Vapor-liquid separator and system comprising vapor-liquid separator

Abstract

The invention relates to a vapor-liquid separator and a system including the vapor-liquid separator. The vapor-liquid separator includes: a first flow path extending between a fluid inlet and a fluid outlet and including a helical portion; a second flow path extending between the first flow path and the steam outlet and fluidly passing steam from the first flow path to the steam outlet and defining a helical portion; and one or more bridges that fluidly couple the first flow path to the second flow path. The helical portion of the first flow path results in a reduction in static pressure and an increase in velocity of the fluid flowing through the first flow path and produces steam flowing into the second flow path via the one or more bridges. Steam received within the second flow path is discharged from the steam outlet, and fluid flowing through the first flow path is discharged from the fluid outlet.

Description

Technical Field

[0001] The field of this disclosure generally relates to heating, ventilation and air conditioning (HVAC) systems, and more specifically, to pressure recovery devices for reversible vapor compression systems. Background Technology

[0002] Vapor compression systems are widely used in climate control applications to provide heat pump, refrigeration, and / or air conditioning capabilities. A typical vapor compression system includes a fluid loop having: a first heat exchanger (e.g., a condenser that changes the phase of the refrigerant from a gaseous / vapor phase to a liquid phase); a second heat exchanger (e.g., an evaporator that changes the phase of the refrigerant from a liquid phase to a gaseous / vapor phase); an expansion device disposed between the first and second heat exchangers; and a compressor that operates to circulate and pressurize a gaseous / vapor phase working fluid (and optionally a lubricating oil) between the first and second heat exchangers (e.g., a condenser and an evaporator). The compressor is typically a mechanical compressor used to pressurize the working fluid, which, while circulating within the system, can subsequently be condensed and evaporated to transfer heat to or from the system.

[0003] The throttling process in the expander leads to significant energy loss and inefficiency during the steam compression cycle. As can be understood, if the steam received by the compressor is at a higher pressure, less energy is required to fully compress the steam to the desired discharge pressure. Several devices are typically used to improve compressor efficiency, such as flash tanks or plate heat exchangers, ejector cycles, centrifugal separators or energy recovery pressure exchangers, and two-phase turbines. Steam injection systems are also used to improve compressor efficiency by supplying medium-pressure steam to the compressor. Because the medium-pressure steam is at a pressure slightly higher than the intake pressure and slightly lower than the discharge pressure, the work required by the compressor to produce steam at the discharge pressure is reduced.

[0004] These expansion energy loss recovery devices can be complex, expensive, and often limited in the amount of steam that can be separated and delivered to the compressor. As is understandable, improved cycle efficiency requires additional expansion energy loss recovery devices, further increasing the complexity and cost of the steam compression system. Therefore, there is a need for an expansion loss recovery device that is less complex, less expensive, and more efficient than current ones.

[0005] This section is intended to introduce the reader to various aspects of the prior art that may be related to the various aspects of this disclosure described below and / or claimed. This discussion is intended to help provide the reader with background information to facilitate a better understanding of the various aspects of this disclosure. Therefore, it should be understood that these statements are to be read in this context, and not as an admission of prior art. Summary of the Invention

[0006] One aspect of this disclosure relates to a vapor-liquid separator including a first flow path, a second flow path, and one or more bridging portions. The first flow path extends between a fluid inlet and a fluid outlet and defines a helical portion. The helical portion causes a decrease in the static pressure and an increase in the velocity of the fluid flowing through the first flow path to generate steam from the fluid. The second flow path extends between the first flow path and a steam outlet and fluidly transfers steam from the first flow path to the steam outlet, and also defines a helical portion. One or more bridging portions upstream of the steam outlet and along the helical portions of each of the first and second flow paths fluidly connect the first flow path to the second flow path. The increased velocity of the fluid flowing through the first flow path causes steam within the first flow path to flow into the second flow path via one or more bridging portions. The steam received in the second flow path is discharged from the steam outlet, and the fluid flowing through the first flow path is discharged from the fluid outlet.

[0007] Another aspect of this disclosure relates to a vapor-liquid separator including a first flow path and a second flow path. The first flow path includes a fluid inlet section, a fluid outlet section, and a first spiral portion extending between the fluid inlet section and the fluid outlet section and fluidly connecting the fluid inlet section to the fluid outlet section. The fluid inlet section generates an increase in the velocity of the fluid flowing through it and a decrease in its static pressure. The fluid outlet section generates a decrease in the velocity of the fluid flowing through it and an increase in its static pressure. The first spiral portion generates an increase in the velocity of the fluid flowing through it and a separation of vapor and fluid. The second fluid flow path includes a vapor outlet section, a second spiral portion extending between the first flow path and the vapor outlet section and fluidly transferring vapor from the first flow path to the vapor outlet section, and one or more bridging portions fluidly connecting the first spiral portion to the second spiral portion. The vapor outlet section defines a vapor outlet and generates an increase in the static pressure and a decrease in the velocity of the vapor flowing through it. The second helical section is intertwined with the first helical section, and the increased velocity of the fluid flowing through the first helical section causes steam within the first helical section to flow into the second helical section. One or more bridging sections allow steam within the first helical section to flow into the second helical section via one or more bridging sections. Receiving steam within the second helical section results in an increased velocity of steam flowing through the second helical section. The steam received within the second helical section is discharged from a steam outlet, and the fluid flowing through the first helical section is discharged from a fluid outlet.

[0008] Another aspect of this disclosure relates to a system comprising a fluid compression circuit and a vapor-liquid separator fluidly connected to the fluid compression circuit. The fluid compression circuit includes a compressor operable to compress pairs of refrigerants. The vapor-liquid separator receives liquid refrigerant from the vapor compression circuit and includes a first flow path, a second flow path, and one or more bridging sections. The first flow path extends between a fluid inlet and a fluid outlet and includes a helical portion that causes a decrease in the static pressure and an increase in the velocity of the liquid refrigerant flowing through the first flow path to generate vapor from the liquid refrigerant. The second flow path extends between the first flow path and a vapor outlet and fluidly transfers the vapor from the first flow path to the vapor outlet. One or more bridging sections fluidly connect the first flow path to the second flow path. The increased velocity of the liquid refrigerant flowing through the first flow path causes the vapor in the first flow path to flow into the second flow path via one or more bridging sections. The vapor received in the second flow path is discharged from the vapor outlet to an intermediate compression stage of the compressor.

[0009] Various modifications exist to the features indicated in relation to the foregoing aspects of this disclosure. Other features may also be incorporated into the foregoing aspects of this disclosure. These modifications and additional features may exist individually or in any combination. For example, various features discussed below with respect to any embodiment of the illustrated embodiments of this disclosure may be incorporated individually or in any combination into any of the foregoing aspects of this disclosure. Attached Figure Description

[0010] Figure 1 This is a schematic diagram of an example vapor compression system, showing the vapor compression system in cooling mode;

[0011] Figure 2A yes Figure 1 A schematic diagram of a steam compression system, showing a steam compression system in heating mode;

[0012] Figure 2B yes Figure 1 A schematic diagram of another embodiment of the vapor compression system including a second indoor heat exchanger;

[0013] Figure 3 It is applicable to Figures 1 to 2B A three-dimensional diagram of an example vapor-liquid separator used in a vapor compression system;

[0014] Figure 4 yes Figure 3 Side view of a vapor-liquid separator;

[0015] Figure 5 yes Figure 4 A magnified view of the detailed area indicated in the image;

[0016] Figure 6 yes Figure 3 A front view of a vapor-liquid separator;

[0017] Figure 7 yes Figure 3 Side view of the spiral portion of the first flow path and the spiral portion of the second flow path of the vapor-liquid separator.

