JP2012241659A - Power generation device using residual pressure of water supply facility - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power generation device using residual pressure of a water supply facility, and always properly controlling a pressure reducing amount without complicating a structure due to measuring equipment.SOLUTION: The rotation angular speed of a hydraulic turbine 11 is detected by an angular speed detection part 14, and an estimated flow rate of the hydraulic turbine 11 is calculated from the relationship between the angular speed detected by the angular speed detection part 14 and the characteristics of the hydraulic turbine 11. The torque of a power generator 12 by an inverter 13 is controlled based on the estimated flow rate Q so that the pressure reducing amount by the hydraulic turbine 11 becomes a target pressure reducing amount. Accordingly, the power generator 12 can be controlled to achieve the target pressure reducing amount without detecting water pressure and a flow rate from flowing water, and the measuring equipment such as a pressure gage and a flow meter becomes unnecessary. With this, the structure can be simplified and reduced in cost, and contribution can be made on the spread of the power generation device 10 capable of using surplus pressure of the water supply facility.

Description

  The present invention relates to a power generation apparatus using residual pressure in a water supply facility that is installed in a water distribution pipeline of a water supply facility and generates power while reducing tap water in the distribution pipeline.

  Conventionally, in water supply facilities, water is distributed from water sources such as dam lakes to consumers such as ordinary households and various facilities through water purification plants, but water is distributed at a high pressure so that tap water can reach the consumers sufficiently. Yes. In this case, since the water distributed to the consumer cannot be used at high pressure, the pressure is reduced using the pressure reducing valve before the water is distributed to the consumer. However, since the surplus pressure due to this depressurization is not effectively used, most of the energy of the water supply pressure is lost at present.

  In addition, as the surplus pressure at the time of decompression is used for power generation, a hydroelectric generator is provided instead of the pressure reducing valve, and the downstream side of the water turbine is decompressed by the rotational resistance of the water turbine due to the power generation load of the generator. Those are known (for example, see Patent Document 1 or 2).

JP 2006-22745 A JP 2002-242813 A

  By the way, as described above, when the tap water in the distribution pipe is depressurized by the water turbine of the generator, the generator is controlled so that the depressurization amount becomes the predetermined target depressurization amount. Because the water pressure on the upstream side of the generator changes due to fluctuations in the discharge pressure of the pressure pump on the side, or the water pressure on the downstream side of the generator changes depending on the water usage status of the consumer, this change in water pressure It is necessary to control the generator accordingly. Therefore, conventionally, pressure gauges and flow meters are provided on the upstream side and downstream side of the water turbine, respectively, and the generator is feedback-controlled so that the target pressure reduction amount is obtained.

  However, when a pressure gauge and a flow meter are provided on the upstream side and the downstream side of the water turbine, respectively, there has been a problem that the structure of the apparatus becomes complicated by these measuring devices, resulting in an increase in cost.

  The present invention has been made in view of the above-mentioned problems, and the object of the present invention is to provide a residual pressure of a water supply facility that can always accurately control the amount of pressure reduction without complicating the structure of the measuring instrument. It is to provide a power generation device.

  In order to achieve the above-mentioned object, the present invention includes a water turbine provided in a distribution pipe through which tap water circulates, and a generator that generates electric power by rotating the water turbine, and the water turbine is caused by the rotational resistance of the water turbine caused by the power generation load of the generator. In the power generation apparatus using residual pressure in a water supply facility that depressurizes the downstream side of the turbine, the angular velocity detection means for detecting the rotational angular velocity of the turbine, and the relationship between the angular velocity detected by the angular velocity detection means and the characteristics of the turbine, Control means for calculating the estimated flow rate and controlling the torque of the generator based on the estimated flow rate so that the reduced pressure amount by the water wheel becomes the target reduced pressure amount.

  As a result, the torque of the generator is controlled based on the estimated flow rate calculated from the relationship between the angular velocity of the turbine detected by the angular velocity detection means and the characteristics of the turbine, so that the amount of decompression by the turbine becomes the target decompression amount. Therefore, the generator can be controlled so that the target pressure reduction amount is obtained without detecting the water pressure or flow rate from the flowing water.

