A pipeline hydrogen blending compressor regulation method, system, device and medium

Abstract

The present application relates to the technical field of pipeline gas transmission engineering, and discloses a pipeline hydrogen blending compressor regulation method, system, device and medium, through constructing a full-link monitoring and dynamic regulation system covering hydrogen blending characteristics, lubricating oil state and bearing dynamics, effectively solving key problems such as oil film pressure attenuation, rotor stability fluctuation and friction torque imbalance caused by hydrogen blending ratio change; the method can accurately match 0%~30% hydrogen blending conditions, stably maintain the oil film pressure at 13~23MPa, control the rotor displacement within the range of ±30~±90μm, and limit the friction torque fluctuation within 1.5~3Nm, so as to ensure the stability of the compressor operation, reduce the friction power loss by 5%~10% and the bearing wear by 15%, and at the same time, have good engineering realizability and system adaptability.

Description

Technical Field

[0001] This invention relates to the field of pipeline gas transmission engineering technology, and in particular to a pipeline hydrogen blending compressor control method, system, equipment and medium. Background Technology

[0002] With the advancement of clean energy strategies, hydrogen-blended natural gas (HCNG) has become an important pathway for the large-scale application of hydrogen energy due to its advantages of "low-carbon transportation + reuse of existing pipeline networks". As the core pressurization equipment in the HCNG transportation system, the centrifugal compressor's operational stability directly determines the pipeline transportation efficiency and safety.

[0003] The sliding bearing of a compressor is a key component ensuring stable rotor operation: it bears load and reduces friction through the lubricating oil film between the journal and the bearing. However, the introduction of hydrogen alters the flow field characteristics of natural gas, thereby affecting the fluid pressure on the compressor rotor surface (the bearing external load amplitude changes significantly when the hydrogen content increases from 0% to 30%). Simultaneously, an increased hydrogen content indirectly affects the working environment of the lubricating oil, leading to the following problems with the sliding bearing: 1. Oil film pressure decay: Simulation results show that for every 5% increase in hydrogen doping ratio, the maximum oil film pressure of the sliding bearing decreases by an average of 0.8-1.2 MPa (e.g., the oil film pressure at a 90° rotation angle is 21.9 MPa without hydrogen doping, but drops to 13.65 MPa with 30% hydrogen doping). The oil film load-bearing capacity decreases, which can easily lead to micro-protrusion contact and aggravate bearing wear. 2. Rotor stability fluctuations: Decreased lubricating oil viscosity (e.g., viscosity at reference temperature drops from 40 mPa). s dropped to 10 mPa s) will increase the displacement range of the rotor in the y / z direction from ±34μm to ±88μm, while increasing the hydrogen doping ratio will reduce the displacement range. The coupling of the two causes the rotor vibration amplitude to fluctuate. 3. Frictional torque imbalance: The frictional torque fluctuation is minimal when the hydrogen doping ratio is 10% (ΔM≈1N). m), but the fluctuation amplitude increases to 3N after the proportion exceeds 20%. Above a certain value (m), frictional power loss increases, and compressor efficiency decreases.

[0004] Existing compressor control methods are mostly designed for pure natural gas operation, without considering the coupling effect of hydrogen blending ratio and lubricating oil characteristics. They lack dynamic threshold setting and precise control methods, which makes the compressor prone to "instability-shutdown" risk when the hydrogen blending ratio fluctuates, thus restricting the continuous operation of hydrogen-blended natural gas transmission systems. Summary of the Invention

[0005] This invention provides a method, system, equipment, and medium for regulating a pipeline hydrogen-blended compressor, in order to overcome the deficiencies of the prior art.

[0006] This invention provides a method for regulating a pipeline hydrogen-blending compressor, comprising: S1. To address the issue of uncontrolled compressors, establish a full-link monitoring system covering hydrogen doping characteristics, lubricating oil status, and bearing dynamics. S2. Based on the full-link monitoring system, a dynamic control threshold system is set up; S3. Obtain real-time parameter data of the compressor to be controlled through the full-link monitoring system; S4. Based on the real-time parameter data of the compressor to be controlled, the adaptive control of the compressor to be controlled is achieved by using a dynamic control threshold system. S5. Repeat steps S3 and S4 at regular intervals.

