JP2013036705A - Outside air processing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an outside air processing device capable of supplying air at a lower temperature and lower humidity than those of the outside air to an indoor space with a simple configuration.SOLUTION: The outside air processing device includes: an air supply passage 13 that sucks the outside air and supplies the air to an indoor space; a desiccant rotor 25 that dehumidifies the air flowing in the air supply passage 13; a first sensible heat exchanger 27 that performs a sensible heat exchange between the dehumidified air and the outside air; a divider unit 31 that divides the air subjected to the sensible heat exchange into two streams; a humidifier 33 that humidifies air in one of the divided streams; and a second sensible heat exchanger 35 that cools air in the other divided stream by performing a sensible heat exchange between the humidified air and air in the other stream. The air cooled by the second sensible heat exchanger 35 is supplied to the indoor space.

Description

  The present invention relates to an outside air processing apparatus that dehumidifies and cools outside air and supplies it to the room.

  In general, building facilities such as offices and hospitals are provided with an outside air processing device that dehumidifies and cools outside air to supply it to the room in order to assist indoor cooling. Conventionally, as this type of outside air treatment device, an air supply passage that communicates between the outdoor suction port and the indoor discharge port, a total heat exchanger that can exchange temperature and humidity, and adsorption and desorption of moisture in the air A dehumidification rotor impregnated or coated with a possible hygroscopic agent, a sensible heat exchanger that can exchange only the temperature, and a supply side cooler that cools the air using the latent heat of water evaporation, etc. The air flowing through the passage passes through the total heat exchanger, the dehumidification rotor, the sensible heat exchanger, and the air supply side cooler sequentially from the outdoor suction port, and is dehumidified and cooled and supplied to the room. It is known (see, for example, Patent Document 1).

JP 2000-111096 A

However, in the conventional configuration, the air supply side cooler is disposed in the air supply ventilation path between the sensible heat exchanger and the indoor outlet, and is a spray type that cools the air by using the latent heat of evaporation of water. Or since it is a vaporization type humidification means, while the temperature of the supplied air falls, there exists a problem that absolute humidity becomes high and it is not suitable for the air conditioning of summer.
The present invention has been made in view of the above-described circumstances, and an object of the present invention is to provide an outside air processing apparatus that can supply air having a lower temperature and lower humidity than outside air into a room with a simple configuration.

  In order to achieve the above object, the present invention provides an air supply path for sucking outside air and supplying it to the room, dehumidifying means for dehumidifying the air flowing through the air supply path, and dehumidified air as outside air or room air. First sensible heat exchange means for sensible heat exchange, distribution means for distributing sensible heat exchanged air into two, humidification means for humidifying one of the distributed air, and the other distributed with the humidified air Sensible heat exchange with the other air to cool the other air, and the air cooled by the second sensible heat exchange means is supplied into the room.

  In this configuration, the distribution means includes a blower fan provided in at least one of an air supply port of the air supply path and an exhaust port for discharging the one air to the outside of the air supply path, and each of the second sensible heat exchangers. Control means for controlling the air flow rate of the blower fan based on the outlet temperature may be provided.

  Further, in the above configuration, the distribution unit includes a blower fan disposed in an opening that communicates the path through which the one air flows and the air supply path upstream of the humidification unit, and the second sensible heat exchange. Control means for controlling the air flow rate of the blower fan based on each outlet temperature of the vessel.

  Further, in the above configuration, the distribution unit includes a damper provided on each of the path through which the one air flows and the air supply path on the upstream side of the humidification unit, and each outlet of the second sensible heat exchanger. Control means for controlling the opening degree of the damper based on the temperature may be provided. The distribution means may set the distribution amount of the one air and the other air substantially equally.

  According to the present invention, the second sensible heat exchange means for sensible heat exchange between one humidified air and the other dehumidified air to cool the other air is provided. Air that has been cooled by utilizing the latent heat of water can be supplied to the room without increasing. In addition, according to the present invention, there is provided distribution means for distributing the dehumidified air that has passed through the dehumidification means and the first sensible heat exchange means into two, and humidifies one of the distributed air to provide the other air Used for cooling. Since this one air is fully dehumidified, the dry bulb temperature and wet bulb temperature after humidification can be lowered compared to those used by humidifying the outside air. For this reason, the cooling efficiency of the other air can be increased by performing sensible heat exchange between the one air having a low dry bulb temperature and a low wet bulb temperature and the other air.