[0018] Figure 8 yes Figure 3 An enlarged view of the spiral portions of the first and second flow paths of the vapor-liquid separator, illustrating the liquid bridging portion connecting the first spiral portion to the second spiral portion.

[0019] Figure 9 yes Figure 3 An enlarged perspective view of the spiral portions of the first and second flow paths of the vapor-liquid separator, illustrating the steam bridging portion connecting the first spiral portion to the second spiral portion.

[0020] Figure 10 It is applicable to Figures 1 to 2B A front view of another embodiment of a vapor-liquid separator used in a vapor compression system;

[0021] Figure 11 yes Figure 10 A cross-sectional view of a vapor-liquid separator;

[0022] Figure 12 yes Figure 11 A magnified view of the detailed area indicated in the image;

[0023] Figure 13 yes Figures 3 to 12 A schematic diagram of another embodiment of a vapor compression system in which a vapor-liquid separator can be implemented;

[0024] Figure 14 yes Figures 3 to 12 A schematic diagram of another embodiment of a vapor compression system in which a vapor-liquid separator can be implemented;

[0025] Figure 15A This is a flowchart of an example method for operating a vapor-liquid separator according to this disclosure; and

[0026] Figure 15B yes Figure 15A The continuation of the flowchart.

[0027] Throughout the accompanying drawings, corresponding reference numerals denote the corresponding parts. Detailed Implementation

[0028] For simplicity, an example of a reversible vapor compression system capable of operating to heat or cool an internal space will be described. However, other example methods and systems can be used to regulate the temperature of an enclosed space. The efficiency of a reversible vapor compression system can be improved by incorporating a vapor-liquid separator, which, compared to a heat exchanger or flash tank, utilizes two helical flow paths fluidly connected by one or more bridging sections to generate more vapor and deliver it to the compressor. The vapor-liquid separator can replace the flash tank and / or heat exchanger used in steam energy-saving loops, thereby reducing the complexity and cost of the steam compressor system.

[0029] Reference Figure 1 and Figure 2A The illustration shows a schematic diagram of an example vapor compression system for cooling or heating an interior space surrounded by an external space, and the example vapor compression system is generally identified by reference numeral 10. It is contemplated that the vapor compression system 10 may be implemented as part of a heating, ventilation, and air conditioning (HVAC) system, a refrigeration system, and / or a heat pump without departing from the scope of this disclosure. The vapor compression system 10 includes a single reversible closed refrigerant loop 12, which includes an indoor heat exchanger 14, an outdoor heat exchanger 16, a multi-way valve or reversing valve 18, a compressor 20, a first expansion device 40, a second expansion device 42, a first vapor-liquid separator 100a, and a second vapor-liquid separator 100b. In other embodiments, the vapor compression system 10 may include multiple refrigerant loops to accommodate multiple compressors, or may operate in parallel with another system, such as a humidity control system. As described further in detail herein, the multi-way valve may be selectively positioned to selectively change the flow direction of the refrigerant through the vapor compression system 10, and thus determine whether the vapor compression system 10 operates to cool or heat the interior space 80.

[0030] Figure 1 The illustration shows a vapor compression system 10, in which a multi-way valve 18 is positioned in a first position for operation in cooling mode. In cooling mode, refrigerant enters compressor 20 as a low-pressure, low-temperature gas (e.g., suction stream) at compressor inlet 22. Compressor 20 increases the pressure of the refrigerant, which exits compressor 20 as a high-pressure, high-temperature gas (e.g., discharge stream) at compressor outlet 24. It is conceivable that compressor 20 can be driven by any suitable motor, and in this embodiment, compressor 20 can be driven by a variable frequency drive (VFD) 26.

[0031] The discharge flow passes through the first discharge path 18a of the multi-way valve 18, which directs the refrigerant to the outdoor heat exchanger 16. The outdoor heat exchanger 16 acts as a condenser, transferring heat Q... 出The refrigerant is removed and heat is released into the external space 82 to convert the refrigerant gas into a high-pressure, high-temperature liquid. A first fan 28 generates a first airflow 30 from the outdoor heat exchanger 16 toward the external space 82 to discharge warm air toward the external space 82. It is conceivable that the first fan 28 can be driven by any suitable motor, and in some embodiments, the first fan 28 can be driven by a second VFD 32.

[0032] Downstream of the outdoor heat exchanger 16, the refrigerant bypasses the second vapor-liquid separator 100b and the second expansion device 42, and flows through the first vapor-liquid separator 100a, which partially expands the liquid refrigerant, and then through the first expansion device 40, which reduces the total pressure and further expands the refrigerant. In some embodiments, the static pressure can be reduced until the current temperature of the liquid refrigerant reaches its boiling point at that pressure and the refrigerant becomes a two-phase mixture as some of the liquid refrigerant boils and turns into a gas. The first expansion device 40 can be a fixed orifice, a thermal expansion valve, an electronic expansion valve, or other type of expansion device that allows the vapor compression system 10 to function as described.

[0033] A first vapor-liquid separator 100a is fluidly connected to an indoor heat exchanger 14, which receives liquid refrigerant or a two-phase mixture of liquid and gaseous refrigerant at its inlet. As described in further detail herein, the first vapor-liquid separator 100a accelerates the fluid (e.g., a saturated or at least partially subcooled liquid) to separate vapor within the fluid. The vapor is directed through a divergence portion of a first flow path of the first vapor-liquid separator 100a to convert the vapor velocity into pressure, and is discharged from a vapor outlet and conveyed through flow paths 52a and 52 to a vapor injection port 50 of an intermediate pressure section of the compressor 20. The liquid separated from the vapor is directed through a divergence portion of a second flow path of the first vapor-liquid separator 100a to convert the liquid velocity into pressure, and is discharged from a fluid outlet and conveyed to a first expansion device 40.

[0034] The expanded liquid refrigerant is guided from the first expansion device 40 to the indoor heat exchanger 14. The indoor heat exchanger 14 functions as an evaporator, in which the refrigerant absorbs heat Q from the interior space 80. 入 This changes the phase of the refrigerant from liquid to gas. A second fan 34 generates a second airflow 36 across the indoor heat exchanger 14 toward the interior space 80, thereby cooling the interior space 80. It is conceivable that the second fan 34 can be driven by any suitable motor, and in some embodiments, the second fan 34 can be driven by a third VFD 38. The gaseous refrigerant flow then passes through the first suction path 18b of the multi-way valve 18 and returns as a suction flow to the compressor inlet 22.

