A multi-generation system and method based on alcohol steam waste heat cascade utilization

Abstract

This invention discloses a multi-generation system and method based on the cascade utilization of waste heat from alcohol vapor. The multi-generation system includes a cascaded heat exchanger, a water distribution module, an organic Rankine cycle power generation module, a medium-temperature thermal energy multi-generation module, and a central control module. Alcohol vapor flows sequentially through a primary heat exchanger core and a secondary heat exchanger core. The high-temperature hot water generated by the primary heat exchanger core enters the evaporator of the organic Rankine cycle power generation module through the primary heat exchanger outlet pipe, driving an expander and a generator to generate electricity. The secondary heat exchanger core is used to condense the alcohol vapor and produce medium-temperature hot water. The medium-temperature hot water is distributed to heating and cooling branch pipes via a second proportional regulating valve through the secondary heat exchanger outlet pipe. The heating branch pipes are used for heating or domestic hot water, while the medium-temperature hot water in the cooling branch is heated by a heat pump and then drives an absorption chiller to generate cooling capacity. The central control module integrates system parameters to regulate water distribution, realizing the cascade utilization of high-grade power generation, medium-temperature heating, and temperature-raising cooling.

Description

Technical Field

[0001] This invention relates to the field of waste heat recovery and comprehensive utilization technology in brewing, specifically to a multi-product system and method based on the cascade utilization of waste heat from brewing steam. Background Technology

[0002] In the winemaking process, distillation generates a large amount of alcohol vapor carrying sensible heat and latent heat of condensation. Alcohol vapor is typically a multi-component mixture of water vapor, ethanol vapor, and small amounts of aroma compounds. To obtain liquid alcohol, the alcohol vapor needs to be condensed. Traditional alcohol cooling systems usually use cooling water, cooling towers, or cooling water tanks as the cold source, condensing the alcohol vapor into liquid through one-time cooling or circulating cooling.

[0003] However, traditional cooling methods have the following problems:

[0004] 1. The cooling water consumption is large, the evaporation loss of the cooling tower is significant, the footprint is large, and the operation requires the configuration of a circulating water pump, water replenishment system and sewage discharge system.

[0005] 2. The large amount of heat energy released by the condensation of alcohol vapor is not effectively recovered and utilized, and is usually directly discharged into the environment or cooling water system, resulting in energy waste;

[0006] 3. Although some existing heat recovery type wine cooling devices can convert the condensation heat of wine vapor into hot water, they usually output hot water as the main output and do not make segmented use according to the temperature change and heat grade difference of wine vapor during the condensation process, which easily leads to the downgrading of high-grade heat energy.

[0007] 4. The brewing workshop may continuously generate waste heat throughout the year, while the heating and domestic hot water loads of the factory area have obvious seasonality and time-limited characteristics; for example, the heating demand is high in winter and decreases or even disappears in summer; if the waste heat is only used for heating, there will still be a problem of a large amount of waste heat that cannot be consumed when the heating load is insufficient.

[0008] 5. Existing systems typically rely on manual adjustment or simple water volume adjustment to control the temperature of the wine output, resulting in a slow response time and difficulty in balancing stable wine quality with efficient utilization of residual heat.

[0009] The organic Rankine cycle is a technology suitable for medium- and low-temperature waste heat power generation, utilizing low-boiling-point organic working fluids to absorb heat from a heat source and convert it into mechanical work and electrical energy. Absorption refrigeration technology can use heat energy to drive refrigeration. Heat pump technology can raise the temperature and improve the quality of medium-temperature hot water. However, how to organically couple the different grades of heat energy from the condensation process of wine vapor with organic Rankine cycle power generation, heating, heat pump heating, and absorption refrigeration, while ensuring the control of wine condensation temperature, year-round load absorption, and economical system operation, remains a pressing technical problem to be solved in the field of comprehensive utilization of brewing waste heat. Summary of the Invention

[0010] To address the technical problems of existing wine cooling systems, such as large waste heat emissions, limited utilization methods, downgraded use of high-grade heat energy, insufficient precision in wine output temperature control, and insufficient seasonal heating load leading to difficulties in year-round waste heat utilization, this invention provides a multi-generation system and method based on the cascade utilization of wine steam waste heat.

[0011] The technical solution is as follows:

[0012] The first aspect of this application relates to a multi-generation system based on the cascade utilization of waste heat from alcoholic beverage steam, comprising:

[0013] A cascaded heat exchange device includes a heat exchanger shell and a primary heat exchange core and a secondary heat exchange core arranged sequentially in the heat exchanger shell along the direction of alcohol vapor flow. The upper part of the heat exchanger shell is provided with an alcohol vapor inlet, and the lower part of the heat exchanger shell is provided with an alcohol outlet. The primary heat exchange core and the secondary heat exchange core are respectively formed with a first hot water exchange channel and a second hot water exchange channel capable of exchanging heat with alcohol vapor. After entering through the alcohol vapor inlet, the alcohol vapor exchanges heat with the water in the first hot water exchange channel and the second hot water exchange channel in sequence, and after condensation at the secondary heat exchange core, it is discharged from the alcohol outlet.

[0014] The water distribution module has a first water supply branch pipe and a second water supply branch pipe. The first water supply branch pipe is connected to the inlet of the first hot water exchange channel, and the second water supply branch pipe is connected to the inlet of the second hot water exchange channel. Both the first water supply branch pipe and the second water supply branch pipe adjust the cold water flow rate through a first proportional regulating valve.

[0015] An organic Rankine cycle power generation module includes an evaporator, an expander, a generator, a condenser, and a working fluid pump. The evaporator, expander, condenser, and working fluid pump form a closed-loop organic working fluid system through pipelines. The expander is driven by the generator. The outlet of the first heat exchange water channel is connected to the heat source inlet of the evaporator through a primary heat exchange outlet pipe, so that the high-temperature hot water obtained from the primary heat exchange can be used as the heat source for the organic Rankine cycle power generation module.

[0016] The medium-temperature combined heat and power (CHP) module includes a secondary heat exchange outlet pipe, a heating branch pipe, and a cooling branch pipe. The secondary heat exchange outlet pipe is connected to the outlet of the second hot water exchange channel and is connected to the heating branch pipe and the cooling branch pipe respectively through a second proportional regulating valve. The heating branch pipe is used to supply medium-temperature hot water. A heat pump and an absorption chiller are sequentially installed on the cooling branch pipe. The heat pump is used to heat the medium-temperature hot water sent from the cooling branch pipe and use it as the driving heat source for the absorption chiller.

[0017] The central control module is communicatively connected to the first proportional regulating valve, the second proportional regulating valve, the heat pump, and the absorption chiller, respectively.

[0018] The central control module is configured to adjust the flow rate of cold water supplied to the first and second water supply branches via a first proportional regulating valve, and to adjust the flow rate of medium-temperature hot water supplied to the heating and cooling branch pipes via a second proportional regulating valve, based on the wine temperature at the wine outlet, the primary heat exchange outlet water temperature in the primary heat exchange outlet pipe, the secondary heat exchange outlet water temperature in the secondary heat exchange outlet pipe, and the heating and cooling loads.

[0019] The above-mentioned multi-generation system based on the cascade utilization of waste heat from alcohol vapor utilizes primary and secondary heat exchange cores. This allows the alcohol vapor to first release high-grade heat for organic Rankine cycle power generation, and then release medium-temperature heat for heating or cooling, avoiding the direct degradation of all heat into ordinary hot water. The central control module adjusts the water volume according to temperature and load, achieving coupled control of power generation, heating, cooling, and alcohol condensation temperature control. This significantly improves the comprehensive utilization rate and year-round absorption capacity of waste heat from alcohol vapor.

