A thermal energy isobaric closed cycle variable load control system

Abstract

The application discloses a heat energy isenthalpic closed cycle variable load control system, a waste heat recovery system, a high-temperature heat pump system and a digital scroll variable load dehumidification system are designed in series, multi-stage cooling and dehumidification are realized, multi-stage heating is realized, three systems are fully utilized to work cooperatively, that is, the purpose of deep dehumidification is achieved, the highest air supply temperature is provided at the same time, isenthalpic energy closed cycle is realized, and the three systems all work in the best and highest efficiency working interval; since the air temperature of the pre-cooler is obviously higher than the air temperature of the reheater, when the air flows through the pre-cooler, the heat pipe working medium in the pipe changes from liquid state into gaseous state, the pressure rises, and is transported to the reheater through the gas pipe connecting pipe; after the air at a lower temperature flows through the reheater, the heat pipe working medium condenses in the reheater, the temperature is lowered, the pressure is lowered, and flows back to the pre-cooler along the liquid pipe connecting pipe; thus, the energy closed cycle is formed, and the system pre-cooling and reheating can be realized through waste heat recovery without consuming external energy.

Description

TECHNICAL FIELD

[0001] The present application relates to a kind of thermal energy isenthalpic closed cycle variable load control system. BACKGROUND

[0002] At present, there are a large number of drying processes in industrial and agricultural production processes, such as tobacco, traditional Chinese medicine, dried fruits, seafood, vegetables, chemical industry, textile printing and dyeing industries, etc. There are a large number of drying processes. A large amount of water vapor needs to be directly discharged, causing energy waste. The overall drying process in China is currently backward, and the energy utilization rate of the equipment is low, resulting in high drying cost and loss of competitiveness. The purpose of the dehumidification type value-added heat source is to solve this problem, the main purpose is: 1) Energy recycling, the sensible heat and latent heat in the exhaust gas discharged during the drying process are recycled. 2) To achieve automatic drying process, unattended throughout the process with the cleanest energy, improve efficiency and reduce operating costs. 3) Provide low-temperature efficiency and compressor protection system, improve heating efficiency, quickly improve internal drying temperature, and protect the compressor system to work effectively for a long time, avoid system low pressure alarm and shutdown due to low temperature. SUMMARY

[0003] The purpose of the present application is to provide a kind of thermal energy isenthalpic closed cycle variable load control system to solve the problems raised in the above background.

[0004] To achieve the above purpose, the present application provides the following technical scheme: a kind of thermal energy isenthalpic closed cycle variable load control system, including high-temperature heat pump system, digital scroll variable load dehumidification system, waste heat recovery system, electric control box, first temperature sensor and second temperature sensor, the high-temperature heat pump system includes primary evaporator, secondary condenser, compressor, first expansion valve, liquid accumulator and circulating fan, the digital scroll variable load dehumidification system includes secondary evaporator, primary condenser, second expansion valve, digital scroll compressor, load regulating valve and circulating fan, the waste heat recovery system includes pre-cooler and reheater, the electric control box is electrically connected with high-temperature heat pump system, digital scroll variable load dehumidification system, waste heat recovery system, electric control box, first temperature sensor and second temperature sensor.

[0005] Preferably, the pre-cooler is connected with the oven, and the pre-cooler, the primary evaporator, the secondary evaporator, the reheater, the primary condenser, the secondary condenser and the oven are connected in sequence by the exhaust gas pipeline to form a circulating loop, and the first temperature sensor is arranged on the exhaust gas pipeline connected between the secondary evaporator and the reheater.

[0006] Preferably, a circulating fan is arranged between the secondary condenser and the oven, the secondary condenser, the oven and the circulating fan are communicated by the exhaust gas pipeline, and the second temperature sensor is arranged on the exhaust gas pipeline connected between the secondary condenser and the circulating fan.

[0007] Preferably, a water collection pan is provided below the primary evaporator and the secondary evaporator, and a drain outlet is provided at the bottom of the water collection pan.

