Ship power conversion thermodynamic cycle system

Abstract

The invention provides a ship power conversion thermodynamic cycle system. The system comprises a compressor, a heat regenerator, an intermediate heat exchanger, a turbine and a cooler. An outlet of the compressor is connected with a first channel inlet of the heat regenerator, a first channel outlet of the heat regenerator is connected with an inlet of the intermediate heat exchanger, an outlet of the intermediate heat exchanger is connected with an inlet of the turbine, an outlet of the turbine is connected with a second channel inlet of the heat regenerator, and a second channel outlet of the heat regenerator is connected with an inlet of the cooler. An outlet of the cooler is connected with an inlet of the compressor; the compressor compression operation is used for determining the actual outlet temperature and the outlet specific entropy of the compressor; the actual outlet temperature and the outlet ratio entropy are determined based on the compressor inlet temperature, the compressor inlet pressure, the cycle pressure ratio, and the isentropic efficiency of the compressor. According to the system, the optimal outlet temperature and specific entropy are determined by accurately controlling the operation conditions of the compressor, such as inlet temperature, pressure and circulating pressure ratio, so that the compression process is optimized, the energy consumption is reduced, and the system efficiency is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of ship power, and particularly relates to a ship power conversion thermal cycle system. Background Art

[0002] In recent years, the fourth-generation reactors have developed rapidly, and their operating temperature can reach up to 500 - 900 °C. Especially for the microreactors represented by the heat pipe reactor, it has obvious advantages compared with other reactor types under the condition of low power levels. Supercritical carbon dioxide (S-CO 2 ₂) is more suitable for nuclear reactors with higher temperatures because the working fluid is single-phase throughout the entire circulation process, with a simple structure and high efficiency, and it also has the potential to reduce costs. The combination of the new reactor and the supercritical CO 2 ₂ Brayton cycle forms a new nuclear power system that can significantly reduce the auxiliary equipment of the system, reduce the volume of the main equipment, and improve the power density and safety of the system.

[0003] Although the S-CO 2 ₂ energy conversion system has obvious advantages, there are still many key basic technologies that have not been broken through in the design and implementation process of the S-CO 2 ₂ energy conversion system. The ship power conversion system is complex in composition and strong in system coupling. In the design process of the marine system, it is necessary to balance improving the system efficiency and reducing the system complexity, which are mutually contradictory. Therefore, the optimization design suitable for the marine power system is crucial. Summary of the Invention

[0004] The present invention provides a ship power conversion thermal cycle system to solve the defect that in the prior art, it is necessary to balance improving the system efficiency and reducing the system complexity during the design process of the marine system, and the two are mutually contradictory.

[0005] The present invention provides a ship power conversion thermal cycle system, including a compressor, a recuperator, an intermediate heat exchanger, a turbine, and a cooler; The outlet of the compressor is connected to the inlet of the first channel of the recuperator, the outlet of the first channel of the recuperator is connected to the inlet of the intermediate heat exchanger, the outlet of the intermediate heat exchanger is connected to the inlet of the turbine, the outlet of the turbine is connected to the inlet of the second channel of the recuperator, the outlet of the second channel of the recuperator is connected to the inlet of the cooler, and the outlet of the cooler is connected to the inlet of the compressor; the fluid sequentially passes through compression by the compressor, preheating by the recuperator, further heating by the intermediate heat exchanger, expansion work by the turbine, heat release by the recuperator, and cooling by the cooler and then returns to the compressor; The compression operation of the compressor is used to determine the first actual outlet temperature and the first outlet specific entropy of the compressor; the first actual outlet temperature and the first outlet specific entropy are determined based on the compressor inlet temperature, the compressor inlet pressure, the cycle pressure ratio, and the isentropic efficiency of the compressor.