  In order to achieve the above object, the present invention includes a water wheel provided in a water distribution pipe through which tap water circulates, and a generator that generates electric power by rotating the water wheel, and the rotational resistance of the water wheel due to the power generation load of the generator. Therefore, in the power generation apparatus using residual pressure of a water supply facility that depressurizes the downstream side of the water turbine, from the relationship between the angular velocity detection means for detecting the rotational angular velocity of the water turbine, and the angular velocity detected by the angular velocity detection means and the characteristics of the water turbine. Control means for calculating the estimated flow rate of the water turbine and controlling the torque of the generator based on the estimated flow rate so that the flow rate of the water turbine becomes the target flow rate.

  Thereby, based on the estimated flow rate calculated from the relationship between the angular velocity of the water turbine detected by the angular velocity detection means and the characteristics of the water turbine, the torque of the generator is controlled so that the flow rate of the water turbine becomes the target flow rate. The generator can be controlled to achieve the target flow rate without detecting the water pressure or flow rate from the flowing water.

  In order to achieve the above object, the present invention includes a water wheel provided in a water distribution pipe through which tap water circulates, and a generator that generates electric power by rotating the water wheel, and the rotational resistance of the water wheel due to the power generation load of the generator. Therefore, in the power generation apparatus using residual pressure of a water supply facility that depressurizes the downstream side of the water turbine, from the relationship between the angular velocity detection means for detecting the rotational angular velocity of the water turbine, and the angular velocity detected by the angular velocity detection means and the characteristics of the water turbine. Control means for calculating the estimated flow rate of the water turbine and controlling the rotational angular velocity of the water wheel based on the estimated flow rate so that the reduced pressure amount by the water wheel becomes the target reduced pressure amount.

  Thereby, based on the estimated flow rate calculated from the relationship between the angular velocity of the turbine detected by the angular velocity detection means and the characteristics of the turbine, the angular velocity of the generator is controlled so that the amount of decompression by the turbine becomes the target decompression amount. Therefore, the generator can be controlled so that the target pressure reduction amount is obtained without detecting the water pressure or flow rate from the flowing water.

  In order to achieve the above object, the present invention includes a water wheel provided in a water distribution pipe through which tap water circulates, and a generator that generates electric power by rotating the water wheel, and the rotational resistance of the water wheel due to the power generation load of the generator. Therefore, in the power generation apparatus using residual pressure of a water supply facility that depressurizes the downstream side of the water turbine, from the relationship between the angular velocity detection means for detecting the rotational angular velocity of the water turbine, and the angular velocity detected by the angular velocity detection means and the characteristics of the water turbine. Control means for calculating an estimated flow rate of the water turbine and controlling a rotational angular velocity of the water turbine based on the estimated flow rate so that the flow rate of the water turbine becomes a target flow rate.

  Thereby, based on the estimated flow rate calculated from the relationship between the angular velocity of the turbine detected by the angular velocity detection means and the characteristics of the turbine, the angular velocity of the generator is controlled so that the flow rate of the turbine becomes the target flow rate. The generator can be controlled to achieve the target flow rate without detecting the water pressure or flow rate from the flowing water.

  According to the present invention, the generator can be controlled without detecting the water pressure or flow rate from the flowing water, so that a measuring device such as a pressure gauge or a flow meter is not necessary. Thereby, since the structure can be simplified and the cost can be reduced, it is possible to contribute to the popularization of power generation devices that can use surplus pressure in water facilities.

Schematic of the water supply facility showing the first embodiment of the present invention Configuration diagram of power generator Flow chart showing operation of control unit Block diagram showing the control system Diagram showing characteristic curve of water turbine Diagram showing turbine efficiency curve The flowchart which shows operation | movement of the control part which concerns on the 2nd Embodiment of this invention. Block diagram showing the control system The flowchart which shows operation | movement of the control part which concerns on the 3rd Embodiment of this invention. Block diagram showing the control system The flowchart which shows operation | movement of the control part which concerns on the 4th Embodiment of this invention. Block diagram showing the control system

  FIG. 1 thru | or 6 shows the 1st Embodiment of this invention, and is related with the electric power generating apparatus which generates electric power, depressurizing the tap water of the distribution pipe line of a water supply facility.

  The water supply facility shown in the figure distributes water from a water source 1 such as a dam lake to a consumer 4 such as a general household or various facilities via a water purification plant 2 and a reservoir 3, so that the tap water can reach the customer 4 sufficiently. The pump 5 distributes water at a high pressure. In this case, the water distribution line 6 between the reservoir 3 and the customer 4 is provided with a power generation device 10 for depressurizing tap water distributed to the customer 4, and the power generated by the power generation device 10 is The power is supplied to a predetermined power usage destination 7.

