Fluid dispenser for priming balance

Abstract

Described herein is an evaporator for a refrigeration system comprising an evaporator shell configured to house a set of tubes, and one or more support structures arranged within the evaporator shell to support the set of tubes, the one or more support structures configured to inhibit mixing of refrigerant fluid between a plurality of sections formed by the one or more support structures; and a redistribution tube configured to fluidly connect at least two of the plurality of sections, and to passively redistribute refrigerant fluid between the at least two of the plurality of sections based on a pressure differential formed across the plurality of sections in the refrigerant fluid. The pressure differential can be caused by a temperature differential between a heat transfer fluid circulating through the set of tubes and the refrigerant fluid.

Description

[0001] Cross-reference to related applications This patent application claims the benefit of U.S. Provisional Patent Application No. 63 / 793,219, filed April 23, 2025, which is incorporated herein by reference in its entirety. Background Technology

[0002] This disclosure relates to the field of refrigeration systems, and more particularly to a fluid redistributor for a heat exchanger. Summary of the Invention

[0003] This document describes an evaporator for a refrigeration system, comprising an evaporator shell configured to house a set of tubes and one or more support structures. The set of support structures is arranged within the evaporator shell to support the set of tubes, and the one or more support structures are configured to prevent mixing of refrigerant fluid between multiple sections formed by the one or more support structures. The evaporator includes a redistribution tube configured to fluidly connect at least two of the multiple sections and to passively redistribute the refrigerant fluid between at least two of the multiple sections based on a pressure differential formed across the multiple sections within the refrigerant fluid.

[0004] In one or more embodiments, a set of tubes includes at least one tube extending within a liquid tank of the evaporator shell, the at least one tube being configured to circulate a heat transfer fluid and exchange heat with the refrigerant and vaporize the refrigerant.

[0005] In one or more embodiments, at least one tube is at least partially immersed in the refrigerant fluid.

[0006] In one or more embodiments, the redistribution conduit includes an external conduit that fluidly connects at least two of the plurality of sections.

[0007] In one or more embodiments, the external tube is connected to each of at least two sections via one or more channels.

[0008] In one or more embodiments, the redistribution pipe includes an internal tube disposed within the evaporator housing, which fluidly connects at least two of a plurality of sections.

[0009] In one or more embodiments, the internal tubes are positioned within the liquid tank of the evaporator shell.

[0010] In one or more embodiments, internal tubing is arranged through one or more support structures of the evaporator shell.

[0011] In one or more embodiments, one or more support structures include one or more baffles configured to impede the flow of refrigerant fluid between adjacent sections.

[0012] In one or more embodiments, one or more support structures include one or more passages configured to allow fluid communication when a pressure differential is present between multiple sections formed adjacent to one or more support structures.

[0013] In one or more embodiments, the evaporator further includes a fluid distributor configured to supply refrigerant fluid from an inlet into the evaporator housing through one or more distributor orifices defined on the fluid distributor.

[0014] In one or more embodiments, the density of one or more distributor orifices decreases from the first end to the second end of the fluid distributor.

[0015] In one or more embodiments, the first end is near the inlet of at least one tube, and the second end is the end opposite to the first end.

[0016] In one or more embodiments, at least one distributor orifice is blocked based on the static pressure of the refrigerant above the orifice.

[0017] In one or more embodiments, the evaporator includes an inlet pipe for supplying refrigerant fluid into the evaporator housing, wherein the inlet pipe is oriented toward a pipe inlet of at least one of a set of pipes to guide the refrigerant fluid.

[0018] In one or more embodiments, the inlet pipe is oriented in a countercurrent manner relative to the flow direction of the heat transfer fluid flow passing through at least one pipe.

[0019] This document describes an evaporator that includes a fluid distributor comprising one or more distributor orifices, wherein the density of the one or more distributor orifices varies across multiple sections of the evaporator shell.

[0020] In one or more embodiments, the density of one or more distributor orifices decreases across multiple sections from the first end to the second end of the fluid distributor.

[0021] In one or more embodiments, the first end is located near the inlet of a set of tubes disposed in the evaporator, and the second end is the end opposite to the first end.

[0022] In one or more embodiments, the density of one or more distribution orifices of the fluid distributor varies according to the temperature gradient of the heat transfer fluid circulating through a set of tubes disposed in the evaporator.

[0023] In one or more embodiments, the evaporator includes an inlet pipe configured to supply refrigerant fluid into the evaporator housing, wherein the inlet pipe is oriented toward a pipe inlet of at least one of a set of pipes to guide the refrigerant fluid.

