Lubricant split system for hvacr system

Abstract

The present disclosure provides a compressor system comprising: a housing having an impeller disposed therein, where the impeller is configured to rotate within an impeller cavity of the housing to compress a working fluid; and a motor disposed within the housing, where the motor includes a rotor shaft coupled to the impeller, and the motor is configured to drive rotation of the rotor shaft and the impeller. The compressor system includes a bearing disposed circumferentially about the rotor shaft, where the bearing is configured to receive lubricant from a lubricant source to facilitate rotation of the rotor shaft; and a lubricant diverting system configured to divert the lubricant from the impeller cavity. The lubricant shunting system includes: a seal configured to prevent flow of the lubricant into the impeller cavity; and a balance piston coupled to the impeller, where the balance piston is configured to divert the lubricant from the seal.

Description

Cross-references to related applications

[0001] This application claims priority and benefit to U.S. Provisional Application No. 63 / 522,641, filed June 22, 2023, entitled “A COMPRESSOR WITH OIL DIVERSIONFEATURES,” which is incorporated herein by reference in its entirety for all purposes. Background Technology

[0002] This section aims to introduce the reader to various aspects of the technology that may relate to the various aspects of this disclosure described below. It is believed that this discussion will 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 should be read in this light, rather than as an endorsement of prior art.

[0003] Heating, ventilation, air conditioning, and refrigeration (HVAC&R) systems, or vapor compression systems, are used in residential, commercial, and industrial environments to control environmental characteristics, such as temperature and humidity, for the occupants of those environments. HVAC&R systems typically circulate a working fluid (e.g., a refrigerant) that changes phase between vapor, liquid, and combinations thereof in response to exposure to varying temperatures and pressures associated with the operation of the HVAC&R system. For example, an HVAC&R system may utilize one or more compressors to circulate the working fluid to a heat exchanger, which transfers heat between the working fluid and another fluid (e.g., a cooling fluid) flowing through the heat exchanger.

[0004] In some applications, the motor powering the compressor may include a rotating component that operates to rotate the compressor impeller, thereby enabling the compressor to compress the working fluid and deliver it to other components of the vapor compression system. In many applications, lubricants such as oil may be directed through various flow paths to lubricate components within the motor and / or compressor. Unfortunately, lubricant within the compressor may escape from the intended flow path and may inadvertently flow into other areas of the compressor (e.g., the working fluid flow path), which can lead to reduced efficiency and / or shortened service life of the compressor and / or motor. Summary of the Invention

[0005] The following provides an overview of certain embodiments disclosed herein. It should be understood that these aspects are presented merely to provide the reader with a brief overview of these particular embodiments, and these aspects are not intended to limit the scope of this disclosure. In fact, this disclosure may cover many aspects that may not be set forth below.

[0006] In one embodiment, a compressor system includes: a housing having an impeller disposed therein, wherein the impeller is configured to rotate within an impeller cavity of the housing to compress a working fluid; and a motor disposed within the housing, wherein the motor includes a rotor shaft coupled to the impeller, and the motor is configured to drive rotation of the rotor shaft and the impeller. The compressor system further includes: a bearing circumferentially disposed about the rotor shaft, wherein the bearing is configured to receive lubricant from a lubricant source to facilitate rotation of the rotor shaft; and a lubricant diversion system configured to divert lubricant from the impeller cavity. The lubricant diversion system includes: a seal configured to prevent lubricant flow into the impeller cavity; and a balance piston coupled to the impeller, wherein the balance piston is configured to divert lubricant from the seal.

[0007] In one embodiment, a heating, ventilation, air conditioning, and cooling (HVAC&R) system includes: a compressor including an impeller configured to rotate within a compression chamber to compress a working fluid and circulate the working fluid through a working fluid circuit; an electric motor coupled to the compressor via a rotor shaft and configured to drive operation of the compressor via rotation of the rotor shaft; and a lubricant diversion system configured to prevent the flow of lubricant into the compression chamber. The lubricant diversion system includes: a balance piston having a wall portion that at least partially defines a chamber configured to trap lubricant; and a seal having a sealing portion configured to engage the wall portion, wherein the balance piston is configured to rotate with the impeller and direct the flow of lubricant within the chamber away from the seal.

[0008] In one embodiment, a lubricant diversion system for a compressor system includes: a balance piston coupled to an impeller of the compressor system. The balance piston includes: a wall portion configured to extend in an axial direction of the compressor system; and a cavity at least partially defined by the wall portion, wherein the cavity is configured to receive lubricant from a bearing of the compressor system. The lubricant diversion system further includes: a seal configured to abut the wall portion and prevent lubricant flow toward the impeller, wherein the balance piston is configured to rotate with the impeller during compressor system operation and divert lubricant from the seal. Attached Figure Description

[0009] A better understanding of the various aspects of this disclosure will be achieved after reading the following detailed description and referring to the accompanying drawings, in which:

[0010] Figure 1 This is a perspective view of an embodiment of a building in a commercial environment that can utilize heating, ventilation, air conditioning and / or cooling (HVAC&R) systems, according to one aspect of this disclosure;

[0011] Figure 2This is a perspective view of an embodiment of a vapor compression system according to one aspect of the present disclosure;

[0012] Figure 3 This is a schematic diagram of an embodiment of a vapor compression system according to one aspect of the present disclosure;

[0013] Figure 4 This is a schematic diagram of an embodiment of a vapor compression system according to one aspect of the present disclosure;

[0014] Figure 5 This is a cross-sectional side view of an embodiment of a compressor of a vapor compression system according to one aspect of the present disclosure, showing the motor and lubricant distribution system of the compressor system;

[0015] Figure 6 It is based on one aspect of this disclosure. Figure 5 A cross-sectional side view of an embodiment of a lubricant distribution system; and

[0016] Figure 7 This is a cross-sectional side view of an embodiment of a lubricant distribution system for a compressor system according to one aspect of this disclosure. Detailed Implementation

[0017] One or more specific embodiments of the present invention will be described below. These described embodiments are examples of the currently disclosed technology. Additionally, in the process of providing a concise description of these embodiments, not all features of actual implementations may be described in the specification. It should be understood that in the development of any such actual implementation, as in any engineering or design project, numerous implementation-specific decisions may be made to achieve specific goals of the developer, such as compliance with system-related and business-related constraints, which may vary from implementation to implementation. Furthermore, it should be understood that such development work may be complex and time-consuming, but is merely a routine task of design, manufacture, and production for those skilled in the art who benefit from this disclosure.

[0018] When describing elements of various embodiments of this disclosure, the articles “a” and “the” are intended to mean that one or more of the element are present. The terms “comprising,” “including,” and “having” are intended to be inclusive and mean that additional elements may be present in addition to the listed elements. Furthermore, it should be understood that references to “one embodiment” or “embodiment” in this disclosure are not intended to exclude the existence of additional embodiments further incorporated into the described features.

