EP0096605A1 - Wärmetauscher mit ringförmigen Kanälen, der mit rotierend und pulsierend strömenden Medien wirkt - Google Patents

Wärmetauscher mit ringförmigen Kanälen, der mit rotierend und pulsierend strömenden Medien wirkt Download PDF

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Publication number
EP0096605A1
EP0096605A1 EP83400976A EP83400976A EP0096605A1 EP 0096605 A1 EP0096605 A1 EP 0096605A1 EP 83400976 A EP83400976 A EP 83400976A EP 83400976 A EP83400976 A EP 83400976A EP 0096605 A1 EP0096605 A1 EP 0096605A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
cylinders
fluids
plate
exchanger according
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Withdrawn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
EP83400976A
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English (en)
French (fr)
Inventor
Nathan Awerbuch
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.)
SUPRATHERM Sarl
Original Assignee
SUPRATHERM Sarl
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 SUPRATHERM Sarl filed Critical SUPRATHERM Sarl
Publication of EP0096605A1 publication Critical patent/EP0096605A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/10—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by imparting a pulsating motion to the flow, e.g. by sonic vibration
    • 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
    • F28D7/06—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 having a single U-bend

Definitions

  • the present invention relates to a heat exchanger with a very high exchange rate and a relatively low pressure drop for all fluids in general and more particularly for the recovery of heat in combustion gases or hot gases from ovens or dryers. .
  • the turbulent regime causes the renewal of the boundary layers and therefore the heat transfer.
  • the turbulent regime is obtained by an increase in the speed of the fluids or by the insertion of obstacles on the course.
  • this turbulent regime defined as disordered displacements of small volumes of fluids in all directions and at variable speeds, leads to collisions with these turbulent masses and therefore constitutes a waste of energy.
  • this turbulence concerns the entire mass of the fluids while the target boundary layers constitute only a very small percentage of the total mass of the fluids.
  • Fig. 1 shows the sector of an annular channel in which circulates a fluid in gyratory movement.
  • the latter can be caused by the rotation of the concave wall (Couette experiment) or by a tangential supply of the fluid (Görtler hypothesis experimentally confirmed by Liepmann in 1943). Note the tendency of the fluid to deviate from the circular direction to the tangential direction.
  • Fig. 2 shows an annular channel in which a fluid animated by a gyratory movement flows, which has generated a stable regime of secondary, transverse movements in the form of co-directional rotation rollers (or rings).
  • Fig. 3 shows these rollers in perspective.
  • These primary as well as secondary movements have the particularity of preserving their non-turbulent regime at very high "relative speeds" which can exceed more than ten times the limit speeds of change from non-turbulent regime to turbulent, of the same fluids, s 'flowing in the same annular canals but in a rectilinear regime therefore non-gyratory.
  • relative speed should be understood to mean the speed of passage of the fluid in front of the concave wall. This can be 10 to 20 times greater than the speed of translation of the fluid which results from the volume flow in the section of the annular channel per unit of time.
  • the present invention implements the action of a valve with periodic closure of a properly designed aeraulic circuit.
  • Any valve with periodic opening and closing causes pulsations of a circulating fluid passing through this valve. If this fluid is compressible and transported by a ventilator, it is found at the closure of the pressure valve at the maximum pressure supplied by the ventilator while accumulating this pressure in the capacity supplied on one side but closed at the outlet. At the opening of the valve the capacity (collector) discharges the accumulated volume at a speed corresponding to its overpressure and to the section of the outlet orifice.
  • valves causing these pulsations can be either mechanical or pneumatic.
  • the rotation of a disc ("butterfly") or of a plate-sealing the outlet section of the collectors, devices fixed to a shaft, by a motor is controlled as indicated on board 2 No. 5 and 10.
  • Figs. 2 and 3 show a tangential supply generating a gyratory flow of the fluid.
  • Fig. 2 a higher speed in the vicinity of the concave curvatures of the cylinders, caused by centrifugal force.
  • Fig. 3 shows that as soon as a certain speed is established, the current abuts against the inverter due to its inertia, which generates turbulence the intensity of which is always equal to the maximum manometric power of the fan at its operating speed.
  • These turbulences constitute an impassable obstacle by the fluid, this results in a fraction of a second of zero flow, constituting the closed position of the valve.
  • the beats of the pneumatic valve are a function of: flow rates, channel dimensions and characteristic curves of the fans. For flow rates ranging from 3,000 to 30,000 m 3 / hour, it can be seen that the pulsations thus generated are between 70 and 7 Hz.
  • the exchangers collectors play the role of a compressed air tank, whose action is in this case comparable to that of a spring or a pendulum which consists in restoring the accumulated energy. .
  • a pneumatic valve constituted by the two contiguous channels with a mechanical valve equipping the outlet of the second fluid as indicated diagrammatically on board No. S.
  • a mechanical valve equipping the outlet of the second fluid as indicated diagrammatically on board No. S.
  • this apparatus can be made economically from acid-resistant steel and used for cooling sulfur-containing combustion gases ("fumes") until the condensation of water vapor produced by the combustion of fuels containing hydrogen.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Surgical Instruments (AREA)
  • Gloves (AREA)
  • Materials For Medical Uses (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP83400976A 1982-06-04 1983-05-16 Wärmetauscher mit ringförmigen Kanälen, der mit rotierend und pulsierend strömenden Medien wirkt Withdrawn EP0096605A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR8209725A FR2528163B1 (fr) 1982-06-04 1982-06-04 Echangeur de chaleur a canaux annulaires fonctionnant avec des fluides en regime d'ecoulement giratoire et pulsatoire