It is a conceptual diagram of the external air processing apparatus concerning 1st embodiment. It is a figure which shows the relationship between the ratio of the supply air quantity with respect to the inhaled external air quantity, and the relationship between cooling capacity. It is a state line diagram of the air in each point set on the path | route through which the air of an external air processing apparatus distribute | circulates. It is a conceptual diagram of the external air processing apparatus concerning 2nd embodiment. It is a conceptual diagram of the external air processing apparatus concerning 3rd embodiment. It is a conceptual diagram of the external air processing apparatus concerning 4th embodiment.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
[First embodiment]
FIG. 1 is a conceptual diagram showing an outside air processing device 1 according to the first embodiment. This outside air processing device 1 is intended to reduce the cooling load in the summer of a separately installed air conditioner by supplying outside air after dehumidifying and cooling the outside air. As shown in FIG. 1, the outside air processing apparatus 1 includes a main body box (housing) 10 formed in a box shape, and the main body box 10 is partitioned by a partition plate 11 and a plurality of paths through which air flows. Is formed. Specifically, the main body box 10 includes an air supply path 13 that sucks outside air OA and supplies the air supply SA into the room, a first exhaust path 15 that sucks outside air OA and discharges the exhaust EA to the outside again, A second exhaust path (a path through which one air flows) 17 is provided that discharges a part of the air that flows in the air path 13 and flows through the air supply path 13 to the outside as exhaust EA.
An outside air introduction fan 21 is provided at the suction port 13A of the air supply path 13, and most of the outside air OA sucked into the air supply path 13 through the suction port 13A by the operation of the outside air introduction fan 21 is a discharge port (air supply port). ) Is supplied to the room through 13B, and the remainder of the outside air OA is discharged to the outside through the discharge port (exhaust port) 17A of the second exhaust path 17. In addition, a regeneration air introduction fan 23 is provided at the suction port 15A of the first exhaust path 15, and by the operation of the regeneration air introduction fan 23, outside air (regeneration) that is sucked into the first exhaust path 15 through the suction port 15A. Air) OA is discharged to the outside through the discharge port 15B.

  The air supply path 13 and the first exhaust path 15 are configured such that air flows in opposition to each other, and the air supply path 13 and the first exhaust path 15 are arranged in order from the side closer to the suction port 13A of the air supply path 13 and the discharge port 15B of the first exhaust path 15. A disc-shaped desiccant rotor (dehumidifying means) 25 and a first sensible heat exchanger (first sensible heat exchange means) 27 are disposed across the air supply path 13 and the first exhaust path 15. In the first exhaust path 15, a heater (heating regeneration means) 29 that heats the flowing air is disposed between the desiccant rotor 25 and the first sensible heat exchanger 27. The heater 29 is formed of, for example, a hot water coil, and is supplied with hot water heated by heat obtained from natural energy such as exhaust heat when burning fuel such as gas or petroleum, or solar heat or geothermal heat. It is like that.

  The desiccant rotor 25 is formed by forming a honeycomb-shaped nonwoven fabric impregnated with a dehumidifying agent such as lithium chloride or silica gel into a rotor shape, and is driven to rotate at a low speed around the rotation shaft 25A. The desiccant rotor 25 moves between the air supply path 13 and the first exhaust path 15 while rotating in a direction orthogonal to the air flow in the air supply path 13 and the first exhaust path 15. The desiccant rotor 25 contacts the outside air OA taken from the suction port 13A in the air supply path 13 and dehumidifies the outside air OA. On the other hand, in the first exhaust path 15, the outside air heated by the heater 29 (for regeneration) Air) Dehumidifying agent is heated and regenerated in contact with OA. That is, the desiccant rotor 25 includes a dehumidifying region 25B that dehumidifies the outside air OA in the air supply path 13, and a regeneration region 25C that is heated and regenerated in contact with the regeneration air heated in the first exhaust path 15.

  The first sensible heat exchanger 27 cools the dehumidified air by performing sensible heat exchange between the air dehumidified by the desiccant rotor 25 and the outside air sucked into the first exhaust passage 15. Although the first sensible heat exchanger 27 is not shown, the aluminum foil or the synthetic resin film formed in a wave shape and the flat aluminum foil or the synthetic resin film are alternately alternated, and the wave directions are alternated. The two flow paths 27A and 27B are orthogonal to each other, and the flow paths 27A and 27B communicate with the air supply path 13 or the first exhaust path 15, respectively. In the first sensible heat exchanger 27, gases passing through the two flow paths are not mixed, and sensible heat is exchanged through an aluminum foil or a synthetic resin film.

The air supply path 13 includes a distribution unit (distribution means) 31 that distributes the air flowing through the air supply path 13 to the downstream side of the first sensible heat exchanger 27, and the second exhaust path 17 is provided in the distribution unit 31. Is connected. In the second exhaust path 17, a humidifier (humidifying means) 33 and a second sensible heat exchanger (second sensible heat exchange means) 35 are arranged in this order from the distributor 31 toward the discharge port 17A. .
The humidifier 33 is impregnated with water supplied to a non-woven fabric formed in a honeycomb shape. The air is passed through the non-woven fabric to humidify the air by containing moisture.
The second sensible heat exchanger 35 cools the other air by sensible heat exchange between one of the air distributed by the distributor 31 and humidified by the humidifier 33 and the other distributed air. It is. Similarly to the first sensible heat exchanger 27, the second sensible heat exchanger 35 has two flow paths 35A and 35B that are orthogonal to each other. Since the other configuration is the same as that of the first sensible heat exchanger 27, the description thereof is omitted.
In the second sensible heat exchanger 35, since the humidified air flowing through the second exhaust path 17 and the dehumidified air flowing through the air supply path 13 exchange sensible heat, the dehumidified air has the latent heat of water. And is supplied into the room through the discharge port 13B. In this case, the second sensible heat exchanger 35 does not mix the gas passing through the two flow paths, so that moisture does not move into the dehumidified air and can prevent an increase in humidity.

