阅读说明：本技术 海上采油平台透平主机无风机带回热循环余热回收效率优化方法 (Method for optimizing recovery efficiency of offshore oil production platform turbine main engine fan-free backheating circulation waste heat ) 是由 刘向龙 曾智 曾丽萍 李文菁 李小华 文科 于 2019-11-25 设计创作，主要内容包括：本发明公开了海上采油平台透平主机回热循环余热回收效率优化方法,所述方法首先定义透平主机的压比参数θ<Sub>C</Sub>、膨胀比参数θ<Sub>D</Sub>确定透平主机的燃烧过程压力保持系数ρ<Sub>Com</Sub>、热回收过程压力保持系数ρ<Sub>R</Sub>、空气侧压力保持系数ρ<Sub>Rk</Sub>和烟气侧压力保持系数ρ<Sub>Ry</Sub>；再根据上述所得参数确定透平主机各出口工质状态点的燃烧温度、烟气比容和压力；得燃料<Image he="50" wi="51" file="DDA0002287236750000015.GIF" imgContent="drawing" imgFormat="GIF" orientation="portrait" inline="no"></Image>E、输出电功率<Image he="52" wi="48" file="DDA0002287236750000016.GIF" imgContent="drawing" imgFormat="GIF" orientation="portrait" inline="no"></Image>E<Sub>P</Sub>和系统输出的热量<Image he="52" wi="50" file="DDA0002287236750000014.GIF" imgContent="drawing" imgFormat="GIF" orientation="portrait" inline="no"></Image>E<Sub>Q</Sub>,最后得出余热回收系统的<Image he="51" wi="50" file="DDA0002287236750000013.GIF" imgContent="drawing" imgFormat="GIF" orientation="portrait" inline="no"></Image>效率ε；从而控制余热回收系统的效率。与现有技术相比,本发明提供的优化方法得到透平主机余热回收时系统<Image he="49" wi="49" file="DDA0002287236750000011.GIF" imgContent="drawing" imgFormat="GIF" orientation="portrait" inline="no"></Image>效率与压比参数及温比参数之间的关系,通过观察各状态点参数,对其压力进行控制,从而使透平主机余热回收时系统<Image he="53" wi="49" file="DDA0002287236750000012.GIF" imgContent="drawing" imgFormat="GIF" orientation="portrait" inline="no"></Image>效率最高。(The invention discloses a method for optimizing the regenerative cycle waste heat recovery efficiency of a turbine main engine of an offshore oil production platform C Expansion ratio parameter theta D Determining a combustion process pressure maintenance factor ρ for a turbine main unit Com Pressure holding coefficient rho in heat recovery process R Air side pressure retention coefficient ρ Rk And flue gas side pressure retention coefficient ρ Ry (ii) a Determining the combustion temperature, the flue gas specific volume and the pressure of each outlet working medium state point of the turbine main machine according to the obtained parameters; obtaining fuel E. Output electric power E P And heat output by the system E Q And finally obtaining a waste heat recovery system An efficiency ε; thereby controlling the efficiency of the waste heat recovery system. Compared with the prior art, the optimization method provided by the invention obtains the system when the turbine main engine waste heat is recovered The relation between the efficiency and the pressure ratio parameter and the temperature ratio parameter controls the pressure of each state point parameter by observing the parameters of each state point, thereby leading the system to recover the waste heat of the turbine main engine The efficiency is highest.)

1. A method for optimizing the recovery efficiency of the heat-recovery circulation waste heat of a fan-free turbine main engine of an offshore oil production platform is characterized by comprising the following steps:

step S1) determining the pressure ratio parameter theta of the turbine main machine according to the inlet and outlet pressure, the inlet and outlet temperature and the flue gas specific heat ratio of the compressor of the turbine main machine_CAnd expansion ratio parameter theta_D；

Step S2) determining the pressure holding coefficient rho of the combustion process of the turbine main engine according to the pressure of the turbine main engine, the pressure of the combustion chamber after the combustion process and the specific heat ratio of the flue gas after the combustion_ComPressure holding coefficient rho in heat recovery process_RAir side pressure retention coefficient ρ_RkAnd flue gas side pressure retention coefficient ρ_RyThen according to the expansion ratio parameter theta obtained in step S1_DObtaining a pressure ratio parameter theta_CAnd expansion ratio parameter theta_DThe relationship between;

step S3) determining the main turbine efficiency η according to the actual outlet temperature of the compressor of the main turbine, the outlet temperature after irreversible loss and the ambient temperature_CExpansion efficiency η_DHeat loss η of regenerative cycle_HAnd flue gas temperature coefficient α_P；