[0007] According to the present invention, a pipeline hydrogen-blended compressor control method includes a full-link monitoring system comprising a hydrogen blending characteristic monitoring unit, a lubricating oil condition monitoring unit, and a bearing dynamics monitoring unit. The hydrogen blending characteristic monitoring unit is used to monitor the hydrogen blending ratio γ (volume fraction), the lubricating oil condition monitoring unit is used to monitor the reference temperature T_ref and the lubricating oil viscosity η_ref, and the bearing dynamics monitoring unit is used to monitor the maximum oil film pressure p_max, the rotor shaft displacement (y_dis, z_dis), and the friction torque M_f.

[0008] According to the present invention, a pipeline hydrogen-blending compressor control method, step S2 includes: A dynamic control threshold system is set based on the coupled operating conditions of hydrogen doping ratio and lubricating oil viscosity. The threshold values ​​for each parameter must meet the following conditions: maximum oil film pressure ≥ cavitation pressure (101325 Pa), rotor shaft displacement ≤ bearing radius clearance (120 μm), and friction torque fluctuation ≤ 3 N. m.

[0009] According to the present invention, a pipeline hydrogen-doped compressor control method includes a dynamic control threshold system comprising: When the hydrogen doping ratio γ is in the range [0, 10%], the lubricating oil viscosity η_ref is at 40 mPa. At a reference temperature of s (T_ref = 30℃), the maximum oil film pressure threshold is 20MPa, the rotor shaft displacement threshold is ±35μm, and the friction torque fluctuation threshold is 2.0N. m; When the hydrogen doping ratio γ is in the range [0, 10%], the lubricating oil viscosity η_ref is at 20 mPa. At reference temperature T_ref = 40℃, the maximum oil film pressure threshold is 18MPa, the rotor shaft displacement threshold is ±65μm, and the friction torque fluctuation threshold is 1.5N. m; When the hydrogen doping ratio γ is in the range (10%, 20%), the lubricating oil viscosity η_ref is at 40 mPa. At a reference temperature of s (T_ref = 30℃), the maximum oil film pressure threshold is 18MPa, the rotor shaft displacement threshold is ±32μm, and the friction torque fluctuation threshold is 2.5N. m; When the hydrogen doping ratio γ is in the range (10%, 20%), the lubricating oil viscosity η_ref is at 20 mPa. At a reference temperature of s (T_ref = 40℃), the maximum oil film pressure threshold is 16MPa, the rotor shaft displacement threshold is ±62μm, and the friction torque fluctuation threshold is 2N. m; When the hydrogen doping ratio γ is in the range (20%, 30%), the lubricating oil viscosity η_ref is at 40 mPa. At reference temperature T_ref = 30℃, the maximum oil film pressure threshold is 15MPa, the rotor shaft displacement threshold is ±30μm, and the friction torque fluctuation threshold is 3.0N. m; When the hydrogen doping ratio γ is in the range (20%, 30%), the lubricating oil viscosity η_ref is within 10 mPa. At reference temperature T_ref = 50℃, the maximum oil film pressure threshold is 13MPa, the rotor shaft displacement threshold is ±90μm, and the friction torque fluctuation threshold is 1.8N. m.

[0010] According to the present invention, a pipeline hydrogen-blending compressor control method includes step S3 as follows: Based on real-time parameter data, derived parameter data is obtained, including lubricating oil viscosity correlation and friction torque fluctuation.

[0011] According to the present invention, a pipeline hydrogen-blending compressor control method is provided, wherein obtaining derived parameter data based on real-time parameter data includes: Based on the viscosity-temperature coefficient, the relationship between the lubricating oil viscosity η_ref and the monitoring reference temperature T_ref is established, which is the lubricating oil viscosity correlation. The expression for the lubricating oil viscosity correlation is: η_ref = η_T0×exp(-α_T×(T_ref - T0)), where α_T represents the viscosity-temperature coefficient.

[0012] According to the present invention, a pipeline hydrogen-blending compressor control method is provided, wherein obtaining derived parameter data based on real-time parameter data includes: The difference between the maximum and minimum values ​​of the friction torque M_f within one crankshaft rotation period (360°) is calculated to obtain the friction torque fluctuation ΔM. The expression for the friction torque fluctuation ΔM is: ΔM = M_f (max) - M_f (min).