  Further, in the present embodiment, the distribution ratio by the distribution unit 31, that is, one air amount flowing through the second exhaust path 17 (flow path 35A) and the other air amount flowing through the air supply path 13 (flow path 35A). A configuration for controlling the ratio is provided. Specifically, the outside air processing apparatus 1 includes temperature sensors 37A and 37B that measure the air temperature disposed at the outlets of the flow paths 35A and 35B of the second sensible heat exchanger, and the discharge port 13B of the air supply path 13. The blower fan 39 is provided with an inverter 41 for setting the rotational speed of the blower fan 39, and a controller (control means) 43 for controlling the rotational speed of the blower fan 39 via the inverter 41. The blower fan 39 and the controller 43 constitute a distribution unit including the distribution unit 31. The temperature sensors 37A and 37B described above are connected to the controller 43, and the controller 43 controls the rotational speed of the blower fan 39 based on the measured temperatures of the temperature sensors 37A and 37B.

Next, the relationship between the ratio of the supply air SA amount to the intake outside air OA amount and the cooling capacity will be described. FIG. 2 is a diagram showing the relationship between the ratio of the supply air SA amount to the sucked outside air OA amount and the cooling capacity.
In FIG. 2, the exhaust (EA) temperature Td is the air temperature at the discharge port 17A (point F) of the second exhaust passage 17, and the supply (SA) temperature Ts is the discharge port 13B (point) of the supply passage 13. The air temperature in E) and the air temperature after humidification are the air temperature (point D) between the humidifier 33 and the second sensible heat exchanger 35, respectively, and the amount of supplied SA relative to the amount of outside air OA sucked The value when the ratio is changed between 10% and 90% is measured. Here, the exhaust temperature Td is measured by the temperature sensor 37B, and the supply air temperature Ts is measured by the temperature sensor 37A.
The cooling capacity is a value obtained by multiplying the amount of supplied air supplied indoors by the temperature difference between the outside air temperature and the supplied air temperature Ts.
According to FIG. 2, the supply air temperature Ts remains unchanged at a value lower than 25 ° C. until the ratio of the supply air SA amount to the sucked outside air OA amount is 50%, but suddenly exceeds 50%. It can be seen that it rises. On the other hand, if the ratio of the supply air SA amount to the sucked outside air OA amount is set low, a large amount of the external air OA is sucked in order to secure the supply air SA amount. The cost for driving 21 increases.
For this reason, in the outside air processing apparatus 1 according to the above configuration, when the supply air is cooled by the second sensible heat exchanger 35, the ratio of the supply air SA amount to the intake outside air OA amount is 45 to 50%, that is, approximately. It turned out to be evenly distributed.

Next, the operation of dehumidifying and cooling the air supplied indoors from the discharge port 13B of the air supply path 13 will be described using the air state diagram shown in FIG. Points A to J shown in FIG. 3 correspond to the points A to J set on the respective paths in FIG.
The desiccant rotor 25 is an operation in which moisture is absorbed into the dehumidifying agent in the air and the operation in which the humidity is released from the dehumidifying agent has no enthalpy change, and the relative humidity after the release and the relative humidity after the adsorption are the same. have.
In the first sensible heat exchanger 27 and the second sensible heat exchanger 35, the temperature of each fluid rises or falls to 90% of the temperature difference between the high temperature fluid and the low temperature fluid. The humidifier 33 has a humidification efficiency of up to 90% relative humidity.

As for the outside air sucked at the points A and G, a dry bulb temperature of 35 ° C. and a wet bulb temperature of 24 ° C., which are ISO and JIS rated cooling conditions in the air conditioner, are described as an example. The relative humidity at points A and G is 40.3%.
When the outside air OA passes through the dehumidifying region 25B of the desiccant rotor 25 and is dehumidified, the dry bulb temperature indicated by point B is 44.3 ° C./wet bulb temperature 24.1 ° C./relative humidity 18.3%. Here, the dry-bulb temperature is rising because it is heated when passing through the desiccant rotor 25.
Next, when the dehumidified air is subjected to sensible heat exchange with the outside air OA in the first sensible heat exchanger 27, as indicated by a point C, the dry bulb temperature is 35.9 ° C./the wet bulb temperature is 21.7 ° C./relative. The humidity is 28.6%, and it is slightly cooled by the outside air.

Subsequently, the air that has passed through the first sensible heat exchanger 27 is distributed into two by the distributor 31. In this configuration, one air amount flowing through the second exhaust path 17 and the other air amount flowing through the air supply path 13 are distributed substantially evenly (50%: 50%). When this one air passes through the humidifier 33 and is humidified, as indicated by a point D, the dry bulb temperature is 23.0 ° C./the wet bulb temperature is 21.7 ° C./the relative humidity is 90.0%.
In this configuration, the dry air that has passed through the desiccant rotor 25 and the first sensible heat exchanger 27 is distributed into two, and the distributed air is humidified and used to cool the other air. Here, since one of the air to be humidified is sufficiently dehumidified before being humidified, the outside air at points A and G is humidified as it is (for example, point K: dry bulb temperature 25.5 ° C./humidity). (Bulb temperature 24.0 ° C./relative humidity 90.0%), the wet bulb temperature after humidification can be reduced by 2.5 ° C. and wet bulb temperature 3.3 ° C.

