KR20210130866A - Flow predictable positive displacement turbine - Google Patents

Abstract

The present invention provides a flux-predictable volumetric turbine, and more specifically, to the flux-predictable volumetric turbine which reduces a pressure and predicts a flux at the same time. To achieve this end, the present invention provides the flux-predictable volumetric turbine which comprises a pair of rotating units prepared to be engaged with each other to rotate. The flux which passes the pair of rotating units is calculated by using a volume, a pressure difference between an inlet and an outlet, a density of fluid, and a rotational speed of the rotating units as variables.

Description

FLOW PREDICTABLE POSITIVE DISPLACEMENT TURBINE

The present invention relates to a positive displacement aberration capable of predicting a flow rate, and more particularly, to a positive displacement aberration capable of predicting a flow rate while reducing pressure and simultaneously predicting a flow rate.

In general, a heat transport pipe network of district heating uses a system for controlling or reducing pressure through a valve to protect user equipment from high-pressure fluid and to supply the fluid over a long distance.

However, pressure control valves such as differential pressure flow control valves (PDCV) and temperature control valves (TCV) have a limit in which pressure control is possible only up to 6 bar, and when high pressure fluid is used, cavitation occurs, causing frequent failures and malfunctions. Because of this, many problems occur, and it is a cause of energy loss and civil complaints.

In order to solve this problem, instead of the differential pressure valve, research has been conducted to apply a positive displacement flow meter that has a long lifespan and can effectively reduce pressure.

1 and 2 are exemplary views showing the occurrence of cavitation during operation of a general positive displacement flow meter.

As shown in FIGS. 1 and 2 , when the positive displacement flow meter is operated, a pair of blades are engaged to rotate.

However, the pair of blades rotating in this way will cause cavitation (C) in the portion in contact with each other.

The cavitation (C) generated in this way prevents the constant passage of the fluid between the pair of blades, thereby making it difficult to accurately measure the flow rate.

Therefore, in the prior art, in order to accurately measure the flow rate, it has to be provided with an electronic device for measuring the flow rate together with a device for reducing the pressure of the fluid.

However, the electronic flow measurement device for measuring the flow rate as described above is expensive, so there is a problem in that it is not economical.

Therefore, there is a need for a positive displacement aberration capable of accurately predicting and measuring the flow rate without cavitation by reducing the pressure at a low cost.

Japanese Patent No. 3310239

SUMMARY OF THE INVENTION An object of the present invention to solve the above problems is to provide a positive displacement aberration capable of predicting the flow rate while reducing the pressure.

The technical problems to be achieved by the present invention are not limited to the technical problems mentioned above, and other technical problems not mentioned can be clearly understood by those of ordinary skill in the art to which the present invention belongs from the description below. There will be.

The configuration of the present invention for achieving the above object includes a pair of rotating parts provided to rotate in engagement with each other, and the flow rate passing through the pair of rotating parts is the volumetric amount, the difference between the inlet pressure and the outlet pressure, the fluid It provides a volumetric aberration capable of predicting a flow rate, characterized in that it is calculated using the density of and the rotational speed of the rotating part as variables.

In an embodiment of the present invention, the flow rate may be calculated by the following equation.

는 유량,

는 용적량[m³], P는 입구측 압력과 출구측 압력의 차이[Pa], ρ는 유체의 밀도[kg/m³], N은 회전자의 회전속도[rev/s])(

is the flow rate,

is the volume [m ³ ], P is the difference between the inlet pressure and the outlet pressure [Pa], ρ is the density of the fluid [kg/m ³ ], N is the rotational speed of the rotor [rev/s])

는 0.00070838834m³인 것을 특징으로 할 수 있다.In an embodiment of the present invention, the

may be characterized as 0.00070838834m ^{3 .}

[kg/m³]이고, 여기서, T는 3barG[℃] 조건에서의 온도인 것을 특징으로 할 수 있다.In an embodiment of the present invention, the density ρ of the fluid is

[kg/m ³ ], where T may be characterized as a temperature in the condition of 3 barG [℃].

In an embodiment of the present invention, the pair of rotating parts, the first rotating part provided on the inner side of the pipe; and a second rotating part provided on the other side of the inner side of the pipe and provided to rotate in engagement with the first rotating part.

In an embodiment of the present invention, the first rotation unit, a first rotor forming a blade; and a first rotation shaft provided at the center of the first rotor to form an axis for rotation of the first rotor.

In an embodiment of the present invention, the second rotating portion, forming a wing, a second rotor provided to rotate in engagement with the first rotor; and a second rotation shaft provided at the center of the second rotor to form an axis for rotation of the second rotor.

In an embodiment of the present invention, the first rotor and the second rotor may be provided in a twisted state by a preset angle.

