US20140202203A1 - Refrigerant evaporator - Google Patents
Refrigerant evaporator Download PDFInfo
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- US20140202203A1 US20140202203A1 US14/226,046 US201414226046A US2014202203A1 US 20140202203 A1 US20140202203 A1 US 20140202203A1 US 201414226046 A US201414226046 A US 201414226046A US 2014202203 A1 US2014202203 A1 US 2014202203A1
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- Prior art keywords
- tubes
- refrigerant
- evaporator
- baffle
- shell
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Classifications
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- 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
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- 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
- F25B39/028—Evaporators having distributing means
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D1/00—Evaporating
- B01D1/04—Evaporators with horizontal tubes
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- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0017—Flooded core heat exchangers
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
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- 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
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- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/0071—Evaporators
Abstract
A refrigerant evaporator includes a shell having a refrigerant inlet and a refrigerant outlet, and a plurality of tubes disposed within the shell and carrying a process fluid. One embodiment includes at least a first plurality of the tubes are immersed in liquid refrigerant within the shell, and at least a second plurality of the tubes are partially immersed in liquid refrigerant and partially surrounded by gaseous refrigerant. The refrigerant evaporator also includes a baffle positioned adjacent the first plurality of tubes and immersed in the liquid refrigerant to displace the liquid refrigerant.
Description
- The present invention relates to heating, ventilation, and air-conditioning (“HVAC”) systems, and more particularly to evaporators and evaporation methods applicable for use in HVAC and similarly associated systems.
- Flooded and falling-film evaporators are typically used in HVAC chillers to cool a process fluid (e.g., water) which, in turn, is typically used in connection with a heat exchanger coil or air-handling unit to cool air moving through the coil or air-handling unit. Due to the interstitial spacing between the tubes within the evaporator through which the process fluid flows, a relatively large quantity of liquid refrigerant is often required to immerse a sufficient number of the tubes to achieve a high working efficiency of the evaporator. Operationally, excess liquid refrigerant between the tubes may contribute relatively little to the overall efficiency of the HVAC chillers, and can be an additional burden on the cost of the operating and maintaining she chillers.
- The present application provides, in one aspect, a refrigerant evaporator including a shell having a refrigerant inlet and a refrigerant outlet, and a plurality of tubes disposed within the shell and carrying a process fluid. The refrigerant evaporator also includes a baffle positioned adjacent at least some of the plurality of tubes and immersed in the liquid refrigerant to displace the liquid refrigerant.
- Other features and aspects of the application will become apparent by consideration of the following detailed description and accompanying drawings.
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FIG. 1 is a cross-sectional view of a flooded refrigerant evaporator in accordance with a first embodiment of the application, taken along line 1-1 inFIG. 2 . -
FIG. 2 is a cross-sectional view of the flooded refrigerant evaporator ofFIG. 1 , taken along line 2-2 inFIG. 1 . -
FIG. 3 is an enlarged view of a portion of the flooded refrigerant evaporator ofFIG. 1 . -
FIG. 4 is a cross-sectional view of a flooded refrigerant evaporator in accordance with a second embodiment of the application, taken along line 4-4 inFIG. 5 . -
FIG. 5 is a cross-sectional view of the flooded refrigerant evaporator ofFIG. 4 , taken along line 5-5 inFIG. 4 . -
FIG. 6 is a cross-sectional view of a falling-film refrigerant evaporator in accordance with a third embodiment of the application, taken along line 6-6 inFIG. 7 . -
FIG. 7 is a cross-sectional view of the filling-film refrigerant evaporator ofFIG. 6 , taken along line 7-7 inFIG. 6 . -
FIG. 8 is an enlarged view of a portion of the falling film refrigerant evaporator ofFIG. 6 . -
FIG. 9 is a cross-sectional view of a falling-film refrigerant evaporator in accordance with a fourth embodiment of the application, taken along line 9-9 in FIG 10. -
FIG. 10 is a cross-sectional view of the falling-film refrigerant evaporator ofFIG. 9 , taken along line 10-10 inFIG. 9 . - Before any embodiments of the invention are explained in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the following drawings. The invention is capable of other embodiments and of being practiced or of being carried out in various ways. Also, it is to be understood that the phraseology and terminology used herein is for the purpose of description and should not be regarded as limiting.