[0020] In some embodiments, the cascaded heat exchange device is a vertical heat exchange device, the primary heat exchange core is located above the secondary heat exchange core, the wine vapor inlet and the wine outlet are connected by a wine vapor channel, and the wine vapor channel passes vertically through the primary heat exchange core and the secondary heat exchange core in sequence.

[0021] A wine temperature sensor is installed at the wine outlet, and the wine temperature sensor is communicatively connected to the central control module.

[0022] The cascaded heat exchanger adopts a vertical heat exchange device, which can utilize the natural flow direction of wine vapor and condensed wine liquid, so that wine vapor passes through the primary heat exchange area and the secondary heat exchange area from top to bottom, reducing gas-liquid short-circuiting and liquid accumulation. The wine liquid temperature sensor can provide real-time feedback on the wine temperature, enabling the central control module to perform closed-loop adjustment of the cooling intensity of the secondary heat exchange, thereby improving the stability of the wine temperature and the consistency of wine quality.

[0023] In some embodiments, the inlet of the first proportional regulating valve is connected to a water treatment device and a main water pump in sequence via a pipeline. The inlet of the main water pump is connected to a municipal water supply or circulating water supply pipe. The water treatment device is used to filter and soften the cold water entering the primary heat exchange core and the secondary heat exchange core.

[0024] The main water pump ensures stable system inlet water pressure and flow. Water treatment equipment reduces scale, blockage, and corrosion caused by suspended solids, hardness ions, and impurities in the water to the heat exchange channels, extending the service life of the primary heat exchange core, secondary heat exchange core, and pipelines, and maintaining stable heat exchange efficiency.

[0025] In some embodiments, the evaporator includes a heat source water side and an organic working fluid side that exchange heat with each other but are isolated from each other;

[0026] The primary heat exchange outlet pipe is connected to the heat source water side inlet of the evaporator, and the heat source water side outlet of the evaporator is connected to the inlet of the main water pump via a circulating water supply pipe.

[0027] The organic working fluid side outlet of the evaporator is connected to the inlet of the expander via a working fluid vapor pipeline. The outlet of the expander is connected to the inlet of the condenser via an exhaust pipeline. The outlet of the condenser is connected to the inlet of the working fluid pump via a liquid working fluid pipeline. The outlet of the working fluid pump is connected to the organic working fluid side inlet of the evaporator via a high-pressure working fluid pipeline.

[0028] The heat source water side and the organic working fluid side of the evaporator are isolated from each other, which can prevent the heat source water from mixing with the organic working fluid and improve operational safety. The outlet of the heat source water side returns to the inlet of the main water pump through the circulating water supply pipe, which can realize the recycling of heat source water and reduce the amount of water to be supplied. The closed loop of the organic working fluid can continuously absorb the heat of the first-stage high-temperature hot water and drive the expander to generate electricity, thereby improving the power output capacity of the system.

[0029] In some embodiments, a heating return water temperature sensor and a heating flow meter are installed at the end of the heating branch pipeline or on the heating return water pipeline.

[0030] The end of the refrigeration branch pipeline or the return water end of the refrigeration network is equipped with a refrigeration return water temperature sensor and a refrigeration flow meter.

[0031] The central control module is configured to calculate the instantaneous heating load and instantaneous cooling load based on the heating return water temperature collected by the heating return water temperature sensor, the heating flow rate collected by the heating flow meter, the cooling return water temperature collected by the cooling return water temperature sensor, and the cooling flow rate collected by the cooling flow meter, and adjust the opening degree of the second proportional regulating valve corresponding to the heating branch pipe and the cooling branch pipe according to the instantaneous heating load and the instantaneous cooling load.

[0032] By collecting terminal temperature and flow data, the central control module can obtain the real-time heating and cooling demand of the plant area, no longer relying on fixed distribution ratios or manual switching; by continuously adjusting the second proportional regulating valve, the medium-temperature hot water generated by the secondary heat exchange can be dynamically distributed according to the actual load, avoiding oversupply of heating branches, undersupply of cooling branches, or the discharge of excess heat, thereby improving the waste heat utilization rate.

[0033] In some implementations, the central control module is equipped with heating priority control logic and cooling branch start threshold.

[0034] When the heating load at the end of the heating branch pipeline is not saturated, the central control module increases the opening degree of the second proportional regulating valve corresponding to the heating branch pipeline.

[0035] When the heating load at the end of the heating branch pipeline reaches saturation, and the flow rate and / or enthalpy of the medium-temperature hot water output from the secondary heat exchange outlet pipeline reaches the starting threshold of the cooling branch, the central control module increases the opening of the second proportional regulating valve corresponding to the cooling branch pipeline and starts the heat pump and absorption chiller.

[0036] When the flow rate and / or enthalpy value of the medium-temperature hot water introduced into the refrigeration branch pipe are lower than the refrigeration branch start-up threshold, the central control module prohibits or delays the start-up of the heat pump and absorption chiller.

[0037] The heating priority control logic can prioritize meeting the direct heat demand of the plant area, such as heating, showering, or cleaning, and reduce energy conversion links; the refrigeration branch start threshold can avoid frequent start-stop or inefficient operation of heat pumps and absorption chillers under low load, reduce auxiliary power consumption, and improve system economy and operational stability.

[0038] In some embodiments, the central control module is communicatively connected to the working fluid pump and is configured to adjust the speed or flow rate of the working fluid pump according to at least one of the following parameters: the heat source inlet temperature of the evaporator, the heat source outlet temperature of the evaporator, the evaporation pressure of the organic working fluid in the evaporator, and the inlet temperature of the expander, so that the organic Rankine cycle power generation module operates within a preset evaporation pressure range.

[0039] By adjusting the speed or flow rate of the working fluid pump, the circulation volume of the organic working fluid can be matched with the heat source capacity provided by the primary heat exchanger. This avoids insufficient evaporation of the organic working fluid, decreased efficiency of the expander, or abnormal evaporation pressure caused by fluctuations in the heat source temperature, ensuring the efficient and stable operation of the organic Rankine cycle power generation module and further improving the energy-saving performance of the system.

[0040] The second aspect of this application relates to a multi-generation method based on the cascade utilization of waste heat from alcohol vapor, implemented using the aforementioned multi-generation system, and comprising the following steps:

[0041] S1. High-grade heat recovery and organic Rankine cycle power generation: The alcohol vapor is sent into the cascade heat exchanger through the alcohol vapor inlet, so that the alcohol vapor first exchanges heat with the first heat exchange core; the cold water entering the first hot water exchange channel through the first water supply branch pipe is heated into high-temperature hot water, and the high-temperature hot water is sent to the heat source water side of the evaporator through the first heat exchange outlet pipe; in the evaporator, the high-temperature hot water is used to heat the organic working fluid, so that the organic working fluid evaporates to form high-pressure organic working fluid steam, and the high-pressure organic working fluid steam enters the expander through the working fluid steam pipeline to expand and do work and drive the generator to generate electricity; the expanded organic working fluid enters the condenser through the exhaust pipe to condense, and then is sent back to the evaporator by the working fluid pump through the high-pressure working fluid pipeline;

[0042] S2, Secondary Condensation Temperature Control and Medium-Temperature Hot Water Production: The alcohol vapor, which has cooled and partially condensed after heat exchange in the primary heat exchange core, continues to flow to the secondary heat exchange core and exchanges heat with it; the cold water entering the second hot water exchange channel through the second water supply branch pipe is heated into medium-temperature hot water, which is then output through the secondary heat exchange outlet pipe; at the same time, the cooling intensity of the secondary heat exchange is controlled by adjusting the opening of the first proportional regulating valve corresponding to the second water supply branch pipe, so that the alcohol vapor is completely condensed into alcohol at the secondary heat exchange core, and the temperature of the alcohol at the outlet is maintained within the preset outlet temperature range.

