CN120042542A - Real-time metering and dynamic regulating and controlling device and method for wet steam - Google Patents

Real-time metering and dynamic regulating and controlling device and method for wet steam Download PDF

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CN120042542A
CN120042542A CN202311581242.XA CN202311581242A CN120042542A CN 120042542 A CN120042542 A CN 120042542A CN 202311581242 A CN202311581242 A CN 202311581242A CN 120042542 A CN120042542 A CN 120042542A
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pressure
flow
wet steam
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radial
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戴宇婷
邹斌
刘廷峰
刘明
盖平原
姜泽菊
李友平
韩艳慧
张紫军
蔡文斌
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China Petroleum and Chemical Corp
Sinopec Shengli Oilfield Co
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Sinopec Shengli Oilfield Co
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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
    • E21B43/16—Enhanced recovery methods for obtaining hydrocarbons
    • E21B43/24—Enhanced recovery methods for obtaining hydrocarbons using heat, e.g. steam injection
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B47/00—Survey of boreholes or wells
    • G—PHYSICS
    • G06—COMPUTING OR CALCULATING; COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B2200/00—Special features related to earth drilling for obtaining oil, gas or water
    • E21B2200/20—Computer models or simulations, e.g. for reservoirs under production, drill bits

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Abstract

The invention provides a device and a method for real-time metering and dynamic regulation of wet steam, wherein the device comprises a venturi nozzle, a swirl vane, a radial central pressure guiding pipe, a radial pipe wall pressure guiding pipe, an upstream axial pressure guiding pipe and a downstream axial pressure guiding pipe, the wet steam enters a flow passage from the left incoming flow direction of the venturi nozzle, the swirl vane carries out swirl shaping on the wet steam flowing out of the venturi nozzle to separate a gas-liquid two-phase fluid phase from a phase, the radial central pressure guiding pipe measures the pressure of a radial central point in a pipe, the radial pipe wall pressure guiding pipe measures the pressure on the inner wall of the pipe, the upstream axial pressure guiding pipe measures the axial incoming flow pressure of the pipe, and the downstream axial pressure guiding pipe measures the pressure after the axial shaping of the pipe. The device and the method for measuring and dynamically regulating the wet steam in real time adopt a specially designed rotational flow double differential pressure type wet saturated steam flow, dryness, temperature and pressure four-parameter on-line monitoring device to evaluate and analyze the dynamic regulating effect.

Description

Real-time metering and dynamic regulating and controlling device and method for wet steam
Technical Field
The invention relates to the technical field of thick oil thermal recovery steam flow monitoring and control, in particular to a device and a method for real-time metering and dynamic regulation and control of wet steam.
Background
Thick oil is an unconventional crude oil with viscosity as high as tens of thousands to millions of centipoise at the temperature of oil layer, and is difficult to flow, and thick oil is difficult to be extracted by conventional oil extraction means. In the heavy oil thermal recovery engineering, along with the conversion from the production mode of steam huff and puff to the production modes of steam flooding, steam Assisted Gravity Drainage (SAGD) and the like in the heavy oil thermal recovery, the accurate steam injection of a well group is realized, and the reduction of the deviation between the actual injection level and the injection allocation level is an important guarantee for ensuring the improvement of the oil reservoir recovery ratio of the steam flooding. The steam huff and puff and steam flooding development are the main modes of the current thickened oil development, the ground steam delivery and distribution work of thermal recovery is finished, the ground steam distribution level is improved, the heat energy effective utilization rate can be effectively improved, and the steam injection cost is saved. The technology realizes reasonable and efficient regulation and control and monitoring of ground steam, on one hand, steam is injected into a required oil well and interval according to the scheme design requirement, the development effect of a heavy oil reservoir is improved, the overall utilization degree of a block is effectively improved, thereby achieving the aim of improving the recovery ratio, on the other hand, the consumption of raw materials such as required coal, heavy oil and the like is reduced, the pollution degree to the environment is reduced, and the national requirement on environmental protection is met.
However, due to the difference of steam absorption capacity among development layers, the historic inheritance of a steam channeling channel, the influence of multiple factors such as one furnace injection and multiple wells, the accurate injection of the superheated steam flooding well group is seriously restricted. Accurate real-time metering and automatic regulation of steam are key points for solving the problem.
At present, steam injected into an oil field basically belongs to a saturated wet steam state, and the measurement and control of the flow and dryness of the steam belongs to the technical field of multiphase flow, wherein the measurement of the phase fraction (dryness) and the measurement of the total flow are two important measurement links of the steam flow. Therefore, the actual production problem can be better solved only by realizing online measurement of double parameters (dryness and flow) of steam.
By searching published technical reports, academic papers, patent and other documents, the following findings are obtained:
In the traditional monitoring method for acquiring multiphase flow parameters in an oil field, a three-phase separator is generally adopted to separate oil, gas and water, or a two-phase separator is adopted to separate gas and liquid phases, and the phases are separated for metering. The 201720697433.6 single-well multiphase flow metering device comprises a gas-liquid separation tank, a gas-phase pipeline and a liquid-phase pipeline, wherein an inlet of the gas-liquid separation tank is connected with an oil well wellhead, a gas-phase outlet is arranged at the upper end of the gas-liquid separation tank, a liquid-phase outlet is arranged at the lower end of the gas-liquid separation tank, a collision plate is arranged at the inlet of the gas-liquid separation tank and used for carrying out collision separation on a gas-liquid mixture, gas enters a mixing pipeline through the gas-phase pipeline, liquid enters the mixing pipeline through the liquid-phase pipeline, a pump on the liquid-phase pipeline can form low pressure in the gas-liquid separation tank, gas-liquid separation is facilitated, a water-containing analyzer and a mass flowmeter are sequentially arranged between the liquid-phase outlet and the pump, the water-containing analyzer is used for monitoring the water content, the mass flowmeter can measure the flow and the density of mixed liquid, and the flow of each phase in the mixed liquid is calculated according to the densities of thick oil and thin oil, and the collision separation method and the low-pressure separation method are combined, so that the gas-liquid separation is more thorough, and the measurement result is more accurate. The separation equipment has the defects of complex device, wide occupied area, high cost, long time separation of oil, gas and water mixtures, long time consumption, high hysteresis and the like, and can not realize continuous single well measurement.
At present, the existing method for monitoring the flow parameters of multiphase flow without separation mostly adopts a combination method of a flowmeter and a water content sensor, for example 201320859265.8 is an integrated device for online measurement of the respective flow rates of oil, water and gas in multiphase flow, but the device adopts a combination method of a venturi flowmeter and a gamma ray phase resolution meter, the flow rate is measured by using a venturi tube, and the phase content of each phase is obtained by using gamma rays, but the method is not suitable for healthy development of industry due to the fact that the method is applied to radioactive rays and has great environmental pollution.
