Flow Meter

Abstract

The flowmeter of the present invention does not use a pressure sensor to measure the flow rate of a fluid. The turbine flow controller (10) as a flowmeter has a controller (40), and in particular, a flow control unit (43). The flow control unit (43) (differential pressure derivation unit) derives the actual differential pressure ΔP between the fluid pressure on the upstream side of the turbine (35A) of the bypass flow path (31A) and the fluid pressure on the downstream side of the turbine (35A) based on the angular velocity ω of the turbine (35A) and the torque T and the gate valve opening D2 of the gate valve (32). In addition, the flow control unit (43) (flow derivation unit) derives the actual flow rate Q1 of the cold and hot water flowing in the main flow path (21A) based on the actual differential pressure ΔP and the valve core opening D1 of the valve core (22) of the main flow path (21A). Thus, the flow rate of the main flow path (21A) is measured. Therefore, according to this embodiment, the flow rate of the cold and hot water in the main flow path (21A) can be measured without using a pressure sensor.

Description

Technical Field

[0001] The present invention relates to a flow meter for measuring the flow rate of a fluid flowing in a flow path. Background Art

[0002] As an existing flow meter, there is a known flow control valve as disclosed in Patent Document 1. This flow control valve measures the flow rate of the fluid flowing in the flow path based on the differential pressure between the upstream side and the downstream side of the valve core in the flow path where the fluid flows and the opening of the valve core, and adjusts the opening of the valve core using the measured flow rate as a feedback value, thereby controlling the flow rate of the fluid. In this flow control valve, the differential pressure is measured by two pressure sensors at respective positions on the upstream side and the downstream side of the valve core on the inner wall of the flow path. In addition, the differential pressure is sometimes measured by a differential pressure sensor, which is a type of pressure sensor.

[0003] [Prior art literature]

[0004] [Patent Document]

[0005] [Patent Document 1] Japanese Patent Application Publication No. 2019-39534 Summary of the invention

[0006] [Problems to be solved by the invention]

[0007] In the existing flow control valve, the pressure sensor is mounted on the valve body constituting the flow path, so the installation environment of the pressure sensor may be relatively harsh. In addition, considering the failure of the pressure sensor, sometimes it is also desirable to ensure that the flow rate of the fluid can be measured without using the pressure sensor.

[0008] An object of the present invention is to measure the flow rate of a fluid without using a pressure sensor.

[0009] [Means for solving the problem]

[0010] In order to solve the above-mentioned problems, the flowmeter of the present invention comprises: a bypass pipe, which has an upstream end connected to a first portion of a main pipe forming a main flow path and a downstream end connected to a second portion downstream of the first portion of the main pipe, and forms a bypass flow path bypassing the main flow path; a rotating body, which is arranged on the bypass flow path and rotated by the fluid flowing in the bypass flow path; a differential pressure deriving section, which is configured to derive the differential pressure between the fluid pressure on the upstream side of the rotating body and the fluid pressure on the downstream side of the rotating body in the bypass flow path based on the angular velocity and torque of the rotating body; and a flow rate deriving section, which is configured to derive the flow rate of the fluid flowing in the main flow path based on the differential pressure derived by the differential pressure deriving section and the opening degree of a main side valve core, the main side valve core being arranged between the first portion and the second portion of the main pipe and controlling the opening area of ​​the main flow path.

[0011] The flow meter further includes a bypass-side valve element that controls an opening area of ​​the bypass flow path, and the differential pressure deriving unit may be configured to derive the differential pressure based on the angular velocity, the torque, and an opening degree of the bypass-side valve element.

[0012] The flow rate derivation unit may also be configured to derive the flow rate of the fluid flowing in the bypass flow path based on the differential pressure derived by the differential pressure derivation unit and at least any one of the angular velocity and the torque, and to derive the total flow rate of the fluid flowing in the main flow path and the bypass flow path by adding the derived flow rate of the main flow path and the flow rate of the bypass flow path.

[0013] The flow meter also has a bypass side valve core that controls the opening area of ​​the bypass flow path, and the flow rate derivation portion can also be constructed to derive the flow rate of the fluid flowing in the bypass flow path based on the differential pressure derived by the differential pressure derivation portion, the angular velocity, and at least any one of the torque and the opening degree of the bypass side valve core.

[0014] The flow meter may include a generator including a turbine as the rotating body and generating electricity by converting rotational energy of the turbine into electrical energy.

[0015] The flow rate derivation unit may be configured to control the flow rate of the fluid flowing through the bypass flow path by driving the generator to control the torque of the turbine.

[0016] The flow meter also has a bypass side valve core that controls the opening area of ​​the bypass flow path, and the flow rate derivation portion can also be configured to drive the generator to control the torque of the turbine and the opening of the bypass side valve core, thereby controlling the flow rate of the fluid flowing in the bypass flow path.

[0017] The flow rate derivation section may also be configured to derive the flow rate of the fluid flowing in the bypass flow path based on at least any one of the differential pressure derived by the differential pressure derivation section and the angular velocity and the torque, add the flow rate of the main flow path and the flow rate of the bypass flow path, derive the total flow rate of the fluid flowing in the main flow path and the bypass flow path, use the total flow rate as a feedback value, at least control the torque of the turbine and the opening of the main side valve core, thereby controlling the total flow rate of the fluid flowing in the main flow path and the bypass flow path.

[0018] The flowmeter also has a bypass side valve core that controls the opening area of ​​the bypass flow path. The flow rate derivation portion can also be constructed to derive the flow rate of the fluid flowing in the bypass flow path based on the differential pressure derived by the differential pressure derivation portion and at least any one of the angular velocity and the torque and the opening of the bypass side valve core, and use the total flow rate as a feedback value to control the torque of the turbine, the opening of the main side valve core and the opening of the bypass valve core, thereby controlling the total flow rate of the fluid flowing in the main flow path and the bypass flow path.

[0019] The flow meter may further include the main pipe.

[0020] The bypass pipe may be provided separately from the main pipe and may be configured in a shape connectable to the main pipe.

[0021] [Effects of the Invention]

[0022] According to the present invention, the flow rate of a fluid can be measured without using a pressure sensor. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 It is a block diagram of an air conditioning control system using a turbine type flow control device to which the flow meter according to the first embodiment of the present invention is applied.

[0024] Figure 2 It is a diagram schematically showing the configuration of a turbine type flow control device to which the flow meter according to the first embodiment of the present invention is applied.

[0025] Figure 3 It means that Figure 2 A perspective view of a turbine type flow control device with the main parts of the generator pulled out.

[0026] Figure 4 yes Figure 2 Block diagram of the main parts of a turbine type flow control device.

[0027] Figure 5 This is a block diagram of the main parts of a turbine type flow control device according to a modified example of the first embodiment.

[0028] Figure 6 It is a diagram schematically showing the configuration of a turbine type flow control device according to a second embodiment of the present invention.

[0029] Figure 7 yes Figure 6 Block diagram of the main parts of a turbine type flow control device.

[0030] Figure 8 This is a block diagram of the main parts of a turbine type flow control device according to a modified example of the second embodiment. DETAILED DESCRIPTION

[0031] Hereinafter, an embodiment and its modification of the flowmeter of the present invention applied to a turbine flow control device will be described with reference to the accompanying drawings. In the following embodiment and its modification, the same reference numerals are given to the same, similar or corresponding parts or elements, and repeated description is omitted.

