US3871407A - Heat exchange apparatus - Google Patents

Heat exchange apparatus Download PDF

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Publication number
US3871407A
US3871407A US371843A US37184373A US3871407A US 3871407 A US3871407 A US 3871407A US 371843 A US371843 A US 371843A US 37184373 A US37184373 A US 37184373A US 3871407 A US3871407 A US 3871407A
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ribs
tube
heat
core
exchange
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US371843A
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Alexandr Vasilievich Bykov
Igor Martynovich Kalnin
Vladimir Nikolaevich Krotkov
Fedor Nikolaevich Dyachkov
Viktor Ivanovich Plokhov
Mikhail Fedotovich Golovinov
Veniamin Kuzmich Erokhov
Jury Stepanovich Starostin
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    • 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
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15D—FLUID DYNAMICS, i.e. METHODS OR MEANS FOR INFLUENCING THE FLOW OF GASES OR LIQUIDS
    • F15D1/00—Influencing flow of fluids
    • F15D1/02—Influencing flow of fluids in pipes or conduits
    • F15D1/06—Influencing flow of fluids in pipes or conduits by influencing the boundary layer
    • F15D1/065—Whereby an element is dispersed in a pipe over the whole length or whereby several elements are regularly distributed in a pipe
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element

Definitions

  • the outer ends of the ribs are shaped as wedges whose'acute ends extend radially from the center of the core, the ends of the ribs being press-fitted into the tube wall on the inner side thereof to a depth equal to the height of the wedges.
  • the invention relates to the field of refrigerating machines, and more particularly to heat-exchange apparatus, such as for refrigerating machines.
  • a widely known evaporator of a refrigerating machine comprises a system of heat-exchange tubes accommodating metallic inserts, each having a centrally disposed, longitudinally extending core provided with a plurality of radially extending ribs integral therewith.
  • the ribs are of trapezoidal cross section with an enlargement toward the inner side of the tube.
  • Each rib terminates in an enlarged shoe which is flat on the side of the outer surface thereof.
  • the centers of the above bases of the shoes are located on a circle of a diameter equal to the inside diameter of the respective tube, and the outer edges of the lateral sides of the "shoes" are located on a circle of a diameter which is greater than the inside diameter of the tube.
  • the ribs are made twisted along a helical line, and openings are made in the ribs to enable the flow of the refrigerant from one passage into another.
  • Intensity ofheat emission of the ribbed surfaces mainly depends upon the intensity of heat emission of the ribs (since the total surface area of the ribs is normally much greater than that of a ribless part of the heat-exhange surface), whereas the helical path of flow results in an improvement of wetting of the inner side of the tube shell (ribless part).
  • an increase takes place only in regard of the heat emission coefficient of the ribless part of the tube, which is of practically minor importance from the viewpoint of the total intensity of the heat emission.
  • a heat-exchange apparatus comprising at least one heat-exchange tube which accommodates a centrally disposed, longitudinally extending corc having at least three radially extending ribs, the outer ends of the ribs being press-fitted into the tube wall on the inner side thereof, wherein the outer ends of the ribs are shaped as wedges according to the invention, the pointed ends of the wedges being directed radially away from the center of the core, andthe wedges being press-fitted with their pointed ends into the surrounding tube wall to a depth equal to the height of the wedges.
  • This construction permits to substantially increase contact pressure between the rib bases and the inner side of the tube, whereby heat-exchange between the ribs and their tube is improved.
  • the lateral sides of the core ribs may have a rough microrelief.
  • FIG- 1 is a longitudinal sectional view of a heat-
  • the apparatus according to the invention comprises a cylindrical metallic housing 1 (FIGS. 1, 2) having one end tightly closed by means of a spherical end wall 2 welded thereto; an annular flange 3 is welded to the other end of the housing and is adapted to support a tube grate 4 and a cover plate 5.
  • the housing 1 accommodates a system consisting of V-shaped heat-exchange tubes 6 having their expanded ends fitted in respective holes of the tube grate 4.
  • the housing 1 is provided with inlet socket pipes 7, 8 and outlet socket pipes 9, 10 for a coolant and a refrigerant, respectively.
  • each heat-exchange tube 6 Mounted in each heat-exchange tube 6 is an aluminium insert 11 (FIG. 3), each comprising a centrally disposed, longitudinally extending core 12 having a number of radially extending, equally spaced ribs 13. Preferably three ribs are provided in each tube.
  • the outer ends or bases of the ribs 13 of each insert 11 are shaped as wedges 14, the acute or pointed end of each wedge being directed radially away from the center of the insert 11.
  • the ribs 13 (FIG. 14) are pressfitted with their acute ends into the walls of the respective tubes 6 on the inner sides thereof to a depth equal to the height of the wedges 14.
  • the lateral sides of the ribs 13 have a rough microrelief 15.
  • the rough microrelief 15 can be obtained by spraying metal onto the lateral sides of the ribs 13, or by the method of electrochemical etching.
  • the microrelief 15 may be of a porous structure, with the void size being commensurable with the diameter of a nucleus of a vapour bubble of a refrigerant during its boiling on the surface of the heat-exchange tubes 6.
  • Refrigerant is fed into the heat-exchange tubes 6 normally in the form of a vapo liquid mixture. Generally it consists of percent of liquid and 20 percent of vapour. While moving along the tubes 6, the liquid phase of the refrigerant is vaporized.
  • the refrig- I erant is completely in the vapour phase.
  • the improvement of the contact heat exchange is ensured due to the fact that the outer ends or bases of the ribs 13 are shaped as wedges 14 which are press-fitted into the wall of the surrounding tube 6 to a depth equal to the entire height of the wedges.
  • a heat-exchange apparatus comprising: at least one heat-exchange tube; a centrally disposed, longitudinally extending core accommodated in said tube; at least three radially extending ribs on each core, the outer ends of said ribs being shaped as wedges having pointed ends directed radially away from the center of said core, and said ribs being press-fitted with said ends into the inner wall of said tube to a depth equal to the height of said wedges, thereby raising the contact pressure between said outer rib ends and said inner tube wall, with concomitant increased contact heatexchange characteristics.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Fluid Mechanics (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Heat-exchange at least one heat-exchange tube accommodating a centrally disposed, longitudinally extending core having at least three radially extending ribs. The outer ends of the ribs are shaped as wedges whose acute ends extend radially from the center of the core, the ends of the ribs being press-fitted into the tube wall on the inner side thereof to a depth equal to the height of the wedges.

