• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    METHOD AND APPLIANCE FOR COMPOSITION BASED ON MONITORING PERFORMANCE OF COMPRESSION CONTROL. The present invention relates to a method and an apparatus for controlling a compressor, where the compressor inlet gas may contain water and / or non-aqueous liquid. The method comprises the steps of measuring the temperature on the inlet and / or outlet side of the compressor (1), the pressure measurement on the inlet and outlet side of the compressor (1) in order to determine a compressor pressure ratio , measurement of fluid mix density at the inlet side and / or asphalt side of the compressor (1), measurement of individual volume fractions of gas, water and non-aqueous liquid at the inlet and / or outlet side of the compressor, measurement fluid velocity on the compressor inlet and / or outlet side, determination of individual non-aqueous gas, water and liquid flow rates and the fluid velocity on the compressor inlet and / or outlet side, and based on compressor pressure ratio determined and total volumetric flow of the actual fluid mix determined and / or measured temperature and / or mixing density (...).
    公开号:BR112013000694B1
    申请号:R112013000694-3
    申请日:2011-07-14
    公开日:2020-11-17
    发明作者:Lars Brenne；Jan Hoydal
    申请人:Statoil Asa；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a method and apparatus for detecting oscillation conditions in a gas compressor and for the anti-oscillation control and mapping of a gas compressor based on real-time measurement of gas compositions and / or individual liquid and / or gas flow rates of the working fluid. The mapping is recognized as identifying the compressor's operating points within the compressor's operating envelope, and parameters, such as the actual volumetric flow rate and / or pressure ratio, are often used for this purpose.
    [0002] The oscillation, or stop, is the lower limit of the stable operation of a compressor where an additional reduction in the volumetric flow rate creates an incidence of oscillation. The appearance of oscillation is associated with flow instabilities, flow reversal in the compressor and a complete break in the compressor's performance. The oscillation can be caused by changes in flow rate, changes in fluid compositions, changes in operating conditions, or due to flow disturbances. It is important to be able to prevent the oscillation from occurring through corrective actions as the oscillation can cause severe damage to the internal parts of the compressor. A limit denoted by the oscillation line is created based on the pressure ratio and volumetric flow rate where the appearance of the stop is identified inside the machine. Such a line of oscillation is covering all combinations of pressure ratios and volumetric flow rates that are possible to obtain within the speed range of the machine. The oscillation line represents the limit of the lower volumetric flow rate where it is possible to operate the compressor.
    [0003] The oscillation limit is an experimentally determined curve that refers to the pressure ratio X the actual volumetric flow rate at the point where the stop is detected for different compressor rotation speeds. An additional reduction in the volumetric flow rate at that point with a constant rotation speed will initiate the oscillation: oscillation curve =
    where QG is the volumetric flow of gas through the compressor, and pi, and p2, are the pressures measured before and after the compressor respectively. The flow rate provided in (1) can alternatively be represented by the differential pressure against the flow device normally installed upstream of the machine.
    [0004] The main objective for an anti-oscillation system is to maintain the high robustness of the system and the economic operation of the compressor system. Such an implementation of a precise control routine increases the machine operating envelope, and less recycling flows are required when operating on the control line. Favorable control routines ensure that the compressor can be used close to the limit of oscillation and stopped with only a small safety margin. An increase in the operating envelope is favorable for long-term operation with a high variation of flow and pressure ratios since its variation often tends to require a new design of the machine if the envelope is limited.
    [0005] Common approaches to prevent a compressor from entering the oscillation regime include speed control and increased volumetric flow rate at the compressor inlet by recirculating the gas from the discharge by opening an anti-oscillation valve. Rapid anti-oscillation routines are usually based on the recirculation of compressed gas that is fed back into the compressor, the recirculation being controlled in real time by a recirculation valve (US3424370, Centrifugal Compressors - a basic guide, Penwell Corporation 2003 ).
    [0006] All oscillation control systems depend on the measurement of one or more signals that contain information that can be used to provide a warning about the occurrence of the oscillation. Various means have been employed to monitor the various operating parameters of a compressor, and to use these measurements to control the operation of the compressor to prevent oscillation. The signals being used to control the oscillation can be based on temperature and pressure measurements upstream and / or downstream of the compressor unit, vibration monitoring, or by measuring the actual gas flow rate at the inlet or outlet of the compressor.
    [0007] There are numerous systems in the prior art to control the flow of gases in a recycling line connected between the discharge and inlet of a centrifugal compressor for the purpose of positively preventing the compressor from oscillating. US Patent No. 3,292,846 of December 20, 1966, illustrates such a control system in which the flow in the recycling line is created in response to the density of the gas discharged and the speed of the compressor to maintain sufficient flow through compressor to prevent it from oscillating.