[0032] [First embodiment]

[0033] like Figure 1 As shown, a turbine flow controller 10 to which the flow meter according to the first embodiment of the present invention is applied is applied to an air conditioning control system 1 for controlling the air conditioning of a room R (a controlled space). The turbine flow controller 10 will be described below after describing the air conditioning control system 1 .

[0034] The air conditioning control system 1 includes a FCU (Fan Coil Unit) 2 , pipes 3 , a temperature sensor 4 , and an air conditioning controller 5 in addition to the turbine type flow control device 10 .

[0035] FCU2 is configured to provide conditioned air to room R, and includes a fan 2A and a heat exchanger (cold and hot water coil) 2B. Fan 2A takes the air of room R into FCU2 and then discharges it into room R. On the other hand, a pipe 3 for circulating cold and hot water is connected to the heat exchanger 2B. The heat exchanger 2B performs heat exchange between the cold and hot water flowing in from the pipe 3 and the air taken in by the fan 2A. The cold and hot water during cooling is cold water cooled by an outdoor unit not shown in the figure, and the cold and hot water during heating is hot water heated by an outdoor unit not shown in the figure. During cooling, cold air is discharged from FCU2 through heat exchange between cold water and air. During heating, warm air is discharged from FCU2 through heat exchange between hot water and air.

[0036] The turbine flow control device 10 is arranged in the middle of the pipe 3 and is Figure 2 ) controls the flow rate of hot and cold water flowing in the pipe 3 (details will be described later).

[0037] The temperature sensor 4 is installed in the room R, and measures the temperature in the room R. The measured temperature is transmitted to the air-conditioning controller 5 .

[0038] The air conditioning controller 5 is composed of a computer such as a PLC (Programmable Logic Controller). As a control output for making the deviation between the temperature measured by the temperature sensor 4 and the set value of the room temperature of the room R zero, the air conditioning controller 5 calculates the flow rate setting value Qsp of the cold and hot water flowing to the heat exchanger 2B of the FCU2, and sends the calculated flow rate setting value Qsp to the turbine flow control device 10. The turbine flow control device 10 controls the flow rate of the cold and hot water flowing in the pipe 3 based on the flow rate setting value Qsp from the air conditioning controller 5. When the flow rate setting value Qsp of the cold and hot water from the air conditioning controller 5 changes, that is, when the flow rate setting value Qsp of the cold and hot water changes due to a load change at the supply destination of the cold and hot water, the turbine flow control device 10 follows the change and changes the flow rate of the cold and hot water flowing in the pipe 3.

[0039] Next, refer to Figure 2 as well as Figure 3 The turbine type flow control device 10 will be described. In the following description, the turbine type flow control device is also simply referred to as the flow control device 10 .

[0040] like Figure 2 As shown, the flow control device 10 includes a main pipe section 20 , a bypass pipe section 30 , a controller 40 , and a battery 50 .

[0041] The main pipe section 20 includes a main pipe 21 , a valve body (main-side valve body) 22 , a valve shaft 23 , a motor 24 , and a valve body opening degree sensor 25 .

[0042] The main pipe 21 is connected to the pipe 3 at both ends and is arranged in the middle of the pipe 3. The main pipe 21 forms a main flow path 21A constituting a circulation path for hot and cold water together with the flow path 3A of the pipe 3. The main flow path 21A is a hollow portion of the main pipe 21 and has a cross section that is substantially the same as the flow path 3A of the pipe 3 (a cross section cut in a direction orthogonal to the central axis of the flow path. Hereinafter, the cross section is the same).

[0043] The valve core 22 is arranged on the main flow path 21A. The valve core 22 changes the opening area of ​​the main flow path 21A by rotating, thereby adjusting the flow rate of hot and cold water flowing in the main flow path 21A. The valve core 22 is connected to a valve shaft 23 rotated by a motor 24, and the valve core 22 is rotated by the motor 24. The valve core opening sensor 25 detects the opening of the valve core 22 that determines the opening area of ​​the main flow path 21A, that is, the valve core opening D1, by detecting the rotation position of the valve shaft 23.

[0044] The bypass pipe portion 30 includes a bypass pipe 31 , a gate valve (bypass-side valve element) 32 , a linear motor 33 , a gate valve opening sensor 34 , a generator 35 , and a position sensor 36 .

[0045] The bypass pipe 31 is connected to the main pipe 21, and forms a bypass flow path 31A that bypasses the main flow path 21A of the main pipe 21. The bypass pipe 31 and the main pipe 21 are joined by welding or the like to form an integral body. The upstream end 31M of the bypass pipe 31 is connected to the first portion 21M on the upstream side of the valve core 22 of the main pipe 21. The downstream end 31N of the bypass pipe 31 is connected to the second portion 21N on the downstream side of the valve core 22 of the main pipe 21. The valve core 22 is arranged between the first portion 21M and the second portion 21N of the main pipe 21, which will be described later. With the above-mentioned configuration, a portion of the cold and hot water flowing from the flow path 3A of the pipe 3 through the main flow path 21A flows into the bypass flow path 31A at a position upstream of the valve core 22, and flows into the main flow path 21A again at a position downstream of the valve core 22. The cross section of the bypass flow path 31A is smaller than that of the main flow path 21A. In other words, the bypass flow path 31A is thinner than the main flow path 21A.

[0046] The gate valve 32 is arranged on the bypass flow path 31A. The gate valve 32 is linearly moved by the linear motor 33, so that the opening area of ​​the bypass flow path 31A changes. The gate valve opening sensor 34 detects the opening of the gate valve 32 that specifies the opening area of ​​the bypass flow path 31A, that is, the gate valve opening D2, by detecting the position of the actuator of the linear motor 33. In addition, the mechanism that moves the gate valve 32 linearly is not limited to the linear motor 33. The mechanism can be composed of, for example, a motor and a conversion mechanism (for example, a pinion and a rack transmission) that converts the rotation of the motor into linear movement. In this case, the gate valve opening sensor 34 detects the gate valve opening D2 by, for example, detecting the rotation position of the shaft rotated by the motor.

[0047] The generator 35 is arranged at a position in the middle of the bypass pipe 31, upstream of the gate valve 32. The generator 35 generates electricity by using the cold and hot water flowing in the bypass flow path 31A. The generator 35 includes a rotor, that is, a turbine 35A, which is rotated by the cold and hot water flowing in the bypass flow path 31A; and a stator 35B that surrounds the outer periphery of the turbine 35A and generates electricity by converting the rotational energy of the turbine 35A into electrical energy.

[0048] like Figure 3 As shown, the turbine 35A is composed of a ring 35AA and an impeller 35AB provided integrally with the ring 35AA at an inner position of the ring 35AA. A permanent magnet is incorporated in the ring 35AA. The impeller 35AB receives the cold and hot water flowing in the bypass flow path 31A and rotates together with the ring 35AA.

[0049] The stator 35B includes a cylindrical core and a plurality of coils (not shown) wound around the core as stator windings, and converts the rotational energy of the turbine 35A that rotates by receiving cold or hot water into electrical energy. Thus, power generation is performed based on the rotation of the turbine 35A.

[0050] As described later, sometimes the generator 35 is supplied with electric power E from the outside. In this case, current flows through the stator winding of the stator 35B, and the generator 35 functions as a motor that controls the torque of the turbine 35A. In this way, the generator 35 can also convert the electric energy from the outside into the rotational energy of the turbine 35A. The flow rate of the cold and hot water flowing in the bypass flow path 31A is controlled by the torque control of the turbine 35A. In addition, in this embodiment, the control of the flow rate of the cold and hot water is performed by the torque control of the turbine 35A and the opening control of the gate valve 32.