[0006] According to a marine power conversion thermal cycle system provided by the present invention, the expansion work operation of the turbine is used to determine the second actual outlet temperature and the second outlet specific entropy of the turbine; The second actual outlet temperature and the second outlet specific entropy are determined based on the compressor inlet temperature, the cycle pressure ratio, the compressor inlet pressure, the cycle temperature ratio, the pressure loss rate of the intermediate heat exchanger, the pressure loss rate of the cooler, and the isentropic efficiency of the turbine.

[0007] According to a marine power conversion thermal cycle system provided by the present invention, the cooling operation of the cooler is used to determine the heat release of the cooler; The heat release of the cooler is determined based on the outlet specific enthalpy and the inlet specific enthalpy of the cooler.

[0008] According to a marine power conversion thermal cycle system provided by the present invention, the outlet specific enthalpy and the inlet specific enthalpy are determined based on the compressor inlet temperature and the compressor inlet pressure.

[0009] According to a marine power conversion thermal cycle system provided by the present invention, the heat release operation of the recuperator is used to determine the heat transfer amount of the recuperator; The heat transfer amount of the recuperator is determined based on the enthalpy value at the outlet of the first channel and the enthalpy value at the outlet of the compressor.

[0010] According to a marine power conversion thermal cycle system provided by the present invention, the enthalpy value at the outlet of the compressor is determined based on the compressor inlet temperature, the compressor inlet pressure, the cycle pressure ratio, and the isentropic efficiency of the compressor.

[0011] According to a marine power conversion thermal cycle system provided by the present invention, the further heating operation of the intermediate heat exchanger is used to determine the heat absorption of the working fluid; The heat absorption of the working fluid is determined based on the outlet specific enthalpy and the inlet specific enthalpy of the intermediate heat exchanger.

[0012] According to a marine power conversion thermal cycle system provided by the present invention, the system further includes a controller, and the controller is respectively connected to the cooler and the intermediate heat exchanger; The controller is specifically used for: Based on the heat absorption of the working fluid and the heat release of the cooler, determine the cycle thermal efficiency.

[0013] The marine power conversion thermodynamic cycle system provided by the present invention, on the one hand, by precisely controlling the operating conditions of the compressor, such as the inlet temperature, pressure, cycle pressure ratio, and isentropic efficiency, the optimal outlet temperature and specific entropy can be determined, thereby optimizing the compression process, reducing energy consumption, and improving the system efficiency; on the other hand, the outlet of the compressor is connected to the inlet of the first channel of the regenerator, the outlet of the first channel of the regenerator is connected to the inlet of the intermediate heat exchanger, the outlet of the intermediate heat exchanger is connected to the inlet of the turbine, the outlet of the turbine is connected to the inlet of the second channel of the regenerator, the outlet of the second channel of the regenerator is connected to the inlet of the cooler, and the outlet of the cooler is connected to the inlet of the compressor; the fluid sequentially passes through compression by the compressor, preheating by the regenerator, further heating by the intermediate heat exchanger, expansion work by the turbine, heat release by the regenerator, and cooling by the cooler and then returns to the compressor, reducing the complexity of the system. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] In order to more clearly illustrate the technical solutions in the present invention or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the drawings in the following description are some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0015] Figure 1 It is a schematic structural diagram of the marine power conversion thermodynamic cycle system provided by the present invention.

[0016] Figure 2 It is a flow chart of the simple regenerative Brayton cycle solution provided by the present invention.

[0017] Figure 3 It is a temperature-entropy diagram of the simple regenerative Brayton cycle solution provided by the present invention. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0018] To make the objectives, technical solutions, and advantages of the present invention clearer, the following will clearly and completely describe the technical solutions in the present invention with reference to the accompanying drawings in the present invention. Obviously, the described embodiments are some, but not all, of the embodiments of the present invention. All other embodiments obtained by those of ordinary skill in the art without creative efforts based on the embodiments in the present invention belong to the scope of protection of the present invention.

[0019] The terms "first", "second", etc. in the present invention are used to distinguish similar objects, rather than to describe a specific order or sequence. It should be understood that such data can be interchanged under appropriate circumstances so that the embodiments of the present application can be implemented in an order other than those illustrated or described herein, and the objects distinguished by "first", "second", etc. are usually of the same kind.