[0024] The above overview is illustrative only and is not intended to be limiting in any way. In addition to the illustrative aspects, embodiments, and features described above, other aspects, embodiments, features, and techniques disclosed herein will become more apparent from the following description taken in conjunction with the accompanying drawings. Attached Figure Description

[0025] The accompanying drawings are included to provide a further understanding of the subject matter disclosure and are incorporated in and constitute a part of this specification. The drawings illustrate exemplary embodiments of the subject matter disclosure and, together with the description, serve to explain the principles of the subject matter disclosure.

[0026] In the accompanying drawings, similar components and / or features may have the same reference numerals. Furthermore, various components of the same type may be distinguished by having a second numeral following the reference numeral to differentiate the similar components. If only the first reference numeral is used in the description, the description applies to any of the similar components having the same first reference numeral, regardless of the second reference numeral.

[0027] Figure 1A An example isometric view of an evaporator with a curved inlet, according to one or more embodiments disclosed in the subject matter, is shown.

[0028] Figure 1B An example representation of an evaporator with a liquid dispenser is shown, according to one or more embodiments disclosed in the subject matter.

[0029] Figure 2 An example view of an evaporator with a passive redistributor tube is shown, according to one or more embodiments disclosed in the subject matter.

[0030] Figure 3 An example view of another embodiment of a passive redistributor tube according to one or more embodiments disclosed in the subject matter is shown.

[0031] Figure 4A and 4B An example view of the support structure of an evaporator according to one or more embodiments disclosed in the subject matter is shown. Detailed Implementation

[0032] The following is a detailed description of the disclosed embodiments of the subject matter, illustrated with the accompanying drawings. The embodiments are so detailed that they clearly convey the subject matter disclosure. However, the amount of detail provided is not intended to limit contemplative variations of the embodiments; rather, it is intended to cover all modifications, equivalents, and alternatives falling within the spirit and scope of the subject matter disclosure as defined by the appended claims.

[0033] Various terms are used herein. Terms used in the claims, unless otherwise specified below, shall be given the broadest definition that a person skilled in the art would give to the term, as reflected in the printed publications and the granting of the patent at the time of application.

[0034] In the specification, when the apparatus is depicted with reference to the accompanying drawings, the spatial relationships between the various components and the spatial orientation of various aspects of the components may be taken into account. However, as will be appreciated by those skilled in the art upon a full reading of the subject matter disclosure, the components described herein can be positioned in any desired orientation. Therefore, the use of terms such as “above,” “below,” “upper,” “lower,” “first,” “second,” or other similar terms that describe the spatial relationships between the various components or the spatial orientation of aspects of such components should be understood as describing the relative relationships between the components or the spatial orientation of aspects of such components, and that the components described herein can be oriented in any desired direction.

[0035] Refrigeration systems are used for cooling, heating, and air conditioning applications. Refrigeration systems remove heat from a refrigerant fluid via vapor compression or a refrigeration cycle. In a refrigeration cycle, the refrigerant fluid exchanges heat through different heat exchangers, thereby supplying or removing heat to or from the surrounding space or heat source, thus controlling the temperature of the surrounding space or heat source. Typically, in cooling applications, heat is released from the refrigerant fluid at the condenser and absorbed by the refrigerant fluid at the evaporator. The evaporator allows the refrigerant fluid to collect heat from the surrounding environment or the refrigerant fluid, thereby lowering its temperature.

[0036] The efficiency of an evaporator depends on its ability to exchange heat with another heat transfer fluid / coolant fluid (such as air or water), which can be improved by maximizing the surface area (or the area where heat exchange can occur) between the refrigerant fluid and the heat transfer fluid / coolant fluid. Therefore, "flooded" evaporators, or shell-and-tube evaporators, are designed to maximize heat exchange.

[0037] Unlike dry evaporators, where the refrigerant fluid primarily vaporizes inside the tubes, in flooded evaporators, the tubes are immersed in liquid refrigerant located inside the shell. The heat transfer fluid flows inside the tubes to be cooled. Flooded evaporators are typically used for improved heat transfer when the liquid refrigerant completely encapsulates the heat exchange tubes, absorbing heat more efficiently. Additionally, the heat transfer fluid is used to cool desired space or process flows.

