EP4680908A2

EP4680908A2 - Heating, ventilation, air conditioning, and refrigeration system tube support and gasket

Info

Publication number: EP4680908A2
Application number: EP24775785.9A
Authority: EP
Inventors: Amit Kumar Paspulati; SR. James Arthur RING; Wayne Allen HENDRIX
Original assignee: Tyco Fire and Security GmbH
Current assignee: Tyco Fire and Security GmbH
Priority date: 2023-03-23
Filing date: 2024-03-22
Publication date: 2026-01-21
Also published as: KR20250157454A; TW202447150A; WO2024197265A2; WO2024197265A3; CN120958286A

Abstract

A heat exchanger (180) for a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system (10) includes a plurality of heat exchange tubes (102), a tube support bracket (200) including a plurality of apertures (202), and a gasket (300) coupled to the tube support bracket (200). The gasket (300) includes a plurality of openings (302), and each opening (302) of the plurality of openings (302) is aligned with a corresponding aperture (202) of the plurality of apertures (202).

Description

HEATING, VENTILATION, AIR CONDITIONING, AND REFRIGERATION SYSTEM TUBE SUPPORT AND GASKET

CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims priority from and the benefit of U.S. Provisional Patent Application No. 63/454,246, entitled “HEATING, VENTILATION, AIR CONDITIONING, AND REFRIGERATION SYSTEM TUBE SUPPORT AND GASKET,” filed March 23, 2023, which is hereby incorporated by reference in its entirety for all purposes.

BACKGROUND

[0002] This section is intended to introduce the reader to various aspects of art that may be related to various aspects of the present disclosure, which are described below. This discussion is believed to be helpful in providing the reader with background information to facilitate a better understanding of the various aspects of the present disclosure. Accordingly, it should be understood that these statements are to be read in this light, and not as admissions of prior art.

[0003] A heating, ventilation, air conditioning, and refrigeration (HVAC&R) system may utilize a working fluid (e.g., a refrigerant) that changes phases between vapor, liquid, and combinations thereof in response to exposure to different temperatures and pressures within components of the HVAC&R system (e.g., vapor compression system, chiller system). The HVAC&R system may place the working fluid in a heat exchange relationship with a conditioning fluid (e.g., water, air) to heat and/or cool the conditioning fluid and may then deliver the conditioning fluid to various destinations to be utilized for other heat transfer purposes. For example, the HVAC&R system may include a heat exchanger (e.g., evaporator, condenser) configured to receive the working fluid and the conditioning fluid and to place the working fluid in the heat exchange relationship with the conditioning fluid. The heated and/or cooled conditioning fluid may then be directed from the heat exchanger to conditioning equipment and/or a conditioned environment serviced by the HVAC&R system. In some applications, the conditioning fluid may be directed through downstream equipment, such as an air handlers or terminal unit, to condition another fluid, such as air.

[0004] In some HVAC&R systems, a conditioning fluid may be cooled by an evaporator within which the working fluid absorbs heat from the conditioning fluid, thereby evaporating the working fluid and cooling the conditioning fluid. The working fluid may then be compressed by a compressor and directed to a condenser. In the condenser, the working fluid may be cooled, typically by a water flow or an air flow, and condensed into a liquid. Evaporators and condensers may have a variety of configurations, such as a shell and tube configuration, a tube and fin configuration, and so forth. In some embodiments, the tubes of the evaporator and/or condenser may extend a length of the evaporator and/or condenser and through corresponding openings (e g., holes) formed in one or more support brackets (e.g., tube support brackets) within the evaporator and/or condenser. In traditional systems, portions of the tubes extending through the openings of the support brackets may be expanded to increase contact with the one or more support brackets and thereby secure the tubes to the support brackets. Unfortunately, expansion of tubes within support brackets may be time consuming, expensive, and/or may decrease an overall heat exchange capacity of the heat exchanger.

SUMMARY

[0005] A summary of certain embodiments disclosed herein is set forth below. It should be understood that these aspects are presented merely to provide the reader with a brief summary of these certain embodiments and that these aspects are not intended to limit the scope of this disclosure. Indeed, this disclosure may encompass a variety of aspects that may not be set forth below.

[0006] In one embodiment, a heat exchanger for a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system includes a plurality of heat exchange tubes, a tube support bracket including a plurality of apertures, and a gasket coupled to the tube support bracket. The gasket includes a plurality of openings, and each opening of the plurality of openings is aligned with a corresponding aperture of the plurality of apertures.

[0007] In another embodiment, a heat exchanger for a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system includes a shell defining an internal volume configured to receive a first fluid, and a plurality of tubes disposed within the internal volume of the shell, where the plurality of tubes is configured to circulate a second fluid therethrough to place the second fluid in a heat exchange relationship with the first fluid. The heat exchanger also includes a tube support bracket disposed within the internal volume, where the tube support bracket includes a plurality of apertures formed therein. The heat exchanger further includes a gasket coupled to the tube support bracket, where the gasket includes a plurality of openings formed therein, and a tube of the plurality of tubes extends through an aperture of the plurality of apertures and through an opening of the plurality of openings corresponding to the aperture.

[0008] In a further embodiment, a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system includes a plurality of heat exchange tubes configured to circulate a fluid therethrough and a tube support bracket including a plurality of apertures. The heat exchanger also includes a damping panel affixed to a surface of the tube support bracket, where the damping panel includes a plurality of openings, and each opening of the plurality of openings is aligned with a respective aperture of the plurality of apertures. Each heat exchange tube of the plurality of heat exchange tubes is configured to extend through a respective opening of the plurality of openings and through a corresponding aperture of the plurality of apertures aligned with the respective opening.

DRAWINGS

[0009] Various aspects of this disclosure may be better understood upon reading the following detailed description and upon reference to the drawings in which: [0010] FIG. l is a perspective view of a building utilizing an embodiment of a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system in a commercial setting, in accordance with an aspect of the present disclosure;

[0011] FIG. 2 is a perspective view of an embodiment of a vapor compression system, in accordance with an aspect of the present disclosure;

[0012] FIG. 3 is a schematic of an embodiment of a vapor compression system, in accordance with an aspect of the present disclosure;

[0013] FIG. 4 is a schematic of an embodiment of a vapor compression system, in accordance with an aspect of the present disclosure;

[0014] FIG. 5 is a schematic of an embodiment of a heat exchange tube of a heat exchanger, illustrating portions of the heat exchange tube with surface enhancements and a portion of the heat exchange tube without surface enhancements, in accordance with an aspect of the present disclosure;

[0015] FIG. 6 is a schematic of an embodiment of a heat exchange tube of a heat exchanger including surface enhancements formed on the heat exchange tube from a first end of the heat exchange tube to a second end of the heat exchange tube, in accordance with an aspect of the present disclosure;

[0016] FIG. 7 is a cross-sectional axial view of an embodiment of a heat exchanger including a tube support bracket configured to support a plurality of heat exchange tubes of the heat exchanger, in accordance with an aspect of the present disclosure;

[0017] FIG. 8 is a perspective view of a portion of an embodiment of a heat exchanger having multiple tube support brackets configured to support a plurality of heat exchange tubes of the heat exchanger, in accordance with an aspect of the present disclosure; [0018] FIG. 9 is a partial perspective view of an embodiment of a tube support and a gasket configured to support a heat exchange tube of a heat exchanger, in accordance with an aspect of the present disclosure; and

[0019] FIG. 10 is an axial view schematic of an embodiment of a portion of a tube support and a gasket of a heat exchanger, in accordance with an aspect of the present disclosure.

DETAILED DESCRIPTION

[0020] One or more specific embodiments will be described below. In an effort to provide a concise description of these embodiments, not all features of an actual implementation are described in the specification. It should be appreciated that in the development of any such actual implementation, as in any engineering or design project, numerous implementation-specific decisions must be made to achieve the developers’ specific goals, such as compliance with system-related and business-related constraints, which may vary from one implementation to another. Moreover, it should be appreciated that such a development effort might be complex and time consuming, but would nevertheless be a routine undertaking of design, fabrication, and manufacture for those of ordinary skill having the benefit of this disclosure.