[0008] Preferably, mutually independent gas pipe connecting pipes and liquid pipe connecting pipes are provided between the precooler and the reheater, and the precooler, gas pipe connecting pipe, reheater and liquid pipe connecting pipe are connected in sequence to form a circulation loop.

[0009] Preferably, a compressor is provided between the primary evaporator and the secondary condenser, and the primary evaporator, the secondary condenser and the compressor are connected via a pipeline.

[0010] Preferably, a first expansion valve and a liquid reservoir are further provided between the primary evaporator and the secondary condenser, the secondary condenser, the liquid reservoir, the first expansion valve and the primary evaporator are connected in sequence through pipelines, and the primary evaporator, the compressor, the secondary condenser, the liquid reservoir and the first expansion valve are connected in sequence through pipelines to form a circulation loop.

[0011] Preferably, the compressor is provided with a regulating valve, which is connected to the high-pressure end and the low-pressure end of the compressor through copper tubes respectively, and the regulating valve is used to control the output of the compressor by turning the regulating valve on and off.

[0012] Compared with the prior art, the present invention is a thermal energy isenthalpic closed cycle variable load control system, the waste heat recovery system, the high temperature heat pump system and the digital vortex variable load dehumidification system adopt a series design to achieve multi-stage cooling and dehumidification, and at the same time achieve multi-stage heating, making full use of the three systems to work together, that is, to achieve the purpose of deep dehumidification, by providing the highest air supply temperature at the same time, realizing isenthalpic energy closed cycle, and at the same time all three systems work in the best and most efficient working range; in the present invention, since the air temperature of the precooler is significantly higher than that of the reheater, when the air flows through the precooler, The heat pipe working medium in the tube changes from liquid to gas, the pressure rises, and is transported to the reheater through the gas pipe connecting pipe; after the lower temperature air flows through the reheater, the heat pipe working medium condenses in the reheater, the temperature and pressure decrease, and it flows back to the precooler along the liquid pipe connecting pipe; this forms an energy closed cycle, through the waste heat recovery, without consuming external energy, it can achieve system precooling and reheating; the precooler and reheater of the present invention are driven by temperature difference, without consuming additional energy; energy is recycled, and the energy in the cold air after the dehumidifier is used for front-end precooling, reducing the dehumidification load and dehumidification power consumption. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] The accompanying drawings are used to provide a further understanding of the present invention and constitute a part of the specification. Together with the embodiments of the present invention, they are used to explain the present invention and do not constitute a limitation of the present invention. In the accompanying drawings:

[0014] Figure 1 The diagram is a structural diagram of a thermal energy isenthalpic closed cycle variable load control system according to the present invention.

[0015] In the figure: 1. Precooler; 2. First-stage evaporator; 3. Second-stage evaporator; 4. Reheater; 5. First-stage condenser; 6. Second-stage condenser; 7. Compressor; 8. First expansion valve; 9. Liquid receiver; 10. Oven; 11. Gas connecting pipe; 12. Liquid connecting pipe; 13. Second expansion valve; 14. Digital scroll compressor; 15. Load regulating valve; 16. Electric control box; 17. First temperature sensor; 18. Second temperature sensor; 19. Circulation fan. DETAILED DESCRIPTION

[0016] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0017] See also Figure 1 As shown, the present invention provides a technical solution: a thermal energy isenthalpic closed-cycle variable-load control system, comprising a high-temperature heat pump system, a digital scroll variable-load dehumidification system, a waste heat recovery system, an electrical control box 16, a first temperature sensor 17, and a second temperature sensor 18. The high-temperature heat pump system includes a primary evaporator 2, a secondary condenser 6, a compressor 7, a first expansion valve 8, a liquid reservoir 9, and a circulating fan 19. The digital scroll variable-load dehumidification system includes a secondary evaporator 3, a primary condenser 5, a second expansion valve 13, a digital scroll compressor 14, a load regulating valve 15, and a circulating fan 19. The waste heat recovery system includes a precooler 1 and a reheater 4. The electrical control box is electrically connected to the high-temperature heat pump system, the digital scroll variable-load dehumidification system, the waste heat recovery system, the electrical control box 16, the first temperature sensor 17, and the second temperature sensor 18. The electrical control box 16, while equipped with a controller and regulator for controlling all components, may also be equipped with an overload protection circuit and an alarm module connected to the controller to generate an alarm to alert the user if it is not functioning properly.

