EP0680594B1 - Heat exchanger device and method of transferring heat - Google Patents

Heat exchanger device and method of transferring heat Download PDF

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Publication number
EP0680594B1
EP0680594B1 EP94905894A EP94905894A EP0680594B1 EP 0680594 B1 EP0680594 B1 EP 0680594B1 EP 94905894 A EP94905894 A EP 94905894A EP 94905894 A EP94905894 A EP 94905894A EP 0680594 B1 EP0680594 B1 EP 0680594B1
Authority
EP
European Patent Office
Prior art keywords
fluid
tube system
tubes
tube
heat exchanger
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.)
Expired - Lifetime
Application number
EP94905894A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0680594A1 (en
Inventor
Klaus Lorenz
Lars Broman
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.)
SOLVIS Solarsysteme GmbH
Original Assignee
SOLVIS Solarsysteme GmbH
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 SOLVIS Solarsysteme GmbH filed Critical SOLVIS Solarsysteme GmbH
Publication of EP0680594A1 publication Critical patent/EP0680594A1/en
Application granted granted Critical
Publication of EP0680594B1 publication Critical patent/EP0680594B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements

Definitions

  • the present invention refers to heat exchangers and in particular to heat exchangers in low temperature systems where heat is to be transferred from a fluid in a circulatory system to a fluid in another system.
  • An example of use of such systems is between a solar collector circuit and an accumulator tank.
  • Heat exchangers are known in the art, for example of US 4,619,317, US 3,556,199, US 3,448,792, SU 958 830.
  • US 4,619,317 relates to a heat exchanger comprising a support frame and a feed line, a heater for the forward flow, heat exchange tubes, a heater for the return flow and a discharge line for a heat transfer medium.
  • the heat exchange tubes are capillary tubes which are fixed interlocking one another by means of connecting elements, and the ends of the capillary tubes lead into the forward flow heater and the return flow heater of the heat transfer medium.
  • the heat exchange capillaries particularly have an external diameter of from 0,1 to 10 mm and wall thicknesses of from 40 % to 5 % of the external diameter of the heat exchange capillaries.
  • the clear spacing between the capillary windings are 1 to 5 times the external diameter of the heat exchange capillaries. Large and small heat exchanger packs or blocks of any desired capacity can be produced.
  • the individual helices of the heat exchange capillaries always have the same pressure drop being provided with the same internal diameter and having the same length.
  • the heat exchange capillaries are arranged with a mutual interlock and connected to one another by connecting elements. These are for example straight wires or even capillaries mounted between the support frames.
  • the US 3,556,199 relates to a free convection cooling method and apparatus.
  • a heat exchanger submerged in a coolant bath being constructed and arranged to obtain the greatest possible temperature-density differential between the circulating transport fluid and environmental coolant productive of strong natural convection currents.
  • heated fluid from a source is pumped to an inlet manifold.
  • the actual heat source is formed by an engine or electronic package or the like with respect to which the heat transport fluid is passed in heat absorbing relation.
  • the liquid of the bath the heat exchanger being provided in has a temperature lower than that at which transport fluid is delivered to heat exchanger.
  • the temperature differential is utilised to cool or to remove excess heat from the transport fluid. Nowhere in the heat exchanger are conditions created in which transport fluid of maximum temperature encounters coolant of minimum temperature. Hot spots or isolated locations of maximum temperature differential which may produce localised heavy convection currents with little or no convection flow in other portions of the heat exchanger, are avoided.
  • the US 3,448,792 relates to a formal convection condenser and a method of use.
  • a rapid heat transfer from a heat exchange fluid to a cooler fluid is effected by deposition of a condenser in the cooler fluid.
  • the heat condenser comprises at least two coils, a smaller coil being positioned within a larger coil.
  • the coils are held in a spaced relationship to each other and an inner and an outer shielding by spacers.
  • the spacers are providing a vertical gap between the coils and shield means.
  • the condenser apparatus is positioned in a liquid container or tank containing a liquid such as water.
  • the apparatus is preferably positioned near the bottom of the container.
  • the heat exchange fluid is superheated steam of a temperature of about 212 to about 900 degrees Fahrenheit or more.
  • the superheated steam is gained for example by passing water at a temperature of about 70 degrees Fahrenheit through a heat storage composition maintained at a temperature of about 900 degrees Fahrenheit. Afterwards the superheated steam is passed into the condenser being submerged in a tank of water. The water having an original temperature of about 70 degrees Fahrenheit afterwards is rapidly heated at a temperature of about 140 degrees Fahrenheit. Thereby strong convection currents are generated by the heat differential. This causes a rapid circulation of water throughout the tank of water being heated.
  • a problem in connection with fluid operated solar collector systems is in a simple and non-expensive way to be able to separate the circulatory system of the solar collector from a fluid operated energy storage system without any considerable part of the supplied energy being lost.
  • This problem is solved by a heat exchanger according to the invention as claimed, the heat exchanger being provided between the systems.
  • the heat exchanger structure according to the invention is particularly intended to optimize the heat transfer for use in which
  • FIG. 1 shows a typical mode of application for the heat exchanger according to the invention in the solar heating technique.
  • the contents of an accumulator tank 1 is heated by heat exchange from the solar collector fluid.
  • the heat exchanger should either be in the tank (2a) built in or connected for self-circulation outside the tank (2b).
  • the solar collector fluid is supplied at 3a and is returned at 4a while self- circulation 5a, 6a occurs in the tank 1 through the heat exchanger 2a.
  • the solar collector fluid circulates the path 3b, 2b, 4b while the fluid in the tank 1 is supplied to the heat exchanger 2b at 5b and is passed through tubes 7 back to the tank at 6b.