    [0008] Some methods are based on pressure and temperature measurements in the compressor inlet and outlet section where the measured profile is compared with a known compressor behavior. An anti-sway system based on temperature measurement is, for example, described in CA 2522760, whereas a system based on measurement of the rate of change of characteristic variables such as temperature, differential pressure, energy consumption is described in US 6,123. 724. These types of measurements are, however, very slow in many real situations where flow properties can change quickly.
    [0009] Many prior art systems measure and compute the compressor's operating point with respect to an oscillation line that is determined based on conventional performance curves for various conditions and the measured volumetric flow rate of the gas is used ωmo a basis for control routines. An example of such a system is described in US 4,156,578 where oscillation is prevented by measuring through the inlet and outlet side of a compressor such variables as compressor inlet pressure, compressor outlet pressure, and differential pressure across flow device arranged in a compressor inlet duct. The oscillation conditions also depend on the properties of the gas, especially the molecular weight of the gas. U.S. 4,825,380 describes a method in which the real-time molecular weight of the gas is estimated online from actual flow, pressure, temperature, and velocity measurements along with compressor performance data.
    [0010] Although the most common method of measuring flow rate through a gas compressor is by using differential pressure devices, other flow metering devices can also be used. U.S. 4,971,516 describes a method and apparatus for operating compressors based on measuring the volumetric flow rate of the gas through the compressor through the use of an acoustic flow meter. The acoustic flow measurement systems will not, however, function properly if the gas contains liquids as drops of liquid or liquid film will cause the sound waves to spread and disturb the measurements significantly.
    [0011] In addition to the aforementioned methods that are based on measuring the characteristics of the working fluid flowing through the compressor, another method is to base control on monitoring the situation of the compressor machinery. U.S. 4,399,548 describes anti-oscillation routines that are based on measuring the vibration level of machinery. This approach suffers from the limitation of different compressors having different signature patterns of pressure fluctuations and the method is, therefore, associated with great uncertainties.
    [0012] A fact common to all the above methods is that they suffer from reduced precision and reliability if the gas contains liquids or the gas composition is changing during the operation of the compressor. For certain applications, for example, for compressing a wet gas containing a certain amount of liquid, prior art control systems will normally exhibit significant measurement errors that can result in inefficient compressor operation and / or failure to prevent oscillation. This is because these prior art systems do not take into account the presence of liquid in the gas. Conventional flow rate measurement systems are not able to discriminate between gas and liquids and are consequently associated with significant volumetric flow rate uncertainties. For example, for a measurement system that is based on the measurement of differential pressure as the fluid is accelerated through a flow constriction, the presence of liquids with a high density will increase the differential pressure since if the volumetric flow rate of the gas is greater than the current one and creates large uncertainties between the measured and actual volumetric rate. In wet gas compressor applications, where the working fluid consists of a gas containing certain amounts of liquid, such increased uncertainties are particularly pronounced due to the combination of high liquid rate and large difference in density between the gas phase and the liquid phase . In traditional systems, this can be interpreted as a wide variation in the flow rate of volumetric gas that does not necessarily represent physical reality.
    [0013] The result, when using conventional compressor control systems, for cases where the gas composition is changing or the gas is containing certain amounts of liquids, it may be that the compressor is entering the oscillation regime for no apparent reason since the oscillation line being used to control the compressor becomes incorrect. It may also be that very large safety margins need to be introduced, causing an operating regime that is not ideal.
    [0014] Monitoring the condition of the compressors in operation is important in order to observe the degradation resulting from the changed process limits, and internal damage. The calculation of the polytropic header that represents the calculated work done by the compressor is usually performed according to equation (2).
    where Ro is the universal gas constant, MWG is the molecular weight of the gas, Zi is the gas compressibility factor, Ti is the suction side temperature, PGI is the inlet gas density, pi is the inlet pressure , p2 is the outlet pressure, and nP is the polytropic exponent.
    [0015] Alternatively, the polytropic header can also be calculated according to equation (3):
    Where

    [0016] The density of the gas at the compressor outlet is represented by pG2 in equation (3) and (4).
    [0017] Additionally, the compressor's polytropic efficiency is determined by
    where hd and ho2 represent the enthalpy of the gas at the compressor inlet and outlet, respectively. This change in enthalpy reflects the actual fluid energy delivered to the fluid through the compressor.
    [0018] In the application of conventional compressor no measurement of gas density is performed so that this property is calculated using a selected equation of state (EOS) and is sensitive to the change in the composition of the real gas that normally changes with the time.
    [0019] The current state of the compressor performance calculation technique is not applicable when the liquid is present in the gas, since equations (2), (3), (4) and (5) are restricted to gas only and may be incorrect even for the gas since the composition of the gas changes over time.
    [0020] It is an objective of the invention to overcome the limitations mentioned above of existing solutions and to integrate a composition and flow measurement solution into the compressor control system in order to achieve a more precise, more robust and more efficient operation of gas compressors.
