EP0131213A2 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP0131213A2
EP0131213A2 EP84107485A EP84107485A EP0131213A2 EP 0131213 A2 EP0131213 A2 EP 0131213A2 EP 84107485 A EP84107485 A EP 84107485A EP 84107485 A EP84107485 A EP 84107485A EP 0131213 A2 EP0131213 A2 EP 0131213A2
Authority
EP
European Patent Office
Prior art keywords
liquid
tube
heat
heat exchanger
level
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.)
Granted
Application number
EP84107485A
Other languages
German (de)
English (en)
Other versions
EP0131213A3 (en
EP0131213B1 (fr
Inventor
Hans H. Sladky
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.)
Sladky Hans H
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT84107485T priority Critical patent/ATE29169T1/de
Publication of EP0131213A2 publication Critical patent/EP0131213A2/fr
Publication of EP0131213A3 publication Critical patent/EP0131213A3/de
Application granted granted Critical
Publication of EP0131213B1 publication Critical patent/EP0131213B1/fr
Expired legal-status Critical Current

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Classifications

    • 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
    • F28D3/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium flows in a continuous film, or trickles freely, over the conduits
    • F28D3/04—Distributing arrangements
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/163—Heat exchange including a means to form fluid film on heat transfer surface, e.g. trickle
    • Y10S165/168—Film formed on interior surface of container or pipe
    • Y10S165/169—Film formed on interior surface of container or pipe inside of vertical pipe
    • Y10S165/17—Distributor "cap" mounted in top end of pipe