  • the heat exchanger performs a temperature raise of the cold water at the bottom of the tank from for example 30 °C up to 60 to 70 °C at through flow. This is performed at a logarithmic temperature difference between primary and secondary side of only about 5 degrees.
  • a heat exchanger promotes the stratification of the tank, enables low values of flows in the solar collector circuit and totally leads to a system with higher performance. This can be accomplished by lower material consumption in the form of thinner tubes in the solar circuit and much less material in the heat exchanger which makes the system much more cost-effective.
  • the heat exchanger is constructed from capillary tubes connected in parallel.
  • a substantially laminar flow in the tubes is obtained, whereby the the heat transfer between the fluid that is pumped through the tubes and the surrounding fluid is considerably improved with respect to tubes of thicker dimensions.
  • the heat exchanger will be particularly well dimensioned at an inner diameter of 1 - 2 mm, preferably 1.5 mm and a wall thickness less than 0.5 mm, preferably about 0.25 mm.
  • the length of each tube should be one metre or more and the number of tubes depends on the power that is to be transmitted.
  • the sizes are based on tubes of copper and pumping of water with antifreeze in the primary circuit.
  • the capillary tubes can be arranged in various ways in order to obtain a good heat exchange, whereby in itself prior known arrangements may be used.
  • the capillary tubes 8 on the outside are provided with a sparsely wound on wire 9, see figure 2.
  • the wire 9, which preferably is constituted by a smooth wire of copper, in the completed heat exchanger serves the function that it partly creates a defined distance between concentric helices of capillary tubes provided with the wire, and partly enhances the heat transfer on the outside by using flange effect and eddy forming of the wire.
  • the capillary tubes 8 can also be wound by a wire of other metal or by a wire consisting of several entwined thinner wires. Normally the wound on wire has only to be fixed to the capillary tube at the ends thereof but it is also possible to fix the wire at evenly spaced intervals or along the entire length thereof. Suitable means for this may be soldering, bonding, immersing in liquid tin or the like. As the heat exchanger is constructed from helically wound capillary tubes all or only a part of the capillary tubes can be wound with wire. It is also possible to use capillary tubes without a wound on wire for a heat exchanger according to the invention, whereby other means may be arranged to keep appropriate distance between the tube helices.
  • capillary tubes In order to produce a heat exchanger according to the invention a number of capillary tubes are first cut to mainly equal length. All capillary tubes will be connected in parallel and they have to be approximately of equal length in order to obtain the same pressure drop and by this the same temperature drop at flowing through at the inside.
  • the capillary tubes then are formed to helices with various diameters in such a way that the pitch angle for each helix is alike. Thereby is achieved that the various helices obtain mainly the same length.
  • a different number of capillaries is provided in respective helix in such a way that the number capillaries is generally proportional to the diameter.
  • the helix 12 with the smallest diameter contains two capillary tubes 12a and 12b wound in helix with the diameter 20 mm whereby the number of turns per tube becomes about 40 and the length of the helix about 400 mm.
  • the next helix 13 with the diameter 30 mm contains three capillary tubes (13a-13c) forming about 27 turns each in order to attain the same length.
  • the third turn 14 with 40 mm diameter contains four capillary tubes (14a-14d), which each attain about 20 turns and the fourth helix 15 with 40 mm diameter contains five capillary tubes (15a-15e), which attains about 16 turns for same length.
  • the 14 capillary tubes in the example will fill up this space equally and the heat transfer from the primary flow to the secondary becomes equal over the entire tube slot.
  • the external diameter of the capillary tube was 2,8 mm and the wire 1 mm.
  • the surrounding tube 10 extends longer than the very heat exchanger part 2 with the capillary tubes to improve the self circulation.
  • the tube 10 shall also be able to accommodate couplings (not shown) between the capillary tubes and the external solar collector circuit, which can be realized in an arbitrary way which allows mainly uniform tube lengths and minor obstruction in the self circulatory circuit.
  • Coupling to the ends of the capillary tubes can preferably be performed by following method: All tubes are brought together into a cover, after which the cover is filled with solder. Thereafter the cover is cut off so that all tube openings appear in the section surface, which then simply can be coupled to inflow and drain respectively. This procedure has proved to be a cost-effective method to join the tubes, without which a heat exchanger with many capillary tubes according to the invention could not have been produced without problems.
  • each cutaway tube end should obtain an elongated curved elliptical shape along the helix.
  • the heat exchanger 2 In order to allow self circulation in the secondary circuit the heat exchanger 2 needs also to be dimensioned such, that the secondary fluid flow is not obstructed too much by the package of helically wound capillary tubes. This is achieved thereby that the fluid volume surrounding the capillary tubes in the heat exchanger part 2 relates to the fluid volume inside the capillary tubes as at least 2:1 and preferably more than 5:1. There is of course also an upper limit above which the heat transfer is deteriorated.
  • the flow direction of the fluid in the self circulatory circuit is in the main perpendicular to the capillary tubes, whereby the specific heat transfer capability is enhanced.
  • a combination of heat transfer from a tube in undisturbed fluid and superponated active flow is utilized and is determined by the density difference between cold and hot water at inlet and outlet respectively secondary side of the heat exchanger as well as the total height of the tube 10.
  • the pressure drop on the self-circulatory side can be within the interval 30 - 100 Pa.
  • the internal pressure loss by pumping should be at least about 100 times larger, preferably about 1000 times larger or more, and can be within the interval of about 10 - 100 kPa.

