EP0680594A1 - Heat exchanger device and method of transferring heat - Google Patents

Heat exchanger device and method of transferring heat

Info

Publication number
EP0680594A1
EP0680594A1 EP94905894A EP94905894A EP0680594A1 EP 0680594 A1 EP0680594 A1 EP 0680594A1 EP 94905894 A EP94905894 A EP 94905894A EP 94905894 A EP94905894 A EP 94905894A EP 0680594 A1 EP0680594 A1 EP 0680594A1
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.)
Granted
Application number
EP94905894A
Other languages
German (de)
French (fr)
Other versions
EP0680594B1 (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

Links

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 heat exchanger structure according to the invention is particularly intended to optimize the heat transfer for use in which

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)

Abstract

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 based energy storage system without any considerable part of the supplied energy being lost. This problem is solved by a heat exchanger (2, 2a, 2b) according to the invention which is provided between the systems. This includes at least two concentric layers (12-15) of helically wound tubes (12a-15e) in a space that is surrounded by mainly cylindric surfaces (10-11). A method according to the invention for transfer of heat between a first fluid that circulates through a tube system (2, 2a, 2b) and a second fluid that surrounds the tube system consists in that the first fluid is pumped through the tube system containing capillary tubes so that the pressure drop across the tube system is at least 100 times larger than the pressure drop across the tube system in the second fluid which is self-circulating.

Description

Heat exchanger device and method of transferring heat.
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.
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 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
-the fluid is pumped on the primary side, i.e. that a relatively large pressure drop is accepted and is utilized for a good heat transfer,
-the fluid on the secondary side flows through the heat exchanger by means of self-circulation, i. e. that the struc¬ ture is optimized in order to obtain a large heat transfer coefficient at the outside despite an extremely low pressure drop,
-a relatively high temperature difference with these low flows on both sides of the heat exchanger is desired.
The invention will now be described in closer detail with reference to the drawing, on which
Figure 1 diagrammatically illustrates an energy storage tank with two alternative locations of a heat exchanger according to the invention,
Figure 2 diagrammatically illustrates production of a capillary tube intended to be included in a heat- exchanger according to the invention, and Figures 3 and 4 diagrammatically illustrate the structural design of the heat exchanger.
Figure 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. In order to minimize the costs of installation, pump and control equip¬ ment, the heat exchanger should either be in the tank (2a) built in or connected for self-circulation outside the tank
(2b) . At the alternative with built in heat exchanger 2a 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. At the other alternative 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.
In contrast to existing systems the heat exchanger according to the invention 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 loga¬ rithmic temperature difference between primary and secondary side of only about 5 degrees. Such 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. By using a number of slender tubes with thin walls with an inner diameter of less than 3 mm and an outer diameter of less than 5 mm 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.
Preferably 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.
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. For the various diameters a different number of capillaries is provided in respective helix in such a way that the number capillaries is generally proportional to the diameter.
In the embodiment according to Figure 3 and 4 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. If the ring shaped space between the central cylinder shaped body 11 and the outer tube 10, which is filled up by the helices 12-15 has the diameters 15 and 55 mm 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.
The tubes 12a-15e contained in the helices 12-15 are shown in Figure 4 for the sake of simplicity as circles to symbolize the approximate distribution of the tubes in an imagined cross section somewhere in the heat exchanger part 2 in Figure 3. By a correct sectional figure each cutaway tube end should obtain an elongated curved elliptical shape along the helix.
As previously mentioned all capillary tubes in the heat ex¬ changer shall have essentially the same length. Since the pressure drop increases somewhat with decreasing diameter of the tube helix this can be compensated by giving the tubes somewhat smaller length with decreasing helix diameter.
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. In the heat exchanger 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.
In an appropriately dimensioned heat exchanger according to the invention 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.

