Air treatment system commissioning method

Abstract

To provide a system capable of automatically adjusting an air volume supplied to each target space to a required air volume.SOLUTION: In a test run method of an air treatment system, as a first step, an air volume target value Qy, which is a target value of an air volume supplied to a target space 100, is set in a second unit 30. As a second step, the second unit 30 is operated, and it is confirmed whether or not a detection value of second air volume detection means 32 is the air volume target value Qy. In the test run method of the air treatment system, since a second controller 52 of the second unit 30 determines front-rear differential pressure even when the air volume of a duct 40 fluctuates, and automatically controls a rotation speed of a second fan 31 based on the front-rear differential pressure, it is easier to adjust the air volume than conventional arts that adjust the air volume according to the damper opening.SELECTED DRAWING: Figure 15B

Description

[Technical Field]

[0001] Regarding the commissioning method for the air treatment system. [Background technology]

[0002] Conventionally, air conditioning systems that control the rotation speed of a blower fan to conditioned the air in a room have been widely used. For example, the air conditioning system described in Patent Document 1 (Japanese Patent Publication No. 10-253132) includes an air conditioning unit having a heat exchanger and an air conditioning fan, a plurality of ventilation units having blower fans, a duct that distributes conditioned air from the air conditioning unit to the ventilation units, and a shutter that adjusts the amount of air passing through the duct. [Overview of the project] [Problems that the invention aims to solve]

[0003] In the air conditioning system described above, the damper opening is adjusted for each air-conditioned space so that the amount of air supplied to that space reaches the target airflow.

[0004] However, adjusting the damper opening for one target space changes the amount of air supplied to other target spaces, requiring repeated adjustments of the damper openings.

[0005] Therefore, there is a challenge in providing a system that automatically adjusts the amount of air supplied to each target space so that it meets the required airflow. [Means for solving the problem]

[0006] The commissioning method for the air treatment system relating to the first aspect is a commissioning method for an air treatment system in which a fan unit connected to a duct communicating between the space to be air treated and the air treatment unit transports air that has undergone predetermined treatment by the air treatment unit to the space to be air treated. The fan unit comprises a fan with a variable rotational speed, a casing, a detection unit, and a control unit. The casing has an intake port and an outlet port and houses the fan. The detection unit detects the airflow rate or an equivalent value of the airflow rate of the fan. The control unit controls the rotational speed of the fan. Based on the value detected by the detection unit, the control unit determines the differential pressure between the intake port and the outlet port, which is the pressure difference of the air, and automatically controls the rotational speed of the fan based on the differential pressure between the intake port and the outlet port. In the first step, an airflow target value, which is the target value of the airflow rate to be supplied to the space to be air treated, is set for the fan unit. In the second step, the fan unit is operated and it is confirmed whether the value detected by the detection unit is the airflow target value.

[0007] In this air treatment system's trial operation method, even if there are fluctuations in the airflow within the duct, the control unit of the fan unit determines the differential pressure across the duct and automatically controls the fan speed based on that differential pressure. This makes airflow adjustment easier compared to conventional systems that adjust airflow by damper opening.

[0008] The commissioning method for the air treatment system relating to the second perspective is the commissioning method for the air treatment system relating to the first perspective, wherein the control unit stores the detected value of the detection unit, the fan rotation speed, and the differential pressure across the front and rear as initial values ​​when the detected value of the detection unit is equal to the target airflow value.

[0009] In the commissioning method for this air treatment system, if the ductwork at the site is not installed according to the design specifications, the fan speed may be increased to provide a margin of safety. In such cases, if the initial airflow target value is recorded—whether it was set to the design value or with a margin of safety—this can be used for readjustment after any abnormalities are found.

[0010] The commissioning method for the air treatment system according to the third viewpoint is a commissioning method for the air treatment system according to the first or second viewpoint, wherein the fan unit includes at least a first fan unit and a second fan unit. The duct includes at least a first path from the air treatment unit to the first fan unit and a second path from the air treatment unit to the second fan unit. When the control unit operates the second fan unit, causing a change in the airflow resistance of the first path and a change in the differential pressure across the first fan unit, the control unit changes the rotational speed of the fan of the first fan unit to a rotational speed that maintains the target airflow value of the first fan unit at the differential pressure across the front and rear after the change.

[0011] In this air treatment system's trial operation method, even if the operation of the second fan unit causes fluctuations in the airflow path connected to the first fan unit, the control unit determines the differential pressure across the path and automatically controls the fan speed based on that differential pressure. Therefore, compared to conventional types that adjust airflow by damper opening, airflow adjustment is easier.

[0012] The commissioning method for the air treatment system according to the fourth perspective is the commissioning method for the air treatment system according to the third perspective, wherein the first path includes a main duct connected to an air treatment unit and a first branch duct branching off from the main duct and connected to a first fan unit. The second path includes a main duct and a second branch duct branching off from the main duct and connected to a second fan unit.

[0013] The commissioning method for the air treatment system relating to the fifth perspective is a commissioning method for the air treatment system relating to the third or fourth perspective, wherein the first fan unit transports air between the air treatment unit and the first space, which is the target space. The target airflow value of the first fan unit when operating it is the maximum airflow value required for the first space, which is pre-entered.

[0014] In the method for commissioning this air treatment system, by setting the maximum air volume value required for the first space as the air volume target value, it is possible to confirm not only whether the maximum air volume value can be achieved but also whether the duct construction is in accordance with the design.

[0015] The method for commissioning the air treatment system according to the sixth aspect is the method for commissioning the air treatment system according to the fifth aspect, in which the second fan unit conveys air between the air treatment unit and a second space different from the first space. The air volume target value of the second fan unit when the second fan unit is operated is the maximum air volume value required for the second space input in advance.

[0016] In the method for commissioning this air treatment system, by setting the maximum air volume value required for the second space as the air volume target value, it is possible to confirm not only whether the maximum air volume value can be achieved but also whether the duct construction is in accordance with the design.

[0017] The method for commissioning the air treatment system according to the seventh aspect is the method for commissioning the air treatment system according to the sixth aspect, in which the air treatment unit has a heat source part and a heat exchange part that performs heat exchange between the heat medium from the heat source part and air. The maximum air volume value required for each of the first space and the second space is determined based on the maximum heat load generated in each of the first space and the second space.

[0018] In the method for commissioning this air treatment system, the air treatment system performs not only ventilation but also air conditioning.

[0019] The method for commissioning the air treatment system according to the eighth aspect is the method for commissioning the air treatment system according to any one of the first to seventh aspects, in which the air treatment system includes a remote operation device. The remote operation device has an input part for inputting the air volume target value of the fan unit and a display part for displaying the air volume of the fan unit.

[0020] In the commissioning method of this air treatment system, it is possible to confirm whether the air volume during commissioning is insufficient with respect to the target air volume value by the numerical value displayed on the display unit. Also, a plurality of fan units can be centrally managed by one remote operation device.

[0021] The commissioning method of the air treatment system according to the ninth aspect is the commissioning method of the air treatment system according to any one of the first aspect to the eighth aspect, wherein the air treatment system, prior to commissioning, After calculating a first pressure loss value, which is a part of the total pressure loss value from the air treatment unit to the target space, a fan unit is selected based on the relationship between the air volume and the differential pressure before and after, the target air volume value, and the first pressure loss value.

Brief Description of the Drawings

[0022] [Figure 1A] It is a conceptual diagram showing the configuration of the air treatment system according to the first embodiment equipped with the second unit. [Figure 1B] It is a cross-sectional side view of the first unit for explaining the flow of outdoor air and supply air. [Figure 1C] It is a cross-sectional side view of the first unit for explaining the flow of indoor air and exhaust air. [Figure 1D] It is a perspective view showing an example of the total heat exchange element. [Figure 1E] It is a schematic diagram showing an example of the configuration of the second unit. [Figure 2] It is a block diagram for explaining the configuration of the controller. <00,00112> [Figure 3] It is a graph showing the relationship between the air volume and the duct resistance with the duct length as a parameter. [Figure 4] It is a graph showing the result of measuring the change in air volume when the rotational speed of the fan motor is changed by 1 [r / m] while changing the differential pressure before and after the second unit. [Figure 5] It is a graph showing the relationship between the air volume and the rotational speed of the fan motor with the differential pressure before and after as a parameter. [Figure 6]This graph shows the relationship between airflow and fan motor rotation speed, with the differential pressure across the front and rear as a parameter. [Figure 7] This graph shows the relationship between wind speed and fan motor rotation speed, with the differential pressure between the front and rear sections as a parameter. [Figure 8] This graph shows the relationship between the differential pressure across the front and rear, the coefficient, and the constant term, derived from Figure 7. [Figure 9] This graph shows the relationship between airflow and fan motor rotation speed, with the differential pressure across the front and rear as a parameter. [Figure 10] This graph shows the relationship between wind speed and fan motor rotation speed. [Figure 11] This is a flowchart for airflow control. [Figure 12] This graph shows the relationship between flow rate and differential pressure across the second fan, with the rotation speed of the second fan motor as a parameter. [Figure 13] Figure 12 is a graph showing the curves that pass through the extreme points at each rotational speed. [Figure 14] This is a configuration comparison diagram showing a comparison between the configuration of a conventional air treatment system and the configuration of this embodiment. [Figure 15A] This table compares the processes from design to operation (management) of an air treatment system between a conventional system and this embodiment. [Figure 15B] This is a flowchart for the trial run mode. [Figure 16] This table compares the components subject to duct pressure loss calculations in the conventional system with those in this embodiment. [Figure 17A] This graph shows the relationship between airflow and differential pressure in a conventional system. [Figure 17B] This graph shows the relationship between airflow and differential pressure in this embodiment. [Figure 18] This is a diagram showing the configuration of the air treatment system according to the second embodiment, in which the second unit is installed. [Figure 19] This is a block diagram illustrating the controller configuration. [Figure 20]This is a diagram showing the configuration of an air treatment system according to a modified example of the second embodiment in which the second unit is installed. [Modes for carrying out the invention]

[0023] <First Embodiment> (1) Overall structure Figure 1A is a diagram showing the configuration of the air treatment system 10 with the second unit 30 installed. In Figure 1A, the air treatment system 10 is located in the ceiling space of one floor of building BL and ventilates the room.