    [0021] It is another objective of the invention to provide an accurate measurement of the UM fraction of liquid from a wet gas flowing through a gas compressor.
    [0022] It is another additional objective of the invention to provide an accurate measurement of the gas and the total density of the working fluid flowing through a gas compressor.
    [0023] It is another objective of the invention to provide an accurate measurement of the molecular weight of the working fluid flowing through a gas compressor.
    [0024] It is another objective of the invention to provide an accurate measurement of the total volumetric flow rate of the working fluid flowing through a gas compressor.
    [0025] It is another objective of the invention to provide an accurate real-time measurement of the total volumetric flow rate of the working fluid flowing through a gas compressor when the gas composition changes over time.
    [0026] It is an additional objective of the invention to provide real-time values for fluid properties such as molecular weight, density and compressibility of the working fluid flowing through a gas compressor when the gas composition changes with the time.
    [0027] It is an additional object of the invention to use the measured total volumetric flow rate, measured machine pressure ratio or calculated header, and measured working fluid properties to accurately determine the operating point of a gas compressor when the composition of the working fluid contains uncertainties.
    [0028] It is another object of the invention to use the measured total volumetric flow rate, measured machine pressure ratio or calculated header, and measured working fluid properties to accurately determine the operating point of a gas compressor when the gas contains undetermined amounts of liquids.
    [0029] It is an additional objective of the invention to use the measured real-time total volumetric flow rate, measured machine pressure ratio or calculated header, and measured working fluid properties to accurately determine the operating point of a gas compressor when the working fluid composition changes over time.
    [0030] It is another objective of the invention to measure the fraction of liquid flowing through the compressor and, thus, to be able to have a floating control line used for protection against oscillation that will depend on the fraction of liquid that enters the machine.
    [0031] It is an additional objective of the invention to use the measured machine pressure ratio or calculated header and flow rate dependent on the operating point in real time to determine the set point of a gas compressor when the gas composition contains uncertainties or uncertain amounts of liquids.
    [0032] It is another additional objective of the invention to improve the precision and robustness of the oscillation prevention routines by using a precisely measured total volumetric flow rate to initiate the recirculation of the working fluid if the operating point is very close to the compressor oscillation regime.
    [0033] Another objective of the invention is to use the flow measurement computer to perform active anti-sway control and directly control the values used to recirculate the exhaust gas to the compressor inlet.
    [0034] It is another objective of the invention to use the measured total volumetric flow rate, the measured gas properties and the pressure ratios measured at different pressure ratios flow rates to accurately determine the oscillation limit for a compressor gas.
    [0035] It is another objective of the invention to use the determined oscillation limit and a determined safety margin at different flow rates and different fluid compositions to accurately determine a multidimensional oscillation control surface.
    [0036] It is an additional object of the invention to use the measured total volumetric flow rate, the measured gas composition, the measured gas properties and the pressure ratios measured at different flow rates and pressure ratios to determine with precision the throttling limit for a gas compressor.
    [0037] It is another additional objective of the invention to use the measured total volumetric flow rate, and the gas properties measured at different flow rates and different fluid compositions to accurately determine an equivalent volume flow rate for a compressor. gas.
    [0038] It is another objective of the invention to define new compressor performance equations being able to calculate parameters such as polytropic header, polytropic exponent, and efficiency when the liquid is present in the gas flow.
    [0039] is another objective of the invention if it detects changes in compressor performance due to liquids present in the feed stream.
    [0040] It is another objective of the invention to determine how the total volumetric flow rate of the liquid and gas is changing through the compressor flow path.
    [0041] These and other objectives are achieved by means of a method according to independent claim 1 and an apparatus according to independent claim 5. Advantageous modalities and / or additional alternatives and characteristics are presented in the dependent claims.
    [0042] The following is a detailed description of the present invention with reference to the drawings, in which:
    [0043] Figure 1 illustrates a schematic illustration of the compressor system that includes the main elements of the invention;
    [0044] Figure 2 shows a schematic longitudinal cross-sectional view of the main elements of the flow measurement device;
    [0045] Figure 3 illustrates the measured liquid fraction of a wet gas X a reference value as a function of time;
    [0046] Figure 4 illustrates an illustration of a typical compressor map with operating point, oscillation curve, oscillation region, choke region and control line (safety margin).
