US20070095512A1 - Shell and tube evaporator - Google Patents
Shell and tube evaporatorDownload PDFInfo
- Publication number
- US20070095512A1 US20070095512A1US11/263,536US26353605AUS2007095512A1US 20070095512 A1US20070095512 A1US 20070095512A1US 26353605 AUS26353605 AUS 26353605AUS 2007095512 A1US2007095512 A1US 2007095512A1
- Authority
- US
- United States
- Prior art keywords
- tube bundle
- water
- tubes
- diameter
- pass
- 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.)
- Abandoned
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-NwaterSubstancesOXLYOFNOQVPJJNP-UHFFFAOYSA-N0.000claimsabstractdescription52
- 238000000034methodMethods0.000claimsabstractdescription10
- 238000005057refrigerationMethods0.000claimsabstractdescription8
- 239000003507refrigerantSubstances0.000description18
- 239000007788liquidSubstances0.000description8
- 238000004891communicationMethods0.000description3
- 239000012530fluidSubstances0.000description3
- 238000010276constructionMethods0.000description2
- 238000009413insulationMethods0.000description2
- 238000006424Flood reactionMethods0.000description1
- 230000004075alterationEffects0.000description1
- UQMRAFJOBWOFNS-UHFFFAOYSA-Nbutyl 2-(2,4-dichlorophenoxy)acetateChemical compoundCCCCOC(=O)COC1=CC=C(Cl)C=C1ClUQMRAFJOBWOFNS-UHFFFAOYSA-N0.000description1
- 238000001816coolingMethods0.000description1
- 238000012423maintenanceMethods0.000description1
- 239000007769metal materialSubstances0.000description1
- 238000012986modificationMethods0.000description1
- 230000004048modificationEffects0.000description1
- 238000009987spinningMethods0.000description1
- 230000007704transitionEffects0.000description1
- 230000008016vaporizationEffects0.000description1
- 238000010792warmingMethods0.000description1
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
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/163—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
- F28D7/1638—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one
- 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
- 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
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49396—Condenser, evaporator or vaporizer making
Definitions
- the present inventionrelates to refrigeration systems. More particularly, the present invention relates to evaporators for use in a refrigeration system.
- Centrifugal chillerswhich are the workhorses of the comfort cooling industry, have very few moving parts (Prior Art FIG. 1 ). Therefore, they usually offer high reliability and low maintenance requirements.
- a moving partis the compressor.
- a centrifugal compressor of the centrifugal chilleracts very much like a centrifugal fan, compressing the vapor flowing through it by spinning it from the center of an impeller wheel radially outward, allowing centrifugal forces to compress the vapor.
- Some machinesuse multiple impellers to compress the refrigerant in stages.
- the compressoris in fluid communication with a shell and tube evaporator, as depicted in prior art FIG. 2 .
- the evaporatoracts to change the state of a refrigerant from a liquid to a vapor by warming the refrigerant. Warm water passes into the evaporator tube bundle and warms the liquid refrigerant, causing the refrigerant to change state to a vapor.
- the refrigerant vaporexits the evaporator at a suction nozzle under the motive force of a suction applied thereto by the compressor. Heat extracted from the liquid refrigerant acts to cool the water in the tube bundle.
- the prior art evaporatorhas a plurality of tubes contained within a shell. The tubes are all the same diameter.
- the present inventionmeets the aforementioned needs of the industry.
- pressure loss in the evaporatoris advantageously reduced as compared to prior art evaporators.
- the tube cost of an evaporatoris reduced by about ten percent as compared to a comparable capability evaporator constructed in the manner of the prior art, as exemplarily depicted in FIGS. 1 and 2 .
- the present inventionis an evaporator for a refrigeration system wherein a flow of water makes a plurality of passes therethrough.
- the evaporatorincludes a tube bundle assembly having a known tube bundle portion associated with each of a plurality of passes of water therethrough, each of a plurality of tubes of a tube bundle portion associated with a first water pass having a lesser diameter than the diameter of tubes of tube bundle portions associated with successive passes of water.
- the present inventionis further a method of forming an evaporator.
- FIG. 1is a perspective view of a partial cut away centrifugal chiller system
- FIG. 2is a partially cut away depiction of a prior art evaporator
- FIG. 3is an end sectional view of an evaporator of the present invention depicting the tube bundle.
- the evaporator of the present inventionis shown generally at 10 in FIG. 3 .
- the evaporator 10is constructed generally in accordance with the construction of the evaporator of the prior art depicted in FIG. 2 . Reference may be made to prior art FIG. 2 for the general portion of the description of the evaporator 10 .
- the evaporator 10is of the shell and tube type construction. Accordingly, the evaporator 10 has a cylindrical shell 12 and a tube bundle 14 .
