VAPOR-LIQUID SEPARATORS AND SYSTEMS INCLUDING THEM

Abstract

A vapor-liquid separator comprises a first flow path extending between a fluid inlet and a fluid outlet and featuring a helical section; a second flow path extending between the first flow path and the vapor outlet, transferring vapor from the first flow path to the vapor outlet and also defining a helical section; and one or more bridges that fluidically couple the first flow path to the second flow. The helical section of the first flow path causes a reduction in static pressure and an increase in velocity of the fluid flowing through the first flow path, generating vapor that flows over the one or more bridges into the second flow path. The vapor received in the second flow path is discharged from the vapor outlet, and the fluid flowing through the first flow path is discharged from the fluid outlet.

Description

TECHNICAL AREA

[0001] The technical field of the disclosure relates generally to heating, ventilation and air conditioning (HVAC) systems and in particular to pressure recovery devices for reversible vapor compression systems. TECHNICAL BACKGROUND

[0002] Vapor compression systems are widely used in climate control to provide heat pump, refrigeration, and / or air conditioning functions. A typical vapor compression system includes a fluid circuit with a first heat exchanger (e.g., a condenser that converts one phase of the refrigerant from a gas / vapor phase to a liquid phase), a second heat exchanger (e.g., an evaporator that converts one phase of the refrigerant from a liquid phase to a gas / vapor phase), an expansion device located between the first and second heat exchangers, and a compressor that can circulate and pressurize a working gas / vapor fluid (and optionally a lubricating oil) between the first and second heat exchangers (e.g., the condenser and evaporator).The compressor is typically a mechanical compressor that serves to pressurize the working fluid, which can then be condensed and evaporated as it circulates within the system to transfer heat into or out of the system.

[0003] The throttling process in the expansion device leads to significant energy losses and inefficiencies during the steam compression cycle. 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. Various devices are typically used to improve compressor efficiency, such as flash tanks or plate heat exchangers, ejector cycles, pressure exchangers with centrifugal separation or energy recovery, and two-phase turbines. Steam injection systems are also used to improve compressor efficiency by supplying the compressor with steam at medium pressure.Since the intermediate pressure steam is at a slightly higher pressure than the intake pressure and a slightly lower pressure than the outlet pressure, the work required by the compressor to produce steam at outlet pressure is reduced.

[0004] These expansion energy loss recovery devices can be complex and expensive, and are often limited in the amount of steam that can be separated and returned to the compressor. As one might expect, higher cycle efficiencies necessitate 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 energy loss recovery device that is less complex, less expensive, and more efficient than current systems.

[0005] This section aims to introduce the reader to various aspects of the prior art that may be related to different aspects of the disclosure described and / or claimed below. It is assumed that this discussion will be helpful in providing the reader with background information that will enable a better understanding of the various aspects of the present disclosure. Accordingly, these statements should be understood in this sense and not as an admission of the prior art. SUMMARY

[0006] One aspect of the disclosure relates to a vapor-liquid separator with a first flow path, a second flow path, and one or more bridges. The first flow path extends between a fluid inlet and a fluid outlet and defines a helical section. The helical section causes a decrease in static pressure and an increase in velocity of a fluid flowing through the first flow path to generate vapor from the fluid. The second flow path extends between and fluidically transfers vapor from the first flow path to a vapor outlet and forms a helical section.The one or more bridges fluidically couple the first flow path with the second flow path upstream of the steam outlet and along the helical section of both the first and second flow paths. The increased velocity of the fluid flowing through the first flow path causes the steam in the first flow path to flow over the one or more bridges into the second flow path. 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 the disclosure relates to a vapor-liquid separator with a first flow path and a second flow path. The first flow path comprises a fluid inlet section, a fluid outlet section, and a first helical section extending between the fluid inlet and outlet sections, fluidically connecting them. The fluid inlet section causes an increase in velocity and a decrease in the static pressure of the fluid flowing through it. The fluid outlet section causes a decrease in velocity and an increase in the static pressure of the fluid flowing through it.The first helical section causes an increase in the velocity of the fluid flowing through it and the separation of steam from the fluid. The second fluid flow path comprises a steam outlet section, a second helical section extending between the first flow path and the steam outlet section, which fluidically transfers steam from the first flow path to the steam outlet section, and one or more bridges that fluidly couple the first and second helical sections. The steam outlet section defines a steam outlet and causes an increase in static pressure and a decrease in the velocity of the steam flowing through it. The second helical section is intertwined with the first helical section.The increased velocity of the fluid flowing through the first helical section causes the steam in the first helical section to flow into the second helical section. One or more bridges allow the steam in the first helical section to flow over them into the second helical section. The steam received in the second helical section causes an increase in the velocity of the steam flowing through it. The steam received in the second helical section is discharged from the steam outlet, and the fluid flowing through the first helical section is discharged from the fluid outlet.

[0008] Another aspect of the disclosure relates to a system with a fluid compression circuit and a vapor-liquid separator that is fluidly connected to the fluid compression circuit. The fluid compression circuit includes a compressor that can be operated to compress a refrigerant. 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 bridges. The first flow path extends between a fluid inlet and a fluid outlet and includes a helical section that causes a reduction in static pressure and an increase in the velocity of the liquid refrigerant flowing through the first flow path, in order to generate vapor from the liquid refrigerant.The second flow path extends between the first flow path and the steam outlet and transfers steam from the first flow path to the steam outlet. One or more bridges fluidically couple the first and second flow paths. The increased velocity of the liquid refrigerant flowing through the first flow path causes the steam in the first flow path to flow over the one or more bridges into the second flow path.

[0009] The steam received in the second flow path is directed from the steam outlet to an intermediate compression stage of the compressor.