Step S4) according to the parameter theta obtained in the steps S1-S3_C、θ_D、η_C、η_D、ρ_Com、ρ_R、ρ_Rk、ρ_Ry、η_HAnd α_PDetermining working medium state point state parameters of each outlet of a turbine main machine;

step S5) according to the parameters obtained from the steps S1 to S4,substituting formula 31 to obtain waste heat recovery system of turbine main engine under different loads

in the formula, α is assumed to be the temperature ratio parameter of waste heat recovery and passes through T₃＝αT₁Obtained by η_GTo the generator efficiency;

step S6) adjusting the pressure ratio parameter and the temperature ratio parameter so as to indirectly maintain the waste heat recovery system

2. The method for optimizing the recovery efficiency of the turbine main engine heat recovery waste heat without the fan and the regenerative cycle of the offshore production platform according to claim 1, wherein before the adjustment of the pressure ratio parameter and the temperature ratio parameter in step S5, the pressure ratio parameter and the temperature ratio parameter are selected and used under different loads

3. The method for optimizing the recovery efficiency of the turbine main engine with the regenerative cycle waste heat without the fan of the offshore production platform according to claim 1, wherein the pressure ratio parameter θ of the turbine main engine in the step S1 is_CAnd expansion ratio parameter theta_DDetermined by equation 1 and equation 2:

θ_C＝T_2'/T₁＝(P₂/P₁)^(γ-1)/γ(1)

θ_D＝T₄/T_5'＝(P₄/P₅)^(γ-1)/γ(2)

wherein gamma is the specific heat ratio of the flue gas, P₁For the pressure, P, at point 1 of the turbine main engine operating state₂For the pressure at point 2 of the turbine main engine operating state, T₁For flue gas temperature, T, at State Point 1 during waste Heat recovery_2’For the flue gas temperature, P, of the state point 2' in the recovery of residual heat₄For turbine main engine state point 4 pressure, P₅For turbine main engine state point 5 pressure, T₄At a state point of 4 temperature, T_5’Is the statepoint 5' temperature.

4. The offshore production platform turbine host fan-free regenerative cycle waste heat recovery efficiency optimization method according to claim 3, wherein the combustion process pressure holding coefficient p of the turbine host is determined in step S2_ComPressure holding coefficient rho in heat recovery process_RAir side pressure retention coefficient ρ_RkAnd flue gas side pressure retention coefficient ρ_RyThe method is determined by formulas 3-6:

ρ_Com＝(P₄/P₃)^(γ-1)/γ(3)

ρ_R＝(P₅/P₄)^(γ-1)/γ(4)

ρ_Rk＝(P₃/P₂)^(γ-1)/γ(5)

ρ_Ry＝(P₆/P₅)^(γ-1)/γ(6)

in the formula, ρ_ComFor the pressure holding coefficient of the combustion process, p_RPressure holding coefficient, p, for heat recovery processes_RkIs the pressure holding coefficient of the air side, p_RyIs the pressure holding coefficient of the flue gas side, gamma is the specific heat ratio of the flue gas, P₂For the pressure, P, at point 2 of the turbine main engine operating state₃For turbine main engine state point 3Pressure, P₄For turbine main engine state point 4 pressure, P₅For turbine main engine state point 5 pressure, P₆The pressure at state point 6 is when the turbine main machine is running.

5. The offshore production platform turbine host fan-free backheating cycle waste heat recovery efficiency optimization method according to claim 4, wherein the intermediate pressure ratio parameter θ of step S2_CAnd expansion ratio parameter theta_DThe relationship between them is shown in equation 7:

θ_D＝θ_Cρ_Rρ_comρ_Rkρ_Ry(7)。

6. the method for optimizing turbine engine fan-less regenerative cycle waste heat recovery efficiency of offshore production platform according to claim 5, wherein the turbine engine efficiency η in step S3_CExpansion efficiency η_DHeat loss η of regenerative cycle_HAnd flue gas temperature coefficient α_PThe method is determined by formulas 8-11:

η_C＝(T_2'-T₁)/(T₂-T₁) (8)

η_D＝(T₄-T₅)/(T₄-T_5') (9)

T₃-T₂＝η_H(T₅-T₆) (10)

α_P＝T₆/T₁(11)

in the formula, T₁For flue gas temperature, T, at State Point 1 during waste Heat recovery_2’For the flue gas temperature, T, of the state point 2' in the case of waste heat recovery₂Temperature of State Point 2, T₄At a state point of 4 temperature, T₅For discharging temperature, T, of waste heat boilers_5’Is the temperature of the state point 5', T₆The exhaust gas temperature after the heat recovery cycle of the main machine.

