US20200378657A1 - Heat transfer circuit with increased bearing lubricant temperature, and method of supplying thereof - Google Patents
Heat transfer circuit with increased bearing lubricant temperature, and method of supplying thereof Download PDFInfo
- Publication number
- US20200378657A1 US20200378657A1 US16/427,763 US201916427763A US2020378657A1 US 20200378657 A1 US20200378657 A1 US 20200378657A1 US 201916427763 A US201916427763 A US 201916427763A US 2020378657 A1 US2020378657 A1 US 2020378657A1
- Authority
- US
- United States
- Prior art keywords
- working fluid
- compressor
- heat transfer
- transfer circuit
- lubricant stream
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
- F25B31/004—Lubrication oil recirculating arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/057—Bearings hydrostatic; hydrodynamic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/006—Cooling of compressor or motor
- F25B31/008—Cooling of compressor or motor by injecting a liquid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/01—Heaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/16—Lubrication
Definitions
- Dotted lines are provided in the Figures to indicate fluid flows through the heat exchangers (e.g., condenser 30 , evaporator 50 ), and should be understood as not specifying a specific path of flow through each heat exchanger. Dashed dotted lines are provided in the Figures to illustrate electronic communications between different features. For example, a dashed dotted line extends from a controller 90 to a temperature sensor 92 as the controller 90 receives measurements (e.g., temperature measurements) from the temperature sensor 92 . For example, a dashed-dotted line extends from the controller 90 to a heater 80 as the controller 90 controls the heater 80 .
- the controller 90 includes memory (not shown) for storing information and a processor (not shown). The controller 90 in FIG.
- gas is introduced to an outer circumference or inner circumference of the meshed scrolls and is suctioned into and trapped in pockets between the intermeshed scrolls.
- the pockets move along the intermeshed scrolls and becomes smaller, which compresses the gas trapped in each pocket.
- the pocket then reaches an outlet and compressed gas is discharged from between the intermeshed scrolls.
- the condenser 430 utilizes a first process fluid PF 1 to cool working fluid flowing through the condenser 430
- the evaporator 450 utilizes the working fluid flowing through the evaporator 450 to cool a second process fluid PF 2 similar to the heat transfer circuit 1 in FIG. 1
- the heat transfer circuit 401 in an embodiment may include additional components than those shown in FIG. 5 .
- the heat transfer circuit 401 is oil-free and lubricated by the refrigerant(s) of the working fluid.
- the heat transfer circuit 401 includes a controller 490 .
- the controller 490 may be the controller of the HVACR.
- the controller 490 controls the heater 480 .
- the controller 490 controls the amount of heat provided by the heater 480 to the working fluid flowing through the heater 480 so that the working fluid supplied to the gas bearing 416 from the lubricant stream 460 has the desired amount of superheat.
- the temperature T 5 of the working fluid supplied to the gas bearing 416 (e.g., the temperature of the working fluid at the outlet 464 ) may be determined directly or indirectly.
- the lubricant stream 460 includes a temperature sensor 492 that senses the temperature T 5 of the working fluid flowing through the lubricant stream 460 .
- the working fluid is suctioned at 910 into a tank (e.g., tank 677 ) from a condenser (e.g., condenser 630 ) by a pump (e.g., pump 665 ) or from a last stage of a compressor (e.g., compressor 610 ) by a thermoelectric cooling device (e.g., thermoelectric cooling device 668 ).
- a tank e.g., tank 677
- a condenser e.g., condenser 630
- a pump e.g., pump 665
- a thermoelectric cooling device e.g., thermoelectric cooling device 668
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Fluid Mechanics (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
- This disclosure relates to heating, ventilation, air conditioning, and refrigeration (“HVACR”) systems. More specifically, embodiments herein relate to heat transfer circuits for HVACR systems.
