Air conditioning system

Abstract

To provide an air conditioning system capable of preventing a temperature rise of an air conditioning target room while reducing a load of a reheating section while saving on energy.SOLUTION: An air conditioning system 10 includes: an air conditioning device 11 for mixing outside air OA and return air RA and feeding out supply air SA which is adjusted into target feed-out temperature / humidity; a supply air temperature measurement sensor TED1 for measuring a temperature of the supply air; a reheating section 21 provided in each air conditioning target room and reheating the supply air; an air supply / exhaust device 24 for introducing, to the air conditioning target room, the supply air having passed through the reheating section; and room temperature measurement sensors T2-4 each for measuring a room temperature inside the air conditioning target room. The target feed-out temperature is adjusted in such a manner that a reheating amount of the reheating section in any air conditioning target room becomes equal to or less than a first reheating amount, and when a measurement value of the room temperature measurement sensor in the air conditioning target room of the reheating section in which the reheating amount is adjusted rises, the air supply / exhaust device of the air conditioning target room is controlled so as to increase a flow rate of the supply air to the air conditioning target room.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] This invention relates to an air conditioning system that controls the temperature and humidity of multiple rooms to be air-conditioned. [Background technology]

[0002] Patent Document 1 proposes an air conditioning system that can control the temperature and humidity of multiple rooms to be air-conditioned to a constant level. This system involves mixing cooled and dehumidified outside air with return air to generate mixed air, performing sensible heat treatment on the air conditioning device to set the temperature of the mixed air to a target supply temperature and a predetermined humidity, supplying it to the rooms to be air-conditioned, and reheating it to a target supply air temperature in a reheating unit provided in each room before supplying it.

[0003] In Patent Document 1, in order to reduce the amount of reheat in the reheat section, the target output temperature of the air conditioning system is set so that the amount of reheat in the reheat section of any of the air-conditioned rooms is zero or low. [Prior art documents] [Patent Documents]

[0004] [Patent Document 1] Japanese Patent Publication No. 2019-143826 [Overview of the project] [Problems that the invention aims to solve]

[0005] However, if the reheat amount of the reheating unit is set to zero or low, and the load in the air-conditioned room increases, causing the temperature to rise, then setting the reheat amount of that room to zero will not prevent the temperature from rising. Therefore, in order to lower the temperature of that room, the target output temperature of the air conditioning unit must be lowered. As a result, the reheat amount of the reheating units in other air-conditioned rooms must be increased, which may not lead to energy savings.

[0006] The present invention aims to provide an air conditioning system that can reduce the load on the reheat section of the air-conditioned room, thereby saving energy, while preventing the temperature of the air-conditioned room from rising. [Means for solving the problem]

[0007] The air conditioning system according to the present invention is An air conditioning system that mixes outside air with return air from multiple rooms to be air-conditioned, and supplies supply air adjusted to a target temperature and target humidity. A supply air temperature measuring sensor for measuring the temperature of the supply air, Each of the aforementioned air-conditioned rooms is provided with a reheating unit that reheats the supply air, A supply and exhaust device is provided in each of the aforementioned rooms to be air-conditioned, which introduces the supply air that has passed through the reheat section into the room to be air-conditioned, and sends return air from the room to be air-conditioned to the air conditioning unit, A room temperature measuring sensor for measuring the room temperature of the room to be air-conditioned, An air conditioning system including, The target output temperature of the air conditioning system is adjusted so that the reheat amount of the reheat section of any of the rooms to be air-conditioned is less than or equal to the first reheat amount. In this state, if the measured value of the room temperature measuring sensor of the reheat section of the room to be air-conditioned rises, the air supply and exhaust system of the room to be air-conditioned is controlled so that the flow rate of the air supplied to that room increases.

[0008] When the reheat amount of the reheat section of any of the rooms to be air-conditioned becomes equal to or greater than the second reheat amount, the target output temperature of the air conditioning system can be increased.

[0009] The air conditioning system may include a latent heat treatment device for cooling and dehumidifying outside air, and an air conditioner for adjusting the humidity of the mixed air to the target delivery temperature and target delivery humidity.

[0010] The supply and exhaust system may include an airflow control device for introducing the mixed air into the room to be air-conditioned, and a room pressure control damper for returning the air from the room to be air-conditioned to the air conditioning system. [Effects of the Invention]

[0011] According to the air conditioning system of the present invention, by raising the target delivery temperature of the air conditioner so that the load of the reheating section in any of the air-conditioned rooms is reduced, energy savings in the reheating section can be achieved. Further, in this state, when the temperature of the air-conditioned room rises, the temperature of the air-conditioned room can be lowered by increasing the operation amount of the supply and exhaust device of the air-conditioned room, and each air-conditioned room can be maintained at a constant temperature and humidity.

