Exhaust gas residual pressure utilization device and working method thereof

Abstract

The present invention discloses a waste gas excess pressure utilization device and a working method thereof, which relate to the technical field of excess pressure utilization and recovery with multiple gas sources and multiple working conditions. The present invention comprises two fermentation tanks and a machine body, a washing tower is provided on one side of the two fermentation tanks, an exhaust pipe is connected on one side of the washing tower, and a shell is fixedly connected on one side of the exhaust pipe, a nozzle part is provided in the shell, an internal chamber of the unit is provided on one side of the shell, a generator is provided on one side of the shell, and impeller blades are electrically fused and connected on one side of the generator, one side of the impeller blades is movably fitted with the nozzle part, and air intake guide ports are symmetrically provided on the outer surface and upper side of the machine body. The waste gas excess pressure utilization device and the working method thereof provided by the present invention solve the problems of cross-talk among multiple gas sources and low efficiency of variable working conditions by introducing tail gases from multiple gas sources into independent air chambers respectively and using nozzle parts to realize the conversion of pressure energy into mechanical energy.

Description

Technical Field

[0001] The present invention relates to the technical field of waste gas waste pressure utilization and recovery in multiple gas sources and multiple working conditions, and is particularly applicable to situations where backflow and cross-flow prevention are required. The present invention relates to a waste gas waste pressure utilization device and a working method thereof. Background Art

[0002] In some applications where there is a large amount of pressurized exhaust gas being discharged and the residual pressure is being utilized, the discharge locations are relatively dispersed, that is, there are multiple gas sources with different pressures, flow rates, and even discharge continuity, and there are also requirements to prevent backflow and cross-gas. A typical pressurized exhaust gas discharge environment is the fermentation process, where each fermentation tank has pressurized exhaust gas and each fermentation tank can be regarded as an independent gas source.

[0003] Due to the varying pressures and flow rates of the gas sources, the continuity of the discharge varies, and there is a requirement that gases cannot be diverted or cross-contaminated. Therefore, fermenter discharge is typically divided into two scenarios: individual discharge. The second scenario involves converging the gases into a single main pipe, but to ensure sufficiently low pressure after converging (the main pipe pressure must be lower than the minimum pressure of each gas source to prevent gas backflow when the gas source is not vented or the pressure is low), this is particularly true in the fermentation production of pharmaceutical raw materials with very strict microbial contamination requirements, such as amino acid fermentation, where cross-contamination and backflow must be avoided.

[0004] This requirement for return air cross-flow is very strict. For multiple gas sources with variable exhaust emissions under various working conditions, the residual pressure utilization cannot simply collect adjacent gas sources into the main pipe and then pass them into the residual pressure utilization unit to perform work. Because the prerequisite for the main pipe to enter the residual pressure utilization unit to perform work is that the pressure before work is very high, which means that the main pipe pressure is too high, which will lead to cross-flow and backflow between gas sources.

[0005] In response to the above problems, the inventors proposed an exhaust gas residual pressure utilization device and a working method thereof to solve the above problems. Summary of the Invention

[0006] In order to solve the problem that the pressurized exhaust gas to be utilized is discharged from multiple sources and cannot be collected into a pressurized pipeline for centralized discharge, and that each exhaust gas discharge location has a large fluctuation in exhaust gas flow and pressure depending on the process conditions when the exhaust gas is discharged, thereby affecting the efficiency of residual pressure utilization; the purpose of the present invention is to provide an exhaust gas residual pressure utilization device and a working method thereof.

[0007] In order to solve the above technical problems, the present invention adopts the following technical solution: a waste gas residual pressure utilization device, including two fermentation tanks and a body, a washing tower is provided on one side of the two fermentation tanks, one side of the washing tower is connected to an exhaust pipe, and one side of the exhaust pipe is fixedly connected to a shell, a nozzle part is provided in the shell, one side of the shell is provided with an internal chamber of the unit, one side of the shell is provided with a generator, and one side of the generator is electrically fused with an impeller blade, and one side of the impeller blade is movably fitted with the nozzle part.

[0008] Preferably, the outer surface and upper side of the body are symmetrically provided with air intake guide ports, one side of the body is provided with an auxiliary system, and one side of the auxiliary system is provided with a main shaft system, the auxiliary system includes a bearing seat, bearings, chassis, auxiliary cylinders, etc., and the body is provided with a regulating valve system.

[0009] Preferably, an air intake cylinder is fixedly provided in the machine body, the nozzle member is located in the machine body, an exhaust cylinder is provided outside the nozzle member, and the exhaust cylinder is fixedly connected to the machine body.

[0010] Preferably, the regulating valve system includes a regulating valve head, and a regulating valve guide rod is symmetrically fixedly connected between the regulating valve head and the body, an isolation air chamber is provided in the air inlet guide port, a regulating valve connecting rod is provided on one side of the regulating valve head, a regulating valve actuator is fixedly provided in the body, and the output end of the regulating valve actuator is connected to the regulating valve connecting rod, a universal joint is rotatably connected between one side of the regulating valve head and the regulating valve connecting rod, an actuator mounting plate is fixedly provided on the body, and the regulating valve actuator is fixedly set on the actuator mounting plate.

[0011] Preferably, the nozzle member includes a nozzle outer ring and a nozzle inner ring, the nozzle outer ring is fixedly arranged on the outside of the nozzle inner ring, the outside of the nozzle inner ring is symmetrically fixed with nozzle partition ribs and nozzle air vanes distributed in a ring, the outsides of the nozzle outer ring and the nozzle inner ring are symmetrically connected with guide columns distributed in a ring, the outer surface of the body is symmetrically provided with working units, and the working units are located between the air chamber partition ribs and the nozzle partition ribs.