- the cylindrical shell 12is preferably an elongate cylinder formed of a metallic material.
- the evaporator 10is designed to be mounted in a horizontal disposition. Accordingly, a plurality of base supports (not shown) may be fixed to the underside of the cylindrical shell 12 for mounting the evaporator 10 in such disposition.
- An insulation jacket 18may be disposed immediately interior to the cylindrical shell 12 .
- the insulation jacket 18preferably has a fluid-tight interior liner 19 .
- the cylindrical shell 12is sealingly capped at either end by shell head 28 .
- a water inlet 20 and a water outlet 22are coupled to a one of the endplates 28 .
- the water inlet 20is disposed lower than the water outlet 22 .
- a refrigerant inlet 24 and a refrigerant outlet 26are coupled to the cylindrical shell 12 .
- the refrigerant outlet 26is in fluid communication with the centrifugal compressor, depicted in FIG. 1 .
- Liquid regrigerantenters the shell through inlet 24 and the bottom of the shell 40 .
- the tube bundle assembly 14includes endplates 30 disposed at either end of the tube bundle assembly 14 .
- Each of the endplates 30is spaced apart from the adjacent shell head 28 in order to define a fluid passage for communication of the water from the first pass to the second pass.
- Each of the endplates 30has a plurality of tube ends 32 sealingly disposed therein.
- the first pass tube bundle portion 36is disposed in the lower portion of the cavity 40 defined within the cylindrical shell 12 .
- the second pass tube bundle portion 38is disposed above the first pass tube bundle portion 36 . It is understood the certain evaporators employ a side to side flow of the refrigerant.
- the diameter of each of the first pass tubes 42is preferably 0.50 inches in diameter to 1.0 inches in diameter and is most preferably 0.75 inches diameter.
- the diameter of the second pass tubes 44is always greater than the diameter of the first pass tubes 42 .
- the diameter of the second pass tubes 44is 0.75 inches to 1.5 inches and most preferably is 1.0 inches diameter.
- the diameter of the first pass tubes 42is 0.75 inches and the diameter of the second pass tubes 44 is 1.0 inches.
- the total area (the total area being arrived at by taking the inside crosssing area of each tube in the tube bundle portion and multiplying it by the total number of tubes in the tube bundle portion) of all the first pass tubes 42is substantially equal to the total area of all the second pass tubes 44 .
- each successive tube portion for successive passeshas a greater tube diameter than the tubes of the previous pass and has a substantially equal total area as that of the tube bundle portion of the preceding pass and, in fact all other tube bundle portions.
- liquid refrigerantflows into the refrigerant inlet 24 and floods the cavity 40 , thereby, submerging the tube bundle assembly 14 .
- Warm wateris pumped into the water inlet 20 and into the first pass tubes 42 of the first pass tube bundle portion 36 .
- the refrigerantmust be in a vapor state in order to be compressed by the compressor.
- the water temperaturereduces and enters the second pass tubes 44 of the second pass tube bundle portion 38 .
- the refrigeranttransitions from a liquid state to a vapor state. Heat energy is transfered from water to refrigerant by vaporizing the liquid refrigerant.
- the now cooled waterthen exits the second pass tubes 44 of the second pass tube bundle portion 38 and passes out of the evaporator 10 by the water outlet 22 .
- a third or a fourth passcould be made by the water by installing a third and fourth bundle portion above the second pass tube bundle portion 38 .
- the third pass bundle portionwould be greater in diameter than the diameter of the second pass tubes 44 and lesser in diameter than the tubes comprising the fourth bundle portion, but each pass bundle portion would have the same total area and therefore the same flow volume, as noted above.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
- The present invention relates to refrigeration systems. More particularly, the present invention relates to evaporators for use in a refrigeration system.
- Centrifugal chillers, which are the workhorses of the comfort cooling industry, have very few moving parts (Prior Art
FIG. 1 ). Therefore, they usually offer high reliability and low maintenance requirements. A moving part is the compressor. A centrifugal compressor of the centrifugal chiller acts very much like a centrifugal fan, compressing the vapor flowing through it by spinning it from the center of an impeller wheel radially outward, allowing centrifugal forces to compress the vapor. Some machines use multiple impellers to compress the refrigerant in stages. - The compressor is in fluid communication with a shell and tube evaporator, as depicted in prior art
FIG. 2 . The evaporator acts to change the state of a refrigerant from a liquid to a vapor by warming the refrigerant. Warm water passes into the evaporator tube bundle and warms the liquid refrigerant, causing the refrigerant to change state to a vapor. The refrigerant vapor exits the evaporator at a suction nozzle under the motive force of a suction applied thereto by the compressor. Heat extracted from the liquid refrigerant acts to cool the water in the tube bundle. It should be noted that the prior art evaporator has a plurality of tubes contained within a shell. The tubes are all the same diameter. - There is a need in the industry to minimize the pressure drop on the water side of the chiller refrigeration system. Further, there is a need to reduce the cost of refrigeration systems without compromising performance.
