Waste gas excess pressure utilization device and working method thereof

Abstract

The invention discloses a waste gas residual pressure utilization device and a working method thereof, and relates to the technical field of multi-gas-source and multi-working-condition residual pressure utilization and recycling, the waste gas residual pressure utilization device comprises two fermentation tanks and a machine body, a washing tower is arranged on one sides of the two fermentation tanks, one side of the washing tower is connected with an exhaust pipeline, and the other side of the washing tower is connected with an exhaust pipe; a shell is fixedly connected to one side of the exhaust pipeline, a nozzle piece is arranged in the shell, a unit internal cavity is formed in one side of the shell, a generator is arranged on one side of the shell, impeller blades are connected to one side of the generator in an electric smelting mode, and one sides of the impeller blades are movably attached to the nozzle piece. According to the waste gas excess pressure utilization device and the working method thereof, tail gas of multiple gas sources is introduced into the independent gas chambers, conversion from pressure energy to mechanical energy is achieved through the nozzle piece, and the problems of multi-gas-source blow-by and low variable working condition efficiency are solved.

Description

Technical Field

[0001] The present invention relates to the technical field of residual pressure utilization and recovery for multiple gas sources and multiple working conditions, and to occasions with requirements for preventing backflow and gas mixing. Specifically, it is an exhaust gas residual pressure utilization device and its working method. Background Art

[0002] In some occasions where there is a large amount of residual pressure utilization of pressurized exhaust gas, because the discharge locations are relatively scattered, that is, there are multiple gas sources, the pressures of the multiple gas sources are different, the flows are different, and even the continuity of discharge is different, and there are requirements for preventing backflow and gas mixing. A typical pressurized exhaust gas discharge environment is the fermentation process. Each fermentation tank has pressurized exhaust gas, and each fermentation tank can be regarded as an independent gas source.

[0003] Due to the different pressures, flows, and discharge continuities of the gas sources, and the requirement that the gases between them cannot flow and mix, usually the discharges of the fermentation tanks are divided into two situations. The first situation is separate discharge. The second situation is to collect them into a main pipe, but in order to ensure that the pressure after collection is low enough (the pressure of the main pipe should be lower than the lowest pressure of each gas source to ensure that the gas will not flow back when the gas source does not exhaust or has a low pressure). For example, in the fermentation production of pharmaceutical raw materials with very strict requirements for preventing bacterial contamination, and the fermentation production of amino acids, etc., there must be no gas mixing or backflow.

[0004] For this kind of exhaust gas discharge with very strict requirements for backflow and gas mixing, and each gas source of multiple gas sources has variable working conditions, the residual pressure utilization cannot simply collect adjacent gas sources into the main pipe and then introduce them into the residual pressure utilization unit to do work, because the prerequisite for the main pipe to enter the residual pressure utilization unit to do work is that the pressure before work is very high, which means that the pressure of the main pipe is too high, resulting in gas mixing, backflow, etc. between the gas sources.

[0005] In view of the above problems, the inventor proposes an exhaust gas residual pressure utilization device and its working method to solve the above problems. Summary of the Invention

[0006] In order to solve the problem that the pressurized exhaust gas to be utilized has multiple gas sources and cannot be collected into a pressurized pipeline for centralized discharge, and at each exhaust gas discharge location, according to the process conditions, there will be large-range fluctuations in the exhaust gas flow and pressure, which will affect the work efficiency of residual pressure utilization; the purpose of the present invention is to provide an exhaust gas residual pressure utilization device and its working method.

[0007] To solve the above technical problems, the present invention adopts the following technical solutions: An exhaust gas residual pressure utilization device includes two fermentation tanks and a machine body. On one side of the two fermentation tanks, there is a scrubbing tower. One side of the scrubbing tower is connected to an exhaust pipeline, and on one side of the exhaust pipeline, there is a fixed connection with a housing. Inside the housing, there is a nozzle member. On one side of the housing, there is an internal chamber of the unit. On one side of the housing, there is a generator, and on one side of the generator, there is an electric melting connection with an impeller blade, and one side of the impeller blade is movably attached to the nozzle member.

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

[0009] Preferably, an intake cylinder body is fixedly provided inside the machine body. The nozzle member is located inside the machine body. On the outside of the nozzle member, there is an exhaust cylinder, and the exhaust cylinder is fixedly connected to the machine body.

[0010] Preferably, the regulating valve system includes a regulating valve head, and symmetrically fixed connection rods between the regulating valve head and the machine body are provided with regulating valve guiding rods. Inside the intake air guiding port, there is an isolation air chamber. On one side of the regulating valve head, there is a regulating valve connecting rod. Inside the machine body, there is a fixedly provided regulating valve actuator, and the output end of the regulating valve actuator is connected to the regulating valve connecting rod. Between one side of the regulating valve head and the regulating valve connecting rod, there is a rotatable connection with a universal joint. On the machine body, there is a fixedly provided actuator mounting plate, and the regulating valve actuator is fixedly arranged 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. On the outside of the nozzle inner ring, symmetrically fixedly provided nozzle separating ribs and nozzle air vanes are distributed in a ring shape. Between the outside of the nozzle outer ring and the nozzle inner ring, symmetrically connected guiding columns are distributed in a ring shape. On the outer surface of the machine body, work units are symmetrically provided, and the work units are located between the air chamber separating ribs and the nozzle separating ribs.