[0043] S3, Medium-Temperature Heat Load Following Distribution: Obtain heating and cooling loads, and continuously proportionally distribute the medium-temperature hot water output from the secondary heat exchange outlet pipe through the second proportional regulating valve according to the heating priority principle; when there is heating demand, at least a portion of the medium-temperature hot water is transported to the heating system and / or domestic hot water system through the heating branch pipe; when the heating load is saturated and there is cooling demand, the surplus medium-temperature hot water is introduced into the cooling branch pipe, heated by the heat pump, and used as the driving heat source for the absorption chiller to generate cooling capacity.

[0044] By adopting the above multi-generation method, the process of condensing wine vapor is coupled with the waste heat power generation, heating and cooling processes in energy level order. This not only completes the condensation of wine vapor and the temperature control of wine output, but also realizes the multi-form output of waste heat, solving the problems of single waste heat utilization and insufficient seasonal absorption in traditional systems.

[0045] In some embodiments, in step S2, the central control module adjusts the opening of the second water supply branch corresponding to the first proportional regulating valve based on the deviation between the real-time wine temperature collected at the wine outlet and the preset wine outlet temperature.

[0046] When the real-time wine temperature is higher than the preset upper limit of the wine dispensing temperature, the opening of the first proportional regulating valve corresponding to the second water supply branch pipe is increased to increase the cold water flow rate of the second water supply branch pipe.

[0047] When the real-time wine temperature is lower than the preset lower limit of the wine outlet temperature, the opening of the second water supply branch corresponding to the first proportional regulating valve is reduced to reduce the cold water flow rate of the second water supply branch.

[0048] By using the outlet temperature of the liquor as feedback to adjust the flow rate of the secondary heat exchanger, closed-loop control of the liquor outlet temperature can be achieved, improving response speed and control accuracy, reducing manual adjustment errors, and ensuring the stability of the condensation temperature of different batches of liquor.

[0049] In some implementations, in step S3, the central control module collects the heating return water temperature and heating flow rate at the end of the heating branch pipeline and the cooling return water temperature and cooling flow rate of the cooling network in real time, and calculates the instantaneous heating load and instantaneous cooling load.

[0050] When the instantaneous heating load does not reach the set upper limit of the heating load, increase the opening of the corresponding heating branch pipeline of the second proportional regulating valve;

[0051] When the return water temperature at the end of the heating branch pipeline reaches the upper limit of the set return water temperature or the instantaneous heating load reaches the upper limit of the set heating load, the heating load is determined to be saturated, and the excess medium-temperature hot water is smoothly transferred to the cooling branch pipeline by adjusting the second proportional regulating valve.

[0052] The heat pump and absorption chiller shall be started only when the flow rate and / or enthalpy of the medium-temperature hot water introduced into the refrigeration branch pipe reaches the start-up threshold required for the economical operation of the absorption chiller; otherwise, the heat pump and absorption chiller shall be kept in a stopped or standby state.

[0053] The above methods enable continuous adjustment based on the actual needs of heating and cooling terminals, achieving a smooth transfer of surplus medium-temperature hot water from heating branches to cooling branches; at the same time, by setting start-up thresholds, inefficient equipment operation is avoided, thereby improving the overall energy-saving effect throughout the year. Attached Figure Description

[0054] Figure 1 This is a schematic diagram of a multi-product system based on the cascade utilization of waste heat from alcohol vapor.

[0055] Figure 2 The logic diagram for the central control module to control the wine dispensing temperature and heat distribution.

[0056] Figure 3 This is a schematic diagram of heat distribution in a multi-generation system based on the cascade utilization of waste heat from alcoholic beverages under a typical operating condition.

[0057] Explanation of reference numerals in the attached figures:

[0058] 1. Wine vapor inlet; 2. Primary heat exchanger core; 3. Secondary heat exchanger core; 4. Evaporator; 5. Expander; 6. Generator; 7. Condenser; 8. Working fluid pump; 9. Heat pump; 10. Absorption chiller; 11. Water treatment equipment; 12. Main water pump; 13. Wine vapor passage; 14. Primary heat exchanger outlet water pipe; 15. Working fluid steam pipe; 16. Exhaust pipe; 17. Liquid working fluid pipe; 18. High-pressure working fluid pipe; 19. Municipal water supply; 20. 21. First water supply branch pipe; 22. Second water supply branch pipe; 23. Wine outlet; 24. Secondary heat exchange outlet pipe; 25. Refrigeration branch pipe; 26. Heating branch pipe; 27. Wine temperature sensor; 28. Heating return water temperature sensor; 39. Heating flow meter; 30. Refrigeration return water temperature sensor; 31. Refrigeration flow meter; 32. Central control module; 33. First proportional regulating valve; 34. Second proportional regulating valve; 35. Heat exchanger housing. Detailed Implementation

[0059] The present invention will be further described below with reference to the embodiments and accompanying drawings.

[0060] Example 1:

[0061] like Figure 1 and Figure 2 As shown, a multi-generation system based on the cascade utilization of waste heat from alcoholic beverage steam mainly includes a cascade heat exchange device, a water distribution module, an organic Rankine cycle power generation module, a medium-temperature thermal energy multi-generation module, and a central control module 33.

[0062] The cascaded heat exchanger includes a heat exchanger shell 37, a primary heat exchange core 2, and a secondary heat exchange core 3. The heat exchanger shell 37 preferably adopts a vertical cylindrical structure or a vertical box structure. A wine vapor inlet 1 is provided at the upper part of the heat exchanger shell 37, and a wine liquid outlet 22 is provided at the lower part. A wine vapor channel 13 is formed between the wine vapor inlet 1 and the wine liquid outlet 22.

[0063] It should be noted that the alcohol vapor channel 13 is a channel for the flow of alcohol vapor and its condensate within the heat exchanger shell 37. It can be the shell-side space inside the heat exchanger shell 37, a pipe installed inside the heat exchanger shell 37, or a pipe combined with the shell-side space inside the primary heat exchanger core 2 and the secondary heat exchanger core 3.

[0064] The primary heat exchange core 2 and the secondary heat exchange core 3 are sequentially arranged inside the heat exchanger shell 37 along the direction of alcohol vapor flow. In this embodiment, the cascaded heat exchange device is preferably a vertical structure, with the primary heat exchange core 2 located above the secondary heat exchange core 3, and the alcohol vapor flowing from top to bottom through the primary heat exchange core 2 and the secondary heat exchange core 3.

[0065] A first heat exchange channel is formed within the primary heat exchange core 2, and a second heat exchange channel is formed within the secondary heat exchange core 3. The first and second heat exchange channels are isolated from the alcohol vapor channel 13, ensuring that heat exchange occurs only between the cooling water and the alcohol vapor without direct mixing. The primary heat exchange core 2 and the secondary heat exchange core 3 can employ common heat exchange structures capable of gas-liquid heat exchange, such as plate heat exchange cores or finned heat exchange cores.