[0012] The working method of the exhaust gas residual pressure utilization device includes the following steps:

[0013] S1. Exhaust gas pretreatment and introduction: The pressurized exhaust gas generated by the fermentation tank first enters the scrubber, where it passes through the packing layer or spray device within the tower for gas-liquid contact purification to remove particulate matter in the exhaust gas and prevent subsequent nozzle blockage. The purified exhaust gas is then transported to the shell through the exhaust pipe. The pipe diameter is designed according to the maximum exhaust gas flow rate, with a flow rate controlled at 10-15m / s. The inner wall is smooth and the elbow has a large curvature radius to reduce the drag along the way and local resistance loss.

[0014] S2. Energy Conversion and Power Generation: Exhaust gas enters the nozzle assembly within the housing, where it expands and accelerates, converting pressure energy into kinetic energy, forming a high-speed airflow. This high-speed airflow impacts the impeller blades, causing them to rotate. The impeller blades drive the generator to generate electricity. The impeller blades are forged from aviation-grade aluminum alloy and treated with a wear-resistant coating. The blade profile conforms to the principles of gas dynamics, and the impact angle is designed to be 30°-45° to efficiently convert the kinetic energy of the airflow.

[0015] S3. Independent processing of multiple gas sources and anti-cross-flow control: Exhaust gases from multiple gas sources enter corresponding isolation chambers through the air inlet guide ports on the outer surface and upper side of the fuselage. Each chamber is completely isolated by an annular partition welded from stainless steel, with an airtightness test pressure of 1.5 times the operating pressure to prevent cross-flow. Each isolation chamber corresponds to an independent nozzle module. After the high-pressure exhaust gas expands and accelerates in its respective nozzle, the pressure quickly drops to the main pipe pressure, preventing cross-flow and backflow between gas sources.

[0016] S4. Variable operating condition adjustment and efficiency optimization: The regulating valve system adjusts according to changes in gas source operating conditions. The regulating valve actuator receives the gas source pressure or flow signal and drives the regulating valve head along the regulating valve guide rod through the regulating valve connecting rod, changing the nozzle flow area. A single air chamber can be equipped with 1-3 groups of regulating valves, which are opened / closed in sequence according to operating conditions such as full flow, 3 / 4 flow, 2 / 4 flow, and 1 / 4 flow, reducing throttling losses. The regulating valve head and actuator are connected by a universal joint to compensate for installation errors and thermal deformation and prevent jamming.

[0017] S5. Auxiliary systems and the main spindle system operate in coordination: The bearing seats in the auxiliary system are water-cooled, with a cooling water flow rate of 2-3 m³ / h and an inlet and outlet temperature difference of ≤15°C. Double-row angular contact ball bearings are used to ensure stable operation of the main spindle system. The chassis is fixed to a concrete foundation with a compressive strength of ≥C30. The auxiliary cylinder quickly cuts off the air supply within 0.3 seconds in an emergency. The main spindle system uses a stepped shaft made of 42CrMo with a quenched and tempered hardness of 28-32 HRC. The support span is optimized according to the impeller diameter, and the critical speed is at least 20% higher than the operating speed to ensure rotational stability.

[0018] S6. Exhaust gas collection and discharge: The exhaust gas after work in each gas chamber is collected in the exhaust cylinder. The exhaust cylinder is an annular collection chamber with a cross-sectional area designed according to the total exhaust volume. The gas flow rate is ≤25m / s. The outer pressure gauge and temperature sensor monitor the exhaust parameters in real time. The collected exhaust gas is discharged to the original process exhaust gas treatment device through the exhaust pipe. By calculating the pipeline resistance, it is ensured that the pressure in the exhaust cylinder will not cause the exhaust gas to flow back to the low-pressure gas source.

[0019] Compared with the prior art, the present invention has the following beneficial effects:

[0020] The present invention introduces each gas source into a separate intake chamber, each with its own nozzle module. High-pressure exhaust gas accelerates expansion after passing through the isolated nozzle modules, rapidly dropping its pressure to the main pipe pressure. Because the pressure in the main pipe is directly connected to the atmosphere and can even utilize the user's induced draft fan, the pressure in the main pipe is extremely low, even slightly negative. This solves the problem of pressurized exhaust gas from multiple gas sources that cannot be centrally utilized.

[0021] The present invention can set 1-3 groups of regulating valves in each air chamber according to the variable working conditions of the process (theoretically, the same number of regulating valves can be set according to the nozzle of each air chamber, but considering the cost-effectiveness, this patent recommends that regulator valves within 3 groups can achieve targeted adjustment of 4 working conditions: full flow, 3 / 4 flow, 2 / 4 flow, 1 / 4 flow, and even a part of the commonly used flow can be taken out and the rest can be adjusted with three groups of regulating valves). This method of opening and closing the regulating valves in sequence for multiple working conditions can reduce throttling losses and ensure that pressure can be efficiently converted into mechanical energy.

[0022] The actuator of the regulating valve of the present invention can be of regulating type and can be interlocked with the pressure or flow signal of each gas source to adjust the working condition, such as constant pressure operation of the intake gas source, or constant flow operation and other operating modes.

[0023] The variable-mode control valve in each air chamber of the present invention is installed by providing a guide post on the nozzle mounting plate. The control valve head, guided by the guide post, opens or closes flow through the corresponding nozzle. A universal joint connects the control valve head to the actuator to prevent jamming caused by inaccurate installation positioning, thermal deformation, or stress-induced misalignment. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0025] Figure 1 It is a schematic diagram of the overall structure of the present invention.

[0026] Figure 2 It is a schematic diagram of the cross-sectional structure of the shell of the present invention.

[0027] Figure 3 It is a schematic diagram of the body structure of the present invention.

[0028] Figure 4 This is a schematic diagram of the variable operating condition adjustment of the multi-chamber gas expansion turbine of the present invention.