[0021] When introducing elements of various embodiments of the present disclosure, the articles “a,” “an,” and “the” are intended to mean that there are one or more of the elements. The terms “comprising,” “including,” and “having” are intended to be inclusive and mean that there may be additional elements other than the listed elements. Additionally, it should be understood that references to “one embodiment” or “an embodiment” of the present disclosure are not intended to be interpreted as excluding the existence of additional embodiments that also incorporate the recited features.

[0022] As used herein, the terms “approximately,” “generally,” and “substantially,” and so forth, are intended to convey that the property value being described may be within a relatively small range of the property value, as those of ordinary skill would understand. For example, when a property value is described as being “approximately” equal to (or, for example, “substantially similar” to) a given value, this is intended to mean that the property value may be within +/- 5%, within +/- 4%, within +/- 3%, within +/- 2%, within +/- 1%, or even closer, of the given value. Similarly, when a given feature is described as being “substantially parallel” to another feature, “generally perpendicular” to another feature, and so forth, this is intended to mean that the given feature is within +/- 5%, within +/- 4%, within +/- 3%, within +/- 2%, within +/- 1%, or even closer, to having the described nature, such as being parallel to another feature, being perpendicular to another feature, and so forth. Further, it should be understood that mathematical terms, such as “planar,” “slope,” “perpendicular,” “parallel,” and so forth are intended to encompass features of surfaces or elements as understood to one of ordinary skill in the relevant art, and should not be rigidly interpreted as might be understood in the mathematical arts. For example, a “planar” surface is intended to encompass a surface that is machined, molded, or otherwise formed to be substantially flat or smooth (within related tolerances) using techniques and tools available to one of ordinary skill in the art. Similarly, a surface having a “slope” is intended to encompass a surface that is machined, molded, or otherwise formed to be oriented at an angle (e.g., incline) with respect to a point of reference using techniques and tools available to one of ordinary skill in the art.

[0023] Embodiments of the present disclosure relate to heating, ventilation, air conditioning, and refrigeration (HVAC&R) systems. The HVAC&R system may include a vapor compression system (e.g., a vapor compression circuit) configured to circulate a working fluid (e.g., a refrigerant) to cool and/or heat a conditioning fluid (e.g., water). The HVAC&R system may then direct the conditioning fluid to other equipment of the HVAC&R system and/or to various downstream equipment (e.g., air handing equipment) to condition a space and/or a component of the various client systems.

[0024] For example, the HVAC&R system may include one or more heat exchangers (e.g., evaporators, condensers) configured to receive the working fluid and a conditioning fluid or cooling fluid and to place the working fluid in the heat exchange relationship (e.g., thermal energy exchange relationship) with the conditioning fluid or cooling fluid. In typical HVAC&R system, a conditioning fluid may be cooled by an evaporator within which the working fluid absorbs heat from the conditioning fluid, thereby evaporating the working fluid and cooling the conditioning fluid. The working fluid may then be compressed by a compressor and transferred to a condenser. In the condenser, the working fluid may be cooled, typically by a water flow or an air flow, and condensed into a liquid. Heat exchangers may have a variety of configurations, such as a shell and tube configuration, a tube and fin configuration, and so forth. In some embodiments, such as a shell and tube configuration, tubes (e.g., a tube bundle, heat exchange tubes) of the heat exchanger may extend through a shell of the heat exchanger along a length of the heat exchanger. The tubes may circulate a cooling fluid or conditioning fluid therethrough, and the shell may receive a working fluid to enable heat exchange between the cooling fluid or conditioning fluid and the working fluid. The tubes may also extend through apertures (e.g., holes) formed in one or more tube support brackets (e.g., baffles, baffle plates, tube support plates) within the shell of the heat exchanger, and the tube support brackets may support or retain a configuration or arrangement of the tubes within the shell.

[0025] In some applications, the tubes may include one or more surface enhancements (e g., finned sections, finned portions, enhanced regions, textured regions, surface features) extending along lengths of the tubes. The surface enhancements may include fins, formations, ridges, rings, helixes, or other surface features formed along an outer surface of the tubes to increase a surface area (e.g., outer surface area) of the tube. In this way, the surface enhancements may increase a heat exchange capacity of the tube, increase a heat transfer coefficient of the tube, improve efficiency of the tube, and so forth. However, traditional tubes may also include sections without surface enhancements (e.g., skipped sections, skipped portions, smooth sections, unmodified sections) that may be bare and/or may not include fins or other surface enhancements. In existing systems, the tubes may be formed with smooth regions, and the smooth regions may be positioned within the apertures of the one or more tube support brackets. The smooth regions of the tube may be expanded (e.g., radially expanded, outwardly expanded) within the apertures to increase contact between the tube and the one or more tube support brackets and thereby create an interface or engagement between the tube and the tube support brackets to positionally fix the tube relative to the tube support brackets. Unfortunately, heat exchangers that include tubes with smooth regions or sections may have a limited heat exchange capacity and/or heat transfer coefficient. Additionally, tube expansion processes utilized to affix the tubes to the tube support brackets may be expensive, time consuming, and/or susceptible to other drawbacks.

[0026] Accordingly, embodiments of the present disclosure are directed to an HVAC&R system (e.g., a heat exchanger) having a gasket for a tube support bracket (e.g., baffle, baffle plate, tube support plate) configured to facilitate securement of tubes (e.g., heat exchange tubes) to the tube support bracket without expansion of the tubes within apertures of the tube support bracket. Indeed, the present techniques enable utilization of tubes without smooth regions or portions (e.g., unmodified portions, fin-less portions) at intersections with a tube support bracket that would otherwise be included to enable expansion of the tube within the openings of the tube support brackets. As the gasket for the tube support bracket enables use of tubes without smooth, fin-less, or “skipped” regions, the tubes may include surface enhancements (e.g., fins) formed along a greater length of the tubes to enable an increase in the heat transfer coefficient of the tubes, and therefore an increase in overall heat exchange capacity of the heat exchanger during operation, as compared to a heat exchanger that includes tubes having smooth, fin-less, or “skipped” sections. Furthermore, in accordance with present techniques, the gasket is configured to engage with the tubes to mitigate vibration of the tubes relative to the tube support brackets, and thereby reduce potential wear and degradation to the tubes and/or tube support brackets that may otherwise be caused by vibration of the tubes. In this way, the gasket may extend the life of the tubes and thus extend the life of the heat exchanger.

[0027] Turning now to the drawings, FIG. 1 is a perspective view of an embodiment of an environment for a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system 10 in a building 12 for atypical commercial setting. The HVAC&R system 10 may include a vapor compression system 14 (e.g., a chiller) that supplies a chilled liquid, which may be used to cool the building 12. The HVAC&R system 10 may also include a boiler 16 to supply warm liquid to heat the building 12 and an air distribution system which circulates air through the building 12. The air distribution system can also include an air return duct 18, an air supply duct 20, and/or an air handler 22. In some embodiments, the air handler 22 may include a heat exchanger that is connected to the boiler 16 and the vapor compression system 14 by conduits 24. The heat exchanger in the air handler 22 may receive either heated liquid from the boiler 16 and/or chilled liquid from the vapor compression system 14, depending on the mode of operation of the HVAC&R system 10. The HVAC&R system 10 is shown with a separate air handler on each floor of building 12, but in other embodiments, the HVAC&R system 10 may include air handlers 22 and/or other components that may be shared between or among floors.

