WO2019205509A1 - 一种带lng冷能利用功能的整体式中间介质汽化器及发电*** - Google Patents

一种带lng冷能利用功能的整体式中间介质汽化器及发电*** Download PDF

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WO2019205509A1
WO2019205509A1 PCT/CN2018/110469 CN2018110469W WO2019205509A1 WO 2019205509 A1 WO2019205509 A1 WO 2019205509A1 CN 2018110469 W CN2018110469 W CN 2018110469W WO 2019205509 A1 WO2019205509 A1 WO 2019205509A1
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heat exchange
intermediate medium
vaporizer
lng
heat
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PCT/CN2018/110469
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English (en)
French (fr)
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姚寿广
李锦峰
陆政德
江镇宇
杨琦国
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江苏科技大学
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Publication of WO2019205509A1 publication Critical patent/WO2019205509A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G7/00—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for
    • F03G7/04—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for using pressure differences or thermal differences occurring in nature
    • F03G7/05—Ocean thermal energy conversion, i.e. OTEC
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C7/00—Methods or apparatus for discharging liquefied, solidified, or compressed gases from pressure vessels, not covered by another subclass
    • F17C7/02—Discharging liquefied gases
    • F17C7/04—Discharging liquefied gases with change of state, e.g. vaporisation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient

Definitions

  • natural gas is usually stored and transported in the form of LNG, and the natural gas (NG) which raises the temperature of -163 ° C to 10 ° C to 25 ° C before the delivery to the user terminal is performed, and the vaporization process is generally carried out in the LNG vaporizer.
  • LNG contains 830-860 MJ/t of cold capacity
  • the use of high-grade cold energy to build a circulating power generation system is the main way to use LNG cooling capacity on a large scale, and to improve the economic benefits, energy saving, environmental protection, etc. of the LNG energy industry.
  • the aspect has great practical significance.
  • vaporizers commonly used in global LNG receiving stations, such as open-frame vaporizers (ORV), submerged combustion vaporizers (SCV), intermediate heat transfer medium vaporizers (IFV), etc., among which there are many intermediate medium gasifiers.
  • ORV open-frame vaporizers
  • SCV submerged combustion vaporizers
  • IOV intermediate heat transfer medium vaporizers
  • the technical problem to be solved by the present invention is to provide a monolithic intermediate medium vaporizer with LNG cold energy utilization function, and a power generation system based on the above integrated intermediate medium vaporizer.
  • the utility model not only solves the drawback that the traditional integral intermediate medium vaporizer can not utilize the LNG cold energy, but also replaces the condenser, the evaporator, the preheater and the adjustment of the traditional split type power generation system by the integral intermediate medium vaporizer with the LNG cold energy utilization function provided by the invention.
  • Thermostats, etc. constitute an efficient and compact LNG cold energy power generation system, which solves the problem that the traditional split LNG cold energy utilization power generation system cannot be applied to the occasion where the space constraint is high.
  • an integrated intermediate medium vaporizer with LNG cold energy utilization function which is innovative in that it comprises a casing having a heat exchange cavity in the casing, and the replacement The thermal cavity is divided into a front heat exchange zone of the vaporizer and a heat exchange zone at the rear of the vaporizer.
  • the shell is also provided with an LNG heat exchange channel, an intermediate medium heat exchange channel, and a seawater heat exchange for separating the heat exchange cavity.
  • a first partition and a second partition of the passage, and a middle partition separating the intermediate medium heat exchange passage into two sections is further connected between the first partition and the second partition, wherein the middle partition is located at the front of the vaporizer a boundary between the heat exchange zone and the heat exchange zone at the rear of the vaporizer, and the low pressure liquid intermediate medium outlet and the high pressure liquid intermediate medium inlet are respectively located at two sides of the middle partition, and the first partition and the second partition are respectively opened A plurality of through holes are inserted into the through holes, and the second separator is not open at the heat exchange area at the front of the vaporizer.
  • the ratio of the front heat exchange zone of the vaporizer to the heat exchange zone at the rear of the vaporizer is 1:1 to 1:1.5.
  • the through holes on the first spacer and the second spacer are distributed in a shape of a shape, and the through holes in the adjacent two columns are staggered.
  • the heat pipe assembly includes a first heat pipe group located at a front heat exchange zone of the vaporizer and a second heat pipe group located at a heat exchange zone at a rear portion of the vaporizer, wherein the heat pipe in the first heat pipe group is inserted into the first baffle
  • the through hole penetrates through the LNG heat exchange channel and the intermediate medium heat exchange channel
  • the heat pipe in the second heat pipe group is sequentially inserted into the through hole on the first partition, the through hole in the second partition, and penetrates the LNG heat exchange passage, Intermediate medium heat exchange channel and seawater heat exchange channel.
  • the plurality of heat pipes in the second half of the front heat exchange zone of the vaporizer are disposed on the outer wall of the condensation section in the LNG heat exchange channel and are provided with annular fins
  • the second heat pipe group All the heat pipes in the middle medium heat exchange channel are provided with annular fins on the outer wall of the condensation section, and the outer wall of the condensation section in the LNG heat exchange channel depends on the application environment temperature and the user's requirement for the final temperature of the NG output.
  • the working fluid in the heat pipe located in the first half of the LNG inlet adopts methane
  • the working fluid in the heat pipe in the second half adopts ethane
  • the heat pipe of the second heat pipe group uses propane.