[0035] Reference Figure 2A The diagram illustrates a vapor compression system 10, in which a multi-way valve 18 is positioned in a second position for operation in heating mode. Similar to cooling mode, refrigerant enters compressor 20 as a low-pressure, low-temperature gas (e.g., suction stream) at compressor inlet 22. Compressor 20 increases the total pressure of the refrigerant, which exits compressor 20 as a high-pressure, high-temperature gas (e.g., discharge stream) at compressor outlet 24. The discharge stream flows through a second discharge path 18c of multi-way valve 18, which directs the refrigerant to indoor heat exchanger 14. Indoor heat exchanger 14 acts as a condenser, transferring heat Q... 出 The refrigerant is removed to convert the refrigerant gas into a high-pressure, high-temperature liquid. A second fan 34 generates a second airflow 36 across the indoor heat exchanger 14 toward the interior space 80, thereby removing heat Q. 出 Released into internal space 80.

[0036] Downstream of the indoor heat exchanger 14, the refrigerant bypasses the first vapor-liquid separator 100a and flows through the second vapor-liquid separator 100b, which reduces the static pressure of the refrigerant. The static pressure can be reduced until the current temperature of the liquid refrigerant at that pressure becomes its boiling point and the refrigerant becomes a two-phase mixture as some of the liquid refrigerant boils and turns into a gas.

[0037] The second vapor-liquid separator 100b is fluidly connected to the outdoor heat exchanger 16, which receives liquid refrigerant or a two-phase mixture of liquid and gaseous refrigerant at its inlet. The outdoor heat exchanger 16 functions as an evaporator, wherein the refrigerant absorbs heat Q from the external space 82. 入 The phase is changed from liquid to gas. The first fan 28 generates a first airflow 30 from the outdoor heat exchanger 16 toward the external space 82. The gaseous refrigerant flow then passes through the second suction path 18d of the multi-way valve 18 and returns as a suction flow to the compressor inlet 22.

[0038] See also Figure 2BIt is conceivable that the vapor compression system 10 may include a second indoor heat exchanger 14a fluidly coupled to the second vapor-liquid separator 100b. The second indoor heat exchanger 14a receives steam or refrigerant gas from the second vapor-liquid separator 100b to perform a first heating stage before the steam or refrigerant gas from the second vapor-liquid separator 100b is returned to be rejoined in the flow from the fluid outlet. As can be understood, utilizing the steam flowing from the second vapor-liquid separator 100b through the second indoor heat exchanger 14a allows the first heating stage to be performed without injecting steam into the compressor 20, and both the efficiency of the vapor compression system 10 and the capacity of the compressor 20 can be improved compared to a vapor compression system without the second indoor heat exchanger 14a.

[0039] Return to reference Figure 1 and Figure 2A The compressor 20 of the vapor compression system 10 includes a vapor injection port 50 operably connected to a vapor injection conduit 52. The vapor injection conduit 52 is fluidly connected via a first vapor injection conduit 52a to the vapor outlet 154 of a first vapor-liquid separator 100a. Figure 3 The vapor separator 100a, 100b is fluidly connected to the steam outlet 154 of the second vapor-liquid separator 100b via a second steam injection conduit 52b. As will be understood, vapor separators 100a, 100b output a larger volume of steam compared to an economizer loop with a flash tank and / or a separate heat exchanger. In this way, it is conceivable that vapor separators 100a, 100b can replace or otherwise eliminate the need for a flash tank and / or a separate heat exchanger when generating and delivering steam to the steam injection port 50 of the compressor 20.

[0040] As will be understood, the geometry and efficiency of the vapor-liquid separator 100a allow for miniaturization or other reduction in size compared to flash tanks or other energy recovery devices typically used in steam injection cycles. It is contemplated that the vapor-liquid separator 100a can be manufactured or otherwise formed using any suitable method. In embodiments, additive manufacturing, subtractive manufacturing, and combinations thereof can be used to form the vapor-liquid separator 100a. It is contemplated that the vapor-liquid separator 100a can be formed by casting using wax and / or phase change materials, 3D printing, investment casting, etc. It is contemplated that the vapor-liquid separator 100a can be formed wholly or partially by 3D printing. It is contemplated that 3D printing can be used to manage pressure boundaries and other critical boundaries, and in embodiments, copper can be used to manage pressure boundaries and / or other critical boundaries.

[0041] Reference Figures 3 to 9The illustration shows a first example vapor-liquid separator 100. In the example embodiment, each of the vapor-liquid separators 100a and 100b is substantially similar, and therefore, for the sake of brevity, only one vapor-liquid separator 100 will be described herein.

[0042] The vapor-liquid separator 100 includes a housing 102, within which a first flow path 110 and a second flow path 150 are defined. Although the housing 102 is generally illustrated as having a rectangular configuration, it is contemplated that the housing 102 may have any suitable shape and / or configuration that enables the vapor-liquid separator 100 to function as described herein. In some embodiments, the housing 102 may have a shape or configuration complementary to the configuration of the first flow path 110 and the second flow path 150. The first flow path 110 defines a fluid inlet converging section 112 that defines a fluid inlet 114 extending through an outer surface 104 of the housing 102. The fluid inlet 114 is fluidly coupled to a refrigeration loop 12 ( Figure 1 and Figure 2A It receives fluid (e.g., a saturated or at least partially subcooled liquid). The fluid inlet converging section 112 defines a generally truncated conical profile having internal dimensions that decrease in a direction extending away from the fluid inlet 114. In this way, the truncated conical profile results in an increase in the velocity of the liquid refrigerant flowing through the fluid inlet converging section 112 and a decrease in the static pressure. In an embodiment, the inner surface 112a of the fluid inlet converging section 112 may define a stepped conical profile having generally linear portions separated by the truncated conical portion. The stepped conical profile of the inner surface 112a can interrupt potential vortex loops of the fluid flowing through the fluid inlet converging section 112, thereby minimizing or otherwise mitigating the formation of vortices along the inner surface 112a of the fluid inlet converging section 112.

[0043] The first flow path 110 defines a fluid outlet divergence section 116, which defines a fluid outlet 118 extending through the outer surface 104 of the housing 102. The fluid outlet 118 is fluidly connected to the cooling loop 12. Figure 1 and Figure 2AThe liquid or two-phase refrigerant is discharged from the vapor-liquid separator 100 or otherwise discharged back into the refrigeration loop 12. The fluid outlet divergence section 116 defines a generally frustoconical profile having an internal dimension that increases in the direction extending toward the fluid outlet 118. In this way, the frustoconical profile results in a decrease in the velocity of the liquid refrigerant flowing through the fluid outlet divergence section 116 and an increase in the static pressure. In an embodiment, the inner surface 116a of the fluid outlet divergence section 116 may define a stepped conical profile having generally linear portions separated by the frustoconical portion. Although the fluid outlet divergence section 116 is generally illustrated as having a profile generally complementary to the profile of the fluid inlet convergence section 112, it is contemplated that the fluid outlet divergence section 116 may include any suitable profile that may be the same as or different from the profile of the fluid inlet convergence section 112.

[0044] Continue to refer to Figures 3 to 9 A first flow path 110 defines a first helical portion 120 that extends between a fluid inlet converging section 112 and a fluid outlet diverging section 116, fluidly connecting the fluid inlet converging section 112 to the fluid outlet diverging section 116. The first helical portion 120 defines a throat 122, the cross-sectional area of ​​which is less than or equal to the cross-sectional area of ​​a portion of the first helical portion 120 adjacent to the fluid inlet converging section 112. However, it is contemplated that the throat may define any cross-sectional area smaller than or larger than the cross-sectional area of ​​the first helical portion 120 and / or the first inlet converging section 112 adjacent to the throat 122. In this way, the throat 122 fluidly connects to the fluid inlet converging section 112 and / or receives liquid or two-phase refrigerant from the fluid inlet converging section 112. The throat 122 engages with the helical profile of the first helical portion 120 to produce an increase in the velocity of the fluid flowing through the first helical portion 120 and to separate vapor from the fluid. In some embodiments, the liquid flowing through the throat 122 and the first spiral portion 120 can be accelerated to approximately equal to the speed of sound of the fluid at the state (e.g., temperature, pressure, etc.) of the fluid flowing through the first spiral portion 120.