In an embodiment of the present invention, the first rotor is provided with a plurality of lengths extending in the radial direction of the first rotation shaft, and the second rotor is provided with a plurality of lengths extending in the radial direction of the second rotation shaft. can be characterized as

In an embodiment of the present invention, each of the first rotor is twisted in a clockwise direction in width, and the second rotor is twisted in a counterclockwise direction in width.

In an embodiment of the present invention, it may further include a pressure measuring unit provided to measure the inlet pressure and the outlet pressure of the pair of rotating parts.

In an embodiment of the present invention, the pressure measuring unit includes: a first sensor provided on the inlet side of the pair of rotating parts to measure the pressure; and a second sensor provided on the outlet side of the pair of rotating parts to measure the pressure.

The configuration of the present invention for achieving the above object provides a water turbine generator to which a positive displacement aberration capable of predicting a flow rate is applied.

The effect of the present invention according to the above configuration is to reduce the pressure pulsation and reduce the pressure pulsation while reducing the pressure difference between the inlet side and the outlet side while the pair of rotors rotate while meshing with each other in a twisted state by a predetermined angle. phenomenon can be reduced.

In addition, the present invention is convenient for maintenance because a phenomenon such as cavitation does not occur when using the conventional differential pressure valve.

And, according to the present invention, it is possible to predict the flow rate without the electronic flow measurement device.

Therefore, according to the present invention, the flow rate can be measured relatively accurately while lowering the pressure of the fluid at a low cost, which is economical.

In addition, the present invention is applied to a water turbine power generation system, and unlike the differential pressure valve that simply controls the flow rate and water pressure, it is economical by generating power according to the rotation of the rotor.

It should be understood that the effects of the present invention are not limited to the above-described effects, and include all effects that can be inferred from the configuration of the invention described in the detailed description or claims of the present invention.

1 and 2 are exemplary views showing the occurrence of cavitation during operation of a general positive displacement flow meter.
3 is an exemplary diagram of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention.
4 is a perspective view of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention.
5 is a cross-sectional view of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention.
6 is a perspective view illustrating a rotor of a positive displacement water wheel capable of predicting a flow rate according to an embodiment of the present invention.
7 is a graph illustrating a difference in inlet and outlet pressures according to the flow rate of a positive displacement water wheel capable of predicting a flow rate according to an embodiment of the present invention.
8 is a graph illustrating a change in hydrodynamic force according to the flow rate of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention.
9 is a graph showing the density of a fluid according to the temperature of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention.
10 is a graph illustrating a change in flow rate according to the variable x of Equation 1 of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention.
11 is a graph illustrating an error rate between a predicted flow rate and a flow rate measurement value calculated according to Equation 1 of a volumetric aberration capable of predicting a flow rate according to an embodiment of the present invention.
12 is an exemplary diagram of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention.
13 is an exemplary view showing the shape of the entrance/exit of a general positive displacement aberration.
14 is a graph showing the inlet pressure pulsation according to time for the shapes of the inlet side and the outlet side according to an embodiment of the present invention.
15 is a graph showing pressure pulsations at the outlet side with respect to the shapes of the inlet side and the outlet side according to an embodiment of the present invention.
16 is a graph illustrating flow rate pulsations with time for shapes of an inlet side and an outlet side according to an embodiment of the present invention.
17 is a graph showing torque pulsations according to time for the shapes of the inlet side and the outlet side according to an embodiment of the present invention.

Hereinafter, the present invention will be described with reference to the accompanying drawings. However, the present invention may be embodied in several different forms, and thus is not limited to the embodiments described herein. And in order to clearly explain the present invention in the drawings, parts irrelevant to the description are omitted, and similar reference numerals are attached to similar parts throughout the specification.

Throughout the specification, when a part is said to be “connected (connected, contacted, coupled)” with another part, it is not only “directly connected” but also “indirectly connected” with another member interposed therebetween. "Including cases where In addition, when a part "includes" a certain component, this means that other components may be further provided without excluding other components unless otherwise stated.

The terms used herein are used only to describe specific embodiments, and are not intended to limit the present invention. The singular expression includes the plural expression unless the context clearly dictates otherwise. In this specification, terms such as "comprises" or "have" are intended to designate that the features, numbers, steps, operations, components, parts, or combinations thereof described in the specification exist, but one or more other features It should be understood that this does not preclude the existence or addition of numbers, steps, operations, components, parts, or combinations thereof.

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

3 is an exemplary diagram of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention, and FIG. 4 is a perspective view of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention.

5 is a cross-sectional view of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention, and FIG. 6 is a perspective view illustrating a rotor of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention.

3 to 6 , the positive displacement aberration 100 capable of predicting a flow rate may include a pair of rotating units 110 and 120 and a pressure measuring unit 130 .