7. The method for optimizing the efficiency of waste heat recovery of a turbine host without a fan and with a regenerative cycle of an offshore production platform according to claim 6, comprising the steps ofStep S4 is a step of obtaining a parameter θ according to the steps S1-S3_C、θ_D、η_C、η_D、ρ_Com、ρ_R、ρ_Rk、ρ_Ry、η_HAnd α_PDetermining the combustion temperature T, the specific volume v and the pressure P of the flue gas of each outlet working medium state point of the turbine main engine through a formula 12-a formula 27;

point 1:

P₁

v₁

T₁

and 2, point:

P₂＝(θ_Cρ_Rk)^γ/(γ-1)P₁(12)

v₂＝[1+(θ_C-1)/η_C](θ_C)^-γ/(γ-1)v₁(13)

T₂＝[1+(θ_C-1)/η_C]T₁(14)

and 3, point:

P₃＝(ρ_Comθ_C)^γ/(γ-1)P₁(15)

v₃(16)

T₃＝((1+(θ_C-1)/η_C)-α_Pη_H+η_Hα(1-η_D(1-1/(θ_Cρ_Comρ_Rρ_Rkρ_Ry))))T₁(17)

and 4, point:

P₄＝(θ_Cρ_Rρ_Rkρ_com)^γ/(γ-1)P₁(18)

v₄＝α(ρ_Rkρ_comθ_C)^-γ/(γ-1)v₁(19)

T₄＝αT₁(20)

and 5, point:

P₅＝(ρ_Rρ_Ry)^-γ/(γ-1)P₁(21)

v₅＝α(ρ_Rρ_Ry)^γ/(γ-1)(1-η_D(1-1/(θ_Cρ_Comρ_Rρ_Ryρ_Rk)))v₁(22)

T₅＝α(1-η_D(1-1/(θ_Cρ_Comρ_Rρ_Rkρ_Ry)))T₁(23)

and 6, point:

P₆＝(ρ_R)^-γ/(γ-1)P₁(24)

v₆(25)

T₆＝α_PT₁(26)

and 7, point:

P₇＝P₁

v₇

T₇

and 8, point:

P₈

v₈

T₈＝α_ST₆(27)

in the formula, P₁～P₈The pressure at 1-8 points of the outlet state point of a turbine main machine with a heat return cycle₁～v₈The specific volume of flue gas, T, of a turbine main engine outlet state point 1-8 with a heat-return cycle₁～T₃1 to 3 point temperature, T₄For turbine main engine exhaust gas temperature, T₅For discharging temperature, T, of waste heat boilers₆～T₇The temperature of the flue gas at the state point 6-7 of the turbine main engine after the regenerative cycle is α_SIs the wind resistance coefficient, T₈The flue gas temperature at state point 8 when there is waste heat recovery.

8. The method for optimizing turbine main engine fan-free regenerative cycle waste heat recovery efficiency of offshore production platform according to claim 7, wherein the step S4 is performed by substituting parameters obtained in the steps S1-S3 into the formulas 28-30 to determine fuel

E_P＝q_mC_Pη_G[(T₄-T₃)-(α_ST₆-T₁)](29)

Wherein E is a fuel，q_mIs the mass flow of flue gas, C_Pη is the constant pressure specific heat capacity of the flue gas_GIs the efficiency of the generator.

9. The method for optimizing the turbine host heat recovery efficiency without fan and with regenerative cycle of offshore production platform according to claim 1, wherein step S5 is performed on the heat recovery system

Technical Field

The invention relates to the field of offshore oil recovery energy recovery, in particular to an optimization method of a control system of a turbine host of an offshore oil recovery platform, and specifically relates to a method for monitoring the working efficiency and carrying out micro-control.