- The present invention meets the aforementioned needs of the industry. By employing greater diameter tubes for each successive pass of the water through the evaporator, pressure loss in the evaporator is advantageously reduced as compared to prior art evaporators. Further, by employing smaller diameter tubes for the initial pass and increasing the size of the tubes for successive passes, the tube cost of an evaporator is reduced by about ten percent as compared to a comparable capability evaporator constructed in the manner of the prior art, as exemplarily depicted in
FIGS. 1 and 2 . - The present invention is an evaporator for a refrigeration system wherein a flow of water makes a plurality of passes therethrough. The evaporator includes a tube bundle assembly having a known tube bundle portion associated with each of a plurality of passes of water therethrough, each of a plurality of tubes of a tube bundle portion associated with a first water pass having a lesser diameter than the diameter of tubes of tube bundle portions associated with successive passes of water. The present invention is further a method of forming an evaporator.
FIG. 1 is a perspective view of a partial cut away centrifugal chiller system;FIG. 2 is a partially cut away depiction of a prior art evaporator; andFIG. 3 is an end sectional view of an evaporator of the present invention depicting the tube bundle.- The evaporator of the present invention is shown generally at10 in
FIG. 3 . Theevaporator 10 is constructed generally in accordance with the construction of the evaporator of the prior art depicted inFIG. 2 . Reference may be made to prior artFIG. 2 for the general portion of the description of theevaporator 10. - Generally, the
evaporator 10 is of the shell and tube type construction. Accordingly, theevaporator 10 has acylindrical shell 12 and atube bundle 14. - The
cylindrical shell 12 is preferably an elongate cylinder formed of a metallic material. Theevaporator 10 is designed to be mounted in a horizontal disposition. Accordingly, a plurality of base supports (not shown) may be fixed to the underside of thecylindrical shell 12 for mounting theevaporator 10 in such disposition. - An
insulation jacket 18 may be disposed immediately interior to thecylindrical shell 12. Theinsulation jacket 18 preferably has a fluid-tightinterior liner 19. Thecylindrical shell 12 is sealingly capped at either end byshell head 28. - A water inlet20 and a
water outlet 22 are coupled to a one of theendplates 28. Preferably, thewater inlet 20 is disposed lower than thewater outlet 22. - A
refrigerant inlet 24 and a refrigerant outlet26 (also known as a suction nozzle) are coupled to thecylindrical shell 12. As noted, therefrigerant outlet 26 is in fluid communication with the centrifugal compressor, depicted inFIG. 1 . Liquid regrigerant enters the shell throughinlet 24 and the bottom of theshell 40. - Referring to
FIG. 3 for the particulars of the present invention, thetube bundle assembly 14 includesendplates 30 disposed at either end of thetube bundle assembly 14. Each of theendplates 30 is spaced apart from theadjacent shell head 28 in order to define a fluid passage for communication of the water from the first pass to the second pass. Each of theendplates 30 has a plurality oftube ends 32 sealingly disposed therein. - As depicted in
FIG. 3 , the first passtube bundle portion 36 is disposed in the lower portion of thecavity 40 defined within thecylindrical shell 12. The second passtube bundle portion 38 is disposed above the first passtube bundle portion 36. It is understood the certain evaporators employ a side to side flow of the refrigerant. There are preferably fewer of thesecond pass tubes 44 in the second passtube bundle portion 38 than there arefirst pass tubes 42 in the first passtube bundle portion 36. The diameter of each of thefirst pass tubes 42 is preferably 0.50 inches in diameter to 1.0 inches in diameter and is most preferably 0.75 inches diameter. The diameter of thesecond pass tubes 44 is always greater than the diameter of thefirst pass tubes 42. Preferably, the diameter of thesecond pass tubes 44 is 0.75 inches to 1.5 inches and most preferably is 1.0 inches diameter. In a preferred configuration of theevaporator 10, the diameter of thefirst pass tubes 42 is 0.75 inches and the diameter of thesecond pass tubes 44 is 1.0 inches. - Preferably, the total area ( the total area being arrived at by taking the inside crosssing area of each tube in the tube bundle portion and multiplying it by the total number of tubes in the tube bundle portion) of all the
first pass tubes 42 is substantially equal to the total area of all thesecond pass tubes 44. Inevaporators 10 having more than two passes, each successive tube portion for successive passes has a greater tube diameter than the tubes of the previous pass and has a substantially equal total area as that of the tube bundle portion of the preceding pass and, in fact all other tube bundle portions. - In operation, liquid refrigerant flows into the