[0019] As used herein, the terms “approximately,” “generally,” “largely,” etc., are intended to convey that the attribute value being described can be within a relatively small range of that attribute value, as would be understood by one of ordinary skill in the art. For example, when an attribute value is described as “approximately” equal to (or, for example, “generally similar” to) a given value, this is intended to convey that the attribute value can be within + / -5%, + / -4%, + / -3%, + / -2%, + / -1%, or even closer to the given value. Similarly, when a given feature is described as “generally parallel” to another feature, “generally perpendicular” to another feature, etc., this is intended to convey that the given feature has the described property, such as being parallel to another feature, perpendicular to another feature, etc., within + / -5%, + / -4%, + / -3%, + / -2%, + / -1%, or even closer to the other feature. Mathematical terms (such as “parallel” and “perpendicular”) should not be interpreted strictly in a rigorous mathematical sense, but rather should be interpreted as such terms would be understood by one of ordinary skill in the art. For example, someone skilled in the art would understand that two lines that are generally parallel to each other are largely parallel, but may deviate slightly from being perfectly parallel.

[0020] As briefly discussed above, heating, ventilation, air conditioning, and / or cooling (HVAC&R) systems can be configured to operate to meet heating and / or cooling needs, such as those within a building, residence, or other suitable structure. For example, an HVAC&R system may include a vapor compression system (e.g., a cooler system, a heat pump system) that transfers heat between a working fluid (e.g., a refrigerant, a heat transfer fluid) and a fluid to be conditioned (e.g., air, water, or brine). In some embodiments, the working fluid and the fluid to be conditioned may be the same fluid (e.g., water). The vapor compression system may include one or more vapor compression loops (e.g., a heat pump, a working fluid loop), each of which includes one or more heat exchangers, such as condensers and evaporators, fluidly connected to each other via one or more conduits (e.g., a vapor compression loop, a working fluid loop, a refrigeration loop). Further, each vapor compression loop may include a compressor configured to pressurize the working fluid and circulate it through the conduits, and thus be able to transfer heat between the working fluid and the fluid to be conditioned via one or more heat exchangers. To facilitate different operating modes, the vapor compression system may include several controllable features or components, such as valves, expansion devices, coil fans, condenser pumps, and / or evaporator pumps. The vapor compression system may include a controller configured to determine the operating mode of the vapor compression system and control the valves, expansion devices, pumps, and fans to operate the vapor compression system in the desired mode. In some embodiments, the vapor compression system may be a heat pump system configured to facilitate the flow of working fluid through the vapor compression loop in different directions for different operating modes. In other embodiments, the working fluid may flow through the vapor compression loop in the same direction during multiple (e.g., all) operating modes.

[0021] Compressors (e.g., centrifugal compressors) for vapor compression systems (e.g., heat pump systems) can be designed for certain operating conditions that may be related to one or more characteristics or parameters of the working fluid (e.g., refrigerant, water). For example, compressors can be designed and / or selected for implementation in HVAC&R systems based on the type of working fluid, the working fluid flow rate (e.g., velocity), the working fluid temperature and pressure conditions at the compressor inlet, and / or the working fluid temperature and pressure conditions at the compressor outlet.

[0022] A compressor may include a compression member (e.g., an impeller) configured to pressurize a working fluid within an impeller chamber. The compressor (e.g., impeller, impeller shaft) may be coupled to an electric motor (e.g., a rotor shaft) configured to drive or power the compressor. For example, the electric motor may include a rotor shaft supported within a motor housing by one or more bearing assemblies (e.g., lubricated bearing assemblies), and this rotor shaft may be coupled to the impeller. By rotating the rotor shaft, the electric motor enables the compressor's compression member (e.g., the impeller) coupled to the rotor shaft to rotate, thereby driving the working fluid through a vapor compression circuit. In some vapor compression systems, a lubricant (e.g., oil) may be directed through the electric motor and / or the compressor (e.g., one or more bearing assemblies) to facilitate rotation of the motor's rotor shaft and thus of the compressor's compression member (e.g., the impeller). During compressor operation (e.g., when the compressor is operating to pressurize the working fluid and direct it through a vapor compression circuit), lubricant may inadvertently leak from the bearing assemblies and may flow toward certain areas within the compressor (e.g., the impeller chamber, the working fluid flow path), which may be undesirable. For example, lubricant within the impeller chamber can be entrained and / or mixed into the working fluid flow and can be discharged by the compressor toward downstream components of the vapor compression system (e.g., heat exchangers). Unfortunately, introducing lubricant into heat exchangers can limit their operating efficiency and / or cause wear and deterioration of their components.

[0023] Some conventional compression systems (e.g., motors and compressors) employ one or more dedicated components (e.g., separate components) to prevent lubricant flow toward and / or into the impeller cavity and to divert lubricant flow from the working fluid flow path within the compressor. Such components may be mounted on the motor's rotating shaft between the compressor impeller and a bearing assembly positioned closest to the compressor impeller. Therefore, conventional components implemented to prevent and / or divert lubricant flow within the compressor occupy axial space on the rotating shaft, increasing the distance between the bearing assembly and the impeller (e.g., axial distance). Unfortunately, this increased distance between the impeller and the bearing assembly can impair rotational dynamic stability. Furthermore, such conventional components may not adequately guide the desired amount of lubricant away from the impeller cavity, and thus, lubricant may still flow into the impeller cavity (e.g., the working fluid flow path) and eventually mix with the working fluid directed to downstream components of the vapor compression system, which is potentially undesirable.

[0024] Therefore, embodiments of this disclosure relate to a lubricant diversion system (e.g., an oil diversion system, an integrated lubricant diversion system) configured to direct lubricant away from the compressor impeller, and thus away from the compressor impeller chamber and the working fluid flow path. That is, embodiments of this disclosure relate to a lubricant diversion system configured to reduce, decrease, and / or prevent lubricant flow into the compression side of a compression system (e.g., the impeller side of a system having a compressor and a motor configured to operate to drive the rotation of the compressor). For example, this embodiment relates to a lubricant diversion system including a balance piston (e.g., an oil slinger ring, an integrated balance piston, a lubricant distributor) coupled to the compressor impeller. Pressure seals (e.g., high-pressure seals, high-pressure gas seals, labyrinth seals) may be mounted on a balance piston and configured to restrict (e.g., prevent) a certain amount of lubricant from moving from the motor side of the compression system to the compression side of the compressor system (e.g., the impeller side, the working fluid flow path), thereby reducing the amount of lubricant mixed with the working fluid guided through the compression side of the compressor system.

[0025] Additionally, the balance piston may include an extension (e.g., a flange, a distributor) that extends beyond the pressure seal in a direction toward the motor side of the compression system (e.g., extending outward from the pressure seal). During compressor operation, the balance piston may rotate with the rotor shaft of the motor and may be configured to divert lubricant from the pressure seal, thereby reducing the amount of lubricant introduced into the impeller chamber and the working fluid flow path. In this way, the reduced amount of lubricant can be mixed with the working fluid guided by the compressor through the vapor compression system, thereby improving the efficiency of the vapor compression system. Furthermore, by employing the lubricant diversion system discussed herein, fewer separate auxiliary components (e.g., dedicated components) can be implemented to divert lubricant from the compression side of the compressor system. In this way, the distance (e.g., axial distance) between the impeller and the support (e.g., bearing) of the rotor shaft coupled to the impeller can be reduced, thereby increasing the resonant frequency of the compressor system and / or improving the rotational dynamic stability of the compressor system.