  • a temperature-regulating heat exchange coil is disposed at the heat exchange zone of the seawater heat exchange channel at the front heat exchange zone of the vaporizer, and the inlet and outlet of the NG temperature-regulating heat exchanger coil extend outside the shell of the integral intermediate medium vaporizer, and The inlet is connected to the NG outlet of the vaporizer LNG heat exchange passage.
  • a power generation system based on the above-mentioned integrated intermediate medium vaporizer which is innovative in that it comprises an integral intermediate medium vaporizer having an LNG heat exchange passage, an intermediate medium heat exchange passage, and a seawater exchange in the integral intermediate medium vaporizer.
  • the hot channel has a LNG inlet and an NG outlet connected to the LNG heat exchange passage on both sides of the integral intermediate medium vaporizer, a low pressure gaseous intermediate medium inlet connected to the intermediate medium heat exchange passage, and a high pressure gaseous intermediate medium outlet, and
  • the seawater inlet and the seawater outlet connected to the seawater heat exchange passage have a low-pressure liquid intermediate medium outlet and a high-pressure liquid intermediate medium inlet connected to the intermediate medium heat exchange passage in the middle of the integral intermediate medium vaporizer, and are connected at the LNG inlet.
  • a working pump A a sea water pump is connected at the seawater inlet, and the working and circulation of the intermediate medium is realized by a turbine between the low-pressure gaseous intermediate medium inlet and the high-pressure gaseous intermediate medium outlet, and the low-pressure liquid intermediate medium outlet and the high-pressure liquid state Intermediate medium is realized between the intermediate medium inlets through a working fluid pump B Supercharged and circulated.
  • the LNG inlet, the low-pressure gaseous intermediate medium inlet, and the seawater outlet are all located on the same side of the integrated intermediate medium vaporizer, and the NG outlet, the high-pressure gaseous intermediate medium outlet, and the seawater inlet are located on the other side of the integrated intermediate medium vaporizer.
  • the invention has the advantages that in the invention, the intermediate medium after the turbine power generation is condensed and liquefied by using a large amount of cold energy released during the vaporization of the LNG, and then pressurized into the vaporizer by the working medium pump to exchange heat with the seawater for heat absorption and vaporization.
  • LNG vaporization cold energy Rankine cycle power generation system not only overcomes the original integrated intermediate medium LNG vaporizer can not use LNG vaporization cold energy, resulting in energy waste and a large amount of low temperature seawater directly discharged into the sea.
  • three different heat pipe working fluids are used for the two heat pipe groups according to the working temperature, thereby ensuring that the two heat pipe groups work normally in the heat exchange process and the ice heat blocking channels do not appear ice blocking.
  • the NG from the outlet of the liquefier LNG channel NG can be exchanged with the seawater in the seawater heat exchange passage, so that the NG can further heat up to a set temperature to facilitate subsequent use. .
  • the LNG inlet, the low-pressure gaseous intermediate medium inlet, and the seawater outlet are all located on the same side of the monolithic intermediate medium vaporizer, and the NG outlet, the high-pressure gaseous intermediate medium outlet, and the seawater inlet are located on the other side of the integral intermediate medium vaporizer, thereby realizing The downstream flow of LNG and intermediate medium in the heat exchange channel, and the seawater and the intermediate medium flow in a countercurrent flow, thereby ensuring that the three media can sufficiently heat exchange and achieve a predetermined target.
  • FIG. 1 is a schematic view of a monolithic intermediate medium vaporizer with LNG cold energy utilization function in the present invention.
  • FIG. 2 is a schematic structural view of a monolithic intermediate medium vaporizer with LNG cold energy utilization function according to the present invention.
  • FIG 3 is a schematic view of a first separator in a monolithic intermediate medium vaporizer with LNG cold energy utilization function according to the present invention.
  • FIG. 4 is a schematic view of a second separator in a monolithic intermediate medium vaporizer with LNG cold energy utilization function of the present invention.
  • Figure 5 is a schematic diagram of a cold energy power generation system based on a monolithic intermediate medium vaporizer with LNG cold energy utilization function in the present invention.
  • the integrated intermediate medium vaporizer 1 with LNG cold energy utilization function of the present embodiment includes a casing 2 which is designed as a semi-cylindrical rectangular shape for the inlet and outlet end faces of the working fluid on both sides.
  • the assembly has a heat exchange cavity in the casing 2, and the heat exchange cavity is divided into a heat exchange zone at the front of the vaporizer and a heat exchange zone at the rear of the vaporizer, a heat exchange zone at the front of the vaporizer and a heat exchange zone at the rear of the vaporizer.
  • the ratio is between 1:1 and 1:1.5, and the housing 2 is further provided with a LNG heat exchange passage 22, an intermediate medium heat exchange passage 23, and a seawater heat exchange passage 24 that divide the heat exchange cavity into a sequence.
  • a partition plate 20 and a second partition plate 19, and the first partition plate 20, the second partition plate 19 and the casing 2 are fixed by welding, between the first partition plate 20 and the second partition plate 19
  • a middle partition 17 which divides the intermediate medium heat exchange passage 23 into two sections, and the middle partition 17 is fixedly connected to the first partition 20 and the second partition 19 by welding, and the middle partition 17 is located The junction between the front heat exchange zone of the vaporizer and the heat exchange zone at the rear of the vaporizer.
