Method and system for coordinated recovery of ship waste heat from multiple sources

Abstract

The application discloses a ship waste heat multi-source coordinated recovery method and system, collects ship multi-source temperature signals and heat exchange pipeline layout, performs heat value rating on the temperature signals to form a heat grade distribution, positions high-quality heat points to establish heat exchange contact, forms a dense heat collection area through cascade strengthening, constructs a heat load fluctuation curve to identify intermittent heat supply sources, establishes a heat road intersection point to form a flexible heat supply field, divides effective temperature stages to configure hierarchical heat exchange to generate a step utilization chain, forms a heat storage and release network to output a coordinated control table, exports a flow direction guide field to identify heat loss nodes to set a compensation channel, maps a network heat state through the step utilization network to obtain a full-network heat spectrum, identifies heat flow convergence characteristics to determine a flow convergence center, performs supply and demand coordination analysis to identify supply and demand differences and reserve capacity, generates a coordination margin to configure a control response strategy, completes waste heat multi-source coordinated recovery, and improves ship energy utilization efficiency and system operation stability.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of heat pump control, in particular to a ship waste heat multi-source coordinated recovery method and system. BACKGROUND

[0002] About 50%-60% of fuel energy is discharged in the form of exhaust gas, cooling water, lubricating oil, etc. during the operation of the main and auxiliary machines of a ship, with temperatures ranging from hundreds of degrees Celsius to tens of degrees Celsius, which contains great recovery potential. Existing recovery technologies mainly focus on a single temperature parameter, and fail to comprehensively evaluate the influence of temperature, flow rate and availability on the value of heat energy, resulting in that high-quality heat sources are not given priority for use, and low-quality heat sources are configured with excessively high investment.

[0003] At the same time, the auxiliary machines of the ship are frequently started and stopped according to the power load, and part of the heat sources presents an intermittent supply feature. The existing system lacks adjustment and buffering means, and is forced to stop or efficiency drops sharply when the heat source is interrupted. In addition, when heat sources of multiple temperature levels flow into the same system, there is a lack of hierarchical matching strategy and step utilization mechanism, the pipeline network design lacks overall optimization, the transmission loss is not identified and recovered, and the dynamic matching ability of supply and demand is insufficient, which restricts the overall performance and stability of waste heat recovery. SUMMARY

[0004] The present application discloses a ship waste heat multi-source coordinated recovery method and system, which forms a heat grade distribution by collecting multi-source temperature signals and performing heat value rating, locates high-quality heat points and forms a dense heat collection area through cascade reinforcement, identifies intermittent heat sources for heat load fluctuations and establishes a flexible heat supply field, configures hierarchical heat exchange and heat storage and release networks to realize temperature gradient utilization, derives a flow direction guide field to obtain a full-network heat spectrum and lock a confluence center, performs supply and demand coordination analysis and configures a regulation and response strategy, and finally realizes the gradient and efficient coordinated recovery of multi-source waste heat.

[0005] The present application discloses a ship waste heat multi-source coordinated recovery method and system, which forms a heat grade distribution by collecting multi-source temperature signals and performing heat value rating, locates high-quality heat points and forms a dense heat collection area through cascade reinforcement, identifies intermittent heat sources for heat load fluctuations and establishes a flexible heat supply field, configures hierarchical heat exchange and heat storage and release networks to realize temperature gradient utilization, derives a flow direction guide field to obtain a full-network heat spectrum and lock a confluence center, performs supply and demand coordination analysis and configures a regulation and response strategy, and finally realizes the gradient and efficient coordinated recovery of multi-source waste heat.

[0006] Collecting multi-source temperature signals and heat exchange pipeline layout during the operation of the ship, the multi-source temperature signals covering the high-temperature section of the main engine and the medium-temperature section of the auxiliary engine, performing heat value rating on the multi-source temperature signals to form a heat grade distribution;

[0007] Based on the heat grade distribution, locating high-quality heat points, performing source analysis on the high-quality heat points to obtain heat dissipation positions, establishing heat exchange contact at the heat dissipation positions to generate a heat collection condition, and implementing cascade reinforcement through the heat collection condition to form a dense heat collection area;

[0008] Constructing a heat load fluctuation curve according to the fluctuation law of the medium-temperature section of the auxiliary engine, identifying intermittent heat sources from the heat load fluctuation curve, matching the intermittent heat sources with the heat exchange pipeline layout to establish heat road intersection points, and deducing flow distribution using the heat road intersection points to form a flexible heat supply field;

[0009] The effective temperature stage is divided based on the temperature level difference of the dense heat collection area, a hierarchical heat exchange is configured in the effective temperature stage to generate a ladder utilization chain, a heat storage and release network is formed based on the ladder utilization chain, and an output coordination control table is cross-arranged according to the heat storage and release network and the flexible heat supply field;

[0010] A flow direction guide field is derived through the resistance distribution of the coordination control table, a full-network thermodynamic spectrum is obtained by reshaping the network thermal state based on the flow direction guide field, and a confluence center is determined by performing convergence feature identification on the full-network thermodynamic spectrum;

[0011] Supply and demand coordination analysis is performed according to the confluence center to identify a supply-demand difference and a reserve capacity, a coordination margin is generated by performing fluctuation evaluation on the supply-demand difference and the reserve capacity, a regulation and control response strategy is configured based on the coordination margin, and waste heat multi-source coordinated recovery is completed.

[0012] The second aspect of the present application proposes a ship waste heat multi-source coordinated recovery system, comprising:

[0013] A heat source rating module is configured to collect multi-source temperature signals and heat exchange pipeline layout during ship operation, the multi-source temperature signals cover the high-temperature section of the main engine and the medium-temperature section of the auxiliary engine, and a heat value rating is performed on the multi-source temperature signals to form a heat grade distribution;

[0014] A heat flow capture module is configured to locate high-quality heat points based on the heat grade distribution, perform source analysis on the high-quality heat points to obtain heat dissipation positions, establish heat exchange contact at the heat dissipation positions to generate a heat collection working condition, and form a dense heat collection area by cascading and strengthening through the heat collection working condition;

[0015] A heat supply deployment module is configured to construct a heat load fluctuation curve according to the fluctuation law of the medium-temperature section of the auxiliary engine, identify intermittent heat supply sources from the heat load fluctuation curve, match the intermittent heat supply sources with the heat exchange pipeline layout to establish heat path intersection points, and derive flow distribution to form a flexible heat supply field using the heat path intersection points;

[0016] A heat storage coordination module is configured to divide an effective temperature stage based on the temperature level difference of the dense heat collection area, configure a hierarchical heat exchange in the effective temperature stage to generate a ladder utilization chain, form a heat storage and release network based on the ladder utilization chain, and cross-arrange an output coordination control table according to the heat storage and release network and the flexible heat supply field;

[0017] A heat network optimization module is configured to derive a flow direction guide field through the resistance distribution of the coordination control table, obtain a full-network thermodynamic spectrum by reshaping the network thermal state based on the flow direction guide field, and determine a confluence center by performing convergence feature identification on the full-network thermodynamic spectrum;

[0018] The supply-demand balance module is used for identifying supply-demand difference and reserve capacity according to supply-demand coordination analysis of the confluence center, performing fluctuation evaluation on the supply-demand difference and the reserve capacity to generate a coordination margin, configuring a regulation and control response strategy based on the coordination margin, and completing the waste heat multi-source coordinated recovery.

[0019] The beneficial effects of the present application are embodied in the following points: 1. A multi-dimensional evaluation system of temperature signal is established, and the heat source is graded by comprehensively analyzing temperature, heat scale and transmission loss, thereby providing a basis for differentiated configuration of different quality heat sources. In the heat collection link, heat exchange contact is established at the heat dissipation position of the high-quality heat source to generate heat collection conditions, a heat blocking boundary is established to block the outward diffusion of heat, and heat flow path optimization is performed to guide heat to converge to the working medium flow channel, thereby forming a preferential heat transfer path to promote directional heat transfer, so that dispersed heat is converged to a concentrated area to form a high heat flux area. Through cascade strengthening and boundary tightening, a dense heat collection area with high power density is constructed in a compact space, thereby meeting the heat capture requirements under the condition of limited space in the ship engine room. 2. In view of the intermittent heat supply problem caused by intermittent operation of auxiliary machines, the start-stop law of the heat source is identified through heat load fluctuation curve analysis and heat supply intermittence, and the flow is adaptively allocated by using the mixed flow driving force converted from the flow velocity deviation at the pipeline confluence node, so that the flow distribution can automatically adapt to the changes of the upstream heat source. At the same time, according to the temperature gradient, a multi-stage heat exchange is configured by dividing the effective temperature level to form a step utilization chain, a phase change heat storage technology is introduced, a heat release starting point is generated by aligning the time of the heat storage working window with the low load period, and the heat storage medium circulation order is arranged according to the temperature level to form a heat supplement timing. Energy is stored when the heat source is in excess and released to supplement when it is insufficient, thereby enhancing the system's tolerance to heat source fluctuations. 3. A global heat flow analysis framework of the pipeline network is constructed, and a flow direction guide field is derived through resistance distribution to identify heat loss nodes formed at positions such as valve throttling, pipe diameter mutation and flow direction sharp turn. The traditional waste heat recovery system only focuses on the primary utilization of the main heat source, while the heat loss caused by resistance concentration in the pipeline transmission process is often regarded as an unavoidable loss. By setting a compensation channel at the heat loss node, the small heat exchanger is used to capture these lost heat, and multiple compensation channels are connected in series according to the temperature level to form a step utilization network, thereby converting the originally lost heat into usable heat resources, and realizing the secondary recovery of waste heat. Further, by locking the key heat collection position through the global heat spectrum, a real-time comparison mechanism of supply and demand is established, the supply-demand difference is quantified, and the corresponding reserve capacity is configured, and according to the system coordination margin, a conventional, active and emergency three-level regulation and control strategy is configured, thereby realizing the coordinated operation and optimized utilization of heat in the whole process under multiple heat sources and multiple working conditions.

[0020] It should be understood that the above general description and the following detailed description are only exemplary and explanatory, and cannot limit the present application. BRIEF DESCRIPTION OF DRAWINGS

[0021] The drawings here show the specific examples of the technical solutions of the present application, and constitute a part of the description together with the specific embodiments, for explaining the technical solutions, principles and effects of the present application.

[0022] Unless specifically stated, the same reference signs in different drawings represent the same or similar technical features, and different reference signs may also be used to represent the same or similar technical features.

[0023] Figure 1 is a flowchart of the ship waste heat multi-source coordinated recovery method of the present application.

[0024] Figure 2 is a structural block diagram of the ship waste heat multi-source coordinated recovery system of the present application. DETAILED DESCRIPTION

[0025] In the following description, for the purpose of explanation and not limitation, specific details are set forth, such as particular system configurations, techniques, etc., in order to provide a thorough understanding of the embodiments of the present application. However, it will be apparent to those skilled in the art that the present application can be practiced in other embodiments that depart from these specific details. In other instances, detailed descriptions of well-known systems, devices, circuits, and methods are omitted so as not to obscure the description of the present application with unnecessary detail.