[0026] Now turn to the attached diagram. Figure 1This is a perspective view of an embodiment of a heating, ventilation, air conditioning, and cooling (HVAC&R) system 10 in a building 12 for a typical commercial environment. The HVAC&R system 10 may include a vapor compression system 14 (e.g., a cooler system, a heat pump system) that supplies chilled liquid for use in cooling the building 12. The HVAC&R system 10 may also include a boiler 16 for supplying warm liquid to heat the building 12 and an air distribution system for circulating air through the building 12. The air distribution system may also include an air return duct 18, an air supply duct 20, and / or an air handler 22. In some embodiments, the air handler 22 may include a heat exchanger connected to the boiler 16 and the vapor compression system 14 via a conduit 24. Depending on the operating mode of the HVAC&R system 10, the heat exchanger in the air handler 22 may receive heated liquid from the boiler 16 or cooled liquid from the vapor compression system 14. HVAC&R system 10 is shown as having a separate air processor on each floor of building 12, but in other embodiments, HVAC&R system 10 may include air processor 22 and / or other components that may be shared between floors.

[0027] Figure 2 and Figure 3 An embodiment of a vapor compression system 14 that can be used in an HVAC&R system 10 is shown. The vapor compression system 14 can circulate a working fluid through a loop beginning with a compressor 32. This loop may also include a condenser 34, an expansion valve or device 36, and a liquid cooler or evaporator 38. The vapor compression system 14 may further include a control panel 40 having an analog-to-digital (A / D) converter 42, a microprocessor 44, non-volatile memory 46, and / or an interface board 48. Some examples of fluids that can be used as a working fluid in the vapor compression system 14 are water (e.g., water vapor), R-718, hydrofluorocarbon (HFC) based refrigerants (e.g., R-410A, R-407, R-134a), hydrofluoroolefins (HFO), “natural” refrigerants (such as ammonia (NH3), R-717, carbon dioxide (CO2), R-744), or hydrocarbon-based refrigerants or any other suitable working fluid.

[0028] In some embodiments, the vapor compression system 14 may use one or more of a variable speed drive (VSD) 52, a motor 50, a compressor 32, a condenser 34, an expansion valve or device 36, and / or an evaporator 38. The motor 50 may drive the compressor 32 and may be powered by the VSD 52. The VSD 52 receives AC power with a specific fixed line voltage and fixed line frequency from an alternating current (AC) power source and supplies power with a variable voltage and frequency to the motor 50. In other embodiments, the motor 50 may be directly powered by an AC or direct current (DC) power source. The motor 50 may include any type of motor that can be powered by a VSD or directly from an AC or DC power source, such as a switched reluctance motor, an induction motor, an electronically commutated permanent magnet motor, or another suitable motor.

[0029] Compressor 32 compresses working fluid vapor and delivers it to condenser 34 through a discharge passage. In some embodiments, compressor 32 may be a centrifugal compressor. The working fluid vapor delivered by compressor 32 to condenser 34 transfers heat to a cooling fluid (e.g., water or air) in condenser 34. Due to the heat transfer with the cooling fluid, the working fluid vapor can condense into working fluid liquid in condenser 34. The liquid working fluid from condenser 34 can flow to evaporator 38 via expansion device 36. Figure 3 In the illustrated embodiment, the condenser 34 is water-cooled and includes a tube bundle 54 connected to a cooling tower 56, which supplies cooling fluid to the condenser.

[0030] The liquid working fluid delivered to evaporator 38 may absorb heat from another cooling fluid, which may or may not be the same cooling fluid used in condenser 34. The liquid working fluid in evaporator 38 may undergo a phase change from liquid working fluid to working fluid vapor. For example... Figure 3 As shown in the illustrated embodiment, the evaporator 38 may include a tube bundle 58 having a supply line 60S and a return line 60R connected to the cooling load 62. Cooling fluid (e.g., water, ethylene glycol, calcium chloride brine, sodium chloride brine, or any other suitable fluid) enters the evaporator 38 via the return line 60R and exits the evaporator 38 via the supply line 60S. The evaporator 38 may reduce the temperature of the cooling fluid in the tube bundle 58 via heat transfer with the working fluid. The tube bundle 58 in the evaporator 38 may comprise multiple tubes and / or multiple tube bundles. In any case, the vapor working fluid exits the evaporator 38 and returns to the compressor 32 via the suction line to complete the cycle.

[0031] Figure 4This is a schematic diagram of a vapor compression system 14, in which an intermediate loop 64 is connected between the condenser 34 and the expansion device 36. The intermediate loop 64 may have an inlet line 68 directly fluidly connected to the condenser 34. In other embodiments, the inlet line 68 may be indirectly fluidly connected to the condenser 34. Figure 4 As shown in the illustrated embodiment, the inlet line 68 includes a first expansion device 66 positioned upstream of the intermediate container 70. In some embodiments, the intermediate container 70 may be a flash tank (e.g., a flash intercooler). In other embodiments, the intermediate container 70 may be configured as a "heat exchanger" or a "surface energy saver". Figure 4 In the illustrated embodiment, the intermediate container 70 serves as a flash tank, and the first expansion device 66 is configured to reduce the pressure of the liquid working fluid received from the condenser 34 (e.g., to expand the liquid working fluid). During the expansion process, a portion of the liquid may evaporate, and thus the intermediate container 70 can be used to separate the vapor from the liquid received from the first expansion device 66.

[0032] Additionally, the intermediate container 70 provides further expansion of the liquid working fluid due to the pressure drop it experiences upon entering the intermediate container 70 (e.g., due to the rapid increase in volume experienced upon entering the intermediate container 70). Vapor in the intermediate container 70 can be drawn in by the compressor 32 through its suction line 74. In other embodiments, vapor in the intermediate container can be drawn into an intermediate stage (e.g., a non-suction stage) of the compressor 32. Due to expansion in the expansion device 66 and / or the intermediate container 70, the enthalpy of the liquid collected in the intermediate container 70 can be lower than the enthalpy of the liquid working fluid leaving the condenser 34. The liquid from the intermediate container 70 can then flow in line 72 through the second expansion device 36 to the evaporator 38.

[0033] It should be understood that any of the features described herein can be incorporated into vapor compression system 14 or any other suitable HVAC&R system. For example, this technology can be incorporated into any HVAC&R system having a compressor, such as compressor 32. The following discussion describes the technology in conjunction with an embodiment of compressor 32 configured as a single-stage compressor. However, it should be noted that the systems and methods described herein can be incorporated into other embodiments of compressor 32 and HVAC&R system 10. Furthermore, this technology can be incorporated into HVAC&R systems utilizing any suitable working fluid.

[0034] According to this technology, an electric motor with rotating components (such as motor 50 for compressor 32) can utilize a lubricant diversion system to enable motor 50 and compressor 32 to operate at various speeds while limiting the amount of fluid migration (e.g., lubricant migration) between the motor cavity of motor 50 and the compression cavity of compressor 32 (e.g., impeller side, impeller space, working fluid flow path, compression chamber) during the operating mode of compressor 32. For example, embodiments of the lubricant diversion system discussed herein are configured to block the flow of fluid (e.g., lubricant) from the motor cavity of motor 50 to the compression cavity of compressor 32, and to divert any escaped lubricant from the compression cavity of compressor 32 and / or redirect any escaped lubricant away from the compression cavity of the compressor.