[0066] After the alcohol vapor enters the alcohol vapor channel 13 from the alcohol vapor inlet 1, it first exchanges heat with the cold water in the primary heat exchange core 2, releasing a higher grade of heat. Then, the alcohol vapor, which has decreased in temperature and partially condensed, continues to flow downwards and exchanges heat with the cold water in the secondary heat exchange core 3, releasing the remaining heat. Finally, it completely condenses into liquid alcohol and is discharged from the liquid alcohol outlet 22.

[0067] In this embodiment, a wine temperature sensor 26 is installed at the wine outlet 22. The wine temperature sensor 26 is used to collect the real-time wine temperature at the wine outlet 22 and transmit the temperature signal to the central control module 33. The wine temperature sensor 26 can be a common temperature sensor such as a resistance temperature sensor, a thermocouple temperature sensor, or a digital temperature sensor.

[0068] The water distribution module includes a main water pump 12, a water treatment device 11, a first proportional regulating valve 35, a first water supply branch pipe 20, and a second water supply branch pipe 21.

[0069] The inlet of the main water pump 12 can be designed to connect only to the municipal water supply 19, or only to the circulating water supply pipe of the plant area (not shown in the figure), or it can be designed to connect to both the municipal water supply 19 and the circulating water supply pipe of the plant area. The main water pump 12 is used to provide pressure for the cold water entering the primary heat exchange core 2 and the secondary heat exchange core 3. The water treatment equipment 11 is installed between the main water pump 12 and the first proportional regulating valve 35, and is used to filter and soften the cold water entering the system.

[0070] The water treatment equipment 11 may include common water treatment devices such as filters and water softeners. The water treatment equipment 11 can reduce scale buildup in the first and second hot water exchange channels, ensuring heat exchange efficiency.

[0071] The inlet of the first proportional regulating valve 35 is connected to the outlet of the water treatment equipment 11. The two outlets of the first proportional regulating valve 35 are connected to the first water supply branch pipe 20 and the second water supply branch pipe 21, respectively. The first water supply branch pipe 20 is connected to the inlet of the first hot water exchange channel of the primary heat exchange core 2, and the second water supply branch pipe 21 is connected to the inlet of the second hot water exchange channel of the secondary heat exchange core 3.

[0072] In one embodiment, the first proportional regulating valve 35 is a one-in-two-out electrically operated three-way proportional distribution valve. The central control module 33 regulates the flow rate of cold water entering the first water supply branch pipe 20 and the second water supply branch pipe 21 by controlling the opening degree and distribution ratio of this electrically operated three-way proportional distribution valve. In another embodiment, the first proportional regulating valve 35 is a valve assembly, which includes a first electrically operated proportional regulating valve installed on the first water supply branch pipe 20 and a second electrically operated proportional regulating valve installed on the second water supply branch pipe 21. The central control module 33 controls the opening degree of the two electrically operated proportional regulating valves respectively, thereby independently regulating the flow rate of cold water in the primary heat exchange core 2 and the secondary heat exchange core 3.

[0073] Flow meters and temperature sensors are installed on both the first water supply branch pipe 20 and the second water supply branch pipe 21. The flow meters are used to collect the water flow rate entering the primary heat exchange core 2 and the secondary heat exchange core 3, and the temperature sensors are used to collect the water temperature entering the corresponding heat exchange core. The above detection data can be sent to the central control module 33 for heat exchange calculation and control correction.

[0074] The organic Rankine cycle power generation module includes an evaporator 4, an expander 5, a generator 6, a condenser 7, a working fluid pump 8, a working fluid steam pipe 15, an exhaust pipe 16, a liquid working fluid pipe 17, and a high-pressure working fluid pipe 18.

[0075] The outlet of the first heat exchange water channel of the primary heat exchange core 2 is connected to the heat source water side inlet of the evaporator 4 through the primary heat exchange outlet water pipe 14. The evaporator 4 includes a heat source water side and an organic working fluid side, which exchange heat with each other but are isolated from each other.

[0076] The high-temperature hot water generated by the primary heat exchanger core 2 enters the heat source water side of the evaporator 4 through the primary heat exchanger outlet pipe 14. After releasing heat to the organic working fluid side in the evaporator 4, the temperature of the high-temperature hot water decreases, and it is discharged through the heat source water side outlet of the evaporator 4. Preferably, the heat source water side outlet of the evaporator 4 is connected to the inlet of the main water pump 12 through a circulating water supply pipe to realize the recycling of heat source water and achieve the purpose of energy saving and environmental protection.

[0077] The organic working fluid outlet of evaporator 4 is connected to the inlet of expander 5 via working fluid vapor pipe 15. The outlet of expander 5 is connected to the inlet of condenser 7 via exhaust pipe 16. The outlet of condenser 7 is connected to the inlet of working fluid pump 8 via liquid working fluid pipe 17. The outlet of working fluid pump 8 is connected to the organic working fluid inlet of evaporator 4 via high-pressure working fluid pipe 18.

[0078] The organic working fluid can be a low-boiling-point organic fluid suitable for medium- and low-temperature heat sources, such as R245fa, isopentane, n-pentane, butane, and other common organic working fluids. The specific working fluid can be determined based on the outlet water temperature of the first-stage heat exchanger, evaporation pressure, condensation temperature, safety, and environmental protection requirements.

[0079] During operation, the organic working fluid absorbs heat from the primary high-temperature hot water in evaporator 4 and evaporates to form high-pressure organic working fluid steam. This high-pressure organic working fluid steam enters expander 5 via working fluid steam pipe 15. Expander 5 expands and performs work, driving generator 6 to output electrical energy. The low-pressure organic working fluid steam after performing work enters condenser 7 via exhaust pipe 16, where it condenses into liquid organic working fluid. The liquid organic working fluid enters working fluid pump 8 via liquid working fluid pipe 17, and after being pressurized by working fluid pump 8, it returns to evaporator 4 via high-pressure working fluid pipe 18, thus forming a closed-loop organic working fluid cycle.

[0080] The central control module 33 is preferably communicatively connected to the working fluid pump 8. The central control module 33 adjusts the speed or flow rate of the working fluid pump 8 based on at least one of the following parameters: the heat source inlet temperature of the evaporator 4, the heat source outlet temperature, the organic working fluid evaporation pressure, and the expander 5 inlet temperature. For example, when the temperature of the first-stage heat exchange outlet water increases and the evaporation pressure is lower than the set value, the central control module 33 can increase the speed of the working fluid pump 8; when the temperature of the first-stage heat exchange outlet water decreases or the evaporation pressure is too high, the central control module 33 can decrease the speed of the working fluid pump 8 to ensure that the organic Rankine cycle power generation module operates within the preset evaporation pressure range.

[0081] In this embodiment, the temperature of the alcohol vapor decreases after heat exchange by the primary heat exchange core 2, and some of the alcohol vapor may have condensed into liquid. The alcohol vapor-liquid mixture continues to flow downwards along the alcohol vapor channel 13 and enters the area where the secondary heat exchange core 3 is located. The second water supply branch pipe 21 sends cold water into the second hot water channel of the secondary heat exchange core 3. After absorbing the remaining heat of the alcohol vapor in the second hot water channel, the cold water heats up to form medium-temperature hot water, which is then output through the secondary heat exchange outlet pipe 23. The alcohol vapor is further cooled and completely condensed at the secondary heat exchange core 3, forming liquid alcohol, which is then discharged through the liquid outlet 22.