[0028] FIGS. 2 and 3 illustrate embodiments of the vapor compression system 14 that can be used in the HVAC&R system 10. The vapor compression system 14 may circulate a working fluid through a working fluid circuit starting with a compressor 32. The working fluid circuit may also include a condenser 34, an expansion valve(s) or device(s) 36, and a liquid chiller or an evaporator 38. The vapor compression system 14 may further include a control panel 40 that has an analog to digital (A/D) converter 42, a microprocessor 44, a non-volatile memory 46, and/or an interface board 48.

[0029] Some examples of fluids that may be used as working fluids in the vapor compression system 14 are hydrofluorocarbon (HFC) based refrigerants, for example, R- 410A, R-407, R-134a, R-1234ze, R1233zd, hydrofluoro olefin (HFO), "natural" working fluids like ammonia (NH3), R-717, carbon dioxide (CO2), R-744, or hydrocarbon based working fluids, water vapor, or any other suitable working fluid. In some embodiments, the vapor compression system 14 may be configured to efficiently utilize working fluids having a normal boiling point of about 19 degrees Celsius (66 degrees Fahrenheit) at one atmosphere of pressure, also referred to as low pressure working fluids, versus a medium pressure working fluid, such as R-134a. As used herein, "normal boiling point" may refer to a boiling point temperature measured at one atmosphere of pressure.

[0030] In some embodiments, the vapor compression system 14 may use one or more of a variable speed drive (VSDs) 52, a motor 50, the compressor 32, the condenser 34, the expansion valve or device 36, and/or the evaporator 38. The motor 50 may drive the compressor 32 and may be powered by a variable speed drive (VSD) 52. The VSD 52 receives alternating current (AC) power having a particular fixed line voltage and fixed line frequency from an AC power source, and provides power having a variable voltage and frequency to the motor 50. In other embodiments, the motor 50 may be powered directly from an AC or direct current (DC) power source. The motor 50 may include any type of motor that can be powered by a VSD or directly from an AC or DC power source, such as a switched reluctance motor, an induction motor, an electronically commutated permanent magnet motor, or another suitable motor.

[0031] The compressor 32 compresses a working fluid vapor and delivers the vapor to the condenser 34 through a discharge passage. In some embodiments, the compressor 32 may be a centrifugal compressor. The working fluid vapor delivered by the compressor 32 to the condenser 34 may transfer heat to a cooling fluid (e.g., water, air) in the condenser 34. The working fluid vapor may condense to a working fluid liquid in the condenser 34 due to thermal heat transfer with the cooling fluid. The liquid working fluid from the condenser 34 may flow through the expansion device 36 to the evaporator 38. In the illustrated embodiment of FIG. 3, the condenser 34 is water-cooled and includes a tube bundle 54 connected to a cooling tower 56, which supplies the cooling fluid to the condenser 34.

[0032] The liquid working fluid delivered to the evaporator 38 may absorb heat from a conditioning fluid, which may or may not be the same as the cooling fluid used in the condenser 34. The liquid working fluid in the evaporator 38 may undergo a phase change from the liquid working fluid to a working fluid vapor. As shown in the illustrated embodiment of FIG. 3, the evaporator 38 may include a tube bundle 58 having a supply line 60S and a return line 60R connected to a cooling load 62. The conditioning fluid of the evaporator 38 (e.g., water, ethylene glycol, calcium chloride brine, sodium chloride brine, or any other suitable fluid) enters the evaporator 38 via return line 60R and exits the evaporator 38 via supply line 60S. The evaporator 38 may reduce the temperature of the cooling fluid in the tube bundle 58 via thermal heat transfer with the working fluid. The tube bundle 58 in the evaporator 38 can include a plurality of tubes and/or a plurality of tube bundles. In any case, the vapor working fluid exits the evaporator 38 and returns to the compressor 32 by a suction line to complete the cycle.

[0033] FIG. 4 is a schematic of an embodiment of the vapor compression system 14 with an intermediate circuit 64 incorporated between condenser 34 and the expansion device 36. The intermediate circuit 64 may have an inlet line 68 that is directly fluidly connected to the condenser 34. In other embodiments, the inlet line 68 may be indirectly fluidly coupled to the condenser 34. As shown in the illustrated embodiment of FIG. 4, the inlet line 68 includes a first expansion device 66 positioned upstream of an intermediate vessel 70. In some embodiments, the intermediate vessel 70 may be a flash tank (e.g., a flash intercooler, an economizer, etc.). In other embodiments, the intermediate vessel 70 may be configured as a heat exchanger or a “surface economizer.” In the illustrated embodiment of FIG. 4, the intermediate vessel 70 is used as a flash tank, and the first expansion device 66 is configured to lower the pressure of (e.g., expand) the liquid working fluid received from the condenser 34. During the expansion process, a portion of the liquid may vaporize, and thus, the intermediate vessel 70 may be used to separate the vapor from the liquid received from the first expansion device 66.

[0034] Additionally, the intermediate vessel 70 may provide for further expansion of the liquid working fluid due to a pressure drop experienced by the liquid working fluid when entering the intermediate vessel 70 (e.g., due to a rapid increase in volume experienced when entering the intermediate vessel 70). The vapor in the intermediate vessel 70 may be drawn by the compressor 32 through a suction line 74 of the compressor 32. In other embodiments, the vapor in the intermediate vessel may be drawn to an intermediate stage of the compressor 32 (e.g., not the suction stage). The liquid that collects in the intermediate vessel 70 may be at a lower enthalpy than the liquid working fluid exiting the condenser 34 because of the expansion in the expansion device 66 and/or the intermediate vessel 70. The liquid from intermediate vessel 70 may then flow in line 72 through a second expansion device 36 to the evaporator 38.

[0035] It should be appreciated that any of the HVAC&R systems discussed above may be utilized in accordance with the present techniques. For example, the present techniques may be incorporated in embodiments of the HVAC&R system 10, the vapor compression system 14, the boiler 16, a chiller, a heat pump, and/or other HVAC&R equipment discussed above. The discussion below describes the present techniques incorporated with embodiments of the vapor compression system 14 (e.g., chiller) of the HVAC&R system 10 configured to supply a cooled conditioning fluid to condition a space and/or a component of various downstream equipment (e.g., air handling equipment) of the HVAC&R system 10. However, it should be noted that the systems and methods described herein may be implemented to similarly provide a heated conditioning fluid to condition a space and/or a component of any suitable system.

[0036] As briefly discussed above, present embodiments are directed to a heat exchanger, such as the condenser 34 and/or the evaporator 38, having a gasket (e.g., gasket blanket, damping panel) for a tube support bracket (e.g., baffle, baffle plate, tube support plate) that facilitates securement of tubes (e.g., heat exchange tubes) within apertures of the tube support bracket. In particular, the gasket enables securement of the tubes within the apertures of the tube support bracket without expansion of the tubes within the apertures of the tube support bracket to create an interference fit or engagement between the tubes and the tube support bracket. Instead, the gasket may be configured to establish an interference fit with the tubes to enable retention of the tubes relative to the tube support bracket.

[0037] The gasket may also be formed from an elastomer (e.g., elastic polymer), such as rubber or poly chloroprene, configured to elastically deform. As a result, the tubes may be formed to include surface enhancements, such as fins, on an outer surface (e.g., outer diameter, outer circumference) of the tubes (e.g., along a length of the tubes) without also including smooth, fin-less, or “skipped” sections (e.g., portions, regions) of the tubes that do not include fins or surface enhancements. As noted above, smooth, fin-less, or “skipped” sections are typically included in existing tubes in order to accommodate expansion of the tubes within apertures of the tube support bracket. Unfortunately, the inclusion of sections without surface enhancements, such as fins, reduces the heat transfer performance of the tubes. The present techniques enable the assembly and manufacture of heat exchangers with tubes that do not include smooth, fin-less, or “skipped” or regions, which enables an increase in the overall heat exchange capacity and/or efficiency of the heat exchanger during operation, as compared to a heat exchanger that includes tubes having smooth or fin-less regions.

