US3826304A - Advantageous configuration of tubing for internal boiling - Google Patents
Advantageous configuration of tubing for internal boiling Download PDFInfo
- Publication number
- US3826304A US3826304A US00086708A US8670870A US3826304A US 3826304 A US3826304 A US 3826304A US 00086708 A US00086708 A US 00086708A US 8670870 A US8670870 A US 8670870A US 3826304 A US3826304 A US 3826304A
- Authority
- US
- United States
- Prior art keywords
- tubing
- ribbing
- convolutions
- inch
- construction
- 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
Links
Images
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
- 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
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
-
- 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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- 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
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
- F28F1/424—Means comprising outside portions integral with inside portions
- F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
Definitions
- the solution to the problem is to provide tubing having its interior unobstructed except to the extent that its inner surface is modifiedto provide radially inwardly extending ribbing in which the ribbing comprises a multiplicity of convolutions extending around the tubing.
- the ribbing may be in the form of axially spaced circumferentially extending separate ribs. Conversely, it may be in the form of a single helical rib or a multiplicityof helical ribs.
- the axial spacing or pitch P of adja-' cent convolutions, for refrigeration application does not exceed inch.
- the depth d or radial extension of the ribbing above the smooth cylindrical interior surface of the tubing is desirably about 1/32 inch, and in any case, between l/64 inch and 3/64 inch, the ratio of pitch to depth of convolution P/d being between 5 and 25.
- the tubing is thin-walled metal tubing having a wall thickness of not more than 0.075 inch.
- FIG. 1 is a fragmentary sectional view of an evaporator constructed in accordance with the present invention.
- FIG. 2 is an enlarged elevational view of a portion of FIGS. 4 and 5 are fragmentary sectional views show- I ing further embodiments of the present invention.
- the percentage of vapor in the flowing refrigerant stream will increase until at the exit end of the tubing virtually all of the liquid will have been converted to vapor, and in some cases the vapor may even be superheated to a few degrees with respect to the exit pressure.
- the mist flow regime is also called the fog-flow regime. It is a liquid-deficient condition in that as the liq uid has been progressively converted to vapor the amount of liquid left'is insufficient to wet the walls of the tube, and the liquid that exists is largely in the form of droplets which are suspended in the flowing stream of vapor. Therefore, further heat transfer becomes difficult because of the low thermal conductivity of vapor as compared with liquid; that is, heat that is being conducted through the tube wall to the inside of the tube must find its way across a vapor barrier in order to cause the remaining liquid droplets to evaporate.
- tubing of thetype just described which may be referred to as LIF tubing, will generally provide 50 to 100 percent more heat transfer (or boiling capacity) and in some cases the straight runs may extend vertically. Also, it is not required that the tubes be U-shaped or utilize U-shaped connectors, as straight lengths of tubing with headers at either end are frequently used.
- LIF tubing provides greatly increased heat transfer as compared to plain or prime tubing of the same diameter, it is subject to the objection that the internal configuration provides greatly increased resistance to flow or increased pressure drop, and the further great objection of increased costs dueboth to a very large increase in material as well as substantially increased cost due to production costs.
- the present invention relates to a different type of tubing having a configuration which has been found to be very effective for the promotion of heat transfer or boiling capacity, but which does not depend ona large increase of internal surface area.
- This type of configuration may be advantageously employed because the amount of metal may be reduced, and because the tubing is more economical to process to the final form.
- the tubing configuration in accordance with the present invention is provided with an unobstructed interior except for a relatively minor configuration of the interior surface.
- the interior surface of the tubing is generally a smooth cylindrical surface provided with ribbing comprising a multiplicity of convolutions extending around the tubing, as will presently be described.
- an evaporator having an enclosure 10 within which is provided tubing in the form of a multiplicity of coils of tubing T.
- the coils as is familiar in the art, constitute a multiplicity of straight tube sections interconnected at their ends by U-shaped connectors;
- I coils generally are connected to a header l2 to which liquid flowing through the tubing extracts heat from ambient fluid and causes boiling or vaporization of the liquid.
- FIG. 1 being schematic in nature, would of course include the familiar shell-and-tube construction of heat exchangers, enclosure 10 representing the shell, while flow to the individual tubes would be provided for by a component known as the channel (symbolized in P16. 1 by header 12). While the tubing for refrigeration purposes will normally be between A and 1- /2 inch outside diameter, in other applications substantially larger tubing may be employed. For example, tubing having 3 to 4-inch outside diameter may be used in falling-film evaporators.
- FIG. 2 there is shown a length of tubing of the type referred to.
- This tubing is thin-walled metal tubing such for example as copper having a smooth exterior cylindrical surface 20 and a smooth interior cylindrical surface 22.
- the smooth interior cylindrical surface 22 is interrupted by radially inwardly extending ribbing 24 comprising a multiplicity of convolutions extending around thetubing.
- the ribbing is formed by a single continuous helical rib having a pitch P.
