US20120067549A1 - Heat recovery apparatus - Google Patents

Heat recovery apparatus Download PDF

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Publication number
US20120067549A1
US20120067549A1 US13/321,151 US201013321151A US2012067549A1 US 20120067549 A1 US20120067549 A1 US 20120067549A1 US 201013321151 A US201013321151 A US 201013321151A US 2012067549 A1 US2012067549 A1 US 2012067549A1
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Prior art keywords
heat
previous
conveyor
generator
heat generator
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English (en)
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Gabriele Comodi
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S TRA G I E Srl
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Assigned to S.TRA.TE.G.I.E. S.R.L. reassignment S.TRA.TE.G.I.E. S.R.L. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: COMODI, GABRIELE
Publication of US20120067549A1 publication Critical patent/US20120067549A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/24—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers
    • F24H1/26—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body
    • F24H1/28—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes
    • F24H1/285—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes with the fire tubes arranged alongside the combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/0005—Details for water heaters
    • F24H9/001—Guiding means
    • F24H9/0026—Guiding means in combustion gas channels
    • F24H9/0031—Guiding means in combustion gas channels with means for changing or adapting the path of the flue gas
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0017—Flooded core heat exchangers
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators

Definitions

  • the present invention refers to an apparatus for recovering thermal energy from the exhaust fumes and gases of heat engines and from the cooling and ventilation air and/or any of the components or auxiliary circuits of the same plants, or of other plants.
  • the invention refers to heat generators adapted to serve as heat recovery apparatuses.
  • said heat generators are fire-tube apparatuses.
  • the invention is especially useful to realize electrical and thermal energy cogeneration plants, particularly in the micro cogeneration sector.
  • Cogeneration is essentially based on using the heat generated by the electricity production phase of thermoelectric generators; such “residual” energy can be used as a heat source for heating buildings or for production and industrial purposes.
  • micro cogeneration enables widespread, small-scale distributed production of electrical energy for households, the tertiary sector and small-sized industries, whose power requirements are relatively modest.
  • micro cogeneration has been hampered by the difficulty of meeting minimum cost per unit of power, yield, reliability and efficiency requirements in small-sized devices. As a consequence, current cogeneration systems range from 100-300 kW to several MW.
  • micro cogeneration market offers substantially two options that are based on the same energy generation concept, but on two different types of prime mover.
  • micro gas turbines can be employed in the 50 to 100 kW range, whereas alternative internal combustion engines with a Diesel or, preferably, an Otto cycle can be used for smaller plants.
  • the thermal energy produced by the functioning of a prime mover (be it an internal combustion engine or a micro gas turbine) is partly dissipated in the external environment by radiation; while this fraction can effectively be reduced, most of the thermal energy is transferred to the combustion gases (whose temperature in fact ranges from 350 to 600° C.) discharged to the flue and to the cooling air of various engine components and auxiliary circuits.
  • Heat is not usually recovered from cooling air, essentially due to its low enthalpy and convective heat transfer coefficient, which would require exchangers endowed with large exchange surfaces, adversely affecting the cost/benefit ratio of the cogenerator. Only rarely is cooling air harnessed to heat water, generally in alternative internal combustion engines.
  • Such devices are usually fitted downstream of the prime mover; they may be exchangers (also known as recuperators), which use the heat of the combustion fumes, for example to preheat the combustion air, or recovery furnaces, where the fumes are further burned or merely cooled via heat exchangers, preferably dedicated to production of steam, hot water or superheated water.
  • exchangers also known as recuperators
  • recuperators use the heat of the combustion fumes, for example to preheat the combustion air, or recovery furnaces, where the fumes are further burned or merely cooled via heat exchangers, preferably dedicated to production of steam, hot water or superheated water.
  • exhaust hot gases discharged by one or multiple heat sources, are cooled on the whole thermal exchange surface of the heat exchanger of a heat generator (in this case, a fire-tube boiler) while in the document U.S. Pat. No. 4,313,399 exhaust hot gases are used as comburent in the combustion chamber of the heat generator, if sufficiently rich in oxygen.
  • the enthalpy of the cooling air of a prime mover and its auxiliary circuits is difficult to reuse, its recovery from the various heat sources of an industrial plant, e.g. the cooling system of a plastic stamping plant; hot air from industrial painting plants; or exhaust fumes from elderly, poorly efficient industrial furnaces and boilers, is even harder.
