WO2007053324A2 - Shell and tube evaporator - Google Patents

Shell and tube evaporator Download PDF

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Publication number
WO2007053324A2
WO2007053324A2 PCT/US2006/040955 US2006040955W WO2007053324A2 WO 2007053324 A2 WO2007053324 A2 WO 2007053324A2 US 2006040955 W US2006040955 W US 2006040955W WO 2007053324 A2 WO2007053324 A2 WO 2007053324A2
Authority
WO
WIPO (PCT)
Prior art keywords
tube bundle
water
tubes
diameter
pass
Prior art date
Application number
PCT/US2006/040955
Other languages
French (fr)
Other versions
WO2007053324A3 (en
Inventor
Wei Chen
Earl Campaigne
Original Assignee
Aaf-Mcquay Inc.
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
Application filed by Aaf-Mcquay Inc. filed Critical Aaf-Mcquay Inc.
Publication of WO2007053324A2 publication Critical patent/WO2007053324A2/en
Publication of WO2007053324A3 publication Critical patent/WO2007053324A3/en

Links

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 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 Figure 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.
  • the prior art evaporator has a plurality of tubes contained within a shell. The tubes are all the same diameter.
  • the present invention meets the aforementioned needs of the industry.
  • pressure loss in the evaporator is advantageously reduced as compared to prior art evaporators.
  • 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.
  • Figure 1 is a perspective view of a partial cut away centrifugal chiller system
  • Figure 2 is a partially cut away depiction of a prior art evaporator
  • Figure 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 at 10 in Figure 3.
  • the evaporator 10 is constructed generally in accordance with the construction of the evaporator of the prior art depicted in Figure 2. Reference may be made to prior art Figure 2 for the general portion of the description of the evaporator 10.
  • the evaporator 10 is of the shell and tube type construction. Accordingly, the evaporator 10 has a cylindrical shell 12 and a tube bundle 14.
  • the cylindrical shell 12 is preferably an elongate cylinder formed of a metallic material.
  • the evaporator 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 the cylindrical shell 12 for mounting the evaporator 10 in such disposition.
  • An insulation jacket 18 may be disposed immediately interior to the cylindrical shell 12.
  • the insulation jacket 18 preferably has a fluid-tight interior liner 19.
  • the cylindrical shell 12 is sealingly capped at either end by shell head 28.
  • a water inlet 20 and a water outlet 22 are coupled to a one of the endplates 28.
  • the water inlet 20 is disposed lower than the water outlet 22.
  • a refrigerant inlet 24 and a refrigerant outlet 26 are coupled to the cylindrical shell 12.
  • the refrigerant outlet 26 is in fluid communication with the centrifugal compressor, depicted in Fig. 1. Liquid refrigerant enters the shell through inlet 24 and the bottom of the shell 40.
  • the tube bundle assembly 14 includes endplates 30 disposed at either end of the tube bundle assembly 14.
  • Each of the endplates 30 is 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 30 has a plurality of tube ends 32 sealingly disposed therein.
  • the first pass tube bundle portion 36 is disposed in the lower portion of the cavity 40 defined within the cylindrical shell 12.
  • the second pass tube bundle portion 38 is disposed above the first pass tube bundle portion 36. It is understood the certain evaporators employ a side to side flow of the refrigerant. There are preferably fewer of the second pass tubes 44 in the second pass tube bundle portion
  • first pass tubes 42 in the first pass tube bundle portion 36.
  • the diameter of each of the first 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 the second pass tubes 44 is always greater than the diameter of the first pass tubes 42.
  • the diameter of the second pass tubes 44 is 0.75 inches to 1.5 inches and most preferably is 1.0 inches diameter.
  • the diameter of the first pass tubes 42 is 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 42 is substantially equal to the total area of all the second pass tubes 44.
  • 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.
  • liquid refrigerant flows into the refrigerant inlet 24 and floods the cavity 40, thereby, submerging the tube bundle assembly 14.
  • Warm water is pumped into the water inlet 20 and into the first pass tubes 42 of the first pass tube bundle portion 36. As the warm water passes through the first pass tube 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.
  • the water temperature reduces and enters the second pass tubes 44 of the second pass tube 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 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 pass could 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 portion would 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.

Abstract

An evaporator for a refrigeration system wherein a water makes a plurality of passes therethrough, 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. A method of forming an evaporator is further included.