[0038] The refrigerant fluid can be a two-phase refrigerant. When it absorbs heat from the heat transfer fluid, the refrigerant fluid vaporizes, thereby creating two volumes of refrigerant fluid in the evaporator shell, namely a vapor phase and a liquid phase.

[0039] However, due to the difference in temperature between the heat transfer fluid and the refrigerant saturation temperature, the heat flux along the length of the tube is typically non-uniform. For example, as the heat transfer fluid circulates through the tube extending along the length of the shell, it can lose heat to the refrigerant fluid, resulting in a lower temperature at the tube outlet compared to the tube inlet. This non-uniformity of heat flux also causes the refrigerant fluid to vaporize differently in different parts or sections of the shell. This imbalance in the volume of the refrigerant fluid can lead to inefficiency, as some sections of the tube along the shell may have less liquid refrigerant due to ejected heat. The problem is exacerbated in single-pass systems and can result in vapor cover or drying out near the water inlet side of the shell.

[0040] The subject matter discloses a passive fluid redistributor tube configured to redistribute liquid refrigerant within a housing. The fluid redistributor utilizes pressure differentials caused by uneven vaporization of the liquid refrigerant at different sections / areas of the housing to redistribute the liquid refrigerant. Furthermore, the fluid redistributor is designed to circulate a heat transfer fluid / coolant fluid that sprays heat onto the liquid refrigerant through the tube to address anticipated uneven heat flux / gradients. (See reference...) Figures 1A to 3 The various embodiments disclosed herein are described in detail.

[0041] Reference Figures 1A to 3 The evaporator 100 may include an evaporator shell 102. The evaporator shell 102 may be configured to contain a two-phase refrigerant fluid therein, which may be partially in a liquid phase and partially in a vapor phase. In one or more embodiments, the evaporator shell 102 may be configured to contain a set of tubes 110.

[0042] The evaporator shell 102 may include an inlet 104 and an outlet 106. Refrigerant fluid may be received through the inlet 104 and discharged through the outlet 106. A liquid refrigerant fluid (also referred to as liquid refrigerant) occupies the bottom portion / section of the evaporator shell 102, from which vapor is dispersed due to vaporization. Furthermore, due to buoyancy, the vapor phase refrigerant fluid may rise to a vapor space within the evaporator shell 102 from which the vapor phase refrigerant fluid or vapor refrigerant may be discharged. In one or more embodiments, the evaporator shell 102 may have a substantially cylindrical geometry. In other embodiments, the evaporator shell 102 may have any polyhedral geometry.

[0043] In one or more embodiments, the evaporator 100 / evaporator housing 102 may be connected to a refrigerant circuit (not shown). The refrigerant circuit may be configured to allow refrigerant fluid to circulate through it as part of a refrigeration cycle. During the refrigeration cycle, the refrigerant fluid may circulate through multiple components, including a compressor, a heat exchanger (such as a condenser), an expansion device, and another heat exchanger (such as the evaporator 100).

[0044] The refrigerant circuit fluidly connects the evaporator 100 to an expansion unit, from which "cold" liquid refrigerant (or a mixture of liquid and gaseous / vaporous refrigerant) can be received through inlet 104. Furthermore, the refrigerant circuit connects the evaporator 100 to a compressor via a compressor line / suction line, through which vaporized refrigerant (potentially at saturation temperature) can be delivered to the compressor line / suction line through outlet 106. Figures 1A to 3 The flow of vapor refrigerant is shown using dashed arrows, while the flow of liquid refrigerant is shown using solid arrows.

[0045] In one or more embodiments, such as Figure 1B As shown, refrigerant fluid can be supplied to the evaporator housing 102 via a fluid distributor 116. The fluid distributor 116 may be configured to distribute / supply refrigerant fluid from inlet 104 to the evaporator housing 102. In some embodiments, the fluid distributor 116 may be fluidly connected to inlet 104 and may extend along the length of the evaporator housing 102. The fluid distributor 116 may include one or more distributor holes or openings (such as distributor hole 117) through which refrigerant fluid from inlet 104 may be distributed within the evaporator housing 102.

[0046] In one or more embodiments, the distributor orifices may be uniformly distributed along the length of the fluid distributor 116 (which may also be along the longitudinal axis AA'). In such embodiments, the flow rate / volume of the refrigerant fluid supplied along the length of the fluid distributor 116 may be substantially uniform.