In order to avoid environmental pollution, 202110668722.4 provides a multiphase flow fluid measurement system, which adopts a method of combining a venturi tube and a microwave sensor, and monitors the flow of wet vapor and liquid phases by acquiring a venturi pressure difference signal and a microwave amplitude value and a phase signal. And furthermore, quick, stable and reliable metering monitoring results can be provided for oil and gas wells under different working conditions, but a large number of water content parameters are needed to be fitted in the method.
Patent 201210419330.5 solves the problems of lower metering precision, poorer accuracy, large structural volume and the like existing in the actual use of the traditional device for measuring the parameters such as pressure, flow, dryness and the like of the wet saturated steam for the steam injection of the oil field, but can not timely adjust the flow of the wet steam.
The multiphase flow monitoring method has the common defects that part of the multiphase flow monitoring method cannot have good reliability and long-term stability under extreme working conditions such as high temperature, high pressure, corrosion, strong electromagnetic interference and the like, and the wet steam flow cannot be timely adjusted although the wet steam flow is monitored.
The prior art is greatly different from the invention, and the technical problem to be solved by the invention is not solved, so that the invention discloses a novel device and a method for measuring and dynamically regulating wet steam in real time.
Disclosure of Invention
The invention aims to provide a device and a method for real-time metering and dynamic regulation of wet steam, which can realize online and non-separation monitoring and control of steam flow of a single well, thereby ensuring accurate steam injection of a well group.
The wet steam real-time metering and dynamic regulating device comprises a Venturi nozzle, a swirl vane, a radial center pressure guiding pipe, a radial pipe wall pressure guiding pipe, an upstream axial pressure guiding pipe and a downstream axial pressure guiding pipe, wherein the Venturi nozzle is an adjustable steam critical flow Venturi nozzle, wet steam enters a flow passage from the left inflow direction of the Venturi nozzle, the right side of the Venturi nozzle is an outlet direction, the swirl vane is positioned on the right side of the Venturi nozzle, the wet steam flowing out of the Venturi nozzle is subjected to swirl shaping, a gas-liquid two-phase fluid phase is isolated from a phase, the radial center pressure guiding pipe measures the pressure of a radial center point in a pipeline, the radial pipe wall pressure guiding pipe measures the pressure on the inner wall of the pipeline, the upstream axial pressure guiding pipe measures the axial inflow pressure of the pipeline, and the downstream axial pressure guiding pipe measures the pressure after the pipeline is axially shaped.
The aim of the invention can be achieved by the following technical measures:
The device for measuring and dynamically regulating and controlling the wet steam in real time further comprises a radial differential pressure flowmeter, wherein the radial differential pressure flowmeter is connected with the radial center pressure guiding pipe and the radial pipe wall pressure guiding pipe, and the radial throttling pressure difference delta P r in the pipeline is calculated according to data transmitted by the radial center pressure guiding pipe and the radial pipe wall pressure guiding pipe.
The wet steam real-time metering and dynamic regulating device further comprises an axial differential pressure flowmeter, wherein the axial differential pressure flowmeter is connected with the upstream axial pressure guiding pipe and the downstream axial pressure guiding pipe, and the axial throttling pressure difference delta P z in the pipeline is calculated according to data transmitted by the upstream axial pressure guiding pipe and the downstream axial pressure guiding pipe.
The real-time wet steam metering and dynamic regulating device further comprises a pressure gauge and a flowmeter, wherein the pressure gauge is positioned at the inlet of the venturi nozzle, the inlet pressure P 1 of the venturi nozzle is measured by the pressure gauge, the flowmeter is positioned at the inlet of the venturi nozzle, and the inlet flow of the venturi nozzle is measured by the flowmeter.
The venturi nozzle comprises a venturi nozzle flow channel, an adjusting hand wheel, an adjusting cone, an adjusting rod, a control motor and a PLC control module, wherein the adjusting cone is coaxial with the venturi nozzle flow channel and is arranged in the venturi nozzle, the control motor is connected with the PLC control module and the adjusting hand wheel, when the flow is required to be adjusted, the PLC control module sends out an instruction and transmits the instruction to the control motor, the control motor drives the adjusting hand wheel to rotate, the adjusting hand wheel is connected with the adjusting rod, the adjusting rod is fixedly connected with the adjusting cone in a coaxial manner and is positioned at the upstream of the adjusting cone, and the adjusting cone moves back and forth in the axial direction under the driving of the adjusting rod through the adjusting hand wheel, so that an automatic adjustable steam critical flow venturi flow channel is formed.
When the cyclone blade performs cyclone shaping of wet steam, the wet steam is separated into uniform annular flow with gas phase inside and liquid phase outside by using density differential pressure of gas and liquid at a certain speed, and uniform annular flow mainly comprising gas phase and uniformly distributed on the wall surface of a pipeline in the form of a liquid film is formed in the center of the pipeline.
The swirl vanes consist of 4-6 swirl vanes with the inclination angle of 45-135 degrees, are arranged in a pipeline, and are optimally designed according to actual engineering requirements.
The aim of the invention can also be achieved by the following technical measures that the method for measuring and dynamically regulating the wet steam in real time adopts a device for measuring and dynamically regulating the wet steam in real time, which comprises the following steps:
Step 1, the venturi nozzle regulates the flow of the wet steam flowing through in a critical flow state;
Step 2, separating the gas-liquid two-phase fluid phase from the phase by the cyclone blade;
step 3, calculating the radial throttling pressure difference delta P r in the pipeline;
step 4, calculating an axial throttling pressure difference delta P z in the pipeline;
and 5, establishing a wet steam double-parameter measurement model to realize double-parameter measurement of wet steam flow and dryness.
The aim of the invention can be achieved by the following technical measures:
In step 1, establishing a critical flow theoretical regulation model of an adjustable critical flow nozzle:
Wherein:
w-wet steam flow, t/h, d-throat diameter of venturi nozzle, mm;
d 0 -diameter of guide rod, mm, L-displacement of adjusting cone, mm, alpha-cone angle of adjusting cone;
P 1 -inlet pressure of critical flow nozzle, MPa, length of throat of H-Venturi nozzle;
ρ -fluid density, kg/m 3;
Through the established critical flow theoretical regulation model of the adjustable critical flow nozzle, the displacement of the regulating cone can be converted, and the calculated displacement of the regulating cone is regulated through the regulating hand wheel, so that the flow is controlled and regulated.
In step 3, the radial center pressure guiding pipe measures the pressure of the radial center point in the pipeline, the radial pipe wall pressure guiding pipe measures the pressure on the inner wall of the pipeline, and the radial differential pressure flowmeter calculates the radial throttling pressure difference delta P r in the pipeline according to the data transmitted by the radial center pressure guiding pipe and the radial pipe wall pressure guiding pipe.