Definitions

  • the invention relates to a thin-film heat exchanger which is suitable for the use of liquids contaminated by solids as a heat-emitting medium, such as e.g. for the use of river, groundwater or the like.
  • a heat source for heat pumps which is clearly superior to the heat exchangers previously used for such purposes in terms of heat transfer coefficient and space requirements.
  • Preferred embodiments of the heat exchanger according to the invention also permit continuous operation which is not interrupted by cleaning work, even with heat-emitting liquids heavily contaminated by solids.
  • Evaporator tubes or plate evaporators placed in the heat-emitting medium (e.g. water) and flowed through by the refrigerant allow a lower cooling limit of approx. + 1 ° C to be maintained, but have a much larger space requirement than tubular boiler evaporators and a somewhat poorer heat transfer coefficient of approx. 300 W / m 2 K. Cleaning the outside of the pipes or plates is cumbersome because they are up to 1.5 m deep in the water-carrying channel and their maximum distance is 100 mm.
  • the heat-emitting medium e.g. water
  • the best heat transfer coefficient of approx. 800 W / m 2 K and the lowest cooling limit of + 0.2 ° C have plate and pipe trickle coolers, ie horizontal pipes or plates through which refrigerant flows, on the outer surfaces of which the heat-emitting liquid flows down as a thin film. This must therefore be arranged above the pipes or plates ten rows of holes in the bottom of a distribution trough with narrow bores, which naturally tend to clog when solid contaminants are present. The cleaning of the surfaces of the pipes or plates also requires labor and business interruption, since the side covers have to be removed for this.
  • the introduction of the liquid into the exchange tube which is flared downwards to a cone, via a weir, such as according to DAS 1 164 990, or through several tangentially arranged feeders, such as according to CH-PS 600 279, does not guarantee that the liquid flow neither at the point of introduction nor at tears off the wall of the conical extension, but forms the desired coherent thin film over the entire length of the inner tube wall.
  • the measure proposed in DD-PS 46 722 is to fasten on the upper part of the heat exchange tube a hollow, rotationally symmetrical body which projects into it and which is expanded towards the bottom and is open at the top and bottom by at least three mounting ribs, the outwardly curved surface of which guides the liquid onto the inner wall of the tube shouldn’t guarantee film formation on the inside wall of the pipe in the intended form, because the width of the opening shown between the rotating body and the inside wall of the pipe would be much too large, quite apart from the fact that the shape of the rotating body also does not allow the liquid flow to be torn off smoothly allows its lower edge so that at least a significant part of the liquid supplied does not even reach the inner tube wall, but falls freely downwards. Even a considerable narrowing of the annular gap would not result in a reliable and uniform film formation due to the unfavorable shape of the rotary body, but would bring with it the same risk of clogging as in known tube and plate trickle coolers.
  • the object of the present invention is therefore to provide a thin-film heat exchanger with upright pipes, which is free from the disadvantages of the known coolers, in particular re results in extraordinarily high heat transfer coefficients and also allowable cooling limits, which are still superior to the lowest known to date, and also allow for special embodiments which, even when using heavily with solids such as sand, mud and the like.
  • Contaminated liquids as heat-emitting medium enables continuous operation not interrupted by cleaning and / or repair work.
  • One of the advantages of the cooler according to the invention is, inter alia, the possibility of allowing water to run down to temperatures below 0 ° C, for example to -1 / 2 ° C, in the supercooled state and thus to better utilize its heat content than is possible with known heat exchangers.
  • the distributor head is preferably axially displaceable in the heat exchange tube and is provided with a bolt projecting from the tube, by means of which it can be set in up and down movement.
  • Preferred embodiments of the invention relate to advantageous embodiments of the distributor head and devices which automatically start the movement of the distributor head when the annular gap becomes blocked and, if this measure does not remove the blockage in the case of particularly heavy soiling, temporarily remove the distributor head completely from the pipe. Further embodiments relate to a special management of the refrigerant circuit, which improves the heat transfer on the refrigerant side and the efficiency of the phase separation of the refrigerant, and measures to further improve the heat transfer on the refrigerant side by reducing the space available to the refrigerant in the evaporator.
  • FIGS. 1 and 2 the application of the invention for operating a heat pump is described below, for example.
  • the heat-emitting medium such as river ground or cooling water 15 reaches a - not shown - supply line in a flow vessel 37, which sits tightly on the upper tube plate 6, in which the heat exchange tubes 1 of the tube bundle are tightly fitted, for example, rolled, u .zw. so that their appropriately somewhat extended upper ends 4 protrude beyond the tube plate 6.
  • the lower tube ends 5 are rolled into the lower tube plate 7 so that they protrude somewhat downwards.
  • the two tube plates 6 and 7 close the boiler 2, in which the heat-absorbing medium 35 surrounding the tubes 1 is located, at the top and bottom.
  • the heat-emitting liquid reaches the heat exchange tubes 1 and is passed through the distributor heads 3 (cf. FIGS. 4, 5 and 6, 7) attached in the upper region thereof, for example conically expanded in its lower region narrow annular gap 14 led to the inner wall 13 of the tubes 1.
  • the lowermost circumference 12 of each distributor head is designed such that the liquid flowing down at this point is torn off smoothly, flows out through the annular gap 14, is applied as a thin film to the inner tube wall 13 and as such flows down the inner tube wall. In order to ensure a smooth tearing off of the liquid at the lowest circumference 12, this is of sharp-edged design, as shown in the figures.
  • the underside of the distributor head 3 is preferably hollowed out, for example conically, in such a way that there is a recess 124 which rises sharply from the lowest circumference 12.
