EP0351247A2 - Récupération de la chaleur des gaz d'échappement - Google Patents

Récupération de la chaleur des gaz d'échappement Download PDF

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Publication number
EP0351247A2
EP0351247A2 EP89307197A EP89307197A EP0351247A2 EP 0351247 A2 EP0351247 A2 EP 0351247A2 EP 89307197 A EP89307197 A EP 89307197A EP 89307197 A EP89307197 A EP 89307197A EP 0351247 A2 EP0351247 A2 EP 0351247A2
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EP
European Patent Office
Prior art keywords
coils
tubes
gases
ring
heat exchange
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP89307197A
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German (de)
English (en)
Other versions
EP0351247A3 (fr
Inventor
Marsun Lipsit
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Roberts E Dawson
Original Assignee
Roberts E Dawson
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Filing date
Publication date
Application filed by Roberts E Dawson filed Critical Roberts E Dawson
Publication of EP0351247A2 publication Critical patent/EP0351247A2/fr
Publication of EP0351247A3 publication Critical patent/EP0351247A3/fr
Withdrawn legal-status Critical Current

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    • 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
    • F28D21/0005—Recuperative heat exchangers the heat being recuperated from exhaust gases for domestic or space-heating systems
    • F28D21/0007—Water heaters
    • 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
    • F28D7/02—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 helically coiled
    • F28D7/024—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 helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F28F9/0131—Auxiliary supports for elements for tubes or tube-assemblies formed by plates
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • 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