[0047] In other embodiments, such as Figure 1B As shown, the distributor orifices may be distributed unevenly / non-uniformly along the length of the fluid distributor 116. In such embodiments, non-uniformity allows the fluid distributor 116 to distribute refrigerant fluid unevenly. Non-uniformity can be achieved by defining distributor orifices on the fluid distributor 116 in a distribution that allows the refrigerant fluid to be distributed unevenly along the length of the evaporator housing 102. The distribution of the distributor orifices may be selected based on a desired fluid flow gradient, which may be a gradient defining the flow rate / volume of the refrigerant fluid to be supplied along the length of the evaporator housing 102 (or between the first and second ends of the evaporator housing 102).

[0048] In one or more embodiments, the evaporator housing 102 may include one or more support structures 108. The support structures 108 may be arranged within the evaporator housing 102 to support a set of pipes 110 and / or prevent / avoid mixing of refrigerant fluid between multiple sections formed by the one or more support structures. The support structures 108 may be configured to act as bottlenecks, blocking / impeding / preventing the flow of liquid refrigerant in the liquid tank between different sections. The support structures 108 may divide the evaporator housing 102 into one or more sections / parts. The support structures 108 may indicate obstacles or barriers that impede the free flow of liquid refrigerant between adjacent sections, thus allowing static pressure differentials to occur due to uneven liquid levels, which in turn arise from differences in vaporization rates.

[0049] In one or more embodiments, such as Figures 1A to 3 As shown, the support structures 108 may be evenly spaced or equidistant from each other along the length of the evaporator shell 102. In other embodiments, the support structures 108 may be unevenly distributed. For example, the separation distance between support structures 108 closer to one end (such as support structures 108-1 and 108-2 closer to the pipe inlet 112 of the tube / set of tubes 110) may be greater than the separation distance between support structures closer to the other end (such as support structures 108-3 and 108-4 closer to the pipe outlet 114). In some embodiments, the set of tubes 110 may include at least one tube disposed through the evaporator shell 102.

[0050] In one or more embodiments, the support structure 108 may be implemented as a panel aligned along a transverse plane (i.e., a plane perpendicular to the longitudinal axis AA'), the panel having holes to receive a set of tubes 110. The panel may be configured to block and / or impede the flow of liquid refrigerant between sections.

[0051] In other embodiments, the support structure 108 may be implemented as a baffle. The baffle may be positioned to impede or block the flow of liquid refrigerant between sections.

[0052] In one or more embodiments, the baffle may include one or more passages. The passages (or orifices or arrangements) may be sized and / or shaped to allow flow of liquid refrigerant between adjacent sections when a pressure differential is generated between each of the adjacent sections. In one or more embodiments, the passages may be configured to operate open when a pressure differential is formed adjacent to the baffle between multiple sections.

[0053] In one or more embodiments, the evaporator housing 102 may include a set of tubes 110. The set of tubes 110 may include at least one tube extending across the length of the evaporator housing 102. The set of tubes 110 may be defined between a tube inlet 112 and a tube outlet 114. In one or more embodiments, the tubes 110 may extend across the length of the evaporator housing 102 or along a longitudinal axis (as shown by axis AA'). In one or more embodiments, the set of tubes 110 may extend along the length of the evaporator housing 102. In other embodiments, the set of tubes 110 may be arranged / distributed in a serpentine manner within the evaporator housing 100, wherein the set of tubes 110 may extend across the length of the evaporator housing 102 multiple times.

[0054] A set of pipes 110 may be configured to circulate a heat transfer fluid / coolant fluid through it. In some embodiments, the heat transfer fluid / coolant fluid may be water. In one or more embodiments, the heat transfer fluid may circulate from pipe inlet 112 to pipe outlet 114. Pipe inlet 112 and pipe outlet 114 may be provided on the end wall of evaporator shell 102.

[0055] In one or more embodiments, the evaporator housing 102 may include at least one coolant tank at one end of the evaporator housing 102. Figure 1A and 1B Showing coolant tanks 113-1 and 113-2 mounted at both ends of evaporator housing 102. In one or more embodiments, a pipe inlet 112 and a pipe outlet 114 may be defined on one of the coolant tanks, such as coolant tank 113-1. Coolant tank 113 allows heat transfer fluid / coolant fluid to circulate through at least some of the pipes in a set of pipes 110. A set of pipes 110 fluidly connects a (first) coolant tank 113-1 at one end to a (second) coolant tank 113-2 at the other end. Coolant fluid can be supplied to the first coolant tank 113-1 through pipe inlet 112, through a first subset of pipes in the set of pipes 110 to the second coolant tank 113-2. The second coolant tank 113-2 then directs coolant fluid received from the first subset of pipes through a second subset of pipes in the set of pipes 110, which returns coolant fluid to the first coolant tank 113-1. Coolant fluid can exit the first coolant tank 113-1 through pipe outlet 114. Therefore, coolant tank 113-1 can be divided to direct coolant fluid from pipe inlet 112 toward the first pipe cluster, and thus prevent coolant fluid from pipe inlet 112 from entering the second pipe cluster. Correspondingly, the division can direct coolant fluid from the second pipe cluster to prevent it from mixing with fluid from pipe inlet 112 and / or entering the first pipe cluster.