Brief Description of the Drawings

[0012] <F [Figure 1] FIG. 1 is a configuration explanatory diagram of an air conditioning system according to an embodiment of the present invention. [Figure 2] FIG. 2 is a graph showing the relationship between the supply air dew point temperature of the latent heat treatment device and the opening degree of the automatic valve MV0 of the cooling coil. [Figure 3] FIG. 3 is a graph showing the relationship between the supply air temperature of the air conditioner and the opening degrees of the automatic valve MV11 of the cooling coil and the automatic valve MV12 of the heating coil. [Figure 4] FIG. 4 is a graph showing the relationship between the supply air dew point temperature of the air conditioner and the opening degrees of the automatic valve MV11 of the cooling coil and the automatic valve MV13 of the humidifier. [Figure 5] FIG. 5 is a graph showing the relationship between the supply air static pressure and the frequency of the inverter-controlled air conditioner fan. [Figure 6] FIG. 6 is a graph showing the relationship between the room temperature of each air-conditioned room, the opening degree of the automatic valve MV2-4 of the reheating section, and the supply air volume of the air volume control device. [Figure 7] FIG. 7 is a graph showing the relationship between the room pressure of each air-conditioned room and the opening degree of the room pressure control damper. [Figure 8] FIG. 8 is a graph showing the relationship between the hot water valve opening degree signal of the reheating section and the target delivery temperature SP of the heating coil of the air conditioner. [Figure 9] FIG. 9 is an explanatory diagram of an air conditioning system showing the conditions of the examples. [Figure 10] FIG. 10 shows the air diagram of the example. [Figure 11]Figure 11 shows the psychrometric chart of the embodiment. [Modes for carrying out the invention]

[0013] Hereinafter, an embodiment of the air conditioning system 10 of the present invention will be described with reference to the drawings.

[0014] As shown in Figure 1, the air conditioning system 10 of the present invention includes a plurality of rooms to be air-conditioned 20 and an air conditioning unit 11. In the illustration, there are three rooms to be air-conditioned 20, each appropriately identified by reference numerals 202, 203, and 204. The number of rooms is not particularly limited, as long as it is two or more.

[0015] The air-conditioned room 20 is a space that is kept at a constant temperature and humidity by various devices included in the air conditioning system 10 of the present invention, and examples include pharmaceutical manufacturing rooms, laboratory animal breeding rooms, clean rooms and other factory facilities, and commercial facilities such as office buildings.

[0016] The air conditioning system 10 mainly consists of an air conditioning unit 11, a reheat unit 21 provided in each air-conditioned room 20, and a supply and exhaust system. In this embodiment, the supply and exhaust system consists of an airflow control device 24 (242-244) and a room pressure control damper PCD2-4. The air conditioning unit 11 and the air-conditioned rooms 20 are connected by ducts.

[0017] The air conditioning unit 11 mixes the outside air OA with the return air RA from the room to be air-conditioned 20 and sends out a mixed air MA with adjusted temperature and humidity. In this embodiment, the return air from the room to be air-conditioned 20 is provided in two systems: return air RA and exhaust air EA. The return air RA is used to generate the mixed air MA, and the exhaust air EA is used for total heat exchange with the outside air OA. In addition, the outside air OA is cooled and dehumidified before being mixed with the return air RA to adjust its temperature and humidity. However, it is also possible to mix the outside air OA with the return air RA without cooling and dehumidifying it after total heat exchange with the exhaust air EA, and then cool, dehumidify, and adjust the temperature and humidity of the mixed air MA.

[0018] As a specific embodiment of the air conditioning system 11, as shown in Figure 1, the air conditioning system 11 includes a total heat exchanger 12 that exchanges total heat between outside air OA and exhaust air EA, a latent heat treatment device 13 that cools and dehumidifies the outside air OA after total heat exchange, and an air conditioner 14 that mixes the outside air OA that has passed through the latent heat treatment device 13 with the return air RA from the room to be air-conditioned 20, adjusts the mixed air MA to a target delivery temperature and humidity, and delivers it.