[0029] Figure 5 This is a structural diagram of the regulating valve system of the present invention.

[0030] Figure 6 This is a schematic diagram of the nozzle structure of the present invention.

[0031] Figure 7 It is a schematic diagram of the surface structure of one side of the body of the present invention.

[0032] Figure 8 Schematic diagram of the relevant structure of the regulating valve system of the present invention.

[0033] In the figure: 1. Fermentation tank; 2. Scrubber; 3. Exhaust duct; 4. Shell; 41. Internal chamber of the unit; 43. Impeller blades; 44. Generator; 5. Body; 51. Intake cylinder; 52. Exhaust cylinder; 53. Nozzle member; 531. Nozzle outer ring; 532. Nozzle inner ring; 533. Nozzle partition rib; 534. Nozzle air blade; 535. Guide column; 54. Working unit; 6. Intake guide port; 7. Auxiliary system; 8. Control valve system; 81. Control valve head; 82. Control valve guide rod; 83. Control valve connecting rod; 84. Control valve actuator; 85. Isolation air chamber; 86. Universal joint; 87. Actuator mounting plate; 9. Spindle system. DETAILED DESCRIPTION

[0034] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0035] Example: Figure 1-8As shown, the present invention provides a waste gas residual pressure utilization device and a working method thereof, comprising two fermentation tanks 1 and a body 5, a washing tower 2 is provided on one side of the two fermentation tanks 1, an exhaust pipe 3 is connected to one side of the washing tower 2, and a shell 4 is fixedly connected to one side of the exhaust pipe 3, a nozzle part 53 is provided in the shell 4, an internal chamber 41 of the unit is provided on one side of the shell 4, a generator 44 is provided on one side of the shell 4, and an impeller blade 43 is connected to one side of the generator 44 by electrofusion, and one side of the impeller blade 43 is movably fitted with the nozzle part 53, the pressurized tail gas generated by the fermentation tank 1 is purified by the washing tower 2, a packing layer or a spray device is provided inside the washing tower 2, and gas-liquid contact purification is achieved by circulating washing liquid to ensure that the tail gas entering the subsequent system does not contain Particulate matter, avoid clogging of the nozzle part 53, the purified exhaust gas enters the shell 4 through the exhaust pipe 3, the diameter of the exhaust pipe 3 is designed according to the maximum exhaust gas flow, the flow rate is controlled at 10-15m / s to reduce the resistance along the way, the inner wall of the pipe is smoothed, and the elbow is designed with a large curvature radius to reduce local resistance loss. The nozzle part 53 in the shell 4 is the core energy conversion component. The high-pressure exhaust gas expands and accelerates in the nozzle part 53 to form a high-speed airflow, which impacts the impeller blades 43 to rotate and drive the generator 44 to generate electricity. The impeller blades 43 are forged with aviation-grade aluminum alloy and the surface is treated with a wear-resistant coating. The blade profile conforms to the principles of gas dynamics and the impact angle is designed to be 30°-45° to ensure that the kinetic energy of the airflow is efficiently converted into rotational mechanical energy.

[0036] The outer surface and upper side of the machine body 5 are symmetrically provided with air intake guide ports 6, one side of the machine body 5 is provided with an auxiliary system 7, and one side of the auxiliary system 7 is provided with a main shaft system 9, the auxiliary system 7 includes a bearing seat, bearings, chassis, auxiliary cylinders, etc., a regulating valve system 8 is provided in the machine body 5, and the air intake guide port 6 has a trumpet-shaped tapered structure. The inlet cross-sectional area is calculated according to the maximum flow rate of the corresponding air source to ensure that the air intake speed is ≤15m / s and the resistance loss is <50Pa. The internal isolation air chamber 85 is completely isolated from the adjacent air chamber by an annular partition. The partition is welded with stainless steel, and the air tightness test pressure reaches 1.5 times the working pressure to ensure that there is no risk of cross-gas. The bearing seat in the auxiliary system 7 adopts a water-cooled structure. The cooling water flow rate is 2-3 m³ / h, the inlet and outlet temperature difference is ≤15°C, the bearings are double-row angular contact ball bearings with a rated dynamic load of 132 kN, the chassis is fixed to the concrete foundation by anchor bolts, and the foundation compressive strength is ≥C30. The auxiliary cylinder is used to quickly cut off the gas source in an emergency, and the response time is ≤0.3s. The main shaft system 9 adopts a stepped shaft structure with a shaft diameter of φ80-φ120 mm, made of 42CrMo, and a quenched and tempered hardness of 28-32 HRC. The support span is optimized according to the impeller diameter to ensure that the critical speed is more than 20% higher than the operating speed. The regulating valve system 8 can adjust the air intake flow area according to the working conditions. The auxiliary system 7 is used to support the main shaft system 9 and provide pneumatic auxiliary adjustment.

[0037] An intake cylinder 51 is fixedly provided in the engine body 5, and a nozzle part 53 is located in the engine body 5. An exhaust cylinder 52 is provided on the outside of the nozzle part 53, and the exhaust cylinder 52 is fixedly connected to the engine body 5. The intake cylinder 51 is used to guide the high-pressure exhaust gas into the nozzle part 53. It adopts a segmented structure, and each section corresponds to an intake air chamber, which is connected by bolts. The sealing surface adopts a metal spiral wound gasket, and the inner wall is processed with a guide groove matching the nozzle part 53. The groove depth is 10 to 15 mm, and the width is designed according to the spacing of the nozzle partition 533 to guide the exhaust gas to enter the nozzle part 53 evenly. The exhaust cylinder 52 collects the exhaust gas after work and discharges it. It is an annular collection chamber with a cross-sectional area designed according to the total exhaust volume. The gas flow rate is ≤25m / s. A pressure gauge and a temperature sensor are set on the outside to monitor the exhaust parameters in real time. It is connected to the engine body 5 through a flange. The roughness of the flange sealing surface Ra ≤3.2μm to ensure no leakage.