  • the radius of the lowest circumference 12 is preferably matched to the inner radius of the tube 1 so that the width of the annular gap 14 is approximately in the range of 0.1 to 1 mm, preferably 0.3 to 0.7 mm.
  • FIGS. 6 and 7 Precise compliance with these dimensional tolerances can be made easier in terms of production technology in accordance with a particular embodiment shown in FIGS. 6 and 7 in that the distributor head 3 is fitted in an extension tube 8 placed on the upper part of the heat exchange tube 1, the inside diameter 10 of which is the same at the location of the distributor head 3 that of the heat exchange tube 1.
  • the inside of the extension tube 10 slightly conical, so that by changing the height at which the Ver dividing head 3 is located, the width of the annular gap 14 can be set within the limits under consideration.
  • An attachment possibility of the top tube 8 on the heat exchange tube 1 is shown in FIG. 6, for example.
  • the heat-emitting liquid flowing down the inside 13 of the tubes 1 as a film transfers its heat to the tube 1 and, via this, to the heat-absorbing medium 35, in the example shown a boiling refrigerant such as NH3 or freone, and emerges at the lower end 5 of the tube cooled down, e.g. with a temperature of -1 / 2 ° C.
  • a boiling refrigerant such as NH3 or freone
  • the tube bundle which in the limit case can also consist of a single tube, is located in the outer boiler 2, which contains the boiling refrigerant 35. This is kept at the boil by the heat absorption from the tubes 1 and by the suction effect of the compressor (not shown) connected to the boiler 2 via the suction line 169 and the separator 160.
  • the density of the refrigerant in the boiler 2 increases its level above that of the vapor-free refrigerant in the sump 36 of the separator 160 and passes through the overflows 161, 162 into the separator 160, from which the vaporous refrigerant is drawn in via the connection 169 by the compressor.
  • the condenser After the refrigerant has been compressed and in the - not shown - the condenser has given off the heat absorbed in the boiler 2 at a higher temperature level and, if appropriate, has been partially relaxed, it is injected through the pipe 109 into the center pipe 159 of the separator 160 via a nozzle 184.
  • the increase in speed caused by the nozzle 184 causes the refrigerant to be sucked out of the overflows 161, 162, which increases the circulation in the boiler 2 and thus improves the heat transfer and allows the liquid / vapor mixture to be applied to the wall opposite the inlet side of the tube 109 with considerable energy 168 of the separator 160 impact, whereby a substantial separation of liquid and steam is already effected.
  • the majority of the separated liquid flows into the sump 36 of the separator 160, from which it returns via line 171 to the lower part of the boiler 2.
  • the vapor which still contains residual liquid droplets, must travel the entire length of the separator 160 until it emerges from it through the suction connection 169 of the suction line of the compressor.
  • the entrained liquid droplets have enough time to settle so that the suction connection 169 is practical liquid-free steam is sucked into the table.
  • part of the interior of the boiler 2 located between the heat exchange tubes 1 is filled by inert fillers 180 such as glass or metal balls or preferably upright rods or tubes closed at the top and bottom.
  • inert fillers 180 such as glass or metal balls or preferably upright rods or tubes closed at the top and bottom.
  • the heat-emitting liquid is contaminated by solid particles, e.g. can easily occur when using groundwater or river water, there is a risk that dirt particles settling in the annular gap 14 lead to malfunctions due to constipation.
  • the distributor head 3 is designed to be axially displaceable in the tube 1 and is preferably provided with guide devices 20, 21, 22. These can consist, for example (see FIGS. 4, 5 and 6, 7) of a cylindrical part 18 which has the inside diameter water of the tube 1 is adapted freely and from which some, appropriately evenly distributed over the circumference, for example in a uniform triangular arrangement passages 23, 24, 25 are removed for the passage of the heat-emitting liquid.
  • the distributor head 3 is connected to the bolt 9, which can move it up and down in the tube 1, as soon as the rise in the liquid level 45 in the supply vessel 37 caused by the blockage exceeds a certain height.
  • this can be brought about by visual observation of the supply vessel 37 and movement of the bolt 9 connected to the distributor head 3 by hand.
  • the distributor head 3 is connected to a device, for example explained in more detail in FIG. 10, which automatically sets it in an upward and downward movement when a predetermined level 45 in the supply vessel 37 is exceeded, as determined by at least one level controller 126.
  • the movement of the distributor head 3 is changed in accordance with a further embodiment of the invention in such a way that it is completely lifted out of the pipe 1, so that even the coarsest mechanical impurities can drain through the pipe, which eliminates the blockage.
  • FIG. 10 A preferred embodiment of this embodiment of the invention is shown in FIG. 10.
  • the two level controllers 126 and 76 are arranged in such a way that they do not respond as long as the liquid level 45 does not rise above the level which arises during operation without clogging. Then all electrical lines of the control system are de-energized and all contacts are in idle status. The contacts of the two microswitches 63 and 128 are closed, the two contacts 136 and 137 of the relay 135 are open and the four-way solenoid valve 70 is in the "OFF" position. In this position, the upper part of the pneumatic cylinder 46 is connected to the compressed air source 74 via line 142, solenoid valve 70 and line 53 and the part below the piston 47 via line 141 to the free atmosphere.
  • the circuit: current source 140 ⁇ contact 125 ⁇ microswitch 63 ⁇ 12 ⁇ relay 135 is closed, the latter closing the two contacts 136 and 137.
  • the closing of the contact 137 does nothing more than ensure that nothing further happens later. This ensures that the circuit remains closed even when the microswitch 63 is opened.
  • the coil 69 of the four-way solenoid valve 70 is excited and this is brought into the "ON" position. In this position, the part of the cylinder 46 located above the piston 47 is connected to the compressed air source 74 via line 141, solenoid valve 70 and line 53.