[0013] According to the present invention, a pipeline hydrogen-blending compressor control method includes step S4 as follows: Based on the deviation between real-time parameter data and the dynamic control threshold system, and according to preset priorities, adaptive control measures are implemented for the compressor to be controlled. The preset priority is as follows: oil film pressure regulation takes precedence over rotor shaft displacement regulation, and rotor shaft displacement regulation takes precedence over friction torque fluctuation regulation. Among them, oil film pressure regulation includes increasing the lubricating oil temperature and reducing the lubricating oil viscosity, thereby increasing the monitored maximum oil film pressure; Rotor shaft displacement control includes adjusting the compressor speed and reducing the displacement range by decreasing centrifugal force; Friction torque fluctuation control includes increasing the supply of lubricating oil and supplementing the oil film thickness to reduce micro-protrusion contact and reduce friction torque fluctuation.

[0014] The present invention also provides a pipeline hydrogen-blending compressor control system, comprising: The end-to-end monitoring system construction module is used to perform step S1: for the compressor to be controlled, build an end-to-end monitoring system covering hydrogen doping characteristics, lubricating oil status and bearing dynamics; The dynamic control threshold system setting module is used to execute step S2: setting a dynamic control threshold system based on the full-link monitoring system; The real-time parameter data acquisition module is used to perform step S3: obtain the real-time parameter data of the compressor to be controlled through the full-link monitoring system; The adaptive control module is used to execute step S4: based on the real-time parameter data of the compressor to be controlled, the adaptive control of the compressor to be controlled is achieved using a dynamic control threshold system. The loop execution module is used to repeatedly execute steps S3 and S4 at regular intervals.

[0015] The present invention also provides an electronic device, including a processor and a memory storing a computer program, wherein the processor executes the computer program to implement any of the above-described pipeline hydrogen-blending compressor control methods.

[0016] The present invention also provides a non-transitory computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements any of the above-described pipeline hydrogen-blending compressor control methods.

[0017] The present invention also provides a computer program product, the computer program product comprising a computer program that can be stored on a non-transitory computer-readable storage medium, and when the computer program is executed by a processor, the computer is able to execute any of the above-described pipeline hydrogen-blending compressor control methods.

[0018] The present invention provides a method, system, equipment, and medium for regulating a pipeline hydrogen-blending compressor, which can bring at least the following beneficial effects: Based on the correlation between "hydrogen doping ratio, lubricating oil viscosity, and bearing dynamic parameters", a dynamic control threshold system is constructed to overcome the control lag problem of traditional fixed thresholds when the hydrogen doping ratio changes. It can adapt to the full range of hydrogen doping conditions from 0% to 30%, ensuring that the compressor can achieve accurate and rapid response under different hydrogen doping conditions.

[0019] By dynamically adjusting the pressure, the maximum oil film pressure is kept stable within the range of 13~23MPa, effectively preventing oil film rupture and contact with micro-protrusions. At the same time, the rotor displacement is controlled within the range of ±30~±90μm (120μm lower than the bearing radius clearance), and the compressor vibration amplitude is suppressed to below 0.1mm / s, significantly reducing the risk of "instability-shutdown" caused by hydrogen doping fluctuations.

[0020] The frictional torque fluctuation range should be controlled within 1.5~3N. m, frictional power loss is reduced by 5%~10%; combined with the effective maintenance of oil film load-bearing capacity, the contact frequency of micro-protrusions is significantly reduced, and the bearing wear is reduced by about 15%, thereby extending the service life of key components and improving the overall operating efficiency of the system.

[0021] The end-to-end monitoring system can use sensors and actuators that are all mature industrial-grade products, without the need for additional hardware development. It is easy to deploy and integrate into existing compressor systems, and has good engineering feasibility and promotion prospects. Attached Figure Description

[0022] To more clearly illustrate the technical solutions in this invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0023] Figure 1 This is a schematic flowchart of a pipeline hydrogen-infused compressor control method provided by the present invention.

[0024] Figure 2 This is a schematic diagram of a pipeline hydrogen-blending compressor control system provided by the present invention.

[0025] Figure 3 This is a schematic diagram of the structure of the electronic device provided by the present invention. Detailed Implementation

[0026] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, embodiments of this invention, and should not be construed as limiting the invention. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without creative effort are within the scope of protection of this invention. In the description of this invention, it should be understood that the terminology used is for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0027] Figure 1 This is a schematic flowchart illustrating a pipeline hydrogen-blending compressor control method provided by the present invention. The executing entity of the pipeline hydrogen-blending compressor control method provided by the present invention can be any applicable terminal-side device or network-side device, such as a pipeline hydrogen-blending compressor control device.