[0020] The present invention provides a marine power conversion thermal cycle system. Figure 1 It is a schematic structural diagram of the marine power conversion thermal cycle system provided by the present invention. As Figure 1 shown, the system includes a compressor 10, a recuperator 20, an intermediate heat exchanger 30, a turbine 40, and a cooler 50; The outlet of the compressor 10 is connected to the inlet of the first channel of the recuperator 20. The outlet of the first channel of the recuperator 20 is connected to the inlet of the intermediate heat exchanger 30. The outlet of the intermediate heat exchanger 30 is connected to the inlet of the turbine 40. The outlet of the turbine 40 is connected to the inlet of the second channel of the recuperator 20. The outlet of the second channel of the recuperator 20 is connected to the inlet of the cooler 50. The outlet of the cooler 50 is connected to the inlet of the compressor 10. The fluid is compressed by the compressor 10, preheated by the recuperator 20, further heated by the intermediate heat exchanger 30, expands and does work by the turbine 40, releases heat by the recuperator 20, and is cooled by the cooler 50 and then returns to the compressor; The compression operation of the compressor 10 is used to determine the first actual outlet temperature and the first outlet specific entropy of the compressor 10. The first actual outlet temperature and the first outlet specific entropy are determined based on the compressor inlet temperature, the compressor inlet pressure, the cycle pressure ratio, and the isentropic efficiency of the compressor.

[0021] Specifically, the marine power conversion thermal cycle system includes a compressor 10, a recuperator 20, an intermediate heat exchanger 30, a turbine 40, and a cooler 50. Among them, the outlet of the compressor 10 is connected to the inlet of the first channel of the recuperator 20. The outlet of the first channel of the recuperator 20 is connected to the inlet of the intermediate heat exchanger 30. The outlet of the intermediate heat exchanger 30 is connected to the inlet of the turbine 40. The outlet of the turbine 40 is connected to the inlet of the second channel of the recuperator 20. The outlet of the second channel of the recuperator 20 is connected to the inlet of the cooler 50. The outlet of the cooler 50 is connected to the inlet of the compressor 10. The fluid is compressed by the compressor 10, preheated by the recuperator 20, further heated by the intermediate heat exchanger 30, expands and does work by the turbine 40, releases heat by the recuperator 20, and is cooled by the cooler 50 and then returns to the compressor.

[0022] Among them, the compressor 10, the turbine 40, and the motor are coaxial to form an integrated unit. The four devices of the compressor 10, the recuperator 20, the turbine 40, and the cooler 50 correspond to the four thermodynamic processes of isentropic compression, constant pressure heat absorption, adiabatic expansion, and constant pressure heat release in the Brayton cycle. The recuperator 20 is arranged to preheat the low-temperature supercritical carbon dioxide at the outlet of the compressor by using the high-temperature exhaust gas of the turbine, thereby recovering part of the exhaust heat and reducing the energy loss of the pre-cooler.

[0023] The compression operation of the compressor 10 is used to determine the first actual outlet temperature of the compressor 10 and the first outlet specific entropy , where the first actual outlet temperature and the first outlet specific entropy are determined based on the compressor inlet temperature , the compressor inlet pressure , the cycle pressure ratio and the isentropic efficiency of the compressor as follows: It can be understood that determining the first actual outlet temperature of the compressor is an isentropic compression process. Based on the known pressure ratio and the compressor inlet and outlet parameters, the first actual outlet temperature and the first outlet specific entropy of the compressor can be obtained.

[0024] It should be noted that the recuperator 20 recovers the heat of the high-temperature fluid at the outlet of the turbine 40 for preheating the fluid at the outlet of the compressor 10. This heat recovery reduces the system's demand for external heating and improves the overall energy utilization efficiency.

[0025] The intermediate heat exchanger 30 further heats the fluid to a higher temperature, so that more energy can be released for work in the turbine 40. This way of staged heating can optimize the heating process and improve the thermal efficiency of the system.