- HVACR systems are generally used to heat, cool, and/or ventilate an enclosed space (e.g., an interior space of a commercial building or a residential building, an interior space of a refrigerated transport unit, or the like). A HVACR system may include a heat transfer circuit for providing cooled or heated air to the area. The heat transfer circuit utilizes a working fluid to cool or heat the air directly or indirectly. Typically, a heat transfer circuit includes a compressor for compressing the working fluid. The compressor includes one or more bearings that require lubrication to operate correctly.
- A HVACR system can include a heat transfer circuit configured to heat and/or cool a process fluid (e.g., air, water and/or glycol, or the like). A working fluid is circulated through the heat transfer circuit. The heat transfer circuit includes a compressor for compressing the working fluid. The working fluid and process fluid separately flow through a heat exchanger to cool and/or heat the process fluid. The heat exchanger may be a condenser or an evaporator.
- The heat transfer circuit includes the compressor having a gas bearing, and a lubricant stream. The lubricant stream supplies gaseous working fluid as the lubricant to the gas bearing to lubricate the gas bearing. The heat transfer circuit includes a heat source configured to prevent liquid working fluid in the gas bearing.
- In an embodiment, the heat source is a heater configured to increase a temperature of the gaseous working fluid flowing through the outlet of the lubricant stream. In an embodiment, the heater is configured to heat the gas bearing and prevent the gaseous working fluid from condensing in the gas bearing.
- In an embodiment, the heat source is an auxiliary compressor that provides compressed gaseous working fluid to the gas bearing during startup or shutdown.
- In an embodiment, the lubricant stream includes a tank and the heat source is a heater disposed in the tank. When the compressor is to be started, the heater is configured to generate compressed gaseous working fluid by vaporizing liquid working fluid in the tank. The lubricant stream supplies the compressed gaseous working fluid to the gas bearing during the startup of the compressor.
- In an embodiment, the working fluid includes one or more low GWP refrigerants. In an embodiment, the working fluid includes at least one HFO refrigerant. In an embodiment, the heat transfer circuit is oil-free and the refrigerant(s) in the working fluid lubricate the heat transfer circuit.
- In an embodiment, the working fluid includes one or more refrigerants, and each of the one or more refrigerants at the outlet of the lubricant stream is gaseous.
- In an embodiment, the working fluid supplied to the gas bearing has a superheat of at or about 4.0° F. or greater than 4.0° F. In an embodiment, the lubricant stream includes the heater. In an embodiment, the working fluid at the inlet of the lubricant stream has a superheat of less than 4.0° F.
- In an embodiment, the inlet of the lubricant stream connects to the main flow path of the heat transfer circuit at the evaporator or after the evaporator and before the condenser. In an embodiment, the lubricant stream includes both a heater and an auxiliary compressor.
- In an embodiment, the heater is an electric heater.
- In an embodiment, the heater is a heat exchanger through which working fluid and a process fluid separately flow. The process fluid heats the working fluid as the working fluid and the second process fluid flow through the heat exchanger. In an embodiment, the process fluid is utilized to cool a heat generating component downstream.
- In an embodiment, a method of supplying lubricant to a gas bearing of a compressor in a heat transfer circuit includes compressing and further heating at least a portion of the working fluid that was heated in the evaporator with a process fluid. The method also includes supplying the compressed and further heated working fluid to the gas bearing of the compressor as the lubricant.
- Both described and other features, aspects, and advantages of a heat transfer circuit and methods of operating a heat transfer circuit will be better understood with the following drawings:
-
FIG. 1 is a schematic diagram of a heat transfer circuit according to an embodiment. -
FIG. 2 is a schematic diagram of a heat transfer circuit according to an embodiment. -
FIG. 3 is a schematic diagram of a heat transfer circuit according to an embodiment. -
FIG. 4 is a schematic diagram of a heat transfer circuit according to an embodiment. -
FIG. 5 is a schematic diagram of a heat transfer circuit according to an embodiment. -
FIG. 6 is a schematic diagram of a heat transfer circuit according to an embodiment. -
FIG. 7 is a schematic diagram of a heat transfer circuit according to an embodiment. -
FIG. 8 is a schematic diagram of a heat transfer circuit according to an embodiment. -
FIG. 9 is a block diagram of a method of supplying lubricant to a gas bearing of a compressor in a heat transfer circuit according to an embodiment. -
FIG. 10 is a block diagram of a method of supplying lubricant to a gas bearing of a compressor in a heat transfer circuit during a shutdown or a startup of the compressor according to an embodiment. - Like reference characters refer to similar features.