[0024] The air treatment system 10 comprises a first unit 20 equipped with a total heat exchanger, second units 30A to 30D that function as either a supply fan unit or an exhaust fan unit, and a duct 40 that connects the first unit 20 to the air treatment target spaces 100A to 100D.

[0025] For the sake of explanation, the target spaces 100A to 100D shown in Figure 1A will be referred to as the first target space 100A, the second target space 100B, the third target space 100C, and the fourth target space 100D, respectively.

[0026] Hereafter, when describing each of the second units 30A to 30D corresponding to each target space 100A to 100D individually, they will be identified by the names first fan unit 30A, second fan unit 30B, third fan unit 30C, and fourth fan unit 30D, starting from the first target space 100.

[0027] The duct 40 includes an air supply duct 41 and a return air duct 46. The first unit 20 is connected to an outside air duct 18, an air supply duct 41, a return air duct 46, and an exhaust duct 19.

[0028] The outside air duct 18 constitutes an air passage connecting the opening 4 leading outside the building BL to the first unit 20. The supply air duct 41 constitutes an air passage connecting the first unit 20 to the outlets 2 provided in each target space 100A to 100D.

[0029] The return air duct 46 constitutes an air passage connecting the intake ports 3 provided in each target space 100A to 100D to the first unit 20. The exhaust duct 19 constitutes an air passage connecting the first unit 20 to the opening 5 that leads outside the building BL.

[0030] The air supply duct 41 is branched into multiple air supply branch ducts 42A to 42D by the air supply branch chamber 91. The multiple air supply branch ducts 42A to 42D branched from the air supply branch chamber 91 are designated as the first air supply branch duct 42A, the second air supply branch duct 42B, the third air supply branch duct 42C, and the fourth air supply branch duct 42D, in order from the first target space 100A side.

[0031] The return air duct 46 is branched into multiple return air branch ducts 47A to 47D by the return air branch chamber 92. The multiple return air branch ducts 47A to 47D branched from the return air branch chamber 92 are designated as the first return air branch duct 47A, the second return air branch duct 47B, the third return air branch duct 47C, and the fourth return air branch duct 47D, in order from the first target space 100A side.

[0032] The first unit 20 includes units that remove dust from the air passing through the unit, change the air temperature, change the air humidity, remove predetermined chemical components and predetermined pathogens from the air, and units that specialize in removing dust from the air and ventilation. The first unit 20 in the first embodiment is the latter.

[0033] The second unit 30 (first fan unit 30A to fourth fan unit 30D) includes a second unit connected to each supply air branch duct 42A to 42D and a second unit connected to each return air branch duct 47A to 47D.

[0034] The second units connected to each of the supply air branch ducts 42A to 42D are connected to the air outlet 2 by supply air communication ducts 43A to 43D. The supply air communication ducts 43A to 43D are designated as the first supply air communication duct 43A, the second supply air communication duct 43B, the third supply air communication duct 43C, and the fourth supply air communication duct 43D, in order from the first target space 100A side.

[0035] The second units connected to each of the return air branch ducts 47A to 47D are connected to the intake port 3 by return air communication ducts 48A to 48D. The return air communication ducts 48A to 48D are designated as the first return air communication duct 48A, the second return air communication duct 48B, the third return air communication duct 48C, and the fourth return air communication duct 48D, in order from the first target space 100A side.

[0036] In the air treatment system 10, since the first unit 20 does not have a fan, the airflow within the first unit 20 is generated by the operation of the second unit 30.

[0037] Therefore, changes in the differential pressure across the second unit 30 are mainly caused by changes in the airflow of the fans of the other second units 30.

[0038] (2) Detailed configuration (2-1) Unit 1, 20 Figure 1B is a cross-sectional side view of the first unit 20 illustrating the flow of outdoor and supply air. Figure 1C is a cross-sectional side view of the first unit illustrating the flow of indoor and exhaust air. Figure 1D is a perspective view showing an example of the total heat exchange element 12.

[0039] In Figures 1B to 1D, the first unit 20 is a total heat exchanger unit. The first unit 20 includes a housing 11, a total heat exchange element 12, a first filter 13, and a second filter 14.

[0040] (2-1-1) Housing 11 and total heat exchange element 12 The housing 11 houses a roughly rectangular prism-shaped total heat exchange element 12 inside. The housing 11 is provided with an opening 11a for connecting to the outside air duct 18, an opening 11b for connecting to the supply air duct 41, an opening 11c for connecting to the return air duct 46, and an opening 11d for connecting to the exhaust duct 19.

[0041] The space inside the housing 11 is mainly divided into four spaces: the first space SP1, the second space SP2, the third space SP3, and the fourth space SP4. The first space SP1 is located on the side of the outside air duct 18 relative to the total heat exchange element 12. The second space SP2 is located on the side of the supply air duct 41 relative to the total heat exchange element 12. The third space SP3 is located on the side of the return air duct 46 relative to the total heat exchange element 12. The fourth space SP4 is located on the side of the exhaust duct 19 relative to the total heat exchange element 12.

[0042] Therefore, the outdoor space SP1 is connected to the outside by the outdoor air duct 18. The indoor space SP2 is connected to the indoor space SP2 by the supply air duct 41. The indoor space SP3 is connected to the indoor space SP3 by the return air duct 46. The outdoor space SP4 is connected to the outside by the exhaust duct 19.

[0043] As shown in the side cross-sectional view of Figure 1B, the outdoor air OA from outside the room reaches the total heat exchange element 12 via the outside air duct 18 when the second unit 30 is activated. Furthermore, the air that has passed through the total heat exchange element 12 is supplied to the room as fresh supply air SA via the supply air duct 41.

[0044] As shown in the side cross-sectional view of Figure 1C, the indoor air RA in the room reaches the total heat exchange element 12 via the return air duct 46 when the second unit 30 is activated. Furthermore, the air that has passed through the total heat exchange element 12 becomes exhaust air EA and is discharged outside the room.

[0045] As shown in Figure 1D, the total heat exchange element 12 performs total heat exchange between the indoor air RA and the outdoor air OA while preventing them from mixing with each other. In other words, the total heat exchange element 12 performs latent heat exchange and sensible heat exchange simultaneously and continuously between the indoor air RA and the outdoor air OA.

[0046] (2-1-2) First filter 13 and second filter 14 The first filter 13 is positioned to cover the portion of the total heat exchange element 12 that is exposed to the third space SP3. The second filter 14 is positioned to cover the portion of the total heat exchange element 12 that is exposed to the first space SP1.

[0047] As a result, dust can be removed from both the outdoor air (OA) and the indoor air (RA) before they are supplied to the total heat exchange element 12, preventing dust from flowing into the total heat exchange element 12.

[0048] (2-2) Unit 2, 30 Figure 1E is a schematic diagram showing an example of the configuration of the second unit 30. The second unit 30 includes a second fan 31, a fan motor 31b for rotating the second fan 31, and a second airflow detection means 32.

[0049] Each fan motor 31b is connected to a corresponding second controller 52, and the rotational speed is sent from the fan motor 31b to the second controller 52. Each second airflow detection means 32 is connected to a corresponding second controller 52.

[0050] The second airflow detection means 32 can be, for example, an airflow sensor, an air velocity sensor, or a differential pressure sensor. In this embodiment, the second airflow detection means 32 detects the amount of air blown by the second fan 31.

[0051] The airflow value detected by the second airflow detection means 32 is input to the second controller 52. The airflow detected by the second airflow detection means 32 is the airflow flowing through the supply air communication ducts 43A to 43D, and is also the supply airflow supplied from each second unit 30 to each target space 100A to 100D.

[0052] (2-3) Remote control 55 Each target space 100A to 100D is equipped with a remote control 55 for remotely setting the airflow for the corresponding second unit 30A to 30D. The remote control 55 is connected to either the first controller 51 or the second controller 52, which constitute the controller 50 described later.

[0053] The remote control 55 has an input unit 550 for inputting the target airflow value of the second unit 30, and a display unit 551 for displaying the airflow of the second unit 30.

[0054] In the first embodiment, the remote control 55 is connected to the second controller 52, and the airflow set from the remote control 55 is input to the first controller 51 via the second controller 52 as an airflow setting value.

[0055] For the sake of explanation, the second controller 52 and remote control 55 are denoted by the last letter of the corresponding target space 100A to 100D. For example, the "second controller 52" and "remote control 55" of the "first fan unit 30A" corresponding to the first target space 100A are referred to as the second controller 52A and remote control 55A.