[0051] The stator 35B is provided with a position sensor 36. The position sensor 36 detects the rotational position Rt of the turbine 35A. As the position sensor 36, for example, an incremental encoder is used, but any sensor may be used. The position sensor 36 may also be a sensor that detects the rotational position Rt by detecting the magnetic poles of a permanent magnet assembled in the ring 35AA of the turbine 35A.

[0052] Back to Figure 2 The controller 40 controls the total flow of cold and hot water in the main flow path 21A and the bypass flow path 31A by controlling the motor 24 of the main pipe section 20, the linear motor 33 of the bypass pipe section 30, and the generator 35. Thus, the flow of cold and hot water flowing in the flow path 3A of the pipe 3 is controlled. When controlling the flow of cold and hot water flowing in the bypass flow path 31A, the controller 40 controls the gate valve opening of the gate valve 32 and controls the torque of the turbine 35A of the generator 35, thereby controlling the flow of cold and hot water flowing in the bypass flow path 31A. The controller 40 performs power operation control and regeneration control. The power operation is to control the supply of electric energy (electric power E) to the generator 35 to drive the generator 35 and provide torque to the turbine 35A when controlling the torque of the turbine 35A. The regeneration control does not supply electric energy to the generator 35, but generates electricity by the generator 35 and recovers electric energy. When the flow rate of the bypass flow path 31A is increased, the controller 40 performs at least one of a control to increase the gate valve opening and a control to increase the angular velocity of the turbine 35A. When the flow rate of the bypass flow path 31A is decreased, the controller 40 performs at least one of a control to decrease the gate valve opening and a control to decrease the angular velocity of the turbine 35A. The controller 40 also performs a control to charge the battery 50 using the recovered electric energy.

[0053] like Figure 4As shown, the controller 40 includes a data communication unit 41, a system control unit 42, a flow control unit 43, a generator control unit 44, an inverter 45, and a power supply circuit 48. The system control unit 42, the flow control unit 43, and the generator control unit 44 are composed of various computers including a memory and one or more processors that execute programs recorded in the memory. The system control unit 42, the flow control unit 43, and the generator control unit 44 may also be composed of various circuits other than a computer.

[0054] The data communication unit 41 is composed of various communication modules, and has a communication function for performing wired communication with the air-conditioning controller 5. Here, the data communication unit 41 communicates with the air-conditioning controller 5 using digital data.

[0055] The system control unit 42 controls the entire system of the turbine type flow control device 10. The system control unit 42 receives various data such as various set values ​​from the air conditioning controller 5 via the data communication unit 41, and transmits various data such as the internal state of the turbine type flow control device 10 to the air conditioning controller 5 via the data communication unit 41. The system control unit 42 outputs the flow rate set value Qsp from the air conditioning controller 5 to the flow control unit 43 as one of the above set values.

[0056] The flow control unit 43 is input with the flow setting value Qsp output by the system control unit 42, the current angular velocity ω and torque T (details will be described later) of the turbine 35A output by the generator control unit 44. Furthermore, the flow control unit 43 is input with the valve core opening D1 detected by the valve core opening sensor 25 and the gate valve opening D2 detected by the gate valve opening sensor 34. The flow control unit 43 controls the motor 24, the linear motor 33, the generator 35, etc. based on the above-mentioned data input, and controls the total flow of the cold and hot water flowing in the main flow path 21A and the cold and hot water flowing in the bypass flow path 31A.

[0057] The flow control unit 43 derives the actual flow rate Q1 of the cold and hot water flowing in the main flow path 21A and the actual flow rate Q2 of the cold and hot water flowing in the bypass flow path 31A. The flow control unit 43 adds the actual flow rate Q1 and the actual flow rate Q2 to derive the total actual flow rate Q3 of the cold and hot water flowing in the main flow path 21A and the bypass flow path 31A. This example is described below. In addition, in "derivation", in addition to obtaining the derived object by calculation, it also includes obtaining the derived object by referring to a table, and the table is stored in a memory appropriately set in the controller 40. The content of the calculation formula or the table is predetermined by the laws of fluid mechanics, dimensional analysis (Buckingham's π theorem, etc.), specifications of various components such as the turbine 35A, experiments, etc.

[0058] The actual flow rates Q1 and Q2 here are derived using dimensionless variables. This variable is obtained through dimensional analysis. Specifically, focusing on the flow rate Q2 of the cold and hot water flowing in the bypass flow path 31A, the differential pressure ΔP between the upstream and downstream sides of the turbine 35A sandwiching the bypass flow path 31A, the torque T of the turbine 35A, and the angular velocity ω, when dimensional analysis is performed according to Buckingham's π theorem, the following equations (1) to (3) can be obtained. πq represents the dimensionless flow rate, πp represents the dimensionless differential pressure, πt represents the dimensionless torque, ρ represents the density of the cold and hot water, and d represents the diameter of the turbine 35A.

[0059] πq=Q2 / (d 3 *ω)···(1)

[0060] πp=ΔP / (ρ*d 2 *ω 2 )···(2)

[0061] πt=T / (ρ*d 5 *ω 2 )···(3)

[0062] Through experiments, the angular velocity ω of the turbine 35A is operated so that the relationship between the dimensionless torque and the dimensionless flow rate or the dimensionless torque and the dimensionless differential pressure becomes equal in each gate valve opening D2 of a specific pitch opening, and the flow rate Q2 and the differential pressure ΔP of the bypass flow path 31A and the torque T of the turbine 35A are actually measured. In particular, the flow rate Q2 and the differential pressure ΔP are measured by various sensors. Then, based on the measurement results, the dimensionless flow rate πq and the dimensionless differential pressure πp are defined as functions of the dimensionless torque πt and the gate valve opening D2, and the following equations (4) and (5) are defined.

[0063] πq=fq(πt,D 2)···(4)

[0064] πp=fp(πt,D 2)···(5)

[0065] When deriving the actual flow rate Q2 of the bypass flow path 31A, the flow control unit 43 first calculates the dimensionless flow rate πq based on the angular velocity ω, the torque T, and the gate valve opening D2 according to the above equations (3) and (4). The above density ρ and diameter d are prepared in advance as fixed values. In addition, the density ρ can also be derived based on the temperature of the cold and hot water detected by the sensor not shown. This is also the case for other calculations. Then, the flow control unit 43 calculates the dimensionless flow rate πq based on the angular velocity ω, the torque T, and the gate valve opening D2. q The actual flow rate Q2 is calculated by transforming the above equation (1) into the following equation (6) with the angular velocity ω. The data of the equations required for these calculations are stored in a memory, for example (the same applies to other calculations).

[0066] Q2=d3 *ω*πq···(6)

[0067] When deriving the actual flow rate Q1 of the main flow path 21A, the flow control unit 43 derives the actual differential pressure ΔP, and derives the actual flow rate Q1 based on the derived actual differential pressure ΔP. Based on the angular velocity ω, the torque T, and the gate valve opening D2, the dimensionless differential pressure πp is calculated according to the above equations (3) and (5). Then, the flow control unit 43 calculates the actual differential pressure ΔP according to the following equation (7) which is a deformation of the above equation (2) based on the dimensionless differential pressure πp and the angular velocity ω.