[0035] For the sake of the following discussion, Figure 5 This is a cross-sectional view of a compressor system 100 (e.g., a compression section) of a vapor compression system 14 (e.g., a heat pump system), which has a compressor (such as compressor 32) and an electric motor (such as electric motor 50 of the vapor compression system 14). In this embodiment, the compressor system 100 includes a housing 101 (e.g., a compressor housing, a motor housing, an outer casing) configured to contain, surround, and / or house components of the compressor system 100, such as compressor 32 and / or electric motor 50. In some embodiments, housing 101 may include a compressor housing portion 102 configured to surround components of compressor 32 and an electric motor housing portion 104 configured to surround components of electric motor 50. Compressor housing portion 102 and electric motor housing portion 104 may be coupled to each other (e.g., mounted, fixed). The rotor shaft 106 (e.g., a shaft) of electric motor 50 may be disposed within the internal volume of electric motor housing portion 104 and may be coupled to compressor 32 and configured to drive compressor 32 when electric motor 50 is in operation. For example, the rotor shaft 106 may be connected to the impeller 108 of the compressor 32 via fasteners 110 (e.g., bolts, rods), so that the impeller 108 can rotate within the impeller chamber 109 (e.g., compression chamber, impeller space) when the motor 50 is running, and the rotor shaft 106 can be driven to rotate so that the impeller 108 of the compressor 32 rotates, so that the compressor 32 can compress the working fluid within the impeller chamber 109 to the desired pressure before guiding the working fluid out of the volute portion 112 of the compressor 32 and along the working fluid circuit toward downstream components of the vapor compression system 14 (e.g., heat exchangers, such as condensers and / or evaporators).

[0036] As shown, the rotor shaft 106 can be a cylindrical component having a length extending along an axial or longitudinal axis or direction 200, a radius extending along a radial axis or direction 202, and a circumference extending along a circumferential axis or direction 204 of the compressor system 100. In some embodiments, the rotor shaft 106 may be supported by one or more bearing assemblies (e.g., lubricated bearing assemblies, bearings), and the bearing assemblies may be configured such that the rotor shaft 106 is rotatable relative to the housing 101 about the longitudinal axis 200 to perform work, such as compressing a working fluid. For example, a first bearing 114 (e.g., a first set of bearings, a first bearing assembly) may be located near a first end of the rotor shaft 106 to which the impeller 108 is secured via fasteners 110. That is, the first bearing 114 may be axially spaced from the impeller 108 (e.g., along the longitudinal axis 200), such as by a distance less than a threshold distance away from the impeller 108. The reduced axial spacing between the bearing 114 and the impeller 108 can improve rotational dynamic stability in the compressor system 100. A second bearing 115 (e.g., a second set of bearings) may be disposed near the second end of the rotor shaft 106 opposite the first end (e.g., near the end of the rotor shaft 106 not connected to the impeller 108). Each bearing 114, 115 may be fluidly coupled to a lubricant source 116 via one or more conduits 118 (e.g., lubricant conduits, lubricant circuits, lubricant flow paths). Each conduit 118 (e.g., flow path) may be configured to direct lubricant toward the corresponding bearing assembly 114, 115, thereby facilitating rotation of the rotor shaft 106 about a longitudinal axis 200 (e.g., within the bearing assembly 114, 115, relative to a radial axis 202). The bearing assemblies 114, 115 may include any suitable bearings arranged circumferentially around the rotor shaft 106 (e.g., in the circumferential direction 204), such as sliding bearings, ball bearings, sleeve bearings, roller bearings, etc.

[0037] In some embodiments, the compressor system 100 of the vapor compression system 14 may include a lubricant diversion system 120 (e.g., an integrated balance piston and lubricant slinger ring, an integrated seal and lubricant slinger ring, an integrated balance piston and lubricant distributor) configured to prevent and / or limit the amount of fluid migration (e.g., lubricant migration) toward the impeller chamber 109 (e.g., preventing and / or limiting the amount of fluid migration from the motor chamber of the motor 50 to the compression chamber of the compressor 32, preventing and / or limiting the amount of fluid migration from the motor housing portion 104 to the compressor housing portion 102) and / or redirect lubricant away from the impeller chamber 109 (e.g., redirecting lubricant away from the compressor housing portion 102, redirecting lubricant away from the impeller 108). For example, the lubricant diversion system 120 may include and / or be integrated with a balance piston 122 configured to reduce thrust load on the impeller 108. The balance piston 122 may be coupled (e.g., integrally coupled, integrally formed, mounted, fixed, mechanically coupled) to the impeller 108 and may rotate with the impeller 108 during operation of the compressor system 100. In some embodiments, thrust may be generated in a direction along the longitudinal axis 200 of the compressor system 100 as the impeller 108 rotates. Therefore, during operation, the balance piston 122 may be configured to engage (e.g., abut) with other components of the compressor system 100 (e.g., housing 101) to limit the thrust (e.g., thrust load) generated on the impeller 108 during operation of the compressor system 100. In the illustrated embodiment, the balance piston 122 is integrally formed with the impeller 108. However, in other embodiments (e.g., Figure 7 The balance piston 122 may be coupled (e.g., mounted, secured) to the impeller 108 via one or more fasteners, as described in more detail below.

[0038] In some embodiments, the balance piston 122 may include a body (e.g., an annular body) and may have a wall portion 124 (e.g., a protrusion, an extension, an axial extension) and a cavity 126 (e.g., an annular cavity, chamber, recess, groove) at least partially defined by the wall portion 124. In some embodiments, a portion of the impeller 108 (e.g., the hub of the impeller 108) may further define the cavity 126. For example, in the illustrated embodiment, the balance piston 122 is integrally formed with the impeller 108, and a portion 111 (e.g., a curved portion, an arcuate portion, a hub) of the impeller 108 that extends at least partially along the radial axis 202 (e.g., extends at a non-zero angle relative to the longitudinal axis 200) may further define the cavity 126. The wall portion 124 may extend in a direction (e.g., a linear direction) along the longitudinal axis 200 of the rotor shaft 106 and may be configured to redirect lubricant that has accidentally escaped from the bearings 114, 115 away from the compression chamber of the compressor system 100 (e.g., away from the compressor housing section 102, away from the impeller chamber 109). In some embodiments, at least a portion of the wall portion 124 (e.g., the distal end of the wall portion, the free end of the wall portion) may extend at an angle (e.g., a non-zero angle) relative to the longitudinal axis 200. For example, in some embodiments, the wall portion 124 may extend at an angle (e.g., a non-zero angle, a radially inward angle) toward the rotor shaft 106, while in other embodiments, the wall portion 124 may extend at an angle (e.g., a non-zero angle, a radially outward angle) away from the rotor shaft 106. By orienting the wall portion 124 at an angle relative to the longitudinal axis 200, the balance piston 122 can more effectively remove lubricant that has escaped from the bearings 114, 115. For example, by orienting the wall portion 124, or at least its distal end, at a radially outward angle relative to the longitudinal axis 200, lubricant guided away from the cavity 126 can flow along the wall portion 124. It is noteworthy that, because the free end of the wall portion 124 is oriented at a radially outward angle relative to the longitudinal axis 200, the free end of the wall portion 124 can extend beyond at least a portion of the seal 130 in a direction along the radial axis 202 away from the rotor shaft 106, thereby preventing and / or limiting the introduction of a certain amount of lubricant into the seal 130.