[0038] The regulating valve system 8 includes a regulating valve head 81, and a regulating valve guide rod 82 is symmetrically fixedly connected between the regulating valve head 81 and the body 5, an isolation air chamber 85 is provided in the air inlet guide port 6, a regulating valve connecting rod 83 is provided on one side of the regulating valve head 81, a regulating valve actuator 84 is fixed in the body 5, and the output end of the regulating valve actuator 84 is connected to the regulating valve connecting rod 83, a universal joint 86 is rotatably connected between one side of the regulating valve head 81 and the regulating valve connecting rod 83, an actuator mounting plate 87 is fixed on the body 5, and the regulating valve actuator 84 is fixed on the actuator mounting plate 87, the regulating valve head 81 is a disc-shaped structure, the surface of which is covered with a fluororubber sealing layer with a hardness of 60±5ShoreA, ensuring that the leakage when closed is less than 0.5% of the rated flow, and the linear motion guidance is achieved through the regulating valve guide rod 82, and the guide The rod adopts a chrome-plated optical axis and is matched with a linear bearing with a friction coefficient of <0.05. The valve regulating actuator 84 uses an electric servo actuator with a rated thrust of 500~1000N, a positioning accuracy of ±0.5mm, and a response time of <0.3s. The output end is connected to the valve regulating head 81 through the valve regulating connecting rod 83, and a universal joint 86 is arranged in the middle, allowing ±5° deflection to compensate for installation errors and center offset caused by thermal deformation to prevent jamming. The actuator mounting plate 87 is fixed to the body 5 with high-strength bolts, and the flatness of the mounting surface is ≤0.1mm, ensuring that the coaxiality of the actuator axis and the axis of the valve regulating head 81 is <0.2mm. The valve regulating actuator 84 drives the valve regulating head 81 to move along the valve regulating guide rod 82 through the valve regulating connecting rod 83. The universal joint 86 can compensate for installation errors and isolate the air chamber 85 to prevent air from flowing between different air chambers.

[0039] The nozzle member 53 includes a nozzle outer ring 531 and a nozzle inner ring 532. The nozzle outer ring 531 is fixedly arranged on the outside of the nozzle inner ring 532. The outside of the nozzle inner ring 532 is symmetrically fixed with nozzle partition ribs 533 and nozzle air vanes 534 distributed in an annular shape. The outer sides of the nozzle outer ring 531 and the nozzle inner ring 532 are symmetrically connected with guide columns 535 distributed in an annular shape. The outer surface of the body 5 is symmetrically provided with working units 54, and the working units 54 are located between the air chamber partition ribs and the nozzle partition ribs 533. The nozzle partition ribs 533 separate the air flows of different air chambers and have a thickness of 5 to 8 mm. They correspond one to one with the air chamber partition ribs and divide the nozzle member 53 into independent flow channels. The number of flow channels is consistent with the number of intake air chambers, with a typical value of 8 to 16. The number of nozzle air vanes 534 in each flow channel is 18 to 24, and a three-dimensional flow design is adopted. The blade installation angle is 35°-45°, and the throat cross-sectional area is designed to be 1 / 4 of the maximum flow rate of the gas source to ensure uniform acceleration of the airflow. The nozzle outer ring 531 and the nozzle inner ring 532 are connected by 6 to 8 guide columns 535, which are evenly distributed circumferentially, with a radial runout of ≤0.08mm. They are made of 304 stainless steel and have a diameter of 10 to 15mm, providing radial support to prevent nozzle deformation. The working unit 54 on the outer surface of the body 5 is a groove structure with a depth of 20 to 30mm, aligned with the outlet position of the nozzle air blade 534, and the inner wall is sprayed with a ceramic coating with a thickness of 0.3mm and a hardness of ≥HV1000 to reduce airflow scouring and wear, and receive high-speed airflow to achieve energy conversion. The nozzle air blade 534 guides the airflow to accelerate, the guide column 535 supports the nozzle structure, and the working unit 54 receives high-speed airflow to achieve energy conversion.

[0040] In some production processes, the exhaust gas emissions come from multiple locations. The exhaust gas emitted from these multiple locations cannot be collected together under pressure for centralized discharge. That is, these exhaust gas emissions are either discharged separately or the main pipe is depressurized after being collected together (an induced draft fan is installed to make the main pipe pressure very low or negative to prevent high pressure in the main pipe) to prevent the exhaust gas from flowing back to a certain discharge point. A typical production process with multiple gas sources for exhaust gas emissions is the fermentation industry. Because each fermentation enterprise has a large number of fermentation tanks 1, the fermentation exhaust gas of each fermentation tank 1 is discharged separately, and the production of fermentation tank 1 is discontinuous. The pressures of the fermentation tanks 1 are different, and some are even in a pressure-free state. This requires that the exhaust gas emissions of the fermentation tanks 1 need to be discharged separately. Even if the pressure in the centralized discharge main pipe cannot be too high, otherwise it will cause the high-pressure gas in the main pipe to flow back into the low-pressure fermentation tank 1. During the fermentation process, a sterile environment is required in the fermentation tank 1. Exhaust reflux is a serious production accident and is absolutely prohibited. In this way, in situations where pressurized exhaust gas discharged from multiple gas sources is utilized, this patent needs to be applied to solve the problem of centralized utilization of exhaust gas emissions from each gas source without causing cross-flow and reflux of exhaust emissions from different gas sources.