[0068] ΔP=ρ*d 2 *ω 2 *πp···(7)

[0069] Here, the upstream end 31M located on the upstream side and the downstream end 31N located on the downstream side of the turbine 35A sandwiching the bypass pipe 31 are respectively connected to the first part 21M and the second part 21N of the valve core 22 sandwiching the main pipe 21. Therefore, the two ends of the bypass flow path 31A are respectively connected to the positions sandwiching the valve core 22 of the main flow path 21A. Therefore, the above-mentioned actual differential pressure ΔP has the same or a certain relationship with the differential pressure of cold and hot water between the upstream side and the downstream side of the valve core 22 in the main flow path 21A. Moreover, the actual flow rate Q1 of the main flow path 21A becomes a value corresponding to the differential pressure ΔP and the valve core opening D1. Therefore, the flow control unit 43 derives the actual flow rate Q1 of cold and hot water flowing in the main flow path 21A based on the valve core opening D1 and the actual differential pressure ΔP of the bypass flow path 31A.

[0070] Regarding the derivation of the actual flow rate Q1, for example, the relationship between the valve core opening D1, the actual differential pressure ΔP, and the capacity coefficient Cvv of the main pipe 21 is obtained through experiments and tabulated. The flow control unit 43 obtains the capacity coefficient Cvv based on the valve core opening D1 and the actual differential pressure ΔP by referring to the above table, and calculates the actual flow rate Q1 by multiplying the value obtained by multiplying the capacity coefficient Cvv by the square root of the actual differential pressure ΔP (Cvv*√ΔP) by a predetermined coefficient. Such a technology can be used, for example, the technology disclosed in "Development of a Valve with Flow Measurement and Control Function (Flow Measurement and Control Function Valve Development)" (azbil Technical Review December 2009 issue, pages 42-48).

[0071] Furthermore, the flow rate control unit 43 adds the actual flow rate Q1 and the actual flow rate Q2 to derive a total actual flow rate Q3 of the main flow path 21A and the bypass flow path 31A.

[0072] As described above, the actual flow rate Q2 depends on the values ​​of the angular velocity ω, the torque T, and the gate valve opening D2. Therefore, it is also possible to actually measure the torque T and the actual flow rate Q2 when the angular velocity ω and the gate valve opening D2 are changed in the bypass pipe section 30 through experiments, and define their relationship in advance using a function or table, and store them in the memory. In this case, the flow control unit 43 can also derive the actual flow rate Q2 based on the angular velocity ω, the torque T, and the gate valve opening D2, with reference to the above-mentioned function or table. Similarly, the actual differential pressure ΔP depends on the values ​​of the angular velocity ω, the torque T, and the gate valve opening D2. Therefore, it is also possible to actually measure the torque T and the actual differential pressure ΔP when the angular velocity ω and the gate valve opening D2 are changed in the bypass pipe section 30 through experiments, and define their relationship in advance using a function or table, and store them in the memory. In addition, during flow control, the gate valve 32 may be fixed to be fully open, and the flow rate of the bypass flow path 31A may be controlled by the turbine 35A. In this case, the gate valve opening D2 may not be used, or the gate valve opening may be fixed to the fully open value.

[0073] Regarding the derivation of the actual flow rate Q1, the relationship between the valve core opening D1, the actual differential pressure ΔP and the actual flow rate Q1 can also be calculated in advance through experiments, etc., and prepared in the memory as a table and / or a functional expression. The flow control unit 43 derives the actual flow rate Q1 based on the valve core opening D1 and the actual differential pressure ΔP using the table and / or functional expression.

[0074] As described above, the controller 40, especially the flow control unit 43, operates as a differential pressure deriving unit that derives the actual differential pressure ΔP based on the angular velocity ω, the torque T, and the gate valve opening D2, and operates as a flow rate deriving unit that derives each actual flow rate Q1 to Q3. That is, the controller 40, especially the flow control unit 43, can also be called a differential pressure deriving unit and a flow rate deriving unit.

[0075] After the total actual flow rate Q3 is derived, the flow control unit 43 uses the total actual flow rate Q3 as a feedback value to control the valve core opening of the valve core 22, the gate valve opening of the gate valve 32, and the torque of the turbine 35A of the generator 35 according to the flow control rule (PI control) in such a way that the total actual flow rate Q3 is close to the flow setting value Qsp. Regarding the torque of the turbine 35A of the generator 35, the flow control unit 43 derives the torque setting value Tsp according to the above-mentioned flow control rule, and outputs it to the generator control unit 44. Thus, the flow control unit 43 controls the torque of the turbine 35A of the generator 35 via the generator control unit 44 (details will be described later). When the flow control unit 43 performs control based on the above-mentioned flow control rule, the valve core opening D1 from the valve core opening sensor 25 is used as a feedback value to drive the motor 24, thereby controlling the valve core opening of the valve core 22. When the flow control unit 43 performs control based on the above-mentioned flow control rule, the gate valve opening D2 from the gate valve opening sensor 34 is used as a feedback value to drive the linear motor 33, thereby controlling the gate valve opening of the gate valve 32. The gate valve opening and the valve core opening are changed from fully open to intermediate opening to fully closed, so that the flow rate of hot and cold water changes. The actual flow rate Q2 is controlled by the gate valve 32 and the turbine 35A, but when the gate valve 32 is fully open, it can also be controlled by only the turbine 35A.

[0076] The generator control unit 44 receives the rotation position Rt of the turbine 35A of the generator 35 detected by the position sensor 36 and the phase voltage value V and the phase current value I output by the inverter 45. As described later, the inverter 45 is controlled by the generator control unit 44 to supply the electric power E for controlling the torque of the turbine 35A to each stator winding of the stator 35B of the generator 35. The inverter 45 detects the values ​​of the phase voltage and the phase current input to the generator 35 when the electric power E is supplied as the phase voltage value V and the phase current value I, and outputs them to the generator control unit 44. In addition, the inverter 45 may detect the phase voltage and the phase current values ​​output when the generator 35 generates electricity as the phase voltage value V and the phase current value I, and output them to the generator control unit 44. In this case, the phase voltage value V and the phase current value I described in the present embodiment include the phase voltage value and the phase current value when the electric power E is supplied and when the electric power E is generated.

[0077] The generator control unit 44 derives the current angular velocity (rotational speed) of the turbine 35A as the angular velocity ω based on the rotational position Rt of the turbine 35A of the generator 35 detected by the position sensor 36. The generator control unit 44 derives the torque T of the turbine 35A based on the phase voltage value V and the phase current value I. The generator control unit 44 uses the derived torque T as a feedback value and controls the inverter 45 according to the torque control rule (PI control) so that the torque T becomes the torque setting value Tsp from the generator control unit 44. The generator control unit 44 outputs the angular velocity ω and the torque T to the flow control unit 43.

[0078] The generator control unit 44 may also derive the torque T of the turbine 35A based on the phase current value I. In addition, the generator control unit 44 may also derive the torque T based on the phase voltage value V, the phase current value I, and the angular velocity ω. In addition, the flow control unit 43 may also derive the angular velocity setting value ωsp instead of the torque setting value Tsp according to the above-mentioned flow control rule, and the generator control unit 44 controls the inverter 45 through feedback control (PI control) so that the angular velocity ω becomes the angular velocity setting value ωsp.