[0019] The total heat exchanger 12 is a device that performs total heat exchange between outside air OA taken in from the outdoors and exhaust EA discharged outdoors from the room to be air-conditioned 20. The exhaust EA from the room to be air-conditioned 20 is discharged outdoors by an exhaust fan (not shown).

[0020] The latent heat treatment device 13 comprises a cooling coil 131 through which chilled water circulates (CS0, CR0) and a latent heat treatment device fan 132 for supplying outside air OA. The cooling coil 131 cools the outside air OA that has passed through the total heat exchanger 12 to below the dew point and performs dehumidification. An automatic valve MV0 for adjusting the flow rate of chilled water CS0 is located in the cooling coil 131. A duct-inserted dew point temperature sensor D0 is located downstream of the latent heat treatment device 13, and the dew point temperature DPED0 of the outside air OA measured by the duct-inserted dew point temperature sensor D0 is transmitted to a dew point temperature controller DIC0.

[0021] The dew point temperature controller DIC0 then controls the automatic valve MV0 based on the dew point temperature DPED0 of the outside air OA, adjusting the amount of cooling of the outside air OA. For example, the opening degree of the automatic valve MV0 adjusted by the dew point temperature controller DIC0 can be proportionally controlled by the supply air dew point temperature of the outside air OA, as shown in Figure 2.

[0022] The air conditioner 14 receives outside air OA, whose humidity has been adjusted by the latent heat treatment device 13, and return air RA from the room to be air-conditioned 20, and mixes them in the mixer 141 to form a mixed air MA. In this embodiment, the return air RA from the room to be air-conditioned 20 is the airflow that returns after passing through the room pressure control damper PCD2-4 of the room to be air-conditioned 20. The air conditioner 14 is equipped with a cooling coil 142 and a heating coil 143 to adjust the temperature of the mixed air MA, and a humidifier 144 to adjust the humidity of the mixed air MA. Cooling water can be circulated through the cooling coil 142 (CS1, CR1), and the flow rate of the cooling water is adjusted by the automatic valve MV11. Hot water can be circulated through the heating coil 143 (HS1, HR1), and the flow rate of the hot water is adjusted by the automatic valve MV12. Humidifier water S can be supplied to the humidifier 144, and the flow rate of the humidifier water S is adjusted by the automatic valve MV13.

[0023] Furthermore, downstream of the humidifier 144, there is a humidifier 144 capable of humidifying the mixed air MA, an air conditioner fan 145 that delivers supply air SA whose temperature and humidity have been adjusted by the air conditioner 14, a duct insertion temperature sensor T1, a duct insertion dew point temperature sensor D1, and a differential pressure sensor dPE1. The duct insertion temperature sensor T1 corresponds to the supply air temperature measurement sensor of the present invention.

[0024] The duct-inserted temperature sensor T1 measures the temperature TED1 of the supply air SA delivered from the air conditioner 14, and the temperature controller TIC1 adjusts the automatic valves MV11 and MV12 of the cooling coil 142 and heating coil 143 to control the flow rate of chilled and hot water so that the temperature of the supply air SA reaches the set target delivery temperature. For example, as shown in Figure 3, the temperature controller TIC1 can be configured to open and close the automatic valves MV11 and MV12 by proportional control according to the difference between the temperature of the supply air SA and the target delivery temperature. The temperature controller TIC1 then controls the opening of the automatic valve MV11 of the cooling coil 142 when the temperature of the supply air SA is higher than the target delivery temperature, and increases the opening of the automatic valve MV12 of the heating coil 143 when the temperature of the supply air SA is lower. In this invention, the target delivery temperature is set considering the hot water valve opening signal HVS of one of the reheat sections 21 of each air-conditioned room 20, which will be described later (see Figure 6). This setting method will be described later.

[0025] The duct-inserted dew point temperature sensor D1 measures the dew point temperature DPED1 of the supply air SA and controls the automatic valves MV11 and MV13 of the cooling coil 142 or humidifier 144 via the dew point temperature controller DIC1 so that the supply air SA is adjusted to the set dew point temperature. The dew point temperature controller DIC1 can be configured to open and close the automatic valves MV11 and MV13 by proportional control according to the difference between the dew point temperature DPED1 of the supply air SA and the set dew point temperature, for example as shown in Figure 4. If the dew point temperature of the supply air SA is higher than the set dew point temperature, the opening of the automatic valve MV11 of the cooling coil 142 is increased to humidify, and if the temperature of the supply air SA is low, the opening of the automatic valve MV13 of the humidifier 144 is increased to dehumidify.