- the external surface of the tube may be perfectly smooth, it is convenient to form the internal ribbing by operations applied exteriorly to the tubing, and hence the exterior surface is normally provided with a contin uous helical groove 26 which is in registration with the internal ribbing.
- the wall thickness of the tubing will not exceed 0.075 inch and may be substantially smaller. Tests have been performed in which the wall thickness of the tubing is as low as 0.016 inch.
- the depth or radial inward extension of the ribbing 24 is illustrated at d in FIG. 2 and this dimension is preferably about 1/32 inch, but in any case, between 1/64 inch and 3/64 inch.
- the tubing illustrates a single continuous groove 26 which of course forms a radially inwardly extending rib 24 in registration therewith.
- the helix has a pitch P representing the axial advance of a single helical convolution of the groove or rib.
- a multiple-start configuration may be employed and excellent results have been obtained when as many as five separate and distinct helical rib and groove formations have been provided, or in other words, a five-start configuratron.
- the internally extending rib has in cross-section a smoothly rounded convex crest and that the transverse curvature reverses to blend smoothly into the adjacent smooth cylindrical inner surface of the tubing.
- This configuration minimizes resistance to flow while at the same time induces a controlled change in direction of flow of material alongthe portion of the smooth cylindrical internal sur face leading up to each rib convolution.
- the present invention is limited to arrangements including tubes designed for internal boiling where the problem of different phase proportions creates difficulties having no counterpart in other types of heat transfer tubing such for example as water tube steam condensers.
- the PM ratio is approximately 10.
- FIG. 3 there is illustrated a further embodiment of the invention in which the tube 30 is provided at its exterior surface with inwardly extending concave grooves 32 in the form of helical corrugations.
- the inner surface of the tube is conformably displaced and forms the internal helical rib 34.
- a single-start helical rib and groove formation is illustrated having a pitch P and the height of the internal rib (or the depth of the internal groove) is again indicated at d.
- the PM ratio is approximately 6.
- FIG. 4 there is illustrated a tube 40 having smooth cylindrical wall sections 42, internal circular or annular ribs 44, and conforming external circular or annular grooves 46. This is similar to the embodiment of FIG. 2, except that ribs 44 are circular rather than helical.
- tube 50 has circular or annular external grooves or corrugations 52 and corresponding internal ribs 54, corresponding to the helical ribs and grooves of FIG. 3'.
- the efficiency of heat exchangers including tubing of the type disclosed herein has been established by extensive testing. The tests have been carried out by a procedure which is described below.
- the tube to be tested is centrally located inside of a second tube called the envelope tube.
- the fluid to be boiled is caused to flow through the test tube at a measured rate.
- a countercurrent flow of water at a measured flow rate is estab- 6 lished through the annular space between the test tube and the envelope tube. Provision is madefor controlling the temperature of the water entering the tube at a given level, for example, 60F.
- This pressure level sets the boiling temperature of the refrigerant according to its inherent vaporpressure properties. As pressure is increased, the saturated boiling temperature increases. By choice, the pressure level is so set that a desired boiling temperature, for example 32F., is required. Thus, the heat'required for evaporation of the refrigerant is abstracted from the water moving through the annulus by heat flow through the wall of the test tube.
- test tube Since the test tube is of substantial length, simulating industrial practice, a substantial pressure drop is associated with the flow of the refrigerant through the tube.
- the pressure drop of the boiling fluid is, of course, recognized to be intensified over that which would be experienced for the same mass flow of the fluid without boiling.
- the pressure-drop encountered with in-tube boiling can be a significant factor, as it not only requires expenditure of energy but it affects the temperature driving force for the transfer of heat. This is so because the boiling temperature is a function of total pressure; and when a fluid is boiling as it passes through a tube, the fluid temperature at the upstream end of the heated section may be several degrees greater than the temperature at the downstream end. In practical situations this effectively lowers the overall driving force for the flow of heat.
- the test rig described above was fitted with pressure-drop measuring means so that this important factor could be dealt with.
- star-insert tubes are made upof aluminum shape or star cross-section, inserted into a sheath tube of copper.
- the amount of star points or radial fins may vary, and several modifications of point shape are used.
- every'effort is made to secure a good mechanical bond between copper and aluminum by a sinking operation to minimize any thermal resistance at the interface'Tubing of this general type dominates the DX-water chiller fieldtoday, although plain tubes are also used.
- tubing in accordance with the present invention is that there is no insert, and hence no concern over the bonding problem or elimination of thermal resistance at the interface. From a caparative value of tubing weight per foot, it will be observed that the'tubing disclosed herein enables a very substantial saving of metal as compared to the starinsert tube, while at the same time provides specifically greater evaporative capacity. It will be noted from the above table that the evaporative capacity of tubing of the presentinvention is nearly double that of plain tub- In practice, the refrigerant enters the evaporator with a substantial part thereof in liquid phase, a typical ratio of liquid to vapor refrigerant being 4/1. The expression substantial liquid phase is intended to signify such predominance of liquid refrigerant.