[0056] A set of tubes 110 may be made of a thermally conductive material that allows the refrigerant fluid to exchange heat with other fluids. In one or more embodiments, the set of tubes 110 may be at least partially submerged in the liquid tank / bottom portion of the evaporator shell 102. Submerging the set of tubes 110 in the liquid tank maximizes the surface area available for heat exchange between the heat transfer fluid and the refrigerant fluid. As the heat transfer fluid / coolant fluid circulates through the set of tubes 110, the heat transfer fluid can exchange heat with the liquid refrigerant in the liquid tank.

[0057] Because it absorbs heat from the heat transfer fluid, the liquid refrigerant in the liquid tank can vaporize. The vaporized refrigerant can rise into the vapor space, and can be discharged from the vapor space to the compressor via outlet 106.

[0058] As stated, the temperature of the heat transfer fluid can vary at different points along the length of a set of pipes 110. For example, since the heat transfer fluid continuously releases heat to the liquid refrigerant, the temperature of the heat transfer fluid entering the evaporator shell 102 can be greater than the temperature of the heat transfer fluid leaving the evaporator shell 102. Furthermore, a reduced temperature gradient can be formed from the pipe inlet 112 to the pipe outlet 114. This temperature non-uniformity can cause different masses of liquid refrigerant to vaporize in each section of the evaporator shell 102. For example, since the temperature of the heat transfer fluid can be greatest in the first section defined between the end wall of the evaporator shell 102 and the support structure 108-1, the mass of liquid refrigerant vaporized in the first section can be greater than the mass of liquid refrigerant vaporized in other sections (such as the second section between support structures 108-1 and 108-2, the third section between support structures 108-2 and 108-3, etc.). Such non-uniformity (if not addressed) can lead to situations where at least one of the tubes in the set 110 is no longer submerged, or vapor barriers form on or around at least some of the tubes in the set 110, hindering or preventing heat exchange between the heat transfer fluid and the liquid refrigerant. Furthermore, the support structure 108 can impede or block the movement of the liquid refrigerant to other adjacent sections in order to achieve equilibrium.

[0059] To address the temperature inhomogeneity of the heat transfer fluid (and consequently, the uneven vaporization of the liquid refrigerant), the evaporator housing 102 may include a (passive) redistribution mechanism that allows the liquid refrigerant level to be consistent / uniform along the length of the evaporator housing 102. The passive redistribution mechanism can passively redistribute the liquid / fluid refrigerant across different sections of the evaporator housing 102 without the need for active mechanisms (such as motors, fans, or pumps). More precisely, to passively redistribute the liquid / fluid refrigerant, the passive redistribution mechanism may be configured to utilize forces (such as gravity or forces developed due to pressure differences across different sections of the evaporator housing 102) to redistribute the fluid refrigerant.

[0060] In one or more embodiments, the redistribution mechanism may involve directing more liquid refrigerant from inlet 104 to an area where more refrigerant vaporization is expected. In some embodiments, such as Figure 1B As shown, more liquid refrigerant can be supplied to such areas by defining a larger distribution of distributor holes / openings on the liquid distributor 116 in such areas, and / or by providing fewer distributor holes / openings in areas where relatively less heat is expected.

[0061] In one or more embodiments, the density (i.e., the number) of distributor orifices defined on the fluid distributor 116 may decrease from a first end of the fluid distributor 116 / evaporator housing 102 (e.g., the end corresponding to the first coolant tank 113-1) to a second end opposite the first end (e.g., the end corresponding to the second coolant tank 113-2). In one or more embodiments, at least one distributor orifice may be blocked based on the static pressure of the refrigerant above the orifice (e.g., using a stopper, cork, etc.). Blocking the distributor orifice allows the flow of refrigerant through the fluid distributor 116.