The rotating units 110 and 120 may be provided as a pair to be rotated by being engaged with each other, and the rotors of the pair of rotating units may be provided in a twisted state by a predetermined angle.

More specifically, the pair of rotating units may include the first rotating unit 110 and the second rotating unit 120 .

The first rotation unit 110 is provided on one side of the inside of the pipe, and may include a first rotation shaft 111 and a first rotor 112 .

The first rotation shaft 111 is provided at the center of the first rotor 112 , and may form an axis for rotation of the first rotor 112 .

The first rotor 112 is provided in a state in which the blades are twisted by a predetermined angle, and may be provided rotatably.

The second rotation shaft 121 is provided at the center of the second rotor 122 , and may form an axis for rotation of the second rotor 122 .

The second rotor 122 is provided in a state in which the blades are twisted by a predetermined angle, and may be provided rotatably.

And in particular, the second rotor 122 may be provided to rotate in engagement with the first rotor 112 . That is, the first rotor 112 and the second rotor 122 may be characterized in that they are provided to rotate while being engaged with each other in a twisted state.

More specifically, the first rotor 112 is provided with a plurality of lengths extending in the radial direction of the first rotation shaft 111 , and the second rotor 122 is the second rotation shaft 121 . The length may be extended in the radial direction to be provided in plurality.

In addition, each of the first rotors 112 may have a width twisted in a clockwise direction, and the second rotor 122 may have a width twisted in a counterclockwise direction.

Here, the widths of the first rotor 112 and the second rotor 122 may refer to thickness directions of the first rotor 112 and the second rotor 122 .

More specifically, the second rotor 122 may be provided in a twisted state by a preset angle along the longitudinal direction of the axis of the rotation shaft 121 . In this case, the second rotor 122 may be provided to be twisted to correspond to the shape of the first rotor 112 in order to be engaged with the first rotor 112 .

In particular, the first rotor 112 and the second rotor 122 may be provided with a plurality of blades protruding and extending in a radial direction from the rotation axis, respectively, and each blade may be independently twisted.

In addition, the first rotor 112 and the second rotor 122 are provided to rotate in opposite directions to each other, and the first rotor 112 and the second rotor 122 each have a casing and It may be provided to allow water to pass through the opposite side.

For example, the water flowing from the upper portion of the first rotor 112 is introduced between the wings constituting the first rotor 112 . And, while the first rotor 112 rotates counterclockwise, the introduced water moves between the casing and the first rotor 112 . And when the introduced water leaves the casing and goes downward, it may be discharged to the lower part.

The twist angle of the first rotor 112 and the second rotor 122 is most preferably 45, but may be provided at an angle of 40 degrees to 50 degrees. However, the twist angle of the rotating part is not limited and can be applied to the content to be described later for predicting the flow rates of the first rotor 112 and the second rotor 122 . Twist angles of the first rotor 112 and the second rotor 122 may be provided to be variable.

As such, in the present invention, as the first rotor 112 and the second rotor 122 are rotated in a twisted state, it is possible to reduce the differential pressure between the inlet side and the discharge side as well as the inlet side And pressure pulsation on the outlet side can be significantly reduced compared to the untwisted rotor.

In addition, the first rotor 112 and the second rotor 122 may be provided to measure the flow rate according to the number of rotations. The present invention thus prepared can measure the flow rate more precisely compared to the conventional differential pressure valve.

The pressure measuring unit 130 may be provided to measure an inlet pressure and an outlet pressure of the pair of rotating units, and may include a first sensor 131 and a second sensor 132 .

The first sensor 131 may be provided on the inlet side of the pair of rotating parts to measure the pressure.

The second sensor 132 may be provided at the outlet side of the pair of rotating parts to measure the pressure.

The first sensor 131 and the second sensor 132 thus provided may be provided to continuously measure the pressure at the inlet side and the outlet side of the pair of rotating parts in real time to monitor the pressure pulsation.

On the other hand, the positive displacement water wheel 100 that can predict the flow rate is the volumetric amount of the first rotor 112 and the second rotor 122, the difference between the inlet pressure and the outlet pressure, the density of the fluid, and the rotation of the rotating part. It may be provided to predict the flow rate using the velocity as a variable. Specifically, the flow rate of the volumetric aberration 100 capable of predicting the flow rate may be measured by Equation 1 below.

는 유량,

는 용적량[m³], P는 입구측 압력과 출구측 압력의 차이[Pa], ρ는 유체의 밀도[kg/m³], N은 회전자의 회전속도[rev/s]를 의미한다.here,

is the flow rate,

where is the volume [m ³ ], P is the difference between the inlet pressure and the outlet pressure [Pa], ρ is the density of the fluid [kg/m ³ ], and N is the rotational speed of the rotor [rev/s].

