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WO1999015847A1 - Echangeur de chaleur et dispositif de refroidissement/chauffage d'eau par absorption utilisant ledit echangeur de chaleur - Google Patents

Echangeur de chaleur et dispositif de refroidissement/chauffage d'eau par absorption utilisant ledit echangeur de chaleur Download PDF

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Publication number
WO1999015847A1
WO1999015847A1 PCT/JP1997/003331 JP9703331W WO9915847A1 WO 1999015847 A1 WO1999015847 A1 WO 1999015847A1 JP 9703331 W JP9703331 W JP 9703331W WO 9915847 A1 WO9915847 A1 WO 9915847A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat transfer
tube
transfer tube
heat
heat exchanger
Prior art date
Application number
PCT/JP1997/003331
Other languages
English (en)
Japanese (ja)
Inventor
Masayuki Shimamura
Michihiko Aizawa
Tomihisa Oouchi
Original Assignee
Hitachi, Ltd.
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 Hitachi, Ltd. filed Critical Hitachi, Ltd.
Priority to PCT/JP1997/003331 priority Critical patent/WO1999015847A1/fr
Publication of WO1999015847A1 publication Critical patent/WO1999015847A1/fr

Links

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
    • F28D5/00—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, using the cooling effect of natural or forced evaporation
    • F28D5/02—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, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B37/00—Absorbers; Adsorbers
    • 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
    • F28F1/006—Tubular elements; Assemblies of tubular elements with variable shape, e.g. with modified tube ends, with different geometrical features
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/62—Absorption based systems

Definitions

  • the present invention relates to an absorption chiller / heater used for a heat exchanger, an air conditioner, and the like, and more particularly to an absorption chiller / heater that can be downsized by improving the efficiency of a heat exchanger of an evaporator and an absorber.
  • heat exchangers used for evaporators, absorbers, low-temperature regenerators, etc. for absorption chillers / heaters have been used in combination with shells and coils, or in combination with general shells and tubes. ing.
  • multiple heat transfer tubes are passed through a high vacuum box-shaped shell, and water is passed through the heat transfer tubes to exchange heat.
  • a box with a partition plate is installed so that the water that passes through the heat transfer tube can be turned multiple times outside the shell.
  • the inside of the heat transfer tube penetrated through the high vacuum shell must be expanded from the inside of the heat transfer tube penetrated into the hole of the tube sheet and sealed so as to seal the pressure obtained by adding water pressure to atmospheric pressure.
  • heat transfer tube and heat transfer tube If there is no interval, or the interval is 1 mn! If it is as narrow as ⁇ 3 mm, the heat transfer tube cannot be brought into close contact with the hole in the tube sheet by expansion. The reason for this is that, because the expansion of the heat transfer tube and the hole formed in the tube sheet are closely adhered to each other by plastic working, if the space between the heat transfer tube and the heat transfer tube is small, the adjacent heat transfer tube will be distorted during the expansion. For this reason, even if the tube is bent and the heat transfer tube adheres tightly, the seal loosens. Therefore, in order to expand the tubes, it is necessary to form a group of heat transfer tubes with a gap of at least 3 mm between the heat transfer tubes, which makes it impossible to reduce the size of the heat exchanger.
  • a refrigerant generally water
  • a solution generally lithium bromide aqueous solution
  • An object of the present invention is to reduce the vertical interval between heat transfer tube groups in a shell and to promote the spread of liquid in the axial direction of the heat transfer tube by capillary action when the liquid flows down from the heat transfer tube to the heat transfer tube.
  • An object of the present invention is to provide a heat exchanger that can be downsized by improving the exchange rate and reducing the vertical spacing of the heat transfer tubes, and a compact absorption chiller / heater using the heat exchanger.
  • the above object is achieved by inserting the end of the heat transfer tube into a tube sheet, bringing the heat transfer tube into close contact with the tube plate, spraying a liquid on the surface of the upper heat transfer tube, and forming a liquid film on the surface of the lower heat transfer tube.
  • heat transfer tubes whose ends are bent in front of a mounting portion of a tube plate are stacked in multiple stages, and the ends of the heat transfer tubes are inserted into the tube plate.
  • the end portions of the inserted heat transfer tubes are placed between the ends of the inserted heat transfer tubes in the upper stage, and the end portions of the inserted heat transfer tubes in the lower stage are located below the ends of the heat transfer tubes. This is achieved by arranging the ends of the heat pipes in a vertically shifted manner.
  • the purpose of the above is to insert the end of the horizontally arranged heat transfer tube into the tube sheet and expand the heat transfer tube.
  • heat is exchanged between the inner and outer surfaces of the heat transfer tube by spraying the liquid on the surface of the upper heat transfer tube and dropping the liquid while forming a liquid film on the surface of the lower heat transfer tube.
  • the end of the heat transfer tube has a shape bent horizontally in front of the tube sheet and obliquely to the tube sheet, and immediately before the tube sheet, bent again at a right angle to the tube sheet.
  • the inserted heat transfer tubes are stacked in multiple stages, and the inserted heat transfer tube ends are located between the upper inserted heat transfer tube ends and the lower inserted heat transfer tubes below the heat transfer tube ends.
  • the heat transfer tubes are arranged so that the ends are shifted from each other in the upper and lower stages so that the ends come to the end. Is arranged so that it is within the range.
  • FIG. 1 is a plan view of an embodiment of the heat exchanger according to the present invention.
  • FIG. 2 is a front view of the embodiment shown in FIG.
  • FIG. 3 is a partially enlarged view of the embodiment shown in FIG.
  • FIG. 4 is an explanatory view of the state of spraying liquid according to the prior art and the vertical spacing between heat transfer tubes.
  • FIG. 5 is an explanatory diagram of the state of spraying of the liquid and the vertical spacing between the heat transfer tubes in the embodiment shown in FIG.
  • FIG. 6 is a left side view of the embodiment shown in FIG.
  • FIG. 7 is a sectional view taken along line AA of the embodiment shown in FIG.
  • FIG. 8 is a plan view of another embodiment of the heat exchanger according to the present invention.
  • FIG. 9 is a plan view of still another embodiment of the heat exchanger according to the present invention. .
  • FIG. 10 is a cycle flow diagram of an absorption type water chiller / heater.
  • Absorption chiller / heater includes high-temperature regenerator 301, low-temperature regenerator 302, condenser 303, evaporator 304, absorber 300, low-temperature heat exchanger 303, high-temperature heat exchange It comprises a vessel 307, a solution pump 308 for circulating the absorbed solution, and a pipe connecting these.
  • the operation during the cooling operation will be described.
  • it is heated by an external heat source to concentrate the solution in the high-temperature regenerator 301, and the refrigerant vapor generated by the heating is guided to the heat exchanger 302A in the low-temperature regenerator 302, and the low-temperature
  • the solution in the regeneration 302 is heated and concentrated to generate a refrigerant vapor, and the introduced refrigerant vapor itself is condensed and liquefied and flows into the condenser 303.
  • the refrigerant vapor generated in the low-temperature regenerator 302 is guided to the condenser 303, and the refrigerant vapor cooled by the cooling water is condensed and liquefied and sent to the evaporator 304.
  • the liquid refrigerant in the evaporator 304 is pressure-fed by the refrigerant pump 309, and is sprayed to the heat exchanger 304A in the evaporator 304.
  • the cold water flowing in the heat exchanger 304 A exchanges heat with the sprayed liquid refrigerant, and the liquid refrigerant evaporates and flows into the absorber 305.
  • the chilled water that has entered through the chilled water inlet is cooled by the latent heat of vaporization at that time, and exits through the chilled water outlet and is supplied to the cooling water for cooling.
  • the concentrated solution concentrated in the high-temperature regenerator 301 and the low-temperature regenerator 302 is sprayed to the heat exchanger 300A in the absorber 350, and cooled in the heat exchanger 300A.
  • the cooled concentrated solution absorbs the refrigerant vapor from the evaporator 304 and becomes a dilute solution.
  • This dilute solution is divided into two by a solution pump 308 via a low-temperature heat exchanger 306, one of which is led to a low-temperature regenerator 302, and the other via a high-temperature heat exchanger 307. Then, it is led to the high-temperature regenerator 301.
  • the above cycle constitutes a cooling cycle.
  • FIG. 1 is a plan view of an embodiment of a meandering heat transfer tube group, in which a heat transfer tube 1 is bent horizontally in a hairpin shape, that is, in front of a tube sheet 2, and again immediately before a tube sheet 2.
  • three heat transfer tubes 1 are used in parallel and bent.
  • FIG. 2 is a side view of FIG. 1, and according to the present embodiment, the hairpin-shaped heat transfer tubes 1 are stacked up and down in multiple stages, and the interval between the upper and lower heat transfer tubes 1 is smaller than that of the conventional one. Narrow) indicates that they can be stacked.
  • Fig. 3 is an enlarged view of the end of the heat transfer tube (part B surrounded by a circle) in Fig. 1.
  • the end of the heat transfer tube is bent horizontally in front of the tube sheet and obliquely to the tube sheet.
  • heat transfer tubes bent at right angles to the tube sheet are stacked in multiple stages again, and each inserted heat transfer tube end portion is placed in the upper stage.
  • the heat transfer tubes are arranged so that the heat transfer tube ends are shifted from each other in the upper and lower stages so that the lower end of the inserted heat transfer tube is located between the inserted heat transfer tube ends and below the heat transfer tube ends. are doing.
  • the positions of the first stage (solid line) and the second stage (two-dot chain line) are shifted as shown in the figure, and the third stage is bent at the same angle as the first stage (that is, the solid line). Furthermore, the fourth stage is bent and added to the same phase as the second stage (two-dot chain line).
  • the vertical distance C of the heat transfer tubes 1 in the expanded portion of the tube sheet 2 is changed to the vertical distance C of the conventional heat transfer tubes shown in FIG. The same spacing can be ensured, and sufficient plastic working allowance can be obtained. That is, the distance between the same longitudinal heat transfer tubes 1 is smaller than that of the conventional heat transfer tube while maintaining the same distance C.
  • Fig. 4 shows the situation of a conventional liquid 5 sprayed by the spraying device 4 when it flows down from the heat transfer tube 1 to the lower heat transfer tube 1 and travels down the heat transfer tube 1 by surface tension to form a liquid film. As can be seen from the figure, the flow width of liquid 6 is reduced as it travels downward.
  • the distance between the vertical heat transfer tubes 1 in the same row is small, and when the liquid flows down from the heat transfer tube 1 to the lower heat transfer tube 1, the liquid 5 Flow
  • the heat transfer tube 6 spreads in the axial direction of the heat transfer tube due to the principle of the capillary tube effect, so that the surface of the heat transfer tube is well wetted over the entire surface and the heat transfer coefficient is improved.
  • FIG. 6 is a left side view of FIG. 2, and shows that the expanded portion of the tube sheet 2 can secure a plastic working allowance as in the conventional case.
  • FIG. 7 is a cross-sectional view taken along the line AA of FIG. 2, and shows that the heat transfer tubes 1 can be arranged with a small vertical space inside the shell 3. It also shows that the refrigerant vapor generated from the heat exchanger 304 A of the evaporator 304 flows into the heat exchanger 304 A of the absorber 304, and the heat transfer tube 1 and the heat transfer tube When the vertical interval of 1 is small, the refrigerant vapor easily flows in the vertical direction as indicated by the arrow in the figure. For this reason, the refrigerant vapor easily flows from the upper side to the lower side in the absorber 305, and the flow in the lateral direction is reduced, so that the evaporation and absorption performance can be exhibited more than before. Therefore, it is possible to realize a high-performance absorption and cooling water heater.
  • FIG. 8 shows another embodiment.
  • the heat transfer tube 1 is formed in a serpentine shape, and the heat transfer tube groups arranged in a horizontal direction are vertically stacked in multiple stages, but the end is bent at 90 °.
  • the bending position is different between the first stage (solid line) and the second stage (two-dot chain line), and the third stage is again bent at the same position as the first stage.
  • FIG. 9 shows still another embodiment.
  • Either heat of evaporator 304, evaporator heat exchanger 304A and absorber 300, absorber heat exchanger 304A and low temperature regenerator 302, low temperature regenerator 302a It may be an exchanger.
  • Heat transfer tubes 10 of different diameters having different diameters at one end, the center and the other end are alternately arranged vertically, and there is no interval B in the heat transfer portion 1OA of the heat transfer tubes 10 or Construct heat transfer tube banks at small intervals ranging from l mm to 3 mm. Both ends of the heat transfer tube 10 of different diameter are slightly larger than the heat transfer portion 1 OA, and the end 10 8 is thicker and the end 10 is thinner than the heat transfer tube 1 OA. Consists of C. Both ends 10 B of the heat transfer tubes 10 of different diameters and IOC can secure the plastic working allowance A necessary for expanding the tube to the tube sheet 2.
  • a plurality of meandering heat transfer tubes bent multiple times in the shape of a hairpin are bundled and horizontally arranged horizontally, and the vertical spacing between the heat transfer tubes is made as close as possible to zero, so that the liquid is discharged.
  • an evaporator that is sprayed from the top of the heat transfer tube group and evaporates, an absorber with absorption, and a low-temperature regenerator the spread of liquid in the axial direction of the heat transfer tubes can be promoted, and the heat transfer coefficient can be improved.
  • the hot and cold water can also be used to shift the phase of the expanded section to the tube sheet.
  • the cooling water inlet / outlet can be provided.
  • the height of the absorption chiller / heater can be made lower than before so that the whole can be made compact.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Selon l'invention, une conduite de transfert de chaleur (1) est cintrée, en une pluralité de points, en forme de zigzag. Une pluralité de conduites de transfert de chaleur (1) en forme de zigzag sont disposées horizontalement côte à côte. Une pile de conduites de transfert de chaleur (1) disposées horizontalement est formée de sorte que les espaces entre les conduites de transfert de chaleur (1) soient aussi réduits que possible. Les parties terminales des conduites de transfert de chaleur (1) sont cintrées, en une pluralité de points, à proximité d'une plaque (2) et insérées dans cette dernière. Etant donné que les conduites de transfert de chaleur (1) sont empilées avec des espaces très faibles, lorsque du liquide pulvérisé sur les conduites de transfert de chaleur horizontales s'écoule d'une conduite à l'autre, le liquide est pulvérisé dans la direction de la conduite de transfert de chaleur par capillarité, et les surfaces entières des conduites de transfert de chaleur sont bien imprégnées. Par conséquent, la transmission calorifique peut être améliorée et les dimensions d'un dispositif de refroidissement/chauffage d'eau par absorption peuvent être réduites.
PCT/JP1997/003331 1997-09-19 1997-09-19 Echangeur de chaleur et dispositif de refroidissement/chauffage d'eau par absorption utilisant ledit echangeur de chaleur WO1999015847A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP1997/003331 WO1999015847A1 (fr) 1997-09-19 1997-09-19 Echangeur de chaleur et dispositif de refroidissement/chauffage d'eau par absorption utilisant ledit echangeur de chaleur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP1997/003331 WO1999015847A1 (fr) 1997-09-19 1997-09-19 Echangeur de chaleur et dispositif de refroidissement/chauffage d'eau par absorption utilisant ledit echangeur de chaleur

Publications (1)

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WO1999015847A1 true WO1999015847A1 (fr) 1999-04-01

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PCT/JP1997/003331 WO1999015847A1 (fr) 1997-09-19 1997-09-19 Echangeur de chaleur et dispositif de refroidissement/chauffage d'eau par absorption utilisant ledit echangeur de chaleur

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WO (1) WO1999015847A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110470153A (zh) * 2019-08-15 2019-11-19 中卫市蓝韵废弃资源综合利用有限公司 一种安全性高的油气冷却器

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5819021B2 (ja) * 1978-05-15 1983-04-15 川崎重工業株式会社 吸収冷凍機
JP2568769B2 (ja) * 1991-09-12 1997-01-08 株式会社日立製作所 吸収冷凍機

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5819021B2 (ja) * 1978-05-15 1983-04-15 川崎重工業株式会社 吸収冷凍機
JP2568769B2 (ja) * 1991-09-12 1997-01-08 株式会社日立製作所 吸収冷凍機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110470153A (zh) * 2019-08-15 2019-11-19 中卫市蓝韵废弃资源综合利用有限公司 一种安全性高的油气冷却器
CN110470153B (zh) * 2019-08-15 2021-03-26 中卫市蓝韵废弃资源综合利用有限公司 一种安全性高的油气冷却器

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