In step 4, the upstream axial pressure guiding pipe measures the axial inflow pressure of the pipeline, the downstream axial pressure guiding pipe measures the pressure after the axial shaping of the pipeline, and the axial differential pressure flowmeter calculates the axial throttling pressure difference delta P z in the pipeline according to the data transmitted by the upstream axial pressure guiding pipe and the downstream axial pressure guiding pipe.
In step 5, mathematical models of radial differential pressure and axial differential pressure are established as formulas (12), (13):
Wherein P r is the ratio of working condition pressure to normal pressure;
t r is the ratio of the working condition temperature to the normal temperature;
K 1 -correction factor for radial pressure difference,
K 2 -correction factor for axial pressure difference,
P r -ratio of operating pressure to normal pressure;
T r -ratio of operating temperature to normal temperature;
a 1 and b 1 -measured constant coefficients at radial pressure differential, respectively
C 1 and d 1 -are the measured index coefficients at radial pressure differential, respectively;
a 2 and b 2 -are measured coefficients at axial pressure differential, respectively;
c 2 and d 2 -are the measured index coefficients at axial pressure differential, respectively;
in step 5, assuming an initial dryness value, solving simultaneously according to formulas (12) and (13), and solving the mass flow and dryness of the wet steam through iterative calculation.
In step 5, the iterative calculation includes:
step1, setting initial dryness to be 0.4 on the assumption of starting;
Step 2, generating a formula (12) of DeltaP z, pr and Tr to obtain q m (n);
Step 3, bringing ΔP r、qm (n) into formula (13) to obtain x (n+1);
step 4, bringing DeltaP z and x (n+1) into formula (12) to obtain q m (n+1);
Step 5, q m (n) and q m (n+1) are brought into formula (14), y is obtained, when y is less than 1%, q m value is obtained, otherwise, n=n+1 is continuously repeated, and the calculation is started.
The device and the method for real-time metering and dynamic regulation of wet steam can realize the functions of steam flow regulation and rotational flow shaping of an automatically adjustable churn nozzle and double-differential-pressure four-parameter test, can realize the regulation of critical flow and critical steam flow regulation by changing the position of a cone-shaped throttle body of a regulating cone at the throat to regulate the size of the throat flow area, and are based on a double-parameter measuring structure, a radial differential-pressure model, an axial differential-pressure calculation model and a calculation flow of rotational flow shaping wet steam flow and dryness, and are regulating and controlling devices capable of realizing automatic program control flow regulation through a machine algorithm.
The device and the method for real-time metering and dynamic regulation of the wet steam can calculate the displacement of the regulating cone according to the designed steam mass flow so as to realize the dynamic regulation of the steam flow. Meanwhile, in order to monitor the regulation and control effect, a special rotational flow double differential pressure type wet saturated steam flow, dryness, temperature and pressure four-parameter on-line monitoring device is adopted to evaluate and analyze the dynamic regulation and control effect.
Drawings
FIG. 1 is a block diagram of one embodiment of a real-time metering and dynamic conditioning apparatus for wet steam in accordance with the present invention;
FIG. 2 is a schematic diagram of the operating principle of an adjustable critical flow venturi nozzle according to an embodiment of the present invention;
FIG. 3 is a schematic view of the annular flow state before and after the swirling flow in an embodiment of the present invention;
FIG. 4 is a schematic diagram of a thermal recovery steam injection flow diagram of an oilfield in a multi-well injection process in accordance with one embodiment of the invention;
FIG. 5 is a schematic diagram of the thermal recovery steam injection flow of an oilfield while rotating a single well;
FIG. 6 is a schematic diagram of a wet steam flow and dryness calculation algorithm in accordance with an embodiment of the present invention;
In the figure, a 1-adjusting hand wheel, a 2-adjusting cone, a 3-Venturi nozzle runner and a 4-radial center pressure guiding pipe are arranged;
a 5-radial differential pressure flowmeter, a 6-radial data connection line, a 7-data processor;
8-radial pipe wall pressure guiding pipe, 9-rotational flow vane, 10-upstream axial pressure guiding pipe;
The system comprises an 11-axial differential pressure flowmeter, a 12-downstream axial pressure guiding pipe, a 13-axial data connecting line;
14-pressure gauge, 15-flowmeter, 16-control motor, 17-control connecting wire;
18-PLC control module and 19-regulating rod.
Detailed Description
It should be noted that the following detailed description is exemplary and is intended to provide further explanation of the invention. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present invention. As used herein, the singular forms also are intended to include the plural forms unless the context clearly indicates otherwise, and furthermore, it should be understood that when the terms "comprises" and/or "comprising" are used in this specification, they specify the presence of stated features, steps, operations, and/or combinations thereof.
The device comprises a Venturi nozzle, a swirl vane, a radial center pressure guiding pipe, a radial pipe wall pressure guiding pipe, an upstream axial pressure guiding pipe, a downstream axial pressure guiding pipe, a radial differential pressure flowmeter, an axial differential pressure flowmeter, a pressure gauge and a flowmeter. The venturi nozzle is an adjustable steam critical flow venturi nozzle, wet steam enters the flow passage from the left incoming flow direction of the venturi nozzle flow passage, the right side of the venturi nozzle flow passage is the outlet direction, the cyclone blades are positioned on the right side of the venturi nozzle flow passage, the wet steam flowing out of the venturi nozzle flow passage is subjected to cyclone shaping, gas-liquid two-phase fluid phases are separated, the radial center pressure guiding pipe measures the pressure of a radial center point in the pipeline, the radial pipe wall pressure guiding pipe measures the pressure on the inner wall of the pipeline, the upstream axial pressure guiding pipe measures the axial incoming flow pressure of the pipeline, and the downstream axial pressure guiding pipe measures the pressure after the pipeline is axially shaped.
The radial differential pressure flowmeter is connected with the radial center pressure guiding pipe and the radial pipe wall pressure guiding pipe, and calculates the radial throttling pressure difference delta P r in the pipeline according to the data transmitted by the radial center pressure guiding pipe and the radial pipe wall pressure guiding pipe.
The axial differential pressure flowmeter is connected with the upstream axial pressure guiding pipe and the downstream axial pressure guiding pipe, and calculates the axial throttling pressure difference delta P z in the pipeline according to the data transmitted by the upstream axial pressure guiding pipe and the downstream axial pressure guiding pipe.
A pressure gauge is located at the outlet of the venturi nozzle, by which the outlet pressure P 1 of the critical flow nozzle is measured.