refrigerant inlet 24 and floods thecavity 40, thereby, submerging thetube bundle assembly 14. Warm water is pumped into thewater inlet 20 and into thefirst pass tubes 42 of the first passtube bundle portion 36. As the warm water passes through the first passtube bundle portion 36, it acts to vaporize the liquid refrigerant. The refrigerant must be in a vapor state in order to be compressed by the compressor. - After passing through the first pass
tube bundle portion 36, the water temperature reduces and enters thesecond pass tubes 44 of the second passtube bundle portion 38. As the water passes through both the first passtube bundle portion 36 and the second passtube bundle portion 38, the refrigerant transitions from a liquid state to a vapor state. Heat energy is transfered from water to refrigerant by vaporizing the liquid refrigerant. The now cooled water then exits thesecond pass tubes 44 of the second passtube bundle portion 38 and passes out of theevaporator 10 by thewater outlet 22. It should be understood that a third or a fourth pass could be made by the water by installing a third and fourth bundle portion above the second passtube bundle portion 38. As noted above, the third pass bundle portion would be greater in diameter than the diameter of thesecond pass tubes 44 and lesser in diameter than the tubes comprising the fourth bundle portion, but each pass bundle portion would have the same total area and therefore the same flow volume, as noted above. - The above disclosure is not intended as limiting. Those skilled in the art will readily observe that numerous modifications and alterations of the device may be made while retaining the teachings of the invention. Accordingly, the above disclosure should be construed as limited only by the restrictions of the appended claims.
Claims (16)
1. An evaporator for a refrigeration system wherein a flow of water makes a plurality of substantially sequential end to end passes therethrough, comprising:
a tube bundle assembly having a known tube bundle portion associated with each of a plurality of passes of water therethrough, each of a plurality of tubes of a tube bundle portion associated with a first water pass having a lesser diameter than the diameter of tubes of tube bundle portions associated with successive passes of water.
2. The evaporator ofclaim 1 wherein the diameter of tubes of tube bundle portions associated with each successive pass of water is greater than the diameter of tubes of tube bundle portion associated with a previous pass of water.
3. The evaporator ofclaim 1 wherein a flow rate of all of the tubes of the tube bundle portions associated with each of the passes of water is substantially equal.
4. The evaporator ofclaim 1 having the tube bundle portion associated with a first water pass and a tube bundle portion associated with a second water pass.
5. The evaporator ofclaim 4 , a plurality of tubes comprising the tube bundle portion associated with the first water pass having a diameter of substantially 0.50 to 1.0 inches.
6. The evaporator ofclaim 4 , a plurality of tubes comprising the tube bundle portion associated with the first water pass having a diameter of substantially 0.75 inches.
7. The evaporator ofclaim 4 , a plurality of tubes comprising the tube bundle portion associated with the second water pass having a diameter of substantially 0.75 to 1.5 inches.
8. The evaporator ofclaim 4 , a plurality of tubes comprising the tube bundle portion associated with the second water pass having a diameter of substantially 1.0 inches.
9. A method of forming an evaporator for a refrigeration system wherein a flow of water makes a plurality of substantially sequential end to end passes therethrough, comprising:
forming a tube bundle assembly, a known tube bundle portion being formed associated with each of the plurality of passes of water therethrough, and forming each of a plurality of tubes of a tube bundle portion associated with a first water pass of a lesser diameter than a diameter of tubes of tube bundle portions associated with successive passes of water.
10. The method ofclaim 9 including forming the diameter of tubes of tube bundle portions associated with each successive pass of water with a greater diameter than the diameter of tubes of a tube bundle portion associated with a previous pass of water.
11. The method ofclaim 9 including substantially equalizing a flow rate of all of the tubes of the tube bundle portions associated with each of the passes of water.
12. The method ofclaim 9 including forming the tube bundle portion associated with a first water pass and forming a tube bundle portion associated with a second water pass.
13. The method ofclaim 12 , including forming a plurality of tubes comprising the tube bundle portion associated with the first water pass having a diameter of substantially0.50 to1.0 inches.
14. The method ofclaim 12 , including forming a plurality of tubes comprising the tube bundle portion associated with the first water pass having a diameter of substantially 0.75 inches.
15. The method ofclaim 12 , including forming a plurality of tubes comprising the tube bundle portion associated with the second water pass having a diameter of substantially 0.75 to 1.5 inches.