- Evaporator construction comprising an enclosure, metal heat exchange tubing in said enclosure for receiving a hydrocarbon or substituted hydrocarbon refrigerant in substantially liquid phase atone end and for discharging the refrigerant in substantially vapor phase at the other, the exerior surface of said tubing being in heat exchange relation with a fluid transiting said enclosure and giving up heat to the refrigerant to vaporize substantially all of the refrigerant, the interior of said tubing being substantially unobstructed except for surface configuration, the interior surface of said tubing being provided with radially inwardly extending ribbing, said ribbing comprising a multiplicity of convolutionsextending around the tubing, the axial pitch P of adjacent convolutions being not greater than inch, the depth d or radial extension of said ribbing being between l/64 inch and 3/64 inch, the ratio of pitch to depth of convolutions P/d being between 5 and 25, said tubing having a wall of substantially uniform thickness, the exterior of said tubing having a multiplicity of groove
Abstract
Description
Claims (26)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US00086708A US3826304A (en) | 1967-10-11 | 1970-11-04 | Advantageous configuration of tubing for internal boiling |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US67461167A | 1967-10-11 | 1967-10-11 | |
US00086708A US3826304A (en) | 1967-10-11 | 1970-11-04 | Advantageous configuration of tubing for internal boiling |
Publications (1)
Publication Number | Publication Date |
---|---|
US3826304A true US3826304A (en) | 1974-07-30 |
Family
ID=26775057
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US00086708A Expired - Lifetime US3826304A (en) | 1967-10-11 | 1970-11-04 | Advantageous configuration of tubing for internal boiling |
Country Status (1)
Country | Link |
---|---|
US (1) | US3826304A (en) |
Cited By (41)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2353038A1 (en) * | 1976-05-24 | 1977-12-23 | Togashi Akira | FLUID FLOW TUBULAR BODY |
DE2755521A1 (en) * | 1976-12-15 | 1978-06-22 | Gen Atomic Co | HEAT TRANSFER PIPE AND METHOD FOR THE PRODUCTION THEREOF |
US4116270A (en) * | 1975-07-30 | 1978-09-26 | Ruf Fedorovich Marushkin | Tubular coiled heat exchanger and device for manufacturing same |
DE2814828A1 (en) * | 1978-04-06 | 1979-10-18 | Metallgesellschaft Ag | GAS COOLER WITH LEADED PIPES |
FR2450433A2 (en) * | 1979-02-27 | 1980-09-26 | Gen Atomic Co | HELICAL GROOVING TUBE FOR HEAT EXCHANGES AND MANUFACTURING METHOD THEREOF |
US4305460A (en) * | 1979-02-27 | 1981-12-15 | General Atomic Company | Heat transfer tube |
US4317335A (en) * | 1979-08-08 | 1982-03-02 | Tokyo Shibaura Denki Kabushiki Kaisha | Refrigerating apparatus |
EP0052522A2 (en) * | 1980-11-19 | 1982-05-26 | New Zealand Dairy & Industrial Supplies Limited | An enhanced surface tube |
FR2496247A1 (en) * | 1980-12-12 | 1982-06-18 | Perot Georges | Continuous defroster for heat pump evaporator - has threaded nut on driven screw with chain or gear drive |
EP0114640A2 (en) * | 1983-01-25 | 1984-08-01 | Wickes Products, Inc. | Finned heat exchanger tube having optimized heat transfer characteristics |
EP0165583A2 (en) * | 1984-06-20 | 1985-12-27 | Hitachi, Ltd. | Heat transfer tube for single phase flow |
EP0455275A2 (en) * | 1987-12-09 | 1991-11-06 | Fujikura Ltd. | Heat pipe and method of manufacturing the same |
US5271376A (en) * | 1991-08-12 | 1993-12-21 | Rheem Manufacturing Company | Serpentined tubular heat exchanger apparatus for a fuel-fired forced air heating furnace |
US5680772A (en) * | 1995-11-29 | 1997-10-28 | Sanyo Electric Co., Ltd. | Absorption type refrigerating machine |
US5960870A (en) * | 1997-01-27 | 1999-10-05 | Kabushiki Kaisha Kobe Seiko Sho | Heat transfer tube for absorber |
EP1148231A1 (en) * | 1999-01-20 | 2001-10-24 | Hino Motors, Ltd. | Egr cooler |
US20040210285A1 (en) * | 2002-04-04 | 2004-10-21 | Steven Yon | Method of manufacturing a heat transfer element for in vivo cooling without undercuts |
US20050199228A1 (en) * | 2002-06-21 | 2005-09-15 | Hino Motors, Ltd | Egr cooler |