[0012] The working method of the exhaust gas residual pressure utilization device includes the following steps: S1. Tail gas pretreatment and introduction: The pressurized tail gas generated by the fermentation tank first enters the scrubbing tower, and gas-liquid contact purification is carried out through the packing layer or spraying device in the tower to remove particulate matter in the tail gas and avoid blockage of the subsequent nozzle member; the purified tail gas is transported to the housing through the exhaust pipeline. The pipe diameter is designed according to the maximum tail gas flow rate, and the flow velocity is controlled at 10 - 15 m / s. The inner wall is smoothly treated and the elbows adopt a large curvature radius to reduce the frictional resistance and local resistance loss; S2. Energy conversion and power generation: The tail gas enters the nozzle part inside the housing, expands and accelerates in the nozzle part, converts the pressure energy into kinetic energy, and forms a high-speed air flow; the high-speed air flow impacts the impeller blades to make them rotate, and the impeller blades drive the generator to rotate and generate electricity. The impeller blades are forged from aviation-grade aluminum alloy, the surface is treated with a wear-resistant coating, the blade profile conforms to the gas dynamics principle, and the impact angle is designed to be 30° - 45° to efficiently convert the kinetic energy of the gas flow; S3. Independent treatment of multiple gas sources and anti-gas cross-flow control: The tail gases of multiple gas sources enter the corresponding isolation gas chambers respectively through the air intake guiding ports on the outer surface and the upper side of the machine body. Each gas chamber is completely isolated by an annular partition. The partition is welded with stainless steel, and the airtightness test pressure reaches 1.5 times the working pressure to prevent gas cross-flow; each isolation gas chamber corresponds to an independent nozzle module. After the high-pressure tail gas expands and accelerates in its respective nozzle, the pressure rapidly drops to the main pipe pressure, avoiding gas cross-flow and backflow between gas sources; S4. Variable condition regulation and efficiency optimization: The regulating valve system adjusts according to the changes in the gas source conditions: The regulating valve actuator receives the gas source pressure or flow signal, drives the regulating valve head to move along the regulating valve guide rod through the regulating valve connecting rod, and changes the flow area of the nozzle; 1 - 3 groups of regulating valves can be set for a single gas chamber, and they are sequentially opened / closed for conditions such as full flow, 3 / 4 flow, 2 / 4 flow, 1 / 4 flow, etc., to reduce throttling losses. The regulating valve head and the actuator are connected by a universal joint to compensate for installation errors and thermal deformations and prevent jamming; S5. Cooperative operation of the auxiliary system and the main shaft system: The bearing housing in the auxiliary system adopts a water-cooled structure, the cooling water flow rate is 2 - 3 m³ / h, and the temperature difference between the inlet and outlet is ≤15°C. Double-row angular contact ball bearings are selected for the bearings to ensure the stable operation of the main shaft system. The chassis is fixed on a concrete foundation with a compressive strength ≥C30. The auxiliary cylinder can quickly cut off the gas source within 0.3 s in case of emergency; The main shaft system uses a stepped shaft made of 42CrMo material, the quenched and tempered hardness is 28 - 32 HRC, the support span is optimized according to the impeller diameter, and the critical speed is more than 20% higher than the working speed to ensure rotational stability; S6. Tail gas collection and discharge: The tail gases after working in each gas chamber are collected in the exhaust cylinder. The exhaust cylinder is an annular collection chamber, and the cross-sectional area is designed according to the total exhaust volume. The gas flow velocity is ≤25 m / s. The external 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.

[0013] Compared with the prior art, the beneficial effects of the present invention are as follows: In the present invention, each gas source is separately introduced into independent intake chambers, and each independent intake chamber has its own nozzle module. The tail gas with high pressure expands rapidly and its pressure drops quickly to the pressure of the main pipe after passing through the isolated nozzle module. Since the pressure in the main pipe is directly connected to the atmosphere, and in some cases, the induced draft fan of the user can be utilized, the pressure in the main pipe is extremely low, even slightly negative. In this way, the problem that the pressurized tail gas emissions from multiple gas sources cannot be centrally utilized is solved.

[0014] In the present invention, 1 - 3 groups of regulating valves can be set in each gas chamber according to the variable operating conditions of the process (theoretically, the same number of regulating valves can be set according to the nozzles in each gas chamber, but considering the cost performance, this patent recommends that no more than 3 groups of regulating valves can achieve targeted regulation of 4 operating conditions: full flow, 3 / 4 flow, 2 / 4 flow, 1 / 4 flow. Even a part of the commonly used flow can be taken out, and the remaining can be regulated by three groups of regulating valves). Sequentially opening and closing the regulating valves for multiple operating conditions in this way can reduce throttling losses and ensure that pressure energy is efficiently converted into mechanical energy.

[0015] In the present invention, the actuator of the regulating valve can be of the regulating type and can be interlocked with the pressure or flow signal of each gas source for variable operating condition regulation. For example, the constant pressure operation or constant flow operation of the intake gas source and other operation modes.

[0016] In the present invention, the installation method of the variable operating condition regulating valve in each gas chamber is to set guide columns on the nozzle mounting plate. The regulating valve head can open or close the flow passage of the corresponding nozzle under the guiding action of the guide columns. The regulating valve head and the actuator are connected by a universal joint to prevent jamming caused by misalignment during installation or central misalignment caused by thermal deformation and stress deformation. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the following drawings are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0018] Figure 1 It is a schematic diagram of the overall structure of the present invention.

[0019] Figure 2 It is a schematic diagram of the sectional structure of the housing of the present invention.

[0020] Figure 3 It is a schematic diagram of the structure of the body of the present invention.