[0045] In some embodiments, the profile of the first helical portion 120 defines a generally circular cross-section adjacent to the fluid inlet converging section 112, transitions along a direction extending away from the fluid inlet converging section 112 to a generally non-circular cross-section such as a curve, an oval, etc., and transitions back to a circular cross-section adjacent to the fluid outlet diverging section 116. However, it is contemplated that the first flow path 110 and / or the first helical portion 120 may define any suitable cross-section at any portion along its length without departing from the scope of this disclosure. As will be understood, the slope or non-circular profile of the first helical portion 120 minimizes or otherwise mitigates the velocity difference between the vapor and liquid refrigerant flowing through the first helical portion 120.

[0046] The second flow path 150 defines a vapor outlet divergence section 152, which defines a vapor outlet 154 extending through the outer surface 104 of the housing 102. The vapor outlet 154 is fluidly connected to the refrigeration loop 12 and via a vapor injection conduit 52 ( Figure 1 and Figure 2A The vapor and / or gaseous refrigerant is discharged from the vapor-liquid separator 100 or otherwise discharged to the vapor injection port 50. The vapor outlet divergence section 152 defines a generally frustoconical profile having an internal dimension that increases in the direction extending toward the vapor outlet 154. In this way, the frustoconical profile results in a decrease in the velocity of the vapor flowing through the vapor outlet divergence section 152 and an increase in the static pressure. In some embodiments, the inner surface 152a of the vapor outlet divergence section 152 may define a stepped conical profile having generally linear portions separated by the frustoconical portion. Although the vapor outlet divergence section 152 is generally illustrated to have a profile that is generally complementary to the profiles of the fluid inlet converging section 112 and / or the fluid outlet divergence section 116, it is contemplated that the vapor outlet divergence section 152 may include any suitable profile that may be the same as or different from the profiles of the fluid inlet converging section 112 and / or the fluid outlet divergence section 116.

[0047] The second flow path 150 defines a second spiral portion 156 that extends between the first flow path 110 and the steam outlet divergence section 152 and transfers steam from the first flow path 110 to the steam outlet divergence section 152. In an embodiment, the second spiral portion 156 may be located at the steam inlet 158 ​​( Figure 5The first helical section 120 extends between the fluid inlet 114 and the vapor outlet 152. As described in further detail herein, the increased velocity of the liquid refrigerant flowing through the first flow path 110 causes vapor to form within the liquid refrigerant. The increased velocity of the liquid refrigerant generates or otherwise induces buoyancy to separate the vapor within the liquid refrigerant, causing the separated vapor to flow into (e.g., radially inward) the vapor inlet 158 ​​and the second helical section 156. In an embodiment, the second helical section 156 intersects or otherwise wraps around the first helical section 120. In this way, the first helical section 120 and the second helical section 156 may be arranged in a stacked or alternating manner in the direction extending between the fluid inlet 114 and each of the fluid outlet 118 and the vapor outlet 154. As described in further detail herein, the increased velocity of the fluid flowing through the first helical section 120 causes vapor within the first helical section 120 to flow into the second helical section 156.

[0048] In some embodiments, the profile of the second spiral portion 156 may have a generally circular cross-section adjacent to the steam inlet 158, transition to a generally non-circular cross-section in a direction extending away from the steam inlet 158, and transition back to a circular cross-section adjacent to the steam outlet divergence section 152. However, it is conceivable that the second flow path 150 and / or the second spiral portion 156 may define any suitable cross-section along any portion of its length that may be the same as or different from the profile of the first flow path 110.

[0049] As can be understood, the number of turns or coils of the first helical portion 120 and the second helical portion 156 affects or otherwise influences the velocity and / or pressure of the liquid refrigerant and vapor flowing through each of the first helical portion 120 and the second helical portion 156. Additionally, as described above, the profile or cross-section of the first helical portion 120 and the second helical portion 156 affects or otherwise influences the velocity of the vapor and liquid refrigerant flowing through each of the first helical portion 120 and the second helical portion 156. In this way, the non-circular cross-section of the first helical portion 120 minimizes or otherwise mitigates the velocity difference between the vapor and liquid refrigerant flowing through the first helical portion 120, and inhibits or otherwise minimizes vapor-liquid remixing. The non-circular cross-section of the second helical portion 156 causes a similar effect to the non-circular cross-section of the first helical portion. It is conceivable that the profile of each of the first helical portion 120 and the second helical portion 156 can vary along their length and can be scaled according to the liquid refrigerant used in the vapor compression system 10. In this way, the geometry of the first helical portion 120 and the second helical portion 156 can be proportional to or otherwise based on the ratio of vapor to liquid flowing through the first helical portion 120 and the second helical portion 156. As can be understood, the density of the refrigerant can determine or otherwise affect the dimensions of the vapor-liquid separator 100.

[0050] Reference Figures 7 to 9 The vapor-liquid separator 100 includes one or more vapor bridging sections or first bridging sections 160 upstream of a fluid outlet 118, fluidly connecting a first helical portion 120 to a second helical portion 156. One or more first bridging sections 160 direct or otherwise allow vapor flow within the first helical portion 120 into the second helical portion 156, resulting in an increased velocity of the vapor flowing through the second helical portion 156. Although the one or more first bridging sections 160 are generally illustrated as discrete tubular passages, it is contemplated that the one or more first bridging sections 160 may include any suitable profile, and each bridging section of the one or more first bridging sections 160 may include the same or different profiles.

[0051] One or more first bridging portions 160 define a steam inlet 162 of a first flow path 110 fluidly connected along the radially inner side of a first helical portion 120 and a steam outlet 164 of a second flow path 150 fluidly connected along the radially outer side of a second helical portion 156 or the area where liquid is collected. In this way, one or more first bridging portions 160 extend between the first helical portion 120 and the second helical portion 156; however, it is contemplated that one or more first bridging portions 160 may extend in any manner relative to the first helical portion 120 and / or the second helical portion 156. In a non-limiting embodiment, one or more first bridging portions 160 extend helically about the first helical portion 120. It is contemplated that, without departing from the scope of this disclosure, one or more first bridging portions 160 may be provided on any coil of each of the first helical portion 120 and the second helical portion 156. In a non-limiting embodiment, the first helical portion 120 and the second helical portion 156 each rotation includes a first bridging portion 160 to minimize or otherwise suppress the overlap of the first flow path 110 and the second flow path 150.