The method for measuring and dynamically regulating the wet steam in real time comprises the following steps:
Step 1, the venturi nozzle regulates the flow of the wet steam flowing through in a critical flow state;
Step 2, separating the gas-liquid two-phase fluid phase from the phase by the cyclone blade;
Step 3, the radial center pressure guiding pipe measures the pressure of a radial center point in the pipeline, the radial pipe wall pressure guiding pipe measures the pressure on the inner wall of the pipeline, and the radial differential pressure flowmeter calculates the radial throttling pressure difference delta P r in the pipeline according to the data transmitted by the radial center pressure guiding pipe and the radial pipe wall pressure guiding pipe;
Step 4, the upstream axial pressure guiding pipe measures the axial inflow pressure of the pipeline, the downstream axial pressure guiding pipe measures the pressure after the axial shaping of the pipeline, and the axial differential pressure flowmeter calculates the axial throttling pressure difference delta P z in the pipeline according to the data transmitted by the upstream axial pressure guiding pipe and the downstream axial pressure guiding pipe;
and 5, establishing a wet steam double-parameter measurement model to realize double-parameter measurement of wet steam flow and dryness.
The following are several embodiments of the invention
Example 1
As shown in FIG. 1, FIG. 1 is a block diagram of an embodiment of the real-time metering and dynamic conditioning apparatus for wet steam of the present invention. The wet steam real-time metering and dynamic regulating device mainly comprises an adjusting hand wheel 1, an adjusting cone 2, a Venturi nozzle runner 3, a radial center pressure guiding pipe 4, a radial differential pressure flowmeter 5, a radial data connecting wire 6, a data processor 7, a radial pipe wall pressure guiding pipe 8, a swirl vane 9, an upstream axial pressure guiding pipe 10, an axial differential pressure flowmeter 11, a downstream axial pressure guiding pipe 12, an axial data connecting wire 13, a pressure gauge 14, a flowmeter 15, a control motor 16, a control connecting wire 17, a PLC control module 18, an adjusting rod 19 and the like.
The automatic adjustable steam critical flow Venturi nozzle is a whole system, namely a Venturi nozzle runner 3, an adjusting hand wheel 1, an adjusting cone 2, an adjusting rod 19, a control motor 16, a control connecting line 17, a PLC control module 18 and the like.
When wet steam enters the flow channel from the left side (i.e. the left side shown in fig. 1) of the venturi nozzle flow channel, the inlet direction of the nozzle is shown here, the tail end of the right side of the regulating cone is the outlet direction, the regulating cone 2 of the device is coaxial with the venturi nozzle flow channel 3 and is arranged in the critical flow venturi nozzle, when the flow of the device needs to be regulated, an instruction is sent out through the PLC control module 18, and then the instruction is transmitted to the control motor 16 through the control connecting wire 17, the control motor 16 drives the regulating hand wheel 1 to rotate, the regulating hand wheel 1 is connected with the regulating rod 19, the regulating rod 19 is fixedly connected with the regulating cone 2 coaxial center and is positioned at the upstream of the regulating cone 2, the regulating cone 2 moves back and forth in the axial direction under the driving of the regulating rod 19 through the regulating hand wheel 1, and forms a variable-area circulation channel with the venturi nozzle, and the automatic adjustable steam critical flow venturi nozzle is formed, and therefore the automatic adjustable steam critical flow venturi nozzle is realized.
The automatic adjustable steam critical flow regulation principle is that when the saturated wet steam at the upstream enters from the inlet of the pipeline, the saturated wet steam firstly flows through the wet steam flow control part, and the core part of the device part is a venturi nozzle capable of adjusting the diameter of the throat. When the upstream saturated wet steam enters the venturi nozzle, similar to a common throttling element, an axial throttling pressure difference is generated between the upstream and the throat of the venturi nozzle, wherein the pressure difference is caused by flow loss, but the structure can realize that the flow velocity is not changed due to the influence of downstream pressure after the flow velocity in the pipeline reaches the critical flow velocity. In order to realize the purpose of adjusting and controlling the flow, the invention innovatively provides an adjusting cone which is matched with the Venturi nozzle, and the adding of the adjusting cone still needs to ensure the critical quantity performance of the original Venturi nozzle.
Example 2
The invention adopts the automatic adjustable steam critical flow Venturi nozzle, and monitors the result of steam flow regulation and control by the monitoring device until the designed flow and dryness are reached.
The dynamic steam flow regulating process is to regulate the displacement of the regulating cone to change the diameter of the throat of the venturi nozzle and to regulate the flow area of the throat, so as to realize the flow regulation of the nozzle in critical flow state. The specific structure is shown in fig. 2. The size of the throat overflow area is regulated by changing the position of the cone-shaped throttle body at the throat, so that the critical flow rate is regulated. Its advantages are convenient regulation and continuous regulation.
In the calculation method of critical steam flow regulation, as shown in fig. 2, both ends of the effective regulation section of the regulation cone are designed to be streamline, so that a flow dead zone is avoided as much as possible, and resistance loss is reduced. The effective adjustment section of the adjustment cone is a truncated cone with a diameter that decreases progressively from upstream to downstream. When the adjustment cone is in its initial position (the position shown by the solid line in the figure), the assumed point N (x, y) is any point on the adjustment cone line. When the adjustment cone is moved downstream by a displacement x from the initial position by manual adjustment, to the position shown by the broken line in the figure, the point N (x, y) moves to a point N' (0, y). The actual throat flow area changes from Ant1 to Ant2.
Ant1＝π(R2-r2) (1)
Ant2＝π(R2-y2) (2)
Wherein R is the throat radius of the Venturi nozzle, and R is the minimum radius of the regulating cone (the radius of the regulating rod). Since r+.y, A nt1≠Ant2. According to the formula (2), when the regulating cone is displaced, the throat area is changed, and then the critical flow is changed, so that the critical flow is regulated. According to the invention, through a large amount of indoor experimental data correction, the finally established critical flow theoretical regulation model of the adjustable critical flow nozzle can be written into the following form:
Wherein:
w-wet steam flow, t/h, d-throat diameter of venturi nozzle, mm;
d 0 -diameter of guide rod, mm, L-displacement of adjusting cone, mm, alpha-cone angle of adjusting cone;
P 1 -inlet pressure of critical flow nozzle, MPa, length of throat of H-Venturi nozzle;
Through the established flow regulation model, the displacement of the regulating cone can be converted, and the calculated displacement of the regulating cone is regulated through a hand wheel, so that the control and regulation of flow are realized. Wherein the inlet pressure P 1 of the critical flow nozzle in the above formula is measured by the pressure gauge 14.
The double-differential-pressure four-parameter test of rotational flow shaping is a test method which firstly needs to perform rotational flow shaping on wet steam and then separately tests shaped gas-liquid two-phase fluid. The rotational flow shaping is a gas-liquid two-phase spiral flow, which is separated into a gas phase and a liquid phase which are outside and uniformly annular by utilizing the density differential pressure of the gas and the liquid at a certain speed, as shown in figure 3, namely the gas phase flows downstream in a spiral manner at the center of a pipeline, and the liquid phase flows downstream in a spiral manner at the side of the pipe wall.