    [0047] The present invention relates to a method and apparatus for controlling the operation and performance of a gas compressor 1 when the properties of the gas are unknown or change over time, or when the gas contains liquid. The invention is used to ensure the optimal operation of a compressor system 15 of the type illustrated in Figure 1. A gas containing fluid and liquid is placed in the system 15 through a pipe 11 and optionally enters a cooler 12. A meter flow rate 2 measures the actual volumetric flow rate of the gas and liquid upstream of compressor 1. Fluid pressure and temperature are measured by a fluid pressure and temperature measuring device 3 downstream of compressor 1, while pressure and temperature readings from fluid pressure and temperature measuring devices 4, 3 are sent to flow meter 2. Two different and optional recycling lines are illustrated: an anti-shake line 9 containing an anti-shake valve 5, and a hot gas overflow line containing a hot gas overflow valve 6. Both valves 5 and 6 are connected to flow meter 2, allowing control of the valves directly from the flow meter 2. The fluid entering the compressor system 15 is pressurized by compressor 1 and leaves the compressor system 15 through a check valve 13 and a pipe 14. Flow meter 2 controls the operating point of compressor 1 by measuring the current volumetric flow rate entering compressor 1 and by calculating the pressure ratio derived from measuring devices 3 and 4. For example, if fluid recycling is necessary to ensure stable operation and / or compressor protection 1, flow meter 2 can open the anti-surge valve 5 on the anti-surge line 9, or alternatively open the hot gas overflow valve 6 on the hot gas overflow line 10. The flow measurement 2 may alternatively be installed in the vicinity of the compressor outlet or one or more similar flow measurement devices may be installed in the vicinity of the compressor inlet and outlet. The properties measured from the flow measurement devices are then used to calculate the compressor performance parameters such as a polytropic header (refer to equation 6 below) and polytropic efficiency (refer to equation 12 below). Control lines 7, 8 communicate with a determination / computer and / or control device (Figure 2).
    [0048] An objective of the present invention is to accurately determine the actual flow rate through compressor 1 even in cases where the molecular weight of the gas changes over time or if the gas contains unknown amounts of liquid, be it water or a liquid not aqueous. Such measurements are important in order to accurately determine the density of the working fluid, the molecular weight of the working fluid, and the total volumetric flow rate that includes both the gas phase and the liquid phase.
    [0049] The flow measurement device 2 contains devices for determining the individual fraction of gas, water and non-aqueous liquids, devices for measuring temperature and pressure for compensation purposes, in addition to devices for measuring fluid velocity.
    [0050] The invention also relates to a method for using measured fractions and flow rates for determining the individual flow rates of gas, water and non-aqueous liquids, total fluid density and molecular weight.
    [0051] With reference to Figure 2, the flow measurement device 22 may comprise six main elements as illustrated: a tubular section 16, a device 17 for measuring the speed of the working fluid, a device 18 for measuring the fraction of water of the working fluid, a device 19 for measuring the density of the working fluid, a device 20 for measuring the pressure and temperature of the working fluid. A computer device (computing device) 21 and / or control device receives data from measuring devices 17, 18, 19, 20 in addition to the pressure and temperature data measured by devices 3 and 4 within the compressor system 15 illustrated in Figure 1. Computing devices and control means can be one device or two separate devices. In the case of two separate units or devices, they must be connected and able to communicate with each other. The surge protection algorithm based on the measured total volumetric flow rate and the compressor pressure ratio is implemented in the computer and / or control device 21 which is an integral part of the flow meter. Based on the data received, the computer and / or the control device 21 is determining the fluid composition and is sending data to other control systems that are connected to it. The flow direction can be up or down. The device can also be located horizontally or having any other inclination. The device can be located on the suction or discharge side of the compressor or both sides of the machine.
    [0052] For application of composition dependent compressor control, it is crucial that the accuracy of the liquid fraction measurement is high, and that the flow meter 2 is capable of detecting sudden fluid changes to ensure the safe operation of the machine and control. Figure 3 illustrates examples of performance obtained in a flow laboratory for an actual flow measurement device.
    [0053] Figure 3 is self-explanatory and illustrates the measured liquid fraction (rates) 24 (geometric axis y) of a wet gas X a reference value (a reference liquid rate line) 25 as a function of time ( geometric axis x).
    [0054] The present invention includes a new set of equations used to calculate the performance of the compressor where the main parameters are measured by a flow measurement device 2 as illustrated in Figure 1. Such equations are also valid when the liquid is present in the gas flowing through the machine and are suggested for use for monitoring machine performance.
    [0055] A polytropic header equation that is valid for dry gas and when liquid and gas are mixed at the compressor inlet is introduced as:
    Where

    [0056] Equation (6) is denoted the single fluid model as the densities of various fluids are combined in a volume density of the mixture representing a fluid. The TP subscript used reflects that the equation is also valid for the flow of two phases (mixture of gas and liquid).
    [0057] The volume density of the gas and liquid mixture is represented by:
    AND
    where the empty fraction of each phase is recognized as A

    [0058] Each phase has in equations (8) and (9) a retention area represented by AFΠ occupied in the transversal area of the ACR tube. The subscript F in equation (10) represents the different fluids present, in which case gas (G), condensate (C), non-aqueous (nonA), and water (W). The similar subscript n represents input 1 and output 2. If no slip exists between the different phases (same speed), equation (10) can be based on the volumetric flow rates of different phases:

    [0059] The total volumetric flow rate is represented by Chot in equation (11).
