CN216788675U - Operation monitoring system for steam-driven and electric feed pump - Google Patents
Operation monitoring system for steam-driven and electric feed pump Download PDFInfo
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- CN216788675U CN216788675U CN202220397849.7U CN202220397849U CN216788675U CN 216788675 U CN216788675 U CN 216788675U CN 202220397849 U CN202220397849 U CN 202220397849U CN 216788675 U CN216788675 U CN 216788675U
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Abstract
The utility model discloses a steam-driven and electric feed pump operation monitoring system, which comprises a feed pump, a preposed pump, a motor, a driving device, a feed water pipeline, a low beta value throat pressure-taking nozzle, a data storage system and the like.
Description
Technical Field
The utility model belongs to the technical field of energy conservation and consumption reduction of coal-fired units, and particularly relates to a steam-driven and electric feed pump operation monitoring system.
Background
For the thermal power generating units above 300MW at present, most of the thermal power generating units adopt an electric water feeding pump system, and for partial air cooling units, the electric water feeding pump is used. The electric water feed pump is the largest service user of the unit, so the operation characteristics of the electric water feed pump have important influence on the energy consumption level of the unit, and the related performances of the electric water feed pump and the hydraulic coupler need to be monitored.
For part of the units, a steam feed pump is adopted, and the feed pump is driven by a small steam turbine. When the unit needs to carry out wide load peak regulation, the running states of the steam-driven feed pump and the small steam turbine change greatly, especially, part of steam-driven feed pump unit systems with the preposed pumps and the steam-driven feed pumps not coaxial, the running of the preposed pumps deviates too far from the design working condition at low load, so that the preposed pumps are easy to break down, and therefore, the monitoring on the running states of the steam-driven feed pump and the small steam turbine is very necessary. Meanwhile, the thermal performance of the steam feed pump and the small turbine has important influence on the energy consumption level of the unit, the related performance of the steam feed pump and the small turbine needs to be monitored, and the thermal performance after overhaul is convenient to test.
When the related performance of the electric water supply pump or the steam-driven water supply pump and the hydraulic coupler is monitored, the shaft power of the water supply pump is difficult to determine, so that the efficiency of the water supply pump needs to be determined by an enthalpy rise method, and then the shaft power of the water supply pump is calculated, so that the efficiency of the driving device can be determined. In order to accurately obtain the efficiency of the feed pump by the enthalpy-rise method, it is necessary to obtain an accurate feed pump inlet and outlet feed water temperature. However, since the medium supplied to the water pump is at a high temperature and a high pressure, it is difficult to measure the flow rate of the medium by the ultrasonic flow meter.
SUMMERY OF THE UTILITY MODEL
The utility model aims to overcome the defects of the prior art and provide a steam-driven and electric feed pump operation monitoring system to realize online performance measurement of the operation characteristics of a feed pump and the whole life cycle performance recording and management of the feed pump, and meanwhile, a low beta value throat pressure-taking nozzle is adopted to measure the feed water flow to avoid errors caused by the flow measurement of a pore plate and accurately know the operation economy of a steam turbine in time.
In order to achieve the purpose, the utility model adopts the following technical scheme to realize the purpose:
a steam-driven and electric feed pump operation monitoring system comprises a deaerator, wherein two output pipelines of the deaerator are respectively connected to an A pre-pump and a B pre-pump, the output end of the A pre-pump is connected with an A feed pump, the output end of the B pre-pump is connected with a B feed pump, and the output pipelines of the A feed pump and the B feed pump are converged and then are jointly connected with a third high-pressure heater;
a low beta value throat pressure-taking flow nozzle at the inlet of the water supply pump A is arranged between the prepositive pump A and the water supply pump A; a low beta value throat pressure-taking flow nozzle at the inlet of the water feeding pump B is arranged between the prepositive pump B and the water feeding pump B.
The utility model is further improved in that:
preferably, an A feed pump inlet pressure gauge is arranged between the A preposed pump and the A feed pump inlet low-beta value throat pressure-taking flow nozzle; and a B feed pump inlet pressure gauge is arranged between the B pre-pump and the low beta value throat pressure taking flow nozzle with the B feed pump inlet.
Preferably, a platinum resistor for water temperature at the inlet of the water supply pump A is arranged between the preposed pump A and the low-beta-value throat pressure-taking flow nozzle at the inlet of the water supply pump A; and a platinum resistor for water temperature at the inlet of the water supply pump B is arranged between the preposed pump B and the low-beta-value throat pressure-taking flow nozzle at the inlet of the water supply pump B.