[0028] See Figure 1 The present invention provides a method for regulating a pipeline hydrogen-blending compressor, which may include: S1. For compressors requiring special control, establish a full-link monitoring system covering hydrogen doping characteristics, lubricating oil status, and bearing dynamics.

[0029] In one embodiment, the end-to-end monitoring system includes a hydrogen doping characteristic monitoring unit, a lubricating oil condition monitoring unit, and a bearing dynamics monitoring unit. The hydrogen doping characteristic monitoring unit is used to monitor the hydrogen doping ratio γ (volume fraction), the lubricating oil condition monitoring unit is used to monitor the reference temperature T_ref and the lubricating oil viscosity η_ref, and the bearing dynamics monitoring unit is used to monitor the maximum oil film pressure p_max, the rotor shaft displacement (y_dis, z_dis), and the friction torque M_f.

[0030] The units and functions of the end-to-end monitoring system in this embodiment are shown in Table 1.

[0031] Table 1

[0032] S2. Based on the full-link monitoring system, a dynamic control threshold system is set up.

[0033] In one embodiment, S2 sets a dynamic control threshold system based on the coupled operating condition of hydrogen doping ratio and lubricating oil viscosity. The threshold values ​​for each parameter must meet the following conditions: maximum oil film pressure ≥ cavitation pressure (101325 Pa), rotor shaft displacement ≤ bearing radius clearance (120 μm), and friction torque fluctuation ≤ 3 N. m.

[0034] The dynamic control threshold system of this embodiment is shown in Table 2.

[0035] Table 2

[0036] Note: The threshold is set based on simulation results, such as η=40mPa without hydrogen doping. At time s, p_max = 21.9 - 23.1 MPa, therefore the p_max threshold is set to 20 MPa; with 15% hydrogen doping, η = 40 mPa. When s, p_max = 18.4-18.8 MPa, so the threshold is set to 18 MPa.

[0037] S3. Obtain real-time parameter data of the compressor to be controlled through the full-link monitoring system.

[0038] In one embodiment, S3 can obtain derived parameter data based on real-time parameter data, wherein the derived parameters include lubricating oil viscosity correlation and friction torque fluctuation.

[0039] This embodiment establishes the relationship between lubricating oil viscosity η_ref and monitoring reference temperature T_ref based on a preset viscosity-temperature coefficient, which is called lubricating oil viscosity correlation. The expression for lubricating oil viscosity correlation is: η_ref = η_T0×exp(-α_T×(T_ref - T0)), where α_T represents the viscosity-temperature coefficient.

[0040] In this embodiment, the difference between the maximum and minimum values ​​of the friction torque M_f within one crankshaft rotation period (360°) is calculated to obtain the friction torque fluctuation ΔM. The expression for the friction torque fluctuation ΔM is: ΔM = M_f (max) - M_f (min).

[0041] S4. Based on the real-time parameter data of the compressor to be controlled, the adaptive control of the compressor to be controlled is achieved by using a dynamic control threshold system.

[0042] In one embodiment, S4 performs adaptive control measures on the compressor to be controlled based on the deviation between real-time parameter data and the dynamic control threshold system and according to a preset priority. The preset priority is: oil film pressure control takes precedence over rotor shaft displacement control, and rotor shaft displacement control takes precedence over friction torque fluctuation control.

[0043] Among them, oil film pressure regulation (p_max < threshold): Based on the principle that "the lower the viscosity, the greater the maximum oil film pressure," this embodiment increases the lubricating oil temperature to reduce η_ref, thereby increasing p_max. The target viscosity η_target is calculated as follows: η_target = η_T0 × exp(-α_T × (T_ref(target) - T0)) Wherein, T_ref (target) is the target temperature that makes p_max reach the threshold, which is calculated by the PLC and then used to control the lubricating oil heating / cooling device (temperature control accuracy ±1℃).

[0044] Example: γ=15%, η_ref=40mPa When s and p_max = 17 MPa (< 18 MPa), set η_target = 35 mPa. s, the reverse calculation yields T_ref (target) = 33℃, the control heating device raises the oil temperature from 30℃ to 33℃, and after 10s p_max rises back to 18.2MPa.

[0045] Among them, rotor displacement control (|y_dis| / |z_dis|>threshold): Adjust the compressor speed (original speed n=4800r / min, corresponding to a rotation frequency of 80Hz) to reduce the displacement range by decreasing the centrifugal force.