Next, when the humidified one air and the other air are subjected to sensible heat exchange in the second sensible heat exchanger 35, the dry bulb temperature 24.3 ° C./wet bulb temperature 18. 1 ° C./relative humidity 55.6%. Here, although the relative humidity at point E appears to be 55.6%, which is higher than the relative humidity at 40.3% of outside air (point A), the absolute humidity at point A is 0.01423 kg / Since the absolute humidity at point E is reduced to 0.01055 kg / kg (DA) while it is kg (DA), air having a lower temperature and lower humidity than the outside air can be supplied indoors. .
As described above, in this configuration, the dry air that has passed through the desiccant rotor 25 and the first sensible heat exchanger 27 is distributed into two, and this distributed air is humidified and used to cool the other air. Therefore, the cooling efficiency of the other air can be increased by causing the second sensible heat exchanger 35 to perform sensible heat exchange between the one air having a low dry bulb temperature and a low wet bulb temperature and the other air. it can.
On the other hand, as shown by the point F, one air passing through the second sensible heat exchanger 35 becomes dry bulb temperature 34.6 ° C./wet bulb temperature 24.9 ° C./relative humidity 46.0% and is discharged outside the room. Is done.

  The outside air that has passed through the first sensible heat exchanger 27 rises to a dry bulb temperature of 43.4 ° C./wet bulb temperature of 26.2 ° C./relative humidity of 25.6% as indicated by point H, Heated by the heater 29, the dry bulb temperature shown at point I is 50.0 ° C./wet bulb temperature 27.7 ° C./relative humidity 18.4%. The heated air passes through the regeneration region 25C of the desiccant rotor 25, and as indicated by point J, the dry bulb temperature is 41.0 ° C./the wet bulb temperature is 27.6 ° C./the relative humidity is 36.6%. It is discharged outside.

As described above, according to the present embodiment, the air supply path 13 that sucks outside air and supplies the air into the room, the desiccant rotor 25 that dehumidifies the air flowing through the air supply path 13, and the dehumidified air as the outside air. The first sensible heat exchanger 27 that exchanges heat, the distribution unit 31 that distributes the sensible heat-exchanged air into two, the humidifier 33 that humidifies one of the distributed air, and the humidified air. The outside air can be dehumidified and cooled with a simple configuration including the second sensible heat exchanger 35 that performs sensible heat exchange with the other air and cools the other air. Further, by using the heater 29 that regenerates the desiccant rotor 25, the outside air can be continuously dehumidified and cooled. Furthermore, the power for operating the outside air introduction fan 21 by using exhaust heat generated by burning fuel such as gas or oil as a heating source of the heater 29 or heat obtained by natural energy such as solar heat or geothermal heat. As long as there is water supplied to the humidifier 33, air having a lower temperature and lower absolute humidity than the outside air can be obtained.
Further, in the second sensible heat exchanger 35, the other air supplied to the room and the humidified air are not mixed. For this reason, the germs mixed in the water for humidification are not mixed in the air supplied indoors, and clean and safe air can be supplied indoors.

As described above, in the outside air processing device 1 according to the present configuration, the amount of one air flowing through the second exhaust path 17 and the other air amount flowing through the air supply path 13 in the distribution unit 31 are substantially equal (50%). : 50%) is important.
Further, as shown in FIG. 2, the supply air temperature Ts remains flat at a value lower than 25 ° C. until the ratio of the supply air SA amount to the sucked outside air OA amount is 50%, but exceeds 50%. And rises rapidly. On the other hand, the exhaust temperature Td of one of the humidified air that contributes to the cooling of the supply air, contrary to the supply air temperature Ts, rapidly increases until the ratio of the supply air SA amount to the sucked outside air OA amount is 50%. Although it rises, if it exceeds 50%, it will remain flat around 35 ° C. For this reason, in this configuration, the point at which the exhaust gas temperature difference ΔT between the exhaust gas temperature Td and the supply air temperature Ts becomes maximum is around 50%, so that the exhaust gas temperature difference ΔT is maximized. One amount of air flowing through the second exhaust path 17 and the other amount of air flowing through the air supply path 13 are distributed.

In the first embodiment, the controller 43 controls the number of revolutions of the blower fan 39 based on the temperature of each path outlet of the second sensible heat exchanger 35 based on the above-described tendency.
The controller 43 obtains the maximum temperature difference ΔTmax of the exhaust gas temperature difference ΔT between the exhaust gas temperature Td and the supply air temperature Ts in the initial operation when the operation of the outside air processing device 1 is started.
First, the controller 43, in a state where the outside air introduction fan 21 is operating at a rotational speed predetermined blower fan 39 is operated at the reference rotational speed Rf, with measures the supply air temperature Ts ₁ by the temperature sensor 37A to measure the exhaust gas temperature Td ₁ by the temperature sensor 37B. Then, a temperature difference ΔT ₁ between the measured exhaust temperature Td ₁ and the supply air temperature Ts ₁ is calculated.
Next, when a predetermined time (5 minutes in the present embodiment) has elapsed since the previous measurement, the controller 43 causes the blower fan 39 to operate at a predetermined rotational speed Rf + ΔR that is larger than the reference rotational speed Rf by a predetermined rotational speed ΔR. Then, the supply air temperature Ts ₂ and the exhaust gas temperature Td ₂ at this time are measured. Then, the controller 43 calculates a temperature difference ΔT ₂ between the measured exhaust gas temperature Td ₂ and the supply air temperature Ts ₂ , and a difference (ΔT ₂ −ΔT) between the current temperature difference ΔT ₂ and the previous temperature difference ΔT _{1. It} is determined whether ₁ ) is positive, that is, greater than 0.