[0026] It should be understood that the term "comprising" as used in the specification and the appended claims indicates the presence of the recited features, integers, steps, operations, elements, and / or components, but does not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof.

[0027] In the present application, the reference to "one embodiment" or "some embodiments" or the like means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment of the application. Thus, the appearances of the phrases "in one embodiment," "in some embodiments," "in other embodiments," "in additional embodiments," and so on, in various places throughout this specification are not necessarily all referring to the same embodiment, unless otherwise specifically stated. The terms "comprising," "including," "having," and their variants are meant to be construed as "including but not limited to," unless otherwise specifically stated.

[0028] The technical solutions of the embodiments of the present application are introduced as follows.

[0029] As shown in Figure 1 The embodiments of the present application provide a ship waste heat multi-source coordinated recovery method, which includes the following steps S110-S160:

[0030] In step S110, multi-source temperature signals in the running of the ship are collected, and the heat exchange pipeline layout is collected. The multi-source temperature signals cover the high-temperature section of the main engine and the medium-temperature section of the auxiliary engine. The heat value rating is performed on the multi-source temperature signals to form a heat grade distribution.

[0031] Specifically, a network of temperature sensors is deployed at key positions of waste heat discharge of the ship main engine and auxiliary engine to monitor the temperature data of each waste heat source in real time. Thermocouple temperature sensors are installed at the main engine exhaust manifold outlet, the supercharger rear end, the cylinder sleeve cooling water outlet, and the oil cooler outlet. The high-temperature section of the main engine includes the main engine exhaust system and the supercharger exhaust system, and the temperature at these positions is usually in the range of 300-500°C. The temperature at the main engine exhaust manifold outlet reflects the initial temperature of the exhaust gas after combustion, and the temperature at the rear end of the supercharger reflects the exhaust gas temperature after the supercharging process. Temperature collection points are set at the exhaust pipe, cooling water circuit, and lubricating oil cooling system outlet of the auxiliary diesel generator set. The medium-temperature section of the auxiliary engine includes the cylinder sleeve cooling water system and the oil cooling system, and the temperature at these positions is usually in the range of 60-100°C. The real-time values of each temperature measurement point are recorded, and the sampling frequency is set to one per second to ensure that the dynamic change process of the temperature can be captured. In the actual operation of the ship, when the main engine is upgraded from the economic speed to the full speed, the exhaust temperature of the main engine rises from 350°C to 450°C, and the cylinder sleeve water temperature rises from 75°C to 85°C. These temperature changes directly reflect the changes in the heat source supply capacity. The heat exchange pipeline layout information is collected, including the pipeline layout, pipe diameter size, pipeline length, and pipeline material of each waste heat source to the heat exchanger. The layout path and spatial position of the main engine exhaust pipeline from the manifold outlet to the waste heat boiler are recorded. The connection mode and pipeline parameters of the cylinder sleeve water pipeline from the main engine cooling water outlet to the plate heat exchanger are recorded. The connection nodes of each pipeline are identified, including the heat source outlet node, the pipeline branch node, the pipeline convergence node, and the heat exchanger inlet node. The connection relationship between the nodes is recorded to form the pipeline topology structure data.

[0032] The heat value rating of multi-source temperature signals forms the heat grade distribution. The temperature values and fluctuation characteristics of each measuring point in the multi-source temperature signal database are extracted, combined with the pipeline parameters in the heat exchange pipeline layout database, and the available heat of each measuring point is analyzed. Through the temperature measuring point value and the corresponding pipeline flow data, the heat flow rate of each heat source is obtained. The main engine exhaust temperature is high but the pipeline heat loss is large, the cylinder jacket water temperature is medium but the flow is large and the pipeline heat loss is small. Establish heat value rating standards, consider the temperature, heat and utilization difficulty, and evaluate the main engine exhaust as a first-class heat value, the supercharger exhaust as a second-class heat value, the cylinder jacket water as a third-class heat value, and the oil cooling water as a fourth-class heat value. Analyze the spatial distribution characteristics of the heat value rating, and the first and second heat values are concentrated in the main engine exhaust system area, and the third and fourth heat values are distributed in the cooling water circulation system area. Statistics of the heat proportion of each heat value grade, the first heat value accounts for 50%-60% of the total available heat, the second accounts for 20%-25%, the third accounts for 15%-20%, and the fourth accounts for 5%-10%. Record the spatial coordinates of each measuring point, the main engine exhaust measuring point (2.5m, 0.3m, 1.8m), the supercharger measuring point (3.2m, -0.5m, 2.1m). Statistics of single-point heat proportion, main engine exhaust 54%, supercharger 22.5%, cylinder jacket water 16.5%, and oil 5.4%. Analyze the temperature fluctuation rate, main engine exhaust 26%, supercharger 22%, cylinder jacket water 9%, and oil 10%. Form the heat grade distribution data, including the heat value grade, spatial coordinates, heat proportion and temperature stability parameters of each measuring point.

[0033] Step S120, based on the heat grade distribution, locate the high-quality heat points, perform source analysis on the high-quality heat points to obtain the heat dissipation position, and establish heat exchange contact at the heat dissipation position to generate heat collection conditions. Through the heat collection conditions, cascade strengthening is implemented to form a dense heat collection area.

[0034] Specifically, high-quality hotspots are located based on the thermal grade distribution. High-temperature regions corresponding to the first and second thermal values are identified from the thermal grade distribution. The spatial coordinates and temperature values of the first thermal value measurement points, which correspond to the key positions of the main engine exhaust system, are extracted. The spatial coordinates and temperature values of the second thermal value measurement points, which correspond to the positions of the turbocharger exhaust gas output, are extracted. The heat proportion and temperature stability of each high-temperature measurement point are analyzed. Measurement points with a heat proportion greater than 10% of the total available heat are marked as high-quality hotspot candidates. Measurement points with a temperature fluctuation amplitude less than 20% of the average value have good stability and are preferentially marked as high-quality hotspots. Measurement points that meet both the heat proportion and stability criteria are determined as high-quality hotspots. In the ship main engine system, the exhaust manifold junction has the highest temperature and the largest exhaust gas flow, and this position is usually identified as the first high-quality hotspot. The turbocharger turbine outlet temperature is slightly lower but the heat is stable, and it is identified as the second high-quality hotspot. The time variation characteristics of the high-quality hotspots are analyzed, and the temperature and heat of the high-quality hotspots under different loads of the main engine show regular fluctuations. The temperature of the first high-quality hotspot can reach 480°C under full load, and it decreases to about 380°C under half load.

[0035] The source of the high-quality hotspot is analyzed to obtain the heat dissipation position. The main engine exhaust manifold corresponding to the first high-quality hotspot is analyzed, and the heat source is traced back to the combustion exhaust gas of each cylinder. The flow path and temperature variation process of the exhaust gas from the cylinder to the manifold are analyzed. The surface of the exhaust manifold is identified as the main heat dissipation position, and the outer wall of the manifold is in contact with the ambient air to produce convective and radiative heat dissipation. The turbocharger turbine corresponding to the second high-quality hotspot is analyzed, and the heat source is traced back to the high-temperature and high-pressure exhaust gas driving the turbine impeller to work. The surface of the turbine shell is identified as the main heat dissipation position, and the outer wall of the shell has a high temperature and dissipates heat to the surrounding environment. For the exhaust pipe high-quality hotspot of the auxiliary generator set, the heat source is traced back to the diesel engine combustion exhaust gas, and the outer surface of the exhaust pipe is identified as the heat dissipation position. In the ship engine room environment, the surface temperature of the main engine exhaust manifold can reach more than 400°C, and if heat recovery is not performed, these high-grade heat will be dissipated to the engine room space through natural convection and radiation, wasting energy and increasing the engine room temperature. The heat dissipation power of each heat dissipation position is measured, and the natural heat dissipation is estimated by the surface temperature, area, and heat transfer coefficient. The natural heat dissipation power of the exhaust manifold can reach 20-30kW, and if this part of the heat can be effectively recovered, the system efficiency will be significantly improved.

[0036] The heat exchange contact is established in the heat dissipation position to generate the heat collection condition. According to the geometric size and temperature characteristics of the heat dissipation position, the heat exchange contact scheme is determined. For the heat dissipation surface of the main engine exhaust manifold, the heat exchange contact relationship between the working medium and the heat dissipation surface is established, and the working medium absorbs the heat of the heat dissipation surface through flow. The heat exchange contact gap parameters are set, and the gap distance affects the contact thermal resistance and the working medium flow resistance. For the heat dissipation surface of the supercharger turbine shell, the attached heat exchange contact relationship is established to reduce the contact thermal resistance. For the heat dissipation surface of the exhaust pipe, the extended heat exchange contact relationship is established to increase the heat collection capacity by increasing the heat exchange contact area. The working medium flow path connecting each heat dissipation position establishes the working medium circulation system. The working medium circulation flow rate parameters are set to adjust the working medium flow rate to make the heat exchange contact reach a stable operating state. The temperature field distribution of the heat exchange contact position is monitored, and temperature monitoring points are arranged on the surface of the heat collection area and the surrounding space to obtain the temperature values of each monitoring point. The inlet and outlet temperatures and flow rate parameters of the working medium are monitored, and when each parameter reaches a stable state and meets the design requirements, the heat collection condition is determined to be formed. In the ship organic Rankine cycle system, when the working medium flows through the heat exchange contact position of the main engine exhaust manifold, the inlet working medium temperature is a set value, the outlet working medium temperature rises to a set value, the temperature difference remains stable, and the heat collection condition is successfully established. The running stability under different working medium flow conditions is tested, the flow rate and temperature rise characteristic curve is drawn, and the best running flow point is determined. The heat collection condition data is formed, including the temperature field distribution of each position, the working medium flow rate, the inlet and outlet temperatures, and the heat exchange power.

[0037] In some embodiments, the heat collection condition is implemented by the cascade strengthening to form a dense heat collection area, including: identifying a heat diffusion boundary based on the temperature field distribution analysis of the heat collection condition; establishing a heat blocking boundary at the heat diffusion boundary to form a heat loss control area; optimizing the heat flow path in the heat loss control area to form a high heat flux area; and determining the range of the dense heat collection area according to the power density distribution of the high heat flux area.