[0056] (2-4) Controller 50 Figure 2 is a block diagram illustrating the configuration of controller 50. In Figure 2, controller 50 includes a first controller 51 and a plurality of second controllers 52A to 52D. The first controller 51 and the plurality of second controllers 52A to 52D are connected to each other.

[0057] (2-4-1) First controller 51 The first controller 51 includes a processor 51a and a memory 51b. The processor 51a reads the airflow control program stored in the memory 51b and outputs the necessary commands to each of the second controllers 52A to 52D. The memory 51b stores the airflow setting values ​​sent via each of the second controllers 52A to 52D as needed.

[0058] The processor 51a calculates the target airflow values ​​to be supplied to each target space 100A to 100D based on the airflow setting values ​​stored in the memory 51b.

[0059] The above description is an example and is not limited to the contents described above.

[0060] (2-4-2) Second controller 52 The second controller 52 includes a processor 52a and a memory 52b. The processor 52a reads the airflow control program for the second fan 31 stored in the memory 52b and outputs the necessary commands to the second fan 31.

[0061] Memory 52b stores the airflow control program for the second fan 31, as well as the target airflow value output from the first controller 51 and the detected value from the second airflow detection means 32, as needed.

[0062] The processor 52a reads the target airflow value stored in the memory 52b and the value detected by the second airflow detection means 32, and calculates the target rotational speed value for the second fan 31.

[0063] The above description is an example and is not limited to the contents described above.

[0064] (3) Overview of the operation of the air treatment system 10 Each second controller 52A to 52D receives the airflow setting value for each target space 100A to 100D from the corresponding remote control 55A to 55D. Each second controller 52A to 52D stores the input airflow setting value.

[0065] Each second controller 52A to 52D transmits the airflow set value and the measured airflow value to the first controller 51. Based on the airflow set value and the measured airflow value, the first controller 51 determines the target airflow value for each second unit 30A to 30D. The first controller 51 transmits the value of the target airflow value to each second controller 52A to 52D.

[0066] The first controller 51 determines the target airflow value for each second fan 31 according to the target airflow value to be supplied to the target space 100A to 100D, and transmits it to each second controller 52A to 52D. In each second unit 30A to 30D, the rotation speed of the second fan 31 is adjusted by the corresponding second controller 52. The rotation speed adjustment of the multiple second fans 31 is performed independently of each other.

[0067] Each second controller 52A to 52D controls the rotation speed of each second fan 31 to match the supply airflow to the target airflow value. Multiple second controllers 52A to 52D independently control the rotation speeds of multiple second fans 31. Each second controller 52A to 52D increases the rotation speed of each second fan 31 if the airflow detected by the second airflow detection means 32 is less than the target airflow value. Each second controller 52A to 52D decreases the rotation speed of each second fan 31 if the airflow detected by the second airflow detection means 32 is greater than the target airflow value.

[0068] Specific details regarding airflow control will be discussed in section (5) "Airflow Control".

[0069] (4) Regarding duct resistance (4-1) Characteristics of duct resistance The length of the duct 40 connecting the first unit 20 and the second unit 30 varies depending on the position of the outlet of the second unit 30, and also on the property in which the first unit 20 and the second unit 30 are installed.

[0070] There is resistance (hereinafter referred to as duct resistance) between the air flowing through the duct 40 and the inner surface of the duct 40, and the static pressure of the air flowing through the duct 40 decreases due to friction. The longer the duct 40, the greater the duct resistance.

[0071] Figure 3 is a graph showing the relationship between airflow rate and duct resistance, with duct length as a parameter. In Figure 3, the duct resistance changes nonlinearly with respect to the airflow rate of the air flowing through duct 40. Therefore, the airflow rate is not proportional to the fan speed. Consequently, the fan speed that achieves the target airflow rate cannot be calculated proportionally.

[0072] (4-2) Airflow characteristics of the second unit 30 The difference between the static pressure at the outlet and the static pressure at the inlet of the second unit 30 is called the differential pressure across the second unit 30.

[0073] Figure 4 is a graph showing the change in airflow when the rotational speed of the fan motor 31b is changed by 1 [r / m], measured by changing the differential pressure across the second unit 30. The rotational speed of the fan motor 31b before the change was 100 [r / m].

[0074] In Figures 3 and 4, changing the airflow causes fluctuations in duct resistance, which in turn changes the differential pressure across the second unit 30. Since the change in airflow when the fan speed is changed by 1 rpm varies depending on the conditions (differential pressure across the unit), adjustment is difficult. Therefore, unless the fan speed is adjusted to account for the change in duct resistance, the target airflow value may not be reached.

[0075] For example, as shown in Figure 5, the airflow rate is 10 [m³ 3 [min] to 15[m 3 Even when changing to [ / min], the amount of rotational speed change required for the fan motor 31b will differ if the duct resistance is different, even if the amount of airflow change is the same. This is because the duct resistance also changes with the change in airflow. Therefore, an airflow adjustment function that takes into account the change in duct resistance is necessary.

[0076] Furthermore, as shown in Figure 1A, when the supply air branch ducts 42A to 42D, which branch off from the supply air duct 41, are each connected to the second unit 30, the differential pressure across the second unit 30 is affected by the airflow changes of the other second units 30.

[0077] Furthermore, as shown in Figure 6, if the airflow of the other second unit 30 changes and the differential pressure between the front and rear increases to the dotted line in Figure 6, simply maintaining the rotational speed of the fan motor 31b will result in an airflow of 10 [m³ 3 [min] to 5[m] 3 The airflow will decrease to the initial 10[m³ / min]. 3 To maintain the [ / min] condition, the rotational speed of the fan motor 31b must be increased.

[0078] On the other hand, if the differential pressure between the front and rear drops to the dashed line in Figure 6, and the rotation speed of the fan motor 31b is maintained, the airflow will be 10 [m³ 3 [min] to 15[m 3 It increases to the initial airflow of 10 [m³ / min], so the initial airflow is 10 [m³ / min]. 3 To maintain the [ / min] condition, the rotational speed of the fan motor 31b must be reduced.

[0079] Therefore, the second unit 30 also needs an airflow maintenance function that takes into account changes in the differential pressure between the front and rear.

[0080] (5) Air volume control As described above, it has been found that controlling the airflow of the second unit 30 requires an airflow maintenance function that takes into account duct resistance and the airflow of other second units 30. However, the duct length varies depending on the property in which the first unit 20 and the second unit 30 are installed, or the installation location of the second unit 30, and the duct resistance also fluctuates depending on the duct length and the airflow of the air flowing through the duct. Therefore, it is difficult to collect data on the relationship between the rotational speed of the fan motor 31b and the airflow using conventional trial run adjustments.

[0081] Therefore, the applicant focused on the fact that changes in duct resistance manifest as a differential pressure across the front and rear sections, and found that by acquiring information on the airflow rate, wind speed, or differential pressure across the front and rear sections of the second unit 30, and using a function that incorporates the rotational speed of the fan motor 31b and the target airflow rate of the fan motor 31b, the target rotational speed of the fan motor 31b or the amount of change in the rotational speed of the fan motor 31b can be calculated.

[0082] This reduces the amount of preliminary testing required and eliminates the need for commissioning when connecting ducts. The airflow control logic is explained below.

[0083] (5-1) Derivation of the differential pressure △P Figure 7 is a graph showing the relationship between wind speed V and the rotational speed N of the fan motor 31b, with the differential pressure ΔP as a parameter. In Figure 7, when the differential pressure ΔP is the same, the rotational speed N of the fan motor 31b can be expressed as a linear equation in relation to wind speed V using coefficient a and constant term b. N = a × V + b [1]

[0084] As shown in Figure 7, when the differential pressure between the front and rear is constant, equation [1] can be derived by conducting a test to obtain values ​​at least three times.

[0085] Furthermore, Figure 8 is a graph showing the relationship between the differential pressure △P derived from Figure 7, the coefficient a, and the constant term b. In Figure 8, the relationship between the differential pressure △P, the coefficient a, and the constant term b can be expressed by the following equation. a = m × △P + n [2] b = p × △P + q [3]

[0086] From equations [1], [2], and [3] above, the relationship between rotational speed N, wind speed V, and differential pressure ΔP can be expressed by the following equation. N=(m×△P+n)×V+(p×△P+q) [4]

[0087] From equation [4], the following equation can be derived. △P=(Nn×Vq) / (m×V+p) [5]

[0088] [5] means that if the wind speed V when the fan motor 31b of the second fan 31 operates at the rotation speed N is measured, the differential pressure ΔP can be calculated.

[0089] Therefore, the rotation speed N of the fan motor 31b, the wind speed V or the air volume Q of the second fan 31, and the differential pressure ΔP are parameters having a relationship in which one of the remaining values is derived from two of those values.

[0090] (5-2) Air volume adjustment function considering duct resistance change From the above formula [5] and the theoretical formula of the fan, a calculation formula for calculating the target rotation speed Ny can be derived. The relationship among the current differential pressure ΔPx, the current air volume Qx, the target differential pressure ΔPy, and the target air volume Qy is from the theoretical formula of the fan, ΔPy / ΔPx=(Qy / Qx) 2 [6] becomes.