[0026] Furthermore, by precisely controlling the operating conditions of the compressor 10 (such as inlet temperature, pressure, cycle pressure ratio, and isentropic efficiency), the optimal outlet temperature and specific entropy can be determined, thereby optimizing the compression process and reducing energy consumption.

[0027] The heat recovery of the recuperator 20 reduces the cooling load of the cooler 50, lowers the energy consumption of the cooling system, and further reduces the operating cost.

[0028] In addition, each device in the system (such as the compressor, turbine, heat exchanger) can be adjusted according to different operating conditions. For example, by changing parameters such as the cycle pressure ratio and inlet temperature to adapt to different operating conditions. This system design can be applied to various fluid working media (such as carbon dioxide, water vapor, etc.). By adjusting the device parameters, different thermodynamic cycles can be achieved, such as the Rankine cycle, Brayton cycle, etc.

[0029] In the system provided by the embodiment of the present invention, the outlet of the compressor is connected to the inlet of the first channel of the recuperator, the outlet of the first channel of the recuperator is connected to the inlet of the intermediate heat exchanger, the outlet of the intermediate heat exchanger is connected to the inlet of the turbine, the outlet of the turbine is connected to the inlet of the second channel of the recuperator, the outlet of the second channel of the recuperator is connected to the inlet of the cooler, and the outlet of the cooler is connected to the inlet of the compressor; the fluid sequentially passes through compression by the compressor, preheating by the recuperator, further heating by the intermediate heat exchanger, expansion work by the turbine, heat release by the recuperator, and cooling by the cooler and then returns to the compressor; the compressor compression operation is used to determine the first actual outlet temperature and the first outlet specific entropy of the compressor; the first actual outlet temperature and the first outlet specific entropy are determined based on the compressor inlet temperature, the compressor inlet pressure, the cycle pressure ratio, and the isentropic efficiency of the compressor. On the one hand, by precisely controlling the operating conditions of the compressor, such as the inlet temperature, pressure, cycle pressure ratio, and isentropic efficiency, this system can determine the optimal outlet temperature and specific entropy, thereby optimizing the compression process, reducing energy consumption, and improving the system efficiency; on the other hand, the outlet of the compressor is connected to the inlet of the first channel of the recuperator, the outlet of the first channel of the recuperator is connected to the inlet of the intermediate heat exchanger, the outlet of the intermediate heat exchanger is connected to the inlet of the turbine, the outlet of the turbine is connected to the inlet of the second channel of the recuperator, the outlet of the second channel of the recuperator is connected to the inlet of the cooler, and the outlet of the cooler is connected to the inlet of the compressor; the fluid sequentially passes through compression by the compressor, preheating by the recuperator, further heating by the intermediate heat exchanger, expansion work by the turbine, heat release by the recuperator, and cooling by the cooler and then returns to the compressor, reducing the complexity of the system.

[0030] Based on the above embodiment, the turbine expansion work operation is used to determine the second actual outlet temperature and the second outlet specific entropy of the turbine; the second actual outlet temperature and the second outlet specific entropy are determined based on the compressor inlet temperature, the cycle pressure ratio, the compressor inlet pressure, the cycle temperature ratio, the pressure loss rate of the intermediate heat exchanger, the pressure loss rate of the cooler, and the isentropic efficiency of the turbine.

[0031] Specifically, the turbine expansion work operation is used to determine the second actual outlet temperature and the second outlet specific entropy of the turbine 40.

[0032] Wherein, the second actual outlet temperature and the second outlet specific entropy are determined based on the compressor inlet temperature 、the cycle pressure ratio 、the compressor inlet pressure 、the cycle temperature ratio 、the pressure loss rate of the intermediate heat exchanger 、the pressure loss rate of the cooler and the isentropic efficiency of the turbine as follows: It is understandable that the turbine undergoes an isentropic expansion process. Based on parameters such as the maximum cycle temperature and the minimum cycle temperature, the actual outlet temperature and specific entropy of the turbine can be obtained.