The swirl vane 9 mainly uses the principle of phase separation in a multiphase flow pipe to apply various external forces in the pipeline, so as to respectively concentrate the randomly dispersed gas-liquid two phases, realize the separation between the gas-liquid two phases and the phases, ensure that each phase of the gas-liquid two phases respectively occupies a specific continuous space in the pipe, have relatively regular and clear interfaces between the two phases, finally form two bundles of single-phase fluid which flow in parallel and stably in the pipe, and can maintain a certain length. The parallel stable gas-liquid two-phase fluid formed in the pipeline is shown in figure 3, the gas phase after passing through the separation state in the pipeline is distributed at the center of the pipeline, the cross section of the fluid is in a circular shape symmetrical about the center of the pipeline, the water phase is tightly attached to the inner side of the pipeline wall, and the cross section of the fluid is in a circular shape symmetrical about the center of the pipeline. Through the phase separation technology, the complicated and changeable gas-liquid two-phase flow is changed into regular single-phase parallel flow in the pipeline, so that the treatment is simplified.
On the other hand, a cyclone is adopted to form an in-pipe phase separation state in the pipe, a radial pressure difference and an axial pressure difference are formed, a wet steam double-parameter measurement model is established, and double-parameter measurement of wet steam flow and dryness is realized by measuring the two pressure differences.
The steam flow, dryness, temperature and pressure four-parameter on-line monitoring principle is that wet steam forms an in-tube phase separation state under the action of a cyclone, a radial pressure difference is formed between a wall surface of a certain cross section and the center of a pipeline under the state due to centrifugal force, and an axial pressure difference is generated between a venturi inlet and a throat part due to throttling action. The two pressure differences are very sensitive to flow and phase content, and have stable corresponding relation under certain conditions. On the basis of finding out the corresponding relation, a wet steam double-parameter measurement model is established, so that double-parameter measurement of wet steam flow and dryness can be realized by measuring two differential pressures, and meanwhile, temperature and pressure parameters are monitored in real time by combining temperature and pressure sensors arranged on pipelines, so that four-parameter real-time on-line is realized.
The double-parameter measurement of the wet steam flow and dryness comprises a radial differential pressure model and an axial differential pressure model. The radial pressure difference model is that the radial pressure difference deltap r in the phase separation state in the gas-liquid two-phase pipe can be regarded as being formed by superposing the radial pressure difference deltap rg of the gas phase from the center of the pipe to the gas-liquid interface and the radial pressure difference deltap rl of the liquid phase from the gas-liquid interface to the pipe wall, namely:
ΔPr＝ΔPrg+ΔPrl (4)
Wherein:
The axial pressure difference model is a phase separation model according to a gas-liquid two-phase flow, and the axial pressure difference Δp z generated when the gas-liquid two-phase forced annular flow flows through the venturi nozzle can be expressed as the sum of pressure drops generated when the gas-liquid two-phase flows through the pipeline with the diameters of D g and D f respectively, namely:
Δpz＝Δpzg+Δpzl (7)
Wherein:
In the method, under the forced annular flow state in the pipe, radial pressure difference is formed between the upper wall surface of a certain cross section and the center of the pipeline, and the radial pressure difference is mainly generated by the action of centrifugal force in the rotational flow process of the gas-liquid two-phase flow. The pressure of the radial central point in the pipeline is measured by the point A through the 4 radial central pressure guiding pipe, the pressure of the radial central point in the pipeline is measured by the point B through the 8 radial pipe wall pressure guiding pipe, the difference value of the pressure and the pressure is the radial throttling pressure difference delta P r in the pipeline, namely delta P r＝PB-PA, the difference value of the pressure and the pressure can be measured by the 5 radial differential pressure flowmeter, and the pressure can be transmitted to the 7 data processor through the 6 radial data connecting line, so that the measurement of the radial throttling pressure difference is completed. And the point C is used for measuring the axial inflow pressure of the pipeline through the 10 upstream axial pressure guiding pipe, the point D is used for measuring the axial reshaping pressure of the pipeline through the 12 downstream axial pressure guiding pipe, the difference value of the two is the axial throttling pressure difference delta P z in the pipeline, namely delta P z＝PD-PC, the difference value of the two can be measured through an 11 axial differential pressure flowmeter, and the difference value is transmitted to a 7 data processor through a 13 axial data connecting wire, so that the measurement of the axial throttling pressure difference is completed. The two pressure differences are very sensitive to flow and phase content, and have stable corresponding relation under certain conditions, and a wet steam double-parameter measurement model is established. Therefore, the differential pressure sensor can be used for measuring the radial throttling differential pressure delta P r and the axial throttling differential pressure delta P z, and double-parameter measurement of the wet steam flow and the dryness can be realized. When the two parameters of the flow rate and the dryness of the wet steam are measured, the dryness of the flow meter is converted according to the established corresponding relation, if the design requirement is not met, the flow meter is required to be adjusted, the displacement relation between the flow rate and the control flow rate adjusting cone is adjusted according to the method, in order to ensure the accuracy of the displacement control quantity of the adjusting cone, a PLC control module is adopted for controlling, after the displacement quantity of the adjusting cone is determined, adjustment data are input into a data processor, the data processor gives a displacement quantity instruction to the PLC control module through a control connecting wire, and the PLC control module controls the automatic and accurate adjustment displacement quantity of a control motor through the control connecting wire, so that the control and monitoring method of the wet steam is realized.
The two-parameter measurement and calculation flow of the wet steam flow and the dryness fraction adopts the stagnation temperature which is the corresponding saturation temperature under the steam inlet pressure, five groups of steam inlet pressures are selected in calculation, seven types of steam dryness fractions are selected in calculation, and six types of mass flow fractions are selected in calculation. These influencing factors were combined to a total of 210 sets of data. Through researches, the axial pressure difference and the radial pressure difference are not only related to mass flow and dryness, but also have certain influence on the mass flow and dryness, and the pressure P and the temperature T take the influence of the pressure and the temperature into consideration on the basis of the measurement models of the formulas (8) and (9). Adding correction coefficients K on the basis of a measurement model through fitting, wherein the correction coefficients K are shown as formulas (10) and (11), and obtaining mathematical models of corrected radial pressure difference and axial pressure difference are shown as formulas (12) and (13):
Wherein P r is the ratio P/0.101325 of the working condition pressure to the normal pressure;
t r is the ratio of working condition temperature to normal temperature T/293.15;
a1＝1.527139098;b1=-0.594416255;
c1＝7.463204582;d1=-49.84616258;
a2＝4.166129518;b2=-37.5766719;
c2＝5.259173348;d2=-38.61585079。
In the middle of ：a3＝1.044793705;b3＝6.081003689;c3＝2.382321195;d3＝19.730353;e3＝22.52160137;f3＝4.083490371;R2＝0.9761.