[0091] From the above formula [5] and [6], (Ny - n×Vy - q) / (m×Vy + p)=(Qy / Qx) 2 ×ΔPx [7] becomes. Also, since Vy=(Qy / Qx)×Vx, Ny=(Qy / Qx) 2 ×ΔPx×{m×(Qy / Qx)×Vx + p}+n×(Qy / Qx)×Vx + q [8] becomes. Hereinafter, this formula [8] is called the first function.

[0092] The technical significance of the first function will be described while referring to FIG. 9. FIG. 9 is a graph showing the relationship between the air volume and the rotation speed of the fan motor 31b with the differential pressure ΔP as a parameter. In FIG. 9, the change in the duct resistance appears as the change in the differential pressure ΔP.

[0093] For example, the rotation speed of the fan motor 31b for maintaining an air volume of 10 [m 3 / min] at a differential pressure of 50 [Pa] is 920 [r / m]. If the duct resistance is constant regardless of the air volume, the air volume is 15 [m3 To change it to [ / min], simply set the rotation speed to 1100 [r / m].

[0094] However, the duct resistance changes by changing the airflow rate. According to Figure 9, when the airflow rate is 15 [m³], the duct resistance changes. 3 By changing the setting to [ / min], the differential pressure across the duct increases to 109.9 [Pa] due to the change in duct resistance. When the differential pressure across the duct is 109.9 [Pa], the airflow is 15 [m³ 3 To maintain [ / min], the rotational speed of the fan motor 31b must be maintained at 1348 [r / m].

[0095] Therefore, an airflow adjustment function that takes into account changes in duct resistance is necessary, and the rotational speed Ny in the first function (equation [8] above) is the rotational speed that takes into account changes in duct resistance.

[0096] When the airflow target value Qy, which is the airflow instruction value from the first controller 51, is changed, the second controller 52 uses the first function to calculate the target rotational speed value of the fan motor 31b of the second fan 31.

[0097] (5-3) Airflow adjustment function that takes into account changes in differential pressure between front and rear If the differential pressure △P does not change after the rotational speed of the fan motor 31b reaches the target rotational speed, that rotational speed will be maintained. However, if the airflow of the other second unit 30 changes, the differential pressure △P will change.

[0098] Figure 10 is a graph showing the relationship between wind speed and the rotational speed of the fan motor 31b. In Figure 10, for example, the rotational speed of the fan motor 31b required to maintain the target wind speed Vy at a differential pressure of 50 [Pa] is 980 [r / m].

[0099] Here, if the differential pressure ΔP increases to the dotted line in Figure 10, simply maintaining the rotational speed of the fan motor 31b at 980 [r / m] will result in insufficient airflow because the wind speed will drop to Vx.

[0100] To maintain the target airflow value, the wind speed needs to be returned from Vx to Vy, which requires increasing the rotational speed of the fan motor 31b by 200 r / m to 1180 r / m.

[0101] The amount of rotational speed change △N of this fan motor 31b is obtained from equations [2] and [4], △N=a×(Vy-Vx) [9] This is the result. Hereafter, we will refer to this equation [9] as the second function.

[0102] The second function is used when calculating the amount of rotational speed change required for the fan motor 31b, even though the target airflow value Qy remains unchanged, due to fluctuations in the differential pressure ΔP.

[0103] Figure 11 is a flowchart of the airflow control process. The following explanation of airflow control will refer to Figure 11.

[0104] (Step S1) First, in step S1, the second controller 52 determines whether or not it has received the airflow target value Qy from the first controller 51. If the second controller 52 has received the airflow target value Qy, it proceeds to step S2. If the second controller 52 has not received the airflow target value Qy, it proceeds to step S6.

[0105] (Step S2) Next, in step S2, the second controller 52 calculates a target wind speed Vy that achieves the target airflow Qy.

[0106] (Step S3) Next, in step S3, the second controller 52 updates the wind speed target value Vy to the value calculated in step S2.

[0107] (Step S4) Next, in step S4, the second controller 52 calculates the target rotational speed Ny of the fan motor 31b, which realizes the wind speed target value Vy updated in step S3, using the first function.

[0108] (Step S5) Next, in step S5, the second controller 52 updates the target rotational speed value of the fan motor 31b to the value Ny calculated in step S4. After updating the target rotational speed value to Ny, the second controller 52 controls the fan motor 31b so that its rotational speed reaches the target value.

[0109] (Step S6) Next, in step S6, the second controller 52 acquires the value detected by the second airflow detection means 32 as the current wind speed Vx.

[0110] (Step S7) Next, in step S7, the second controller 52 calculates the difference between the target wind speed Vy and the current wind speed Vx.

[0111] (Step S8) Next, in step S8, the second controller 52 calculates the differential pressure △P.

[0112] (Step S9) Next, in step S9, the second controller 52 calculates the coefficient a as a control parameter.

[0113] (Step S10) Next, in step S10, the second controller 52 applies the difference between the wind speed target value Vy calculated in step S7 and the current wind speed Vx, and the coefficient a calculated in step S9, to the second function to calculate the rotational speed change amount △N.

[0114] (Step S11) Next, in step S11, the second controller 52 calculates a target rotational speed value Ny based on the rotational speed change amount △N calculated in step S10.

[0115] (Step S12) Next, in step S12, the second controller 52 updates the rotational speed to the target rotational speed value Ny calculated in step S11. Then, the second controller 52 returns to step S1.

[0116] As described above, when the first controller 51 provides an instruction for an airflow target value, the first program from step S1 to step S5 is executed, and when the first controller 51 does not provide an instruction for an airflow target value, the second program from step S6 to step S12 is executed.

[0117] The first program calculates the target rotational speed using the first function, and the second program calculates the amount of rotational speed change using the second function.

[0118] Furthermore, the rotational speed target value Ny can be calculated using the second function, and the second controller 52 can switch between the first program and the second program. Therefore, even when a new airflow target value Qy or wind speed target value Vy is obtained in the second unit 30, the rotational speed can be controlled by calculating the rotational speed change amount △N using the second function without using the first function.

[0119] (5-4) Surging detection function (5-4-1) Factors causing surging Figure 12 is a graph showing the relationship between airflow Q and the differential pressure △P, with the rotational speed N of the fan motor 31b of the second fan 31 as a parameter. In Figure 12, the horizontal axis represents airflow Q, and the vertical axis represents the differential pressure △P.

[0120] As shown in Figure 12, in the second unit 30, when the airflow Q changes while the rotational speed N of the fan motor 31b of the second fan 31 is kept constant, the differential pressure ΔP across the front and rear surfaces has one extreme value where it changes from rising to falling. Hereafter, the point that shows an extreme value will be called the extreme value point.

[0121] At this extreme point, the airflow counteracts the resistance of the duct 40 connected to the second unit 30. Therefore, as the airflow decreases from this point, the resistance of the duct 40 decreases. Consequently, the airflow then shifts to the right of the extreme point, increasing. As a result, the resistance of the duct 40 increases, pushing back the air. This repeated behavior of air is called surging.

[0122] Surging causes periodic pressure fluctuations, resulting in noise and vibration that adversely affect the equipment. Normally, fans are used in a way that avoids such airflow and its vicinity. However, in the air processing system 10 according to this embodiment, the differential pressure between the front and rear of the second unit 30 fluctuates due to increases and decreases in the discharge pressure of the first unit 20 and the airflow of the other second unit 30, so it may unintentionally reach the extreme value shown in Figure 12.

[0123] (5-4-2) Method for determining surging Figure 13 is a graph showing the curves passing through the extreme points at each rotational speed shown in Figure 12. In Figure 12, surging occurs when the airflow deflects to the left of the extreme point. Therefore, if the combination of airflow and differential pressure is outside the region enclosed by the vertical axis and curve in Figure 13 (hereinafter referred to as the surging region), surging will not occur. The curve shown in Figure 13 can be expressed by equation: f(Q) = r × Q 2 +s × Q

[10] Therefore, r and s can be determined by experimental data.

[0124] (5-4-2-1) Surging determination based on current airflow Qx Therefore, the f(Qx) calculated by substituting the current airflow rate Qx into equation

[10] above corresponds to the differential pressure across the airflow rate Qx that can cause surging.

[0125] If the current differential pressure △Px is within the surge generation region, then △Px - f(Qx) ≥ 0. Conversely, if the current differential pressure △Px is outside the surge generation region, then △Px - f(Qx) < 0.

[0126] For example, when the second controller 52 receives an instruction signal for the target airflow value Qy from the first controller 51, the second controller 52 uses equation [6]: △Py / △Px=(Qy / Qx) 2 Substitute the target airflow value Qy, the current differential pressure △Px, and the airflow value Qx into the equation to calculate the target differential pressure △Py. Furthermore, substitute the target airflow value Qy into the above equation

[10] to calculate f(Qy).

[0127] If the target differential pressure △Py is within the surge generation region, then △Py - f(Qy) ≥ 0. Conversely, if the target differential pressure △Py is outside the surge generation region, then △Py - f(Qy) < 0.

[0128] Therefore, whether or not the target airflow value Qy causes surging can be determined by whether or not △Py-f(Qy)≧0.

[0129] (6) Selection method for the second unit 30 (6-1) Overview of Conventional Systems and This Embodiment Figure 14 is a configuration comparison diagram comparing the configuration of a conventional air treatment system with the configuration of this embodiment. In Figure 14, the upper section shows the schematic configuration of the conventional system, and the lower section shows the schematic configuration of this embodiment.