Landscapes

  • 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)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Power Steering Mechanism (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
EP84107485A 1983-07-06 1984-06-28 Echangeur de chaleur Expired EP0131213B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84107485T ATE29169T1 (de) 1983-07-06 1984-06-28 Waermeaustauscher.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3324330A DE3324330A1 (de) 1983-07-06 1983-07-06 Waermeuebertrager
DE3324330 1983-07-06

Publications (3)

Publication Number Publication Date
EP0131213A2 true EP0131213A2 (fr) 1985-01-16
EP0131213A3 EP0131213A3 (en) 1985-05-15
EP0131213B1 EP0131213B1 (fr) 1987-08-26

Family

ID=6203286

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84107485A Expired EP0131213B1 (fr) 1983-07-06 1984-06-28 Echangeur de chaleur

Country Status (5)

Country Link
US (2) US4799542A (fr)
EP (1) EP0131213B1 (fr)
AT (1) ATE29169T1 (fr)
DE (2) DE3324330A1 (fr)
IL (1) IL72371A (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4799542A (en) * 1983-07-06 1989-01-24 Hans Sladky Heat exchanger with thin-film evaporator
FR2626191A1 (fr) * 1988-01-21 1989-07-28 Cezus Co Europ Zirconium Procede et dispositif d'exploitation d'un appareil fonctionnant par ruissellement d'un film liquide, et application a la separation des tetrachlorures de zr et hf
DE4228923A1 (de) * 1992-08-30 1994-03-03 Sladky Hans Vorrichtung zur Kühlung von Flüssigkeiten

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5291943A (en) * 1992-12-29 1994-03-08 The Regents Of The University Of California Heat transfer enhancement using tangential injection
WO1998041798A1 (fr) * 1997-03-17 1998-09-24 Hitachi, Ltd. Distributeur de liquide, echangeur thermique a couches minces et refrigerateur a absorption
US5979440A (en) * 1997-06-16 1999-11-09 Sequal Technologies, Inc. Methods and apparatus to generate liquid ambulatory oxygen from an oxygen concentrator
US6856778B2 (en) * 2002-08-15 2005-02-15 Hewlett-Packard Development Company, L.P. System and method for recycling hydrocarbon-based carrier liquid
MY147654A (en) * 2002-11-13 2012-12-31 Deka Products Lp Pressurized vapor cycle liquid distillation
US7488158B2 (en) * 2002-11-13 2009-02-10 Deka Products Limited Partnership Fluid transfer using devices with rotatable housings
US8366883B2 (en) * 2002-11-13 2013-02-05 Deka Products Limited Partnership Pressurized vapor cycle liquid distillation
US8069676B2 (en) 2002-11-13 2011-12-06 Deka Products Limited Partnership Water vapor distillation apparatus, method and system
MXPA05005245A (es) * 2002-11-13 2005-09-08 Deka Products Lp Destilacion con presurizacion de vapor.
US8511105B2 (en) 2002-11-13 2013-08-20 Deka Products Limited Partnership Water vending apparatus
US7597784B2 (en) * 2002-11-13 2009-10-06 Deka Products Limited Partnership Pressurized vapor cycle liquid distillation
WO2006029457A1 (fr) * 2004-09-16 2006-03-23 Rheem Australia Pty Limited Chauffe-eau a recyclage
US8291968B2 (en) * 2005-08-09 2012-10-23 Eestech, Inc. Distributor for a flowable medium
US11826681B2 (en) 2006-06-30 2023-11-28 Deka Products Limited Partneship Water vapor distillation apparatus, method and system
KR101826492B1 (ko) 2007-06-07 2018-03-22 데카 프로덕츠 리미티드 파트너쉽 수증기 증류 장치, 방법 및 시스템
US11884555B2 (en) 2007-06-07 2024-01-30 Deka Products Limited Partnership Water vapor distillation apparatus, method and system
US8359877B2 (en) * 2008-08-15 2013-01-29 Deka Products Limited Partnership Water vending apparatus
EP2641036A4 (fr) * 2010-11-16 2016-08-17 Zahid Hussain Ayub Évaporateur à couche mince
US9211482B2 (en) * 2011-08-19 2015-12-15 Waterpointe—Global, LLC Methods and apparatus for purifying liquid using regenerating heat exchange
WO2014018896A1 (fr) 2012-07-27 2014-01-30 Deka Products Limited Partnership Commande de la conductivité dans une sortie d'eau de production destinée à un évaporateur
EP3786561B1 (fr) * 2019-09-02 2022-12-14 Orion Engineered Carbons IP GmbH & Co. KG Dispositif antisalissure pour échangeurs thermiques et son utilisation

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DE3324330A1 (de) * 1983-07-06 1985-01-24 Hans 2000 Hamburg Sladky Waermeuebertrager

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4799542A (en) * 1983-07-06 1989-01-24 Hans Sladky Heat exchanger with thin-film evaporator
US4848447A (en) * 1983-07-06 1989-07-18 Sladky Hans Tube-type heat exchanger and liquid distributor head therefor
FR2626191A1 (fr) * 1988-01-21 1989-07-28 Cezus Co Europ Zirconium Procede et dispositif d'exploitation d'un appareil fonctionnant par ruissellement d'un film liquide, et application a la separation des tetrachlorures de zr et hf
DE4228923A1 (de) * 1992-08-30 1994-03-03 Sladky Hans Vorrichtung zur Kühlung von Flüssigkeiten

Also Published As

Publication number Publication date
IL72371A (en) 1988-09-30
EP0131213A3 (en) 1985-05-15
DE3465623D1 (en) 1987-10-01
US4848447A (en) 1989-07-18
US4799542A (en) 1989-01-24
EP0131213B1 (fr) 1987-08-26
ATE29169T1 (de) 1987-09-15
DE3324330A1 (de) 1985-01-24

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