JP2012145289A - Air conditioning system using snow - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air conditioning system using snow capable of drastically reducing operational energy when a cooling load in an intermediate period or the summer season is large by preventing the insufficient humidification of air feeding while effectively performing the outer air cooling using outer air during the intermediate period or the winter season.SOLUTION: A mechanical chamber 2 has: an outer air path 4 communicating with an outer air introduction port 3; a return air path 7 communicating with an air-conditioning objective chamber 6 via an return air intake 5; a mixing part 9 which makes the outer air path 4 divisionally communicate with the return air path 7; and an air-feeding path 11 which divisionally communicates with the mixing part 9 and communicates with the air-conditioning objective chamber 6 via an air-feeding wind path 10. A snow storage part 30 in which snow is deposited is disposed outdoors, a first step humidifier 12 which insulates and humidifies return air RA is disposed at the return air path 7, a cooling coil 15, a second step humidifier 14 which insulates and humidifies mixed air MA and an air-feeding fan 19 are disposed at the air-feeding path 11, an outer air fan 23 is disposed at the outer air path 4, an exhaust fan 27 is disposed at the air-conditioning objective chamber 6, outer air OA and snow-cooled outer air SOA are switched and guided to the outer air path 4, and the cold heat of snow-cooled water 36 is guided to the cooling coil 15.

Description

  The present invention relates to an air conditioning system using snow. In particular, the present invention relates to an air-conditioning system using snow that can be applied when a heat load in a room to be air-conditioned is generated throughout the year, there is almost no latent heat load of a person or the like, and the indoor humidity allowable range is severe.

  In Internet data centers, computer rooms, etc., air conditioners (coolers) are provided year-round to provide an environment in which equipment operates normally by removing heat generated from equipment and maintaining a predetermined humidity. However, since the devices such as the Internet data center and the computer room generate a lot of heat, the return air temperature to the air conditioner is high, so the return air is A large amount of energy (electric power) is consumed throughout the year to cool and supply air to the set temperature.

  In general office buildings where there are no computers or server racks that generate a large amount of heat in the air-conditioned room, the temperature of the return air is reduced by using outside air, and the energy consumed by the refrigerator in the cooling coil is reduced. There is an outside air-conditioning system that is configured as described above, for example, Patent Document 1 by the present applicant. The outside-air-use air conditioning system disclosed in Patent Document 1 includes a first air passage that communicates with the outside air system and incorporates outside air OA into the air conditioner, and a return air RA that is introduced into the air conditioning target room via the return air system. A second flow passage that humidifies the air flow by a humidifier, a third flow passage that communicates with the first flow passage and the second flow passage and communicates with the air-conditioning target chamber through an air supply system. The cooling means connected to is provided in the first flow path and the second flow path.

JP 2007-064556 A

  According to Patent Document 1, energy saving can be achieved by using the outside air OA having a temperature lower than room temperature in the intermediate period (spring or autumn) and winter. However, since only the return air RA is humidified, there is a problem that the cooling effect by humidification cannot be utilized to the maximum, and there are computers and server racks that generate a large amount of heat in the air-conditioned room. When applying to a place where cooling with a large amount of outside air is necessary, if the ratio of taking in the outside air OA is increased to a predetermined value or more, the humidity of the supply air SA decreases, and therefore, the intake of the outside air OA is restricted. If there is a problem and the extraneous air cooling heat cannot be utilized to the maximum extent, and further cooling of the supply air SA is necessary, it is necessary to cool the return air RA and the outside air OA with the cooling means connected to the refrigerator. However, there has been a case where the operating energy (electric power) of the refrigerator is increased.

  In view of the above situation, the present invention has a device that generates a large amount of heat indoors and has a narrow indoor temperature and humidity tolerance range and is strictly controlled in the intermediate period and winter season (for example, in the case of a computer room, the relative humidity range is relatively In some cases, the humidity is controlled at ± 10%.) When performing outdoor air cooling using the outside air in the air-conditioned room, it is possible to prevent insufficient humidification with respect to the supply air by mixing a large amount of outside air. In order to make the most of the cooling effect, and in the intermediate and summer seasons, when the cooling load is large and the cooling capacity is insufficient only with the outside air mixing cooling, the snow cooling outside air from the snow storage section is mixed with the return air. And / or use the cold heat of the snow effectively by cooling the supply air SA by the cooling means using the cold heat of the snow cold water from the snow storage unit, and minimize the use of the cold heat supply device such as a refrigerator. Driving to the limit Significant reduction in Nerugi was so attained, in which none for the purpose of providing an air conditioning system using the snow.

In the air conditioning system using snow according to claim 1 of the present invention, the machine room communicates with the outside air passage which is the first flow passage communicating with the outside air inlet and the air conditioning target room via the return air intake. A return air passage that is a second flow passage, and the outside air passage and the return air passage communicated with the outside air passage and the return air passage through a mixing portion that is partitioned, and are separated from the mixing portion and an air supply air passage An air supply passage that is a third flow passage communicating with the air-conditioned room via
Outside the room, there is a snow storage section that accumulates snow,
The return air passage is provided with first-stage humidification means for adiabatic humidification of the return air from the return air intake with water, and the air supply passage is provided with the outside air from the outside air inlet and the return air intake. A second stage humidifying means for adiabatically humidifying the air-fuel mixture mixed with the return air, and a cold heat supply means for supplying a cooling medium capable of supplying the cold heat of the snow cold water from the snow storage section to the circulation channel. The cooling means is a cooling coil, and the air supply means for supplying the air-fuel mixture in the air supply passage to the air-conditioning target room through the air supply passage, and the temperature and humidity state of the air-fuel mixture is provided in the outside air passage An outside air supply means capable of adjusting the air volume for conveying outside air for adjusting the air volume is installed, and in the air conditioning target room, an exhaust means for exhausting a part of the indoor air is installed, and the outside air introduction port is provided. Is the outside air that can be switched between the outside air and the snow-cooled outside air cooled by the snow in the snow storage tank. Those of the air conditioning system, using the snow, characterized in that they have installed switch means.

  Further, in the air conditioning system using snow according to claim 2 of the present invention, the cold heat supply means connected to the cooling means cools the cold cold water taken out from the snow storage unit to the cold medium. The heat generated by the refrigerator and the heat generated by the refrigerator can be appropriately transferred by the heat exchanger.

  In the air conditioning system using snow according to claim 3 of the present invention, the air volume of the outside air supply means is measured according to the absolute humidity calculated by measuring the humidification quantity of the first stage humidification means at the return air intake. In accordance with the enthalpy measured and calculated in the mixing section, the humidification amount of the second-stage humidifying means is measured in the supply air passage, and the control device controls each according to the calculated absolute humidity It is characterized by that.

  Further, in the air conditioning system using snow according to claim 4 of the present invention, the air supply system is located on the same enthalpy line as the enthalpy of the supply air set temperature / humidity point supplied to the air conditioning target room through the supply air passage. Set the minimum absolute humidity point at the entrance of the second-stage humidifier that can humidify to the set absolute humidity of the air supplied to the road as a boundary point, and connect the return air set temperature / humidity point and the boundary point to the boundary point The area extending to the left side of the boundary point on the T-Xa air diagram is divided in half by the straight line extended to the side, and the minimum absolute humidity point at the inlet of the first stage humidifier that can humidify to the set absolute humidity of the supply and return air is dried. By dividing the right region of the boundary point on the T-Xa air diagram into two parts by the curve connected at the boundary point right region of the T-Xa air diagram for each sphere temperature, at least on the T-Xa air diagram The state of the outside air obtained by measuring the temperature and humidity divided into four areas with the boundary point at the top There characterized in that it comprises a control unit for switching the operation mode either included in any of the four regions.

  In the air conditioning system using snow according to claim 5 of the present invention, the outside air state point is included in an upper region of a straight line connecting the return air set temperature / humidity point and the boundary point and extending to the boundary point side. In this case, the first-stage humidifying means is turned OFF, the air volume of the outside air feeding means is controlled based on the enthalpy obtained from the air temperature measurement value of the mixing unit, and the air temperature and humidity measurement value in the supply air passage is obtained. And a control device for controlling the humidification amount of the second-stage humidification means based on the absolute humidity.