  • a first object of the disclosed invention is to devise a simple and economical heat recovery method in relation to the amount of thermal and electrical power involved.
  • a second object of the invention is to devise a heat recovery method characterized by low pollutant emissions and environmental impact.
  • An additional object of the invention is to devise a heat recovery method characterized by high flexibility in terms of the amount of heat to be recovered.
  • a further object of the disclosed invention is to devise a heat recovery method characterized by high flexibility in terms of the number and type of plants from which heat can be recovered.
  • a still further object of the present invention is to devise a method to integrate the heat recovery and production systems with electricity and/or mechanical power production plants.
  • Another object of the invention is to devise high flexibility means to integrate a prime mover and a fire-tube boiler in terms of the amount of electrical power to be integrated.
  • FIG. 1 is a schematic perspective view of a heat generator according to the prior art
  • FIG. 2 is a block diagram of a heat recovery apparatus according to the disclosed invention.
  • FIGS. 4 a , 4 b , and 4 c report three side and front cross-sections of the apparatus illustrated in FIG. 2 , with emphasis on the heat generator according to a first variant of the invention.
  • FIGS. 5 a and 5 b are two side and front cross-sections of the apparatus shown in FIG. 2 , with special reference to the heat generator, according to an additional variant of the invention;
  • FIG. 5 c reports a detail of the variant shown in FIGS. 5 a and 5 b.
  • FIG. 2 of the attached diagrams 1 indicates overall the heat recovery apparatus, the subject of the invention, which includes one or multiple generic heat sources 2 and a heat generator 3 .
  • said generic heat sources 2 can be electrical and/or mechanical power generators, such as internal combustion engines, micro gas turbines, steam turbines, fuel cells; simpler heat sources such as low-efficiency heat generators, whose fumes can still be used to extract thermal energy; and even simpler devices such as heat exchanger batteries of cooling systems of plants such as plastic stamping or extrusion machines.
  • said heat sources 2 emit heat substantially as hot gases, i.e. combustion gases F 1 and/or cooling and ventilation air F 2 heated by the cooling of various types of equipment.
  • Said heat sources 2 can be for instance:
  • Hot gases F 1 and F 2 generated by said heat sources 2 , are often insufficient in amount and/or temperature for heat recovery to be feasible and/or economical through individual recovery apparatuses.
  • FIGS. 1 and 2 schematically show the combustion chamber (or furnace) 31 , the heat exchanger 32 , and the flue 36 of the heat generator 3 .
  • the enthalpy of the hot gases F 1 and F 2 issuing from the heat source 2 is recovered by said generator 3 .
  • combustion gases F 1 whose temperature is sufficiently high, are sent to the exchanger 32 to transfer heat, whereas the cooling air F 2 is used in the same generator 3 as combustion air for the furnace 31 .
  • the heat generator 3 is preferably a type for production of steam and/or hot water and/or diathermic oil; in particular, it is a fire-tube boiler (see FIG. 1 ). Since the technology and operating principles of the fire-tube boiler 3 (henceforth the boiler) are well known, a short description will suffice here.
  • the features of the fire-tube boiler 3 shown in the schematic view of FIG. 1 and in FIGS. 4 a through 5 c are a furnace 31 , usually cylindrical, where combustion occurs, and a number of pipes 33 , constituting overall the exchanger 32 , carrying the exhaust gases. Said pipes 33 are arranged into bundles (or fume circuits) in which the gases course, passing through the boiler 3 once or multiple times.
  • the furnace 31 and pipes 33 are surrounded by water A (in liquid and steam state); the water is contained in a cylindrical vessel 38 fitted at either end with pipe plates 3801 for the insertion of the furnace 31 and pipes 33 .
  • the exhaust gases issuing from the furnace 31 which coincides with the first fume circuit 3101 , pass through a first inversion chamber 34 ; from said chamber they are sent, confined above by a partition 3401 , into the pipes 33 of the second fume circuit 3302 , and from there to a second inversion chamber 35 , which is usually found on the front of the boiler 3 (note the direction of the arrows F on various pipes 33 in FIG. 1 ), and finally, sufficiently cooled after coursing through the third fume circuit 3303 , they are conveyed to the flue 36 .
  • a hatch 37 for inspection and maintenance, commonly found on the front of the boiler 3 is schematically drawn in FIGS. 4 a through 5 c.
  • the boiler 3 Upstream of the furnace 31 the boiler 3 also includes at least a burner and the respective fan (or blower), to supply combustion air (not shown in the figures).
  • a conveyor 4 carries said combustion gases F 1 to at least one part of the exchanger 32 , to recover their thermal energy.
  • the inspection hatch 37 is modified compared with the prior art, to accommodate the conveyor 4 passing through it.
  • Said conveyor 4 is characterized by an outer part 41 connected directly, or indirectly through ducts, to said one or multiple heat sources 2 , to collect their combustion gases F 1 , and by an inner part 42 , which is designed to couple to one or more pipes 33 of the heat exchanger 32 of the fire-tube boiler 3 , in particular one or more pipes 33 of at least the third fume circuit 3303 , and whose opening 4201 presses against the front pipe plate 3801 .