Preferably, the feed pump A is connected with a feed pump hydraulic coupler A, and the feed pump hydraulic coupler A is connected with a feed pump driving motor A;
the water feeding pump B is connected with a water feeding pump B hydraulic coupler; and the B feed pump hydraulic coupler is connected with a B feed pump driving motor.
Preferably, an A feed pump driving motor ammeter is arranged between the A feed pump hydraulic coupler and the A feed pump driving motor; and an ammeter of the B water-feeding pump driving motor is arranged between the B water-feeding pump hydraulic coupler and the B water-feeding pump driving motor.
Preferably, the feed pump A is connected with a small turbine A; the water feeding pump B is connected with a small steam turbine B.
Preferably, the steam inlet of the small turbine A is provided with a small turbine inlet pressure gauge A, a small turbine inlet temperature thermocouple A and a small turbine inlet flow orifice plate A; and a steam outlet of the small turbine A is provided with a small turbine exhaust pressure absolute pressure meter A.
Preferably, the steam inlet of the small steam turbine B is provided with a small steam turbine B inlet pressure gauge, a small steam turbine B inlet temperature thermocouple and a small steam turbine B inlet flow orifice plate; and a steam outlet of the small steam turbine B is provided with a small steam turbine B steam exhaust pressure absolute pressure meter.
Preferably, an output pressure gauge of the water supply pump A and a water temperature platinum resistor of the water supply pump outlet A are sequentially arranged on an output pipeline of the water supply pump A.
Preferably, an output pipeline of the water supply pump B is sequentially provided with a water supply pump outlet pressure gauge B and a water supply pump outlet water temperature platinum resistor B.
Compared with the prior art, the utility model has the following beneficial effects:
the utility model discloses a steam-driven and electric feed pump operation monitoring system, which comprises a feed pump, a preposed pump, a driving device, a feed pipe, a low beta value throat pressure-taking nozzle, a data storage system and the like, wherein the system can obtain real-time feed pump operation characteristics by arranging different measuring devices at different positions of the whole system, thereby realizing the performance management of the feed pump in the whole life cycle, timely proposing the suggestion of maintenance or modification, ensuring that the feed pump operates in a high-efficiency interval and reducing the power consumption of the feed pump; the water supply flow is measured by the low-beta-value throat pressure-taking nozzle, the accurate variation of the water supply flow is monitored, errors caused by the measurement of the flow by the orifice plate are avoided, and the performance change of the steam turbine is effectively monitored.
Furthermore, the feed water flow entering the economizer is directly measured through the low beta value throat pressure-taking nozzle, so that the possible leakage of the heater tube bundle and the influence of the seal water of the feed water pump and the water level change of the deaerator on the determination of the final feed water flow can be avoided.
Furthermore, double measuring points are adopted, errors are effectively reduced, and a high-precision A-grade platinum resistor is used. Signals such as a water supply flow differential pressure, a water supply pump water inlet and outlet temperature value, a water supply pump water inlet and outlet pressure value, a preposed pump water inlet and outlet pressure value, a water supply pump driving motor current and the like measured by the low-beta-value throat pressure-taking nozzle are all connected into the SIS system, then the water supply pump efficiency is obtained through calculation, the online management of the water supply pump performance is realized, and the operation states of the water supply pump and the hydraulic coupler are mastered in the whole life cycle.
Furthermore, the transmission efficiency of the hydraulic coupler near the design power is high, but when the hydraulic coupler deviates far from the design working condition, the efficiency is reduced very quickly, the transmission efficiency of the hydraulic coupler needs to be monitored in real time through an online monitoring system, effective control measures are convenient to take, and the purpose of improving the efficiency of the hydraulic coupler is achieved.
Drawings
FIG. 1 is a block diagram of an electric drive system according to an embodiment of the present invention;
FIG. 2 is a diagram of a pneumatic drive system according to a second embodiment of the present invention;
FIG. 3 is a graph relating flow rate and efficiency of the electrically driven feed water pump of the present invention;
FIG. 4 is a graph showing the relationship between the flow rate and the lift of the electrically driven feed water pump according to the present invention;
FIG. 5 is a graph of electric drive feed pump flow and shaft power in accordance with the present invention;
fig. 6 is a graph relating the speed ratio and the efficiency of the fluid coupling according to the present invention.