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FIGS. 1 and 2 illustrate a floodedrefrigerant evaporator 10 used in connection with an HVAC chiller to cool a process fluid (e.g., water). Such a process fluid may be used with a heat exchanger coil or air-handling unit to cool air moving through the coil or air-handling unit. Theevaporator 10 includes a shell 14 having aninlet 18 through which liquid refrigerant enters the shell 14, an outlet 22 through which gaseous refrigerant exits the shell 14, and a plurality oftubes 26 disposed within the shell 14 for carrying the process fluid. In the illustrated construction of theevaporator 10, the shell 14 includes a cylindrical shape (FIG. 1 ) though such shape is not a limitation of the present application or embodiment given that other shapes are also contemplated. Therefrigerant inlet 18 and the refrigerant outlet 22 are located below and above thetubes 26, respectively, to flood the shell 14 with liquid refrigerant by introducing the liquid refrigerant below thetubes 26. - The
tubes 26 are oriented substantially horizontally relative to a support surface of therefrigerant evaporator 10 in a series of rows (FIGS. 1 and 2 ) though such orientation is not a limitation of the present application or embodiment. Thetubes 26 depicted in the illustrated embodiment are spaced relative to each other by a triangular pitch (FIG. 1 ). Alternatively, the tubes could have a rectangular pitch as shown inFIGS. 6 and 9 . The liquid refrigerant has atop surface 30, and a first plurality of thetubes 26 are immersed in the liquid refrigerant and located entirely below thetop surface 30 of the liquid refrigerant (FIG. 1 ). A second plurality of thetubes 26 are located at least partially above thefop surface 30 of the liquid refrigerant, and are at least partially immersed in liquid refrigerant and at least partially surrounded by gaseous refrigerant. A third plurality of thetubes 26 are surrounded by gaseous refrigerant and located entirely above thetop surface 30 of the liquid refrigerant. - With reference to
FIGS. 1 and 2 , therefrigerant evaporator 10 also includes abaffle 34 immersed in the liquid refrigerant and positioned adjacent to thetubes 26 that are immersed in the liquid refrigerant. Thebaffle 34 includes a plurality ofapertures 38 through which thetubes 26 are received (FIG. 1 ). Thetubes 26 include an outer diameter less than that of theapertures 38 in which thetubes 26 are received, thereby forming anannular gap 42 between each of thetubes 26 and thebaffle 34 through which liquid refrigerant may flow (FIGS. 1 and 3 ). In an alternative construction, thebaffle 34 may be positioned betweenadjacent tubes 26 that are immersed in the liquid refrigerant and include an outer peripheral surface containing a plurality of grooves in which the tubes are received. Alternatively, thebaffle 34 may have a smooth outer peripheral surface without any grooves and be located toward the bottom of the shell 14 below thetubes 26. In the illustrated construction of theevaporator 10 at least a portion of thebaffle 34 is located between thelower-most tubes 26 and the shell 14 (FIGS. 1 and 2 ). Also, in the illustrated construction of theevaporator 10, the shell 14 includes a first length L0 and thebaffle 34 includes a second length L1 such that L1 is about 50% of the length L0 (FIG. 2 ). Alternatively, thebaffle 34 may include a length L1 that is at least about 75% or about 95% of the length L0. - In operation of the flooded
refrigerant evaporator 10, liquid refrigerant flows into the shell 14 via therefrigerant inlet 18. Near therefrigerant inlet 18, the shell 14 is occupied by nearly pure liquid refrigerant because the liquid refrigerant in this region has yet to exchange heat with thetubes 26 to cause it to evaporate. Accordingly, it is considered that liquid refrigerant in this region of the shell 14 has a low void fraction. As thebaffle 34 occupies some of the internal volume of the shell 14, thebaffle 34 displaces incoming liquid refrigerant relative to the condition if thebaffle 34 were not provided. In other words, by displacing the liquid refrigerant, the presence of thebaffle 34 can act to effectively raise thetop surface 30 of liquid refrigerant in the shell 14. Liquid refrigerant flows through each of theannular gaps 42 and contacts the outer periphery of thetubes 26. Contact between thetubes 26 and the liquid refrigerant allows heat to be transferred from the process fluid to the liquid refrigerant. This causes the