  The power generation device 10 according to the present embodiment includes a water wheel 11 provided in the water distribution pipe 6, a power generator 12 that generates power by the rotation of the water wheel 11, an inverter 13 that can apply arbitrary torque to the power generator 12, and the water wheel 11. Are provided with an angular velocity detection unit 14 that detects the rotational angular velocity of the motor 13 and a control unit 15 that controls the torque of the inverter 13 so that the amount of pressure reduction by the water turbine 11 becomes the target pressure reduction amount.

  The water turbine 11 is composed of, for example, a well-known Francis-type pump reversing water turbine, and is rotated by water flowing through the water distribution pipe 6.

  The generator 12 is a known synchronous generator that generates AC power of commercial frequency, for example, and rotates integrally with the water turbine 11.

  The inverter 13 is configured to supply the electric power generated by the generator 12 to the power usage destination 7 and to control the torque that becomes the rotational resistance of the water turbine 11.

  The angular velocity detection unit 14 is configured to detect the rotational angular velocity of the water turbine 11 from the voltage angular velocity or current angular velocity of the inverter 13.

  The control unit 15 is constituted by a microcomputer, and controls a torque command value to the inverter 13 by a program described later.

  In the power generation device 10 configured as described above, the water turbine 11 is rotated by tap water flowing through the water distribution pipe 6, and downstream of the water turbine 11 by the power generation load of the generator 12 by the inverter 13 (rotational resistance of the water turbine 11). While the pressure is reduced, the power generated by the generator 12 is supplied to the power usage destination 7 via the inverter 13. At that time, the torque of the generator 12 by the inverter 13 is controlled by the control unit 15 so that the pressure reduction amount (pressure difference between the upstream side and the downstream side of the water turbine 11) becomes a predetermined target pressure reduction amount.

Here, operation | movement of the control part 15 is demonstrated with reference to the flowchart of FIG. First, the rotational angular velocity ω of the water turbine 11 is detected by the angular velocity detector 14 (S1), and the flow rate Q of the water turbine 11 is determined from the torque command value T ^ref and the rotational angular velocity ω based on the relationship between the rotational angular velocity ω and the characteristics of the water turbine 11. Is estimated (S2). Next, a torque command value T ^ref for realizing the target pressure reduction amount H ^ref is calculated from the estimated flow rate Q (S3), and the pressure reduction amount H is estimated from the estimated flow rate Q (S4). Subsequently, a difference between the estimated pressure reduction amount H and the target pressure reduction amount H ^ref is ^calculated, and a feedback term (PI control term) of the pressure reduction amount is added to the torque command value T ^ref (S5), and a predetermined target angular velocity ω ^ref and angular velocity are added. The difference from ω is taken, and the angular velocity feedback term (P control term) is added to the torque command value T ^ref (S6). The torque command value T ^ref is output to the inverter 13 (S7), and after a predetermined time has elapsed (S8), the process returns to step S1 and the operations of steps S1 to S8 are repeated.

Further, as shown in the block diagram of FIG. 4, the control unit 15 includes a flow rate estimator 16, a torque command value setter 17, a pressure reduction amount estimator 18, a first comparator 19, a second comparator 20, A first adder 21 and a second adder 22 are provided. The flow rate estimator 16 calculates the estimated flow rate Q from the relationship between the characteristics of the water wheel 11 and the rotational angular velocity ω, and the characteristics of the water wheel 11 are obtained in advance by experiments or the like. The torque command value setter 17 calculates a torque command value T ^ref from the estimated flow rate Q and the target pressure reduction amount H ^ref using a function based on the efficiency characteristics of the water turbine 11. The decompression amount estimator 18 calculates an estimated decompression amount H from the estimated flow rate Q using a function based on the performance of the water turbine 11. The first comparator 19 calculates a deviation between the target pressure reduction amount H ^ref and the estimated pressure reduction amount H. The deviation is proportionally integrated by the PI element 23, and then the first adder 21 performs torque. It is added to the command value ^Tref . The second comparator 20 calculates a deviation between the target angular velocity ω ^ref and the angular velocity ω. The deviation is proportionally calculated by the P element 24 and then the torque command value is calculated by the second adder 22. ^Added to Tref. In this case, a rated speed or a maximum efficiency angle is set as the target angular speed ω ^ref .

