US3240265A - Refrigeration evaporator system of the flooded type - Google Patents
Refrigeration evaporator system of the flooded type Download PDFInfo
- Publication number
- US3240265A US3240265A US228055A US22805562A US3240265A US 3240265 A US3240265 A US 3240265A US 228055 A US228055 A US 228055A US 22805562 A US22805562 A US 22805562A US 3240265 A US3240265 A US 3240265A
- Authority
- US
- United States
- Prior art keywords
- tubes
- shell
- refrigerant
- tube
- liquid refrigerant
- 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
- 238000005057 refrigeration Methods 0.000 title description 14
- 239000003507 refrigerant Substances 0.000 claims description 76
- 239000007788 liquid Substances 0.000 claims description 52
- 239000012530 fluid Substances 0.000 claims description 3
- 238000004891 communication Methods 0.000 claims description 2
- 230000009471 action Effects 0.000 description 16
- 238000009835 boiling Methods 0.000 description 12
- 238000009826 distribution Methods 0.000 description 8
- 238000012546 transfer Methods 0.000 description 8
- 238000009736 wetting Methods 0.000 description 7
- 230000008016 vaporization Effects 0.000 description 6
- 238000009413 insulation Methods 0.000 description 5
- 238000009834 vaporization Methods 0.000 description 5
- 230000008901 benefit Effects 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000005012 migration Effects 0.000 description 3
- 238000013508 migration Methods 0.000 description 3
- 238000009827 uniform distribution Methods 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 238000013459 approach Methods 0.000 description 2
- 230000005587 bubbling Effects 0.000 description 2
- 239000012141 concentrate Substances 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 239000012212 insulator Substances 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- BHELIUBJHYAEDK-OAIUPTLZSA-N Aspoxicillin Chemical compound C1([C@H](C(=O)N[C@@H]2C(N3[C@H](C(C)(C)S[C@@H]32)C(O)=O)=O)NC(=O)[C@H](N)CC(=O)NC)=CC=C(O)C=C1 BHELIUBJHYAEDK-OAIUPTLZSA-N 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000003292 diminished effect Effects 0.000 description 1
- 238000009422 external insulation Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000003472 neutralizing effect Effects 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000003892 spreading Methods 0.000 description 1
- 230000007480 spreading Effects 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
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
- a further object is to provide an improved refrigeration evaporator wherein the bubbling action due to flash vaporization of a portion of the entering liquid refrigerant is substantially evenly distributed throughout the evaporator to substantially evenly splash liquid over the heat exchange tubes that are exposed above the liquid.
- a further object is to provide an improved refrigerant evaporator of the tube shell type incorporating an improved tube bundle arrangement and wherein full utilization of the splashing action of the flashing refrigerant is realized.
- an object of the present invention is to provide a low profile evaporator that can be used per se or in any desired environment, such as in a unitary shell with an associated refrigerant condenser, if desired.
- 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 refrigcrant 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 10.
- 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 16 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.
- Tube bundle configuration By reference to FIGURE 1, it will be noted that 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 flat 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 the 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.
- 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 fan-like 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 42.
- circulator tubes 44 comprising a downcomer 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 downcomer 46, then horizontally via the lateral arm 48 below the tube bundle 20 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 elbow-nozzles 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.
- the specific design of the block 60, cap member 62 and block 64 is not critical. However, the function they perform is highly important, namely to prevent vapor from escaping up through any open channels, and thus, the blocks are inserted near the top of the channels. It will be appreciated that if the open channels were not blocked, they would function much in the manner of a chimney. A low pressure condition would thus result at the bottom of the channels. This low pressure condition would accelerate vaporization of refrigerant directly beneath the channels. The splashing action caused by this vaporization would thus occur directly beneath the channels and result in a large portion of the splashed refrigerant being directed up the channels rather than through the tubes. It is desired to have splashing occur beneath the tubes so that the tubes will be wetted. By preventing the occurrence of low pressure conditions at the bottom of the open channels, vaporization of refrigerant will take place uniformly over the entire pool of refrigerant thus resulting an flashing of liquid refrigerant evenly on the tubes.