[0010] There are various refinements to the features mentioned in connection with the aspects of this disclosure mentioned above. Further features may also be included in these aspects. These refinements and additional features may occur individually or in any combination. For example, various features discussed below in relation to one of the embodiments of this disclosure may be included individually or in any combination in any of the aspects of this disclosure described above. BRIEF DESCRIPTION OF THE DRAWINGS Fig. Figure 1 is a schematic diagram of an exemplary vapor compression system, showing the vapor compression system in a cooling mode; Fig. 2A is a schematic diagram of the vapor compression system from Fig. 1, which shows the steam compression system in a heating mode; Fig. Figure 2B is a schematic diagram of another embodiment of the vapor compression system from Fig. 1 with a second internal heat exchanger; Fig. Figure 3 is a perspective view of an exemplary vapor-liquid separator for use in the vapor compression systems of the Fig. 1-2B is suitable; Fig. Figure 4 is a side view of the vapor-liquid separator made of Fig. 3; Fig. 5 is an enlarged view of the in Fig. 4 specified area; Fig. Figure 6 is a front view of the vapor-liquid separator made of Fig. 3; Fig. Figure 7 is a side view of a helical section of a first flow path and a helical section of a second flow path of the vapor-liquid separator made of Fig. 3; Fig. Figure 8 is an enlarged view of the helical sections of the first and second flow paths of the vapor-liquid separator of Fig. 3, which shows the fluid bridges that couple the first helical section to the second helical section; Fig. Figure 9 is an enlarged, perspective view of the helical sections of the first and second flow paths of the vapor-liquid separator. Fig. 3, which shows the steam bridges connecting the first helical section to the second helical section; Fig. Figure 10 shows a view of another embodiment of a vapor-liquid separator, intended for use in the vapor compression systems of the Fig. 1-2B is suitable; Fig. Figure 11 is a cross-sectional view of the vapor-liquid separator made of Fig. 10; Fig. 12 is an enlarged view of the in Fig. 11 specified area; Fig. Figure 13 is a schematic diagram of another embodiment of a vapor compression system, in which the vapor-liquid separators of the Fig. 3-12 can be used; Fig. Figure 14 is a schematic diagram of another embodiment of a vapor compression system, in which the vapor-liquid separators of the Fig. 3-12 can be used; Fig. Figure 15A is a flowchart of an exemplary method for operating a vapor-liquid separator according to the disclosure; and Fig. 15B is a continuation of the flowchart from Fig. 15A.

[0011] The corresponding reference symbols indicate the relevant parts in the drawings. DETAILED DESCRIPTION

[0012] For the sake of brevity, examples relating to an operational reversible vapor compression system for heating or cooling an interior space are described. However, other exemplary methods and systems for regulating the temperature of an enclosed space can also be used. The efficiency of a reversible vapor compression system can be increased by incorporating a vapor-liquid separator, which utilizes two helical flow paths fluidly coupled by one or more bridges to generate and supply more vapor to a compressor than a heat exchanger, flash tank, or expander. The vapor-liquid separator can replace a flash tank and / or heat exchanger used in a vapor-saving circuit, thereby reducing the complexity and cost of the vapor compressor system.

[0013] In the Fig. 1 and Fig. Figure 2A shows schematic diagrams of an exemplary vapor compression system for cooling or heating an interior space surrounded by an exterior space, and is generally designated by reference numeral 10. The vapor compression system 10 can be used as part of a heating, ventilation, and air conditioning (HVAC) system, a cooling system, and / or a heat pump without derogating from the scope of the disclosure. The vapor compression system 10 comprises a single, reversible, closed refrigerant circuit 12, which includes an interior heat exchanger 14, an exterior heat exchanger 16, a multi-way 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 can comprise multiple refrigerant circuits to accommodate several compressors, or it can be operated in parallel with another system, e.g., a humidity control system. As described in detail here, the multi-way valve can be operated, or 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 is operated for cooling or heating the interior 80.

[0014] Fig. Figure 1 shows the vapor compression system 10 with the multi-way valve 18 in a first position for operation in a cooling mode. In cooling mode, the refrigerant enters the compressor 20 as a low-pressure, low-temperature gas at an inlet of the compressor, or compressor inlet 22 (e.g., a suction flow). The compressor 20 increases the pressure of the refrigerant, which exits the compressor 20 as a high-pressure, high-temperature gas at an outlet of the compressor, or compressor outlet 24 (e.g., as a discharge flow). The compressor 20 can be driven by any suitable engine and, in exemplary embodiments, can also be driven by a variable frequency drive (VFD) 26.

[0015] The discharge flow passes through a first flow path 18a of the multi-way valve 18, which directs the refrigerant to the outdoor heat exchanger 16. The outdoor heat exchanger 16 functions as a condenser, transferring heat Q to the refrigerant. out The system extracts heat and transfers it to an outdoor space 82 to convert the refrigerant gas into a high-pressure, high-temperature liquid. A first blower 28 generates a first airflow 30 from the outdoor heat exchanger 16 towards the outdoor space 82 to carry warm air into the outdoor space 82. The first blower 28 can be driven by any suitable power engine and, in exemplary embodiments, can be driven by a second VFD 32.

[0016] Downstream of the external 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 overall 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 part 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 another type of expansion device that allows the vapor compression system 10 to operate as described.

[0017] The first vapor-liquid separator 100a is fluidically connected to the internal heat exchanger 14, which receives liquid refrigerant or a two-phase mixture of liquid and gaseous refrigerant at its inlet. As described in detail here, the first vapor-liquid separator 100a causes the fluid (e.g., saturated or at least partially supercooled liquid) to accelerate, thereby separating the vapor from the fluid. The vapor is passed through a divergent section of a first flow path of the first vapor-liquid separator 100a to convert the vapor velocity into pressure, which is discharged from a vapor outlet and directed via flow paths 52a and 52 to a vapor injection port 50 of an intermediate pressure section of the compressor 20. The vapor separated from the fluid is then transferred to the internal heat exchanger 14.Separated liquid is passed through a divergent section of a second flow path of the first vapor-liquid separator 100a to convert the velocity of the liquid into pressure, which exits from a fluid outlet and is fed to the first expansion device 40.

[0018] The expanded liquid refrigerant is directed from the first expansion device 40 to the internal heat exchanger 14. The internal heat exchanger 14 functions as an evaporator, transferring heat Q from the refrigerant. inThe refrigerant is drawn from the interior 80 to change its phase from liquid to gaseous. A second blower 34 generates a second airflow 36 through, or over, the interior heat exchanger 14 towards the interior 80, thus cooling the interior 80. The second blower 34 can be driven by any suitable engine and, in exemplary embodiments, can be driven by a third VFD 38. The gaseous refrigerant flow then flows through a first suction flow path 18b of the multi-way valve 18 and is returned as a suction flow to the inlet of the compressor 22.

[0019] With reference to Fig. Figure 2A shows the vapor compression system 10 with the multi-way valve 18 in a second position for operation in a heating mode. Similar to the cooling mode, the refrigerant enters the compressor 20 at the compressor inlet 22 as a low-pressure, low-temperature gas (e.g., a suction flow). The compressor 20 increases the overall pressure of the refrigerant, which exits the compressor 20 at the compressor outlet 24 as a high-pressure, high-temperature gas (e.g., a discharge flow). The discharge flow passes through a second flow path 18c of the multi-way valve 18, which directs the refrigerant to the internal heat exchanger 14. The internal heat exchanger 14 acts as a condenser, transferring heat Q to the refrigerant. out The second blower 34 extracts the refrigerant gas to convert it into a liquid at high pressure and high temperature. The second blower 34 generates the second airflow 36 through, or via, the internal heat exchanger 14 towards the interior 80, thereby releasing heat Q. outinto the interior 80 from.