  Here, a method of calculating the estimated flow rate Q and the estimated reduced pressure H will be described. First, as described above, since the characteristics of the water turbine are used for calculating the estimated flow rate Q, the characteristics of the water turbine and the efficiency of the water turbine are obtained by experiments as follows.

In this experiment, the variables π1 and π2 used in the calculation formula are defined as in the formulas (1) and (2), the angular velocity ω [rad / s], the loss head h [m], and the flow rate Q of the turbine rotated by water flow. By measuring [m ³ / s], a turbine characteristic curve with variables π1 and π2 is created as shown in FIG. D [m] is the diameter of the water wheel (impeller), and g [m / s ² ] is the gravity constant.

π1 = Q / ωd ³ (1)
π ² = gh / d ² ω ² (2)
Next, after giving the torque command value to the inverter, adjust the flow rate with the valve and adjust the rotation speed to the target value, and adjust the angular speed ω, decompression amount H, flow rate Q, torque command value, and generated current of the rotating turbine Then, as shown in FIG. 6, the turbine efficiency curve is created by the efficiency of the turbine and the generator and the variable π1.

In addition, the relational expression between the energy of running water and the work performed by the water turbine is expressed by the following formula (3) from the law of energy conservation. Here, η is the energy efficiency (0 ≦ η ≦ 1) of the turbine, ρ [kg / m ³ ] is the density of water, and T [N / m] is the torque of the turbine (generator).

η (Q) ρghQ = Tω (3)
Then, using Equation (3), a function obtained by approximating the turbine characteristic curve of FIG. 5 and a function obtained by approximating the turbine efficiency curve of FIG. 6, an equation for variables π1 and π2 is derived, By solving this and obtaining π 1 and π 2, the estimated flow rate Q and the estimated reduced pressure H are calculated by the following equations (4) and (5).

Q = ωd ³ π1 (4)
h = d ² ω ² π ² / g (5)
Next, a method for setting the torque command value T ^ref will be described. The torque command value T ^ref is calculated from the estimated flow rate Q using the function based on the efficiency characteristics of the water turbine 11 as described above, and the feedback term of the decompression amount H and the feedback term of the angular velocity ω are added to obtain the following: It can be obtained from equation (6).

T ^ref = η (Q) ρgQH ^ref / ω
+ _GH (s) ( ^Href- H)
+ Gω (s) (ω ^ref −ω) (6)
Here, the first term on the right side is derived from the equation (3). The second term on the right side is a feedback term (PI control term) of the decompression amount H, and G _H (s) is the feedback controller. The third term on the right side is a feedback term (P control term) of the angular velocity ω, and Gω (s) is the feedback controller.

  Thus, according to this embodiment, the water turbine 11 provided in the water distribution pipe 6 through which tap water circulates and the generator 12 that generates electric power by the rotation of the water turbine 11, and the water turbine by the power generation load of the generator 12. Since the downstream side of the water turbine 11 is depressurized by the rotational resistance of 11, the surplus pressure due to the depressurization can be converted into electric power and used effectively at the power usage destination 7. For example, the power usage destination 7 can usually be used as an auxiliary power source such as a street light, but supplies power to ordinary homes and various facilities in the event of a disaster, a power generation facility accident, or a power failure due to power shortage. It is also possible. At that time, when a power failure occurs in some area, not only the power of the power generation apparatus 10 installed in that area is used, but also the power of the power generation apparatus 10 in other nearby areas is used as the power failure area. If power is transmitted, effective use during a power outage can be achieved more effectively.

In the present embodiment, the rotational angular velocity ω of the water turbine 11 is detected by the angular velocity detector 14, and the estimated flow rate Q of the water turbine 11 is calculated from the relationship between the angular velocity ω detected by the angular velocity detector 14 and the characteristics of the water turbine 11. Since the torque of the generator 12 by the inverter 13 is controlled based on the estimated flow rate Q so that the pressure reduction amount H by the water turbine 11 becomes the target pressure reduction amount ^Href , the target can be obtained without detecting the water pressure or the flow rate from running water. The generator 12 can be controlled so that the amount of pressure is reduced, and a measuring instrument such as a pressure gauge or a flow meter is not required. Thereby, since the structure can be simplified and the cost can be reduced, it is possible to contribute to the popularization of the power generation apparatus 10 that can use the surplus pressure of the water supply facility.

  Further, since the estimated flow rate Q is calculated based on the rotational angular velocity ω of the water turbine 11, the torque can be controlled without depending on the rotational speed of the water turbine 11, and the rotational speed fluctuates due to a change in the flow rate. Even in an environment, the relationship between the flow rate and the reduced pressure amount can be determined accurately.

