Engine heat recovery method, system and equipment, storage medium and program product

Abstract

The embodiment of the invention provides an engine heat recovery method, system and equipment, a storage medium and a program product, and relates to the field of vehicle engines. At least one heat recovery system is arranged in an engine system, state parameters of the heat recovery system are determined through a control unit, and the state parameters of the heat recovery system comprise the input heat of a flow divider valve of the heat recovery system and the maximum absorbable heat of the heat recovery system; the control unit adjusts the opening degree of the flow divider valve of the heat recovery system according to the state parameters of the heat recovery system. One or more heat recovery systems are arranged, meanwhile, through state parameter monitoring and flow divider valve opening adjustment, engine waste heat resources are fully utilized, damage to the engine and the heat recovery systems is avoided, maximum energy utilization is achieved, and the energy conversion efficiency is effectively improved.

Description

Technical Field

[0001] The present application relates to the field of vehicle engines, and in particular, to an engine heat recovery method, system, device, storage medium, and program product. Background Art

[0002] When a vehicle engine burns fuel to generate power, a large amount of high-temperature exhaust gas is produced. The temperature of these exhaust gases contains a huge amount of heat. For example, in a gasoline engine, the exhaust gas generated after fuel combustion is discharged outside the vehicle through the exhaust system. The heat carried by these exhaust gases is not effectively utilized but directly dissipated into the environment. The generation of this part of heat is because the combustion process cannot completely convert the chemical energy of the fuel into mechanical energy, and a large amount of energy exists in the exhaust gas in the form of heat. Moreover, the temperature of the exhaust system itself is relatively high, and heat will be transferred to surrounding components through heat conduction during operation. At the same time, when the high-temperature exhaust gas flows in the exhaust pipe, heat will also be dissipated into the air through convection.

[0003] The existing engines have a relatively single way of utilizing waste heat. Usually, only the energy in the exhaust gas is considered for recovery, while the energy in the intercooler and coolant is not utilized, resulting in a low energy conversion efficiency. Summary of the Invention

[0004] Embodiments of the present application provide an engine heat recovery method, system, device, storage medium, and program product to achieve the effect of improving energy conversion efficiency.

[0005] In a first aspect, an embodiment of the present application provides an engine heat recovery method applied to an engine system. The engine system includes: an engine, a control unit, a turbocharger, an intercooler, a radiator, a post-treatment system, and at least one heat recovery system. The exhaust end of the engine is connected to the input end of the turbocharger. The intercooler is arranged on the intake pipe between the turbocharger and the engine. The radiator is arranged on the coolant pipe between the coolant output end and the coolant input end of the engine. The post-treatment system is arranged on the exhaust pipe after the turbocharger;

[0006] The at least one heat recovery system includes at least one of the following: a heat recovery system arranged in parallel at both ends of the intercooler through its own flow diversion valve, a heat recovery system arranged at both ends of the radiator through its own flow diversion valve, and a heat recovery system arranged after the post-treatment system through its own flow diversion valve;

[0007] The control unit is communicatively connected to the heat recovery system and the flow diversion valve;

[0008] The method includes:

[0009] The control unit determines the state parameters of the heat recovery system, and the state parameters of the heat recovery system include: the input heat of the shunt valve of the heat recovery system itself, and the maximum heat that can be absorbed by the heat recovery system;

[0010] The control unit adjusts the opening degree of the shunt valve of the heat recovery system itself according to the state parameters of the heat recovery system.

[0011] In a possible implementation manner, the adjusting the opening degree of the shunt valve of the heat recovery system itself according to the state parameters of the heat recovery system includes:

[0012] When the input heat of the shunt valve is less than or equal to the maximum heat that can be absorbed by the heat recovery system, the opening degree of the recovery side of the shunt valve is set to the maximum;

[0013] When the input heat of the shunt valve is greater than or equal to the maximum heat that can be absorbed by the heat recovery system, the opening degree of the recovery side of the shunt valve is determined according to the maximum heat that can be absorbed, and the maximum heat that can be absorbed is positively correlated with the opening degree of the recovery side of the shunt valve.

[0014] In a possible implementation manner, the determining the opening degree of the recovery side of the shunt valve according to the maximum heat that can be absorbed includes:

[0015] Converting the maximum heat that can be absorbed into the maximum receivable flow rate of the heat recovery system, and the maximum heat that can be absorbed is positively correlated with the maximum receivable flow rate;

[0016] Calculating the ratio of the maximum receivable flow rate to the maximum passing flow rate corresponding to the maximum opening degree of the recovery side of the shunt valve as the opening degree factor of the recovery side;

[0017] Calculating the product of the maximum opening degree of the recovery side of the shunt valve and the opening degree factor of the recovery side as the opening degree of the recovery side of the shunt valve.

[0018] In a possible implementation manner, the converting the maximum heat that can be absorbed into the maximum receivable flow rate of the heat recovery system includes:

[0019] Calculating the ratio of the maximum heat that can be absorbed to the target specific heat capacity and the target temperature difference corresponding to the heat recovery system as the maximum receivable flow rate of the heat recovery system;

[0020] When the heat recovery system is the heat recovery system at both ends of the intercooler, the target specific heat capacity is the specific heat capacity of the gas entering the turbocharger, and the target temperature difference is the difference between the output gas temperature of the turbocharger and the input gas temperature of the turbocharger;

[0021] When the heat recovery system is a heat recovery system arranged at both ends of the radiator, the target specific heat capacity is the specific heat capacity of the engine's coolant, and the target temperature difference is the difference between the output coolant temperature of the engine and the input coolant temperature of the engine;

[0022] When the heat recovery system is a heat recovery system arranged after the aftertreatment system, the target specific heat capacity is the specific heat capacity of the engine's exhaust gas, and the target temperature difference is the difference between the exhaust gas temperature and the ambient temperature.

[0023] In a possible implementation manner, determining the state parameters of the heat recovery system includes:

[0024] Calculating the product of the target specific heat capacity, the target temperature difference, and the input flow rate of the self-shunt valve corresponding to the heat recovery system as the input heat of the heat recovery system;

[0025] According to the resistivity, thermal conductivity, ambient temperature, conversion coefficient, temperature difference between the input temperature of the heat recovery system and the ambient temperature of the thermoelectric generator, load resistance, and internal resistance of the thermoelectric generator of the thermoelectric generator of the heat recovery system, calculating the maximum heat that the heat recovery system can receive. The maximum heat that can be received is positively correlated with the following items: the square of the temperature difference, the load resistance, the resistivity, and the thermal conductivity. The maximum heat that can be received is negatively correlated with the following items: the square of the total resistance composed of the load resistance and the internal resistance of the thermoelectric generator, the ambient temperature, and the conversion coefficient.

[0026] In a possible implementation manner, the method further includes:

[0027] Obtaining the historical electricity consumption of the vehicle;

[0028] Determining the number of closed shunt valves according to the historical electricity consumption, and the number of closed shunt valves is positively correlated with the historical electricity consumption;

[0029] According to the number of closed shunt valves, setting the recovery side opening degree of the shunt valves of multiple heat recovery systems to the minimum opening degree.