FIG. 7 is a graph relating flow rate and efficiency of a steam driven feed water pump according to the present invention;
FIG. 8 is a graph showing the relationship between the flow rate and the head of a steam driven feed water pump according to the present invention;
FIG. 9 is a correlation plot of shaft power versus flow rate for a steam driven feed water pump of the present invention.
Wherein: 1-a deaerator; 2-A pre-pump; 3-A water supply pump inlet pressure gauge; 4-A water temperature platinum resistor at the inlet of the water supply pump; a low beta value throat pressure-taking flow nozzle at the inlet of the 5-A water supply pump; 6-A water supply pump driving motor ammeter; 7-A water supply pump driving motor; 8-A feed pump fluid coupling; 9-A feed pump; 10-A water supply pump outlet pressure gauge; 11-A water supply pump outlet water temperature platinum resistor; 12-B pre-pump; 13-B water supply pump inlet pressure gauge; 14-B water temperature platinum resistor at the inlet of the feed pump; 15-B water supply pump inlet low beta value throat pressure taking flow nozzle; the 16-A water supply pump drives a motor ammeter; 17-B water supply pump driving motor; a water pump fluid coupling of 18-B; 19-B feed water pump; 20-B water supply pump outlet pressure gauge; 21-B water supply pump outlet water temperature platinum resistor; 22-a third high pressure heater; 23-A pre-pump inlet stop valve; 24-A small turbine inlet pressure gauge; 25-A small turbine inlet temperature thermocouple; 26-A small steam turbine inlet flow orifice plate; 27-A small steam turbine exhaust pressure absolute pressure meter; 28-B pre-pump inlet stop valve; 29-B small turbine inlet pressure gauge; 30-B small turbine inlet temperature thermocouple; 31-B small turbine inlet flow orifice plate; and the 32-B small turbine exhaust pressure absolute pressure meter.
Detailed Description
The utility model is described in further detail below with reference to the accompanying drawings:
in the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention; the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance; furthermore, unless expressly stated or limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly and encompass, for example, both fixed and removable connections; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
The utility model aims to provide a real-time monitoring system for the running characteristics of a water feed pump and a hydraulic coupler, so that the on-line performance measurement of the running characteristics of the water feed pump is realized, the whole life cycle performance recording and management of the water feed pump are realized, meanwhile, a low beta value throat pressure-taking nozzle is adopted to measure the water feed flow, the error caused by the flow measurement of a pore plate is avoided, and the running economy of a steam turbine is known timely and accurately.
Referring to fig. 1, a deaerator 1 is provided with two output ends, which are respectively connected with a pre-pump a 2 and a pre-pump B12; the output end of the A pre-pump 2 is connected with the input end of the A feed pump 9; the output end of the B pre-pump 12 is connected with the input end of the B water feeding pump 19, and the output end of the B water feeding pump 19 and the output end of the A water feeding pump 9 are gathered and then are connected with a third high-pressure heater 22 together.
Further, the water feed pump of the present invention is driven by electric or pneumatic means.
Example 1
The feed pump is driven by an electric motor.
Along the direction of water flow, an A water supply pump inlet pressure gauge 3, an A water supply pump inlet water temperature platinum resistor 4 and an A water supply pump inlet low beta value throat pressure taking flow nozzle 5 are sequentially arranged between an A prepositive pump 2 and an A water supply pump 9, a power input shaft of the A water supply pump 9 is connected with an A water supply pump hydraulic coupler 8, the A water supply pump hydraulic coupler 8 is connected with an A water supply pump driving motor 7, and an A water supply pump driving motor ammeter 6 is arranged between the A water supply pump hydraulic coupler 8 and the A water supply pump driving motor 7; before the A feed water pump 9 is merged with the B feed water pump 19, a feed water pump outlet pressure gauge A10 and an A feed water pump outlet water temperature platinum resistor 11 are arranged on an output pipeline of the A feed water pump 9.
Along the direction of water flow, a B water supply pump inlet pressure gauge 13, a B water supply pump inlet water temperature platinum resistor 14 and a B water supply pump inlet low beta value throat pressure taking flow nozzle 15 are sequentially arranged between a B preposed pump 12 and a B water supply pump 19, a power input shaft of the B water supply pump 19 is connected with a B water supply pump hydraulic coupler 18, the B water supply pump hydraulic coupler 18 is connected with a B water supply pump driving motor 17, and a B water supply pump driving motor ammeter 16 is arranged between the B water supply pump hydraulic coupler 18 and the B water supply pump driving motor 17; before the water feeding pump 19B is merged with the water feeding pump 9A, a water feeding pump outlet pressure gauge B and a water feeding pump outlet water temperature platinum resistor 21B are arranged on an output pipeline of the water feeding pump 19.
The working process of the device is as follows:
the feed water is deoxidized and heated in the deaerator 1, the water which is output from the deaerator 1 and is deoxidized and heated enters the feed water pump after being pressurized by two preposed pumps, and finally converges to the feed water main pipe and enters the No. 3 high-pressure heater 22 after being further pressurized in the two feed water pumps. A feed pump driving motor 7 drives A feed pump 9 to work, B feed pump driving motor 17 drives B feed pump 19 to work, and A feed pump fluid coupling 8 and B feed pump fluid coupling 18 are used for variable speed adjustment, the current of the motor is measured through A feed pump driving motor ammeter 6 and B feed pump driving motor ammeter 16, then the power consumption of the feed pump is calculated, then feed pump outlet pressure gauge 10 and B feed pump outlet pressure gauge 20 of the A feed pump 9 and B feed pump 19 are used for measuring the feed outlet pressure of the A feed pump 9 and B feed pump 19, and outlet water temperature of the A feed pump 9 and B feed pump 19 is measured through A feed pump outlet water temperature platinum resistor 11 and B feed pump outlet water temperature platinum resistor 21.
The feed water is deoxidized and heated in the deaerator 1 and respectively enters the A preposed pump 2 and the B preposed pump 12, the inlet pressure of the A feed pump 9 is measured by the A feed pump inlet pressure gauge 3, and the inlet pressure of the B feed pump 19 is measured by the B feed pump inlet pressure gauge 13; the water temperature of the inlet of the water feeding pump 9A is measured through the water temperature platinum resistor 4 of the water feeding pump A, and the water temperature of the inlet of the water feeding pump 19B is measured through the water temperature platinum resistor 14 of the water feeding pump B; the water supply flow of the water supply pump A9 is measured through the low beta value throat pressure taking flow nozzle 5 at the inlet of the water supply pump A, the water supply flow of the water supply pump B19 is measured through the low beta value throat pressure taking flow nozzle 15 at the inlet of the water supply pump B, and accurate measurement of inlet parameters of the water supply pump is achieved.
After the feed water is pressurized in the two preposed pumps respectively, the feed water enters the feed water pump A9 and the feed water pump B19 respectively, the feed water pump A9 drives a motor to drive the feed water pump to work by using the feed water pump A driving motor 7, the feed water pump A hydraulic coupler 8 is used for carrying out variable speed regulation, the current of the feed water pump A9 is measured by the feed water pump A driving motor ammeter 6 in the process, and the power consumption of the feed water pump A9 is further calculated. The water supply outlet pressure of the A water supply pump 9 is calculated through an A water supply pump outlet pressure gauge 10, and the outlet water temperature of the A water supply pump 9 is measured through an A water supply pump outlet water temperature platinum resistor 11. The B-feed water pump 12 is driven by a B-feed water pump driving motor 17 and is subjected to variable speed regulation by using a B-feed water pump fluid coupling 18, and in the process, the current of the B-feed water pump 19 is measured by a B-feed water pump driving motor ammeter 16, and the power consumption of the B-feed water pump 19 is further calculated. The water supply outlet pressure of the water supply pump B19 is calculated through a water supply pump outlet pressure gauge 20 of the water supply pump B, and the outlet water temperature of the water supply pump B19 is measured through a water supply pump outlet water temperature platinum resistor 21 of the water supply pump B.
Example 2
The feed pump is driven by steam.