In the middle of ：a4＝4.774612495;b4＝10.37545863;c4＝2.782537121;d4＝0.945170937;e4＝8.765867032;f4＝2.063769126;R2＝0.9438.
From the above, the operating pressure and temperature are known conditions, and the measured model independent variables are radial pressure difference and axial pressure difference. Assuming an initial dryness value, solving simultaneously according to formulas (12) and (13), and solving the mass flow and dryness of the wet steam through iterative calculation. The iterative algorithm is shown in fig. 6.
Step1, setting initial dryness to be 0.4 on the assumption of starting;
Step 2, generating a formula (12) of DeltaP z, pr and Tr to obtain q m (n);
Step 3, bringing ΔP r、qm (n) into formula (13) to obtain x (n+1);
step 4, bringing DeltaP z and x (n+1) into formula (12) to obtain q m (n+1);
Step 5, substituting q m (n) and q m (n+1) into equation (14) to obtain y when y <1%
If the obtained q m value is available, otherwise, n=n+1 is continuously repeated to start calculation.
The wet steam flow control and monitoring device designed by the invention can well realize the regulation and control of the wet steam flow of the ground of the oil well, the regulated and controlled parameters are monitored by the monitoring means, the injection parameters are known in time, and the regulation is carried out at any time according to the requirements.
After the saturated wet steam has passed through the flow control section, it goes to a downstream monitoring section of the apparatus. The monitoring part innovation of the device provides that 9 cyclone blades are adopted for carrying out cyclone shaping on wet steam. The main process is that when wet steam passes through the rotational flow shaping function of the 9 rotational flow blades, a uniform annular flow which is mainly in gas phase and uniformly distributed on the wall surface of the pipeline in the form of a liquid film is formed in the center of the pipeline. Wherein the 9 swirl vane parts consist of 4-6 swirl vanes with the inclination angle of 45-135 degrees and are arranged in the pipeline. The number and the inclination angle of the cyclone blades can be optimally designed according to actual engineering requirements.
FIG. 2 shows the structural relationship of the adjustment cone to the critical flow throat flow area. In the figure, the adjusting cone moves from left to right, and generates displacement L on the x-axis, so that the overflow area at the critical flow throat is changed, and the critical flow is adjusted. In the process of designing the adjusting cone, each parameter is comprehensively determined according to an established critical flow theoretical regulation model of the adjustable critical flow nozzle, namely a formula (3) described in the text.
FIG. 3 shows a schematic view of the annular flow state before and after the swirling flow. When the multiphase fluid flows into the double-parameter measuring device of the wet steam flow and dryness of the rotational flow integer from the adjustable flow control device, firstly, the multiphase fluid passes through the rotational flow blade, and under the action of the rotational flow blade, the complex multiphase fluid is shaped into uniform fluid with gas core inside and liquid film outside, so as to measure the wet steam flow and dryness.
Example 3
Along with popularization and application of large-displacement boilers, one-boiler multi-well becomes a main form of steam injection, steam is influenced by pipe network structures, backpressure differences of all wells and steam differentiation phenomena in the ground conveying process, dryness differences exist among steam injection wells generally, sometimes the dryness differences reach more than 20%, the development of heavy oil reservoirs mainly depends on heat energy carried by wet steam, and the dryness differences among wells can lead to waste of heat energy resources and even influence the development effect of heavy oil wells.
For the case of a single well for oil field site application, we can use a parallel connection mode of multiple groups of devices to connect to the ground distribution device, and the specific structure is shown in fig. 5. The device is mainly connected to a ground connecting pipeline between the steam injection boiler and the wellhead of the steam injection well.
By adopting the method, the steam injection boiler is independently connected with the device on site, as shown in fig. 5, the steady flow and the dryness of the boiler are compared with the monitoring result of the device through actual measurement, and the error is as follows, so that the method is proved to be capable of completely controlling and metering the steam injection flow and the dryness on site.
TABLE 1 measurement results and errors at different flows
Measuring flow Boiler flow Relative error Dryness measurement Dryness of boiler Relative error
(kg/h) (kg/h) (%) (%) (%) (%)
1 6130 6150 -0.33 0.6636 0.6473 1.63
2 6330 6240 1.44 0.7363 0.7616 -2.53
3 7440 7450 -0.13 0.7631 0.7661 -0.30
4 7540 7600 -0.79 0.7746 0.7541 2.05
5 7690 7680 0.13 0.7475 0.7619 -1.44
6 7880 8070 -2.35 0.7564 0.7403 1.61
7 7990 8070 -1.00 0.7837 0.7886 -0.49
For the case of one injection multi-well in oilfield field application, we can use a parallel connection mode of multiple groups of devices to connect into the surface distribution device, and the specific structure is shown in fig. 4. The device is mainly connected to a ground connecting pipeline between the steam injection boiler and the wellhead of the steam injection well. The real-time monitoring data of a certain well are as follows:
TABLE 2 pressure, temperature, flow, dryness of certain well
It should be noted that the above description is only a preferred embodiment of the present invention, and not intended to limit the present invention, but although the present invention has been described in detail with reference to the above embodiment, it will be apparent to those skilled in the art that modifications may be made to the technical solutions described in the above embodiment, or equivalents may be substituted for some of the technical features thereof. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Other than the technical features described in the specification, all are known to those skilled in the art.