[0026] The automatic valve MV11 of the cooling coil 142 is controlled to open and close by two devices: a temperature controller TIC1 and a dew point temperature controller DIC1. In this embodiment, the automatic valve MV11 operates at the higher of the two opening degrees output by the temperature controller TIC1 and the dew point temperature controller DIC1. A high selector HSL1 is inserted between the temperature controller TIC1 and the dew point temperature controller DIC1 to achieve this.

[0027] The differential pressure sensor dPE1 measures the static pressure of the supplied air SA, and the differential pressure controller PIC1 controls the air conditioner fan 145 based on this static pressure. For example, the air conditioner fan 145 is controlled by an inverter INV, and the differential pressure controller PIC1 controls the frequency of the air conditioner fan 145 based on the static pressure of the supplied air, thereby changing the rotation speed and making the flow rate of the supplied air SA variable, as shown in Figure 5.

[0028] As described above, the air conditioning unit 11 mixes the outside air OA and the return air RA, and the air conditioner 14 adjusts the temperature of the supply air SA to the target delivery temperature and the dew point temperature to the set dew point temperature. This supply air SA is then delivered from the air conditioner fan 145 at a predetermined pressure.

[0029] Downstream of the air conditioning unit 11, ducts are provided that branch off and connect to each air-conditioned room 20, and supply air SA from the air conditioning unit 11 is distributed and supplied through these ducts.

[0030] Each duct leading to the air-conditioned rooms 20 (202-204) is equipped with an airflow control device 24 (242-244) for introducing supply air SA and a reheat unit 21 (212-214). Each air-conditioned room 20 is also equipped with an indoor temperature sensor T2-4 for measuring the room temperature TE2-4. The measured room temperature TE2-4 is transmitted to a temperature controller TIC2-4, which controls the airflow control device 242-244 and the reheat unit 212-214. The indoor temperature sensor T2-4 corresponds to the room temperature measurement sensor of the present invention.

[0031] In a specific embodiment, the airflow control device 24 is, for example, a constant airflow control device (CAV), and the airflow control device 24 constitutes the supply and exhaust system of the present invention. The airflow control device 24 introduces a predetermined flow rate of supply air SA into the air-conditioned room 20. The airflow control device 24 may also be a variable airflow control device (VAV). Based on the room temperature TE2-4, the flow rate of the supply air SA introduced into the air-conditioned rooms 202-204 is controlled by the temperature controller TIC2-4 of the airflow control devices 242-244.

[0032] Furthermore, the reheating section 212-214 is, for example, a heating coil, through which hot water can be circulated (HS2-4, HR2-4), and the flow rate of the hot water is regulated by the automatic valve MV2-4. The opening degree of the automatic valve MV2-4 is controlled by the temperature controller TIC2-4 based on the room temperature TE2-4.

[0033] Figure 6 is a graph showing the relationship between the supply airflow rate from the airflow control device 24 and the opening degree of the automatic valve MV2-4 of the reheat unit 21, with respect to the room temperature of each air-conditioned room 20. In this invention, as shown in Figure 6, when the room temperature rises above the target temperature SP, the output of the airflow control devices 242-244 of the corresponding air-conditioned rooms 202-204 is increased to increase the airflow rate of the supplied air SA and lower the temperature. Also, when the room temperature falls below the target temperature SP, the opening degree of the corresponding automatic valve MV2-4 is increased to heat the supply air SA and raise the room temperature.

[0034] The opening degree of the automatic valve MV2-4 is transmitted to the air conditioning unit 11 as a hot water valve opening signal HVS2-4. The air conditioning unit 11 is equipped with two low selectors LSL1-2 and two high selectors HSL11-12. The hot water valve opening signal HVSL, which has the lowest opening degree among the automatic valves MV2-4 of the reheating unit 212-214, and the hot water valve opening signal HVSH, which has the highest opening degree, are selected and input to the temperature controller TIC1. The control of the temperature controller TIC1 after the input of the hot water valve opening signals HVSL and HVSH will be described later.

[0035] The exhaust from the air-conditioned rooms 202-204 is supplied via two systems: natural exhaust (EA) and return air (RA) from the room pressure control damper PCD2-4. The exhaust EA is sent to the total heat exchanger 12 for total heat exchange with the outside air (OA). The return air (RA) is supplied from the room pressure control damper PCD2-4 to the air conditioner 14 and mixed with the outside air (OA). The room pressure control damper PCD2-4 is a room pressure control device whose door opening degree is variable based on differential pressure. It is controlled by the differential pressure controller PIC2-4 based on the measurement value of the differential pressure sensor dPE2-4, which measures the differential pressure between the room pressure of the air-conditioned rooms 202-204 and the return air (RA) duct. Specifically, as shown in Figure 7, when the room pressure is low, the room pressure control damper PCD2-4 maintains its minimum opening degree and performs proportional control, increasing the opening degree as the room pressure increases.