- A heating, ventilation, air conditioning, and refrigeration system (“HVACR”) is generally configured to heat and/or cool an enclosed space (e.g., an interior space of a commercial building or a residential building, an interior space of a refrigerated transport unit, or the like). The HVACR system includes a heat transfer circuit to heat or cool a process fluid (e.g., air, water and/or glycol, or the like). A working fluid flows through the heat transfer circuit and is utilized to heat or cool the process fluid. The process fluid may heat and/or cool an enclosed space directly or indirectly. For example, indirect heating and/or cooling may include the working fluid heating and/or cooling an intermediate fluid (e.g., air, water and/or glycol, or the like), and then the heated/cooled intermediate fluid heating and/or cooling the process fluid.
- A working fluid includes one or more refrigerants. A working fluid may also include one or more additional components. For example, an additional component may be, but is not limited to, impurities, refrigeration system additives, tracers, ultraviolet (“UV”) dyes, and/or solubilizing agents.
- There has been recent movement (e.g., the Kigali Amendment to the Montreal Protocol, the Paris Agreement, United States' Significant New Alternatives Policy (“SNAP”)) to limit the types of refrigerants utilized in HVACR systems as concerns about environmental impact (e.g., ozone depletion, global warming impact) have increased. In particular, the movement has been to replace ozone depleting refrigerants (e.g., chlorofluorocarbons (CFCs), hydrochlorofluorocarbons (HCFCs), or the like) and high global warming potential refrigerants with refrigerants that have a lower environmental impact.
- The replacement refrigerants have lower global warming potentials (“GWPs”), and are non-ozone depleting, lower in toxicity, compatible with the materials of the heat transfer circuit and its equipment, and chemically stable over the life of the equipment of the heat transfer circuit. For example, previous refrigerants having higher GWPs are R134a, R22, R125 and the like. Lower GWP refrigerants include, but are not limited to, for example, hydrofluoroolefin (“HFO”) refrigerants. HFO refrigerants include, but are not limited to, for example, R1234ze (e.g., R1234ze(E)), R1336mzz (e.g., R1336mzz(Z)), R1234yf, R1233zd, R1234yf, and the like. The lower GWP refrigerants can be utilized in refrigerant mixtures such as, but not limited to, R452B, R454B, R466A, R513A, R514A, and the like. In an embodiment, lower GWP refrigerants include non-ozone depleting, lower GWP HFCs such as, but not limited to, R32 and the like. In an embodiment, the lower GWP refrigerants have a GWP of less than 700.
- The heat transfer circuit includes a compressor that compresses the working fluid. The compressor includes one or more gas bearings. The gas bearing(s) forms a thin layer of compressed gas to prevent contact between bearing surfaces (e.g., an outer surface of the bearing, an outer surface of a shaft, a thrust surface, or the like). A gas bearing may be an aerostatic gas bearing or an aerodynamic-aerostatic hybrid gas bearing.
- In an embodiment, an aerostatic gas bearing utilizes an external source of compressed gas to form the thin layer of gas during normal operation of the compressor. An external source of compressed gas is gas compressed by the compressor. Normal operation of the compressor does not occur when the compressor is starting up or shutting down.
- In an embodiment, an aerostatic-aerodynamic hybrid gas bearing utilizes both an external source of pressurized gas and a bearing surface that is specifically configured to generate/promote formation of the thin gas layer when rotated or facing a rotating surface. The aerostatic-aerodynamic hybrid gas bearing utilizes an external source of gas until the shaft of the compressor reaches a speed at which its bearing surface is able to generate the thin gas layer. Both aerostatic gas bearings and aerostatic-dynamic hybrid gas bearings utilize an external source of gas.