[0038] Furthermore, the gasket is configured to mitigate vibration of the tubes, thereby reducing potential wear and degradation to the tube and/or tube support brackets that may otherwise be caused by vibration of the tube. In this way, the gasket may extend the useful life of the tubes and thus extend the useful life of the heat exchanger. As used herein, a “skipped” tube may refer to a heat exchange tube having surface enhancement features, such as fins, formed on certain portions of an outer diameter or surface of the tube and also having one or more smooth (e.g., fin-less, unmodified, unenhanced) regions or portions along the length of the tube to accommodate expansion of the tube within an aperture of a tube support bracket. As used herein, a “finned” tube may refer to a heat exchange tube having fins or other surface enhancement features formed on the outer diameter or surface of the tube (e.g., along an entire heat transfer length of the tube) and without having one or more smooth or fin-less regions formed along the length of the tube to accommodate expansion of the tube within an aperture of a tube support bracket.

[0039] With the foregoing in mind, FIG. 5 is a schematic of an embodiment of a heat exchange tube that may be included in a tube bundle of a heat exchanger of a vapor compression system of an HVAC&R system. In particular, FIG. 5 is a schematic of an embodiment of a skipped tube 100 of a heat exchanger of an HVAC&R system. In some embodiments, the skipped tube 100 may be formed from a conductive metallic material, such as, for example, copper, steel, stainless steel, copper-nickel, titanium, aluminum, or any combination thereof. As illustrated, the skipped tube 100 may include enhanced areas or regions (e.g., textured surface, surface enhancements), such as finned sections 104 (e.g., finned portions, finned regions, enhanced sections, textured sections), configured to increase an outer surface area of the tube 100, and thus increase a heat transfer coefficient of the finned sections 104 of the skipped tube 100. The enhanced regions, or finned sections 104, may include a plurality of fins 106 (e.g., ridges) alternating with a plurality of valleys 108 formed in an outer surface 111 of the skipped tube 100. Each fin 106 of the plurality of fins 106 and each valley 108 of the plurality of valleys 108 extends radially outward from a central axis 110 (e.g., a center) of the skipped tube 100 and substantially around a circumference of the skipped tube 100. In some embodiments, each fin 106 of the plurality of fins 106 may each be a discrete fin, separate and distinct from other fins 106. In other embodiments, the fins 106 may be formed via one or more continuously formed ribbon-like structures (e.g., a helix) that spiral around an outer surface of the skipped tube 100 within the finned sections 104. The plurality of fins 106 (e.g., ridges) and the plurality of valleys 108 of the finned sections 104 may be formed via mechanical depression (e.g., deformation) of the outer surface 111 (e.g., the finned regions 104) of the skipped tube 100. For example, the plurality of fins 106 may be formed using one or more molds (e.g., discs, rollers) having a desired pattern that is pressed onto the outer surface 111 of the skipped tube 100 to form a textured surface 112 (e.g., the plurality of fins 106 alternating with the plurality of valleys 108, textured outer surface, surface enhancement) of the finned sections 104.

[0040] Detailed view 114 of FIG. 5 illustrates a cross-sectional schematic view of the skipped tube 100 at an apex 118 (e.g., crest) of one of the fins 106 (e.g., a ridge). The detailed view 114 also depicts a trough 126 of one of the valleys 108 in the finned sections 104. As illustrated, the skipped tube 100 may be generally circular and may include an inner wall 122 (e.g., inner diameter) defining a hollow cavity 124 (e.g., flow path, passage) within which a fluid (e.g., a conditioning fluid, a cooling fluid, water, brine) may flow. Specifically, the apex 118 of the fin 106 (e g., ridge) may correspond to a location (e.g., along the central axis 110) within the finned section 104 of the skipped tube 100 at which a first thickness 120 (e.g., radial thickness) of the skipped tube 100 (e.g., extending radially from the central axis 110 to the apex 118) is an upper (e.g., greatest) value. The trough 126 of the valley 108 may correspond to a location (e.g., along the central axis 110) within the finned section 104 at which a second thickness 128 (e.g., radial thickness) of the skipped tube 100 (e.g., extending radially from the central axis 110 to the trough 126) is a lower (e g., least) value. In other words, the first thickness 120 of the skipped tube 100 is greater than the second thickness 128 of the skipped tube 100 in the finned section 104.

[0041] Furthermore, the skipped tube 100 may include one or more smooth sections 130 (e.g., fin-less sections, unenhanced sections) along a length 116 of the skipped tube 100. The one or more smooth sections 130 may include little or no enhanced textured surface. In other words, the smooth sections 130 may be sections of the skipped tube 100 that have no fins 106 (e.g., fin-less) and/or are without any substantially textured surface or surface enhancements. As a result, the smooth sections 130 of the skipped tube 100 may have a lower heat transfer coefficient than the finned sections 104 (e.g., enhanced sections) of the skipped tube 100. As discussed herein, the smooth sections 130 may be disposed at positions along the skipped tube 100 that interface (e.g., cross, overlap, intersect, extend within) with a tube support bracket (e.g., baffle, baffle plate, tube support plate) to facilitate expansion of the skipped tube 100 at an interface point to increase contact of the skipped tube 100 with the tube support bracket.

[0042] However, expansion of the skipped tube 100 may cause the thickness of the skipped tube 100 to thin and/or decrease in tube wall thickness. Therefore, the skipped tube 100 may include the smooth sections 130 at the interface locations to allow for expansion of the skipped tube 100 at the interface locations. In particular, the smooth sections 130 may not undergo a process of producing the textured surface 112 of the skipped tube 100, such as the fins 106 and valleys 108, which may otherwise cause thinning of the skipped tube 100. The thickness of the skipped tube 100 in the enhanced sections and/or finned sections 104 (e.g., the second thickness 128) may not be sufficiently great or large to accommodate expansion of the skipped tube 100 without compromising a structural and/or material integrity of the skipped tube 100. Thus, the smooth sections 130 (e g., un-enhanced areas, fin-less sections) may have a thickness that allows for expansion of the skipped tube 100 to enable the increase in contact between the skipped tube 100 and the tube support bracket at the interface locations without compromising the structural integrity of the skipped tube 100. As an example, detailed view 132 of FIG. 5 illustrates a cross-sectional schematic view of the skipped tube 100 at the smooth section 130. In some embodiments, a third thickness 134 (e.g., radial thickness) of the skipped tube 100 of the smooth section 130 may be substantially equal or similar to the first thickness 120 of the skipped tube 100 between the inner wall 122 and the apex 118 of the fin 106 of the finned section 104 and may be greater than the second thickness 128 of the skipped tube 100 between the inner wall 122 and the floor 126 of the valley 108 of the finned section 104.

[0043] In some embodiments, each of the smooth sections 130 may include one or more transition regions 136 and one or more bare regions 140 (e.g., smooth regions). In particular, the one or more transition regions 136 may be sections of the skipped tube 100 between the finned sections 104 and the one or more bare sections 140 that include a roughed surface 138 different from that of the finned sections 104 or the bare regions 140. In particular, the roughed surfaces 138 of the transition regions 136 may yield a reduced ratio of heat exchange surface area to volume of the skipped tube 100 than the ratio of heat exchange surface area to volume of the finned sections 104 of the skipped tube 100.