Claims (14)

1.湿蒸汽实时计量和动态调控装置，其特征在于，该湿蒸汽实时计量和动态调控装置包括文丘里喷嘴、旋流叶片、径向中心引压管、径向管壁引压管、上游轴向引压管、下游轴向引压管，该文丘里喷嘴为可调式蒸汽临界流文丘里喷嘴，湿蒸汽从该文丘里喷嘴的左侧来流方向进入流道内，该文丘里喷嘴的右侧为出口方向，该旋流叶片位于该文丘里喷嘴的右侧，将该文丘里喷嘴流出的湿蒸汽进行旋流整形，将气液两相流体相与相之间进行隔离，该径向中心引压管测量管道内径向中心点的压力，该径向管壁引压管测量管道内壁上的压力，该上游轴向引压管测量管道轴向来流压力，该下游轴向引压管测量管道轴向整形后的压力。1. A device for real-time metering and dynamic regulation of wet steam, characterized in that the device comprises a venturi nozzle, a swirl blade, a radial center pressure-inducing pipe, a radial tube wall pressure-inducing pipe, an upstream axial pressure-inducing pipe, and a downstream axial pressure-inducing pipe, wherein the venturi nozzle is an adjustable steam critical flow venturi nozzle, and wet steam enters the flow channel from the left side of the venturi nozzle in the incoming flow direction, and the right side of the venturi nozzle is the outlet direction. The swirl blade is located on the right side of the venturi nozzle, and the wet steam flowing out of the venturi nozzle is swirl-shaped to isolate the gas-liquid two-phase fluid from phase to phase. The radial center pressure-inducing pipe measures the pressure at the radial center point in the pipeline, the radial tube wall pressure-inducing pipe measures the pressure on the inner wall of the pipeline, the upstream axial pressure-inducing pipe measures the axial incoming flow pressure of the pipeline, and the downstream axial pressure-inducing pipe measures the pressure of the pipeline after axial shaping. 2.根据权利要求1所述的湿蒸汽实时计量和动态调控装置，其特征在于，该湿蒸汽实时计量和动态调控装置还包括径向差压流量计，该径向差压流量计连接于该径向中心引压管、该径向管壁引压管，根据该径向中心引压管、该径向管壁引压管传输过来的数据，计算管道内径向节流压差ΔPr。2. The device for real-time metering and dynamic control of wet steam according to claim 1 is characterized in that the device further comprises a radial differential pressure flowmeter, which is connected to the radial center pressure guide pipe and the radial wall pressure guide pipe, and calculates the radial throttling pressure difference ΔP r in the pipeline according to the data transmitted by the radial center pressure guide pipe and the radial wall pressure guide pipe. 3.根据权利要求1所述的湿蒸汽实时计量和动态调控装置，其特征在于，该湿蒸汽实时计量和动态调控装置还包括轴向差压流量计，该轴向差压流量计连接于该上游轴向引压管、该下游轴向引压管，根据该上游轴向引压管、该下游轴向引压管传输过来的数据，计算管道内的轴向节流压差ΔPz。3. The device for real-time metering and dynamic control of wet steam according to claim 1 is characterized in that the device for real-time metering and dynamic control of wet steam further comprises an axial differential pressure flowmeter, which is connected to the upstream axial pressure-guiding pipe and the downstream axial pressure-guiding pipe, and calculates the axial throttling pressure difference ΔP z in the pipeline according to the data transmitted by the upstream axial pressure-guiding pipe and the downstream axial pressure-guiding pipe. 4.根据权利要求1所述的湿蒸汽实时计量和动态调控装置，其特征在于，该湿蒸汽实时计量和动态调控装置还包括压力计和流量计，该压力计位于该文丘里喷嘴的进口处，该文丘里喷嘴的进口压力P1通过该压力计测得，该流量计位于该文丘里喷嘴的进口处，该文丘里喷嘴的进口流量通过该流量计测得。4. The device for real-time metering and dynamic control of wet steam according to claim 1 is characterized in that it further comprises a pressure gauge and a flow meter, the pressure gauge being located at the inlet of the venturi nozzle, and the inlet pressure P1 of the venturi nozzle being measured by the pressure gauge, and the flow meter being located at the inlet of the venturi nozzle, and the inlet flow rate of the venturi nozzle being measured by the flow meter. 5.根据权利要求1所述的湿蒸汽实时计量和动态调控装置，其特征在于，该文丘里喷嘴包括文丘里喷嘴流道、调节手轮、调节锥、调节杆、控制电机和PLC控制模块，该调节锥与该文丘里喷嘴流道同轴心且置于该文丘里喷嘴内部，该控制电机连接于该PLC控制模块和该调节手轮，当流量大小需要调节时，该PLC控制模块发出指令，并将指令传输给该控制电机，该控制电机带动该调节手轮进行转动，而该调节手轮连接于该调节杆，该调节杆与该调节锥同轴心固定连接且位于该调节锥上游，该调节锥通过该调节手轮在该调节杆的带动下在轴向上来回移动，形成自动可调式蒸汽临界流文丘里流道。5. The device for real-time metering and dynamic control of wet steam according to claim 1 is characterized in that the Venturi nozzle comprises a Venturi nozzle flow channel, an adjusting hand wheel, an adjusting cone, an adjusting rod, a control motor and a PLC control module, the adjusting cone is coaxial with the Venturi nozzle flow channel and is placed inside the Venturi nozzle, the control motor is connected to the PLC control module and the adjusting hand wheel, when the flow rate needs to be adjusted, the PLC control module issues an instruction and transmits the instruction to the control motor, the control motor drives the adjusting hand wheel to rotate, and the adjusting hand wheel is connected to the adjusting rod, the adjusting rod is fixedly connected to the adjusting cone coaxially and is located upstream of the adjusting cone, the adjusting cone moves back and forth in the axial direction through the adjusting hand wheel under the drive of the adjusting rod, so as to form an automatically adjustable steam critical flow Venturi flow channel. 6.根据权利要求1所述的湿蒸汽实时计量和动态调控装置，其特征在于，该旋流叶片进行湿蒸汽的旋流整形时，利用气液在一定速度下的密度差压，将其分离成气相在内，液相在外的均匀环状流，在管道中心形成以气相为主，液体以液膜的形式均匀的分布在管道壁面的均匀环状流。6. The device for real-time metering and dynamic control of wet steam according to claim 1 is characterized in that when the swirl blade performs swirl shaping of the wet steam, the density differential pressure between gas and liquid at a certain speed is utilized to separate the wet steam into a uniform annular flow with the gas phase inside and the liquid phase outside, thereby forming a uniform annular flow with the gas phase as the main phase in the center of the pipeline and the liquid evenly distributed on the pipeline wall in the form of a liquid film. 7.根据权利要求6所述的湿蒸汽实时计量和动态调控装置，其特征在于，该旋流叶片由4-6个倾角为45°-135°的旋流叶片组成，并安装在管道中，该旋流叶片的个数与倾角根据实际工程需要进行优化设计。7. The wet steam real-time metering and dynamic control device according to claim 6 is characterized in that the swirl blades are composed of 4-6 swirl blades with an inclination angle of 45°-135° and are installed in the pipeline. The number and inclination angle of the swirl blades are optimized according to actual engineering needs. 8.