[0062] In one or more embodiments, the distribution of the distributor orifices may correspond to the (expected) temperature gradient or heat flux formed on pipe 110 during the circulation of the heat transfer fluid. In such embodiments, the refrigerant fluid flow rate to evaporator shell 102 can be greater in areas where more distributor orifices are defined on fluid distributor 116 compared to areas with fewer distributor orifices in fluid distributor 116. Since the distribution of the distributor orifices may correspond to the distribution of the expected / predicted temperature gradient or heat flux on pipe 110, more liquid refrigerant can be directed toward the hotter areas of pipe 110 compared to colder areas, thereby compensating for increased vaporization (and therefore, a decrease in liquid refrigerant level) at the hotter areas of pipe 110.

[0063] In other embodiments, liquid refrigerant can be guided toward pipe inlet 112 (or any other region) by defining inlet 104 and / or inlet pipe 105 connected to inlet 104 at an inclination or angle toward pipe inlet 112. In one or more embodiments, as Figure 1A As shown, the inlet pipe 105 to the evaporator housing 102 can be oriented to transport / flow refrigerant fluid from one end (e.g., the end corresponding to the first refrigerant tank 113-1) towards the other end (i.e., the end corresponding to the second refrigerant tank 113-2) to guide more liquid refrigerant toward the pipe inlet 112. In such embodiments, the inlet pipe 105 can be oriented in a counter-current arrangement relative to the pipe 110. Guiding more liquid refrigerant to the pipe inlet 112 can compensate for increased vaporization of the liquid refrigerant near the pipe inlet 112.

[0064] In one or more embodiments, such as Figure 2 and 3 As shown, the redistribution mechanism may include redistribution pipes (such as redistribution pipes 118A and 118B). Redistribution pipes 118A or 118B may be configured to fluidly connect one or more sections of the evaporator housing 102 (such as those formed between support structures 108). This fluid connection allows liquid refrigerant to flow between different sections or regions within the evaporator housing 102. In some embodiments, a fluid distributor 116 may be adapted to operate as redistribution pipes 118A or 118B.

[0065] Reference Figure 2 The redistribution pipe 118A may be an external pipe configured to fluidly connect different parts (such as sections formed by the support structure 108). The fluid connection allows liquid refrigerant to flow from one section to another, thereby redistributing liquid refrigerant throughout the evaporator shell 102.

[0066] In one or more embodiments, the external tube may be an external tube / pipe connected to the evaporator housing 102. The external tube may be connected to each (or at least two) of the sections inside the evaporator housing 102 via one or more channels extending from the external tube to each of the sections. In one or more embodiments, a redistribution tube 118A may be connected to the bottom of each section.

[0067] Due to heat flux distribution and unequal vaporization, different amounts / volumes / quantities of refrigerant fluid may remain as liquid or in liquid form within the sections. Therefore, the static pressure in each section may differ. For example, the static pressure may be higher in sections with more liquid refrigerant. In contrast, the static pressure may be lower at the bottom of the evaporator shell 102 in areas where vapor cover occurs. Fluid connections provided by external pipes facilitate the redistribution of liquid refrigerant from sections with higher static pressure (corresponding to sections experiencing less liquid refrigerant vaporization) to sections with lower static pressure (corresponding to sections experiencing increased / higher liquid refrigerant vaporization). The pressure difference between sections allows liquid refrigerant to flow through the redistribution pipe 118A and is redistributed based on the pressure difference in each section, thereby ensuring an average refrigerant level across the evaporator shell 102.

[0068] In one or more embodiments, the redistribution pipe (such as outer pipe 118A or inner pipe 118B) may be configured to passively redistribute the liquid refrigerant. "Passive redistribution" may correspond to causing the refrigerant fluid to be driven or moved by natural forces rather than by an active mechanism using external work or active mechanical propulsion. Forces driving passive redistribution may include, but are not limited to, gravity acting at different liquid column heights, hydrostatic pressure gradients resulting from changes in fluid density (e.g., due to varying void fractions), and / or thermodynamic forces experienced by the refrigerant fluid, which can cause changes in the distribution of potential energy across the refrigerant fluid. Thus, the fluid refrigerant flows from regions of higher potential energy to regions of lower potential energy to restore a state of hydraulic or thermodynamic equilibrium without the application of an external kinetic energy source, such as a pump, impeller, or power actuator.