In this determination, when the difference between the current temperature difference ΔT ₂ and the previous temperature difference ΔT ₁ is greater than 0, the temperature difference ΔT has not reached the maximum temperature difference ΔTmax. After a predetermined time has elapsed since the previous measurement, the rotational speed of the blower fan 39 is operated at a predetermined rotational speed Rf + nΔR (n is 2, 3,... N) that is further increased by the rotational speed ΔR, and the temperature difference ΔT _n at this time is The process is continued until the difference from the previously calculated temperature difference ΔT _n−1 is minus, that is, smaller than 0.
On the other hand, when the difference between the current temperature difference ΔT _n and the previously calculated temperature difference ΔT _n−1 is negative, that is, smaller than 0, the temperature difference ΔT has passed the maximum temperature difference ΔTmax. Therefore, the temperature difference ΔT _n at this time is set as the maximum temperature difference ΔTmax, and the setting operation for the maximum temperature difference is completed.

Next, the rotation speed of the blower fan 39 is set using the set maximum temperature difference ΔTmax. First, the controller 43, in a state where the outside air introduction fan 21 is operating at a rotational speed predetermined blower fan 39 is operated at the reference rotational speed Rf, with measures the supply air temperature Ts ₁ by the temperature sensor 37A to measure the exhaust gas temperature Td ₁ by the temperature sensor 37B. Then, a temperature difference ΔT ₁ between the measured exhaust temperature Td ₁ and the supply air temperature Ts ₁ is calculated.
Then, the controller 43 calculates an additional rotation number ΔR ₁ calculated by multiplying the difference (ΔTmax−ΔT ₁ ) between the set maximum temperature difference ΔTmax and the calculated temperature difference ΔT ₁ by a predetermined coefficient K, The blower fan 39 is operated at a rotational speed Rf ₁ (Rf + ΔR ₁ ) obtained by adding the additional rotational speed ΔR ₁ to the reference rotational speed Rf.
Subsequently, when a predetermined time (in this embodiment, 5 minutes) elapses from the previous measurement, the supply air temperature Ts ₂ and the exhaust gas temperature Td ₂ at this time are measured, and the measured exhaust gas temperature Td ₂ and supply air temperature Ts are measured. calculating the temperature difference [Delta] T ₂ and _2.
Then, the controller 43 adds a predetermined coefficient K to the difference (ΔTmax−ΔT ₂ ) between the set maximum temperature difference ΔTmax and the calculated temperature difference ΔT ₂ , the current temperature difference ΔT _2, and the previous temperature difference ΔT ₁ . difference (ΔT ₂ -ΔT ₁₎ plus and minus signs and calculates the sum rotational speed [Delta] R ₂ calculated by multiplying the number of revolutions _Rf 2 obtained by adding the addition rotational speed [Delta] R ₂ to the previous rotational speed Rf ₁ (Rf ₁ + ΔR ₂ ), the blower fan 39 is operated. In this case, if the difference (ΔT _n −ΔT _n−1 ) between the current temperature difference ΔT _n and the previous temperature difference ΔT _n−1 is negative, the calculated additional rotational speed ΔR _n is used as the previous rotational speed Rf. Subtract from _n-1 . Also, when [Delta] T _n calculated is larger than the .DELTA.Tmax that is set, it sets the [Delta] T _n as a new maximum temperature difference .DELTA.Tmax.
By performing such control at predetermined time (5 minutes) intervals, the rotational speed (air flow rate) of the blower fan 39 can be finely adjusted, and the amount of one air flowing through the second exhaust path 17 (exhaust air EA). ) And the other amount of air flowing through the air supply path 13 (supply air SA) can be held substantially evenly (50%: 50%). As a result, in the second sensible heat exchanger 35, The cooling capacity can be maximized.

  According to the first embodiment, the blower fan 39 provided at the discharge port 13B of the air supply path 13 and the exhaust temperature Td and the supply air temperature Ts, which are outlet temperatures of the second sensible heat exchanger 35, are used. And the controller 43 that controls the amount of air blown by the blower fan 39, the distribution amount of air flowing through each path of the second sensible heat exchanger 35 can be simplified without actually measuring the amount of air supplied to the room. Can be adjusted.

  In addition, according to the first embodiment, since the amount of one air flowing through the second exhaust path 17 and the amount of the other air flowing through the air supply path 13 are set substantially evenly, the other air is The second sensible heat exchanger 35 can be cooled to the maximum.

[Second Embodiment]
FIG. 4 is a schematic diagram of the outside air processing apparatus 100 according to the second embodiment. The same components as those in the outside air processing device 1 according to the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
The outside air processing device 100 has a distribution ratio by the distribution unit 31, that is, one air amount flowing through the second exhaust path 17 (flow path 35A) and the other air amount flowing through the air supply path 13 (flow path 35A). A configuration for controlling the ratio is provided. Specifically, the outside air processing apparatus 100 is arranged on the upstream side of the humidifier 33, and the blower fan 113 disposed in the opening 110 that communicates the second exhaust path 17 and the air supply path 13, and the rotation of the blower fan 113. An inverter 141 for setting the number and a controller (control means) 143 for controlling the rotation speed of the blower fan 113 via the inverter 141 are provided. The blower fan 113 and the controller 143 constitute a distribution unit including the distribution unit 31. Further, the blower fan 113 is configured to be able to change the blowing direction between the second exhaust path 17 and the air supply path 13 according to the rotation direction. The temperature sensors 37A and 37B described above are connected to the controller 143, and the controller 143 controls the rotational speed of the blower fan 113 based on the measured temperatures of the temperature sensors 37A and 37B.