[0021] Figure 4 It is a schematic diagram of the variable operating condition regulation of the multi - gas chamber of the gas expansion work turbine of the present invention.

[0022] Figure 5 This is a schematic structural diagram of the regulating valve system of the present invention.

[0023] Figure 6 This is a schematic structural diagram of the nozzle part of the present invention.

[0024] Figure 7 This is a schematic structural diagram of one side surface of the body of the present invention.

[0025] Figure 8 This is a schematic structural diagram of the relevant structures of the regulating valve system of the present invention.

[0026] In the figure: 1, fermentation tank; 2, scrubbing tower; 3, exhaust pipeline; 4, housing; 41, internal chamber of the unit; 43, impeller blade; 44, generator; 5, body; 51, intake cylinder block; 52, exhaust cylinder; 53, nozzle part; 531, nozzle outer ring; 532, nozzle inner ring; 533, nozzle partition rib; 534, nozzle air vane; 535, guide post; 54, work unit; 6, intake guiding port; 7, auxiliary system; 8, regulating valve system; 81, regulating valve head; 82, regulating valve guide rod; 83, regulating valve connecting rod; 84, regulating valve actuator; 85, isolation air chamber; 86, universal joint; 87, actuator mounting plate; 9, main shaft system. Specific embodiments

[0027] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0028] Embodiment: As Figure 1-8As shown in the figure, the present invention provides a device for utilizing waste gas residual pressure and its working method, including two fermentation tanks 1 and a body 5. A scrubbing tower 2 is provided on one side of the two fermentation tanks 1. An exhaust pipe 3 is connected to one side of the scrubbing tower 2, and a housing 4 is fixedly connected to one side of the exhaust pipe 3. A nozzle member 53 is provided inside 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 fused to one side of the generator 44. One side of the impeller blade 43 is movably fitted with the nozzle member 53. The pressurized tail gas generated by the fermentation tank 1 is purified by the scrubbing tower 2. A packing layer or a spraying device is provided inside the scrubbing tower 2, and gas-liquid contact purification is achieved through circulating washing liquid to ensure that the tail gas entering the subsequent system does not contain particulate matter and prevent the nozzle member 53 from being blocked. The purified tail gas enters the housing 4 through the exhaust pipe 3. The diameter of the exhaust pipe 3 is designed according to the maximum tail gas flow rate, and the flow velocity is controlled at 10-15 m / s to reduce the frictional resistance along the way. The inner wall of the pipe is made smooth, and the elbow is designed with a large curvature radius to reduce the local resistance loss. The nozzle member 53 inside the housing 4 is the core energy conversion component. The high-pressure tail gas expands and accelerates in the nozzle member 53 to form a high-speed air flow, which impacts the impeller blade 43 to rotate and drives the generator 44 to generate electricity. The impeller blade 43 is forged from aviation-grade aluminum alloy, the surface is treated with a wear-resistant coating, and the blade profile conforms to the principle of gas dynamics. The impact angle is designed to be 30°-45° to ensure the efficient conversion of gas flow kinetic energy into rotational mechanical energy.

[0029] Intake guiding ports 6 are symmetrically provided on the outer surface and the upper side of the body 5. An auxiliary system 7 is provided on one side of the body 5, and a main shaft system 9 is provided on one side of the auxiliary system 7. The auxiliary system 7 includes a bearing seat, bearings, a chassis, auxiliary cylinders, etc. A regulating valve system 8 is provided inside the body 5. The intake guiding port 6 has a trumpet-shaped tapered structure inside, and the inlet cross-sectional area is calculated according to the maximum flow rate of the corresponding gas source to ensure that the intake speed ≤ 15 m / s and the resistance loss < 50 Pa. The internal isolation gas chamber 85 is completely isolated from the adjacent gas chamber by an annular partition. The partition is welded with stainless steel, and the airtightness test pressure reaches 1.5 times the working pressure to ensure no risk of gas leakage. The bearing seat in the auxiliary system 7 adopts a water-cooled structure, the cooling water flow rate is 2-3 m³ / h, and the temperature difference between the inlet and outlet ≤ 15 °C. The bearings are selected as 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 compressive strength of the foundation ≥ C30. The auxiliary cylinder is used to quickly cut off the gas source in case of emergency, and the response time ≤ 0.3 s. The main shaft system 9 adopts a stepped shaft structure, the shaft diameter is φ80-φ120 mm, the material is 42CrMo, and the quenched and tempered hardness is 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 working speed. The regulating valve system 8 can adjust the intake flow area according to the working conditions, and the auxiliary system 7 is used to support the main shaft system 9 and provide pneumatic auxiliary adjustment.

[0030] An intake cylinder block 51 is fixedly arranged inside the body 5. The nozzle part 53 is located inside the body 5. An exhaust cylinder 52 is arranged outside the nozzle part 53, and the exhaust cylinder 52 is fixedly connected to the body 5. The intake cylinder block 51 is used to guide high-pressure exhaust gas into the nozzle part 53. It adopts a segmented structure, with each segment corresponding to an intake air chamber. It is connected by bolts. The sealing surface uses a metal wound gasket. The inner wall is machined with a diversion groove matching the nozzle part 53. The groove depth is 10 - 15 mm, and the width is designed according to the spacing of the nozzle partition ribs 533 to guide the exhaust gas into the nozzle part 53 evenly. The exhaust cylinder 52 collects the exhaust gas after doing work and discharges it. It is a ring-shaped collection chamber, and the cross-sectional area is designed according to the total exhaust volume. The gas flow velocity ≤ 25 m / s. A pressure gauge and a temperature sensor are arranged on the outside to monitor the exhaust parameters in real time. It is connected to the body 5 through a flange. The roughness Ra of the flange sealing surface ≤ 3.2 μm to ensure no leakage.