[0069] For example, the first section defined between the end wall of the evaporator shell 102 and the first support structure 108-1 may experience a greater heat flux from the tubes 110. Due to the greater heat flux, the mass of liquid refrigerant in the first section may vaporize more than the mass of liquid refrigerant in another / second section (such as, among other things, the section defined between the second support structure 108-2 and the third support structure 108-3). Therefore, the liquid refrigerant level in the first section may be lower than the liquid refrigerant level in the second section, and / or a vapor overlay may form around some of the top tubes in the set of tubes 110 in the first section. Both situations can prevent the heat transfer fluid circulating through the tubes 110 from efficiently expelling heat. In addition, the higher vaporization rate in the first section may result in a higher void fraction in the first section. Due to the lower vaporization rate, the void fraction value may decrease in subsequent sections.

[0070] In such cases, due to the lower liquid level and higher void fraction, the first section can have a lower static pressure than the second section. Therefore, as from Figure 2 As indicated by the arrow shown, liquid refrigerant (or a low-quality liquid-vapor mixture) can move / flow from the second section, which has a higher static pressure, to the first section via an external pipe. This movement of the liquid refrigerant (or two-phase mixture) balances the static pressure between the first and second sections, and also balances the liquid refrigerant level distribution between them, thereby balancing the charge / pressure in the evaporator 100. To facilitate the flow of liquid (or low-quality two-phase mixture), redistribution pipes 118A and / or 118B may be located at the bottom of the evaporator shell, or the connection may be located in the bottom portion of the evaporator shell.

[0071] In some applications, space constraints can prevent the implementation of external piping. In such cases, alternative solutions for redistribution can be provided.

[0072] Reference Figure 3In one or more embodiments, the redistribution mechanism may include an internal tube (also referred to as redistribution tube 118B) disposed within the evaporator housing 102.

[0073] In one or more embodiments, the redistribution pipe 118B may be an internal pipe disposed inside the evaporator housing 102. In one or more embodiments, the internal pipe may be positioned within the liquid tank of the evaporator housing 102. In some embodiments, such as Figure 3 As shown, the redistribution pipe 118B can be positioned at the bottom of the evaporator housing 102. The internal pipe can extend across the length of the evaporator housing 102 and can pass through the support structure 108.

[0074] In one or more embodiments, the internal tubing may be configured to fluidly connect different sections of the evaporator housing 102. In one or more embodiments, the redistribution tubing 118A, 118B may be open at the ends. Based on the pressure difference between the sections, the fluid connection may allow the liquid refrigerant to be redistributed from sections with higher static pressure to sections with lower static pressure, thereby maintaining an average liquid level across the evaporator housing 102.

[0075] It can be recognized that, Figure 2 and 3 The evaporator 100 shown may also include an inlet 104 and a fluid distributor 116, which are hidden for clarity.

[0076] In addition, the internal tube / redistribution tube 118B can be located within the evaporator housing 102. The internal tube / redistribution tube 118B provides a more compact design.

[0077] Figure 4A and 4B An example design for support structure 108 is shown. In one or more embodiments, support structure 108 may have cutouts / passages, such as passages 402 and 404. Figure 4B As shown, in one or more embodiments, the passage 402 may have a chordal geometric profile. Furthermore, in one or more embodiments, as... Figure 4B As shown, passage 404 may have a geometric profile of circular segments. The passage may be configured to allow liquid refrigerant flow through support structure 108. Liquid refrigerant can move between adjacent sections of support structure 108 via the passage due to pressure differentials generated between different sections of evaporator shell 102. In one or more embodiments, the passage may be shaped and / or sized to allow (or otherwise impede) the flow of liquid refrigerant when the pressure differential is greater than a threshold.

[0078] Therefore, this disclosure provides a redistribution mechanism or redistribution pipe for evaporator shell 102. The redistribution mechanism / pipe passively prevents vapor cover and improves the efficiency of evaporator 100 (and the refrigeration system) by allowing liquid refrigerant to flow between different sections of evaporator shell 102 based on the pressure difference between sections. The redistribution mechanism / pipe levels the liquid level in each section of evaporator shell 102 and maintains an average fluid distribution. By controlling the liquid refrigerant level in the redistribution sections, the redistribution mechanism / pipe ensures that pipe 110 remains fully submerged in the liquid tank, thereby improving the heat exchange efficiency of evaporator 100.

