US3675710A - High efficiency vapor condenser and method - Google Patents

High efficiency vapor condenser and method Download PDF

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Publication number
US3675710A
US3675710A US121755A US3675710DA US3675710A US 3675710 A US3675710 A US 3675710A US 121755 A US121755 A US 121755A US 3675710D A US3675710D A US 3675710DA US 3675710 A US3675710 A US 3675710A
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vapor
flow
velocity
tubular walls
method defined
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US121755A
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Roderick E Ristow
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/08—Auxiliary systems, arrangements, or devices for collecting and removing condensate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0444—Condensers with an integrated receiver where the flow of refrigerant through the condenser receiver is split into two or more flows, each flow following a different path through the condenser receiver
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/02—Centrifugal separation of gas, liquid or oil

Definitions

  • Provision for drainage of condensate at closely spaced intervals facilitates condensate removal and enables the vapor to have wiping contact with a maximum interior surface area of the heat exchange wall. If tubes of similar size are employed throughout, control of vapor velocity is obtained by selecting a varying number of tubes in parallel at different flow levels and additionally by causing the vapor to flow in a spiral path to increase its velocity and wiping contact with the heat exchange surfaces.
  • This invention relates to evaporative condensers, and more particularly to an improved heat exchange apparatus and method wherein heat exchange efficiency is enhanced by so proportioning the flow path as to assure relatively high velocity flow initially and lower flow velocity as condensation progresses.
  • the high initial velocity promotes heat transfer by fast wiping contact with the exchanger walls as well as internal turbulence to aid in bringing all portions of the vapor into contact with the wall surface.
  • the variable velocity flow is obtained without need for specially constructed tubes simply by utilizing a smaller number of tubes in the higher velocity passes. By this technique the same size of tubes may be used throughout.
  • a thin spiral strip extending lengthwise of tubing conducting superheated vapor is found beneficial.
  • the number of tubes in a pass may be determined by the location of partitions in the headers. Maximum surface contact is obtained by collecting condensate as it forms and draining it away in a path out of contact with vapor.
  • Another object of the invention is to provide an improved vapor condensing heat exchanger of variable velocity flow achieved with tubes of similar size so arranged as to provide a substantially smaller cross sectionalflow .area for hot vapor than for vapor dissipating latent heat of condensation.
  • Another object of the invention is the provision of a high efficiency, low cost, lightweight condenser utilizing a plurality of similar sized tubes arranged between headers partitioned to provide a much smaller number of tubes in the flow path for incoming hot vapor than for vapor undergoing condensation thereby to provide much higher velocity flow initially than for vapor passing through the condensing phase.
  • Another object of the invention is the provision of a high efficiency vapor condenser and method utilizing a plurality of passes for vapor through heat exchange tubing of substantially the same diameter and spacing which tubing is arranged and constructed to provide a relatively high velocity spiralling flow for entering superheated vapor and relatively slower flow for vapor cooled substantially to the dew point.
  • Another object of the invention is the provision of a heat exchange apparatus and method for use in condensing vapor having a plurality of passes formed from similar sized tubing and forming one or more relatively high velocity vapor passes at the upper level of the exchanger and relatively low velocity passes in lower portions of the exchanger along with means for collecting condensate as it forms and draining it away in a path out of contact with the uncondensed vapor.
  • FIG. 1 is a view partially in vertical cross section through one preferred embodiment of a heat exchanger embodying the principles of this invention
  • FIG. 2 is a cross sectional view taken along line 2-2 on FIG. 1 with portions of the header casing broken away;
  • FIG. 3 is a cross sectional view on an enlarged scale through a single tube of the exchanger.
  • FIG. 4 is a cross sectional view through a lower tube of the exchanger and illustrative of operating conditions in a conventional heat exchanger lacking means for purging condensate.
  • FIG. 1 there is shown a preferred arrangement of an evaporative condenser, designated generally 10, incorporating the features of this invention.
  • the heat exchanger comprises a pair of similar headers ll, 12 fabricated from sheet stock welded or brazed together and interconnected between their adjacent faces by a multiplicity of tubes 13 of the same size and preferably inclined slightly to the horizontal in the direction of fluid flow.
  • One or more hot vapor supply tubes 14, 14. open into the upper end of header l2 and condensate is drained away by conduits 15 leading from the lower end of this same header.