In addition, since the difference between the estimated pressure reduction amount H calculated from the estimated flow rate Q and the target pressure reduction amount H ^ref is proportionally integrated by the PI element 23 and added to the torque command value T ^ref , the target pressure reduction amount is followed. Therefore, an appropriate torque command can be given.

Further, since the difference between the rotational angular velocity ω detected by the angular velocity detecting unit 14 and the predetermined target angular velocity ω ^ref is proportionally calculated by the P element 24 and added to the torque command value T ^ref , the rotational speed of the water wheel 11 Can be stabilized.

  Further, since the torque is applied to the generator 12 by the inverter 13, the power generated by the generator 12 can be output to the power usage destination 7 via the inverter 13, which is extremely advantageous for practical use.

  In this case, since the rotational angular velocity ω of the water turbine 11 is detected from the inverter 13, a dedicated measuring device for detecting the angular velocity is not required, which is extremely advantageous in simplifying the structure.

  7 and 8 show a second embodiment of the present invention, and the same reference numerals are given to the same components as those in the previous embodiment.

  In the first embodiment, the amount of pressure reduction is controlled by controlling the torque of the generator 12 by the inverter 13. However, in this embodiment, the torque of the generator 12 is controlled by the inverter 13. By controlling, the flow rate of the water turbine 11 is controlled.

As shown in the flowchart of FIG. 7, the control unit 15 of the present embodiment first detects the rotational angular velocity ω of the water turbine 11 by the angular velocity detection unit 14 (S10), and determines the relationship between the rotational angular velocity ω and the characteristics of the water turbine 11. Based on the torque command value T ^ref and the rotational angular velocity ω, the flow rate Q of the water turbine 11 is estimated (S11). Next, the pressure reduction amount H is estimated from the estimated flow rate Q (S12), and a torque command value T ^ref for realizing the target flow rate Q ^ref is calculated from the estimated pressure reduction amount H (S13). Subsequently, the difference between the estimated flow rate Q and the target flow rate Q ^ref is calculated, a flow rate feedback term (PI control term) is added to the torque command value T ^ref (S14), and the predetermined target angular velocity ω ^ref and angular velocity ω The difference is taken and an angular velocity feedback term (P control term) is added to the torque command value T ^ref (S15). The torque command value T ^ref is output to the inverter 13 (S16), and after a predetermined time has elapsed (S17), the process returns to step S10 and the operations of steps S10 to S17 are repeated.

Further, as shown in the block diagram of FIG. 8, the control unit 15 of the present embodiment includes a flow rate estimator 16, a torque command value setting unit 17, a decompression amount estimator 18, a first comparator 19, and a second comparator. A comparator 20, a first adder 21, and a second adder 22 are provided. The flow rate estimator 16 calculates the estimated flow rate Q from the relationship between the characteristics of the water wheel 11 and the rotational angular velocity ω, and the characteristics of the water wheel 11 are obtained in advance by experiments or the like. The decompression amount estimator 18 calculates an estimated decompression amount H from the estimated flow rate Q using a function based on the performance of the water turbine 11. The torque command value setter 17 calculates a torque command value T ^ref from the estimated pressure reduction amount H and the target flow rate Q ^ref using a function based on the efficiency characteristics of the water turbine 11. The first comparator 19 obtains a deviation between the target flow rate Q ^ref and the estimated flow rate Q. The deviation is subjected to a proportional-integral calculation by the PI element 23, and then the torque command value is obtained by the first adder 21. ^Added to Tref. The second comparator 20 calculates a deviation between the target angular velocity ω ^ref and the angular velocity ω. The deviation is proportionally calculated by the P element 24 and then the torque command value is calculated by the second adder 22. ^Added to Tref. In this case, a rated speed or a maximum efficiency angle is set as the target angular speed ω ^ref .

Next, a method for setting the torque command value T ^ref will be described. The torque command value T ^ref is calculated from the estimated flow rate Q using the function based on the efficiency characteristics of the water turbine 11 as described above, and the following equation is obtained by adding the feedback term of the flow rate Q and the feedback term of the angular velocity ω. Calculated from (7).