[0044] FIG. 6 is a schematic of an embodiment of a heat exchange tube that may be included in a tube bundle (e.g., the tube bundle 54, the tube bundle 58) of a heat exchanger (e.g., condenser 34, evaporator 38) of the vapor compression system 14 of the HVAC&R system 10. In particular, FIG. 6 is a schematic of an embodiment of a finned heat exchange tube 102 that may be utilized in a heat exchanger (e.g., condenser 34, evaporator 38) of the HVAC&R system 10. In some embodiments, the finned tube 102 may be formed from a conductive metallic material, such as, for example, copper, steel, stainless steel, coppernickel, titanium, aluminum, or any combination thereof. As illustrated, the finned tube 102 may include a surface enhancement (e.g., textured surface), such as a finned section 142 (e.g., finned region, finned surface, surface enhancement), that may extend along a length 141 (e.g., substantially an entirety of the length 141, an entirety of the length 141) of the finned tube 102 (e.g., without intervening smooth sections). In other words, the finned section 142 may extend from a first longitudinal end portion 143 of the finned tube 102 to a second longitudinal end portion 145 of the finned tube 102. In addition, as discussed herein, the finned section 142 may be configured to increase a surface area (e.g., outer surface area) of the finned tube 102, and thus increase heat transfer coefficient of the finned tube 102, such as by facilitating an increase in heat transfer between a first fluid direct across the finned tube 102 (e.g., across the outer surface) and a second fluid directed through (e.g., within) the finned tube 102.

[0045] The finned section 142 may include a plurality of fins 144 (e.g., ridges, surface enhancements) alternating with a plurality of valleys 146. Each fin 144 and each valley 146 may generally extend radially from a central axis 148 (e.g., a center) of the finned tube 102 and substantially around a circumference of the finned tube 102. In some embodiments, each fin 144 of the plurality of fins 144 may each be a discrete fin, separate and distinct from other fins 144. In other embodiments, the fins 144 may be one or more continuously formed ribbon-like structures (e.g., helixes) that spiral around an outer surface 174 of the finned tube 102. The plurality of fins 144 (e.g., ridges) and the plurality of valleys 146 of the finned tube 102 (e.g., finned section 142) may be formed via mechanical depression (e.g., deformation) of the outer surface 174 of the finned tube 102. For example, the plurality of fins 144 may be formed using one or more molds (e.g., discs, rollers) having a desired pattern that is pressed onto the outer surface 174 of the finned tube 102 to form a textured surface 150 (e.g., the plurality of fins 144 alternating with the plurality of valleys 146, textured outer surface, surface enhancement) along the outer surface 174 of the finned tube 102 (e.g., from the first longitudinal end portion 143 to the second longitudinal end portion 145). [0046] As an example, detailed view 152 of FIG. 6 illustrates a cross-sectional view of the finned tube 102 at an apex 154 (e.g., crest) of one of the fins 144. The detailed view 152 also depicts a trough 158 of one of the valleys 146. As illustrated, the finned tube 102 may be generally circular and may include an inner wall 160 (e.g., inner surface) defining a hollow cavity 162 (e.g., flow path, passage) within which a fluid (e.g., a conditioning fluid, a cooling fluid, water, brine) may flow. Specifically, the apex 154 of the fin 144 (e.g., ridge) may correspond to a location (e.g., along the central axis 148) of the finned tube 102 at which a first thickness 164 (e.g., radial thickness) of the finned tube 102 (e.g., extending radially from the central axis 148 to the apex 154) is an upper (e g., greatest) value. The trough 158 of the valley 146 may correspond to a location (e.g., along the central axis 148) of the finned tube 102 at which a second thickness 166 (e.g., radial thickness) of the finned tube 102 is a lower (e.g., least) value. In other words, the first thickness 164 of the finned tube 102 is greater than the second thickness 166 of the finned tube 102.

[0047] Furthermore, the finned tube 102 may have an inner diameter 170 defined by the inner wall 160 of the finned tube 102. In some embodiments, the inner diameter 170 may be generally and/or substantially constant along the length 141 of the finned tube 102. An outer diameter 172 of the finned tube 102 may vary along the length 141 of the finned tube 102, such as due to the formation of the fins 144 and the valleys 146 (e.g., the finned section 142, the textured surface 150, surface enhancements) on the outer surface 174 of the finned tube 102. In some embodiments, a magnitude of the outer diameter 172 may vary between approximately 18 millimeters (mm) to 20 mm, between approximately 17 mm and 19 mm, between approximately 18.7 mm and 19 mm, or any other suitable range along the length 141 of the finned tube 102. The magnitude of the outer diameter 172 may vary along the length 141 due to variation in the thickness (e.g., radial thickness) of the finned tube 102 (e.g., first thickness 164, second thickness 166) created by the formation of the fins 144 (e g., ridges) and the valleys 146 in the outer surface 174. In this way, the pattern of the textured surface 150 having the fins 144 and the valleys 146 may increase a surface area of the outer surface 174, as well as increase ratio of heat exchange surface area of the finned tube 102 to volume of fluid within the finned tube 102. The increased surface area of the outer surface 174 may enable an increase in the heat transfer coefficient (e.g., heat transfer capacity) of the finned tube 102.

[0048] The textured surface 150 (e.g., fins 144, valleys 146) formed on the outer surface 174 and extending from the first longitudinal end portion 143 to the second longitudinal end portion 145 (e.g., along the length 141) without an intervening smooth section formed along the length 141 may enable improved heat transfer via the finned tube 102, as compared to an embodiment of the skipped tube 100 having one or more smooth sections 130 (e.g., fin-less sections) that are incorporated to accommodate expansion of the skipped tube 100. It should be appreciated that, in some embodiments, the textured surface 150 of the finned tube 102 may have alternative geometries (e.g., surface enhancements) in addition to, or instead of, the fins 144 (e.g., ridges) and the valleys 146. For example, the finned tube 102 (e.g., heat exchange tube, tube) may include surface enhancements such as cross-hatching, stippling, divots, peaks, and/or other surface enhancements that may increase the surface area of the outer surface 174 of the finned tube 102. In any case, the surface enhancements formed on the outer surface 174 of the finned tube 102 may be formed along an entirety or substantially an entirety of the length 141 of the finned tube 102 (e.g., without one or more intervening smooth or bare sections), in accordance with the present techniques. In some embodiments, the inner wall 160 of the finned tube 102 may include a second textured surface, which may be substantially the same as, or different from, the textured surface 150 of the outer surface 174 of the finned tube 102.

[0049] As discussed herein, the use of the finned tubes 102 incorporating the present techniques within a heat exchanger, such as the condenser 34 and/or the evaporator 38, of the vapor compression system 14 of the HVAC&R system 10 improves operation of the HVAC&R system 10. For example, the finned tubes 102 enable an increase in the heat transfer coefficient of a heat exchanger having the finned tubes 102, an increase in the overall heat exchange capacity of the HVAC&R system 10, and an increase in efficiency of the heat exchanger and/or HVAC&R system, as compared to a heat exchanger that includes skipped tubes 100. In particular, the finned tubes 102 having the textured surface 150 formed along the length 141 (e.g., an entirety of the length 141) without intervening smooth sections provides a greater heat exchange surface area of the outer surface 174 (e.g., relative to a volume of fluid directed through the finned tube 102) compared to that of the skipped tube 100, due to the presence of one or more smooth sections 130 (e.g., unenhanced sections, fin-less sections) on the outer surface 111 of the skipped tube 100.

[0050] FIG. 7 is a cross-sectional axial view of an embodiment of a heat exchanger 180 within which heat exchange tubes, such as the finned tubes 102, may be incorporated, in accordance with present techniques. As similarly described above, the heat exchanger 180 may be incorporated with an embodiment of the vapor compression system 14 and may be configured to enable heat transfer between two or more fluid flows. To this end, the heat exchanger 180 includes a shell 182 defining an internal volume 184 configured to receive a first fluid, such as a working fluid circulated through the vapor compression system 14. A plurality of the finned tubes 102 may be disposed within the shell 182 and may be configured to circulate a second fluid (e.g., cooling fluid, conditioning fluid) therethrough. In this way, the first fluid may be directed across the plurality of finned tubes 102, and heat may be exchanged between the first fluid and the second fluid directed through the finned tubes 102.

