 35.0 ° C There are three types: DB / 18.8g / kgDA (Case (3)).

  First, the specifications of the precooling evaporator 25, the aftercooling cooler 33, and the evaporator 30 (overall heat transfer coefficient x transfer coefficient) are set under the outside air condition of Case (2) at a heat source water temperature of 30.5 ° C / evaporation temperature of 20 ° C. Thermal area) and operating conditions were defined. Tables 2 to 4 show the dry-bulb temperature of air, absolute humidity, enthalpy, and precooling evaporator 25, aftercooling cooler 33, at each position a to e in the above-described outside air processing apparatus 1 in FIG. The capability of the evaporator 30 is shown. As shown in Table 2, the indoor air supply SA in Case (2) (column e in Tables 2 to 4) is 25.9 ° C. DB / 10.50 g / kgDA.

  Next, the precooling evaporator 25, the aftercooling cooler 33, and the evaporator 30 are used to determine the operating conditions under the outside air conditions of Case (1) and Case (3). The outlet air of the vessel 25 (column b in Tables 2 to 4) is fixed at 22.8 ° C. DB / 16.60 g / kgDA, so that the amount of dehumidification in the desiccant rotor 15 of Case (2) (16.60-10.50 = 6.10 g / The evaporation temperature was determined so that kgDA) was maintained. As shown in Table 3, the indoor air supply SA (column e) in Case (1) was 26.5 ° C DB, and the evaporation temperature was 21.6 ° C. Further, as shown in Table 4, the indoor air supply SA (column e) in Case (3) was 25.1 ° C. DB, and the evaporation temperature was 18.4 ° C. The change in the outside air conditions in the range of Tables 2 to 4 gave a change of 1.4 deg. (26.5 ° C DB to 25.1 ° C DB) to the indoor air supply temperature.

  Here, since the outside air conditions in Table 1 are not in an extreme range so that the dehumidification amount in the desiccant rotor 15 is maintained, the change in the supply air temperature (1.4 deg.) Is as described above. When the sensible heat load of OA is extremely small, the supply air SA is supercooled, and the flow rate control of the hot heat source water supplied to the regeneration heat source evaporator 31 as described above is required.

  As described above, the aftercool cooler 33 increases the controllability (controllability of the supply air temperature) of the ability of the heat pump circuit 12 in which the evaporators 25, 30, and 31 are arranged in series. This will be described next by comparing the change in the supply air temperature (1.4 deg.) With the change in the supply air temperature when the cooling source water is not supplied to the aftercool cooler 33.

  Tables 5 to 7 show that when no cooling source water is supplied to the aftercool cooler 33, the air dry bulb temperature, absolute humidity, enthalpy, and precool evaporator 25, aftercool cooler 33, evaporator Shows 30 abilities. There are three types of outside air conditions: Case (1), Case (2), and Case (3) in Table 1.

  As before, the specifications of the precooling evaporator 25, the aftercooling cooler 33, and the evaporator 30 under the outside air conditions of Case (2) are set at an evaporation temperature of 20 ° C and a heat source water temperature of 30.5 ° C. Heat transfer coefficient x heat transfer area) and operating conditions were determined. As shown in Table 5, the indoor air supply SA (row e) in Case (2) is 25.9 ° C. DB / 10.50 g / kgDA.

  Next, the precooling evaporator 25, the aftercooling cooler 33, and the evaporator 30 are used to determine the operating conditions under the outside air conditions of Case (1) and Case (3). Dehumidification amount (16.60-10.50 = 6.10 g / kgDA) in the desiccant rotor 15 of Case (2) is maintained by fixing the outlet air of the vessel 25 (row b) to 22.8 ° C DB / 16.60g / kgDA. The evaporation temperature was determined so that As shown in Table 6, the indoor air supply (case e) in Case (1) was 27.0 ° C DB, and the evaporation temperature was 21.6 ° C. Further, as shown in Table 7, the indoor air supply (column e) in Case (3) was 24.6 ° C. DB, and the evaporation temperature was 18.4 ° C. The change in the outside air condition in the range of Table 1 gave a change of 2.4 deg. (27.0 ° C. DB to 24.6 ° C. DB) to the indoor air supply temperature.

  In this way, the change in the supply air temperature (2.4 deg.) When the cold heat source water is not supplied to the aftercool cooler 33 is the change in the supply air temperature when the cold heat source water is supplied as described above (1.4 deg.). deg.) was enlarged 1.7 times. In other words, the aftercool cooler 33 halves the change in the supply air temperature.

  This explains that the aftercool cooler 33 increases the controllability (controllability of the supply air temperature) of the ability of the heat pump circuit 12 in which the evaporators 25, 30, and 31 are arranged in series. It is.