T ^ref = η (Q) ρghQ ^ref / ω
+ G _Q (s) (Q ^ref −Q)
+ Gω (s) (ω ^ref −ω) (7)
Here, the first term on the right side is derived from the equation (3). The second term on the right side is a feedback term (PI control term) of the flow rate Q, and G _Q (s) is the feedback controller. The third term on the right side is a feedback term (P control term) of the angular velocity ω, and Gω (s) is the feedback controller. The method for calculating the estimated flow rate Q is the same as that in the first embodiment.

Thus, according to the present embodiment, the rotational angular velocity ω of the water turbine 11 is detected by the angular velocity detection unit 14, and the estimated flow rate of the water turbine 11 is determined from the relationship between the angular velocity ω detected by the angular velocity detection unit 14 and the characteristics of the water turbine 11. Q is calculated, and the torque of the generator 12 by the inverter 13 is controlled based on the estimated flow Q so that the flow Q of the water turbine 11 becomes the target flow Q ^ref. Further, the generator 12 can be controlled so as to achieve the target flow rate without detecting the flow rate, and a measuring instrument such as a pressure gauge or a flow meter is not necessary. Other effects are the same as those of the above embodiment.

  FIG. 9 and FIG. 10 show a third embodiment of the present invention, and the same reference numerals are given to the same components as those in the previous embodiment.

  In the first and second embodiments, the inverter 13 that can control the torque of the generator 12 is used. However, the inverter 13 of the present embodiment is configured to be able to control the rotational angular velocity of the generator 12. That is, in the first and second embodiments, the pressure reduction amount or the flow rate is controlled by controlling the torque of the generator 12 by the inverter 13, but in this embodiment, the inverter 13 Thus, the amount of pressure reduction is controlled by controlling the rotational angular velocity of the generator 12.

As shown in the flowchart of FIG. 9, the control unit 15 of the present embodiment first detects the rotational angular velocity ω of the water turbine 11 by the angular velocity detection unit 14 (S20), and determines the relationship between the rotational angular velocity ω and the characteristics of the water turbine 11. Based on the generator torque T and the rotational angular velocity ω, the flow rate Q of the water turbine 11 is estimated (S21). Next, an angular velocity command value ω ^ref for realizing the target pressure reduction amount H ^ref is calculated from the estimated flow rate Q (S22), and the pressure reduction amount H is estimated from the estimated flow rate Q (S23). Subsequently, a difference between the estimated pressure reduction amount H and the target pressure reduction amount H ^ref is ^calculated, and a feedback term (PI control term) of the pressure reduction amount is added to the angular velocity command value ω ^ref (S24). The angular velocity command value ω ^ref is output to the inverter 13 (S25), and after a predetermined time has elapsed (S26), the process returns to step S20 to repeat the operations of steps S20 to S26.

Further, as shown in the block diagram of FIG. 10, the control unit 15 of the present embodiment includes a flow rate estimator 16, an angular velocity command value setter 25, a decompression amount estimator 18, a comparator 26, and an adder 27. Yes. The flow rate estimator 16 calculates an estimated flow rate Q from the generator torque T and the rotational angular velocity ω on the basis of the relationship between the rotational angular velocity ω and the characteristics of the water turbine 11. Obtained by. The angular velocity command value setter 25 calculates an angular velocity command value ω ^ref from the estimated flow rate Q and the target pressure reduction amount H ^ref using a function based on the efficiency characteristics of the water turbine 11. The decompression amount estimator 18 calculates an estimated decompression amount H from the estimated flow rate Q using a function based on the performance of the water turbine 11. The comparator 26 obtains a deviation between the target pressure reduction amount H ^ref and the estimated pressure reduction amount H. The deviation is proportionally integrated by the PI element 23 and then added to the angular velocity command value ω ^ref by the adder 27. Is done.

Next, a method for setting the angular velocity command value ω ^ref will be described. The angular velocity command value ω ^ref is calculated from the estimated flow rate Q using the function based on the efficiency characteristics of the water turbine 11 as described above, and is obtained from the following equation (8) by adding the feedback term of the pressure reduction amount H. It is done.

ω ^ref = η (Q) ρgQH ^ref / T
+ G _H (s) (H ^ref −H) (8)
Here, the first term on the right side is derived from the equation (3). The second term on the right side is a feedback term (PI control term) of the decompression amount H, and G _H (s) is the feedback controller. The method for calculating the estimated flow rate Q and the estimated pressure reduction amount H is the same as in the first embodiment.