[0039] Cavity 126 is fluidly coupled to channel 128 and can be configured to receive (e.g., capture) lubricant escaping from bearings 114, 115 (e.g., lubricant within housing 101, lubricant within motor housing portion 104). Impeller 108 and / or balancing piston 122 can guide the lubricant captured in cavity 126 toward channel 128. For example, as balancing piston 122 rotates (e.g., via impeller 108), lubricant in cavity 126 can impinge on wall portion 124 and / or portion 111 of impeller 108 before being guided out of cavity 126 and into (e.g., through) channel 128. That is, as impeller 108 rotates, a centrifugal force can be generated along radial axis 202 and away from rotor shaft 106, which causes lubricant in cavity 126 to flow toward and / or along portion 111 of impeller 108 and wall portion 124 (e.g., at least partially along radial axis 202) away from rotor shaft 106. As the lubricant flows away from the rotor shaft 106, it can impinge on the wall portion 124 of the balance piston 122 and / or the portion 111 of the impeller 108, thereby allowing the lubricant to be directed (e.g., diverted) into the channel 128. The channel 128 can be configured to deliver the lubricant away from the housing 101 (e.g., away from the impeller cavity 109 to the periphery of the housing 101) before returning the lubricant to the lubricant source 116.

[0040] In some embodiments, a seal 130 (e.g., a high-pressure gas seal, a pressure seal, a labyrinth seal) may be disposed (e.g., mounted) on a balance piston 122 and configured to engage (e.g., abut) with a wall portion 124 of the balance piston 122 to limit (e.g., prevent) fluid migration (e.g., lubricant migration) from the motor housing section 104 to the compressor housing section 102 (e.g., prevent fluid migration into the impeller cavity 109) and / or fluid migration (e.g., working fluid migration) from the compressor housing portion 102 to the motor housing portion 104. For example, the seal 130 may be a labyrinth seal having a sealing extension and a T-shaped cross-section with a toothed surface configured to prevent fluid (e.g., lubricant) flowing within the channel 128 from flowing through the seal 130 toward the impeller cavity 109. Alternatively, the seal 130 may be configured to prevent the flow (e.g., leakage) of working fluid from the working fluid flow path within the compressor housing section 102 into the motor housing section 104.

[0041] In some embodiments, the wall portion 124 of the balance piston 122 may be configured to extend beyond the seal 130 in a direction along the longitudinal axis 200 (e.g., the axial axis) of the compressor system 100 (e.g., extending beyond the lateral boundary of the seal 130, extending beyond the lateral periphery of the seal 130, and extending further toward the motor housing portion 104 relative to the seal 130 along the longitudinal axis 200) to facilitate the diversion of lubricant from the impeller cavity 109. For example, the wall portion 124 may extend a length along the longitudinal axis 200, and this length of the wall portion 124 may be greater than the length of the seal 130 along the longitudinal axis 200 (e.g., greater than the length of the sealing portion of the seal 130 that engages with the wall portion 124), such that the wall portion 124 extends beyond the lateral boundary of the seal 130 along the longitudinal axis 200. As centrifugal force (e.g., generated by the rotation of impeller 108 and / or balance piston 122) directs the lubricant away from rotor shaft 106 (e.g., in the direction along radial axis 202), portions 111 and / or wall portions 124 of impeller 108 may further divert lubricant from seal 130, thereby limiting a certain amount of lubricant introduced into seal 130, as described in more detail below. By reducing the amount of lubricant introduced into seal 130, the reduced amount of lubricant can be directed into impeller cavity 109, thereby slowing down the mixing of lubricant with working fluid in impeller cavity 109, which allows compressor system 100 and vapor compression system 14 to operate more efficiently.

[0042] As noted above, according to this technology, the combination of the wall portion 124 and the balance piston 122 (e.g., lubricant distribution system 120) with the impeller 108 allows the impeller 108 to be positioned closer to the bearing 114 (e.g., along the longitudinal axis 200) (e.g., less than a threshold distance). In this way, the resonant frequency of the rotor shaft 106 can be increased, and / or the rotational dynamic stability of the compressor system 100 can be improved. For this purpose, in some embodiments, the bearing 114 may extend at least partially along the longitudinal axis 200 into the cavity 126 of the balance piston 122 (e.g., at least partially positioned within the cavity 126). By positioning the bearing 114 at least partially within the cavity 126, the rotor shaft 106, bearing 114, and impeller 108 (e.g., compressor system 100) can be assembled with reduced axial dimensions (e.g., along the longitudinal axis 200), which achieves improved rotational dynamic stability while also reducing the costs associated with the manufacture and assembly of such compressor systems. For example, by positioning the bearing 114 at least partially within the cavity 126, a shorter rotor shaft 106 can be implemented in the compressor system 100 compared to a conventional compressor system.

[0043] In some embodiments, the compressor system 100 may include one or more sensors 140 configured to detect various operating parameters and / or operating conditions of the compressor system 100. The one or more sensors 140 may be located throughout the compressor 32 and / or motor 50 and may be configured to detect data indicating the temperature, pressure, flow rate, or composition of a fluid (e.g., working fluid, lubricant) being guided through the compressor 32 and / or motor 50. Such data may also be used to determine the amount of lubricant within the compressor housing portion 102 and / or motor housing portion 104. For example, data detected by one of the sensors 140 may indicate that the pressure and / or temperature of the working fluid is outside a threshold range that may indicate a threshold amount of lubricant (e.g., an undesirable amount) within the working fluid. The one or more sensors 140 may transmit the detected data to a controller 150 (e.g., control panel 40, control system, automation controller), enabling the controller 150 to control the operation of the compressor system 100. For example, controller 150 may be configured to control the amount of lubricant directed from lubricant source 116 to bearing 114 and / or control the rotational speed of motor 50 (e.g., and thus the rotational speed of impeller 108 and balance piston 122) based on data from one or more sensors 140, as described in more detail below. That is, in some embodiments, certain components of compressor system 100 may be communicatively coupled to controller 150, thereby enabling controller 150 to control the operation of compressor system 100 and / or lubricant distribution system 120 (e.g., by controlling the rotational speed of balance piston 122), as described in more detail below.

[0044] In some embodiments, controller 150 may include processing circuitry 152 (e.g., one or more microprocessors) and memory 154. For example, controller 150 may include non-transitory code or instructions stored in a machine-readable medium (e.g., memory 154) used by processing circuitry 152 to implement the techniques disclosed herein. Memory 154 may include volatile memory, such as read-only memory (ROM), optical disc drive, hard disk drive, solid-state drive, or any other non-transitory computer-readable medium storing instructions that, when executed by processing circuitry 152, control the operation of compressor system 100 and / or lubricant distribution system 120. Controller 150 may monitor and control the operation of lubricant distribution system 120, for example, by controlling the rotational rate of rotor shaft 106, and therefore the rotational rate of impeller 108 and / or balance piston 122.