[0020] Downstream of the internal 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 reaches its boiling point at that pressure, and the refrigerant becomes a two-phase mixture as part of the liquid refrigerant boils and turns into a gas.

[0021] The second vapor-liquid separator 100b is fluidically connected to the external heat exchanger 16, which receives liquid refrigerant or a two-phase mixture of liquid and gaseous refrigerant at its inlet. The external heat exchanger 16 functions as an evaporator, whereby the refrigerant absorbs heat Q. inThe refrigerant is drawn from the outside space 82 and changes its phase from a liquid to a gas. The first blower 28 generates the first airflow 30 from the outside heat exchanger 16 towards the outside space 82. The gaseous refrigerant flow then flows through a second suction flow path 18d of the multi-way valve 18 and is returned as a suction flow to the inlet 22 of the compressor.

[0022] With further reference to Fig. 2B provides that the vapor compression system 10 may include a second internal heat exchanger 14a, which is flow-coupled with the second vapor-liquid separator 100b. The second internal heat exchanger 14a receives vapor or refrigerant gas from the second vapor-liquid separator 100b to perform a first heating stage before it is returned to rejoin the flow from the fluid outlet. As can be seen, by using the vapor from the second vapor-liquid separator 100b flowing through the second internal heat exchanger 14a, the first heating stage can be performed without injecting vapor into the compressor 20, and both the efficiency of the vapor compression system 10 and the capacity of the compressor 20 can be increased compared to vapor compression systems without the second internal heat exchanger 14a.

[0023] Referring to the Fig. 1 and Fig. 2A The compressor 20 of the vapor compression system 10 includes a connection 50 for vapor injection, or a vapor injection connection 50, which is operably connected to a vapor injection line (vapor injection conduit) 52. The vapor injection line 52 is connected to the vapor outlet 154 via a first vapor injection line 52a ( Fig. 3) The first vapor-liquid separator 100a is flow-coupled and is flow-coupled via a second vapor injection line 52b to the vapor outlet 154 of the second vapor-liquid separator 100b. As can be seen, the vapor-liquid separators 100a and 100b output a larger quantity of vapor compared to an economizer loop with a flash tank and / or a separate heat exchanger. In this way, the vapor-liquid separators 100a and 100b can replace a flash tank and / or a separate heat exchanger or otherwise avoid the need for a flash tank and / or a separate heat exchanger when generating and delivering vapor to the vapor injection port 50 of the compressor 20.

[0024] The geometry and efficiency of the vapor-liquid separator 100a allow it to be miniaturized or otherwise reduced in size compared to a flash tank or other energy recovery devices typically used in vapor injection cycles. The vapor-liquid separator 100a is intended to be manufactured or otherwise shaped using any suitable method. In exemplary embodiments, the vapor-liquid separator 100a can be manufactured by additive manufacturing, reductive manufacturing, etc., and combinations thereof. It is intended that the vapor-liquid separator 100a can be manufactured by casting using a wax and / or phase-change material, 3D printing, investment casting, etc. It is intended that the vapor-liquid separator 100a can be manufactured entirely or partially by 3D printing.It is envisaged that 3D printing can be used to manage printing limits and other important boundaries, and in embodiments, copper can be used to manage the printing and / or other important boundaries.

[0025] With reference to the Fig. Figure 3-9 presents a first example of a vapor-liquid separator 100. In this embodiment, the vapor-liquid separators 100a and 100b are essentially identical, so for the sake of brevity, only one vapor-liquid separator 100 is described here.

[0026] The vapor-liquid separator 100 comprises a housing 102 in which a first flow path 110 and a second flow path 150 are defined. Although the housing 102 is generally shown to be rectangular, it can 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 can have a shape or configuration that is complementary to the configuration of the first flow path 110 and the second flow path 150. The first flow path 110 defines a converging section of a fluid inlet, or converging fluid inlet section 112, which defines a fluid inlet 114 extending through an outer surface 104 of the housing 102. The fluid inlet 114 is connected to the cooling circuit 12 ( Fig. 1 and Fig. 2A) fluidically, or flow-wise, coupled and receives fluid (e.g., saturated or at least partially supercooled liquid). The converging fluid inlet section 112 defines a generally frustoconical profile with an inner dimension that decreases in a direction extending away from the fluid inlet 114. In this way, the frustoconical profile causes an increase in velocity and a decrease in the static pressure of the liquid refrigerant flowing through the converging fluid inlet section 112. In exemplary embodiments, an inner surface 112a of the converging fluid inlet section 112 can define a stepped conical profile, which generally has linear sections separated by frustoconical sections.The stepped conical profile of the inner surface 112a can interrupt potential eddy current loops of the fluid flowing through the converging fluid inlet section 112 and thus minimize or otherwise reduce the formation of eddy currents along the inner surface 112a of the converging fluid inlet section 112.

[0027] The first flow path 110 defines a diverging section of a fluid outlet, or a diverging fluid outlet section 116, which defines a fluid outlet 118 extending through the outer surface 104 of the housing 102. The fluid outlet 118 is connected to the cooling circuit 12 ( Fig. 1 and Fig. 2A) is fluidically coupled and discharges liquid or two-phase refrigerant from the vapor-liquid separator 100 back into the cooling circuit 12, or carries it away or releases it therein in some other way. The diverging fluid outlet section 116 defines a generally frustoconical profile with an inner dimension that increases towards the fluid outlet 118. In this way, the frustoconical profile causes a reduction in velocity and an increase in the static pressure of the liquid refrigerant flowing through the diverging fluid outlet section 116. In exemplary embodiments, an inner surface 116a of the diverging fluid outlet section 116 can define a stepped conical profile with generally linear sections separated by frustoconical sections.Although in general a profile is shown that corresponds to the profile of the converging fluid inlet section 112, the diverging fluid outlet section 116 may have any suitable profile, which may be the same as or different from the profile of the converging fluid inlet section 112.

[0028] Continuing from Fig. 3-9 defines the first flow path 110 as a first helical section 120, which extends between the converging fluid inlet section 112 and the diverging fluid outlet section 116 and connects them fluidically, or in terms of flow. The first helical section 120 defines a constriction (throat) 122 with a cross-sectional area that is less than or equal to the cross-sectional area of ​​a section of the first helical section 120 adjacent to the converging fluid inlet section 112, although it is provided that the constriction can define any cross-sectional area that is less than or larger than the cross-sectional area of ​​the first helical section 120 and / or the first converging inlet section 112 adjacent to the constriction 122. In this way, the constriction 122 is fluidically coupled and / or receives liquid or two-phase refrigerant from the converging fluid inlet section 112.The constriction 122 interacts with the helical profile of the first helical section 120 to increase the velocity of the fluid flowing through the first helical section 120 and to separate any vapor from the fluid. In some embodiments, the fluid flowing through the constriction 122 and the first helical section 120 can be accelerated to approximately the speed of sound for the fluid under the given conditions (e.g., temperature, pressure, etc.) of the fluid flowing through the first helical section 120.