[0130] In conventional systems, air supplied by the fan of the total heat exchanger unit is guided through ducts to each target space A to D, and the opening of dampers corresponding to each target space A to D is adjusted so that the airflow reaches the target value. For example, when the opening of the damper corresponding to target space A is adjusted, the airflow to the other target spaces B, C and D changes, so the opening of each damper needs to be adjusted repeatedly.

[0131] On the other hand, in this embodiment, the first unit 20 is equipped with a total heat exchange element 12 but does not have a fan. Therefore, air passes through the total heat exchange element 12 when the second fan 31 of the second units 30A to 30D, which correspond to each target space 100A to 100D, is operated. The amount of airflow required for each target space 100A to 100D is automatically adjusted by the second units 30A to 30D, which correspond to each target space 100A to 100D.

[0132] (6-2) Comparison of the Conventional System and This Embodiment in the Design Procedure Figure 15A is a table comparing the processes from design to operation (management) of the air treatment system 10 between a conventional system and this embodiment. In Figure 15A, the processes are divided into four items: design, construction, inspection, and management, and the work procedures are described for each process item.

[0133] This document will explain the procedure of this embodiment (see the right column of the table in Figure 15A), and, where necessary, will introduce the differences from conventional systems.

[0134] (Design procedure A1b) Here, the required ventilation volume (airflow) for each target space 100A to 100D is calculated. The required ventilation volume (airflow target value) is calculated by multiplying the maximum occupancy set for each target space by the required ventilation volume per person.

[0135] (Design procedure A2b) Here, the ventilation path through which air circulates via ducts is determined. The ventilation path is considered while taking into account other equipment such as air conditioners, lighting, and fire alarms.

[0136] (Design procedure A3b) Here, the equipment components are selected. These components include ducts and their sizes, branch connectors, indoor terminals, and outdoor terminals.

[0137] (Design procedure A4b) Here, we calculate the pressure loss in the ventilation path. In this embodiment, a rough calculation of the duct pressure loss is sufficient. In contrast, conventional systems require detailed calculations to accommodate complex ventilation paths.

[0138] Figure 16 is a table comparing the conventional system and this embodiment regarding the components subject to duct pressure loss calculation. In Figure 16, in the conventional system, components whose pressure loss is less than 10% of the total pressure loss are also included in the duct pressure loss calculation.

[0139] In contrast, in this embodiment, components whose pressure loss is less than 10% of the total pressure loss are excluded from the calculation of duct pressure loss.

[0140] In the second unit 30, the second controller 52 utilizes the fact that fluctuations in duct resistance due to airflow fluctuations manifest as changes in the differential pressure across the front and rear sections. The second controller 52 calculates the differential pressure across the front and rear sections from the measured airflow and the rotation speed of the second fan 31, and controls the rotation speed of the second fan 31 to achieve the target airflow value at the calculated differential pressure across the front and rear sections.

[0141] Therefore, even if the airflow fluctuates due to pressure loss from components whose pressure loss accounts for less than 10% of the total pressure loss, the target airflow value can be maintained by controlling the rotational speed of the second fan 31 by the second unit 30.

[0142] Therefore, as long as the second unit 30 is within its operating range, the airflow can be adjusted at the installation site, and the pressure loss calculation only needs to be performed for components whose ratio to the total pressure loss is 10% or more.

[0143] Hereafter, the sum of the component components that cause a loss of 10% or more relative to the total pressure loss will be referred to as the "first pressure loss value."

[0144] The first pressure loss value does not need to be calculated for all ventilation paths; it only needs to be calculated for the ventilation path with the largest pressure loss value among the ventilation paths connecting the first unit 20 to each of the target spaces 100A to 100D. This is because, in the selection of the second unit 30, if the second unit 30 is connected to the ventilation path with the largest pressure loss value, it can also be used as a second unit connected to a ventilation path shorter than that one.

[0145] (Design procedure A5b) Here, the model for the second unit 30 is selected. The method for selecting the blower will be explained below with reference to Figures 17A and 17B.

[0146] (Conventional system) Figure 17A is a graph showing the relationship between airflow and differential pressure in a conventional system. In Figure 17A, the upward-sloping curve represents the relationship between airflow and pressure loss in the ventilation path. As the airflow through the ventilation path increases, the resistance in the duct and other equipment components increases, and the pressure loss increases. The solid line in Figure 17A represents the design value of the pressure loss, and the two dotted lines flanking the solid line represent the upper and lower limits of the variation in pressure loss, taking into account that it may differ from the design value when actually assembled.

[0147] Furthermore, in Figure 17A, the downward-sloping dashed line represents the relationship between the differential pressure across the fan of the total heat exchanger unit and the airflow rate. The two double-dashed lines flanking the dashed line represent the upper and lower limits of the airflow variation for each fan.

[0148] For example, if the target airflow value is 500 m 3 When the value is / h, in a conventional system, the airflow is 500m 3 A unit is selected that can ensure a differential pressure (corresponding to the duct static pressure) in the range where the variation in pressure loss and the variation in airflow overlap at / h.

[0149] (Embodiment) Figure 17B is a graph showing the relationship between airflow and differential pressure in this embodiment. In Figure 17B, the upward-sloping curve represents the relationship between airflow and pressure loss in the ventilation path. The solid line in Figure 17B represents the design value of the pressure loss, and the two dotted lines flanking the solid line indicate the upper and lower limits of the variation in pressure loss, taking into account that it may differ from the design value when actually assembled.

[0150] Furthermore, in Figure 17B, the area enclosed by the four straight lines and two curves represents the drivable range R of the second unit 30.

[0151] In this embodiment, first, the model of the second unit 30 is selected such that the target airflow value Qy is at or near the median of the third range R3, which is the range of airflow that the second unit 30 can change. Therefore, the selection process is easier compared to selecting the model of a unit in a conventional system.

[0152] (Design procedure A6b) Here, we verify the capabilities of the second unit 30. Specifically, we check whether the required capabilities of the second unit 30 are within the operating range R of the selected second unit 30.

[0153] (Explanation of the operating range R of the second unit) The first range R1 of the operable range R represents the range of variation of the first pressure loss value relative to the airflow target value Qy. The second range R2 is the range of the differential pressure ΔPx that the second unit 30 can change. The first range R1 is within the range of the second range R2.

[0154] Pressure loss is a form of airflow resistance, and since it depends on the length of the duct and the airflow rate inside the duct, measuring fluctuations in airflow resistance is extremely difficult. However, fluctuations in the easily measurable differential pressure ΔPx can be used as a substitute.

[0155] Therefore, if the first range R1, which indicates the range of variation of the first pressure loss value with respect to the target airflow value Qy, is within the second range R2 of the differential pressure ΔPx that the second unit 30 can change, then errors in selecting the second unit 30 can be avoided.

[0156] The third range R3 of the operable range R is the range in which the target airflow value Qy can be changed by the second unit 30. The allowable airflow range of the second unit 30 is set considering motor reliability on the lower side and economic rationality in relation to the input to the second fan 31 on the higher side.

[0157] If the adjustable airflow range of the second unit 30 is set too large, reliability will be lost at lower values, and economic rationality will be lost at higher values ​​in relation to the input to the second fan 31. Therefore, if the target airflow value Qy is within the third range of airflow adjustable by the second unit 30, both reliability and economic rationality can be achieved.

[0158] Furthermore, the surging boundary R4 is a boundary (see Figure 13) that passes through the extreme value of the curve (see Figure 12) showing the relationship between the airflow of the second fan 31 and the differential pressure across it, measured for each rotational speed of the second fan 31. The first range R1 does not overlap with the surging boundary R4. Therefore, surging can be prevented.

[0159] In this embodiment, for example, the target airflow value Qy is 500 m 3 For a value of 500 m³ / h, the airflow rate is 500 m³. 3 / h is within the third range of airflow that the second unit 30 can change. Also, airflow of 500m 3 The first range R1, which is the variation range of the first pressure loss value at / h, is 320 to 440 Pa, which is within the second range R2 (0 to 580 Pa) of the differential pressure ΔPx that the second unit 30 can change, and does not overlap with the surging boundary R4. With this, the performance verification of the second unit 30 is complete.

[0160] For reference, in conventional systems, after confirming capacity using a PQ diagram, provisional airflow and damper openings are set.

[0161] (6-3) Comparison of the Conventional System and the Embodiment in Construction Procedures (Construction Procedure B1b) Here, the first unit 20, the second unit 30, and the duct 40 are installed. If there are multiple second units 30, automatic airflow control is possible simply by inputting the target airflow value Qy for each second unit 30.

[0162] In contrast, with conventional systems, after the installation of the total heat exchanger unit, dampers, and ducts is complete, the damper opening must be adjusted for each target space. Adjusting the damper opening for one target space affects the airflow in other target spaces, requiring repeated adjustments of the damper openings, which is a time-consuming process.

[0163] (6-4) Comparison of the Conventional System and the Embodiment in the Inspection Procedure (Inspection Procedure C1b) Here, we check the installation status of equipment such as the first unit 20, the second unit 30, and the duct 40. Similar checks are performed in conventional systems, although there are differences in the equipment.

[0164] (Inspection procedure C2b) Here, we conduct performance tests on the equipment. Specifically, the test is completed simply by operating the equipment in trial mode.

[0165] For the sake of explanation, the ventilation paths through which air flows between the first unit 20 and each of the target spaces 100A to 100D via the supply air duct 41 are referred to as the first path, second path, third path, and fourth path, in order from the first target space 100A side.