Background

The advantages of large power, small volume, high efficiency, low pollution of exhaust gas and the like of a gas turbine (turbine) generator set are receiving more and more attention. On the ocean oil production facility, an offshore oil production gas platform and a large floating production, storage and offloading tanker (FPSO) and the like have independence and particularity due to the fact that an electric power system adopted by the offshore oil production gas platform and the large floating production, storage and offloading tanker (FPSO) is far away from the land. Generally, a generator is selected by an offshore platform power system, the voltage regulating action time is short, the regulating speed is high, and the generator has strong excitation capacity and overload capacity. The turbine main engine generator set completely meets the characteristics, and has the characteristics of high efficiency, quick start, stable operation and the like.

As the exhaust gas temperature of the turbine main engine is as high as 400-600 ℃, in order to fully utilize the waste heat, a waste heat recovery device of a turbine main engine generator set can be additionally arranged. The waste heat recovery device is characterized in that a set of heat exchanger is additionally arranged on an exhaust flue of a turbine main engine generator set. Namely, the waste gas boiler and a set of oil-fired and gas-fired boiler are combined into a set of hot oil (medium) boiler. The heated medium is heated in series by a waste gas boiler and an oil and gas boiler. The temperature of the smoke outlet of the device can be reduced to 200-300 ℃. The waste heat is fully utilized, so that the energy is saved, the atmospheric pollution is reduced, and the use cost of the turbine main engine is indirectly reduced.

In all differences from the simple open Brayton co-production cycle, we have added a regenerator to the regenerative cycle. The air pressurized by the compressor firstly enters the heat regenerator to exchange heat with high-temperature exhaust gas from a turbine, so that the air temperature is increased. The primarily heated compressed air enters the combustion chamber, so that the combustion efficiency is improved, and after the compressed air is mixed with the fuel and combusted, the heat energy released by the combustion of the fuel is absorbed, so that the temperature of the compressed air is further increased. High-temperature flue gas enters a turbine to do work through expansion, electric energy is output outwards, generally, exhaust of a marine turbine main machine is directly exhausted into the atmosphere after heat energy is released by a heat regenerator, and cogeneration cycle is achieved.

Disclosure of Invention

The Brayton Cycle (Brayton Cycle) is an ideal Cycle for constant pressure heating, also known as the joule Cycle or gas refrigerator Cycle. The refrigeration cycle uses gas as working medium, the working process comprises four processes of isentropic compression, isobaric cooling, isentropic expansion and isobaric heat absorption, which are similar to the four working processes of a vapor compression type refrigerator, and the difference between the four working processes is that the working medium does not generate state change in the Brayton cycle. The method analyzes several thermodynamic systems, selects a simple open Brayton Cycle to analyze and optimize the waste heat recovery, and considers a turbine host on an oil production platform as a key device in the Brayton system.

Aiming at the problems in the prior art, the invention provides a fan-free backheating circulation waste heat recovery efficiency optimization method for a turbine main engine of an offshore oil production platform, which can adjust the working efficiency of waste heat recovery equipment according to the load change of the turbine main engine and maximize the waste heat utilization rate.

In order to solve the technical problems, the technical scheme provided by the invention is as follows:

the invention provides a method for optimizing the recovery efficiency of the heat-recovery-cycle waste heat of a non-fan zone of a turbine main engine of an offshore oil production platform, which comprises the following steps:

step S1) determining the pressure ratio parameter theta of the turbine main machine according to the inlet and outlet pressure, the inlet and outlet temperature and the flue gas specific heat ratio of the compressor of the turbine main machine_CAnd expansion ratio parameter theta_D；

Step S2) determining the pressure holding coefficient rho of the combustion process of the turbine main engine according to the pressure of the turbine main engine, the pressure of the combustion chamber after the combustion process and the specific heat ratio of the flue gas after the combustion_ComPressure holding coefficient rho in heat recovery process_RAir side pressure retention coefficient ρ_RkAnd a flue gas side pressure holding coefficient ρ_RyThen according to the expansion ratio parameter theta obtained in step S1_DObtaining a pressure ratio parameter theta_CAnd expansion ratio parameter theta_DThe relationship between;

step S3) determining turbine main engine efficiency η according to actual outlet temperature of turbine main engine compressor, outlet temperature after irreversible loss and environment temperature_CExpansion efficiency η_DHeat loss η of regenerative cycle_HAnd flue gas temperature coefficient α_P；

Step S4) according to the parameter theta obtained in the steps S1-S3_C、θ_D、η_C、η_D、ρ_Com、ρ_R、ρ_Rk、ρ_Ry、η_HAnd α_PDetermining working medium state point state parameters of each outlet of a turbine main machine;

step S5) determining the waste heat recovery system under different loads of the turbine main engine according to the parameters obtained in the steps S1-S4Efficiency epsilon, adjusting pressure ratio parameter and temperature ratio parameter to indirectly maintain waste heat recovery system

Efficiency epsilon is the highest value;

step S6).