16. The method ofclaim 12 , including forming a plurality of tubes comprising the tube bundle portion associated with the second water pass having a diameter of substantially 1.0 inches.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US11/263,536US20070095512A1 (en) | 2005-10-31 | 2005-10-31 | Shell and tube evaporator |
| PCT/US2006/040955WO2007053324A2 (en) | 2005-10-31 | 2006-10-18 | Shell and tube evaporator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US11/263,536US20070095512A1 (en) | 2005-10-31 | 2005-10-31 | Shell and tube evaporator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| US20070095512A1true US20070095512A1 (en) | 2007-05-03 |
Family
ID=37994749
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| US11/263,536AbandonedUS20070095512A1 (en) | 2005-10-31 | 2005-10-31 | Shell and tube evaporator |
Country Status (2)
| Country | Link |
|---|---|
| US (1) | US20070095512A1 (en) |
| WO (1) | WO2007053324A2 (en) |
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20070107886A1 (en)* | 2005-11-14 | 2007-05-17 | Wei Chen | Evaporator for a refrigeration system |
| US20120006524A1 (en)* | 2010-07-09 | 2012-01-12 | Honeywell International Inc. | Optimized tube bundle configuration for controlling a heat exchanger wall temperature |
| US20120037347A1 (en)* | 2010-08-11 | 2012-02-16 | Honeywell International Inc. | Method of controlling tube temperatures to prevent freezing of fluids in cross counterflow shell and tube heat exchanger |
| WO2013010671A3 (en)* | 2011-07-19 | 2013-04-25 | Maschinenwerk Misselhorn Gmbh | Heat exchanger |
| US20140262180A1 (en)* | 2013-03-15 | 2014-09-18 | Coolit Systems Inc. | Manifolded heat exchangers and related systems |
| DE102015120706A1 (en)* | 2015-11-30 | 2017-06-01 | Aerodyn Engineering Gmbh | Air-cooled oil tank |
| US10365667B2 (en) | 2011-08-11 | 2019-07-30 | Coolit Systems, Inc. | Flow-path controllers and related systems |
| US10364809B2 (en) | 2013-03-15 | 2019-07-30 | Coolit Systems, Inc. | Sensors, multiplexed communication techniques, and related systems |
| US11395443B2 (en) | 2020-05-11 | 2022-07-19 | Coolit Systems, Inc. | Liquid pumping units, and related systems and methods |
| US11452243B2 (en) | 2017-10-12 | 2022-09-20 | Coolit Systems, Inc. | Cooling system, controllers and methods |
| US11473860B2 (en) | 2019-04-25 | 2022-10-18 | Coolit Systems, Inc. | Cooling module with leak detector and related systems |
| US11662037B2 (en) | 2019-01-18 | 2023-05-30 | Coolit Systems, Inc. | Fluid flow control valve for fluid flow systems, and methods |
| US12188733B2 (en) | 2021-05-20 | 2025-01-07 | Coolit Systems, Inc. | Modular fluid heat exchange systems |
| US12200914B2 (en) | 2022-01-24 | 2025-01-14 | Coolit Systems, Inc. | Smart components, systems and methods for transferring heat |
| US12366870B2 (en) | 2013-03-15 | 2025-07-22 | Coolit Systems, Inc. | Flow-path controllers and related systems |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2022120802A (en) | 2021-02-05 | 2022-08-18 | 住友化学株式会社 | Phosphor and method for producing phosphor |
| JP2022120801A (en) | 2021-02-05 | 2022-08-18 | 住友化学株式会社 | Phosphor manufacturing method and phosphor |
Citations (33)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1917595A (en)* | 1929-07-16 | 1933-07-11 | Elliott Co | Heater |
| US2343542A (en)* | 1944-03-07 | Heat extractor | ||
| US2919903A (en)* | 1957-03-18 | 1960-01-05 | Phillips Petroleum Co | Shell-tube heat exchange apparatus for condensate subcooling |
| US3427227A (en)* | 1967-01-25 | 1969-02-11 | Westinghouse Electric Corp | Flash evaporator with duct and baffle means |
| US3595299A (en)* | 1968-07-29 | 1971-07-27 | Linde Ag | Apparatus for the evaporation of low-temperature liquefied gases |
| US3732922A (en)* | 1970-03-06 | 1973-05-15 | Stein Industrie | Heat-exchanger module |
| US3875988A (en)* | 1972-02-25 | 1975-04-08 | Ebara Mfg | Multiple effect evaporator apparatus |
| US4006602A (en)* | 1974-08-05 | 1977-02-08 | Fanberg Ralph Z | Refrigeration apparatus and method |
| US4049410A (en)* | 1974-07-29 | 1977-09-20 | Allan Sinclair Miller | Gas compressors |