  • This invention relates to the recovery of heat from gases and particularly relates to improved apparatus for maximizing the recovery of heat from gases (for example waste or flue gases).
  • Heat recovery systems are known in which exhaust gases from a source of heat (for example a hot air furnace or boiler) are passed through a heat exchanger in which coil(s) or tube(s) are disposed into which the heat may be transferred. Examples of such systems are shown in U.S. Patent Nos. 4,210,201, 4,136,731, 4,037,567, 4,066,210, and 3,896,992.
  • European Patent Application No. 84307512.8 discloses apparatus involving heat transfer which includes a plurality of sets of elements such as cylinders arrayed in rows perpendicular to the direction of flow of the fluid and in which the elements of adjacent rows are staggered with respect to each other.
  • the application teaches that the elements of each row are spatially separated from each other so that open flow space would normally completely surround each element.
  • a partition extends from each element generally parallel to the direction of flow of fluid. Each partition bridges between a pair of elements in alternate rows and is positioned so that it is symmetrically spaced from the adjacent elements of the intervening row. The partitions block by-pass flow of the fluid along diagonal paths between the elements.
  • fluid flow is contained and directed, being funnelled and streamed in an orderly unidirectional flow.
  • Reference SU 1285264 discloses a staggered cluster of tubes (2) with longitudinal fins.
  • the even rows in the cluster are offset in the direction of the odd ones towards the motion of the gas.
  • the offset is not more than , where d is the diameter of the tubes (mm.), S1 is the transverse pitch of the tube cluster (mm.), and S2 is the longitudinal pitch of the tube cluster (mm.).
  • the diagonally-directed flows inside the tube cluster are forced towards the lower parts of the tubes and the diagonal velocities are increased, blowing the friable ash deposits from the bottoms of the tubes.
  • the tubes are thus self-cleaning.
  • U.S. Patent No. 4,079,754 relates to apparatus for passing fluid on a controlled basis in either of two opposite directions.
  • U.S. Patent No. 3,688,800 discloses a fluid flow restrictor comprising a series of rows of baffles placed in the path of fluid flow with the baffles in succeeding rows staggered with respect to those in adjacent rows so that as the fluid flows it is constrained to change its direction repeatedly.
  • U.S. Patent No. 4,456,033 teaches a flow restrictor to minimize noise and cavitation, or other adverse effects, in regulating the flow of a high pressure fluid.
  • the restrictor defines a myriad of tortuous, dissimilar, intertwined, and commingled energy dissipating chambered flow paths edgewise through a stack of sheets of perforated stock material. Adjacent sheets have their perforations out of registration with one another, the inlet and outlet to the restrictor being edgewise through the stack through open-sided ones of the perforations of the several sheets of stock.
  • U.S Patent No. 4,019,573 teaches a heat exchanger for exchanging heat between fluids comprising a conduit for flow of a first fluid therethrough comprising a manifold with a single port in one area and a pair of ports in another area and a plurality of spaced fluid tubes attached to the pair of ports with the combination of the plurality of tubes having outer peripheral surfaces describing a cylinder and the inner confronting peripheral surfaces spaced apart to provide an open area therebetween for flow of a second fluid therethrough and means for directing the second fluid over and around both the inner and outer peripheral surfaces and through the open area between the tubes for achieving maximum surface area heat transfer with minimum cross sectional area of conduits.
  • U.S. Patent No. 4,512,288 (corresponding to Canadian patent No. 1,235,615) discloses a heat recovery system which recovers heat from flue gases from a furnace or the like and a hot water cylinder. Flue gases are passed through series of chambers in which coils are located. Water is passed through the coils in a direction opposite to flue gas flow to maximize heat transfer and the heated water is passed to either a heat radiating system or into preheater tank for the hot water supply. The coils for the heat radiation and water heating are in separate circuits and the flue gases from the hot water is passed only over the coil used for water heating. Pumps are used for water recirculation in both the heat radiating circuit and the water heating circuit. The system has application to domestic and industrial furnaces which provide gaseous combustion products with recoverable thermal energy and permits the use of a small diameter exhaust vent without adversely affecting the ignition and combustion system of conventional furnaces.
  • This device allows the flue gases to make three passes through a heat exchanger.
  • the unit also condenses the water vapour in the flue products.
  • the heat of the exhaust gas is transferred by the heat exchanger to the domestic hot water system, in effect, preheating it.
  • the Tess unit was developed by the installing contractor, Roger Michaud Services of Timmins. As a result, the overall efficiency of the heating plant has increased from 60 to 90 per cent.
  • the total cost of the complete renovations to the hotel's energy systems was approximately $30,000. For the first 11 months of 1986, the energy savings totaled $11,073.50. This gives a payback time of approximately 2.5 years.
  • Hot make-up or return water is pumped (12) into the water inlet (13) of unit 3 into the copper coil (14) and progressively through the double coils (14, 15, 16) exiting at hot water outlet (17).
  • Hot water from any separate set of coils provides an infinite temperature range from 130°F to 210°F.
  • This hot water can be utilized for domestic hot water, hanging heaters, preheated boiler water or preheated air for furnace combustion. As the hot gases pass over the coils carrying cooler water; there is condensing effect.
  • the distilled water is collected and drained from each module in the condensate line (18). An exhaust temperature of 140°F will provide only a few drops of water per minute with the balance expelled with the exhaust while an exhaust temperature of 80°F will produce hundreds of gallons of distilled water per day.”
  • heat exchange apparatus comprising at least two adjacent (for example horizontally spaced) rows (columns) of tubes (parallel rows of tubes - an inner row and an outer row -) or at least two spaced (for example horizontally concentrically disposed) rings (for example cylindrical columns) of helical coils (for example an inner and an outer ring) for the transfer of heat thereinto from gases wherein the tubes of the inner row are, or the inner ring of coils is staggered with respect to the tubes of the outer row or ring of coils to block the flow of gases and the inner row or ring is spaced from the outer by such amount to prevent streaming of the gases to maximize turbulence of the gases passing thereby, thereby enhancing heat transfer from the gases to the tubes or coils.
  • the source of the hot gases may be a boiler, exhaust gases, flue gases or the like.