[0045] In some embodiments, controller 150 may control the operation of compressor system 100 based on feedback received from one or more sensors 140. For example, upon receiving sensor data indicating a threshold amount of lubricant within impeller chamber 109, controller 150 may signal lubricant source 116 to reduce the amount of lubricant directed toward bearing 114. Alternatively, controller 150 may signal motor 50 to increase the rotational speed (e.g., slew rate) of rotor shaft 106. By increasing the rotational speed of rotor shaft 106, the rotational speed of impeller 108 and balance piston 122 can be increased, thereby enabling lubricant diversion system 120 to guide lubricant along passage 128 and away from seal 130 in a more efficient manner relative to a compressor operating at a lower speed. For example, increasing the rotational speed of impeller 108 and balance piston 122 can increase the aforementioned centrifugal force acting on lubricant within chamber 126, thereby reducing the tendency of lubricant to flow toward impeller chamber 109. In this way, lubricant movement into the impeller chamber 109 can be prevented and / or limited, thereby reducing the amount of mixing between the working fluid and the lubricant and improving the efficiency of the vapor compression system employing the compressor system 100. It should be understood that in some embodiments, the controller 150 may control the operation of the compressor system 100 based on manual input provided by an operator associated with the compressor 32.

[0046] Figure 6 This is an embodiment of the compressor system 100. Figure 5 A cross-sectional side view taken within the dashed line 5-5 shows an embodiment of the lubricant distribution system 120. (As shown...) Figure 6 As shown, the lubricant distribution system 120 includes a balance piston 122 having a wall portion 124 that at least partially defines a cavity 126. In the illustrated embodiment, the balance piston 122 is integrally formed with the impeller 108 (e.g., integrally formed as a single component), and thus, a portion 111 of the impeller 108 further defines the cavity 126. Additionally, a portion 160 of the housing 101 (e.g., a portion of the motor housing portion 104) may further define the cavity 126. As noted above, the cavity 126 may be configured to receive lubricant that has escaped from the bearing 114, and the portion 111 of the impeller 108, the balance piston 122, and / or the wall portion 124 may guide the lubricant toward a channel 128, thereby enabling the channel 128 to guide the lubricant away from the compressor system 100 (e.g., returning the lubricant to the lubricant source 116). For example, the centrifugal force generated during the rotation of the balance piston 122 and the impeller 108 can cause the lubricant in the cavity 126 to flow along the lubricant flow path 162 toward the channel 128.

[0047] Due to the geometry of the portion 111 of the cavity 126, which at least partially defines the impeller 108, the cavity 126 may have an inclined profile (e.g., relative to the longitudinal axis 200) that facilitates the diversion of lubricant from the impeller cavity 109 (e.g., at least partially along the radial axis 202) and / or from the seal 130. For example, when lubricant escapes from the bearing 114, the lubricant may move toward the impeller cavity 109 in a first direction 170 (e.g., along the longitudinal axis 200). However, rotation of the balance piston 122 may force the lubricant to move in a second direction 172 along a lubricant flow path 162 that extends at least partially along the radial axis 202 away from the rotor shaft 106. As the lubricant moves along the lubricant flow path 162 in the second direction 172, it can impinge on portion 111 of the impeller 108, causing the lubricant to flow in a third direction 174, which extends at least partially relative to the radial axis 202 at an angle (e.g., a non-zero angle, a radially outward angle) in a direction opposite to direction 170. That is, the balance piston 122 (e.g., portion 111 of the impeller 108 and wall portion 124) can be configured to modify the flow direction of the lubricant within cavity 126 to facilitate the diversion of lubricant away from the compressor system 100. Additionally, due to the inclined profile of cavity 126, a tangential force can be generated, which further aids in diverting lubricant from cavity 126 and into channel 128. For example, because portions 111 of the impeller 108, 124 of the wall, and 160 of the housing 101 alter the flow direction of the lubricant within the cavity 126, a tangential force acting in the opposite direction to direction 170 can be applied to the lubricant flow when the lubricant flow changes direction. In this way, the tangential force can further divert the lubricant toward the channel 128, allowing the lubricant to bypass the seal 130 (e.g., be diverted from it). That is, compared to a conventional compressor system, an increased amount of lubricant within the cavity 126 can be guided through the channel 128 and away from the impeller cavity 109. Furthermore, the centrifugal force generated by the rotation of the impeller 108 and the balance piston 122 can increase the velocity of the lubricant flowing within the channel 128. As the velocity of the lubricant guided through the channel 128 increases, the tendency of the lubricant to change direction and / or flow toward the seal 130 is reduced (e.g., due to inertia), thereby allowing a reduced amount of lubricant to be introduced into the seal 130. Subsequently, a reduced amount of lubricant can be directed into the impeller chamber 109, thereby slowing down the introduction of lubricant into the working fluid being guided through the compressor system 100, which improves the efficiency of the vapor compression system 14.

[0048] As noted above, in some embodiments, at least a portion of the bearing 114 may extend in a direction along the longitudinal axis 200 (e.g., horizontally), such that the bearing 114 is at least partially positioned within the cavity 126 (e.g., radially positioned within the cavity relative to the radial axis 202 and longitudinally positioned within the cavity relative to the longitudinal axis 200). By positioning at least a portion of the bearing 114 within the cavity 126, the first end 180 of the bearing 114 (e.g., the end of the bearing 114 proximal to the impeller 108) may be less than a threshold distance from the impeller 108. The more compact positioning (e.g., axial positioning) of the bearing 114 and the impeller 108 relative to each other (e.g., along the rotor shaft 106) reduces the amount of axial space 182 between the impeller 108 and the bearing 114, thereby improving the rotational dynamic stability of the compressor system 100 while reducing the costs associated with the manufacture and assembly of such compressor systems.

[0049] As noted above, in some embodiments, at least a portion of the wall portion 124 may extend beyond the lateral boundary 184 (e.g., lateral periphery, axial edge) of the seal 130 (e.g., the sealing portion of the seal 130 that engages with the wall portion 124) in a direction along the longitudinal axis 200. By extending the wall portion 124 beyond the lateral boundary 184 of the seal 130 (e.g., along the longitudinal axis 200 toward the motor 50), a reduced amount of lubricant can be introduced into the seal 130. For example, as the impeller 108 rotates with the balance piston 122, the lubricant may flow along the lubricant flow path 162 before reaching the distal end 186 (e.g., the free end of the wall portion 124). Upon reaching the distal end 186 of the wall portion 124, the lubricant may be flung (e.g., pushed, forced, driven) away from the rotor shaft 106 and into the channel 128 in a direction along the radial axis 202 (e.g., radially outward). It is noteworthy that the centrifugal force generated during the rotation of the impeller 108 and the balancing piston 122, and / or the tangential force generated when the lubricant impacts portions of the impeller 108 and / or the balancing piston 122 (e.g., portion 111 of the impeller 108, portion 160 of the housing 101, and wall portion 124), can direct the lubricant out of the cavity 126 at a velocity that allows the lubricant flow to bypass the seal 130. In this way, the likelihood and / or tendency for the lubricant to flow toward the seal 130 and the impeller cavity 109 in direction 170 can be reduced. Furthermore, the additional clearance provided by extending the wall portion 124 beyond the lateral boundary 184 of the seal 130 can further divert lubricant from the seal 130, and thus reduce the amount of lubricant introduced into the seal 130. Additionally, as noted above, in some embodiments, the distal end 186 of the wall portion 124 may extend at an angle (e.g., a non-zero angle relative to the longitudinal axis 200, a radially outward angle) to facilitate the diversion of lubricant from the seal 130. For example, in embodiments where the distal end 186 of the wall portion 124 extends at a radially outward angle relative to the longitudinal axis 200, the distal end 186 of the wall portion 124 may be at least partially aligned with a portion of the seal 130 along the longitudinal axis 200. In this way, the distal end 186 of the wall portion 124 can be used to shield and / or prevent lubricant from reaching the seal 130.