  Further, in the air conditioning system using snow according to claim 6 of the present invention, the state point of the outside air is included in a straight lower region extending from the return air set temperature / humidity point and the boundary point to the boundary point side. In this case, the humidification amount of the first-stage humidification means is controlled based on the absolute humidity obtained from the return temperature humidity measurement value at the return air inlet, and the outside air is sent based on the enthalpy obtained from the air temperature measurement value of the mixing section. A control device is provided that controls the air volume of the supply means and controls the humidification amount of the second-stage humidification means based on the absolute humidity obtained from the measured value of the supplied air temperature and humidity in the supply air passage.

  In the air conditioning system using snow according to claim 7 of the present invention, the minimum absolute humidity point at the inlet of the second stage humidifying means capable of humidifying to the set absolute humidity of the supply air and the return air is set to T− for each dry bulb temperature. When the outside air condition point is included in the upper area of the curve connected to the right area of the boundary point on the Xa air diagram, the second stage is based on the absolute humidity obtained from the measured air temperature and humidity in the air supply path. A controller for controlling the amount of humidification of the humidifying means, turning off the first-stage humidifying means, and controlling the amount of heat supplied by the cooling medium and supplied to the cooling means based on the supply air temperature in the supply air passage It is characterized by providing.

  In the air conditioning system using snow according to claim 8 of the present invention, the minimum absolute humidity point at the inlet of the second stage humidifying means capable of humidifying to the set absolute humidity of the supply air and the return air is set to T− for each dry bulb temperature. When the outside air state point is included in the lower area of the curve connected to the right side of the boundary point on the Xa air diagram, one step is based on the absolute humidity obtained from the measured return air temperature and humidity at the return air inlet. Control the humidification amount of the eye humidification means, control the air volume of the outside air supply means based on the enthalpy determined by the air temperature measurement value of the mixing section, and obtain the absolute value determined by the air temperature humidity measurement value in the supply air passage A control device is provided that controls the amount of humidification of the second-stage humidifying unit based on humidity and controls the amount of heat supplied by the cooling medium and supplied to the cooling unit based on the supply air temperature in the supply air passage. It is characterized by.

  In the air conditioning system using snow according to claim 9 of the present invention, it is judged whether or not the cold heat of the snow cold water taken out from the snow storage part can be used, and flows through the circulation flow path of the cold heat supply means. It has a snow cold water utilization operation command part which controls supply of cold heat which snow cold water has to the cold heat medium.

  In the air conditioning system using snow according to claim 10 of the present invention, if the outside air state point does not apply to any of the cases of claims 5 to 8 on the T-Xa air diagram, First cooling to supply the outside air passage, second cooling to supply the cold heat of the snow cooling water to the cooling medium flowing through the circulation flow path of the cold heat supply means, and circulation of the cold heat supply means when the cold heat is insufficient It has a command unit corresponding to a maximum load time for performing the third cooling for supplying the cooling heat generated by the refrigerator to the cooling medium flowing through the flow path.

  According to the outside-air-use air conditioning system of the present invention, when performing outside-air cooling using outside air in an intermediate period or winter season, a first-stage humidifier that humidifies return air and a mixture of outside air and return air are humidified 2 By providing the stage humidifier, it is possible to prevent the supply air from being insufficiently humidified, to use the cooling effect by humidification, and to maximize the cooling effect by using outside air. Furthermore, in the intermediate period and summer, when the cooling load is large and the cooling capacity is insufficient only with the outside air mixed cooling, the snow cooling outside air from the snow storage section is mixed with the return air and / or from the snow storage section. By cooling the supply air with the cooling means using the cold energy of snow cold water, the cold energy of the snow can be effectively utilized, and the use of a cold heat supply device such as a refrigerator can be minimized to greatly reduce the operating energy. An excellent effect can be achieved.

It is a side view showing a schematic structure of an air-conditioning system using snow of the present invention. It is a block diagram which shows an example of the control apparatus with which the air conditioning system using the snow of FIG. 1 is equipped, and the structure of the operation command part of the area | region of the operation mode 1, and the operation command part of the area | region of the operation mode 2. FIG. It is a block diagram which shows the state provided with the operation command part of the area | region of the operation mode 1 by the control apparatus of FIG. 2, and the operation command part of the area | region of the operation mode 2 in the air conditioning system using snow. 4 is a block diagram illustrating a configuration of an operation command unit in an operation mode 3 region. FIG. FIG. 7 is a block diagram illustrating a state in which an operation command unit in the operation mode 3 region of FIG. 4 and an operation command unit in the operation mode 4 region of FIG. 6 are provided in an air conditioning system using snow. 6 is a block diagram showing a configuration of an operation command unit in a region of an operation mode 4. FIG. 6 is a block diagram showing a part of the configuration of an operation command unit in the region of an operation mode 5. FIG. It is the block diagram which took out and showed the part which cannot be written in FIG. 7a. It is a block diagram which shows the state provided with the operation command part of the area | region of the operation mode 5 of FIG. 7a, FIG. 7b in the air conditioning system using snow. It is a block diagram which shows the structure of a snow cold water utilization operation instruction | indication part. It is a block diagram which shows the state provided with the snow cold water utilization operation instruction | indication part of FIG. 9 in the air conditioning system using snow. FIG. 2 is an air diagram showing a relationship among dry bulb temperature, absolute humidity, isoenthalpy, and saturation curve in the air conditioning system using snow of FIG. 1. It is a flowchart which shows the calculation method of the operation mode in the air conditioning system using the snow of FIG.

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

  FIG. 1 shows an embodiment of an air-conditioning system using snow. The air-conditioning system 1 using snow communicates with the inside of the machine room 2 to the outside air inlet 3 which is an outside air louver or the like. The outside air passage 4 that is a road, the return air passage 7 that is the second flow passage communicating with the air-conditioning target chamber 6 via the return air inlet 5, the outside air passage 4 and the return air passage 7 are communicated with the outside air OA and returned. In order to mix the air RA into the air-fuel mixture MA, the mixing section 9 in which the outside air side and the air-conditioning target room are partitioned by the partition wall 8, and the air-fuel mixture MA in the mixing section 9 are introduced to supply the air flow path 10. And a supply section 11 which is a third flow path partitioned by a mixing section 9 and a casing for supplying the supply air SA to the air-conditioning target chamber 6.

  The return air passage 7 is provided with a first-stage humidifier 12 (first-stage humidification means) for humidifying the return air RA from the return air intake 5 into the return air RA ′. For example, a part of the machine room 2 is partitioned by a heat insulating panel 13 or the like, the return air intake 5 is provided at one end, and the other end is provided with a return air filter 7 ′ as a return air passage 7. 5 and the return air filter 7 'are provided with a first stage humidifier 12 with a drain pan attached to the lower part. The first stage humidifier 12 is a water humidifier, and the return air before and after humidification changes adiabatically. V1 is a first stage adjustment valve for adjusting the spray amount of the first stage humidifier 12. The return air filter 7 'may not be provided.

  The air supply passage 11 is an air conditioner having a casing, and is introduced into the air supply passage 11 from the outside air OA from the outside air inlet 3 and the return air inlet 5 and is humidified by the first-stage humidifier 12. A second-stage humidifier 14 (second-stage humidifying means) for humidifying the air-fuel mixture MA mixed with the returned air RA ′ is provided with a drain pan attached to the lower part. The second-stage humidifier 14 is a water humidifier, and the air-fuel mixture MA before and after humidification changes adiabatically. V2 is a second stage adjustment valve for adjusting the spray amount of the second stage humidifier 14. The first-stage and second-stage humidifiers 12 and 14 are so-called water humidifiers such as water sprays, vaporizer humidifiers, ultrasonic humidifiers, etc. that do not heat the humidified water and become adiabatic changes before and after treatment air humidification. Can be used.