[0029] In some embodiments, the profile of the first helical section 120 defines a generally circular cross-section adjacent to the converging fluid inlet section 112, which transitions into a generally non-circular cross-section, such as curvilinear, ovoid, etc., in a direction extending away from the converging fluid inlet section 112, and transitions back into a circular cross-section adjacent to the diverging fluid outlet section 116, although it is conceivable that the first flow path 110 and / or the first helical section 120 could have a suitable cross-section at any section along its length without this deviating from the scope of the disclosure. As can be seen, the inclination or non-circular profile of the first helical section 120 minimizes a velocity difference between steam, or...vaporous and liquid refrigerant flowing through the first helical section 120, or mitigates it in some other way.

[0030] The second flow path 150 defines a diverging section of a vapor outlet, or a diverging vapor outlet section 152, which defines a vapor outlet 154 extending through the outer surface 104 of the housing 102. The vapor outlet 154 is fluidically coupled to the cooling circuit 12 and carries vapor, or vaporous and / or gaseous refrigerant from the vapor-liquid separator 100 via the vapor injection line 52 ( Fig. 1 and Fig. 2A) to the steam injection port 50 or discharges it there otherwise. The diverging steam outlet section 152 defines a generally frustoconical profile with an inner dimension that increases in one direction towards the steam outlet 154. In this way, the frustoconical profile causes a reduction in velocity and an increase in the static pressure of the steam flowing through the diverging steam outlet section 152. In some embodiments, an inner surface 152a of the diverging steam outlet section 152 can define a stepped conical profile, which generally has linear sections separated by frustoconical sections.Although in general a profile is shown that corresponds to the profile of the converging fluid inlet section 112 and / or the diverging fluid outlet section 116, the diverging steam outlet section 152 may have any suitable profile, which may be the same as or different from the profile of the converging fluid inlet section 112 and / or the diverging fluid outlet section 116.

[0031] The second flow path 150 defines a second helical section 156 that extends between the first flow path 110 and the diverging steam outlet section 152 and directs steam from the first flow path 110 to the diverging steam outlet section 152. In exemplary embodiments, the second helical section 156 can extend between a steam inlet 158 ​​( Fig. 5) and the diverging vapor outlet section 152. As described in detail here, the increased velocity of the liquid refrigerant flowing through the first flow path 110 causes vapor to form within the liquid refrigerant. The increasing velocity of the liquid refrigerant generates or otherwise causes a buoyancy force to separate the vapor within the liquid refrigerant, and allows the separated vapor to flow into the vapor inlet 158 ​​and the second helical section 156 (e.g., radially inwards). In exemplary embodiments, the second helical section 156 is interdigitated or otherwise intertwined with the first helical section 120.In this way, the first helical section 120 and the second helical section 156 can be arranged stacked or alternately in a direction extending between the fluid inlet 114 and each of the fluid outlet 118 and the steam outlet 154. As described in detail here, the increased velocity of the fluid flowing through the first helical section 120 causes the steam in the first helical section 120 to flow into the second helical section 156.

[0032] In some embodiments, the profile of the second helical section 156 adjacent to the steam inlet 158 ​​may have a generally circular cross-section, 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 diverging steam outlet section 152, although it is conceivable that the second flow path 150 and / or the second helical section 156 may define any suitable cross-section at any section along its length, which may be the same as or different from the profile of the first flow path 110.

[0033] As can be seen, the number of turns or coils of the first helical section 120 and the second helical section 156 influences, or otherwise affects, the velocity and / or pressure of the liquid refrigerant and vapor flowing through each of the first and second helical sections 120, 156. Furthermore, as described above, the profile or cross-section of the first and second helical sections 120, 156 influences, or otherwise affects, the velocity of each of the vapor, gaseous, and liquid refrigerant flowing through the first and second helical sections 120, 156.In this way, the non-circular cross-section of the first helical section 120 minimizes or otherwise reduces a velocity difference between the vapor and the liquid refrigerant flowing through the first helical section 120 and prevents or otherwise minimizes the remixing of vapor and liquid. The non-circular cross-section of the second helical section 156 produces similar effects to the non-circular cross-section of the first helical section. The profile of the first and second helical sections 120, 156 is designed to be variable along their length and scaled according to the liquid refrigerant used in the vapor compression system 10.In this way, the geometry of the first and second helical sections 120, 156 can be proportional or otherwise based on a ratio of vapor and liquid flowing through the first and second helical sections 120, 156. As can be imagined, the density of the refrigerant can determine or otherwise influence the size of the vapor-liquid separator 100.

[0034] Referring to the Fig. 7-9 The steam-liquid separator 100 includes one or more steam or first bridges 160 that fluidically couple the first helical section 120 with the second helical section 156 upstream of the fluid outlet 118. The one or more first bridges 160 channel the steam within the first helical section 120 or otherwise allow it to flow into the second helical section 156, thereby increasing the velocity of the steam flowing through the second helical section 156. Although generally depicted as discrete tubular passages, it is conceivable that the one or more first bridges 160 have any suitable profile, and each bridge of the one or more first bridges 160 can have the same or a different profile.

[0035] The one or more first bridges 160 define a fluid inlet 162, which is fluidically coupled to the first flow path 110 along a radial inside of the first helical section 120, and a vapor outlet 164, which is fluidically coupled to the second flow path 150 along a radial outside or a region where liquid is collected, of the second helical section 156. In this way, the one or more first bridges 160 extend between the first helical section 120 and the second helical section 156, although it is conceivable that the one or more first bridges 160 could extend in any way relative to the first helical section 120 and / or the second helical section 156.In a non-limiting embodiment, the one or more first bridges 160 extend helically around the first helical section 120. It is provided that the one or more first bridges 160 can be arranged on any turn of both the first helical section 120 and the second helical section 156 without this deviating from the scope of the disclosure. In a non-limiting embodiment, the first and the second helical sections 120, 156 have one first bridge 160 per revolution to minimize or otherwise prevent an overlap of the first and second flow paths 110, 150.

[0036] It is provided that the steam outlet 164 of one or more first bridges 160 can be fluidically coupled with the second hollow inner section downstream of the steam inlet 162, where the static pressure of the steam flowing through the second flow path 150 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 seen, by arranging or locating the steam outlet 164 downstream of the steam inlet 162, a quantity of steam is conveyed or otherwise increased that flows through the one or more first bridges to the second flow path 150.In exemplary embodiments, the steam inlet 162 is fluidically coupled to the first flow path 110 along a radial inner side of the first helical section 120, and a steam outlet 164 is fluidly coupled to the second flow path 150 along a radial outer side of the second helical section 156.