  • the internal part 42 is designed to rotate and translate axially with respect to the outer part 41 , where it is partially inserted, to allow coupling of the conveyor 4 to one or multiple pipes 33 , as required by the flow rate and temperature of the combustion gases F 1 , or to prevent the conveyor 4 from interfering with said pipes 33 if no combustion gases F 1 from which energy can be recovered are present.
  • said conveyor 4 is preferably a telescopic conduit consisting of an outer part 41 coupled hermetically to the inspection hatch 37 , and of an inner part 42 capable of rotation and axial translation with respect to the outer part 41 , where it is partially inserted, via a telescopic coupling 5 (schematically represented in the enclosed figures).
  • said rotation is enabled by the circular conduit tracts 4101 and 4205 of said joint 5 , to which the outer 41 and inner part 42 of the conduit 4 are coupled (see in particular FIG. 5 c ).
  • the opening 4201 of the mobile internal part 42 is preferably elliptical and/or circular.
  • Axial translation of the inner part 42 with respect to the fixed external part 41 enables the opening 4201 to approach the pipe plate 3801 within the inversion chamber 35 , to intercept said one or more pipes 33 , whereas its rotation selects the pipes 33 of said plate 3801 that will carry the combustion gases F 1 of the heat source 2 , and consequently the number of passes of the combustion gases F 1 through the heat generator 3 .
  • said pipes 33 intercepted by said opening 4201 , therefore define the part 3201 of the heat exchanger 32 of the boiler 3 dedicated to cooling the sole combustion gases F 1 of said one or multiple heat sources 2 .
  • the conduit 4 is capable of connecting to a suitable number of pipes 33 belonging solely to the third fume circuit 3303 , whereas, as clearly shown in FIGS. 4 b and/or 4 c , the inner part 42 of the conduit 4 , as a result of its rotation, can connect simultaneously to multiple pipes 33 of the third circuit 3303 and to at least one pipe 33 of the second circuit 3302 .
  • the combustion gases F 1 of the heat source 2 therefore course through the heat generator 3 just once, via the third fume circuit 3303 , whereas in the example illustrated in FIG. 4 b and/or 4 c , part of said combustion gases F 1 pass through the boiler 3 three times.
  • part of said gases F 1 pass through the boiler 3 in front to back direction, through one or more pipes 33 of the second fume circuit 3302 , their direction is then reversed in the inversion chamber 34 , whence they pass through those pipes 33 of the second fume circuit 3302 that are not intercepted by the opening 4201 of the conduit 4 , and subsequently they pass through the third and last fume circuit 3303 , before finally going to the flue 36 .
  • the pipes 33 of any fume circuit that are not intercepted by the opening 4201 continue to carry the products of the internal combustion of the boiler 3 , or a mixture of said products and said combustion gases F 1 (like the pipes 33 of the second circuit 3302 , not exclusively dedicated to carrying the same combustion gases F 1 , shown in the example of FIG. 4 b ) along the direction of the arrows F and of their vector representation (depicted in the enclosed figures, where “x” indicates a vector pointing into the page and “•” a vector pointing out of the page).
  • FIGS. 5 a to 5 c Similar considerations also apply to the variant shown in FIGS. 5 a to 5 c , which differs from the previous configuration by the circular (rather than generically elliptical) section of the opening 4201 of the conduit 4 .
  • the centre of, the opening 4201 must be offset with respect to the centre of the fixed external part 41 .
  • the inner part 42 has a first tract 4202 , whose axis is parallel to the fixed outer part 41 , and another tract 4203 (designed to couple through its own opening 4201 to the pipe plate 3801 ), whose axis is parallel to the first; the two tracts 4202 and 4203 are connected through a junction 4204 .
  • the conduit 4 is completed by an interception organ 43 , e.g. a butterfly valve 43 , positioned in the fixed part 41 , designed to exclude the heat source 2 from the boiler 3 in case of malfunction or maintenance, or in the event that the heat recovery apparatus 1 of the disclosed invention is operated as a traditional fire-tube boiler 3 .
  • an interception organ 43 e.g. a butterfly valve 43 , positioned in the fixed part 41 , designed to exclude the heat source 2 from the boiler 3 in case of malfunction or maintenance, or in the event that the heat recovery apparatus 1 of the disclosed invention is operated as a traditional fire-tube boiler 3 .
  • valve 43 must therefore be closed, while the mobile inner part 42 of the conduit 4 is retracted inside the fixed part 41 , so that all the pipes 33 of the boiler 3 carry exclusively the products of its internal combustion.
  • One or more magnets can also be fitted in close proximity to the opening 4201 of the conduit 4 , for an enhanced coupling of the conduit 4 and the pipe plate 3801 , and thus a perfect seal.
  • any means known in the prior art can be used to press the opening 4201 against the pipe plate 3801 .
  • an additional fan (not shown) can be applied to the flue 36 , to enhance circulation of the combustion gases F 1 through the fire-tube boiler 3 , by forcing them through said pipes 33 of its exchanger 32 .