  A cooling coil 15 constituting cooling means is provided downstream of the second-stage humidifier 14 in the air supply passage 11. The cooling by the cooling coil 15 shown in FIG. 1 is for performing cooling when the supply air SA does not reach the target temperature in outside air intake / water spray humidification. The cooling heat supply means for supplying a cooling medium to the cooling coil 15 is provided with a circulation channel 16 for circulating the cooling medium by a circulation pump P3. The circulation channel 16 is provided with a secondary side of the snow cold water heat exchanger 38, a secondary side of the refrigerator generated cold heat heat exchanger 17, and a valve V3 for controlling the flow rate of the cooling medium in the middle thereof. Yes. Between the primary side of the refrigerator-generated cold heat exchanger 17 and the refrigerator R2, a cold water circulation passage 18 for circulating cold water by a cold water pump P4 is provided. Further, the chilled water circulation channel 18 is provided with a bypass pipe that can bypass part or all of the chilled water conveyed by the chilled water pump P4 from the refrigerator-generated cold heat exchanger 17 and a control valve V6 in the bypass pipe. Yes.

  An air supply fan 19 (air supply means) for supplying the air supply SA of the air supply passage 11 to the air supply air passage 10 is provided downstream of the cooling coil 15 of the air supply passage 11. An air supply air passage 10 in FIG. 1 shows a case where the air supply SA from the air supply passage 11 is supplied to the air-conditioning target chamber 6 through a space 20 below the floor. This is often seen in computer rooms, data centers, and the like, and the air in the air-conditioned room 6 is heated using the flow of air that is heated and raised by a large amount of heat generated by the equipment 21 such as server racks and computers. By quickly guiding the returned air to the return air intake 5 and the exhaust means, the air is blown out from the floor so that the air can be effectively cooled without stagnation in the room, and the return air is returned on the ceiling side. I try to take it.

  An outside air filter 22 is provided upstream of the outside air passage 4 and downstream of the outside air introduction port 3, and fresh outside air OA from the outside air introduction port 3 is taken in the downstream side of the outside air filter 22 to return the air. An outside air fan 23 (outside air feeding means) is provided so as to be fed to the mixing unit 9 together with the air RA ′.

  Further, an exhaust air passage 26 having an exhaust port 25 is connected to a required position of the air-conditioning target room 6 so that a part of the room air in the air-conditioning target room 6 is discharged to the outside as exhaust EA. The air passage 26 is provided with an exhaust fan 27 (exhaust means). The exhaust fan 27 is adapted to each area of the air-conditioning target room 6 by taking outside air OA into a large amount / a small amount for each area obtained by subdividing the air-conditioning target room 6 by switching the operating state of the indoor equipment. This is to prevent a pressure difference from occurring.

  The flow rate of exhaust EA discharged from the exhaust fan 27 is controlled by an inverter controller 28 of the fan motor, and the flow rate of external air OA sucked from the outside air fan 23 is controlled by the inverter controller 29 of the fan motor. The rotation speed of the outside air fan 23 and the exhaust fan 27 is controlled so that the amount of exhaust air EA discharged by the exhaust fan 27 per unit time is equal to the suction amount of the outside air OA per unit time by the outside air fan 23. The air supply fan 19 always supplies a constant supply air SA to the air-conditioning target chamber 6. In FIG. 1, RAs is a detector for the dry bulb temperature T and relative humidity H of the return air RA, RAs 'is a detector for the dry bulb temperature T and relative humidity H of the humidified return air RA', and OAs is the outside air OA. A detector for dry bulb temperature T and relative humidity H, Ms is a detector for dry bulb temperature T and relative humidity H of air-fuel mixture MA, and SAs is a detector for dry bulb temperature T and relative humidity H of supply air SA.

  On the other hand, a snow storage unit 30 in which snow is accumulated is provided outside the room. The snow storage unit 30 is a partly modified snow dumping site that has been conventionally practiced in snowfall areas. Explaining the structure where no snow has accumulated in the snow dumping area, a plurality of continuous grooves 32 in which U-shaped troughs 31 are continuously arranged in a straight line so that the opening faces upward in one direction of the site are formed in parallel. Then, the bottom surfaces of the plurality of continuous grooves 32 are provided with gradients in the same direction, and the ground having a longitudinal direction perpendicular to one direction of the site is dug and connected to a snow mountain lower pit formed as a frame. The plurality of continuous grooves 32 are installed on the site of the snow storage unit 30 almost uniformly at a predetermined interval. The upper part of the continuous groove 32 is provided with a grating having a gap opening that is smaller than a dimension in which the bridging of snow accumulated 10 cm or more is broken, and the ground gradient of the entire site is made to be a downward slope toward the continuous groove 32. . An end of the snow cold water 36 is connected to the lower side of the lower pit of the snowy mountain. The snow storage unit 30 as a whole is formed by stacking snow 33 on the site of the snow storage unit 30. The snow storage unit 30 is configured to accumulate snow in the winter and to use the cold heat of the snow for cooling in the intermediate period (spring and autumn) and summer. When using for cooling, the water discharged from the hose etc. carried by the operator is directed downward from the upper part of the continuous groove 32 of the snow 33 loaded in the snow storage unit 30 at a predetermined interval (for example, 2 m). Then, a part of the snow 33 of the snowy mountain is melted until the grating is seen, and a hole 34 is formed so that the outside air above the snowy mountain and the continuous groove 32 communicate with each other.

  Further, one end 35a of an outside air duct 35, which is an underground duct only in a plan view of the snow storage portion 30, is connected to an upper side surface of the snow mountain lower pit, and a snow outside air damper D1 is connected to the outside air duct 35. And an outside air switching means comprising an outside air damper D2. An outside air duct 35 between the snow outside air damper D1 and the outside air damper D2 communicates with the outside air introduction port 3, and a continuous groove is formed from the hole 34 of the snow 33 by switching between the snow outside air damper D1 and the outside air damper D2. The snow-cooled outside air SOA 32 and the outside air OA can be switched and sucked by the outside air fan 23. SOAs are detectors for the dry-bulb temperature T and relative humidity H of the snow-cooled outside air SOA.

  Further, the snow cold water 36 made of the melted snow received in the snow mountain lower pit provided at the lower part of the snow storage part is stored in the snow cold water tank 37 by gravity drop or pump-up and provided in the circulation channel 16. Between the primary side of the snow cold water heat exchanger 38 and the snow cold water tank 37, a snow cold water circulation passage 39 for circulating the snow cold water 36 by the snow cold water pump P2 is provided. Further, the snow cold water circulation passage 39 is provided with a bypass pipe that can bypass part or all of the snow cold water conveyed by the snow cold water pump P2 from the snow cold water heat exchanger 38, and a control valve V5 in the bypass pipe. In addition, a filter 40 is also provided in the snow cold water circulation channel main pipe.

  Further, a backup heat source having a brine refrigerator R1 may be connected to the snow cold water tank 37. The backup heat source includes a backup snow cold water circulation passage 42 including a backup snow cold water pump P5 and a filter 41, which is connected to a return pipe in the vicinity of the introduction pipe of the snow cold water 36 of the snow cold water tank 37. A backup brine circulation channel 44 having a backup brine pump P1 is provided between the primary side of the backup heat exchanger 43 provided with the secondary side in the cold water circulation channel 42 and the brine refrigerator R1. Further, the backup brine circulation passage 44 is provided with a bypass pipe that can bypass part or all of the brine conveyed by the backup brine pump P1 from the backup heat exchanger 43, and a control valve V4 in the bypass pipe. . The brine refrigerator R1 functions as a backup when the refrigerator R2 of the cold water circulation passage 18 fails and when the temperature of the snow cold water 36 in the snow cold water tank 37 rises above a predetermined temperature. is there. This backup heat source may not be provided, and can be substituted by preparing a plurality of refrigerators R2 of the cold water circulation passage 18 in backup. L is a water level gauge for the snow cold water 36 in the snow cold water tank 37, T1s is a thermometer for the snow cold water 36 in the snow cold water tank 37, T2s is a thermometer for the cooling medium in the circulation channel 16, and T3s is cold water in the cold water circulation channel 18. , P1s is a pressure gauge of the cooling medium of the circulation channel 16.