Thus, according to the present embodiment, the rotational angular velocity ω of the water turbine 11 is detected by the angular velocity detection unit 14, and the estimated flow rate of the water turbine 11 is determined from the relationship between the angular velocity ω detected by the angular velocity detection unit 14 and the characteristics of the water turbine 11. calculating a Q, since to control the angular velocity of the generator 12 by the inverter 13 based on the estimated flow rate Q as pressure reduction amount H by waterwheel 11 becomes equal to the target pressure reduction amount H ^ref, as in the embodiment, running water Therefore, it is possible to control the generator 12 so that the target pressure reduction amount is obtained without detecting the water pressure or the flow rate from the measuring device, and a measuring instrument such as a pressure gauge or a flow meter becomes unnecessary. Other effects are the same as those of the above embodiment.

  FIG. 11 and FIG. 12 show a fourth embodiment of the present invention, and the same reference numerals are given to the same components as those in the previous embodiment.

  In the first and second embodiments, the inverter 13 that can control the torque of the generator 12 is used. However, the inverter 13 of the present embodiment is configured to be able to control the rotational angular velocity of the generator 12. That is, in the first and second embodiments, the pressure reduction amount or the flow rate is controlled by controlling the torque of the generator 12 by the inverter 13, but in this embodiment, the inverter 13 Thus, the flow rate is controlled by controlling the rotational angular velocity of the generator 12.

As shown in the flowchart of FIG. 11, the control unit 15 of the present embodiment first detects the rotational angular velocity ω of the water turbine 11 by the angular velocity detection unit 14 (S30), and determines the relationship between the rotational angular velocity ω and the characteristics of the water turbine 11. Based on the generator torque T and the rotational angular velocity ω, the flow rate Q of the water turbine 11 is estimated (S31). Next, the depressurization amount H is estimated from the estimated flow rate Q (S32), and the angular velocity command value ω ^ref for realizing the target flow rate ^Qref is calculated from the estimated depressurization amount H (S33). Subsequently, the difference between the estimated flow rate Q and the target flow rate Q ^ref is taken, and a flow rate feedback term (PI control term) is added to the angular velocity command value ω ^ref (S34). The angular velocity command value ω ^ref is output to the inverter 13 (S35), and after a predetermined time has elapsed (S36), the process returns to step S30 to repeat the operations of steps S30 to S36.

Further, as shown in the block diagram of FIG. 12, the control unit 15 of the present embodiment includes a flow rate estimator 16, a pressure reduction amount estimator 18, an angular velocity command value setting unit 25, a comparator 26, and an adder 27. Yes. The flow rate estimator 16 calculates an estimated flow rate Q from the generator torque T and the rotational angular velocity ω on the basis of the relationship between the rotational angular velocity ω and the characteristics of the water turbine 11. Obtained by. The decompression amount estimator 18 calculates an estimated decompression amount H from the estimated flow rate Q using a function based on the performance of the water turbine 11. The angular velocity command value setter 25 calculates an angular velocity command value ω ^ref from the estimated pressure reduction amount H and the target flow rate Q ^ref using a function based on the efficiency characteristics of the water turbine 11. The comparator 26 obtains a deviation between the target flow rate Q ^ref and the estimated flow rate Q. The deviation is proportionally integrated by the PI element 23 and then added to the angular velocity command value ω ^ref by the adder 27. .

Next, a method for setting the angular velocity command value ω ^ref will be described. The angular velocity command value ω ^ref is calculated from the estimated flow rate Q using the function based on the efficiency characteristics of the water turbine 11 as described above, and is obtained from the following equation (9) by adding the feedback term of the flow rate Q. .

ω ^ref = η (Q) ρghQ ^ref / T
+ G _Q (s) (Q ^ref −Q) (9)
Here, the first term on the right side is derived from the equation (3). The second term on the right side is a feedback term (PI control term) of the flow rate Q, and G _H (s) is the feedback controller. The method for calculating the estimated flow rate Q is the same as that in the first embodiment.

Thus, according to the present embodiment, the rotational angular velocity ω of the water turbine 11 is detected by the angular velocity detection unit 14, and the estimated flow rate of the water turbine 11 is determined from the relationship between the angular velocity ω detected by the angular velocity detection unit 14 and the characteristics of the water turbine 11. Q is calculated, and the angular velocity of the generator 12 by the inverter 13 is controlled based on the estimated flow Q so that the flow Q of the water turbine 11 becomes the target flow Q ^ref. Further, the generator 12 can be controlled so as to achieve the target flow rate without detecting the flow rate, and a measuring instrument such as a pressure gauge or a flow meter is not necessary. Other effects are the same as those of the above embodiment.