  • an LNG inlet 12 On both sides of the casing of the integrated intermediate medium vaporizer 1, there are an LNG inlet 12, an NG outlet 4 communicating with the LNG heat exchange passage 22, a low-pressure gaseous intermediate medium inlet 11 communicating with the intermediate medium heat exchange passage 23, and a high-pressure gas state.
  • the intermediate medium outlet 18, the high pressure liquid intermediate medium inlet 16, and the low pressure liquid intermediate medium outlet 18 and the high pressure liquid intermediate medium inlet 16 are respectively located on both sides of the intermediate partition 17.
  • the LNG inlet 12, the low-pressure gaseous intermediate medium inlet 11 and the seawater outlet 10 are all located on the same side of the casing 2 of the monolithic intermediate medium vaporizer 1, and the NG outlet 4, the high-pressure gaseous intermediate medium outlet 5, and the seawater inlet 6 are located in the integral intermediate medium vaporizer.
  • the other side of the casing 2 of the first embodiment adopts such a design to realize the downstream flow of the LNG and the intermediate medium in the heat exchange passage, and the seawater and the intermediate medium flow in a countercurrent flow, thereby ensuring that the three mediums can sufficiently exchange heat and Achieve the intended goal.
  • the specific structure of the first partition 20 is as shown in FIG. 3, and the specific structure of the second partition 19 is as shown in FIG.
  • a plurality of through holes 21 are defined in the partition plate 20 and the second partition plate 19.
  • the through holes 21 in the first partition plate 20 and the second partition plate 19 are arranged in a shape of a shape, and the through holes in the adjacent two columns are arranged.
  • the staggered distribution, and the second partition 19 is not open at the front heat exchange zone of the vaporizer.
  • a heat pipe assembly is inserted in the through hole 21, and the heat pipe assembly includes a first heat pipe group located at a heat exchange area at a front portion of the vaporizer and a second heat pipe group located at a heat exchange area at a rear portion of the vaporizer, wherein Each of the first heat pipes 15 constituting the first heat pipe group is inserted into the through hole 21 of the first separator 20 and penetrates the LNG heat exchange passage 22 and the intermediate medium heat exchange passage 23 to form a second heat pipe 3 in the second heat pipe group.
  • the through holes 21 in the first partition plate 20 and the through holes 21 in the second partition plate 19 are sequentially inserted into the through holes 21 and penetrate the LNG heat exchange passage 22, the intermediate medium heat exchange passage 23 and the seawater heat exchange passage 24.
  • the outer wall of the condensation section of the LNG heat exchange passage 22 near the second half of the front heat exchange zone of the vaporizer is provided with annular fins, and each of the second heat pipe groups
  • the second heat pipe 3 is provided with annular fins on the outer wall of the condensation section of the intermediate medium heat exchange passage 23, and each second heat pipe 3 in the second heat pipe group is located on the outer wall of the condensation section of the LNG heat exchange passage 22, depending on the specific application.
  • the ambient temperature and the user's requirements for the output NG temperature determine whether or not the annular fins are fitted.
  • the heat pipe of the first heat pipe group has a large amount of released cold when the LNG is vaporized.
  • the working medium in the first heat pipe 15 located in the first half of the LNG inlet 12 adopts methane, and the second half in the second half.
  • the working medium in one heat pipe 15 uses ethane
  • the working medium in each second heat pipe 3 of the second heat pipe group uses propane. Different working fluids are used in each heat pipe to ensure that each heat pipe works normally during heat exchange and there is no ice blockage in each channel.
  • the present embodiment is based on the power generation system of the integral intermediate medium vaporizer, as shown in FIG. 5, comprising an integral intermediate medium vaporizer 1, a sea water pump 7, a working fluid pump 8, and a turbine 9, in the seawater of the integrated intermediate medium vaporizer 1.
  • a sea water pump 7 is connected to the inlet 6 , and the intermediate medium is circulated through a turbine 9 between the low-pressure gaseous intermediate medium inlet 11 and the high-pressure gaseous intermediate medium outlet 5 , between the low-pressure liquid intermediate medium outlet 18 and the high-pressure liquid intermediate medium inlet 16 .
  • the circulation of the intermediate medium is achieved by a working fluid pump 8.
  • a temperature-regulating heat exchange coil 14 is further disposed at the heat exchange passage of the seawater heat exchange passage 24 at the front heat exchange zone of the vaporizer, and the inlet and outlet of the temperature-regulating heat exchange coil 14 extend out of the casing 2 of the integral intermediate medium vaporizer 1
  • the inlet end of the temperature-regulating heat exchange coil 14 is connected to the NG outlet 4 through an NG temperature-regulating liquid inlet pipe 25, and the other end of the temperature-regulating heat-exchange coil 14 is connected to an NG temperature-regulating liquid outlet pipe.
  • the integral intermediate medium vaporizer 1 adopts a step vaporization technology, and the intermediate medium propane is used as an intermediate refrigerant, so as to avoid ice blockage caused by the low temperature of the cooling medium, and ensure that the three mediums can fully perform heat exchange, achieving -162 ° C
  • the LNG endothermic reaches the set temperature NG state, and the flow direction of LNG and the two heat exchange mediums in the respective heat exchange chamber channels is required: propane and LNG are forward flow, sea water and LNG are reverse flow; and the first group of heat pipes According to the temperature range of LNG, the medium working medium adopts methane in the first half of the inlet, ethane in the second half, and propane in the second group.