[0018] The precooler 1 in this embodiment is connected to the oven 10, and the precooler 1, the first-level evaporator 2, the second-level evaporator 3, the reheater 4, the first-level condenser 5, the second-level condenser 6 and the oven 10 are connected in sequence through an exhaust gas pipeline to form a circulation loop. A first temperature sensor 17 is provided on the exhaust gas pipeline connected between the second-level evaporator 3 and the reheater 4, and a circulation fan 19 is provided between the second-level condenser 6 and the oven 10. The second-level condenser 6, the oven 10 and the circulation fan 19 are connected through an exhaust gas pipeline, and a second temperature sensor 18 is provided on the exhaust gas pipeline connected between the second-level condenser 6 and the circulation fan 19.

[0019] In this embodiment, a water collection tray 20 is provided below the primary evaporator 2 and the secondary evaporator 3 for collecting condensed water condensed from moisture in the air. A drain port is provided at the bottom of the water collection tray 20 for discharging the condensed water.

[0020] In this embodiment, independent gas and liquid connecting pipes 11 and 12 are provided between the precooler 1 and the reheater 4. The precooler 1, gas connecting pipe 11, reheater 4, and liquid connecting pipe 12 are sequentially connected to form a circulation loop. A portion of the vaporized working fluid in the precooler 1 enters the reheater 4 through the gas connecting pipe 11. The gas entering the heat pipe of the reheater 4 liquefies and then flows back to the precooler 1 through the liquid connecting pipe 12. Because the air temperature in the precooler 1 is significantly higher than that in the reheater 4, as the air flows through the precooler 1, the working fluid in the heat pipe changes from liquid to gas, increasing its pressure. The working fluid is then transported to the reheater 4 through the gas connecting pipe 11. After the cooler air flows through the reheater 4, the working fluid condenses within the reheater 4, reducing its temperature and pressure, and then flows back to the precooler 1 along the liquid connecting pipe 12. This forms a closed energy cycle, achieving system precooling and reheating through waste heat recovery without consuming external energy.

[0021] In this embodiment, a compressor 7 is provided between the primary evaporator 2 and the secondary condenser 6. The primary evaporator 2, the secondary condenser 6 and the compressor 7 are connected by a pipeline. A first expansion valve 8 and a liquid reservoir 9 are also provided between the primary evaporator 2 and the secondary condenser 6. The secondary condenser 6, the liquid reservoir 9, the first expansion valve 8 and the primary evaporator 2 are connected in sequence through a pipeline. The primary evaporator 2, the compressor 7, the secondary condenser 6, the liquid reservoir 9 and the first expansion valve 8 are connected in sequence through a pipeline to form a circulation loop. A regulating valve is provided on the compressor 7. The regulating valve is connected to the high-pressure end and the low-pressure end of the compressor 7 respectively through a copper tube. The regulating valve is used to control the output of the compressor 7 by turning the regulating valve on and off. When in use, when the supply air temperature changes, the regulating valve is adjusted to adjust the output capacity of the compressor 7 to adjust the system supply air temperature, ensuring that the maximum evaporation temperature can reach 40°C and the condensation temperature can reach above 85°C, ensuring that a higher supply air temperature can be provided.