[0079] The inverter 45 receives the main power from the power supply circuit 48 and operates under the control of the generator control unit 44, and outputs the power E for controlling the torque of the turbine 35A of the generator 35 to the stator winding of the stator 35B of the generator 35. As a result, a phase current flows through the stator winding of the stator 35B, and a torque is applied to the turbine 35A. Under the control of the generator control unit 44, the inverter 45 also operates in a manner that the stator 35B of the generator 35 converts the rotational energy of the turbine 35A rotated by the cold and hot water flowing in the bypass flow path 31A into electrical energy. The flow rate of the cold and hot water flowing in the bypass flow path 31A is controlled by the turbine 35A controlled by the operation in this manner, and finally the flow rate of the cold and hot water in the bypass flow path 31A is controlled so that the total actual flow rate Q3 of the cold and hot water in the main flow path 21A and the cold and hot water in the bypass flow path 31A becomes the flow rate setting value Qsp from the air conditioning controller 5.

[0080] The inverter 45 may also be configured to supply the power obtained by the above conversion to the battery 50 to charge the battery 50. In addition, the inverter 45 detects and outputs the phase current value I and the phase voltage value V. In addition to the phase current value I and the phase voltage value V input to the generator 35 during power supply, the phase current value I and the phase voltage value V may also include the phase current value I and the phase voltage value V output from the generator 35 during power generation as described above.

[0081] The power circuit 48 distributes the power obtained by combining the power from the external power source U1 such as the commercial power source and the stored power stored in the battery 50 as the power used in the turbine type flow control device 10. In this example, the power circuit 48 supplies the power to the inverter 45 as the main power, and also supplies power to the data communication unit 41, the system control unit 42, the flow control unit 43, the generator control unit 44, etc. The power circuit 48 preferentially distributes the stored power so that the stored power of the battery 50 is consumed preferentially over the power from the external power source U1. When the stored power stored in the battery 50 is insufficient, the power circuit 48 distributes the power that matches the power supplied from the external power source U1. In addition, the power circuit 48 distributes the power without supplying the power stored in the battery 50 to the commercial power source. As a result, the power stored in the battery 50 is consumed in the flow control device 10. The power circuit 48 is connected to the external power source U1 by wire.

[0082] As described above, in the present embodiment, the controller 40, particularly the flow control unit 43, operates as a differential pressure deriving unit, and derives the actual differential pressure ΔP between the fluid pressure on the upstream side of the turbine 35A of the bypass flow path 31A and the fluid pressure on the downstream side of the turbine 35A based on the angular velocity ω and torque T of the turbine 35A and the gate valve opening D2 of the gate valve 32. In addition, the gate valve 32 may be always controlled to be fully open during the operation of the flow control device 10, and the gate valve 32 is not essential, so it may be omitted. In this case, the differential pressure deriving unit may be configured to derive the actual differential pressure ΔP based on the angular velocity ω and torque T without using the gate valve opening D2. In this case, in the above-mentioned equations (4) and (5), the gate valve opening D2 may be set to a fully open value, or the equations (4) and (5) may be set to a function of a dimensionless flow rate or a dimensionless differential pressure and a dimensionless torque. Furthermore, the controller 40, in particular, the flow control unit 43 acts as a flow rate derivation unit, and derives the actual flow rate Q1 of the cold and hot water flowing in the main flow path 21A based on the actual differential pressure ΔP and the valve core opening D1 of the valve core 22 of the main flow path 21A. Thus, the flow rate of the main flow path 21A is measured. Therefore, according to this embodiment, the flow rate of the cold and hot water in the main flow path 21A can be measured without using a pressure sensor. In addition, the method of obtaining the actual differential pressure ΔP is arbitrary.

[0083] In addition, the controller 40 (flow rate derivation unit) derives the actual flow rate Q2 of the bypass flow path 31A based on the angular velocity ω and the torque T and the gate valve opening D2 of the gate valve 32, and adds the derived actual flow rate Q1 and the actual flow rate Q2 to derive the total actual flow rate Q3. Therefore, through this configuration, the total actual flow rate Q3 can be measured without using a pressure sensor, in other words, the flow rate of cold and hot water flowing in the flow path 3A of the pipe 3 connected to the main flow path 21A can be measured. In addition, when the gate valve 32 is omitted as described above, the controller 40 (flow rate derivation unit) can also be configured to derive the actual flow rate Q2 based on the angular velocity ω and the torque T without using the gate valve opening D2. In addition, the controller 40 (flow rate derivation unit) can also derive the actual flow rate Q2 based on at least the former of the actual differential pressure ΔP and the gate valve opening D2, similarly to the actual flow rate Q1. The controller 40 (flow rate derivation unit) can also derive the actual flow rate Q2 based on the angular velocity ω and the torque T and the actual differential pressure ΔP. Of course, the gate valve opening D2 may also be further used.

[0084] In the above embodiment, the turbine 35A is formed as a part of the generator 35, and power is generated by the rotation of the turbine 35A. Thus, the turbine 35A is effectively used.

[0085] Furthermore, in the above-mentioned embodiment, the controller 40 (flow rate derivation unit) controls the torque of the turbine 35A by driving the generator 35, thereby controlling the actual flow rate Q2 of the bypass flow path 31A, so that the turbine 35A is further effectively utilized. In this embodiment, the controller 40 (flow rate derivation unit) also controls the opening of the gate valve 32, thereby more appropriately controlling the actual flow rate Q2.

[0086] Furthermore, the controller 40 (flow rate derivation unit) uses the total actual flow rate Q3 as a feedback value, and controls the total actual flow rate Q3 by controlling the torque of the turbine 35A, the opening of the valve core 22, and the opening of the gate valve 32. In this way, not only the flow rate can be derived, but also the flow rate can be controlled. In addition, as described above, when the gate valve 32 is fully opened and fixed, the opening of the gate valve 32 may not be controlled.

[0087] The flow control device 10 includes the main pipe 21 in addition to the bypass pipe 31, and is therefore easily connected to the pipe 3. In addition, the flow control device 10 may be provided to replace a flow control valve that is conventionally provided in the middle of the pipe 3. In addition, by changing the design of the control valve that controls the opening of the valve core 22 to the structure of the present embodiment, a flow control valve that can measure and control the flow rate can be obtained without adding a pressure sensor.

[0088] Furthermore, since the turbine 35A is provided on the bypass pipe 31 instead of the main pipe 21, even if the main pipe 21 is configured to be thicker as the pipe 3 is configured to be thicker, since the turbine 35A and the generator 35 are provided on the bypass pipe 31 which is thinner than the bypass pipe 31, it is possible to suppress the increase in size of the turbine 35A and the generator 35 compared to when they are provided on the main pipe 21. Furthermore, even if it is necessary to change the thickness of the main pipe 21 according to the installation destination of the flow control device 10, since the thickness of the bypass pipe 31 can be fixed, it is possible to achieve commonality of the generator 35. By suppressing the increase in size and commonality of the generator 35, it is possible to achieve miniaturization and cost reduction of the flow control device 10.

[0089] In addition, in the present embodiment, the flow control device 10 is configured such that the power generated by the generator 35 and stored in the storage battery 50 is not supplied to the commercial power supply, that is, not sold, but is consumed in the flow control device 10. Therefore, by suppressing the enlargement of the generator 35, it is also possible to suppress the situation where the power generation amount of the generator 35 is more than necessary. As a result, in the flow control device 10, it is possible to suppress the enlargement of the hardware and the like that consumes the surplus power, and it is possible to suppress the enlargement of the device and the increase in the manufacturing cost.