Next, the air distribution control operation in this embodiment will be described.
Also in the second embodiment, the controller 143 sets the maximum temperature difference ΔTmax of the exhaust gas temperature difference ΔT between the exhaust gas temperature Td and the supply air temperature Ts at the initial operation time when the operation of the outside air processing device 100 is started. Ask. Since the calculation method of the maximum temperature difference ΔTmax of the exhaust air temperature difference ΔT is the same as that in the first embodiment, the description thereof is omitted.

Next, the rotation speed of the blower fan 113 is set using the set maximum temperature difference ΔTmax. First, the controller 143 causes the air to flow from the second exhaust path 17 to the air supply path 13 at the reference rotation speed Rf while the outside air introduction fan 21 is operating at a predetermined rotation speed. rotate the, with measures the supply air temperature Ts ₁ by the temperature sensor 37A, which measures the exhaust gas temperature Td ₁ by the temperature sensor 37B. Then, a temperature difference ΔT ₁ between the measured exhaust temperature Td ₁ and the supply air temperature Ts ₁ is calculated.
Then, the controller 143 calculates an additional rotation number ΔR ₁ calculated by multiplying a difference (ΔTmax−ΔT ₁ ) between the set maximum temperature difference ΔTmax and the calculated temperature difference ΔT ₁ by a predetermined coefficient K, The blower fan 113 is operated at a rotational speed Rf ₁ (Rf + ΔR ₁ ) obtained by adding the additional rotational speed ΔR ₁ to the reference rotational speed Rf.
Subsequently, when a predetermined time (in this embodiment, 5 minutes) elapses from the previous measurement, the supply air temperature Ts ₂ and the exhaust gas temperature Td ₂ at this time are measured, and the measured exhaust gas temperature Td ₂ and supply air temperature Ts are measured. calculating the temperature difference [Delta] T ₂ and _2.
Then, the controller 143 adds a predetermined coefficient K to the difference (ΔTmax−ΔT ₂ ) between the set maximum temperature difference ΔTmax and the calculated temperature difference ΔT ₂ , the current temperature difference ΔT _2, and the previous temperature difference ΔT ₁ . difference (ΔT ₂ -ΔT ₁₎ plus and minus signs and calculates the sum rotational speed [Delta] R ₂ calculated by multiplying the number of revolutions _Rf 2 obtained by adding the addition rotational speed [Delta] R ₂ to the previous rotational speed Rf ₁ (Rf ₁ + ΔR ₂ ), the blower fan 113 is operated. In this case, if the difference (ΔT _n −ΔT _n−1 ) between the current temperature difference ΔT _n and the previous temperature difference ΔT _n−1 is negative, the calculated additional rotational speed ΔR _n is used as the previous rotational speed Rf. Subtract from _n-1 . In the middle of this control, when the rotation speed Rf _n becomes smaller than 0, the controller 143 rotates the rotation direction and the rotation speed of the blower fan 113 so that the air flows from the air supply path 13 to the second exhaust path 17. To control. Also, when [Delta] T _n calculated is larger than the .DELTA.Tmax that is set, it sets the [Delta] T _n as a new maximum temperature difference .DELTA.Tmax.
By performing such control at predetermined time (5 minutes) intervals, the rotational direction and the rotational speed (air flow rate) of the blower fan 113 can be finely adjusted, and the amount of one air flowing through the second exhaust path 17 The amount of distribution between the (exhaust air EA) and the other amount of air flowing through the air supply path 13 (supply air SA) can be kept substantially equal (50%: 50%), and thus the second sensible heat exchanger. The cooling capacity at 35 can be maximized.

  According to the second embodiment, on the upstream side of the humidifier 33, the blower fan 113 disposed in the opening 110 communicating the second exhaust path 17 and the air supply path 13, and the second sensible heat exchanger 35 Since the controller 143 for controlling the rotational speed of the blower fan 113 is provided based on the exhaust temperature Td and the supply air temperature Ts, which are outlet temperatures, it is possible to perform the first measurement without measuring the amount of air actually supplied into the room. 2 The distribution amount of the air flowing through each path of the sensible heat exchanger 35 can be easily adjusted.

[Third embodiment]
FIG. 5 is a schematic diagram of an outside air processing apparatus 200 according to the third embodiment. The same components as those in the outside air processing device 1 according to the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
The outside air processing apparatus 200 has a distribution ratio by the distribution unit 31, that is, one air amount flowing through the second exhaust path 17 (flow path 35A) and the other air amount flowing through the air supply path 13 (flow path 35A). A configuration for controlling the ratio is provided. Specifically, the outside air processing apparatus 200 includes an exhaust damper 210 provided in the second exhaust path 17, an air supply damper 211 provided in the air supply path 13, the exhaust damper 210 and the air supply A damper operating motor 213 that operates the damper 211, an inverter 241 that sets the rotational speed of the damper operating motor 213, and a controller (control means) 243 that controls the rotational speed of the damper operating motor 213 via the inverter 241. Prepare.
In this embodiment, the exhaust damper 210 and the air supply damper 211 are operated by a single damper operating motor 213, and the exhaust damper 210 and the air supply damper 211 operate in reverse. That is, when the exhaust damper 210 operates in the opening direction, the air supply damper 211 operates in the closing direction, and the distribution ratio of the air flowing through the second exhaust path 17 and the air supply path 13 is controlled. Is done.