[0033] It should be noted that by considering the pressure loss rate and isentropic efficiency, the energy losses of the system can be more accurately evaluated, enabling measures to be taken to reduce these losses and improve the overall efficiency of the system. The determination of these parameters can help the system better adapt to variable operating conditions and ensure high efficiency even when deviating from the design conditions.

[0034] Based on the above embodiments, the cooling operation of the cooler is used to determine the heat release of the cooler; The heat release of the cooler is determined based on the specific enthalpy at the outlet and the specific enthalpy at the inlet of the cooler.

[0035] Specifically, the cooling operation of the cooler is used to determine the heat release of cooler 50, where the heat release of cooler 50 is based on the specific enthalpy at the outlet of cooler 50 and the specific enthalpy at the inlet. Determined.

[0036] Among them, the specific enthalpy at the outlet and the specific enthalpy at the inlet are determined based on the compressor inlet temperature and the compressor inlet pressure.

[0037] The outlet of cooler 50 is the inlet of the compressor. According to the constant-pressure heat release process, the heat release of the working fluid in the cooler can be obtained as: Changes in the compressor inlet temperature and pressure will directly affect the specific enthalpies at the inlet and outlet of the cooler, thereby affecting the heat release. By determining the heat release in this way, the system can better adapt to changes in the operating conditions, timely adjust the operating parameters of the cooler, and ensure efficient operation of the system under different conditions.

[0038] Based on the above embodiments, the heat release operation of the regenerator is used to determine the heat exchange amount of the regenerator; The heat exchange amount of the regenerator is determined based on the enthalpy value at the outlet of the first channel and the enthalpy value at the outlet of the compressor.

[0039] Specifically, ignoring the heat and pressure losses in the pipe section, the high-pressure side inlet of regenerator 20 is the same as the outlet of compressor 10, the low-pressure side outlet is the same as the inlet of cooler 50, and the low-pressure side inlet is the same as the inlet of turbine 40.

[0040] The heat exchange amount of the regenerator is determined based on the enthalpy value at the outlet of the first channel and the enthalpy value at the outlet of the compressor. The formula is as follows: Among them, represents the heat exchange amount of the regenerator, represents the enthalpy value at the outlet of the first channel, represents the enthalpy value at the outlet of the compressor, represents the inlet temperature of the compressor, represents the inlet pressure of the compressor, represents the cycle pressure ratio, represents the isentropic efficiency of the compressor.

[0041] Among them, the outlet pressure of the high-pressure side is: The heat absorption of the high-pressure side is equal to the heat release of the low-pressure side. Therefore, the enthalpy value at the outlet of the high-pressure side (the enthalpy value at the outlet of the first channel) can be obtained: Furthermore, the heat exchange amount of the regenerator is: Among them, represents the heat exchange amount of the regenerator, represents the inlet temperature of the compressor, represents the cycle temperature ratio, represents the inlet pressure of the compressor, represents the cycle pressure ratio, represents the pressure loss rate of the intermediate heat exchanger, represents the pressure loss rate of the cooler, represents the isentropic efficiency of the turbine, represents the isentropic efficiency of the compressor, represents the pressure loss rate of the high-pressure side of the regenerator, represents the pressure loss rate of the low-pressure side of the regenerator, represents the temperature difference at the ends of the regenerator (the difference between the inlet temperature of the high-pressure side and the outlet temperature of the low-pressure side of the regenerator).

[0042] Based on the above embodiments, the further heating operation of the intermediate heat exchanger is used to determine the heat absorption of the working fluid; The heat absorption of the working fluid is determined based on the specific enthalpy at the outlet and the specific enthalpy at the inlet of the intermediate heat exchanger.