[0046] Example: γ=25%, η_ref=10mPa When s and y_dis = 92μm (> ±90μm), the variable frequency drive is controlled to reduce the speed to 4500r / min (f=75Hz), and after 5s, y_dis drops to 86μm.

[0047] Among them, friction torque fluctuation control (ΔM > threshold): Increase the supply of lubricating oil (original flow rate Q=30L / min) to supplement the oil film thickness to reduce micro-protrusion contact (1.2) and reduce M_f fluctuation.

[0048] Example: γ=20%, η_ref=20mPa s, ΔM = 2.3N m (>2.0N) When the flow rate is increased to 31.5 L / min, the variable pump is controlled to increase the flow rate to 31.5 L / min. After 8 seconds, ΔM drops to 1.9 N. m.

[0049] S5. Repeat steps S3 and S4 at regular intervals to form a closed loop of "monitoring-analysis-control" to ensure that the compressor is always in a stable operating condition when the hydrogen blending ratio changes dynamically.

[0050] In one embodiment, a software and hardware integrated end-to-end monitoring system can be built for the compressor to be controlled. The monitoring hardware in the end-to-end monitoring system monitors the data of the compressor to be controlled, and then the control software processes the data according to the real-time data and the preset control system, and then issues control commands to the compressor to be controlled. The end-to-end monitoring system can communicate directly with the control system of the compressor to be controlled through software. When the end-to-end monitoring system issues control commands to the compressor to be controlled, the compressor to be controlled performs adaptive control according to the control commands.

[0051] The following specific embodiment illustrates the pipeline hydrogen-blending compressor control method provided by the present invention.

[0052] (I) System Setup 1. Hardware configuration: Hydrogen doping ratio monitoring: Gas chromatograph (model GC-2014); Lubricating oil monitoring: viscosity sensor (model SV-10) + platinum resistance temperature sensor (PT100); Dynamic monitoring: miniature pressure sensor (model Kulite XCQ-062), eddy current displacement sensor (model KD2306), torque sensor (model JN338); Control and execution: PLC (Siemens S7-1200), electric heater (power 5kW), cooling coil (flow rate 10L / min), variable frequency drive (model ACS510), variable lubricating oil pump (model PV2R12).

[0053] 2. Software Configuration: The threshold system and control algorithm (such as viscosity-temperature inverse calculation formula) of Table 2 are pre-stored in the PLC, and the parameters are displayed in real time and manually intervened through the touch screen.

[0054] (II) Implementation Steps 1. Initialization: Set the compressor's basic parameters (journal diameter 102mm, bearing radius clearance 120μm, rotor mass 39.77kg, see document table 1), initial speed 4800r / min, initial lubricating oil temperature 30℃, flow rate 30L / min; 2. Threshold entry: Enter the threshold values ​​from Table 1 into the PLC and set the parameter acquisition frequency to 1Hz; 3. Dynamic control test: Stage 1 (γ=5%, η_ref=40mPa) s): Data collected: p_max = 21.5 MPa, y_dis = 32 μm, ΔM = 1.8 N m are all within the threshold and do not require adjustment; Stage 2 (γ=15%, η_ref=40mPa) s): p_max drops to 17.5MPa (<18MPa), the PLC calculates the target oil temperature as 33℃, controls the heater to heat up, and after 10s p_max=18.2MPa; Stage 3 (γ=25%, η_ref=10mPa) s): y_dis=92μm (>±90μm), PLC controlled the speed to drop to 4500r / min, after 5s y_dis=86μm; Stage 4 (γ=20%, η_ref=20mPa) s): ΔM = 2.3N m (>2.0N) The PLC controlled the oil pump flow rate to increase to 31.5 L / min, and after 8 seconds, ΔM = 1.9 N. m.

[0055] (III) Effect Verification After 72 hours of continuous operation, the hydrogen doping ratio fluctuated randomly between 0% and 30%. Monitoring results showed that: Maximum oil film pressure: 13.2-22.8 MPa (all ≥ threshold); Rotor displacement: y direction -86 to +85μm, z direction -85 to +86μm (both ≤ threshold); Frictional torque fluctuation: 1.4-2.9N m (all ≤ threshold); Compressor efficiency: stable at 88%-92% (90% efficiency in pure natural gas operation, still reaching 88% when hydrogen is added at 30%).