US7017651B1 (en) * | 2000-09-13 | 2006-03-28 | Raytheon Company | Method and apparatus for temperature gradient control in an electronic system |
US20070000651A1 (en) * | 2003-05-10 | 2007-01-04 | Zengyuan Guo | An enhanced heat transfer tube with discrete bidirectionally inclined ribs |
US20070081295A1 (en) * | 2005-10-11 | 2007-04-12 | Applied Materials, Inc. | Capacitively coupled plasma reactor having a cooled/heated wafer support with uniform temperature distribution |
US20070081296A1 (en) * | 2005-10-11 | 2007-04-12 | Applied Materials, Inc. | Method of operating a capacitively coupled plasma reactor with dual temperature control loops |
US20070081294A1 (en) * | 2005-10-11 | 2007-04-12 | Applied Materials, Inc. | Capacitively coupled plasma reactor having very agile wafer temperature control |
US20070091537A1 (en) * | 2005-10-20 | 2007-04-26 | Applied Materials, Inc. | Method for agile workpiece temperature control in a plasma reactor using a thermal model |
US20070097580A1 (en) * | 2005-10-11 | 2007-05-03 | Applied Materials, Inc. | Method of cooling a wafer support at a uniform temperature in a capacitively coupled plasma reactor |
US20070187067A1 (en) * | 2006-02-15 | 2007-08-16 | Hitachi Cable, Ltd. | Heat transfer tube and heat exchanger using same |
US20080149309A1 (en) * | 2005-03-25 | 2008-06-26 | Tsinghua University | Hot Water Heat Transfer Pipe |
US20090013676A1 (en) * | 2007-07-11 | 2009-01-15 | Andreas Capelle | Lightweight flow heat exchanger |
US20090056131A1 (en) * | 2007-08-31 | 2009-03-05 | Retermia Oy | Equipment and Method for Making a Needle-Fin Tube, and a Needle-Fin Tube |
US20090071639A1 (en) * | 2005-05-16 | 2009-03-19 | Daikin Industries , Ltd. | Heat exchanger |
US20090229802A1 (en) * | 2005-10-07 | 2009-09-17 | Hino Motors, Ltd. | Egr cooler |
US20100218912A1 (en) * | 2008-04-07 | 2010-09-02 | Lane Lawless | Method, apparatus, header, and composition for ground heat exchange |
US20100252243A1 (en) * | 2009-04-03 | 2010-10-07 | Liu Huazhao | Refrigerant distributor for heat exchanger and heat exchanger |
CN101865623A (en) * | 2010-06-24 | 2010-10-20 | 宁波连通设备制造有限公司 | Helical flat pipe for waste heat boiler |
US20140116668A1 (en) * | 2012-10-31 | 2014-05-01 | GM Global Technology Operations LLC | Cooler pipe and method of forming |
CN104428620A (en) * | 2012-07-05 | 2015-03-18 | 利乐拉瓦尔集团及财务有限公司 | Improved tubular heat exchanger |
DE102008015337B4 (en) * | 2008-03-20 | 2015-03-19 | Joma-Polytec Gmbh | Absorber tube of a solar collector and solar collector |
US9121630B1 (en) | 2008-04-07 | 2015-09-01 | Rygan Corp. | Method, apparatus, conduit, and composition for low thermal resistance ground heat exchange |
CN106104190A (en) * | 2014-01-20 | 2016-11-09 | 尼奥迪斯有限公司 | Conduit for the improvement of heat exchanger |
CN110234411A (en) * | 2017-02-03 | 2019-09-13 | 维美德公司 | The method of heat-transfer pipe and manufacture heat-transfer pipe |
US11493282B2 (en) * | 2016-08-05 | 2022-11-08 | Obshestvo S Ogranichennoi Otvetstvennost'u “Reinnolts Lab” | Shell and tube condenser and the heat exchange tube of a shell and tube condenser (variants) |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2819731A (en) * | 1954-11-16 | 1958-01-14 | Gen Motors Corp | Refrigerating apparatus |
US2913009A (en) * | 1956-07-16 | 1959-11-17 | Calumet & Hecla | Internal and internal-external surface heat exchange tubing |
US3022049A (en) * | 1959-07-10 | 1962-02-20 | Gen Electric | Heat exchange tubing |
CA736374A (en) * | 1966-06-14 | Nakayama Kunihiro | Heat exchange tubes | |
US3450193A (en) * | 1967-10-31 | 1969-06-17 | Olin Mathieson | Corrugated tubing |
US3481394A (en) * | 1967-06-26 | 1969-12-02 | Calumet & Hecla Corp | Configuration of heat transfer tubing for vapor condensation on its outer surface |
-
1970
- 1970-11-04 US US00086708A patent/US3826304A/en not_active Expired - Lifetime
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA736374A (en) * | 1966-06-14 | Nakayama Kunihiro | Heat exchange tubes | |
US2819731A (en) * | 1954-11-16 | 1958-01-14 | Gen Motors Corp | Refrigerating apparatus |
US2913009A (en) * | 1956-07-16 | 1959-11-17 | Calumet & Hecla | Internal and internal-external surface heat exchange tubing |