[0036] In each of the air-conditioned rooms 202-204, the temperature controller TIC2-4 controls the respective airflow control devices 242-244 and reheat units 212-214 based on the temperature TE2-4 detected by the room's indoor temperature sensor T2-4. In this embodiment, as shown in Figure 6, when the room temperature of the air-conditioned room 20 is lower than the target value SP, the reheat unit 21 heats the supply air SA. Conversely, when the room temperature rises above the target value SP, the opening of the automatic valve MV2-4 is increased to increase the amount of supply air SA supplied from the airflow control device 242-244 to the air-conditioned rooms 202-204. This increase in airflow from the airflow control device 24 lowers the temperature of the air-conditioned room 20 to the target value SP. At this time, the room pressure control damper PCD2-4 also moves, so the room pressure is kept constant.

[0037] As described above, the air conditioning system 10 of the present invention exchanges total heat between the outside air OA taken into the air conditioning device 11 and the exhaust EA from the room to be air-conditioned 20 in the total heat exchanger 12, and adjusts the humidity in the latent heat treatment device 13. Then, in the air conditioner 14, the outside air OA and the return air RA are mixed in the mixer 141, and the temperature TED1 and dew point temperature DPED1 of the supply air SA sent out from the air conditioner 14 are referenced to adjust the opening of the automatic valves MV11-13 of the cooling coil 142, heating coil 143 and humidifier 144 using the temperature controller TIC1 and the dew point temperature controller DIC1 so that the target supply temperature and target supply humidity are achieved, and the supply air SA with the target supply temperature and target supply humidity is sent out by the air conditioner fan 145.

[0038] The supplied air SA is delivered to each air-conditioned room 202-204. In each air-conditioned room 202-204, the temperature controller TIC2-4 controls the airflow control device 242-244 and the reheat unit 212-214 according to the room temperature TE2-4, adjusting the air-conditioned room 202-204 to a predetermined temperature. In addition, the room pressure in the air-conditioned rooms 202-204 is kept constant by the room pressure control damper PCD2-4.

[0039] Exhaust air EA from the air-conditioned rooms 202-204 is released to the outside via the total heat exchanger 12, and return air RA released from the room pressure control damper PCD2-4 is returned to the air conditioning unit 11.

[0040] In the above-mentioned air conditioning system 10, the present invention achieves energy saving of the air conditioning system 10 by performing the following control.

[0041] First, the target output temperature of the air conditioner 14 is adjusted so that the reheat amount of the reheat section 212-214 of any of the air-conditioned rooms 202-204 is less than or equal to the first reheat amount. The first reheat amount can be set so that the output of the reheat section 212-214 is zero or low, for example, 10% or less. This increases the amount of heating by the air conditioner 14, but reduces the reheat amount of the reheat section 212-214 of the air-conditioned rooms 202-204, thereby achieving energy savings. In the following explanation, the first reheat amount is assumed to be zero.

[0042] Furthermore, during this time, in the air-conditioned rooms 202-204 of the reheat section 212-214 where the reheat amount falls below the first reheat amount, the measured value of the indoor temperature sensor T2-4 may rise. In this case, as shown in Figure 6, the room temperature of the air-conditioned room 202-204 is lowered by increasing the supply airflow of only the airflow control device 242-244 for that air-conditioned room 202-204. This makes it possible to adjust the room temperature of the air-conditioned room 202-204 without changing the target output temperature of the air conditioner 14.

[0043] On the other hand, if the reheat amount of the reheat section 212-214 of any of the air-conditioned rooms 202-204 exceeds the second reheat amount, the target output temperature SP of the air conditioner 14 is increased. The second reheat amount can be set so that the output of the reheat section 212-214 is 100% or close to 100%, for example, 90% or more. In the following explanation, the second reheat amount is assumed to be 100%.

[0044] The above control can be implemented according to the following procedure.

[0045] Each temperature controller TIC2-4 in each of the air-conditioned rooms 202-204 is configured to transmit a hot water valve opening signal HVS2-4 to the air conditioner 14.