[0031] The regulating valve system 8 includes a regulating valve head 81. Symmetrically fixed connections are provided between the regulating valve head 81 and the body 5 with regulating valve guide rods 82. An isolation air chamber 85 is arranged inside the intake guiding port 6. A regulating valve connecting rod 83 is arranged on one side of the regulating valve head 81. A regulating valve actuator 84 is fixedly arranged inside 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 fixedly arranged on the body 5, and the regulating valve actuator 84 is fixedly arranged on the actuator mounting plate 87. The regulating valve head 81 is of a disc-shaped structure, and its surface is covered with a fluororubber sealing layer. The hardness of the sealing layer is 60 ± 5 Shore A to ensure that the leakage amount < 0.5% of the rated flow when closed. It realizes linear motion guidance through the regulating valve guide rod 82. The guide rod uses a chrome-plated optical axis, cooperating with a linear bearing, and the friction coefficient < 0.05. The regulating valve actuator 84 selects an electric servo actuator, with a rated thrust of 500 - 1000 N, a positioning accuracy of ± 0.5 mm, a response time < 0.3 s. The output end is connected to the regulating valve head 81 through the regulating valve connecting rod 83, and a universal joint 86 is arranged in the middle, allowing a ± 5° deflection to compensate for the central offset caused by installation errors and thermal deformation, preventing jamming. The actuator mounting plate 87 is fixed to the body 5 with high-strength bolts. The flatness of the mounting surface ≤ 0.1 mm to ensure that the coaxiality of the actuator axis and the regulating valve head 81 axis < 0.2 mm. 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 the isolation air chamber 85 prevents gas from leaking between different air chambers.

[0032] The nozzle part 53 includes a nozzle outer ring 531 and a nozzle inner ring 532. The nozzle outer ring 531 is fixedly arranged on the outer side of the nozzle inner ring 532. Symmetrically and fixedly arranged on the outer side of the nozzle inner ring 532 are annularly distributed nozzle partition ribs 533 and nozzle airfoils 534. Symmetrically connected between the outer sides of the nozzle outer ring 531 and the nozzle inner ring 532 are annularly distributed guide columns 535. On the outer surface of the machine body 5, symmetrically arranged are work units 54, and the work units 54 are located between the air chamber partition ribs and the nozzle partition ribs 533. The nozzle partition ribs 533 separate the airflows of different air chambers, with a thickness of 5 - 8 mm, corresponding one by one to the air chamber partition ribs, dividing the nozzle part 53 into independent flow channels. The number of flow channels is the same as the number of intake air chambers, typically 8 - 16. The number of nozzle airfoils 534 in each flow channel is 18 - 24. A three-dimensional flow design is adopted, with the blade installation angle being 35° - 45°. The throat cross-sectional area is designed according to 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 - 8 guide columns 535, which are evenly distributed circumferentially, with a radial runout ≤ 0.08 mm. The material is 304 stainless steel, with a diameter of 10 - 15 mm, providing radial support to prevent nozzle deformation. The work units 54 on the outer surface of the machine body 5 are of a groove structure, with a depth of 20 - 30 mm, aligned with the outlet position of the nozzle airfoils 534. The inner wall is sprayed with a ceramic coating, with a thickness of 0.3 mm and a hardness ≥ HV1000, reducing erosion and wear by the airflow, receiving the high-speed airflow to achieve energy conversion. The nozzle airfoils 534 guide the airflow to accelerate, the guide columns 535 support the nozzle structure, and the work units 54 receive the high-speed airflow to achieve energy conversion.

[0033] In some production processes, the air sources of tail gas emissions are from multiple locations. The tail gases emitted from these multiple locations cannot be collected together under pressure for centralized emission. That is, these tail gas emissions are either discharged separately or, after being collected together, the collecting main pipe needs to be depressurized (installing a draft fan to make the pressure in the main pipe a very low pressure or negative pressure to prevent high pressure in the main pipe), to prevent the reverse flow of the tail gas into a certain emission point. A typical production process of multi-air-source tail gas emission is the fermentation industry. Because each fermentation enterprise has a very large number of fermentation tanks 1, the fermentation tail gas of each fermentation tank 1 is discharged separately. The production of the fermentation tank 1 is non-continuous, and the pressures of the fermentation tanks 1 are different, and some are even in a non-pressure state. This requires that the tail gas emissions of the fermentation tanks 1 need to be discharged separately. Even when discharging centrally, the pressure in the main pipe cannot be too high, otherwise the gas with high pressure in the main pipe will flow back into the fermentation tank 1 with low pressure. And during the fermentation process, a sterile environment is required in the fermentation tank 1, and exhaust gas backflow is a serious production accident and is absolutely prohibited. Thus, in the case of using the pressurized tail gas of multi-air-source emissions, this patent needs to be applied to solve the problem of centralized utilization of the tail gas emissions of each air source without causing cross-flow and backflow problems of the tail gas emissions of different air sources.