  • LNG heat exchange process LNG in the initial state (state parameter: 1.5 MPa, -162 ° C or so) flows from the LNG inlet 12 on the right side of the casing 2, and the LNG flows through the first heat pipe group 15 in the front heat exchange zone of the carburetor, Fully absorb the heat released by propane; change to the gas-liquid two-phase state in the middle part of the heat exchange zone in the front part of the vaporizer; change to the superheated NG state when it flows to the middle of the vaporizer; at this time, the NG passes through the rear heat exchange zone of the vaporizer
  • the heat absorbed by the seawater again becomes a gaseous NG of 5 to 10 ° C; the gaseous NG flows into the temperature-regulating heat exchange coil 14 through the NG temperature-adjusting liquid inlet pipe 25, and further absorbs heat to reach 10 to 15 ° C, and finally heats up the NG.
  • the NG temperature regulating liquid outlet pipe flows out for the user to use.
  • Propane heat exchange process low temperature and low pressure gaseous propane flowing through the turbine 9 (status parameter: 0.11 MPa, about -40 ° C), flowing from the low pressure gaseous intermediate medium inlet 11 on the right side of the casing 2 into the first half of the intermediate medium heat exchange passage 23
  • propane flows through the alternately arranged first heat pipe group, which acts as an intermediate heat medium to transfer heat absorbed from the seawater so that the LNG absorbs heat to a saturated NG state while absorbing from the LNG
  • the amount of cold released is changed to a liquid state (state parameter: 0.1 MPa, -42 ° C) at the outlet of the low-pressure liquid intermediate medium at the front of the monolithic intermediate medium vaporizer 1 into the working fluid pump 8, after which the propane is passed through the working fluid pump.
  • Seawater heat exchange process seawater is pumped from the seawater inlet 6 into the seawater heat exchange channel 24 of the integrated intermediate medium vaporizer 1 by seawater pump 7.
  • seawater is supplied to the intermediate medium for heat exchange.
  • the high-pressure low-temperature liquid propane of the hot aisle 23 and the NG of the 22 in the LNG heat exchange passage cause the inflowing liquid propane to vaporize and the NG temperature rises to 5 to 10 ° C, and then flows through the temperature-regulating heat exchange coil 14 and exchanges with the temperature adjustment.