  • FIGS. 4 a and 5 a (envisaging a single pass of the combustion gases F 1 through the boiler 3 ) are preferable where the thermal power dissipation (and/or temperature) of the combustion gases F 1 is low, whereas those shown in FIGS. 4 b and 4 c , 5 b , or any other configuration envisaging three passes of the gases F 1 through the boiler, are preferable with higher values of thermal power dissipation.
  • the number of pipes 33 intercepted by the conduit 4 and, consequently, the number of passes of the gases F 1 through the boiler 3 are aimed to achieve the lowest possible temperature of the combustion gases F 1 at the exit from the boiler 3 .
  • the configuration (particularly the rotation angle of the mobile internal part 42 of the conduit 4 ) can be selected manually.
  • an electronic control unit selecting the most appropriate configuration of the conduit 4 in response to the changes in said physical parameters, which are detected through special sensors.
  • the one or multiple heat sources 2 may entail the possibility of recovering in the boiler 3 , besides the combustion gases F 1 , the thermal energy of the cooling and/or ventilation air F 2 , for instance of engine components and auxiliary circuits of the heat source 2 itself, which would otherwise be dispersed in the environment.
  • cooling and/or ventilation air F 2 warmer than the ambient temperature (from 60° C. to 90° C.), is sent by known means directly to the furnace 31 of the boiler 3 and used as combustion air.
  • the heat source 2 therefore serves as a preheater unit of the combustion air for the internal combustion of the boiler 3 .
  • Recovery of such additional heat energy in the boiler 3 coupled to the heat recovered from the combustion gases F 1 , therefore increases the overall efficiency of the heat recovery apparatus 1 , which is subject of the invention.
  • the heat source 2 is preferably a prime mover for electrical energy production. Even more preferably such prime mover 2 is, as noted above, an internal combustion engine or a micro gas turbine, two well-established and reliable technologies that require no further description.
  • the heat recovery apparatus 1 according to this preferred embodiment is therefore a cogeneration plant for combined electrical and thermal power production, to which all the above considerations apply.
  • the prime mover 2 can lack the traditional integrated recuperator, since it is connected (through said conveyor 4 ) to the boiler 3 , where the heat that would otherwise be dissipated as combustion gases F 1 and cooling and/or ventilation air F 2 is efficiently recovered.
  • prime mover 2 (or in general the heat source 2 ) can be joined, through the telescopic conduit 4 , to the back of the fire-tube boiler 3 , rather than at the level of the inspection hatch (suitably modified to house said conduit 4 ) as described above.
  • the mobile inner part 42 is capable only of axial translation with respect to the fixed part 41 , not also of rotation.
  • Such configuration is especially practical, as noted above, when the physical parameters of the combustion gases F 1 are substantially constant over time and the part 3201 of the heat exchanger 32 dedicated to said combustion gases F 1 can be selected manually.
  • the conveyor 4 includes only the external part 41 (henceforth, for the sake of simplicity, the conduit 41 ), hermetically coupled to the inspection hatch 37 but capable of axial translation to connect to the pipes 33 of the exchanger 32 of the boiler 3 dedicated to said combustion gases F 1 .
  • the apparatus for heat recovery 1 described above in its preferred embodiment and variants can achieve the intended goals, particularly heat recovery from diverse types of machines in a simple and economical way.
  • the heat source 2 is a prime mover (even though the reasoning also applies to the more general case of any alternative heat source 2 )
  • the possibility to dedicate part of the heat exchanger 32 of the boiler 3 to cooling the sole combustion gases F 1 of said prime mover 2 and to recover cooling and/or ventilation air F 2 significantly enhances the overall efficiency of the cogeneration apparatus 1 and allows nearly total recovery of its thermal loss.
  • integration of an existing boiler 3 with an engine 2 suitable for electricity generation can be achieved with a modest investment by any user, who can select the most appropriate size for their level of consumption.
  • Said cogeneration apparatuses 1 are therefore capable of meeting also a user demand characterized by high thermal and low electrical power production. This is easily achieved by replacing the standard hatch 37 of the fire-tube boiler 3 with an additional hatch capable of housing and supporting the conveyor 4 .
  • the disclosed cogeneration apparatus 1 is also characterized by a longer service life than traditional systems, to the extent that it enables separate maintenance or replacement of the prime mover 2 and the fire-tube boiler 3 , where needed; in addition, repair or replacement of either component does not involve the interruption, even temporary, of electrical and/or thermal power generation.
  • the heat generator 3 can also be a water-tube boiler.
US13/321,151 2009-05-20 2010-05-18 Heat recovery apparatus Abandoned US20120067549A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
ITAN2009A000023A IT1394354B1 (it) 2009-05-20 2009-05-20 Apparato di recupero calore
ITAN2009A000023 2009-05-20
PCT/IB2010/001174 WO2010133951A1 (en) 2009-05-20 2010-05-18 Heat recovery apparatus