[0034] In response to this situation, if we want to centrally utilize the residual pressure of the pressurized tail gas from multiple gas sources for power generation, the solution of this patent is to divide the gas chamber of the power generation equipment using the residual pressure of the tail gas into several units, which are isolated from each other. The working units 54 are also divided into several parts. In this way, the tail gas at each tail gas emission point is connected to a separate gas chamber, and the tail gas is separately guided to the working unit 54 in the gas chamber. After the tail gas has done work, it is collected 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 pressure, thus solving the problem of reverse flow and gas cross-flow in the tail gas emissions from different gas source locations. The axial flow turbine form of the multi-gas-source tail gas emissions of the present invention is discharged into the corresponding isolated gas chambers.

[0035] For the tail gas emissions at each emission location, often with the changes in production, the flow rate and pressure of the tail gas emissions also change. This patent has been specifically designed for the working conditions changes at each tail gas emission location, and can change the flow area of the working unit 54 of each working unit 54 in real time to adapt to the residual pressure utilization under different working conditions.

[0036] One-to-one intake mode of multiple gas sources (the number of gas sources is generally preferably 2 - 24) and the working unit 54 of the residual pressure utilization unit: The multiple gas sources enter the mutually isolated working units 54 respectively, that is, the pressurized tail gas from different gas sources is discharged into different intake ports and mutually isolated high-pressure gas chambers of a single device. Each gas chamber has a separate nozzle. After the high-pressure gas expands and accelerates in the nozzle, it impacts the blades on the impeller to do work, converting the pressure energy into mechanical energy to the greatest extent.

[0037] Each group of working units (gas chambers) has an adjustment mechanism with a variable flow area: Only by being able to change the flow area can the highest efficiency of the tail gas residual pressure utilization be ensured when the working conditions of each gas source change. This invention patent has designed the individual gas chambers of the gas expansion turbine to meet the requirement that when the working conditions of each gas source change, the flow area of the mutually isolated gas chambers can be changed to adapt to the changed working conditions.

[0038] During specific implementation, it is necessary to first determine the number of mutually isolated gas chambers and the pitch circle diameter of the unit. The principle is: The pressurized tail gas from all gas sources enters a single device, that is, as many mutually isolated gas chambers 85 as possible are set in a single device to correspond to the gas sources one by one.

[0039] 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 5000 Nm3 / h, it is very difficult to design a single unit with more than 16 gas chambers, and the cost will increase sharply. It is necessary to add a multi-gas-chamber unit to receive the tail gas emissions from the remaining gas sources.

[0040] Because the vast majority of the discharge pressures of the pressurized tail gas emissions from multiple gas sources are relatively low (most are below 0.3 MPa gauge pressure) and the flow rates are relatively large, a design method with a large-diameter impeller is selected to increase the flow area. The speed obtained after the tail gas expansion is generally set to twice the pitch circle speed. On this basis, two types of generators 44 with different speeds are selected, the generator 44 with two pole pairs at 3000 rpm and the generator 44 with four pole pairs at 1500 rpm.

[0041] In most cases, especially when the pressurized tail gas pressure is less than 0.2 MPa and the flow rate is greater than 30000 Nm3 / h, since the pitch circle diameter is relatively large, the speed obtained after the tail gas expansion in the single-stage case can generally be set to twice the pitch circle speed. However, when the pressure of the pressurized tail gas is greater than 0.2 MPa and the flow rate is small, in order to increase the conversion efficiency, a small-diameter high-speed single-stage turbine is generally selected for the impeller diameter. Here, we should avoid using the structure of a multi-stage turbine, because if a multi-stage turbine structure is adopted, there will be a certain pressure after the first stage, and after the first stage, multiple gas sources have been aggregated together. If there is a certain pressure, it will cause the tail gas to flow back to the gas source with a relatively low pressure.

[0042] All gas sources enter the unit to do work and converge in the exhaust cylinder 52, and are then discharged through the exhaust pipeline 3 to the tail gas treatment device of the original process. According to the size of the aggregated gas volume, the inlet diameter of the tail gas treatment process, the pipeline length, and the number of valve elbows, etc., the pipeline resistance is calculated to prevent the pressure in the exhaust cylinder 52 of all gas sources from being too high, causing the tail gas to flow back to a gas source with a low pressure.

[0043] According to the above five points, the number of gas chambers where single devices are isolated from each other is mainly considered: Whether it will cause exhaust backpressure (production process safety).

[0044] The ratio of the flow velocity of the expanded gas to the velocity at the pitch circle (high or low conversion efficiency). 3. The external dimensions of the unit (economy).

[0045] Next, determine the number and geometric dimensions of the variable operating condition regulating valves for each gas chamber. Determine the number of regulating valves according to the operating conditions of the corresponding gas source. Generally, it is based on the flow operating conditions of the corresponding gas source (the flow variable operating condition points with obvious step differences). The number of regulating valves is generally one less than the number of variable operating condition points.

[0046] Determine the number of nozzles blocked by each valve head according to the tail gas flow rate of each operating condition and the flow-through size of the nozzles of a single turbine, and then the size of the valve head can be determined.

[0047] Determine the lifting force required to open the valve according to the size of the valve head and the pressure difference before and after the valve head. Determine the stroke required for full opening according to the size of the valve head. After determining the lifting force and stroke, an appropriate actuator can be selected.

[0048] Based on the number of regulating valves, the geometric dimensions of the valve heads, the stroke of the regulating valves, and the selected external dimensions of the actuator, determine the form and dimensions of the mounting bracket.

[0049] The design of the main components is as follows. For the design of the intake guiding port 6, the main consideration is to reduce the intake resistance, control the exhaust gas introduction speed within 5 - 15 m / s, and control the intake resistance within 50 Pa.

