CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims priority from and the benefit of U.S. Provisional Application No. 63/397,244, entitled “HEAT EXCHANGER FOR HVAC&R SYSTEM,” filed August 11, 2022, which is herein 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] Chiller systems, or vapor compression systems, 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 chiller system. The chiller system may place the working fluid in a heat exchange relationship with a conditioning fluid (e.g., water) and may deliver the conditioning fluid to conditioning equipment and/or a conditioned environment serviced by the chiller system. For example, the chiller system may include a heat exchanger configured to receive the working fluid and the conditioning fluid to place the working fluid in the heat exchange relationship with the conditioning fluid. The conditioning fluid may be directed from the heat exchanger to other equipment, such as air handlers, to condition other fluids, such as air in a building. The working fluid may be directed from the heat exchanger through other components of the chiller system, such as a compressor and/or a condenser, configured to process (e.g., pressurize, cool) the working fluid to enable the working fluid to provide further conditioning of the conditioning fluid. Unfortunately, in some embodiments, the working fluid may not efficiently flow through the heat exchanger. For this reason, the chiller system may not efficiently operate to condition the conditioning fluid via the working fluid.

SUMMARY

[0004] 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.

[0005] In one embodiment, a heat exchanger includes a first section of an interior volume of the heat exchanger. The first section includes a plurality of heat exchanger tubes and is configured to direct a working fluid flow across the plurality of heat exchanger tubes from an inlet of the heat exchanger. The heat exchanger includes a second section of the interior volume, where the second section is configured to direct the working fluid to an outlet of the heat exchanger. The outlet includes a center axis extending therethrough. The second section overlaps with the center axis and the first section is offset from the center axis.

[0006] In another embodiment, a heat exchanger of a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system includes a shell having an interior volume. The shell also includes an inlet configured to direct working fluid into the interior volume and a discharge outlet configured to discharge the working fluid from the interior volume. The discharge outlet includes a center axis. The heat exchanger includes a first set of tubes disposed within the interior volume and configured to circulate a conditioning fluid therethrough to exchange heat with the working fluid directed across the first set of tubes, where the first set of tubes is offset from the center axis. The heat exchanger includes a second set of tubes disposed within the interior volume and configured to circulate the conditioning fluid therethrough to exchange heat with the working fluid directed across the second set of tubes, where the second set of tubes is offset from the center axis. The heat exchanger includes a discharge column extending between the first set of tubes and the second set of tubes, where the discharge column overlaps with the center axis and is configured to direct the working fluid toward the discharge outlet.

[0007] In another embodiment, a heat exchanger of a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system includes a shell defining an interior volume. The shell includes an inlet and an outlet, and the outlet includes a center axis. The heat exchanger includes a plurality of partitions disposed within the shell to define a first section of the interior volume and a second section of the interior volume. The first section is offset from the center axis, the second section overlaps with the center axis, and the first section includes a plurality of heat exchanger tubes disposed therein. The first section is configured to direct a flow of working fluid across the plurality of heat exchanger tubes and the second section is configured to direct the flow of working fluid to the outlet to discharge the flow of working fluid from the interior volume of the heat exchanger.

DRAWINGS

[0008] Various aspects of this disclosure may be better understood upon reading the following detailed description and upon reference to the drawings in which:

[0009] FIG. 1 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;

[0010] FIG. 2 is a perspective view of an embodiment of a vapor compression system, in accordance with an aspect of the present disclosure; [0011] FIG. 3 is a schematic of an embodiment of the vapor compression system of FIG. 2, in accordance with an aspect of the present disclosure;

[0012] FIG. 4 is a schematic of an embodiment of the vapor compression system of FIG. 2, in accordance with an aspect of the present disclosure;

[0013] FIG. 5 is a partial perspective axial cross-sectional view of an embodiment of a heat exchanger of a vapor compression system, in accordance with an aspect of the present disclosure; and

[0014] FIG. 6 is an axial cross-sectional view of an embodiment of a heat exchanger of a vapor compression system, in accordance with an aspect of the present disclosure.

DETAILED DESCRIPTION

[0015] 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.

[0016] 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.