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US20120067549A1 true US20120067549A1 (en) 2012-03-22

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US (1) US20120067549A1 (zh)
EP (1) EP2443398A1 (zh)
CN (1) CN102439375A (zh)
IT (1) IT1394354B1 (zh)
RU (1) RU2491481C1 (zh)
WO (1) WO2010133951A1 (zh)

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EP3270086A1 (en) * 2016-07-11 2018-01-17 In Kyu Park Heat exchanger for recovery of waste heat
CN108036394A (zh) * 2018-01-02 2018-05-15 董传勇 多功能电磁采暖炉
CN109000272A (zh) * 2018-09-20 2018-12-14 山东路通道路材料有限公司 一种热量回收的沥青烟气处理系统及处理方法
CN111765783A (zh) * 2020-08-07 2020-10-13 东营市延旭环保科技有限公司 一种环保沼气发电用余热回收设备
US11119454B2 (en) * 2018-03-30 2021-09-14 General Electric Company System and method for power generation control

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CN106091386A (zh) * 2015-06-16 2016-11-09 熵零股份有限公司 流体加热器
RU2611700C1 (ru) * 2015-10-22 2017-02-28 Федеральное государственное бюджетное образовательное учреждение высшего образования "Юго-Западный государственный университет" (ЮЗГУ) Автономная тепловая пушка
US10641552B2 (en) * 2015-12-23 2020-05-05 Tesla, Inc. Heat-recovering temperature-gradient based oven system
CN105546562A (zh) * 2016-01-29 2016-05-04 上海久试电力技术有限公司 控制烟温的烟道和控制方法以及烟道的改进方法
CN107664439B (zh) * 2017-08-30 2019-06-11 昆明理工大学 一种燃油炉窑烟气余热利用系统
CL2020002674A1 (es) * 2020-10-15 2021-01-04 Eduardo Uribe Ramos Sergio Dispositivo de intercambio de calor no presurizado de gran poder de transferencia de calor con un menor gasto energético.

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CN102439375A (zh) 2012-05-02
EP2443398A1 (en) 2012-04-25
WO2010133951A1 (en) 2010-11-25

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