는 0.00070838834m³이다.At this time, the

is 0.00070838834 m ³ .

And, the density of the fluid may be calculated by Equation 2 below.

Here, ρ is the density of the fluid [kg/m ³ ], and T is the temperature in the condition of 3 barG [℃].

In order to derive and verify Equations 1 and 2 above, the flow rate measured using a temperature-controllable performance test facility and the predicted flow rate according to Equation 1 were compared.

No. Flowrate Effective Head Hydraulic Power Hydraulic Efficiency Inlet Pressure Outlet Pressure Del P Inlet Temp Out Temp unit m ³ /h m kW % bar bar bar ℃ ℃ 15 ℃ One 55.187 69.481 6.674 63.880 9.930 3.120 6.810 14.6 14.6 2 54.368 59.782 5.632 63.590 8.940 3.070 5.870 14.4 14.4 3 53.944 53.514 5.007 63.650 8.300 3.050 5.250 14.9 14.9 4 53.405 47.853 4.384 62.960 7.710 3.020 4.690 15.1 15.1 5 52.979 42.709 3.822 61.980 7.190 3.000 4.190 15.3 15.3 6 52.167 36.099 3.060 59.630 6.540 3.000 3.540 15.5 15.5 7 51.413 30.140 2.325 55.070 5.970 3.020 2.950 15.7 15.7 8 50.579 23.654 1.588 48.720 5.320 3.000 2.320 15.8 15.8 9 49.241 16.784 0.789 35.050 4.650 3.010 1.640 16.0 16.0 10 48.676 13.443 0.428 24.000 4.310 3.000 1.310 16.1 16.1

No. Rotation Speed Torque Tank Press Density Head massflow rate X Q_predict Error unit rpm N*m bar kg/m ³ m kg/s m ³ /h % 15 ℃ One 902 70.700 1.460 999.267 69.470 15.318 4.041 55.067 -0.218 2 901 59.700 1.460 999.299 59.879 15.092 3.487 54.411 0.080 3 901 53.100 1.470 999.218 53.559 14.973 3.119 53.912 -0.059 4 900 46.500 1.470 999.185 47.847 14.823 2.789 53.420 0.028 5 902 40.500 1.470 999.151 42.748 14.704 2.487 52.921 -0.109 6 900 32.500 1.480 999.117 36.118 14.478 2.106 52.213 0.088 7 899 24.700 1.480 999.083 30.099 14.268 1.757 51.462 0.096 8 902 16.800 1.480 999.066 23.671 14.037 1.377 50.500 -0.157 9 899 8.400 1.490 999.031 16.734 13.665 0.977 49.256 0.031 10 902 4.500 1.490 999.014 13.367 13.508 0.778 48.519 -0.322

The above Tables 1 and 2 show the measured flow rate, effective head, manual force, fluid efficiency, inlet and outlet pressure and differential pressure, inlet and outlet temperature, rotational speed, rotational force, and internal pressure when the water temperature is 15 ° C. , density, head, mass flow rate, the values in parentheses of Equation 1, the predicted flow rate measured by Equation 1, and the error rate between the predicted flow rate and the measured flow rate are in order.

No. Flowrate Effective Head Hydraulic Power Hydraulic Efficiency Inlet Pressure Outlet Pressure Del P Inlet Temp Out Temp unit m ³ /h m kW % bar bar bar ℃ ℃ 50 ℃ 11 55.437 71.394 6.740 62.500 10.100 3.100 7.000 50.3 50.3 12 54.687 61.792 5.846 63.490 9.120 3.060 6.060 50.4 50.4 13 54.196 54.950 5.152 63.490 8.440 3.050 5.390 50.0 50.0 14 53.727 49.296 4.582 63.490 7.830 3.000 4.830 50.5 50.5 15 52.847 42.857 3.813 61.770 7.250 3.050 4.200 50.6 50.6 16 52.209 36.252 3.076 59.650 6.620 3.060 3.560 50.7 50.7 17 51.766 31.277 2.526 57.260 6.100 3.030 3.070 50.8 50.8 18 50.677 25.072 1.847 53.340 5.460 3.000 2.460 50.8 50.8 19 49.799 19.481 1.241 46.960 4.920 3.010 1.910 50.9 50.9 20 48.947 14.550 0.708 36.510 4.430 3.000 1.430 50.9 50.9 21 48.256 12.339 0.432 26.650 4.220 3.010 1.210 51.0 51.0