Description

United States Patent Byltov et a1.
[ HEAT EXCHANGE APPARATUS [22] Filed: June 20, 11973 [21} Appl. No.: 371,843
[ Mar. 18, 1975 [52] [1.8. CI. 138/38, 165/179 [51] Int. Cl. FlSd l/00 [58] Field of Search 165/179, 109 T; 138/38 [56] References Cited UNITED STATES PATENTS 2,960,114 11/1960 Hinde 165/179 Primary Examiner-Charles Sukalo [57] ABSTRACT Heat-exchange at least one heat-exchange tube accommodating a centrally disposed, longitudinally extending core having at least three radially extending ribs. The outer ends of the ribs are shaped as wedges whose'acute ends extend radially from the center of the core, the ends of the ribs being press-fitted into the tube wall on the inner side thereof to a depth equal to the height of the wedges.
2 Claims, 4 Drawing Figures PATENTEDHAR I 81975 sum 1 BF 2 mwLm HEAT EXCHANGE APPARATUS The invention relates to the field of refrigerating machines, and more particularly to heat-exchange apparatus, such as for refrigerating machines.
A widely known evaporator of a refrigerating machine comprises a system of heat-exchange tubes accommodating metallic inserts, each having a centrally disposed, longitudinally extending core provided with a plurality of radially extending ribs integral therewith. The ribs are of trapezoidal cross section with an enlargement toward the inner side of the tube. Each rib terminates in an enlarged shoe which is flat on the side of the outer surface thereof. The centers of the above bases of the shoes are located on a circle of a diameter equal to the inside diameter of the respective tube, and the outer edges of the lateral sides of the "shoes" are located on a circle of a diameter which is greater than the inside diameter of the tube.
When the insert is placed into its tube, the inner surface of the latter is subjected to deformation at the points of contact with the outer lateral sides of the shoe" so that an arc is formed with a radius greater than the inside radius of the tube (cf. US. Pat. No. 2,895,506 of 1959).
In order to obtain an increased thermal performance, it is necessary to improve the wetting of the tube surface (vapour separation) and to ensure more uniform distribution of the refrigerant between the tube passages.
For that purpose, in known constructions the ribs are made twisted along a helical line, and openings are made in the ribs to enable the flow of the refrigerant from one passage into another.
Contact heat exchange is improved between the ribs and the tubes by increasing the area of contact between the ribs and the tube surfaces, and for that purpose the rib bases are made T-shaped.
However, known constructions exhibit the following disadvantages:
Intensity ofheat emission of the ribbed surfaces mainly depends upon the intensity of heat emission of the ribs (since the total surface area of the ribs is normally much greater than that of a ribless part of the heat-exhange surface), whereas the helical path of flow results in an improvement of wetting of the inner side of the tube shell (ribless part). Thus an increase takes place only in regard of the heat emission coefficient of the ribless part of the tube, which is of practically minor importance from the viewpoint of the total intensity of the heat emission.
The efficiency of the heat transfer from the tube to the core (or vice versa) is rather low.
The use of the Tshaped bases of the core ribs pro-' vides for an increased contact area between each tube and its ribs, the contact rib tube being, however,
worse.
It is an object of the invention to provide a heatexchange apparatus having a construction to improve its thermal performance by ensuring more intensive heat emission of the ribbed cores and by improving the contact heat exchange between the ribs and the respective tube.
The above object is accomplished by the provision of a heat-exchange apparatus, comprising at least one heat-exchange tube which accommodates a centrally disposed, longitudinally extending corc having at least three radially extending ribs, the outer ends of the ribs being press-fitted into the tube wall on the inner side thereof, wherein the outer ends of the ribs are shaped as wedges according to the invention, the pointed ends of the wedges being directed radially away from the center of the core, andthe wedges being press-fitted with their pointed ends into the surrounding tube wall to a depth equal to the height of the wedges.