[0090] In addition, in this embodiment, since the turbine 35A and the like are provided on the bypass pipe 31, even if the size of the main pipe 21 needs to be changed according to the size (particularly the thickness) of the pipe 3 at the destination of the flow control device 10, the size of the bypass pipe 31, the turbine 35A and the like can be fixed, so that the cost of design change of the flow control device 10 can be reduced. In addition, the flow control device 10 can be miniaturized. In addition, since the bypass flow path 31A is thin, the flow rate of cold and hot water during power generation can also be reduced.

[0091] In addition, in this embodiment, a gate valve 32 is provided on the bypass flow path 31A in the middle of the bypass pipe 31. The opening area of ​​the bypass flow path 31A is controlled by the gate valve 32. Furthermore, by using the gate valve 32, the thickness of the bypass pipe 31 is independent of the thickness of the main pipe 21 and is thinner than the thickness of the main pipe 21, so even if the gate valve 32 of the bypass pipe 31 is fully opened for initial power generation, the pressure drop of the pump during the initial water diversion can be reduced.

[0092] [Modification of the first embodiment]

[0093] [Modification 1]

[0094] The connection between the controller 40 and the air conditioning controller 5 and the connection between the power supply circuit 48 and the external power supply U1 may be wirelessly connected. Figure 5As in the turbine flow control device 110 (hereinafter also referred to as the flow control device 110) shown in FIG. 1 , a wireless data communication unit 141 for wireless communication with the air conditioning controller 5 may be provided instead of the data communication unit 41. The wireless data communication unit 141 includes an antenna, modulates the data to be transmitted to the air conditioning controller 5, and transmits the modulated data from the antenna to the air conditioning controller 5. The wireless data communication unit 141 demodulates the data received from the air conditioning controller 5 via the antenna, and outputs the demodulated data to the system control unit 42. With such a configuration, wireless data communication is realized.

[0095] In addition, if Figure 5 As shown, the flow control device 110 can also be configured to wirelessly receive power from an external power source U1. The external power source U1 is connected to a wireless power supply unit U2. The flow control device 110 includes a wireless power receiving unit 149. The wireless power supply unit U2 and the wireless power receiving unit 149 are composed of various circuits that supply power wirelessly. The power from the external power source U1 is wirelessly supplied to the wireless power receiving unit 149 via the wireless power supply unit U2. The wireless power receiving unit 149 supplies the received power to the power supply circuit 48. This configuration realizes wireless power supply. The power supply circuit 48 allocates the power stored in the battery 50 to the inverter 45 and the flow control unit 43, etc., in priority to the power received by the wireless power receiving unit 149. As a result, the controller 40 consumes the power stored in the battery 50 in priority to the power received by the wireless power receiving unit 149. As a result, the power received by wireless power can be reduced.

[0096] By making both data communication and power supply wireless, all wiring to the flow control device 110 is eliminated. As a result, wirelessization can be expected to contribute to reducing environmental loads by eliminating wiring materials and wiring man-hours.

[0097] [Modification 2]

[0098] like Figure 5As shown, the flow control device 110 may further include a residual meter 160 for detecting the residual amount of power stored in the battery 50. The flow control unit 43, i.e., the controller 40, may also control at least the torque of the turbine 35A and the opening of the valve core 22 according to the residual amount of power of the battery 50 detected by the residual meter 160. For example, if the residual amount of power of the battery 50 is lower than the first threshold, the controller 40 enables the generator 35 to generate power and controls the opening of the valve core 22, thereby making the total actual flow rate Q3 of the cold and hot water flowing in the main flow path 21A and the bypass flow path 31A close to the flow setting value Qsp. On the other hand, if the residual amount of power of the battery 50 is greater than the second threshold, the controller 40 does not enable the generator 35 to generate power and controls the opening of the valve core 22 so that the total actual flow rate Q3 is close to the flow setting value Qsp. In this way, appropriate power generation and flow control can be performed. In addition, the controller 40 may further control the opening of the gate valve 32 according to the residual amount of power of the battery 50. For example, during power generation, in order to ensure the flow of hot and cold water required for power generation, the controller 40 may control the gate valve 32 to be fixed to a fully open position or to an opening greater than a predetermined opening position, or may control the total actual flow rate Q3 by changing the opening position of the gate valve 32 to an opening greater than a predetermined opening position. In addition, when the generator 35 is not generating power, the controller 40 may control the opening positions of the valve core 22 and the gate valve 32 to make the total actual flow rate Q3 close to the flow rate setting value Qsp.

[0099] [Second embodiment]

[0100] like Figure 6 As shown, the turbine type flow control device 210 (hereinafter also referred to as the flow control device 210) of the second embodiment includes a main pipe section 220 and a bypass pipe section 230. The flow control device 210 may also be a device in which an existing flow control valve or an opening control valve is assembled as the main pipe section 220. The flow control device 210 may include a bypass pipe section 230 but not include the main pipe section 220. In this case, an existing or already installed flow control valve or opening control valve may also be used as the main pipe section 220.

[0101] The main pipe section 220 includes the main pipe 21 and other components 21 to 26, and also includes a main side controller 240A having a part of the functions of the controller 40. The main pipe 21 is disposed midway in the pipe 3 by connecting both ends of a bypass pipe 231 of the bypass pipe section 230 to the pipe 3.

[0102] The bypass pipe section 230 includes the components 32 to 36 such as the gate valve 32 , a battery 50 , a bypass pipe 231 instead of the bypass pipe 31 , and a bypass-side controller 240B having a part of the functions of the controller 40 .

[0103] The bypass pipe 231 includes a bypass pipe body 231H forming a bypass flow path 31A, and an upstream end 231M and a downstream end 231N connected to both ends of the bypass pipe body 231H. The upstream end 231M is connected to the upstream end of the pipe 3 and the valve core 22 of the main pipe 21, that is, the first portion 21M. The downstream end 231N is connected to the downstream end of the pipe 3 and the valve core 22 of the main pipe 21, that is, the second portion 21N. In this way, the bypass pipe 31 is provided separately from the main pipe 21, and is configured to be connectable to the main pipe 21. In addition, the above-mentioned connections here are performed by fastening the flanges provided on each pipe with bolts and nuts. These connections can also be performed by separately provided pipe joints, etc. The upstream end 231M and the downstream end 231N form flow paths 231B and 231C connected to the main flow path 21A and the flow path 3A of the pipe 3, respectively. The cross sections of the flow paths 231B and 231C are consistent with the cross sections of the main flow path 21A and the flow path 3A. The bypass flow path 31A is connected to the main flow path 21A of the main pipe 21 via the flow paths 231B and 231C, bypassing the main flow path 21A. A portion of the cold and hot water flowing from the flow path 3A of the pipe 3 to the flow path 231B flows to the bypass flow path 31A. The remaining portion of the cold and hot water flows through the main flow path 21A.

[0104] The main-side controller 240A controls the flow rate of the cold and hot water flowing in the main flow path 21A by controlling the motor 24. The bypass-side controller 240B controls the flow rate of the cold and hot water flowing in the bypass flow path 31A by controlling the linear motor 33 and the generator 35. The main-side controller 240A and the bypass-side controller 240B cooperate to control the total flow rate of the cold and hot water in the main flow path 21A and the bypass flow path 31A. The bypass-side controller 240B controls the torque of the turbine 35A, the power generation of the generator 35, and the opening of the gate valve 32 in the same manner as the controller 40. In the following, the bypass-side controller 240B is described first, and then the main-side controller 240A is described.