[0079] While the subject matter disclosure has been described with reference to exemplary embodiments, those skilled in the art will understand that various changes may be made without departing from the scope of the subject matter disclosure as defined by the appended claims, and equivalents may be substituted for its elements. Modifications may be made to adapt particular cases or materials to the teachings of the subject matter disclosure without departing from the scope of the subject matter disclosure. Therefore, it is intended that the subject matter disclosure be limited to the specific embodiments disclosed, but rather that the subject matter disclosure include all embodiments falling within the scope of the subject matter disclosure as defined by the appended claims.

[0080] In interpreting the specification, all terms should be interpreted in the broadest possible manner consistent with the context. In particular, the terms “comprising” and “including” should be interpreted as referring to an element, component, or step in a non-exclusive manner, indicating that the referenced element, component, or step may exist, be used, or be combined with other elements, components, or steps not explicitly referenced. When a claim in the specification refers to at least one thing selected from the group consisting of A, B, C, ..., and N, the text should be interpreted as requiring only one element from the group, not A plus N, or B plus N, etc.

Claims

1. An evaporator for a refrigeration system, comprising: An evaporator housing configured to house a set of tubes, and one or more support structures arranged within the evaporator housing to support the set of tubes, the one or more support structures configured to prevent refrigerant fluid from mixing between multiple sections formed by the one or more support structures; as well as A redistribution pipe is configured to fluidly connect at least two of the plurality of sections and to passively redistribute the refrigerant fluid between at least two of the plurality of sections based on a pressure differential formed across the plurality of sections within the refrigerant fluid.

2. The evaporator according to claim 1, wherein, The set of tubes includes at least one tube extending within the liquid tank of the evaporator shell, the at least one tube being configured to circulate a heat transfer fluid to exchange heat with the refrigerant fluid and to vaporize the refrigerant fluid.

3. The evaporator according to claim 2, wherein, The at least one tube is at least partially immersed in the refrigerant fluid.

4. The evaporator according to claim 1, wherein, The redistribution conduit includes an external conduit that fluidly connects to at least two of the plurality of sections.

5. The evaporator according to claim 1, wherein, The external pipe is connected to each of at least two of the plurality of sections via one or more channels.

6. The evaporator according to claim 1, wherein, The redistribution pipe includes an internal tube disposed within the evaporator shell, which fluidly connects to at least two of the plurality of sections.

7. The evaporator according to claim 6, wherein, The internal tube is positioned within the liquid tank of the evaporator shell.

8. The evaporator according to claim 6, wherein, The internal tubes are arranged through one or more support structures of the evaporator shell.

9. The evaporator according to claim 1, wherein, The one or more support structures include one or more baffles configured to impede the flow of the refrigerant fluid between adjacent sections from the plurality of sections.

10. The evaporator according to claim 1, wherein, The one or more support structures include one or more passages configured to allow fluid communication when the pressure differential is adjacent to the one or more support structures formed between the plurality of sections.

11. The evaporator of claim 1, further comprising a fluid distributor configured to supply the refrigerant fluid from an inlet into the evaporator housing through one or more distributor orifices defined on the fluid distributor.

12. The evaporator according to claim 11, wherein, The density of the one or more distributor orifices decreases from the first end to the second end of the fluid distributor.

13. The evaporator according to claim 11, wherein, The first end is near the inlet of at least one tube, and the second end is the end opposite to the first end.

14. The evaporator of claim 1, further comprising an inlet pipe configured to supply the refrigerant fluid into the evaporator housing, wherein the inlet pipe is oriented toward a pipe inlet of at least one of the set of pipes to guide the refrigerant fluid.

15. The evaporator according to claim 14, wherein, The inlet pipe is oriented in a countercurrent manner relative to the flow direction of the heat transfer fluid passing through the at least one pipe.

16. An evaporator comprising: A fluid distributor comprising one or more distributor orifices, wherein the density of the one or more distributor orifices varies across multiple sections of the evaporator shell.

17. The evaporator according to claim 16, wherein, The density of the one or more distributor orifices decreases across the plurality of sections from the first end to the second end of the fluid distributor.

18. The evaporator according to claim 17, wherein, The first end is located near the inlet of a set of tubes disposed in the evaporator, and the second end is the end opposite to the first end.

19. The evaporator according to claim 16, wherein, The density of the one or more distribution orifices of the fluid distributor varies according to the temperature gradient of the heat transfer fluid circulating through a set of tubes disposed in the evaporator.

20. The evaporator of claim 16, further comprising an inlet pipe configured to supply the refrigerant fluid into the evaporator housing, wherein the inlet pipe is oriented toward a pipe inlet of at least one of the set of pipes to guide the refrigerant fluid.

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