[0082] The central control module 33 acquires the real-time temperature of the liquid at the liquid outlet 22 through the liquid temperature sensor 26. The central control module 33 compares the real-time liquid temperature with the preset dispensing temperature and adjusts the opening degree of the first proportional regulating valve 35 corresponding to the second water supply branch pipe 21 according to the comparison result.

[0083] It should be noted that the preset distillation temperature range can be set according to the aroma type of the liquor, the distillation stage, the distillation process, or the company's standards.

[0084] When the real-time wine temperature is higher than the preset upper limit of the wine outlet temperature, the central control module 33 increases the opening of the first proportional regulating valve 35 corresponding to the second water supply branch pipe 21, thereby increasing the flow rate of cold water entering the second hot water exchange channel, enhancing the secondary heat exchange cooling intensity, and thus reducing the wine outlet temperature.

[0085] When the real-time temperature of the liquor is lower than the preset lower limit of the liquor outlet temperature, the central control module 33 reduces the opening of the first proportional regulating valve 35 corresponding to the second water supply branch pipe 21, thereby reducing the flow rate of cold water entering the second hot water exchange channel, reducing the intensity of secondary heat exchange cooling, and thus preventing the liquor from becoming too cold.

[0086] When the real-time wine temperature is within the preset range, the central control module 33 maintains the current opening degree or makes a slight correction.

[0087] In this embodiment, the central control module 33 can adjust the first proportional control valve 35 using PID control, fuzzy control, or a combination of PID and fuzzy control. Specifically, the deviation between the real-time wine temperature and the preset wine outlet temperature is used as the control input, and the valve opening of the second water supply branch pipe 21 is used as the control output to achieve closed-loop control of the wine outlet temperature.

[0088] The medium-temperature combined heat and power module includes a secondary heat exchange outlet water pipe 23, a heating branch pipe 25, a cooling branch pipe 24, a second proportional regulating valve 36, a heat pump 9, and an absorption chiller 10.

[0089] The secondary heat exchange outlet pipe 23 is connected to the outlet of the second hot water channel of the secondary heat exchange core 3. The medium-temperature hot water generated by the secondary heat exchange core 3 is output through the secondary heat exchange outlet pipe 23 and then distributed to the heating branch pipe 25 and the cooling branch pipe 24 by the second proportional regulating valve 36.

[0090] In one embodiment, the second proportional regulating valve 36 is a one-in-two-out electrically operated three-way proportional distribution valve. Its inlet end is connected to the secondary heat exchange outlet pipe 23, and its two outlet ends are connected to the heating branch pipe 25 and the cooling branch pipe 24, respectively. In another embodiment, the second proportional regulating valve 36 is a valve assembly, which includes a heating-side electrically operated proportional regulating valve installed on the heating branch pipe 25 and a cooling-side electrically operated proportional regulating valve installed on the cooling branch pipe 24. The central control module 33 adjusts the opening degree of the heating-side and cooling-side electrically operated proportional regulating valves respectively, thereby controlling the flow distribution of medium-temperature hot water between the heating and cooling branches.

[0091] The heating branch pipe 25 can connect to the plant's heating system, domestic hot water system, shower system, and other medium-temperature hot water heating equipment. A heating return water temperature sensor 29 and a heating flow meter 30 are installed at the end of the heating branch pipe 25 or on the heating return water pipe. The heating return water temperature sensor 29 is used to collect the heating return water temperature, and the heating flow meter 30 is used to collect the water flow rate of the heating return water or the heating branch pipe.

[0092] A heat pump 9 and an absorption chiller 10 are sequentially installed on the refrigeration branch pipe 24. The medium-temperature hot water introduced into the refrigeration branch pipe 24 first enters the heat pump 9, which heats the hot water to the required driving temperature of the absorption chiller 10. The heated hot water is then sent to the absorption chiller 10. The absorption chiller 10 can be a common absorption refrigeration device suitable for hot water driving, such as a lithium bromide absorption chiller. The cooling capacity output by the absorption chiller 10 can be used for factory air conditioning, process cooling, auxiliary cooling of liquids, cold storage, or other refrigeration needs. A refrigeration return water temperature sensor 31 and a refrigeration flow meter 32 are installed at the end of the refrigeration branch pipe 24 or at the return water end of the refrigeration network.

[0093] In this embodiment, when the medium-temperature hot water is used directly for heating, it can meet the needs of domestic hot water, cleaning, or low-temperature heating in the factory area; when used for cooling, the heat pump 9 can heat the medium-temperature hot water to the driving temperature required by the absorption chiller 10, and then drive the absorption chiller 10 to generate cooling capacity.

[0094] The central control module 33 can be a common control device capable of signal acquisition and valve control, such as a PLC, DCS, industrial control computer, or embedded controller. In this embodiment, the central control module 33 is communicatively connected to at least the first proportional regulating valve 35, the second proportional regulating valve 36, the liquid temperature sensor 26, the heat pump 9, the absorption chiller 10, the heating return water temperature sensor 29, the heating flow meter 30, the cooling return water temperature sensor 31, the cooling flow meter 32, and the working fluid pump 8.

[0095] Temperature sensors and flow meters can also be installed on the primary heat exchange outlet pipe 14 and the secondary heat exchange outlet pipe 23. A pressure sensor can also be installed inside the evaporator 4, and a temperature sensor can also be installed at the inlet of the expander 5. All these sensors are connected to the central control module 33.

[0096] The central control module 33 can calculate the instantaneous heating load based on the data collected by the heating return water temperature sensor 29 and the heating flow meter 30. The central control module 33 can also calculate the instantaneous cooling load based on the data collected by the cooling return water temperature sensor 31 and the cooling flow meter 32.

[0097] The central control module 33 adjusts the second proportional regulating valve 36 according to the instantaneous heating load and instantaneous cooling load, so that the medium-temperature hot water output from the secondary heat exchange outlet pipe 23 is continuously and proportionally distributed between the heating branch pipe 25 and the cooling branch pipe 24.

[0098] In this embodiment, the central control module 33 is equipped with heating priority control logic and cooling branch start threshold.

[0099] The heating priority control logic means that when there is a heating demand in the heating branch of the plant area but it has not reached saturation, the central control module 33 prioritizes increasing the opening of the corresponding heating branch pipeline 25 of the second proportional regulating valve 36, so that medium-temperature hot water can enter the heating branch pipeline 25 first.

[0100] The heating load saturation state can be determined by any one or a combination of the following conditions: the heating return water temperature at the end of the heating branch pipeline 25 reaches the upper limit of the set return water temperature; the flow rate of the heating branch reaches the set maximum flow rate, but the temperature difference between the supply and return water is lower than the set temperature difference; the instantaneous heating load reaches the upper limit of the set heating load; and the heating terminal equipment reports that the heating demand has been met.

[0101] When the heating load reaches saturation, the central control module 33 gradually reduces the opening of the heating branch pipe 25 corresponding to the second proportional regulating valve 36 and increases the opening of the corresponding cooling branch pipe 24, so that the excess medium-temperature hot water is smoothly transferred to the cooling branch pipe 24.

[0102] The starting threshold for the refrigeration branch can include any one or a combination of the following conditions: the flow rate of the medium-temperature hot water introduced into the refrigeration branch pipe 24 reaches the set minimum flow rate; the temperature of the medium-temperature hot water introduced into the refrigeration branch pipe 24 reaches the set minimum temperature; the enthalpy value of the medium-temperature hot water introduced into the refrigeration branch pipe 24 reaches the set minimum enthalpy value; the load of the refrigeration terminal reaches the minimum load required for the economical operation of the absorption chiller 10; and the expected operating efficiency of the heat pump 9 reaches the set value.