No. Rotation Speed Torque Tank Press Density Head massflow rate X Q_predict Error unit rpm Nm bar kg/m ³ m kg/s m ³ /h % 50 ℃ 11 902 71.300 0.940 988.013 72.221 15.215 4.201 55.226 -0.380 12 902 61.900 0.960 987.968 62.526 15.08 3.637 54.601 -0.157 13 903 54.500 0.940 988.15 55.603 14.876 3.231 54.069 -0.234 14 903 48.500 0.970 987.922 49.837 14.744 2.896 53.584 -0.266 15 898 40.600 0.980 987.876 43.339 14.502 2.532 53.000 0.289 16 900 32.700 0.990 987.83 36.737 14.326 2.142 52.285 0.145 17 903 26.700 1.000 987.785 31.682 14.204 1.841 51.654 -0.217 18 898 19.600 1.010 987.785 25.387 13.905 1.483 50.787 0.218 19 899 13.200 1.010 987.738 19.712 13.663 1.150 49.830 0.063 20 902 7.500 1.020 987.738 14.758 13.430 0.858 48.830 -0.239 21 898 4.600 1.020 987.692 12.488 13.239 0.730 48.327 0.147

The above Tables 3 and 4 show the measured flow rate, effective head, manual force, fluid efficiency, inlet and outlet pressure and differential pressure, inlet and outlet temperature, rotational speed, rotational force, and internal pressure when the water temperature is 50 ° C. , density, head, mass flow rate, the values in parentheses of Equation 1, the predicted flow rate measured by Equation 1, and the error rate between the predicted flow rate and the measured flow rate are in order.

No. Flowrate Effective Head Hydraulic Power Hydraulic Efficiency Inlet Pressure Outlet Pressure Del P Inlet Temp Out Temp unit m ³ /h m kW % bar bar bar ℃ ℃ 110 ℃_1 22 54.697 61.356 5.179 56.640 9.130 3.110 6.020 109.4 109.4 23 55.280 67.642 5.769 56.620 9.810 3.180 6.630 109.7 109.7 24 55.804 80.061 6.782 55.700 11.120 3.260 7.860 110.0 110.0 25 54.467 57.724 4.982 58.150 8.770 3.100 5.670 110.1 110.1 26 53.971 51.968 4.481 58.630 8.160 3.060 5.100 110.1 110.1 27 53.191 43.044 3.689 59.130 7.180 2.950 4.230 110.0 110.0 28 53.008 42.489 3.669 59.780 7.180 3.010 4.170 109.9 109.9 29 52.328 35.296 3.051 60.630 6.540 3.080 3.460 109.8 109.8 30 51.647 30.181 2.555 60.140 6.040 3.080 2.960 109.7 109.7 31 51.124 25.864 2.075 57.590 5.550 3.010 2.540 109.6 109.6 32 50.051 20.489 1.442 51.600 5.020 3.010 2.010 109.4 109.4 33 49.021 14.881 0.817 41.090 4.480 3.020 1.460 109.3 109.3 34 48.413 12.459 0.538 32.720 4.220 3.000 1.220 109.2 109.2

No. Rotation Speed Torque Tank Press Density Head massflow rate X Q_predict Error unit rpm Nm bar kg/m ³ m kg/s m ³ /h % 110 ℃_1 22 902 54.900 1.520 950.576 64.557 14.443 3.755 54.745 0.088 23 904 60.900 1.560 950.343 71.115 14.593 4.128 55.155 -0.226 24 900 72.000 1.610 950.11 84.330 14.728 4.916 55.574 -0.412 25 902 52.700 1.520 950.032 60.838 14.374 3.539 54.478 0.020 26 901 47.500 1.510 950.032 54.722 14.243 3.187 54.008 0.068 27 903 39.000 1.470 950.11 45.383 14.038 2.637 53.175 -0.030 28 901 38.900 1.460 950.188 44.736 13.991 2.605 53.122 0.216 29 903 32.300 1.430 950.266 37.116 13.813 2.157 52.314 -0.027 30 902 27.000 1.400 950.343 31.750 13.634 1.847 51.667 0.039 31 905 21.900 1.380 950.421 27.243 13.497 1.579 51.035 -0.175 32 901 15.300 1.360 950.576 21.555 13.216 1.255 50.150 0.198 33 901 8.700 1.330 950.654 15.655 12.945 0.912 49.026 0.010 34 900 5.700 1.310 950.731 13.081 12.785 0.763 48.460 0.097

No. Flowrate Effective Head Hydraulic Power Hydraulic Efficiency Inlet Pressure Outlet Pressure Del P Inlet Temp Out Temp unit m^3/h m kW % bar bar bar ℃ ℃ 110 ℃_2 35 55.776 78.214 6.737 56.670 10.800 3.120 7.680 110.9 110.9 36 54.976 66.585 5.664 56.790 9.620 3.090 6.530 110.8 110.8 37 54.628 58.109 5.102 58.980 8.770 3.070 5.700 110.9 110.9 38 53.678 48.128 4.240 60.240 7.710 2.990 4.720 110.9 110.9 39 52.923 40.312 3.515 60.470 6.980 3.020 3.960 111.0 111.0 40 52.238 33.372 2.892 60.870 6.290 3.020 3.270 110.9 110.9 41 51.022 25.571 2.055 57.790 5.540 3.030 2.510 110.9 110.9 42 49.947 19.444 1.350 51.010 4.950 3.040 1.910 110.9 110.9 43 48.347 12.206 0.536 33.340 4.200 3.000 1.200 110.9 110.9