US3022049A (en) * | 1959-07-10 | 1962-02-20 | Gen Electric | Heat exchange tubing |
US3481394A (en) * | 1967-06-26 | 1969-12-02 | Calumet & Hecla Corp | Configuration of heat transfer tubing for vapor condensation on its outer surface |
US3450193A (en) * | 1967-10-31 | 1969-06-17 | Olin Mathieson | Corrugated tubing |
Cited By (89)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4116270A (en) * | 1975-07-30 | 1978-09-26 | Ruf Fedorovich Marushkin | Tubular coiled heat exchanger and device for manufacturing same |
FR2353038A1 (en) * | 1976-05-24 | 1977-12-23 | Togashi Akira | FLUID FLOW TUBULAR BODY |
DE2755521A1 (en) * | 1976-12-15 | 1978-06-22 | Gen Atomic Co | HEAT TRANSFER PIPE AND METHOD FOR THE PRODUCTION THEREOF |
FR2374610A1 (en) * | 1976-12-15 | 1978-07-13 | Gen Atomic Co | HELICOIDAL RIBBON TUBE FOR HEAT EXCHANGES AND ITS MANUFACTURING PROCESS |
DE2814828A1 (en) * | 1978-04-06 | 1979-10-18 | Metallgesellschaft Ag | GAS COOLER WITH LEADED PIPES |
EP0004983A1 (en) * | 1978-04-06 | 1979-10-31 | Metallgesellschaft Ag | Gas-cooler with lead tubes finned on the inside |
FR2450433A2 (en) * | 1979-02-27 | 1980-09-26 | Gen Atomic Co | HELICAL GROOVING TUBE FOR HEAT EXCHANGES AND MANUFACTURING METHOD THEREOF |
US4305460A (en) * | 1979-02-27 | 1981-12-15 | General Atomic Company | Heat transfer tube |
US4317335A (en) * | 1979-08-08 | 1982-03-02 | Tokyo Shibaura Denki Kabushiki Kaisha | Refrigerating apparatus |
EP0052522A2 (en) * | 1980-11-19 | 1982-05-26 | New Zealand Dairy & Industrial Supplies Limited | An enhanced surface tube |
EP0052522A3 (en) * | 1980-11-19 | 1982-11-24 | New Zealand Dairy & Industrial Supplies Limited | An enhanced surface tube |
FR2496247A1 (en) * | 1980-12-12 | 1982-06-18 | Perot Georges | Continuous defroster for heat pump evaporator - has threaded nut on driven screw with chain or gear drive |
EP0114640A2 (en) * | 1983-01-25 | 1984-08-01 | Wickes Products, Inc. | Finned heat exchanger tube having optimized heat transfer characteristics |
EP0114640A3 (en) * | 1983-01-25 | 1984-08-15 | Gulf And Western Industries, Inc. | Finned heat exchanger tube having optimized heat transfer characteristics |
EP0165583A2 (en) * | 1984-06-20 | 1985-12-27 | Hitachi, Ltd. | Heat transfer tube for single phase flow |
EP0165583A3 (en) * | 1984-06-20 | 1986-10-22 | Hitachi, Ltd. | Heat transfer tube for single phase flow |
EP0455275A2 (en) * | 1987-12-09 | 1991-11-06 | Fujikura Ltd. | Heat pipe and method of manufacturing the same |
EP0455275A3 (en) * | 1987-12-09 | 1991-11-21 | Fujikura Ltd. | Heat pipe and method of manufacturing the same |
US5271376A (en) * | 1991-08-12 | 1993-12-21 | Rheem Manufacturing Company | Serpentined tubular heat exchanger apparatus for a fuel-fired forced air heating furnace |
US5680772A (en) * | 1995-11-29 | 1997-10-28 | Sanyo Electric Co., Ltd. | Absorption type refrigerating machine |
US5960870A (en) * | 1997-01-27 | 1999-10-05 | Kabushiki Kaisha Kobe Seiko Sho | Heat transfer tube for absorber |
EP1148231A1 (en) * | 1999-01-20 | 2001-10-24 | Hino Motors, Ltd. | Egr cooler |
EP1148231A4 (en) * | 1999-01-20 | 2008-02-13 | Hino Motors Ltd | Egr cooler |
US7017651B1 (en) * | 2000-09-13 | 2006-03-28 | Raytheon Company | Method and apparatus for temperature gradient control in an electronic system |
US20040210285A1 (en) * | 2002-04-04 | 2004-10-21 | Steven Yon | Method of manufacturing a heat transfer element for in vivo cooling without undercuts |
US7288109B2 (en) * | 2002-04-04 | 2007-10-30 | Innercool Therapies. Inc. | Method of manufacturing a heat transfer element for in vivo cooling without undercuts |
US8172889B2 (en) | 2002-04-04 | 2012-05-08 | Innercoll Therapies, Inc. | Method of manufacturing a heat transfer element for in vivo cooling without undercuts |
US7080634B2 (en) * | 2002-06-21 | 2006-07-25 | Hino Motors, Ltd. | EGR cooler |
US20050199228A1 (en) * | 2002-06-21 | 2005-09-15 | Hino Motors, Ltd | Egr cooler |
US20070000651A1 (en) * | 2003-05-10 | 2007-01-04 | Zengyuan Guo | An enhanced heat transfer tube with discrete bidirectionally inclined ribs |