  • the NG in the heat coil 14 exchanges heat, because the seawater in the channel is reversely flowing with LNG and propane, so at the evaporation end of the second group of heat pipes, the energy supplied by the seawater can satisfy the vaporization of the rear high pressure propane, and The heat absorption of the LNG was brought to a set state, and the seawater as an exothermic medium was lowered from 20 ° C to 14 to 15 ° C throughout the process.
  • the monolithic intermediate medium vaporizer 1 replaces the preheater, evaporator and condenser in the original low temperature Rankine cycle to form a low temperature Rankine cycle power generation system composed of the vaporizer, the liquid pump and the steam turbine, which not only overcomes the original whole
  • the intermediate medium LNG vaporizer can not use LNG vaporization cold energy, resulting in waste of energy and a large amount of low-temperature seawater directly discharged into the sea, which causes the marine ecological impact.
  • this new integrated vaporizer replaces the original LNG cold energy utilization in the low temperature Rankine cycle.
  • the preheater, the evaporator, the condenser and the thermostat constitute an LNG cold energy power generation system, which can not only efficiently utilize the cold energy released by the LNG vaporization, but also compares with the conventional split type cold energy power generation system with LNG vaporization.
  • the system has a small footprint and a small footprint.

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Abstract

一种带LNG冷能利用功能的整体式中间介质汽化器（1）和基于整体式中间介质汽化器的发电***，汽化器（1）包括一壳体（2），在壳体（2）内具有一换热空腔，该换热空腔分为汽化器前部换热区与汽化器后部换热区，所述壳体（2）内还设置有将换热空腔分隔为依次分布的LNG换热通道（22）、中间介质换热通道（23）、海水换热通道（24）的第一隔板（20）、第二隔板（19），在第一隔板（20）与第二隔板（19）之间还连接有一将中间介质换热通道（23）分隔为两段的中隔板（17），第一隔板（20）与第二隔板（19）上均开有若干通孔，在通孔内***有热管组件，其利用LNG汽化冷能发电的同时，通过该整体式中间介质汽化器的使用，大大节省了设备投入，减少了占地空间，实现了***高效节能减排的目标。

Description

一种带LNG冷能利用功能的整体式中间介质汽化器及发电*** 技术领域
本发明涉及液化天然气冷能利用领域，特别涉及一种带LNG冷能利用功能的整体式中间介质汽化器，还涉及一种基于上述整体式中间介质汽化器的发电***。
背景技术
我国经济飞速发展，对能源的需求日益剧增，但由于对于煤、石油等能源的过度使用已对环境造成巨大负担。天然气作为一种洁净能源，在此背景之下备受青睐，并得到广泛的开发和利用。
目前天然气通常是以LNG的形式进行储运,在输送到用户终端前实现将-163℃左右温度的LNG提高到10℃～25℃的天然气(NG)，而汽化的过程一般在LNG汽化器中进行。由于液化天然气蕴含830～860MJ/t的冷量，利用高品位的冷能构建循环发电***是大规模利用LNG冷量的主要方式，对于提高LNG能源产业的经济效益、节能减排及环境保护等方面具有重大的现实意义。
目前，全球LNG接收站常用的汽化器有三种类型，如开架式汽化器(ORV)、浸没燃烧式汽化器(SCV)、带中间传热介质汽化器(IFV)等，其中带中间介质气化器又是很多接收站的首选。
但目前使用最为广泛的整体式中间介质汽化器(IFV)大多采用海水汽化LNG，虽然汽化效率高、结构紧凑运行稳定，但为对海洋的生态污染降至最低，往往采用大流量的海水使海水进出口温差很小， 由此需要水泵强制循环，耗功较大。最为垢病的是大量LNG汽化冷能无法直接利用。为利用LNG汽化冷能，只能将整体式中间介质汽化器(IFV)拆分为预热器、蒸发器、冷凝器及调温器等构成分置式的LNG冷能发电***，不仅进一步增大***功耗，而且带来所需占地面积及空间大的问题。虽然陆地接收站这一问题不突出，但对船舶及海上FSRU平台等这些对占地面积及空间有严格约束的LNG汽化场合，传统通过分置式中间介质汽化器形成的LNG冷能发电***就难以甚至无法使用。