[0105] The bypass side controller 240B includes a data communication unit 241B, a system control unit 242B, a flow control unit 243B, and a power supply circuit 248B in addition to the generator control unit 44 and the inverter 45. These are basically the same as the data communication unit 41, the system control unit 42, the flow control unit 43, and the power supply circuit 48 of the first embodiment, but are different in the following points.

[0106] The data communication unit 241B can communicate with the data communication unit 241A of the main controller 240A by wire in addition to communicating with the air conditioning controller 5. The data communication unit 241B receives the valve core opening D1 of the valve core 22. The data communication unit 241B provides the valve core opening D1 to the flow control unit 243B via the system control unit 242B. The system control unit 242B controls the entire system of the bypass pipe unit 230. The system control unit 242B sends various data such as the internal state of the bypass pipe unit 230 via the data communication unit 241B.

[0107] The flow control unit 243B derives actual flow rates Q1 and Q2 of the main passage 21A and the bypass passage 31A, and the total actual flow rate Q3 of the main passage 21A and the bypass passage 31A, similarly to the flow control unit 43. Here, as described above, the flow control unit 43 of the first embodiment controls the valve opening of the valve body 22, the gate valve opening of the gate valve 32, and the torque of the turbine 35A of the generator 35 so that the total actual flow rate Q3 approaches the flow setting value Qsp. On the other hand, in the present embodiment, since the valve body 22 is provided on the main pipe section 220, the flow control unit 243B cannot directly control the valve opening of the valve body 22. Therefore, the flow control unit 243B controls the gate valve opening of the gate valve 32 and the torque of the turbine 35A of the generator 35 so that the total actual flow rate Q3 approaches the flow setting value Qsp, and derives the valve opening setting value as the target value of the valve opening. The derived valve body opening setting value is provided to the data communication unit 241A of the master-side controller 240A via the system control unit 242B and the data communication unit 241B.

[0108] The power circuit 248B distributes part of the power obtained by combining the power from the external power source U1 such as a commercial power source and the stored power stored in the storage battery 50 to the power circuit 248A described later of the master-side controller 240A through a wire. The power circuit 248B, like the power circuit 48 of the first embodiment, preferentially distributes the stored power so that the stored power of the storage battery 50 is consumed preferentially over the power from the external power source U1.

[0109] The master-side controller 240A includes a data communication unit 241A, a system control unit 242A, a flow rate control unit 243A, and a power supply circuit 248A.

[0110] The data communication unit 241A is composed of various communication modules, and has a communication function for performing wired communication with the data communication unit 241B of the bypass pipe unit 230. The system control unit 242A controls the entire system of the main pipe unit 220. The system control unit 242A receives various data such as various set values ​​from the air conditioning controller 5 via the data communication units 241A and 241B, and transmits various data such as the internal state of the main pipe unit 220 to the air conditioning controller 5 via the data communication units 241A and 241B. The above-mentioned valve core opening setting value provided to the data communication unit 241A is provided to the flow control unit 243A via the system control unit 242A.

[0111] The valve core opening D1 detected by the valve core opening sensor 25 is input to the flow control unit 243A. The flow control unit 243A sends the input valve core opening D1 to the bypass side controller 240B via the system control unit 242A and the data communication unit 241A. The flow control unit 243A uses the input valve core opening D1 as a feedback value and controls the valve core opening of the valve core 22 according to the flow control rule (PI control) so that the valve core opening D1 is close to the valve core opening setting value.

[0112] As described above, the main-side controller 240A on the main side and the bypass-side controller 240B on the bypass side cooperate to control the total flow of the cold and hot water flowing in the main flow path 21A and the bypass flow path 31A to approach the flow setting value Qsp from the air-conditioning controller 5. In addition, the bypass-side controller 240B controls the torque of the turbine 35A and the opening of the gate valve 32, and controls the opening of the valve core 22 through the main-side controller 240A, thereby controlling the above-mentioned total flow to approach the flow setting value Qsp.

[0113] As described above, in the second embodiment, the bypass side controller 240B also functions as the differential pressure deriving unit and the flow rate deriving unit, and can derive the actual flow rate Q1 of the main flow path 21A, the actual flow rate of the bypass flow path 31A, and the total actual flow rate Q3 of the two. Thus, these flow rates can be measured without using a pressure sensor. In addition, these flow rates can also be controlled. In addition, as in the first embodiment, the gate valve 32 and the opening of the gate valve may not be necessary.

[0114] In addition, as shown in the present embodiment, the main pipe section 220 and the bypass pipe section 230 can be combined separately, so that only the bypass pipe section 230 is added, and a flow control valve or an opening control valve can be used as the main pipe section 220. The flow control valve can measure the existing flow rate, and the opening control valve cannot measure the flow rate, but controls the opening of the valve core 22 according to the input of the opening from the outside. Therefore, the flow control device 210 can be introduced at a low cost. In addition, the existing equipment can also be used, and the development man-hours for the installation of the flow control device 210 are also reduced. Further, as in the above-mentioned embodiment, by inputting the valve core opening setting value (the target value of the opening of the valve core 22) to the main pipe section 220 to control the opening of the valve core 22, the main pipe section 220 can be introduced into the bypass pipe section 230 (flow control device 10) as an existing opening control valve, and the existing opening control valve can be upgraded to a flow control device 10 that can independently control the flow rate.

[0115] [Variation of the Second Embodiment]

[0116] As in the modified example of the first embodiment, one or both of the connection between the bypass controller 240B and the air conditioning controller 5 and the connection between the power supply circuit 248B and the external power supply U1 may be wirelessly connected. Figure 8 In the embodiment of the present invention, as in the turbine flow control device 310 (hereinafter also referred to as the flow control device 110), a wireless data communication unit 341B similar to the wireless data communication unit 141 is provided to replace the data communication unit 241B, and the wireless data communication unit 141 communicates with the air conditioning controller 5 in a wireless manner. Furthermore, a wireless data communication unit 341A may be provided to replace the data communication unit 241A of the main controller 240A, and wireless communication is performed through the wireless data communication unit 341A and the wireless data communication unit 341B. With such a configuration, wireless data communication is realized.

[0117] In addition, if Figure 8 As shown, the flow control device 310 can also be configured to receive power from an external power source U1 in a wireless manner. The external power source U1 is connected to a wireless power supply unit U2. The flow control device 310 has a wireless power receiving unit 149BA that is the same as the wireless power receiving unit 149. The power from the external power source U1 is wirelessly supplied to the wireless power receiving unit 149BA via the wireless power supply unit U2. The wireless power receiving unit 149BA supplies the received power to the power supply circuit 248B. With this configuration, wireless power supply is achieved. Furthermore, as Figure 8 As shown, a wireless power supply unit 149BB and a wireless power receiving unit 149AA may be provided in the main-side controller 240A and the bypass-side controller 240B, respectively, and the power supplied from the power supply circuit 248B to the power supply circuit 248A may be transmitted wirelessly.

[0118] The above-mentioned modification 2 of the first embodiment can also be applied to the second embodiment.

[0119] [Regarding Modifications of the First Embodiment, the Second Embodiment, etc.]

[0120] The air conditioning controller 5 of the above embodiment outputs the flow setting value Qsp as digital data, but the flow setting Qsp may also be output in the form of analog data such as 4-20mA or 0-10V. In this case, analog-digital conversion is appropriately performed on the side of the flow control device 10, etc. When such a modified example is adopted, the instruction from the air conditioning controller 5 is only the flow setting value Qsp, and there is no data transmitted from the data communication unit 41, etc. on the side of the flow control device 10, etc. to the air conditioning controller 5, and the communication may be wired communication.