| US4397740A (en)* | 1982-09-30 | 1983-08-09 | Phillips Petroleum Company | Method and apparatus for cooling thermally cracked hydrocarbon gases |
| US4475588A (en)* | 1981-09-28 | 1984-10-09 | Mcquay Inc. | Heat exchanger with tubes fixed at baffles |
| US4497363A (en)* | 1982-04-28 | 1985-02-05 | Heronemus William E | Plate-pin panel heat exchanger and panel components therefor |
| USH52H (en)* | 1983-12-08 | 1986-04-01 | The United States Of America As Represented By The United States Department Of Energy | Heat exchanger |
| US5099656A (en)* | 1991-01-25 | 1992-03-31 | Uniflow Manufacturing Company | Evaporator design |
| US5203405A (en)* | 1992-02-03 | 1993-04-20 | Phillips Petroleum Company | Two pass shell and tube heat exchanger with return annular distributor |
| US5392815A (en)* | 1993-08-05 | 1995-02-28 | Pacific Gas And Electric Company | Gradational tube bundle flow conditioner for providing a natural flow profile to facilitate accurate orifice metering in fluid filled conduits |
| US5479784A (en)* | 1994-05-09 | 1996-01-02 | Carrier Corporation | Refrigerant distribution device |
| US5509466A (en)* | 1994-11-10 | 1996-04-23 | York International Corporation | Condenser with drainage member for reducing the volume of liquid in the reservoir |
| US5531266A (en)* | 1993-12-28 | 1996-07-02 | Uop | Method of indirect heat exchange for two phase flow distribution |
| US5538598A (en)* | 1992-03-23 | 1996-07-23 | Fsr Patented Technologies, Ltd. | Liquid purifying/distillation device |
| US6189491B1 (en)* | 1996-12-12 | 2001-02-20 | Siemens Aktiengesellschaft | Steam generator |
| US6223555B1 (en)* | 1999-06-08 | 2001-05-01 | Visteon Global Technologies, Inc. | Accumulator for an air conditioning system |
| US6273180B1 (en)* | 1998-12-23 | 2001-08-14 | L'air Liquide, Societe Anonyme Pour L'etude Et L'eploitation Des Procedes Georges Claude | Heat exchanger for preheating an oxidizing gas |
| US6293112B1 (en)* | 1999-12-17 | 2001-09-25 | American Standard International Inc. | Falling film evaporator for a vapor compression refrigeration chiller |
| US6516627B2 (en)* | 2001-05-04 | 2003-02-11 | American Standard International Inc. | Flowing pool shell and tube evaporator |
| US6536231B2 (en)* | 2001-05-31 | 2003-03-25 | Carrier Corporation | Tube and shell heat exchanger for multiple circuit refrigerant system |
| US6684938B2 (en)* | 1999-01-20 | 2004-02-03 | Hino Motors, Ltd. | EGR cooler |
| US20040194932A1 (en)* | 2003-02-25 | 2004-10-07 | Honeywell International Inc. | Solid buffer rods in high temperature heat exchanger |
| US6868695B1 (en)* | 2004-04-13 | 2005-03-22 | American Standard International Inc. | Flow distributor and baffle system for a falling film evaporator |
| US20050061489A1 (en)* | 2003-09-22 | 2005-03-24 | Visteon Global Technologies, Inc. | Integrated multi-function return tube for combo heat exchangers |
| US7069734B2 (en)* | 2003-04-17 | 2006-07-04 | Aaf-Mcquay Inc. | Methods for detecting surge in centrifugal compressors |
| US7073572B2 (en)* | 2003-06-18 | 2006-07-11 | Zahid Hussain Ayub | Flooded evaporator with various kinds of tubes |
| US20070235173A1 (en)* | 2006-04-10 | 2007-10-11 | Aaf-Mcquary Inc. | Shell and tube evaporator |
- 2005
- 2005-10-31USUS11/263,536patent/US20070095512A1/ennot_activeAbandoned
- 2006
- 2006-10-18WOPCT/US2006/040955patent/WO2007053324A2/enactiveApplication Filing
Patent Citations (33)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2343542A (en)* | 1944-03-07 | Heat extractor | ||
| US1917595A (en)* | 1929-07-16 | 1933-07-11 | Elliott Co | Heater |
| US2919903A (en)* | 1957-03-18 | 1960-01-05 | Phillips Petroleum Co | Shell-tube heat exchange apparatus for condensate subcooling |
| US3427227A (en)* | 1967-01-25 | 1969-02-11 | Westinghouse Electric Corp | Flash evaporator with duct and baffle means |
| US3595299A (en)* | 1968-07-29 | 1971-07-27 | Linde Ag | Apparatus for the evaporation of low-temperature liquefied gases |
| US3732922A (en)* | 1970-03-06 | 1973-05-15 | Stein Industrie | Heat-exchanger module |
| US3875988A (en)* | 1972-02-25 | 1975-04-08 | Ebara Mfg | Multiple effect evaporator apparatus |
| US4049410A (en)* | 1974-07-29 | 1977-09-20 | Allan Sinclair Miller | Gas compressors |