[0056] The pipeline hydrogen-blending compressor control method provided by this invention has the following advantages: Based on the end-to-end monitoring and coupling relationship of "hydrogen doping ratio - lubricating oil viscosity - bearing dynamic parameters", a dynamic control system with intervals and thresholds is constructed, covering hydrogen doping ratios of 0%–30% and 10–40 mPa. The viscosity range of s effectively solves the problems of lag and mismatch in the control of traditional fixed threshold under hydrogen doping fluctuations.

[0057] By prioritizing oil film pressure and then rotor displacement, the maximum oil film pressure is maintained at 13–23 MPa (always higher than the cavitation pressure of 101325 Pa), the rotor displacement is controlled within ±30–±90 μm (lower than the bearing radius clearance of 120 μm), and the vibration amplitude is <0.1 mm / s. This system avoids oil film rupture and rotor collision, ensuring continuous and reliable operation.

[0058] While ensuring safety and stability, the fluctuation range of frictional torque should be controlled within 1.5–3N. m, frictional power loss is reduced by 5%–10%; combined with the effective maintenance of oil film load-bearing capacity, micro-protrusion contact is significantly reduced, bearing wear is reduced by about 15%, and overall energy efficiency and lifespan are improved simultaneously.

[0059] The sensors used (such as gas chromatographs, miniature pressure sensors, and eddy current displacement sensors) are all mature industrial-grade products, with complete monitoring parameter combinations and well-defined accuracy; the control algorithm is based on publicly available parameters (such as a viscosity-temperature coefficient of 0.04℃). - ¹) With simulation calibration thresholds, no additional hardware development is required, making it easy to deploy quickly in existing compressor systems.

[0060] The pipeline hydrogen-blending compressor control system provided by the present invention is described below. The pipeline hydrogen-blending compressor control system described below can be referred to in correspondence with the pipeline hydrogen-blending compressor control method described above.

[0061] See Figure 2 The present invention provides a pipeline hydrogen-blending compressor control system, which may include: The end-to-end monitoring system construction module is used to perform step S1: for the compressor to be controlled, build an end-to-end monitoring system covering hydrogen doping characteristics, lubricating oil status and bearing dynamics; The dynamic control threshold system setting module is used to execute step S2: setting a dynamic control threshold system based on the full-link monitoring system; The real-time parameter data acquisition module is used to perform step S3: obtain the real-time parameter data of the compressor to be controlled through the full-link monitoring system; The adaptive control module is used to execute step S4: based on the real-time parameter data of the compressor to be controlled, the adaptive control of the compressor to be controlled is achieved using a dynamic control threshold system. The loop execution module is used to repeatedly execute steps S3 and S4 at regular intervals.

[0062] Figure 3 An example is a schematic diagram of the physical structure of an electronic device, such as... Figure 3As shown, the electronic device may include a processor 810, a communications interface 820, a memory 830, and a communication bus 840, wherein the processor 810, the communications interface 820, and the memory 830 communicate with each other via the communication bus 840. The processor 810 can call logical instructions in the memory 830 to execute the following steps: S1. To address the issue of uncontrolled compressors, establish a full-link monitoring system covering hydrogen doping characteristics, lubricating oil status, and bearing dynamics. S2. Based on the full-link monitoring system, a dynamic control threshold system is set up; S3. Obtain real-time parameter data of the compressor to be controlled through the full-link monitoring system; S4. Based on the real-time parameter data of the compressor to be controlled, the adaptive control of the compressor to be controlled is achieved by using a dynamic control threshold system. S5. Repeat steps S3 and S4 at regular intervals.

[0063] Furthermore, the logical instructions in the aforementioned memory 830 can be implemented as software functional units and, when sold or used as independent products, can be stored in a computer-readable storage medium. Based on this understanding, the technical solution of the present invention, essentially, or the part that contributes to the prior art, or a part of the technical solution, can be embodied in the form of a software product. This computer software product is stored in a storage medium and includes several instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) to execute all or part of the steps of the methods described in the various embodiments of the present invention. The aforementioned storage medium includes various media capable of storing program code, such as USB flash drives, portable hard drives, read-only memory (ROM), random access memory (RAM), magnetic disks, or optical disks.