[0050] Figure 7This is a cross-sectional side view, part of an embodiment of compressor system 100, illustrating an embodiment of lubricant distribution system 300. Lubricant distribution system 300 may include features similar to those of lubricant distribution system 120 described above. For example, lubricant distribution system 300 may include a balance piston 302, a passage 304, and a seal 306 (e.g., a high-pressure gas seal) disposed within the motor housing portion 104 of compressor system 100. In the illustrated embodiment, balance piston 302 includes a first portion 308 (e.g., rotor shaft portion, first axial portion, linear portion, mounting portion) configured to at least partially surround and / or radially engage with rotor shaft 106. The first portion 308 may extend in a direction along longitudinal axis 200 (e.g., linear direction, longitudinal direction) and may be configured to engage (e.g., abut, contact) rotor shaft 106. The balancing piston 302 may include a second portion 310 (e.g., impeller portion, impeller hub portion, radial portion) extending from a first portion 308 in a direction along the radial axis 202 (e.g., radial direction) and a third portion 312 (e.g., wall portion, extension, second axial portion, linear portion) extending from the second portion 310 in a direction along the longitudinal axis 200 (e.g., linear direction, longitudinal direction). In some embodiments, the third portion 312 may extend at an angle (e.g., a non-zero angle, a radially inward angle) toward the rotor shaft 106, while in other embodiments, the third portion 312 may extend at an angle (e.g., a non-zero angle, a radially outward angle) away from the rotor shaft 106. By orienting the third portion 312 at an angle relative to the longitudinal axis 200, the balancing piston 302 can more effectively divert lubricant that has escaped from the bearings 114, 115 away from the impeller cavity 109, as described above. It should be understood that the balance piston 302 may be made of a single material, or alternatively, each of the first part 308, the second part 310 and the third part 312 may be joined together by any suitable technique (e.g., welding, brazing).

[0051] like Figure 7As shown, the first portion 308, the second portion 310, and the third portion 312 may collectively define a cavity 314 (e.g., a C-shaped cavity, chamber, recess, or recess) configured to trap lubricant that may escape and / or flow out of the bearing 114. Similar to the balancing piston 122 described above, rotation of the impeller 108 and the balancing piston 302 causes lubricant within the cavity 314 to flow along the lubricant flow path 316 toward the channel 304, thereby allowing the lubricant to bypass the seal 306. As noted above, in some embodiments, the balancing piston 302 may be mechanically coupled (e.g., attached, secured) to the impeller 108. For example, in the illustrated embodiment, a fastener 318 extends through the second portion 310 of the balancing piston 302 and into the body (e.g., hub) of the impeller 108 (e.g., in the direction along the longitudinal axis 200) to secure the balancing piston 302 to the impeller 108. Therefore, when the motor 50 is running to drive the compressor 32 (e.g., when the motor 50 is running to rotate the impeller 108), the balance piston 302 can also rotate, thereby allowing the lubricant to be diverted from the impeller cavity 109 in the manner described above and / or allowing the lubricant to bypass the seal 306.

[0052] Similar to the embodiments described above, the third portion 312 of the balance piston 302 may be configured to extend beyond the seal 306 in a direction along the longitudinal axis 200 (e.g., beyond the lateral boundary 320 of the seal 306) to facilitate the diversion of lubricant from the impeller cavity 109. For example, the third portion 312 may extend a length along the longitudinal axis 200, and this length may be greater than the length of the seal 306 along the longitudinal axis 200, such that the third portion 312 extends beyond the lateral boundary 320 of the seal 306 in a direction 322 along the longitudinal axis 200 toward the bearing 114. In this way, an additional clearance can be provided between the channel 304 and the seal 306, thereby reducing the amount of lubricant introduced into the seal 306.

[0053] Furthermore, as noted above, this technology allows the bearing 114, rotor shaft 106, and impeller 108 to be assembled in a more compact (e.g., axially compact) arrangement. That is, the bearing 114 and impeller 108 can be positioned closer to each other along the longitudinal axis 200. In this way, this technology achieves improved rotational dynamic stability of the compressor system 100. For this purpose, the bearing 114 can extend at least partially along the longitudinal axis 200 into the cavity 314 of the balance piston 302 (e.g., at least partially positioned within the cavity 314). By positioning the bearing 114 at least partially within the cavity 314, the axial distance between the impeller 108 and the bearing 114 can be reduced, thereby improving the rotational dynamic stability of the compressor system 100. That is, compared to existing systems that incorporate separate and / or dedicated components to reduce lubricant flow from the bearing to the impeller, the distance 324 between the first end 180 of the impeller 108 and the bearing 114 along the longitudinal axis 200 can be reduced.

[0054] During operation of the compressor system 100, the lubricant diversion system 300 may be configured to guide the lubricant collected in the cavity 314 toward the periphery (e.g., radial periphery) of the compressor system 100 (e.g., away from the impeller cavity 109, away from the seal 306). For example, similar to the operation of the lubricant diversion system 120, the balance piston 302 of the lubricant diversion system 300 may be configured to rotate together with the impeller 108 to divert (e.g., jerk, force) the lubricant out of the cavity 314. The rotation of the balance piston 302 generates a centrifugal force acting on the lubricant in the cavity 314, causing the lubricant in the cavity 314 to flow at least partially along the radial axis 202 away from the rotor shaft 106 (e.g., radially outward). As the lubricant moves along the radial axis 202 away from the rotor shaft 106, the lubricant may impinge on the balance piston 302 (e.g., impinge on the second portion 310 and / or the third portion 312) between being guided out of the cavity 314 and into the passage 304. Furthermore, the centrifugal force generated during the rotation of the balance piston 302 can increase the velocity of the lubricant flow (e.g., from cavity 314 to channel 304). Since the centrifugal force is directed in a direction away from the rotor shaft 106 along the radial axis 202, it can act on the lubricant flow as it reaches the distal end (e.g., the free end) of the third portion 312, thereby forcing the lubricant flow out of cavity 314 and into channel 304. Notably, because the third portion 314 extends axially beyond the lateral boundary 320 of the seal 306 (e.g., towards motor 50), a reduced amount of lubricant can flow toward the seal 306. Conversely, because the centrifugal force forces the lubricant away from the rotor shaft 106, the lubricant can bypass the seal 306.

