System for utilizing pressure difference and waste heat of exhaust gas in pneumatic test of turbomachinery

Abstract

The invention relates to a turbomachinery pneumatic test exhaust gas pressure difference and waste heat utilization system which comprises an evaporation pressure stabilizer, high-temperature and high-pressure exhaust gas is introduced into the evaporation pressure stabilizer, and an exhaust gas outlet of the evaporation pressure stabilizer is connected with a first turbo expander through a second pipeline. High-temperature low-pressure organic working medium steam of the evaporation pressure stabilizer is communicated with a second turbo expander through a third pipeline, and the output end of the first turbo expander and the output end of the second turbo expander are connected with a first magnetic suspension generator and a second magnetic suspension generator respectively. Low-temperature and low-pressure gas of the first turbo expander communicates with a first heat exchange channel in the condenser through a fourth pipeline, and low-pressure organic working medium steam of the second turbo expander communicates with a second heat exchange channel of the condenser through a fifth pipeline. According to the system, input high-pressure gas can be decompressed to generate power into low-pressure gas, meanwhile, the cooling capacity of the low-temperature gas is recycled through the organic Rankine cycle, and the residual pressure and the residual heat of the gas can be fully utilized.

Description

Technical Field

[0001] The present invention relates to the technical field of waste heat utilization in pneumatic tests of turbomachinery. Specifically, it relates to a differential pressure and waste heat utilization system for the discharged gas in the pneumatic test of turbomachinery. Background Art

[0002] Currently, the pneumatic performance test of turbomachinery is an important means to study the internal gas flow characteristics of turbomachinery and evaluate its performance. Turbomachinery is a device that converts the energy of a fluid into mechanical energy or converts mechanical energy into the energy of a fluid. In the pneumatic performance test, in order to simulate the actual working conditions, the fluid is usually made to flow at high speed and undergo energy conversion in the turbomachinery. For example, in the test of a gas turbine, fuel combustion generates high-temperature and high-pressure gas. The gas expands and does work in the turbine, converting heat energy into mechanical energy, and at the same time discharging high-temperature and high-pressure waste gas. At present, there is no good utilization of this part of the gas and its pressure, resulting in waste of waste heat and residual energy in papermaking. Summary of the Invention

[0003] The present invention aims to solve at least one of the technical problems in the related art to some extent.

[0004] Therefore, an embodiment of the present invention provides a differential pressure and waste heat utilization system for the discharged gas in the pneumatic test of turbomachinery. Without generating additional carbon emissions, this differential pressure and waste heat utilization system can reduce the pressure of the input high-pressure gas to generate electricity to a low-pressure gas. During the pressure reduction process, the temperature of the gas drops, and the organic Rankine cycle is used to recover the cold energy of the low-temperature gas, making full use of the residual pressure and waste heat of the gas.

[0005] The differential pressure and waste heat utilization system for the exhaust gas of the turbomachinery aerodynamic test in the embodiments of the present invention includes: an evaporation pressure stabilizer. The high-temperature and high-pressure exhaust gas from the turbomachinery aerodynamic test is introduced into the evaporation pressure stabilizer through a first pipeline. The exhaust gas outlet of the evaporation pressure stabilizer is connected to a first turbine expander through a second pipeline. The high-temperature and low-pressure organic working medium steam of the evaporation pressure stabilizer is respectively connected to a second turbine expander through a third pipeline. The output ends of the first turbine expander and the second turbine expander are respectively connected to a first magnetic levitation generator and a second magnetic levitation generator. The low-temperature and low-pressure gas of the first turbine expander is connected to a first heat exchange channel in a condenser through a fourth pipeline. The low-pressure organic working medium steam of the second turbine expander is connected to a second heat exchange channel in the condenser through a fifth pipeline. A normal-temperature gas discharge port communicating with the first heat exchange channel is arranged on the condenser. The second heat exchange channel of the condenser is connected to the evaporation pressure stabilizer through a sixth pipeline. Among them, the first pipeline, the evaporation pressure stabilizer, the first turbine expander and the first magnetic levitation generator form a differential pressure power generation system. The evaporation pressure stabilizer, the second turbine expander, the second magnetic levitation generator and the condenser form a low-temperature power generation system. The differential pressure power generation system utilizes the differential pressure of the high-temperature and high-pressure exhaust gas to generate electricity through the first turbine expander and the first magnetic levitation generator. At the same time, the high-temperature steam generated by the evaporation pressure stabilizer can act on the second turbine expander to generate electricity through the second magnetic levitation generator. Then, the heat exchange between the exhaust gas and the organic working medium is realized through the condenser, achieving the full utilization of waste heat. Therefore, this system combines and couples the utilization of differential pressure and waste heat, and adopts a magnetic levitation generator, which can ensure the efficient conversion of pressure energy, mechanical energy and electrical energy, and greatly improve the energy utilization rate of the system.

[0006] Further, a pressure monitoring device and a pressure regulating valve are arranged on the second pipeline, which can monitor the gas pressure entering the first magnetic levitation generator. The pressure regulating valve can control the opening degree of the gas flow to increase or decrease according to whether the detected value of the pressure monitoring device is less than or greater than the predetermined pressure range.

[0007] And / or, an emergency branch is further arranged on the second pipeline. A cut-off valve is arranged between the emergency branch and the second pipeline. When the system is working normally, the cut-off valve is opened and the emergency branch is closed. When the pressure regulating valve cannot adjust the pressure to the predetermined pressure range, the cut-off valve is closed and the emergency branch is opened, ensuring the safety of the system.

[0008] Further, a check valve is installed on the first pipeline to prevent the high-temperature and high-pressure exhaust gas from flowing back to the turbomachinery aerodynamic performance test bench.

[0009] Preferably, the condenser is a shell-and-tube heat exchanger, a finned-tube heat exchanger or a plate heat exchanger, which can achieve sufficient heat exchange, convert the low-temperature waste gas into normal-temperature gas, and at the same time convert the gaseous organic working medium into a liquid working medium for recycling.

[0010] Preferably, the evaporation pressure stabilizer includes an evaporation chamber and a waste gas chamber which are separated up and down. A steam outlet for connecting with the third pipeline is connected to the evaporation chamber. A pressure stabilizing system is arranged between the evaporation chamber and the steam outlet. The evaporation chamber is filled with an organic working medium.

[0011] Heat pipes are evenly distributed in the evaporation pressure stabilizer, and each heat pipe includes a condensation section located in the evaporation chamber and an evaporation section located in the waste gas chamber.

[0012] The waste gas chamber is provided with a waste gas inlet communicating with the first pipeline and a waste gas outlet communicating with the second pipeline. The evaporation chamber, the waste gas chamber and the pressure stabilizing system are integrated together, with a compact structure, and can be installed as a whole. The number of heat pipes is large and they are evenly arranged, so that heat absorption and heat release are carried out simultaneously, the heat exchange efficiency is high, and the evaporation temperature can be flexibly controlled.

[0013] Preferably, the pressure stabilizing system includes a pipeline connecting the steam outlet and the evaporation chamber, and a pressure monitor and a solenoid valve are arranged on the pipeline.

[0014] And / or, the evaporation chamber and the pressure stabilizing system are separated by a first partition plate.

[0015] The steam pressure in the pressure stabilizing system can be monitored in real time through the pressure monitor. After the pressure reaches the set value, the solenoid valve opens and discharges from the steam outlet, so that the power generation of the low-temperature power generation system is relatively stable.

[0016] Preferably, a second partition plate extending towards the waste gas chamber is arranged in the middle of the third partition plate, and third partition plates connected to the bottom of the evaporation chamber are arranged around the second partition plate. The space between the third partition plate and the second partition plate and the space inside the second partition plate form a steam guiding channel communicating with the pressure stabilizing system. The saturated steam generated by the heated organic working medium can enter the pressure stabilizing system along the steam guiding channel. The flow efficiency of the steam is high, and the saturated steam is further heated after being diverted by the third partition plate to form superheated high-pressure steam, which can improve the utilization of waste heat.

[0017] Preferably, a fourth partition and a fifth partition are provided between the evaporation chamber and the exhaust gas chamber. A porous medium material is filled between the fourth partition and the fifth partition. The heat pipe penetrates through the fourth partition and the fifth partition. The porous medium material can effectively prevent the liquid organic working medium from entering the exhaust gas chamber. At the same time, the porous medium material has a large specific surface area and good thermal conductivity, which can increase the heat transfer area and heat transfer efficiency between the evaporation chamber and the exhaust gas chamber;

[0018] And / or, a liquid storage tank for storing the organic working medium is communicated with one side of the evaporation chamber. The sixth pipeline is communicated with the liquid storage tank. The pressure of the steam can be controlled by controlling the flow rate of the organic working medium input from the liquid storage tank into the evaporation chamber.

[0019] Preferably, the exhaust gas inlet is arranged in the middle of the exhaust gas chamber, and the exhaust gas outlet is arranged on the side of the exhaust gas chamber. A spiral flow passage extending from the middle to the side is formed in the exhaust gas chamber by a wind guiding plate. The heat pipes are uniformly arranged along the spiral flow passage, so that the high-temperature waste heat exhaust steam can flow quickly along the spiral flow passage and be discharged smoothly from the exhaust gas outlet. In this way, the heat exchange time between the hot exhaust gas and the evaporation section of the heat pipe can be increased, and the energy in the heat source can be utilized to the greatest extent.

[0020] Preferably, fins are arranged on the outer wall of the evaporation section of the heat pipe, which can improve the heat absorption efficiency of the evaporation section.

[0021] Compared with the prior art, the present invention has the following beneficial effects:

[0022] It has a pressure difference power generation system and a low-temperature power generation system that are independent of each other and coupled together. Among them, the first pipeline, the evaporation pressure stabilizer, the first turbine expander and the first magnetic levitation generator constitute the pressure difference power generation system, and the evaporation pressure stabilizer, the second turbine expander, the second magnetic levitation generator and the condenser constitute the low-temperature power generation system. The pressure difference power generation system utilizes the pressure difference of the high-temperature and high-pressure discharged exhaust gas to generate electricity through the first turbine expander and the first magnetic levitation generator. At the same time, the high-temperature steam generated by the evaporation pressure stabilizer can act on the second turbine expander to generate electricity through the second magnetic levitation generator, and then the heat exchange between the exhaust gas and the organic working medium is realized through the condenser, achieving the full utilization of waste heat. Therefore, this system combines and couples the pressure difference and waste heat for utilization, and uses a magnetic levitation generator, which can ensure the efficient conversion of pressure energy, mechanical energy and electrical energy, and greatly improve the energy utilization rate of the system;

[0023] The evaporation pressure stabilizer integrates the evaporation chamber, the exhaust gas chamber and the pressure stabilizing system, with a compact structure, and can be installed as a whole. The exhaust gas inlet is used to connect with the high-temperature waste heat exhaust steam to make full use of its waste heat. There are many heat pipes and they are uniformly arranged, absorbing heat and releasing heat simultaneously, with high heat exchange efficiency, and the evaporation temperature can be flexibly controlled. Brief Description of the Drawings

[0024] Figure 1 is the system schematic diagram of the embodiment of the present invention.

[0025] Figure 2 is the overall sectional structure diagram of the embodiment of the present invention;

[0026] Figure 3 is the schematic diagram of the exhaust gas chamber air guide plate of the embodiment of the present invention.

[0027] Reference Signs:

[0028] 1. Evaporation pressure stabilizer, 2. First turbine expander, 3. First magnetic levitation generator, 4. Working fluid pump, 5. Condenser, 6. Second magnetic levitation generator, 7. Second turbine expander, 8. First pipeline, 9. Second pipeline, 10. Sixth pipeline, 11. Fourth pipeline, 12. Third pipeline, 13. Fifth pipeline 14. Normal temperature gas discharge port, 101. Pressure stabilization system, 102. Evaporation chamber, 103. Heat pipe, 104. Fourth partition, 105. Exhaust gas outlet, 106. Air guide plate, 107. Exhaust gas inlet, 108. Drainage port, 109. Exhaust gas chamber, 110. Fifth partition, 111. Porous medium material, 112. Liquid storage tank, 113. Third partition, 114. Third partition, 115. Second partition, 116. Steam outlet, 131. Condensation section, 132. Evaporation section. Detailed Description of the Embodiment

[0029] The embodiments of the present invention will be described in detail below. The examples of the embodiments are shown in the drawings. The embodiments described below with reference to the drawings are exemplary and are intended to explain the present invention and should not be construed as limiting the present invention.

[0030] Reference will be made below to the attached Figures 1 to 3 to describe the differential pressure and waste heat utilization system for the exhaust gas discharged in the turbine machinery pneumatic test according to the embodiment of the present invention.

[0031] As Figures 1 to 3As shown in the figure, the differential pressure and waste heat utilization system for the exhaust gas of the turbomachinery aerodynamic test in the embodiment of the present invention includes an evaporation pressure stabilizer 1. The high-temperature and high-pressure exhaust gas from the turbomachinery aerodynamic test is introduced into the evaporation pressure stabilizer 1 through a first pipeline 8. The exhaust gas outlet of the evaporation pressure stabilizer 1 is connected to a first turbine expander 2 through a second pipeline 9. The high-temperature and low-pressure organic working medium steam of the evaporation pressure stabilizer 1 is respectively connected to a second turbine expander 7 through a third pipeline 12. The output ends of the first turbine expander 2 and the second turbine expander 7 are respectively connected to a first magnetic levitation generator 3 and a second magnetic levitation generator 6. The low-temperature and low-pressure gas of the first turbine expander 2 is connected to a first heat exchange channel in a condenser 5 through a fourth pipeline 11. The low-pressure organic working medium steam of the second turbine expander 7 is connected to a second heat exchange channel in the condenser 5 through a fifth pipeline 13. A normal-temperature gas discharge port 14 communicating with the first heat exchange channel is arranged on the condenser 5. The second heat exchange channel of the condenser 5 is connected to the evaporation pressure stabilizer 1 through a sixth pipeline 10. Among them, the first pipeline 8, the evaporation pressure stabilizer 1, the first turbine expander 2, and the first magnetic levitation generator 3 form a differential pressure power generation system. The evaporation pressure stabilizer 1, the second turbine expander 7, the second magnetic levitation generator 6, and the condenser 5 form a low-temperature power generation system. The differential pressure power generation system utilizes the differential pressure of the high-temperature and high-pressure exhaust gas to generate electricity through the first turbine expander 2 and the first magnetic levitation generator 3. At the same time, the high-temperature steam generated by the evaporation pressure stabilizer 1 can act on the second turbine expander 7 to generate electricity through the second magnetic levitation generator 6. The heat exchange between the exhaust gas and the organic working medium is realized through the condenser 5, achieving the full utilization of waste heat. Therefore, this system combines and couples the utilization of differential pressure and waste heat, and adopts a magnetic levitation generator, which can ensure the efficient conversion of pressure energy, mechanical energy, and electrical energy, greatly improving the energy utilization rate of the system.

[0032] Specifically, when the differential pressure power generation system works, the high-temperature and high-pressure exhaust gas from the turbomachinery aerodynamic test enters the evaporation pressure stabilizer 1 through the first pipeline 8, exchanges heat with the heat pipe evaporation section in the evaporation pressure stabilizer 1. The high-temperature and high-pressure gas after heat exchange is introduced into the first turbine expander 2 through the second pipeline 9, driving the first turbine expander 2 to rotate. The rotating first turbine expander 2 drives the first magnetic levitation generator 3 to rotate for power generation.

[0033] At the same time, when the low-temperature power generation system works, the organic working medium is heated inside the evaporation pressure stabilizer 1. The heated organic working medium generates high-pressure steam. After the steam pressure reaches the set value, it is introduced into the second turbine expander 7 through the third pipeline 12. The second turbine expander 7 rotates, and the rotating second turbine expander 7 drives the second magnetic levitation generator 6 to rotate for power generation.

[0034] The normal-temperature and high-pressure waste gas entering the first turbine expander 2 expands and reduces pressure in the first turbine expander 2. During the pressure reduction process, the temperature of the gas drops, forming a low-temperature and low-pressure gas. The low-temperature and low-pressure gas is introduced into the condenser 5 through the fourth pipeline 11 to exchange heat with the low-pressure organic working medium steam discharged from the outside of the second turbine expander 7. After the organic working medium steam cools down, it is liquefied to form a liquefied organic working medium, while the low-temperature gas absorbs heat and warms up to a normal-temperature gas, which is directly discharged from the normal-temperature gas discharge port 14. The liquid-phase organic working medium after heat exchange is introduced into the evaporation stabilizer 1 by the working medium pump 4 on the sixth pipeline 10 for recycling.

[0035] Among them, the first turbine expander 2 and the second turbine expander 7 are turbine machines that convert the internal energy of the gas into mechanical energy. After the high-temperature and high-pressure gas enters the expander, it expands and accelerates in the nozzle, converting the internal energy of the gas into kinetic energy to form a high-speed gas flow. The high-speed gas flow impacts the impeller, causing the impeller to rotate, thereby converting the kinetic energy into mechanical energy and outputting work externally. During this process, the pressure and temperature of the gas decrease significantly, achieving a refrigeration effect.

[0036] The first magnetic levitation generator 3 and the second magnetic levitation generator 6 are generators that use magnetic levitation technology to support rotating components, and have advantages such as high efficiency, low loss, and low noise. They use the acting force of the magnetic field to suspend the rotor in the air, eliminating the mechanical friction between the bearing and the rotating shaft in the traditional generator. Generally, magnetic levitation is achieved through electromagnetic force or permanent magnetic force. For example, the strong magnetic field generated by superconducting materials at low temperatures interacts with permanent magnets, or a controllable magnetic field is generated by an electromagnetic coil to achieve the suspension support of the rotor. Its power generation principle is similar to that of traditional generators.

[0037] In this embodiment, a pressure monitoring device and a pressure regulating valve (not shown in the figure) are provided on the second pipeline 9, which can monitor the gas pressure entering the first magnetic levitation generator 3. The pressure regulating valve can control the gas flow to increase or decrease the opening degree when the detection value of the pressure monitoring device is less than or greater than the predetermined pressure range. Among them, the pressure monitoring device can adopt a mechanical pressure monitoring device, such as a bourdon tube pressure gauge, a diaphragm pressure gauge, a bellows pressure gauge, etc., or an electronic pressure monitoring device, including a piezoresistive pressure sensor, a piezoelectric pressure sensor, a capacitive pressure sensor, etc., or an intelligent pressure monitoring device, which, on the basis of the electronic pressure monitoring device, integrates a microprocessor and a communication function, can automatically collect, process, store, and transmit pressure data, and can realize functions such as remote monitoring and fault diagnosis;

[0038] The basic working principle of the pressure regulating valve is to utilize the throttling effect between the valve core and the valve seat, control the gas flow rate by changing the flow area, and thus achieve the regulation of the outlet pressure. A direct-acting pressure regulating valve can be adopted, which directly utilizes the change of the outlet pressure to drive the movement of the valve core to achieve pressure regulation; or an indirect-acting pressure regulating valve: controls the action of the main valve through a pilot valve. The pilot valve generates a control signal according to the change of the outlet pressure and drives the movement of the main valve core, thereby achieving precise regulation of the outlet pressure.

[0039] And / or, an emergency branch (not shown in the figure) is further provided on the second pipeline 9. A on-off valve is provided between the emergency branch and the second pipeline 9. When the system is working normally, the on-off valve is opened and the emergency branch is closed. When the pressure regulating valve fails to adjust the pressure to the predetermined pressure range, the on-off valve is closed and the emergency branch is opened, ensuring the safety of the system. The combination of the emergency branch and the on-off valve is mainly to meet the safety requirements.

[0040] Meanwhile, a check valve is installed on the first pipeline 8 to prevent the high-temperature and high-pressure exhaust gas from flowing back to the turbine machinery aerodynamic performance test bench.

[0041] In this embodiment, the condenser 5 is a shell-and-tube heat exchanger or a finned-tube heat exchanger or a plate heat exchanger, which can achieve sufficient heat exchange, convert the low-temperature exhaust gas into normal-temperature gas, and at the same time convert the gaseous organic working medium into a liquid working medium for recycling. No matter which type of condenser 5 it is, it must have a first heat exchange channel and a second heat exchange channel inside, and the two media flow independently in the two heat exchange channels for heat exchange.

[0042] As Figures 2 - 3 shown, as a specific embodiment of the evaporation pressure stabilizer 1, the evaporation pressure stabilizer 1 includes an evaporation chamber 102 and an exhaust gas chamber 109 which are separated up and down. A steam outlet 116 for connecting with the third pipeline 12 is connected to the evaporation chamber 102. A pressure stabilizing system 101 is provided between the evaporation chamber 102 and the steam outlet 116. The evaporation chamber 102 is filled with an organic working medium;

[0043] Heat pipes 103 are evenly distributed in the evaporation pressure stabilizer 1, and the heat pipes 103 include a condensation section 131 located in the evaporation chamber 102 and an evaporation section 132 located in the exhaust gas chamber 109;

[0044] An exhaust gas inlet 107 communicating with the first pipeline 8 and an exhaust gas outlet 105 communicating with the second pipeline 9 are provided on the exhaust gas chamber 109. Integrating the evaporation chamber 102, the exhaust gas chamber 109 and the pressure stabilizing system 101 together, the structure is compact and can be installed as a whole. The number of heat pipes 103 is large and evenly arranged, heat absorption and heat release are carried out simultaneously, the heat exchange efficiency is high, and the evaporation temperature can be flexibly controlled.

[0045] Specifically, the evaporation pressure stabilizer in this embodiment can be an integral tank body. The interior of the tank body is divided into upper and lower layers. The upper layer is the evaporation chamber 102, and the organic working fluid filled inside can be vaporized to generate saturated steam under the heating of the heat pipe 103. The lower layer is the waste gas chamber 109, into which high-temperature waste heat exhaust steam is introduced. The high-temperature waste steam can fully exchange heat with the heat pipe 103, heating the heat pipe 103 while reducing the temperature of the high-temperature waste steam. Among them, common organic working fluids include R123, R134a, R245fa, pentane, isopentane, etc. For example, R123 has relatively low critical temperature and pressure and is suitable for medium and low-temperature heat sources; pentane has a relatively low boiling point and can generate a higher cycle efficiency under low-temperature heat sources.

[0046] The pressure stabilization system 101 is used to control the discharge pressure of the high-temperature steam generated by the organic working fluid. Therefore, the stable air pressure entering the second turbine expander 7 can improve the stability of power generation.

[0047] In this embodiment, the pressure stabilization system 101 includes a pipeline connecting the steam outlet 116 and the evaporation chamber 102, and a pressure monitor and a solenoid valve are arranged on the pipeline;

[0048] And / or, the evaporation chamber 102 and the pressure stabilization system 101 are separated by a first partition 113.

[0049] The steam pressure in the pressure stabilization system can be monitored in real time through the pressure monitor. After the pressure reaches the set value, the solenoid valve opens and discharges from the steam outlet 116, so that the power generation of the low-temperature power generation system is relatively stable. The pressure stabilization system 101 can be arranged at the top of the tank body, inside the tank cover arranged at the top of the tank body. The pressure monitor can adopt an electronic pressure monitor to monitor the pressure when high-temperature and high-pressure steam passes through. The specific pressure set value can be set through an external controller, and the solenoid valve can adopt a conventional electric control solenoid valve and be controlled uniformly with the pressure monitor.

[0050] In an alternative embodiment, a second partition 115 extending towards the waste gas chamber 109 is arranged in the middle of the third partition 113. A third partition 114 connected to the bottom of the evaporation chamber 102 is arranged around the second partition 115. The space between the third partition 114 and the second partition 115 and the space inside the second partition 115 enclose a steam guiding channel connected to the pressure stabilization system 101. The saturated steam generated by the heated organic working fluid can enter the pressure stabilization system 101 along the steam guiding channel. The flow efficiency of the steam is high, and the saturated steam is further heated after being diverted by the third partition 114 to form superheated high-pressure steam, which can improve the utilization of waste heat.

[0051] Specifically, the second partition 115 can be cylindrical or square. There is a gap between the lower end of the second partition 115 and the bottom of the evaporation chamber 102. The arrangement shape of the third partition 114 can be the same as that of the second partition 115. A heat pipe 103 can also be arranged within the range enclosed by the second partition 115 and the third partition 114. The evaporation chamber 102 outside the third partition 114 can be defined as an outer circular evaporation zone, where the organic working fluid is concentrated. The heat pipe 103 heats the organic working fluid to form saturated steam. The saturated steam flows upward, crosses the third partition 114, and then flows downward into the inner circular superheat zone enclosed by the third partition 114, where it is further heated by the heat pipe 103 to form high-pressure steam. Then, it enters the channel enclosed by the second partition 115 from bottom to top and smoothly enters the pressure stabilizing system 101.

[0052] Preferably, a fourth partition 104 and a fifth partition 110 are arranged between the evaporation chamber 102 and the exhaust gas chamber 109. A porous medium material 111 is filled between the fourth partition 104 and the fifth partition 110. The heat pipe 103 passes through the fourth partition 104 and the fifth partition 110. The porous medium material 111 can effectively prevent the liquid organic working fluid from entering the exhaust gas chamber 109. At the same time, the porous medium material has a large specific surface area and good thermal conductivity, which can increase the heat transfer area and heat transfer efficiency between the evaporation chamber and the exhaust gas chamber. A sealing structure needs to be made between the heat pipe 103 and the fourth partition 104 and the fifth partition 110, and conventional sealing rings or sealants can be used for sealing. The porous medium material here can be selected as needed, such as metal foam, sintered metal powder material, ceramic porous material, etc.

[0053] And / or, a liquid storage tank 112 for storing the organic working fluid is communicated with one side of the evaporation chamber 102. The sixth pipeline 10 is communicated with the liquid storage tank 112. The pressure of the steam can be controlled by controlling the flow rate of the organic working fluid input from the liquid storage tank 112 into the evaporation chamber 102. A flow control valve for adjusting the flow rate of the organic working fluid can be arranged in the liquid storage tank 112. A liquid level sensor can be installed in the evaporation chamber 2, and the opening and closing of the flow control valve can be controlled according to the value of the liquid level sensor, so as to adjust the flow rate of the organic working fluid and thus control the pressure of the steam.

[0054] In this embodiment, the waste gas inlet 107 is arranged in the middle of the waste gas chamber 109, and the waste gas outlet 105 is arranged on the side of the waste gas chamber 109. A spiral flow channel extending from the middle to the side is formed in the waste gas chamber 109 by a wind guiding plate 106. The heat pipes 103 are uniformly arranged along the spiral flow channel, so that the high-temperature waste heat steam can flow rapidly along the spiral flow channel and be discharged smoothly from the waste gas outlet 105. This can increase the heat exchange time between the hot waste gas and the evaporation section 132 of the heat pipe 103, and utilize the energy in the heat source to the greatest extent.

[0055] To improve the heat exchange efficiency, fins are arranged on the outer wall of the evaporation section 132 of the heat pipe 103, which can improve the heat absorption efficiency of the evaporation section 132. Fins can also be selectively arranged on the evaporation section 132, and the shape of the fins can be selected according to needs, such as straight fins, corrugated fins, spiral fins, etc.

[0056] Meanwhile, a sewage outlet 108 is connected to the bottom of the waste gas chamber 109, which can timely discharge the liquid waste condensed in the waste gas chamber 109 to avoid affecting the heat exchange efficiency.

[0057] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. They are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation of the present invention.

[0058] In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include at least one of these features. In the description of the present invention, "a plurality" means at least two, such as two, three, etc., unless otherwise specifically defined.

[0059] In the present invention, unless otherwise clearly specified or limited, terms such as "installed", "connected", "coupled", "fixed", etc. shall be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; it may be a mechanical connection, an electrical connection, or communicable with each other; it may be directly connected, or indirectly connected through an intermediate medium, and may be the internal communication between two components or the interaction relationship between two components, unless otherwise clearly limited. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0060] In the present invention, unless otherwise clearly specified or limited, the first feature being "on" or "under" the second feature may be that the first and second features are in direct contact, or the first and second features are indirectly in contact through an intermediate medium. Moreover, the first feature being "above", "over" and "on top of" the second feature may be that the first feature is directly above or obliquely above the second feature, or merely indicates that the first feature has a higher horizontal height than the second feature. The first feature being "under", "beneath" and "underneath" the second feature may be that the first feature is directly below or obliquely below the second feature, or merely indicates that the first feature has a lower horizontal height than the second feature.

[0061] In the present invention, terms such as "one embodiment", "some embodiments", "example", "specific example", or "some examples", etc. mean that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in a suitable manner in any one or more embodiments or examples. In addition, without contradiction, those skilled in the art can combine and combine the different embodiments or examples described in this specification and the features of different embodiments or examples.

[0062] Although the above embodiments have been shown and described, it can be understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Any changes, modifications, substitutions, and variations made by those of ordinary skill in the art to the above embodiments are within the protection scope of the present invention.

Claims

1. A differential pressure and waste heat utilization system for the exhaust gas of a turbomachinery pneumatic test, characterized in that Including: An evaporation pressure stabilizer (1), high-temperature and high-pressure exhaust gas from a pneumatic test of a turbomachine is introduced into the evaporation pressure stabilizer (1) through a first pipeline (8). The exhaust gas outlet of the evaporation pressure stabilizer (1) is connected to a first turbine expander (2) through a second pipeline (9). The high-temperature and low-pressure organic working medium steam of the evaporation pressure stabilizer (1) is respectively connected to a second turbine expander (7) through a third pipeline (12). The output ends of the first turbine expander (2) and the second turbine expander (7) are respectively connected to a first magnetic levitation generator (3) and a second magnetic levitation generator (6). The low-temperature and low-pressure gas of the first turbine expander (2) is connected to a first heat exchange channel in a condenser (5) through a fourth pipeline (11). The low-pressure organic working medium steam of the second turbine expander (7) is connected to a second heat exchange channel of the condenser (5) through a fifth pipeline (13). A normal temperature gas discharge port (14) communicating with the first heat exchange channel is arranged on the condenser (5). The second heat exchange channel of the condenser (5) is connected to the evaporation pressure stabilizer (1) through a sixth pipeline (10).

2. The differential pressure and waste heat utilization system for the exhaust gas of the turbomachinery pneumatic test according to claim 1, characterized in that, A pressure monitoring device and a pressure regulating valve are arranged on the second pipeline (9); And / or, an emergency branch is further arranged on the second pipeline (9), and a cut-off valve is arranged between the emergency branch and the second pipeline (9).

3. The differential pressure and waste heat utilization system for the exhaust gas of the turbomachinery pneumatic test according to claim 1, characterized in that A check valve is installed on the first pipeline (8).

4. The differential pressure and waste heat utilization system for the exhaust gas of the turbomachinery pneumatic test according to claim 1, characterized in that The condenser (5) is a shell-and-tube heat exchanger, or a finned-tube heat exchanger, or a plate heat exchanger.

5. The differential pressure and waste heat utilization system for the exhaust gas of the turbomachinery aerodynamic test according to any one of claims 1-4, characterized in that, The evaporation pressure stabilizer (1) includes an evaporation chamber (102) and an exhaust gas chamber (109) which are separated up and down. A steam outlet (116) for connecting with the third pipeline (12) is connected to the evaporation chamber (102). A pressure stabilizing system (101) is arranged between the evaporation chamber (102) and the steam outlet (116). Organic working medium is filled inside the evaporation chamber (102); Heat pipes (103) are evenly distributed in the evaporation pressure stabilizer (1), and each heat pipe (103) includes a condensation section (131) located in the evaporation chamber (102) and an evaporation section (132) located in the exhaust gas chamber (109); The exhaust gas chamber (109) is provided with an exhaust gas inlet (107) communicating with the first pipeline (8) and an exhaust gas outlet (105) communicating with the second pipeline (9).

6. The differential pressure and waste heat utilization system for the exhaust gas of the turbomachinery pneumatic test according to claim 5, characterized in that, The pressure stabilizing system (101) includes a pipeline connecting the steam outlet (116) and the evaporation chamber (102), and a pressure monitor and a solenoid valve are arranged on the pipeline; And / or, the evaporation chamber (102) and the pressure stabilizing system (101) are separated by a first partition (113).

7. The differential pressure and waste heat utilization system for the exhaust gas of the turbomachinery pneumatic test according to claim 6, characterized in that, A second partition (115) extending towards the exhaust gas chamber (109) is arranged in the middle of the third partition (113). A third partition (114) connected to the bottom of the evaporation chamber (102) is arranged around the second partition (115). The space between the third partition (114) and the second partition (115) and the space inside the second partition (115) form a steam guiding channel communicating with the pressure stabilizing system (101).

8. The differential pressure and waste heat utilization system for the exhaust gas of the turbomachinery pneumatic test according to claim 5, characterized in that, A fourth partition plate (104) and a fifth partition plate (110) are provided between the evaporation chamber (102) and the exhaust gas chamber (109). A porous medium material (111) is filled between the fourth partition plate (104) and the fifth partition plate (110). The heat pipe (103) is penetrated through the fourth partition plate (104) and the fifth partition plate (110). And / or, a liquid storage tank (112) for storing an organic working medium is communicated with one side of the evaporation chamber (102). The sixth pipeline (10) is communicated with the liquid storage tank (112).

9. The differential pressure and waste heat utilization system for the exhaust gas of the turbomachinery pneumatic test according to claim 5, wherein, The exhaust gas inlet (107) is arranged in the middle of the exhaust gas chamber (109), and the exhaust gas outlet (105) is arranged at the side of the exhaust gas chamber (109). A spiral flow passage extending from the middle to the side is formed in the exhaust gas chamber (109) by a wind guiding plate (106). The heat pipes (103) are uniformly arranged along the spiral flow passage.

10. The differential pressure and waste heat utilization system for the exhaust gas of the turbomachinery pneumatic test according to claim 5, characterized in that, Fins are arranged on the outer wall of the evaporation section (132) of the heat pipe (103).

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