[0038] The heat diffusion boundary is identified based on temperature field distribution analysis in heat collection condition. Temperature field distribution information is extracted from heat collection condition data. Temperature data of the surface of the heat collection region and the surrounding space are measured. Temperature monitoring points are arranged at different distances outside the surface. Temperature values of each monitoring point are obtained, and a temperature distribution curve with respect to the spatial distance is drawn. The temperature decay law along the space is analyzed to identify the size and direction characteristics of the temperature gradient. The heat diffusion boundary is defined as the position where the temperature difference between the surface of the heat collection region and the environment decreases to a certain proportion of the initial temperature difference. Outside the exhaust heat collection region of the main engine, there is a significant temperature difference between the surface and the environment, and the temperature difference decreases significantly when a certain distance away from the surface. This position is the heat diffusion boundary. The distance of the heat diffusion boundary around each heat collection region is measured. A short boundary distance indicates a small heat diffusion range, and a long boundary distance indicates a large heat loss. The spatial shape characteristics of the heat diffusion boundary are analyzed to identify the direction and region of the main heat loss. The heat loss to the environment within the diffusion boundary is estimated by integrating the temperature field. Without control measures, the heat loss of each heat collection region to the environment can reach a certain proportion of the heat collection power.

[0039] A heat loss control region is formed by establishing a heat blocking boundary at the heat diffusion boundary. Based on the position and temperature distribution characteristics of the heat diffusion boundary, a heat resistance enhancement scheme is determined. The heat transfer mode at the heat diffusion boundary is analyzed, including convective heat transfer and radiative heat transfer. The total heat transfer coefficient at the boundary is calculated, which is composed of convective heat transfer coefficient and radiative heat transfer coefficient. The heat resistance enhancement target is set to increase the heat resistance at the boundary position to several times of the original value, and the heat resistance is inversely proportional to the heat transfer coefficient. Heat resistance enhancement is achieved by reducing the heat transfer coefficient at the boundary, which can be achieved by controlling the temperature gradient outside the boundary and the surface emission characteristics. The temperature control target value outside the boundary is set to approach the ambient temperature, and the temperature difference is controlled within the set range. The actual temperature outside the boundary is monitored, and when the actual temperature approaches the target temperature, it is determined that the heat blocking boundary is successfully established. The heat loss control region formed is the space region inside the heat blocking boundary, and the heat retention rate of this region is the ratio of the retained heat to the initial heat. The higher the ratio, the better the heat loss control effect. In the application of ship engine room, the temperature outside the boundary is reduced to near the ambient temperature by heat resistance enhancement, and the heat retention rate is significantly improved.

[0040] For example, the heat flow path optimization in the heat loss control region to form a high heat flux area includes: obtaining a heat driving force field based on the temperature gradient distribution of the heat loss control region; determining a heat transfer enhancement region according to the heat driving force field; performing heat flow directionality analysis in the heat transfer enhancement region to form a preferential heat transfer path; and forming a high heat flux area through the heat flow aggregation effect of the preferential heat transfer path.

[0041] The thermal driving force field is obtained based on the temperature gradient distribution of the heat loss control region. The temperature distribution data of the internal space of the heat loss control region is extracted. The temperature values are obtained at different spatial positions between the heat source surface and the working fluid flow channel. The variation trend of the temperature along the space is analyzed, and the speed and direction of the temperature variation are identified. The temperature gradient at each position is calculated, which is defined as the temperature variation per unit distance, and is obtained by the temperature difference and distance between adjacent positions, G = ΔT / Δx, where ΔT is the temperature difference and Δx is the spatial distance. The direction of the temperature gradient points to the direction of temperature reduction, i.e. the main direction of heat transfer. The size of the temperature gradient reflects the driving force strength of heat transfer, and the greater the gradient, the stronger the driving force. The temperature gradient values and directions of each spatial position are combined to form the thermal driving force field. The thermal driving force field describes the driving force distribution condition of heat transfer in the heat loss control region. In the ship heat collection system, the temperature of the heat source surface is high and the temperature of the working fluid flow channel is relatively low, and there is a significant temperature gradient between the two, which generates a thermal driving force to drive heat transfer. The areas with the strongest driving force in the thermal driving force field are identified, which correspond to the spatial positions with the largest temperature gradient. The spatial distribution uniformity of the thermal driving force field is analyzed, and the uneven distribution of the driving force indicates the existence of heat transfer bottleneck positions.

[0042] The heat transfer enhancement region is determined according to the thermal driving force field. The thermal driving force values of each position in the thermal driving force field are extracted, which correspond to the size of the temperature gradient at that position. The thermal driving force values are classified into high, medium and low levels. The high and low level thresholds are set, and the positions with a thermal driving force greater than the high level threshold are classified as high driving force regions, the positions between the high and low level thresholds are classified as medium driving force regions, and the positions with a thermal driving force less than the low level threshold are classified as low driving force regions. A mapping relationship between the heat transfer enhancement degree and the thermal driving force level is established, and the high driving force region is configured with a high enhancement degree coefficient, the medium driving force region is configured with a medium enhancement degree coefficient, and the low driving force region is configured with a low enhancement degree coefficient. The enhancement degree coefficient reflects the enhancement multiple of the heat transfer capacity, and the larger the coefficient, the more the heat transfer capacity is improved. The region configured with the enhancement degree coefficient is defined as the heat transfer enhancement region. The heat transfer coefficient of the heat transfer enhancement region is the baseline heat transfer coefficient multiplied by the enhancement degree coefficient. In the ship exhaust heat collection system, the region with the largest temperature gradient is classified as a high driving force region and is configured with the highest enhancement degree coefficient, and the heat transfer coefficient of this region is improved most significantly.

[0043] The heat flow directionality analysis in the heat transfer enhancement region forms the preferential heat transfer paths. A path search method is established to traverse all possible paths from each high temperature point on the heat source surface to each location in the working fluid flow channel. The heat transfer resistance of each candidate path is evaluated, including the path length resistance and the path thermal resistance. The path length resistance is proportional to the path length, and the path thermal resistance is related to the thermal resistance distribution of the path passing region. The path comprehensive resistance index is defined to consider the influence of path length and path thermal resistance, and the comprehensive resistance index is composed of length term and thermal resistance term weighted. The numerical values of the comprehensive resistance index of all candidate paths are calculated and sorted from small to large. The paths with the smallest comprehensive resistance index are selected as the preferential heat transfer paths. The spatial distribution characteristics of the preferential heat transfer paths are analyzed to identify the starting point, end point and intermediate passing region of the path. The proportion of the heat flow of the preferential heat transfer path to the total heat flow reflects the heat flow carrying capacity of the path. By adjusting the heat transfer parameters, the proportion of the heat flow of the preferential path increases from a lower value to a higher value. In the ship heat collection system, through path search and resistance evaluation, the path with the minimum heat transfer resistance is identified as the preferential heat transfer path, and the proportion of the heat flow of the path is significantly higher than that of other paths.

[0044] The heat flow aggregation effect of the preferential heat transfer path forms the high heat flux region. The heat flow convergence at the end point of the preferential heat transfer path is analyzed. Multiple preferential heat transfer paths converge heat from different spatial locations to a limited area near the working fluid flow channel. The area of the convergence region is much smaller than the total area of the heat source surface. The heat flux density of the convergence region is evaluated, which is the heat flow per unit area. Due to the decrease in the convergence area and the basic maintenance of the total heat flow, the heat flux density of the convergence region increases significantly. The region with a higher value of heat flux density is defined as the high heat flux region. The high heat flux region is located directly above or adjacent to the working fluid flow channel, and heat can be efficiently transferred to the flowing working fluid. In the ship exhaust heat collection system, through the design of preferential heat transfer paths, the heat of a larger area of the heat source surface is converged to a smaller area of the working fluid flow channel region, and the heat flux density is significantly improved. The heat flux density value of the high heat flux region is measured and compared with the surrounding region to verify the aggregation effect. The establishment of the high heat flux region enables the working fluid to absorb sufficient heat in a shorter flow channel length, and the size of the heat exchanger is correspondingly reduced. The temperature stability and heat flux density fluctuation characteristics of the high heat flux region are analyzed to ensure that the high heat flux density does not cause local temperature to be too high or the working fluid to be degraded.

[0045] The range of the dense heat collection zone is determined according to the power density distribution of the high heat flux zone. The spatial range and power density numerical distribution of the high heat flux zone are identified. The high heat flux zone is mainly concentrated in a limited space around the working fluid flow channel. The heat flux density data of each position in the high heat flux zone is extracted, and the power density distribution is obtained combined with the spatial geometric information. The power density is defined as the heat collection power in unit volume, and the power density is obtained by volume integration, wherein Q is the heat collection power, and V is the spatial volume. The spatial distribution characteristics of the power density are analyzed, and the spatial region where the power density reaches the set threshold value is identified. The region where the power density exceeds the threshold value is defined as the dense heat collection zone, and the boundary of the dense heat collection zone is determined by the power density threshold value. In the ship waste heat recovery system, through cascade enhancement and heat flow path optimization, higher heat collection power is realized in a limited space, and the power density reaches a higher level. The spatial coordinate range, geometric size, total heat collection power and average power density data of the dense heat collection zone are recorded. The compactness of the dense heat collection zone is analyzed, and the compactness is evaluated by the unit volume heat collection power. The higher the value is, the better the compactness is, which indicates that higher heat collection capacity is realized in a smaller space.

[0046] In step S130, a heat load fluctuation curve is constructed according to the fluctuation law of the auxiliary machine medium temperature section, a discontinuous heat supply source is identified from the heat load fluctuation curve, the discontinuous heat supply source is matched with the heat exchange pipeline layout to establish a heat road intersection point, and the heat road intersection point is used to deduce the flow distribution to form a flexible heating field.

[0047] Specifically, the thermal load fluctuation curve is constructed according to the fluctuation law of the auxiliary machine middle temperature section. The temperature variation characteristics of each measuring point in the middle temperature section of the auxiliary machine are analyzed. The operation of the auxiliary generator set is affected by the ship power load. The change of load leads to the start and stop of the unit and the adjustment of power, which in turn causes the temperature fluctuation of the middle temperature section heat source. Record the temperature time series data of the auxiliary machine middle temperature section under typical navigation conditions. During the port stay, only the auxiliary generator set is running, and the temperature of the middle temperature section heat source is relatively stable. During the port departure and arrival stage, the ship power load increases, and multiple auxiliary machines run simultaneously, causing the temperature of the middle temperature section heat source to rise. During the ocean voyage stage, according to the degree of automation and power demand of the ship, the auxiliary machine may be in single machine operation or multi-machine parallel state, and the temperature presents periodic fluctuation. Through the temperature data and the heat proportion information in the heat grade distribution, the thermal load value of the auxiliary machine middle temperature section at each time is obtained. Thermal load is defined as the amount of heat available for recovery per unit time, which is closely related to temperature and flow. In actual ship operation, when the auxiliary machine starts from the shutdown state, the cylinder sleeve water temperature gradually rises from the ambient temperature to the operating temperature, and the thermal load increases from zero to the rated value. This process takes 10-20 minutes. When the auxiliary machine is shut down, the cylinder sleeve water temperature gradually decreases, and the thermal load decreases accordingly until it disappears. Draw the curve of thermal load change with time, with time on the horizontal axis and thermal load value on the vertical axis. The curve clearly shows the fluctuation characteristics of the thermal load of the middle temperature section of the auxiliary machine, including fluctuation amplitude, fluctuation frequency and fluctuation trend. Identify the peak and valley values in the curve, the peak value corresponds to the full load running time of the auxiliary machine, and the valley value corresponds to the shutdown or low load running time of the auxiliary machine.