[0017] As used herein, the terms “approximately,” “generally,” “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 convey 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 convey 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. Mathematical terms, such as “parallel” and “perpendicular,” should not be rigidly interpreted in a strict mathematical sense, but should instead be interpreted as one of ordinary skill in the art would interpret such terms. For example, one of ordinary skill in the art would understand that two lines that are substantially parallel to each other are parallel to a substantial degree, but may have minor deviation from exactly parallel.

[0018] Embodiments of the present disclosure relate to a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system, such as a chiller, having a vapor compression system with a heat exchanger. The vapor compression system (e.g., a vapor compression circuit) may circulate a working fluid (e.g., a heat transfer fluid, 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 to condition a space and/or a component serviced by the HVAC&R system. Tn some embodiments, the heat exchanger may be an evaporator configured to place the working fluid in a heat exchange relationship with the conditioning fluid to enable heat transfer between the working fluid and the conditioning fluid in order to condition the conditioning fluid, such as to reduce a temperature of the conditioning fluid.

[0019] The heat exchanger may define an internal volume configured to receive the working fluid from another component of the vapor compression system, such as a condenser configured to cool the working fluid. The heat exchanger may also be configured to direct the conditioning fluid through the internal volume, such as through tubes positioned within the internal volume. The working fluid may be directed across the tubes, and heat may be transferred between the working fluid directed across the tubes and the conditioning fluid directed through the tubes. The heat exchange may cause a portion of the working fluid to vaporize. The heat exchanger may also include an outlet, such as a suction outlet, configured to discharge the working fluid (e.g., vapor working fluid) from the internal volume, out of the heat exchanger, and toward a different component of the vapor compression system, such as a compressor. In this manner, the working fluid may flow along a flow path that extends across the tubes and toward the outlet. Unfortunately, in certain existing heat exchangers, the working fluid may not efficiently flow along the flow path and toward the outlet. As an example, the direction of flow of the working fluid along the flow path may change, which may cause increased pressure drop of the working fluid. As a result, the flow rate of the vapor working fluid through the heat exchanger toward the outlet may be reduced. As such, the working fluid may not flow desirably through the vapor compression system, and operation of the vapor compression system may be inefficient.

[0020] Thus, it is now recognized that reducing a pressure drop of the working fluid directed along the flow path of a heat exchanger may improve operation of the vapor compression system. Accordingly, the present disclosure is directed to a heat exchanger arranged to provide an improved (e.g., more direct, less obstructed) flow path of the vapor working fluid toward an outlet of the heat exchanger. Tn some embodiments, the outlet may include a center axis (e.g., central axis), and the heat exchanger may include inlet sections (e.g., falling film sections) that are offset from the center axis. The inlet sections may include first tubes through which the conditioning fluid may be directed. Working fluid (e.g., liquid working fluid) may be directed into the heat exchanger and across the first tubes to enable the working fluid to exchange heat with the conditioning fluid directed through the first tubes. The working fluid may flow from the inlet sections to an intermediate section (e.g., a flooded section) of the heat exchanger. The intermediate section may include second tubes through which the conditioning fluid may be directed. The second tubes may be submerged in the liquid working fluid in the intermediate section to enable the working fluid to exchange heat with the conditioning fluid directed through the second tubes. The working fluid may also be directed from the intermediate section to an outlet section (e.g., a suction section) of the heat exchanger to flow toward an opening (e.g., an outlet opening, suction outlet) for discharge from the heat exchanger. In embodiments disclosed herein, the intermediate section and the outlet section may overlap with the center axis (e.g., be at least partially aligned along the center axis).

[0021] The overlap between the intermediate section and the outlet section (e.g., alignment along the center axis), as well as the offset of the inlet sections from the center axis, may provide a more direct flow path for the working fluid from the intermediate section, to the outlet section, and to the opening to enable improved discharge of the working fluid from the heat exchanger. For example, the flow path to the opening may be associated with a reduced flow resistance as compared to the flow resistance for working fluid along flow paths of existing heat exchangers (e.g., a heat exchanger in which the inlet section may overlap with the center axis of the opening) to enable the working fluid to flow more readily toward the opening of the outlet. Thus, the working fluid flow, such as a flow rate of the working fluid, through the heat exchanger and the vapor compression system may be more desirable (e.g., with reduced pressure drop, more efficient), and operation of the vapor compression system may be improved. Additionally or alternatively, the more efficient flow of the working fluid through the vapor compression system provided by the heat exchanger configurations disclosed herein may enable a reduced total amount of the working fluid to be implemented for circulation through the vapor compression system, thereby reducing a cost associated with manufacture and/or operation of the vapor compression system.