This construction permits to substantially increase contact pressure between the rib bases and the inner side of the tube, whereby heat-exchange between the ribs and their tube is improved.
According to the invention the lateral sides of the core ribs may have a rough microrelief.
This enables more intensive heat emission of the ribs.
The invention will now be described in detail, with reference to a specific, preferred embodiment thereof illustrated in the accompanying drawings, in which:
FIG- 1 is a longitudinal sectional view of a heat- The apparatus according to the invention comprises a cylindrical metallic housing 1 (FIGS. 1, 2) having one end tightly closed by means of a spherical end wall 2 welded thereto; an annular flange 3 is welded to the other end of the housing and is adapted to support a tube grate 4 and a cover plate 5.
The housing 1 accommodates a system consisting of V-shaped heat-exchange tubes 6 having their expanded ends fitted in respective holes of the tube grate 4.
The housing 1 is provided with inlet socket pipes 7, 8 and outlet socket pipes 9, 10 for a coolant and a refrigerant, respectively.
Mounted in each heat-exchange tube 6 is an aluminium insert 11 (FIG. 3), each comprising a centrally disposed, longitudinally extending core 12 having a number of radially extending, equally spaced ribs 13. Preferably three ribs are provided in each tube.
The outer ends or bases of the ribs 13 of each insert 11 are shaped as wedges 14, the acute or pointed end of each wedge being directed radially away from the center of the insert 11. The ribs 13 (FIG. 14) are pressfitted with their acute ends into the walls of the respective tubes 6 on the inner sides thereof to a depth equal to the height of the wedges 14.
In order to improve heat exchange, the lateral sides of the ribs 13 have a rough microrelief 15.
The rough microrelief 15 can be obtained by spraying metal onto the lateral sides of the ribs 13, or by the method of electrochemical etching.
The microrelief 15 may be of a porous structure, with the void size being commensurable with the diameter of a nucleus of a vapour bubble of a refrigerant during its boiling on the surface of the heat-exchange tubes 6.
The apparatus functions as follows: Refrigerant is fed into the heat-exchange tubes 6 normally in the form of a vapo liquid mixture. Generally it consists of percent of liquid and 20 percent of vapour. While moving along the tubes 6, the liquid phase of the refrigerant is vaporized.
Having passed the heat-exchange tubes 6, the refrig- I erant is completely in the vapour phase.
The provision of the rough microrelief on the lateral sides of the ribs 13 enables an increase of the number of the effective vapour formation centers, thereby making the boiling of the refrigerant more intensive in the tubes 6.
The improvement of the contact heat exchange is ensured due to the fact that the outer ends or bases of the ribs 13 are shaped as wedges 14 which are press-fitted into the wall of the surrounding tube 6 to a depth equal to the entire height of the wedges.
The refrigerant leaving the tubes 6 through the outlet socket pipe 10 is sucked into a compressor.
The heat-exchange apparatus according to the invention exhibits the following advantages:
reduced weight and size;
lower manufacturing cost;
lower consumption of refrigerant;
convenient transportation, assembly and operation.
The use of the heat-exchange apparatus according to 4 the invention makes it possible to improve the thermal performance by making the heat emission of the ribbed cores more intensive and by improving the contact heat exchange between the ribs and their tube.
What is claimed is:
l. A heat-exchange apparatus comprising: at least one heat-exchange tube; a centrally disposed, longitudinally extending core accommodated in said tube; at least three radially extending ribs on each core, the outer ends of said ribs being shaped as wedges having pointed ends directed radially away from the center of said core, and said ribs being press-fitted with said ends into the inner wall of said tube to a depth equal to the height of said wedges, thereby raising the contact pressure between said outer rib ends and said inner tube wall, with concomitant increased contact heatexchange characteristics.
2. The apparatus as defined in claim 1, wherein the lateral sides of said ribs have a rough microrelief.

Claims (2)

1. A heat-exchange apparatus comprising: at least one heatexchange tube; a centrally disposed, longitudinally extending core accommodated in said tube; at least three radially extending ribs on each core, the outer ends of said ribs being shaped as wedges having pointed ends directed radially away from the center of said core, and said ribs being press-fitted with said ends into the inner wall of said tube to a depth equal to the height of said wedges, thereby raising the contact pressure between said outer rib ends and said inner tube wall, with concomitant increased contact heat-exchange characteristics.
2. The apparatus as defined in claim 1, wherein the lateral sides of said ribs have a rough microrelief.
US371843A 1973-06-20 1973-06-20 Heat exchange apparatus Expired - Lifetime US3871407A (en)

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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4022655A (en) * 1973-12-12 1977-05-10 Commissariat A L'energie Atomique Device for limiting accidental pressure overloads in a nuclear reactor confinement structure
US4190105A (en) * 1976-08-11 1980-02-26 Gerhard Dankowski Heat exchange tube
US4360058A (en) * 1979-05-12 1982-11-23 Sueddeutsche Kuehlerfabrik Julius Fr. Behr Gmbh & Co. Kg Process for the preparation of a surface of a metal wall for the transfer of heat
US4367791A (en) * 1978-01-27 1983-01-11 Kobe Steel, Ltd. Heat transfer tubing for natural gas evaporator
US4724899A (en) * 1986-12-16 1988-02-16 Nordson Corporation Expandable insert for a heat exchanger
FR2898406A1 (en) * 2006-03-13 2007-09-14 Peugeot Citroen Automobiles Sa Heat exchange element for cooling engine of motor vehicle, has central hub and lateral legs with small base and large base that is connected to central hub by rounded surfaces, where ends of lateral legs arranged in form of polyhedron
US20080142203A1 (en) * 2006-11-22 2008-06-19 Johnson Controls Technology Company Multichannel Heat Exchanger With Dissimilar Multichannel Tubes
US20080141706A1 (en) * 2006-11-22 2008-06-19 Johnson Controls Technology Company Multichannel Evaporator with Flow Mixing Manifold
US20100050685A1 (en) * 2008-08-28 2010-03-04 Johnson Controls Technology Company Multichannel Heat Exchanger with Dissimilar Flow
US8691502B2 (en) 2008-10-31 2014-04-08 Tremrx, Inc. T-cell vaccination with viral vectors via mechanical epidermal disruption
US10995998B2 (en) * 2015-07-30 2021-05-04 Senior Uk Limited Finned coaxial cooler
US20210222924A1 (en) * 2018-10-25 2021-07-22 Heatcraft Refrigeration Products Llc Evaporator coil insert

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2960114A (en) * 1957-04-26 1960-11-15 Bell & Gossett Co Innerfinned heat transfer tubes

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2960114A (en) * 1957-04-26 1960-11-15 Bell & Gossett Co Innerfinned heat transfer tubes