[0030] In a second aspect, an embodiment of the present application provides an engine system, which includes: an engine, a control unit, a turbocharger, an intercooler, a radiator, an aftertreatment system, and at least one heat recovery system. The exhaust end of the engine is connected to the input end of the turbocharger. The intercooler is arranged on the intake pipe between the turbocharger and the engine. The radiator is arranged on the coolant pipe between the coolant output end of the engine and the coolant input end of the engine. The aftertreatment system is arranged on the exhaust pipe after the turbocharger;

[0031] The at least one heat recovery system includes at least one of the following: a heat recovery system arranged in parallel at both ends of the intercooler through its own shunt valve, a heat recovery system arranged at both ends of the radiator through its own shunt valve, and a heat recovery system arranged after the post-treatment system through its own shunt valve;

[0032] The control unit is communicatively connected to the heat recovery system and the shunt valve;

[0033] The control unit is configured to determine state parameters of the heat recovery system, where the state parameters of the heat recovery system include: the input heat of the self-shunt valve of the heat recovery system, and the maximum heat absorbable by the heat recovery system; and adjust the opening degree of the self-shunt valve of the heat recovery system according to the state parameters of the heat recovery system.

[0034] In a possible implementation manner, the control unit is specifically configured to:

[0035] When the input heat of the shunt valve is less than or equal to the maximum heat absorbable by the heat recovery system, set the opening degree of the recovery side of the shunt valve to the maximum;

[0036] When the input heat of the shunt valve is greater than or equal to the maximum heat absorbable by the heat recovery system, determine the opening degree of the recovery side of the shunt valve according to the maximum heat absorbable, and the maximum heat absorbable is positively correlated with the opening degree of the recovery side of the shunt valve.

[0037] In a possible implementation manner, the control unit is specifically further configured to:

[0038] Convert the maximum heat absorbable into the maximum receivable flow rate of the heat recovery system, where the maximum heat absorbable is positively correlated with the maximum receivable flow rate;

[0039] Calculate the ratio of the maximum receivable flow rate to the maximum passing flow rate corresponding to the maximum opening degree of the recovery side of the shunt valve as the recovery side opening factor;

[0040] Calculate the product of the maximum opening degree of the recovery side of the shunt valve and the recovery side opening factor as the opening degree of the recovery side of the shunt valve.

[0041] In a possible implementation manner, the control unit is specifically further configured to:

[0042] Calculate the ratio of the maximum heat absorbable to the target specific heat capacity and the target temperature difference corresponding to the heat recovery system as the maximum receivable flow rate of the heat recovery system;

[0043] When the heat recovery system is the heat recovery system at both ends of the intercooler, the target specific heat capacity is the specific heat capacity of the gas entering the turbocharger, and the target temperature difference is the difference between the output gas temperature and the input gas temperature of the turbocharger;

[0044] When the heat recovery system is the heat recovery system arranged at both ends of the radiator, the target specific heat capacity is the specific heat capacity of the coolant of the engine, and the target temperature difference is the difference between the output coolant temperature and the input coolant temperature of the engine;

[0045] When the heat recovery system is the heat recovery system arranged after the aftertreatment system, the target specific heat capacity is the specific heat capacity of the exhaust gas of the engine, and the target temperature difference is the difference between the exhaust gas temperature and the ambient temperature.

[0046] In a possible implementation manner, the control unit is further specifically configured to:

[0047] Calculate the product of the target specific heat capacity, the target temperature difference corresponding to the heat recovery system, and the input flow rate of its own diverter valve as the input heat of the heat recovery system;

[0048] According to the resistivity, thermal conductivity, ambient temperature, conversion coefficient of the thermoelectric generator of the heat recovery system, the temperature difference between the input temperature of the heat recovery system and the ambient temperature of the thermoelectric generator, load resistance, and internal resistance of the thermoelectric generator, calculate the maximum heat that the heat recovery system can receive. The maximum heat that can be received is positively correlated with the following items: the square of the temperature difference, the load resistance, the resistivity, and the thermal conductivity. The maximum heat that can be received is negatively correlated with the following items: the square of the total resistance composed of the load resistance and the internal resistance of the thermoelectric generator, the ambient temperature, and the conversion coefficient.

[0049] In a possible implementation manner, the control unit is further specifically configured to:

[0050] Obtain the historical power consumption of the vehicle;

[0051] Determine the number of closed diverter valves according to the historical power consumption, and the number of closed diverter valves is positively correlated with the historical power consumption;

[0052] According to the number of closed diverter valves, set the opening degree of the recovery side of the diverter valves of multiple heat recovery systems to the minimum opening degree.

[0053] In a third aspect, an embodiment of the present application provides an electronic device, including: a memory, a processor;

[0054] The memory stores computer execution instructions;

[0055] The processor executes the computer-executable instructions stored in the memory, so that the processor executes the above first aspect and / or various possible implementation manners of the first aspect.

[0056] In a fourth aspect, an embodiment of the present application provides a computer-readable storage medium, in which computer-executable instructions are stored, and when the computer-executable instructions are executed by a processor, they are used to implement the above first aspect and / or various possible implementation manners of the first aspect.

[0057] In a fifth aspect, an embodiment of the present application provides a computer program product, including a computer program, and when the computer program is executed by a processor, it implements the above first aspect and / or various possible implementation manners of the first aspect.

[0058] The engine heat recovery method, system, device, storage medium and program product provided by the embodiments of the present application, the method includes: a control unit determines state parameters of a heat recovery system, and the state parameters of the heat recovery system include: the input heat of a shunt valve of the heat recovery system itself, the maximum heat that the heat recovery system can absorb; the control unit adjusts the opening degree of the shunt valve of the heat recovery system itself according to the state parameters of the heat recovery system. By setting one or more heat recovery systems, and at the same time through state parameter monitoring and shunt valve opening degree adjustment, not only the waste heat resources of the engine are fully utilized, but also damage to the engine and the heat recovery system itself is avoided, the maximization of energy utilization is achieved, and the energy conversion efficiency is effectively improved. Description of the Drawings

[0059] The drawings here are incorporated into the description and form a part of this description, showing embodiments consistent with the present application, and are used together with the description to explain the principles of the present application.

[0060] Figure 1 It is a schematic structural diagram of the engine system provided by the present application;

[0061] Figure 2 It is a schematic structure of the installation position of the heat recovery system provided by the present application Figure 1 ;

[0062] Figure 3 It is a schematic structure of the installation position of the heat recovery system provided by the present application Figure 2 ;

[0063] Figure 4 It is a schematic structure of the installation position of the heat recovery system provided by the present application Figure 3 ;

[0064] Figure 5 It is a schematic flow chart of the engine heat recovery method provided by the present application;

[0065] Figure 6Schematic diagram of the hardware structure of the electronic device provided by this application. Description of the drawings:

[0067] 1 - Engine; 2 - Control unit; 3 - Turbocharger; 4 - Intercooler; 5 - Radiator; 6 - Aftertreatment system; 7 - Heat recovery system;

[0068] 11 - Intake pipe; 12 - Coolant pipe; 13 - Tailpipe; 14 - Intake manifold; 15 - Exhaust manifold;

[0069] 31 - Compressor housing of the turbocharger; 32 - Turbine housing of the turbocharger;

[0070] 71 - Diverter valve.

