US3306063A - Method of evaporating liquid refrigerant in a semi-flooded type evaporator - Google Patents

Method of evaporating liquid refrigerant in a semi-flooded type evaporator Download PDF

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Publication number
US3306063A
US3306063A US478500A US47850065A US3306063A US 3306063 A US3306063 A US 3306063A US 478500 A US478500 A US 478500A US 47850065 A US47850065 A US 47850065A US 3306063 A US3306063 A US 3306063A
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US
United States
Prior art keywords
refrigerant
pool
liquid refrigerant
evaporator
liquid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US478500A
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English (en)
Inventor
Peter A Weller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
MERCANTILE TEXAS CREDIT Corp
American Radiator and Standard Sanitary Corp
Original Assignee
American Radiator and Standard Sanitary Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to GB1050268D priority Critical patent/GB1050268A/en
Priority to BE637665D priority patent/BE637665A/xx
Priority to NL298469D priority patent/NL298469A/xx
Priority claimed from US228055A external-priority patent/US3240265A/en
Priority to SE9634/63A priority patent/SE300437B/xx
Priority to DEA44188A priority patent/DE1274598B/de
Priority to CH1215863A priority patent/CH441399A/fr
Priority to FR949495A priority patent/FR1372158A/fr
Application filed by American Radiator and Standard Sanitary Corp filed Critical American Radiator and Standard Sanitary Corp
Priority to US478500A priority patent/US3306063A/en
Publication of US3306063A publication Critical patent/US3306063A/en
Application granted granted Critical
Assigned to MERCANTILE TEXAS CREDIT CORPORATION reassignment MERCANTILE TEXAS CREDIT CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SYNDER GENERAL CORPORATION
Assigned to SNYDER GENERAL CORPORATION reassignment SNYDER GENERAL CORPORATION ASSIGNS THE ENTIRE INTEREST, AS OF APRIL 2, 1982 SUBJECT TO LICENSES AND CONDITIONS RECITED, SEE DOCUMENT FOR DETAILS Assignors: SINGER COMPANY, THE
Anticipated expiration legal-status Critical
Assigned to CITICORP INDUSTRIAL CREDIT, INC., reassignment CITICORP INDUSTRIAL CREDIT, INC., SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SYNDER GENERAL CORPORATION A TX CORP
Assigned to CITICORP NORTH AMERICA, INC. reassignment CITICORP NORTH AMERICA, INC. SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SNYDERGENERAL CORPORATION, A MN CORP.
Assigned to SNYDERGENERAL CORPORATION, A MN CORP. reassignment SNYDERGENERAL CORPORATION, A MN CORP. RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: MCREDIT
Assigned to SNYDERGENERAL CORPORATION, A CORP. OF MINNESOTA, MCQUAY INC., A CORP. OF MINNESOTA reassignment SNYDERGENERAL CORPORATION, A CORP. OF MINNESOTA RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: CITICORP NORTH AMERICA, INC.
Assigned to SNYDERGENERAL CORPORATION A CORP. OF DELAWARE reassignment SNYDERGENERAL CORPORATION A CORP. OF DELAWARE RELEASE BY SECOND PARTY OF A SECURITY AGREEMENT RECORDED AT REEL 5013 FRAME 592. Assignors: CITICORP NORTH AMERICA, INC. A CORP. OF DELAWARE
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • 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
    • F25B2339/02—Details of evaporators
    • F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
    • F25B2339/0242—Evaporators with refrigerant in a vessel in which is situated a heat exchanger having tubular elements