Along the direction of water flow, an A water supply pump inlet pressure gauge 3, an A water supply pump inlet water temperature platinum resistor 4 and an A water supply pump inlet low beta value throat pressure taking flow nozzle 5 are sequentially arranged between an A front-mounted pump 2 and an A water supply pump 9, the A water supply pump 9 is connected with a power output shaft of a small turbine A through a power input shaft, a small turbine A inlet pressure gauge 24, a small turbine A inlet temperature thermocouple 25 and a small turbine A inlet flow pore plate 26 are arranged at a steam inlet of the small turbine A, and a small turbine A exhaust pressure absolute pressure gauge 27 is arranged at a steam outlet of the small turbine A; before the A feed pump 9 is merged with the B feed pump 19, a feed pump outlet pressure gauge A10 and an A feed pump outlet water temperature platinum resistor 11 are arranged on an output pipeline of the A feed pump 9.
Along the direction of water flow, a B water supply pump inlet pressure gauge 13, a B water supply pump inlet water temperature platinum resistor 14 and a B water supply pump inlet low beta value throat pressure taking flow nozzle 15 are sequentially arranged between a B front pump 12 and a B water supply pump 19, the B water supply pump is connected with a power output shaft of a B small turbine through a power input shaft, a B small turbine inlet pressure gauge 29, a B small turbine inlet temperature thermocouple 30 and a B small turbine inlet flow orifice plate 31 are arranged at a steam inlet of the B small turbine, and a B small turbine exhaust pressure absolute pressure gauge 32 is arranged at a steam outlet of the B small turbine; before the water feeding pump 19B is merged with the water feeding pump 9A, a water feeding pump outlet pressure gauge B and a water feeding pump outlet water temperature platinum resistor 21B are arranged on an output pipeline of the water feeding pump 19.
The working process of the device is as follows:
the water supply is deoxidized and heated in the deaerator 1, the water which is output from the deaerator 1 and is deoxidized and heated enters the water supply pump after being pressurized by the two preposed pumps, and finally converges in the water supply main pipe and enters the No. 3 high-pressure heater 22 after being further pressurized in the two water supply pumps. The A small turbine drives the A water feeding pump 9 to work, the inlet pressure of the A small turbine is measured through an A small turbine inlet pressure gauge 24, the A small turbine inlet temperature thermocouple 25 measures the inlet steam temperature of the A small turbine, an A small turbine inlet flow pore plate 26 measures the inlet steam flow of the A small turbine, and an A small turbine exhaust pressure insulation gauge 27 measures the exhaust pressure of the A small turbine to achieve thermodynamic calculation of the small turbine. And then the water supply outlet pressure of the A water supply pump 9 and the B water supply pump 19 is measured through an A water supply pump outlet pressure gauge 10 and a B water supply pump outlet pressure gauge 20, and the outlet water temperature of the A water supply pump 9 and the B water supply pump outlet water temperature platinum resistor 21 is measured through an A water supply pump outlet water temperature platinum resistor 11 and a B water supply pump outlet water temperature platinum resistor 21.
The small turbine B drives the water feeding pump B19 to work, the inlet pressure of the small turbine B is measured through a small turbine B inlet pressure gauge 29, the inlet temperature thermocouple 30 of the small turbine B measures the inlet steam temperature of the small turbine B, the small turbine B inlet flow pore plate 31 measures the inlet steam flow of the small turbine B, and the small turbine B exhaust pressure insulation gauge 32 measures the exhaust pressure of the small turbine B to achieve thermodynamic calculation of the small turbine.
After the feed water is pressurized in the pre-pump, the feed water enters a steam-driven A feed water pump 9 and a steam-driven B feed water pump 19, the feed water outlet pressure of the A feed water pump 9 and the feed water outlet pressure of the B feed water pump 19 are measured through an A feed water pump outlet pressure gauge 10 and a B feed water pump outlet pressure gauge 20, the outlet water temperature of the A feed water pump 9 and the outlet water temperature of the B feed water pump 19 are measured through an A feed water pump outlet water temperature platinum resistor 11 and a B feed water pump outlet water temperature platinum resistor 21, and after the feed water is further pressurized in the steam-driven feed water pump, the feed water is converged to a feed water main pipe to enter a No. 3 high-pressure heater 22.
The feed water is deoxidized and heated in the deaerator 1 and respectively enters the A preposed pump 2 and the B preposed pump 12, the inlet pressure of the A feed pump 9 is measured by the A feed pump inlet pressure gauge 3, and the inlet pressure of the B feed pump 19 is measured by the B feed pump inlet pressure gauge 13; the water temperature of the inlet of the water feeding pump 9A is measured through the water temperature platinum resistor 4 of the water feeding pump A, and the water temperature of the inlet of the water feeding pump 19B is measured through the water temperature platinum resistor 14 of the water feeding pump B; the water supply flow of the water supply pump A9 is measured through the low beta value throat pressure taking flow nozzle 5 at the inlet of the water supply pump A, the water supply flow of the water supply pump B19 is measured through the low beta value throat pressure taking flow nozzle 15 at the inlet of the water supply pump B, and accurate measurement of inlet parameters of the water supply pump is achieved.