- Transverse wall I 6 and its insulation function In FIGURE 1, there is shown one method of construction for achieving the rectangular tube bundle required for optimum results, wherein the evaporator is in its own individual shell.
- the transverse 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.
- a vapor space 66 is provided between the concave bottom 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 ex tends well above the top of tube bundle 20 and thus the vapor space 66 below wall 16 is vented to the upper vapor space 74 above wall 16 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 compression 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 insula tion is required over the bottom of the shell, thus contributing to manufacturing economy and operating efliciency of the unit.
- Vapor outlet for the unit is provided at 78.
- vapor space 66 When it is understood that stagnant gaseous refrigerant, either hot or cold, is a good heat insulator, the economy of the present invention is fully appreciated. Because the vapor space 66 is hor zontal and narrow, convection currents are kept to a low level.
- a desired height for space 66 is about one inch per foot of concavity.
- a dimension 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 refriger ant 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 warmest area of the evaporator and the other areas become essentially oil free. This is obviously undesirable because it negates the effect of the oil in the major part of the evaporator and amplifies the natural differences 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 13, given sufficient subjacent suppoht as by tube bundle supports of a subjacent condenser of a unitary shell structure mentioned above.
- the bottom wall 18 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 efficient evaporator tube bundle arrangement and liquid refrigerant distribution system than has heretofore been provided in the prior art.
- a further advantage of the present invention resides in the fact that greatest utilization of oil for tube wetting and for uniform boiling action and heat transfer efficiency is provided by the novel and uniform refrigerant distribution system of the present invention.
- a liquid refrigerant evaporator comprising an elongated hollow shell forming a fluid-tight enclosure, a plurality of longitudinally extending tubes in said shell, said tubes being spaced apart both vertically and horizontally, at least one transversely extending tube support sheet within the shell intermediate the ends of the shell defining separate compartments within the shell, said tube support sheet having tube openings therein for said tubes, each of said tubes passing through one of said tube openings and being supported by the tube support sheet, a pool of liquid refrigerant in each compartment of the shell,
- said pools each having a depth suificient only to submerge some of the lower tubes, said tube support sheet having flow openings therein extending from a point above the level of the pools of liquid refrigerant to a point below the level thereof to provide for fluid communication between the compartments, a layer of oil overlying each pool of liquid refrigerant, a plurality of first discharge nozzles submerged in each pool of refrigerant, said first nozzles being spaced apart to result in a uniform distribution in the pools of liquid refrigerant discharged therefrom, the first nozzles in each compartment being aimed with respect to each other to cause continuous circulatory movement of each pool of refrigerant within its compartment to result in continuous migration of the oil in each compartment to maintain the oil in each compartment as a uniform layer, the direction of the circulatory movement of the refrigerant in each compartment being the same as the refrigerant movement in the other compartment, at least one second discharge nozzle in each compartment submerged in the liquid refrigerant, each of said second nozzles being positioned at