[0050] The design of the nozzle group mainly considers the rationality of the nozzle profile and the need to isolate the nozzle groups from each other. For example, Figure 8 , in the intake cylinder block 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 mutually independent and isolated nozzle groups.

[0051] Regarding the design of the variable-condition regulating valve, the regulating principle of the variable-condition regulating valve causes the actuator to move up and down, driving the connecting rod and the valve head to open and close, corresponding to the number of nozzles, thus achieving the purpose of changing the flow area.

[0052] The working method of the waste gas residual pressure utilization device includes the following steps: S1. Tail gas pretreatment and introduction: The pressurized tail gas generated by the fermentation tank 1 first enters the scrubbing tower 2, and gas-liquid contact purification is carried out through the packing layer or spraying device in the tower to remove particulate matter in the tail gas and avoid clogging of the subsequent nozzle parts 53; the purified tail gas is transported to the housing 4 through the exhaust pipe 3. The pipe diameter is designed according to the maximum tail gas flow rate, the flow velocity is controlled within 10 - 15 m / s, the inner wall is smoothly treated, and the elbows use large curvature radii to reduce the frictional resistance and local resistance losses; S2. Energy conversion and power generation: The tail gas enters the nozzle parts 53 in the housing 4, expands and accelerates in the nozzle parts, converts the pressure energy into kinetic energy, and forms a high-speed air flow; the high-speed air flow impacts the impeller blades 43 to make them rotate, and the impeller blades drive the generator 44 to rotate and generate electricity. The impeller blades are forged from aviation-grade aluminum alloy, the surface is treated with a wear-resistant coating, the blade profile conforms to the gas dynamics principle, and the impact angle is designed to be 30° - 45° to efficiently convert the kinetic energy of the gas flow; S3. Independent treatment of multiple gas sources and anti-cross-flow control: The tail gases of multiple gas sources enter the corresponding isolated air chambers 85 through the intake guiding ports 6 on the outer surface and the upper side of the body 5 respectively. Each air chamber is completely isolated by an annular partition. The partition is welded with stainless steel, and the airtightness test pressure reaches 1.5 times the working pressure to prevent cross-flow; each isolated air chamber corresponds to an independent nozzle module (nozzle parts 53). After the high-pressure tail gas expands and accelerates in its respective nozzle, the pressure rapidly drops to the main pipe pressure (the main pipe pressure is extremely low or slightly negative), avoiding cross-flow and backflow between the gas sources; S4. Variable operating condition adjustment and efficiency optimization: The regulating valve system 8 adjusts according to the changes in the gas source operating conditions (pressure, flow rate): The regulating valve actuator 84 receives the gas source pressure or flow rate signal, drives the regulating valve head 81 to move along the regulating valve guide rod 82 through the regulating valve connecting rod 83, and changes the flow area of the nozzle; 1 - 3 groups of regulating valves can be set in a single air chamber, which are sequentially opened / closed for operating conditions such as full flow rate, 3 / 4 flow rate, 2 / 4 flow rate, 1 / 4 flow rate, etc., 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. Cooperative operation of the auxiliary system and the main shaft system: The bearing housing in the auxiliary system 7 adopts a water-cooled structure, with a cooling water flow rate of 2 - 3 m³ / h and an inlet and outlet temperature difference ≤ 15°C. Double-row angular contact ball bearings are selected for the bearings to ensure the stable operation of the main shaft system 9. The chassis is fixed on a concrete foundation with a compressive strength ≥ C30. The auxiliary cylinder quickly cuts off the gas source within 0.3 s in case of emergency; The main shaft system 9 adopts a stepped shaft made of 42CrMo material, 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 more than 20% higher than the operating speed to ensure rotational stability; S6. Tail gas collection and emission: The tail gas after work in each air chamber is collected in the exhaust cylinder 52. The exhaust cylinder is an annular collection chamber, and the cross-sectional area is designed according to the total exhaust gas volume. The gas flow velocity ≤ 25 m / s. The external 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 pipeline. By calculating the pipeline resistance (considering 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.