liquid refrigerant to evaporate into gaseous refrigerant (e.g., phase change), which increases the void fraction of the surrounding liquid refrigerant. It should be understood that in one aspect the refrigerant passing through each of theannular gaps 42 around the periphery of thetubes 26 is locally isolated for a period of time from the rest of the refrigerant in the shell and absorbs the heat from the process fluid and evaporates into gaseous refrigerant. The gaseous refrigerant bubbles through theannular gaps 42 before exiting thebaffle 34 and then exits the shelf 14 via the refrigerant outlet 22. The void fraction within the shell 14 progressively increases from where liquid refrigerant enters the shell 14 via therefrigerant inlet 18 towards thetop surface 30 of liquid refrigerant. By displacing liquid refrigerant in the shell 14 toward regions within the shell 14 which would otherwise have a high void traction of liquid refrigerant in absence of thebaffle 34, the inclusion of thebaffle 34 reduces the amount of liquid refrigerant that is used compared to a typical flooded refrigerant evaporator without reducing the working efficiency of the evaporator. - The present application contemplates that the baffles may have a length less than the length of the Shell. A plurality of baffles may be used to obtain the desired balance of refrigerant and thermal performance. Further, in one form of the present application the baffle(s) may extend the substantial length of the shell.
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FIGS. 4 and 5 illustrate a second construction of a flooded refrigerant evaporator 46 used in connection with an HVAC chiller to cool a process fluid. Like components are identified with like reference numerals with the letter “a,” and will not be described again in detail. Rather than incorporating only asingle baffle 34 like that shown inFIGS. 1 and 2 and described above, the evaporator 46 includes a plurality of baffles located in different positions throughout the shell 14 a. Particularly, the flooded refrigerant evaporator 46 includes afirst baffle 50 positioned adjacent thelower-most tubes 26 a, a second andthird baffle 54, 58 located above thefirst baffle 50 and axially spaced from each other, and a forth baffle 62 located above and axially spaced between the second andthird baffles 54, 58. Alternatively, the evaporator 46 may include more or fewer baffles that may be distributed throughout the shell 14 a in various combinations and configuration. In the illustrated construction of the evaporator 46, the first, second, andthird baffles tubes 26 a that are immersed in the liquid refrigerant (FIG. 4 ). The fourth baffle 62 is not entirely immersed in liquid refrigerant and is positioned adjacent to thetubes 26 a that are at least partially immersed in liquid refrigerant and at least partially surrounded by gaseous refrigerant. - The
baffles apertures 38 a through which thetubes 26 a are received. Thetubes 26 a include an outer diameter less than that of theapertures 38 a in which thetubes 26 a are received, thereby forming an annular gap 42 a between each of thetubes 26 a and thebaffles baffles tubes 26 a is received. As such, the grooves 66 in adjacent baffles (e.g., the first andsecond baffles 50, 54, or the first andthird baffles 50, 58) collectively define an annular gap 68 through which liquid refrigerant may flow. In the illustrated construction of the evaporator 46, at least a portion of thelower-most baffle 50 is located between thelower-most tubes 26 a and the shell 14 a (FIGS. 4 and 5 ). Also, in the illustrated construction of the evaporator 46, the shell 14 a includes a first length L0 and thefirst baffle 50 includes a second length L1 such that L1 is about 95% of the length L0 (FIG. 5 ). The second, third, andfourth baffles 54, 58, 62 include a third, fourth, and fifth length L2, L3, L4, respectively, such that the lengths L2, L3, and L4 are each about 25% of the length L0 (FIG. 5 ). Alternatively, each of thebaffles 54, 58, 62 may include a length that is at least about 25% to at least about 95% of the length L0. - The flooded refrigerant evaporator 46 operates in an identical fashion as the
evaporator 10 shown inFIGS. 1 and 2 and described above. However, each of thebaffles respective baffles -