  • the hot gases may be introduced normal (at right angles) to the orientation of the at least two adjacent spaced rows of the tubes or spaced rings of coils.
  • the gases engaging the adjacent rows of tubes or rings of coils are blocked and caused to bounce or deflect off the surfaces of the tubes or rings of coils in a random manner to maximize turbulence - to create as much turbulence as possible in three dimensions.
  • the spacing between the tubes or coils in the same row or ring, respectively can be of generally any usable size provided the space between is less than the diameter of the tube or coil in advance (in front) of the row or ring of coils having regard to the direction of flow of the gas towards the tube or coils and the space between adjacent rows or rings of coils does not permit streaming.
  • the diameters of the adjacent rows of tubes and rings of coils may be the same or different.
  • the rows of spaced tubes or spaced rings of coils are preferably parallel or concentric as the case may be and the spacing from one another must be such that streaming of the gases passing the tubes or coils must be prevented.
  • at least two spaced parallel rows of tubes (the tubes in each row being spaced from one another) - an inner row of tubes and an outer row of tubes - or at least two spaced (concentric) rings of helical coils (the coils in each ring being spaced from one another) - an inner ring of helical coils and an outer concentric ring of helical coils - the spacing between the adjacent tubes of the same row or helical coils of the same ring (for example of the outer ring) was a distance equal to the distance calculated by multiplying a factor of about .500/.875 or about .571 (.5714) by the outside diameter of the coils of the adjacent inner ring of coils or the outside diameter of the tubes of the adjacent inner row - the distance between the coils of the same
  • the second (inner) row or ring may be spaced from the first (outer) row or outer ring by a distance equal to the distance calculated by multiplying a factor of 1.250/.875 or about 1.429 (1.4286) by the outside diameter of the tubes of the adjacent inner row or the outer diameter of the coils of the adjacent inner ring of coils measuring in the opposite plane (for example horizontal plane).
  • This mathematical relationship holds through the whole structure (whether 2 or 8 or more rings of coils or rows of tubes are used) so that if a third further inner ring of coils is provided, its spacing from the 2nd ring for calculation purposes is as if third ring is the 2nd ring (inner) and the 2nd ring is the first outer ring.
  • the coils or tubes are carried in an enclosed chamber (preferably a turbulence chamber) having an inlet opening for gas to enter the chamber and an outlet for leaving the chamber, the gas in one embodiment being directed to engage the tubes or coils at right angles and in another embodiment be deflected (for example by a deflector, e.g. a conical deflector, situated proximate the entry) for angular engagement of the coils or tubes (in three dimensions) and further deflection.
  • a deflector e.g. a conical deflector, situated proximate the entry
  • the coils or tubes preferably carry liquid and hot gases (e.g. waste or flue) into the chamber.
  • heat may be transferred from the flue gases by the heat exchange coils or tubes to the liquid (for example water) that have been positioned to maximize turbulence for maximizing recovery of heat.
  • Baffles or deflectors in one embodiment containing holes and in another embodiment without holes may be strategically located in the chamber to encourage deflection to reduce streaming of the gases and keep the gas streams splitting and "bouncing".
  • the baffles or deflectors when the baffles or deflectors are inserted angularly through rows of tubes or coils of the rings which have been spaced in accordance with the factors of .571 and 1.429, the angle of insertion or entry of the baffles or deflectors inserted angularly downwardly through the rows or coils, is in the order of 25 o (for example to the horizontal).
  • a plate may be provided across the lower portion of the chamber between the tubes and/or coils and the gas outlet with restricted openings provided therethrough.
  • the plate acts as a pressure plate to prevent dead spaces at the corners of the chamber (for example meeting of side wall and bottom).
  • the gases passing through the restricted openings is turbulent and draws any stagnant air from the "dead space”.
  • Applicant believes the use of the plate evens out the vacuum across the diameter of the chamber preventing dead air space and gas streaming. With the bouncing and deflection of the gases, the temperature in the chamber at all places in the chamber is the same - homogeneous.
  • a number of chambers may be joined and the coils in adjacent chambers may be connected to one another with the flow of fluid (for example water) opposite the flow of the gases from chamber to chamber.
  • fluid for example water
  • a stream of hot flue gas is initiated.
  • the 90° angle change of direction of the flow from one (vertical) plane to another (horizontal) plane creates the initial-turbulence (i.e. the molecules on the outside of an elbow (right angle) must travel faster than the inner molecules of the stream as the stream is pushed from the boiler by the boiler fan and pulled by the induction fan into the molecular turbulence chamber).
  • the molecules are spinning within the stream.
  • the main stream is split several times by the circular surface of the coils.
  • the directional flow of the individual streams is around the surface of the coil exposing the once centre (a) molecules to the thermal conducting (copper) tube.
  • the stream (b) continues, it is split again into a smaller stream (c) exposing the centre molecules of the (B) stream to the thermal conducting (copper) tube (2) of the inner coil.
  • this stream breakup occurs upon impact of the copper coils, individual molecules bounce from the coil surface in an infinite number of directions as determined by a molecule or particle impacting a curved coil surface.
  • the molecule upon impact with each coil will transfer its thermal energy to the cooler (copper) surface.
  • Each molecule will strike the coils on several occasions or rebound from the container wall.
  • the stream is redirected by a directional baffle plate (a metal projection of 90° or greater) for example affixed to the container wall or passing between tubes of adjacent rows or rings of adjacent coils.
  • a directional baffle plate a metal projection of 90° or greater
  • the stream created by the vacuum will again demonstrated the same action of split streaming and molecular bouncing as the stream impacts the coils. Further thermal energy is then continually given up to the copper coil carrying a colder fluid.
  • the application of the invention may be any vapourized element or compound or mixture of elements and compounds requiring a maximum molecular surface exposure to the atoms or molecules of another solid, liquid or vapourized element, or compound or mixture of same, for example:
  • any stream of vapour(s) or liquid(s) in a static or dynamic motion is considered as layers of molecules stacked atop each other with molecules holding their relative positions when the fluid or vapour briefly is at rest or in a flow pattern. Consequently when thermal energy (i.e. heat is applied to the surface of the stream), the time for that energy to penetrate to the centre of the stream is dependent on the thermal conductivity of each molecule. The rate of penetration of heat into all molecules of the stream is a result of each molecule being heated and transferring that heat energy to the cooler molecule next to it. Conversely in a hot thermal stream in order to give up its energy molecules in the centre of the stream must transfer that energy from the center of the stream to the cooler surface.
  • a faster method of transferring the inner heat to the outer molecules of the stream or vice versa is to expose the inner molecules directly to that surface.
  • Such a method of accomplishing this is by creating turbulence in the stream.
  • the turbulence causes the molecules to rapidly change their relative positions in the stream allowing every molecule to be exposed to the surface of the molecules of the colder atoms or molecules.
  • This turbulence and the subsequent surface exposure of the molecules of the hotter substance to the surface molecules of another substance transfers the heat energy very quickly through the stream allowing the homogeneous mixture to obtain an equal temperature throughout the stream.
  • a plurality of chambers are provided between which the gases pass (in one direction from one to another, for example under negative pressure) and the gases are spun to add turbulence.
  • the chamber may be covered by insulation and a cover.
  • the tubes or coils may be supported from hangers suspended from the top of the chambers (which top may be separate from the side wall). Each hanger may comprise holes therein to receive the tubes or coil portions and be secured thereto by for example welded bands.
  • the hanger may be bent at one edge along its length and may be cut through the openings to provide two portions.
  • the coils may be placed in the openings or recesses of the openings in one portion of the hanger and the second or other portion of the hanger secured to the first portion, thereby securing the coils to the hanger (which is suspended from the top).
  • Each set of coils or tubes in the same plane is preferably secured to the top of the chamber by one hanger.
  • turbulence chambers 20 each comprising inlets 22 and outlets 24, the outlet of one being the inlet of the chamber next adjacent to it.
  • a source of hot gases (now shown) is drawn through the chambers by negative pressure created by induction fan 26.
  • Pressure plates 28 may be provided across the end of the chamber between the heat exchange rings of helical coils 30 (shown in Figure 2 for example) and/or tubes and the outlet 24. Plate 28 has restricted openings 32 therethrough (see also Figure 2). The plate acts as a pressure plate to prevent dead spaces at the corners of the chamber.
  • the gas is introduced at 90° (normal) to the orientation of the chamber to engage the heat exchange coils "head on" as at 34 in Figure 2.
  • triangular deflector 36 is provided at the mouth of inlet 22 to deflect the gases to cause turbulence.
  • Baffles 38 are provided to keep the gases bouncing and deflecting.
  • each chamber 20 three rings 30 of helical coils identified as 30A, 30B, and 30C (see Figure 2) are provided for transferring water or other fluid for being heated by the flue gases.
  • the outer ring 30A is positioned so that the spacing between the vertical spaced helical coils is such that the coils of rings 30B within ring 30A is staggered to fill the openings between the coils of ring 30A and be close enough to ring 30A to ensure no streaming of the gas but rather encourage continuous turbulence.
  • coils 30B and 30C see Figures 11 and 12). The distances between the coils are as has been previously calculated and with this spacing have provided efficient results.
  • hot flue gases from a positive pressure source enters chamber 20 and is directed outward by the conical flow diverter 36 into the inner set of spiral coils 30C.
  • the gas stream is split by the coil and while the coil carrying a colder liquid absorbs the thermal energy the stream is further split by coils 30B and still further by 30A.
  • the molecules in the stream flow around the coils or impact on the coils they transfer their thermal energy to the coil contacted.
  • the molecules bounce in infinite directions as they impact all coils 30A, 30B, and 30C in chamber 20 giving up their thermal energy to the impacted coil.
  • As the stream and molecules are bounced either towards the centre or the outside of the chamber; both bounce back towards the coil from the side of the chamber or the central diverter cylinder 40.
  • the molecules and small streams tend to collect and form larger streams downward along the sides and central diverter cylinder 40.
  • the streams follow these until a directional baffle bar 38 is encountered.
  • the negative pressure created by an induction fan causes the stream to be redirected into the coils 30A, 30B and 30C creating a repeat of the phenomena described previously.
  • the phenomena continues to the bottom of the chamber repeatedly exchanging the molecular thermal energy into the copper coils impacted or contacted.
  • chambers 20′ are connected with pipes 50 for carrying liquids connecting coils 30A, 30B and 30C in the chambers 30′.
  • Each of the chambers 30′ is surrounded by insulation 52 (sides, top, etc.) and covered by a cover metal material 54.
  • induction fan 26 draws the flue gases through the chambers as shown by the arrows.
  • the helical coils are each secured to the separate tops 30 ⁇ by hanger supports 56 (see Figures 8 and 9) by stainless submerged arc welding for ease of removal of the coils.
  • the top 30 ⁇ is separate from the side wall 31 so the system can be serviced.
  • Metal hanger supports 56 hold the helical coils of the rings 30A, 30B and 30C in place and are silver soldered to the coils.
  • Each hanger support 56 is an elongated piece of metal, one edge being angled at 60 for strengthening purposes (see Figure 10).
  • Each hanger system 56 carries apertures to precisely receive the coils and the elongated hanger is cut for ease of mounting the coils.
  • each chamber 120 comprises inlet 122 (on top) and outlet 124 (below). Exhaust heat flows from boiler 119 in the direction of the arrows through the chambers 120. Fluid pipes 126 are provided through which fluid to be heated flows in the opposite direction to the direction of flow of the exhaust gases.
  • each chamber 120 With reference to Figure 19, the internal configuration of each chamber 120 is shown. Three rings 130A, 130B and 130C of helical coils are shown for the transfer of heat thereto from exhaust gases entering inlet 122 of chamber 120 prior to exiting through outlet 124.
  • Deflectors 132 are carried on vertical shaft 136.
  • baffles or deflectors 140 may be pushed through the spaces between rings 130A, 130B and 130C floating therebetween.
  • the angle of the baffles or deflectors to the horizontal is about 25 o .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP89307197A 1988-07-15 1989-07-14 Récupération de la chaleur des gaz d'échappement Withdrawn EP0351247A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CA572208 1988-07-15
CA572208 1988-07-15