By adopting the on-line measuring system for the thermal performance of the steam-driven water-feeding pump and the small turbine, the real-time thermal performance of the steam-driven water-feeding pump and the small turbine can be obtained, the performance management of the steam-driven water-feeding pump and the small turbine in the whole life cycle is realized, the suggestion of maintenance or modification is put forward in time, the steam-driven water-feeding pump and the small turbine are ensured to be operated in an efficient interval, and the power consumption of the water-feeding pump is reduced; meanwhile, the low-beta-value throat pressure-taking nozzle is adopted to measure the water supply flow, so that errors caused by the flow measured by the orifice plate are avoided, and the performance change of the steam turbine is effectively monitored.
The process of calculating the relevant data by using the measuring table comprises the following steps:
the data obtained on line is completely entered into a DCS database through a distribution acquisition system, and then is accessed into an SIS system, and the following formula is utilized.
Head of feed pump
In the formula: h- -head, m;
p2- -outlet pressure, Pa;
p1- -inlet pressure, Pa;
rho-average density of inlet and outlet water, kg/m 3;
g- -gravitational acceleration, 9.806m/s 2;
z 2-outlet measuring cross-sectional elevation, m;
z 1-inlet measurement cross-sectional elevation, m;
v2- -outlet pipe flow velocity, m/s;
v1- -inlet line flow velocity, m/s.
Efficiency of feed pump
In the formula: ν m-average inlet and outlet specific volumes m 3/kg;
h2- -outlet water enthalpy, kJ/kg;
h1- -inlet water enthalpy, kJ/kg;
balancing device and shaft seal leakage flow loss, pump body heat dissipation loss energy.
-energy lost per unit mass of the fluid machine.
Shaft power of feed pump
In the formula: h- -head, m;
rho- - - -average density of inlet and outlet, kg/m 3;
q- -outlet flow, m 3/s.
Efficiency of small steam turbine
In the formula: etatEfficiency,%;
g- -inflow in kg/s;
h1-enthalpy of admission, kJ/kg;
hs-ideal exhaust enthalpy, kJ/kg;
conversion of feed pump performance
And converting the performance parameters at the actually measured rotating speed of the pump to the performance parameters at the rated rotating speed according to the following formula.
In the formula: q0-flow at rated speed;
h0-head at rated speed;
pa0- -shaft power at nominal speed;
n0- -nominal speed;
n- -test rotational speed.
For example 1, the pump efficiency and the following performance operating curves were calculated for the electric drive feed water pump in the SIS system as shown in fig. 3, 4, 5 and 6 below. The pump efficiency can be seen from the flow-efficiency graph of the water supply pump in fig. 3, the matching degree of the pump head and the flow is represented by the flow-head graph of the water supply pump in fig. 4, the power consumption and the output condition of the pump under different flow are represented by the flow-shaft power graph of the water supply pump in fig. 5, and the transmission efficiency of the hydraulic coupler is rapidly reduced along with the reduction of the speed ratio by the efficiency graph of the hydraulic coupler in fig. 6 under different speed ratios.
For example 2, the pump-cycling efficiency and the following performance operating curves were calculated in the SIS system for the steam-driven feedwater pump, as shown in fig. 7-8 below. The efficiency of the feed pump can be seen from the curve of the flow rate and the efficiency of the feed pump in fig. 7, the matching degree of the pump head and the flow rate is represented by the flow rate-head curve chart of the feed pump in fig. 8, and the power consumption and the treatment condition of the pump under different flow rates can be seen from fig. 9.