Claims

1. Method of transferring heat between a first fluid cir¬ culating through a tube system and a second fluid that sur- rounds the tube system, characterized in that the first fluid is pumped through the tube system, which is constructed from capillary tubes so that the pressure drop across the tube system is at least 100 times larger than the pressure drop across the tube system in the second fluid, which is self- circulating.
2. Method according to claim 1, characterized in that the pressure drop across the tube system in the first fluid amounts to 10 - 100 kPa.
3. Heat exchanger device for transfer of heat between a first fluid that circulates through a tube system to a second fluid that surrounds the tube system, characterized in that, the tube system (2) includes at least two concentric layers (12-15) of helically wound tubes (12a-15e) in a space that is surrounded by mainly cylindric surfaces (10-11) , that the tubes (12a-15e) are of a capillary type with small internal diameter, that the first fluid is intended to be pumped (3a- 4a,3b-4b) through the tube system (2, 2a, 2b) and that the space is intended to be arranged in or in connection to a tank (1) so that the second fluid can flow (5a-6a, 5b-6b) through the heat exchanger device by self-circulation.
4. Device according to claim 3 characterized in that the cylindrical surface (10) , which surrounds the tube system
(2,2a,2b) is extended to improve the self-circulation.
5. Device according to claim 3 or 4, characterized in that each layer of helically wound tubes (12-15) contains at least two tubes (12a-15e) , that all tubes (12a-15e) are of essentially the same length and that the number of tubes in respective layer in the main is proportional to the diameter of the helix.
6. Device according to any of claims 2-5, characterized in that the first fluid is pumped through the tube system containing capillary tubes so that the pressure drop across the tube system amounts to about 10-100 kPa and that the other fluid is self-circulating so that the pressure drop in this will be in the order of at the highest 100 Pa.
7. Device according to any of claims 2-6, characterized in that the inner diameter of the capillary tubes (12a-15e) is less than 3 mm and that the outer diameter is less than 5 mm.
8. Device according to any of claims 2-7, characterized in that the fluid volume in the space that surrounds the tube system (2,2a, 2b) is at least the double and preferably five times as large as the total fluid volume inside the tubes.
9. Device according to any of claims 2-8, characterized in that the tube system (2, 2a, 2b) is joined together by all capillary tubes at one end of the tube system being brought together in a cover, that the cover is filled by solder, that the cover is cut off so that all tube openings appear at the cut surface, which then simply can be connected to inflow and drain respectively.
10. Device according to any of claims 2-9, characterized in that in each layer of helically wound tubes (12-15) at least one consists of a tube that is surrounded by a flange and that the flange consists of a wire (9) wound about the tube (8) .
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
SE9300209A SE9300209L (en) 1993-01-23 1993-01-23 Heat
SE9300209 1993-01-23
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 true EP0680594A1 (en) 1995-11-08
EP0680594B1 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 (en)
AT (1) ATE196686T1 (en)
AU (1) AU5981994A (en)
DE (1) DE69426016T2 (en)
SE (1) SE9300209L (en)
WO (1) WO1994017355A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0942250A1 (en) * 1998-03-09 1999-09-15 Romabau AG Cryogenic heat exchanger

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 (en) * 1977-07-08 1979-07-12 Elpag Ag Chur, Chur (Schweiz) Process for the production of thin-walled metal pipes
NL7811007A (en) * 1978-11-06 1980-05-08 Akzo Nv Apparatus for transferring heat by means of hollow wires.
NO148830C (en) * 1979-10-15 1983-12-21 Cinderella DEVICE FOR HEATING OF FLUID, e.g. LIQUID FREON
DE3126618C2 (en) * 1981-07-06 1986-08-07 Akzo Gmbh, 5600 Wuppertal Hollow fiber heat exchanger
DE3320632A1 (en) * 1983-06-08 1984-12-13 Hoechst Ag, 6230 Frankfurt HEAT EXCHANGER

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9417355A1 *

Also Published As

Publication number Publication date
DE69426016D1 (en) 2000-11-02
AU5981994A (en) 1994-08-15
ATE196686T1 (en) 2000-10-15
SE9300209L (en) 1994-07-24
WO1994017355A1 (en) 1994-08-04
SE9300209D0 (en) 1993-01-23
DE69426016T2 (en) 2001-02-22
EP0680594B1 (en) 2000-09-27

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