[0051] To retain a position, configuration, and/or arrangement of the finned tubes 102 within the internal volume 184, the heat exchanger 180 may include one or more a tube support brackets 200 (e.g., baffle, baffle plate, tube support plate) disposed within the internal volume 184 of the heat exchanger 180. In some embodiments, the tube support bracket 200 may be fabricated from a single piece (e.g., single sheet) of material, such as copper, steel, stainless steel, copper-nickel, titanium, aluminum, another metallic material, a composite material, or any other suitable material. One or more of the tube support brackets 200 may secured within the internal volume 184 to an internal wall 256 of the shell 180. The one or more tube support brackets 200 may secured to the internal wall 256 of the heat exchanger 180 via any suitable fastening technique, such as one or more fasteners, brazing, an adhesive, and/or welding. In some embodiments, the tube support bracket 200 may have a semi-circular shape or geometry and may extend within the internal volume 184 along a portion of a height 204, with respect to a vertical axis 250, of the heat exchanger 180 (e.g., the shell 182, the internal volume 184). The tube support bracket 200 also extends within the internal volume 184 along a width 206, with respect to a lateral axis 252, of the heat exchanger 180 (e.g., the shell 182, the internal volume 184). In the illustrated embodiment, the tube support bracket 200 extends across an entirety of the width 206. It should be appreciated that the tube support bracket 200 may have any suitable geometry (e.g., outer geometry), shape, and/or configuration configured to enable support and retention of the finned tubes 102 within the internal volume 184, in accordance with the present techniques.

[0052] In addition, the tube support bracket 200 may include a plurality of apertures 202 (e.g., gaps, holes, openings) formed therein. Each aperture 202 is configured to receive a corresponding heat exchange tube (e.g., finned tube 102) disposed within the internal volume 184. Indeed, the heat exchanger 180 may include multiple tube support brackets 200, which may have similar configurations, and each heat exchange tube may extend through a respective aperture 202 of each tube support bracket 200. The apertures 202 may be arranged in any suitable arrangement (e.g., pattern, geometry) so as to support and retain a desired configuration, arrangement, and/or position of the heat exchange tubes (e g., finned tubes 102) within the heat exchanger 180. For example, in the illustrated embodiment, the apertures 202 are arranged in a series of rows 240 (e.g., offset rows, staggered rows) arranged and/or arrayed along the vertical axis 250. The apertures 202 of adjacent rows 240 (e.g., vertically adjacent rows) may be staggered relative to one another, such as relative to the vertical axis 250 and/or along the lateral axis 252. For example, a first center 212 (e.g., central axis) of a first aperture 214 in a first row 216 of apertures 202 is offset from (e g., not aligned with) a second center 218 (e.g., central axis) of a second aperture 220 in a second row 222 of apertures 202. A third center 224 (e.g., central axis) of a third aperture 226 in a third row 228 of apertures 202 is aligned with the first center 212 of the first aperture 214. Furthermore, each aperture 202 may have a diameter 230 (e g., approximately 17 mm, 18 mm, 19 mm, 18 mm to 19 mm, 19.2 mm to 19.35 mm). The diameter 230 of the apertures 202 may be greater (e.g., slightly greater) than an outer diameter of the heat exchange tubes (e.g., the outer diameter 172 of the finned tube 102). In this way, the heat exchange tubes (e.g., finned tubes 102) may be readily inserted through the apertures 202 during assembly of the heat exchanger 180. Additionally, in some embodiments, the smaller outer diameter of the heat exchange tubes may enable the heat exchange tubes may be positioned within corresponding apertures 202, such that the heat exchange tubes are generally offset (e.g., radially offset) from edges of the tube support bracket 200 defining the apertures 202. In particular, the heat exchange tubes may be positioned coaxially with corresponding apertures 202 (e.g., central axis 148 colinear with the first center 214). In other words, the heat exchange tubes may not directly contact the tube support bracket 200 in an assembled configuration. Thus, during operation of the heat exchanger 180, vibrations induced within the tube support bracket 200 may not be imparted to the heat exchange tubes (e.g., finned tubes 102), and vice versa.

[0053] The tube support brackets 200 may yet support a portion of a weight of the heat exchange tubes (e.g., finned tubes 102) and may facilitate and maintain proper positioning and/or alignment of the heat exchange tubes (e.g., finned tubes 102) within the heat exchanger 180. To this end, the heat exchanger 180 includes one or more gaskets (e.g., damping panels) corresponding to each tube support bracket 200, as described in further detail below. Each gasket may be secured to one of the tube support brackets 200 and may be configured to receive and engage with one of the heat exchange tubes to enable retention of the heat exchange tubes within the internal volume 184 in a desired position.

[0054] With the foregoing in mind, FIG. 8 is a perspective view of an embodiment of a portion of the heat exchanger 180 having multiple tube support brackets 200 (e.g., baffles, baffle plates) arranged within the internal volume 184 of the heat exchanger 180. For clarity, certain components of the heat exchanger 180, such as shell 182, are depicted with hidden or dashed lines to better illustrate internal components, such as the tube support brackets 200 and heat exchange tubes (e.g., finned tubes 102), within the heat exchanger 180. It should be understood that the heat exchanger 180 may include a corresponding heat exchange tube (e.g., finned tube 102) extending through each hole 202 of each tube support bracket 200. As in the illustrated embodiment, the heat exchanger 180 may include multiple tube support brackets 200 (e.g., 4, 5, 6, 7, 8, 9, 10, or more). The tube support brackets 200 may be arrayed within the internal volume 184 of the shell 182 along a length of the shell 182 (e.g., along a longitudinal axis 254 of the heat exchanger 180). For example, the tube support brackets 200 may be spaced apart and/or separated from one another (e.g., from adjacent tube support brackets 200) by a distance 208 apart along the longitudinal axis 254, such as along a length or partial length 210 of the heat exchanger 180. In this way, the multiple tube support brackets 200, in conjunction with the gaskets described below, may support a weight of the heat exchange tubes (e.g., finned tubes 102) and may maintain proper positioning and/or alignment (e.g., reduce sagging and/or bending) of the heat exchange tubes (e g., finned tubes 102) along the length or partial length 210 of the heat exchanger 180. Indeed, the multiple tube support brackets 200 spaced apart from one another may enable more desirable distribution of the weight of the heat exchange tubes. Proper support and positioning of the heat exchange tubes (e.g., finned tubes 102) may extend the useful life of the heat exchange tubes and thus the useful life of the heat exchanger 180.

[0055] It should be understood that, in other embodiments, the tube support brackets 200 may be configured and/or manufactured in alternative geometries, shaped, configurations, and/or arrangements to provide a desired configuration and/or arrangement of the heat exchanger 180 (e.g., heat exchanger tubes, finned tubes 102, tube bundle). For example, in some embodiments, a first tube support bracket may be disposed substantially along a bottom half, with respect to the vertical axis 250, of the heat exchanger 180, with the next consecutive (e.g., second, adjacent) tube support bracket disposed substantially along a top half, with respect to the vertical axis 250, of the heat exchanger 180. Remaining tube support brackets may repeat this alternating arrangement along the length or partial length 210 of the heat exchanger 180. In this way, the tube support brackets 200 may be positioned so as to achieve a desired flow path and/or desired velocity of fluid (e.g., conditioning fluid, cooling fluid, working fluid) within the heat exchanger 180.

[0056] As briefly discussed above, vibrations may be induced in the heat exchange tubes (e.g., finned tubes 102) during operation of the heat exchanger 180. For example, flow-induced eddies of the working fluid (e.g., refrigerant) directed through the shell 182 and across the heat exchange tubes and/or within flow of the fluid (e.g., water, conditioning fluid, cooling fluid) directed through the heat exchange tubes may generate vibrations within the heat exchange tubes. As indicated above, the use of the finned tubes 102 instead of the skipped tubes 100 within the heat exchanger 180 is desirable because the finned tubes 102 do not have the smooth sections 130 and therefore provide an increased heat transfer coefficient, which improves a heat exchange capacity, rate, and/or efficiency of the heat exchanger 180. However, manufacturing the textured surface 150 (e.g., the finned section 142) of the finned tubes 102 along an entirety or substantial entirety of the lengths 141 of the finned tubes 102 may create thinning (e.g., decrease thickness) of the finned tubes 102. Therefore, tube expansion techniques to secure the finned tubes 102 to the tube support brackets 200 to mitigate vibration of the finned tubes 102 may compromise the integrity of the finned tube 102 and may not be suitable. Therefore, embodiments of the present disclosure are directed to a gasket (e.g., gasket blanket, damping panel) configured to be utilized with the tube support brackets 200 (e.g., baffles, baffle plates) to enable securement of the finned tubes 102 within the heat exchanger 180.