Next, the air distribution control operation in this embodiment will be described.
The controller 243 obtains the maximum temperature difference ΔTmax of the exhaust gas supply temperature difference ΔT between the exhaust temperature Td and the supply air temperature Ts in the initial operation when the operation of the outside air processing device 1 is started.
First, the controller 243 sets the exhaust damper 210 and the air supply damper 211 to the reference opening position Dv while the outside air introduction fan 21 is operating at a predetermined rotational speed, and supplies the temperature by the temperature sensor 37A. with measuring the air temperature Ts _1, to measure the exhaust gas temperature Td ₁ by the temperature sensor 37B. Then, a temperature difference ΔT ₁ between the measured exhaust temperature Td ₁ and the supply air temperature Ts ₁ is calculated. In this case, the reference opening position Dv of the exhaust damper 210 and the air supply damper 211 refers to a position set to an opening of 70% with respect to the opening areas of the second exhaust path 17 and the air supply path 13. .
Next, when a predetermined time (5 minutes in the present embodiment) elapses from the previous measurement, the controller 243 operates the damper operating motor 213 so that the air supply damper 211 has a predetermined opening (for example, a reference opening position Dv). 5%) a predetermined opening Dv + ΔD opened by ΔD, and the exhaust damper 210 is set to a predetermined opening Dv−ΔD closed by a predetermined opening (5%) ΔD from the reference opening position Dv. The supply air temperature Ts ₂ and the exhaust gas temperature Td ₂ are respectively measured. Then, the controller 243 calculates a temperature difference ΔT ₂ between the measured exhaust temperature Td ₂ and the supply air temperature Ts ₂ , and a difference (ΔT ₂ −ΔT) between the current temperature difference ΔT ₂ and the previous temperature difference ΔT _{1. It} is determined whether ₁ ) is positive, that is, greater than 0.

In this determination, when the difference between the current temperature difference ΔT ₂ and the previous temperature difference ΔT ₁ is greater than 0, the temperature difference ΔT has not reached the maximum temperature difference ΔTmax. After a predetermined time has elapsed since the previous measurement, the opening degree of the air supply damper 211 is further set to a predetermined opening degree Dv + nΔD (n is 2, 3,... N) opened by a predetermined opening degree ΔD, and the exhaust damper The opening degree 210 is further set to a predetermined opening degree Dv−nΔD (n is 2, 3,... N) blocked by a predetermined opening degree ΔD, and the temperature difference ΔT _n at this time and the temperature calculated the previous time Continue until the difference from the difference ΔT _n−1 is negative, that is, less than 0.
On the other hand, when the difference between the current temperature difference ΔT _n and the previously calculated temperature difference ΔT _n−1 is negative, that is, smaller than 0, the temperature difference ΔT has passed the maximum temperature difference ΔTmax. Therefore, the temperature difference ΔT _n at this time is set as the maximum temperature difference ΔTmax, and the setting operation for the maximum temperature difference is completed.

Next, the opening degree of the supply damper 211 and the exhaust damper 210 is set using the set maximum temperature difference ΔTmax. Here, the opening degree of the air supply damper 211 will be described.
First, the controller 243 sets the supply damper 211 to the reference opening position Dv while the outside air introduction fan 21 is operating at a predetermined rotation speed, and sets the supply air temperature Ts ₁ by the temperature sensor 37A. In addition to the measurement, the exhaust gas temperature Td ₁ is measured by the temperature sensor 37B. Then, a temperature difference ΔT ₁ between the measured exhaust temperature Td ₁ and the supply air temperature Ts ₁ is calculated.
The controller 243 calculates a damper operation amount ΔD ₁ calculated by multiplying a difference (ΔTmax−ΔT ₁ ) between the set maximum temperature difference ΔTmax and the calculated temperature difference ΔT ₁ by a predetermined coefficient K, and this damper operation. An amount Dv ₁ (Dv + ΔD ₁ ) is obtained by adding the amount ΔD ₁ to the reference opening position Dv of the air supply damper 211.
Subsequently, when a predetermined time (in this embodiment, 5 minutes) elapses from the previous measurement, the supply air temperature Ts ₂ and the exhaust gas temperature Td ₂ at this time are measured, and the measured exhaust gas temperature Td ₂ and supply air temperature Ts are measured. calculating the temperature difference [Delta] T ₂ and _2.
Then, the controller 243 adds a predetermined coefficient K to the difference (ΔTmax−ΔT ₂ ) between the set maximum temperature difference ΔTmax and the calculated temperature difference ΔT ₂ , the current temperature difference ΔT _2, and the previous temperature difference ΔT ₁ . A damper operation amount ΔD ₂ calculated by multiplying the difference (ΔT ₂ −ΔT ₁ ) by a positive / negative sign is calculated, and the damper operation amount ΔD ₂ is added to the previous opening Dv ₁ to obtain an opening Dv ₂ (Dv _The damper operating motor 213 is operated so that ₁ + ΔD ₂ ). In this case, if the difference (ΔT _n −ΔT _n−1 ) between the current temperature difference ΔT _n and the previous temperature difference ΔT _n−1 is negative, the calculated damper operation amount ΔD _n is used as the previous opening Dv. Subtract from _n-1 . Also, when [Delta] T _n calculated is larger than the .DELTA.Tmax that is set, it sets the [Delta] T _n as a new maximum temperature difference .DELTA.Tmax.
By performing such control at predetermined time intervals (5 minutes), the opening degree (air flow rate) of the supply damper 211 and the exhaust damper 210 can be finely adjusted and flows through the second exhaust path 17. The distribution amount of one air amount (exhaust EA) and the other air amount (supply air SA) flowing through the air supply path 13 can be kept substantially equal (50%: 50%). The cooling capacity of the sensible heat exchanger 35 can be maximized.