US20080149309A1 (en) * | 2005-03-25 | 2008-06-26 | Tsinghua University | Hot Water Heat Transfer Pipe |
US8215380B2 (en) * | 2005-03-25 | 2012-07-10 | Tsinghua University | Hot water heat transfer pipe |
US20090071639A1 (en) * | 2005-05-16 | 2009-03-19 | Daikin Industries , Ltd. | Heat exchanger |
US20090229802A1 (en) * | 2005-10-07 | 2009-09-17 | Hino Motors, Ltd. | Egr cooler |
US8079409B2 (en) * | 2005-10-07 | 2011-12-20 | Hino Motors, Ltd. | EGR cooler |
US20070097580A1 (en) * | 2005-10-11 | 2007-05-03 | Applied Materials, Inc. | Method of cooling a wafer support at a uniform temperature in a capacitively coupled plasma reactor |
US8157951B2 (en) | 2005-10-11 | 2012-04-17 | Applied Materials, Inc. | Capacitively coupled plasma reactor having very agile wafer temperature control |
US8337660B2 (en) | 2005-10-11 | 2012-12-25 | B/E Aerospace, Inc. | Capacitively coupled plasma reactor having very agile wafer temperature control |
US20100303680A1 (en) * | 2005-10-11 | 2010-12-02 | Buchberger Douglas A Jr | Capacitively coupled plasma reactor having very agile wafer temperature control |
US8801893B2 (en) | 2005-10-11 | 2014-08-12 | Be Aerospace, Inc. | Method of cooling a wafer support at a uniform temperature in a capacitively coupled plasma reactor |
US8092638B2 (en) | 2005-10-11 | 2012-01-10 | Applied Materials Inc. | Capacitively coupled plasma reactor having a cooled/heated wafer support with uniform temperature distribution |
US20070081294A1 (en) * | 2005-10-11 | 2007-04-12 | Applied Materials, Inc. | Capacitively coupled plasma reactor having very agile wafer temperature control |
US20070081296A1 (en) * | 2005-10-11 | 2007-04-12 | Applied Materials, Inc. | Method of operating a capacitively coupled plasma reactor with dual temperature control loops |
US20070081295A1 (en) * | 2005-10-11 | 2007-04-12 | Applied Materials, Inc. | Capacitively coupled plasma reactor having a cooled/heated wafer support with uniform temperature distribution |
US8034180B2 (en) * | 2005-10-11 | 2011-10-11 | Applied Materials, Inc. | Method of cooling a wafer support at a uniform temperature in a capacitively coupled plasma reactor |
US7988872B2 (en) | 2005-10-11 | 2011-08-02 | Applied Materials, Inc. | Method of operating a capacitively coupled plasma reactor with dual temperature control loops |
US20100300621A1 (en) * | 2005-10-11 | 2010-12-02 | Paul Lukas Brillhart | Method of cooling a wafer support at a uniform temperature in a capacitively coupled plasma reactor |
US8221580B2 (en) | 2005-10-20 | 2012-07-17 | Applied Materials, Inc. | Plasma reactor with wafer backside thermal loop, two-phase internal pedestal thermal loop and a control processor governing both loops |
US20070091537A1 (en) * | 2005-10-20 | 2007-04-26 | Applied Materials, Inc. | Method for agile workpiece temperature control in a plasma reactor using a thermal model |
US20100314046A1 (en) * | 2005-10-20 | 2010-12-16 | Paul Lukas Brillhart | Plasma reactor with a multiple zone thermal control feed forward control apparatus |
US20100319851A1 (en) * | 2005-10-20 | 2010-12-23 | Buchberger Jr Douglas A | Plasma reactor with feed forward thermal control system using a thermal model for accommodating rf power changes or wafer temperature changes |
US20110065279A1 (en) * | 2005-10-20 | 2011-03-17 | Buchberger Jr Douglas A | Method of processing a workpiece in a plasma reactor using feed forward thermal control |
US20110068085A1 (en) * | 2005-10-20 | 2011-03-24 | Paul Lukas Brillhart | Method of processing a workpiece in a plasma reactor using multiple zone feed forward thermal control |
US8980044B2 (en) | 2005-10-20 | 2015-03-17 | Be Aerospace, Inc. | Plasma reactor with a multiple zone thermal control feed forward control apparatus |
US8012304B2 (en) | 2005-10-20 | 2011-09-06 | Applied Materials, Inc. | Plasma reactor with a multiple zone thermal control feed forward control apparatus |
US8021521B2 (en) | 2005-10-20 | 2011-09-20 | Applied Materials, Inc. | Method for agile workpiece temperature control in a plasma reactor using a thermal model |
US20070089834A1 (en) * | 2005-10-20 | 2007-04-26 | Applied Materials, Inc. | Plasma reactor with a multiple zone thermal control feed forward control apparatus |