[0041] In this case, if we want to concentrate on using the residual pressure of pressurized tail gas from multiple gas sources to generate electricity, the solution of this patent is to divide the air chamber of the power generation equipment using the residual pressure of the tail gas into several units. Each unit is isolated from each other, and the working unit 54 is also divided into several units. In this way, the tail gas from each tail gas discharge point is connected to a separate air chamber, and the tail gas is separately diverted to the working unit 54 in the air chamber. After the tail gas has done the work, it is collected together and discharged into the main pipe. There is an induced draft fan behind the main pipe, so the pressure in the main pipe is slightly negative, thus solving the backflow and cross-flow problem of tail gas emissions from different gas source locations. The axial flow turbine form of the present invention discharges tail gas from multiple gas sources into corresponding isolated air chambers.

[0042] The exhaust emissions at each emission location often change with the changes in production, and the flow rate and pressure of the exhaust emissions also change. This patent is specially designed for the changes in working conditions at each exhaust emission location, and can change the flow area of ​​each working unit 54 in real time to adapt to the residual pressure utilization of different working conditions.

[0043] One-to-one air intake mode of the working unit 54 of the multiple air sources (the number of air sources is generally 2 to 24) and the residual pressure utilization unit: multiple air sources enter the mutually isolated working units 54 respectively, that is, the pressurized exhaust gases of different air sources are discharged to different air inlets of a single device and mutually isolated high-pressure air chambers. Each air chamber has a separate nozzle. The high-pressure gas expands and accelerates in the nozzle and then impacts the blades on the impeller to perform work, thereby converting pressure energy into mechanical energy to the greatest extent.

[0044] Each working unit (chamber) has a variable flow area adjustment mechanism. Only by being able to adjust the flow area can the highest efficiency of exhaust residual pressure be achieved when the gas source operating conditions change. This patented design for the separate chambers of the gas expansion turbine allows the turbine to adjust the flow area of ​​these isolated chambers to adapt to changing operating conditions.

[0045] In specific implementation, the number of mutually isolated air chambers and the pitch circle diameter of the unit must be determined first. The principle is: the pressurized exhaust gas of all gas sources enters a single device, that is, a single device is equipped with as many mutually isolated air chambers 85 as possible corresponding to the gas sources.

[0046] According to experience, when the number of gas sources is more than 16 and the maximum gas volume of a single gas source is greater than 5000Nm3 / h, it is very difficult to design a single unit with more than 16 gas chambers. The cost will increase sharply and an additional multi-chamber unit will be needed to accept the exhaust gas from the remaining gas sources.

[0047] Because most of the pressurized exhaust gas emissions from multiple gas sources have low emission pressures (most of which are lower than the gauge pressure of 0.3MPa) and large flow rates, a large-diameter impeller design is used to increase the flow area. The speed obtained after the exhaust gas expands is generally set to twice the pitch circle speed. On this basis, two speeds of generators 44 are selected, a two-pole pair 3000rpm generator 44 and a four-pole pair 1500rpm generator 44.

[0048] In most cases, especially when the pressurized exhaust pressure is less than 0.2MPa and the flow rate is greater than 30,000Nm3 / h, the pitch circle diameter is relatively large to meet the speed obtained after the exhaust gas expansion in a single-stage case, which is generally set to twice the pitch circle speed. However, when the pressurized exhaust pressure is greater than 0.2MPa and the flow rate is small, in order to increase the conversion efficiency, the impeller diameter is generally selected to be a small diameter, high-speed single-stage turbine. Here, we should avoid using a multi-stage turbine structure. If a multi-stage turbine structure is adopted, there will be a certain pressure after the first stage. After the first stage, multiple gas sources have been aggregated together. If a certain pressure is reached, it will cause the exhaust gas to flow back to the gas source with relatively low pressure.

[0049] After all the gas sources enter the unit and work, they are collected in the exhaust cylinder 52 and discharged to the exhaust gas treatment device of the original process through the exhaust pipe 3. The pipeline resistance is calculated based on the amount of gas collected, the inlet diameter of the exhaust gas treatment process, the pipeline length and the number of valve elbows to prevent the pressure of all gas sources in the exhaust cylinder 52 from being too high, causing the exhaust gas to flow back to a gas source with lower pressure.

[0050] Based on the above five points, the number of gas chambers that isolate each other for a single device should be considered:

[0051] Whether it will cause exhaust pressure buildup (production process safety).

[0052] The ratio of the airflow velocity after expansion to the velocity at the pitch circle (conversion efficiency). 3. Unit dimensions (economic efficiency).

[0053] Next, determine the number and geometric dimensions of the variable operating condition control valves for each air chamber. The number of control valves is determined based on the operating conditions of the corresponding gas source. Generally, it is based on the flow operating conditions of the corresponding gas source (flow variable operating condition points with obvious cross-step differences). The number of control valves is generally the number of variable operating condition points minus one.

[0054] The size of the valve head can be determined by determining the number of nozzles blocked in each valve head according to the exhaust gas flow rate in each operating condition and the flow size of the nozzle of a single turbine.

[0055] The lifting force required to open the valve is determined based on the size of the valve head and the pressure difference before and after the valve head. The stroke required for full opening is determined based on the size of the valve head. Once the lifting force and stroke are determined, the appropriate actuator can be selected.

[0056] The form and size of the mounting bracket are determined according to the number of regulating valves, the geometric dimensions of the valve head, the regulating valve stroke, and the overall dimensions of the selected actuator.

[0057] The design of the main parts is that the design of the air intake guide port 6 mainly considers reducing the air intake resistance, controlling the exhaust gas introduction speed within 5 to 15 m / s, and controlling the air intake resistance within 50 Pa.

[0058] The design of the nozzle group mainly considers the rationality of the nozzle profile and the isolation between the nozzle groups, such as Figure 8 In the intake cylinder body 51, the air chambers are separated from each other by partition ribs, and the nozzles are also separated by partition ribs corresponding to the partition ribs of the air chambers, so that the nozzle part is divided into nozzle groups that are independently isolated from each other.

