LNG COLD POWER GENERATION USING MIXED WORKING FLUID

Abstract

LNG cold power generator includes: a working fluid including carbon dioxide and ethane; a pump; an evaporator; a turbine; and a condenser. A molar ratio of the carbon dioxide and the ethane is 8595:15:0.5. The working fluid is used in a closed Rankine cycle. A supply pressure of supplied LNG is adjusted to a pressure at which it becomes a saturated liquid. A temperature at an outlet of the condenser is adjusted to a saturated vapor temperature of LNG. A pressure at an outlet of the pump is adjusted to a critical pressure of a mixed working fluid. The cycle includes two turbines and a heater provided therebetween. The heater heats the working fluid to prevent condensation thereof.

Claims

1. LNG cold power generation comprising: a working fluid comprising carbon dioxide and ethane; a pump; an evaporator; a turbine; and a condenser.

2. The LNG cold power generation of claim 1, wherein a molar ratio of the carbon dioxide and the ethane is 8595:15:0.5.

3. The LNG cold power generation of claim 1, wherein the working fluid is used in a closed Rankine cycle.

4. The LNG cold power generation of claim 1, wherein a supply pressure of supplied LNG is adjusted to a pressure at which it becomes a saturated liquid.

5. The LNG cold power generation of claim 1, wherein a temperature at an outlet of the condenser is adjusted to a saturated vapor temperature of LNG.

6. The LNG cold power generation of claim 1, wherein a pressure at an outlet of the pump is adjusted to a critical pressure of a mixed working fluid.

7. The LNG cold power generation of claim 3, wherein the cycle comprises two turbines and a heater provided therebetween.

8. The LNG cold power generation of claim 7, wherein the heater heats the working fluid to prevent condensation thereof.

9. The LNG cold power generation of claim 1, wherein either or both of the evaporator and the heater utilize waste heat in a process.

Description

BRIEF DESCRIPTION OF THE DRAWING

[0018] FIG. 1 schematically illustrates an open Rankine cycle.

[0019] FIG. 2 schematically illustrates a power production flowsheet of the open Rankine cycle using PRO/II with PROVISION.

[0020] FIG. 3 schematically illustrates a closed Rankine cycle.

[0021] FIG. 4 schematically illustrates a flowsheet of the closed Rankine cycle for LNG cold power generation using PRO/II with PROVISION.

[0022] FIG. 5 schematically illustrates a flowsheet of the closed Rankine cycle for LNG cold power generation using a mixed working fluid according to the present disclosure.

DETAILED DESCRIPTION

[0023] The present disclosure provides LNG cold power generation including a working fluid comprising carbon dioxide and ethane, a pump, an evaporator, a turbine, and a condenser.

[0024] Hereinafter, preferred embodiments of the present disclosure will be described with reference to the accompanying drawings.

[0025] When describing the embodiments, it should be noted that the same reference numerals are used throughout the drawings to designate the same or similar components. When it is determined that the detailed description of the known art related to the present disclosure may obscure the gist of the present disclosure, the detailed description will be omitted. In the drawings, components will not be shown to scale.

[0026] It will be understood that, although the terms first, second, A, B, (a), (b), etc. may be used herein to describe various components, these components should not be limited by these terms. These terms are only used to distinguish one component from another component.

[0027] It will be understood that when a component is referred to as being coupled or connected to another component, it can be directly coupled or connected to the other component or intervening components may be present therebetween.

[0028] Furthermore, when a first component such as a layer, a film, a region, or a plate is disposed above or on a second component, the first component may be not only directly above the second component but a third component may be interposed between them. To the contrary, when a first component is directly above a second component, no component may be present between them.

[0029] FIG. 1 shows a conceptual diagram of the simplest open Rankine cycle for LNG cold power generation using a working fluid.

[0030] Referring to FIG. 1, LNG, which is at a pressure condition slightly higher than normal pressure around 162 C., becomes high-pressure LNG after being pressurized by a pump. Thereafter, when heat exchange is performed by seawater, LNG evaporates and changes a phase into high-pressure natural gas. Power may be produced by operating a turbine using the high-pressure natural gas.

[0031] Tokyo Gas Co. produced about 290 kW of power using 10 ton/h of LNG.

[0032] Since the exact components of LNG are not known, typical gas components were used among LNG components imported into Korea Gas Corporation, as shown in Table 2.

TABLE-US-00002 TABLE 2 Component Mole % Nitrogen 0.04 Methane 89.26 Ethane 8.64 Propane 1.44 I-butane 0.27 N-butane 0.35 MW (kg/k-mole) 17.924 GHV (kcal/Sm.sup.3) 10,450

[0033] As a result of performing a computer simulation using LNG and using PRO/II with PROVISION V10.2 from AVEVA Group Limited, as shown in FIG. 2, computer simulation results shown in Table 3 below were obtained. The net power obtained through Table 3 below was 300 kW, which was higher than 290 kW obtained from Tokyo Gas Co.