  The air conditioning system 1 using snow of FIG. 1 includes the control device shown in FIG. In FIG. 2, C1 is an outside air operation system controller that constitutes a control device, and the outside air operation system controller C1 is provided so that the temperature and humidity of the outside air OA can be measured without being affected by solar radiation or wind. A measured value (OA Tm, OA Hm) from one detector OAs is input to calculate an outside air state point. Further, from the control and monitoring device 45 such as an adjustment PC, the supply air condition (temperature, relative humidity), the return air condition (temperature, relative humidity), the first stage humidifier saturation efficiency, the second stage humidifier saturation efficiency, Set absolute humidity, SA enthalpy, RA enthalpy, first stage post-humidification conditions (temperature, relative humidity) = RA ', mixture enthalpy = M', first stage humidification limit line coefficient, second stage humidification limit line coefficient, etc. Saturation efficiency line coefficient etc. are input.

  Then, the absolute humidity and enthalpy are calculated from the measured values of the outside air state point and the return air state point and used for control. By the way, in this specification, symbols of numerical values expressing air state points are T for dry bulb temperature, H for relative humidity, Xa for absolute humidity, and (H) for enthalpy. Various methods are conceivable for the detection and calculation, and the measurement value detected by the detector is given to the converter, and necessary measurement calculation values (absolute humidity Xa, enthalpy (H), etc.) obtained by the converter are given. A method of giving to the outside air operation system controller C1 and a method of calculating the calculation operation value (absolute humidity, enthalpy, etc.) in the outside air operation system controller C1 and further directly measuring the necessary measurement values ( (Absolute humidity, enthalpy, etc.) may be measured with a dedicated measuring instrument.

  Then, the outside air-operated operation system controller C1 to which the above parameters are inputted creates an operation mode map by the T-Xa air line indicating the relationship between the dry bulb temperature, the absolute humidity, the isoenthalpy, and the saturation curve shown in FIG. The computer 46 has a calculation unit 46 that calculates a plurality of operation mode regions. Specifically, the calculation unit 46 in FIG. 11 sets the supply air that is on the same enthalpy line as the SA enthalpy that is supplied to the air-conditioning target room through the supply air passage and that is supplied through the supply air passage. The minimum absolute humidity point at the entrance of the second stage humidifying means capable of humidifying up to absolute humidity is set as the boundary point M, and the return air set temperature / humidity point and the boundary point M are connected to extend to the boundary point side (boundary line = RA-M) divides the left side region of the boundary point on the T-Xa air diagram into two parts, and sets the minimum absolute humidity point at the inlet of the first stage humidifying means that can humidify to the set absolute humidity of the supply and return air for each dry bulb By dividing the right side region of the boundary point on the T-Xa air diagram into two parts by the curve (MN) connected at the right side region of the boundary point on the T-Xa air diagram for each temperature, at least the T-Xa air The diagram is divided into four operating mode areas with the boundary point M at the apex, and the return air condition RA An area larger than the large and the first-stage humidifier after conditions RA 'and return air condition line connecting the RA than relative humidity Xa, is set as an area of 5 th operation mode.

  Next, the meaning of dividing into regions of operation modes 1 to 5 on the T-Xa air diagram of FIG. 11 based on the parameters of the operation region map will be described.

  When the state point of the outside air OA is in the region of the operation mode 1, the mixture of the return air RA and the outside air OA is mixed on the line segment M-SA by adjusting the amount of the return air obtained by reducing the amount of outside air and hence the exhaust gas. The point can be moved. Since the point M is the farthest point that can reach the point SA by the humidification cooling of the second-stage humidifier 14, if the mixing point of the return air RA and the outside air OA can be on the line segment M-SA, the second-stage humidification The humidification and cooling of the vessel 14 can bring the state from the mixing point to the point SA. That is, in the state of the amount of outside air OA where the mixing point exists at the point where the straight line connecting the state point of the outside air OA and the point RA intersects the line segment M-SA, the state of the point SA is set by the second stage humidifier 14. It can be. This is referred to as “mixing second-stage humidification single operation”.

  At this time, the state of the outside air OA is further lowered from the region of the operation mode 1 or the temperature is high, and the inclination with respect to the horizontal is larger than the straight line RA-M, that is, the state point of the outside air OA is lower than the straight line RA-M. When coming to the side, the straight line connecting the point RA and the state point of the outside air OA does not intersect the line segment M-SA. In other words, even if the return air RA and the outside air OA are mixed with the point SA so as to have the same enthalpy, the state becomes lower right than the point M on the line. Not reach. This is because the point M is the farthest point from the saturation curve that can reach the point SA by the second-stage humidifier 14. Therefore, when the state point of the outside air OA comes below the straight line RA-M, the air state from the point RA to the point SA cannot be created in the “mixed second-stage humidification single operation”.

  Since the straight line RA-M can be expressed by a linear function (Xa = a1 × T + b1) on the T-Xa air diagram of FIG. 11, the state of the outside air OA can be determined using this function. . Specifically, when the outside air OA is smaller than the set absolute humidity (straight line SA-RA), smaller than the enthalpy of the set SA, and the outside air dry bulb temperature T and the outside air absolute humidity AH, AH> = a1 × T + b1 If there is, it is determined that the state point of the outside air OA is in the region of the operation mode 1, and the “mixing second-stage humidification single operation” is performed.

  When the outside air is in the operation mode 2 region, the point RA is first humidified by the first-stage humidifier 12 to be a point RA ′. Since the straight line connecting the point RA ′ and the state point of the outside air OA in the region of the operation mode 2 can intersect with the line segment M-SA, the first-stage humidifier 12 is placed on the line segment M-SA. If the return air RA ′ after humidification and the outside air OA are mixed, the point SA can be reached by humidification by the second-stage humidifier 14. This is referred to as “mixing two-stage humidification operation”.

  The straight line RA′-M can be represented by a linear function (Xa = a2 × T + b2) on the T-Xa air diagram of FIG. Here, the straight line RA′-M separates the operation modes 1 and 2 and the operation modes 3 and 4 and is a boundary line. That is, the region on the right side of the state of the outside air OA RA′-M is a region where the point SA cannot be reached only by mixing and humidifying the outside air OA and the return air RA. Cooling is required. However, the slope a2 is either positive or negative depending on the saturation efficiency of the humidifier and other conditions (supply air SA, return air RA). Therefore, the conditions for performing the “mixed two-stage humidification operation” are AH <a1 × T + b1 when the outside air OA is smaller than the enthalpy of the set SA, and the outside air dry bulb temperature T and the outside air absolute humidity AH, and a2 This is a case where AH ≧ a2 × T + b2 when> 0 or AH ≦ a2 × T + b2 when a2 <0.

  As described above, if the straight line between the state point of the outside air OA and the return air RA or the straight line between the state point of the outside air OA and RA ′ does not intersect the line segment M-SA, only the humidification and the mixing of the outside air OA are performed. Then, the point RA cannot be reached from the point SA. This is the region for operation mode 3 and the region for operation mode 4 (outlined). In these regions, the cooling coil 15 is cooled by supplying cold heat from the snow cold water 36, and if the cold heat is still insufficient, the cooling coil 15 can finally be cooled by the cold heat from the refrigerator R2.

  First, when the state of the outside air OA is in the region of the operation mode 4, that is, on the line of the curve MN or above it on the T-Xa air diagram in which the horizontal axis represents the dry bulb temperature and the vertical axis represents the absolute humidity. When there is a state point of the outside air OA, the curve MN is saturated so that each point can be reached when each point from the point SA to the point RA is an arrival point, like the point M with respect to the point SA. Since it is a set of points farthest from the curve, it is possible to reach the straight line SA-RA by humidifying the taken-in outside air OA as it is with the second-stage humidifier 14 (with an equal enthalpy change). From the reached point to the point SA, cooling by the cooling coil 15 is performed. This is referred to as “all outside air second-stage humidification single operation”.

  The operating conditions at this time are as follows: the enthalpy of the outside air OA is larger than the SA enthalpy, smaller than the RA enthalpy, the humidity is smaller than the set absolute humidity, and the curve MN on the T-Xa air diagram is an arbitrary function Xa. = F3 (T) is a case where AH> f3 (T) with the outside air dry bulb temperature T and the outside air absolute humidity AH.