Description

SHELL AND TUBE EVAPORATOR
Technical Field
The present invention relates to refrigeration systems. More particularly, the present invention relates to evaporators for use in a refrigeration system.
Background of the Invention Centrifugal chillers, which are the workhorses of the comfort cooling industry, have very few moving parts (Prior Art Figure 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. Summary of the Invention
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.
Brief Description of the Drawings
Figure 1 is a perspective view of a partial cut away centrifugal chiller system; Figure 2 is a partially cut away depiction of a prior art evaporator; and Figure 3 is an end sectional view of an evaporator of the present invention depicting the tube bundle.
Detailed Description of the Drawings
The evaporator of the present invention is shown generally at 10 in Figure 3. The evaporator 10 is constructed generally in accordance with the construction of the evaporator of the prior art depicted in Figure 2. Reference may be made to prior art Figure 2 for the general portion of the description of the evaporator 10.
Generally, the evaporator 10 is of the shell and tube type construction. Accordingly, the evaporator 10 has a cylindrical shell 12 and a tube bundle 14.
The cylindrical shell 12 is preferably an elongate cylinder formed of a metallic material. The evaporator 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 the cylindrical shell 12 for mounting the evaporator 10 in such disposition.
An insulation jacket 18 may be disposed immediately interior to the cylindrical shell 12. The insulation jacket 18 preferably has a fluid-tight interior liner 19. The cylindrical shell 12 is sealingly capped at either end by shell head 28.
A water inlet 20 and a water outlet 22 are coupled to a one of the endplates 28. Preferably, the water inlet 20 is disposed lower than the water outlet 22.
A refrigerant inlet 24 and a refrigerant outlet 26 (also known as a suction nozzle) are coupled to the cylindrical shell 12. As noted, the refrigerant outlet 26 is in fluid communication with the centrifugal compressor, depicted in Fig. 1. Liquid refrigerant enters the shell through inlet 24 and the bottom of the shell 40.
Referring to Figure 3 for the particulars of the present invention, the tube bundle assembly 14 includes endplates 30 disposed at either end of the tube bundle assembly 14. Each of the endplates 30 is 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 30 has a plurality of tube ends 32 sealingly disposed therein.
As depicted in Figure 3, the first pass tube bundle portion 36 is disposed in the lower portion of the cavity 40 defined within the cylindrical shell 12. The second pass tube bundle portion 38 is disposed above the first pass tube bundle portion 36. It is understood the certain evaporators employ a side to side flow of the refrigerant. There are preferably fewer of the second pass tubes 44 in the second pass tube bundle portion
38 than there are first pass tubes 42 in the first pass tube bundle portion 36. The diameter of each of the first 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 the second pass tubes 44 is always greater than the diameter of the first pass tubes 42. Preferably, the diameter of the second pass tubes 44 is 0.75 inches to 1.5 inches and most preferably is 1.0 inches diameter. In a preferred configuration of the evaporator 10, the diameter of the first pass tubes 42 is 0.75 inches and the diameter of the second 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 the second pass tubes 44. In evaporators 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 the cavity 40, thereby, submerging the tube bundle assembly 14. Warm water is pumped into the water inlet 20 and into the first pass tubes 42 of the first pass tube bundle portion 36. As the warm water passes through the first pass tube 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 the second pass tubes 44 of the second pass tube bundle portion 38. As the water passes through both the first pass tube bundle portion 36 and the second pass tube 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 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. 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 pass tube bundle portion 38. As noted above, the third pass bundle portion would 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.
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

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 of claim 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 of claim 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 of claim 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 of claim 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 of claim 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 of claim 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 of claim 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 of claim 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 of claim 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 of claim 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 of claim 12, including forming 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.
14. The method of claim 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 of claim 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 of claim 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.
PCT/US2006/040955 2005-10-31 2006-10-18 Shell and tube evaporator WO2007053324A2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US11/263,536 2005-10-31
US11/263,536 US20070095512A1 (en) 2005-10-31 2005-10-31 Shell and tube evaporator

Publications (2)

Publication Number Publication Date
WO2007053324A2 true WO2007053324A2 (en) 2007-05-10
WO2007053324A3 WO2007053324A3 (en) 2007-12-13

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PCT/US2006/040955 WO2007053324A2 (en) 2005-10-31 2006-10-18 Shell and tube evaporator

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WO (1) WO2007053324A2 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022168704A1 (en) 2021-02-05 2022-08-11 住友化学株式会社 Phosphor production method and phosphor
WO2022168705A1 (en) 2021-02-05 2022-08-11 住友化学株式会社 Phosphor and method for producing phosphor

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070107886A1 (en) * 2005-11-14 2007-05-17 Wei Chen Evaporator for a refrigeration system
US9943014B2 (en) * 2013-03-15 2018-04-10 Coolit Systems, Inc. Manifolded heat exchangers and related systems
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
DE102011108094A1 (en) * 2011-07-19 2013-01-24 Maschinenwerk Misselhorn Gmbh heat exchangers
US10365667B2 (en) 2011-08-11 2019-07-30 Coolit Systems, Inc. Flow-path controllers and related systems
WO2014141162A1 (en) 2013-03-15 2014-09-18 Coolit Systems, Inc. Sensors, multiplexed communication techniques, and related systems
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
WO2021229365A1 (en) 2020-05-11 2021-11-18 Coolit Systems, Inc. Liquid pumping units, and related systems and methods

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4475588A (en) * 1981-09-28 1984-10-09 Mcquay Inc. Heat exchanger with tubes fixed at baffles
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

Family Cites Families (30)

* Cited by examiner, † Cited by third party
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
NL136756C (en) * 1967-01-25 Westinghouse Electric Corp
DE1751779A1 (en) * 1968-07-29 1971-05-06 Linde Ag Device for evaporating liquids at low temperatures
US3732922A (en) * 1970-03-06 1973-05-15 Stein Industrie Heat-exchanger module
JPS5237992B2 (en) * 1972-02-25 1977-09-26
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
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
DE19651678A1 (en) * 1996-12-12 1998-06-25 Siemens Ag Steam generator
US20030111209A1 (en) * 1999-01-20 2003-06-19 Hino Motors, Ltd. EGR cooler
US6223555B1 (en) * 1999-06-08 2001-05-01 Visteon Global Technologies, Inc. Accumulator for an air conditioning system
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
US6988540B2 (en) * 2003-02-25 2006-01-24 Honeywell International Inc. Solid buffer rods in high temperature heat exchanger
CN100397000C (en) * 2003-04-17 2008-06-25 阿拂迈克奎公司 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
US7073570B2 (en) * 2003-09-22 2006-07-11 Visteon Global Technologies, Inc. Automotive heat exchanger
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

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4475588A (en) * 1981-09-28 1984-10-09 Mcquay Inc. Heat exchanger with tubes fixed at baffles
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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022168704A1 (en) 2021-02-05 2022-08-11 住友化学株式会社 Phosphor production method and phosphor
WO2022168705A1 (en) 2021-02-05 2022-08-11 住友化学株式会社 Phosphor and method for producing phosphor

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US20070095512A1 (en) 2007-05-03

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