- A heat transfer circuit can be configured to provide compressed working fluid to the gas bearing(s) of the compressor. Each of the gas bearing(s) utilizes the compressed working fluid as the external source of pressurized gas to form the thin layer of gas that prevents contact between its bearing surfaces. A refrigerant increases in temperature when compressed. The lower GWP refrigerants have differing thermodynamic properties than previous refrigerants such as R134a R22, R125 or the like due to their different chemical structure. The replacement refrigerants have a larger heat capacity when compared to the previous refrigerants. For example, this larger heat capacity results from the lower GWP refrigerants having molecules with more atoms and/or a more complex structure. When compressed in a compressor, this larger heat capacity causes a working that contains one or more of the lower GWP refrigerants to be discharged from the compressor at a temperature closer to their temperature at which they begin to condense than the previous refrigerants. When a refrigerant in a working fluid is partially or fully replaced with a lower GWP refrigerant, this can result in the compressed working fluid discharged from the compressor having a lesser amount of superheat (relative to a working fluid without the lower GWP refrigerant). The superheat of a working fluid is the difference between its current temperature and its dew point at the same pressure (e.g., T(Px)superheat=T(Px)Current−T(Px)Dew Point). The dew point is the temperature at which the working fluid begins to condense at the same pressure. As a working fluid that includes lower GWP refrigerant(s) is closer the temperature/pressure at which it condenses, partial condensation of the working fluid can occur when flowing into and through the gas bearing(s), which can lower performance and/or damage the gas bearing(s) and/or the compressor. Embodiments described herein are directed to heat transfer circuits and methods of supplying lubricant to the gas bearing(s) of the compressor that address lubrication condensation issues that can occur due to, for example, the use of lower GWP refrigerant(s).
-
FIG. 1 is a schematic diagram of a heat transfer circuit 1 according to an embodiment. In an embodiment, the heat transfer circuit 1 may be utilized in a HVACR system. The heat transfer circuit 1 includes acompressor 10, acondenser 30, anexpansion device 40, and anevaporator 50. In an embodiment, the heat transfer circuit 1 can be modified to include additional components, such as, for example, an economizer heat exchanger, one or more valve(s), sensor(s) (e.g., a flow sensor, a temperature sensor), a receiver tank, or the like. - The components of the heat transfer circuit 1 are fluidly connected. The heat transfer circuit 1 can be configured as a cooling system that can be operated in a cooling mode (e.g., a fluid chiller of an HVACR system, an air conditioning system, or the like), or the heat transfer circuit 1 may be configured as a heat pump system that can be run in a cooling mode or a heating mode.
- A working fluid flows through the heat transfer circuit 1. The
main flow path 5 of the working fluid through the heat transfer circuit 1 extends from thecompressor 10, through thecondenser 30, theexpansion device 40, theevaporator 50, and back to thecompressor 10. More specifically, themain flow path 5 extends from anoutlet 14 of thecompressor 10 back to asuction inlet 12 of thecompressor 10. The working fluid includes one or more lower GWP refrigerants. In an embodiment, the working fluid includes one or more HFOs refrigerants. In an embodiment, the heat transfer circuit 1 is oil-free and lubricated by the refrigerant(s) of the working fluid. - Dotted lines are provided in the Figures to indicate fluid flows through the heat exchangers (e.g.,
condenser 30, evaporator 50), and should be understood as not specifying a specific path of flow through each heat exchanger. Dashed dotted lines are provided in the Figures to illustrate electronic communications between different features. For example, a dashed dotted line extends from acontroller 90 to atemperature sensor 92 as thecontroller 90 receives measurements (e.g., temperature measurements) from thetemperature sensor 92. For example, a dashed-dotted line extends from thecontroller 90 to aheater 80 as thecontroller 90 controls theheater 80. In an embodiment, thecontroller 90 includes memory (not shown) for storing information and a processor (not shown). Thecontroller 90 inFIG. 1 and described below is described/shown as a single component. However, it should be appreciated that a “controller” as shown in the Figures and described herein may include multiple discrete or interconnected components that include a memory (not shown) and a processor (not shown) in an embodiment. - Working fluid in a lower pressure gaseous state is drawn into the