Publications (2)

Publication Number Publication Date
EP0351247A2 true EP0351247A2 (fr) 1990-01-17
EP0351247A3 EP0351247A3 (fr) 1990-04-25

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Cited By (14)

* Cited by examiner, † Cited by third party
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EP0440886A1 (fr) * 1990-01-12 1991-08-14 MAN Gutehoffnungshütte Aktiengesellschaft Réacteur à lit fluidifié
WO2001055661A1 (fr) * 2000-01-26 2001-08-02 Huai Yin Hui Huang Tai Yang Neng You Xian Gong Si Echangeur thermique a gaine en spirale assemblee
WO2003040641A1 (fr) * 2001-11-09 2003-05-15 Aalborg Industries A/S Echangeur de chaleur, dispositif comprenant un echangeur de chaleur et procede de fabrication de cet echangeur de chaleur
ITTV20080151A1 (it) * 2008-11-24 2010-05-25 Giorgio Eberle Dispositivo per il recupero del calore.
FR2958735A1 (fr) * 2010-04-13 2011-10-14 Air Proc Components Echangeur perfectionne air/liquide et installation contenant ledit echangeur pour la recuperation de l'energie contenue dans de l'air vicie, en particulier celui extrait des cuisines professionnelles
WO2011148178A3 (fr) * 2010-05-26 2012-07-26 Heat Recovery Solutions Ltd Echangeur de chaleur
FR3018332A1 (fr) * 2014-03-05 2015-09-11 Snecma Systeme de maintien de tuyaux
EP2946161A4 (fr) * 2013-01-15 2016-11-02 Gilles Savard Échangeur thermique air-liquide
US10012413B2 (en) 2014-04-15 2018-07-03 Ecr International, Inc. Heat exchanger
CN110595229A (zh) * 2019-09-19 2019-12-20 国网四川省电力公司电力科学研究院 一种变直径螺旋管式压缩空气储能换热装置及系统
CN112128969A (zh) * 2020-09-30 2020-12-25 青海迎芳节能产品科技开发有限公司 一种工业节能环保炉
WO2021144682A1 (fr) 2020-01-13 2021-07-22 Stamenic Aleksandar Dispositif d'échange d'énergie entre milieux à structure et performances améliorées
CN113999058A (zh) * 2021-12-15 2022-02-01 中国农业科学院农业环境与可持续发展研究所 一种分布式有机生活垃圾一体化堆肥设备
CN115235287A (zh) * 2022-07-27 2022-10-25 苏州敬天爱人环境科技有限公司 废气余热回收利用设备