Definitions

  • This invention relates to refrigeration evaporator systems, and more particularly to an improved refrigeration evaporator of the flooded type, and to the method of operation.
  • An important object of the present invention is to provide a method of evaporating liquid refrigerant in a refrigeration evaporator of the heavy duty industrial semifiooded type.
  • a further object is to provide a method of evaporating liquid refrigerant wherein the bubbling action due to flash vaporization of a portion of the entering liquid refrigerant is substantially equally distributed throughout the evaporator to substantially evenly splash liquid over the heat exchange tubes that are exposed above the liquid.
  • Another object of the invention is to provide a method wherein a thin layer of oil is resent on the pool of liquid refrigerant, circulation being provided within the evaporator to maintain the layer of oil evenly over the surface of the pool of refrigerant.
  • Another object is to provide a method of evaporating liquid refrigerant from a shallow, horizontal pool of uniform depth on which a uniform covering layer of oil is provided for improved heat transfer.
  • FIGURE 1 is a transverse sectional view of a refrigerant evaporator made in accordance with the present invention.
  • FIGURE 2 is a longitudinal sectional view showing a schematic arrangement of a liquid refrigerant distribution system in an evaporator made in accordance with the present invention.
  • the present invention relates to a novel and improved refrigeration evaporator of the semi-flooded type wherein the bubbling action due to the liquid refrigerant which boils is fully utilized to splash liquid over all of the heat exchange tubes, even when operating with a liquid level substantially below the top of the tube bundle.
  • a tube bundle which in transverse cross section has a relatively shallow, even depth, and with vapor diverters strategically located in the bundle to force the rising vapor uniformly through the entire tube bundle for uniform tube wetting; and by a liquid refrigerant delivery system assuring uniform spreading of the entering liquid refrigerant over the bottom of the unit.
  • an improved refrigeration evaporator in accordance with the present invention is designated by the reference numeral 18.
  • This unit includes an upper dome-like shell of pressure resistant material such as steel, and designated by the numeral 12.
  • An outer insulation layer is provided at 14.
  • a flat transverse wall 16 is provided across the bottom of the upper steel shell 12 to support the tube bundle as will be hereinafter set forth.
  • the shell 12 and wall 15 are joined by welding as at 17.
  • a concave wall 18 Across the bottom of the unit there is provided a concave wall 18, so configured in order to resist internal pressures of the unit and, as will be evident from the following description, providing a vapor space beneath the Wall 16 for insulation, and for purposes of equalizing pressures above and below wall 16.
  • the tube bundle is designated broadly by the number 20 and is of generally rectilinear outer configuration. Actually, the tube bundle is rectangular in cross section and the bounding sides, top and bottom, are generally straight lines. It will also be noted that the tubes 22 of the bundle 20 lie in a generally straight line along the bottom, conforming to the fiat upper surface of the intermediate or fiat transverse wall 16.
  • every vertical column of tubes designated by the reference numeral 24 is essentially of the same height and thus operates with substantially the same submergence to obtain complete tube wetting.
  • a distribution main tube designated by the reference numeral 26 extends axially of the unit for conducting liquid and flash gas from the high side float or other valve of a suitable refrigeration system. It should be noted at this point that liquid refrigerant on the condenser side of a float valve is at a higher temperature and higher pressure than refrigerant on the evaporator side of the float valve. As soon as liquid refrigerant passes through the float valve, it is subjected to the temperature and pressure conditions on the evaporator side. The lower temperature and lower pressure on the evaporator side results in a portion of the liquid refrigerant which passes through the float immediately vaporizing. This is termed flash vaporization.
  • a plurality of feeder tubes 28 Extending downwardly from the distributor main 26 are a plurality of feeder tubes 28 of vertical disposition and uniformly spaced along the length of the main 26.
  • Nozzles 30 are provided at the bottom end of each of the vertical feeder tubes 28 and are directed horizontally and sized to impart a moderate velocity to the incoming refrigerant and are directed in the fanlike pattern shown by the arrows 32, FIGURE 2, to create a uniform circulation across the bottom of each compartment 34, 36 and 38 defined by the transverse end tube sheets 40 and the transverse tube support sheets 4-2.
  • circulator tubes 44 comprising a down comer 46 and a lateral feed 48 with an upturned end elbow-nozzle 50.
  • the circulator tubes 44 run from the distribution tube 26 downward via the down comer 46, then horizontally via the lateral arm 48 below the tube bundle to the outer edges, then rise and turn via the elbow-nozzle 50 towards the tube support sheets 42, in the manner shown, so as to impart a jet of refrigerant through Openings 52 at the lower corners of the tube support sheets 42.
  • These jets are arranged to effect the circulation between compartments in the same direction of rotation, as indicated by arrows 51, and in the same direction as the local circulation within each compartment 34, 36, 38, as designated by the arrows 32.
  • openings 52 be high enough and the raised elbownozzles 50 be at a proper level to cause the high concentration of surface oil to migrate from one compartment to another in a continuous and uniform pattern, thereby preventing the concentration of oil in any one location and the depletion of oil in any other location.
  • the total circulation pattern provides a uniform covering of oil over the entire body of liquid refrigerant within the unit.
  • FIGURE 1 there is shown one method of com struction for achieving the rectangular tube bundle re quired for optimum results, wherein the evaporator is in its own individual shell.