suction inlet 12 of thecompressor 10. In an embodiment, thecompressor 10 is a centrifugal compressor, a screw compressor, or a scroll compressor. A centrifugal compressor utilizes a series rotating blades connected to a shaft and/or plate to compress a gas. In an embodiment, gas is introduced to an outer radius of the blades as the shaft and/or plate is rotated. As the blades are rotated, gas is suctioned radially inwards and is then discharged in the axial direction. The blades rotate at speeds that result in the suctioned gas being compressed as it flows radially inward. Accordingly, the compressed gas is discharged in the axial direction. In another embodiment, gas is supplied along the axis of the shaft and/or plate, and the rotating blades gas compress the gas by forcing the gas to flow radially outward. Accordingly, the compressed gas is discharged in the radial direction. A screw compressor utilizes meshed screws in which one or more of the meshed screws are rotated to compress a gas. In an embodiment, gas is introduced to an end or side of the meshed screws and is compressed between the meshed screws as meshed screw(s) are rotated. The gas is then discharged from a second end of the meshed screws from a side or end of the screws. A scroll compressor utilizes at least one pair of intermeshed scrolls in which one or both of the scrolls are rotated relative to each other. In an embodiment, gas is introduced to an outer circumference or inner circumference of the meshed scrolls and is suctioned into and trapped in pockets between the intermeshed scrolls. As the intermeshed scrolls rotate relative to teach other, the pockets move along the intermeshed scrolls and becomes smaller, which compresses the gas trapped in each pocket. The pocket then reaches an outlet and compressed gas is discharged from between the intermeshed scrolls. - The
compressor 10 includes at least onegas bearing 16. Thegas bearing 16 may be a thrust gas bearing and/or a radial gas bearing. Thegas bearing 16 is an aerostatic gas bearing or an aerodynamic-aerostatic hybrid gas bearing. Thegas bearing 16 utilizes an external source of compressed gas to form a thin layer of gas that prevents contact between its bearing surfaces. - The working fluid is compressed as it flows through the
compressor 10 from thesuction inlet 12 to theoutlet 14 of thecompressor 10. The compression of the working fluid in thecompressor 10 also causes the temperature of the working fluid to increase. Accordingly, the compression of the working fluid also causes the temperature of the working fluid at theoutlet 14 of thecompressor 10 to have an increased temperature (relative to the temperature of working fluid at the inlet 12). - The higher pressure and temperature working fluid is discharged the
outlet 14 of the compressor. The majority of the working fluid flows from theoutlet 14 of thecompressor 10 through themain flow path 5 to thecondenser 30. A portion of the working fluid discharged from theoutlet 14 of the compressor and flows into aninlet 62 of thelubricant stream 60. Thelubricant stream 60 is discussed in more detail below. - A first process fluid PF1 flows through the condenser separate from the working fluid. The
condenser 30 is a heat exchanger that allows the working fluid and the first process fluid PF1 to be a heat transfer relationship without physically mixing as they flow through thecondenser 30. As the working fluid flows through thecondenser 30, the working fluid is cooled by the first process fluid PF1. Accordingly, the first process fluid PF1 is heated by the working fluid and exits thecondenser 30 at a higher temperature relative to temperature at which it entered thecondenser 30. In an embodiment, the first process fluid PF1 may be air, water and/or glycol, or the like that is suitable for absorbing and transferring heat from the working fluid and the heat transfer circuit 1. For example, the first process fluid PF1 may be ambient air circulated from an outside atmosphere, water to be heated as hot water, or any suitable fluid for transferring heat from the heat transfer circuit 1. The working fluid becomes liquid or mostly liquid as it is cooled in thecondenser 30. - The liquid/gaseous working fluid flows from the