    [0060] The compressor efficiency is then calculated according to:
    where hTP2 (n = 2) and hTPi (n = 1) are defined as:

    [0061] The enthalpy calculation based on equation (13) uses the mass fraction of each phase present in the flow at the input (n = 1) and output (n = 2) of the machine:

    [0062] The mass flow rate is denoted m and the subscript Tot reflects the total flow in equation (14). The subscript F in equation (10) represents the different fluids present, in which case gas (G), condensate (C), non-aqueous (nonA), and water (W).
    [0063] For dry gas only, equations (6) and (7) are identical to equations (3) and (4) respectively since all liquid fractions are equal to zero and do not contribute to the equations. The use of the flow measurement device 2 in Figure 1 ensures that the density of the gas is measured and the molecular weight of the gas is known and, in this way, the calculated work done by the machine is precisely determined. If a flow measurement device 2 is used for both the inlet and outlet side of the compressor, all relevant parameters needed to calculate the compressor header (equations (6) and (7)) can be measured and uncertainties in the known state equations (EOS) and possible changed gas composition are eliminated.
    [0064] Similarly, if the process gas contains water (W), condensed material (C) and / or other non-aqueous liquids (nonA), the calculated header is still valid using equations (6) and ( 7) since all liquid fractions are measured by the flow measurement device 2 in Figure 1. The volume density of the mixture is measured by the flow measurement device 2, measurement of all parameters used in equations (6) and (7), which reduces the uncertainties in the calculation.
    [0065] An objective of the present invention is to prevent oscillation by controlling the recirculation valve or an on / off valve known as a hot gas overflow valve based on a real-time measurement of compressor performance and volumetric flow rate. gas and liquids through the machine.
    [0066] The phenomenon of oscillation in a gas compressor depends on the total volumetric flow rate, pressure ratio, machine condition, and on the composition and molecular weight of the gas.
    [0067] The Yp polytropic header is a function of gas composition through molecular weight, compressibility and compression coefficient and is also a function of the pressure ratio and inlet temperature:

    [0068] The oscillation limit is an experimentally determined curve that refers to the pressure ratio X actual volumetric flow rate at the point where the stop is detected for different compressor rotation speeds. An additional reduction in the volumetric flow rate at that point with a constant speed of rotation will initiate the oscillation: f oscillation curve =
    'alternatively oscillation curve =
    where QTOÍ is the total volumetric flow through the compressor:
    and the liquid flow rate (QL) can be divided into non-aqueous liquid and water:

    [0069] The oscillation line, which is usually defined by the use of differential pressure from a flow measurement device and the pressure ratio through the machine, is not applicable if liquids are present in the gas flow. By using the flow measurement device 2 in Figure 1 the actual volumetric flow rate can be used as an oscillation control parameter together with a pressure ratio as the total volumetric flow rate is measured and, thus, valid for both a dry gas and a mixture consisting of gas and liquid. In case the flow measurement device 2 is used on both the inlet and outlet side of the machine, the polytropic header can be used instead of the pressure ratio in the oscillation control since the density of gas and liquids is measured directly and is not dependent on a temperature measurement that has a slow response when gradients occur.
    [0070] The actual operating point for the gas compressor is defined by the actual polytropic header or the pressure ratio and the actual total flow rate at a given point in time.
    [0071] With reference now to Figure 4, an operating point 31 on a compressor map with an oscillation line 30, and a control line 29 is illustrated. In addition, the geometric axis x 26 illustrates the total volumetric flow rate, the geometric axis y 27 illustrates the pressure ratio through the machine, and the curved line ranges 28 illustrate the constant speed lines. If the pressure ratio at the actual operating point 31 exceeds the swing control line 29 in the left direction, the recirculation valve is opened. The swing control line 29 is provided as the swing line 30 plus a safety margin. The activation of the recirculation valve can be performed directly by the flow meter computer or by an external control system that receives data from the flow meter 2.
    [0072] If the flow measurement device is used on both the inlet and outlet sides of the machine, the liquid fraction can be measured on the inlet and outlet side of the compressor 1. Scaling of the internal parts of the compressor may occur as the liquid evaporates in the machine, and such encrustation can significantly affect the compressor's operating envelope. In this way, the oscillation line can change as the liquid evaporates. According to an embodiment of the present invention, a routine can be incorporated into an anti-sway control logic and provides warning if the liquid fraction results in a short-term degradation by measuring the rates of liquid entering and leaving the machine. Alternatively, a floating control line logic can be implemented to control the machine while the liquid is evaporated through the compressor.
    [0073] If the flow measurement device is used on both the inlet and outlet sides of the machine, the change in fluid density due to the evaporation of the liquid through the compressor can be used to determine the fluid composition.