[0052] It is conceivable that the steam outlets 164 of one or more first bridging portions 160 can be fluidly connected to the second hollow interior portion downstream of the steam inlet 162, where the static pressure of the steam flowing through the second flow path 150 downstream of the steam inlet 162 is lower than the static pressure of the steam flowing through the second flow path 150 upstream of the steam inlet 162. As can be understood, positioning the steam outlets 164 downstream of the steam inlet 162 facilitates or otherwise increases the amount of steam flowing through one or more first bridging portions to the second flow path 150. In one embodiment, the steam inlet 162 is fluidly connected to the first flow path 110 along the radially inner side of the first helical portion 120, and the steam outlets 164 are fluidly connected to the second flow path 150 along the radially outer side of the second helical portion 156.

[0053] In some embodiments, the vapor-liquid separator 100 includes one or more liquid bridging sections, two-phase bridging sections, or second bridging sections 170 upstream of a fluid outlet 118, fluidly connecting a first helical portion 120 to a second helical portion 156. One or more second bridging sections 170 direct or otherwise allow liquid refrigerant within the second helical portion 156 to flow into the first helical portion 120. Although one or more second bridging sections 170 are generally illustrated as discrete tubular passages, it is contemplated that, without departing from this disclosure, one or more second bridging sections 170 may include any suitable profile, and each bridging section of one or more second bridging sections 170 may include a profile that is the same as or different from each other, or a profile that is the same as or different from one or more first bridging sections 160. One or more second bridging sections 170 define a liquid inlet 172 fluidly connected along the radially outer side of the second helical portion 156 to a second flow path 150 and a liquid outlet 174 fluidly connected along the first helical portion 120 to a first flow path 110. In this manner, one or more second bridging portions 170 extend between the first helical portion 120 and the second helical portion 156; however, it is contemplated that one or more second bridging portions 170 may extend in any manner relative to the first helical portion 120 and / or the second helical portion 156. In a non-limiting embodiment, one or more second bridging portions 170 extend helically about the first helical portion 120. It is contemplated that one or more second bridging portions 170 may be disposed on any coil of each of the first helical portion 120 and the second helical portion 156. In a non-limiting embodiment, the first helical portion 120 and the second helical portion 156 include one second bridging portion 170 per revolution to minimize or otherwise suppress the overlap of the first flow path 110 and the second flow path 150.

[0054] Reference Figures 3 to 9In operation, the fluid inlet 114 of the vapor-liquid separator 100 receives fluid, which in this embodiment is a liquid refrigerant (e.g., a saturated or at least partially subcooled liquid). The liquid refrigerant received by the fluid inlet 114 flows through the fluid inlet converging section 112, resulting in an increase in the velocity of the liquid refrigerant and a decrease in its static pressure. The liquid refrigerant is received by a first helical section 120, in which a throat 122 engages with the helical profile of the first helical section 120 to generate an increase in the velocity of the liquid refrigerant, which forms vapor within the liquid refrigerant. The increased velocity of the liquid refrigerant generates or otherwise induces buoyancy to separate the vapor within the liquid refrigerant, causing the separated vapor to flow toward the radially inward portion of the first helical section 120. The separated vapor flows through one or more first bridging sections 160 and into a second helical section 156 of a second flow path 150.

[0055] As can be understood, as the liquid refrigerant flows toward the fluid outlet divergence section 116 through the first spiral section 120, the vapor continues to separate from the liquid refrigerant and flows through one or more first bridging sections 160. The vapor received within the second spiral section 156 increases the velocity of the vapor flowing through the second spiral section 156 to approximately equal to the speed of sound at the vapor's state (e.g., temperature, pressure, etc.). Any liquid present within the second spiral section 156 flows toward the radially outer portion of the second spiral section 156 and is guided into the first spiral section 120 through one or more second bridging sections 170. The vapor flowing through the second spiral section 156 is received by the vapor outlet divergence section 152, in which the diverging frustoconical profile of the vapor outlet divergence section 152 results in a decrease in vapor velocity and an increase in static pressure. The vapor is discharged from the vapor outlet 154, where it is guided through the first vapor injection conduit 52a to the vapor injection port 50 of the compressor 20.

[0056] The increased velocity of the liquid refrigerant flowing through the first helical section 120 continues to form and separate vapor within the liquid refrigerant. Additional vapor separated from the liquid refrigerant flowing through the first helical section 120 flows radially inward toward the first helical section 120 and flows through one or more first bridging sections 160 into the second helical section 156. The liquid refrigerant flowing through the first helical section 120 flows into the fluid outlet divergence section 116, where the diverging frustoconical profile of the fluid outlet divergence section 116 causes a decrease in the velocity of the liquid refrigerant and an increase in the static pressure. The liquid refrigerant is discharged from the fluid outlet 118, where it is directed to the first expansion device 40.

[0057] Reference Figures 10 to 12 The illustration depicts another embodiment of a vapor-liquid separator, generally identified by reference numeral 200. The vapor-liquid separator 200 includes a housing 202, within which a first flow path 210 and a second flow path 250 are defined. Although the housing 202 is generally illustrated as having a rectangular configuration, it is contemplated that the housing 202 may include any configuration without departing from the scope of this disclosure, and in embodiments, the housing 202 may include a configuration complementary to the configuration of the first flow path 210 and the second flow path 250. The first flow path 210 defines a first hollow internal portion 212 extending between a fluid inlet 214 extending through an outer surface 204 of the housing 202 and a fluid outlet 216 extending through the outer surface 204 of the housing 202. The first flow path 210 includes a converging inlet section 218 having an internal dimension decreasing in a direction extending away from the fluid inlet 214. In an embodiment, the converging inlet section 218 defines a throat 220.

[0058] Fluid inlet 214 is fluidly connected to refrigeration loop 12 ( Figure 1 and Figure 2A The first flow path 210 receives fluid (e.g., a saturated or at least partially subcooled liquid). The first flow path 210 includes a helical portion 222 fluidly coupled to the converging inlet section 218 downstream of it, and in an embodiment, the helical portion 222 is fluidly coupled to the converging inlet section 218 downstream of the throat 220. As can be understood, the converging inlet section 218 and the helical portion 222 result in a decrease in the static pressure and an increase in the velocity of the liquid refrigerant flowing through the first flow path 210, and generate vapor from the liquid refrigerant.

[0059] The helical portion 222 includes an increasing internal dimension in the direction extending toward the fluid outlet 216. In some embodiments, the helical portion 222 may include a diverging outlet section 224 having an increasing internal dimension in the direction extending toward the fluid outlet 216. As will be understood, the increased internal dimensions of the helical portion 222 and / or the diverging outlet section 224 result in a decrease in the velocity of the liquid refrigerant flowing through the helical portion 222 and exiting the fluid outlet 216 and an increase in the static pressure. Although the first flow path 210 is generally illustrated as having a circular profile, it is contemplated that the first flow path 210 may include any profile that may be the same or different along the same length as the first flow path 210 without departing from the scope of this disclosure. It is contemplated that the helical portion 222 may include a variable pitch extending toward the fluid outlet 216. Although the helical portion 222 is generally illustrated as having a pitch that increases in the direction extending toward the fluid outlet 216, it is conceivable that, without departing from the scope of this disclosure, the helical portion 222 may include any pitch that may be constant, decrease in the direction extending toward the fluid outlet 216, or may be variable.