FIGS. 6 and 7 illustrate a falling-film refrigerant evaporator 70 used in connection with an HVAC chiller to cool a process fluid (e.g., water). Such a process fluid may be used with a heat exchanger coil or air-handling unit to cool air moving through the coil or air-handling unit. The evaporator 70 includes ashell 74 having aninlet 78 through which liquid refrigerant enters theshell 74, anoutlet 82 through which gaseous refrigerant exits theshell 74, and a plurality oftubes 86 disposed within theshell 74 for carrying a process fluid. In the illustrated construction of the evaporator 70, theshell 74 includes a cylindrical shape (FIG. 6 ). Alternatively, the shell may include a non-cylindrical shape. Therefrigerant inlet 78 andoutlet 82 are located above thetubes 86 to fill theshell 74 with liquid refrigerant by introducing the liquid refrigerant above thetubes 86. - The
tubes 86 are oriented substantially horizontally relative to a support surface of the refrigerant evaporator 70 in a series of rows (FIGS. 6 and 7 ) though such orientation is only a non-limiting example of various possible orientations. Thetubes 86 in the illustrated embodiment are spaced relative to each other by a rectangular pitch (FIG. 6 ). Alternatively, the tubes could have a triangular pitch as shown inFIGS. 1 and 4 . The liquid refrigerant has atop surface 90, and a first plurality of thetubes 86 are immersed in the liquid refrigerant and located entirely below thetop surface 90 of the liquid refrigerant (FIG. 6 ). A second plurality of thetubes 86 are located at least partially above thetop surface 90 of the liquid refrigerant, and are at least partially immersed in liquid refrigerant and at least partially surrounded by gaseous refrigerant. A third plurality of thetubes 86 are located entirely above thetop surface 90 of the liquid refrigerant and are surrounded by gaseous refrigerant (FIG. 6 ). - With reference to
FIGS. 6 and 7 , the falling-film refrigerant evaporator 70 also includes a baffle 94 immersed in the liquid refrigerant and positioned adjacent to thetubes 86 that are immersed in the liquid refrigerant. The baffle 94 includes a plurality ofapertures 98 through which thetubes 86 are received. Thetubes 86 include an outer diameter less than that of theapertures 98 in which thetubes 86 are received, thereby forming anannular gap 102 between each of thetubes 86 and the baffle 94 through which liquid refrigerant may flow (FIGS. 6 and 8 ). In an alternative construction, the baffle 94 may be positioned betweenadjacent tubes 86 that are immersed in the liquid refrigerant and include an outer peripheral surface containing a plurality of grooves in which thetubes 86 are received. Alternatively, the baffle 94 may have a smooth other peripheral surface without airy grooves and be located toward the bottom and sides of theshell 74 below and adjacent thetubes 86, respectively. In the illustrated construction of the evaporator 70 at least a portion of the baffle 94 is located between thelower-most tubes 86 and the shell 74 (FIGS. 6 and 7 ). Also, in the illustrated construction of the evaporator 70, theshell 74 includes a first length L0 and the baffle 94 includes a second length L1 such that L1 is about 50% of the length of L0. Alternatively, the baffle 94 may include a length L1 that is at least about 75% or about 95% of the length L0. - In operation of the falling-film evaporator 70, liquid refrigerant falls from the
refrigerant inlet 78 down through thetubes 86 generally row by row. Near the region of the bottom portion of theshell 74, theshell 74 is occupied by nearly pure liquid refrigerant because the liquid refrigerant in this region has yet to exchange heat with thetubes 86 to cause it to evaporate. Accordingly, it is considered that liquid refrigerant in this region of theshell 74 has a low void fraction. As the baffle 94 occupies some of the internal volume of theshell 74, the baffle 94 displaces incoming liquid refrigerant upwardly in theshell 74 toward thetubes 86 above thetop surface 90 of liquid refrigerant relative to the condition if the baffle 94 were not provided. In other words, by displacing the liquid refrigerant, the presence of the baffle 94 can act to effectively raise thetop surface 90 of liquid refrigerant in theshell 74. Liquid refrigerant flows through each of theannular gaps 102 and contacts the outer periphery of thetubes 86. Contact between thetubes 86 and the liquid refrigerant allows heat to be transferred from the process fluid to the liquid refrigerant. This causes the liquid refrigerant to evaporate into gaseous refrigerant, which increases the void fraction of the surrounding liquid refrigerant. The gaseous refrigerant bubbles through theannular gaps 102 before exiting the baffle 94 and then exits theshell 74 via therefrigerant outlet 82. The void fraction within theshell 74 progressively increases from the bottom of theshell 74 towards thetop surface 90 of liquid refrigerant. By displacing liquid refrigerant in theshell 74 toward regions within theshell 74 which would otherwise have a high void fraction of liquid refrigerant in absence of the baffle 94, the baffle 94 reduces the amount of liquid refrigerant that is used compared to a typical falling-film evaporator without reducing the working efficiency of the evaporator. -