| US4006602A (en)* | 1974-08-05 | 1977-02-08 | Fanberg Ralph Z | Refrigeration apparatus and method |
| US4475588A (en)* | 1981-09-28 | 1984-10-09 | Mcquay Inc. | Heat exchanger with tubes fixed at baffles |
| US4497363A (en)* | 1982-04-28 | 1985-02-05 | Heronemus William E | Plate-pin panel heat exchanger and panel components therefor |
| US4397740A (en)* | 1982-09-30 | 1983-08-09 | Phillips Petroleum Company | Method and apparatus for cooling thermally cracked hydrocarbon gases |
| USH52H (en)* | 1983-12-08 | 1986-04-01 | The United States Of America As Represented By The United States Department Of Energy | Heat exchanger |
| US5099656A (en)* | 1991-01-25 | 1992-03-31 | Uniflow Manufacturing Company | Evaporator design |
| US5203405A (en)* | 1992-02-03 | 1993-04-20 | Phillips Petroleum Company | Two pass shell and tube heat exchanger with return annular distributor |
| US5538598A (en)* | 1992-03-23 | 1996-07-23 | Fsr Patented Technologies, Ltd. | Liquid purifying/distillation device |
| US5392815A (en)* | 1993-08-05 | 1995-02-28 | Pacific Gas And Electric Company | Gradational tube bundle flow conditioner for providing a natural flow profile to facilitate accurate orifice metering in fluid filled conduits |
| US5531266A (en)* | 1993-12-28 | 1996-07-02 | Uop | Method of indirect heat exchange for two phase flow distribution |
| US5479784A (en)* | 1994-05-09 | 1996-01-02 | Carrier Corporation | Refrigerant distribution device |
| US5509466A (en)* | 1994-11-10 | 1996-04-23 | York International Corporation | Condenser with drainage member for reducing the volume of liquid in the reservoir |
| US6189491B1 (en)* | 1996-12-12 | 2001-02-20 | Siemens Aktiengesellschaft | Steam generator |
| US6273180B1 (en)* | 1998-12-23 | 2001-08-14 | L'air Liquide, Societe Anonyme Pour L'etude Et L'eploitation Des Procedes Georges Claude | Heat exchanger for preheating an oxidizing gas |
| US6684938B2 (en)* | 1999-01-20 | 2004-02-03 | Hino Motors, Ltd. | EGR cooler |
| US6223555B1 (en)* | 1999-06-08 | 2001-05-01 | Visteon Global Technologies, Inc. | Accumulator for an air conditioning system |
| US6293112B1 (en)* | 1999-12-17 | 2001-09-25 | American Standard International Inc. | Falling film evaporator for a vapor compression refrigeration chiller |
| US6516627B2 (en)* | 2001-05-04 | 2003-02-11 | American Standard International Inc. | Flowing pool shell and tube evaporator |
| US6536231B2 (en)* | 2001-05-31 | 2003-03-25 | Carrier Corporation | Tube and shell heat exchanger for multiple circuit refrigerant system |
| US20040194932A1 (en)* | 2003-02-25 | 2004-10-07 | Honeywell International Inc. | Solid buffer rods in high temperature heat exchanger |
| US7069734B2 (en)* | 2003-04-17 | 2006-07-04 | Aaf-Mcquay Inc. | Methods for detecting surge in centrifugal compressors |
| US7073572B2 (en)* | 2003-06-18 | 2006-07-11 | Zahid Hussain Ayub | Flooded evaporator with various kinds of tubes |
| US20050061489A1 (en)* | 2003-09-22 | 2005-03-24 | Visteon Global Technologies, Inc. | Integrated multi-function return tube for combo heat exchangers |
| US6868695B1 (en)* | 2004-04-13 | 2005-03-22 | American Standard International Inc. | Flow distributor and baffle system for a falling film evaporator |
| US20070235173A1 (en)* | 2006-04-10 | 2007-10-11 | Aaf-Mcquary Inc. | Shell and tube evaporator |
Cited By (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20070107886A1 (en)* | 2005-11-14 | 2007-05-17 | Wei Chen | Evaporator for a refrigeration system |
| US20120006524A1 (en)* | 2010-07-09 | 2012-01-12 | Honeywell International Inc. | Optimized tube bundle configuration for controlling a heat exchanger wall temperature |
| US20120037347A1 (en)* | 2010-08-11 | 2012-02-16 | Honeywell International Inc. | Method of controlling tube temperatures to prevent freezing of fluids in cross counterflow shell and tube heat exchanger |
| WO2013010671A3 (en)* | 2011-07-19 | 2013-04-25 | Maschinenwerk Misselhorn Gmbh | Heat exchanger |
| US10365667B2 (en) | 2011-08-11 | 2019-07-30 | Coolit Systems, Inc. | Flow-path controllers and related systems |