[0046] The air conditioner 14 is equipped with two low selectors LSL1-2, and the hot water valve opening signal HVSL with the lowest opening degree among the automatic valves MV2-4 of the reheat section 212-214 is input to the temperature controller TIC1.

[0047] Furthermore, the air conditioner 14 is equipped with two high selectors HSL11-12, and the hot water valve opening signal HVSL, which has the highest opening degree among the automatic valves MV2-4 of the reheat section 212-214, is input to the temperature controller TIC1.

[0048] First, the output of the heating coil 143 of the air conditioner 14 is controlled so that the output of at least one reheat unit 212-214 in the air-conditioned rooms 202-204 is less than or equal to a first reheat amount. The reheat unit 212-214 whose output is adjusted to less than or equal to the first reheat amount is usually the reheat unit of the air-conditioned room (any of 202-204) with the largest heat load. Specifically, the hot water valve opening signal HVS2-4 of the automatic valve MV2-4 of the reheat unit 212-214 is transmitted to the air conditioner 14, and the low selector LSL1-2 of the air conditioner 14 selects the smallest hot water valve opening signal HVSL, which is then input to the temperature controller TIC1. Since the hot water valve release signal HVS2-4 corresponds to the reheat amount of the reheat units 212-214, the temperature controller TIC1 determines whether the selected hot water valve release signal HVSL is zero (i.e., the output of any of the corresponding reheat units 212-214 is zero). If the hot water valve release signal HVSL is zero, the automatic valve MV12 is adjusted so that the output of the heating coil 143 is maintained.

[0049] On the other hand, if the hot water valve opening signal HVSL is greater than zero, the temperature controller TIC1 corrects the target supply air temperature SP of the supply air SA to the increased side. The target supply air temperature SP can have a set range. When the target supply air temperature SP is corrected to the increased side, as shown in Figure 8, the temperature controller TIC1 increases the opening of the automatic valve MV12 of the heating coil 143. As a result, the supply air SA becomes the increased target supply air temperature SP, the temperature of the supply air SA supplied to each air-conditioned room 202-204 increases, and the opening of the automatic valves MV2-4 of the reheat section 212-214 of each air-conditioned room 202-204 decreases. The hot water valve opening signal HSV2-4 of the automatic valve MV2-4 is fed back to the temperature controller TIC1 again, and the above control continues until the minimum value HSVL of any of the hot water valve opening signals HSV2-4 becomes zero. Then, when the hot water valve release signal HVSL becomes zero, the automatic valve MV12 is adjusted so that the output of the heating coil 143 is maintained.

[0050] As a result, the output of the reheat units 212-214 in each air-conditioned room 202-204 is reduced, thus achieving energy savings.

[0051] Furthermore, with the above control, if the opening degree of the automatic valve MV12 is adjusted, the heat load may increase in the air-conditioned rooms 202-204 where the output of the reheating units 212-214 is zero, causing the room temperature TE to rise. In this case, the temperature controller TIC1 does not immediately correct the target supply air temperature SP to the increased stage side and increase the opening degree of the automatic valve MV12 of the heating coil 143, but rather temporarily increases the supply air volume of the air volume control device 242-244 of the air-conditioned room (either of 202-204). As the room temperature of the air-conditioned room 202-204 decreases due to the increase in supply air volume, the room temperature of the air-conditioned room 202-204 can be adjusted without changing the target output temperature SP of the air conditioner 14. Therefore, the air conditioner 14 does not need to change the output of the heating coil 143, thus reducing energy consumption associated with output changes.

[0052] On the other hand, if the output of the reheat section 212-214 of any of the air-conditioned rooms 202-204 reaches 100%, that is, if the hot water valve opening signal HSV2-4 reaches 100%, the target delivery temperature SP of the air conditioner 14 is corrected to increase the setting. The hot water valve opening signal HSV2-4 is selected by the high selector HSL11-12 of the air conditioner 14, which selects the hot water valve opening signal HSVH with the largest value, and this hot water valve opening signal HSVH is input to the temperature controller TIC1. If this hot water valve opening signal HSVH is less than 100%, the temperature controller TIC1 maintains the output of the heating coil 143 with the same setting. On the other hand, if the hot water valve opening signal HSVH reaches 100%, the room temperature of the air-conditioned room 202-204 cannot be maintained, and there is a risk that the room temperature will drop. For this reason, the temperature controller TIC1 corrects the target delivery temperature SP to increase the setting. Furthermore, the target supply air temperature SP can be set to a range. When the target supply air temperature SP is corrected to the increased level, as shown in Figure 7, the temperature controller TIC1 increases the opening of the automatic valve MV12 of the heating coil 143. As a result, the supply air SA becomes the increased target supply air temperature SP, the temperature of the supply air SA supplied to each air-conditioned room 202-204 increases, and the opening of the automatic valves MV2-4 of the reheat section 212-214 of each air-conditioned room 202-204 decreases. The hot water valve opening signal HSV2-4 of the automatic valve MV2-4 is fed back to the temperature controller TIC1 again, and the above control continues until the maximum value HSVH of any of the hot water valve opening signals HSV2-4 falls below 100%. Then, when the hot water valve opening signal HVSH falls below 100%, the automatic valve MV12 is adjusted so that the output of the heating coil 143 is maintained. [Examples]