- a liquid refrigerant evaporator comprising an elongated hollow shell forming a fluid-tight enclosure, a plurality of longitudinally extending tube bundles in said shell, each tube bundle comprising a plurality of substantially parallel closely adjacent tubes, said tube bundles being spaced horizontally apart to define relatively wide unobstructed vertical passages therebetween, a longitudinally extending block in each of said vertical passages to prevent the passage of fluid thereby, said tubes being spaced apart both vertically and horizontally, a pool of liquid refrigerant in the shell having a depth sufficient only to submerge some of the lower tubes, a layer of oil floating on the pool, a plurality of discharge nozzles submerged in the pool of refrigerant, said nozzles being spaced apart to result in a uniform distribution in the pool of liquid refrigerant discharged therefrom, said nozzles being aimed with respect to each other to cause continuous circulatory movement in the pool of refrigerant to result in continuous migration of the oil to maintain the oil as a uniform layer, and means
- a liquid refrigerant evaporator comprising an elongated hollow shell forming a fluid-tight enclosure, a plurality of longitudinally extending tubes in said shell, said tubes being spaced apart both vertically and horizontally and defining, in transverse cross section, a tube bundle of substantially rectangular configuration, a substantially flat imperforate horizontally disposed bottom wall beneath the tubes, a pool of liquid refrigerant of substantially uniform depth contained by the shell and the bottom wall, said pool having a depth sufiicient only to submerge some of the lower tubes, a layer of oil overlying the pool of refrigerant, a plurality of discharge nozzles submerged in the pool of refrigerant, said nozzles being spaced apart to result in a uniform distribution in the pool of liquid refrigerant discharged therefrom, said nozzles being aimed with respect to each other to cause continuous circulatory movement of the pool of refrigerant to result in continuous migration of the oil to maintain the oil as a uniform layer, and means to supply liquid refrigerant
Landscapes
- 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)
Description
Claims (1)
Priority Applications (10)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB1050268D GB1050268A (en) | 1962-10-03 | ||
BE637665D BE637665A (en) | 1962-10-03 | ||
NL298469D NL298469A (en) | 1962-10-03 | ||
US228055A US3240265A (en) | 1962-10-03 | 1962-10-03 | Refrigeration evaporator system of the flooded type |
SE9634/63A SE300437B (en) | 1962-10-03 | 1963-09-03 | |
AT760363A AT250410B (en) | 1962-10-03 | 1963-09-20 | Method for evaporating liquid refrigerant in a refrigerant evaporation system of the flooded type and evaporator for this |
DEA44188A DE1274598B (en) | 1962-10-03 | 1963-10-02 | Liquid evaporator |
CH1215863A CH441399A (en) | 1962-10-03 | 1963-10-03 | Process for evaporating a liquid refrigerant and evaporator for the implementation of this process |
FR949495A FR1372158A (en) | 1962-10-03 | 1963-10-03 | refrigeration evaporator and its method of operation |
US478500A US3306063A (en) | 1962-10-03 | 1965-06-01 | Method of evaporating liquid refrigerant in a semi-flooded type evaporator |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US228055A US3240265A (en) | 1962-10-03 | 1962-10-03 | Refrigeration evaporator system of the flooded type |
Publications (1)
Publication Number | Publication Date |
---|---|
US3240265A true US3240265A (en) | 1966-03-15 |
Family
ID=22855585
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US228055A Expired - Lifetime US3240265A (en) | 1962-10-03 | 1962-10-03 | Refrigeration evaporator system of the flooded type |
Country Status (2)
Country | Link |
---|---|
US (1) | US3240265A (en) |
AT (1) | AT250410B (en) |
Cited By (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3299653A (en) * | 1965-10-20 | 1967-01-24 | Carrier Corp | Refrigeration system |