[0022] 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 a typical 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 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.

[0023] FIGS. 2 and 3 are 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 (e.g., a heat transfer fluid, a refrigerant) through a circuit starting with a compressor 32. The 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.

[0024] 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” refrigerants like ammonia (NH3), R-717, carbon dioxide (CO2), R-744, or hydrocarbon based refrigerants, water vapor, or any other suitable refrigerant. 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.

[0025] 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.

[0026] 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 or 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. [0027] The liquid working fluid delivered to the evaporator 38 may absorb heat from a conditioning fluid, which may or may not be the same 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 conditioning 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.

[0028] FIG. 4 is a schematic 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. [0029] Additionally, the intermediate vessel 70 may provide for further expansion of the liquid working fluid because of 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 due to 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.

[0030] It should be appreciated that any of the features described herein may be incorporated with the vapor compression system 14 or any other suitable HVAC&R systems. For example, the present techniques may be incorporated with any HVAC&R system having an economizer, such as the intermediate vessel 70, and a compressor, such as the compressor 32. The discussion below describes the present techniques incorporated with embodiments of the compressor 32 configured as a single stage compressor. However, it should be noted that the systems and methods described herein may be incorporated with other embodiments of the compressor 32 and HVAC&R system 10.

[0031] With the foregoing in mind, FIG. 5 is a partial perspective axial cross- sectional view of an embodiment of a heat exchanger 100. For example, the heat exchanger 100 may be representative of the evaporator 38, taken along line 5-5. The heat exchanger 100 includes a shell 101 (e.g., an enclosure) that defines an interior volume 102 through which a working fluid and a conditioning fluid may flow. For example, the heat exchanger 100 may include tubes 104 (e g., heat exchanger tubes, tube bundle) configured to direct the conditioning fluid through the interior volume 102. The heat exchanger 100 may also include inlets 106 (e.g., one or more inlets) configured to direct the working fluid into the interior volume 102. For example, the inlets 106 may include one or more sprayers, nozzles, and/or headers that may output liquid working fluid onto first tubes 104A (e.g., first tube bundle) within the interior volume 102. The inlets 106 and the first tubes 104A may be positioned at respective first sections 108 of the interior volume 102. That is, each first section 108 may include a respective set of the first tubes 104A (e.g., respective set or portion of a first tube bundle of the first tubes 104 A). The first sections 108 may include, for instance, falling film sections, where the liquid working fluid may flow across the first tubes 104A via a gravitational force (e.g., generally along a first direction 1 18, such as a direction of gravity) and may exchange heat with the conditioning fluid that may be directed through the first tubes 104A.

[0032] In some embodiments, the heat exchanger 100 may include a distributor plate 110 (e.g., one or more distributor plates, a respective distributor plate associated with each first section 108), such as a perforated plate, that may facilitate distribution of the working fluid received via the inlets 106 across the first tubes 104A. Thus, the distributor plate 110 may increase a quantity of the first tubes 104A across which the working fluid may flow to increase a surface area (e.g., heat transfer surface area) of contact between the working fluid and the first tubes 104 A, thereby enabling greater heat exchange between the working fluid and the conditioning fluid via the first tubes 104A. In the illustrated embodiment, the inlets 106 are oriented obliquely relative to a first axis 112 (e.g., a vertical axis, an axis extending generally along the first direction 118). In additional or alternative embodiments, the inlets 106 may be oriented generally parallel to the first axis 112 (e.g., the inlets 106 may be configured to discharge working fluid generally along the first direction 118).