发明内容
本发明要解决的技术问题是提供一种带LNG冷能利用功能的整体式中间介质汽化器，以及一种基于上述整体式中间介质汽化器的发电***。既解决传统整体式中间介质汽化器无法利用LNG冷能的弊端，又由本发明提供的带LNG冷能利用功能的整体中间介质汽化器取代传统分置式发电***的冷凝器、蒸发器、预热器及调温器等，构成高效紧凑的LNG冷能发电***，解决传统分置式LNG冷能利用发电***无法应用于占地空间约束要求高的场合的难题。
为解决上述技术问题，本发明的技术方案为：一种带LNG冷能利用功能的整体式中间介质汽化器，其创新点在于：包括一壳体，在壳体内具有一换热空腔，该换热空腔分为汽化器前部换热区与汽化器后部换热区，所述壳体内还设置有将换热空腔分隔为依次分布的LNG换热通道、中间介质换热通道、海水换热通道的第一隔板、第二隔板，在第一隔板与第二隔板之间还连接有一将中间介质换热通道分隔为 两段的中隔板，该中隔板位于汽化器前部换热区与汽化器后部换热区的交界处，且低压液态中间介质出口、高压液态中间介质进口分别位于中隔板的两侧，所述第一隔板与第二隔板上均开有若干通孔，在通孔内***有热管组件，且第二隔板上位于汽化器前部换热区处不开通孔。
进一步的，所述汽化器前部换热区与汽化器后部换热区的比例为1:1～1:1.5。
进一步的，所述第一隔板与第二隔板上的通孔呈品字形阵列分布，且相邻两纵列中的通孔交错分布。
进一步的，所述热管组件包括位于汽化器前部换热区的第一热管组以及位于汽化器后部换热区的第二热管组，其中，第一热管组中的热管***第一隔板上的通孔内并贯穿LNG换热通道与中间介质换热通道，第二热管组中的热管依次***第一隔板上的通孔、第二隔板上的通孔内并贯穿LNG换热通道、中间介质换热通道与海水换热通道。
进一步的，在第一热管组中的热管中，汽化器前部换热区后半段的数排热管位于LNG换热通道中的冷凝段外壁上均套装有环形翅片，所述第二热管组中的所有热管位于中间介质换热通道中的冷凝段外壁上均套装有环形翅片，而位于LNG换热通道中的冷凝段外壁上视应用环境温度及用户对NG输出终温的要求决定是否套装环形翅片
进一步的，所述第一热管组的热管中，位于靠近LNG进口的前半段中的热管中的工质采用甲烷，后半段中的热管中的工质采用乙烷，第二热管组的热管中的工质采用丙烷。
进一步的，在海水换热通道位于汽化器前部换热区处还设置有一调温换热盘管，该NG调温换热盘管的进出口均伸出整体式中间介质汽化器的壳体外，且其进口与汽化器LNG换热通道NG出口连接。
一种基于上述整体式中间介质汽化器的发电***，其创新点在于：包括一整体式中间介质汽化器，在整体式中间介质汽化器内具有一LNG换热通道、一中间介质换热通道、一海水换热通道，同时在整体式中间介质汽化器的两侧具有与LNG换热通道相连通的LNG进口、NG出口，与中间介质换热通道相连通的低压气态中间介质进口、高压气态中间介质出口，与海水换热通道相连通的海水进口、海水出口，在整体式中间介质汽化器的中部位置还具有与中间介质换热通道相连通的低压液态中间介质出口、高压液态中间介质进口，在LNG进口处连接有一工质泵A，在海水进口处连接有一海水泵，所述低压气态中间介质进口与高压气态中间介质出口之间通过一透平实现中间介质的做功与流通，低压液态中间介质出口与高压液态中间介质进口之间通过一工质泵B实现中间介质的增压与流通。
进一步的，所述LNG进口、低压气态中间介质进口、海水出口均位于整体式中间介质汽化器的同一侧，NG出口、高压气态中间介质出口、海水进口位于整体式中间介质汽化器的另一侧。
本发明的优点在于：在本发明中，经过透平发电后的中间介质利用LNG汽化时释放的大量冷能发生冷凝液化，之后经工质泵加压进入汽化器中与海水换热进行吸热汽化，实现连续循环发电，与现有的LNG汽化冷能朗肯循环发电***相比，不仅克服了原整体式中间介质 LNG汽化器无法利用LNG汽化冷能，导致能源浪费及大量低温海水直接排入海中造成对海洋生态影响的弊端，而且将此新型整体式汽化器取代原LNG冷能利用低温朗肯循环中的预热器、蒸发器、冷凝器及调温器等构成LNG冷能发电***，不仅能将LNG汽化释放的冷能进行高效利用，而且与传统分置式带LNG汽化的冷能发电系系相比，***紧凑占用空间小。
在本发明中，对于两热管组根据工作温度分段采用三种不同的热管工质，从而保证两热管组在换热过程中正常工作且各换热通道不会出现冰堵。
通过在第一热管组以及第二热管组中的热管冷凝段外壁上加装环形翅片，从而能够强化热管外侧气态工质传热，有效的降低传热热阻，保证整个***的高效运行。
通过NG调温换热盘管、可使从汽化器LNG通道NG出口出来的NG与海水换热通道内的海水再进行换热，使得NG能够进一步吸热升温至设定温度，以方便后续的使用。
采用LNG进口、低压气态中间介质进口、海水出口均位于整体式中间介质汽化器的同一侧，NG出口、高压气态中间介质出口、海水进口位于整体式中间介质汽化器的另一侧的设计，即实现了换热通道内LNG与中间介质的顺流流动，而海水与中间介质为逆流流动，从而保证了三种介质可以充分换热并且实现预定目标。
附图说明
下面结合附图和具体实施方式对本发明作进一步详细的说明。
图1为本发明中带LNG冷能利用功能的整体式中间介质汽化器的示意图。
图2为本发明带LNG冷能利用功能的整体式中间介质汽化器的结构示意图。
图3为本发明中带LNG冷能利用功能的整体式中间介质汽化器中第一隔板的示意图。
图4为本发明带LNG冷能利用功能的整体式中间介质汽化器中第二隔板的示意图。
图5为本发明中基于带LNG冷能利用功能的整体式中间介质汽化器的冷能发电***示意图。
具体实施方式
下面的实施例可以使本专业的技术人员更全面地理解本发明，但并不因此将本发明限制在所述的实施例范围之中。
实施例