No. Rotation Speed Torque Tank Press Density Head massflow rate X Q_predict Error unit rpm Nm bar kg/m ³ m kg/s m ³ /h % 110 ℃_2 35 899 71.500 1.500 949.408 82.459 14.710 4.813 55.580 -0.351 36 899 60.200 1.520 949.486 70.106 14.500 4.092 55.119 0.260 37 902 54.000 1.520 949.408 61.200 14.407 3.560 54.505 -0.225 38 900 45.000 1.500 949.408 50.678 14.156 2.955 53.672 -0.011 39 901 37.300 1.530 949.33 42.522 13.956 2.476 52.903 -0.037 40 903 30.600 1.510 949.408 35.110 13.776 2.040 52.080 -0.302 41 900 21.800 1.500 949.408 26.950 13.456 1.571 51.014 -0.016 42 900 14.300 1.510 949.408 20.507 13.172 1.196 49.970 0.047 43 898 5.700 1.490 949.408 12.884 12.750 0.753 48.421 0.152

Tables 5 to 8 show the flow rate, effective head, manual force, fluid efficiency, inlet and outlet pressure and differential pressure, inlet and outlet temperature, rotational speed, rotational force, and internal pressure measured when the water temperature is 110° C. , density, head, mass flow rate, the values in parentheses of Equation 1, the predicted flow rate measured by Equation 1, and the error rate between the predicted flow rate and the measured flow rate are in order.

7 to 11 of the present invention are graphs showing the values derived in Tables 1 to 8 above.

7 is a graph showing the difference between the inlet and outlet pressures according to the flow rate of the positive displacement water wheel capable of predicting the flow rate according to an embodiment of the present invention, and FIG. 8 is a flow rate prediction possible according to an embodiment of the present invention. It is a graph showing the change of hydraulic pressure according to the flow rate of the positive displacement water wheel.

Referring to FIG. 7 , it can be seen that when the difference between the inlet pressure and the outlet pressure increases, the flow rate also increases.

And, referring to FIG. 8 , as the hydraulic force increases, the flow rate also increases.

9 is a graph showing the density of a fluid according to the temperature of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention.

Referring to FIG. 9 , it can be seen that the fluid density decreases as the temperature increases. When the graph thereof is functionalized, Equation 2 is derived.

10 is a graph illustrating a change in flow rate according to variable x in Equation 1 of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention.

이다.Here, the variable x in FIG. 10 is

am.

Referring to FIG. 10 , it can be confirmed that the flow rate linearly increases when the variable x increases.

11 is a graph illustrating an error rate between a predicted flow rate calculated according to Equation 1 of a volumetric aberration capable of predicting a flow rate and an error rate of a flow rate measurement value according to an embodiment of the present invention.

Referring to Tables 1 to 8 and FIG. 11 , an error rate according to each experiment can be confirmed.

As disclosed, using Equation 1 of the present invention, it can be seen that the predicted flow rate value can be calculated so that the flow rate measurement value has an error rate of within 0.4%.

As such, in the conventional positive displacement flow meter, it was difficult to predict and calculate the correct flow rate due to the cavitation phenomenon. By automatically calculating, even if cavitation occurs, it is possible to find out the measured flow rate and the predicted flow rate within an error rate of 0.4%.

The positive displacement water wheel 100 capable of predicting the flow rate according to the present invention may be applied to a water wheel generator.

Specifically, the positive displacement water wheel 100 capable of predicting the flow rate according to the present invention may be installed in a heat transport pipe network of district heating in the form of a water turbine generator.

As such, the positive displacement water wheel 100, which can predict the flow rate installed in the heat transport pipe network, is provided to produce power as the first rotor 112 and the second rotor 122 are rotated by high-pressure water, The power generated may be provided to provide a pump that delivers water at high pressure.

To this end, although not shown, the water turbine generator may further include an energy storage device (ESS), a system power source, a pump driving unit, and the like.

As such, the positive displacement water wheel 100 having a differential pressure control and flow rate integration function of the present invention is applied to a water turbine generator, simply controlling the flow rate and water pressure, and lowering the high pressure water to the target water pressure to waste energy. Alternatively, by generating power according to the rotation of the first rotor 112 and the second rotor, more economical operation than the related art is possible.

Meanwhile, the positive displacement water wheel 100 capable of predicting a flow rate according to the present invention may further include an inlet 140 and an outlet 150 .