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Publication number Priority date Publication date Assignee Title
GB461210A (en) * 1935-03-30 1937-02-12 Bolidens Gruv Ab Improvements in tubular gas cooling apparatus
US2830798A (en) * 1953-02-13 1958-04-15 Garrett Corp Axial flow oil cooler having cross baffles
CH435347A (de) * 1962-05-17 1967-05-15 Waagner Biro Ag Verfahren zur Begrenzung der Wandtemperatur einer Trennwand zwischen wärmetauschenden Medien und Vorrichtung zur Durchführung des Verfahrens
US3403727A (en) * 1965-04-30 1968-10-01 Linde Ag Crossflow countercurrent heat exchanger with inner and outer-tube sections made up of closely packed coaxially nested layers of helicoidally wound tubes
GB1163804A (en) * 1967-06-16 1969-09-10 Richmond Engineering Company I Water Heating Apparatus
US4210203A (en) * 1976-10-21 1980-07-01 Aktiebolaget Atomenergi Heat exchanger apparatus
FR2476804A1 (fr) * 1980-02-25 1981-08-28 Sageot Jean Claude Economiseur pour chaudiere de chauffage central a circulation d'eau
GB2119074A (en) * 1982-04-16 1983-11-09 Steinecker Maschf Gmbh Heat exchanger
US4512288A (en) * 1983-07-15 1985-04-23 Roger Michaud Furnace heat exchanger

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB461210A (en) * 1935-03-30 1937-02-12 Bolidens Gruv Ab Improvements in tubular gas cooling apparatus
US2830798A (en) * 1953-02-13 1958-04-15 Garrett Corp Axial flow oil cooler having cross baffles
CH435347A (de) * 1962-05-17 1967-05-15 Waagner Biro Ag Verfahren zur Begrenzung der Wandtemperatur einer Trennwand zwischen wärmetauschenden Medien und Vorrichtung zur Durchführung des Verfahrens
US3403727A (en) * 1965-04-30 1968-10-01 Linde Ag Crossflow countercurrent heat exchanger with inner and outer-tube sections made up of closely packed coaxially nested layers of helicoidally wound tubes
GB1163804A (en) * 1967-06-16 1969-09-10 Richmond Engineering Company I Water Heating Apparatus
US4210203A (en) * 1976-10-21 1980-07-01 Aktiebolaget Atomenergi Heat exchanger apparatus
FR2476804A1 (fr) * 1980-02-25 1981-08-28 Sageot Jean Claude Economiseur pour chaudiere de chauffage central a circulation d'eau
GB2119074A (en) * 1982-04-16 1983-11-09 Steinecker Maschf Gmbh Heat exchanger
US4512288A (en) * 1983-07-15 1985-04-23 Roger Michaud Furnace heat exchanger

Cited By (25)

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WO2021144682A1 (fr) 2020-01-13 2021-07-22 Stamenic Aleksandar Dispositif d'échange d'énergie entre milieux à structure et performances améliorées
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CN113999058A (zh) * 2021-12-15 2022-02-01 中国农业科学院农业环境与可持续发展研究所 一种分布式有机生活垃圾一体化堆肥设备
CN115235287A (zh) * 2022-07-27 2022-10-25 苏州敬天爱人环境科技有限公司 废气余热回收利用设备
CN115235287B (zh) * 2022-07-27 2023-10-20 苏州敬天爱人环境科技有限公司 废气余热回收利用设备

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