FIGS. 9 and 10 illustrate a second construction of a falling-film refrigerant evaporator 106 used in connection with an HVAC chiller to cool a process fluid. Like components are identified with like reference numerals with the letter “a,” and will not be described again in detail. Rather than incorporating only a single baffle 94 like that shown inFIGS. 6 and 7 and described above, theevaporator 106 includes a plurality of baffles located in different positions throughout the shell 74 a. Particularly, the falling-film refrigerant evaporator 106 includes a first baffle 110 positioned adjacent the lower-most tubes 86 a, a second and third baffle 114, 118 located above the first baffle 110 and axially spaced from each other, and afourth baffle 122 located above and axially spaced between the second and third baffles 114, 118. Alternatively, theevaporator 106 may include more or fewer baffles that may be distributed throughout the shell 74 a in various combinations. In the illustrated construction of theevaporator 106, the first, second, and third baffles 110, 114, 118 are immersed in liquid refrigerant and positioned adjacent to the tubes 86 a that are immersed in the liquid refrigerant (FIG. 9 ). Thefourth baffle 122 is not entirely immersed in liquid refrigerant and is positioned adjacent to the tubes 86 a that are at least partially immersed in liquid refrigerant and at least partially surrounded by gaseous refrigerant. Thefourth baffle 122 is also positioned adjacent to the tubes 86 a that are surrounded by gaseous refrigerant. - The
baffles 110, 114, 118, 122 each include a plurality of apertures 98 a through which the tubes 86 a are received. The tubes 86 a include an outer diameter less than that of the apertures 98 a in which the tubes 86 a are received, thereby forming an annular gap 102 a between each of the tubes 86 a and thebaffles 110, 114, 118, 122 through which liquid refrigerant may flow. In the illustrated construction of theevaporator 106 at least a portion of the lower-most baffle 110 is located between the lower-most tubes 86 a and the shell 74 a (FIGS. 9 and 10 ). Also, in the illustrated construction of theevaporator 106, the shell 74 a includes a first length L0 and the first baffle 110 includes a second length L1 such that L1 is about 95% of the length L0 (FIG. 10 ). The second, third, andfourth baffles 114, 118, 122 include a third, fourth, and fifth length L2, L3, L4, respectively, such that the lengths L2, L3, and L4 are each about 25% of the length L0 (FIG. 10 ). Alternatively, each of thebaffles 114, 118, 122 may include a length that is at least about 25% to at least about 95% of the length L0. - The falling-
film refrigerant evaporator 106 operates in an identical fashion as the evaporator 70 shown inFIGS. 6 and 7 and described above. However, each of thebaffles 110, 114, 118, 122 contributes to the displacement of the liquid refrigerant within the shell 74 a and amount commensurate with the volume with therespective baffles 110, 114, 118, 122. - In operation, embodiments of the present application can systematically control and/or influence the rate of heat exchange by the two phased flow of refrigerant in a multi-dimensional environment while utilizing a static baffle, in a lower portion of the shell, for liquid refrigerant displacement. The present application can be modified in one or more variants to one or more of its elements to enable an improved apparatus and method for improving the heat exchange (i.e., maximizing the reduction of heat) while optimizing the use of lesser refrigerant. It will be further appreciated that instructions of operation and/or assembly of various embodiments of the present application can take the form of a kit, a retrofit assembly, or general method for operation and that such instructions may be available in a variety of formats including but not limited to print, electronic, oral, and/or visual medium. Similarly, embodiments of the present application may be modified in one or more variants to one or more of the characteristics of its operation (e.g., variation in process fluid temperature, vapor velocity, etc.) to enable an improved apparatus and method for improving the heat exchange (i.e., maximizing the reduction of heat) while optimizing the use of lesser refrigerant. In one embodiment the liquid refrigerant is displaced by the physical structure of the baffle and by the refrigerant vapor generated within the