  According to the third embodiment, the exhaust damper 210 provided in the second exhaust path 17, the supply damper 211 provided in the supply path 13, and the outlet temperatures of the second sensible heat exchanger 35. Since the controller 243 for controlling the opening degree of the exhaust damper 210 and the supply damper 211 is provided based on the exhaust temperature Td and the supply air temperature Ts, the amount of air actually supplied into the room is not measured. In both cases, the distribution amount of the air flowing through each path of the second sensible heat exchanger 35 can be easily adjusted.

[Fourth embodiment]
FIG. 6 is a schematic diagram of an outside air processing device 300 according to the fourth embodiment. The same components as those in the outside air processing device 1 according to the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
The outside air processing apparatus 300 has a distribution ratio by the distribution unit 31, that is, one air amount flowing through the second exhaust path 17 (flow path 35A) and the other air amount flowing through the air supply path 13 (flow path 35A). A configuration for controlling the ratio is provided. Specifically, the outside air processing apparatus 300 includes a shielding plate 310 that is provided in the second exhaust path 17 and the air supply path 13 and shields the paths, and the shielding plate 310 communicates with the second exhaust path 17. An exhaust side passage window 311 and an air supply side passage window 313 communicating with the air supply path 13 are provided in parallel. The opening area of each of these passage windows is set to an area in which the amount of air flowing through the air supply path 13 is 45 to 50% of the amount of outside air sucked through a test in advance.
In this embodiment, the area of the passage window cannot be changed following the change in the outside air temperature, but the air that has been dehumidified and cooled can be supplied indoors with a simple configuration.

As mentioned above, although this invention was demonstrated based on one Embodiment of this invention, this invention is not limited to this. For example, in the above-described embodiment, the first exhaust path 15 is configured to suck outside air as regeneration air, but may be configured to suck indoor air instead. In summer, since the temperature of the cooled indoor air is lower than the outside air temperature, the first sensible heat exchanger 27 performs sensible heat exchange between the room air and the dehumidified air. The temperature of the dehumidified air can be further reduced, and as a result, the supply air temperature can be reduced.
In the above-described embodiment, the desiccant rotor is employed as the dehumidifying means, but other configurations may be employed as long as the sucked outside air can be dehumidified.
In the above-described embodiment, the orthogonal sensible heat exchanger is adopted as the first sensible heat exchange means and the second sensible heat exchange means, but a sensible heat rotor may be adopted instead. .
Further, in the above-described embodiment, the heater 29 that is heated with warm water is used as the heating means, but it may be heated with electricity, steam, or the like.

1, 100, 200, 300 Outside air processing device 13 Air supply path 13A Suction port 13B Discharge port (air supply port)
15 First exhaust path 17 Second exhaust path (path through which one air flows)
17A Discharge port (exhaust port)
21 Outside air introduction fan 23 Regenerative air introduction fan 25 Desiccant rotor (dehumidification means)
27 1st sensible heat exchanger (1st sensible heat exchange means)
29 Heater 31 Distributor (Distributor)
33 Humidifier (humidifying means)
35 Second sensible heat exchanger (second sensible heat exchange means)
37A Temperature sensor 37B Temperature sensor 39 Blower fan 41, 141, 241, 341 Inverter 43, 143, 243, 343 Controller (control means)
DESCRIPTION OF SYMBOLS 110 Opening 113 Blower fan 210 Exhaust damper 211 Supply damper 213 Damper operating motor 310 Shielding plate 311 Exhaust side passage window 313 Supply side passage window

Claims (5)

  An air supply path for sucking outside air and supplying it into the room; dehumidifying means for dehumidifying the air flowing through the air supply path; first sensible heat exchange means for sensible heat exchange of the dehumidified air with the outside air or room air; Distributing means for distributing the sensible heat-exchanged air into two, humidifying means for humidifying one of the distributed air, and sensible heat exchange between the humidified air and the other distributed air And a second sensible heat exchange means for cooling the air, and the air cooled by the second sensible heat exchange means is supplied into the room.   The distribution means is based on a blower fan provided in at least one of an air supply port of the air supply path and an exhaust port for discharging the one air to the outside, and each outlet temperature of the second sensible heat exchanger. The outside air processing apparatus according to claim 1, further comprising a control unit that controls an air blowing amount of the blower fan.   The distribution means is arranged at an upstream side of the humidification means, and a blower fan disposed in an opening that communicates the path through which the one air flows and the air supply path, and each outlet temperature of the second sensible heat exchanger. The outside air processing apparatus according to claim 1, further comprising: a control unit that controls a blowing amount of the blowing fan.   The distribution means, on the upstream side of the humidification means, based on dampers respectively provided in the path through which the one air flows and the air supply path, and the outlet temperatures of the second sensible heat exchanger, The outside air processing apparatus according to claim 1, further comprising a control unit that controls the opening degree of the damper.   The outside air processing apparatus according to any one of claims 1 to 4, wherein the distribution unit sets a distribution amount of the one air and the other air substantially equally.

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