[0071] Through the above drawings, specific embodiments of this application have been shown, and there will be more detailed descriptions hereinafter. These drawings and text descriptions are not intended to limit the scope of the concept of this application in any way, but to illustrate the concept of this application to those skilled in the art by referring to specific embodiments. Detailed description of the specific embodiments

[0072] Here, the exemplary embodiments will be described in detail, and the examples are shown in the drawings. When the following description refers to the drawings, unless otherwise indicated, the same numbers in different drawings represent the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with this application. On the contrary, they are merely examples of devices and methods consistent with some aspects of this application as detailed in the appended claims.

[0073] First, the terms involved in this application are explained:

[0074] Engine: For example, an internal combustion engine such as a gasoline engine or a diesel engine. The internal combustion engine converts chemical energy into mechanical energy through the combustion of fuel. For example, a gasoline engine ignites a mixture of gasoline and air through a spark plug to generate an explosive force to drive the piston. A diesel engine, on the other hand, burns diesel in the cylinder by compression ignition, which is characterized by a large compression ratio and relatively high thermal efficiency.

[0075] Turbocharger: Used to increase the air intake of an internal combustion engine. It uses the energy of the exhaust gas discharged from the engine to drive the turbine, and the turbine rotates to drive the compressor impeller coaxially, so that the air entering the cylinder is compressed.

[0076] Intercooler: When installed between the turbocharger and the engine intake port, it is used to cool the supercharged air. Since the temperature of the supercharged air will increase, and too high a temperature will affect the air density, which in turn affects the charging efficiency of the engine. The intercooler cools down the hot supercharged air by increasing the air heat dissipation area, increases the air density, and enables more air to enter the cylinder.

[0077] Radiator: It dissipates the heat generated by the engine through the circulation of the coolant. When the engine is working, the heat generated is transferred to the coolant through components such as the cylinder liner. After absorbing the heat, the temperature of the coolant rises. Then the coolant is pumped into the radiator, and the coolant in the radiator exchanges heat with the outside air through the heat dissipation pipes and fins.

[0078] Aftertreatment system: It converts harmful gases into harmless substances through the action of catalysts.

[0079] In the prior art, when the vehicle engine burns fuel to generate power, a large amount of high-temperature exhaust gas is produced. These exhaust gases contain a huge amount of heat. For example, in a gasoline engine, the exhaust gas generated after fuel combustion is discharged outside the vehicle through the exhaust system. The heat carried by these exhaust gases is not effectively utilized but directly dissipated into the environment. The generation of this part of the heat is because the combustion process cannot completely convert the chemical energy of the fuel into mechanical energy, and a large amount of energy exists in the exhaust gas in the form of heat. Moreover, the temperature of the exhaust system itself is relatively high, and during operation, it will transfer heat to the surrounding components through heat conduction. At the same time, when the high-temperature exhaust gas flows in the exhaust pipe, it will also dissipate heat into the air through convection.

[0080] The existing engines have a relatively single way of utilizing waste heat. Usually, only the energy in the exhaust gas is considered for recovery, while the energy in the intercooler and coolant is not utilized, resulting in a low energy conversion efficiency.

[0081] The engine heat recovery method provided by this application, through the technical means of adjusting the opening degree of the shunt valve of the heat recovery system itself based on the state parameters of the heat recovery system, effectively improves the heat recovery efficiency and solves the technical problem of energy waste caused by low energy conversion efficiency.

[0082] The following will specifically describe the technical solutions of this application and how the technical solutions of this application solve the above technical problems with specific embodiments. These specific embodiments can be combined with each other, and the same or similar concepts or processes may not be repeated in some embodiments. The embodiments of this application will be described below with reference to the accompanying drawings.

[0083] Figure 1 It is a schematic structural diagram of the engine system provided by this application; Figure 2 The structural schematic of the installation position of the heat recovery system provided by this application Figure 1 ; Figure 3 The structural schematic of the installation position of the heat recovery system provided by this application Figure 2 ; Figure 4 The structural schematic of the installation position of the heat recovery system provided by this application Figure 3 ; Figure 5Schematic flow diagram of the engine heat recovery method provided by this application. As Figures 1-5 shown, this embodiment provides an engine heat recovery method applied to an engine system.

[0084] The engine system includes: an engine 1, a control unit 2, a turbocharger 3, an intercooler 4, a radiator 5, an aftertreatment system 6, and at least one heat recovery system 7. The exhaust end of the engine 1 is connected to the input end of the turbocharger 3. The intercooler 4 is arranged on the intake pipe 11 between the turbocharger 3 and the engine 1. The radiator 5 is arranged on the coolant pipe 12 between the coolant output end of the engine 1 and the coolant input end of the engine 1. The aftertreatment system 6 is arranged on the tail pipe 13 after the turbocharger 3.

[0085] Specifically, there is a gas inlet on the compressor housing 31 of the turbocharger 3. The intake pipe 11 of the gas inlet of the compressor housing 31 of the turbocharger 3 is connected to the intake manifold 14 of the engine 1. The exhaust gas inlet of the turbine housing 32 of the turbocharger 3 is connected to the exhaust manifold 15 of the engine 1. The exhaust gas discharged from the engine 1 drives the turbine of the turbocharger 3 to rotate. The turbine is coaxially connected to the compressor impeller. The rotation of the turbine drives the impeller to compress the air from the intake pipe 11. Since the energy of the exhaust gas is utilized, the air is pressurized and then enters the cylinder, making the combustion process more complete.

[0086] The temperature of the pressurized air will increase. The intercooler 4 reduces the air temperature through heat exchange. The coolant flows in the internal pipes of the intercooler 4 and absorbs the heat of the air. After the air temperature decreases, the density increases, and the oxygen content per unit volume relatively increases; when this cold air enters the cylinder, the combustion efficiency can be further improved.

[0087] The engine 1 generates heat during operation. The coolant absorbs the heat and then the temperature rises. The coolant in the radiator 5 circulates in the pipes and exchanges heat with the outside air through the radiator fins.

[0088] The heat recovery system 7 utilizes waste heat to generate electricity, directly converting thermal energy into electrical energy and improving energy utilization efficiency.

[0089] At least one heat recovery system 7 includes at least one of the following: a heat recovery system 7 arranged in parallel at both ends of the intercooler 4 through its own shunt valve 71, a heat recovery system 7 arranged at both ends of the radiator 5 through its own shunt valve 71, and a heat recovery system 7 arranged after the aftertreatment system 6 through its own shunt valve 71.

[0090] Specifically, the waste heat recovery system 7 can supply power to the electrical equipment of the vehicle by recovering waste heat for power generation, reducing the burden on the vehicle battery, or storing the excess electrical energy, thereby reducing costs and improving energy utilization efficiency. In the actual application process, two or more of these three waste heat recovery systems 7 can be set according to actual needs, and corresponding flow control valves 71 are provided at the corresponding positions.

[0091] As Figure 2 shown, the waste heat recovery system 7 is arranged in parallel at both ends of the intercooler 4 through its own flow control valve 71: the exhaust end of the engine 1 is connected to the input end of the turbocharger 3, the output end of the turbocharger 3 is connected to the input end of the intercooler flow control valve 71, the two output ends of the intercooler flow control valve 71 are respectively connected to the input end of the intercooler 4 and the input end of the waste heat recovery system 7 of the intercooler 4, and the output end of the intercooler 4 and the output end of the waste heat recovery system 7 of the intercooler 4 are both connected to the intake end of the engine 1.