  When the outside air OA is smaller than the set absolute humidity and smaller than the RA enthalpy, the above operation modes 1, 2, and 4 are not applied, and this case is a region of the operation mode 3. In this case, first, the return air RA is changed to return air RA ′ by the first-stage humidifier 12. Next, the return air RA ′ after humidification and the outside air OA are mixed so that the curves MN intersect. At this time, on the T-Xa air diagram with the dry bulb temperature on the horizontal axis and the absolute humidity on the vertical axis, the intersection of the straight line connecting the return air RA ′ and the outside air OA and the curve MN is obtained. The mixing control is performed so that the dry bulb temperature and the absolute humidity at the intersection are obtained. Then, in order to cause the air-fuel mixture MA to reach a point on the straight line SA-RA by the second-stage humidifier 14, cooling with the cooling coil 15 is performed. This is referred to as “mixing two-stage humidification + cooler combined operation”. Since the curve MN can be expressed by an arbitrary function Xa = f3 (T) on the T-Xa air diagram in which the horizontal axis represents the dry bulb temperature and the vertical axis represents the absolute humidity, the return air RA ′ and the outside air When a straight line connecting the OA state points is represented by a linear function or curve, the dry bulb temperature and absolute humidity after mixing can be obtained by calculating the intersection.

  The case where the above-described operation modes 1 to 4 do not apply corresponds to the operation mode 5 region. In this region, the snow-cooled outside air SOA from the snow storage unit 30 is used in the outside air passage if available. In the case where the first cooling to be supplied is performed, and the second cooling for supplying the cold heat of the snow cold water to the cooling medium flowing through the circulation flow path 16 of the cold heat supply means is performed. The supply air SA is maintained at the required supply air temperature by performing the third cooling that supplies the cold heat generated by the refrigerator to the cooling medium flowing through the circulation flow path 16.

  Next, based on the parameters of the operation mode map, the outside air state point measured by the detector OAs is substituted for the regions of the operation modes 1 to 5 divided on the T-Xa air diagram forming the operation mode map. A method for obtaining the operation mode will be described with reference to the flowchart of FIG.

  In the flowchart of FIG. 12, in the step of comparing the absolute humidity Xa of the outside air OAi measurement value and the absolute humidity Xa of the supply air setting value, OAi (Xa) is smaller than SA (Xa), so that the outside air cooling is performed. One of the possible conditions is met. If NO here, there is no cold of the outside air, which corresponds to the operation mode 5, and the cold heat source depends on the heat source such as the snow-cooled outside air SOA and / or snow cold water, and a refrigerator. If YES, in the step of comparing the enthalpy OAi (H) of the next outside air OAi measurement value with the enthalpy SA (H) of the supply air setting value SA, OAi (H) is smaller than SA (H), The condition that the outside air cooling can be performed only in combination with the previous step is established. If NO here, there is no cold of the outside air, which corresponds to the operation mode 5, and the cold heat source depends on the heat source such as the snow-cooled outside air SOA and / or snow cold water, and a refrigerator. If YES, in the step of comparing the enthalpy OAi (H) of the next outside air OAi measurement value with the enthalpy SA (H) of the supply air setting value SA, OAi (H) is smaller than SA (H), By mixing the outside air OAi with the return air RA, the air-fuel mixture is directly cooled by using the outside air, and the condition for bringing the air to the predetermined supply air setting value SA by using water humidification is established. If NO here, the cold air of the outside air is less for direct use, so it corresponds to the operation mode 3 or the operation mode 4 and is cooled by the cooling coil 15 by the cold heat of the snow cold water 36 in the snow cold water tank 37, and further the refrigerator R2 Cool using the cold heat from If YES, it corresponds to the operation mode 1 or the operation mode 2, and the use of the snow-cooled outside air SOA and the cooling by the cooling coil 15 do not have to be used. Then, when the flow of YES is advanced, the absolute humidity OAi (Xa) of the next outside air OAi measurement value, the return air set temperature / humidity point which is a boundary line, and the boundary line are extended to the boundary point side absolute In the step of comparing the humidity value (Xa) = a1 * OA (T) + b1, OAi (Xa) is larger than (Xa) = a1 * OA (T) + b1, so that OAi is mixed with the return air RA. As a result, the air-fuel mixture is directly cooled using the outside air, and the condition of bringing the air-fuel mixture to the predetermined air supply set value SA by using the second-stage humidifier is established. If YES, it corresponds to operation mode 1. If NO here, in the next step, when the outside air OAi (H) is smaller than the enthalpy of the set supply air SA (H), and when the outside air OAi has a dry bulb temperature T and an absolute humidity AH, AH <a1 × T + b1 Yes, if aH> a2 × T + b2 when a2> 0 or AH ≦ a2 × T + b2 when a2 <0 (YES), this corresponds to operation mode 2, and if NO, operation mode 3 Equivalent to.

  In the step of comparing the enthalpy OAi (H) of the outside air OAs measurement value and the enthalpy SA (H) of the supply air setting value SA, when OAi (H) is larger than SA (H), it corresponds to the operation mode 5; In this case, the cooling air is insufficient only by mixing the outside air OAi with the return air RA. Therefore, in this case, the first cooling supplied to the outside air passage is performed in order to use the snow-cooled outside air SOA, and further, the cooling heat supply means When the second cooling is performed to supply the cold heat of the snow chilled water to the cooling medium flowing through the circulation flow path 16 and the cold heat is still insufficient, a refrigerator is connected to the cooling heat medium flowing through the circulation flow path 16 of the cold heat supply means. Third cooling is performed to supply the generated cold energy.

  Next, the operation of the control device of the air conditioning system 1 using snow will be described with reference to FIGS.

  As described above, the outside-air operating system controller C1 shown in FIGS. 2 and 3 has a measured value that is a state point of the return air RA measured by the detector RAs and a state point of the outside air OA measured by the detector OAs. The absolute humidity and the enthalpy are calculated from the measured values of the outside air state point and the return air state point and used for control. In C1, the initial value or set values and condition values set at the start of operation are air supply conditions (temperature, relative humidity), return air conditions (temperature, relative humidity), and first stage humidifier saturation efficiency. 2nd stage humidifier saturation efficiency, return air intake setting absolute humidity, supply airway setting absolute humidity, SA enthalpy, RA enthalpy, 1st stage post-humidification conditions (temperature, relative humidity) = RA ', mixture The operation mode map output from the control monitoring device 45 such as an adjustment PC (personal computer), such as enthalpy = M ′, first stage humidification limit line coefficient, second stage humidification limit line coefficient, equal saturation efficiency line coefficient, etc. The calculation unit 46 receives parameters necessary for the creation, and the calculation unit 46 compares the numerical range derived from these values with the measured value of the outside air state point, and enters any region of the operation modes 1 to 5. Calculate whether it is applicable Cormorant. Furthermore, commands are given to the controllers C2 to C6 and C7 on the basis of the determination result of which region the outside air temperature is on the operation mode map. The heat generation load in the air-conditioned room has changed significantly, the set point of the supply air SA has changed, or the set point of the return air RA, which should be the temperature and humidity condition of the air-conditioned room, has changed due to equipment changes In this case, since it is necessary to update the parameters of the operation mode map, the return air condition (temperature, relative humidity) given as a set value from the control monitoring device 45 such as an adjustment PC (personal computer) regularly. And the measured value of the detector RAs are compared and verified, and the parameters are updated if necessary. The parameter is updated arbitrarily by the administrator.

  C2 shown in FIG. 2 is a controller having an operation command unit 1-a in the region of the operation mode 1. The operation command unit 1-a receives an operation instruction and an air supply SA from a higher-level outside air utilization operation system controller C1. The temperature / humidity setting value is received and an OFF instruction is given to the first stage adjustment valve V1 via the V1 instruction section 47, and a V2 instruction section 48 having an absolute humidity calculation section is provided to the second stage adjustment valve V2. An operation signal is given to the V2 indicator 48, and a measured value (S A Tm, SA Hm) of the temperature and humidity of the supply air SA is given to the V2 indicator 48 to calculate the absolute humidity so that the absolute humidity becomes the set absolute humidity. The opening degree of the second stage adjustment valve V2 is controlled. When the second-stage humidifier 14 is operated, the set value becomes the set absolute humidity in any mode of operation, so the signal from the operation command unit 1-a only needs to be a signal of operation or stop, It is not necessary to enter a set value. Further, the fan instruction unit 49 having an enthalpy calculation unit receives the enthalpy installation value of the mixture MA = the enthalpy setting value of the SA condition from the operation command unit 1-a, and determines the actual temperature and humidity of the mixture MA. The rotational speeds of the outside air fan 23 and the exhaust fan 27 are controlled while observing the measured values (MTm, MHm). The exhaust fan 27 only needs to exhaust the same amount as the amount of outside air taken in. Therefore, if the outside air fan 23 and the exhaust fan 27 have the same capacity, for example, the exhaust fan 27 may be controlled to be the same as the rotational speed of the outside air fan 23, or The outside differential pressure may be measured, and the rotational speed may be controlled so as to eliminate the differential pressure.