[0037] In some embodiments, the vapor-liquid separator 100 includes one or more liquid or two-phase or second bridges 170 that fluidically couple the first helical section 120 to the second helical section 156 upstream of the fluid outlet 118. The one or more second bridges 170 channel the liquid refrigerant within the second helical section 156 or otherwise allow it to flow into the first helical section 120. Although generally depicted as discrete tubular passages, it is conceivable that the one or more second bridges 170 have any suitable profile, and each bridge of the one or more second bridges 170 can have the same or a different profile than the one or more first bridges 160 without deviating from the disclosure.The one or more second bridges 170 define a fluid inlet 172, which is fluidically coupled to the second flow path 150 along a radial outer surface of the second helical section 156, and a fluid outlet 174, which is fluidically coupled to the first flow path 110 along the first helical section 120. In this way, the one or more second bridges 170 extend between the first helical section 120 and the second helical section 156, although it is conceivable that the one or more second bridges 170 could extend in any way relative to the first helical section 120 and / or the second helical section 156. In a non-restrictive embodiment, the one or more second bridges 170 extend helically around the first helical section 120.It is provided that one or more second bridges 170 can be arranged on any turn of both the first helical section 120 and the second helical section 156. In a non-restrictive embodiment, the first and second helical sections 120, 156 include a second bridge 170 once per revolution to minimize or otherwise prevent an overlap of the first and second flow paths 110, 150.

[0038] With reference to the Fig. 3-9 The fluid inlet 114 of the vapor-liquid separator 100 receives a fluid during operation, which in exemplary embodiments is a liquid refrigerant (e.g., saturated or at least partially supercooled liquid). The liquid refrigerant received by the fluid inlet 114 flows through the converging fluid inlet section 112, causing an increase in velocity and a decrease in the static pressure of the liquid refrigerant. The liquid refrigerant is received by the first helical section 120, where the constriction 122 interacts with the helical profile of the first helical section 120 to generate an increase in the velocity of the liquid refrigerant, causing vapor to develop within the liquid refrigerant.The increasing velocity of the liquid refrigerant generates or otherwise causes a buoyant force to separate the vapor in the liquid refrigerant, and causes the separated vapor to flow towards a radially inner section of the first helical section 120. The separated vapor flows through the one or more first bridges 160 and into the second helical section 156 of the second flow path 150.

[0039] As can be seen, the vapor continues to be separated from the liquid refrigerant and flows through one or more of the first bridges 160, while the liquid refrigerant flows through the first helical section 120 towards the diverging fluid outlet section 116. The vapor received in the second helical section 156 causes the velocity of the vapor flowing through the second helical section 156 to increase to approximately the speed of sound for the vapor's condition (e.g., temperature, pressure, etc.). Any liquid present in the second helical section 156 flows towards the radially outer section of the second helical section 156 and is directed through one or more of the second bridges 170 into the first helical section 120.The steam flowing through the second helical section 156 is received by the diverging steam outlet section 152, the diverging frustoconical profile of which causes a decrease in velocity and an increase in the static pressure of the steam. The steam exits the steam outlet 154, where it is directed through the first steam injection line 52a to the steam injection port 50 of the compressor 20.

[0040] Due to the increased velocity of the liquid refrigerant flowing through the first helical section 120, vapor continues to be generated and separated from the liquid refrigerant. The additional vapor separated from the liquid refrigerant flowing through the first helical section 120 flows to the radially inner side of the first helical section 120 and over the one or more first bridges 160 into the second helical section 156. The liquid refrigerant flowing through the first helical section 120 flows into the diverging fluid outlet section 116, where the diverging frustoconical profile of the diverging fluid outlet section 116 causes a decrease in velocity and an increase in the static pressure of the liquid refrigerant. The liquid refrigerant exits the fluid outlet 118, where it is directed to the first expansion device 40.

[0041] With reference to the Fig. Figure 10-12 describes another embodiment of a vapor-liquid separator, generally designated by reference numeral 200. The vapor-liquid separator 200 comprises a housing 202 in which a first flow path 210 and a second flow path 250 are defined. Although the housing 202 is generally shown to be rectangular, it can have any configuration, and in embodiments, it can have a configuration complementary to the configuration of the first flow path 210 and the second flow path 250 without deviating from the scope of the disclosure. The first flow path 210 defines a first hollow inner section 212 extending between a fluid inlet 214, which extends through an outer surface 204 of the housing 202, and a fluid outlet 216, which extends through the outer surface 204 of the housing 202.The first flow path 210 comprises a converging inlet section 218 with an inner dimension that decreases in a direction extending away from the fluid inlet 214. In exemplary embodiments, the converging inlet section 218 defines a constriction 220.

[0042] The fluid inlet 214 is fluidically, or flow-wise, connected to the cooling circuit 12 ( Fig. 1 and Fig. 2A) is coupled and receives fluid (e.g., saturated or at least partially supercooled liquid). The first flow path 210 comprises a helical section 222, which is fluidically coupled to the converging inlet section 218 at a downstream position of the converging inlet section 218 and, in exemplary embodiments, downstream of the constriction 220. As can be seen, the converging inlet section 218 and the helical section 222 cause a reduction in the static pressure and an increase in the velocity of the liquid refrigerant flowing through the first flow path 210, generating vapor from the liquid refrigerant.

[0043] The helical section 222 has an inner dimension that increases in a direction toward the fluid outlet 216. In some embodiments, the helical section 222 may have a diverging outlet section 224 with an inner dimension that increases in a direction extending toward the fluid outlet 216. As can be seen, the increasing inner dimension of the helical section 222 and / or the diverging outlet section 224 causes a decrease in velocity and an increase in the static pressure of the liquid refrigerant flowing through the helical section 222 and exiting the fluid outlet 216. Although a circular profile is generally shown, the first flow path 210 may have any profile, which may be the same or different along its length without deviating from the scope of the disclosure.It is provided that the helical section 222 can have a variable pitch extending towards the fluid outlet 216. Although a pitch increasing in one direction towards the fluid outlet 216 is generally shown, it is provided that the helical section 222 can have any pitch, which can be constant, decrease in one direction towards the fluid outlet 216, or be variable, without deviating from the scope of the disclosure.