    [0074] If large amounts of liquid (slug) arrive or appear in the machine during operation, two flow measurement devices can be used upstream of the machine. The distance between these two flow meters should be selected to ensure that sufficient time is available to open the recycling valve 5, referring to Figure 1, or to reduce the compressor operating speed before the liquid slug enters the machine. Such flow measurement devices can be connected to each other to ensure quick response.
    权利要求:
    Claims (10)
    [0001]
    1. Method for protecting against oscillation of a compressor (1) with an inlet side and an outlet side, in which a flow or stream of gas entering the compressor comprises quantities that vary with the time of water and / or liquid not aqueous, by continuous or discontinuous measurement and / or determination of various parameters of fluids passing through said compressor (1), the method comprising the steps of: (a) measuring the temperature on the inlet and / or outlet side of the compressor (1 ); (b) pressure measurement on the inlet and outlet side of the compressor (1) in order to determine a compressor pressure ratio; (c) measuring the mix fluid density on the inlet and / or outlet side of the compressor (1); (d) measurement of the individual volume fractions of gas, water and non-aqueous liquid on the inlet and / or outlet side of the compressor; (e) measurement of fluid velocity on the inlet and / or outlet side of the compressor; (f) determination of individual flow rates of gas, water and non-aqueous liquid based on the measured individual volume fractions of gas, water and non-aqueous liquid and the fluid velocity on the compressor inlet and / or outlet side; (g) based on the individual determined flow rates of gas, water and non-aqueous liquid, the determination of a total volumetric flow rate of the actual fluid mixture of gas and liquid on the compressor inlet and / or outlet side; and (h) based on the determined compressor pressure ratio and total vol-lumetric flow of the actual actual fluid mixture and / or measured temperature and / or density of the fluid mixture measured on the compressor inlet and / or outlet side ( 1) according to steps a to g, control (7,8) a recirculation valve position of at least one recirculation valve (5, 6) disposed between the inlet and outlet side of said compressor (1 ) in order to ensure that the compressor does not enter an oscillation regime.
    [0002]
    Method according to claim 1, in which the compressor performance is determined based on the total density of the measured fluid mixture and determined parameters such as gas composition, gas and liquid properties.
    [0003]
    3. Method according to claim 2, in which the performance of the compressor is determined using a polytropic header equation:
    [0004]
    Method according to one of the preceding claims, in which the gas is recirculated from the outlet side to the inlet side of the compressor (1) when the liquid fraction exceeds a maximum determined value and / or pulsed material sado.
    [0005]
    5. Device for protection against oscillation of a compressor (1), where the flow of incoming gas from the compressor or stream contains varying amounts with the time of water and / or non-aqueous liquid, by continuous or discontinuous measurement and / or determination of various fluid parameters passing through said compressor (1), the apparatus comprising: (a) devices (20) for measuring the temperature on the inlet and / or outlet side of the compressor (1); (b) devices (20) for measuring the pressure on the inlet and outlet side of the compressor (1) in order to determine the pressure ratio of the compressor; (c) devices (19) for measuring the density of fluid mixture on the compressor inlet and / or outlet side (1); (d) devices (18) for measuring individual volume fractions of gas, water and non-aqueous liquid on the inlet and / or outlet side of the compressor; (e) devices (17) for measuring the fluid velocity on the inlet and / or outlet side of the compressor; (f) computing devices (21) for determining individual flow rates of gas, water and non-aqueous liquid based on the measured individual volume fractions of gas, water and non-aqueous liquid and fluid velocity on the inlet side and / or compressor outlet, and for determining a total volumetric flow rate of the actual fluid mixture of gas and liquid on the inlet and / or compressor outlet side based on the individual determined flow rates of the gas, water and non-liquid aqueous; and (g) control devices (7, 8) for controlling the recirculation valve position of at least one recirculation valve (5, 6) disposed between the inlet and outlet side of said compressor (1) in order to guarantee that the compressor does not enter an oscillation regime based on the data of the computing device (21).
    [0006]
    Apparatus according to claim 5, in which the compressor (1) comprises two or more recirculation valves (5, 6).
    [0007]
    Apparatus according to claim 5 or 6, in which the determination and / or control device (21) is located near or in the vicinity of the measuring device (3, 4, 17, 18, 19, 20) .
    [0008]
    Apparatus according to claim 5 or 6, in which the determination and / or control device (21) is located remotely from the measurement device (3, 4, 17, 18, 19, 20).
    [0009]
    Apparatus according to any of claims 5 to 8, in which the computing and determining device and the control device are integrated into a unit or device.
    [0010]
    Apparatus according to any one of claims 5 to 8, in which the computing or determining device and the control device are two separate units or devices communicating with each other.