  C3 shown in FIG. 2 is a controller having an operation command unit 2-a in the region of the operation mode 2, and the operation command unit 2-a receives an operation instruction from an upper outside air operation system controller C1, an air supply The temperature / humidity setting value of SA is received, a constant opening degree instruction of the first stage control valve V1 is given to the V1 instruction section 47, an operation signal is given to the second stage regulation valve V2 to the V2 instruction section 48, and V2 The indication unit 48 is given a measured value (SA Tm, SA Hm) of the temperature and humidity of the supply air SA to calculate the absolute humidity, and the opening degree of the second stage control valve V2 so that the absolute humidity becomes the set absolute humidity. To control. The fan instruction unit 49 receives the installation value of the enthalpy of the mixture MA = the enthalpy setting value of the SA condition from the operation command unit 2-a, and the measured value of the temperature and humidity of the actual mixture MA (M Tm, M Hm), the rotational speeds of the outside air fan 23 and the exhaust fan 27 are controlled.

  C4 shown in FIGS. 4 and 5 is a controller having the operation command unit 3-a in the region of the operation mode 3, and the operation instruction unit 3-a operates from the upper outside air operation system controller C1 in FIG. An instruction and a set value of the temperature and humidity of the air-fuel mixture MA are received, a constant opening instruction is given to the first stage adjustment valve V1, and a constant opening instruction is given to the second stage adjustment valve V2. The fan instruction unit 49 receives the installation value of the enthalpy of the air-fuel mixture MA from the operation command unit 3-a = the enthalpy setting value of the SA condition, and the measured value of the temperature and humidity of the actual air-fuel mixture MA (M Tm, M Hm), the rotational speeds of the outside air fan 23 and the exhaust fan 27 are controlled. In the region of the operation mode 3, when the cooling temperature is insufficient, mixing of the snow-cooled outside air SOA from the snow storage unit 30 with the return air RA may be combined, and when the cooling is still insufficient. Can be cooled by the cooling coil 15 using the cold heat of the snow-cold water 36, and if it is still insufficient, it can be finally cooled by the cold heat of the refrigerator R2. Here, operation power (energy) such as compression power of the refrigeration cycle can be reduced by preferentially using the snow-cooled outside air SOA and the snow-cooled water 36 from the snow storage unit 30.

  C5 shown in FIGS. 6 and 5 is a controller having an operation command unit 4-a in the region of the operation mode 4, and the operation instruction unit 4-a is operated from the upper outside air operation system controller C1 in FIG. The instruction and the set value of the temperature and humidity of the supply air SA are received, and a constant rotation speed instruction is given to the fan instruction section 49 to control the outside air fan 23 and the exhaust fan 27 at a constant rotation speed. An operation signal is given to the V2 instruction unit 48 from the operation instruction unit 4-a, the absolute humidity is calculated from the measured value (S A Tm, SA Hm) of the supply air SA, and the absolute humidity becomes the set absolute humidity. Thus, the opening degree of the second stage adjustment valve V2 is controlled. Thereafter, the opening degree of the control valve V3 of the circulation channel 16 of the cold heat supply means is controlled so as to reach the set value from the measured value of the detector SAs that measures SA. In the region of the operation mode 4, when the cooling temperature is insufficient, mixing of the snow-cooled outside air SOA from the snow storage unit 30 with the return air RA may be combined, and when the cooling is still insufficient. Can be cooled by the cooling coil 15 using the cold heat of the snow-cold water 36, and if it is still insufficient, it can be finally cooled by the cold heat of the refrigerator R2. Here, operation power (energy) such as compression power of the refrigeration cycle can be reduced by preferentially using the snow-cooled outside air SOA and the snow-cooled water 36 from the snow storage unit 30.

C6 shown in FIG. 7a, FIG. 7b, and FIG. 8 is a controller having an operation command unit 5-a (maximum load response command unit) in the region of the operation mode 5, and is the upper outside air operation system controller C1 in FIG. From the operation instruction and the set value of the temperature and humidity of the supply air SA, the V1 instruction section 47 instructs the first stage adjustment valve V1 to turn off, the V2 instruction section 48 instructs the second stage adjustment valve V2 to turn off, An OFF instruction to the outside air fan 23 and the exhaust fan 27 by the fan instruction unit 49 and an opening instruction value of the control valve V3 provided in the circulation flow path 16 of the cold heat supply means are given (operations A to D).
The administrator visually confirms the remaining amount of snow in the snow storage unit 30 to make a use judgment of the snow-cooled outside air system, and when it is available, turns on the manual switch 50 and hands it over to the subsequent automatic control. When this manual switch 50 is ON, after the set time of the daily timer 51 that counts the steady effect time in which each of the operations A to D is considered to be in a steady state, the operation proceeds to the snow-cooled outside air intake operation of the operation E. Based on the snow-cooled outside air state point calculated from the measured value of the detector SOAs after the set time of the timer 52, the operation proceeds to operation F in which the subsequent operation mode is further determined. At the start of the snow-cooled outside air system operation (operation E), an open instruction is given to the snow outside air damper D1, a close instruction is given to the outside air damper D2, and the fan instruction section 49 determines the temperature measurement value (M Tm) of the mixture MA. The enthalpy calculation of the air-fuel mixture MA is performed from the humidity measurement value (M Hm), the rotation speed instruction values are given to the outside air fan 23 and the exhaust fan 27, and the first cooling by the snow-cooled outside air SOA is performed. At this time, the V2 instruction unit 48 gives an opening degree instruction value to the second stage adjustment valve V2.

  After the operation E (F operation), as shown in FIG. 7B, after the timer 52 waits for the steady effect time of the operation E, the temperature measurement value (SOA Tm) and the humidity measurement value (SOA) of the snow-cooled outside air SOA (SnowOA) are waited for. Hm), the calculation unit 53 calculates the enthalpy of the snow-cooled outside air SOA, and the region determination unit 54 determines whether the snow-cooled outside air SOA is in the operation mode 1 region or the operation mode 5 region. When it is determined that the vehicle is in the operation mode 1, the V3 instruction unit 55 is instructed to turn off the valve V3, and the snow-cooled outside air operation is continued. If it is determined that the vehicle is in the operation mode 5 region, an instruction to open the snow outside air damper D1 and an instruction to close the outside air damper D2 are given, and the rotation instruction to the outside air fan 23 and the exhaust fan 27 is given to the fan instruction section 49. In addition, an OFF instruction to the second stage adjusting valve V2 is given to the V2 indicator 48, and an opening degree instruction value is given to the valve V3 of the circulation channel 16 provided with the cooling coil 15. At this time, the snow storage part 30 2nd cooling which supplies the cold heat of the snow-cold water 36 from to the cooling coil 15 of a cooling means is performed. If the cold energy is still insufficient, the third cooling for supplying the cold heat of the refrigerator R2 to the cooling coil 15 of the cooling means is performed.

  C7 shown in FIG. 9 and FIG. 10 is a controller having a snow cold water use operation instruction unit 56 for performing control using the cold heat of the snow cold water 36 independently of the outside air use operation system controller C1. The snow cold water use operation instruction unit 56 determines whether the snow cold water system can be used based on the water level measured by the water level meter L of the snow cold water tank 37 and the snow cold water temperature measured by the thermometer T1s. When the snow chilled water system is available, the availability instruction unit 57 gives an instruction to turn off the valve V5 (bypass cutoff), and gives an instruction value to the pumps P2 and P3. Thereby, cooling using the cold heat by the snow cold water 36 of the snow cold water tank 37 is performed. In addition, when the snow cold water use operation instruction unit 56 supplies the snow cold water 36, the cooling with the snow cold outside air SOA is simultaneously performed. When the temperature of the snow cold water 36 in the snow cold water tank 37 rises above a predetermined temperature, an OFF instruction (bypass bypass) is given to the valve V4, an instruction value is given to the pumps P1, P5, and the brine refrigerator R1 is turned on. Then, backup cooling is performed by the brine refrigerator R1. When the snow chilled water system cannot be used, the unusable instruction unit 58 gives an ON instruction (bypass) for the valve V5, gives an OFF instruction (bypass bypass) for the valve V6, gives an instruction value to the pumps P1 and P2, and freezes The machine R2 is turned on and cooling by the refrigerator R2 is performed.