Hereinafter, it will be described in more detail with reference to the following drawings.

12 is an exemplary diagram of a positive displacement aberration capable of predicting a flow rate according to an embodiment of the present invention, and FIG. 13 is an exemplary diagram illustrating an entrance/exit shape of a general positive displacement aberration.

As shown in FIG. 13 , a general positive displacement aberration has a shape of a circle (1), a rectangle (2), or a square (3) on the inlet and outlet sides of the aberration, and there is no change in height.

The conventional positive displacement aberration provided in this way has a large pressure pulsation at the inlet side and the outlet side, and in particular, there is a problem in that the pressure pulsation is very large during initial operation.

On the other hand, as shown in FIG. 12 , the inlet 140 and the outlet 150 of the present invention are closer to the rotating parts 110 and 120 in order to reduce the pressure pulsation on the inlet and outlet side of the rotating parts 110 and 120 . It is characterized in that it is provided so that the inner area is gradually expanded.

The inlet 140 is provided on the inlet side of the first rotating unit 110 and the second rotating unit 120 , and includes an inlet pipe 141 and an inlet expansion pipe 142 .

The inlet pipe 141 may be provided on the inlet side of the first rotating part 110 and the second rotating part 120 to introduce the fluid toward the first rotating part 110 and the second rotating part 120 . can

The inlet expansion pipe 142 is provided to extend from the inlet pipe 141 toward the first rotating part 110 and the second rotating part 120, and the first rotating part 110 and the second rotating part ( 120) may be provided to gradually expand the area as it approaches.

In this case, the length of the inlet extension tube 142 may be provided to correspond to the area of the inlet tube 141 . Preferably, the length of the inlet expansion pipe 142 may be provided to be the same as the area of the inlet pipe 141 . However, the length of the inlet expansion pipe 142 is not limited thereto.

The discharge unit 150 is provided at the outlet side of the first rotating unit 110 and the second rotating unit 120 , and includes a discharge pipe 151 and a discharge expansion pipe 152 .

The discharge pipe 151 may be provided on an outlet side of the first rotating unit 110 and the second rotating unit 120 to discharge the fluid from the first rotating unit 110 and the second rotating unit 120 . .

The discharge extension pipe 152 is provided to extend from the discharge pipe 151 toward the first rotating part 110 and the second rotating part 120 , and the first rotating part 110 and the second rotating part 120 . ) can be provided to gradually expand the area as it approaches

In this case, the length of the discharge extension pipe 152 may be provided to correspond to the area of the discharge pipe 151 . Preferably, the length of the discharge extension pipe 152 may be provided to be the same as the area of the discharge pipe 151 . However, the length of the discharge expansion pipe 152 is not limited thereto.

14 is a graph showing the inlet pressure pulsation over time with respect to the shape of the inlet side and the outlet side according to an embodiment of the present invention, and FIG. 15 is the shape of the inlet side and the outlet side according to an embodiment of the present invention. It is a graph showing the pressure pulsation at the outlet side with respect to time.

And, Figure 16 is a graph showing the flow rate pulsation with time for the shape of the inlet side and the outlet side according to an embodiment of the present invention, Figure 17 is the shape of the inlet side and the outlet side according to an embodiment of the present invention It is a graph showing the torque pulsation with time for

As shown in FIGS. 14 to 17 , it can be seen that the pressure pulsation during initial driving is greatly reduced by the shape of the inlet 140 and the outlet 150 according to the present invention prepared in this way.

Specifically, the present invention generally provides the inlet and outlet pressures, flow rates, and torques of the first and second rotating parts 110 and 120 compared to the prior art having an inlet pipe and an outlet pipe having constant diameter and area. It can be seen that the pulsation is greatly reduced.

The inlet unit 140 and the outlet unit 150 of the present invention thus prepared can reduce the occurrence of cavitation due to pressure pulsation during initial driving, and enable stable operation and more accurate flow rate measurement.

Referring back to FIG. 12 , the pressure measuring unit 130 may be provided to measure an inlet pressure and an outlet pressure of the pair of rotating units, and a first sensor 131 and a second sensor 132 . may include

The first sensor 131 may be provided on the inlet side of the pair of rotating parts to measure the pressure.

The second sensor 132 may be provided at the outlet side of the pair of rotating parts to measure the pressure.

The first sensor 131 and the second sensor 132 thus provided may be provided to continuously measure the pressure at the inlet side and the outlet side of the pair of rotating parts in real time to monitor the pressure pulsation.

The positive displacement water wheel 100 for reducing the pressure pulsation according to the present invention may be applied to a water turbine generator.

Specifically, the positive displacement water wheel 100 for reducing pressure pulsation according to the present invention may be installed in a heat transport pipe network of district heating in the form of a water turbine generator.