本实施例带LNG冷能利用功能的整体式中间介质汽化器1，如图1和2所示，包括一壳体2，该壳体2为两侧工质进出口端面设计为半圆柱型的长方形组合体，在壳体2内具有一换热空腔，该换热空腔分为汽化器前部换热区与汽化器后部换热区，汽化器前部换热区与汽化器后部换热区的比例在1：1～1:1.5之间，在壳体2内还设置有将换热空腔分隔为依次分布的LNG换热通道22、中间介质换热通道23、海水换热通道24的第一隔板20、第二隔板19，且第一隔板20、第二隔板19与壳体2之间均采用焊接的固定方式，在第一隔板20与第 二隔板19之间还连接有一将中间介质换热通道23分隔为两段的中隔板17，且中隔板17采用焊接的方式与第一隔板20、第二隔板19固定连接，该中隔板17位于汽化器前部换热区与汽化器后部换热区的交界处。
在整体式中间介质汽化器1的壳体的两侧具有与LNG换热通道22相连通的LNG进口12、NG出口4，与中间介质换热通道23相连通的低压气态中间介质进口11、高压气态中间介质出口5，与海水换热通道24相连通的海水进口6、海水出口10，在整体式中间介质汽化器1的壳体2的中部位置还具有与中间介质换热通道23相连通的低压液态中间介质出口18、高压液态中间介质进口16，且低压液态中间介质出口18、高压液态中间介质进口16分别位于中隔板17的两侧。
LNG进口12、低压气态中间介质进口11、海水出口10均位于整体式中间介质汽化器1的壳体2的同一侧，NG出口4、高压气态中间介质出口5、海水进口6位于整体式中间介质汽化器1的壳体2的另一侧，采用这样的设计即实现了换热通道内LNG与中间介质的顺流流动，而海水与中间介质为逆流流动，从而保证了三种介质可以充分换热并且实现预定目标。
本实施例中带LNG冷能利用功能的整体式中间介质汽化器中，第一隔板20的具体结构，如图3所示，第二隔板19的具体结构，如图4所示，第一隔板20与第二隔板19上均开有若干通孔21，第一隔板20与第二隔板19上的通孔21呈品字形阵列分布，且相邻两纵列中 的通孔交错分布，且第二隔板19上位于汽化器前部换热区处不开通孔。
如图1和图2所示，在通孔21内***有热管组件，热管组件包括位于汽化器前部换热区的第一热管组以及位于汽化器后部换热区的第二热管组，其中，组成第一热管组中的各个第一热管15***第一隔板20上的通孔21内并贯穿LNG换热通道22与中间介质换热通道23，组成第二热管组中的第二热管3依次***第一隔板20上的通孔21、第二隔板19上的通孔21内并贯穿LNG换热通道22、中间介质换热通道23与海水换热通道24。
在第一热管组中的第一热管15中，靠近汽化器前部换热区后半段的位于LNG换热通道22的冷凝段外壁上均套装有环形翅片，在第二热管组中的各个第二热管3位于中间介质换热通道23的冷凝段外壁上均套装有环形翅片，而第二热管组中的各个第二热管3位于LNG换热通道22的的冷凝段外壁上视具体应用环境温度及用户对输出NG温度的要求决定是否套装环形翅片。通过在第一热管组以及第二热管组中的热管冷凝段外壁上加装环形翅片，从而能够强化热管外侧气态工质传热，有效的降低传热热阻，保证整个***的高效运行。
第一热管组的热管，由于LNG汽化时释放冷量大，随着LNG温度的变化，位于靠近LNG进口12的前半段中的第一热管15中的工质采用甲烷，后半段中的第一热管15中的工质采用乙烷，第二热管组的各个第二热管3中的工质采用丙烷。对于各个热管中采用不同的工质，从而保证各个热管在换热过程中正常工作且各通道不会出现冰 堵。
本实施例基于此整体式中间介质汽化器的发电***，如图5所示，包括整体式中间介质汽化器1、海水泵7、工质泵8和透平9，在整体式中间介质汽化器1的海水进口6处连接有一海水泵7，低压气态中间介质进口11与高压气态中间介质出口5之间通过一透平9实现中间介质的流通，低压液态中间介质出口18与高压液态中间介质进口16之间通过一工质泵8实现中间介质的流通。
在海水换热通道24位于汽化器前部换热区处还设置有一调温换热盘管14，该调温换热盘管14的进出口均伸出整体式中间介质汽化器的1的壳体2外，且调温换热盘管14的进口端通过一NG调温进液管道25与NG出口4相连，调温换热盘管14的另一端出口连接有一NG调温出液管道。通过调温换热盘管14、NG调温进液管道25及与NG出口4之间的配合，可使NG出口4出来的NG与海水换热通道内的海水进行换热升温，以方便后续的使用。
工作原理：在本实施例中，中间介质以丙烷为例作进一步的说明：
本发明专利中整体式中间介质汽化器1采用梯级汽化技术，中间介质丙烷作为中间冷媒，为避免冷却介质因温度过低而导致冰堵，且保证三种介质能够充分进行换热，实现-162℃的LNG吸热达到设定温度的NG状态，要求LNG与两种换热介质在各自换热腔通道中流向为:丙烷与LNG为顺向流动，海水与LNG为逆向流动；且第一组热管中工质根据LNG温度变化范围，在自进口的前半段热采用甲烷，其后半段采用乙烷，第二组热管中工质采用丙烷。
以单级为例：
LNG换热流程：初始状态的LNG(状态参数：1.5MPa，-162℃左右)从壳体2的右侧的LNG进口12流入，在汽化器前部换热区LNG流过第一热管组15，充分吸收丙烷释放的热量；在汽化器前部换热区的中段位置变为气液两相状态；待其流至汽化器中部位置时变为过热NG状态；此时的NG经过汽化器后部换热区，再次吸收海水的热量变为5～10℃的气态NG；气态NG经NG调温进液管道25流入调温换热盘管14中，进一步吸热达到10～15℃，最终升温后的NG从NG调温出液管道流出，供用户使用。
丙烷换热流程:经透平9流出的低温低压的气态丙烷(状态参数：0.11MPa，-40℃左右)，从壳体2右侧低压气态中间介质进口11流入中间介质换热通道23的前半段，在整体式中间介质汽化器1汽化器前部换热区丙烷流过交替排列的第一热管组，其作为中间热媒传递从海水吸收的热量使得LNG吸热达到饱和NG状态，同时吸收从LNG释放的冷量，在整体式中间介质汽化器1前部低压液态中间介质出口18处丙烷变为液态(状态参数：0.1MPa，-42℃左右)进入工质泵8中，之后丙烷经由工质泵8加压后变为低温高压的液态(状态参数：0.73MPa，-42℃左右)从整体式中间介质汽化器1汽化器后部换热区的高压液态中间介质进口16流入整体式中间介质汽化器1的中间介质换热通道23内，在整体式中间介质汽化器1汽化器后部换热区的LNG换热通道22、中间介质换热通道23及海水换热通道24中仅设置一组贯通的第二热管3，海水中的热量通过第二热管3使刚流入 的液态丙烷汽化为过热状态，同时使饱和状态NG吸热达到过热状态，此时高温高压的气态丙烷(状态参数：0.73MPa，15℃)从壳体2左侧的高压气态中间介质出口5流出，经由透平9做功带动发电机工作产生电能，此时透平9膨胀机可输出的机械功为13330KJ/h，在整个换热过程中，通过调节进入中间介质换热通道23中丙烷的流量，并匹配LNG汽化量，可实现实时工况的调节。