US5561987A (en) * | 1995-05-25 | 1996-10-08 | American Standard Inc. | Falling film evaporator with vapor-liquid separator |
US5588596A (en) * | 1995-05-25 | 1996-12-31 | American Standard Inc. | Falling film evaporator with refrigerant distribution system |
US20060080998A1 (en) * | 2004-10-13 | 2006-04-20 | Paul De Larminat | Falling film evaporator |
US20080163637A1 (en) * | 2007-01-04 | 2008-07-10 | American Standard International Inc. | Gas trap distributor for an evaporator |
US20090178790A1 (en) * | 2008-01-11 | 2009-07-16 | Johnson Controls Technology Company | Vapor compression system |
US20110017432A1 (en) * | 2009-07-22 | 2011-01-27 | Johnson Controls Technology Company | Compact evaporator for chillers |
US20110056664A1 (en) * | 2009-09-08 | 2011-03-10 | Johnson Controls Technology Company | Vapor compression system |
US20110120181A1 (en) * | 2006-12-21 | 2011-05-26 | Johnson Controls Technology Company | Falling film evaporator |
US20150013950A1 (en) * | 2013-07-11 | 2015-01-15 | Aaf-Mcquay Inc. | Heat exchanger |
US20150013951A1 (en) * | 2013-07-11 | 2015-01-15 | Aaf-Mcquay Inc. | Heat exchanger |
JP2016056966A (en) * | 2014-09-05 | 2016-04-21 | 三菱重工業株式会社 | Turbo refrigerator |
US9429317B2 (en) | 2010-10-05 | 2016-08-30 | Edward Stock | Wastewater evaporation apparatus and method |
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 |
US10209013B2 (en) | 2010-09-03 | 2019-02-19 | Johnson Controls Technology Company | Vapor compression system |
Citations (11)
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US213836A (en) * | 1879-04-01 | Improvement in water-coolers | ||
US1856467A (en) * | 1929-09-09 | 1932-05-03 | Pevely Dairy Company | Liquid cooler |
US1937802A (en) * | 1931-10-12 | 1933-12-05 | Frick Co | Heat exchanger |
US2059725A (en) * | 1934-03-09 | 1936-11-03 | Carrier Engineering Corp | Shell and tube evaporator |
US2107053A (en) * | 1935-10-28 | 1938-02-01 | Herbert L Somers | Method of refrigeration |
US2146058A (en) * | 1936-12-18 | 1939-02-07 | Doyle Charles Herbert | Refrigerating method |
US2147788A (en) * | 1936-06-15 | 1939-02-21 | Norman H Gay | Ebullition-type cooler |
US2247107A (en) * | 1938-09-30 | 1941-06-24 | Buensod Stacey Air Conditionin | Refrigerant evaporator |
US2312313A (en) * | 1941-10-17 | 1943-03-02 | York Ice Machinery Corp | Evaporator |
US2854828A (en) * | 1956-04-02 | 1958-10-07 | Frick Co | Free flow evaporator |
US2863297A (en) * | 1955-03-29 | 1958-12-09 | Herrick L Johnston Inc | Method and apparatus for storing liquified gases |
-
1962
- 1962-10-03 US US228055A patent/US3240265A/en not_active Expired - Lifetime
-
1963
- 1963-09-20 AT AT760363A patent/AT250410B/en active
Patent Citations (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US213836A (en) * | 1879-04-01 | Improvement in water-coolers | ||
US1856467A (en) * | 1929-09-09 | 1932-05-03 | Pevely Dairy Company | Liquid cooler |
US1937802A (en) * | 1931-10-12 | 1933-12-05 | Frick Co | Heat exchanger |
US2059725A (en) * | 1934-03-09 | 1936-11-03 | Carrier Engineering Corp | Shell and tube evaporator |
US2107053A (en) * | 1935-10-28 | 1938-02-01 | Herbert L Somers | Method of refrigeration |
US2147788A (en) * | 1936-06-15 | 1939-02-21 | Norman H Gay | Ebullition-type cooler |
US2146058A (en) * | 1936-12-18 | 1939-02-07 | Doyle Charles Herbert | Refrigerating method |
US2247107A (en) * | 1938-09-30 | 1941-06-24 | Buensod Stacey Air Conditionin | Refrigerant evaporator |
US2312313A (en) * | 1941-10-17 | 1943-03-02 | York Ice Machinery Corp | Evaporator |
US2863297A (en) * | 1955-03-29 | 1958-12-09 | Herrick L Johnston Inc | Method and apparatus for storing liquified gases |
US2854828A (en) * | 1956-04-02 | 1958-10-07 | Frick Co | Free flow evaporator |
Cited By (38)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3299653A (en) * | 1965-10-20 | 1967-01-24 | Carrier Corp | Refrigeration system |
GB2315849A (en) * | 1995-05-25 | 1998-02-11 | American Standard Inc | Falling film evaporator with vapor-liquid separator |