湿蒸汽实时计量和动态调控方法，其特征在于，该湿蒸汽实时计量和动态调控方法采用了权利要求1所述的湿蒸汽实时计量和动态调控装置，包括：8. A method for real-time metering and dynamic regulation of wet steam, characterized in that the method adopts the device for real-time metering and dynamic regulation of wet steam according to claim 1, comprising: 步骤1，文丘里喷嘴将流经的湿蒸汽在临界流状态下进行流量调节；Step 1, the venturi nozzle regulates the flow rate of the wet steam flowing through it in a critical flow state; 步骤2，旋流叶片将气液两相流体相与相之间进行隔离；Step 2, the swirl blades isolate the gas-liquid two-phase fluid from each other; 步骤3，计算管道内径向节流压差ΔPr；Step 3, calculating the radial throttling pressure difference ΔP r in the pipeline; 步骤4，计算管道内的轴向节流压差ΔPz；Step 4, calculating the axial throttling pressure difference ΔP z in the pipeline; 步骤5，建立湿蒸汽双参数测量模型，实现湿蒸汽流量和干度的双参数测量。Step 5: Establish a dual-parameter measurement model for wet steam to achieve dual-parameter measurement of wet steam flow and dryness. 9.根据权利要求8所述的湿蒸汽实时计量和动态调控方法，其特征在于，在步骤1，建立可调式临界流喷嘴的临界流理论调控模型：9. The method for real-time metering and dynamic control of wet steam according to claim 8, characterized in that, in step 1, a critical flow theory control model of an adjustable critical flow nozzle is established: 其中：in: W-湿蒸汽流量，t/h；d-文丘里喷嘴的吼口直径,mm；W-wet steam flow, t/h; d-venturi nozzle diameter, mm; d0-导杆直径，mm；L-调节锥位移，mm；α-调节锥锥角，度；d 0 - guide rod diameter, mm; L - adjustment cone displacement, mm; α - adjustment cone angle, degrees; P1-临界流喷嘴的进口压力，MPa；H-文丘里喷嘴喉部的长度；P 1 - inlet pressure of critical flow nozzle, MPa; H - length of the venturi nozzle throat; ρ-流体密度，kg/m3；ρ-fluid density, kg/m 3 ; 通过上述建立的可调式临界流喷嘴的临界流理论调控模型，就可以换算出调节锥的位移量，计算出的调节锥的位移量通过调节手轮来实现调节，进而实现流量的控制调节。Through the critical flow theory control model of the adjustable critical flow nozzle established above, the displacement of the regulating cone can be converted. The calculated displacement of the regulating cone is adjusted by adjusting the hand wheel, thereby realizing the control and regulation of the flow rate. 10.根据权利要求8所述的湿蒸汽实时计量和动态调控方法，其特征在于，在步骤3，径向中心引压管测量管道内径向中心点的压力，径向管壁引压管来测量管道内壁上的压力，径向差压流量计根据该径向中心引压管、径向管壁引压管传输过来的数据，计算管道内径向节流压差ΔPr。10. The method for real-time metering and dynamic control of wet steam according to claim 8, characterized in that, in step 3, the radial center pressure pipe measures the pressure at the radial center point in the pipeline, the radial wall pressure pipe measures the pressure on the inner wall of the pipeline, and the radial differential pressure flowmeter calculates the radial throttling pressure difference ΔP r in the pipeline based on the data transmitted by the radial center pressure pipe and the radial wall pressure pipe. 11.根据权利要求8所述的湿蒸汽实时计量和动态调控方法，其特征在于，在步骤4，上游轴向引压管测量管道轴向来流压力，下游轴向引压管来测量管道轴向整形后的压力，轴向差压流量计根据该上游轴向引压管、下游轴向引压管传输过来的数据，计算管道内的轴向节流压差ΔPz。11. The method for real-time metering and dynamic control of wet steam according to claim 8, characterized in that, in step 4, the upstream axial pressure-guiding pipe measures the axial incoming flow pressure of the pipeline, and the downstream axial pressure-guiding pipe measures the pressure of the pipeline after axial shaping, and the axial differential pressure flowmeter calculates the axial throttling pressure difference ΔP z in the pipeline based on the data transmitted by the upstream axial pressure-guiding pipe and the downstream axial pressure-guiding pipe. 12.根据权利要求8所述的湿蒸汽实时计量和动态调控方法，其特征在于，在步骤5，建立径向压差和轴向压差的数学模型如式(12)、(13)：12. The method for real-time metering and dynamic control of wet steam according to claim 8, characterized in that, in step 5, a mathematical model of radial pressure difference and axial pressure difference is established as shown in formulas (12) and (13): 式中：Pr为工况压力与常压比值；Where: P r is the ratio of working pressure to normal pressure; Tr为工况温度与常温比值；T r is the ratio of operating temperature to normal temperature; K1-径向压差的修正系数，K 1 - correction factor for radial pressure difference, K2-轴向压差的修正系数，K 2 - correction factor for axial pressure difference, Pr-工况压力与常压比值；P r - ratio of operating pressure to normal pressure; Tr-工况温度与常温比值；T r - ratio of operating temperature to normal temperature; a1和b1-分别为径向压差时的测得的常数系数a 1 and b 1 - are the measured constant coefficients for radial pressure difference c1和d1-分别为径向压差时的测得的指数系数；c 1 and d 1 - respectively, the measured exponential coefficients at radial pressure difference; a2和b2-分别为轴向压差时的测得的系数；a 2 and b 2 - respectively, the measured coefficients for axial pressure difference; c2和d2-分别为轴向压差时的测得的指数系数；c 2 and d 2 - respectively, the measured exponential coefficients at axial pressure difference; 13.根据权利要求12所述的湿蒸汽实时计量和动态调控方法，其特征在于，在步骤5，假设初始干度值，根据公式(12)、(13)联立求解，通过迭代计算，求解湿蒸汽的质量流量和干度。13. The method for real-time metering and dynamic control of wet steam according to claim 12 is characterized in that, in step 5, an initial dryness value is assumed, and the mass flow rate and dryness of the wet steam are solved by iterative calculation according to formulas (12) and (13). 14.根据权利要求13所述的湿蒸汽实时计量和动态调控方法，其特征在于，在步骤5，迭代计算包括：14. The method for real-time metering and dynamic control of wet steam according to claim 13, characterized in that in step 5, the iterative calculation comprises: 步骤1：假设开始，设置初始干度为0.4；Step 1: Assume that at the beginning, set the initial dryness to 0.4; 步骤2：将ΔPz，Pr，Tr代人公式(12)得到qm(n)；Step 2: Substitute ΔP z , Pr, Tr into formula (12) to obtain q m (n); 步骤3：将ΔPr、qm(n)带入公式(13)中得到x(n+1)；Step 3: Substitute ΔP r and q m (n) into formula (13) to obtain x(n+1); 步骤4：将ΔPz、x(n+1)带入公式(12)中得到qm(n+1)；Step 4: Substitute ΔP z and x(n+1) into formula (12) to obtain q m (n+1); 步骤5：将qm(n)和qm(n+1)带入公式(14)，得出y，当y<1％时，得到的qm值可取，否则将n＝n+1继续重复步骤一开始计算。Step 5: Substitute q m (n) and q m (n+1) into formula (14) to obtain y. When y<1%, the obtained q m value is acceptable. Otherwise, set n=n+1 and repeat the calculation in step 1.
CN202311581242.XA 2023-11-24 2023-11-24 Real-time metering and dynamic regulating and controlling device and method for wet steam Pending CN120042542A (en)

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US12546412B1 (en) * 2024-05-20 2026-02-10 Michael D. McFetters Variable venturi valve

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US12546412B1 (en) * 2024-05-20 2026-02-10 Michael D. McFetters Variable venturi valve

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