[0166] For example, the first path includes an air supply duct 41 connected to the first unit 20 and a first air supply branch duct 42A that branches off from the air supply duct 41 and is connected to the first fan unit 30A. Similarly, the second path includes an air supply duct 41 connected to the first unit 20 and a second air supply branch duct 42B that branches off from the air supply duct 41 and is connected to the second fan unit 30B.

[0167] If, for example, a service person confirms in Figure 1A that the first fan unit 30A has reached the target airflow value and stabilized, and then activates the second fan unit 30B, the first air supply branch duct 42A and the second air supply branch duct 42B are connected via the air supply duct 41 and the air supply branch chamber 92. Therefore, the airflow through the first air supply duct 42A will also fluctuate due to the influence of the airflow within the second air supply branch duct 42B.

[0168] In such a case, the airflow of the first fan unit 30A will also fluctuate, raising concerns that the amount of air blown from the first supply air communication duct 43A into the first target space 100A may deviate from the target airflow value.

[0169] However, the first fan unit 30A, which is the second unit 30, calculates the front-to-back pressure difference from the measured airflow rate and the rotation speed of the second fan 31, even if the front-to-back pressure difference changes due to fluctuations in duct resistance, and controls the rotation speed of the second fan 31 to achieve the airflow target value Qy at the calculated front-to-back pressure difference. Therefore, airflow adjustment by the operator is unnecessary.

[0170] In contrast, conventional systems require installing a wind speed chamber at the air outlet of each target space to measure the wind speed and calculate the airflow rate. If the airflow rate is not appropriate, the damper opening must be repeatedly adjusted, making the airflow adjustment process complex.

[0171] (6-5) Comparison of the Conventional System and the Embodiment in Management Procedures (Management Procedure D1b) Here, the airflow is checked. The actual airflow is checked using a remote control. The second unit 30 is equipped with a second airflow detection means 32, which is an air velocity sensor, so the operator can check the actual air velocity using the remote control.

[0172] In contrast, conventional systems require installing a wind speed chamber at the air outlet of each target space to measure the wind speed and calculate the airflow rate. Therefore, if the airflow rate is not appropriate, it is necessary to repeatedly adjust the damper opening, making the airflow adjustment process complicated.

[0173] (6-6) Operation in trial mode As described in the inspection procedure C2b above, the performance test is performed by operating the equipment in commissioning mode.

[0174] The following explanation, using Figure 15B as an example, describes a case where a service person conducts a trial run of an air treatment system in the first target space 100A.

[0175] Figure 15B is a flowchart of the trial operation mode. In Figure 15B, the trial operation mode is started when the second controller 52A receives a trial operation start signal from the corresponding remote control 55A.

[0176] (Step S21) In step S21, the second controller 52A determines whether or not it has received a test run start signal from the remote control 55A. If the second controller 52A has received a test run start signal from the remote control 55A, it proceeds to step S22.

[0177] (Step S22) Next, in step S22, the second controller 52A determines whether or not an airflow target value Qy has been input.

[0178] Originally, the target airflow value Qy is a value that the first controller 51 instructs the second controller 52 of each corresponding second unit 30A to 30D according to the state of each target space 100A to 100D. However, during trial operation, the value set by the service person via the remote control 55 is assumed to be the target airflow value Qy.

[0179] The target airflow values ​​set for each target space 100A to 100D during trial operation are the maximum airflow values ​​required for each target space 100A to 100D, and are calculated by multiplying the maximum occupancy rate set for each target space by the required ventilation rate per person.

[0180] However, if the ductwork at the site is not carried out according to the design, the rotation speed of the second fan 31 may be increased to provide some headroom. In this embodiment, the initial setting value of the airflow target value Qy is stored in the memory 52b of the second controller 52. This allows it to be determined whether the airflow target value Qy is set according to the design value or with some headroom, and this information is used when readjusting after an abnormality occurs.

[0181] When the second controller 52A receives the target airflow value Qy from the remote control 55A, it proceeds to step S23.

[0182] (Step S23) Next, in step S23, the second controller 52A calculates the wind speed required to achieve the target airflow value Qy and updates the target wind speed value Vy to the calculated value.

[0183] (Step S24) Next, in step S24, the second controller 52A calculates the target rotational speed Ny of the fan motor 31b, which realizes the wind speed target Vy updated in step S23, using the first function ([8] equation).

[0184] (Step S25) Next, in step S25, the second controller 52A updates the target rotational speed value of the fan motor 31b to the value Ny calculated in step S24. After updating the target rotational speed value to Ny, the second controller 52A controls the fan motor 31b so that its rotational speed reaches the target value.

[0185] (Step S26) Next, in step S26, the second controller 52A acquires the wind speed derived based on the detected value of the second airflow detection means 32 as the current wind speed Vx.

[0186] If the second airflow detection means 32 is an airflow sensor, the wind speed can be derived by dividing the detected value by the cross-sectional area of ​​the path in which the airflow sensor is located. If the second airflow detection means 32 is a wind speed sensor, the detected value can be used as the wind speed.

[0187] (Step S27) Next, in step S27, the second controller 52A calculates the difference between the target wind speed Vy and the current wind speed Vx.

[0188] (Step S28) Next, in step S28, the second controller 52A calculates the differential pressure △P.

[0189] (Step S29) Next, in step S29, the second controller 52A calculates the coefficient a as a control parameter using equation [2].

[0190] (Step S30) Next, in step S30, the second controller 52A applies the difference between the wind speed target value Vy calculated in step S27 and the current wind speed Vx, and the coefficient a calculated in step S29, to the second function ([9] equation) to calculate the rotational speed change amount △N.

[0191] (Step S31) Next, in step S31, the second controller 52A calculates a target rotational speed value Ny based on the rotational speed change amount △N calculated in step S30.

[0192] (Step S32) Next, in step S32, the second controller 52A updates the rotational speed to the rotational speed target value Ny calculated in step S31.

[0193] (Step S33) The second controller 52A then determines whether or not it has received a test run stop signal from the remote control 55A. If the second controller 52A receives a test run stop signal from the remote control 55A, it terminates the test run.

[0194] On the other hand, if the second controller 52A has not received a test run stop signal from the remote control 55A, it returns to step S21.

[0195] During the trial run, the service person can display the actual airflow on the display unit 551 of the remote control 55A. In addition, the remote control 55A can display not only the airflow of the second unit 30 (first fan unit 30A) corresponding to the first target space 100A where the remote control 55A is installed, but also the airflow of second units corresponding to other target spaces.

[0196] For example, a service person uses the remote control 55A to input the maximum airflow value required for the first target space 100A as the airflow target value Qy. The service person can monitor the airflow supplied from the fan unit 30A to the first target space 100A from the display unit 551 of the remote control 55A.

[0197] Furthermore, after the airflow supplied to the first target space 100A reaches the target airflow value Qy, the service person moves to the second target space 100B and uses the remote control 55B to input the maximum airflow value required for the second target space 100B as the target airflow value Qy, and starts the trial run of the second unit 30 (second fan unit 30B) corresponding to the second target space 100B.

[0198] The service personnel can monitor, from within the second target space 100B, whether the airflow from the first fan unit 30A to the first target space 100A deviates from the target airflow value, using the display unit 551 of the remote control 55B, after airflow to the second target space 100B has started. Therefore, the effort required for commissioning is reduced.

[0199] (7) Characteristics (7-1) In the commissioning method for the air treatment system, the first step is to set the airflow target value Qy, which is the target value of the airflow to be supplied to the target space 100, in the second unit 30. In the second step, the second unit 30 is operated and it is confirmed whether the detected value of the second airflow detection means 32 is the airflow target value Qy.

[0200] In this air treatment system's trial operation method, even if there are fluctuations in the airflow of the duct 40, the second controller 52 of the second unit 30 determines the differential pressure across the duct and automatically controls the rotation speed of the second fan 31 based on that differential pressure. Therefore, compared to conventional types that adjust airflow by damper opening, airflow adjustment is easier.

[0201] (7-2) The second controller 52 stores the detected value of the second airflow detection means 32, the rotation speed of the second fan 31, and the differential pressure across the front and rear as initial values ​​when the detected value of the second airflow detection means 32 is equal to the target airflow value.

[0202] In the commissioning method for this air treatment system, if the ductwork at the site is not installed according to the design, the rotation speed of the second fan 31 may be increased to provide a margin of safety. In such cases, if the initial value of the airflow target value Qy is recorded—whether it was set to the design value or with a margin of safety—this can be used when readjusting after any abnormalities are found.

[0203] (7-3) The duct 40 includes at least a first path from the first unit 20 to the first fan unit 30A and a second path from the first unit 20 to the second fan unit 30B. When the second fan unit 30B is activated, causing a change in the ventilation resistance of the first path and a change in the differential pressure across the first fan unit 30A, the second controller 52B of the first fan unit 30A changes the rotational speed of the second fan 31 of the first fan unit 30A to a rotational speed that maintains the target airflow value of the first fan unit at the changed differential pressure across the first fan unit.

[0204] In this air treatment system's trial operation method, even if the operation of the second fan unit 30B causes fluctuations in the airflow path connected to the first fan unit 30A, the second controller 52A of the first fan unit 30A determines the differential pressure across the front and rear, and automatically controls the rotation speed of the second fan 31 based on that differential pressure. Therefore, compared to conventional types that adjust airflow by damper opening, airflow adjustment is easier.