gaps 42 between the outer surface of the tubes and the baffle. - While the invention has been illustrated and described in detail in the drawings and foregoing description, the same is to be considered as illustrative and not restrictive in character, it being understood that only the preferred embodiments have been shown and described and that all changes and modifications that come within the spirit of the inventions are desired to be protected. It should be understood that while the use of words such as preferable, preferably, preferred or more preferred utilized in the description above indicate that the feature so described may be more desirable, it nonetheless may not be necessary and embodiments lacing the same may be contemplated as within the scope of the invention, the scope being defined by the claims that follow. In reading the claims, it is intended that when words such as “a,” “an,” “at least one,” or “at least one portion” are used there is no intention to limit the claim to only one item unless specifically stated to the contrary in the claim. When the language “at least a portion” and/or “a portion” is used the item can include a portion and/or the entire item unless specifically stated to the contrary.
Claims (24)
1. A refrigerant evaporator comprising:
a shell including a refrigerant inlet and a refrigerant outlet;
a plurality of tubes disposed within the shell and carrying a process fluid including at least a first plurality of tubes being immersed in liquid refrigerant within the shell, and at least a second plurality of tubes being at least partially surrounded by gaseous refrigerant; and
a baffle positioned adjacent the first plurality of tubes and immersed in the liquid refrigerant to displace the liquid refrigerant upwardly in the shell toward the second plurality of tubes.
2. The refrigerant evaporator of claim 1 , wherein the baffle is at least partially immersed in the liquid refrigerant to displace the liquid refrigerant.
3. The refrigerant evaporator of claim 1 , wherein the baffle includes a plurality of apertures through which the corresponding first plurality of tubes are received.
4. The refrigerant evaporator of claim 3 , wherein each of the first plurality of tubes includes an outer diameter less than a diameter of the apertures in the baffle in which the tubes are respectively received, thereby defining an annular gap separating each of the first plurality of tubes and the baffle.
5. The refrigerant evaporator of claim 4 , wherein liquid refrigerant is capable of being flowed through a plurality of annular gaps to contact an outer periphery of the first plurality of tubes.
6. The refrigerant evaporator of claim 1 , wherein the shell includes a first length, and wherein the baffle includes a second length of at least about 50% of the first length.
7. The refrigerant evaporator of claim 1 , wherein the shell includes a first length, and wherein the baffle includes a second length of at least about 75% of the first length.
8. The refrigerant evaporator of claim 1 , wherein the shell includes a first length, and wherein the baffle includes a second length of at least about 95% of the first length.
9. The refrigerant evaporator of claim 1 , wherein the baffle is a first baffle, and wherein the refrigerant evaporator further includes a second baffle positioned adjacent the first plurality of tubes and immersed in the liquid refrigerant.
10. The refrigerant evaporator of claim 9 , wherein the second baffle is axially spaced from the first baffle along the length of the shell.
11. The refrigerant evaporator of claim 9 , wherein the second baffle includes a plurality of apertures through which the corresponding first plurality of the tubes are received.
12. The refrigerant evaporator of claim 9 , wherein the second baffle includes a plurality of apertures through which a corresponding third plurality of the tubes are received, and wherein the third plurality of tubes are immersed in liquid refrigerant within the shell.