海水换热流程:海水经海水泵7从海水进口6压入整体式中间介质汽化器1的海水换热通道24中，首先，在汽化器后部换热区内，海水将热量提供给流入中间介质换热通道23的高压低温液态丙烷以及LNG换热通道里22的NG，使得流入的液态丙烷汽化以及NG温度升高到5～10℃，之后流经调温换热盘管14并与调温换热盘管14中的NG进行换热，因为通道中的海水与LNG、丙烷为逆向流动，因而在第二组热管的蒸发端处，海水提供的能量可以满足后部高压丙烷的汽化，并可使LNG吸热升温达到设定状态，整个过程中作为放热介质的海水从20℃降至14～15℃。
将此整体式中间介质汽化器1取代原低温朗肯循环中的预热器、蒸发器及冷凝器，形成由此汽化器、液体泵及汽轮机所构成的低温朗肯循环发电***，不仅克服了原整体式中间介质LNG汽化器无法利用LNG汽化冷能，导致能源浪费及大量低温海水直接排入海中造成对海洋生态影响的弊端，而且将此新型整体式汽化器取代原LNG冷能利用低温朗肯循环中的预热器、蒸发器、冷凝器及调温器等构成LNG冷能发电***，不仅能将LNG汽化释放的冷能进行高效利用，而且与传统 分置式带LNG汽化的冷能发电系系相比，***紧凑占用空间小。本行业的技术人员应该了解，本发明不受上述实施例的限制，上述实施例和说明书中描述的只是说明本发明的原理，在不脱离本发明精神和范围的前提下，本发明还会有各种变化和改进，这些变化和改进都落入要求保护的本发明范围内。本发明要求保护范围由所附的权利要求书及其等效物界定。

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  1. 一种带LNG冷能利用功能的整体式中间介质汽化器，其特征在于：包括一壳体，在壳体内具有一换热空腔，该换热空腔分为汽化器前部换热区与汽化器后部换热区，所述壳体内还设置有将换热空腔分隔为依次分布的LNG换热通道、中间介质换热通道、海水换热通道的第一隔板、第二隔板，在第一隔板与第二隔板之间还连接有一将中间介质换热通道分隔为两段的中隔板，该中隔板位于汽化器前部换热区与汽化器后部换热区的交界处，且低压液态中间介质出口、高压液态中间介质进口分别位于中隔板的两侧，所述第一隔板与第二隔板上均开有若干通孔，在通孔内***有热管组件，且第二隔板上位于汽化器前部换热区处不开通孔。
  2. 根据权利要求1所述的带LNG冷能利用功能的整体式中间介质汽化器，其特征在于：所述汽化器前部换热区与汽化器后部换热区的比例为1:1～1:1.5。
  3. 根据权利要求1所述的带LNG冷能利用功能的整体式中间介质汽化器，其特征在于：所述第一隔板与第二隔板上的通孔呈品字形阵列分布，且相邻两纵列中的通孔交错分布。
  4. 根据权利要求1所述的带LNG冷能利用功能的整体式中间介质汽化器，其特征在于：所述热管组件包括位于汽化器前部换热区的第一热管组以及位于汽化器后部换热区的第二热管组，其中，第一热管组中的热管***第一隔板上的通孔内并贯穿LNG换热通道与中间介质换热通道，第二热管组中的热管依次***第一隔板上 的通孔、第二隔板上的通孔内并贯穿LNG换热通道、中间介质换热通道与海水换热通道。
  5. 根据权利要求4所述的带LNG冷能利用功能的整体式中间介质汽化器，其特征在于：在第一热管组中的热管中，汽化器前部换热区后半段的数排热管位于LNG换热通道中的冷凝段外壁上均套装有环形翅片，所述第二热管组中的所有热管位于中间介质换热通道中的冷凝段外壁上均套装有环形翅片，而位于LNG换热通道中的冷凝段外壁上视应用环境温度及用户对NG输出终温的要求决定是否套装环形翅片。
  6. 根据权利要求4所述的带LNG冷能利用功能的整体式中间介质汽化器，其特征在于：所述第一热管组的热管中，位于靠近LNG进口的前半段中的热管中的工质采用甲烷，后半段中的热管中的工质采用乙烷，第二热管组的热管中的工质采用丙烷。
  7. 根据权利要求1所述的带LNG冷能利用功能的整体式中间介质汽化器，其特征在于：在海水换热通道位于汽化器前部换热区处还设置有一调温换热盘管，该NG调温换热盘管的进出口均伸出整体式中间介质汽化器的壳体外，且其进口与汽化器LNG换热通道NG出口连接。
  8. 一种基于权利要求1所述的整体式中间介质汽化器的发电***，其特征在于：包括一整体式中间介质汽化器，在整体式中间介质汽化器内具有一LNG换热通道、一中间介质换热通道、一海水换热通道，同时在整体式中间介质汽化器的两侧具有与LNG换热通 道相连通的LNG进口、NG出口，与中间介质换热通道相连通的低压气态中间介质进口、高压气态中间介质出口，与海水换热通道相连通的海水进口、海水出口，在整体式中间介质汽化器的中部位置还具有与中间介质换热通道相连通的低压液态中间介质出口、高压液态中间介质进口，在LNG进口处连接有一工质泵A，在海水进口处连接有一海水泵，所述低压气态中间介质进口与高压气态中间介质出口之间通过一透平实现中间介质的做功与流通，低压液态中间介质出口与高压液态中间介质进口之间通过一工质泵B实现中间介质的增压与流通。
  9. 根据权利要求8所述的发电***，其特征在于：所述LNG进口、低压气态中间介质进口、海水出口均位于整体式中间介质汽化器的同一侧，NG出口、高压气态中间介质出口、海水进口位于整体式中间介质汽化器的另一侧。
PCT/CN2018/110469 2018-04-23 2018-10-16 一种带lng冷能利用功能的整体式中间介质汽化器及发电*** WO2019205509A1 (zh)

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