Cited By (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4022655A (en) * 1973-12-12 1977-05-10 Commissariat A L'energie Atomique Device for limiting accidental pressure overloads in a nuclear reactor confinement structure
US4190105A (en) * 1976-08-11 1980-02-26 Gerhard Dankowski Heat exchange tube
US4367791A (en) * 1978-01-27 1983-01-11 Kobe Steel, Ltd. Heat transfer tubing for natural gas evaporator
US4360058A (en) * 1979-05-12 1982-11-23 Sueddeutsche Kuehlerfabrik Julius Fr. Behr Gmbh & Co. Kg Process for the preparation of a surface of a metal wall for the transfer of heat
US4724899A (en) * 1986-12-16 1988-02-16 Nordson Corporation Expandable insert for a heat exchanger
FR2898406A1 (en) * 2006-03-13 2007-09-14 Peugeot Citroen Automobiles Sa Heat exchange element for cooling engine of motor vehicle, has central hub and lateral legs with small base and large base that is connected to central hub by rounded surfaces, where ends of lateral legs arranged in form of polyhedron
US20090288440A1 (en) * 2006-11-22 2009-11-26 Johnson Controls Technology Company Multichannel Heat Exchanger with Dissimilar Tube Spacing
US7832231B2 (en) 2006-11-22 2010-11-16 Johnson Controls Technology Company Multichannel evaporator with flow separating manifold
US20080141708A1 (en) * 2006-11-22 2008-06-19 Johnson Controls Technology Company Space-Saving Multichannel Heat Exchanger
US20080141706A1 (en) * 2006-11-22 2008-06-19 Johnson Controls Technology Company Multichannel Evaporator with Flow Mixing Manifold
US20080141707A1 (en) * 2006-11-22 2008-06-19 Johnson Controls Technology Company Multichannel Evaporator with Flow Separating Manifold
US20080141686A1 (en) * 2006-11-22 2008-06-19 Johnson Controls Technology Company Multichannel Evaporator With Flow Mixing Multichannel Tubes
US20080141709A1 (en) * 2006-11-22 2008-06-19 Johnson Controls Technology Company Multi-Block Circuit Multichannel Heat Exchanger
US20080148760A1 (en) * 2006-11-22 2008-06-26 Johnson Controls Technology Company Multichannel Heat Exchanger With Dissimilar Tube Spacing
US20080142203A1 (en) * 2006-11-22 2008-06-19 Johnson Controls Technology Company Multichannel Heat Exchanger With Dissimilar Multichannel Tubes
US8281615B2 (en) 2006-11-22 2012-10-09 Johnson Controls Technology Company Multichannel evaporator with flow mixing manifold
US7677057B2 (en) 2006-11-22 2010-03-16 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar tube spacing
US7757753B2 (en) 2006-11-22 2010-07-20 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar multichannel tubes
US7802439B2 (en) 2006-11-22 2010-09-28 Johnson Controls Technology Company Multichannel evaporator with flow mixing multichannel tubes
US20080141525A1 (en) * 2006-11-22 2008-06-19 Johnson Controls Technology Company Method for Making a Shaped Multichannel Heat Exchanger
US7895860B2 (en) 2006-11-22 2011-03-01 Johnson Controls Technology Company Multichannel evaporator with flow mixing manifold
US20110132587A1 (en) * 2006-11-22 2011-06-09 Johnson Controls Technology Company Multichannel Evaporator with Flow Mixing Manifold
US7980094B2 (en) 2006-11-22 2011-07-19 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar tube spacing
US8234881B2 (en) 2008-08-28 2012-08-07 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar flow
US20100050685A1 (en) * 2008-08-28 2010-03-04 Johnson Controls Technology Company Multichannel Heat Exchanger with Dissimilar Flow
US8938988B2 (en) 2008-08-28 2015-01-27 Johnson Controls Technology Company Multichannel heat exchanger with dissimilar flow
US8691502B2 (en) 2008-10-31 2014-04-08 Tremrx, Inc. T-cell vaccination with viral vectors via mechanical epidermal disruption
US9416371B2 (en) 2008-10-31 2016-08-16 Tremrx, Inc. T-cell vaccination with viral vectors via mechanical epidermal disruption
US10995998B2 (en) * 2015-07-30 2021-05-04 Senior Uk Limited Finned coaxial cooler
US20210222924A1 (en) * 2018-10-25 2021-07-22 Heatcraft Refrigeration Products Llc Evaporator coil insert
US11885539B2 (en) * 2018-10-25 2024-01-30 Heatcraft Refrigeration Products Llc Evaporator coil insert

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