[0092] When the engine 1 is working, part of the high-temperature coolant is diverted from one end of the intercooler 4 through its own flow control valve 71 during the process of heat dissipation through the intercooler 4. The heat of this part of the high-temperature coolant can be utilized by the waste heat recovery system 7, and the thermal energy is converted into electrical energy for the vehicle to use through heat conversion, effectively improving energy utilization efficiency.

[0093] As Figure 3 shown, the waste heat recovery system 7 is arranged through its own flow control valve 71 at both ends of the radiator 5: the coolant output end of the engine 1 is connected to the input end of the radiator flow control valve 71, the two output ends of the radiator flow control valve 71 are respectively connected to the input end of the radiator 5 and the input end of the radiator recovery system, and the output end of the radiator 5 and the output end of the radiator recovery system are both connected to the coolant input end of the engine 1.

[0094] The heat generated by the engine 1 raises the temperature of the coolant, and heat dissipation takes place at the radiator 5. Part of the coolant diverted from one end of the radiator 5 through its own flow control valve 71 has the heat carried by the coolant acquired by the heat exchange component of the waste heat recovery system 7.

[0095] As Figure 4 shown, the waste heat recovery system 7 is arranged through its own flow control valve 71 after the aftertreatment system 6: the exhaust end of the engine 1 is also connected to the aftertreatment system 6, the output end of the aftertreatment system 6 is connected to the input end of the tail gas flow control valve 71, one output end of the tail gas flow control valve 71 is connected to the tail gas waste heat recovery system 7, and the other output end of the tail gas flow control valve 71 discharges the tail gas into the air.

[0096] In the post-treatment system 6, after the exhaust gas of the engine 1 passes through treatments such as a catalytic converter and a particulate trap, it still has a certain temperature. The self-shunt valve 71 is arranged after the post-treatment system 6 and diverts part of the exhaust gas to the heat recovery channel. In this channel, the heat of the exhaust gas is converted by the heat recovery system 7, further reducing the energy waste of the exhaust gas of the engine 1. In the application of waste heat power generation, the power source of the vehicle is increased and can be used for the operation of vehicle lighting, starting, and other electrical accessories.

[0097] The control unit 2 is communicatively connected to the heat recovery system 7 and the shunt valve 71.

[0098] Specifically, the control unit 2 is connected to the heat recovery system 7 and the shunt valve 71 through communication lines, and can determine the state parameters of the heat recovery system 7. The state parameters of the heat recovery system 7 include: the input heat of the self-shunt valve 71 of the heat recovery system 7, and the maximum heat that the heat recovery system 7 can absorb. According to these parameters, the control unit 2 accurately judges when to start the heat recovery system 7 and how to adjust the shunt valve 71, realizing high-precision control of the heat recovery system 7. By precisely adjusting the opening degree of the shunt valve 71, the flow rate of the working medium entering the heat recovery system 7 can be made to meet the heat recovery requirements. For example, in the heat recovery system 7 at both ends of the radiator 5, the control unit 2 can dynamically adjust the shunt valve 71 according to the change of the coolant temperature, so that the heat exchanger is always in an efficient working state, avoiding the influence of too large or too small working medium flow rate on the heat recovery efficiency.

[0099] The process of the engine heat recovery method specifically includes the following steps:

[0100] Step S101: The control unit determines the state parameters of the heat recovery system. The state parameters of the heat recovery system include: the input heat of the self-shunt valve of the heat recovery system, and the maximum heat that the heat recovery system can absorb.

[0101] Specifically, it can accurately understand the currently available heat resources of the heat recovery system, providing a basis for subsequent reasonable heat distribution. Through the precise calculation of the input heat, the control unit can understand how much heat can be obtained under different engine operating conditions. The maximum heat that can be absorbed helps to ensure the safe operation of the heat recovery system within a safe range, preventing system overheating, equipment damage, or affecting the normal operation of the engine due to excessive heat absorption.

[0102] Step S102: The control unit adjusts the opening degree of the self-shunt valve of the heat recovery system according to the state parameters of the heat recovery system.

[0103] Specifically, if the input heat is lower than the maximum absorbable heat, the control unit will increase the opening of the diverter valve to allow more working fluid to flow into the heat recovery system to achieve full energy recovery; if the input heat is close to or exceeds the maximum absorbable heat, the control unit will reduce the opening of the diverter valve to avoid overloading the heat recovery system. By reasonably adjusting the opening of the diverter valve, the heat recovery system can absorb as much available heat as possible and improve energy recovery efficiency. Under different engine operating conditions, the heat recovery system can be well matched with the engine to maximize the conversion of waste heat into useful energy.

[0104] The engine heat recovery method provided in the embodiment of the present invention, by setting up one or more heat recovery systems and simultaneously through state parameter monitoring and diverter valve opening adjustment, fully utilizes the engine waste heat resources and avoids damage to the engine and the heat recovery system itself, thereby maximizing energy utilization and effectively improving energy conversion efficiency.

[0105] This embodiment describes in detail the process of adjusting the opening of the diverter valve of the heat recovery system according to the state parameters of the heat recovery system in the above embodiment. The specific implementation of the process includes the following steps:

[0106] Step a1, when the input heat of the diverter valve is less than or equal to the maximum absorbable heat of the heat recovery system, the recovery side opening of the diverter valve is set to the maximum.

[0107] Specifically, after the control unit monitors the input heat situation, it compares it with the preset maximum absorbable heat value. When the input heat of the diverter valve is less than or equal to the maximum absorbable heat of the heat recovery system, the heat provided by the current heat source is within the processing capacity of the heat recovery system, and the recovery side opening of the diverter valve is adjusted to the maximum by issuing a command. Valve adjustment can be achieved by changing the position of the electric or pneumatic actuator of the valve, so that the channel of the diverter valve is fully opened, allowing the working fluid (such as coolant, exhaust gas, etc.) to flow smoothly into the heat recovery system, so as to make fuller use of thermal energy and improve energy efficiency.

[0108] Step a2, when the input heat of the diverter valve is greater than or equal to the maximum absorbable heat of the heat recovery system, the recovery side opening of the diverter valve is determined according to the maximum absorbable heat, and the maximum absorbable heat is positively correlated to the recovery side opening of the diverter valve. For example, in the heat recovery system after the post-processing system, if the engine exhaust temperature is too high and the heat carried by the exhaust gas exceeds the maximum processing capacity of the heat recovery device, it is necessary to calculate a suitable diverter valve opening according to the maximum absorbable heat, so that part of the exhaust gas enters the heat recovery system, while the other part bypasses to avoid overheating of the system. Effectively protect the heat recovery system from the impact of excessive heat.

[0109] Specifically, when the input heat of the flow diversion valve is greater than or equal to the maximum heat that can be absorbed by the heat recovery system, it is necessary to determine the opening of the recovery side of the flow diversion valve according to the maximum heat that can be absorbed.

[0110] In the embodiment of the present invention, by adjusting the opening of the flow diversion valve according to the input heat and the maximum heat that can be absorbed, the heat recovery system can adapt to different engine operating conditions. Under different low heat input conditions, efficient heat recovery and reasonable system operation can be achieved, maximizing the energy utilization efficiency. At the same time, through reasonable opening control, damage to the heat recovery system caused by excessive heat is effectively avoided, and the service life is extended.

[0111] In some optional embodiments, the specific implementation method of determining the opening of the recovery side of the flow diversion valve in step a2 above includes the following steps:

[0112] Step b1, convert the maximum heat that can be absorbed into the maximum flow rate that can be received by the heat recovery system. The maximum heat that can be absorbed is positively correlated with the maximum flow rate that can be received.

[0113] Specifically, converting the maximum heat that can be absorbed into the maximum flow rate that can be received provides a reference value for subsequent calculation of the opening of the recovery side of the flow diversion valve. The maximum flow rate that can be received is the processing limit of the heat recovery system under the current operating conditions. For example, when the engine load changes, the coolant flow rate entering the heat recovery system can be adjusted according to the real-time maximum flow rate that can be received to ensure that the system will not be affected by too large or too small a flow rate. The mapping table between the preset absorbable heat and the receivable flow rate can be used to obtain the maximum flow rate that can be received corresponding to the maximum absorbable heat by querying the mapping table.

[0114] Step b2, calculate the ratio of the maximum flow rate that can be received to the maximum flow rate passing through the maximum opening of the recovery side of the flow diversion valve as the opening factor of the recovery side.

[0115] Specifically, the ratio reflects the relationship between the current processing capacity of the heat recovery system and the maximum allowable flow rate of the flow diversion valve. Considering the heat load demand of the heat recovery system and the physical limitations of the flow diversion valve, the opening factor of the recovery side can accurately adjust the opening of the flow diversion valve according to the actual system state. Through the opening factor of the recovery side, the opening of the flow diversion valve can be associated with the actual demand of the heat recovery system to achieve more accurate flow control. The opening factor of the recovery side can dynamically adjust the opening according to the actual situation, avoiding problems such as system overheating or insufficient flow caused by setting a fixed opening, effectively enhancing the stability of the entire system, and ensuring the efficient operation of the heat recovery system.

[0116] Step b3, calculate the product of the maximum opening of the recovery side of the flow diversion valve and the opening factor of the recovery side as the opening of the recovery side of the flow diversion valve.

[0117] Specifically, by comprehensively calculating the maximum opening degree of the recovery side of the flow dividing valve and the opening degree factor of the recovery side, the performance of the flow dividing valve under different working conditions is ensured, so that the opening degree can meet the energy requirements of the heat recovery system without exceeding the bearing capacity of the valve and the system, and the waste heat can be recovered and utilized with the highest efficiency.

[0118] In the embodiment of the present invention, the opening degree of the recovery side of the flow dividing valve is accurately determined through calculation and analysis, so that the heat recovery system can be automatically adjusted to the operating state with the highest efficiency according to different working conditions. This accurate adaptation improves the efficiency of energy recovery and reduces energy waste.

[0119] In some optional implementation manners, the specific implementation manner of converting the maximum absorbable heat into the maximum receivable flow rate of the heat recovery system in step b1 includes the following steps:

[0120] Step c1, calculate the ratio of the maximum absorbable heat to the target specific heat capacity and the target temperature difference corresponding to the heat recovery system, and use it as the maximum receivable flow rate of the heat recovery system.

[0121] Specifically, due to the different states and heat transfer characteristics of the working medium in the heat recovery system under different application scenarios. By determining the target specific heat capacity and the target temperature difference to adapt to the characteristics of different heat recovery systems. For example, whether it is the heat recovery system at both ends of the intercooler, the heat recovery system at both ends of the radiator, or the heat recovery system after the post-treatment system, the heat can be converted into the corresponding flow rate for subsequent calculation and control of the opening degree of the flow dividing valve.

[0122] For example: The heat calculation methods under different application scenarios are as follows, where Q is the maximum absorbable heat and G is the maximum receivable flow rate.

[0123] When the heat recovery system is the heat recovery system at both ends of the intercooler, after the engine intake system is pressurized by the supercharger, the heat carried by the intake air is:

[0124] Q ap =G ap c ap (t1 - t2)

[0125] In the formula, Q ap is the heat carried by the intake air, G ap is the intake air flow rate, c ap is the specific heat capacity of the intake air, t1 is the output gas temperature, and t2 is the input gas temperature.

[0126] When the heat recovery system is the heat recovery system arranged at both ends of the radiator, after the engine coolant flows out of the engine water outlet, the heat carried by the cooling heat is:

[0127] Q lp =G lp clp (t3 - t4)

[0128] Wherein, Q lp is the heat carried by the coolant, G lp is the coolant flow rate, c lp is the specific heat capacity of the coolant, t3 is the output coolant temperature, and t4 is the input coolant temperature;

[0129] When the heat recovery system is a heat recovery system set after the aftertreatment system, the heat carried by the engine exhaust gas is:

[0130] Q tp = G tp c tp (t5 - t6)

[0131] Wherein, Q tp is the heat carried by the exhaust gas, G tp is the exhaust gas flow rate, c tp is the specific heat capacity of the exhaust gas, t5 is the exhaust gas temperature, and t6 is the ambient temperature.

[0132] Step c2, when the heat recovery system is a heat recovery system at both ends of the intercooler, the target specific heat capacity is the specific heat capacity of the gas entering the turbocharger, and the target temperature difference is the difference between the output gas temperature and the input gas temperature of the turbocharger.

[0133] Specifically, by calculating the maximum receivable flow rate based on the specific heat capacity and temperature difference of the gas entering the turbocharger, it can accurately adapt to the working characteristics of the turbocharger and the heat generation situation. This helps to ensure that the heat recovery system does not affect the normal operation of the turbocharger due to excessive or insufficient received flow rate, and at the same time can maximize the recovery of the waste heat generated by the turbocharger, improving the energy utilization efficiency of the entire power system.

[0134] Step c3, when the heat recovery system is a heat recovery system at both ends of the radiator, the target specific heat capacity is the specific heat capacity of the engine coolant, and the target temperature difference is the difference between the output coolant temperature and the input coolant temperature of the engine.

[0135] Specifically, by calculating based on the specific heat capacity and temperature difference of the engine coolant, it can accurately determine the maximum receivable flow rate of the heat recovery system at both ends of the radiator, thereby realizing the effective recovery of the engine cooling waste heat.

[0136] Step c4, when the heat recovery system is a heat recovery system set after the aftertreatment system, the target specific heat capacity is the specific heat capacity of the engine exhaust gas, and the target temperature difference is the difference between the exhaust gas temperature and the ambient temperature.

[0137] Specifically, by calculating the maximum receivable flow rate based on the specific heat capacity and temperature difference of the engine exhaust gas, the waste heat in the exhaust gas can be efficiently recovered, improving the energy utilization rate of the entire power system.

[0138] By analyzing the situations of different installation positions of the heat recovery system in the embodiments of the present invention, the heat can be accurately converted into the corresponding flow rate, providing precise data support for the operation of the heat recovery system, determining the appropriate maximum receivable flow rate, and avoiding the problems of insufficient or excessive heat recovery caused by flow rate mismatch. At the same time, the characteristics of different working fluids and the energy change situations at different positions are comprehensively considered, having strong adaptability.

[0139] In some optional implementation manners, the specific implementation manner of determining the state parameters of the heat recovery system in the above step S101 includes the following steps:

[0140] Step d1: Calculate the product of the target specific heat capacity, target temperature difference, and the input flow rate of the self-shunt valve of the heat recovery system as the input heat of the heat recovery system.

[0141] Specifically, by calculating the input heat, the heat obtained by the heat recovery system from the outside can be accurately determined, providing an accurate data basis for subsequent analysis of the system performance, determination of the maximum receivable heat, and optimization of the system operation. Among them, the specific heat capacity, temperature difference, and flow rate are comprehensively considered, enabling accurate analysis of the input heat under different working conditions, and helping to improve the versatility and adaptability of the heat recovery system.

[0142] Step d2: Calculate the maximum receivable heat of the heat recovery system according to the resistivity, thermal conductivity, ambient temperature, conversion coefficient, temperature difference between the input temperature of the heat recovery system and the ambient temperature of the thermoelectric generator, load resistance, and internal resistance of the thermoelectric generator. The maximum receivable heat is positively correlated with the following items: the square of the temperature difference, load resistance, resistivity, and thermal conductivity. The maximum receivable heat is negatively correlated with the following items: the square of the total resistance composed of the load resistance and the internal resistance of the thermoelectric generator, ambient temperature, and conversion coefficient.

[0143] Specifically, the input temperature is the temperature of the gas, or coolant, or exhaust gas input into the heat recovery system. By considering multiple relevant factors to analyze the maximum receivable heat, the highest energy conversion ability of the thermoelectric generator under the current working conditions can be accurately determined. Considering the influence of factors such as ambient temperature and load resistance on the maximum receivable heat can predict the performance changes of the system under different working conditions in advance. When the ambient temperature rises or the load resistance changes, by adjusting the operation parameters of the heat recovery system (such as flow rate, temperature control, etc.), it can be ensured that the thermoelectric generator always operates within the safe maximum power reception range, avoiding system damage caused by overload or unstable working conditions, thus ensuring the stable operation of the system.

[0144] Specifically, according to the resistivity, thermal conductivity, ambient temperature, conversion coefficient, and Seebeck coefficient of the thermoelectric generator in the heat recovery system, calculate the energy conversion efficiency of the heat recovery system;

[0145] Since the Seebeck coefficient α is determined by the inherent properties of the material itself, the energy conversion efficiency of semiconductor materials can be approximately calculated as:

[0146]

[0147] In the formula, ρ is the resistivity of the material, λ is the thermal conductivity, T is the ambient temperature, and μ is the conversion coefficient.

[0148] And according to the temperature difference between the input temperature of the heat recovery system and the ambient temperature of the thermoelectric generator, the load resistance, the internal resistance of the thermoelectric generator, and the Seebeck coefficient, calculate the output electric power of the heat recovery system;

[0149] The potential difference generated by semiconductor thermoelectric power generation is jointly determined by the Seebeck coefficient of the semiconductor material and the temperature difference between the cold end and the hot end. The output voltage of the thermoelectric generator is:

[0150]

[0151] In the formula, U is the voltage, α is the Seebeck coefficient, T h is the input temperature, T l is the ambient temperature, the internal resistance of the generator is r, and the load resistance is R;

[0152] The output power is:

[0153]

[0154] Take the ratio of the output electric power to the energy conversion efficiency as the maximum heat that can be received by the heat recovery system;

[0155] The maximum absorption power of the heat sink in the cooler heat recovery system is:

[0156]

[0157] The absorption power of the heat sink in the radiator heat recovery system is:

[0158]

[0159] The absorption power of the heat sink in the exhaust gas heat recovery system is:

[0160]

[0161] When the internal resistance of the generator and the load resistance are the same or close, and the internal resistance is equal to the load resistance, the maximum output power can be obtained:

[0162]

[0163] In the formula, P omax is the maximum output power of the heat sink, α is the Seebeck coefficient, T h is the input temperature, T l is the ambient temperature, and r is the internal resistance of the power generation chip.

[0164] In the embodiments of the present invention, by comprehensively considering various influencing factors, the performance of the heat recovery system under different installation position conditions is analyzed, making the analysis and calculation results closer to the actual situation.

[0165] In some optional embodiments, it further includes:

[0166] Step e1, obtaining the historical power consumption of the vehicle.

[0167] Specifically, by analyzing the level and change trend of the historical power consumption, the power consumption requirements of the vehicle under different working conditions can be understood, so as to more reasonably allocate the heat of the heat recovery system for power generation.

[0168] Step e2, determining the number of closed flow control valves according to the historical power consumption, and the number of closed flow control valves is positively correlated with the historical power consumption.

[0169] Specifically, by reasonably setting the number of closed flow control valves, the distribution of heat in the heat recovery system can be effectively adjusted. When more heat is needed for power generation, increasing the number of closed flow control valves can reduce the heat loss in other parts, making more heat concentrate on the power generation link of the heat recovery system, thereby improving the power generation efficiency.

[0170] Step e3, setting the opening degree of the recovery side of the flow control valves of multiple heat recovery systems to the minimum opening degree according to the number of closed flow control valves.

[0171] Specifically, based on the working principle and actual requirements of the heat recovery system, the opening degree of the recovery side of the flow control valves of multiple heat recovery systems is set to the minimum opening degree. Setting the opening degree to the minimum opening degree can limit the heat flow entering the heat recovery system and keep it at a relatively stable and low level. For example, when the historical power consumption is very low and the power is sufficient, all the flow control valves can be closed without heat recovery to reduce the loss of the heat recovery system.

[0172] In this embodiment, by comprehensively considering various factors such as the historical power consumption information of the vehicle, the current power consumption requirements and the stability of the system, the heat recovery system is optimized to maximize the recovery and utilization of the waste heat emitted by the vehicle and convert it into electric energy, thereby reducing the vehicle's dependence on external power sources, reducing energy consumption, saving energy and increasing efficiency at the same time.

[0173] Figure 1The structural schematic diagram of the engine system provided for this application. As Figure 1 shown, the engine system includes: an engine 1, a control unit 2, a turbocharger 3, an intercooler 4, a radiator 5, a post-treatment system 6, and at least one heat recovery system 7. The exhaust end of the engine 1 is connected to the input end of the turbocharger 3. The intercooler 4 is arranged on the intake pipe 11 between the turbocharger 3 and the engine 1. The radiator 5 is arranged on the coolant pipe 12 between the coolant output end of the engine 1 and the coolant input end of the engine 1. The post-treatment system 6 is arranged on the tail pipe 13 after the turbocharger 3;

[0174] At least one heat recovery system 7 includes at least one of the following: a heat recovery system 7 arranged in parallel at both ends of the intercooler 4 through its own diverter valve 71, a heat recovery system 7 arranged at both ends of the radiator 5 through its own diverter valve 71, and a heat recovery system 7 arranged after the post-treatment system 6 through its own diverter valve 71;

[0175] The control unit 2 is communicatively connected to the heat recovery system 7 and the diverter valve 71;

[0176] The control unit 2 is used to determine the state parameters of the heat recovery system 7. The state parameters of the heat recovery system 7 include: the input heat of the diverter valve 71 of the heat recovery system 7 itself, and the maximum absorbable heat of the heat recovery system 7. According to the state parameters of the heat recovery system 7, the opening degree of the diverter valve 71 of the heat recovery system 7 itself is adjusted.

[0177] In a possible implementation manner, the control unit is specifically used for:

[0178] When the input heat of the diverter valve is less than or equal to the maximum absorbable heat of the heat recovery system, set the opening degree of the recovery side of the diverter valve to the maximum;

[0179] When the input heat of the diverter valve is greater than or equal to the maximum absorbable heat of the heat recovery system, determine the opening degree of the recovery side of the diverter valve according to the maximum absorbable heat. The maximum absorbable heat is positively correlated with the opening degree of the recovery side of the diverter valve.

[0180] In a possible implementation manner, the control unit is specifically further used for:

[0181] Convert the maximum absorbable heat into the maximum receivable flow rate of the heat recovery system. The maximum absorbable heat is positively correlated with the maximum receivable flow rate;

[0182] Calculate the ratio of the maximum receivable flow rate to the maximum passing flow rate corresponding to the maximum opening degree of the recovery side of the diverter valve as the recovery side opening factor;

[0183] Calculate the product of the maximum opening degree of the recovery side of the diverter valve and the recovery side opening factor as the opening degree of the recovery side of the diverter valve.

[0184] In a possible implementation, the control unit is specifically further configured to:

[0185] Calculate the ratio of the maximum absorbable heat to the target specific heat capacity and the target temperature difference corresponding to the heat recovery system as the maximum receivable flow rate of the heat recovery system;

[0186] When the heat recovery system is the heat recovery system at both ends of the intercooler, the target specific heat capacity is the specific heat capacity of the gas entering the turbocharger, and the target temperature difference is the difference between the output gas temperature and the input gas temperature of the turbocharger;

[0187] When the heat recovery system is the heat recovery system arranged at both ends of the radiator, the target specific heat capacity is the specific heat capacity of the engine coolant, and the target temperature difference is the difference between the output coolant temperature and the input coolant temperature of the engine;

[0188] When the heat recovery system is the heat recovery system arranged after the aftertreatment system, the target specific heat capacity is the specific heat capacity of the engine exhaust gas, and the target temperature difference is the difference between the exhaust gas temperature and the ambient temperature.

[0189] In a possible implementation, the control unit is specifically further configured to:

[0190] Calculate the product of the target specific heat capacity, the target temperature difference corresponding to the heat recovery system, and the input flow rate of its own flow control valve as the input heat of the heat recovery system;

[0191] According to the resistivity, thermal conductivity, ambient temperature, conversion coefficient, temperature difference between the input temperature of the heat recovery system and the ambient temperature of the thermoelectric generator of the heat recovery system, load resistance, and internal resistance of the thermoelectric generator, calculate the maximum receivable heat of the heat recovery system. The maximum receivable heat is positively correlated with the following items: the square of the temperature difference, load resistance, resistivity, and thermal conductivity. The maximum receivable heat is negatively correlated with the following items: the square of the total resistance composed of the load resistance and the internal resistance of the thermoelectric generator, ambient temperature, and conversion coefficient.

[0192] In a possible implementation, the control unit is specifically further configured to:

[0193] Obtain the historical electricity consumption of the vehicle;

[0194] Determine the number of closed flow control valves according to the historical electricity consumption. The number of closed flow control valves is positively correlated with the historical electricity consumption;

[0195] Set the recovery side opening degree of the flow control valves of multiple heat recovery systems to the minimum opening degree according to the number of closed flow control valves.

[0196] The control unit in the engine system provided in this embodiment can be used to execute the above-mentioned engine heat recovery method, and its implementation principle and technical effects are similar, which will not be elaborated here in this embodiment.

[0197] Figure 6 The following is a schematic diagram of the hardware structure of the electronic device provided in this application. As Figure 6 shown, the electronic device 60 includes: at least one processor 601 and a memory 602. Optionally, the electronic device 60 further includes a communication component 603. Among them, the processor 601, the memory 602, and the communication component 603 are connected through a bus 604.

[0198] In the specific implementation process, at least one processor 601 executes the computer-executable instructions stored in the memory 602, so that at least one processor 601 executes the above method.

[0199] For the specific implementation process of the processor 601, reference can be made to the above method embodiment, and its implementation principle and technical effects are similar, which will not be elaborated here in this embodiment.

[0200] In the above embodiment, it should be understood that the processor may be a central processing unit (English: Central Processing Unit, abbreviated: CPU), or other general-purpose processors, digital signal processors (English: Digital Signal Processor, abbreviated: DSP), application-specific integrated circuits (English: Application Specific Integrated Circuit, abbreviated: ASIC), etc. The general-purpose processor may be a microprocessor or the processor may also be any conventional processor, etc. The steps of the method disclosed in combination with the invention can be directly embodied as being executed by a hardware processor, or executed by a combination of hardware and software modules in the processor.

[0201] The memory may include a high-speed memory (Random Access Memory, RAM), and may also include a non-volatile memory (Non-volatile Memory, NVM), such as at least one disk memory.

[0202] The bus can be an Industry Standard Architecture (ISA) bus, a Peripheral Component Interconnect (PCI) bus, an Extended Industry Standard Architecture (EISA) bus, or the like. The bus can be divided into an address bus, a data bus, a control bus, etc. For the sake of convenience in representation, the buses in the drawings of this application are not limited to only one bus or one type of bus.

[0203] This application also provides a computer program product, including a computer program which, when executed by a processor, implements the above method.

[0204] This application also provides a computer-readable storage medium storing computer-executable instructions, which, when executed by a processor, implement the above method.

[0205] The above-mentioned readable storage medium can be implemented by any type of volatile or non-volatile storage device or a combination thereof, such as a static random access memory (SRAM), an electrically erasable programmable read-only memory (EEPROM), an erasable programmable read-only memory (EPROM), a programmable read-only memory (PROM), a read-only memory (ROM), a magnetic memory, a flash memory, a magnetic disk or an optical disk. The readable storage medium can be any available medium accessible by a general-purpose or special-purpose computer.

[0206] An exemplary readable storage medium is coupled to the processor, enabling the processor to read information from and write information to the readable storage medium. Of course, the readable storage medium can also be a component of the processor. The processor and the readable storage medium can be located in an Application Specific Integrated Circuit (ASIC). Of course, the processor and the readable storage medium can also exist as discrete components in a device.

[0207] The division of units is only a logical function division. In actual implementation, there can be other division methods. For example, multiple units or components can be combined or integrated into another system, or some features can be ignored or not executed. Another point is that the displayed or discussed coupling or direct coupling or communication connection between each other can be through some interfaces, and the indirect coupling or communication connection of devices or units can be in an electrical, mechanical or other form.

[0208] The units described as separate components may or may not be physically separated. The components shown as units may or may not be physical units, that is, they may be located in one place or distributed across multiple network units. Some or all of these units can be selected according to actual needs to achieve the purpose of the solution of this embodiment.

[0209] In addition, in each embodiment of the present invention, the various functional units may be integrated in a processing unit, may exist separately as individual physical units, or two or more units may be integrated in one unit.

[0210] If the functions are implemented in the form of software functional units and sold or used as independent products, they can be stored in a computer-readable storage medium. Based on this understanding, the technical solution of the present invention, in essence, or the part that contributes to the prior art, or part of this technical solution, can be embodied in the form of a software product. This computer software product is stored in a storage medium and includes several instructions for causing a computer device (which may be a personal computer, a server, or a network device, etc.) to execute all or part of the steps of the methods of the various embodiments of the present invention. The aforementioned storage medium includes: USB flash drives, mobile hard disks, read-only memories (ROM, Read-Only Memory), random access memories (RAM, Random Access Memory), magnetic disks, or optical discs, etc., which can store program codes.

[0211] Those of ordinary skill in the art can understand that all or part of the steps of implementing the above method embodiments can be completed by hardware related to program instructions. The aforementioned program can be stored in a computer-readable storage medium. When this program is executed, it performs the steps including the above method embodiments; and the aforementioned storage medium includes: ROM, RAM, magnetic disks, or optical discs, etc., which can store program codes.

[0212] Finally, it should be noted that: After considering the specification and practicing the invention disclosed herein, those skilled in the art will easily think of other implementation schemes of the present invention. The present invention aims to cover any variations, uses, or adaptive changes of the present invention, which follow the general principles of the present invention and include common general knowledge or conventional technical means in the technical field not disclosed in the present invention. It is not limited to the exact structures described above and shown in the drawings, and various modifications and changes can be made without departing from its scope. The scope of the present invention is only limited by the appended claims.

Claims

1. An engine heat recovery method, characterized in that, Applied to an engine system, the engine system includes: an engine, a control unit, a turbocharger, an intercooler, a radiator, a post-treatment system, and at least one heat recovery system. The exhaust end of the engine is connected to the input end of the turbocharger. The intercooler is arranged on the intake pipe between the turbocharger and the engine. The radiator is arranged on the coolant pipe between the coolant output end of the engine and the coolant input end of the engine. The post-treatment system is arranged on the tail pipe after the turbocharger; The at least one heat recovery system includes at least one of the following: a heat recovery system arranged in parallel at both ends of the intercooler through its own diverter valve, a heat recovery system arranged at both ends of the radiator through its own diverter valve, and a heat recovery system arranged after the post-treatment system through its own diverter valve; The control unit is communicatively connected to the heat recovery system and the diverter valve; The method includes: The control unit determines the state parameters of the heat recovery system. The state parameters of the heat recovery system include: the input heat of the diverter valve of the heat recovery system itself, and the maximum heat that the heat recovery system can absorb; The control unit adjusts the opening degree of the diverter valve of the heat recovery system itself according to the state parameters of the heat recovery system.

2. The method according to claim 1, wherein The adjusting the opening degree of the diverter valve of the heat recovery system itself according to the state parameters of the heat recovery system includes: When the input heat of the diverter valve is less than or equal to the maximum heat that the heat recovery system can absorb, set the opening degree of the recovery side of the diverter valve to the maximum; When the input heat of the diverter valve is greater than or equal to the maximum heat that the heat recovery system can absorb, determine the opening degree of the recovery side of the diverter valve according to the maximum heat that can be absorbed. The maximum heat that can be absorbed is positively correlated with the opening degree of the recovery side of the diverter valve.

3. The method according to claim 2, wherein The determining the opening degree of the recovery side of the diverter valve according to the maximum heat that can be absorbed includes: Convert the maximum heat that can be absorbed into the maximum receivable flow rate of the heat recovery system. The maximum heat that can be absorbed is positively correlated with the maximum receivable flow rate; Calculate the ratio of the maximum receivable flow rate to the maximum passing flow rate corresponding to the maximum opening degree of the recovery side of the diverter valve as the recovery side opening factor; Calculate the product of the maximum opening degree of the recovery side of the diverter valve and the recovery side opening factor as the opening degree of the recovery side of the diverter valve.

4. The method according to claim 3, wherein The converting the maximum heat that can be absorbed into the maximum receivable flow rate of the heat recovery system includes: Calculate the ratio of the maximum heat that can be absorbed to the target specific heat capacity and the target temperature difference corresponding to the heat recovery system as the maximum receivable flow rate of the heat recovery system; When the heat recovery system is the heat recovery system at both ends of the intercooler, the target specific heat capacity is the specific heat capacity of the gas entering the turbocharger, and the target temperature difference is the difference between the output gas temperature of the turbocharger and the input gas temperature of the turbocharger; When the heat recovery system is a heat recovery system arranged at both ends of the radiator, the target specific heat capacity is the specific heat capacity of the engine's coolant, and the target temperature difference is the difference between the output coolant temperature of the engine and the input coolant temperature of the engine; When the heat recovery system is a heat recovery system arranged after the aftertreatment system, the target specific heat capacity is the specific heat capacity of the engine's exhaust gas, and the target temperature difference is the difference between the exhaust gas temperature and the ambient temperature.

5. The method according to claim 4, wherein Determining the state parameters of the heat recovery system includes: Calculating the product of the target specific heat capacity, the target temperature difference, and the input flow rate of the self-shunt valve corresponding to the heat recovery system as the input heat of the heat recovery system; Calculating the maximum heat that can be received by the heat recovery system based on the resistivity, thermal conductivity, ambient temperature, conversion coefficient, temperature difference between the input temperature of the heat recovery system and the ambient temperature of the thermoelectric generator, load resistance, and internal resistance of the thermoelectric generator of the thermoelectric generator of the heat recovery system. The maximum heat that can be received is positively correlated with the following items: the square of the temperature difference, the load resistance, the resistivity, and the thermal conductivity. The maximum heat that can be received is negatively correlated with the following items: the square of the total resistance composed of the load resistance and the internal resistance of the thermoelectric generator, the ambient temperature, and the conversion coefficient.

6. The method according to claim 2, wherein The method further includes: Obtaining the historical power consumption of the vehicle; Determining the number of closed shunt valves according to the historical power consumption, and the number of closed shunt valves is positively correlated with the historical power consumption; According to the number of closed shunt valves, setting the opening degree of the recovery side of the shunt valves of multiple heat recovery systems to the minimum opening degree.

7. An engine system, characterized in that, The engine system includes: an engine, a control unit, a turbocharger, an intercooler, a radiator, an aftertreatment system, and at least one heat recovery system. The exhaust end of the engine is connected to the input end of the turbocharger. The intercooler is arranged on the intake pipe between the turbocharger and the engine. The radiator is arranged on the coolant pipe between the coolant output end of the engine and the coolant input end of the engine. The aftertreatment system is arranged on the exhaust pipe after the turbocharger; The at least one heat recovery system includes at least one of the following: a heat recovery system arranged in parallel at both ends of the intercooler through its own shunt valve, a heat recovery system arranged at both ends of the radiator through its own shunt valve, and a heat recovery system arranged after the aftertreatment system through its own shunt valve; The control unit is communicatively connected to the heat recovery system and the shunt valve; The control unit is used to determine the state parameters of the heat recovery system. The state parameters of the heat recovery system include: the input heat of the self-shunt valve of the heat recovery system, the maximum heat that can be absorbed by the heat recovery system; and adjusting the opening degree of the self-shunt valve of the heat recovery system according to the state parameters of the heat recovery system.

8. An electronic device, characterized in that, Including: A memory, a processor; The memory stores computer execution instructions; The processor executes the computer-executable instructions stored in the memory, such that the processor performs the method according to any one of claims 1-6.

9. A computer-readable storage medium, characterized in that, Computer-executable instructions are stored in the computer-readable storage medium, and when the computer-executable instructions are executed by a processor, they are used to implement the method according to any one of claims 1-6.

10. A computer program product, characterized in that, It includes a computer program which, when executed by a processor, implements the method according to any one of claims 1-6.

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