[0033] In some embodiments, the first tubes 104A of the first section 108 may include multiple passes. For example, the conditioning fluid may be directed through a first pass 114 (e g., first tube bundle) of the first tubes 104A and from the first pass 1 14 of the first tubes 104A through a second pass 116 (e.g., second tube bundle) of the first tubes 104A. The working fluid may flow across the first pass 114 of the first tubes 104A and across the second pass 116 of the first tubes 104A. For instance, the working fluid may generally flow in the first direction 118 (e.g., a downward direction along the first axis 112) from the first pass 114 toward the second pass 116, such as via a gravitational force. The conditioning fluid may exchange heat with the working fluid at the first pass 114, and the conditioning fluid may further exchange heat with the working fluid at the second pass 116. Thus, the second pass 116 may enable further conditioning of the conditioning fluid via the working fluid. The first pass 114 may be offset from the second pass 116 by a distance to provide a gap 119 (e.g., a space) between the first pass 1 14 and the second pass 116. The gap 1 19 may block heat transfer between the conditioning fluid flow directed through the first pass 114 and the conditioning fluid flow directed through the second pass 116, thereby enabling more desirable heat exchange (e.g., initial heat exchange) between the conditioning fluid and the working fluid at the first pass 114 and more desirable heat exchange (e.g., additional heat exchange) between the conditioning fluid and the working fluid at the second pass 116.

[0034] The working fluid may also flow from the first sections 108 (e.g., the second pass 116) in the first direction 118 toward a second section 120 (e.g., an intermediate section) of the interior volume 102. The second section 120 may include second tubes 104B (e.g., a third tube bundle, additional set of tubes) configured to direct the conditioning fluid through the interior volume 102. The working fluid may flow across the second tubes 104B to exchange heat with the conditioning fluid directed through the second tubes 104B. Heat exchange between the working fluid and the conditioning fluid may vaporize a portion of the working fluid. The vapor working fluid may be directed from the second section 120 to a third section 122 of the interior volume 102 for discharge from the heat exchanger 100. As such, the second section 120 may be configured to direct working fluid from the first sections 108 to the third section 122.

[0035] For example, the heat exchanger 100 may include an opening or outlet 124 (e.g., a discharge opening, a discharge outlet) formed through the shell 101. The third section 122 may be void (e.g., partially void, completely void) of any heat exchanger tubes (e.g., tubes 104) and may direct vapor working fluid toward the opening 124 in a second direction 126, opposite the first direction 118, to exit the heat exchanger 100. For instance, a pipe 127 (e.g., a suction pipe, outlet conduit) may be fluidly coupled to the opening 124 and may be configured to receive the working fluid directed through the opening 124. In some embodiments, the pipe 127 may be fluidly coupled to a compressor (e.g., the compressor 32), and the compressor may provide a suction pressure or suction force that urges flow of the vapor working fluid within the interior volume 102 through the opening 124, into the pipe 127, and toward the compressor.

[0036] In some embodiments, the second section 120 may include a flooded section in which the second tubes 104B may remain at least partially submerged within liquid working fluid. That is, liquid working fluid that is not vaporized by heat exchange with the conditioning fluid via the first tubes 104A and/or second tubes 104B may remain in the second section 120 and remain in contact with the second tubes 104B to exchange heat with the conditioning fluid directed through the second tubes 104B. Thus, the working fluid may continually condition the conditioning fluid while in the second section 120, such as until the working fluid is vaporized and is directed toward the opening 124 for discharge from the heat exchanger 100. In some embodiments, the heat exchanger 100 may be configured to retain a level of liquid working fluid in the second section 120 that is sufficient to submerge each of the second tubes 104B within the liquid working fluid. In other embodiments, the heat exchanger 100 may be configured such that a first subset of the second tubes 104B is submerged within the liquid working fluid and a second subset of the second tubes 104B protrudes above (e.g., extends out of, resides above) the liquid working fluid contained within the second section 120.