[0059] Regarding the design of the variable operating condition control valve, the adjustment principle of the variable operating condition control valve makes the actuator move up and down, driving the connecting rod and valve head to open and close, and the corresponding number of nozzles, thus achieving the purpose of changing the flow area.

[0060] The working method of the exhaust gas residual pressure utilization device includes the following steps:

[0061] S1. Exhaust Gas Pretreatment and Introduction: The pressurized exhaust gas from fermenter 1 first enters scrubber 2, where it undergoes gas-liquid contact purification via the tower's packing layer or spray device to remove particulate matter and prevent subsequent clogging of nozzle 53. The purified exhaust gas is then transported to housing 4 via exhaust pipe 3. The pipe diameter is designed for maximum exhaust gas flow, with a flow rate controlled at 10-15 m / s. The inner wall is smooth, and elbows have a large curvature radius to reduce drag along the pipe and local resistance losses.

[0062] S2. Energy Conversion and Power Generation: Exhaust gas enters the nozzle assembly 53 within the housing 4, where it expands and accelerates, converting pressure energy into kinetic energy, forming a high-speed airflow. The high-speed airflow impacts the impeller blades 43, causing them to rotate. The impeller blades drive the generator 44 to generate electricity. The impeller blades are forged from aviation-grade aluminum alloy and treated with a wear-resistant coating. The blade profile conforms to the principles of gas dynamics, and the impact angle is designed to be 30°-45° to efficiently convert the kinetic energy of the airflow.

[0063] S3. Independent processing of multiple gas sources and anti-cross-flow control: Exhaust gases from multiple gas sources enter corresponding isolation chambers 85 through the outer surface of the housing 5 and the upper air inlet 6. Each chamber is completely isolated by an annular partition plate welded from stainless steel with an airtightness test pressure of 1.5 times the operating pressure to prevent cross-flow. Each isolation chamber corresponds to an independent nozzle module (nozzle assembly 53). After the high-pressure exhaust gas expands and accelerates in its respective nozzle, its pressure quickly drops to the main pipe pressure (which is extremely low or slightly negative), preventing cross-flow and backflow between gas sources.

[0064] S4. Variable Operating Condition Adjustment and Efficiency Optimization: The regulating valve system 8 adjusts according to changes in the gas source operating conditions (pressure, flow). The regulating valve actuator 84 receives the gas source pressure or flow signal and drives the regulating valve head 81 along the regulating valve guide rod 82 via the regulating valve connecting rod 83 to change the nozzle flow area. A single air chamber can be equipped with 1-3 sets of regulating valves, which can be opened and closed sequentially according to operating conditions such as full flow, 3 / 4 flow, 2 / 4 flow, and 1 / 4 flow, reducing throttling losses. The regulating valve head and actuator are connected by a universal joint 86 to compensate for installation errors and thermal deformation and prevent jamming.

[0065] S5. Auxiliary systems and the main spindle system operate in coordination: The bearing seat in auxiliary system 7 is water-cooled, with a cooling water flow rate of 2-3 m³ / h and an inlet and outlet temperature difference of ≤15°C. Double-row angular contact ball bearings are used to ensure stable operation of main spindle system 9. The chassis is fixed to a concrete foundation with a compressive strength of ≥C30. The auxiliary cylinder quickly cuts off the air supply within 0.3 seconds in an emergency. Main spindle system 9 uses a stepped shaft made of 42CrMo with a quenched and tempered hardness of 28-32 HRC. The support span is optimized according to the impeller diameter, and the critical speed is at least 20% higher than the operating speed to ensure rotational stability.

[0066] S6. Collection and discharge of tail gas: The tail gas after work in each gas chamber is collected in the exhaust cylinder 52. The exhaust cylinder is an annular collection chamber with a cross-sectional area designed according to the total exhaust volume. The gas flow rate is ≤25m / s. The outer pressure gauge and temperature sensor monitor the exhaust parameters in real time. The collected tail gas is discharged to the original process tail gas treatment device through the exhaust pipe. By calculating the pipeline resistance (taking into account the gas volume, inlet diameter, pipeline length, number of valve elbows, etc.), it is ensured that the pressure in the exhaust cylinder will not cause the tail gas to flow back to the low-pressure gas source.

[0067] Working principle: The pressurized tail gas generated by the fermentation tank 1 is purified by the washing tower 2. A packing layer or a spray device is set inside the washing tower 2. The gas-liquid contact purification is achieved by circulating the washing liquid to ensure that the tail gas entering the subsequent system does not contain particulate matter and avoid clogging of the nozzle part 53. The purified tail gas enters the shell 4 through the exhaust pipe 3. The diameter of the exhaust pipe 3 is designed according to the maximum tail gas flow rate. The flow rate is controlled at 10-15m / s to reduce the resistance along the way. The inner wall of the pipe is smoothed and the elbow is designed with a large curvature radius to reduce local resistance loss. The nozzle part 53 in the shell 4 is the core energy conversion component. The high-pressure tail gas expands and accelerates in the nozzle part 53 to form a high-speed airflow, which impacts the impeller blades 43 to rotate and drive the generator 44 to generate electricity. The impeller blades 43 are forged with aviation-grade aluminum alloy and the surface is treated with a wear-resistant coating. The blade profile conforms to the principles of gas dynamics and the impact angle is designed to be 30°-45° to ensure that the kinetic energy of the airflow is efficiently converted into rotational mechanical energy.