TABLE-US-00003 TABLE 3 Feed CH4 162 C. 1.5 atm 10,000 kg/h P1Pump outlet pump power pressure: efficiency: required: 50 atm 56% 44 kW E1 heat outlet 1.8935 10.sup.6 exchanger temperature: kcal/h 1 C. Ex1 turbo outlet efficiency: power gained: net power: expander pressure: 75% 344 kW 300 kW 12 atm E2 heat outlet 0.5483 10.sup.6 exchanger temperature: kcal/h 25 C.

[0034] FIG. 3 illustrates a schematic view of a closed Rankine cycle. Since the advantage of the closed Rankine cycle of FIG. 3 is that the pressure of evaporated natural gas can be maintained at high pressure compared to the open Rankine cycle, it is possible to additionally generate power through the turbine.

[0035] Tokyo Gas Co. achieved the power generation effect of 442 kW by using 10 ton/h of LNG cold heat through LNG cold power generation using propane as the working fluid in the closed Rankine cycle as shown in FIG. 3.

[0036] FIG. 4 illustrates a flowsheet implementing the closed Rankine cycle using PRO/II with PROVISION.

[0037] Table 4 below summarizes the computer simulation results using PRO/II with PROVISION in FIG. 4.

TABLE-US-00004 TABLE 4 Item Result Unit LNG mass flow rate 10,000 kg/h Turbine power 374.69 kW Turbine efficiency 85 % Propane circulation flow rate 7,874 kg/h Pump power required 17.01 kW Pump efficiency 805 % Working fluid condenser duty 0.8970 10.sup.6 kcal/h Working fluid evaporator duty 1.2046 10.sup.6 kcal/h Pump outlet pressure 40 bar Turbine outlet pressure 0.696 bar Working fluid evaporator outlet 50 C. temperature Working fluid condenser outlet 120 C. temperature LNG evaporator outlet temperature 53 C.

[0038] According to Table 4, the net power obtained from cold heat of 1 ton/h of LNG is 35.768 kW. Moreover, since the temperature at the outlet of the working fluid evaporator is 120 C., the working fluid should be evaporated using steam. To obtain steam, the combustion of natural gas is required. In Table 2 above, the molecular weight of LNG is 17.924 kg/k-mole and GHV is 10,450 kcal/Sm.sup.3, the mass flow rate of LNG required to supply heat equivalent to 1.2046106 kcal/h, which is the heat duty of the working fluid evaporator, is 92.24 kg/h. This means that 92.24 kg/h of natural gas is consumed per hour to generate LNG cold power using propane as the working fluid.

[0039] The selection conditions for the working fluid for application to the closed Rankine cycle using the LNG cold heat according to the present disclosure are as follows.

[0040] First, a working fluid that may operate at a high pressure at the outlet of the pump is preferred. This is related to the critical pressure of the working fluid. The pressure at the outlet of the pump is generally pressurized close to the critical pressure.

[0041] Second, the lower temperature at the outlet of the working fluid condenser, achieved through heat exchange with LNG, the more advantageous it is. This is because the pressure at the outlet of an expansion valve may be lowered and an expansion ratio in the turbine may be increased, thereby obtaining more power. The temperature at the outlet of the working fluid condenser is related to the freezing point of the working fluid. Because the outlet of the working fluid condenser is directly connected to the pump, there is a restriction that the temperature should be maintained above the freezing point of the working fluid.

[0042] Third, the lower temperature at the outlet of the working fluid evaporator, the more advantageous it is. In the case of FIG. 4, when propane is used as the working fluid, the temperature at the outlet of the evaporator is 120 C. In this case, because low pressure (LP) steam should be used to evaporate the working fluid, consumption of the natural gas due to combustion occurs.

[0043] In order to select a working fluid that satisfies the above conditions, Table 5 below summarizes some basic physical properties for several working fluid candidates.

TABLE-US-00005 TABLE 5 Item CO.sub.2 C.sub.2H.sub.6 C.sub.2H.sub.4 Critical pressure (bar) 73.83 48.72 50.40 Freezing point ( C.) 56.57 182.8 169.15 Critical temperature ( C.) 31.06 32.17 9.19

[0044] Among the working fluid candidates shown in Table 5 above, carbon dioxide is advantageous because it has the highest value at 73.83 bar in terms of the critical pressure. In terms of the freezing point, an ethane component is advantageous because it has the lowest value at 182.8 C. However, in this case, because it is lower than the supply temperature of LNG, there is a disadvantage that the cold heat of LNG due to the complete evaporation of LNG may not be fully utilized. Finally, the lower critical temperature of the working fluid when being pressurized close to critical pressure by the pump and then fully evaporated in the working fluid evaporator, the more advantageous it is. In this case, ethylene is the most advantageous because the critical temperature of ethylene is as low as 9.19 C.

[0045] Table 6 below shows the components, temperature and pressure conditions of LNG used in the present disclosure.