    类似技术:
    公开号 | 公开日 | 专利标题
    BR112013000694B1|2020-11-17|COMPOSITION METHOD AND APPARATUS BASED ON MONITORING PERFORMANCE OF COMPRESSION CONTROL
    JP3453228B2|2003-10-06|Flow meter for multi-phase fluid flow of high void fraction and its measuring method
    Goto1992|Study of internal flows in a mixed-flow pump impeller at various tip clearances using three-dimensional viscous flow computations
    WO2014194729A1|2014-12-11|Device and method for online measurement of gas-phase flux and liquid-phase flux of moisture in horizontal pipe
    BR112017004986B1|2021-06-15|METHOD FOR INDICATING FUEL CONTAMINATION IN AN ENGINE SYSTEM, AND, GAUGE ELECTRONICS FOR FLOW METERS
    CN103562688A|2014-02-05|Flowmeter for two-phase gas/liquid cryogenic fluids
    BR112016007273B1|2020-12-29|method for determining flows of a mixture of multiple components and device for determining flows of a mixture of multiple components in a pipe
    US10655997B2|2020-05-19|Flowmeter for two-phase fluid with simultaneous or alternating measurement of the gas phase and the liquid phase
    KR101381700B1|2014-04-04|A water gauge
    BR112016007272B1|2021-01-05|method for determining flows of a mixture of multiple components and device for determining flows of a mixture of multiple components in a pipe
    KR101178038B1|2012-08-29|Differential pressure-type mass flow meter with double nozzles
    US10712183B2|2020-07-14|Determining flow rates of multiphase fluids
    Li et al.2017|Mass flowrate measurement of wet steam using combined V-cone and vortex flowmeters
    Goto1990|Study of internal flows in a mixed-flow pump impeller at various tip clearances using 3D viscous flow computations
    Bakken et al.2017|Volute Flow Influence on Wet Gas Compressor Performance
    BR112017028145B1|2021-01-12|determination of the phasic composition of a fluid flow
    Mehlum et al.2020|Experimental analysis of Venturi-tube behavior in wet gas conditions
    CN216081610U|2022-03-18|Precession vortex flowmeter capable of measuring multiphase flow
    CN207485617U|2018-06-12|A kind of water pump serial-connection system with water balance function
    EP3832140A1|2021-06-09|Method for operating a pump, in particular a multiphase pump
    KR101864875B1|2018-06-07|Slurry pump control system and method using slurry concentration measurement
    KR20190132241A|2019-11-27|Compressor and method for controlling the flow rate
    Mark et al.1990|The turbine meter applied to void fraction determination in two-phase flow
    Bakken et al.2019|Wet Gas Compressor Modeling and Performance Scaling
    TOMASZEWSKA-WACH et al.2019|INFLUENCE OF THE ORIFICE SHAPE ON MASS FLOW MEASUREMENTS OF AIR WATER MIXTURE
    同族专利:
    公开号 | 公开日
    CA2804854C|2018-08-14|
    AU2011278293B2|2015-09-10|
    BR112013000694A2|2016-05-17|
    NO20101007A1|2012-01-16|
    WO2012007553A1|2012-01-19|
    GB201300431D0|2013-02-27|
    GB2494835A|2013-03-20|
    NO333438B1|2013-06-03|
    CA2804854A1|2012-01-19|
    AU2011278293A1|2013-01-24|
    GB2494835B|2017-06-28|
    US20170002822A1|2017-01-05|
    US20130170952A1|2013-07-04|
    US9416790B2|2016-08-16|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3292846A|1964-03-30|1966-12-20|Phillips Petroleum Co|Centrifugal compressor operation|
    US3424370A|1967-03-13|1969-01-28|Carrier Corp|Gas compression systems|
    US4156578A|1977-08-02|1979-05-29|Agar Instrumentation Incorporated|Control of centrifugal compressors|
    US4399548A|1981-04-13|1983-08-16|Castleberry Kimberly N|Compressor surge counter|
    IN162594B|1983-10-07|1988-06-18|Babcock & Wilcox Co|
    US4825380A|1987-05-19|1989-04-25|Phillips Petroleum Company|Molecular weight determination for constraint control of a compressor|
    US4971516A|1988-05-04|1990-11-20|Exxon Research & Engineering Company|Surge control in compressors|
    US4949276A|1988-10-26|1990-08-14|Compressor Controls Corp.|Method and apparatus for preventing surge in a dynamic compressor|
    US5508943A|1994-04-07|1996-04-16|Compressor Controls Corporation|Method and apparatus for measuring the distance of a turbocompressor's operating point to the surge limit interface|
    WO1997024591A1|1996-01-02|1997-07-10|Woodward Governor Company|Surge prevention control system for dynamic compressors|