[0057] FIG. 9 is a partial perspective view of an embodiment of a portion of the heat exchanger 180, illustrating a gasket 300 coupled to (e.g., interfaced with, aligned with, in secured to) an embodiment of the tube support bracket 200 of the heat exchanger 180. As illustrated, the finned tubes 102 may extend through both the gasket 300 and the tube support bracket 200. The gasket 300 may include a plurality of openings 302 (e.g., gaps, apertures, holes), and each opening 302 may be configured to receive one of the finned tubes 102. Accordingly, each opening 302 may be aligned with a corresponding aperture 202 of the tube support bracket 200. That is, corresponding openings 302 and corresponding apertures 202 may be generally coaxial to enable extension of corresponding finned tubes 102 therethrough.

[0058] As mentioned above, the gasket 300 may be secured to the tube support bracket 200. For example, a first surface 304 of the gasket 300 may abut a second surface 306 of the tube support bracket 200. In some embodiments, a substantial entirety of the first surface 304 may abut a substantial entirety of the second surface 306. In this way, a weight of the finned tubes 102 imparted to the gasket 300 may be adequately or desirably transferred to the tube support bracket 200 and to the shell 182. Additionally, the gasket 300 may include a first shape or geometry 308 (e.g., outer geometry) that corresponds with (e.g., matches) a second shape or geometry 310 (e.g., outer geometry) of the tube support bracket 200. The gasket 300 may be fastened (e.g., coupled, directly coupled, secured, affixed) to the tube support bracket 200 via any suitable technique. For example, rivets 312 may extend through the gasket 300 and the tube support bracket 200 to secure the gasket 300 and the tube support bracket 200 to one another. Additionally or alternatively, the gasket 300 and the tube support bracket 200 may be secured to one another via an adhesive, a molding process, one or more alternative fasteners (e.g., bolts, screws and nuts), another suitable fastening technique, or any combination thereof.

[0059] In some embodiments, the gasket 300 may be formed from an elastic and/or elastomeric material. For example, the gasket 300 may be formed from natural rubber, synthetic rubber, polychloroprene, or another suitable elastomer. The material utilized to form the gasket 300 may be selected based on a desired compatibility with a working fluid (e g., refrigerant) circulated through the heat exchanger 180 (e.g., the shell 182) and directed across the finned tubes 102. Thus, the working fluid may contact the gasket 300, and the gasket 300 may not degrade over time due to contact with the working fluid (e.g., refrigerant) and/or due to exposure to elevated temperatures (e.g., approximately 200 to 300 degrees Fahrenheit) and/or reduced temperatures (e g., approximately 0 to 50 degrees Fahrenheit) within the heat exchanger 180. Furthermore, the gasket 300 may be formed as a single (e.g., continuous) sheet of material. The gasket 300 may be formed to have a thickness 314 of desirable magnitude (e.g., approximately 0.125 inches, 0.25 inches, 0.5 inches) to enable the gasket 300 to adequately absorb vibrations of the finned tubes 102. In addition, in some embodiments, the one or more openings 302 may be formed in the single sheet of material, such as by a cutting or punching manufacturing technique. Additionally or alternatively, the gasket 300 may be formed utilizing a molding process.

[0060] As described in further detail below, the gasket 300 is configured to engage with the finned tubes 102 to retain the finned tubes 102 in a desired position. For example, the gasket 300 (e g., the openings 302) may have dimensions configured to abut and capture the finned tubes 102 extending through the openings 302. As the gasket 300 may be formed from an elastomer or other elastic (e.g., flexible) material, the gasket 300 may not impart forces onto the finned tubes 102 that may affect or alter a structural geometry (e.g., fins 144) of the finned tubes 102. Instead, the material of the gasket 300 may deform to accommodate the finned tubes 102, including physical features of the finned tubes 102, such as the textured surface 150, the fins 144, and so forth. For example, each opening 302 of the gasket 300 may be defined by a respective inner edge 316 of the gasket, and, during installation of the finned tubes 102 within and/or through the openings 302, the inner edge 316 may deform to accommodate, capture, and maintain physical geometries (e.g., fins 144) of the finned tubes 102 within the openings 302 without alteration to the physical geometries. Similarly, during operation of the heat exchanger 180, vibrations induced in the finned tubes 102 may be imparted to and absorbed by the gasket 300, and the physical geometries, (e.g., textured surface 150, fins 144, first thickness 164, second thickness 166) may remain generally unaltered. Accordingly, the finned section 142 of the finned tube 102 may extend within and through the openings 302 of the gasket 300 without compromising the structural integrity of the finned tube 102. In this way, the finned tube 102 may include the finned section 142 formed along substantially an entirety of the length 141 of the finned tube 102 (e.g., without smooth sections for tube expansion within the apertures 202 of the tube support bracket 200) to enable improved heat transfer, as described above. [0061] With the foregoing in mind, FIG. 10 is a schematic of an embodiment of the gasket 300 and the tube support bracket 200 of the heat exchanger 180. As discussed above, the gasket 300 includes the openings 302, which are aligned (e.g., coaxial) with the one or more apertures 202 of the tube support bracket 200, and are configured to receive the finned tubes 102 therethrough. Each opening 302 of the gasket 300 may have a diameter 320 defined by the corresponding inner edge 316 forming the opening 302. The diameter 320 of the openings 302 may be smaller than the diameters 230 of the corresponding apertures 202 of the tube support bracket 200 aligned with the openings 302. For example, the diameter 320 may be approximately 17 mm, 18 mm, 18.4 mm, 18.4 mm to 18.7 mm, 19 mm, or any other suitable dimension.

[0062] In some embodiments, the diameter 320 of the openings 302 may be less (e.g., slightly less) than the outer diameter 172 of the finned tubes 102 (e g., defined by the fins 144), and the diameter 230 of the apertures 202 may be greater than the outer diameter 172 of the finned tubes 102. As a result, the openings 302 of the gasket 300 may enable engagement with the finned tubes 102 via an interference fit. In other words, the finned tubes 102 may extend through the openings 302, and the outer diameters 172 of the finned tubes 102 (e.g., the fins 144) may interface with (e.g., contact, abut, press against) the inner edge 316 forming the opening 302. As the gasket 300 may be formed from an elastomeric material, the inner edge 316 of the gasket 300 may deform to receive, accommodate, and retain the finned tube 102, including the fins 144, without physically altering or degrading the fins 144 and/or outer surface 174 of the finned tube 102. The interference fit established between the finned tube 102 and the gasket 300 may also enable more effective damping of vibrations induced in the finned tubes 102. Moreover, the interference fit may provide an increase in contact (e.g., physical contact) between the finned tubes 102 and the gasket 300 and thereby increase the coefficient of friction (e.g., resistance to relative movement) between the finned tubes 102 and the gasket 300. The smaller relative dimension of the diameter 320 of the openings 302, as well as the flexibility and/or elasticity of the material utilized to form the gasket 300, may facilitate improved (e.g., cheaper, more efficient, faster) assembly of the finned tubes 102 through the tube support brackets 200 within the heat exchanger 180 without imparting undesired forces on the finned tubes 102 (e.g., via unintentional or inadvertent contact between the finned tubes 102 and the tube support bracket 200). Furthermore, as the diameter 230 of the apertures 202 of the tube support bracket 200 may be greater than the outer diameter 172 of the finned tubes 102, the finned tubes 102, including the fins 144, may not physically contact the tube support bracket 200 during assembly and/or in an assembled configuration of the heat exchanger 180 but may nevertheless be desirably retained in the assembled configuration by the gasket 300. In this way, undesired contact between the finned tubes 102 (e.g., formed from metal) and the tube support bracket 200 (e.g., formed from metal) may be avoided, thereby mitigating the potential for wear and degradation on the finned tubes 102 during assembly and/or during operation of the heat exchanger 180.