[0053] Working principle: The pressurized tail gas generated by the fermenter 1 is purified by the scrubber 2. A packing layer or a spraying device is arranged inside the scrubber 2, and gas-liquid contact purification is realized through the circulating scrubbing 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 housing 4 through the exhaust pipeline 3. The diameter of the exhaust pipeline 3 is designed according to the maximum tail gas flow rate, and the flow velocity is controlled at 10 - 15 m / s to reduce the frictional resistance along the way. The inner wall of the pipeline is made smooth, and the elbows are designed with a large curvature radius to reduce the local resistance loss. The nozzle part 53 in the housing 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 gas flow, which impacts the impeller blades 43 to rotate and drives the generator 44 to generate electricity. The impeller blades 43 are forged from aviation-grade aluminum alloy, and the surface is treated with a wear-resistant coating. The blade profile conforms to the gas dynamics principle, and the impact angle is designed to be 30° - 45° to ensure the efficient conversion of gas kinetic energy into rotational mechanical energy; The intake guide port 6 has a horn-shaped tapered structure inside. The inlet cross-sectional area is calculated based on the maximum flow rate of the corresponding gas source to ensure that the intake speed ≤ 15 m / s and the resistance loss < 50 Pa. 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 airtightness test pressure reaches 1.5 times the working pressure to ensure no risk of air leakage. The bearing housing in the auxiliary system 7 adopts a water-cooled structure, with a cooling water flow rate of 2 - 3 m³ / h and an inlet and outlet temperature difference ≤ 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 through anchor bolts, and the compressive strength of the foundation ≥ C30. The auxiliary cylinder is used to quickly cut off the gas source in case of emergency, with a response time ≤ 0.3 s. The main shaft system 9 adopts a stepped shaft structure, with a shaft diameter of φ80 - φ120 mm, made of 42CrMo material, and the quenched and tempered hardness is 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 working speed. The regulating valve system 8 can adjust the 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 regulation; The intake cylinder block 51 is used to guide the high-pressure tail gas into the nozzle part 53. It adopts a segmented structure, with each segment corresponding to an intake air chamber, and is connected by bolts. The sealing surface uses a metal wound gasket. The inner wall is machined with a diversion groove matching the nozzle part 53, with a groove depth of 10 - 15 mm and a width designed according to the spacing of the nozzle partition ribs 533 to guide the tail gas into the nozzle part 53 evenly. The exhaust cylinder 52 collects the tail gas after work and discharges it. It is an annular collection chamber, and the cross-sectional area is designed according to the total exhaust volume. The gas flow velocity ≤ 25 m / s. A pressure gauge and a temperature sensor are arranged on the outside to monitor the exhaust parameters in real time. It is connected to the body 5 through a flange, and the roughness of the flange sealing surface Ra ≤ 3.2 μm to ensure no leakage; The regulating valve head 81 has a disc-shaped structure, with a fluororubber sealing layer covering the surface. The hardness of the sealing layer is 60 ± 5 Shore A to ensure that the leakage amount < 0.5% of the rated flow rate when closed. It realizes linear motion guidance through the regulating valve guide rod 82. The guide rod uses a chrome-plated optical axis and is matched with a linear bearing, with a friction coefficient < 0.05. The regulating valve actuator 84 selects an electric servo actuator, with a rated thrust of 500 - 1000 N, a positioning accuracy of ± 0.5 mm, and a response time < 0.3 s. The output end is connected to the regulating valve head 81 through the regulating valve connecting rod 83, and a universal joint 86 is arranged in the middle, allowing a ± 5° deflection to compensate for the center offset caused by installation errors and thermal deformation, preventing jamming. The actuator mounting plate 87 is fixed to the body 5 with high-strength bolts, and the flatness of the mounting surface ≤ 0.1 mm to ensure that the coaxiality of the actuator axis and the regulating valve head 81 axis < 0.2 mm. 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 the isolation air chamber 85 prevents air leakage between different air chambers; The nozzle partition ribs 533 separate the airflows of different air chambers, with a thickness of 5 - 8 mm, corresponding one-to-one with the air chamber partition ribs, dividing the nozzle part 53 into independent flow channels. The number of flow channels is the same as the number of intake air chambers, with a typical value of 8 - 16. The number of nozzle air vanes 534 in each flow channel is 18 - 24. A three-dimensional flow design is adopted, with the blade installation angle of 35° - 45°. The throat cross-sectional area is designed according to 1 / 4 of the maximum flow rate of the air source to ensure uniform acceleration of the airflow. Between the nozzle outer ring 531 and the nozzle inner ring 532, they are connected by 6 - 8 guide columns 535, which are evenly distributed circumferentially, with a radial runout ≤ 0.08 mm. The material is 304 stainless steel, with a diameter of 10 - 15 mm, providing radial support to prevent nozzle deformation. The work unit 54 on the outer surface of the body 5 is of a groove structure, with a depth of 20 - 30 mm, aligned with the outlet position of the nozzle air vanes 534. The inner wall is sprayed with a ceramic coating with a thickness of 0.3 mm and a hardness ≥ HV1000 to reduce airflow erosion and wear and receive high-speed airflow to achieve energy conversion. The nozzle air vanes 534 guide the airflow to accelerate, the guide columns 535 support the nozzle structure, and the work unit 54 receives high-speed airflow to achieve energy conversion.

[0054] Obviously, those skilled in the art can make various modifications and variations to the present invention without departing from the spirit and scope of the present invention. Thus, if these modifications and variations of the present invention fall within the scope of the claims of the present invention and their equivalent technologies, the present invention is also intended to include these modifications and variations.

Claims

1. An exhaust gas residual pressure utilization device, comprising two fermentation tanks (1) and a machine body (5), characterized in that: On one side of the two fermentation tanks (1), there is a scrubbing tower (2). On one side of the scrubbing tower (2), there is an exhaust pipeline (3) connected. And on one side of the exhaust pipeline (3), there is a shell (4) fixedly connected. Inside the shell (4), there is a nozzle member (53). On one side of the shell (4), there is an internal chamber of the unit (41). On one side of the shell (4), there is a generator (44). And on one side of the generator (44), there is an impeller blade (43) electrically connected. One side of the impeller blade (43) is in movable contact with the nozzle member (53).

2. The waste gas residual pressure utilization device according to claim 1, characterized in that: On the outer surface and the upper side of the body (5), there are intake air guiding ports (6) symmetrically arranged. On one side of the body (5), there is an auxiliary system (7). And on one side of the auxiliary system (7), there is a main shaft system (9). Inside the body (5), there is a regulating valve system (8).

3. An exhaust gas residual pressure utilization device according to claim 2, characterized in that: Inside the body (5), there is an intake cylinder block (51) fixedly arranged. The nozzle member (53) is located inside the body (5). On the outside of the nozzle member (53), there is an exhaust cylinder (52). And the exhaust cylinder (52) is fixedly connected to the body (5).