[0044] With continued reference to the Fig. In Figures 10-12, the second flow path 250 defines a second hollow inner section 252, which extends between the first hollow inner section 212 of the first flow path 210 and a vapor outlet 254 and transfers vapor from the first hollow inner section 212 of the first flow path 210 to the vapor outlet 254, which extends through the outer surface 204 of the casing 202. In exemplary embodiments, the second hollow inner section 252 can extend between and connect a vapor inlet 262 and the vapor outlet 254. The vapor inlet 262 is located downstream of the fluid inlet 214 and receives the vapor separated from the liquid refrigerant, which flows through the helical section 222 of the first flow path 210. The second flow path 250 comprises a helical section 256, which is fluidically coupled to both the steam inlet 262 and the steam outlet 254.The helical section 256 of the second flow path 250 has an inner dimension that increases in one direction towards the steam outlet 254. As can be seen, the increasing inner dimension of the helical section 256 causes a decrease in velocity and an increase in the static pressure of the steam flowing through the helical section 256 and exiting the steam outlet 254.

[0045] The steam outlet 254 is fluidically coupled to the first steam injection line 52a ( Fig. 1 and Fig. 2A), to direct steam from the steam outlet 254 of the steam-liquid separator 200 to the steam injection port 50 of the compressor 20. In the exemplary embodiment, the helical section 222 of the first flow path 210 is arranged radially outside the helical section 256 of the second flow path 250, although it is conceivable that the first and second helical sections 222, 256 could be arranged in any relation to each other without deviating from the scope of the disclosure. In a non-limiting embodiment, the helical section 222 of the first flow path 210 is arranged concentrically around the helical section 256 of the second flow path 250.

[0046] The steam-liquid separator 200 comprises one or more bridges 260 which fluidly couple the first hollow inner section 212 with the second hollow inner section 252 upstream of the steam outlet 254 and along the helical sections 222, 256 of each of the first and second flow paths 210, 250. In exemplary embodiments, the one or more bridges 260 are a single continuous bridge between the helical section 222 of the first flow path 210 and the helical section 256 of the second flow path 250. In this way, the increased velocity of the liquid refrigerant flowing through the helical section 222 of the first flow path 210 causes the vapor in the liquid refrigerant to flow over the one or more bridges 260 into the second hollow inner section 252 of the helical section of the second flow path 250.Although generally described as a single continuous bridge, it is conceivable that the one or more bridges 260 are not connected or are otherwise spaced apart from each other and form a multitude of discrete bridges.

[0047] The steam-fluid separator 200 works in a similar way to the steam-fluid separator 100, and therefore the operation of the steam-fluid separator 200 is not described in detail here for the sake of brevity.

[0048] With reference to Fig. Figure 13 is a schematic diagram of another embodiment of a vapor compression system with the vapor-liquid separator 100, 200, and is generally designated by reference numeral 1300. The vapor compression system 1300 is essentially similar to the vapor compression system 10, so for the sake of brevity, only the differences between the two are described in detail here.

[0049] The vapor compression system 1300 is a single-stage compression system with a single, reversible, closed refrigerant circuit 1302, comprising an internal heat exchanger 1304, an external heat exchanger 1306, a first multi-way or reversing valve 1308, a second multi-way or reversing valve 1310, the compressor 20, an expansion device 1314, a vapor-liquid separator 100, and a flow valve 1316. In other embodiments of the present disclosure, the vapor compression system 1300 may comprise multiple refrigerant circuits to accommodate multiple compressors, or it may be operated in parallel with another system, such as a humidity control system.The flow valve 1316 can be positioned between a first position, which allows the vapor flow from the vapor-liquid separator 100 to the inlet 22 of the compressor, and a second position, which prevents the vapor flow from the vapor-liquid separator 100 to the inlet 22 of the compressor, while allowing the refrigerant flow from the injection port 50 back to the inlet 22 of the compressor in order to reduce displacement of the compressor 20.

[0050] With reference to Fig. Figure 14 is a schematic diagram of another embodiment of a vapor compression system using the vapor-liquid separator 100, 200, and is generally designated by reference numeral 1400. The vapor compression system 1400 is essentially similar to the vapor compression systems 10 and 1400, so for the sake of brevity, only the differences between them are described in detail here.

[0051] The vapor compression system 1400 is a multi-stage compression system and comprises a shut-off valve 1460, which is arranged between the vapor-liquid separator 100 and the flow valve 1416, and an expansion valve 1462, which is arranged upstream of the vapor-liquid separator 100. The shut-off valve 1460 can be positioned between a first position, which prevents the vapor flow from the vapor-liquid separator 100 to the flow valve 1416 and thus to the injection port 50, and a second position, which allows the vapor flow from the vapor-liquid separator 100 to the flow valve 1416 and thus to the injection port 50.

[0052] In the Fig. 15A and Fig.Figure 15B describes a method for operating a vapor-liquid separator and is generally designated by reference numeral 1500. The liquid inlet of the first flow path of the vapor-liquid separator receives 1502 saturated liquid, supercooled liquid, or a two-phase refrigerant with low vapor quality. The converging fluid inlet section causes 1504 the fluid flowing through the converging fluid inlet section to reduce its static pressure, or the static pressure of the fluid decreases and its velocity increases. The fluid flowing through the converging fluid inlet section is received by a helical section of the first flow path 1506, which causes 1508 the fluid flowing through the helical section to reduce its static pressure, or the static pressure of the fluid decreases and its velocity increases, generating vapor from the fluid.The increased velocity of the fluid flowing through the helical section of the first flow path generates a buoyant force 1510, which causes the vapor separated from the fluid to flow over one or more bridges into the second flow path. In exemplary embodiments, the fluid flowing through the helical section of the second flow path is transferred over one or more fluid bridges into the first helical section of the first flow path 1512. The vapor flowing through the second flow path is received by the diverging vapor outlet section 1514, which causes the vapor 1516 to decrease its velocity and increase its static pressure, and exit from the vapor outlet 1518. The fluid flowing through the first flow path is received by the diverging fluid outlet section 1520 and discharged from the fluid outlet 1522.