Below, the operation | movement outline | summary of each operation mode is demonstrated.
I) Mixed second stage humidification single operation (operation in the region of operation mode 1)

  In this case, the operation command unit 1-a in the region of the operation mode 1 receives an OFF command for closing the first-stage adjustment valve V1 from the outside-air utilization operation system controller C1, and the V1 instruction unit 47 sets the first-stage adjustment valve V1. The V2 indicating unit 48 having the absolute humidity calculation unit is set to OFF and gives an operation signal to the second-stage adjusting valve V2, and the V2 indicating unit 48 has a measured value (SA Tm, SA) of the supply air SA from the detector SAm. Hm) is given to calculate the absolute humidity, and the opening degree of the second stage adjustment valve V2 is controlled so that the absolute humidity becomes the set absolute humidity. When the second-stage humidifier 14 is operated, the set value becomes the set absolute humidity in any mode of operation. Therefore, the signal from the outside air operation system controller C1 is only input of the set value at the time of initial adjustment. It's okay. Further, the fan instruction unit 49 receives the set value of the mixture enthalpy M ′, that is, the enthalpy set value on the M-SA line, from the operation command unit 1-a, and the actual temperature and humidity (M Tm by the detector Mm). , MHm), the rotational speed of the outside air fan 23 is controlled based on the deviation from the measured value of the air-fuel mixture enthalpy M ′.

In the above state, the temperature / humidity of the supply air SA passing through the cooling coil 15 satisfies the set supply air condition, so that cooling by the cooling means is unnecessary. The exhaust fan 27 only needs to exhaust the same amount as the amount of outside air taken in, except for the amount of pressurized air. For example, if the outside air fan 23 and the exhaust fan 27 have the same capacity, the rotation speed of the outside air fan 23 It may be controlled in the same way, or the differential pressure inside and outside the room may be measured and the rotational speed may be controlled so as to eliminate the differential pressure.
II) Mixing two-stage humidification operation (operation in the region of operation mode 2)

  In this case, the operation command unit 2-a in the region of the operation mode 2 gives a constant opening instruction of the first-stage control valve V1 from the outside air operation system controller C1, and the measured value (SA Tm) of the temperature and humidity of the supply air SA. , SA Hm), the absolute humidity is calculated from the first control valve V1 through the V1 command section 47. When operating the first stage humidifier 12, the absolute humidity of the return air RA ′ is set as the set absolute humidity from the operation parameters, and the opening control of the first stage control valve V <b> 1 is performed from the measured value of the absolute humidity of RA ′. Since the inlet condition of the first-stage humidifier 12 is constant (RA) and RA ′ is set from the capacity (saturation efficiency) of the first-stage humidifier 12, basically, the first-stage humidifying valve V1 It is not necessary to control the opening degree, and it may be simpler that the signal from the outside air operation system controller C1 to the V1 command unit 47 is only a signal of operation or stop.

  The fan instruction unit 49 receives the set value of the mixture enthalpy M ′, that is, the enthalpy set value on the M-SA line, from the outside air operation system controller C1, and the actual temperature and humidity (M Tm, M Hm) by the detector Mm. ), The rotational speed of the outside air fan 23 and the exhaust fan 27 is controlled based on the deviation from the measured value of the air-fuel mixture enthalpy M ′.

The V2 command unit 48 receives an absolute humidity setting value signal having a deviation that opens the second stage control valve V2 and adjusts the opening degree from the outside air operation system controller C1, and the measured value of the supply air SA by the detector SAm. The opening degree of the second-stage regulating valve V2 is controlled so that the absolute humidity is determined from (SA Tm, SA Hm) and becomes the set absolute humidity.
III) Mixed two-stage humidification + cooling coil combined operation (operation in the region of operation mode 3)

  In this case, the operation command unit 3-a in the region of the operation mode 3 receives the set value of the absolute humidity having a deviation in the direction in which the first stage adjustment valve V1 is opened and the flow rate can be adjusted, from the outside air operation system controller C1. The first stage adjustment valve V1 is opened via the V1 instruction section 47.

  The fan instruction unit 49 receives the installation value of the air-fuel mixture enthalpy M ′ from the outside air operation system controller C1 (at the dry bulb temperature and the absolute humidity at the intersection of the straight line connecting the RA ′ and the outside air state point and the curve MM ′). Enthalpy) is received, and the rotational speed of the outside air fan 23 is controlled based on the deviation from the measured value of the mixture enthalpy M ′ calculated from the actual temperature and humidity from the detector Mm.

The V2 instructing unit 4 receives an absolute humidity set value signal having a deviation such that the first stage control valve V1 is opened and the opening degree is adjusted from the outside air operation system controller C1, and the supply SA is measured by the detector SAm. The opening degree of the second-stage regulating valve V2 is controlled so that the absolute humidity is determined from the values (SA Tm, SA Hm) so that the absolute humidity becomes the set absolute humidity. In the region of the operation mode 3, when the cooling temperature is insufficient, the snow-cooled outside air SOA from the snow storage unit 30 may be mixed with the return air RA. The cooling coil 15 is used to cool the snow cold water 36 using the cold heat, and when it is insufficient, it can be finally cooled by the cold heat generated by the refrigerator R2. Here, operation power (energy) such as compression power of the refrigeration cycle can be reduced by preferentially using the snow-cooled outside air SOA and the snow-cooled water 36 from the snow storage unit 30.
IV) All outside air second-stage humidification single operation (operation in operation mode 4 area)

  In this case, the operation command unit 4-a in the region of the operation mode 4 turns off the first stage adjustment valve V1 (not shown) in response to a command from the outside air utilization operation system controller C1, and the fan instruction unit 49 operates as the outside air utilization operation system controller. The outside air fan 23 and the exhaust fan 27 are controlled at a constant rotational speed by a constant rotational speed command from C1.

  The V2 instruction unit 48 receives an absolute humidity setting value signal having a deviation that opens the second stage control valve V2 and adjusts the opening degree from the outside air operation system controller C1, and the measured value of the supply air SA by the detector SAm. The opening degree of the second-stage regulating valve V2 is controlled so that the absolute humidity is determined from (SA Tm, SA Hm) and becomes the set absolute humidity. When the cooling temperature is insufficient in the region of the operation mode 4, the snow-cooled outside air SOA from the snow storage unit 30 may be mixed with the return air RA. The cooling coil 15 is used to cool the snow cold water 36 using the cold heat, and when it is insufficient, it can be finally cooled by the cold heat generated by the refrigerator R2. Here, operation power (energy) such as compression power of the refrigeration cycle can be reduced by preferentially using the snow-cooled outside air SOA and the snow-cooled water 36 from the snow storage unit 30.

  Further, in the case of the operation mode 5 that does not apply to any of the above operation modes 1 to 4, the operation command unit 5-a in the region of the operation mode 5 receives the command from the outside air operation system controller C1 to The cooling coil 15 is used to control the measured temperature of the supply air SA to the set temperature. At this time, when the snow-cooled outside air SOA from the snow storage unit 30 is available, the snow-cooled outside air SOA is mixed with the return air RA to perform the first cooling that lowers the temperature of the air-fuel mixture MA, and further, cooling means The second cooling for supplying the cold heat of the snow cold water 36 to the cooling coil 15 is performed, and if the cold heat is still insufficient, the third cooling for finally supplying the cold heat from the refrigerator R2 to the cooling coil 15 of the cooling means is performed. . Here, operation power (energy) such as compression power of the refrigeration cycle can be reduced by preferentially using the cold heat of the snow cold water 36 from the snow storage unit 30.