[0064] On the other hand, the present invention also provides a computer program product, the computer program product comprising a computer program, the computer program being able to be stored on a non-transitory computer-readable storage medium, and the computer program being executed by a processor, enabling the computer to perform the following steps: S1. To address the issue of uncontrolled compressors, establish a full-link monitoring system covering hydrogen doping characteristics, lubricating oil status, and bearing dynamics. S2. Based on the full-link monitoring system, a dynamic control threshold system is set up; S3. Obtain real-time parameter data of the compressor to be controlled through the full-link monitoring system; S4. Based on the real-time parameter data of the compressor to be controlled, the adaptive control of the compressor to be controlled is achieved by using a dynamic control threshold system. S5. Repeat steps S3 and S4 at regular intervals.

[0065] In another aspect, the present invention also provides a non-transitory computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, performs the following steps: S1. To address the issue of uncontrolled compressors, establish a full-link monitoring system covering hydrogen doping characteristics, lubricating oil status, and bearing dynamics. S2. Based on the full-link monitoring system, a dynamic control threshold system is set up; S3. Obtain real-time parameter data of the compressor to be controlled through the full-link monitoring system; S4. Based on the real-time parameter data of the compressor to be controlled, the adaptive control of the compressor to be controlled is achieved by using a dynamic control threshold system. S5. Repeat steps S3 and S4 at regular intervals.

[0066] The device embodiments described above are merely illustrative. The units described as separate components may or may not be physically separate. The components shown as units may or may not be physical units; that is, they may be located in one place or distributed across multiple network units. Some or all of the modules can be selected to achieve the purpose of this embodiment according to actual needs. Those skilled in the art can understand and implement this without any creative effort.

[0067] Through the above description of the embodiments, those skilled in the art can clearly understand that each embodiment can be implemented by means of software plus necessary general-purpose hardware platforms, and of course, it can also be implemented by hardware. Based on this understanding, the above technical solutions, in essence or the part that contributes to the prior art, can be embodied in the form of a software product. This computer software product can be stored in a computer-readable storage medium, such as ROM / RAM, magnetic disk, optical disk, etc., and includes several instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) to execute the methods described in the various embodiments or some parts of the embodiments.

[0068] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A method for regulating a pipeline hydrogen-blending compressor, characterized in that, include: S1. To address the issue of uncontrolled compressors, establish a full-link monitoring system covering hydrogen doping characteristics, lubricating oil status, and bearing dynamics. S2. Based on the full-link monitoring system, a dynamic control threshold system is set up; S3. Obtain real-time parameter data of the compressor to be controlled through the full-link monitoring system; S4. Based on the real-time parameter data of the compressor to be controlled, the adaptive control of the compressor to be controlled is achieved by using a dynamic control threshold system. S5. Repeat steps S3 and S4 at regular intervals.

2. The pipeline hydrogen-blending compressor control method according to claim 1, characterized in that, The end-to-end monitoring system includes a hydrogen doping characteristic monitoring unit, a lubricating oil condition monitoring unit, and a bearing dynamics monitoring unit. The hydrogen doping characteristic monitoring unit is used to monitor the hydrogen doping ratio γ, the lubricating oil condition monitoring unit is used to monitor the reference temperature T_ref and the lubricating oil viscosity η_ref, and the bearing dynamics monitoring unit is used to monitor the maximum oil film pressure p_max, the rotor shaft displacement y_dis / z_dis, and the friction torque M_f.

3. The pipeline hydrogen-blending compressor control method according to claim 2, characterized in that, Step S2 includes: A dynamic control threshold system is set up based on the coupled operating conditions of hydrogen doping ratio and lubricating oil viscosity. The threshold values ​​for each parameter must meet the following conditions: maximum oil film pressure ≥ cavitation pressure, rotor shaft displacement ≤ bearing radius clearance, and friction torque fluctuation ≤ 3N. m.