[0103] When the flow rate and / or enthalpy of the medium-temperature hot water introduced into the refrigeration branch pipe 24 reaches the refrigeration branch start-up threshold, the central control module 33 starts the heat pump 9 and the absorption chiller 10. Otherwise, the central control module 33 prohibits or delays the start-up of the heat pump 9 and the absorption chiller 10, keeping them in a stopped or standby state.

[0104] This control logic can prevent the heat pump 9 and the absorption chiller 10 from frequently starting and stopping under low load, thereby reducing unnecessary power consumption and equipment wear.

[0105] Example 2:

[0106] A multi-generation method based on the cascade utilization of waste heat from alcohol vapor, implemented using the aforementioned multi-generation system, includes the following steps:

[0107] S1, high-grade heat recovery and organic Rankine cycle power generation

[0108] The alcohol vapor is fed into the cascaded heat exchanger through the alcohol vapor inlet 1. After entering the alcohol vapor channel 13, the alcohol vapor first flows through the area where the primary heat exchange core 2 is located. The first water supply branch pipe 20 sends cold water into the first hot water exchange channel of the primary heat exchange core 2. The cold water absorbs the high-grade heat from the alcohol vapor in the first hot water exchange channel and is heated into high-temperature hot water.

[0109] High-temperature hot water enters the heat source water side of evaporator 4 through the primary heat exchange outlet pipe 14. In evaporator 4, the high-temperature hot water transfers heat to the organic working fluid. The organic working fluid absorbs heat and evaporates to form high-pressure organic working fluid steam. The high-pressure organic working fluid steam enters expander 5 through working fluid steam pipe 15, expands, and performs work. Expander 5 drives generator 6 to generate electricity.

[0110] The expanded organic working fluid enters the condenser 7 through the exhaust pipe 16 and is condensed into liquid organic working fluid. The liquid organic working fluid enters the working fluid pump 8 through the liquid working fluid pipe 17, and is then pressurized by the working fluid pump 8 and sent back to the evaporator 4 through the high-pressure working fluid pipe 18, completing a closed loop.

[0111] S2, two-stage condensation temperature control and medium-temperature hot water production

[0112] After being heated by the primary heat exchanger 2, the cooled and partially condensed alcohol vapor continues to flow along the alcohol vapor channel 13 to the secondary heat exchanger 3. The second water supply branch pipe 21 delivers cold water into the second hot water channel of the secondary heat exchanger 3. In the second hot water channel, the cold water absorbs the remaining heat from the alcohol vapor and is heated to medium-temperature hot water. The medium-temperature hot water is then output through the secondary heat exchanger outlet pipe 23.

[0113] Meanwhile, the central control module 33 adjusts the opening of the first proportional regulating valve 35 corresponding to the second water supply branch pipe 21 based on the deviation between the real-time wine temperature collected at the wine outlet 22 and the preset wine outlet temperature, thereby controlling the intensity of the secondary heat exchange cooling.

[0114] When the real-time wine temperature is higher than the preset upper limit of the wine dispensing temperature, the central control module 33 increases the opening of the first proportional regulating valve 35 corresponding to the second water supply branch pipe 21 to increase the cold water flow rate of the second water supply branch pipe 21.

[0115] When the real-time wine temperature is lower than the preset lower limit of the wine temperature, the central control module 33 reduces the opening of the first proportional regulating valve 35 corresponding to the second water supply branch pipe 21, so as to reduce the cold water flow of the second water supply branch pipe 21.

[0116] Through the above control, the wine vapor is completely condensed into wine liquid at the secondary heat exchange core 3, and the wine liquid temperature at the wine liquid outlet 22 is maintained within the preset wine liquid temperature range.

[0117] S3, medium-temperature heat load distribution

[0118] The central control module 33 acquires the heating load and cooling load, and according to the principle of heating priority, continuously proportionally diverts the medium-temperature hot water output from the secondary heat exchange outlet pipe 23 through the second proportional regulating valve 36.

[0119] When there is a heating demand, the central control module 33 increases the opening of the second proportional regulating valve 36 corresponding to the heating branch pipeline 25, and delivers at least a portion of the medium-temperature hot water to the heating system and / or domestic hot water system through the heating branch pipeline 25.

[0120] When the heating load is saturated and there is a cooling demand, the central control module 33 adjusts the second proportional regulating valve 36 to introduce excess medium-temperature hot water into the cooling branch pipe 24. The medium-temperature hot water is heated by the heat pump 9 and used as the driving heat source for the absorption chiller 10. The absorption chiller 10 generates cooling capacity and outputs it to the cooling terminal.

[0121] When the flow rate and / or enthalpy value of the medium-temperature hot water introduced into the refrigeration branch pipe 24 do not reach the start-up threshold required for the economical operation of the absorption chiller 10, the central control module 33 maintains the heat pump 9 and the absorption chiller 10 in a stopped or standby state.

[0122] Please see Figure 3 To further illustrate the operation of this invention, a typical operating condition is given below:

[0123] Assume the total heat released by the complete condensation of alcohol vapor in the cascaded heat exchanger is 1000kW. The first-stage heat exchanger core 2 extracts approximately 350kW (about 35%) of this high-grade heat, heating the cold water in the first water supply branch pipe 20 to form high-temperature hot water. This high-temperature hot water then enters the evaporator 4, driving the organic Rankine cycle power generation module to generate electricity. Based on an actual operating efficiency of approximately 5% for the organic Rankine cycle power generation module, this stage can stably output approximately 17.5 kW of electricity. Forcibly increasing the heat exchange ratio in this stage would lower the average temperature of the heat source, causing a sharp drop in power generation efficiency. Therefore, approximately 35% is the optimal balance point between power generation efficiency and heat exchange area. This portion of the output electricity is fed into the plant's power grid, directly offsetting the mains power consumption costs of the mains-consuming equipment.

[0124] The alcohol vapors after the first-stage heat exchange continue into the second-stage heat exchange core 3. The second-stage heat exchange core 3 extracts approximately 600kW (about 60%) of the medium-temperature heat, which heats the cold water in the second water supply branch pipe 21 to form medium-temperature hot water. This medium-temperature hot water is then output through the second-stage heat exchange outlet pipe 23 and distributed to the heating branch pipe 25 and the cooling branch pipe 24 according to the plant's needs. This 600kW of latent heat cannot be efficiently used for power generation, but it perfectly matches the plant's heating and cooling temperature requirements. The central control module 33 distributes this portion of heat according to the load: in winter or during peak heating season, priority is given to allocating (e.g., 400 kW) directly for heating or showering in the plant area, 100% replacing the original gas boiler consumption in the plant area; in summer or when heating is saturated, the surplus heat (e.g., 200 kW) is smoothly transferred to the cooling branch 24. Under the premise of consuming a small amount of auxiliary power (e.g., 30 kW) to drive the heat pump 9, the absorption chiller 10 is introduced to produce about 161 kW of process cooling capacity, which greatly reduces the power consumption of the traditional air conditioning system.

[0125] The irreversible heat loss of the system accounts for about 5%: the remaining about 50 kW of heat is lost due to unavoidable physical losses such as heat exchanger shell 37 and friction loss along the pipeline.