[0048] Identify the intermittent heat sources from the thermal load fluctuation curve. Continuous heat sources correspond to sections of the curve that remain stable or change slowly for a long time, while intermittent heat sources correspond to sections of the curve that frequently experience sudden changes and interruptions. Identify the time points in the curve where the thermal load suddenly drops to zero or near zero, as these points indicate the occurrence of heat supply interruptions. Calculate the duration and frequency of heat supply interruptions. Interruptions lasting less than 30 minutes are classified as short interruptions, interruptions lasting between 30 minutes and 2 hours are classified as medium-length interruptions, and interruptions lasting more than 2 hours are classified as long interruptions. Intermittent heat sources with high occurrence frequencies have a greater impact on the stability of the waste heat recovery system. Analyze the operation modes of each auxiliary unit to identify which units belong to continuous operation units and which units belong to intermittent operation units. Continuous operation of the main auxiliary machine usually serves as a continuous heat source, providing stable heat input for the waste heat recovery system. Intermittent operation of the auxiliary generator set belongs to intermittent heat sources, with frequent start-stop and uncertain running time. In ship applications, emergency generator sets are usually in standby state and only start running in special cases, so their thermal load curve presents obvious intermittent characteristics. Classify the identified intermittent heat sources, including heat source number, system affiliation, interruption frequency, and interruption duration.

[0049] In some embodiments, the matching the intermittent heat source with the heat exchange pipeline layout to establish a heat path intersection point comprises: performing heat supply timing analysis on the intermittent heat source to obtain a heat supply intermittency; constructing a pipeline connection chain based on the heat exchange pipeline layout; spatially mapping the heat supply intermittency and the pipeline connection chain to form a heat flow distribution coefficient; and establishing a heat path intersection point according to the heat flow distribution coefficient.

[0050] The heat supply timing analysis on the intermittent heat source generates a heat supply intermittency. The start-stop time records of each heat source are extracted from the identified intermittent heat source data. The running time and downtime of each intermittent heat source in a statistical period are analyzed. The running time is the time when the heat source provides heat in the working state, and the downtime is the time when the heat source does not provide heat in the stopped state. Through the proportional relationship between the running time and the downtime, the heat supply intermittency I = t stop / (t run + t stop) is defined, where t run is the running time, t stop is the downtime, and the heat supply intermittency value ranges from 0 to 1. The larger the heat supply intermittency, the higher the downtime proportion of the heat source, and the stronger the intermittency of the heat supply. The smaller the heat supply intermittency, the higher the running time proportion of the heat source, and the better the continuity of the heat supply. As a continuously running power device, the heat supply intermittency of the ship engine is usually less than 0.1, indicating that the heat supply is highly continuous. The auxiliary generator set starts and stops according to the power load, and its heat supply intermittency may be between 0.3 and 0.7, indicating that the heat supply presents obvious intermittent characteristics. The emergency generator set is in standby state usually, and its heat supply intermittency is close to 1, indicating that it almost does not provide continuous heat supply.

[0051] The pipeline connection chain is constructed based on the heat exchange pipeline layout. The pipeline topology structure information is extracted from the heat exchange pipeline layout data. The pipeline connection nodes from the heat sources to the heat exchanger are identified, the connection relationship between the nodes is extracted, and the upstream and downstream nodes of each node are determined. The pipeline path is represented as a pipeline connection chain, which is composed of nodes and connection segments. The nodes of the pipeline connection chain represent the pipeline connection points, and the connection segments represent the pipelines between the nodes. The structure type of the pipeline connection chain is analyzed. In the series type pipeline connection chain, the nodes are connected in sequence, the outlet of the previous node is directly connected to the inlet of the next node, and the heat flow is transmitted along a single path. In the parallel type pipeline connection chain, multiple pipelines branch out from the common starting node and converge at the termination node, and the heat flow is transmitted along multiple paths in parallel. The key node types in the pipeline connection chain are identified. At the branch node, one pipeline branches into multiple branches, and the flow is distributed at the branch node. At the convergence node, multiple branches merge into one main road, and the flow is collected at the convergence node. In the pipeline layout of the ship waste heat recovery system, the pipeline connection chains of multiple heat sources such as main engine exhaust, cylinder water and lubricating oil are collected at the convergence node before the evaporator inlet, which is the key convergence position of the pipeline connection chain. When the auxiliary generator set is arranged in parallel, the cooling water pipelines of each set form a parallel type pipeline connection chain, which converges at the main pipeline inlet node.

[0052] The heat supply intermittence is spatially mapped with the pipeline connection chain to form a heat flow distribution coefficient. The heat supply intermittence of each intermittent heat supply source is marked at the starting point of the corresponding pipeline connection chain. The propagation of the heat supply intermittence along the pipeline connection chain is analyzed. The intermittence of the intermittent heat supply source will propagate along the connected pipeline, affecting the flow stability of the downstream node. At the pipeline convergence point, the heat supply intermittence of multiple upstream pipelines jointly affects the flow characteristics of the convergence point. The heat flow distribution coefficient at the convergence point is established to reflect the relative size of the contribution of each upstream pipeline to the convergence point flow. The heat flow distribution coefficient K_i = Q_i / Q_total, where Q_i is the heat flow of the i-th upstream pipeline, and Q_total is the total heat flow at the convergence point. The heat flow is related to the pipeline flow and temperature, and the pipeline with large flow and high temperature has a larger heat flow distribution coefficient. The influence of heat supply intermittence on heat flow distribution coefficient is considered. The heat flow distribution coefficient of the pipeline with high heat supply intermittence has poor time stability and often changes suddenly. The heat flow distribution coefficient of the pipeline with low heat supply intermittence is relatively stable. The heat flow distribution coefficient of the main engine cylinder water pipeline is stable at a high level for a long time due to its low heat supply intermittence. The heat flow distribution coefficient of the auxiliary pipeline changes suddenly when the auxiliary machine starts and stops, rises when it runs, and drops to zero when it stops.

[0053] The heat flow distribution coefficients are used to establish the heat road junctions. The nodes with the most significant changes in heat flow distribution coefficients are identified in the pipeline connection chain. These nodes are usually located at the junctions of multiple pipelines, and at least one pipeline is connected to an intermittent heating source. The time-varying characteristics of the heat flow distribution coefficients at these nodes are analyzed. When the intermittent heating source is started, the heat flow distribution coefficient of the corresponding pipeline increases from zero to a certain value, and the total flow at the junction increases. When the intermittent heating source is stopped, the heat flow distribution coefficient of the corresponding pipeline decreases to zero, and the total flow at the junction decreases. Nodes with a fluctuation amplitude of the heat flow distribution coefficient exceeding a certain threshold are selected as heat road junctions. The fluctuation amplitude is defined as the difference between the maximum and minimum values of the heat flow distribution coefficient. Nodes with a fluctuation amplitude greater than 0.2 are marked as significant fluctuation nodes. The junction of the ship auxiliary machinery cooling water main and the main engine cooling water pipeline is determined as a key heat road junction due to the frequent start and stop of the auxiliary machinery, resulting in a large fluctuation amplitude of the heat flow distribution coefficient at this point.

[0054] In some embodiments, the use of the heat road junctions to derive flow distribution forms a flexible heating field, including: identifying flow rate deviations of the heat carrier medium at the heat road junctions; converting the flow rate deviations into a mixed flow driving force to generate adaptive flow splitting; performing heat load change analysis on the adaptive flow splitting to form dynamic matching; and constructing a flexible heating field through the dynamic matching.

[0055] Flow rate deviations of the heat carrier medium at the heat road junctions are identified. Flow rate measurement devices are installed at the heat road junctions to monitor the flow rates of each pipeline that flows into the junction. Ultrasonic flow meters or turbine flow meters are used to obtain real-time flow rate data. The numerical values and variation trends of the flow rates of each pipeline are analyzed. The flow rate of the main engine side pipeline is usually kept at a high level due to its large and stable flow. The flow rate of the auxiliary machinery side pipeline fluctuates due to the random start and stop of the group, and the flow rate presents a fluctuation characteristic. The flow rate deviation is defined as the difference between the flow rate of each pipeline and the average flow rate. When the flow rate of a pipeline is higher than the average value, the pipeline contributes more to the flow of the junction. When the flow rate of a pipeline is lower than the average value, the pipeline contributes less to the flow of the junction. During ship operation, when the auxiliary machinery is suddenly started, the flow rate of the auxiliary machinery side pipeline rapidly increases from zero, while the flow rate of the main engine side pipeline remains stable, resulting in a significant flow rate deviation between the two sides. The time-varying characteristics of the flow rate deviation are analyzed. Sudden changes in the flow rate deviation correspond to start and stop events of the intermittent heating source. Slow changes in the flow rate deviation correspond to gradual adjustment processes of the heat load.

[0056] The conversion of flow velocity deviation into mixed flow driving force generates adaptive flow distribution. At the junction of the heat exchanger, fluids with different flow velocities meet and generate mixed flow. The fluid with high flow velocity pushes the fluid with low flow velocity, promoting the mixing of the two. The greater the flow velocity deviation, the stronger the mixed flow driving force. The relationship between flow velocity deviation and mixed flow driving force is established, and the driving force is proportional to the square of the flow velocity difference. The influence of mixed flow driving force on fluid distribution is analyzed. Downstream of the junction, the fluid is distributed to each outlet pipeline according to a certain proportion. The existence of mixed flow driving force changes the distribution proportion of the fluid, so that the flow distribution automatically adjusts to adapt to the change of upstream flow. This automatic adjustment process based on fluid mechanics is called adaptive flow distribution. In the ship system, when the auxiliary machine starts and the flow velocity on the auxiliary machine side increases, the mixed flow driving force increases, and the fluid on the auxiliary machine side occupies a larger flow share downstream of the junction, automatically forming a new flow distribution balance. The response time of adaptive flow distribution is analyzed. The inertia of fluid flow makes it take a certain time to adjust the flow distribution, usually between a few seconds and tens of seconds.

[0057] The analysis of heat load change of adaptive flow distribution forms dynamic matching. After the adaptive flow distribution is formed, the flow and temperature of each branch are measured. Through the combination of flow and temperature and the specific heat capacity of the heat carrier medium, the heat load Q=m×c×ΔT of each branch is obtained, where m is the mass flow, c is the specific heat capacity, and ΔT is the temperature difference. The heat load redistribution caused by adaptive flow distribution is analyzed, and the heat load of some branches increases, while the heat load of some branches decreases. The ratio of the heat load of each branch to the total heat load is defined as the dynamic matching R_i=Q_i / Q_total, where R_i is the dynamic matching of the i-th branch, Q_i is the heat load of the i-th branch, and Q_total is the total heat load. Dynamic matching reflects the real-time distribution relationship of heat load among heat users. In the ship waste heat recovery system, the preheating section, boiling section and superheating section of the evaporator require different heat load matching, and the design matching of each section is determined according to the phase change characteristics of the working medium. In the actual operation of the ship, when the auxiliary machine suddenly stops and the total heat load decreases, the dynamic matching of each section changes, and if no adjustment is made, it may lead to insufficient heat load in the boiling section.

[0058] A flexible heating field is constructed by dynamic matching. The design matching data of each heat-using equipment is extracted as the matching benchmark. The real-time dynamic matching is compared with the design matching to calculate the matching deviation ΔR_i=R_i-R_i_design, where R_i is the real-time dynamic matching and R_i_design is the design matching. When the matching deviation exceeds the set threshold, the flow regulation mechanism is started. According to the positive and negative and size of the matching deviation, the flow adjustment direction and amplitude of each branch are determined. The negative matching deviation indicates that the heat load of the branch is insufficient and the flow needs to be increased. The positive matching deviation indicates that the heat load of the branch is excessive and the flow can be reduced. A feedback regulation loop of dynamic matching is established, and the matching deviation is input as a feedback signal to the flow regulation device. The flow regulation device adjusts the flow distribution of each branch according to the feedback signal, so that the dynamic matching gradually returns to the design matching. The heat road intersection point with dynamic matching feedback regulation capability and the downstream flow distribution area are defined as a flexible heating field. When a certain auxiliary machine is shut down, causing the total heat load to decrease, the flexible heating field detects that the boiling section matching deviation is negative, automatically increases the flow proportion of the boiling section branch, and at the same time reduces the flow proportion of the superheating section, to preferentially ensure the heating demand of the boiling section. Through continuous monitoring and feedback regulation of dynamic matching, the flexible heating field realizes self-adaptive adjustment to the fluctuation of intermittent heating sources.

[0059] In step S140, the effective temperature level is divided based on the temperature level difference of the dense heat collection area, the hierarchical heat exchange is configured in the effective temperature level to generate a step utilization chain, the heat storage and release network is formed based on the step utilization chain, and the output coordination control table is cross-arranged according to the heat storage and release network and the flexible heating field.

[0060] Specifically, the effective temperature level is divided based on the temperature level difference of the dense heat collection area. The temperature characteristics of each dense heat collection area are analyzed to identify the difference in temperature. The first dense heat collection area corresponds to the main engine exhaust system, the heat source temperature is in the range of 350-450°C, which belongs to the high temperature area. The second dense heat collection area corresponds to the supercharger exhaust gas, the heat source temperature is in the range of 280-350°C, which belongs to the medium-high temperature area. The third dense heat collection area corresponds to the cylinder sleeve cooling water, the heat source temperature is in the range of 75-90°C, which belongs to the medium temperature area. The temperature level difference is defined as the temperature difference between different heat collection areas. The temperature level difference between the high temperature area and the medium-high temperature area is about 70-100°C, and the temperature level difference between the medium-high temperature area and the medium temperature area is about 190-260°C. The effective temperature level is divided according to the temperature level difference. The effective temperature level refers to the temperature level difference suitable for gradient utilization. If the temperature level difference is too small, the utilization value is limited, and if the temperature level difference is too large, multiple heat exchanges are required. Adjacent heat collection areas with a temperature level difference greater than 50°C are defined as an effective temperature level. In the ship waste heat recovery system, the first effective temperature level is formed between the main engine exhaust and the supercharger exhaust, the temperature decreases from 450°C to 280°C, and this temperature range is suitable for driving a high-temperature evaporation process. The second effective temperature level is formed between the supercharger exhaust and the cylinder sleeve water, the temperature decreases from 350°C to 75°C, and this temperature range is suitable for multi-stage preheating.

[0061] The hierarchical heat exchange is configured in the effective temperature step to form a step utilization chain. In the first effective temperature step, a high-temperature stage heat exchange is configured as a first stage heat exchange link. The temperature range of the high-temperature stage heat exchange is determined to match the temperature span of the first effective temperature step, so that the working medium can absorb the high-grade heat of the main engine exhaust. The temperature rise target of the working medium in the high-temperature stage heat exchange is set, and the working medium rises from the inlet temperature to the intermediate temperature. In the second effective temperature step, a medium-temperature stage heat exchange is configured as a second stage heat exchange link. The temperature range of the medium-temperature stage heat exchange is determined to match the second effective temperature step, and the working medium is further heated by the heat of the supercharger exhaust and part of the cylinder jacket water. The temperature rise target of the working medium in the medium-temperature stage heat exchange is set, and the working medium continues to rise from the intermediate temperature to a higher temperature. In the third effective temperature step, a low-temperature stage heat exchange is configured as a third stage heat exchange link. The temperature range of the low-temperature stage heat exchange is determined to match the third effective temperature step, and the working medium is supplemented by the remaining cylinder jacket water waste heat. The flow connection relationship between the hierarchical heat exchanges is established. The flow sequence of the working medium is determined, and the working medium flows through the low-temperature stage heat exchange, the medium-temperature stage heat exchange and the high-temperature stage heat exchange in turn, and is gradually heated to form a step utilization path. The heat exchange matching of the step utilization chain is analyzed, and the temperature range of each stage heat exchange should be adapted to the temperature range of the corresponding effective temperature step. In the ship organic Rankine cycle system, the working medium flows along the step utilization chain and experiences a heating process with multiple temperature differences, each difference corresponding to an effective temperature step, so that the waste heat of each temperature level is fully absorbed.

[0062] Based on the step utilization chain, a heat storage and release network is formed. The temperature level and heat load data of each stage heat exchange are extracted from the step utilization chain. The heat supply and demand matching characteristics of each temperature level are analyzed, and the temperature section with time mismatch between supply and demand is identified. A heat storage node is set in the temperature section with time mismatch between supply and demand, and the role of the heat storage node is to realize the time transfer of heat. The heat storage capacity demand of the heat storage node is determined according to the fluctuation amplitude of the heat source of each temperature section, and the temperature section with larger fluctuation amplitude needs to be configured with larger heat storage capacity. The charging and discharging rate demand of the heat storage node is determined according to the duration of the heat source fluctuation, and the temperature section with longer duration needs higher charging and discharging rate. A high-temperature heat storage node is configured in the high-temperature section, and the heat storage temperature range of the node matches the heat exchange temperature of the high-temperature section. A medium-temperature heat storage node is configured in the medium-temperature section, and the heat storage temperature range of the node matches the heat exchange temperature of the medium-temperature section. A low-temperature heat storage node is configured in the low-temperature section. When the main engine load suddenly increases, causing excess heat in the high-temperature section, the high-temperature heat storage node absorbs the excess heat for storage. When the main engine load decreases, causing insufficient heat in the high-temperature section, the high-temperature heat storage node releases the stored heat for supplement. The heat flow connection relationship between each heat storage node and each stage heat exchange of the step utilization chain is established, and the charging path and the discharging path are determined. The charging path connects the heat source side and the heat storage node, realizing the transmission of excess heat to the heat storage node. The discharging path connects the heat storage node and the heat utilization side, realizing the transmission of stored heat to the heat utilization side.

[0063] In some embodiments, the outputting the coordination control table according to the cross arrangement of the heat storage and release network and the flexible heat supply field comprises: extracting a phase change heat storage temperature zone from the heat storage and release network; matching the phase change heat storage temperature zone with a low load period of the flexible heat supply field to generate a heat supplement timing; embedding a high temperature residual heat transfer instruction in the heat supplement timing to form a heat balance chain; and expanding the heat balance chain to generate the coordination control table.

[0064] The phase change heat storage temperature zone is extracted from the heat storage and release network. The characteristics of the phase change materials used in each heat storage node in the heat storage and release network are analyzed. The phase change material absorbs or releases a large amount of latent heat during the solid-liquid phase change process, while the temperature remains constant. This constant temperature is called the phase change temperature, and the corresponding temperature range is called the phase change heat storage temperature zone. The phase change heat storage temperature zone of the high-temperature section heat storage node is extracted. The high-temperature section uses molten salt material, and the phase change temperature is in the range of 220-240°C, which is suitable for storing high-grade heat. The phase change heat storage temperature zone of the medium-temperature section heat storage node is extracted. The medium-temperature section uses paraffin material, and the phase change temperature is in the range of 120-140°C, which is suitable for storing medium-grade heat. The phase change heat storage temperature zone of the low-temperature section heat storage node is extracted. The low-temperature section uses hydrated salt material, and the phase change temperature is in the range of 80-100°C, which is suitable for storing low-grade heat. The heat storage capacity is related to the mass of the phase change material and the phase change latent heat, and the larger the capacity, the stronger the energy storage capability.

[0065] For example, the matching the phase change heat storage temperature zone with a low load period of the flexible heat supply field to generate a heat supplement timing comprises: determining a heat storage working window based on the temperature range of the phase change heat storage temperature zone; identifying a low load period from the flexible heat supply field to obtain a heat supplement opportunity; time aligning the heat storage working window with the heat supplement opportunity to generate a heat release start point; and arranging a heat storage medium circulation sequence according to the heat release start point to form a heat supplement timing.

[0066] The temperature range of each phase change thermal storage temperature zone is extracted. The phase change temperature of high-temperature section phase change material is between 220℃ and 240℃, the lower limit temperature is 220℃ corresponding to the beginning of solid phase melting, and the upper limit temperature is 240℃ corresponding to the complete formation of liquid phase. The thermal storage working window is defined as the temperature range in which the phase change material can effectively store and release heat. During the heat storage process, the heat source temperature must be higher than the upper limit of the phase change temperature to transfer enough heat to the phase change material. During the heat release process, the heat side temperature must be lower than the lower limit of the phase change temperature to obtain heat from the phase change material. The matching relationship between each phase change thermal storage temperature zone and the temperature of the cascade utilization chain is analyzed. The high-temperature section thermal storage working window matches the main engine exhaust temperature, which is usually in the range of 350℃-450℃, much higher than the upper limit of the thermal storage working window, meeting the heat charging condition. The medium-temperature section thermal storage working window matches the temperature range of the supercharger exhaust gas. The low-temperature section thermal storage working window matches the cylinder jacket water temperature. By reasonably selecting the phase change temperature of the phase change material, the thermal storage working window is matched with the heat source and heat demand of each temperature level, realizing efficient heat storage and release.

[0067] The low-load period is identified in the flexible heating field to obtain the heat supplement opportunity. The load fluctuation data of the flexible heating field is analyzed to identify the time period when the heat source supply is insufficient. The characteristics of the low-load period are that the flow and temperature of the heat road intersection point are lower than the set value. Through flow monitoring, it is found that the intermittent heat source shutdown leads to a decrease in total flow, and through temperature monitoring, it is found that the main engine load reduction leads to a decrease in heat source temperature. The occurrence rules of the low-load period are counted, including the starting time, duration and load reduction amplitude. Some low-load periods have regularity, such as the main engine load reduction during night anchoring. Some low-load periods have randomness, such as the random shutdown of auxiliary machines. The heat supplement opportunity is obtained, which is the time when the heat storage device needs to be started to release heat after the low-load period starts. The heat supplement opportunity does not necessarily coincide with the starting time of the low-load period, and the thermal inertia and response time of the system need to be considered. In ship operation, when the main engine load is detected to start to decrease, it is predicted that the low-load period will be entered soon, and the preparation for heat release of the heat storage device is made in advance.

[0068] The heat storage working window is time-aligned with the heat supplement opportunity to generate a heat release starting point. The temperature information of the heat storage working window is associated with the time information of the heat supplement opportunity. When the heat supplement opportunity arrives, the temperature state of each heat storage device is checked to determine whether it is within the heat storage working window. Only the heat storage device whose temperature is within the working window and whose heat storage material is in a charging state can start heat release. The heat release starting point is generated, which contains information in two dimensions of time and temperature. The time dimension specifies when to start heat release, and the temperature dimension specifies at what temperature condition to start heat release. In the ship system, when entering the night anchoring working condition, the system determines that the temperature of the high-temperature section heat storage device is 240°C, which is the upper limit of the working window, and the heat storage material has completely melted and is in a charging state. At this time, it is the heat release starting point of the high-temperature section. The heat release starting points of the medium-temperature section and the low-temperature section heat storage devices are determined in turn. Through time alignment, the heat storage devices of each temperature level are ensured to release heat at the right time, avoiding premature or late release.

[0069] According to the heat release starting point, the heat storage medium circulation sequence is arranged to form a heat supplement timing. According to the time sequence and temperature level of each heat release starting point, the circulation sequence of the heat storage medium is arranged. The heat storage medium refers to the heat-carrying fluid circulating between the heat storage device and the heat exchanger. The heat storage medium circulation of the high-temperature section heat storage device is started first, as the high-temperature section releases the highest grade heat, and the high-grade heat demand is prioritized. After the high-temperature section heat storage medium absorbs heat from the heat storage device, it flows to the high-temperature heat exchanger to release heat, and then returns to the heat storage device to form a cycle. After the high-temperature section heat supplement reaches a certain level, the heat storage medium circulation of the medium-temperature section heat storage device is started. The medium-temperature section supplements medium-grade heat to further improve the system's heating capacity. Finally, the low-temperature section heat storage device is started to circulate to supplement low-grade heat. The formed heat supplement timing specifies the starting order, starting time, circulation flow rate, and duration of each temperature level heat storage device. Under the night anchoring working condition of the ship, the heat supplement timing first starts the high-temperature section heat storage device at 22:00, with a circulation flow rate of 80% of the rated value and a duration of 2 hours. Then the medium-temperature section heat storage device is started at 00:00, with a circulation flow rate of 60% of the rated value and a duration of 3 hours. Finally, the low-temperature section heat storage device is started at 03:00, with a circulation flow rate of 40% of the rated value and a duration of 2 hours. Through this orderly heat supplement timing, the stable operation of the waste heat recovery system is maintained during the low load period.

[0070] The high-temperature waste heat dump instruction is embedded in the heat supplement timing to form a heat balance chain. The surplus of high-temperature waste heat during the high-load period is analyzed. When the main engine is running at full load, the exhaust gas temperature may exceed the bearing capacity of the waste heat recovery system, and the surplus high-temperature waste heat needs to be dumped. The high-temperature waste heat dump instruction is embedded in the heat supplement timing, which specifies the triggering conditions and dump methods of the dump instruction. When the exhaust gas temperature exceeds the set threshold, the dump instruction is triggered. The dump methods include guiding the high-temperature waste heat into the high-temperature section of the heat storage device for storage, or discharging it to the chimney through a bypass. A heat balance chain is established, which connects the heat source side, the heat storage side and the heat utilization side. The heat source side provides heat, the surplus heat is dumped to the heat storage side, and the heat storage side releases heat to the heat utilization side when needed. The heat balance chain realizes the time transfer and grade matching of heat. The surplus high-temperature waste heat generated during the day when the main engine is running at high load is stored in the heat storage device, and these heat is released during the night when the main engine is running at low load, realizing the peak load shifting and valley filling of heat.

[0071] A coordinated control table is generated along the heat balance chain. Along the path of the heat balance chain, each control node and control object is identified. The heat balance chain consists of three links: the heat source side, the heat storage side and the heat utilization side. The control nodes of the heat source side include temperature and flow monitoring points of each heat source, the control nodes of the heat storage side include charge and discharge heat switching valves of the heat storage device, and the control nodes of the heat utilization side include flow regulating valves of each stage of heat exchanger. For different operating conditions, the control strategy of each control node is determined. Under high-load conditions, the heat supply of the heat source side is sufficient, and the control strategy is the heat storage mode, the heat storage device charge valve is opened, and the discharge valve is closed. Under low-load conditions, the heat supply of the heat source side is insufficient, and the control strategy is the heat discharge mode, the heat storage device discharge valve is opened, and the charge valve is closed. The coordinated control table is compiled, and the control parameter settings under different conditions are displayed in table form. The first column of the table is the working condition name, such as high-load condition, low-load condition, transition condition, etc. The other columns of the table are the set values of each control object, such as valve opening, flow setting, temperature setting, etc.

[0072] In step S150, the flow direction guide field is derived through the resistance distribution of the coordinated control table, the network thermal state is reshaped based on the flow direction guide field, the full-network thermal spectrum is obtained, and the convergence center is determined by identifying the convergence characteristics of the full-network thermal spectrum.

[0073] Specifically, the flow direction guide field is derived by coordinating the resistance distribution of the control table. The control parameters such as valve opening and flow setting under each working condition are extracted from the coordinated control table. The flow resistance characteristics at each control node are analyzed. The valve opening directly affects the flow resistance, the smaller the opening, the greater the resistance, and the greater the opening, the smaller the resistance. The flow setting affects the resistance along the pipeline and the local resistance, and the resistance increases in a square relationship with the increase of the flow. Extract the valve opening data of different working conditions in the coordinated control table, and convert the opening to the corresponding resistance coefficient. The full opening state resistance coefficient is the smallest, the half open state resistance coefficient increases, and the closed state resistance coefficient tends to infinity. Analyze the spatial distribution characteristics of the resistance in the entire pipeline network. The main pipeline has relatively small resistance per unit length due to large flow and large pipe diameter. The branch pipeline has relatively large resistance per unit length due to small flow and small pipe diameter. The local resistance of the valve, elbow, tee and other concentrated positions increases significantly. In the ship waste heat recovery system, the switching valve at the inlet of the heat storage device has a large difference in opening between the heat storage mode and the heat release mode, resulting in a significant change in the resistance distribution at this position with the working condition. According to the size and direction of the resistance distribution, the flow direction guide field is derived. The flow direction guide field describes the preferential flow direction of the fluid in the pipeline network. The path with small resistance corresponds to the strong guide direction of the flow direction guide field, and the fluid preferentially flows along these paths. The path with large resistance corresponds to the weak guide direction of the flow direction guide field, and the fluid flow is small or not.

[0074] In some embodiments, the full network thermodynamic spectrum is obtained by remodeling the network thermal state based on the flow direction guide field, including: identifying resistance concentration points based on the flow direction guide field to generate heat loss nodes; setting a heat recovery branch at the heat loss node to form a compensation channel; connecting the compensation channels to generate a cascade utilization network; and mapping to generate a full network thermodynamic spectrum.

[0075] Resistance concentration points are identified based on the flow direction guide field to generate heat loss nodes. The resistance values of each node are extracted from the flow direction guide field. The resistance concentration point corresponds to the position where the resistance value is significantly higher than that of the surrounding nodes. The reasons for resistance concentration are identified, including factors such as valve throttling, pipe diameter mutation, and flow direction sudden change. Resistance concentration caused by partially closed valves can be changed by adjusting the valve opening. Resistance concentration caused by pipe diameter mutation and flow direction sudden change is structural and difficult to eliminate by operation adjustment. The influence of resistance concentration points on the system is analyzed. Resistance concentration leads to an increase in local pressure drop and an increase in power consumption of fluid flow. The flow velocity changes dramatically near the resistance concentration point, generating vortex and turbulence, increasing energy dissipation. These energy dissipations are eventually converted into heat loss, forming heat loss. Resistance concentration points that produce significant heat loss are marked as heat loss nodes. In the ship waste heat recovery system, multiple control valves in the pipeline have obvious throttling effect in the half open state, and the flow direction changes at the pipeline elbow cause impact loss, which can become heat loss nodes.

[0076] A compensation channel is formed by setting a heat recovery branch at the heat loss node. A small heat exchanger is installed near the heat loss node to recover the lost heat. One side of the heat exchanger is connected to the high-temperature area near the heat loss node, and the other side is connected to the low-temperature fluid that needs to be preheated. The heat of the heat loss node is transferred to the low-temperature fluid through the heat exchanger, realizing the recovery and utilization of heat. The piping connection of the heat recovery branch is designed, and the branch is branched from the heat loss node and returns to the main pipeline or is connected to other heat-using equipment after passing through the heat exchanger. The heat recovery branch forms a compensation channel, and the heat recovered by the compensation channel compensates for the heat loss of the heat loss node. In ship applications, the elbow of the main engine exhaust pipeline has a higher temperature and heat loss. A jacketed heat exchanger is installed on the outer wall of the elbow to absorb the heat lost by the elbow with low-temperature working medium. The temperature of the working medium increases from the inlet to the outlet, realizing the recovery of part of the heat loss. The inlet and outlet temperature difference and flow of the compensation channel are measured to obtain the recovered heat value of the compensation channel.

[0077] A cascade utilization network is generated by connecting the compensation channels in series. The temperature levels of each compensation channel are analyzed, and the temperature classification of the compensation channel is determined according to the temperature of the heat loss node. High-temperature compensation channels, medium-temperature compensation channels, and low-temperature compensation channels are connected in series according to temperature from high to low. The principle of series connection is that the outlet fluid of the high-temperature compensation channel enters the inlet of the medium-temperature compensation channel, and the outlet fluid of the medium-temperature compensation channel enters the inlet of the low-temperature compensation channel. The fluid circulation path between the compensation channels is established, and the compensation channels are connected in turn through the pipeline. The heat recovered by the high-temperature compensation channel is first transferred to the fluid that needs high-temperature preheating, and the fluid with reduced temperature after heat exchange flows into the medium-temperature compensation channel to continue recovering the heat loss in the medium-temperature section. The fluid at the outlet of the medium-temperature compensation channel enters the low-temperature compensation channel to further recover the heat loss in the low-temperature section. Through this series connection method, a multi-stage recovery cascade utilization network is formed. The high-temperature heat loss at the elbow of the exhaust pipeline is first recovered to preheat the working medium, then flows through the valve at the cylinder liner water pipeline to recover the medium-temperature heat loss, and finally flows through the low-temperature pipeline section to recover the residual heat, forming a complete cascade recovery path. The topology of the cascade utilization network is recorded, including the connection order of each compensation channel, the flow direction of the fluid, and the heat exchange power.

[0078] The heat flow data of each compensation channel in the cascade utilization network is extracted, including the mass flow, inlet and outlet temperature and recovered heat of each channel. The spatial position coordinates of each compensation channel are mapped with the corresponding heat flow values. Through the mapping relationship, the heat flow contribution of the cascade utilization network is superimposed on the basis of the original heat distribution of the pipeline network. For each spatial position node, the heat flow of the main pipeline and the heat flow of the compensation channel near the position are numerically superimposed. The heat flow value after superposition updates the total heat flow of the node. All nodes in the pipeline network are traversed to complete the superposition and update of the heat flow one by one. At the position of the heat loss node, the effective heat flow of the node increases due to the recovery of part of the heat loss by the compensation channel. At the node where the compensation channel converges into the main pipeline, the heat flow of the node increases due to the heat input of the compensation channel. Through the update of the heat flow of all nodes in the network, the heat flow distribution of the whole network containing the contribution of the cascade utilization network is obtained. The updated heat flow distribution is displayed in the form of a graph to form the whole network heat spectrum.

[0079] The convergence center is determined by identifying the convergence characteristics of the whole network heat spectrum. The whole network heat spectrum contains the heat flow distribution information of each node in the pipeline network. By analyzing the heat spectrum, the key positions of heat collection can be identified to provide core control points for system supply and demand coordination. The nodes where multiple high heat flow pipelines converge are identified by analyzing the convergence characteristics of the heat flow in the whole network heat spectrum. These nodes are the key positions of heat collection. At the convergence node, heat flows from different heat sources or different paths converge, and the total heat flow reaches a peak value. The heat flow values and the number of converging pipelines of each convergence node are counted. A calculation formula for the total heat flow of the convergence node Q_node =∑Q_i is established, where Q_node is the total heat flow of the convergence node and Q_i is the heat flow of the i-th converging pipeline. The node with the largest heat flow and the most converging pipelines is defined as the convergence center. The convergence center is the core of heat collection in the whole pipeline network and has the greatest impact on system operation. In the ship waste heat recovery system, the inlet of the evaporator is usually the convergence center, where the pipelines of multiple heat sources such as main engine exhaust, supercharger exhaust and cylinder jacket water converge, and the total heat flow is the largest.

[0080] In step S160, supply and demand coordination analysis is performed according to the convergence center to identify the supply and demand difference and the reserve capacity, the fluctuation of the supply and demand difference and the reserve capacity is evaluated to generate a coordination margin, a regulation and control response strategy is configured based on the coordination margin, and the waste heat multi-source coordinated recovery is completed.

[0081] In some embodiments, the supply and demand coordination analysis according to the convergence center to identify the supply and demand difference and the reserve capacity includes: counting the heat collection flow from the convergence center to form a collected heat; analyzing the distribution heat based on the convergence center; performing difference analysis on the collected heat and the distribution heat to generate a supply and demand difference; and adding a safety margin based on the supply and demand difference to generate a reserve capacity.

[0082] The collected heat is calculated from the collected flow rate at the junction center. Real-time flow rate data and temperature data are obtained from the monitoring devices of each inlet pipe at the junction center. The type of heat source and the heat supply characteristics corresponding to each inlet pipe are identified. The main engine exhaust pipe has a small flow rate but a very high temperature, and the heat carried by unit mass flow rate is large. The cylinder jacket water pipe has a large flow rate but a moderate temperature, and the total heat flow rate is considerable. The flow rate and temperature of the heat release pipe of the thermal storage device vary according to the storage state. The heat flow rate of each inlet pipe is calculated by the mass flow rate, specific heat capacity, and temperature of each pipe. The formula for calculating the collected heat is Q_in =∑(m_i×c_i×T_i), where Q_in is the collected heat, m_i is the mass flow rate of the i-th inlet pipe, c_i is the specific heat capacity, and T_i is the temperature. The heat flow rates of all inlet pipes are summed to obtain the total collected heat at the junction center. The collected heat represents the total heat supply capacity of the system at the current time. During ship operation, the collected heat reaches a maximum value when the main engine and auxiliary machines are running simultaneously, including the heat contributions of the main engine exhaust, the supercharger exhaust, and multiple auxiliary machine cylinder jacket waters. When only the main engine is running at low load at night, the collected heat decreases, mainly from the contributions of the main engine exhaust and a single auxiliary machine.

[0083] The distribution heat is calculated based on the distribution flow rate of each outlet at the junction center. Real-time flow rate data and temperature data are obtained from the monitoring devices of each outlet pipe at the junction center. The type of heat-using equipment and the heat demand characteristics corresponding to each outlet pipe are identified. The preheating section of the evaporator requires moderate heat flow rate to heat the working medium from low temperature to saturation temperature. The boiling section of the evaporator requires large heat flow rate to provide the latent heat of vaporization required for the phase change of the working medium. The superheating section of the evaporator requires small heat flow rate to heat the saturated steam into superheated steam. The heat flow rate of each outlet pipe is calculated by the mass flow rate, specific heat capacity, and temperature of each pipe. The formula for calculating the distribution heat is Q_out =∑(m_j×c_j×T_j), where Q_out is the distribution heat, m_j is the mass flow rate of the j-th outlet pipe, c_j is the specific heat capacity, and T_j is the temperature. The heat flow rates of all outlet pipes are summed to obtain the total distribution heat at the junction center. The distribution heat represents the total heat demand of the system at the current time. During ship operation, the distribution heat reaches a maximum value when the waste heat recovery system is running at full load, and each section of the evaporator requires sufficient heat input. When the system is running at reduced load, the distribution heat decreases accordingly.

[0084] The difference between the collected heat and the distributed heat is analyzed to obtain the supply-demand difference. The supply-demand difference AQ = Q_in - Q_out is calculated, where Q_in is the collected heat and Q_out is the distributed heat. The positive and negative signs and the numerical value of the supply-demand difference are analyzed. A positive supply-demand difference indicates that the heat supply capacity is greater than the heat demand, and there is excess heat in the system. A negative supply-demand difference indicates that the heat supply capacity is less than the heat demand, and there is a heat gap in the system. The absolute value of the supply-demand difference reflects the degree of imbalance between supply and demand, and the greater the absolute value, the more serious the imbalance. In actual ship operation, during the day, the main and auxiliary engines are running at high load, while the waste heat recovery system may be running at partial load. The positive supply-demand difference can reach tens of kilowatts, indicating that a large amount of excess heat is not utilized. At night, the main and auxiliary engines are running at low load, while the waste heat recovery system needs to maintain operation. The negative supply-demand difference indicates that there is a heat gap that needs to be supplemented by the heat storage device. The numerical range of the supply-demand difference under different operating conditions is counted, and the maximum positive difference and the maximum negative difference are identified. The absolute value of the maximum negative difference determines the lower limit of the required reserve capacity.

[0085] The reserve capacity is generated by adding a safety margin to the supply-demand difference. The maximum negative difference in the supply-demand difference statistical data is extracted, which corresponds to the maximum heat gap that the system may face. The maximum negative difference is taken as the basic requirement value of the reserve capacity. Considering the uncertainty in actual operation and the safety margin requirement, a safety margin is added to the basic requirement value. The principle of setting the safety margin is to ensure that the system can still operate under the expected worst operating conditions. The safety margin is usually set as a certain percentage of the basic requirement value, and the percentage is determined according to the system reliability requirement. The reserve capacity C_reserve = |AQ_min| x (1 + a) is generated, where AQ_min is the maximum negative difference and a is the safety margin coefficient. The reserve capacity is realized through the capacity design of the heat storage device, and the total heat storage capacity of the heat storage device should not be less than the reserve capacity. According to the supply-demand difference analysis of the night anchoring condition, the maximum heat gap of the system may reach a certain value. After considering the safety margin, the heat storage device needs to have the corresponding heat storage capacity to continuously supplement the heat and maintain the system operation during the entire night anchoring period.

[0086] The fluctuation of the supply-demand difference and the reserve capacity is evaluated to generate a coordination margin. Time series data of the supply-demand difference is extracted, and the fluctuation amplitude of the supply-demand difference is calculated, which is the difference between the maximum supply-demand difference and the minimum supply-demand difference, reflecting the degree of imbalance between supply and demand. The change frequency of the supply-demand difference is counted, and the fluctuation frequency is evaluated by the number of positive and negative switches per unit time. During the high-load sailing period, the supply-demand difference fluctuates in the positive value range, and during the low-load anchoring period, the supply-demand difference fluctuates in the negative value range. The time series data of the reserve capacity is extracted, and the availability of the reserve capacity is calculated, which is the ratio of the current heat storage capacity to the total reserve capacity, reflecting the availability of the reserve capacity. In the actual operation of the ship, the heat storage capacity gradually increases during the daytime sailing, the availability rises, and the heat storage capacity gradually decreases during the nighttime anchoring, the availability falls, and the reserve capacity presents periodic fluctuation. A coordination margin calculation model is established, and the coordination margin M=U / (1+k×A) is defined, where U is the availability of the reserve capacity, A is the fluctuation amplitude of the supply-demand difference, and k is the fluctuation sensitivity coefficient. The formula shows that the higher the availability of the reserve capacity and the smaller the fluctuation amplitude of the supply-demand difference, the larger the coordination margin. When the coordination margin is greater than the set adequate threshold, the system has sufficient adjustment margin. When the coordination margin is less than the set tight threshold, the system faces the risk of imbalance.

[0087] Based on the coordination margin, a regulation and control response strategy is configured. Different regulation strategies are formulated according to the size of the coordination margin. The coordination margin is divided into three levels of adequate, moderate and tight. The adequate level corresponds to the case where the coordination margin is greater than the set threshold, and the system has enough adjustment margin to respond to fluctuations. The moderate level corresponds to the case where the coordination margin is within the normal range, and the system needs to be moderately regulated to maintain balance. The tight level corresponds to the case where the coordination margin is less than the safety threshold, and the system needs to take active measures to prevent imbalance. A conventional response strategy is configured for the adequate level. The conventional strategy includes running according to the standard process, regularly monitoring the supply and demand status, and performing preventive maintenance. An active response strategy is configured for the moderate level. The active strategy includes adjusting the heat source flow distribution in real time, optimizing the heat allocation of each heat-using equipment, and starting or stopping the heat charging and discharging of the heat storage device in a timely manner. An emergency response strategy is configured for the tight level. The emergency strategy includes limiting the heating of secondary heat-using equipment, prioritizing the heat demand of critical equipment, and starting a backup heat source or increasing the output of the main heat source. In the operation of the ship, when the coordination margin enters the tight level, the system automatically reduces the heating capacity of the superheating section, concentrates the heat to ensure the stable operation of the boiling section, and starts the backup auxiliary machine to increase the heat source supply. In the whole voyage of the ship, through multi-source coordination recovery, the waste heat recovery system can stably operate in various working conditions, the excess heat is fully recovered for backup when the main engine is under high load, and the stored heat is released to maintain system operation when the main engine is under low load, finally realizing efficient utilization of waste heat resources.

[0088] In order to perform the ship waste heat multi-source coordination recovery method corresponding to the above-mentioned method embodiment, the corresponding functions and technical effects are realized. Referring toFigure 2 , Figure 2 A structural block diagram of a ship waste heat multi-source coordinated recovery system 200 provided by an embodiment of the present application is shown. For ease of illustration, only parts related to the present embodiment are shown. The ship waste heat multi-source coordinated recovery system 200 provided by the embodiment of the present application includes:

[0089] A heat source rating module 201 is configured to collect multi-source temperature signals in ship operation and heat exchange pipeline layout, the multi-source temperature signals cover high-temperature sections of main engines and medium-temperature sections of auxiliary machines, and perform heat value rating on the multi-source temperature signals to form a heat grade distribution;

[0090] A heat flow capture module 202 is configured to locate high-quality heat points based on the heat grade distribution, perform source analysis on the high-quality heat points to obtain heat dissipation positions, establish heat exchange contact at the heat dissipation positions to generate heat collection conditions, and implement cascade strengthening through the heat collection conditions to form a dense heat collection area;

[0091] A heat supply deployment module 203 is configured to construct a heat load fluctuation curve according to fluctuation rules of the medium-temperature sections of the auxiliary machines, identify intermittent heat supply sources from the heat load fluctuation curve, match the intermittent heat supply sources with the heat exchange pipeline layout to establish heat road intersection points, and derive flow distribution using the heat road intersection points to form a flexible heat supply field;

[0092] A heat storage coordination module 204 is configured to divide effective temperature stages based on temperature differences of the dense heat collection area, configure hierarchical heat exchange in the effective temperature stages to generate a ladder utilization chain, form a heat storage and release network based on the ladder utilization chain, and cross-arrange an output coordination control table according to the heat storage and release network and the flexible heat supply field;

[0093] A heat network optimization module 205 is configured to derive a flow direction guide field through resistance distribution of the coordination control table, reshape a network heat state based on the flow direction guide field to obtain a full-network thermal spectrum, and perform convergence feature recognition on the full-network thermal spectrum to determine a convergence center;

[0094] A supply and demand balance module 206 is configured to perform supply and demand coordination analysis according to the convergence center to identify a supply-demand difference value and a reserve capacity, perform fluctuation evaluation on the supply-demand difference value and the reserve capacity to generate a coordination margin, configure a regulation and control response strategy based on the coordination margin, and complete waste heat multi-source coordinated recovery.

[0095] The ship waste heat multi-source coordinated recovery system 200 described above can implement the ship waste heat multi-source coordinated recovery method of the method embodiment described above. The optional items in the method embodiment described above are also applicable to the present embodiment, which will not be described in detail here. The remaining contents of the present embodiment can refer to the contents of the method embodiment described above, which will not be described in detail in the present embodiment.

[0096] The above examples are intended to illustrate and deduce the technical solutions of the present application, and to completely describe the technical solutions, objects and effects of the present application. The purpose is to make the public more thoroughly and comprehensively understand the disclosed content of the present application, and does not limit the protection scope of the present application.

[0097] The above examples are not based on an exhaustive enumeration of the present application, and there can be many other unlisted embodiments. Any substitution and improvement made without violating the concept of the present application shall fall within the protection scope of the present application.

Claims

1. A method for coordinated multi-source recovery of waste heat from a marine vessel, characterized in that, The method comprises the following steps: Collecting multiple-source temperature signals and heat exchange pipeline layout during ship operation, wherein the multiple-source temperature signals cover high-temperature sections of main engines and medium-temperature sections of auxiliary machines, and performing heat value rating on the multiple-source temperature signals to form a heat grade distribution; Locating high-quality heat points based on the heat grade distribution, performing source analysis on the high-quality heat points to obtain heat dissipation positions, establishing heat exchange contact at the heat dissipation positions to generate a heat collection working condition, and implementing cascade strengthening through the heat collection working condition to form a dense heat collection area; Constructing a heat load fluctuation curve according to fluctuation rules of the medium-temperature sections of the auxiliary machines, identifying intermittent heat supply sources from the heat load fluctuation curve, matching the intermittent heat supply sources with the heat exchange pipeline layout to establish heat path intersection points, and deducing flow distribution using the heat path intersection points to form a flexible heat supply field; Dividing effective temperature stages based on temperature differences of the dense heat collection area, configuring hierarchical heat exchange in the effective temperature stages to generate a step utilization chain, forming a heat storage and release network based on the step utilization chain, and cross-compiling an output coordination control table according to the heat storage and release network and the flexible heat supply field; Deriving a flow direction guide field through resistance distribution of the coordination control table, remodeling a network thermal state based on the flow direction guide field to obtain a full-network heat spectrum, and identifying a confluence center by performing convergence feature recognition on the full-network heat spectrum; Performing supply and demand coordination analysis according to the confluence center to identify a supply-demand difference and a reserve capacity, generating a coordination margin by performing fluctuation evaluation on the supply-demand difference and the reserve capacity, configuring a regulation and control response strategy based on the coordination margin, and completing waste heat multi-source coordination recovery.

2. The method of claim 1, wherein, The method of implementing cascade strengthening through the heat collection working condition to form a dense heat collection area comprises the following steps: Analyzing and identifying a heat diffusion boundary based on temperature field distribution of the heat collection working condition; Establishing a heat blocking boundary at the heat diffusion boundary to form a heat loss control area; Performing heat flow path optimization in the heat loss control area to form a high-heat-flux area; Determining a dense heat collection area range according to power density distribution of the high-heat-flux area.

3. The method of claim 1, wherein, The method of matching the intermittent heat supply sources with the heat exchange pipeline layout to establish heat path intersection points comprises the following steps: Performing heat supply timing analysis on the intermittent heat supply sources to generate a heat supply intermittence; Constructing a pipeline connection chain based on the heat exchange pipeline layout; Forming a heat flow distribution coefficient by spatially mapping the heat supply intermittence and the pipeline connection chain; Establishing heat path intersection points according to the heat flow distribution coefficient.

4. The method of claim 1, wherein, The method of deducing flow distribution using the heat path intersection points to form a flexible heat supply field comprises the following steps: Identifying flow velocity deviation of a heat-carrying medium at the heat path intersection points; Converting the flow velocity deviation into a mixed flow driving force to generate an adaptive flow splitting; Performing heat load change analysis on the adaptive flow splitting to form a dynamic matching; Constructing a flexible heat supply field through the dynamic matching.

5. The method of claim 1, wherein, The method of cross-compiling an output coordination control table according to the heat storage and release network and the flexible heat supply field comprises the following steps: Extracting a phase change heat storage temperature zone from the heat storage and release network; Matching the phase change heat storage temperature zone with a low load period of the flexible heat supply field to generate a heat supplement timing; Embedding a high-temperature waste heat transfer instruction in the heat supplement timing to form a heat balance chain; Expanding along the heat balance chain to generate a coordination control table.

6. The method of claim 1, wherein, The full-network thermodynamic spectrum is obtained based on the flow direction guide field, including: The resistance concentration point is identified based on the flow direction guide field to generate a heat loss node; The heat recovery branch is arranged at the heat loss node to form a compensation channel; The compensation channel is connected in series to generate a cascade utilization network; The full-network thermodynamic spectrum is generated through the cascade utilization network mapping.

7. The method of claim 1, wherein, The supply-demand coordination analysis is performed according to the confluence center to identify the supply-demand difference and reserve capacity, including: The heat collection flow is counted from the confluence center to form collected heat; The distribution flow of each outlet is analyzed based on the confluence center to form distributed heat; The supply-demand difference is generated by difference analysis of the collected heat and the distributed heat; The reserve capacity is generated by adding a safety margin according to the supply-demand difference.

8. The method of claim 2, wherein, The heat flow path optimization is performed in the heat loss control area to form a high heat flux area, including: The heat driving force field is obtained based on the temperature gradient distribution of the heat loss control area; The heat transfer strengthening area is determined according to the heat driving force field; The heat flow directionality analysis is performed in the heat transfer strengthening area to form a preferential heat transfer path; The high heat flux area is formed by the heat flow aggregation effect of the preferential heat transfer path.

9. The method of claim 5, wherein, The heat supplement timing is generated by matching the phase change heat storage temperature zone with the low load period of the flexible heat supply field, including: The heat storage working window is determined based on the temperature range of the phase change heat storage temperature zone; The heat supplement opportunity is obtained by identifying the low load period from the flexible heat supply field; The heat release starting point is generated by time alignment of the heat storage working window and the heat supplement opportunity; The heat supplement timing is formed by arranging the heat storage medium circulation sequence according to the heat release starting point.

10. A ship waste heat multi-source coordinated recovery system, characterized in that, It includes: A heat source rating module for collecting multi-source temperature signals and heat exchange pipeline layout during ship operation, the multi-source temperature signals covering the high temperature section of the main engine and the medium temperature section of the auxiliary machine, and performing heat value rating on the multi-source temperature signals to form a heat grade distribution; A heat flow capture module for locating high-quality heat points based on the heat grade distribution, performing source analysis on the high-quality heat points to obtain heat dissipation positions, establishing heat exchange contact at the heat dissipation positions to generate heat collection conditions, and forming a dense heat collection area through cascade strengthening of the heat collection conditions; A heat supply allocation module for constructing a heat load fluctuation curve according to the fluctuation law of the medium temperature section of the auxiliary machine, identifying intermittent heat supply sources from the heat load fluctuation curve, matching the intermittent heat supply sources with the heat exchange pipeline layout to establish heat path intersection points, and deriving flow distribution using the heat path intersection points to form a flexible heat supply field; A heat storage coordination module for dividing effective temperature stages based on the temperature difference of the dense heat collection area, configuring hierarchical heat exchange in the effective temperature stages to generate a cascade utilization chain, forming a heat storage and release network based on the cascade utilization chain, and cross-compiling an output coordination control table according to the heat storage and release network and the flexible heat supply field; A heat network optimization module for deriving a flow direction guide field through the resistance distribution of the coordination control table, obtaining a full-network thermodynamic spectrum based on the flow direction guide field, identifying a confluence center by gathering characteristics of the full-network thermodynamic spectrum, and The supply-demand balance module is used for identifying a supply-demand difference and a reserve capacity according to the supply-demand coordination analysis of the confluence center, performing fluctuation evaluation on the supply-demand difference and the reserve capacity to generate a coordination margin, configuring a regulation and control response strategy based on the coordination margin, and completing the waste heat multi-source coordination recovery.

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