All signals of the measured values are transmitted to an electronic room through a communication cable, all enter a DCS database through a distribution acquisition system, then are accessed to an SIS system, and are calculated and analyzed in the SIS system, so that real-time online monitoring is realized.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the utility model, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (10)
1. The operation monitoring system of the steam-driven and electric water-feeding pump is characterized by comprising a deaerator (1), wherein two output pipelines of the deaerator (1) are respectively connected to an A pre-pump (2) and a B pre-pump (12), the output end of the A pre-pump (2) is connected with an A water-feeding pump (9), the output end of the B pre-pump (12) is connected with a B water-feeding pump (19), and a third high-pressure heater (22) is jointly connected after the output pipelines of the A water-feeding pump (9) and the B water-feeding pump (19) are converged;
a low beta value throat pressure-taking flow nozzle (5) at the inlet of the A water supply pump is arranged between the A prepositive pump (2) and the A water supply pump (9); a low beta value throat pressure-taking flow nozzle (15) at the inlet of the feed water pump B is arranged between the preposed pump B (12) and the feed water pump B (19).
2. The system for monitoring the operation of the steam-driven and electric feed water pump as claimed in claim 1, characterized in that an A feed water pump inlet pressure gauge (3) is arranged between the A pre-pump (2) and the A feed water pump inlet low beta value throat pressure-taking flow nozzle (5); and a B feed pump inlet pressure gauge (13) is arranged between the B pre-pump (12) and the low beta value throat pressure-taking flow nozzle (15) with the B feed pump inlet.
3. The system for monitoring the operation of the steam-driven and electric feed water pump as claimed in claim 1, characterized in that a platinum resistor (4) for the inlet water temperature of the A feed water pump is arranged between the A pre-pump (2) and the low beta value throat pressure-taking flow nozzle (5) of the inlet of the A feed water pump; and a platinum resistor (14) for water temperature at the inlet of the water supply pump B is arranged between the prepositive pump B (12) and the low beta value throat pressure-taking flow nozzle (15) at the inlet of the water supply pump B.
4. The system for monitoring the operation of the steam-driven and electric feed water pumps as claimed in claim 1, characterized in that an A feed water pump fluid coupling (8) is connected to the A feed water pump (9), and an A feed water pump drive motor (7) is connected to the A feed water pump fluid coupling (8);
the water feeding pump B (19) is connected with a water feeding pump B hydraulic coupler (18); and the B feed pump hydraulic coupler (18) is connected with a B feed pump driving motor (17).
5. The system for monitoring the operation of the steam-driven and electric feed-water pump as recited in claim 4, characterized in that an A feed-water pump drive motor ammeter (6) is arranged between the A feed-water pump fluid coupling (8) and the A feed-water pump drive motor (7); and a B feed water pump driving motor ammeter (16) is arranged between the B feed water pump hydraulic coupler (18) and the B feed water pump driving motor (17).
6. The system for monitoring the operation of the steam-driven and electric feed water pump as claimed in claim 1, characterized in that the A feed water pump (9) is connected with an A small steam turbine; the water feeding pump (19) B is connected with a small turbine B.
7. The system for monitoring the operation of the steam-driven and electric feed water pump according to claim 6, characterized in that a steam inlet of the small turbine A is provided with a small turbine inlet pressure gauge (24), a small turbine inlet temperature thermocouple (25) and a small turbine inlet flow orifice plate (26); and a steam outlet of the small turbine A is provided with a small turbine A steam exhaust pressure absolute pressure meter (28).
8. The system for monitoring the operation of the steam-driven and electric feed water pump according to claim 6, characterized in that a steam inlet of the small steam turbine B is provided with a small steam turbine B inlet pressure gauge (29), a small steam turbine B inlet temperature thermocouple (30) and a small steam turbine B inlet flow orifice plate (31); and a steam outlet of the small turbine B is provided with a small turbine B steam exhaust pressure absolute pressure meter (32).
9. The steam-driven and electric feed-water pump operation monitoring system according to claim 1, wherein an output pipeline of the feed-water pump A (9) is provided with a feed-water pump outlet pressure gauge A (10) and a feed-water pump outlet water temperature platinum resistor A (11) in sequence.
10. The steam-driven and electric feed water pump operation monitoring system according to any one of claims 1 to 9, characterized in that an output pipeline of the B feed water pump (19) is provided with a B feed water pump outlet pressure gauge (20) and a B feed water pump outlet water temperature platinum resistor (21) in sequence.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220397849.7U CN216788675U (en) | 2022-02-25 | 2022-02-25 | Operation monitoring system for steam-driven and electric feed pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220397849.7U CN216788675U (en) | 2022-02-25 | 2022-02-25 | Operation monitoring system for steam-driven and electric feed pump |
Publications (1)
| Publication Number | Publication Date |
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