[0126] Based on the first law of thermodynamics, in the above embodiment, with an input of 1000 kW waste heat and 30 kW auxiliary power, the system outputs 17.5 kW of electrical energy, 400 kW of heat energy, and 161 kW of cooling energy, achieving a stable overall energy utilization rate of approximately 56.1%. In contrast, the energy utilization rate of traditional direct-vent cooling tower systems is 0%, while existing single heat recovery systems, limited by seasonal absorption, typically have an annual comprehensive utilization rate hovering between 10% and 30%. The heat distribution logic of this invention strictly adheres to the principles of temperature matching and tiered utilization, achieving maximum energy absorption. This invention can absorb waste heat from alcohol vapor under different operating conditions throughout the year, avoiding the problem of waste heat being discharged during summer or low-load periods in single-heating modes.

[0127] The following is a further explanation of the seasonal operating mode:

[0128] 1. Winter Heating Priority Mode: During winter, the plant area experiences high demands for heating and domestic hot water. The central control module 33 prioritizes increasing the opening of the second proportional regulating valve 36 corresponding to the heating branch pipe 25, ensuring that the medium-temperature hot water output from the secondary heat exchange outlet pipe 23 preferentially enters the heating branch pipe 25. If the heating load is not saturated, the cooling branch pipe 24 can remain closed or in standby mode with a low flow rate.

[0129] 2. Summer Cooling and Cooling Mode: Summer heating load is low, but there may still be demand for air conditioning or process cooling in the plant area. After the central control module 33 detects that the heating load at the end of the heating branch pipe 25 is saturated, it distributes the surplus medium-temperature hot water to the cooling branch pipe 24 through the second proportional regulating valve 36. When the cooling branch start-up threshold is met, the heat pump 9 and absorption chiller 10 are started to convert waste heat into cooling.

[0130] 3. Spring and Autumn Transition Mode: During spring and autumn, there may be simultaneous demand for domestic hot water and a certain amount of cooling. The central control module 33 adjusts the second proportional regulating valve 36 according to the instantaneous heating load and instantaneous cooling load, so that medium-temperature hot water is distributed proportionally to the heating branch pipe 25 and the cooling branch pipe 24.

[0131] 4. Low-load operation mode: When both heating and cooling loads are low, the central control module 33 can prioritize the operation of the organic Rankine cycle power generation module while reducing the secondary hot water flow to the minimum required for wine outlet temperature control. If the cooling branch does not reach the start-up threshold, the heat pump 9 and absorption chiller 10 remain in a stopped or standby state.

[0132] To improve system safety and stability, the central control module 33 can also be configured with the following abnormal protection logic: When the real-time liquid temperature at the liquid outlet 22 continuously exceeds the preset upper limit of the liquid outlet temperature, the central control module 33 increases the opening of the second water supply branch pipe 21 corresponding to the first proportional regulating valve 35; if the cooling requirement is still not met after increasing the opening to the maximum, an alarm signal is issued, prompting a reduction in the amount of liquid steam entering the system or activation of the backup cooling device. When the temperature of the high-temperature hot water in the primary heat exchange outlet pipe 14 is lower than the minimum operating temperature of the organic Rankine cycle power generation module, the central control module 33 reduces the speed of the working fluid pump 8 or suspends the operation of the organic Rankine cycle power generation module to prevent the expander 5 from operating under inefficient conditions. When the evaporation pressure of the organic working fluid in the evaporator 4 exceeds the set upper limit, the central control module 33 reduces the speed of the working fluid pump 8 or cuts off the flow of heat source water into the evaporator 4, and issues an alarm. When the flow rate of the heating branch pipe 25 or the cooling branch pipe 24 decreases abnormally, the central control module 33 determines that there may be a valve malfunction, pipe blockage, or terminal closure, and reduces the opening of the corresponding branch or shuts down for protection as appropriate. When the heat pump 9 or the absorption chiller 10 malfunctions, the central control module 33 closes or reduces the opening of the second proportional regulating valve 36 corresponding to the cooling branch pipe 24, and preferentially transfers the medium-temperature hot water to the heating branch pipe 25 or other safe consumption paths.

[0133] Through the above-mentioned anomaly protection, the present invention can adapt to the actual working conditions of large fluctuations in alcohol vapor flow and temperature during the brewing process, thereby improving the safety and reliability of the system.

[0134] This invention can be applied to the distillation and condensation process of brewing enterprises. Through this invention, while completing the condensation of alcohol vapor and controlling the temperature of the alcohol output, waste heat can be used for power generation, heating and cooling, thereby improving the comprehensive utilization rate of energy, reducing cooling water consumption and waste heat emissions, and has good industrial application value.

[0135] Finally, it should be noted that the above description is merely a preferred embodiment of the present invention. Those skilled in the art, under the guidance of the present invention, can make various similar representations without departing from the spirit and claims of the present invention, and such modifications all fall within the protection scope of the present invention.

Claims

1. A poly-generation system based on cascade utilization of wine vapor residual heat, characterized in that, include: A cascaded heat exchange device includes a heat exchanger shell and a primary heat exchange core and a secondary heat exchange core arranged sequentially in the heat exchanger shell along the direction of alcohol vapor flow. The upper part of the heat exchanger shell is provided with an alcohol vapor inlet, and the lower part of the heat exchanger shell is provided with an alcohol outlet. The primary heat exchange core and the secondary heat exchange core are respectively formed with a first hot water exchange channel and a second hot water exchange channel capable of exchanging heat with alcohol vapor. After entering through the alcohol vapor inlet, the alcohol vapor exchanges heat with the water in the first hot water exchange channel and the second hot water exchange channel in sequence, and after condensation at the secondary heat exchange core, it is discharged from the alcohol outlet. The water distribution module has a first water supply branch pipe and a second water supply branch pipe. The first water supply branch pipe is connected to the inlet of the first hot water exchange channel, and the second water supply branch pipe is connected to the inlet of the second hot water exchange channel. Both the first water supply branch pipe and the second water supply branch pipe adjust the cold water flow rate through a first proportional regulating valve. An organic Rankine cycle power generation module includes an evaporator, an expander, a generator, a condenser, and a working fluid pump. The evaporator, expander, condenser, and working fluid pump form a closed-loop organic working fluid system through pipelines. The expander is driven by the generator. The outlet of the first heat exchange water channel is connected to the heat source inlet of the evaporator through a primary heat exchange outlet pipe, so that the high-temperature hot water obtained from the primary heat exchange can be used as the heat source for the organic Rankine cycle power generation module. The medium-temperature combined heat and power (CHP) module includes a secondary heat exchange outlet pipe, a heating branch pipe, and a cooling branch pipe. The secondary heat exchange outlet pipe is connected to the outlet of the second hot water exchange channel and is connected to the heating branch pipe and the cooling branch pipe respectively through a second proportional regulating valve. The heating branch pipe is used to supply medium-temperature hot water. A heat pump and an absorption chiller are sequentially installed on the cooling branch pipe. The heat pump is used to heat the medium-temperature hot water sent from the cooling branch pipe and use it as the driving heat source for the absorption chiller. The central control module is communicatively connected to the first proportional regulating valve, the second proportional regulating valve, the heat pump, and the absorption chiller, respectively. The central control module is configured to adjust the flow rate of cold water supplied to the first and second water supply branches via a first proportional regulating valve, and to adjust the flow rate of medium-temperature hot water supplied to the heating and cooling branch pipes via a second proportional regulating valve, based on the wine temperature at the wine outlet, the primary heat exchange outlet water temperature in the primary heat exchange outlet pipe, the secondary heat exchange outlet water temperature in the secondary heat exchange outlet pipe, and the heating and cooling loads.

