EP0800048B1 - Wärmetauscher - Google Patents

Wärmetauscher Download PDF

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Publication number
EP0800048B1
EP0800048B1 EP95902945A EP95902945A EP0800048B1 EP 0800048 B1 EP0800048 B1 EP 0800048B1 EP 95902945 A EP95902945 A EP 95902945A EP 95902945 A EP95902945 A EP 95902945A EP 0800048 B1 EP0800048 B1 EP 0800048B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanging
flowpassages
annular
flowpassage
heat
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
EP95902945A
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English (en)
French (fr)
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EP0800048A1 (de
EP0800048A4 (de
Inventor
Shuzo Nomura
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.)
Individual
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Individual
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Filing date
Publication date
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Priority claimed from PCT/JP1994/002090 external-priority patent/WO1996018859A1/ja
Publication of EP0800048A1 publication Critical patent/EP0800048A1/de
Publication of EP0800048A4 publication Critical patent/EP0800048A4/de
Application granted granted Critical
Publication of EP0800048B1 publication Critical patent/EP0800048B1/de
Anticipated expiration legal-status Critical
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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
    • F28D1/00—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 is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—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 is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0206—Heat exchangers immersed in a large body of liquid
    • F28D1/0213—Heat exchangers immersed in a large body of liquid for heating or cooling a liquid in a tank
    • 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
    • F28D7/005—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 for only one medium being tubes having bent portions or being assembled from bent tubes or being tubes having a toroidal configuration