  • the trans verse plate 16 is continuous, forming the required flat bottom of the evaporator proper for holding liquid refrigerant at a desired uniform depth.
  • the underlying curved bottom 18 forms the bottom exterior wall of the shell. As previously indicated, this is of concave configuration and therefore resistant to internal pressures; I
  • a vapor space 66 is provided between the concave bot;- tom wall 18 and the flat transverse bundle support wall 16 to provide a dead gas space for purposes of thermal insulation against inward heat transfer from the ambient atmosphere.
  • vent tube 68 is connected at its lower end into an opening 70 in wall 16 and extends upwardly above the top level of the tube bundle 20. It will be noted that the top 72 of vent tube 68 extends well above the top oftube bundle 20 and thus the vapor space 66 below wall 16 is vented to the upper vapor space 74 above wall1-6 and the tube bundle, thereby equalizing pressures on the opposite sides of wall 16 and preventing any lateral load tendency to buckle the same.
  • Bottom wall 18 thus works on pure tension or com pression to maintain the shell shape when portions 12 and 16 are subjected to internal or external pressures; Because the vapor space 66 is filled with refrigerant gas at very low pressure, it acts as an insulator so that no external insulation is required over the bottom of the shell, thus contributing to manufacturing economy and operating efficiency of the unit. v
  • Vapor outlet for the unit is provided at 78.
  • a desired height for space 66,- as indicated at the point 76 is about one inch per foot of concavity.
  • a dimen sion at the point 76 would be about 1 /2 to about 3 inches. This assures that convection and eddy currents are kept to a minimum, thus substantially neutralizing heat transfer to the interior of the unit from ambient surroundings.
  • the strongest boiling action occurs at the entering water, i.e., where the water temperature is highest. This causes the level of refrigerant to drop in this region of an evaporator and thus effects a gradient of surface flow from the other areas of the evaporator to this warmest area. Because the fresh, clean refrigerant from the condenser is being brought in at the bottom and because of the boiling action, the oil is concentrated near the top of the refrigerant. Thus, the surface flow mentioned above carries the oil with it and the oil concentrates at the warm-' est area of the evaporator and the other areas become essentially oil free. This is obviously undesirable be cause it negates the effect of the oil in the major part of the evaporator and amplifies the natural difference in boiling action due to difference in water temperature.
  • the present invention by utilizing a uniform refrigerant level by the aforedisclosed distribution and circulation system, distributes the liquid refrigerant in such a way that oil distribution is maintained uniform as a layer over the entire body of liquid and the tendency for it to concentrate is therefore counteracted.
  • the wall 18 has related to the wall 18 as being of concave configuration.
  • the broad scope of invention would include a flat wall at 18, given sufficient subjacent support as by tube bundle supports of a subjacent condenser of a unitary shell structure mentioned above.
  • the bottom wall 13 may be insulated in some applications where heat transfer must be kept to an absolute nil level.
  • the present invention provides a unique and more highly evaporator tube bundle arrangement and liquid refrigerant distribution system than has heretofore being provided in the prior art.
  • a further advantage of the present invention resides in the fact that greatest utilization of oil for tube wetting ancl for uniform boiling action and heat transfer efficiency is provided by the novel and uniform refrigerant distribution system of the present invention.
  • a method of evaporating liquid refrigerant in a refrigeration evaporator system of the semi-flooded type in which the evaporator includes an elongated hollow shell having therein an axially extending tube bundle partially submerged in a pool of liquid refrigerant and wherein the boiling action of the refrigerant splashes liquid from a lower level over the upper tubes characterized in the steps of forming the liquid refrigerant into at least one horizontally disposed pool of uniform depth, moving the refrigerant from a point of higher pressure than the pressure in the evaporator into said pool in a plurality of streams flowing parallel to the bottom thereof and directed in a horizontal fan pattern which produces a swirling motion in the pool about a horizontal circle and uniformly distributes the incoming refrigerant throughout the pool, thereby resulting in flash vaporization of a portion of the incoming refrigerant due to the pressure differential whereby, as a result of the uniform distribution of the incoming refrigerant, the flash vaporization occurs uniformly throughout the pool, and
  • a method according to claim 1 characterized in that the streams of liquid refrigerant originate along the longitudinal axis of the pool and are directed outwardly therefrom towards the outer edges of the pool.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Sorption Type Refrigeration Machines (AREA)
US478500A 1962-10-03 1965-06-01 Method of evaporating liquid refrigerant in a semi-flooded type evaporator Expired - Lifetime US3306063A (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
GB1050268D GB1050268A (xx) 1962-10-03
BE637665D BE637665A (xx) 1962-10-03
NL298469D NL298469A (xx) 1962-10-03
SE9634/63A SE300437B (xx) 1962-10-03 1963-09-03
DEA44188A DE1274598B (de) 1962-10-03 1963-10-02 Fluessigkeitsverdampfer
CH1215863A CH441399A (fr) 1962-10-03 1963-10-03 Procédé pour faire évaporer un réfrigérant liquide et évaporateur pour la mise en oeuvre de ce procédé
FR949495A FR1372158A (fr) 1962-10-03 1963-10-03 évaporateur de réfrigération et son procédé de fonctionnement
US478500A US3306063A (en) 1962-10-03 1965-06-01 Method of evaporating liquid refrigerant in a semi-flooded type evaporator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US228055A US3240265A (en) 1962-10-03 1962-10-03 Refrigeration evaporator system of the flooded type
US478500A US3306063A (en) 1962-10-03 1965-06-01 Method of evaporating liquid refrigerant in a semi-flooded type evaporator