[0053] The working fluid is intended to contain at least one refrigerant suitable for use in a vapor compression cycle. Non-restrictive examples of suitable refrigerants include natural refrigerants (e.g., carbon dioxide, water, ammonia, hydrocarbons, etc.), fluorocarbon-based refrigerants, and refrigerants with a low global warming potential, such as the ASHRAE-classified A1 and A2L refrigerants. Non-restrictive examples of A1 refrigerants are carbon dioxide (R-744), chlorodifluoromethane (R-22), 1,1-difluoroethane (R-152a), 1,1,1,2-tetrafluoroethane (R-134A) and R-410A (a near azeotropic mixture of difluoromethane (R-32) and pentafluoroethane (R-125)), and trifluoromonochloropropenes (R-1233, including cis- and trans-1-chloro-3,3,3-trifluoropropene (HFO-1233zd) isomers (HFO-1233zd(Z) and HFO-1233zd(E)), and hexafluorobutenes (HFO-1336, including HFO-1336mzz(Z), 1336mzz(E)).Non-restrictive examples of A2L refrigerants are difluoromethane (R-32) and hydrofluoroolefins (HFOs). Suitable HFO refrigerants are described, for example, in US Patent No. 4,788,352 to Smutny and US Patent No. 8,444,874 to Singh et al., the relevant sections of which are incorporated by reference. HFOs can include 2,3,3,3-tetrafluoropropene-1-ene (HFO-1234yf) and trans-1,3,3,3-tetrafluoropropene-1-ene (HFO-1234ze).Non-restrictive suitable examples of specific HFO refrigerants include 3,3,3-trifluoropropene (HFO-1234zf), HFO-1234 refrigerants such as 2,3,3,3-tetrafluoropropene (HFO-1234yf), 1,2,3,3-tetrafluoropropene (HFO-1234ze), cis- and trans-1,3,3,3-tetrafluoropropene (HFO-1234ye), pentafluoropropenes (HFO-1225) such as 1,1,3,3,3,-pentafluoropropene (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 those with a hydrogen on the terminal unsaturated carbon, such as 1,2,3,3,3-pentafluoropropene (HFO-1225yez), fluorochloropropenes such as trifluorine, monochloropropenes (HFO-1233) such as 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-difluoroethene (R-1132(E)) and any combinations thereof.In certain cases, the HFO refrigerant can be selected from the group consisting of: R-1234yf, R-1234ze, R-1233zd(E), R-1233zd(Z), R-1336mzz(Z), R-1336mzz(E), R-1132(E) and their combinations. In some examples, these refrigerants are used in combination with other A1 or A2L refrigerants or other refrigerants, such as A3, B1, or B2 refrigerants, including natural or flammable refrigerants (e.g., dimethyl ether (R-E170) or propane (C3H8 or R-290)).

[0054] The vapor compression system 10 operates in some examples with a working fluid containing a refrigerant mixture of at least two refrigerants. Suitable refrigerant mixtures and suitable control devices for use with such refrigerant mixtures are described, for example, in U.S. Patent Application No. 17 / 507,403 by Welch et al., filed in October 2021 and published on April 27, 2023, as U.S. Patent Publication No. 2023 / 0130167, the entire disclosure of which is hereby incorporated by reference. It is intended that features of the vapor compression system 10 may be used in any combination with the systems described in U.S. Patent Application No. 2023 / 0130167, which are incorporated herein by reference. In certain examples, the refrigerant mixture contains an A1 refrigerant, such as carbon dioxide (R-744), mixed with at least one other refrigerant.As can be seen, carbon dioxide refrigerant is suitable for use in a subcritical system design. An example of a suitable, non-limiting refrigerant mixture is CO2 (R-744) as a more volatile high-pressure refrigerant mixed with an HFO refrigerant (e.g., R-1233zd(E)) as a less volatile low-pressure fluid. The refrigerant mixture can be a high-glide mixture containing a first refrigerant (e.g., CO2) with a relatively low normal boiling point (at a pressure of 1 atmosphere (atm)) and a second refrigerant with a relatively higher normal boiling point. The difference between the normal boiling points of the first and second refrigerants is greater than or equal to 25 °C.For example, if the refrigerant mixture contains CO2 with a normal boiling point of about 78 °C at 1 atm and R-1233zd(e) with a normal boiling point of about 18 °C at 1 atm, the difference in boiling points is about 96 °C.

[0055] Suitable working fluid refrigerant mixtures include a refrigerant from the group consisting of: R-744, R-22, R-134A, R-410A, R-1234yf, R-1234ze, R-1233zd(E), R-1233zd(Z), R-1336mzz(Z), R-1336mzz(E), and combinations thereof. Alternatively, a first refrigerant and a second refrigerant contained in the refrigerant mixture may be selected independently from the group consisting of: R-744, R-22, R-152a, R-134A, R-410A, R-E170, R-32, HFOs, 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, HFOs and combinations thereof, and the second refrigerant is selected from the group consisting of: 2,3,3,3-Tetrafluoropropene-1-ene (R1234yf), 1,3,3,3-Tetrafluoropropene-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.

[0056] The working fluid can contain one or more refrigerants, such as those described above, in combination with a cooling lubricant. The working fluid can, for example, contain a synthetic oil. The lubricant can, in some examples, contain a polyvinyl ether oil (PVE), a polyalphaolefin oil (PAO), a polylene glycol oil (PAG), alkylbenzene, mineral oil, or an ester-based oil, such as polyol ester oil (POE). POE oils can be used when carbon dioxide (R-744) is present in the working fluid (e.g., in a refrigerant mixture). Suitable POE oils can contain a compound formed from a carboxylic acid and a polyol.Such POE compounds can be formed from a carboxylic acid selected from the group consisting of: n-pentanoic acid, 2-methylbutanoic acid, n-hexanoic acid, n-heptanoic acid, 3,3,5-trimethylhexanoic acid, 2-ethylhexanoic acid, n-octanoic acid, n-nonanoic acid and isononanic acid, as well as combinations thereof, and a polyol selected from the group consisting of: pentaerythritol, dipentaerythritol, neopentyl glycol, trimethylpropanol and combinations thereof.

[0057] Among the technical advantages of the methods and systems described here is the increased efficiency of a reversible steam compression system through the integration of a vapor-liquid separator. This separator utilizes two helical flow paths, fluidically coupled by one or more bridges, to generate and deliver more steam to the compressor than a heat exchanger or flash tank. The vapor-liquid separator can replace a flash tank and / or heat exchanger in a steam-saving circuit, thereby reducing the complexity and cost of the steam compressor system.

[0058] The terms “approximately”, “essentially”, “required” and “approximately” used herein, when in connection with ranges of dimensions, concentrations, temperatures or other physical or chemical properties or characteristics, are intended to cover deviations that may exist at the upper and / or lower limits of the ranges of properties or characteristics, including, for example, deviations resulting from rounding, measurement procedures or other statistical errors.

[0059] When introducing elements of the present disclosure or its embodiment(s), the articles "a," "an," "the," "the," and "said" mean that there is one or more of these elements. The expressions "comprising," "including," "containing," and "exhibiting" are meant to be all-encompassing and mean that there may be other elements besides those listed. The use of terms indicating a particular orientation (e.g., "above," "below," "side," etc.) serves to simplify the description and does not require a specific orientation of the described object.