[0037] The heat exchanger 100 may include partitions 128 (e.g., a plurality of partitions, plates, barriers) extending at least partially along the first axis 112 and positioned between the first sections 108 and the third section 122. Tn some embodiments, the partitions 128 may extend within the interior volume 102 along a length (e.g., a longitudinal length, an entire longitudinal length) of the shell 101 (e.g., the interior volume 102), such as from a first longitudinal end of the shell 101 to a second, opposite longitudinal end of the shell 101. The partitions 128 may block flow of working fluid from the first sections 108 directly to the third section 122 (e.g., without flowing through the second section 120, such as across the second tubes 104B). Thus, the partitions 128 may increase an amount or level of the working fluid in the second section 120 to enable increased heat exchange with the conditioning fluid directed through the second tubes 104B. For example, the partitions 128 may extend past the first tubes 104A (e.g., past the second pass 116 of the first tubes 104A, in the first direction 118) toward the second section 120 to force the working fluid to flow at least partially through the second section 120, such as in a third flow direction 132 around ends 130 (e.g., distal ends, lower ends) of the partitions 128, and into the third section 122. The partitions 128 may also block flow of the working fluid from the third section 122 to the first sections 108, thereby directing and/or causing the working fluid to flow through the opening 124. In this manner, the partitions 128 may define a discharge column 133 (e g., suction column) extending from the second section 120 to the opening 124 and between the first tubes 104A (e g., first sections 108, respective sets of first tubes of first sections 108) positioned at opposite sides of the discharge column 133. Accordingly, the discharge column 133 is configured to direct the working fluid along the first axis 112 from the second section 120 and between the first tubes 104A (e.g., first sections 108) toward the opening 124. In some embodiments, the discharge column 133 may thus form a portion of the third section 122 of the interior volume 102 of the heat exchanger 100. As such, it should be understood that the discharge column 133 (e.g., at least a portion of the third section 122) may be defined by and/or between the partitions 128.

[0038J Each of the first tubes 104A and the second tubes 104B may be arranged in a manner that accommodates a contour of a perimeter of the shell 101. For example, in the illustrated embodiment, the shell 101 has a generally circular geometry. Therefore, the first tubes 104A and the second tubes 104B may be positioned generally along (e.g., adjacent) a curved contour 135 of the shell 101, such as more adjacent to an inner surface 134 of the shell 101. Positioning of the tubes 104 along the inner surface 134 of the shell 101 may enable more compact positioning of the tubes 104, thereby improving efficient usage of space within the interior volume 102 by the tubes 104 and enabling an increased quantity of the tubes 104 to be positioned in the first sections 108 and/or in the second section 120 of the heat exchanger 100. The increased quantity of the tubes 104 may increase efficiency of heat exchange between the working fluid and the conditioning fluid. Additionally or alternatively, a desirable quantity of the tubes 104 may be positioned in a smaller volume, thereby enabling implementation of a smaller shell 101, which may reduce manufacturing costs, such as by reducing an amount of working fluid implemented to circulate through the heat exchanger 100 and/or by reducing an amount of material used to fabricate the shell 101.

[0039] In some embodiments, there may be a greater total quantity of the first tubes 104A in the first sections 108 relative to the quantity of the second tubes 104B in the second section 120. For example, the ratio of the quantity of the first tubes 104A in the first sections 108 to the quantity of the second tubes 104B in the second section 120 may be approximately 3:2. In alternative embodiments, there may be a greater quantity of the second tubes 104B in the second section 120 relative to the total quantity of the first tubes 104A in the first sections 108. As an example, the quantity of the first tubes 104A in the first sections 108 and the quantity of the second tubes 104B in the second section 120 may be based on a manufacture specification associated with the heat exchanger 100, such as a total amount of working fluid to be circulated through an HVAC&R system utilizing the heat exchanger 100. For instance, a greater quantity of the second tubes 104B may be implemented in the second section 120 for HVAC&R systems utilizing a greater amount of working fluid, because a greater amount of working fluid may be available to remain in the second section 120 (e.g., for submergence of the second tubes 104B). Additionally or alternatively, the quantity of the first tubes 104A in the first sections 108 and/or the quantity of the second tubes 104B in the second section 120 may be based on a target performance of the heat exchanger 100, such as an efficiency of the heat exchanger 100 to condition the conditioning fluid via the first tubes 104A as compared to via the second tubes 104B. [0040] In the illustrated embodiment, the opening 124 includes and/or defines a center axis 136 (e.g., central axis) extending through a center (e.g., centroid) of the opening 124 along the first axis 112. In some embodiments, the center axis 136 may bisect the shell 101 at opposing ends of the shell 101. That is, the center axis 136 may extend generally along a diametric dimension of the shell 101 (e.g., in embodiments where the shell 101 includes a generally cylindrical geometry). Each of the second section 120 and the third section 122 may overlap with the center axis 136 (e.g., be at least partially aligned with and/or along the center axis 136), and each of the first sections 108 may be offset from the center axis 136 (e.g., not overlap with the center axis 136) Thus, the third section 122 may extend directly (e.g., linearly) from the opening 124 to the second section 120 to facilitate improved flow of the working fluid from the second section 120 to the opening 124 via the third section 122. That is, the working fluid may flow more readily and/or desirably, such as at an increased flow rate and/or with a reduced pressure drop, to the opening 124 for discharge from the heat exchanger 100.