  • Partitions 18 are welded in place between the interior walls of the header as in the manner shown in FIGS. 1 and 2. Note that the uppennost partition 18 in header 12 is immediately below the top row 19 of tubes whereas the upper partition 18 in header 11 is located between the second and third rows 20, 26 of tubes. The next lower partition 18 in header 12 is located between the fourth and fifth layers of tubes, whereas the second partition 18 from the top of header 11 is below the sixth layer of tubes.
  • barrier means such as spiral conductive strips 22 in upper rows 19 and 20 and possibly in one or more of the next lower rows of tubing if the vapor passing through these rows is still in a super heated condition. It is usually undesirable to employ the strips 22 in tubing conveying condensate as the presence of the strips interferes with proper drainage of condensate'and this is undesirable because restricting the flow area and direct contact of vapor with the heat exchange surface.
  • the axial distance between convolutions or the pitch distance of the spiral in strips 22 found to provide excellent results is two to three inches when using nominal three quarter inch tubing.
  • Strips 22 are proportioned to have a snug fit within the tubing to aid efficient heat transfer to the tube walls and preferably are smooth surfaced. As will be recognized, the limited number of flow paths together with the spiralling path of flow along the two upper passes of tubign 19, 20 causes the hot vapor to flow at high velocity and in brisk turbulent rubbing contact with all interior surfaces thereby providing unusually high efficiency heat transfer.
  • the relatively high velocity flow in layers 19, 20 assures high efficiency heat exchange and turbulent action within the tubes resulting in all portions of the superheated vapor coming repeatedly into contact with the tube surface.
  • An evaporative cooling medium is preferably passed over the exterior of all tubes in accordance with customary practice to can-y away the sensible heat and later the latent heat of evaporation. As the vapor temperature lowers and approaches the dew point, high velocity flow is not found particularly helpful in expediting condensation. However, it is important that a maximum interior surface area of the exchanger be maintained free of condensate.
  • each of headers 11 and 12 is provided with a plurality of condensate drain pipes 29 extending at intervals between holes in partitions 18 and condensate collecting sumps 30 in the bottoms of the headers.
  • Tubes 29 have their lower ends nonnally submerged in condensate in sumps 30 to safeguard against vapor by passing from a higher level of the exchanger to the drain outlet conduit 15.
  • Drain pipes 29 are of sufficient capacity to drain condensate as it forms in the tubes directly to the collection sumps. In consequence the maximum level of condensate in any tube 32 normally does not exceed that inidcated generally at 33 in FIG. 3.
  • a typical similar tube 32' in a conventional prior art condenser, particularly in lower passes thereof, would be at a much higher level such as at indicated 33' in FIG. 4. Under these conditions, it is at once apparent that a major portion of the heat exchange tube is isolated from contact with the vapor.
  • That method defined in claim 1 characterized in the steps of providing approximately one-half asmuch vapor flow area along the initial length of said serpentine flow path as along the remainder thereof thereby to provide an initial vapor flow velocity of the order of double the vapor flow velocity along the remainder of said serpentine flow path.
  • That method defined in claim 1 characterized in the steps of forming said serpentine flow passages from tubular walls of substantially the same length arranged generally parallel to one another and supporting their adjacent opposite ends by respective header assemblies formed from metal plates welded together.
  • That method defined in claim 1 characterized in the step of utilizing tubular walls of substantially the same cross-sectional area to form all of said vapor flow passages.
  • That method defined in claim 3 characterized in the step of utilizing tubular walls of substantially the same diameter to interconnect said headers.
  • That method defined in claim 3 characterized in the step of carrying out the step of draining away condensate from points confined within said header assemblies.
  • That method defined in claim 1 characterized in the step of providing barrier means in the flow path of said superheated vapor to increase the velocity thereof and the wiping action between the vapor and the interior surfaces of said vapor flow passages thereby enhancing the efficiency of heat exchange between said vapor and the heat absorbing fluid in contact with the exterior of said tubular walls.
  • That method defined in claim 1 characterized in the steps of utilizing a substantially lesser number of tubular walls in parallel with one another to provide flow passages for superheated vapor than for flow passages for vapor approaching the dew point, inserting spiral strips of heat conductive material lengthwise of the interior of said lesser number of tubular walls whereby said superheated vapor flows therethrough at relatively high velocity and in a spiralling path tending to throw the vapor by centrifugal action into firmer wiping contact with said tubular walls to enhance heat exchange.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US121755A 1971-03-08 1971-03-08 High efficiency vapor condenser and method Expired - Lifetime US3675710A (en)