2. The polygeneration system of claim 1, wherein, The cascaded heat exchange device is a vertical heat exchange device. The first-stage heat exchange core is located above the second-stage heat exchange core. The wine vapor inlet and the wine outlet are connected by a wine vapor channel, which vertically passes through the first-stage heat exchange core and the second-stage heat exchange core in sequence. A wine temperature sensor is installed at the wine outlet, and the wine temperature sensor is communicatively connected to the central control module.

3. The multi-generation system according to claim 1, characterized in that, The inlet of the first proportional regulating valve is connected to the water treatment equipment and the main water pump in sequence through a pipeline. The inlet of the main water pump is connected to the municipal water supply or circulating water supply pipe. The water treatment equipment is used to filter and soften the cold water entering the primary heat exchange core and the secondary heat exchange core.

4. The multi-product system according to claim 3, characterized in that, The evaporator includes a heat source water side and an organic working fluid side that exchange heat with each other but are isolated from each other; The primary heat exchange outlet pipe is connected to the heat source water side inlet of the evaporator, and the heat source water side outlet of the evaporator is connected to the inlet of the main water pump via a circulating water supply pipe. The organic working fluid side outlet of the evaporator is connected to the inlet of the expander via a working fluid vapor pipe. The outlet of the expander is connected to the inlet of the condenser via an exhaust pipe. The outlet of the condenser is connected to the inlet of the working fluid pump via a liquid working fluid pipe. The outlet of the working fluid pump is connected to the organic working fluid side inlet of the evaporator via a high-pressure working fluid pipe.

5. The multi-generation system according to claim 1, characterized in that, A heating return water temperature sensor and a heating flow meter are installed at the end of the heating branch pipeline or on the heating return water pipeline. The end of the refrigeration branch pipeline or the return water end of the refrigeration network is equipped with a refrigeration return water temperature sensor and a refrigeration flow meter. The central control module is configured to calculate the instantaneous heating load and instantaneous cooling load based on the heating return water temperature collected by the heating return water temperature sensor, the heating flow rate collected by the heating flow meter, the cooling return water temperature collected by the cooling return water temperature sensor, and the cooling flow rate collected by the cooling flow meter, and adjust the opening degree of the second proportional regulating valve corresponding to the heating branch pipe and the cooling branch pipe according to the instantaneous heating load and the instantaneous cooling load.

6. The multi-generation system according to claim 1, characterized in that, The central control module is equipped with heating priority control logic and cooling branch start threshold. When the heating load at the end of the heating branch pipeline is not saturated, the central control module increases the opening degree of the second proportional regulating valve corresponding to the heating branch pipeline. When the heating load at the end of the heating branch pipeline reaches saturation, and the flow rate and / or enthalpy of the medium-temperature hot water output from the secondary heat exchange outlet pipeline reaches the starting threshold of the cooling branch, the central control module increases the opening of the second proportional regulating valve corresponding to the cooling branch pipeline and starts the heat pump and absorption chiller. When the flow rate and / or enthalpy value of the medium-temperature hot water introduced into the refrigeration branch pipe are lower than the refrigeration branch start-up threshold, the central control module prohibits or delays the start-up of the heat pump and absorption chiller.

7. The multi-generation system according to claim 1, characterized in that, The central control module is communicatively connected to the working fluid pump and is configured to adjust the speed or flow rate of the working fluid pump according to at least one of the following parameters: the heat source inlet temperature of the evaporator, the heat source outlet temperature of the evaporator, the evaporation pressure of the organic working fluid in the evaporator, and the inlet temperature of the expander, so that the organic Rankine cycle power generation module operates within a preset evaporation pressure range.

8. A multi-product method based on the cascade utilization of waste heat from brewing steam, characterized in that, The implementation of the multi-generation system according to any one of claims 1 to 7 includes the following steps: S1. High-grade heat recovery and organic Rankine cycle power generation: The alcohol vapor is sent into the cascade heat exchanger through the alcohol vapor inlet, so that the alcohol vapor first exchanges heat with the first heat exchange core; the cold water entering the first hot water exchange channel through the first water supply branch pipe is heated into high-temperature hot water, and the high-temperature hot water is sent to the heat source water side of the evaporator through the first heat exchange outlet pipe; in the evaporator, the high-temperature hot water is used to heat the organic working fluid, so that the organic working fluid evaporates to form high-pressure organic working fluid steam, and the high-pressure organic working fluid steam enters the expander through the working fluid steam pipeline to expand and do work and drive the generator to generate electricity; the expanded organic working fluid enters the condenser through the exhaust pipe to condense, and then is sent back to the evaporator by the working fluid pump through the high-pressure working fluid pipeline; S2, Secondary Condensation Temperature Control and Medium-Temperature Hot Water Production: The alcohol vapor, which has cooled and partially condensed after heat exchange in the primary heat exchange core, continues to flow to the secondary heat exchange core and exchanges heat with it; the cold water entering the second hot water exchange channel through the second water supply branch pipe is heated into medium-temperature hot water, which is then output through the secondary heat exchange outlet pipe; at the same time, the cooling intensity of the secondary heat exchange is controlled by adjusting the opening of the first proportional regulating valve corresponding to the second water supply branch pipe, so that the alcohol vapor is completely condensed into alcohol at the secondary heat exchange core, and the temperature of the alcohol at the outlet is maintained within the preset outlet temperature range. S3, Medium-Temperature Heat Load Following Distribution: Obtain heating and cooling loads, and continuously proportionally distribute the medium-temperature hot water output from the secondary heat exchange outlet pipe through the second proportional regulating valve according to the heating priority principle; when there is heating demand, at least a portion of the medium-temperature hot water is transported to the heating system and / or domestic hot water system through the heating branch pipe; when the heating load is saturated and there is cooling demand, the surplus medium-temperature hot water is introduced into the cooling branch pipe, heated by the heat pump, and used as the driving heat source for the absorption chiller to generate cooling capacity.

9. The method for polygeneration according to claim 8, characterized in that, In step S2, the central control module adjusts the opening of the second water supply branch pipe corresponding to the first proportional regulating valve based on the deviation between the real-time wine temperature collected at the wine outlet and the preset wine outlet temperature. When the real-time wine temperature is higher than the preset upper limit of the wine dispensing temperature, the opening of the first proportional regulating valve corresponding to the second water supply branch pipe is increased to increase the cold water flow rate of the second water supply branch pipe. When the real-time wine temperature is lower than the preset lower limit of the wine outlet temperature, the opening of the second water supply branch corresponding to the first proportional regulating valve is reduced to reduce the cold water flow rate of the second water supply branch.

10. The method for polygeneration according to claim 8, characterized in that, In step S3, the central control module collects the heating return water temperature and heating flow rate at the end of the heating branch pipeline and the cooling return water temperature and cooling flow rate of the cooling network in real time, and calculates the instantaneous heating load and instantaneous cooling load. When the instantaneous heating load does not reach the set upper limit of the heating load, increase the opening of the corresponding heating branch pipeline of the second proportional regulating valve; When the return water temperature at the end of the heating branch pipeline reaches the upper limit of the set return water temperature or the instantaneous heating load reaches the upper limit of the set heating load, the heating load is determined to be saturated, and the excess medium-temperature hot water is smoothly transferred to the cooling branch pipeline by adjusting the second proportional regulating valve. The heat pump and absorption chiller shall be started only when the flow rate and / or enthalpy of the medium-temperature hot water introduced into the refrigeration branch pipe reaches the start-up threshold required for the economical operation of the absorption chiller; otherwise, the heat pump and absorption chiller shall be kept in a stopped or standby state.

Images