[0041] For this reason, the heat exchanger 100 may operate more efficiently, such as to circulate the working fluid through the heat exchanger 100 and/or the HVAC&R system and/or to condition the conditioning fluid via the working fluid. Additionally or alternatively, the improved flow of the working fluid may enable another component of an HVAC&R system having the heat exchanger 100 to operate more efficiently. For example, the increased and/or improved flow of working fluid through the opening 124 to a compressor may enable the compressor to operate at a reduced capacity, stage, or speed to draw a sufficient flow rate (e.g., amount) of the working fluid from the heat exchanger 100, thereby reducing a cost associated with operation of the compressor. As a further example, the increased flow of the working fluid through the heat exchanger 100 may increase and/or improve circulation of the working fluid through an HVAC&R system having the heat exchanger 100. As such, a reduced amount of working fluid may be implemented to enable desirable operation of the HVAC&R system, such as operation of the heat exchanger 100 to condition the conditioning fluid via the working fluid. Therefore, a cost associated with implementation of the working fluid may be reduced. [0042] The offset arrangement of the first sections 108 from the center axis 136 may also guide and/or force the working fluid to flow from the first sections 108, through the second section 120, and to the third section 122 to exit the heat exchanger 100. In this way, the working fluid may be forced across the second tubes 104B, such as for submersion of the second tubes 104B within the working fluid. As such, the offset arrangement of the first sections 108 from the center axis 136 may enable more efficient operation of the second tubes 104B to condition the conditioning fluid.

[0043] The first sections 108 may be symmetrical about the center axis 136 in some embodiments. In alternative embodiments, the first sections 108 may be asymmetrical about the center axis 136. As an example, the first sections 108 may have a different number of first tubes 104A. As another example, the first sections 108 may have differently sized volumes. In further embodiments, the heat exchanger 100 may have a different number of first sections 108, such as a single first section 108 that is offset from the center axis 136.

[0044] Baffles or guides 138 (e.g., carryover baffles, diverter plates) may be coupled to the partitions 128, and each baffle 138 may extend from a corresponding partition 128 (e g., one of the partitions 128) into the third section 122, such as across the center axis 136. The baffles 138 may provide a desired amount flow resistance to the working fluid flowing through the third section 122. For example, the baffles 138 may reduce a pressure and/or velocity of the working fluid to reduce energy (e.g., kinetic energy) of the working fluid. The reduction of energy may cause condensation of a portion of the working fluid, which may result in removal of moisture from the working fluid flowing toward the opening 124. Similarly, the baffles 138 may cause moisture or fluid entrained in the vapor working fluid to impinge against the baffles 138 and flow toward the second section 120 (e.g., in the first direction 118). Thus, the baffles 138 may reduce an amount of moisture contained or entrained within the working fluid exiting the heat exchanger 100. Reducing the moisture content of the working fluid may enable desirable operation of equipment downstream of the heat exchanger 100, such as a compressor configured to receive and pressurize the working fluid discharged by the heat exchanger 100. As such, the baffles 138 may further improve operation of an HVAC&R system having the heat exchanger 100.