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US12175571A 1971-03-08 1971-03-08

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JP (1) JPS513579B2 (enrdf_load_html_response)

Cited By (51)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3835920A (en) * 1972-02-22 1974-09-17 Gen Motors Corp Compact fluid heat exchanger
US3968836A (en) * 1974-08-05 1976-07-13 Hudson Products Corporation Heat exchanger
US4018209A (en) * 1975-11-12 1977-04-19 Gene Ferruccio Bonvicini Air heater
US4047562A (en) * 1975-05-16 1977-09-13 Sulzer Brothers Limited Heat exchanger utilizing a vaporized heat-containing medium
US4141410A (en) * 1976-04-20 1979-02-27 Sasakura Engineering Company, Limited Evaporator
US4141409A (en) * 1977-04-21 1979-02-27 Karmazin Products Corporation Condenser header construction
US4165783A (en) * 1971-12-17 1979-08-28 Brown Boveri & Company Limited Heat exchanger for two vapor media
US4240502A (en) * 1979-11-26 1980-12-23 Hudson Products Corporation Condensing heat exchanger
US4243094A (en) * 1979-01-11 1981-01-06 Karmazin Products Corporation Condenser header construction
US4271821A (en) * 1980-08-08 1981-06-09 Kerr Colin C Solar energy collector
EP0050699A1 (fr) * 1980-10-23 1982-05-05 Hamon-Sobelco S.A. Batterie de condensation directe par air à pressions d'échappement multiples et ensemble comportant de telles batteries
US4446915A (en) * 1982-04-14 1984-05-08 The Trane Company Heat exchanger tube circuits
US4621686A (en) * 1984-01-05 1986-11-11 Intertherm, Inc. Water vapor-condensing secondary heat exchanger
US4632181A (en) * 1983-03-03 1986-12-30 Graham Robert G Ceramic heat exchanger
US4805692A (en) * 1987-03-10 1989-02-21 Pure Water, Inc. Condenser for water purification apparatus
EP0314585A1 (fr) * 1987-10-29 1989-05-03 Vicarb Echangeur de chaleur gaz/liquide avec condensation
US4903389A (en) * 1988-05-31 1990-02-27 General Motors Corporation Heat exchanger with laminated header and method of manufacture
US5049240A (en) * 1989-02-10 1991-09-17 Shell Oil Company Vaccum distillation system
US5190100A (en) * 1986-07-29 1993-03-02 Showa Aluminum Corporation Condenser for use in a car cooling system
US5246064A (en) * 1986-07-29 1993-09-21 Showa Aluminum Corporation Condenser for use in a car cooling system
US5458190A (en) * 1986-07-29 1995-10-17 Showa Aluminum Corporation Condenser
US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
US5586598A (en) * 1993-12-21 1996-12-24 Sanden Corporation Heat exchanger
USRE35655E (en) * 1986-07-29 1997-11-11 Showa Aluminum Corporation Condenser for use in a car cooling system
USRE35742E (en) * 1986-07-29 1998-03-17 Showa Aluminum Corporation Condenser for use in a car cooling system
US5752566A (en) * 1997-01-16 1998-05-19 Ford Motor Company High capacity condenser
US5775414A (en) * 1996-06-13 1998-07-07 Graham; Robert G. High temperature high pressure air-to-air heat exchangers and assemblies useful therein
US5941303A (en) * 1997-11-04 1999-08-24 Thermal Components Extruded manifold with multiple passages and cross-counterflow heat exchanger incorporating same
US5979543A (en) * 1995-10-26 1999-11-09 Graham; Robert G. Low to medium pressure high temperature all-ceramic air to air indirect heat exchangers with novel ball joints and assemblies
US6550273B2 (en) * 1997-12-16 2003-04-22 Matsushita Electric Industrial Co., Ltd. Air conditioner using flammable refrigerant
US6695522B1 (en) 1995-10-26 2004-02-24 Robert G. Graham Low to medium pressure high temperature all-ceramic air to air indirect heat exchangers with novel ball joints and assemblies
US20050051299A1 (en) * 2003-09-08 2005-03-10 Graham Robert G. Heat exchangers with novel ball joints and assemblies and processes using such heat exchangers
US20050280995A1 (en) * 2003-03-31 2005-12-22 Sanyo Denki Co., Ltd. Electronic component cooling apparatus
US20080031773A1 (en) * 2006-08-03 2008-02-07 Terumo Cardiovascular Systems Corporation Thermoelectric temperature control for extracorporeal blood circuit
US20080314378A1 (en) * 2007-06-22 2008-12-25 Johnson Controls Technology Company Heat exchanger
US20090183867A1 (en) * 2008-01-23 2009-07-23 Compressor Systems Inc. Varying ambient heat exchanger for a compressor
US20100095688A1 (en) * 2006-12-15 2010-04-22 Taras Michael F Refrigerant distribution improvement in parallell flow heat exchanger manifolds
WO2010057509A1 (de) * 2008-11-24 2010-05-27 Rwe Power Aktiengesellschaft Indirekt beheizter wirbelschichttrockner
US20100139313A1 (en) * 2006-12-15 2010-06-10 Taras Michael F Refrigerant vapor injection for distribution improvement in parallel flow heat exchanger manifolds
US20100263845A1 (en) * 2009-04-15 2010-10-21 Yoshiyasu Fujiwara Heat exchanger
US20130126140A1 (en) * 2011-11-18 2013-05-23 Taegyun Park Heat exchanger
US20130227946A1 (en) * 2010-09-28 2013-09-05 Jürgen Berger Tube bundle heat exchanger and waste gas heat recovery device
CN104246413A (zh) * 2012-04-26 2014-12-24 Lg电子株式会社 热交换器
US20140377155A1 (en) * 2013-06-21 2014-12-25 Phillips 66 Company Process for in-situ production of low dissolved hydrogen sulfide, degassed, sulfur from claus sulfur recovery
US20150192061A1 (en) * 2012-06-27 2015-07-09 Valeo Systemes Thermiques Heat Exchanger, Particularly Motor Vehicle Engine Charge Air Cooler
US20160348982A1 (en) * 2015-06-01 2016-12-01 GM Global Technology Operations LLC Heat exchanger with flexible port elevation and mixing
US20170307297A1 (en) * 2011-09-28 2017-10-26 Orcan Energy Ag Device and Method For Condensation of Steam From ORC Systems
US11333451B2 (en) * 2017-06-11 2022-05-17 Zvi Livni Plate and shell heat exchanging system having a divided manifold tube
USD1046085S1 (en) 2021-10-22 2024-10-08 Baltimore Aircoil Company, Inc. Heat exchanger tube
USD1078948S1 (en) * 2021-01-18 2025-06-10 Baltimore Aircoil Company, Inc. Indirect heat exchanger tube controlled wrinkle bend
US12392562B2 (en) 2021-01-18 2025-08-19 Baltimore Aircoil Company, Inc. Indirect heat exchanger pressure vessel with controlled wrinkle bends

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5383468U (enrdf_load_html_response) * 1976-12-10 1978-07-10
JPS5383467U (enrdf_load_html_response) * 1976-12-10 1978-07-10
JP2516408Y2 (ja) * 1990-04-27 1996-11-06 昭和アルミニウム株式会社 熱交換器

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US1578830A (en) * 1921-08-12 1926-03-30 Griscom Russell Co Heat exchanger
GB284413A (en) * 1926-11-01 1928-02-01 Harold Tindale Improvements in the method of cooling or heating industrial gases and apparatus therefor
US1759011A (en) * 1928-04-30 1930-05-20 Superheater Co Ltd Reheater
GB913270A (en) * 1960-08-12 1962-12-19 Daimler Benz Ag Improvements relating to motor-vehicle air-heating heat exchangers

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1578830A (en) * 1921-08-12 1926-03-30 Griscom Russell Co Heat exchanger
GB284413A (en) * 1926-11-01 1928-02-01 Harold Tindale Improvements in the method of cooling or heating industrial gases and apparatus therefor
US1759011A (en) * 1928-04-30 1930-05-20 Superheater Co Ltd Reheater
GB913270A (en) * 1960-08-12 1962-12-19 Daimler Benz Ag Improvements relating to motor-vehicle air-heating heat exchangers