[0022] In this embodiment, a second expansion valve 13 is provided between the secondary evaporator 3 and the primary condenser 5, and the secondary evaporator 3, the second expansion valve 13 and the primary condenser 5 are connected through a pipeline. A digital scroll compressor 14 is also provided between the secondary evaporator 3 and the primary condenser 5, and the secondary evaporator 3, the digital scroll compressor 14 and the primary condenser 5 are connected through a pipeline. The secondary evaporator 3, the second expansion valve 13, the primary condenser 5 and the digital scroll compressor 14 are connected in sequence through pipelines to form a circulation loop, and a load regulating valve 15 is provided on the digital scroll compressor 14, and the load regulating valve 15 is respectively connected to the high-pressure end of the digital scroll compressor 14 and the low-pressure end of the digital scroll compressor 14 through a copper tube, and the load regulating valve 15 is used to control the output of the digital scroll compressor 14 by turning the load regulating valve 15 on and off. During use, when the air inlet load changes, the load regulating valve 15 is adjusted to adjust the output capacity of the digital scroll compressor 14 to adjust the system's refrigeration and dehumidification load, ensuring that the system does not freeze and can continue to work and maintain stable air supply conditions.

[0023] The working principle and use method of a thermal energy isenthalpic closed cycle variable load control system of the present invention include the following:

[0024] 1) Closed energy cycle: During the drying process in the drying oven 10, water vapor enters the precooler 1 along with the hot air driven by the circulating fan 19. After being precooled by the precooler 1, the temperature is reduced, and then the air flows through the primary evaporator 2 and the secondary evaporator 3 to further reduce the temperature, and the moisture in the air condenses out. The condensed water is collected by the water collection tray 20 and discharged through the drain outlet; the air after passing through the primary evaporator 2 and the secondary evaporator 3 flows through the reheater 4, and the temperature is increased. At the same time, the heat in the air entering the primary evaporator 2 and the secondary evaporator 3 is used to heat the cold air in the primary evaporator 2 and the secondary evaporator 3, realizing a closed energy cycle and reducing the relative humidity; thereafter, the air flows through the primary condenser 5 and the secondary condenser 6, and the air temperature is increased to the temperature required for drying, and the relative humidity is very low, and then the air enters the drying oven 10 again, realizing moisture removal without heat removal, and a closed energy cycle.

[0025] 2) Waste heat recovery: Water vapor enters the precooler 1 along with the hot air driven by the circulating fan 19. After passing through the precooler 1, the air temperature drops and approaches the saturation state of the air. At this time, the air passes through the first evaporator 2 and the second evaporator 3, and the air temperature drops further. Most of the water in the air is condensed, the absolute humidity drops, and the relative humidity is very high, reaching the saturation state; the air circulates further and passes through the reheater 4, and the temperature rises. At this time, the absolute humidity of the air remains unchanged, and the relative humidity drops significantly, thereby achieving the required The temperature and humidity requirements are met; since the air temperature of the precooler 1 is significantly higher than that of the reheater 4, when the air flows through the precooler 1, the heat pipe working medium in the pipe changes from liquid to gas, the pressure rises, and is transported to the reheater 4 through the gas pipe connecting pipe 11; after the lower temperature air flows through the reheater 4, the heat pipe working medium condenses in the reheater 4, the temperature and pressure decrease, and it flows back to the precooler 1 along the liquid pipe connecting pipe 12; this forms a closed energy cycle, and through waste heat recovery, the system precooling and reheating can be achieved without consuming external energy.

[0026] 3) Digital variable load dehumidification: When the air passes through the secondary evaporator 3, it will condense into condensed water when it encounters cold. The condensed water is collected by the water accumulation tray 20 and discharged through the drain outlet. The low-temperature dry air after cooling and dehumidification then flows into the digital scroll compressor 14. The digital scroll compressor 14 compresses the low-temperature dry air into high-temperature and high-pressure gas. The high-temperature and high-pressure gas enters the primary condenser 5, and is heated by the primary condenser 5 to form a high-temperature and high-pressure liquid. The high-temperature and high-pressure liquid is reduced in pressure by the second expansion valve 13 and enters the secondary evaporator 3. In this cycle, the condensed water is continuously discharged, and the air humidity is continuously reduced.