[0045] One or more of the baffles 138 may be angled obliquely relative to a second axis 140 (e.g., a horizontal axis, a lateral axis), such as toward the opening 124. That is, in some embodiments, the baffles 138 may be oriented such that respective first end portions 141 (e.g., base end portions) of the baffles 138 coupled to the partitions 128 are positioned beneath (e.g., relative to and/or along the first axis 112, with respect to a direction of gravity) respective second end portions 143 (e.g., distal end portions) of the baffles 138. To this end, the baffles 138 may extend from the partitions 128 at least partially toward the opening 124 (e.g., from the first end portion 141 to the second end portion 143). Thus, the baffles 138 may guide the working fluid flow through the third section 122 toward the opening 124. In some embodiments, the second end portions 143 of some of or all of the baffles 138 may overlap with one another along the second axis 140.

[0046] By way of example, as further described below, the working fluid may flow in a serpentine, winding, or zigzag path through the third section 122 and around the baffles 138 toward the opening 124. One or more of the baffles 138 may also receive (e.g., collect, retain) moisture removed from the working fluid as the working fluid flows through the third section 122. For example, in some embodiments, the compressor 32 may draw (e.g., via the pipe 127) a flow of working fluid 145 along the third section 122 in the second direction 126, such that the working fluid 145 may flow around the baffles 138 in the serpentine, winding, or zigzag path. The working fluid 145 may be in a generally gaseous (e.g., vapor) state and, in some embodiments, may include liquid droplets 147 (e.g., liquid working fluid) suspended therein. Flow of the working fluid 145 around the baffles 138 may cause the liquid droplets 147 to condense or otherwise collect on upper surfaces 149 of the baffles 138, on lower surfaces 151 of the baffles 138, or both. [0047] The angled orientation of the baffles 138 may guide the condensed liquid working fluid (e.g., the liquid droplets 147) received by the baffles 138 toward the second section 120. For instance, based on the orientation of the baffles 138 within the heat exchanger 100 (e.g., an angled orientation, a sloped orientation), a gravitational force may drive movement of liquid working fluid (e.g., the liquid droplets 147) along the baffles 138 (e.g., along the upper surfaces 149, along the lower surfaces 151, or both) toward a corresponding partition 128 to which the baffles 138 may be coupled. Each baffle 138 may also include one or more slots 142 (e g., apertures, openings, passages), which may be formed in the baffle 138, such as adjacent to the corresponding partition 128 to which the baffle 138 is attached. The slots 142 may enable the liquid working fluid (e g., the liquid droplets 147) that may be accumulated on the upper surfaces 149 to flow through the baffle 138 and toward the second section 120. In other words, moisture removed from the vapor working fluid may flow along the baffle 138, through the slots 142, and to the second section 120. Thus, the slots 142 may facilitate an increase in the amount of working fluid in the second section 120, such as the amount of liquid working fluid in which the second tubes 104B may be submerged.

[0048] In additional or alternative embodiments, different features may be incorporated to direct the working fluid through the third section 122 and reduce moisture contained within the working fluid (e.g., vapor working fluid) directed out of the heat exchanger 100. As an example, a different arrangement of the baffles 138, such as different arrangements and/or configurations in which the baffles 138 may extend from the partitions 128, may be implemented. As another example, a different component, such as a mesh, may be utilized in the third section 122. As a further example, the partitions 128 may have a different (e.g., non-linear, curved, serpentine) shape that provides an amount flow resistance to the working fluid to reduce the energy of the working fluid and cause the working fluid to release moisture during flow through the third section 122. [0049] FIG. 6 is an axial cross-sectional view of an embodiment of the heat exchanger 100. In the illustrated embodiment, the inlets 106 are coupled to the inner surface 134 of the shell 101 and are oriented generally parallel to the first axis 112 to output the working fluid (e.g., liquid working fluid) onto the first tubes 104A (e.g., in the first direction 118). To this end, the inlets 106 may direct the working fluid along a flow path 160 through the interior volume 102 of the heat exchanger 100. For example, as discussed above, the flow path 160 may generally extend in the first direction 118 from the inlets 106, across the first tubes 104 A, and toward the second tubes 104B in the second section 120. Additionally, the flow path 160 may extend in the second direction 126 from the second section 120 toward the third section 122.