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)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
EP94905894A 1993-01-23 1994-01-24 Heat exchanger device and method of transferring heat Expired - Lifetime EP0680594B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
SE9300209 1993-01-23
SE9300209A SE9300209L (sv) 1993-01-23 1993-01-23 Värmeväxlare
PCT/SE1994/000048 WO1994017355A1 (en) 1993-01-23 1994-01-24 Heat exchanger device and method of transferring heat

Publications (2)

Publication Number Publication Date
EP0680594A1 EP0680594A1 (en) 1995-11-08
EP0680594B1 true EP0680594B1 (en) 2000-09-27

Family

ID=20388645

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94905894A Expired - Lifetime EP0680594B1 (en) 1993-01-23 1994-01-24 Heat exchanger device and method of transferring heat

Country Status (6)

Country Link
EP (1) EP0680594B1 (sv)
AT (1) ATE196686T1 (sv)
AU (1) AU5981994A (sv)
DE (1) DE69426016T2 (sv)
SE (1) SE9300209L (sv)
WO (1) WO1994017355A1 (sv)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0942250A1 (de) * 1998-03-09 1999-09-15 Romabau AG Tieftemperatur-Wärmetauscher

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3116790A (en) * 1958-03-28 1964-01-07 Kohlenscheidungs Gmbh Tube heat exchanger
US3251401A (en) * 1964-05-11 1966-05-17 M B Gardner Co Inc Heat exchanger
US3448792A (en) * 1966-11-07 1969-06-10 Hooker Chemical Corp Thermal convection condenser and method of use
US3556199A (en) * 1968-05-13 1971-01-19 United Aircraft Prod Free convection cooling method and apparatus
US3718181A (en) * 1970-08-17 1973-02-27 Du Pont Plastic heat exchange apparatus
DE2731027C2 (de) * 1977-07-08 1979-07-12 Elpag Ag Chur, Chur (Schweiz) Verfahren zur Herstellung von dünnwandigen Metallrohren
NL7811007A (nl) * 1978-11-06 1980-05-08 Akzo Nv Inrichting voor het overdragen van warmte door middel van holle draden.
NO148830C (no) * 1979-10-15 1983-12-21 Cinderella Anordning til forvarming av vaeske, f.eks. vaeskeformig freon
DE3126618C2 (de) * 1981-07-06 1986-08-07 Akzo Gmbh, 5600 Wuppertal Wärmeaustauscher aus Hohlfäden
DE3320632A1 (de) * 1983-06-08 1984-12-13 Hoechst Ag, 6230 Frankfurt Waermeaustauscher

Also Published As

Publication number Publication date
SE9300209D0 (sv) 1993-01-23
DE69426016D1 (de) 2000-11-02
EP0680594A1 (en) 1995-11-08
WO1994017355A1 (en) 1994-08-04
SE9300209L (sv) 1994-07-24
ATE196686T1 (de) 2000-10-15
AU5981994A (en) 1994-08-15
DE69426016T2 (de) 2001-02-22

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