[0205] (7-4) The first path includes an air supply duct 41 connected to the first unit 20 and a first air supply branch duct 42A that branches off from the air supply duct 41 and is connected to the first fan unit 30A. Alternatively, the first path includes a return air duct 46 connected to the first unit 20 and a first return air branch duct 47A that branches off from the return air duct 46 and is connected to the first fan unit 30A.

[0206] The second path includes an air supply duct 41 connected to the first unit 20, and a second air supply branch duct 42B that branches off from the air supply duct 41 and is connected to the second fan unit 30B.

[0207] Alternatively, the second path includes a return air duct 46 connected to the first unit 20 and a second return air branch duct 47B that branches off from the return air duct 46 and is connected to the second fan unit 30B.

[0208] (7-5) When operating the first fan unit 30A, the target airflow value Qy for the first fan unit 30A is the maximum airflow value required for the first space 100A, which is pre-entered. When operating the second fan unit 30B, the target airflow value Qy for the second fan unit 30B is the maximum airflow value required for the second space 100B, which is pre-entered.

[0209] In this air treatment system commissioning method, the maximum airflow values ​​required for the first space 100A and the second space 100B are set as the target airflow values ​​for the first fan unit 30A and the second fan unit 30B, respectively. This allows for verification not only of whether the maximum airflow values ​​can be achieved, but also whether the ductwork is constructed as designed.

[0210] (7-5) In the commissioning method for the air treatment system, service personnel can check whether the airflow of the second unit 30 during commissioning is insufficient compared to the target airflow value Qy by looking at the numerical value displayed on the display unit 551 of the remote control 55. Furthermore, multiple second units 30 can be centrally managed with a single remote control 55.

[0211] (7-6) In the air treatment system, prior to commissioning, a first pressure loss value, which is a portion of the total pressure loss value from the first unit 20 to each target space 100A to 100D, is calculated. Then, based on the relationship between airflow and differential pressure, the target airflow value, and the first pressure loss value, the second unit 30 is selected.

[0212] (8) Modification of the first embodiment (8-1) In the first embodiment described above, the exhaust second unit 30 is provided in each of the multiple return air branch ducts 47A to 47D, but the configuration is not limited to this. For example, as a modified example, the exhaust duct may be configured in which only one exhaust second unit 30 is provided.

[0213] (8-2) In the first embodiment described above, the first unit 20 is an example of a ventilation device that only has a total heat exchange element 12 that simultaneously and continuously performs latent heat exchange and sensible heat exchange between indoor air RA and outdoor air OA, but it is not limited to this.

[0214] For example, the first unit 20 may further include, in addition to the total heat exchange element 12, a heat source and a heat exchange unit that performs heat exchange between the heat transfer medium from the heat source and the air. The maximum airflow value required for each target space 100A to 100D is determined based on the maximum heat load generated in each target space 100A to 100D. Therefore, the air treatment system can perform not only ventilation but also air conditioning.

[0215] <Second Embodiment> The air treatment system of the above embodiment was described as a ventilation system that can circulate air to the total heat exchange element 12 of the first unit 20, which does not have a fan, by utilizing the second unit 30 as an air supply fan unit and an exhaust fan unit.

[0216] Here, the method for selecting the second unit 30 can also be applied to an air treatment system comprising a first unit 220 having a first fan 21 for discharging the generated conditioned air, and a second unit 30 connected to the first unit 220 via a duct 40.

[0217] The following will provide specific examples to illustrate this point.

[0218] (1) Composition Figure 18 is a diagram showing the configuration of the air treatment system 210 according to the second embodiment, in which the second unit 30 is installed. In Figure 18, the air treatment system 210 comprises a first unit 220, a plurality of second units 30, a duct 40, and a controller 50.

[0219] (1-1) Unit 1, 220 The first unit 220 includes a first fan 21, a heat exchanger 22, a first airflow detection means 23, a temperature sensor 24, and a water flow control valve 25. The heat exchanger 22 is supplied with a heat transfer medium from the heat source unit 60, such as chilled water or hot water. The heat transfer medium supplied to the heat exchanger 22 may be something other than chilled water or hot water, such as brine.

[0220] The first airflow detection means 23 can be, for example, an airflow sensor, an air velocity sensor, or a differential pressure sensor. In this embodiment, the first airflow detection means 23 detects the airflow rate supplied by the first fan 21. The first airflow detection means 23 is connected to the first controller 51. The airflow value detected by the first airflow detection means 23 is transmitted from the first airflow detection means 23 to the first controller 51. The airflow detected by the first airflow detection means 23 is the airflow rate flowing through the supply air duct 41 of the duct 40, and is also the total amount of supply air supplied to the target space 100 from the plurality of second units 30.

[0221] The temperature sensor 24 detects the temperature of the supply air SA sent from the first fan 21 to the duct 40. The temperature sensor 24 is connected to the first controller 51. The value detected by the temperature sensor 24 is input to the first controller 51.

[0222] The first unit 220 is connected to the target space 100 via the ventilation passage 82. The indoor air RA returning from the target space 100 through the ventilation passage 82 is sent by the first fan 21 through the heat exchanger 22 to the duct 40. This becomes the supply air SA.

[0223] The indoor air RA that returns from the target space 100 is the air that was inside the target space 100. As it passes through the heat exchanger 22, the returning indoor air RA exchanges heat with the chilled or hot water flowing through the heat exchanger 22 and becomes conditioned air.

[0224] The amount of heat supplied to the supply air SA, which undergoes heat exchange in the heat exchanger 22 and is sent to the duct 40, is controlled by the water flow control valve 25. The opening degree of the water flow control valve 25 is controlled by the first controller 51. When the opening degree of the water flow control valve 25 is increased, the amount of water flowing into the heat exchanger 22 increases, and the amount of heat exchanged between the heat exchanger 22 and the air per unit time increases. Conversely, when the opening degree of the water flow control valve 25 is decreased, the amount of water flowing into the heat exchanger 22 decreases, and the amount of heat exchanged between the heat exchanger 22 and the air per unit time decreases.

[0225] (1-2) Unit 2, 30 Figure 18 shows a typical example of an air treatment system 210 comprising multiple second units 30, in which an air treatment system comprising two second units 30 is installed for a single target space 100.

[0226] The number of second units 30 may be three or more and can be set as appropriate. The number of target spaces 100 in which the second units 30 are installed may be two or more.

[0227] (1-3) Duct 40 The duct 40 distributes the supply air SA, which is sent from the first unit 220 by the first fan 21, to a plurality of second units 30. The duct 40 includes an air supply duct 41 and an air supply branch duct 42 that branches off from the air supply duct 41.

[0228] Figure 18 shows a case where the air supply duct 41 is located outside the first unit 220, but the air supply duct 41 may also be located inside the first unit 220, or it may be arranged to extend from inside the first unit 220 to outside the first unit 220.

[0229] When the air supply duct 41 is located within the first unit 220, a portion of the casing 26 of the first unit 220 may function as the air supply duct 41. Figure 18 shows an example where the inlet 41a of the air supply duct 41 is connected to the first unit 220.

[0230] The first fan 21 is located inside the first unit 220. Here, all the air blown out from the first fan 21 is configured to flow into the duct 40.

[0231] The outlet 41b of the supply air duct 41 of duct 40 is connected to the inlet 42a of the supply air branch duct 42. A configuration using a branch chamber may also be used to branch the supply air from the supply air duct 41 to the supply air branch duct 42.

[0232] The casing 33 of the second unit 30 has an inlet 33a and an outlet 33b, and the multiple outlets 42b of the supply air branch duct 42 are connected to the inlets 33a of the multiple second units 30.

[0233] Each second unit 30 and the target space 100 are connected by a ventilation passage 81. The inlet 81a of the ventilation passage 81 is connected to the outlet 33b of the second unit 30. Each second fan 31 generates an airflow within the second unit 30 from the outlet 42b of the duct 40 toward the inlet 81a of the ventilation passage 81. Therefore, each second fan 31 draws in supply air SA from the outlet 42b of the supply air branch duct 42.

[0234] (1-4) Controller 50 Figure 19 is a block diagram illustrating the configuration of the controller 50. In Figure 19, the controller 50 includes a first controller 51 and a plurality of second controllers 52. The first controller 51 and the plurality of second controllers 52 are connected to each other.

[0235] Multiple remote sensors 70, each functioning as a temperature sensor, are installed in the target space 100. Each remote sensor 70 transmits data indicating the temperature of the indoor air RA in the target space 100 to the corresponding second controller 52.

[0236] (1-4-1) First controller 51 The first controller 51 includes a processor 51a and a memory 51b. The processor 51a reads the air volume control program of the first fan 21 stored in the memory 51b and outputs necessary commands to the first fan 21 and each second controller 52.

[0237] In addition to the air volume control program of the first fan 21, the memory 51b stores the detection values of the first air volume detection means 23 and the temperature sensor 24 at any time.

[0238] The processor 51a reads the detection values of the first air volume detection means 23 and the temperature sensor 24 stored in the memory 51b, and calculates the air volume target value of the first fan 21 (the total amount of the target air volume to be supplied to the target space 100).

[0239] The above description is an example and is not limited to the above description content.