13. The refrigerant evaporator of claim 1 , wherein the evaporator is configured as a flooded evaporator in which the refrigerant inlet is located below the plurality of tubes and in which the refrigerant outlet is located above the plurality of tubes.
14. The refrigerant evaporator of claim 1 , wherein the evaporator is configured as a falling-film evaporator in which the refrigerant inlet and the refrigerant outlet are both located above the plurality of tubes.
15. The refrigerant evaporator of claim 1 , whereto the plurality of tubes are oriented substantially horizontally relative to a support surface of the refrigerant evaporator.
16. The refrigerant evaporator of claim 1 , wherein the plurality of tubes are spaced relative to each by a rectangular pitch.
17. The refrigerant evaporator of claim 1 , wherein the plurality of tubes are spaced relative to each by a triangular pitch.
18. The refrigerant evaporator of claim 1 , wherein at least a portion of the baffle is located between the lower-most tubes in the first plurality of tubes and the shell.
19. The refrigerant evaporator of claim 1 , wherein the shell includes a cylindrical shape.
20. The refrigerant evaporator of claim 19 , wherein the first plurality of tubes are arranged in a first row, wherein the second plurality of tubes are arranged in a second row, and wherein the number of tubes in the second row exceeds the number of tubes in the first row.
21. An apparatus for controlling a rate of heat exchange of liquid refrigerant in a multi-dimensional environment comprising in combination or tor assembly:
a refrigerant evaporator having a shell configured to receive the liquid refrigerant;
a plurality of tubes disposed within the shell configured for traversing a process fluid, the plurality of tubes having an upper plurality of tubes and a lower plurality of tubes configurable proximate to one another;
one or more baffles configurable to be positioned adjacent to the lower plurality of tubes and capable of being immersed in the liquid refrigerant for displacing the liquid refrigerant upwardly in the shell toward the upper plurality of tubes.
22. The apparatus of claim 21 , further including instructions of operation and/or assembly in a format of any of a print, electronic, oral, or visual medium.
23. The apparatus of claim 21 wherein the apparatus is in a kit form.
24. The apparatus of claim 21 wherein the apparatus includes at least three baffles.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/226,046 US20140202203A1 (en) | 2011-09-26 | 2014-03-26 | Refrigerant evaporator |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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US201161539325P | 2011-09-26 | 2011-09-26 | |
PCT/US2012/057353 WO2013049219A1 (en) | 2011-09-26 | 2012-09-26 | Refrigerant evaporator |
US14/226,046 US20140202203A1 (en) | 2011-09-26 | 2014-03-26 | Refrigerant evaporator |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US2012/057353 Continuation WO2013049219A1 (en) | 2011-09-26 | 2012-09-26 | Refrigerant evaporator |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140202203A1 true US20140202203A1 (en) | 2014-07-24 |
Family
ID=47996368
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/226,046 Abandoned US20140202203A1 (en) | 2011-09-26 | 2014-03-26 | Refrigerant evaporator |
Country Status (3)
Country | Link |
---|---|
US (1) | US20140202203A1 (en) |
EP (1) | EP2769161A4 (en) |
WO (1) | WO2013049219A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3961139A1 (en) * | 2020-08-27 | 2022-03-02 | Carrier Corporation | Methods of forming protective surface treatments on heat exchangers in-situ |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
IN2015DN03086A (en) * | 2012-09-26 | 2015-10-02 | Trane Int Inc | |
FR3038037B1 (en) * | 2015-06-29 | 2018-04-20 | Trane International Inc. | SUCTION DUCT AND DUAL SUCTION DUCT FOR AN IMMERSION EVAPORATOR |