[0053] The energy reduction rate achieved by implementing the present invention was calculated for the air conditioning system 10 described using Figure 1. Note that the figures are approximate.

[0054] Figure 9 shows the flow rates of outside air (OA), supply air (SA), and return air (RA), as well as the output of the heating coil 143 of the air conditioner 14. For clarity, some symbols and equipment details have been omitted in Figure 9; please refer to Figure 1 for the symbols and other details.

[0055] <Example 1> Consider the case where the air volume of the supply air SA for each of the air-conditioned rooms 202, 203, and 204 is 5000 m S4 / h, with a total of 15000 m 3 / h. Also refer to the air diagrams in Figures 10 and 11.

[0056] Normally, as shown in Figure 9, for the air-conditioned room 202, assume that the supply air SA is 5000 m 3 / h, at 15°C, and the room temperature TE2 is maintained at 23°C (the opening degree of the automatic valve MV2 of the reheater 212 is 0%). Also, for the air-conditioned rooms 203 and 204, assume that the supply air SA is 5000 m 3 / h, at 18°C, and the room temperatures TE3 and TE4 are maintained at 23°C (the opening degrees of the automatic valves MV3 and MV4 of the reheaters 213 and 214 are 30% and 2 respectively).

[0057] In this state, if the heat load of the air-conditioned room 202 increases and the room temperature TE2 becomes 25°C, then the indoor load increases from the initial Δt = 8°C (room temperature 23°C - temperature of the supply air SA 15°C) to Δt = 10°C (room temperature 25 - temperature of the supply air SA 15°C).

[0058] -Conventional method- When the load of the air-conditioned room increases, in order to maintain the room temperature at 23°C, the temperature of the supply air SA is lowered from 15°C to 13°C for response. As a result, the room temperature TE2 of the air-conditioned room 202 is maintained at 23°C, but for the air-conditioned rooms 203 and 204, since the room temperatures TE3 and TE4 decrease, it is necessary to increase the opening degrees of the automatic valves MV3 and MV4 of the reheaters 213 and 214 to increase the output.

[0059] That is, the energy increases q S1 、q S3 、q S4 of the heating coil 143 of the air conditioner 14 and the reheaters 213 and 214 are respectively q S1 = 15000×1.2×2°C×1 / 3600 = approximately 10 kW q S3 = 5000×1.2×2°C×1 / 3600 = approximately 3.3 kW [[ID=4�]]q S4= 5000 × 1.2 × 2℃ × 1 / 3600 = approximately 3.3kW The total energy increment is q S1 +q S3 +q S4 This amounts to approximately 16.6kW.

[0060] -The method of this invention- On the other hand, in this invention, when the load on the air-conditioned room 202 increases, the airflow control device 242 increases to maintain the room temperature TE2 of the air-conditioned room 202 at 23°C. Specifically, when the load (Δt = 10°C), q S1 =5000×1.2×10℃×1 / 3600=approx. 16.7kW Therefore, this q S1 To address this by increasing the airflow, the required airflow Q for the air-conditioned room 202 is: 16.7kW = Q × 1.2 × 8°C × 1 / 3600, i.e., Q = 6263m 2 / h This results in 1263m 3 It will be necessary to increase the airflow in room 202, which is the air-conditioned room, by / h.

[0061] Airflow: 1263 m³ 2 The energy increase due to the increase in / h is the increase in cooling energy Δq of the air conditioner 14. S1 And the increment Δq of the driving force of the air conditioner fan 145 f It is the sum of the two.