Preferably, before the pressure ratio parameter and the temperature ratio parameter are adjusted in step S5, the pressure ratio parameter and the temperature ratio parameter are selectedUnder different loads

Extreme values of the efficiency epsilon determine the pressure ratio parameter theta of the main turbine_CBy the pressure ratio parameter theta_CThe temperature of the turbine main machine controls the pressure of the compressor of the turbine main machine, thereby indirectly maintaining the waste heat recovery system

The efficiency epsilon is the highest value.

Preferably, the pressure ratio parameter θ of the turbine main unit in step S1_CAnd expansion ratio parameter theta_DDetermined by equation 1 and equation 2:

θ_C＝T_2'/T₁＝(P₂/P₁)^(γ-1)/γ(1)

θ_D＝T₄/T_5'＝(P₄/P₅)^(γ-1)/γ(2)

wherein gamma is the specific heat ratio of the flue gas, P₁For the pressure, P, at point 1 of the turbine main engine operating state₂For the pressure at point 2 of the operating state of the main turbine₁For flue gas temperature, T, at State Point 1 during waste Heat recovery_2’For the flue gas temperature, P, of the state point 2' in the recovery of residual heat₄For turbine main engine state point 4 pressure, P₅For turbine main engine state point 5 pressure, T₄At a state point of 4 temperature, T_5’Is the statepoint 5' temperature.

Preferably, the combustion process pressure maintenance coefficient ρ of the turbine main unit is determined in step S2_ComPressure retention coefficient rho in heat recovery process_RAir side pressure retention coefficient ρ_RkAnd flue gas side pressure retention coefficient ρ_RyThe method is determined by formulas 3-6:

ρ_Com＝(P₄/P₃)^(γ-1)/γ(3)

ρ_R＝(P₅/P₄)^(γ-1)/γ(4)

ρ_Rk＝(P₃/P₂)^(γ-1)/γ(5)

ρ_Ry＝(P₆/P₅)^(γ-1)/γ(6)

in the formula, ρ_ComFor the pressure holding coefficient of the combustion process, p_RPressure holding coefficient, p, for heat recovery processes_RkIs the pressure holding coefficient of the air side, p_RyIs the pressure holding coefficient of the flue gas side, gamma is the specific heat ratio of the flue gas, P₂For the pressure, P, at point 2 of the turbine main engine operating state₃For turbine main engine state point 3 pressure, P₄For turbine main engine state point 4 pressure, P₅For turbine main engine state point 5 pressure, P₆The pressure at state point 6 is when the turbine main machine is running.

Preferably, the intermediate pressure ratio parameter θ of step S2_CAnd expansion ratio parameter theta_DThe relationship between them is shown in equation 7:

θ_D＝θ_Cρ_Rρ_comρ_Rkρ_Ry(7)。

preferably, turbine engine efficiency η in step S3_CExpansion efficiency η_DHeat loss η of regenerative cycle_HAnd flue gas temperature coefficient α_PThe method is determined by formulas 8-11:

η_C＝(T_2'-T₁)/(T₂-T₁) (8)

η_D＝(T₄-T₅)/(T₄-T_5') (9)

T₃-T₂＝η_H(T₅-T₆) (10)

α_P＝T₆/T₁(11)

in the formula, T₁For flue gas temperature, T, at State Point 1 during waste Heat recovery_2’For the flue gas temperature, T, of the state point 2' in the recovery of residual heat₂Temperature of State Point 2, T₄At a state point of 4 temperature, T₅For discharging temperature, T, of waste heat boilers_5’Is the temperature of the state point 5', T₆The exhaust gas temperature after the heat recovery cycle of the main machine.