[0060] Continue to refer to Figures 10 to 12 The second flow path 250 defines a second hollow interior portion 252 that extends between the first hollow interior portion 212 of the first flow path 210 and a steam outlet 254 extending through the outer surface 204 of the housing 202, and transfers steam from the first hollow interior portion 212 of the first flow path 210 to the steam outlet 254 extending through the outer surface 204 of the housing 202. In an embodiment, the second hollow interior portion 252 may extend between a steam inlet 262 and a steam outlet 254, connecting the steam inlet 262 to the steam outlet 254. The steam inlet 262 is located downstream of the fluid inlet 214 and receives steam separated from the liquid refrigerant flowing through the spiral portion 222 of the first flow path 210. The second flow path 250 includes a spiral portion 256 that is fluidly coupled to each of the steam inlet 262 and the steam outlet 254. The spiral portion 256 of the second flow path 250 includes an internal dimension that increases in the direction extending toward the steam outlet 254. As can be understood, the increased internal dimensions of the spiral section 256 result in a decrease in the velocity of the steam flowing through the spiral section 256 and exiting the steam outlet 254, and an increase in the static pressure.

[0061] Steam outlet 254 is fluidly connected to the first steam injection conduit 52a. Figure 1 and Figure 2AThis directs steam from the steam outlet 254 of the vapor-liquid separator 200 to the steam injection port 50 of the compressor 20. In an exemplary embodiment, the helical portion 222 of the first flow path 210 is arranged radially outward from the helical portion 256 of the second flow path 250; however, it is contemplated that the first helical portion 222 and the second helical portion 256 may be arranged relative to each other in any relationship without departing from the scope of this disclosure. In a non-limiting embodiment, the helical portion 222 of the first flow path 210 is arranged concentrically about the helical portion 256 of the second flow path 250.

[0062] The vapor-liquid separator 200 includes one or more bridging sections 260 that fluidly connect a first hollow interior portion 212 to a second hollow interior portion 252 upstream of the vapor outlet 254 and along the helical portions 222, 256 of each of the first flow path 210 and the second flow path 250. In an embodiment, the one or more bridging sections 260 are a single continuous bridging section between the helical portion 222 of the first flow path 210 and the helical portion 256 of the second flow path 250. In this way, the increased velocity of the liquid refrigerant flowing through the helical portion 222 of the first flow path 210 causes vapor within the liquid refrigerant to flow via the one or more bridging sections 260 into the second hollow interior portion 252 of the helical portion of the second flow path 250. Although generally described as a single continuous bridging section, it is contemplated that the one or more bridging sections 260 may be discontinuous, or differently, may be arranged in a spaced-apart relationship to form multiple discrete bridging sections.

[0063] Vapor-liquid separator 200 operates in a similar manner to vapor-liquid separator 100, and therefore, for the sake of brevity, the operation of vapor-liquid separator 200 will not be described in detail herein.

[0064] Reference Figure 13 The figure illustrates a schematic diagram of another embodiment of a vapor compression system utilizing vapor-liquid separators 100 and 200, and the vapor compression system is generally identified by reference numeral 1300. Vapor compression system 1300 is substantially similar to vapor compression system 10, and therefore, for the sake of brevity, this document will only describe in detail the differences between vapor compression system 1300 and vapor compression system 10.

[0065] The vapor compression system 1300 is a single-stage compression system comprising a single reversible closed refrigerant loop 1302, which includes an indoor heat exchanger 1304, an outdoor heat exchanger 1306, a first multi-way valve or reversing valve 1308, a second multi-way valve or reversing valve 1310, a compressor 20, an expansion device 1314, a vapor-liquid separator 100, and a flow valve 1316. In other embodiments of this disclosure, the vapor compression system 1300 may include multiple refrigerant loops to accommodate multiple compressors, or may operate in parallel with another system, such as a humidity control system. The flow valve 1316 is switchable between a first position that allows vapor to flow from the vapor-liquid separator 100 to the compressor inlet 22, and a second position that prevents vapor from flowing from the vapor-liquid separator 100 to the compressor inlet 22 while allowing refrigerant to flow back from the injection port 50 to the compressor inlet 22, thereby reducing the displacement of the compressor 20.

[0066] Reference Figure 14 The illustration shows a schematic diagram of another embodiment of a vapor compression system utilizing vapor-liquid separators 100 and 200, and the vapor compression system is generally identified by reference numeral 1400. Vapor compression system 1400 is substantially similar to vapor compression systems 10 and 1400, and therefore, for the sake of brevity, this document will only describe in detail the differences between vapor compression system 1400 and vapor compression systems 10 and 1400.

[0067] The vapor compression system 1400 is a multi-stage compression system and includes a shut-off valve 1460 inserted between the vapor-liquid separator 100 and the flow valve 1416, and an expansion valve 1462 disposed upstream of the vapor-liquid separator 100. The shut-off valve 1460 is switchable between a first position and a second position, the first position inhibiting the flow of vapor from the vapor-liquid separator 100 to the flow valve 1416 and thus to the injection port 50, and the second position allowing vapor to flow from the vapor-liquid separator 100 to the flow valve 1416 and thus to the injection port 50.

[0068] Go to Figure 15A and Figure 15BThe figure illustrates a method of operating a vapor-liquid separator, and the method of operating the vapor-liquid separator is generally identified by reference numeral 1500. The liquid inlet of the first flow path of the vapor-liquid separator receives 1502 saturated liquid, subcooled liquid, or a two-phase refrigerant with low vapor mass. A fluid inlet convergence section causes 1504 a decrease in static pressure and an increase in velocity of the fluid flowing through the fluid inlet convergence section. 1506 The spiral portion of the first flow path receives 1506 the fluid flowing through the fluid inlet convergence section, which causes 1508 a decrease in static pressure and an increase in velocity of the fluid flowing through the spiral portion, and vapor is generated from the fluid. The increased velocity of the fluid flowing through the spiral portion of the first flow path generates 1510 buoyancy, causing the vapor separated from the fluid to flow into a second flow path via one or more bridging sections. In an embodiment, the fluid flowing through the spiral portion of the second flow path is transferred 1512 to the first spiral portion of the first flow path via one or more fluid bridging sections. The steam outlet divergence section receives 1514 steam flowing through the second flow path, which causes 1516 the steam velocity to decrease and the static pressure to increase, and the steam is discharged from the steam outlet 1518. The fluid outlet divergence section receives 1520 fluid flowing through the first flow path, and the fluid flowing through the first flow path is discharged from the fluid outlet 1522.