  As described above, according to the air conditioning system using snow of the present invention, the first stage humidifier 12 that humidifies the return air RA and the outside air OA when performing outside air cooling using outside air in the intermediate period or winter season. Provided with the second stage humidifier 14 for humidifying the air-fuel mixture MA of the return air RA and the humidification of the supply air SA can be prevented, and the cooling effect by the humidification can be used, and therefore the cooling by the use of the outside air There is an effect to maximize the effect. Furthermore, even when the cooling load is large and the cooling capacity is insufficient only by the outside air mixed cooling in the intermediate period or winter season, the snow cooling outside air SOA from the snow storage unit 30 is mixed with the return air RA and / or the snow storage. The supply air SA is cooled by the cooling means using the cold heat of the snow cold water 36 from the section 30 so that the cold heat of the snow is effectively used and the use of the cold heat supply device such as a refrigerator is minimized. Energy can be greatly reduced.

  The air conditioning system using snow according to the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the present invention.

DESCRIPTION OF SYMBOLS 1 Air-conditioning system using snow 3 Outside air introduction port 4 Outside air passage 5 Return air intake 6 Air-conditioning target room 7 Return air passage 9 Mixing part 10 Supply air passage 11 Supply air passage 12 First stage humidifier (first stage humidifier) )
14 Second stage humidifier (second stage humidifier)
15 Cooling coil (cooling means)
16 Circulating channel 17 Refrigerator-generated cold heat exchanger 19 Air supply fan (air supply means)
23 Outside air fan (outside air feeding means)
27 Exhaust fan (exhaust means)
30 Snow storage part 31 U-shaped groove 32 Continuous groove 33 Snow 36 Snow cold water 37 Snow cold water tank 38 Snow cold water heat exchanger 56 Snow cold water use operation instruction part 5-a Operation command part of operation mode 5 area (corresponding to maximum load) Command section)
D1 Snow outside air damper (outside air switching means)
D2 Outside air damper (outside air switching means)
R1 brine refrigerator R2 refrigerator

Claims (10)

The machine room includes an outside air passage which is a first flow passage communicating with the outside air introduction port, a return air passage which is a second flow passage communicating with the air-conditioning target chamber via the return air inlet, the outside air passage, The outside air passage and the return air passage communicate with the return air passage through a partitioned mixing section, and are a third flow passage that is partitioned from the mixing section and communicates with the air-conditioning target chamber through a supply air passage. An air supply passage,
Outside the room, there is a snow storage section that accumulates snow,
The return air passage is provided with first-stage humidification means for adiabatic humidification of the return air from the return air intake with water, and the air supply passage is provided with the outside air from the outside air inlet and the return air intake. A second stage humidifying means for adiabatically humidifying the air-fuel mixture mixed with the return air, and a cold heat supply means for supplying a cooling medium capable of supplying the cold heat of the snow cold water from the snow storage section to the circulation channel. The cooling means is a cooling coil, and the air supply means for supplying the air-fuel mixture in the air supply passage to the air-conditioning target room through the air supply passage, and the temperature and humidity state of the air-fuel mixture is provided in the outside air passage An outside air supply means capable of adjusting the air volume for conveying outside air for adjusting the air volume is installed, and in the air conditioning target room, an exhaust means for exhausting a part of the indoor air is installed, and the outside air introduction port is provided. Is the outside air that can be switched between the outside air and the snow-cooled outside air cooled by the snow in the snow storage tank. Air conditioning system using the snow, characterized in that they have installed switch means.   The cold supply means connected to the cooling means, with respect to the cooling medium, the cold heat of snow cold water taken out from the snow storage unit to the outside by a heat exchanger, the cold generated by the refrigerator by a heat exchanger, The air conditioning system using snow according to claim 1, wherein heat can be appropriately transferred.   The humidification amount of the first stage humidifying means is measured at the return air intake and is calculated according to the absolute humidity. The air volume of the outside air supply means is measured at the mixing section and the second stage according to the calculated enthalpy. The air conditioning system using snow according to claim 1 or 2, further comprising a control device that controls the humidification amount of the humidification means in accordance with the absolute humidity calculated by measuring the humidification amount in the supply air passage. system.   It is on the same enthalpy line as the enthalpy of the air supply setting temperature / humidity point supplied to the air conditioning target room and can be humidified up to the set absolute humidity of the air supply supplied through the air supply path 2 The minimum absolute humidity point at the inlet of the stage humidifying means is set as the boundary point, and the left side of the boundary point on the T-Xa air diagram is defined by a straight line connecting the return air temperature / humidity point and the boundary point to the boundary point side. Divide the area into two and connect the minimum absolute humidity point at the inlet of the first stage humidifier that can humidify to the set absolute humidity of the supply and return air at the right side of the boundary point on the T-Xa air diagram for each dry bulb temperature By dividing the right area of the boundary point on the T-Xa air diagram by the curve, the temperature and humidity are measured by dividing the area at least on the T-Xa air diagram into four areas having the boundary point at the apex. The operation mode is switched depending on which of the four regions the outside air state point is included. Air conditioning systems using snow according to any one of claims 1 to 3, characterized in that it comprises a control device.   If the outside air state point is included in the upper area of the straight line connecting the return air set temperature / humidity point and the boundary point to the boundary point side, the first stage humidification means is turned OFF and the air temperature of the mixing section A control device that controls the air volume of the outside air supply means based on the enthalpy obtained from the measured value and controls the humidification amount of the second stage humidifying means based on the absolute humidity obtained from the measured air temperature and humidity in the air supply air passage. The air conditioning system using snow according to claim 4.   When the outside air state point is included in the lower area of the straight line connecting the return air set temperature / humidity point and the boundary point to the boundary point side, it was obtained from the return air temperature measurement value of the return air inlet Controls the humidification amount of the first-stage humidification means based on the absolute humidity, controls the air volume of the outside air supply means based on the enthalpy obtained from the air temperature measurement value of the mixing section, and measures the air supply humidity in the supply air passage 5. The air conditioning system using snow according to claim 4, further comprising a control device that controls a humidification amount of the second-stage humidification unit based on the absolute humidity obtained by the step.   In the upper area of the curve connecting the minimum absolute humidity point at the entrance of the second stage humidifying means that can humidify to the set absolute humidity of the supply and return air at the right side of the boundary point on the T-Xa air diagram for each dry bulb temperature When the outside air state point is included, the humidification amount of the second-stage humidifying means is controlled based on the absolute humidity obtained from the measured temperature of the supplied air temperature in the supply air path, the first-stage humidifying means is turned OFF, 5. The air conditioning system using snow according to claim 4, further comprising a control device that controls the amount of heat supplied by the cooling medium and supplied to the cooling unit based on a supply air temperature in the supply air passage. .   In the lower area of the curve connecting the minimum absolute humidity point at the entrance of the second stage humidifying means that can humidify to the set absolute humidity of the supply and return air at the right side of the boundary point on the T-Xa air diagram for each dry bulb temperature When the outside air state point is included, the humidification amount of the first-stage humidifying means is controlled based on the absolute humidity obtained from the return temperature humidity measurement value of the return air inlet, and the air temperature measurement value of the mixing unit is used. The air volume of the outside air supply means is controlled based on the obtained enthalpy, and the humidification amount of the second stage humidifying means is controlled based on the absolute humidity obtained from the measured air temperature and humidity in the supply air path. 5. The air conditioning system using snow according to claim 4, further comprising: a control device that controls the amount of heat supplied to the cooling means that the cooling medium has, based on a supply air temperature in the road.   Use of snow cold water for controlling the supply of cold heat of the snow cold water to the cold medium flowing through the circulation channel of the cold heat supply means by judging the availability of the cold heat of the snow cold water taken out from the snow storage unit The air conditioning system using snow according to claim 7 or 8, further comprising an operation command unit.   When the outside air state point does not apply to the case of any of claims 5 to 8 on the T-Xa air diagram, the first cooling for supplying the snow-cooled outside air to the outside air passage, and the circulation flow of the cold heat supply means A second cooling for supplying the cold heat of the snow chilled water to the cooling medium flowing through the passage; and a second cooling for supplying the cold generated by the refrigerator to the cooling heat medium flowing through the circulation flow path of the cold heat supply means when the cold heat is insufficient. 3. An air-conditioning system using snow, characterized by having a maximum load response command unit that performs cooling.

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