    US5971712A|1996-05-22|1999-10-26|Ingersoll-Rand Company|Method for detecting the occurrence of surge in a centrifugal compressor|
    US5967742A|1997-12-23|1999-10-19|Compressor Controls Corporation|Method and apparatus for preventing surge while taking a turbocompressor off-line from a parallel configuration|
    CA2395613C|1999-12-31|2009-09-15|Shell Canada Limited|Method and system for optimizing the performance of a rotodynamic multi-phase flow booster|
    NO313926B1|2000-11-08|2002-12-23|Abb Research Ltd|Compressor Controls|
    US6917857B2|2000-12-15|2005-07-12|American Standard International Inc.|Magnetically overridden flow control device|
    US6503048B1|2001-08-27|2003-01-07|Compressor Controls Corporation|Method and apparatus for estimating flow in compressors with sidestreams|
    JP4565282B2|2003-04-17|2010-10-20|エーエーエフ−マックウェイインク．|Surge detection method for centrifugal compressor|
    US7094019B1|2004-05-17|2006-08-22|Continuous Control Solutions, Inc.|System and method of surge limit control for turbo compressors|
    NO328277B1|2008-04-21|2010-01-18|Statoil Asa|Gas Compression System|
    AU2009301191B2|2008-10-07|2012-08-23|Shell Internationale Research Maatschappij B.V.|Method of controlling a compressor and apparatus therefor|
    US20120100013A9|2010-05-11|2012-04-26|Krishnan Narayanan|Method of surge protection for a dynamic compressor using a surge parameter|ITBA20110037A1|2011-07-07|2013-01-08|Ind Plant Consultant Srl|METHOD FOR PROTECTION OF CENTRIFUGAL COMPRESSORS FROM THE PUMPING PHENOMENON|
    ITCO20110039A1|2011-09-29|2013-03-30|Nuovo Pignone Spa|SYSTEMS AND METHODS TO DETERMINE A LEVEL OF DIRTY COMPRESSORS|
    CN102878100B|2012-09-21|2014-12-24|西安陕鼓动力股份有限公司|Control method for preventing surging generated during normal halting of single-shaft purified terephthalic acidcompressor unit|
    ITCO20120056A1|2012-11-07|2014-05-08|Nuovo Pignone Srl|METHOD OF OPERATING A COMPRESSOR IN CASE OF MALFUNCTION OF ONE OR MORE SIZES OF MEASUREMENT|
    US9518778B2|2012-12-26|2016-12-13|Praxair Technology, Inc.|Air separation method and apparatus|
    ITFI20130063A1|2013-03-26|2014-09-27|Nuovo Pignone Srl|"METHODS AND SYSTEMS FOR ANTISURGE CONTROL OF TURBO COMPRESSORS WITH SIDE STREAM"|
    WO2014191312A1|2013-05-29|2014-12-04|Siemens Aktiengesellschaft|Method for operating a compressor, and arrangement with a compressor|
    CA2949450C|2014-06-02|2018-11-06|Praxair Technology, Inc.|Air separation system and method|
    CN104389804A|2014-11-20|2015-03-04|哈尔滨广瀚燃气轮机有限公司|Surge protection device|
    RU2724429C2|2015-06-26|2020-06-23|Статойл Петролеум Ас|Determining phase composition of fluid medium flow|
    NO341968B1|2015-10-09|2018-03-05|Fmc Kongsberg Subsea As|Method for controlling liquid content in gas flow to a wet gas compressor|
    IT201600070852A1|2016-07-07|2018-01-07|Nuovo Pignone Tecnologie Srl|COMPRESSOR-FREE PUMPING PROTECTION IN HUMID GAS CONDITIONS|
    IT201600070842A1|2016-07-07|2018-01-07|Nuovo Pignone Tecnologie Srl|METHOD AND ADAPTIVE ANTI-PUMP CONTROL SYSTEM|
    US11143056B2|2016-08-17|2021-10-12|General Electric Company|System and method for gas turbine compressor cleaning|
    US10995746B2|2017-01-17|2021-05-04|Innio Jenbacher Gmbh & Co Og|Two-stage reciprocating compressor optimization control system|
    CN111946651A|2020-08-12|2020-11-17|中国大唐集团科学技术研究院有限公司华东电力试验研究院|Fan stall early warning method and system|
    法律状态:
    2018-12-26| B06F| Objections, documents and/or translations needed after an examination request according art. 34 industrial property law|
    2019-11-19| B06U| Preliminary requirement: requests with searches performed by other patent offices: suspension of the patent application procedure|
    2020-07-14| B09A| Decision: intention to grant|
    2020-11-17| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 14/07/2011, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    NO20101007|2010-07-14|
    NO20101007A|NO333438B1|2010-07-14|2010-07-14|Method and apparatus for composition-based compressor control and performance monitoring.|
    PCT/EP2011/062078|WO2012007553A1|2010-07-14|2011-07-14|A method and apparatus for composition based compressor control and performance monitoring|
    [返回顶部]