[0069] It is conceivable that the working fluid may include at least one refrigerant suitable for use in a vapor compression cycle. Non-limiting examples of suitable refrigerants include natural refrigerants (e.g., carbon dioxide, water, ammonia, hydrocarbons, etc.), fluorocarbon-based refrigerants, and refrigerants with low global warming potential, such as ASHRAE Classification A1 and A2L refrigerants. Non-limiting examples of A1 refrigerants include carbon dioxide (R-744), dichlorofluoromethane (R-22), 1,1-difluoroethane (R152a), 1,1,1,2-tetrafluoroethane (R134A), and R410A (a near-azeotropic mixture of difluoromethane (R-32) and pentafluoroethane (R-125)), and trifluorochloropropene (R-1233, including cis- and trans-1-chloro-3,3, 3-Trifluoropropylene (HFO-1233zd) isomers (HFO-1233zd(Z) and HFO-1233zd(E)) and hexafluorobutene (HFO-1336, including HFO-1336mzz(Z) and 1336mzz(E)). Non-limiting examples of A2L refrigerants include difluoromethane (R-32) and hydrofluoroolefins (HFO). Suitable HFO refrigerants are described, for example, in U.S. Patent No. 4,788,352 to Smutny and U.S. Patent No. 8,444,874 to Singh et al., the relevant portions of which are incorporated herein by reference. HFO may include 2,3,3,3-tetrafluoroprop-1-ene (HFO-1234yf) and trans-1,3,3,3-tetrafluoroprop-1-ene (HFO-1234ze).Non-limiting suitable examples of specific HFO refrigerants include 3,3,3-trifluoropropylene (HFO-1234zf), HFO-1234 refrigerants such as 2,3,3,3-tetrafluoropropylene (HFO-1234yf), 1,2,3,3-tetrafluoropropylene (HFO-1234ze), cis- and trans-1,3,3,3-tetrafluoropropylene (HFO-1234ye), and pentafluoropropylene (HFO-1225) such as 1,1,3,3,3-pentafluoropropylene. Alkenes (HFO-1225zc), hexafluorobutenes (HFO-1336) such as cis-1,1,1,4,4,4-hexafluoro-2-butene (HFO-1336mzz-Z) and trans-1,1,1,4,4,4-hexafluoro-2-butene (R1336mzz(E)), or compounds with hydrogen at the terminal unsaturated carbon such as 1,2,3,3,3, pentafluoropropylene (HFO-1225yez), fluorochloropropylenes such as trifluoropropylene, monochloropropylene (H HFO refrigerants include CF3CCl═CH2 (HFO-1233xf) and CF3CH═CHCl (HFO-1233zd) (including trans (E) and cis (Z) isomers (HFO-1233zd(E) and HFO-1233zd(Z)), (E)-1,2-difluoroethylene (R-1132(E)), and any combination thereof. In some respects, HFO refrigerants may be selected from the group consisting of: R-1234y f, R-1234ze, R1233zd(E), R1233zd(Z), R1336mzz(Z), R1336mzz(E), R-1132(E), and combinations thereof. In some examples, these refrigerants are used in combination with other A1 or A2L refrigerants or other refrigerants, such as A3 or B1 or B2 refrigerants—including natural or flammable refrigerants (e.g., dimethyl ether (R-E170) or propane (C3H8 or R-290)).

[0070] In some examples, the vapor compression system 10 operates using a working fluid comprising a refrigerant blend consisting of at least two refrigerants. Suitable refrigerant blends and suitable climate control systems for use with such refrigerant blends are described, for example, in U.S. Patent Application Serial No. 17 / 507,403, filed October 2021 and published April 27, 2023, by Welch et al., as U.S. Patent Application Publication No. 2023 / 0130167, the entire disclosure of which is incorporated herein by reference. It is contemplated that the features of the vapor compression system 10 can be used in any combination with the system described in U.S. Patent Application Publication No. 2023 / 0130167, which is previously incorporated herein by reference. In some examples, the refrigerant blend comprises an A1 refrigerant mixed with at least one other refrigerant, such as carbon dioxide (R-744). As will be understood, carbon dioxide refrigerant is suitable for use in subcritical system designs. An example of a suitable non-limiting refrigerant blend includes CO2 (R-744), a more volatile high-pressure refrigerant, mixed with an HFO refrigerant (e.g., R-1233zd(E)), a less volatile low-pressure fluid. The refrigerant blend can be a “high-slip” refrigerant blend having a first refrigerant (e.g., CO2) and a second refrigerant, the first refrigerant having a relatively low normal boiling point (at 1 atm) and the second refrigerant having a relatively high normal boiling point. The difference between the normal boiling points of the first and second refrigerants is greater than or equal to 25°C. As a non-limiting example, the refrigerant blend includes CO2 having a normal boiling point of approximately 78°C at 1 atm and R-1233zd(e) having a normal boiling point of approximately 18°C ​​at 1 atm, with a difference in boiling points of approximately 96°C.

[0071] Suitable working fluid refrigerant blends include refrigerants selected from the group consisting of: R-744, R-22, R134A, R410A, R-1234yf, R-1234ze, R1233zd(E), R1233zd(Z), R1336mzz(Z), R1336mzz(E), and combinations thereof. Alternatively, the first and second refrigerants included in the refrigerant blends are independently selected from the group consisting of: R-744, R-22, R152a, R134A, R410A, R-E170, R-32, HFO, R-290, R-601 (pentane), hexane, and combinations thereof. In some examples, the first refrigerant is selected from the group consisting of R-744, R-22, R134A, R410A, R-E170, R-32, HFO and combinations thereof, and the second refrigerant is selected from the group consisting of 2,3,3,3-tetrafluoroprop-1-ene (R1234yf), 1,3,3,3-tetrafluoroprop-1-ene (R-1234ze), 1-chloro-3,3,3-trifluoropropene (HFO-1233zd(E)), 1-chloro-3,3,3-trifluoropropene (HFO-1233zd(Z)), 1,1,1,4,4,4-hexafluoro-2-butene (HFO-1336mzz) and combinations thereof.

[0072] The working fluid may include one or more refrigerants in combination with a refrigeration lubricant, such as the refrigerants described above. For example, the working fluid may include synthetic oils. In some examples, the lubricant may include polyvinyl ether (PVE) oil, polyalphaolefin (PAO), polyalkylene glycol (PAG), alkylbenzene, mineral oil, or ester-based oil such as polyol ester (POE) oil. POE oil may be suitably used in the presence of carbon dioxide (R-744) in the working fluid (e.g., in a refrigerant blend). Suitable POE oils may include compounds formed from carboxylic acids and polyols. Such POE compounds may be formed from carboxylic acids and polyols selected from the group consisting of: valeric acid, 2-methylbutyric acid, hexanoic acid, heptanoic acid, 3,3,5-trimethylhexanoic acid, 2-ethylhexanoic acid, octanoic acid, nonanoic acid, and isononanoic acid, and combinations thereof; and the polyols selected from the group consisting of: pentaerythritol, dipentaerythritol, neopentyl glycol, trimethylpropanol, and combinations thereof.

[0073] The technical benefits of the methods and systems described herein include improved efficiency of reversible vapor compression systems by incorporating a vapor-liquid separator. Compared to heat exchangers or flash tanks, the vapor-liquid separator utilizes two helical flow paths fluidly connected by one or more bridging sections to generate more vapor and deliver it to the compressor. The vapor-liquid separator can replace flash tanks and / or heat exchangers used in vapor energy-saving loops, thereby reducing the complexity and cost of vapor compressor systems.

[0074] As used herein, when used in conjunction with ranges of size, concentration, temperature or other physical or chemical properties or characteristics, the terms “about,” “basically,” “essentially,” and “approximately” are intended to cover variations that may exist within the upper and / or lower limits of the range of properties or characteristics, including variations caused, for example, by rounding, measurement methods, or other statistical changes.

[0075] When elements or embodiments of this disclosure are introduced, the articles “a,” “an,” “the,” and “the” are intended to indicate the presence of one or more elements. The terms “comprising,” “including,” “containing,” and “having” are intended to be inclusive and mean that additional elements may be present in addition to those listed. The use of terms indicating a particular orientation (e.g., “top,” “bottom,” “side,” etc.) is for ease of description and does not require any particular orientation of the described object.