[0043] Specifically, the further heating operation of the intermediate heat exchanger is used to determine the heat absorption of the working fluid. Among them, the heat source inlet is the same as the outlet of the high-pressure side of the regenerator, and the outlet is the same as the inlet of the turbine. The heat absorption of the working fluid can be obtained as: Among them, represents the heat absorption of the working fluid, represents the specific enthalpy at the outlet of the intermediate heat exchanger, represents the specific enthalpy at the inlet of the intermediate heat exchanger, represents the inlet temperature of the compressor, represents the cycle temperature ratio, represents the compressor inlet pressure, represents the cycle pressure ratio, represents the pressure loss rate of the intermediate heat exchanger, represents the pressure loss rate of the cooler, represents the isentropic efficiency of the turbine, represents the isentropic efficiency of the compressor, represents the pressure loss rate of the high-pressure side of the recuperator, represents the pressure loss rate of the low-pressure side of the recuperator, represents the temperature difference at the ends of the recuperator.

[0044] Based on the above embodiments, the system further includes a controller, and the controller is respectively connected to the cooler and the intermediate heat exchanger; The controller is specifically configured to: Determine the cycle thermal efficiency based on the heat absorption of the working fluid and the heat release of the cooler.

[0045] Specifically, the system further includes a controller, and the controller is respectively connected to the cooler 50 and the intermediate heat exchanger 30.

[0046] Among them, the controller is specifically configured to: Determine the cycle thermal efficiency based on the heat absorption of the working fluid and the heat release of the cooler. The formula for the cycle thermal efficiency is: It should be noted that the present invention proposes a thermal cycle calculation method for a new power conversion system of a ship power plant, which can solve the thermal system calculation of a simple regenerative Brayton cycle. Based on this thermal system calculation, the key parameters and thermal characteristics of the equipment of the supercritical two-cycle system can be obtained, and the influence of operating parameters on the comprehensive performance of the system can be analyzed. Moreover, a component-based construction method is adopted to establish corresponding thermal models for different thermodynamic processes of the system, realizing the system calculation of the thermal cycle of the new power conversion system. The established model has good scalability and is applicable to the simple regenerative cycle under marine conditions and the Brayton cycle system with different physical properties.

[0047] To sum up, the present invention proposes a new nuclear power system optimization design and modeling method applied to ship installations. This method mainly aims at the supercritical carbon dioxide Brayton cycle energy conversion system, considers the marine conditions of the ship power plant, establishes a new nuclear power system model based on the marine supercritical carbon dioxide Brayton cycle, conducts system simulation calculations, forms an overall scheme of an advanced nuclear power system, obtains the system operating parameters, and studies the influence of operating parameters on the comprehensive performance of the system. Conduct an in-depth analysis of the operating characteristics of the S-CO 2 energy conversion system, and study S-CO 2The deep mechanism and characteristic laws of the thermohydraulic behavior characteristics of key equipment in the energy conversion system are analyzed, and the influence mechanism and nonlinear characteristics of the complex behavior characteristics of the system operation are dissected.

[0048] Figure 2 It is the flow chart of the simple recuperative Brayton cycle scheme provided by the present invention. Figure 3 It is the temperature-entropy diagram of the simple recuperative Brayton cycle scheme provided by the present invention. As Figure 2 、 Figure 3 shown, the highest temperature of the cycle is the outlet temperature of the intermediate heat exchanger , and the lowest temperature of the cycle is the temperature at point 1o at the outlet of the cooler ; the highest pressure of the cycle is the pressure at point 2o at the outlet of the compressor , and the lowest pressure of the cycle is the pressure at point 2i at the inlet of the compressor . In the modeling process, the heat loss and pressure loss of the connecting pipe sections between components are ignored, and 、 、 、 、 、 、 、 、 、 and other 10 parameters that are convenient to be given values with reference to engineering design experience are regarded as known quantities.

[0049] First, determine the values of the cycle parameters. According to the known parameters, the values of other parameters in the system can be obtained in sequence. By adjusting different cycle parameters, the influence on the cycle thermal efficiency, etc. can be analyzed.

[0050] The device embodiments described above are merely illustrative. 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 to multiple network units. Some or all of the modules can be selected according to actual needs to achieve the purpose of the solution of this embodiment. Those of ordinary skill in the art can understand and implement it without creative labor.