[0068] The air inlet guide port 6 has a trumpet-shaped tapered structure. The inlet cross-sectional area is calculated based on the maximum flow rate of the corresponding air source to ensure that the air intake velocity is ≤15m / s and the resistance loss is <50Pa. The internal isolation air chamber 85 is completely isolated from the adjacent air chamber by an annular partition. The partition is welded with stainless steel. The air tightness test pressure reaches 1.5 times the working pressure to ensure that there is no risk of cross-flow. The bearing seat in the auxiliary system 7 adopts a water-cooled structure with a cooling water flow rate of 2-3m³ / h and an inlet and outlet temperature difference of ≤15℃. The bearing uses a double-row angular contact ball bearing with a rated dynamic load of 132k N, the chassis is fixed to the concrete foundation by anchor bolts, and the foundation compressive strength is ≥ C30. The auxiliary cylinder is used to quickly cut off the air supply in an emergency, with a response time of ≤ 0.3s. The main shaft system 9 adopts a stepped shaft structure with a shaft diameter of φ80-φ120mm, made of 42CrMo, and a quenched and tempered hardness of 28-32HRC. The support span is optimized according to the impeller diameter to ensure that the critical speed is more than 20% higher than the operating speed. The regulating valve system 8 can adjust the air intake flow area according to the working conditions. The auxiliary system 7 is used to support the main shaft system 9 and provide pneumatic auxiliary adjustment;

[0069] The intake cylinder 51 is used to guide high-pressure exhaust gas into the nozzle member 53. It adopts a segmented structure, with each segment corresponding to an intake air chamber. The two sections are connected by bolts. The sealing surface uses a metal spiral wound gasket. The inner wall is machined with a guide groove that matches the nozzle member 53. The groove depth is 10-15mm, and the width is designed according to the spacing of the nozzle partition 533. It guides the exhaust gas to enter the nozzle member 53 evenly. The exhaust cylinder 52 collects the exhaust gas after work and discharges it. It is an annular collection chamber with a cross-sectional area designed according to the total exhaust volume. The gas flow rate is ≤25m / s. A pressure gauge and temperature sensor are installed on the outside to monitor the exhaust parameters in real time. It is connected to the body 5 by a flange. The flange sealing surface roughness Ra ≤3.2μm to ensure no leakage.

[0070] The regulating valve head 81 is a disc-shaped structure, the surface of which is covered with a fluororubber sealing layer with a hardness of 60±5ShoreA, ensuring that the leakage is less than 0.5% of the rated flow when closed. The linear motion is guided by the regulating valve guide rod 82. The guide rod adopts a chrome-plated optical axis and is matched with a linear bearing with a friction coefficient of less than 0.05. The regulating valve actuator 84 uses an electric servo actuator with a rated thrust of 500~1000N, a positioning accuracy of ±0.5mm, and a response time of less than 0.3s. The output end is connected to the regulating valve through the regulating valve connecting rod 83. The actuator mounting plate 87 is fixed to the body 5 with high-strength bolts. The flatness of the mounting surface is ≤0.1mm. The coaxiality between the actuator axis and the axis of the regulating valve head 81 is ensured to be less than 0.2mm. The regulating valve actuator 84 drives the regulating valve head 81 to move along the regulating valve guide rod 82 through the regulating valve connecting rod 83. The universal joint 86 can compensate for installation errors and isolate the air chamber 85 to prevent cross-flow of different air chambers.

[0071] The nozzle partition ribs 533 separate the airflows of different air chambers, with a thickness of 5 to 8 mm, corresponding to the air chamber partition ribs one by one, dividing the nozzle member 53 into independent flow channels. The number of flow channels is consistent with the number of intake air chambers, with a typical value of 8 to 16. The number of nozzle air blades 534 in each flow channel is 18 to 24, adopting a three-dimensional flow design, with a blade installation angle of 35°-45°, and a throat cross-sectional area designed to be 1 / 4 of the maximum flow rate of the air source to ensure uniform acceleration of the airflow. The nozzle outer ring 531 and the nozzle inner ring 532 are connected by 6 to 8 guide columns 535, which are evenly distributed circumferentially and radially. The runout is ≤0.08mm, the material is 304 stainless steel, the diameter is 10-15mm, it provides radial support to prevent the nozzle from deforming, the working unit 54 on the outer surface of the body 5 is a groove structure with a depth of 20-30mm, aligned with the outlet position of the nozzle air blade 534, the inner wall is sprayed with a ceramic coating with a thickness of 0.3mm and a hardness of ≥HV1000, which reduces air flow erosion and wear, receives high-speed airflow to achieve energy conversion, the nozzle air blade 534 guides the airflow to accelerate, the guide column 535 supports the nozzle structure, and the working unit 54 receives high-speed airflow to achieve energy conversion.

[0072] Obviously, those skilled in the art may make various changes and modifications to the present invention without departing from the spirit and scope of the present invention. Thus, if such changes and modifications fall within the scope of the claims and their equivalents, the present invention is intended to include such changes and modifications.

Claims

1. A waste gas residual pressure utilization device, comprising two fermentation tanks (1) and a body (5), characterized in that: A washing tower (2) is provided on one side of the two fermentation tanks (1), an exhaust pipe (3) is connected to one side of the washing tower (2), and a housing (4) is fixedly connected to one side of the exhaust pipe (3), a nozzle member (53) is provided in the housing (4), an internal chamber (41) of the unit is provided on one side of the housing (4), a generator (44) is provided on one side of the housing (4), and an impeller blade (43) is electrically connected to one side of the generator (44), and one side of the impeller blade (43) is movably fitted with the nozzle member (53); The outer surface and upper side of the machine body (5) are symmetrically provided with air intake guide ports (6); an auxiliary system (7) is provided on one side of the machine body (5); and a main shaft system (9) is provided on one side of the auxiliary system (7); and a regulating valve system (8) is provided inside the machine body (5); The regulating valve system (8) includes a regulating valve head (81), and a regulating valve guide rod (82) is symmetrically fixedly connected between the regulating valve head (81) and the body (5). An isolation air chamber (85) is provided in the air inlet guide port (6). A regulating valve connecting rod (83) is provided on one side of the regulating valve head (81). A regulating valve actuator (84) is fixedly provided in the body (5), and an output end of the regulating valve actuator (84) is connected to the regulating valve connecting rod (83).