Preferably, step S4 is based on stepThe parameter θ obtained in steps S1 to S3_C、θ_D、η_C、η_D、ρ_Com、ρ_R、ρ_Rk、ρ_Ry、 η_HAnd α_PDetermining the combustion temperature T, the flue gas specific volume v and the pressure P of each outlet working medium state point of the turbine main engine through formulas 12 to 27;

point 1:

P₁

v₁

T₁

and 2, point:

P₂＝(θ_Cρ_Rk)^γ/(γ-1)P₁(12)

v₂＝[1+(θ_C-1)/η_C](θ_C)^-γ/(γ-1)v₁(13)

T₂＝[1+(θ_C-1)/η_C]T₁(14)

and 3, point:

P₃＝(ρ_Comθ_C)^γ/(γ-1)P₁(15)

v₃(16)

T₃＝((1+(θ_C-1)/η_C)-α_Pη_H+η_Hα(1-η_D(1-1/(θ_Cρ_Comρ_Rρ_Rkρ_Ry))))T₁(17)

and 4, point:

P₄＝(θ_Cρ_Rρ_Rkρ_com)^γ/(γ-1)P₁(18)

v₄＝α(ρ_Rkρ_comθ_C)^-γ/(γ-1)v₁(19)

T₄＝αT₁(20)

and 5, point:

P₅＝(ρ_Rρ_Ry)^-γ/(γ-1)P₁(21)

v₅＝α(ρ_Rρ_Ry)^γ/(γ-1)(1-η_D(1-1/(θ_Cρ_Comρ_Rρ_Ryρ_Rk)))v₁(22)

T₅＝α(1-η_D(1-1/(θ_Cρ_Comρ_Rρ_Rkρ_Ry)))T₁(23)

and 6, point:

P₆＝(ρ_R)^-γ/(γ-1)P₁(24)

v₆(25)

T₆＝α_PT₁(26)

and 7, point:

P₇＝P₁

v₇

T₇

and 8, point:

P₈

v₈

T₈＝α_ST₆(27)

in the formula, P₁～P₈The pressure, v, of a state point 1-8 points of a turbine main engine with a heat return cycle₁～v₈The specific volume of the flue gas, T, of a state point 1-8 of a turbine main engine₁～T₃1-3 point temperature, T, of a turbine main engine₄For turbine main engine exhaust gas temperature, T₅For discharging temperature, T, of waste heat boilers₆～T₇The temperature of the flue gas at the state point 6-7 of the turbine main engine after the regenerative cycle is α_SIs the wind resistance coefficient, T₈The flue gas temperature at state point 8 when there is waste heat recovery. The temperature and pressure of the state point 8 are both given by the manufacturer of the turbine main engine, generally, the tail flue gas is exhausted after the regenerative cycle when the turbine main engine operates, and if the waste heat recovery is carried out, the waste heat recovery is also carried out afterwards.

Preferably, the fuel is determined in step S4 by substituting the parameters obtained in steps S1S 3 into equations 28 to 30

E. Output electric powerE_P：

E_P＝q_mC_Pη_G[(T₄-T₃)-(α_ST₆-T₁)](29)

In the formula, α is assumed to be the temperature ratio parameter of waste heat recovery and passes through T₃＝αT₁To obtain E as fuel

q_mIs the mass flow of flue gas, C_Pη is the constant pressure specific heat capacity of the flue gas_GIs the efficiency of the generator.

Preferably, the step S5 is that of a waste heat recovery system

The conversion relation between the efficiency epsilon and the pressure ratio parameter and the temperature ratio parameter is obtained to obtain a relation diagram, and the relation diagram is calculated by an automatic control system of the turbine main machine to obtain the relation diagram for maintaining the waste heat recovery systemThe efficiency epsilon is the pressure at the outlet of the compressor state point 2 required by the turbine main engine at the highest value.

Compared with the prior art, the method for optimizing the waste heat recovery of the offshore oil production platform turbine host provided by the invention has the advantages that when the offshore oil production platform turbine host is subjected to a waste heat recovery process, the waste heat recovery process is carried out through a computing system

Efficiency, thereby obtaining a system for recovering the waste heat of the turbine main engine

The relation between the efficiency and the pressure ratio parameter and the temperature ratio parameter further controls the pressure of each state point during the waste heat recovery of the turbine main engine, and controls the pressure of each state point by observing the parameters of each state point, thereby ensuring that the system during the waste heat recovery of the turbine main engine

The efficiency is the highest.

Drawings

FIG. 1 is a temperature entropy diagram of an irreversible simple open Brayton co-production cycle for recovering waste heat of a turbine main engine according to an embodiment of the present invention;

FIG. 2 is a diagram of a regenerative cycle T-S of an offshore turbine main unit.

Detailed Description

The following detailed description of embodiments of the invention refers to the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating the present invention, are given by way of illustration and explanation only, not limitation.