4. The pipeline hydrogen-blending compressor control method according to claim 3, characterized in that, The dynamic control threshold system includes: When the hydrogen doping ratio γ is in the range [0, 10%], the lubricating oil viscosity η_ref is at 40 mPa. When the reference temperature T_ref = 30℃, the maximum oil film pressure threshold is 20MPa, the rotor shaft displacement threshold is ±35μm, and the friction torque fluctuation threshold is 2.0N. m; When the hydrogen doping ratio γ is in the range [0, 10%], the lubricating oil viscosity η_ref is at 20 mPa. When the reference temperature T_ref = 40℃, the maximum oil film pressure threshold is 18MPa, the rotor shaft displacement threshold is ±65μm, and the friction torque fluctuation threshold is 1.5N. m; When the hydrogen doping ratio γ is in the range (10%, 20%), the lubricating oil viscosity η_ref is at 40 mPa. When s and / or the monitoring reference temperature T_ref = 30℃, the maximum oil film pressure threshold is 18MPa, the rotor shaft displacement threshold is ±32μm, and the friction torque fluctuation threshold is 2.5N. m; When the hydrogen doping ratio γ is in the range (10%, 20%), the lubricating oil viscosity η_ref is at 20 mPa. When the reference temperature T_ref = 40℃, the maximum oil film pressure threshold is 16MPa, the rotor shaft displacement threshold is ±62μm, and the friction torque fluctuation threshold is 2N. m; When the hydrogen doping ratio γ is in the range (20%, 30%), the lubricating oil viscosity η_ref is at 40 mPa. When the reference temperature T_ref = 30℃, the maximum oil film pressure threshold is 15MPa, the rotor shaft displacement threshold is ±30μm, and the friction torque fluctuation threshold is 3.0N. m; When the hydrogen doping ratio γ is in the range (20%, 30%), the lubricating oil viscosity η_ref is within 10 mPa. When s and / or the monitoring reference temperature T_ref = 50℃, the maximum oil film pressure threshold is 13MPa, the rotor shaft displacement threshold is ±90μm, and the friction torque fluctuation threshold is 1.8N. m.

5. The pipeline hydrogen-blending compressor control method according to claim 4, characterized in that, Step S3 includes: Based on real-time parameter data, derived parameter data is obtained, including lubricating oil viscosity correlation and friction torque fluctuation.

6. The pipeline hydrogen-blending compressor control method according to claim 5, characterized in that, The process of obtaining derived parameter data based on real-time parameter data includes: Based on the viscosity-temperature coefficient, the relationship between the lubricating oil viscosity η_ref and the monitoring reference temperature T_ref is established, which is the lubricating oil viscosity correlation. The expression for the lubricating oil viscosity correlation is: η_ref = η_T0×exp(-α_T×(T_ref - T0)), where α_T represents the viscosity-temperature coefficient. The difference between the maximum and minimum values ​​of the friction torque M_f within one crankshaft rotation period is calculated to obtain the friction torque fluctuation ΔM. The expression for the friction torque fluctuation ΔM is: ΔM = M_f(max) - M_f(min).

7. The pipeline hydrogen-blending compressor control method according to any one of claims 1-6, characterized in that, Step S4 includes: Based on the deviation between real-time parameter data and the dynamic control threshold system, and according to preset priorities, adaptive control measures are implemented for the compressor to be controlled. The preset priority is as follows: oil film pressure regulation takes precedence over rotor shaft displacement regulation, and rotor shaft displacement regulation takes precedence over friction torque fluctuation regulation. Among them, oil film pressure regulation includes increasing the lubricating oil temperature and reducing the lubricating oil viscosity, thereby increasing the monitored maximum oil film pressure; Rotor shaft displacement control includes adjusting the compressor speed and reducing the displacement range by decreasing centrifugal force; Friction torque fluctuation control includes increasing the supply of lubricating oil and supplementing the oil film thickness to reduce micro-protrusion contact and reduce friction torque fluctuation.

8. A pipeline hydrogen-blending compressor control system, characterized in that, include: The end-to-end monitoring system construction module is used to perform step S1: for the compressor to be controlled, build an end-to-end monitoring system covering hydrogen doping characteristics, lubricating oil status and bearing dynamics; The dynamic control threshold system setting module is used to execute step S2: setting a dynamic control threshold system based on the full-link monitoring system; The real-time parameter data acquisition module is used to perform step S3: obtain the real-time parameter data of the compressor to be controlled through the full-link monitoring system; The adaptive control module is used to execute step S4: based on the real-time parameter data of the compressor to be controlled, the adaptive control of the compressor to be controlled is achieved using a dynamic control threshold system. The loop execution module is used to repeatedly execute steps S3 and S4 at regular intervals.

9. An electronic device comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, characterized in that, When the processor executes the program, it implements the pipeline hydrogen-blending compressor control method as described in any one of claims 1 to 7.

10. A non-transitory computer-readable storage medium having a computer program stored thereon, characterized in that, When the computer program is executed by the processor, it implements the pipeline hydrogen-blending compressor control method as described in any one of claims 1 to 7.

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