  DESCRIPTION OF SYMBOLS 10 ... Power generation device, 11 ... Water wheel, 12 ... Generator, 13 ... Inverter, 14 ... Angular velocity detection part, 15 ... Control part.

Claims (11)

A water supply facility equipped with a water turbine provided in a distribution pipe through which tap water circulates and a generator that generates electricity by rotating the turbine, and the downstream side of the turbine is depressurized by the rotational resistance of the turbine caused by the power generation load of the generator In the residual pressure power generation device of
Angular velocity detection means for detecting the rotational angular velocity of the water wheel;
Control that calculates the estimated flow rate of the water turbine from the relationship between the angular velocity detected by the angular velocity detection means and the characteristics of the turbine, and controls the torque of the generator based on the estimated flow rate so that the reduced pressure amount by the turbine becomes the target reduced pressure amount A power generation device using residual pressure of a water supply facility. 2. The water supply facility according to claim 1, wherein the control unit is configured to perform a proportional-integral operation on a difference between an estimated pressure reduction amount calculated from the estimated flow rate and a target pressure reduction amount, and to add to a torque command value. Residual pressure generator. A water supply facility equipped with a water turbine provided in a distribution pipe through which tap water circulates and a generator that generates electricity by rotating the turbine, and the downstream side of the turbine is depressurized by the rotational resistance of the turbine caused by the power generation load of the generator In the residual pressure power generation device of
Angular velocity detection means for detecting the rotational angular velocity of the water wheel;
Control means for calculating the estimated flow rate of the water turbine from the relationship between the angular velocity detected by the angular velocity detection means and the characteristics of the water turbine, and for controlling the torque of the generator based on the estimated flow rate so that the flow rate of the water turbine becomes the target flow rate; A power generation device using residual pressure in a water supply facility. The residual pressure utilization power generation apparatus of the water supply facility according to claim 3, wherein the control means is configured to perform a proportional-integral calculation on a difference between the estimated flow rate and the target flow rate and to add the torque command value. The control means is configured to proportionally calculate a difference between an angular velocity detected by the angular velocity detection means and a predetermined target angular velocity and add it to a torque command value. Power generation equipment using residual pressure of the water supply facility described. A water supply facility equipped with a water turbine provided in a distribution pipe through which tap water circulates and a generator that generates electricity by rotating the turbine, and the downstream side of the turbine is depressurized by the rotational resistance of the turbine caused by the power generation load of the generator In the residual pressure power generation device of
Angular velocity detection means for detecting the rotational angular velocity of the water wheel;
Control for calculating the estimated flow rate of the turbine based on the relationship between the angular velocity detected by the angular velocity detection means and the characteristics of the turbine, and controlling the rotational angular velocity of the turbine based on the estimated flow rate so that the reduced pressure amount by the turbine becomes the target reduced pressure amount A power generation device using residual pressure of a water supply facility. The water supply facility according to claim 6, wherein the control unit is configured to perform a proportional-integral operation on a difference between the estimated pressure reduction amount calculated from the estimated flow rate and the target pressure reduction amount and add the difference to the angular velocity command value. Residual pressure generator. A water supply facility equipped with a water turbine provided in a distribution pipe through which tap water circulates and a generator that generates electricity by rotating the turbine, and the downstream side of the turbine is depressurized by the rotational resistance of the turbine caused by the power generation load of the generator In the residual pressure power generation device of
Angular velocity detection means for detecting the rotational angular velocity of the water wheel;
Control means for calculating an estimated flow rate of the water turbine from the relationship between the angular velocity detected by the angular velocity detection means and the characteristics of the turbine, and for controlling the rotational angular speed of the turbine based on the estimated flow rate so that the flow rate of the turbine becomes the target flow rate; A power generation device using residual pressure in a water supply facility. The residual pressure utilization power generation apparatus of a water supply facility according to claim 8, wherein the control means is configured to perform a proportional-integral calculation on a difference between the estimated flow rate and a target flow rate and add the result to an angular velocity command value. The residual pressure utilization power generation apparatus of the water supply facility as described in any one of Claim 1 thru | or 9 provided with the inverter which provides the electric power generation load used as the rotation resistance of a water turbine to the said generator. The residual pressure utilization power generation apparatus of the water supply facility according to claim 10, wherein the angular velocity detection means is configured to detect a rotational angular velocity of a water turbine from an inverter.

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