[0027] Step 4) High-temperature heat pump heating: When the air passes through the first-stage evaporator 2, it will condense into condensed water when it encounters cold. The condensed water is collected by the water collection tray 20 and discharged through the drain outlet. The low-temperature dry air after cooling and dehumidification then flows into the compressor 7. The compressor 7 compresses the low-temperature dry air into high-temperature and high-pressure gas and blows out hot air, thereby increasing the air temperature and achieving a heating effect; the high-temperature and high-pressure gas enters the secondary condenser 6, and is heated by the secondary condenser 6 to form a high-temperature and high-pressure liquid. The high-temperature and high-pressure liquid enters the liquid reservoir 9, and is then reduced in pressure by the first expansion valve 8 and enters the first evaporator 2. It evaporates and vaporizes to absorb heat and becomes gas. The gas enters the compressor 7 again for compression, and the next cycle begins.

[0028] While embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions, and variations may be made to these embodiments without departing from the principles and spirit of the invention, and that the scope of the invention is defined by the appended claims and their equivalents.

Claims

1. A heat energy isenthalpic closed cycle variable load control system, comprising a high-temperature heat pump system, a digital vortex variable load dehumidification system, a waste heat recovery system, an electric control box (16), a first temperature sensor (17) and a second temperature sensor (18), characterized in that: The high-temperature heat pump system includes a primary evaporator (2), a secondary condenser (6), a compressor (7), a first expansion valve (8), a liquid reservoir (9), and a circulating fan (19); the digital scroll variable load dehumidification system includes a secondary evaporator (3), a primary condenser (5), a second expansion valve (13), a digital scroll compressor (14), a load regulating valve (15), and a circulating fan (19); the waste heat recovery system includes a precooler (1) and a reheater (4); and the electric control box is electrically connected to the high-temperature heat pump system, the digital scroll variable load dehumidification system, the waste heat recovery system, the electric control box (16), the first temperature sensor (17), and the second temperature sensor (18); The precooler (1) is connected to the drying oven (10); the precooler (1), the primary evaporator (2), the secondary evaporator (3), the reheater (4), the primary condenser (5), the secondary condenser (6) and the drying oven (10) are sequentially connected via an exhaust gas pipeline to form a circulation loop; a first temperature sensor (17) is provided on the exhaust gas pipeline connected between the secondary evaporator (3) and the reheater (4); A compressor (7) is provided between the primary evaporator (2) and the secondary condenser (6), and the primary evaporator (2), the secondary condenser (6) and the compressor (7) are connected via a pipeline; A first expansion valve (8) and a liquid reservoir (9) are further provided between the primary evaporator (2) and the secondary condenser (6); the secondary condenser (6), the liquid reservoir (9), the first expansion valve (8) and the primary evaporator (2) are sequentially connected via pipelines; and the primary evaporator (2), the compressor (7), the secondary condenser (6), the liquid reservoir (9) and the first expansion valve (8) are sequentially connected via pipelines to form a circulation loop.

2. The thermal energy isenthalpic closed cycle variable load control system according to claim 1, characterized in that: A circulating fan (19) is provided between the secondary condenser (6) and the drying oven (10); the secondary condenser (6), the drying oven (10) and the circulating fan (19) are connected via an exhaust gas pipeline; a second temperature sensor (18) is provided on the exhaust gas pipeline connected between the secondary condenser (6) and the circulating fan (19).

3. The thermal energy isenthalpic closed cycle variable load control system according to claim 1, characterized in that: A water collection tray (20) is provided below the primary evaporator (2) and the secondary evaporator (3), and a drainage outlet is provided at the bottom of the water collection tray (20).

4. The thermal energy isenthalpic closed cycle variable load control system according to claim 1, characterized in that: An independent gas pipe connecting pipe (11) and a liquid pipe connecting pipe (12) are provided between the precooler (1) and the reheater (4); the precooler (1), the gas pipe connecting pipe (11), the reheater (4) and the liquid pipe connecting pipe (12) are sequentially connected to form a circulation loop.

5. The thermal energy isenthalpic closed cycle variable load control system according to claim 1, characterized in that: The compressor (7) is provided with a regulating valve, which is connected to the high-pressure end of the compressor (7) and the low-pressure end of the compressor (7) through copper pipes, respectively. The regulating valve is used to control the output of the compressor (7) by switching the regulating valve on and off.

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