As such, the positive displacement water wheel 100 for reducing pressure pulsation installed in the heat transport pipe network is provided to produce electric power as the first rotor 112 and the second rotor 122 are rotated by high-pressure water. , the generated power may be provided to provide a pump that transports water at high pressure.

To this end, although not shown, the water turbine generator may further include an energy storage device (ESS), a system power source, a pump driving unit, and the like.

As such, the positive displacement water wheel 100 for reducing pressure pulsation of the present invention is applied to a water turbine generator, and unlike the differential pressure valve, which wastes energy by simply controlling the flow rate and water pressure, and lowering the high pressure water to the target water pressure, the above By generating electric power according to the rotation of the first rotor 112 and the second rotor, more economical operation than the related art is possible.

The above description of the present invention is for illustration, and those of ordinary skill in the art to which the present invention pertains can understand that it can be easily modified into other specific forms without changing the technical spirit or essential features of the present invention. will be. Therefore, it should be understood that the embodiments described above are illustrative in all respects and not restrictive. For example, each component described as a single type may be implemented in a dispersed form, and likewise components described as distributed may be implemented in a combined form.

The scope of the present invention is indicated by the following claims, and all changes or modifications derived from the meaning and scope of the claims and their equivalent concepts should be construed as being included in the scope of the present invention.

100: positive displacement aberration with predictable flow rate
110: first rotating part 111: first rotating shaft
112: first rotor 120: second rotation unit
121: second rotation shaft 122: second rotor
130: pressure measuring unit 131: first sensor
132: second sensor 140: inlet
141: inlet pipe 142: inlet expansion pipe
150: discharge unit 151: discharge pipe
152: discharge expansion pipe

Claims (14)

It includes a pair of rotating parts provided to rotate in engagement with each other,
The flow rate passing through the pair of rotating parts is a positive displacement aberration capable of predicting a flow rate, characterized in that it is calculated using a volumetric amount, a difference between the inlet pressure and the outlet pressure, the density of the fluid, and the rotation speed of the rotating part as variables.
The method of claim 1,
The flow rate is a volumetric aberration capable of predicting a flow rate, characterized in that calculated by the following equation.

(

is the flow rate,

is the volume [m ³ ], P is the difference between the inlet pressure and the outlet pressure [Pa], ρ is the density of the fluid [kg/m ³ ], N is the rotational speed of the rotor [rev/s])
3. The method of claim 2,
remind

is 0.00070838834m ³ Volumetric aberration capable of predicting flow rate.
3. The method of claim 2,
The density ρ of the fluid is

[kg/m ³ ],
Here, T is a volumetric aberration capable of predicting a flow rate, characterized in that it is a temperature in the condition of 3 barG [℃].
The method of claim 1,
The pair of rotating parts,
a first rotating part provided on one side of the inside of the pipe; and
A positive displacement water wheel for predicting a flow rate, characterized in that it is provided on the other side of the inner side of the pipe and includes a second rotating part provided to rotate in engagement with the first rotating part.
6. The method of claim 5,
The first rotation unit,
a first rotor forming a wing; and
and a first rotation shaft provided at the center of the first rotor to form an axis for rotation of the first rotor.
7. The method of claim 6,
The second rotation unit,
a second rotor that forms a blade and is provided to rotate in engagement with the first rotor; and
and a second rotation shaft provided at the center of the second rotor to form an axis for rotation of the second rotor.
8. The method of claim 7,
The positive displacement aberration capable of predicting a flow rate, characterized in that the first rotor and the second rotor are provided in a twisted state by a predetermined angle.
9. The method of claim 8,
The first rotor is provided with a plurality of lengths extending in the radial direction of the first rotation shaft,
The second rotor is a positive displacement aberration capable of predicting a flow rate, characterized in that provided with a plurality of length extending in the radial direction of the second rotation shaft.
10. The method of claim 9,
Each of the first rotor is twisted in width clockwise, and the second rotor is twisted in width counterclockwise.
The method of claim 1,
Volumetric aberration capable of predicting flow rate, characterized in that it further comprises a pressure measuring unit provided to measure the inlet pressure and the outlet pressure of the pair of rotating parts.
12. The method of claim 11,
The pressure measuring unit,
a first sensor provided on the inlet side of the pair of rotating parts to measure the pressure; and
and a second sensor provided on the outlet side of the pair of rotating parts to measure the pressure.
The method of claim 1,
an inlet provided on the inlet side of the rotating part; and
It includes a discharge part provided on the outlet side of the rotating part,
The volumetric aberration capable of predicting a flow rate, characterized in that the inlet part and the outlet part are provided such that an inner area of the inlet part is gradually expanded as it approaches the rotating part.
A water turbine generator to which the positive displacement aberration capable of predicting the flow rate according to claim 1 is applied.

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