Definitions

  • the present invention relates to a heat exchanging flowpassage comprising the features of the preamble of claim 1 and to a heat exchanging apparatus using a heat exchanging flow passage.
  • nitrogen, oxygen, argon and other gases are stored in a superlow temperature storage tank in a liquefied state.
  • the stored liquefied gas is fed to an evaporator where the gas is vaporized and gasified at an atmospheric temperature or in hot water.
  • cooling heat of the liquefied gas is not effectively utilized but is wasted.
  • gases such as air, nitrogen, oxygen, argon, hydrogen, etc., or fluids such as a mixture of liquid and gas, etc.
  • a heat exchanger is intervened between a superlow temperature storage tank and an evaporator.
  • the conventional heat exchangers heretofore used have various configurations such as a coil type, a double tube type, a water injection type, a bushing type, a finned multitube type, etc.
  • the conventional heat exchangers as described above are poor in cooling effect because the fluid to be cooled flows through the tube regularly and is less affected by a temperature from wall surfaces of the tube. So, when being restricted as in an expansion valve at downstream in order to enhance the cooling effect, a large quantity of fluids cannot be cooled. Accordingly, there was a problem in that the conventional heat exchangers cannot be utilized in the case where a large quantity of fluids at a constant temperature need be secured.
  • the present invention is to overcome the problem as noted above with respect to prior art. It is an object of the present invention to provide a heat exchanging apparatus which can heat-exchange a large quantity of fluids efficiently without restricting the fluids, and accordingly, a large quantity of heat exchanging fluids at a constant pressure and at a constant temperature can be obtained and conveniently utilized, and in which the construction thereof can be simplified to thereby remove troubles and to lower the cost.
  • the heat exchanging flowpassage has tanks on the supply port side and on the discharge port side, and the supply path and the discharge path are communicated with the tanks.
  • the heat exchanging vessel when the heat exchanging vessel is filled with the heat transfer medium and the fluid for heat exchange is supplied from the supply path to the heat exchanging flowpassage, the thus supplied fluid in the heat exchanging flowpassage flows into the plurality of the peripheral flowpassages arranged in parallel and the communicating flowpassages for communicating them.
  • the fluid since the positions of the inlet and the outlet in the peripheral flowpassages are deviated in a peripheral direction, the fluid flows as a turbulence while repetitively impinging upon the wall surfaces of the heat exchanging flowpassages, during which the fluid can carry away heat of the heat transfer medium or heat of the fluid can be carried away by the heat transfer medium, and the fluid after heat exchange can be discharged outside the heat exchanging vessel from the discharge path.
  • the fluid is caused to flow in a turbulent state while repetitively impinging upon the wall surfaces of the heat exchanging flowpassages whereby the fluid is much affected by the temperature of the wall surfaces, and the fluids fed from the communicating flowpassages in the peripheral flowpassages are placed in the same condition and dispersed, thus enabling the effective heat exchange of a large quantity of fluids without restricting the fluids.
  • the heat exchanging flowpassages can be configured by connection of flowpassages, the construction can be simplified.
  • FIG. 1 is a perspective view of main parts showing a heat exchanging apparatus according to one embodiment of the present invention.
  • FIG. 2 is a schematic systematic view showing a using example in which the heat exchanging apparatus is incorporated between a superlow temperature storage tank for liquefied nitrogen and an evaporator.
  • FIG. 3 is a system constitutional view of an apparatus used for cooling experiments of dry air using the heat exchanging apparatus according to one embodiment of the present invention.
  • FIG. 4 is a graph showing the results of cooling experiments of dry air using a heat exchanging apparatus (a 2-stage ring type) according to one embodiment of the present invention (an axis of abscissa: passage time; an axis of ordinate: temperature of dry air to be discharged).
  • FIG. 5 is a graph showing the results of cooling experiments of dry air using a heat exchanging apparatus (a 5-stage ring type) according to one embodiment of the present invention (an axis of abscissa: passage time; an axis of ordinate: temperature of dry air to be discharged).
  • FIG. 6 is a table indicating the values every flow rate of dry air shown in the graph of FIG. 5.
  • FIG. 1 is a perspective view of main parts showing a heat exchanging apparatus according to one embodiment of the present invention
  • FIG. 2 is a schematic systematic view showing a using example in which the heat exchanging apparatus is incorporated between a superlow temperature storage tank for liquefied nitrogen and an evaporator.
  • a superlow temperature storage tank 1 can store liquefied nitrogen at -196°C.
  • the superlow temperatue storage tank 1 has its bottom communicated with a bottom of a heat exchanging vessel 3 of a heat exchanging apparatus 2 according to the present invention by means of a tube 4, and a valve 5 is provided in the middle of the tube 4.
  • An upper portion of the heat exchanging vessel 3 is communicated with an inlet of an evaporator 6 by means of a tube 8, and a supply tube 9 is communicatd with an outlet of the evaporator 6.
  • a heat exchanging flowpassage 10 is arranged within the heat exchanging vessel 3 of the heat exchanging apparatus 2 as will be described later, and a supply tube 11 and a discharge tube 12 for dry air inserted into the heat exchanging vessel 3 are communicated with the heat exchanging flowpassage 10.
  • Valves 13 and 14 are provided in the middle of the supply tube 11 and the discharge tube 12, respectively, the discharge tube 12 being communicated with a tank 15.
  • a plurality of supply tubes 16 are communicated with the tank 15, and a valve 17 is provided in the middle of each of the supply tubes 16.
  • the heat exchanging flowpassage 10 is composed of annular tubes 18 communicated in a circumferential direction which constitute peripheral flowpassages, communicating tubes 19 which constitute communicating passages, a tank 20 on the supply port side, a tank 21 on the discharge port side, and the like, as shown in FIG. 1.
  • Plural rows (5 rows in the illustrated embodiment) of the annular tubes 18 are arranged in a parallel state so as to have a desired spacing in a vertical direction around a vertical axis.
  • the annular tubes 18 adjacent to each other are communicated at plural locations by the communicating tubes 19 in a vertical direction.
  • the communicating tubes 19 in each of upper and lower rows are arranged substantially at equal intervals while being alternately deviated in a peripheral direction to each other so that the positions of an inlet and an outlet at the annular tube 18 in each row are alternately deviated in a peripheral direction, the inlet and the outlet being set so that the inlet and the outlet are not opposed on a straight line.
  • the tank 20 on the supply port side and the tank 21 on the discharge port side are arranged on the lower inside and on the upper inside of the plural rows of the annular tubes 18.
  • the tank 20 on the supply port side is communicated in its intermediate portion with the lowermost annular tube 18 by means of communicating tubes 22 arranged radially, and the tank 21 on the discharge port side is communicated in its upper end portion with the uppermost annular tube 18 by means of communicating tubes 23 arranged radially.
  • the supply tube 11 is communicated with the bottom of the tank 20 on the supply port side, and the discharge tube 12 is communicated with the bottom of the tank 21 on the discharge port side.
  • the heat exchanging vessel 3, the annular tubes 18 constituting the said heat exchanging flowpassage 10, the communicating tubes 19, the tanks 20 and 21, the communicating tubes 22 and 23, the supply tube 11, and the discharge tube 12 are formed of materials which withstand a low temperature, for example, such as stainless steel and copper.
  • a liquefied nitrogen which is a heat transfer medium, is supplied into and filled in the heat exchanging vessel 3 of the heat exchanging apparatus 2 by the tube 4 from the superlow temperature storage tank 1.
  • the vessel 3 is applied with a heat insulating material 7 to prevent it from being frozen.
  • dry air to be cooled by heat exchange is supplied to the tank 20 on the supply port side of the heat exchanging flowpassage 10 immersed with the liquefied nitrogen from the supply tube 11.
  • the dry air supplied into the tank 20 flows into the lowermost annular tube 18 passing through the communicating tubes 22, and flows from the lowermost annular tube 18 into its upper annular tube 18 passing through the communicating tubes 19.
  • the dry air sequentially flows into the upper level annular tube 18 passing through the communicating tubes 19, and flows from the uppermost annular tube 18 into the tank 21 on the discharge port side passing through the communicating tubes 23.
  • cooling heat of the liquefied nitrogen which is a refrigerant, is carried away from the wall surfaces thereof (that is, heat of dry air is carried away) to cool them while the dry air is flowing in a manner as described above.
  • the dry air flows into the lowermost annular tube 18 from the communicating tubes 22, it impinges upon the wall surface of the annular tube 18.
  • the dry air repetitively impinges upon the wall surface and flows in a turbulent state which is much affected by the temperature of the wall surface, and dry air fed from the communicating tubes 19 on each line in the annular tubes 18 is placed in the same condition so that dry air does not flow only in a fixed line but is dispersed. Therefore, it is possible to efficiently carry away cooling heat of the liquefied nitrogen (that is, heat of dry air is carried away).
  • the dry air cooled by the heat exchange as described above flows from the tank 21 into the tank 15 by the discharge tube 12, and can be distributed into using sites as desired by the plurality of the supply tubes 16. At each using site, the dry air can be mixed with air at normal temperature to adjust it to a suitable temperature for use.
  • the liquefied nitrogen from which cooling heat was carried away by the heat exchange is introduced into the evaporator 6 by the tube 8 and vaporized at an atmospheric temperature or in hot water into nitrogen gas. The thus obtained nitrogen gas can be supplied to the using site as desired by the supply tube 9.
  • liquefied nitrogen is directly supplied to the evaporator 6.
  • liquefied nitrogen is supplied to the evaporator 6, by which the temperature of liquefied nitrogen rises. Therefore, the evaporating efficiency obtained by the evaporator 6 can be improved.
  • FIG. 4 is a graph indicating temperatures of cooled dry air discharged from the heat exchanger with respect to the passage time from the start of supplying dry air in the case where a 2-stage ring type heat exchanger (in FIG. 1, two uppermost and lowermost annular tubes 18 are used, between which is connected the communicating tubes 19) was used.
  • FIG. 5 is a graph indicating temperatures of cooled dry air discharged from the heat exchanger with respect to the passage time from the start of supplying dry air in the case where a 5-stage ring type heat exchanger was used.
  • the tubes 18, 19, 11 and 12 having a circular section have been used for the peripheral flowpassage, the communicating flowpassage, the supply path, the discharge path or the like, it is to be noted that a square and an oval in section may be also used.
  • the peripheral flowpassage is not limited to an annular shape but a square and an oval can be used.
  • the communicating tubes 19 are not always arranged at equal intervals.
  • the annular tubes may be different in diameter.
  • the communicating tubes may not connect adjoining annular tubes, but for example, they may alternately connect annular tubes.
  • a heating medium can be used.
  • a fluid subjected to heat exchange there can be used, other than dry air, gases such as nitrogen, oxygen, hydrogen, argon, natural gas, etc., and a mixture of liquid and gas.
  • a plurality of rows of annular tubes 18 as peripheral flowpassages may be arranged in parallel in a lateral direction around a horizontal axis.
  • the present invention can be variously changed in design within a scope not departing from the basic technical idea thereof.
  • the heat exchanging vessel when the heat exchanging vessel is filled with the heat transfer medium and the fluid for heat exchange is supplied from the supply path to the heat exchanging flowpassage, the thus supplied fluid in the heat exchanging flowpassage flows into the plurality of the peripheral flowpassages arranged in parallel and the communicating flowpassages for communicating them.
  • the fluid since the positions of the inlet and the outlet in the peripheral flowpassages are deviated in a peripheral direction, the fluid flows as a turbulence while repetitively impinging upon the wall surfaces of the heat exchanging flowpassages, during which the fluid can carry away heat of the heat transfer medium or heat of the fluid can be carried away by the heat transfer medium, and the fluid after heat exchange can be discharged outside the heat exchanging vessel from the discharge path.
  • the fluid is caused to flow in a turbulent state while repetitively impinging upon the wall surfaces of the heat exchanging flowpassages whereby the fluid is much affected by the temperature of the wall surfaces.
  • the temperature is lowered due to the turbulent expansion of the fluid, and the fluids fed from the communicating flowpassages in the peripheral flowpassages are placed in the same condition and dispersed without flowing in a specified communication flow passesge, thus enabling the effective heatexchange of a large quantity of fluids without restricting the fluids. Accordingly, a large quantity of heat exchanging fluids at a constant temperature can be obtained and conveniently utilized.
  • the heat exchanging flowpassages can be configured by connection of flowpassages, the construction can be simplified. Accordingly, troubles can be removed, and the cost can be lowered.
  • the heat exchanging flowpassage has tanks on the supply port side and on the discharge port side, respectively, and the supply path and the discharge path are communicated with the respective tanks whereby the fluid is once stayed in the tank on the supply port side from the supply path and the fluid can be supplied to the communicating flowpassages in each line at constant pressure and at constant flow rate, and the fluid heat exchanged to a constant temperature is once stayed in the tank on the exhaust port side from the communicating flowpassages in each line and can be supplied to the using site at constant pressure and at constant flow rate, thus enabling further stable utilization.
  • the heat exchanging apparatus is useful as a heat exchanging apparatus for air cooling and as a heat exchanging apparatus for air conditioning having a large capacity, and is suitable for use with a heat exchanging apparatus particularly for a freezing warehouse or the like which is large in scale and requires a low temperature.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (8)

  1. Wärmetauscher-Strömungskanal (10) für eine Wärmeaustauschvorrichtung (2), aufweisend:
    mehrere ringförmige Strömungskanäle (18), die im wesentlichen parallel angeordnet sind, und
    mehrere Verbindungs-Strömungskanäle (19), welche die ringförmigen Strömungskanäle (18) an mehreren Stellen verbinden,
    dadurch gekennzeichnet, dass
    die Verbindungs-Strömungskanäle (19) in Umfangsrichtung zueinander versetzt abzweigen, so dass die Stellen einer Einlaßöffnung und einer Auslaßöffnung an jedem ringförmigen Strömungskanal (18) in Umfangsrichtung versetzt angeordnet sind.
  2. Wärmetauscher-Strömungskanal (10) für eine Wärmeaustauschvorrichtung (2) nach Anspruch 1,
    dadurch gekennzeichnet, dass
    die Verbindungs-Strömungskanäle (19) zwischen zwei ringförmigen Strömungskanälen (18) im wesentlichen in gleichen Abständen angeordnet sind.
  3. Wärmetauscher-Strömungskanal (10) für eine Wärmeaustauschvorrichtung (2) nach Anspruch 1 oder 2,
    dadurch gekennzeichnet, dass
    ein Tankbehälter (20) auf der Seite der Zufuhröffnung und ein Tankbehälter (21) auf der Seite der Abführöffnung vorgesehen ist.
  4. Wärmetauscher-Strömungskanal (10) für eine Wärmeaustauschvorrichtung (2) nach Anspruch 3,
    dadurch gekennzeichnet, dass
    der Tankbehälter (20) auf der Seite der Zuführöffnung an ein Ende der ringförmigen Strömungskanäle (18) angeschlossen ist und der Tankbehälter (21) auf der Seite der Abführöffnung an dem anderen Ende der ringförmigen Strömungskanäle (18) angeschlossen ist.
  5. Wärmetauscher-Strömungskanal (10) für eine Wärmeaustauschvorrichtung (2) nach Anspruch 4,
    dadurch gekennzeichnet, dass
    ein Ende der ringförmigen Strömungskanäle (18) durch Verbindungs-Strömungskanäle (22) an den Tankbehälter (20) auf der Seite der Zuführöffnung angeschlossen ist.
  6. Wärmetauscher-Strömungskanal (10) für eine Wärmeaustauschvorrichtung (2) nach Anspruch 4 oder 5,
    dadurch gekennzeichnet, dass
    das andere Ende der ringförmigen Strömungskanäle (18) durch Verbindungs-Strömungskanäle (23) an den Tankbehälter (21) auf der Seite der Abführöffnung angeschlossen ist.
  7. Wärmeaustauschvorrichtung (2), aufweisend:
    einen Wärmetauscher-Behälter (3), dem ein Wärmeübertragungsmedium zugeführt und entnommen wird,
    einen Wärmetauscher-Strömungskanal (10) nach den Ansprüchen 1 bis 6, der im Wärmetauscher-Behälter (3) vorgesehen ist, und
    einen Zuführkanal (11) und einen Abführkanal (12), welche an den Wärmetauscher-Strömungskanal (10) angeschlossen sind.
  8. Wärmeaustauschvorrichtung (2) nach Anspruch 7,
    dadurch gekennzeichnet, dass
    der Zuführkanal (11) an den Tankbehälter (20) auf der Seite der Zuführöffnung angeschlossen ist und der Abführkanal (12) an den Tankbehälter (21) auf der Seite der Abführöffnung angeschlossen ist.
EP95902945A 1994-12-14 1994-12-14 Wärmetauscher Expired - Lifetime EP0800048B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
BR9408636A BR9408636A (pt) 1994-12-14 1994-12-14 Passagem de fluxo de troca de calor para aparelho de troca de calor e aparelho de troca de calor
PCT/JP1994/002090 WO1996018859A1 (en) 1994-12-14 1994-12-14 Heat exchanger

Publications (3)

Publication Number Publication Date
EP0800048A1 EP0800048A1 (de) 1997-10-08
EP0800048A4 EP0800048A4 (de) 1999-07-07
EP0800048B1 true EP0800048B1 (de) 2003-04-16

Family

ID=25664687

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95902945A Expired - Lifetime EP0800048B1 (de) 1994-12-14 1994-12-14 Wärmetauscher

Country Status (3)

Country Link
EP (1) EP0800048B1 (de)
AU (1) AU705772B2 (de)
BR (1) BR9408636A (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006005885A1 (de) * 2006-02-09 2007-08-16 Messer Group Gmbh Vorrichtung zum Kühlen von flüssigen oder gasförmigen Medien

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191401364A (en) * 1913-01-18 1914-03-26 Karl Schroeder Improvements in Steam-heated Radiators.
AU590192B2 (en) * 1984-02-13 1989-11-02 Ice-Cel Thermal Storage Pty Limited Heat exchanger
CA1306535C (en) * 1988-08-09 1992-08-18 Sytec Enclosures Company, A Partnership Shelter device for the protection and thermal conditioning of apparatus, in particular electronic apparatus generating heat
DE59006905D1 (de) * 1990-03-09 1994-09-29 Zehnder Verkauf Verwaltung Heizkörper.
US5178124A (en) * 1991-08-12 1993-01-12 Rheem Manufacturing Company Plastic secondary heat exchanger apparatus for a high efficiency condensing furnace
DE9406183U1 (de) * 1994-04-14 1994-07-07 H. Krantz-Tkt Gmbh, 51465 Bergisch Gladbach Kühleinrichtung

Also Published As

Publication number Publication date
AU705772B2 (en) 1999-06-03
BR9408636A (pt) 1997-12-23
AU1200295A (en) 1996-07-03
EP0800048A1 (de) 1997-10-08
EP0800048A4 (de) 1999-07-07

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