[0055] As described above, this disclosure provides one or more technical effects that are useful in operating compressor systems configured to circulate lubricant to facilitate the operation of the compressor system. Embodiments of this disclosure may include a lubricant diversion system configured to divert escaped lubricant from an impeller cavity in which the impeller of the compressor system is positioned. The lubricant diversion system may include a balance piston coupled to the impeller, the balance piston including structural portions that facilitate the collection (e.g., trapping) and diversion (e.g., discharge) of lubricant from the impeller cavity. For example, the balance piston may include a wall portion that at least partially defines a cavity configured to trap lubricant that may escape from the bearings of the compressor system. The wall portion may extend axially beyond the lateral boundary of a seal, such that the lubricant trapped by the cavity may be guided into a channel, thereby allowing the lubricant to bypass the seal. In this way, a reduced amount of lubricant may be introduced into the impeller cavity. Furthermore, by employing the lubricant diversion system discussed herein, the bearings configured to support the rotor shaft of the motor operatively coupled to the compressor can be positioned (e.g., assembled) closer to the axial proximal side of the impeller, compared to conventional compressor systems. In other words, employing the lubricant diversion system discussed herein reduces the axial distance between the bearings and the impeller, thereby improving the rotational dynamic stability of the compressor system while reducing the costs associated with the manufacture and assembly of such compressor systems. Further, by reducing the amount of lubricant introduced into the impeller cavity, this reduced amount of lubricant can be introduced into the working fluid (e.g., refrigerant) guided through the compressor, thereby avoiding the introduction of lubricant into downstream components of the compressor system (e.g., heat exchangers, such as evaporators and / or condensers), which can result in increased heat exchange efficiency in such components.

[0056] While only certain features and embodiments have been described and illustrated, those skilled in the art can make numerous modifications and alterations (e.g., changes in size, dimensions, structure, shape and proportion of various elements, values ​​of parameters (e.g., temperature, pressure, etc.), installation arrangement, use of materials, color, orientation, etc.) without substantially departing from the novel teachings and advantages of the subject matter set forth in the claims. The order or sequence of any process or method steps may be varied or reordered according to alternative embodiments. Therefore, it should be understood that the appended claims are intended to cover all such modifications and alterations that fall within the true spirit of the invention.

[0057] Furthermore, in an effort to provide a concise description of exemplary embodiments, not all features of actual implementations may be described, such as those not relevant to the currently anticipated optimal mode or those unrelated to activation. It should be understood that, as in any engineering or design project, numerous implementation-specific decisions may be made in the development of any such actual implementation. Such development work may be complex and time-consuming, but for those skilled in the art who benefit from this disclosure, these are routine tasks of design, fabrication, and production without requiring excessive experimentation.

[0058] The technical references presented and claimed herein apply to tangible objects and specific examples of practical nature that arguably improve the technical field of the invention and are therefore not abstract, intangible, or purely theoretical. Furthermore, if any claim appended to this specification contains one or more elements expressed as "means for [performing] [function]..." or "steps for [performing] [function]...", such elements are contemplated under 35 USC 112(f). However, for any claim containing elements specified in any other manner, it is intended that such elements not be interpreted under 35 USC 112(f).

Claims

1. A compressor system, comprising: a housing including an impeller disposed therein, wherein the impeller is configured to rotate within an impeller cavity of the housing to compress a working fluid; a motor disposed within the housing, wherein the motor includes a rotor shaft coupled to the impeller, and the motor is configured to drive rotation of the rotor shaft and the impeller; a bearing disposed circumferentially about the rotor shaft, wherein the bearing is configured to receive a lubricant from a lubricant source to facilitate rotation of the rotor shaft; and a lubricant shunt system configured to shunt the lubricant out of the impeller cavity, the lubricant shunt system including: a seal configured to block a flow of the lubricant into the impeller cavity; and a balance piston coupled to the impeller, wherein the balance piston is configured to shunt the lubricant from the seal.

2. The compressor system of claim 1, wherein the balance piston includes a wall portion configured to at least partially define a cavity configured to capture the lubricant that escapes from the bearing.

3. The compressor system of claim 2, wherein the lubricant shunt system includes a channel defined within the housing, the cavity is fluidly coupled to the channel, and the balance piston is configured to direct the lubricant toward the channel during rotation of the balance piston.

4. The compressor system of claim 2, wherein the balance piston is configured to direct the flow of the lubricant through the cavity and radially away from the rotor shaft to bypass the seal.

5. The compressor system of claim 2, wherein the wall portion extends axially beyond a lateral boundary of the seal in an axial direction toward the bearing.

6. The compressor system of claim 2, wherein the seal is configured to interface with a surface of the wall portion to block the flow of the lubricant into the impeller cavity.

7. The compressor system of claim 2, wherein the bearing extends at least partially within the cavity in an axial direction.

8. The compressor system of claim 1, wherein the balance piston is integrally formed with the impeller.

9. The compressor system of claim 1, wherein the balance piston is coupled to the impeller via one or more fasteners.

10. The compressor system of claim 1, wherein the seal is a labyrinth seal.

11. The compressor system of claim 1, comprising: one or more sensors configured to detect data indicative of an amount of the lubricant within the housing; and a controller configured to control operation of the compressor system based on the amount of the lubricant within the housing.

12. The compressor system of claim 11, wherein the controller is configured to increase a rotational speed of the motor based on the amount of the lubricant exceeding a threshold amount.

13. A heating, ventilation, air conditioning, and refrigeration (HVAC&R) system, comprising: a compressor including an impeller configured to rotate within a compression cavity to compress a working fluid and circulate the working fluid through a working fluid circuit; an electric machine coupled to the compressor via a rotor shaft and configured to drive operation of the compressor via rotation of the rotor shaft; and a lubricant shunt system configured to block a flow of a lubricant into the compression cavity, wherein the lubricant shunt system includes: a balance piston including a wall portion at least partially defining a chamber configured to trap the lubricant; and a seal including a sealing portion configured to engage with the wall portion, wherein the balance piston is configured to rotate with the impeller and direct the lubricant within the chamber to flow away from the seal.

14. The HVAC&R system of claim 13, including a bearing configured to receive the lubricant from a lubricant source, wherein the bearing at least partially extends into the chamber in an axial direction.

15. The HVAC&R system of claim 14, wherein the sealing portion of the seal extends a first length in the axial direction, the wall portion of the balance piston extends a second length in the axial direction, and the first length is less than the second length such that the wall portion extends toward the electric machine and beyond an edge of the sealing portion in the axial direction.

16. The HVAC&R system of claim 13, wherein a portion of the impeller at least partially defines the chamber, and wherein the chamber includes a sloped profile configured to shunt the flow of the lubricant away from the seal.

17. A lubricant shunt system for a compressor system, comprising: a balance piston coupled to an impeller of the compressor system, wherein the balance piston includes: a wall portion configured to extend in an axial direction of the compressor system; and a cavity at least partially defined by the wall portion, wherein the cavity is configured to receive a lubricant from a bearing of the compressor system; and a seal configured to abut the wall portion and block a flow of the lubricant toward the impeller, wherein the balance piston is configured to rotate with the impeller during operation of the compressor system and shunt the lubricant away from the seal.

18. The lubricant shunt system of claim 17, wherein the balance piston is integrally formed with the impeller as a unitary body.

19. The lubricant shunt system of claim 18, wherein the cavity is at least partially defined by a hub of the impeller.

20. The lubricant shunt system of claim 17, wherein the balance piston includes an additional wall portion extending in a radial direction and configured to abut the impeller, and the balance piston is coupled to the impeller via one or more fasteners extending through the additional wall portion and into the impeller. ​ ​

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