US8608900B2 (en) | 2005-10-20 | 2013-12-17 | B/E Aerospace, Inc. | Plasma reactor with feed forward thermal control system using a thermal model for accommodating RF power changes or wafer temperature changes |
US8546267B2 (en) | 2005-10-20 | 2013-10-01 | B/E Aerospace, Inc. | Method of processing a workpiece in a plasma reactor using multiple zone feed forward thermal control |
US8092639B2 (en) | 2005-10-20 | 2012-01-10 | Advanced Thermal Sciences Corporation | Plasma reactor with feed forward thermal control system using a thermal model for accommodating RF power changes or wafer temperature changes |
US20070091540A1 (en) * | 2005-10-20 | 2007-04-26 | Applied Materials, Inc. | Method of processing a workpiece in a plasma reactor using multiple zone feed forward thermal control |
US20070091538A1 (en) * | 2005-10-20 | 2007-04-26 | Buchberger Douglas A Jr | Plasma reactor with wafer backside thermal loop, two-phase internal pedestal thermal loop and a control processor governing both loops |
US8329586B2 (en) | 2005-10-20 | 2012-12-11 | Applied Materials, Inc. | Method of processing a workpiece in a plasma reactor using feed forward thermal control |
US20070091541A1 (en) * | 2005-10-20 | 2007-04-26 | Applied Materials, Inc. | Method of processing a workpiece in a plasma reactor using feed forward thermal control |
US20070187067A1 (en) * | 2006-02-15 | 2007-08-16 | Hitachi Cable, Ltd. | Heat transfer tube and heat exchanger using same |
US20090013676A1 (en) * | 2007-07-11 | 2009-01-15 | Andreas Capelle | Lightweight flow heat exchanger |
US20090056131A1 (en) * | 2007-08-31 | 2009-03-05 | Retermia Oy | Equipment and Method for Making a Needle-Fin Tube, and a Needle-Fin Tube |
US8132326B2 (en) * | 2007-08-31 | 2012-03-13 | Retermia Oy | Method and apparatus for forming a finned heat exchanger tube that includes an internal fin structure that is a spring formed from a spiral wire wound around a mandrel |
DE102008015337B4 (en) * | 2008-03-20 | 2015-03-19 | Joma-Polytec Gmbh | Absorber tube of a solar collector and solar collector |
US9816023B2 (en) * | 2008-04-07 | 2017-11-14 | Rygan Corp | Method, apparatus, header, and composition for ground heat exchange |
US20100218912A1 (en) * | 2008-04-07 | 2010-09-02 | Lane Lawless | Method, apparatus, header, and composition for ground heat exchange |
US9121630B1 (en) | 2008-04-07 | 2015-09-01 | Rygan Corp. | Method, apparatus, conduit, and composition for low thermal resistance ground heat exchange |
US20100252243A1 (en) * | 2009-04-03 | 2010-10-07 | Liu Huazhao | Refrigerant distributor for heat exchanger and heat exchanger |
US9423190B2 (en) * | 2009-04-03 | 2016-08-23 | Sanhua (Hangzhou) Micro Channel Heat Exchanger Co. | Refrigerant distributor for heat exchanger and heat exchanger |
CN101865623A (en) * | 2010-06-24 | 2010-10-20 | 宁波连通设备制造有限公司 | Helical flat pipe for waste heat boiler |
CN101865623B (en) * | 2010-06-24 | 2012-04-25 | 宁波连通设备制造有限公司 | Helical flat pipe for waste heat boiler |
CN104428620A (en) * | 2012-07-05 | 2015-03-18 | 利乐拉瓦尔集团及财务有限公司 | Improved tubular heat exchanger |
US20140116668A1 (en) * | 2012-10-31 | 2014-05-01 | GM Global Technology Operations LLC | Cooler pipe and method of forming |
US20160341491A1 (en) * | 2014-01-20 | 2016-11-24 | Neotiss Sas | Improved tube for a heat exchanger |
EP3097377A1 (en) * | 2014-01-20 | 2016-11-30 | Neotiss SAS | Improved tube for a heat exchanger |
JP2017503146A (en) * | 2014-01-20 | 2017-01-26 | ネオティス エスアーエスNeotiss Sas | Improved heat exchanger tube |
CN106104190A (en) * | 2014-01-20 | 2016-11-09 | 尼奥迪斯有限公司 | Conduit for the improvement of heat exchanger |
EP3097377B1 (en) * | 2014-01-20 | 2022-04-20 | Neotiss SAS | Improved tube for a heat exchanger |
US11493282B2 (en) * | 2016-08-05 | 2022-11-08 | Obshestvo S Ogranichennoi Otvetstvennost'u “Reinnolts Lab” | Shell and tube condenser and the heat exchange tube of a shell and tube condenser (variants) |
CN110234411A (en) * | 2017-02-03 | 2019-09-13 | 维美德公司 | The method of heat-transfer pipe and manufacture heat-transfer pipe |