[0063] In the manner described above, present embodiments enable an increase in heat transfer coefficient of heat exchange tubes and an increase heat exchange capacity and/or efficiency of a heat exchanger including the heat exchange tubes via implementation of a gasket with a tube support bracket. The gasket enables formation of surface enhancements along a greater extent or surface area of the heat exchange tube (e.g., without smooth or bare sections), which provides improved heat transfer, while also enabling desired retention of the heat exchange tubes in a particular arrangement or position within the heat exchanger. Furthermore, the gasket enables reduced wear and degradation on the heat exchange tubes that may otherwise be caused by vibrations induced in the heat exchange tubes during operation of the heat exchanger. In this way, the gasket may also extend the useful or operational life of the heat exchange tubes and the heat exchanger generally. The disclosed techniques also enable improvements to overall cost and efficiency in production of the heat exchangers by enabling simplified manufacturing of the heat exchanger, including the avoidance of tube expansion processes that are typically utilized in conventional designs.

[0064] While only certain features and embodiments of the present disclosure have been illustrated and described, many modifications and changes may occur to those skilled in the art (e g., variations in sizes, dimensions, structures, shapes and proportions of the various elements, values of parameters (e.g., temperatures, pressures, etc., mounting arrangements, use of materials, colors, orientations, etc.) without materially departing from the novel teachings and advantages of the subject matter recited in the claims. The order or sequence of any process or method steps may be varied or re-sequenced according to alternative embodiments. It is, therefore, to be noted that the appended claims are intended to cover all such modifications and changes as fall within the true spirit of the present disclosure.

[0065] Furthermore, in an effort to provide a concise description of the exemplary embodiments, all features of an actual implementation may not have been described (i.e., those unrelated to the presently contemplated best mode of carrying out the present disclosure, or those unrelated to enabling the claimed embodiments). It should be appreciated that in the development of any such actual implementation, as in any engineering or design project, numerous implementation specific decisions may be made. Such a development effort might be complex and time consuming, but would nevertheless be a routine undertaking of design, fabrication, and manufacture for those of ordinary skill having the benefit of this disclosure, without undue experimentation.

[0066] The techniques presented and claimed herein are referenced and applied to material objects and concrete examples of a practical nature that demonstrably improve the present technical field and, as such, are not abstract, intangible or purely theoretical. Further, if any claims appended to the end of this specification contain one or more elements designated as “means for [perform]ing [a function], . or “step for [perform]ing [a function]...”, it is intended that such elements are to be interpreted under 35 U.S.C. 112(f). However, for any claims containing elements designated in any other manner, it is intended that such elements are not to be interpreted under 35 U.S.C. 112(f).

Claims

CLAIMS:

1. A heat exchanger for a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system, comprising: a plurality of heat exchange tubes; a tube support bracket comprising a plurality of apertures; and a gasket coupled to the tube support bracket, wherein the gasket comprises a plurality of openings, and each opening of the plurality of openings is aligned with a corresponding aperture of the plurality of apertures.

2. The heat exchanger of claim 1, wherein each heat exchange tube of the plurality of heat exchange tubes extends through a respective opening of the plurality of openings and through the corresponding aperture of the plurality of apertures.

3. The heat exchanger of claim 2, wherein each opening of the plurality of openings comprises a first diameter, each aperture of the plurality of apertures comprises a second diameter, and the first diameter is less than the second diameter.

4. The heat exchanger of claim 3, wherein the gasket is configured to engage with each heat exchange tube of the plurality of heat exchange tubes to retain each heat exchange tube of the plurality of heat exchange tubes within the respective opening of the plurality of openings and within the corresponding aperture of the plurality of apertures via an interference fit between the gasket and the heat exchange tube.

5. The heat exchanger of claim 1, wherein the gasket comprises a synthetic rubber material.

6. The heat exchanger of claim 1, wherein the gasket is coupled to the tube support bracket via one or more rivets.

7. The heat exchanger of claim 1, wherein the gasket comprises a first outer geometry and the tube support bracket comprises a second outer geometry corresponding to the first outer geometry.

8. The heat exchanger of claim 1, wherein each heat exchange tube of the plurality of heat exchange tubes comprises a surface enhancement formed in an outer surface of the heat exchange tube.

9. The heat exchanger of claim 8, wherein each heat exchange tube of the plurality of heat exchange tubes extends through a respective opening of the plurality of openings and through the corresponding aperture of the plurality of apertures, and the respective surface enhancement of each heat exchange tube of the plurality of heat exchange tubes extends through the respective opening of the plurality of openings and through the corresponding aperture of the plurality of apertures.

10. The heat exchanger of claim 9, wherein the surface enhancement comprises a plurality of fins formed in the outer surface of the heat exchange tube.

11. A heat exchanger for a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system, comprising: a shell defining an internal volume configured to receive a first fluid; a plurality of tubes disposed within the internal volume of the shell, wherein the plurality of tubes is configured to circulate a second fluid therethrough to place the second fluid in a heat exchange relationship with the first fluid; a tube support bracket disposed within the internal volume of the shell, wherein the tube support bracket comprises a plurality of apertures formed therein; and a gasket coupled to the tube support bracket, wherein the gasket comprises a plurality of openings formed therein, wherein a tube of the plurality of tubes extends through an aperture of the plurality of apertures and through an opening of the plurality of openings corresponding to the aperture.

12. The heat exchanger of claim 11, wherein the aperture comprises a first inner diameter, the opening comprises a second inner diameter, and the second inner diameter is less than the first inner diameter.

13. The heat exchanger of claim 12, wherein the gasket comprises an inner edge defining the opening, and the tube is engaged with the inner edge via an interference fit.

14. The heat exchanger of claim 11, wherein the tube comprises a textured outer surface formed along a length of the tube, and the textured outer surface is disposed within the aperture and within the opening.

15. The heat exchanger of claim 11, wherein the gasket comprises an elastomer, and the tube support bracket comprises a metal.

16. The heat exchanger of claim 15, wherein the gasket is coupled to the tube support bracket via an adhesive.

17. A heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system, comprising: a plurality of heat exchange tubes configured to circulate a fluid therethrough; a tube support bracket comprising a plurality of apertures; and a damping panel affixed to a surface of the tube support bracket, wherein the damping panel comprises a plurality of openings, and each opening of the plurality of openings is aligned with a corresponding aperture of the plurality of apertures, and wherein each heat exchange tube of the plurality of heat exchange tubes is configured to extend through a respective opening of the plurality of openings and through a corresponding aperture of the plurality of apertures aligned with the respective opening.

18. The HVAC&R system of claim 17, wherein each heat exchange tube of the plurality of heat exchange tubes comprises an outer diameter, each aperture of the plurality of apertures comprises a first inner diameter, each opening of the plurality of openings comprises a second inner diameter, the second inner diameter is less than the outer diameter, and the first inner diameter is greater than the outer diameter.

19. The HVAC&R system of claim 18, wherein the damping panel is formed from an elastomeric material.

20. The HVAC&R system of claim 17, wherein each heat exchange tube of the plurality of heat exchange tubes comprises a plurality of fins formed in an outer surface of the heat exchange tube, and the plurality of fins extends through the respective opening of the plurality of openings and through the corresponding aperture of the plurality of apertures.