Publications (1)

Publication Number Publication Date
EP0096605A1 true EP0096605A1 (de) 1983-12-21

Family

ID=9274622

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83400976A Withdrawn EP0096605A1 (de) 1982-06-04 1983-05-16 Wärmetauscher mit ringförmigen Kanälen, der mit rotierend und pulsierend strömenden Medien wirkt

Country Status (6)

Country Link
EP (1) EP0096605A1 (de)
JP (1) JPS594886A (de)
DK (1) DK253683A (de)
FI (1) FI832017L (de)
FR (1) FR2528163B1 (de)
NO (1) NO832013L (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100126033A1 (en) * 2006-04-21 2010-05-27 Osvaldo Ricardo Haurie Cylindrical dryer having conduits provided within a plurality of holding plates
CN108759542A (zh) * 2018-06-12 2018-11-06 丁厚全 一种曲面板圆桶式换热器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6157093A (ja) * 1984-08-28 1986-03-22 Fujitsu Ltd 磁気バブルメモリカセツト装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR55494E (fr) * 1942-12-12 1952-06-30 Westinghouse Freins & Signaux Perfectionnements aux échangeurs de chaleur
US2662749A (en) * 1949-01-21 1953-12-15 Hydrocarbon Research Inc Annular flow heat exchanger
US2870997A (en) * 1953-06-10 1959-01-27 Soderstrom Sten Heat exchanger
FR1257804A (fr) * 1960-02-25 1961-04-07 Thomson Houston Comp Francaise Perfectionnements aux chemises d'eau de refroidissement
FR1419583A (fr) * 1964-01-17 1965-12-03 échangeurs de chaleur à chicanes emboîtables et démontables
FR2107868A1 (de) * 1970-09-22 1972-05-12 Interatom
FR2307237A1 (fr) * 1975-04-10 1976-11-05 Conditionair Appareil echangeur-refroidisseur pour fluides gazeux

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR55494E (fr) * 1942-12-12 1952-06-30 Westinghouse Freins & Signaux Perfectionnements aux échangeurs de chaleur
US2662749A (en) * 1949-01-21 1953-12-15 Hydrocarbon Research Inc Annular flow heat exchanger
US2870997A (en) * 1953-06-10 1959-01-27 Soderstrom Sten Heat exchanger
FR1257804A (fr) * 1960-02-25 1961-04-07 Thomson Houston Comp Francaise Perfectionnements aux chemises d'eau de refroidissement
FR1419583A (fr) * 1964-01-17 1965-12-03 échangeurs de chaleur à chicanes emboîtables et démontables
FR2107868A1 (de) * 1970-09-22 1972-05-12 Interatom
FR2307237A1 (fr) * 1975-04-10 1976-11-05 Conditionair Appareil echangeur-refroidisseur pour fluides gazeux

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100126033A1 (en) * 2006-04-21 2010-05-27 Osvaldo Ricardo Haurie Cylindrical dryer having conduits provided within a plurality of holding plates
US8127462B2 (en) * 2006-04-21 2012-03-06 Osvaldo Ricardo Haurie Cylindrical dryer having conduits provided within a plurality of holding plates
CN108759542A (zh) * 2018-06-12 2018-11-06 丁厚全 一种曲面板圆桶式换热器
CN108759542B (zh) * 2018-06-12 2024-05-10 丁厚全 一种曲面板圆桶式换热器

Also Published As

Publication number Publication date
FI832017A0 (fi) 1983-06-03
FI832017L (fi) 1983-12-05
FR2528163A1 (fr) 1983-12-09
FR2528163B1 (fr) 1988-07-08
JPS594886A (ja) 1984-01-11
NO832013L (no) 1983-12-05
DK253683D0 (da) 1983-06-03
DK253683A (da) 1983-12-05

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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Effective date: 19830610

AK Designated contracting states

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STAA Information on the status of an ep patent application or granted ep patent

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18D Application deemed to be withdrawn

Effective date: 19850513

RIN1 Information on inventor provided before grant (corrected)

Inventor name: AWERBUCH, NATHAN