4. The waste gas residual pressure utilization device according to claim 3, characterized in that: The regulating valve system (8) includes a regulating valve head (81). And between the regulating valve head (81) and the body (5), there are regulating valve guide rods (82) symmetrically fixedly connected. Inside the intake air guiding port (6), there is an isolation air chamber (85). On one side of the regulating valve head (81), there is a regulating valve connecting rod (83). Inside the body (5), there is a regulating valve actuator (84) fixedly arranged. And the output end of the regulating valve actuator (84) is connected to the regulating valve connecting rod (83).

5. The waste gas residual pressure utilization device according to claim 4, wherein: The auxiliary system (7) includes a bearing seat, bearings, a chassis, and an auxiliary cylinder.

6. The waste gas residual pressure utilization device according to claim 5, characterized in that: 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). On the outside of the nozzle inner ring (532), there are nozzle partition ribs (533) and nozzle air vanes (534) symmetrically fixedly arranged in a circular distribution.

7. The waste gas residual pressure utilization device according to claim 6, characterized in that: Between the outside of the nozzle outer ring (531) and the nozzle inner ring (532), there are guide columns (535) symmetrically connected in a circular distribution.

8. The waste gas residual pressure utilization device according to claim 7, characterized in that: On the outer surface of the body (5), there are work units (54) symmetrically arranged. And the work units (54) are located between the air chamber partition ribs and the nozzle partition ribs (533).

9. The waste gas residual pressure utilization device according to claim 8, wherein: Between one side of the regulating valve head (81) and the regulating valve connecting rod (83), there is a universal joint (86) rotatably connected. On the body (5), there is an actuator mounting plate (87) fixedly arranged. The regulating valve actuator (84) is fixedly arranged on the actuator mounting plate (87).

10. A working method of an exhaust gas residual pressure utilization device according to claim 9, characterized in that, Including the following steps: S1. Tail gas pretreatment and introduction: The pressurized tail gas generated by the fermentation tank (1) first enters the scrubbing tower (2). Through the packing layer or spraying device in the tower, gas-liquid contact purification is carried out to remove particulate matter in the tail gas and avoid blockage of the subsequent nozzle member (53). The purified tail gas is transported to the shell (4) through the exhaust pipeline (3). The pipe diameter is designed according to the maximum tail gas flow rate, and the flow velocity is controlled at 10 - 15 m / s. The inner wall is smoothly processed and the elbows adopt large curvature radii to reduce the frictional resistance and local resistance loss along the way; S2. Energy conversion and power generation: The exhaust gas enters the nozzle part (53) inside the housing (4), expands and accelerates in the nozzle part, converts the pressure energy into kinetic energy, and forms a high-speed air flow; the high-speed air flow impacts the impeller blades (43) to make them rotate, and the impeller blades drive the generator (44) to rotate and generate electricity. The impeller blades are forged from aerospace-grade aluminum alloy, the surface is treated with a wear-resistant coating, the blade profile conforms to the gas dynamics principle, and the impact angle is designed to be 30°-45° to efficiently convert the kinetic energy of the gas flow; S3. Multi-gas-source independent treatment and anti-gas-crossing control: The exhaust gases of multiple gas sources enter the corresponding isolation gas chambers (85) respectively through the air intake guiding ports (6) on the outer surface and the upper side of the machine body (5). Each gas chamber is completely isolated by an annular partition. The partition is welded with stainless steel, and the airtightness test pressure reaches 1.5 times the working pressure to prevent gas crossing; Each isolation gas chamber corresponds to an independent nozzle module (nozzle part 53). After the high-pressure exhaust gas expands and accelerates in its respective nozzle, the pressure rapidly drops to the main pipe pressure (the main pipe pressure is extremely low or slightly negative), avoiding gas crossing and backflow between gas sources; S4. Variable-condition regulation and efficiency optimization: The regulating valve system (8) adjusts according to the changes in the gas source conditions (pressure, flow rate): The regulating valve actuator (84) receives the gas source pressure or flow rate signal, drives the regulating valve head (81) to move along the regulating valve guiding rod (82) through the regulating valve connecting rod (83), and changes the nozzle flow area; 1-3 groups of regulating valves can be set in a single gas chamber, which are sequentially opened / closed for working conditions such as full flow, 3 / 4 flow, 2 / 4 flow, 1 / 4 flow, etc., 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 deformations and prevent jamming; S5. Cooperative operation of the auxiliary system and the main shaft system: The bearing housing in the auxiliary system (7) adopts a water-cooled structure, the cooling water flow rate is 2-3 m³ / h, and the inlet and outlet temperature difference ≤ 15°C. Double-row angular contact ball bearings are selected for the bearings to ensure the stable operation of the main shaft system (9). The chassis is fixed on a concrete foundation with a compressive strength ≥ C30. The auxiliary cylinder can quickly cut off the gas source within 0.3 s in case of emergency; The main shaft system (9) adopts a stepped shaft made of 42CrMo material, the quenched and tempered hardness is 28-32 HRC, the support span is optimized according to the impeller diameter, and the critical speed is more than 20% higher than the working speed to ensure rotational stability; S6. Exhaust gas collection and discharge: The exhaust gases after working in each gas chamber are collected in the exhaust cylinder (52). The exhaust cylinder is an annular collection chamber, and the cross-sectional area is designed according to the total exhaust gas volume. The gas flow velocity ≤ 25 m / s. The external 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 pipe resistance (considering the gas volume, inlet diameter, pipe length, number of valves and elbows, etc.), 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.

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