[0050] As discussed above, the baffles 138 may extend into the third section 122 to form a serpentine flow path 161 in the third section 122. Thus, the baffles 138 may modify flow (e.g., linear flow) of working fluid from the second section 120, directly through the third section 122, and to the opening 124. For example, the working fluid may flow in curved directions 162 around the baffles 138 (e.g., along the serpentine flow path 161) to flow through the third section 122 to the opening 124. Flow of the working fluid in the curved directions 162 may reduce energy (e.g., kinetic energy) of the working fluid and cause a portion of the working fluid to condense, thereby enabling removal of moisture (e.g., liquid working fluid) from the working fluid and blocking entrainment of the moisture within the vapor working fluid discharged through the opening 124 (e.g., toward a compressor, such as the compressor 32).

[0051] In the illustrated embodiment, the heat exchanger 100 includes three baffles 138. However, the heat exchanger 100 may include any suitable number of baffles 138, such as one baffle 138, two baffles 138, or more than three baffles 138, in additional or alternative embodiments. Each baffle 138 may include a flange 164, which may be mounted, attached, coupled, and/or secured to one of the partitions 128 to secure the baffle 138 within the third section 122. For example, a fastener, an adhesive, a weld, a punch, an interference fit, or any other feature may couple the flange 164 directly to the partition 128. Additionally, each baffle 138 may include a guide flange 166 extending crosswise from the corresponding flange 164 and into the third section 122 in an installed configuration of the baffle 138. Extension of the guide flanges 166 into the third section 122 may force the working fluid to flow in the curved directions 162 around the guide flanges 166 to flow toward the opening 124.

[0052] As an example, one or more guide flanges 166 of the baffles 138 may overlap with one another and/or with the center axis 136. As such, the baffles 138 may include overlapping portions 167, where second end portions 143 of the baffles 138 overlap with one another along the second axis 140. To this end, the guide flanges 166 may block a direct or linear flow of the working fluid from the second section 102, through the third section 122, and to the opening 124. Indeed, the guide flanges 166 may extend obliquely toward the opening 124 to guide the working fluid flow toward the opening 124. For example, each guide flange 166 may form an angle 169 between 45 degrees and 75 degrees with respect to the corresponding flange 164 and the corresponding partition 128 in the installed configuration. In some embodiments, the center axis 136 may extend through (e.g., overlap with) the overlapping portions 167.

[0053] Additionally, such orientation of the guide flanges 166 may guide moisture toward the second section 120. For example, the slots 142 may be formed at an interface 168 (e.g., a bend) between the flange 164 and the guide flange 166 of each baffle 138. The guide flanges 166 may receive moisture released from the working fluid as the working fluid flows (e.g., in the curved directions 162) through the third section 122, and the moisture may flow along the guide flanges 166, such as via a gravitational force, to the slots 142. The slots 142 may enable flow of the moisture through the baffle 138 to the second section 120. Similarly, the partitions 128 and/or the flanges 164 of the baffle 138 may receive moisture and guide the moisture toward the slots 142 to flow to the second section 120. Thus, the slots 142 may facilitate directing moisture removed from the working fluid at various portions of the third section 122 to flow toward the second section 120. [0054] The partitions 128 may generally extend along the first axis 112 and along the first tubes 104A of the first sections 108. The partitions 128 may also extend outwardly, such as away from the center axis 136, between the first tubes 104A and the opening 124. That is, the partitions 128 may include flared portions 171 that taper or flare outward (e.g., radially outward) along the second direction 126 to increase a cross-sectional area of the third section 122 at an outlet portion 170 of the third section 122 adjacent to the opening 124. The increased cross-sectional area at the outlet portion 170 may diffuse the working fluid flow and reduce a velocity of the working fluid flow adjacent to the opening 124. The reduced velocity of the working fluid flow adjacent to the opening 124 may mitigate pressure drop (e.g., caused by frictional forces) of the working fluid flow into the opening 124. Thus, the working fluid may flow more readily into the opening 124. For instance, the flared portions 171 of the outlet portion 170 may reduce the velocity and/or pressure of the working fluid flowing into the opening 124 to facilitate flow of the working fluid through the opening 124 at a desirable flow rate. Therefore, the tapering of the partitions 128 at the outlet portion 170 may further facilitate flow of the working fluid through the opening 124.

[0055] 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 resequenced 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.

[0056] 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.

[0057] 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).