Publications (1)

Publication Number Publication Date
US3306063A true US3306063A (en) 1967-02-28

Family

ID=26922014

Family Applications (1)

Application Number Title Priority Date Filing Date
US478500A Expired - Lifetime US3306063A (en) 1962-10-03 1965-06-01 Method of evaporating liquid refrigerant in a semi-flooded type evaporator

Country Status (7)

Country Link
US (1) US3306063A (xx)
BE (1) BE637665A (xx)
CH (1) CH441399A (xx)
DE (1) DE1274598B (xx)
GB (1) GB1050268A (xx)
NL (1) NL298469A (xx)
SE (1) SE300437B (xx)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100319395A1 (en) * 2008-01-11 2010-12-23 Johnson Controls Technology Company Heat exchanger
US20180306519A1 (en) * 2015-10-21 2018-10-25 Technip France Device for the exchange of heat between a first fluid intended to be vaporized and a second fluid intended to be cooled and/or condensed, and associated installation and method
CN115031440A (zh) * 2022-07-29 2022-09-09 湖南东尤水汽能节能有限公司 一种浸泡换热式水汽能热泵空气调节装置

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1937802A (en) * 1931-10-12 1933-12-05 Frick Co Heat exchanger
US2022787A (en) * 1933-04-14 1935-12-03 Gen Motors Corp Refrigerating apparatus
US2059725A (en) * 1934-03-09 1936-11-03 Carrier Engineering Corp Shell and tube evaporator
US2114128A (en) * 1935-04-05 1938-04-12 Gen Motors Corp Refrigerating apparatus
US2147788A (en) * 1936-06-15 1939-02-21 Norman H Gay Ebullition-type cooler
US2189731A (en) * 1938-08-13 1940-02-06 B F Sturtevant Co Sprayed evaporator
US2440930A (en) * 1945-04-02 1948-05-04 Gen Electric Cooling system
US2854828A (en) * 1956-04-02 1958-10-07 Frick Co Free flow evaporator
US3210955A (en) * 1963-07-22 1965-10-12 Carrier Corp Refrigeration apparatus

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2964926A (en) * 1958-10-17 1960-12-20 Trane Co Flooded water chiller

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1937802A (en) * 1931-10-12 1933-12-05 Frick Co Heat exchanger
US2022787A (en) * 1933-04-14 1935-12-03 Gen Motors Corp Refrigerating apparatus
US2059725A (en) * 1934-03-09 1936-11-03 Carrier Engineering Corp Shell and tube evaporator
US2114128A (en) * 1935-04-05 1938-04-12 Gen Motors Corp Refrigerating apparatus
US2147788A (en) * 1936-06-15 1939-02-21 Norman H Gay Ebullition-type cooler
US2189731A (en) * 1938-08-13 1940-02-06 B F Sturtevant Co Sprayed evaporator
US2440930A (en) * 1945-04-02 1948-05-04 Gen Electric Cooling system
US2854828A (en) * 1956-04-02 1958-10-07 Frick Co Free flow evaporator
US3210955A (en) * 1963-07-22 1965-10-12 Carrier Corp Refrigeration apparatus

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100319395A1 (en) * 2008-01-11 2010-12-23 Johnson Controls Technology Company Heat exchanger
US8863551B2 (en) * 2008-01-11 2014-10-21 Johnson Controls Technology Company Heat exchanger
US20180306519A1 (en) * 2015-10-21 2018-10-25 Technip France Device for the exchange of heat between a first fluid intended to be vaporized and a second fluid intended to be cooled and/or condensed, and associated installation and method
US11686531B2 (en) * 2015-10-21 2023-06-27 Technip Energies France Device for the exchange of heat between a first fluid intended to be vaporized and a second fluid intended to be cooled and/or condensed, and associated installation and method
CN115031440A (zh) * 2022-07-29 2022-09-09 湖南东尤水汽能节能有限公司 一种浸泡换热式水汽能热泵空气调节装置
CN115031440B (zh) * 2022-07-29 2024-01-16 湖南东尤水汽能节能有限公司 一种浸泡换热式水汽能热泵空气调节装置

Also Published As

Publication number Publication date
GB1050268A (xx)
BE637665A (xx)
NL298469A (xx)
CH441399A (fr) 1967-08-15
DE1274598B (de) 1968-08-08
SE300437B (xx) 1968-04-29

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