[0076] Since various changes can be made to the above-described constructions and methods without departing from the scope of this disclosure, all content contained in the above description and shown in the accompanying drawings should be interpreted as illustrative and not restrictive.

Claims

1. A vapor-liquid separator, comprising: A first flow path extends between a fluid inlet and a fluid outlet, wherein the first flow path defines a helical portion, wherein the helical portion causes a decrease in the static pressure and an increase in the velocity of the fluid flowing through the first flow path, so as to generate steam from the fluid. A second flow path extends between the first flow path and the steam outlet and fluidly transfers steam from the first flow path to the steam outlet, wherein the second flow path defines a spiral portion; and One or more bridging portions upstream of the steam outlet and along a helical portion of each of the first and second flow paths fluidly connect the first flow path to the second flow path, wherein an increased velocity of the fluid flowing through the first flow path causes steam in the first flow path to flow into the second flow path via the one or more bridging portions. The steam received in the second flow path is discharged from the steam outlet, and the fluid flowing through the first flow path is discharged from the fluid outlet.

2. The vapor-liquid separator according to claim 1, wherein, The one or more bridging portions include at least one steam bridging portion, the at least one steam bridging portion comprising a radially inner connection to a steam inlet of the first flow path along a spiral portion of the first flow path, and a radially outer connection to a steam outlet of the second flow path along a spiral portion of the second flow path, to allow steam in the first flow path to flow into the second flow path.

3. The vapor-liquid separator according to claim 1, wherein, The one or more bridging portions include at least one liquid bridging portion, the at least one liquid bridging portion including a region from which liquid is collected in the spiral portion of the second flow path to a liquid inlet of the second flow path, and a region along the spiral portion of the first flow path to a fluid outlet of the first flow path, to allow liquid in the second flow path to flow into the first flow path.

4. The vapor-liquid separator according to claim 1, wherein, The one or more bridging sections terminate upstream of each of the steam outlet and the fluid outlet, wherein the first flow path and the second flow path include corresponding first divergence sections and second divergence sections downstream of the termination points of the one or more bridging sections. The cross-sectional area of ​​the first diverging section increases as the first flow path extends toward the fluid outlet, thereby increasing the static pressure of the fluid flowing through the first diverging section. The cross-sectional area of ​​the second diverging section increases as the second flow path extends toward the steam outlet, thereby increasing the static pressure of the steam flowing through the second diverging section.

5. The vapor-liquid separator according to claim 1, wherein, The one or more bridging portions include a single continuous bridging portion between the first flow path and the second flow path. The first flow path is arranged radially outward from the second flow path.

6. The vapor-liquid separator according to claim 1, wherein, The spiral portion of the first flow path is intertwined with the spiral portion of the second flow path.

7. The vapor-liquid separator according to claim 6, wherein, The one or more bridging portions include discrete tubular bridging portion passages extending between the first flow path and the second flow path.

8. The vapor-liquid separator according to claim 6, wherein, The spiral portion of the first flow path or the spiral portion of the second flow path defines a non-circular cross-section.

9. The vapor-liquid separator of claim 1, further comprising an integral body defining the first flow path, the second flow path, and the one or more bridging portions.

10. The vapor-liquid separator according to claim 1, further comprising: A first conduit, the first conduit defining the first flow path; A second conduit, the second conduit defining the second flow path; as well as At least one third catheter, the at least one third catheter defining the one or more bridging portions and fluidly connecting the first catheter to the second catheter.

11. A vapor-liquid separator, the vapor-liquid separator comprising: A first flow path, the first flow path comprising: A fluid inlet section that generates an increase in the velocity of the fluid flowing through the fluid inlet section and a decrease in the static pressure; A fluid outlet section, wherein the fluid outlet section causes a decrease in the velocity of the fluid flowing through the fluid outlet section and an increase in the static pressure; and A first spiral portion extends between the fluid inlet section and the fluid outlet section and fluidly connects the fluid inlet section to the fluid outlet section. This first spiral portion increases the velocity of the fluid flowing through it and causes separation of vapor and fluid. The second fluid flow path includes: A steam outlet section that defines a steam outlet and causes an increase in the static pressure and a decrease in the velocity of the steam flowing through the steam outlet section; A second spiral portion extends between the first flow path and the steam outlet section and fluidly transfers steam from the first flow path to the steam outlet section. The second spiral portion is wrapped around the first spiral portion, wherein an increased velocity of the fluid flowing through the first spiral portion causes steam within the first spiral portion to flow into the second spiral portion; and One or more bridging portions fluidly connect the first helical portion to the second helical portion, the bridging portions allowing steam in the first helical portion to flow into the second helical portion via the bridging portions, wherein receiving steam in the second helical portion results in an increase in the velocity of the steam flowing through the second helical portion. The steam received in the second spiral section is discharged from the steam outlet, and the fluid flowing through the first spiral section is discharged from the fluid outlet.

12. The vapor-liquid separator according to claim 11, wherein, The first spiral portion transitions from a circular profile adjacent to the fluid inlet section to a non-circular profile along the direction extending from the fluid inlet section to the fluid outlet section, and then transitions to a circular profile adjacent to the fluid outlet section.

13. The vapor-liquid separator according to claim 12, wherein, The second spiral portion transitions from a non-circular profile to a circular profile adjacent to the steam outlet section along the direction extending toward the steam outlet section.

14. The vapor-liquid separator according to claim 11, wherein, Each of the one or more bridging portions includes a discrete tubular passage extending between the first helical portion and the second helical portion.

15. The vapor-liquid separator of claim 11, further comprising one or more second bridging portions upstream of each of the fluid outlet and the vapor outlet, the one or more second bridging portions allowing fluid flowing in the second helical portion to flow into the first helical portion.

16. A system comprising: A fluid compression circuit, the fluid compression circuit including a compressor capable of operating to compress pairs of refrigerants; as well as A vapor-liquid separator, fluidly connected to the fluid compression circuit to receive liquid refrigerant from the fluid compression circuit, the vapor-liquid separator comprising: A first flow path extends between a fluid inlet and a fluid outlet, wherein the first flow path includes a spiral portion that causes a decrease in the static pressure and an increase in the velocity of the liquid refrigerant flowing through the first flow path, so as to generate vapor from the liquid refrigerant. A second flow path extends between the first flow path and the steam outlet and fluidly transfers steam from the first flow path to the steam outlet; and One or more bridging portions fluidly connect the first flow path to the second flow path, wherein an increased velocity of the liquid refrigerant flowing through the first flow path causes vapor within the first flow path to flow into the second flow path via the one or more bridging portions. The steam received in the second flow path is discharged from the steam outlet to the intermediate compression stage of the compressor.

17. The system according to claim 16, wherein, The one or more bridging sections of the vapor-liquid separator terminate upstream of each of the steam outlet and the fluid outlet, wherein the first flow path and the second flow path include corresponding first divergence sections and second divergence sections downstream of the termination positions of the one or more bridging sections.

18. The system according to claim 16, wherein, The first flow path is arranged radially outward from the second flow path.

19. The system according to claim 16, wherein, The spiral portion of the first flow path is intertwined with the spiral portion of the second flow path.

20. The system according to claim 19, wherein, The one or more bridging portions include discrete tubular bridging portion passages extending between the first flow path and the second flow path.

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