[0240] (1-4-2) Second controller 52 The second controller 52 includes a processor 52a and a memory 52b. The processor 52a reads the air volume control program of the second fan 31 stored in the memory 52b and outputs necessary commands to the second fan 31.

[0241] In addition to the air volume control program of the second fan 31, the memory 52b stores the air volume target value output from the first controller 51 and the detection value of the second air volume detection means 32 at any time.

[0242] The processor 52a reads the air volume target value and the detection value of the second air volume detection means 32 stored in the memory 52b, and calculates the rotation number target value of the second fan 31.

[0243] The above description is an example and is not limited to the above description content.

[0244] (1-5) Operation Each second fan 31 can change the differential pressure between the intake port 33a and the outlet port 33b of each second unit 30 by changing the rotation speed of the motor. Assuming that the static pressure of the duct 40 is constant, each second fan 31 can increase the differential pressure between the intake port 33a and the outlet port 33b of each second unit 30 by increasing its rotation speed.

[0245] When the differential pressure across the second unit 30 increases, the volume of supply air SA flowing through the ventilation passage 81 increases. This change in the volume of air flowing changes the volume of supply air blown out into the target space 100 from the outlet 81b of each ventilation passage 81.

[0246] The controller 50 includes a first controller 51 and a plurality of second controllers 52. The first controller 51 and the plurality of second controllers 52 are connected to each other.

[0247] The first controller 51 controls the rotation speed of the fan motor 21b of the first fan 21. When the rotation speed of the first fan 21 increases, the amount of air blown by the first fan 21 increases.

[0248] One second controller 52 is provided for each second unit 30. Each second controller 52 controls the airflow of the corresponding second fan 31. Each second controller 52 stores the target airflow value received from the first controller 51.

[0249] Each second controller 52 increases the rotation speed of the second fan 31 if the supply airflow is insufficient compared to the target airflow value. Conversely, if the supply airflow is excessive compared to the target airflow value, the second controller 52 decreases the rotation speed of the second fan 31.

[0250] The controller 50 obtains information on the amount of air supplied to the target space 100 by the multiple second fans 31. The information on the amount of air is, for example, the required supply airflow rate that should be supplied to the target space 100 per second or per minute.

[0251] Each second controller 52 outputs air volume information to the first controller 51. Based on the obtained air volume information, the first controller 51 determines the output to be requested from the first fan 21.

[0252] In the air treatment system 10, "front-to-back pressure difference" is introduced as a variable in the calculation formula for the rotational speed target value. This allows the constantly changing duct resistance to be reflected in the calculation of the airflow target value, thereby shortening the response time of the output value (airflow) to the input value (rotational speed).

[0253] (1-6) Selection method for the second unit 30 The method for selecting the second unit 30 described in the first embodiment is applied to the selection of the second unit 30 in the second embodiment.

[0254] Furthermore, the first pressure loss value does not need to be calculated for all ventilation paths; it only needs to be calculated for the ventilation path with the largest pressure loss value among the two paths connecting the first unit 20 and the target space 100. This is because, in the selection of the second unit 30, if the second unit 30 is connected to the ventilation path with the largest pressure loss value, it can also be used as a second unit connected to a ventilation path shorter than that one.

[0255] (2) Modified form of the second embodiment In the second embodiment described above, the first unit 220 has a first fan 21, but the first unit 220 does not necessarily require a first fan 21. The method for selecting the second unit 30 of this disclosure is also applicable to a second unit that is connected to a first unit without a fan via a duct.

[0256] Figure 20 is a configuration diagram of an air treatment system 210 according to a modified example of the second embodiment in which the second unit is installed. In Figure 20, the air treatment system 210 is located in the ceiling space of one floor of the building.

[0257] The difference between the air treatment system 210 and the air treatment system of FIG. 18 is that the first unit 220 does not have a first fan, and the other configurations are the same as those of the air treatment system of FIG. 18. Therefore, the same components as those of the air treatment system of FIG. 18 are denoted by the same reference numerals, and the description thereof will be omitted.

[0258] In the air treatment system 210, since the first unit 220 does not have a fan, the air flow in the first unit 220 is generated by the second unit 30.

[0259] Therefore, although the change in the differential pressure before and after the second unit 30 is mainly caused by the change in the air volume of the second fan 31 of the other second units 30, since "differential pressure before and after" is introduced as a variable in the arithmetic expression of the rotational speed target value, the change in the duct resistance that changes moment by moment can be reflected in the calculation of the air volume target value, and the response time of the output value (air volume) to the input value (rotational speed) can be shortened.

[0260] For the selection of the second unit 30 in the modification of the second embodiment, the selection method of the second unit 30 described in the first embodiment is applicable.

[0261] As described above, the embodiments of the present disclosure have been described, but it will be understood that various changes in form and details are possible without departing from the spirit and scope of the present disclosure described in the claims.

Description of Reference Numerals

[0262] 10 Air treatment system 20 First unit (air treatment unit) 30 Second unit (fan unit) 30A First fan unit 30B Second fan unit 31 Second fan (fan) 32 Second air volume detection means (detection unit) 33 Casing 33a Suction port 33b Outlet 40 Duct 41. Air supply duct (main duct) 42A First air supply branch duct (first branch duct) 42B Second air supply branch duct (second branch duct) 50 Controller (Control Unit) 51 First Controller (Control Unit) 52 Second Controller (Control Unit) 55 Remote control (remote operation device) 550 Input section 551 Display section 100 Target space 100A First Target Space 100B Second Object Space 210 Air Treatment System 220 Unit 1 (Air Processing Unit) [Prior art documents] [Patent Documents]

[0263] [Patent Document 1] Japanese Patent Application Publication No. 10-253132

Claims

1. A fan unit connected to a duct (40) that connects the space to be air-treated (100) and the air-treatment unit (20) is used in an air-treatment system that transports air that has undergone predetermined treatment by the air-treatment unit (20) to the space to be treated (100). This is a trial run method, The aforementioned target space (100) includes at least a first target space (100A) and a second target space (100B) that is different from the first target space (100A), The fan unit (30) includes at least a first fan unit (30A) and a second fan unit (30B), The duct (40) comprises at least, A first path from the air processing unit (20) through the first fan unit (30A) to the first target space (100A), A second path from the air processing unit (20) through the second fan unit (30B) to the second target space (100B), Includes, The first fan unit (30A) transports air between the air processing unit (20) and the first target space (100A). The second fan unit (30B) transports air between the air processing unit (20) and the second target space (100B). The first fan unit (30A) and the second fan unit (30B) each have, A fan with variable rotation speed (31), A casing (33) having an intake port (33a) and an outlet port (33b), and housing the fan (31), A detection unit (32) for detecting the airflow (Qx) or wind speed (Vx) of the fan (31), A control unit (50) that controls the rotation speed of the fan (31), Equipped with, The control unit (50) determines the current front-to-back pressure difference (△Px) based on the detected value of the detection unit (32) and the rotation speed of the fan (31) in order to utilize the change in front-to-back pressure difference, which is the air pressure difference between the intake port (33a) and the outlet port (33b), as a substitute value indicating the change in the airflow resistance of the duct (40), and automatically controls the rotation speed of the fan (31) to a rotation speed target value that yields the target airflow target value (Qy), which is the target airflow amount supplied to the target space (100), based on the front-to-back pressure difference (△Px). It is a fan unit (30), As the first step, the airflow target value (Qy) is set for the first fan unit (30A), and the first fan unit (30A) is operated. As the second step, the target rotational speed value is updated based on the target airflow value, the airflow, and the differential pressure across the front and rear. As the third step, it is confirmed whether the detected value of the detection unit (32) is equal to the target airflow value (Qy). When the second fan unit (30B) is activated, causing a change in the ventilation resistance of the first path and a change in the differential pressure (ΔPx) across the first fan unit (30A), the control unit (50) changes the rotational speed of the fan (31) of the first fan unit (30A) to a rotational speed that maintains the target airflow value (Qy) of the first fan unit (30A) at the changed differential pressure. Method for commissioning an air treatment system.

2. The first route is The main duct (41) connected to the air treatment unit (20), A first branch duct (42A) is branched from the main duct (41) and connected to the first fan unit (30A), Includes, The second route is, The main duct (41) and, A second branch duct (42B) is branched from the main duct (41) and connected to the second fan unit (30B), including, A method for commissioning an air treatment system according to claim 1.

3. The target airflow value of the first fan unit (30A) when operating the first fan unit (30A) is the maximum airflow value required for the first space (100A) which has been pre-entered. A method for commissioning an air treatment system according to claim 1 or claim 2.

4. The target airflow value of the second fan unit (30B) when operating the second fan unit (30B) is the maximum airflow value required for the second space (100B) which has been pre-entered. A method for commissioning an air treatment system according to claim 3.

5. The air processing unit (20) includes a heat source section and a heat exchange section that performs heat exchange between a heat transfer medium from the heat source section and air. The maximum airflow value required for the first space (100A) is determined based on the maximum heat load generated in the first space (100A). The maximum airflow value required for the second space (100B) is determined based on the maximum heat load generated in the second space (100B). A method for commissioning an air treatment system according to claim 1 or claim 2.

6. The air treatment system includes a remote control device, The remote control device is The fan unit (30) has an input unit for inputting an airflow target value, A display unit for displaying the airflow of the fan unit (30), Having, A method for commissioning an air treatment system according to any one of claims 1 to 5.

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