  FIG. 4 shows an operating state (the operating states in Tables 2 to 4) when cold source water is supplied to the aftercool cooler 33 on the air diagram. FIG. 5 shows on the air diagram the operating state (the operating states in Tables 5 to 7) when the cold source water is not supplied to the aftercool cooler 33. Further, FIG. 6 shows the effect of the change in the outside air condition (change in the outside air temperature) on the supply air temperature in the range of Table 1 when the cold heat source water is supplied to the aftercool cooler 33 and when it is not supplied. This is a summary. For reference, FIG. 6 also shows changes in the capacity of the precooling evaporator 25 and the evaporation temperature.

  Further, in the outside air condition (No. 2) in Table 8 and the outside air condition (No. 3) in Table 9, as described above, the influence of the change in the outside air condition (change in the outside air temperature) on the supply air temperature is The case where the cold source water is supplied to the cooler 33 and the case where it is not supplied were examined. Under the outdoor air conditions in Table 1, the absolute humidity was higher as the dry bulb temperature was higher, but under the outdoor air conditions (No. 2) in Table 8, the absolute humidity was lower as the dry bulb temperature was higher. Further, in the outdoor air condition (No. 3) in Table 9, the absolute humidity is constant regardless of the dry bulb temperature.

  FIG. 7 shows an operating state in the case where the cold source water is supplied to the aftercool cooler 33 under the outside air condition (No. 2) in Table 8. FIG. 8 shows the aftercooling cooling. The operation state when the cold source water is not supplied to the vessel 33 is shown on the air diagram. Further, FIG. 9 shows the effect of the change in the outside air condition (change in the outside air temperature) on the supply air temperature in the range of Table 8 when the heat source water is supplied to the aftercooling cooling heat exchanger and when it is not supplied. It is shown collectively. For reference, FIG. 9 also shows changes in the capacity of the precooling evaporator 25 and the evaporation temperature.

  FIG. 10 is an air diagram showing the operating state when cold source water is supplied to the aftercool cooler 33 under the outside air condition (No. 3) in Table 9. FIG. 11 shows aftercooling cooling. The operation state when the cold source water is not supplied to the vessel 33 is shown on the air diagram. In addition, FIG. 12 shows the effect of the change in the outside air condition (change in the outside air temperature) on the supply air temperature in the range of Table 9 when the cold source water is supplied to the aftercool cooler 33 and when it is not supplied. It is shown collectively. For reference, FIG. 12 also shows changes in the capacity of the precooling evaporator 25 and the evaporation temperature.

  In the outside air condition (No. 2) and the outside air condition (No. 3), the change in the capacity of the precooling evaporator 25 is small and the change in the evaporation temperature is small, so the change in the supply air temperature is also small. As a result, there was little difference in the change in the supply air temperature between when the cold heat source water was supplied to the aftercool cooler 33 and when it was not supplied.

  Next, in the outside air processing apparatus 2 shown in FIG. 13, another condenser 40 is provided between the expansion valve 26 and the condenser 27 in the first flow path 21 of the heat pump circuit 12. The other condenser 40 is supplied with cold heat source water cooled by a cold heat source device (for example, a cooling tower) separate from the refrigeration cycle of the heat pump circuit 12. Except for the point that another condenser 40 is provided between the expansion valve 26 and the condenser 27, the outside air processing device 2 shown in FIG. 13 is substantially the same as the outside air processing device 1 described above with reference to FIGS. In general. Therefore, the same components as those in FIGS. 1 and 2 are denoted by the same reference numerals in FIG. In the condition where the sensible heat load is large in the outside air load, in addition to the condenser 27 provided in the first flow path 21 as in the outside air processing device 2 shown in FIG. May be necessary.

  In the outside air processing device 3 shown in FIG. 14, the regeneration heat source evaporator 31 is omitted from the second flow path 22. In the outside air processing device 3 shown in FIG. 14, another condenser 40 is provided between the expansion valve 26 and the condenser 27 as in the outside air processing device 2 shown in FIG. Except for the point that the regenerative heat source evaporator 31 is omitted and another condenser 40 is provided between the expansion valve 26 and the condenser 27, the outside air processing device 3 shown in FIG. The configuration is substantially the same as the described outside air processing apparatus 1. Accordingly, common components are denoted by the same reference numerals as those in FIGS. 1 and 2 in FIG. As described above, the regeneration heat source evaporator 31 may be unnecessary depending on the load condition. For example, when the ratio of the latent heat load in the outside air load does not always change greatly, the supply air temperature is overcooled even without the regeneration heat source evaporator 31 as in the outside air processing device 3 shown in FIG. In addition, the regeneration air temperature does not become overheated (the protruding temperature of the compressor 32 is overheated).