TABLE-US-00006 TABLE 6 Component Mole % Nitrogen 0.21 Methane 91.33 Ethane 5.36 Propane 2.14 I-butane 0.46 N-butane 0.48 I-pentane 0.02 Total (%) 100.000 Temperature ( C.) 130 Pressure (MPaG) 7.00 Flow rate (Ton/h) 180

[0046] In order to completely utilize the latent heat of LNG, the supply pressure of LNG is lowered to 0.605 MpaG where it becomes a saturated liquid. Under these conditions, the temperature at which all LNG evaporates is found to be 54.125 C. To completely utilize the cold heat of LNG and ensure that the temperature of the mixed working fluid at the outlet of the condenser differs by only 3 C. from the temperature after the LNG evaporates, the composition of carbon dioxide and ethylene to achieve 51.125 C. is preferably 10 mol % carbon dioxide and 90 mol % ethylene.

[0047] In Table 5, a mixed working fluid containing 90 mol % carbon dioxide and 10 mol % ethane is used in a process shown in FIG. 5 to design the power production process using the LNG cold heat. Here, E3 is a mixed working fluid condenser, which exchanges heat with the LNG, so it is substantially the same heat exchanger as E4.

[0048] Table 7 below intensively shows some physical properties of carbon dioxide and ethane.

TABLE-US-00007 TABLE 7 Component CO.sub.2 C.sub.2H.sub.6 Pc (bar) 73.83 48.72 Melting point ( C.) 56.57 182.8 Critical temperature ( C.) 31.6 32.17 Vapor pressure at 51.125 C. 6.518 5.317

[0049] Table 8 below summarizes the computer simulation results in FIG. 5.

TABLE-US-00008 TABLE 8 Item Result Unit LNG mass flow rate 631.81 kg/h Power of first turbine 15.25 kW Efficiency of first turbine 85 % Outlet pressure of first turbine 16.918 bar Outlet temperature of first turbine 22.538 C. Inlet temperature of first turbine 69.215 C. Power of second turbine 9.96 kW Efficiency of second turbine 85 % Outlet pressure of second turbine 8.627 Bar Outlet temperature of second 30.414 C. turbine Inlet temperature of second turbine 69 C. Working fluid evaporator outlet 69.215 C. temperature Working fluid condenser outlet 51.125 C. temperature Working fluid circulation flow rate 1,000 kg/h Pump power required 2.1030 kW Pump efficiency 85 % Working fluid condenser duty 0.0984 10.sup.6 kcal/h Working fluid evaporator duty 0.0930 10.sup.6 kcal/h Pump outlet pressure 47.67 bar

[0050] As shown in Table 8 above, in order to completely utilize the latent heat of LNG, the temperature at which LNG fully evaporates in an evaporator E4 to become saturated vapor is-54.125 C. Thus, the temperature of the working fluid at the outlet of a condenser E3 is set to 54.125 C. At this time, it is expanded at the outlet of a turbine EX1 or EX2 to reach a pressure at which it becomes saturated liquid. Since the expected melting point (or freezing point) of the mixed working fluid is about 69.193 C., there is a margin of about 15 C. The pressure at the outlet of a pump P1 is pressurized to 67.67 bar, which is 95% of the critical pressure of the mixed working fluid. The temperature at the outlet of a working fluid evaporator E1 and the outlet of a heater E2 between two turbines EX1 and EX2 is set to 69 C. This is determined as a minimum temperature necessary to prevent condensate from forming at the outlet of the first turbine EX1 in FIG. 5. If condensation occurs at the outlet of the first turbine EX1, the amount of power produced is reduced. Since the critical temperature of both components is around 30 C. and the pressure at the outlet of the pump P1 is set to 95% of the critical pressure of two mixed working fluids, the temperature at the outlet of the evaporator E1 may be lower than 30 C. when heated to a saturated vapor state.

[0051] According to Table 8, the net power obtained from cold heat of 1 ton/h of LNG is 36.573 kW. Although this is slightly higher than the net power of 35.768 kW obtained when propane is used as the working fluid, it can be seen that the temperature of working fluid at the outlet of the evaporator is 69.215 C. It can be seen that this is a temperature much lower than 120 C., which is the temperature of the propane working fluid at the outlet of the evaporator. It can be seen that this is a low temperature that is available through the utilization of waste heat in the process. Further, this process is advantageous in that it eliminates the need to consume 92.24 kg/h of natural gas, as compared to the power generation process that utilizes the LNG cold heat with propane as the working fluid.

[0052] Although the present disclosure has been described above with reference to preferred embodiments, it will understood by those skilled in the art that various modifications and changes may be made to the present disclosure without departing from the idea and scope of the present disclosure as set forth in the following claims.

[0053] Accordingly, embodiments disclosed herein are illustrative and not restrictive, and the scope of the present disclosure is not limited by these embodiments. The scope of protection of the present disclosure should be interpreted as defined in the appended claims, and all changes that fall within meets and bounds of the claims, or equivalence of such meets and bounds should be interpreted as being included in the scope of rights of the present disclosure.