EP3544708A4 (en) * | 2017-02-03 | 2020-04-15 | Valmet AB | Heat transfer tube and method for manufacturing a heat transfer tube |
US10926189B2 (en) | 2017-02-03 | 2021-02-23 | Valmet Ab | Heat transfer tube and method for manufacturing a heat transfer tube |
US10933342B2 (en) | 2017-02-03 | 2021-03-02 | Valmet Ab | Heat transfer tube and method for manufacturing a heat transfer tube |
US10981080B2 (en) | 2017-02-03 | 2021-04-20 | Valmet Ab | Heat transfer tube and method for manufacturing a heat transfer tube |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US3826304A (en) | Advantageous configuration of tubing for internal boiling | |
US5054548A (en) | High performance heat transfer surface for high pressure refrigerants | |
CA1064718A (en) | High performance heat exchanger | |
US5669441A (en) | Heat transfer tube and method of manufacture | |
US2341319A (en) | Heat exchanger | |
US3696861A (en) | Heat transfer surface having a high boiling heat transfer coefficient | |
US3675710A (en) | High efficiency vapor condenser and method | |
US3217799A (en) | Steam condenser of the water tube type | |
JP4395378B2 (en) | HEAT TRANSFER TUBE, INCLUDING METHOD OF MANUFACTURING AND USING HEAT TRANSFER TUBE | |
JP2865858B2 (en) | Absorber for diffusion absorber | |
US20080236803A1 (en) | Finned tube with indentations | |
CN210400120U (en) | Spiral flat pipe with spiral T-shaped fins outside pipe | |
US4790371A (en) | Tube-type heat exchanger | |
Bergles | Heat transfer augmentation | |
GB1338495A (en) | Tubular heat exchangers | |
JPS5773392A (en) | Corrugated fin type heat exchanger | |
US3893504A (en) | Method for transferring heat | |
JPS5826519B2 (en) | Red-bellied woodpecker | |
JP2012167854A (en) | Heat transfer tube for falling liquid film evaporator, and turbo refrigerator using the same | |
US2395004A (en) | Method of and apparatus for evaporating liquids and condensing vapors | |
SU1183817A1 (en) | Shell-and-tube heat exchanger | |
JPH10115495A (en) | Heat transfer tube for in-pipe condensation | |
JPH08105699A (en) | Heat transfer tube with inside grooves | |
EP0074384B1 (en) | Heat exchanger | |
RU89680U1 (en) | EVAPORATOR |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: WOLVERINE TUBE, INC., 2100 MARKET STREET, N.E., DE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:UOP INC.,;REEL/FRAME:004657/0711 Effective date: 19861027 Owner name: WOLVERINE TUBE, INC., A DE. CORP.,ALABAMA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:UOP INC.,;REEL/FRAME:004657/0711 Effective date: 19861027 |
|
AS | Assignment |
Owner name: BANK OF NOVA SCOTIA, THE, 44 KING STREET, WEST, TO Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:WOLVERINE ACQUISITION CORP. A CORP. OF DE;REEL/FRAME:004696/0897 Effective date: 19870313 |
|
AS | Assignment |
Owner name: WOLVERINE ACQUISITION CORP., CORPORATION TRUST CEN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:WOLVERINE TUBE, INC.,;REEL/FRAME:004728/0083 Effective date: 19870318 Owner name: WOLVERINE ACQUISITION CORP., A DE CORP,DELAWARE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WOLVERINE TUBE, INC.,;REEL/FRAME:004728/0083 Effective date: 19870318 |
|
AS | Assignment |
Owner name: WOLVERINE TUBE, INC., A CORP. OF AL Free format text: CHANGE OF NAME;ASSIGNOR:WOLVERINE ACQUISITION CORP.;REEL/FRAME:004827/0237 Effective date: 19870626 Owner name: WOLVERINE TUBE, INC., A CORP. OF AL,ALABAMA Free format text: CHANGE OF NAME;ASSIGNOR:WOLVERINE ACQUISITION CORP.;REEL/FRAME:004827/0237 Effective date: 19870626 |
|
AS | Assignment |
Owner name: WOLVERINE TUBE, INC., 2100 MARKET STREET, N.E., P. Free format text: RELEASED BY SECURED PARTY;ASSIGNOR:BANK OF NOVA SCOTIA, THE;REEL/FRAME:005639/0755 Effective date: 19910123 |
|
AS | Assignment |
Owner name: SECURITY PACIFIC NATIONAL BANK Free format text: SECURITY INTEREST;ASSIGNOR:WOLVERINE TUBE, INC.;REEL/FRAME:005648/0195 Effective date: 19910124 |
|
AS | Assignment |
Owner name: WOLVERINE TUBE, INC., ALABAMA Free format text: RELEASED BY SECURED PARTY;ASSIGNOR:BANK OF AMERICA TRUST AND SAVINGS ASSOCIATION, SUCCESSOR BY MERGER TO SECURITY PACIFIC NATIONAL BANK;REEL/FRAME:006401/0575 Effective date: 19930108 |