[0121] A part of the generator 35 may also be provided outside the bypass duct 31. For example, in the above-mentioned embodiment, the stator 35B is arranged in the middle of the bypass duct 31, but it may be arranged outside the bypass duct 31 separately from the bypass duct 31. In this case, the generator 35 includes, for example, a turbine 35A arranged in the middle of the bypass flow path 31A in the bypass duct 31 and a transmission mechanism that transmits the rotation of the turbine 35A to the outside of the bypass duct 31. In addition, the generator 35 includes: a rotor that is arranged outside the bypass duct 31 and rotates due to the rotation of the turbine 35A transmitted by the transmission mechanism; and a stator 35B that is arranged outside the bypass duct 31 and converts the rotational energy of the rotor into electrical energy.

[0122] The main side valve core, i.e., the valve core 22, provided on the main flow path 21A can be any valve core as long as it controls the opening area of ​​the main flow path 21A. The bypass side valve core, i.e., the gate valve 32, provided on the bypass flow path 31A can also be changed to other various valve cores that control the opening area of ​​the bypass flow path 31A. When controlling the flow rate of the bypass flow path 31A, the valve cores such as the gate valve 32 can also be fully opened. The valve cores such as the gate valve 32 can also be in any state of fully open and fully closed, and can be controlled in a manner that does not stop at the intermediate opening. The valve cores such as the gate valve 32 can also be omitted. The power stored in the battery 50 can also be sold to the commercial power supply constituting the external power supply U1 via the power supply circuit 48 or 248B as needed. The component used in the derivation of the actual flow rate Q1 of the main flow path can also be a rotating body other than the turbine 35A. For example, an impeller that does not generate electricity can also be used. The angular velocity ω and the torque T can also be detected by any method. The above-mentioned control rules used in the flow control by the controller 40 or the like may be any control rules as long as they are control rules such as modern control rules that can appropriately control the control object, and are not limited to the PI control rules. In order to reduce costs, it is preferred that a pressure sensor is not provided on the main pipe 21 side, but a pressure sensor may be provided on the main pipe 21. Even in such a case, since the pressure sensor is damaged, the bypass pipe portion 30 can measure the flow rate of the main flow path 21A.

[0123] The present invention is not limited to the flow control device of the air conditioning control system, but can also be applied to the flow control device used in other systems, and can also be expanded to general industrial equipment. The present invention can be applied to various flow meters other than the flow meter used as the flow control device. The fluid for measuring or controlling the flow is not limited to liquids such as cold and hot water, but can also be gases such as gas.

[0124] [Scope of the Invention]

[0125] The present invention has been described above with reference to the embodiments and variations, but the present invention is not limited to the above embodiments and variations. For example, the present invention includes various changes to the above embodiments and variations that can be understood by those skilled in the art within the scope of the technical concept of the present invention. The various structures listed in the above embodiments and variations can be appropriately combined within the scope of no contradiction.

[0126] [Explanation of symbols]

[0127] 1… Air conditioning control system, 2… FCU, 3… Piping, 3A… Flow path, 5… Air conditioning controller, 10, 110, 210, 310… Turbine flow control device (flow meter), 20, 220… Main pipe, 21… Main pipe, 21A… Main flow path, 21M… First part, 21N… Second part, 22… Valve core, 23… Valve shaft, 24… Motor, 25… Valve core opening sensor, 30, 230… Bypass pipe, 31, 231… Bypass pipe, 31A…bypass flow path, 31M, 231M…upstream end, 31N, 231N…downstream end, 231H…bypass pipe body, 231B, 231C…flow path, 32…gate valve, 33…linear motor, 34…gate valve opening sensor, 35…generator, 35A…turbine, 35B…stator, 36…position sensor, 40…controller, 50…battery, 240A…main side controller, 240B…bypass side controller.

Claims

1. A flow meter, characterized in that: have: a bypass pipe having an upstream end connected to a first portion of a main pipe forming a main flow path and a downstream end connected to a second portion of the main pipe downstream of the first portion, and forming a bypass flow path bypassing the main flow path; a rotating body disposed in the bypass flow path and rotated by the fluid flowing in the bypass flow path; A bypass side valve core, which controls the opening area of ​​the bypass flow path; a differential pressure deriving unit configured to derive a differential pressure between a fluid pressure on an upstream side of the rotating body and a fluid pressure on a downstream side of the rotating body in the bypass flow path based on an angular velocity and a torque of the rotating body and an opening degree of the bypass-side valve element; as well as A flow rate derivation section is configured to derive a flow rate of a fluid flowing in the main flow path based on the differential pressure derived by the differential pressure derivation section and an opening of a main-side valve element, wherein the main-side valve element is arranged between the first portion and the second portion of the main pipe and controls an opening area of ​​the main flow path.

2. The flow meter according to claim 1, characterized in that The flow rate derivation unit is configured to derive the flow rate of the fluid flowing in the bypass flow path based on the differential pressure derived by the differential pressure derivation unit and at least any one of the angular velocity and the torque, and to derive the total flow rate of the fluid flowing in the main flow path and the bypass flow path by adding the derived flow rate of the main flow path and the flow rate of the bypass flow path.

3. The flow meter according to claim 2, characterized in that: It also includes a bypass side valve element for controlling the opening area of ​​the bypass flow path, The flow rate deriving unit is configured to derive a flow rate of the fluid flowing in the bypass flow path based on at least one of the differential pressure derived by the differential pressure deriving unit, the angular velocity, and the torque, and an opening degree of the bypass-side valve element.

4. The flow meter according to claim 1, characterized in that: A generator is provided that includes a turbine as the rotating body and generates electricity by converting rotational energy of the turbine into electrical energy.

5. The flow meter according to claim 4, characterized in that: The flow rate derivation unit is configured to control the flow rate of the fluid flowing through the bypass flow path by driving the generator to control the torque of the turbine.

6. The flow meter according to claim 5, characterized in that It also includes a bypass side valve element for controlling the opening area of ​​the bypass flow path, The flow rate derivation unit is configured to control the flow rate of the fluid flowing through the bypass flow path by driving the generator to control the torque of the turbine and the opening degree of the bypass-side valve element.

7. The flow meter according to claim 5 or 6, characterized in that: The flow rate deriving unit is configured to derive a flow rate of the fluid flowing in the bypass flow path based on the differential pressure derived by the differential pressure deriving unit and at least one of the angular velocity and the torque. The flow rate of the main flow path and the flow rate of the bypass flow path are added together to derive a total flow rate of the fluid flowing in the main flow path and the bypass flow path, By controlling at least the torque of the turbine and the opening degree of the primary-side valve body using the total flow rate as a feedback value, the total flow rate of the fluid flowing in the main flow path and the bypass flow path is controlled.

8. The flow meter according to claim 7, characterized in that It also includes a bypass side valve element for controlling the opening area of ​​the bypass flow path, The flow rate deriving unit is configured to derive a flow rate of the fluid flowing in the bypass flow path based on at least one of the differential pressure derived by the differential pressure deriving unit, the angular velocity, and the torque, and an opening degree of the bypass side valve element. The torque of the turbine, the opening of the main valve body, and the opening of the bypass valve body are controlled using the total flow rate as a feedback value, thereby controlling the total flow rate of the fluid flowing in the main flow path and the bypass flow path.

9. The flow meter according to claim 1, characterized in that The supervisor is also provided.

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