| US11714432B2 (en) | 2011-08-11 | 2023-08-01 | Coolit Systems, Inc. | Flow-path controllers and related systems |
| US11661936B2 (en) | 2013-03-15 | 2023-05-30 | Coolit Systems, Inc. | Sensors, multiplexed communication techniques, and related systems |
| US20140262180A1 (en)* | 2013-03-15 | 2014-09-18 | Coolit Systems Inc. | Manifolded heat exchangers and related systems |
| US12366870B2 (en) | 2013-03-15 | 2025-07-22 | Coolit Systems, Inc. | Flow-path controllers and related systems |
| US9943014B2 (en)* | 2013-03-15 | 2018-04-10 | Coolit Systems, Inc. | Manifolded heat exchangers and related systems |
| US10364809B2 (en) | 2013-03-15 | 2019-07-30 | Coolit Systems, Inc. | Sensors, multiplexed communication techniques, and related systems |
| DE102015120706A1 (en)* | 2015-11-30 | 2017-06-01 | Aerodyn Engineering Gmbh | Air-cooled oil tank |
| DE102015120706B4 (en)* | 2015-11-30 | 2018-03-22 | Aerodyn Engineering Gmbh | Air-cooled oil tank |
| US11452243B2 (en) | 2017-10-12 | 2022-09-20 | Coolit Systems, Inc. | Cooling system, controllers and methods |
| US11662037B2 (en) | 2019-01-18 | 2023-05-30 | Coolit Systems, Inc. | Fluid flow control valve for fluid flow systems, and methods |
| US11473860B2 (en) | 2019-04-25 | 2022-10-18 | Coolit Systems, Inc. | Cooling module with leak detector and related systems |
| US11725890B2 (en) | 2019-04-25 | 2023-08-15 | Coolit Systems, Inc. | Cooling module with leak detector and related systems |
| US12031779B2 (en) | 2019-04-25 | 2024-07-09 | Coolit Systems, Inc. | Cooling module with leak detector and related systems |
| US11395443B2 (en) | 2020-05-11 | 2022-07-19 | Coolit Systems, Inc. | Liquid pumping units, and related systems and methods |
| US12193193B2 (en) | 2020-05-11 | 2025-01-07 | Coolit Systems, Inc. | Liquid pumping units, and related systems and methods |
| US12188733B2 (en) | 2021-05-20 | 2025-01-07 | Coolit Systems, Inc. | Modular fluid heat exchange systems |
| US12200914B2 (en) | 2022-01-24 | 2025-01-14 | Coolit Systems, Inc. | Smart components, systems and methods for transferring heat |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2007053324A2 (en) | 2007-05-10 |
| WO2007053324A3 (en) | 2007-12-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| WO2007053324A2 (en) | Shell and tube evaporator | |
| EP1872068B1 (en) | Multi-part heat exchanger | |
| CN107850359B (en) | Evaporator and turbo refrigeration device provided with same | |
| WO2007058737A2 (en) | Evaporator for a refrigeration system | |
| US10222104B2 (en) | Distributor and turbo refrigerating machine and evaporator having the same | |
| EP1921399A2 (en) | Two stage transcritical refrigeration system | |
| CN100582630C (en) | Heat exchanger for a refrigerating device | |
| KR20070073827A (en) | Efficient Heat Exchanger for Cooling Process | |
| US20120048514A1 (en) | Cooling systems and methods | |
| JP6458680B2 (en) | Heat exchanger | |
| JP5316465B2 (en) | Evaporator unit | |
| EP1373809B1 (en) | Apparatus and method for discharging vapour and liquid | |
| US6910349B2 (en) | Suction connection for dual centrifugal compressor refrigeration systems | |
| JP5381875B2 (en) | Evaporator unit | |
| US9562705B2 (en) | Energy recovery apparatus for use in a refrigeration system | |
| JP2008138895A (en) | Evaporator unit | |
| US5499509A (en) | Noise control in a centrifugal chiller | |
| US9145880B2 (en) | Compressor manifold assembly | |
| EP3504490B1 (en) | Falling film evaporator | |
| US9243650B2 (en) | Fin array for use in a centrifugal fan | |
| US10012421B2 (en) | Evaporator for an appliance | |
| CN105953481A (en) | Condenser and refrigerator comprising same | |
| KR200303998Y1 (en) | Oil-separator of cooling unit | |
| JP6878550B2 (en) | Refrigerator | |
| KR100479733B1 (en) | Refrigerant distributor for split-type air conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| AS | Assignment | Owner name:AAF-MCQUAY INC., MINNESOTA Free format text:ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:CHEN, WEI;CAMPAIGNE, EARL;REEL/FRAME:017138/0138 Effective date:20060106 | |
| STCB | Information on status: application discontinuation | Free format text:ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |