A self-pressurized magnetic levitation low-temperature waste heat power generation system

Abstract

The present invention relates to a self-pressurized magnetic levitation low-temperature waste heat power generation system, comprising a preheater, wherein a working fluid outlet I of the preheater is connected to a working fluid inlet I of an evaporator, a working fluid outlet II of the evaporator is connected to a working fluid inlet II of a magnetic levitation turbine generator, a working fluid outlet III of the magnetic levitation turbine generator is connected to a heat exchange inlet I of the preheater, a heat exchange outlet I of the preheater is connected to a heat exchange inlet II of an air-cooled condenser, a heat exchange outlet II of the air-cooled condenser is connected to an inlet I of a low-pressure buffer tank, an outlet I of the low-pressure buffer tank is connected to an inlet II of a piston cylinder, an outlet II of the piston cylinder is connected to an inlet III of a high-pressure buffer tank, and an outlet III of the high-pressure buffer tank is connected to a working fluid inlet III of the preheater. This invention has low energy consumption and high power generation efficiency.

Description

Technical Field

[0001] The present invention relates to a power generation system, in particular to a low-temperature waste heat power generation system. Background Art

[0002] Processing, manufacturing, metallurgy, smelting, and waste incineration (disposal) industries constantly generate heat-containing gases. While some large enterprises recycle high-temperature gases, they don't fully utilize gases below (or even below) 250°C due to the high cost of recycling. This phenomenon is extremely common and represents a significant waste of energy.

[0003] The principle of the Organic Rankine Cycle is to fully utilize the energy-saving and high-speed characteristics of the magnetic levitation generator. It converts industrial low-temperature (80℃-250℃) waste hot liquid and waste hot flue gas into high-pressure organic vapor through heat exchange, thereby driving the magnetic levitation turbine generator to generate electricity, maximizing the energy obtained from the waste gas, achieving zero fuel (excluding waste heat costs), reducing heat emissions, efficiently recovering waste heat, and outputting clean electricity.

[0004] At present, the common low-temperature waste heat power generation system includes an evaporator, a turbine generator, a condenser, a working fluid pump and a cooling tower. The condenser is used to cool the working fluid, and the condenser is cooled by a cooling tower. The cooling tower generally adopts water cooling, and has a relatively complex structure and high energy consumption. In addition, the working fluid pump is used to transport the working fluid, which has high energy consumption. Summary of the Invention

[0005] Purpose of the invention: The purpose of the present invention is to overcome the deficiencies in the prior art and provide a self-pressurized magnetic levitation low-temperature waste heat power generation system with low energy consumption and high power generation efficiency.

[0006] Technical solution: In order to solve the above technical problems, the present invention provides a self-pressurized magnetic levitation low-temperature waste heat power generation system, which includes a preheater, wherein the working fluid outlet I of the preheater is connected to the working fluid inlet I of the evaporator, the working fluid outlet II of the evaporator is connected to the working fluid inlet II of the magnetic levitation turbine generator, the working fluid outlet III of the magnetic levitation turbine generator is connected to the heat exchange inlet I of the preheater, the heat exchange outlet I of the preheater is connected to the heat exchange inlet II of the air-cooled condenser, the heat exchange outlet II of the air-cooled condenser is connected to the inlet I of the low-pressure buffer tank, the outlet I of the low-pressure buffer tank is connected to the inlet II of the piston cylinder, and the piston cylinder is connected to the working fluid outlet I of the preheater. Outlet II of the cylinder is connected to inlet III of the high-pressure buffer tank, which is connected to the working medium inlet III of the preheater. The piston cylinder is connected to a two-position four-way solenoid valve. A self-operated pressure reducing valve is provided on pipe I between the working medium outlet II of the evaporator and the working medium inlet II of the magnetic levitation turbine generator. Port I of the two-position four-way solenoid valve is connected to pipe I at the front end of the self-operated pressure reducing valve. A bypass pipe is provided between pipe I at the rear end of the self-operated pressure reducing valve and pipe II connected to the working medium inlet II of the magnetic levitation turbine generator. A regulating valve is provided on the bypass pipe. Port II of the two-position four-way solenoid valve is connected to pipe II.