[0060] Since various modifications can be made to the above designs and methods without deviating from the scope of the disclosure, all information contained in the above description and shown in the accompanying drawings is to be understood as illustrative and not as limiting. QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] US 17 / 507,403

[0054] US 2023 / 0130167

[0054] US 2023 / 0130167

[0054]

Claims

[1] Vapor-liquid separator, comprising: a first flow path extending between a fluid inlet and a fluid outlet, wherein the first flow path defines a helical section, the helical section causing a reduction in static pressure and an increase in velocity of a fluid flowing through the first flow path to generate steam from the fluid; a second flow path extending between the first flow path and a steam outlet, transferring steam fluidically from the first flow path to the steam outlet, the second flow path defining a helical section; and one or more bridges that fluidly connect the first flow path with the second flow path upstream of the steam outlet and along the helical section of both the first flow path and the second flow path, wherein the increased velocity of the fluid flowing through the first flow path causes steam within the first flow path to flow over the one or more bridges into the second flow path; wherein 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] Vapor-liquid separator according to claim 1, wherein the one or more bridges comprise at least one vapor bridge comprising a vapor inlet which is fluidically coupled to the first flow path along a radial inside of the helical section of the first flow path, and a vapor outlet which is fluidically coupled to the second flow path along a radial outside of the helical section of the second flow path, in order to allow vapor to flow from within the first flow path into the second flow path. [3] Vapor-liquid separator according to claim 1, wherein the one or more bridges comprise at least one liquid bridge comprising a liquid inlet which is fluidically coupled to the second flow path from a region in which liquid collects in the helical section of the second flow path, and a fluid outlet which is fluidly coupled to the first flow path along the helical section of the first flow path to allow liquid in the second flow path to flow into the first flow path. [4] Vapor-liquid separator according to claim 1, wherein the one or more bridges terminate at a position upstream of both the vapor outlet and the fluid outlet, wherein the first and second flow paths each have a first and a second diverging section downstream of the position where the one or more bridges terminate, wherein a cross-sectional area of ​​the first diverging section increases as the first flow path extends towards the fluid outlet in order to generate an increase in the static pressure of the fluid flowing through the first diverging section, wherein a cross-sectional area of ​​the second diverging section increases as the second flow path extends towards the steam outlet in order to generate an increase in the static pressure of the steam flowing through the second diverging section. [5] Vapor-liquid separator according to claim 1, wherein the one or more bridges consist of a single continuous bridge between the first flow path and the second flow path, wherein the first flow path is arranged radially outwards from the second flow path. [6] Vapor-liquid separator according to claim 1, wherein the helical section of the first flow path is intertwined with the helical section of the second flow path. [7] Vapor-liquid separator according to claim 6, wherein the one or more bridges comprise discrete tubular bridge passages extending between the first and the second flow path. [8] Vapor-liquid separator according to claim 6, wherein the helical section of the first flow path or the helical section of the second flow path defines a non-circular cross-section. [9] Vapor-liquid separator according to claim 1, further comprising a single body defining the first flow path, the second flow path and the one or more bridges. [10] Vapor-liquid separator according to claim 1, further comprising a first conduit that defines the first flow path; a second conduit that defines the second flow path; and at least one third line that defines one or more bridges and couples the first line to the second line in terms of flow. [11] Vapor-liquid separator with a first flow path with: a fluid inlet section that generates an increase in velocity and a decrease in the static pressure of a fluid flowing through the fluid inlet section; a fluid outlet section that produces a decrease in velocity and an increase in the static pressure of a fluid flowing through the fluid outlet section; and a first helical section extending between the fluid inlet section and the fluid outlet section, connecting them fluidically, wherein the first helical section generates an increase in the velocity of the fluid flowing through the first helical section and a separation of vapor from the fluid; and a second flow path for the fluid, with: a steam outlet section that defines a steam outlet which produces an increase in static pressure and a decrease in the velocity of the steam flowing through the steam outlet section; a second helical section extending between the first flow path and the steam outlet section, transferring steam from the first flow path to the steam outlet section, the second helical section being intertwined with the first helical section, the increased velocity of the fluid flowing through the first helical section causing steam within the first helical section to flow into the second helical section; and one or more bridges that fluidly couple the first helical section with the second helical section, wherein the one or more bridges allow the steam in the first helical section to flow over the one or more bridges into the second helical section, wherein the steam received in the second helical section generates an increase in the velocity of the steam flowing through the second helical section, wherein the steam received in the second helical section is discharged from the steam outlet and the fluid flowing through the first helical section is discharged from the fluid outlet. [12] Vapor-liquid separator according to claim 11, wherein the first helical section transitions in a direction extending from the fluid inlet section to the fluid outlet section from a circular profile adjacent to the fluid inlet section to a non-circular profile and to a circular profile adjacent to the fluid outlet section. [13] Vapor-liquid separator according to claim 12, wherein the second helical section transitions in a direction extending towards the vapor outlet section from a non-circular profile to a circular profile adjacent to the vapor outlet section. [14] Vapor-liquid separator according to claim 11, wherein each bridge of the one or more bridges has discrete tubular passages extending between the first and second helical section. [15] Vapor-liquid separator according to claim 11, further comprising one or more second bridges which fluidically couple the second helical section with the first helical section upstream of the fluid outlet and the vapor outlet, wherein the one or more second bridges enable fluid flowing in the second helical section to flow into the first helical section. [16] System that includes: a fluid compression circuit with a compressor that can be operated to compress a refrigerant; and a vapor-liquid separator which is fluidically connected to the fluid compression circuit to receive liquid refrigerant from it, wherein the vapor-liquid separator comprises: a first flow path extending between a fluid inlet and a fluid outlet, wherein the first flow path has a helical section which causes a reduction in static pressure and an increase in velocity of the liquid refrigerant flowing through the first flow path in order to generate vapor from the liquid refrigerant; a second flow path extending between the first flow path and a steam outlet, transferring steam from the first flow path to the steam outlet; and a second flow path extending between the first flow path and a steam outlet, transferring steam from the first flow path to the steam outlet; and one or more bridges that fluidically couple the first flow path with the second flow path, wherein the increased velocity of the liquid refrigerant flowing through the first flow path causes vapor in the first flow path to flow over the one or more bridges into the second flow path, wherein the steam received in the second flow path is diverted from the steam outlet to an intermediate compression stage of the compressor. [17] System according to claim 16, wherein the one or more bridges of the vapor-liquid separator terminate at a position upstream of both the vapor outlet and the fluid outlet, wherein the first and second flow paths each comprise a first and a second diverging section downstream of the position where the one or more bridges terminate. [18] System according to claim 16, wherein the first flow path is arranged radially outwards from the second flow path. [19] System according to claim 16, wherein the helical section of the first flow path is intertwined with the helical section of the second flow path. [20] System according to claim 19, wherein the one or more bridges comprise discrete tubular bridge passages extending between the first and the second flow path.

Images