Cited By (75)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4165783A (en) * 1971-12-17 1979-08-28 Brown Boveri & Company Limited Heat exchanger for two vapor media
US3835920A (en) * 1972-02-22 1974-09-17 Gen Motors Corp Compact fluid heat exchanger
US3968836A (en) * 1974-08-05 1976-07-13 Hudson Products Corporation Heat exchanger
US4047562A (en) * 1975-05-16 1977-09-13 Sulzer Brothers Limited Heat exchanger utilizing a vaporized heat-containing medium
US4018209A (en) * 1975-11-12 1977-04-19 Gene Ferruccio Bonvicini Air heater
US4141410A (en) * 1976-04-20 1979-02-27 Sasakura Engineering Company, Limited Evaporator
US4141409A (en) * 1977-04-21 1979-02-27 Karmazin Products Corporation Condenser header construction
US4243094A (en) * 1979-01-11 1981-01-06 Karmazin Products Corporation Condenser header construction
US4240502A (en) * 1979-11-26 1980-12-23 Hudson Products Corporation Condensing heat exchanger
US4271821A (en) * 1980-08-08 1981-06-09 Kerr Colin C Solar energy collector
EP0050699A1 (fr) * 1980-10-23 1982-05-05 Hamon-Sobelco S.A. Batterie de condensation directe par air à pressions d'échappement multiples et ensemble comportant de telles batteries
US4446915A (en) * 1982-04-14 1984-05-08 The Trane Company Heat exchanger tube circuits
US4632181A (en) * 1983-03-03 1986-12-30 Graham Robert G Ceramic heat exchanger
US4621686A (en) * 1984-01-05 1986-11-11 Intertherm, Inc. Water vapor-condensing secondary heat exchanger
USRE35742E (en) * 1986-07-29 1998-03-17 Showa Aluminum Corporation Condenser for use in a car cooling system
USRE35655E (en) * 1986-07-29 1997-11-11 Showa Aluminum Corporation Condenser for use in a car cooling system
USRE35711E (en) * 1986-07-29 1998-01-06 Showa Aluminum Corporation Condenser for use in a car cooling system
US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
US5458190A (en) * 1986-07-29 1995-10-17 Showa Aluminum Corporation Condenser
US5246064A (en) * 1986-07-29 1993-09-21 Showa Aluminum Corporation Condenser for use in a car cooling system
US5190100A (en) * 1986-07-29 1993-03-02 Showa Aluminum Corporation Condenser for use in a car cooling system
US4805692A (en) * 1987-03-10 1989-02-21 Pure Water, Inc. Condenser for water purification apparatus
US4850426A (en) * 1987-10-29 1989-07-25 Vicarb Gas/liquid heat exchanger with condensation
EP0314585A1 (fr) * 1987-10-29 1989-05-03 Vicarb Echangeur de chaleur gaz/liquide avec condensation
FR2622685A1 (fr) * 1987-10-29 1989-05-05 Vicarb Sa Echangeur de chaleur gaz/liquide avec condensation
US4903389A (en) * 1988-05-31 1990-02-27 General Motors Corporation Heat exchanger with laminated header and method of manufacture
US5049240A (en) * 1989-02-10 1991-09-17 Shell Oil Company Vaccum distillation system
US5586598A (en) * 1993-12-21 1996-12-24 Sanden Corporation Heat exchanger
US5797184A (en) * 1993-12-21 1998-08-25 Sanden Corporation Method of making a heat exchanger
US5979543A (en) * 1995-10-26 1999-11-09 Graham; Robert G. Low to medium pressure high temperature all-ceramic air to air indirect heat exchangers with novel ball joints and assemblies
US6206603B1 (en) 1995-10-26 2001-03-27 Robert G. Graham Low to medium pressure high temperature all-ceramic air to air indirect heat exchangers with novel ball joints and assemblies
US6695522B1 (en) 1995-10-26 2004-02-24 Robert G. Graham Low to medium pressure high temperature all-ceramic air to air indirect heat exchangers with novel ball joints and assemblies
US5775414A (en) * 1996-06-13 1998-07-07 Graham; Robert G. High temperature high pressure air-to-air heat exchangers and assemblies useful therein
US5752566A (en) * 1997-01-16 1998-05-19 Ford Motor Company High capacity condenser
US5941303A (en) * 1997-11-04 1999-08-24 Thermal Components Extruded manifold with multiple passages and cross-counterflow heat exchanger incorporating same
US6550273B2 (en) * 1997-12-16 2003-04-22 Matsushita Electric Industrial Co., Ltd. Air conditioner using flammable refrigerant
US20050280995A1 (en) * 2003-03-31 2005-12-22 Sanyo Denki Co., Ltd. Electronic component cooling apparatus
US7762317B2 (en) 2003-09-08 2010-07-27 Heat Transfer International, Inc. Heat exchangers with novel ball joints and assemblies and processes using such heat exchangers
US7294314B2 (en) 2003-09-08 2007-11-13 Graham Robert G Heat exchangers with novel ball joints and assemblies and processes using such heat exchangers
US20050051299A1 (en) * 2003-09-08 2005-03-10 Graham Robert G. Heat exchangers with novel ball joints and assemblies and processes using such heat exchangers