  Moreover, the external air processing apparatuses 1 to 3 shown in FIGS. 1, 2, 13, and 14 can also perform a heating and humidifying operation. As shown in FIG. 2, in the heating and humidifying operation state, the four-way valve 20 is connected to the entrance P1 and the entrance P4, the entrance P2 and the entrance P3 are connected, and the precooling evaporator 25 functions as a condenser. The condenser 27, the evaporator 30, and the regeneration heat source evaporator 31 function as an evaporator. In the heat pump circuit 12, after the refrigerant that has absorbed heat by the condenser 27 (functioning as an evaporator), the evaporator 30, and the regeneration heat source evaporator 31 and is evaporated into gas is compressed by the compressor 32, The refrigerant that has radiated heat and became liquid by the precooling evaporator 25 (functioning as a condenser) is supplied to the condenser 27 (functioning as an evaporator), the evaporator 30, and the regeneration heat source evaporator 31 via the expansion valve 26. To go. Thus, in the heat pump circuit 12, a refrigeration cycle is performed in which heat is absorbed by the condenser 27 (functioning as an evaporator), the evaporator 30 and the regeneration heat source evaporator 31, and radiated by the precooling evaporator 25 (functioning as a condenser). . Also in the outside air processing apparatuses 2 and 3 shown in FIGS. 13 and 14, the heating and humidifying operation can be performed by switching the four-way valve 20.

  Here, as shown in FIG. 15, an air conditioning system 52 that performs individual air conditioning by distributing a plurality of water heat source small heat pump units 50 with a built-in compressor in a building 51 is known. In this air conditioning system 52, heat source water is supplied to each water heat source small heat pump unit 50 through a pipe 55 and a pump 56, and the heat source water cooled by the cold heat source device (cooling tower) 57 or the heat source device ( The heat source water heated by the boiler 58 is appropriately selected and supplied to each water heat source small heat pump unit 50. Thereby, the individual air conditioning of cooling or heating is performed by each water heat source small heat pump unit 50. Further, each water heat source small heat pump unit 50 can be operated only by blowing or can be stopped.

  In the air conditioning system 52 that performs such individual air conditioning, it is also conceivable to partially arrange the outside air processing apparatuses 1 to 3 according to the embodiments of the present invention described above with reference to FIGS. Similarly to each water heat source small heat pump unit 50, the heat source water is also supplied to the outside air processing apparatuses 1 to 3 through the pipe 55. Thus, by arranging the outside air processing devices 1 to 3 with a built-in compressor in the air conditioning system 52 and processing (dehumidifying) the latent heat load in the outside air processing devices 1 to 3 during cooling operation, for example, each water heat source small heat pump unit 50 can process only the sensible heat load (cool without dehumidification), or each water heat source small heat pump unit 50 mainly processes the sensible heat load (minimum dehumidification and cooling) The water heat source small heat pump unit 50 can process the cooling load with “high efficiency” at “high evaporation temperature”.

  INDUSTRIAL APPLICABILITY The present invention is useful for an outside air processing apparatus that performs indoor cooling and dehumidifying operation.

DESCRIPTION OF SYMBOLS 1 Outside air processing apparatus 10 Supply path 11 Exhaust path 12 Heat pump circuit 15 Desiccant rotor P1, P2, P3, P4 Entrance / exit 20 Four-way valve 21 First flow path 22 Second flow path 25 Precooling evaporator 26 Expansion valve 27 Condensation 30 Evaporator 31 Regenerative heat source evaporator 32 Compressor 33 Aftercool cooler 50 Water heat source small heat pump unit 51 Building 52 Air conditioning system 55 Pipe 56 Pump 57 Cold heat source device 58 Thermal source device

Claims (4)

An outside air processing device that dehumidifies outside air using a desiccant rotor and supplies the air-conditioned space,
A heat pump circuit that performs a refrigeration cycle by circulating refrigerant in the order of an evaporator, a compressor, a condenser, and an expansion valve,
The desiccant rotor is rotatably disposed across the exhaust passage and the air supply passage;
The evaporator of the heat pump circuit is disposed downstream of the desiccant rotor in the air supply path;
A condenser of the heat pump circuit is disposed upstream of the desiccant rotor in the exhaust passage;
An after-cooling cooler that cools using cold source water that is different from the heat pump circuit is disposed between the desiccant rotor and the evaporator in the air supply path. apparatus. The heat pump circuit further comprises a precooling evaporator;
The outside air processing apparatus according to claim 1, wherein the precooling evaporator is disposed upstream of the desiccant rotor in the air supply path.   In the heat pump circuit, between the evaporator and the compressor, a regenerative heat source evaporator that evaporates a refrigerant using a heat source water of a system different from the heat pump circuit is disposed, The outside air processing apparatus according to claim 1 or 2.   The said heat pump circuit WHEREIN: The another condenser which cools a refrigerant | coolant using the cold source water of a different system from the said heat pump circuit is arrange | positioned between the said expansion valve and the said condenser, It is characterized by the above-mentioned. Item 4. The outside air processing device according to any one of Items 1 to 3.

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