WO1996037741A1 (en) * | 1995-05-25 | 1996-11-28 | American Standard Inc. | Falling film evaporator with vapor-liquid separator |
US5645124A (en) * | 1995-05-25 | 1997-07-08 | American Standard Inc. | Falling film evaporator with refrigerant distribution system |
US5638691A (en) * | 1995-05-25 | 1997-06-17 | American Standard Inc. | Falling film evaporator with refrigerant distribution system |
US5588596A (en) * | 1995-05-25 | 1996-12-31 | American Standard Inc. | Falling film evaporator with refrigerant distribution system |
US5561987A (en) * | 1995-05-25 | 1996-10-08 | American Standard Inc. | Falling film evaporator with vapor-liquid separator |
GB2315849B (en) * | 1995-05-25 | 1999-10-27 | American Standard Inc | Evaporator with falling film and flooded evaporator portions |
US7849710B2 (en) | 2004-10-13 | 2010-12-14 | York International Corporation | Falling film evaporator |
US20060080998A1 (en) * | 2004-10-13 | 2006-04-20 | Paul De Larminat | Falling film evaporator |
US20110120181A1 (en) * | 2006-12-21 | 2011-05-26 | Johnson Controls Technology Company | Falling film evaporator |
US8650905B2 (en) | 2006-12-21 | 2014-02-18 | Johnson Controls Technology Company | Falling film evaporator |
US20080163637A1 (en) * | 2007-01-04 | 2008-07-10 | American Standard International Inc. | Gas trap distributor for an evaporator |
US7421855B2 (en) | 2007-01-04 | 2008-09-09 | Trane International Inc. | Gas trap distributor for an evaporator |
EP2541172A2 (en) | 2007-01-04 | 2013-01-02 | Trane International Inc. | Gas Trap Distributor for an Evaporator |
US20100319395A1 (en) * | 2008-01-11 | 2010-12-23 | Johnson Controls Technology Company | Heat exchanger |
US20100326108A1 (en) * | 2008-01-11 | 2010-12-30 | Johnson Controls Technology Company | Vapor compression system |
US20100242533A1 (en) * | 2008-01-11 | 2010-09-30 | Johnson Controls Technology Company | Heat exchanger |
US20090178790A1 (en) * | 2008-01-11 | 2009-07-16 | Johnson Controls Technology Company | Vapor compression system |
US8302426B2 (en) | 2008-01-11 | 2012-11-06 | Johnson Controls Technology Company | Heat exchanger |
US20100276130A1 (en) * | 2008-01-11 | 2010-11-04 | Johnson Controls Technology Company | Heat exchanger |
US8863551B2 (en) * | 2008-01-11 | 2014-10-21 | Johnson Controls Technology Company | Heat exchanger |
US10317117B2 (en) | 2008-01-11 | 2019-06-11 | Johnson Controls Technology Company | Vapor compression system |
US9347715B2 (en) | 2008-01-11 | 2016-05-24 | Johnson Controls Technology Company | Vapor compression system |
US20110017432A1 (en) * | 2009-07-22 | 2011-01-27 | Johnson Controls Technology Company | Compact evaporator for chillers |
US8944152B2 (en) * | 2009-07-22 | 2015-02-03 | Johnson Controls Technology Company | Compact evaporator for chillers |
US20110056664A1 (en) * | 2009-09-08 | 2011-03-10 | Johnson Controls Technology Company | Vapor compression system |
US10209013B2 (en) | 2010-09-03 | 2019-02-19 | Johnson Controls Technology Company | Vapor compression system |
US9429317B2 (en) | 2010-10-05 | 2016-08-30 | Edward Stock | Wastewater evaporation apparatus and method |
US20150013951A1 (en) * | 2013-07-11 | 2015-01-15 | Aaf-Mcquay Inc. | Heat exchanger |
US9658003B2 (en) * | 2013-07-11 | 2017-05-23 | Daikin Applied Americas Inc. | Heat exchanger |
US9677818B2 (en) * | 2013-07-11 | 2017-06-13 | Daikin Applied Americas Inc. | Heat exchanger |
US20150013950A1 (en) * | 2013-07-11 | 2015-01-15 | Aaf-Mcquay Inc. | Heat exchanger |
JP2016056966A (en) * | 2014-09-05 | 2016-04-21 | 三菱重工業株式会社 | Turbo refrigerator |
US20170254568A1 (en) * | 2014-09-05 | 2017-09-07 | Mitsubishi Heavy Industries, Ltd. | Centrifugal chiller |
US10254014B2 (en) * | 2014-09-05 | 2019-04-09 | Mitsubishi Heavy Industries Thermal Systems, Ltd. | Centrifugal chiller |
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 |
Also Published As
Publication number | Publication date |
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AT250410B (en) | 1966-11-10 |
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