US20080041563A1 (en) * 2003-09-08 2008-02-21 Graham Robert G Heat exchangers with novel ball joints and assemblies and processes using such heat exchangers
US8240368B2 (en) 2003-09-08 2012-08-14 Graham Robert G Heat exchangers with novel ball joints and assemblies and processes using such heat exchangers
US20100224350A1 (en) * 2003-09-08 2010-09-09 Graham Robert G Heat exchangers with novel ball joints and assemblies and processes using such heat exchangers
US7588549B2 (en) * 2006-08-03 2009-09-15 Terumo Cardiovascular Systems Corporation Thermoelectric temperature control for extracorporeal blood circuit
US20080031773A1 (en) * 2006-08-03 2008-02-07 Terumo Cardiovascular Systems Corporation Thermoelectric temperature control for extracorporeal blood circuit
US20100139313A1 (en) * 2006-12-15 2010-06-10 Taras Michael F Refrigerant vapor injection for distribution improvement in parallel flow heat exchanger manifolds
US8528358B2 (en) * 2006-12-15 2013-09-10 Carrier Corporation Refrigerant vapor injection for distribution improvement in parallel flow heat exchanger manifolds
EP2092262A4 (en) * 2006-12-15 2011-05-11 Carrier Corp REFRIGERANT STEAM INJECTION FOR DISTRIBUTION IN PARALLEL HEAT EXCHANGE DISTRIBUTORS
EP2097701A4 (en) * 2006-12-15 2011-05-11 Carrier Corp REFRIGERANT DISTRIBUTION ENHANCEMENT IN PARALLEL HEAT EXCHANGE DISTRIBUTORS
US20100095688A1 (en) * 2006-12-15 2010-04-22 Taras Michael F Refrigerant distribution improvement in parallell flow heat exchanger manifolds
US8955507B2 (en) 2007-06-22 2015-02-17 Johnson Controls Technology Company Heat exchanger
US10024608B2 (en) 2007-06-22 2018-07-17 Johnson Controls Technology Company Heat exchanger
US20080314378A1 (en) * 2007-06-22 2008-12-25 Johnson Controls Technology Company Heat exchanger
US8393318B2 (en) * 2007-06-22 2013-03-12 Johnson Controls Technology Company Heat exchanger
US20090183867A1 (en) * 2008-01-23 2009-07-23 Compressor Systems Inc. Varying ambient heat exchanger for a compressor
US20110283555A1 (en) * 2008-11-24 2011-11-24 Rwe Power Aktiengesellschaft Indirectly heated fluidized bed dryer
WO2010057509A1 (de) * 2008-11-24 2010-05-27 Rwe Power Aktiengesellschaft Indirekt beheizter wirbelschichttrockner
US20100263845A1 (en) * 2009-04-15 2010-10-21 Yoshiyasu Fujiwara Heat exchanger
US20130227946A1 (en) * 2010-09-28 2013-09-05 Jürgen Berger Tube bundle heat exchanger and waste gas heat recovery device
US10605532B2 (en) * 2011-09-28 2020-03-31 Orcan Energy Ag Device and method for condensation of steam from ORC systems
US20170307297A1 (en) * 2011-09-28 2017-10-26 Orcan Energy Ag Device and Method For Condensation of Steam From ORC Systems
US20130126140A1 (en) * 2011-11-18 2013-05-23 Taegyun Park Heat exchanger
US9033029B2 (en) * 2011-11-18 2015-05-19 Lg Electronics Inc. Heat exchanger
CN104246413A (zh) * 2012-04-26 2014-12-24 Lg电子株式会社 热交换器
CN104246413B (zh) * 2012-04-26 2016-08-17 Lg电子株式会社 热交换器
US10551127B2 (en) 2012-04-26 2020-02-04 Lg Electronics Inc. Heat exchanger
US20150192061A1 (en) * 2012-06-27 2015-07-09 Valeo Systemes Thermiques Heat Exchanger, Particularly Motor Vehicle Engine Charge Air Cooler
US10240515B2 (en) * 2012-06-27 2019-03-26 Valeo Systemes Thermiques Heat exchanger, particularly motor vehicle engine charge air cooler
US9192887B2 (en) * 2013-06-21 2015-11-24 Phillips 66 Company Process for in-situ production of low dissolved hydrogen sulfide, degassed, sulfur from claus sulfur recovery
US20140377155A1 (en) * 2013-06-21 2014-12-25 Phillips 66 Company Process for in-situ production of low dissolved hydrogen sulfide, degassed, sulfur from claus sulfur recovery
US20160348982A1 (en) * 2015-06-01 2016-12-01 GM Global Technology Operations LLC Heat exchanger with flexible port elevation and mixing
US11333451B2 (en) * 2017-06-11 2022-05-17 Zvi Livni Plate and shell heat exchanging system having a divided manifold tube
USD1078948S1 (en) * 2021-01-18 2025-06-10 Baltimore Aircoil Company, Inc. Indirect heat exchanger tube controlled wrinkle bend
US12392562B2 (en) 2021-01-18 2025-08-19 Baltimore Aircoil Company, Inc. Indirect heat exchanger pressure vessel with controlled wrinkle bends
USD1046085S1 (en) 2021-10-22 2024-10-08 Baltimore Aircoil Company, Inc. Heat exchanger tube

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Publication number Publication date
JPS4857243A (enrdf_load_html_response) 1973-08-11
JPS513579B2 (enrdf_load_html_response) 1976-02-04

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