[0007] The air-cooled condenser includes a connecting seat, a shell and a lower header, an upper header is provided in the connecting seat, and a plurality of condensing tubes are provided on the inner side of the shell between the upper header and the lower header, the condensing tubes are divided into a large diameter section, a medium diameter section and a small diameter section, one end of the large diameter section is connected to the upper header, and one end of the small diameter section is connected to the lower header, cooling fins are provided on the medium diameter section and the small diameter section of the condensing tube, an air duct is provided in the middle of the connecting seat, the air duct is connected to the inside of the shell, a fan is provided in the air duct, an upper header inlet I and an upper header inlet II are provided on the connecting seat, the upper header inlet I and the upper header inlet II are connected to the upper header, and a lower header outlet is provided on the lower header.

[0008] Furthermore, a heat source inlet and a heat source outlet are provided on the evaporator.

[0009] Furthermore, the working fluid used in the evaporator is pentafluoropropane.

[0010] Furthermore, the shell includes a rectangular surface I, a trapezoidal surface I, a rectangular surface II and a trapezoidal surface II, which are connected in sequence.

[0011] Furthermore, the upper header inlet I and the upper header inlet II are arranged at two opposite corners of the connecting seat.

[0012] Furthermore, the condenser tubes are arranged in two rows, one row is arranged on the inner side of the rectangular surface I, and the other row is arranged on the inner side of the rectangular surface II.

[0013] Furthermore, the inner diameter ratio of the large diameter section, the medium diameter section and the small diameter section of the condenser tube is (15-17): (6-8): (2-4).

[0014] Beneficial effect: Compared with the prior art, the present invention has the following significant advantages: the overall structure of the present invention is reasonably set up, the working fluid directly enters the condenser tube in the air-cooled condenser for heat exchange, and the condenser tube adopts a segmented + fin structure. The first section of the condenser tube is for gaseous working fluid cooling, adopts a large diameter and low flow rate, the second section is for gaseous working fluid condensation into liquid, adopts heat dissipation fins to increase the heat exchange area, the diameter becomes smaller, and the flow rate is maintained at a low level, the third section is for liquid working fluid cooling, adopts heat dissipation fins, and the tube diameter is the smallest. The inner diameter ratio of the large diameter section, the medium diameter section and the small diameter section is (15-17): (6-8): (2-4), the three-section structure optimizes the flow rate, reduces pipeline loss, and adopts air cooling as a whole, does not require circulating cooling water, and does not require spraying water. This system adopts ORC cycle, the working fluid is pentafluoropropane, the heat source is steam, and the cold source is air, realizing two-stage evaporation and two-stage cooling, adopts cylinder piston to provide pressurization, does not require motor drive, reduces energy consumption, and has high power generation efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 It is a schematic diagram of the connection structure of the present invention;

[0016] Figure 2 It is a schematic diagram of the front internal structure of the air-cooled condenser of the present invention;

[0017] Figure 3 It is a schematic diagram of the side internal structure of the air-cooled condenser of the present invention;

[0018] Figure 4 It is a top view of the air-cooled condenser of the present invention. DETAILED DESCRIPTION

[0019] The present invention will be further described below with reference to the accompanying drawings and examples.

[0020] like Figure 1 、 Figure 2 、 Figure 3 and Figure 4As shown, the self-pressurized magnetic levitation low-temperature waste heat power generation system described in the present invention includes a preheater 1, the working fluid outlet I of the preheater 1 is connected to the working fluid inlet I of the evaporator 2, the working fluid outlet II of the evaporator 2 is connected to the working fluid inlet II of the magnetic levitation turbine generator 3, the working fluid used in the evaporator 2 is pentafluoropropane, and a heat source inlet and a heat source outlet are provided on the evaporator 2, the working fluid outlet III of the magnetic levitation turbine generator 3 is connected to the heat exchange inlet I of the preheater 1, the heat exchange outlet I of the preheater 1 is connected to the heat exchange inlet II of the air-cooled condenser 4, the heat exchange outlet II of the air-cooled condenser 4 is connected to the inlet I of the low-pressure buffer tank 5, the outlet I of the low-pressure buffer tank 5 is connected to the inlet II of the piston cylinder 6, Outlet II of the piston cylinder 6 is connected to inlet III of the high-pressure buffer tank 7, which is connected to the working medium inlet III of the preheater 1. The piston cylinder 6 is connected to a two-position four-way solenoid valve 8. A self-operated pressure reducing valve 10 is provided on a pipe I9 between the working medium outlet II of the evaporator 2 and the working medium inlet II of the magnetic levitation turbine generator 3. Port I of the two-position four-way solenoid valve 8 is connected to pipe I9 at the front end of the self-operated pressure reducing valve 10. A bypass pipe 12 is provided between pipe I9 at the rear end of the self-operated pressure reducing valve 10 and pipe II11 connected to the working medium inlet II of the magnetic levitation turbine generator 3. A regulating valve 13 is provided on the bypass pipe 12. Port II of the two-position four-way solenoid valve 8 is connected to pipe II11.

[0021] The air-cooled condenser 4 includes a connecting seat 26, a shell 15 and a lower header 16, an upper header 14 is provided in the connecting seat 26, the shell 15 includes a rectangular surface I, a trapezoidal surface I, a rectangular surface II and a trapezoidal surface II, which are connected in sequence, and two rows of condensing tubes are provided on the inner side of the shell 15 between the upper header 14 and the lower header 16, one row of which is provided on the inner side of the rectangular surface I and the other row is provided on the inner side of the rectangular surface II, the condensing tubes are divided into a large diameter section 17, a medium diameter section 18 and a small diameter section 19, and the inner diameter ratio of the large diameter section 17, the medium diameter section 18 and the small diameter section 19 of the condensing tube is (15-17): (6-8): (2-4), the large diameter section 17 One end is connected to the upper header 14, and one end of the small diameter section 19 is connected to the lower header 16. Heat dissipation fins 20 are provided on the medium diameter section 18 and the small diameter section 19 of the condenser tube. A wind tube 21 is provided in the middle of the connecting seat 26. The wind tube 21 is connected to the interior of the shell 15. A fan 22 is provided in the wind tube 21. An upper header inlet I 23 and an upper header inlet II 24 are provided on the connecting seat 26. The upper header inlet I 23 and the upper header inlet II 24 are provided at two opposite corners of the connecting seat 26. The upper header inlet I 23 and the upper header inlet II 24 are connected to the upper header 14. A lower header outlet 25 is provided on the lower header 16.

[0022] Figure 1 middle,

[0023] A-piston cylinder pressure increased to above 2.0Mpa;

[0024] B- High-pressure buffer tank stabilizes the supply of high-pressure liquid working fluid;

[0025] C- High-pressure liquid working fluid exchanges heat with the expanded low-pressure gaseous working fluid for preheating;

[0026] D- High-pressure liquid working fluid is preheated and then heated in the evaporator to become a superheated high-pressure and high-temperature gaseous working fluid;

[0027] E-High temperature and high pressure superheated working fluid is cooled and decompressed into low temperature gaseous working fluid through magnetic levitation turbine expander;

[0028] F-heat exchange cooling between low temperature gaseous working medium and pressurized liquid working medium

[0029] G- low temperature gaseous working medium is cooled into low pressure liquid working medium through air condenser;

[0030] H- low temperature liquid working medium is supplied by the low pressure buffer tank to stabilize the liquid working medium;

[0031] I- Bypass of the magnetically suspended turbo expander to maintain the pressure difference and flow stability before and after the turbo expander;

[0032] P- low quality heat source, such as 1.0Mpa saturated steam;

[0033] Q- low quality heat source, hot water around 60℃.

[0034] The workflow of the present invention is as follows:

[0035] A two-position, four-way solenoid valve switches the pressure on both sides of the cylinder, controlling the piston cylinder to transfer the low-pressure liquid working fluid from the low-pressure buffer tank to the high-pressure buffer tank. The pressure in the high-pressure buffer tank is maintained at the set pressure by a self-operated pressure reducing valve. The working fluid in the high-pressure buffer tank is continuously pressurized by the piston cylinder and transferred to the preheater for heat exchange with the low-pressure gaseous working fluid at the outlet of the magnetic levitation turbine expander, achieving preheating. After preheating, the working fluid at the preheater outlet enters the evaporator for heat exchange with the heat source, becoming high-temperature, high-pressure superheated steam. The self-operated pressure reducing valve and regulating valve maintain the set pressure and a certain degree of superheat before entering the magnetic levitation turbine expander to drive the turbine impeller to generate electricity. Simultaneously, the working fluid is cooled and reduced in pressure to a low-pressure, low-temperature gaseous working fluid. The low-temperature, low-pressure gaseous working fluid enters the preheater for heat exchange with the high-pressure, low-temperature liquid working fluid at the outlet of the high-pressure buffer tank. After cooling, it enters the air-cooled condenser to condense into low-temperature, low-pressure liquid working fluid, which is then stored in the low-pressure buffer tank. The piston cylinder then pressurizes the working fluid and returns it to the high-pressure buffer tank for circulation.

[0036] The present invention provides a train of thought and method. There are many methods and approaches to implement the technical solution. The above is only a preferred embodiment of the present invention. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present invention. These improvements and modifications should also be regarded as the scope of protection of the present invention. All components not specified in this embodiment can be implemented using existing technologies.

Claims

1. A self-pressurized magnetic levitation low-temperature waste heat power generation system, characterized by: It comprises a preheater (1), wherein the working fluid outlet I of the preheater (1) is connected to the working fluid inlet I of the evaporator (2), the working fluid outlet II of the evaporator (2) is connected to the working fluid inlet II of the magnetic levitation turbine generator (3), the working fluid outlet III of the magnetic levitation turbine generator (3) is connected to the heat exchange inlet I of the preheater (1), the heat exchange outlet I of the preheater (1) is connected to the heat exchange inlet II of the air-cooled condenser (4), the heat exchange outlet II of the air-cooled condenser (4) is connected to the inlet I of the low-pressure buffer tank (5), the outlet I of the low-pressure buffer tank (5) is connected to the inlet II of the piston cylinder (6), the outlet II of the piston cylinder (6) is connected to the inlet III of the high-pressure buffer tank (7), and the outlet of the high-pressure buffer tank (7) is connected to the inlet Ⅲ is connected to the working medium inlet Ⅲ of the preheater (1), the piston cylinder (6) is connected to the two-position four-way solenoid valve (8), a self-operated pressure reducing valve (10) is provided on the pipeline Ⅰ (9) between the working medium outlet Ⅱ of the evaporator (2) and the working medium inlet Ⅱ of the magnetic levitation turbine generator (3), the port Ⅰ of the two-position four-way solenoid valve (8) is connected to the pipeline Ⅰ (9) at the front end of the self-operated pressure reducing valve (10), a bypass pipeline (12) is provided between the pipeline Ⅰ (9) at the rear end of the self-operated pressure reducing valve (10) and the pipeline Ⅱ (11) connected to the working medium inlet Ⅱ of the magnetic levitation turbine generator (3), a regulating valve (13) is provided on the bypass pipeline (12), and the port Ⅱ of the two-position four-way solenoid valve (8) is connected to the pipeline Ⅱ (11); The air-cooled condenser (4) comprises a connecting seat (26), a shell (15) and a lower header (16); an upper header (14) is provided in the connecting seat (26); a plurality of condensing pipes are provided on the inner side of the shell (15) between the upper header (14) and the lower header (16); the condensing pipes are divided into a large diameter section (17), a medium diameter section (18) and a small diameter section (19); one end of the large diameter section (17) is connected to the upper header (14); one end of the small diameter section (19) is connected to the lower header (16); The large diameter section (18) and the small diameter section (19) are provided with heat dissipation fins (20), a wind tube (21) is provided in the middle of the connecting seat (26), the wind tube (21) is connected to the interior of the shell (15), a fan (22) is provided in the wind tube (21), an upper header inlet I (23) and an upper header inlet II (24) are provided on the connecting seat (26), the upper header inlet I (23) and the upper header inlet II (24) are connected to the upper header (14), and a lower header outlet (25) is provided on the lower header (16).

2. The self-pressurized magnetic levitation low-temperature waste heat power generation system according to claim 1 is characterized in that: The evaporator (2) is provided with a heat source inlet and a heat source outlet.

3. The self-pressurized magnetic levitation low-temperature waste heat power generation system according to claim 1 is characterized in that: The working fluid used in the evaporator (2) is pentafluoropropane.

4. The self-pressurized magnetic levitation low-temperature waste heat power generation system according to claim 1 is characterized in that: The shell (15) comprises a rectangular surface I, a trapezoidal surface I, a rectangular surface II and a trapezoidal surface II, which are connected in sequence.

5. The self-pressurized magnetic levitation low-temperature waste heat power generation system according to claim 1 is characterized in that: The upper header inlet I (23) and the upper header inlet II (24) are arranged at two opposite corners of the connecting seat (26).

6. The self-pressurized magnetic levitation low-temperature waste heat power generation system according to claim 4 is characterized in that: The condensing tubes are arranged in two rows, one row is arranged on the inner side of the rectangular surface I, and the other row is arranged on the inner side of the rectangular surface II.

7. The self-pressurized magnetic levitation low-temperature waste heat power generation system according to claim 1 is characterized in that: The inner diameter ratio of the large diameter section (17), the medium diameter section (18) and the small diameter section (19) of the condenser tube is (15-17): (6-8): (2-4).

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