CN104567132B (en) * | 2015-01-20 | 2017-02-22 | 珠海格力电器股份有限公司 | Fluid baffle structure and air conditioning equipment evaporator |
CN113028857A (en) * | 2019-12-24 | 2021-06-25 | 开利公司 | Heat exchanger and heat exchange system including the same |
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US2749600A (en) * | 1954-02-18 | 1956-06-12 | Rosenblads Patenter Ab | Method of making heat exchangers |
US2805049A (en) * | 1954-01-27 | 1957-09-03 | Union Carbide Corp | Heat exchanger tube spacers |
US3191396A (en) * | 1963-01-14 | 1965-06-29 | Carrier Corp | Refrigeration system and apparatus for operation at low loads |
US4448348A (en) * | 1982-08-19 | 1984-05-15 | Bidwell Malcolm A | Forced air flue heater device |
US4593757A (en) * | 1984-10-19 | 1986-06-10 | Phillips Petroleum Company | Rod baffle heat exchange apparatus and method |
US4991648A (en) * | 1989-02-10 | 1991-02-12 | Mitsubishi Jukogyo Kabushiki Kaisha | Multi-tube type heat transfer apparatus |
US5044427A (en) * | 1990-08-31 | 1991-09-03 | Phillips Petroleum Company | Heat exchanger |
US6952931B2 (en) * | 2003-10-06 | 2005-10-11 | Asp Corporation | Refrigerant monitoring system and method |
US20080190591A1 (en) * | 2007-02-08 | 2008-08-14 | Ayub Zahid H | Low charge refrigerant flooded evaporator |
US20090165497A1 (en) * | 2007-12-31 | 2009-07-02 | Johnson Controls Technology Company | Heat exchanger |
US20100319395A1 (en) * | 2008-01-11 | 2010-12-23 | Johnson Controls Technology Company | Heat exchanger |
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 |
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US3833058A (en) * | 1973-01-09 | 1974-09-03 | Sulzer Ag | Evaporator |
US5839294A (en) * | 1996-11-19 | 1998-11-24 | Carrier Corporation | Chiller with hybrid falling film evaporator |
TWI320094B (en) * | 2006-12-21 | 2010-02-01 | Spray type heat exchang device |
-
2012
- 2012-09-26 EP EP12836091.4A patent/EP2769161A4/en not_active Withdrawn
- 2012-09-26 WO PCT/US2012/057353 patent/WO2013049219A1/en active Application Filing
-
2014
- 2014-03-26 US US14/226,046 patent/US20140202203A1/en not_active Abandoned
Patent Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2805049A (en) * | 1954-01-27 | 1957-09-03 | Union Carbide Corp | Heat exchanger tube spacers |
US2749600A (en) * | 1954-02-18 | 1956-06-12 | Rosenblads Patenter Ab | Method of making heat exchangers |
US3191396A (en) * | 1963-01-14 | 1965-06-29 | Carrier Corp | Refrigeration system and apparatus for operation at low loads |
US4448348A (en) * | 1982-08-19 | 1984-05-15 | Bidwell Malcolm A | Forced air flue heater device |
US4593757A (en) * | 1984-10-19 | 1986-06-10 | Phillips Petroleum Company | Rod baffle heat exchange apparatus and method |
US4991648A (en) * | 1989-02-10 | 1991-02-12 | Mitsubishi Jukogyo Kabushiki Kaisha | Multi-tube type heat transfer apparatus |
US5044427A (en) * | 1990-08-31 | 1991-09-03 | Phillips Petroleum Company | Heat exchanger |
US6952931B2 (en) * | 2003-10-06 | 2005-10-11 | Asp Corporation | Refrigerant monitoring system and method |
US20080190591A1 (en) * | 2007-02-08 | 2008-08-14 | Ayub Zahid H | Low charge refrigerant flooded evaporator |
US20090165497A1 (en) * | 2007-12-31 | 2009-07-02 | Johnson Controls Technology Company | Heat exchanger |
US20100319395A1 (en) * | 2008-01-11 | 2010-12-23 | Johnson Controls Technology Company | Heat exchanger |
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 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3961139A1 (en) * | 2020-08-27 | 2022-03-02 | Carrier Corporation | Methods of forming protective surface treatments on heat exchangers in-situ |
Also Published As
Publication number | Publication date |
---|---|
EP2769161A4 (en) | 2015-08-05 |
EP2769161A1 (en) | 2014-08-27 |
WO2013049219A1 (en) | 2013-04-04 |
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