[0051] Through the description of the above embodiments, those skilled in the art can clearly understand that each embodiment can be implemented by means of software plus a necessary general hardware platform, and of course, it can also be implemented by hardware. Based on such an understanding, the essence of the above technical solution or the part that contributes to the prior art can be embodied in the form of a software product. The computer software product can be stored in a computer-readable storage medium, such as ROM / RAM, magnetic disk, optical disk, etc., and includes several instructions to enable a computer device (which can be a personal computer, server, or network device, etc.) to execute the methods described in each embodiment or some parts of the embodiments.

[0052] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that they can still modify the technical solutions recorded in the foregoing embodiments, or perform equivalent replacements for some of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A ship power conversion thermal cycle system, characterized in that: Including compressor, recuperator, intermediate heat exchanger, turbine and cooler; The outlet of the compressor is connected to the inlet of the first channel of the regenerator, the outlet of the first channel of the regenerator is connected to the inlet of the intermediate heat exchanger, the outlet of the intermediate heat exchanger is connected to the inlet of the turbine, the outlet of the turbine is connected to the inlet of the second channel of the regenerator, the outlet of the second channel of the regenerator is connected to the inlet of the cooler, and the outlet of the cooler is connected to the inlet of the compressor; the fluid is compressed by the compressor, preheated by the regenerator, further heated by the intermediate heat exchanger, expanded by the turbine to do work, released by the regenerator, and cooled by the cooler, and then returns to the compressor; The compressor compression operation is used to determine a first actual outlet temperature and a first outlet specific entropy of the compressor; the first actual outlet temperature and the first outlet specific entropy are determined based on a compressor inlet temperature, a compressor inlet pressure, a cycle pressure ratio and an isentropic efficiency of the compressor.

2. The ship power conversion thermal cycle system according to claim 1, characterized in that: The turbine expansion work operation is used to determine a second actual outlet temperature and a second outlet specific entropy of the turbine; The second actual outlet temperature and the second outlet specific entropy are determined based on the compressor inlet temperature, the cycle pressure ratio, the compressor inlet pressure, the cycle temperature ratio, the intermediate heat exchanger pressure loss rate, the cooler pressure loss rate and the isentropic efficiency of the turbine.

3. The ship power conversion thermal cycle system according to claim 1, characterized in that: The cooler cooling operation is used to determine the heat release of the cooler; The heat release amount of the cooler is determined based on the outlet specific enthalpy and inlet specific enthalpy of the cooler.

4. The ship power conversion thermal cycle system according to claim 3, characterized in that: The outlet specific enthalpy and the inlet specific enthalpy are determined based on the compressor inlet temperature and the compressor inlet pressure.

5. The ship power conversion thermal cycle system according to any one of claims 1 to 4, characterized in that: The heat release operation of the regenerator is used to determine the heat exchange capacity of the regenerator; The heat exchange amount of the regenerator is determined based on the enthalpy value of the outlet of the first channel and the outlet enthalpy value of the compressor.

6. The ship power conversion thermal cycle system according to claim 5, characterized in that: The outlet enthalpy value of the compressor is determined based on the compressor inlet temperature, the compressor inlet pressure, the cycle pressure ratio, and the isentropic efficiency of the compressor.

7. The ship power conversion thermal cycle system according to any one of claims 1 to 4, characterized in that: The intermediate heat exchanger is further heated to determine the amount of heat absorbed by the working fluid; The amount of heat absorbed by the working fluid is determined based on the outlet specific enthalpy and the inlet specific enthalpy of the intermediate heat exchanger.

8. The ship power conversion thermal cycle system according to any one of claims 1 to 4, characterized in that: The system further comprises a controller, wherein the controller is connected to the cooler and the intermediate heat exchanger respectively; The controller is specifically used for: The cycle thermal efficiency is determined based on the amount of heat absorbed by the working fluid and the amount of heat released by the cooler.

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