2. The exhaust gas residual pressure utilization device according to claim 1, characterized in that: An air intake cylinder (51) is fixedly provided in the machine body (5), the nozzle member (53) is located in the machine body (5), an exhaust cylinder (52) is provided outside the nozzle member (53), and the exhaust cylinder (52) is fixedly connected to the machine body (5).

3. The exhaust gas residual pressure utilization device according to claim 1, characterized in that: The auxiliary system (7) includes a bearing seat, a bearing, a chassis and an auxiliary cylinder.

4. The exhaust gas residual pressure utilization device according to claim 1, characterized in that: The nozzle member (53) comprises a nozzle outer ring (531) and a nozzle inner ring (532), wherein the nozzle outer ring (531) is fixedly arranged on the outside of the nozzle inner ring (532), and nozzle partition ribs (533) and nozzle air vanes (534) distributed in an annular shape are symmetrically fixedly arranged on the outside of the nozzle inner ring (532).

5. The exhaust gas residual pressure utilization device according to claim 4, characterized in that: Guide pillars (535) distributed in an annular shape are symmetrically connected between the outer sides of the nozzle outer ring (531) and the outer sides of the nozzle inner ring (532).

6. The exhaust gas residual pressure utilization device according to claim 4, characterized in that: The outer surface of the machine body (5) is symmetrically provided with a working unit (54), and the working unit (54) is located between the air chamber partition rib and the nozzle partition rib (533).

7. The exhaust gas residual pressure utilization device according to claim 1, characterized in that: A universal joint (86) is rotatably connected between one side of the regulating valve head (81) and the regulating valve connecting rod (83); an actuator mounting plate (87) is fixedly provided on the machine body (5); and the regulating valve actuator (84) is fixedly provided on the actuator mounting plate (87).

8. A working method for the exhaust gas residual pressure utilization device according to any one of claims 1 to 7, characterized in that: The following steps are involved: S1. Tail gas pretreatment and introduction: The pressurized tail gas generated by the fermentation tank (1) first enters the scrubbing tower (2), where it is purified by gas-liquid contact through the packing layer or spray device in the tower to remove particulate matter in the tail gas and avoid clogging of the subsequent nozzle component (53); the purified tail gas is transported to the shell (4) through the exhaust pipe (3). The pipe diameter is designed according to the maximum tail gas flow rate, and the flow rate is controlled at 10-15m / s. The inner wall is smooth and the elbow adopts a large curvature radius to reduce the resistance along the way and the local resistance loss; S2. Energy conversion and power generation: The exhaust gas enters the nozzle member (53) in the housing (4), expands and accelerates in the nozzle member, converts pressure energy into kinetic energy, and forms a high-speed airflow; the high-speed airflow impacts the impeller blades (43) to rotate, and the impeller blades drive the generator (44) to rotate and generate electricity. The impeller blades are forged from aviation-grade aluminum alloy, and the surface is treated with a wear-resistant coating. The blade profile conforms to the principles of gas dynamics, and the impact angle is designed to be 30°-45° to efficiently convert the kinetic energy of the airflow; S3. Independent processing of multiple gas sources and anti-cross-flow control: The exhaust gases of multiple gas sources enter the corresponding isolation chambers (85) through the outer surface of the body (5) and the air inlet guide port (6) on the upper side. Each chamber is completely isolated by an annular partition. The partition is welded with stainless steel. The air tightness test pressure reaches 1.5 times the working pressure to prevent cross-flow. Each isolation chamber corresponds to an independent nozzle module. After the high-pressure exhaust gas expands and accelerates in each nozzle, the pressure drops quickly to the main pipe pressure to avoid cross-flow and backflow between gas sources. S4. Adjustment of variable working conditions and efficiency optimization: The regulating valve system (8) is adjusted according to the change of the working conditions of the gas source: the regulating valve actuator (84) receives the gas source pressure or flow signal, and drives the regulating valve head (81) to move along the regulating valve guide rod (82) through the regulating valve connecting rod (83), thereby changing the nozzle flow area; a single air chamber can be provided with 1-3 groups of regulating valves, which are sequentially opened / closed for full flow, 3 / 4 flow, 2 / 4 flow, 1 / 4 flow and other working conditions to reduce throttling losses; the regulating valve head and the actuator are connected by a universal joint (86) to compensate for installation errors and thermal deformation and prevent jamming; S5. The auxiliary system and the main shaft system operate in coordination: the bearing seat in the auxiliary system (7) adopts a water-cooled structure, with a cooling water flow rate of 2 to 3 m³ / h and an inlet and outlet temperature difference of ≤15°C. The bearings are double-row angular contact ball bearings to ensure the stable operation of the main shaft system (9). The chassis is fixed to a concrete foundation with a compressive strength of ≥C30. The auxiliary cylinder can quickly cut off the air supply within 0.3 seconds in an emergency. The main shaft system (9) adopts a stepped shaft made of 42CrMo material with a tempering hardness of 28-32HRC. The support span is optimized according to the impeller diameter. The critical speed is more than 20% higher than the working speed to ensure rotation stability. S6. Collection and discharge of tail gas: The tail gas after work in each chamber is collected in the exhaust cylinder (52). The exhaust cylinder is an annular collection chamber with a cross-sectional area designed according to the total exhaust volume. The gas flow rate is ≤25m / s. The outer pressure gauge and temperature sensor monitor the exhaust parameters in real time. The collected tail gas is discharged to the original process tail gas treatment device through the exhaust pipe. By calculating the pipe resistance, it is ensured that the pressure in the exhaust cylinder will not cause the tail gas to flow back to the low-pressure gas source.

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