[0062] Increment in cooling energy Δq S1 teeth, q S1 = 15000 × 1.2 × (21.98℃ - 15℃) × 1 / 3600 = approximately 34.9kW and q S1 = 16263 × 1.2 × (22.05℃ - 15℃) × 1 / 3600 = approximately 38.2 kW (where the mixture MA(P) is at 22.05℃, see Figure 11) - difference Δq S1 This is approximately 3.3kW.

[0063] Furthermore, the driving force increment Δq of the air conditioner fan 145 f teeth, Δqf = 7.5kW × (16263 / 15000) 3 -7.5kW = approximately 2.0kW This is the result.

[0064] Therefore, the airflow is 1263 m³ 2 The energy increase due to the increase in / h is approximately 3.3kW + approximately 2.0kW = approximately 5.3kW.

[0065] As a result, the method of the present invention was able to reduce the energy increase by approximately 68% (approximately 16.6kW - approximately 5.3kW) / 16.6kW compared to the conventional method.

[0066] <Example 2> In the above embodiment, under normal circumstances, as shown in parentheses in Figure 9, the room 202 to be air-conditioned has a supply air SA of 1000 m³. 3 / h, 15℃, room temperature TE2 is 23℃, air-conditioned rooms 203 and 204 have a supply air SA of 7000m 3 Assume the energy consumption is 18°C, room temperature TE3,4 is maintained at 23°C. In this case, the energy increase could be reduced by approximately 94%.

[0067] As can be seen from Example 2, in the present invention, the smaller the airflow in the air-conditioned room with increased load, the greater the energy-saving effect.

[0068] The above description of the embodiments is for the purpose of explaining the present invention and should not be interpreted as limiting or narrowing the scope of the invention described in the claims. Furthermore, the configuration of each part of the present invention is not limited to the above embodiments, and various modifications are possible within the technical scope described in the claims.

[0069] For example, in the above embodiment, the air conditioning system 10 of the present invention individually controls each piece of equipment in the air conditioning device 11 and the room to be air-conditioned 20 using a temperature controller TIC1-4, a dew point temperature controller DIC1, etc. However, some or all of these can also be controlled by a control device that includes a computer such as a CPU and a storage device such as volatile or non-volatile memory. Furthermore, the control device can also be defined as a configuration that includes a temperature controller TIC1-4, a dew point temperature controller DIC1, etc. [Explanation of Symbols]

[0070] 10. Air conditioning system 11 Air conditioner 12 Total heat exchanger 13 Latent heat treatment device 14. Air conditioner 142 Cooling coil 143 Heating coil 20(202-204) Rooms subject to air conditioning 21(212-214) Reheating section 24(242-244) Airflow control device T1 Air supply temperature measurement sensor (duct insertion temperature sensor) T2-4 Room Temperature Measurement Sensor (Indoor Temperature Sensor)

Claims

1. An air conditioning system that mixes outside air with return air from multiple rooms to be air-conditioned, and supplies supply air adjusted to a target temperature and target humidity. A supply air temperature measuring sensor for measuring the temperature of the supply air, Each of the aforementioned air-conditioned rooms is provided with a reheating unit that reheats the supply air, A supply and exhaust device is provided in each of the aforementioned rooms to be air-conditioned, which introduces the supply air that has passed through the reheat section into the room to be air-conditioned, and sends return air from the room to be air-conditioned to the air conditioning unit, A room temperature measuring sensor for measuring the room temperature of the room to be air-conditioned, An air conditioning system including, The target discharge temperature of the air conditioning system is adjusted so that the reheat amount of the reheat section of any of the rooms to be air-conditioned is less than or equal to the first reheat amount. In this state, if the measured value of the room temperature sensor of the reheat section of the room to be air-conditioned rises, the air supply and exhaust system of the room to be air-conditioned is controlled so that the air supply flow rate to the room increases. Air conditioning system.

2. When the reheat amount of the reheat section of any of the rooms to be air-conditioned becomes equal to or greater than the second reheat amount, the target output temperature of the air conditioning system is raised. The air conditioning system according to claim 1.

3. The air conditioning system comprises a latent heat treatment device for cooling and dehumidifying the outside air, and an air conditioner for adjusting the humidity of the mixture of the outside air and the return air to the target discharge temperature and target discharge humidity. The air conditioning system according to claim 2.

4. The supply and exhaust system includes an airflow control device for introducing the mixed air into the room to be air-conditioned, and a room pressure control damper for returning the air from the room to be air-conditioned to the air conditioning system. The air conditioning system according to claim 3.

Images