condenser 30 to theexpansion device 40. Theexpansion device 40 allows the working fluid to expand. The expansion causes the working fluid to significantly decrease in temperature. An “expansion device” as described herein may also be referred to as an expander. In an embodiment, the expander may be an expansion valve, expansion plate, expansion vessel, orifice, or the like, or other such types of expansion mechanisms. It should be appreciated that the expander may be any type of expander used in the field for expanding a working fluid to cause the working fluid to decrease in temperature. - The lower temperature gaseous/liquid working fluid then flows from the
expansion device 40 to and through theevaporator 50. A second process fluid PF2 also flows through theevaporator 50 separately from the working fluid. Theevaporator 50 is a heat exchanger that allows the working fluid and the second process fluid PF2 to be in a heat transfer relationship within theevaporator 50 without physically mixing. As the working fluid and the second process fluid PF2 flow through theevaporator 50, the working fluid absorbs heat from the second process fluid PF2 which cools the second process fluid PF2. Accordingly, the second process fluid PF2 exits theevaporator 50 at a lower temperature than the temperature at which it entered theevaporator 50. The working fluid is gaseous or mostly gaseous as it exits theevaporator 50. The working fluid flows from theevaporator 50 to thesuction inlet 12 of thecompressor 10. - In an embodiment, the second process fluid PF2 is air cooled by the HVACR system and ventilated to the enclosed space to be conditioned. In an embodiment, the second process fluid PF2 is an intermediate fluid (e.g., water, heat transfer fluid, or the like), and the cooled second process fluid PF2 may be utilized by the HVACR system to cool air in or ventilated to the enclosed space to be conditioned.
- A portion of the compressed working fluid that is discharged from the
compressor 10 flows into thelubricant stream 60 instead of flowing to thecondenser 30. In an embodiment, the portion of the compressed working fluid that flows into thelubricant stream 60 is at or about 0.2% to at or about 5% by volume of the working fluid discharged from thecompressor 10. In an embodiment, the portion of the compressed working fluid that flows into thelubricant stream 60 is at or about 0.2% to at or about 5% by volume of the working fluid compressed by thecompressor 10. - As discussed above, the
compressor 10 includes agas bearing 16 that needs compressed gaseous lubricant to operate properly. Compressed working fluid is supplied to thegas bearing 16 by thelubricant stream 60 to lubricate thegas bearing 16. The working fluid supplied to thegas bearing 16 is gaseous. More specifically, the refrigerant(s) of the working fluid supplied to the gas bearing 16 from the lubricant stream are each gaseous. Thegas bearing 16 forms a thin layer of flowing gaseous working fluid between its bearing surfaces (not shown) to prevent contact between the bearing surfaces. The gas in the thin layer then mixes with working fluid entering thecompressor 10 through thesuction inlet 12, and is compressed and discharged from theoutlet 14 of thecompressor 10. - As shown in
FIG. 1 , thelubricant stream 60 includes aheater 80 configured to heat the working fluid as the working fluid passes through thelubricant stream 60. Theheater 80 is disposed between theinlet 62 and theoutlet 64 of thelubricant stream 60. In an embodiment, theheater 80 is a heat source of the heat transfer circuit 1. - In an embodiment, the working fluid discharged by the
compressor 10 has a superheat of less than 4° F. In an embodiment, the working fluid discharged by the compressor has a superheat of less than 3° F. Theheater 80 is configured to heat the working fluid such that compressed working fluid supplied to thegas bearing 16 has a desired amount of superheat. In an embodiment, the desired amount of superheat is at or about 4° F. or greater than 4° F. In an embodiment, the desired amount of superheat is at or about 4.5° F. or greater than 4.5° F. In an embodiment, the desired amount of superheat is at or about 5° F. or greater than 5° F. - The
heater 80 increases the amount of superheat of the compressed working fluid supplied to the gas bearing 16 of thecompressor 10. This greater amount of superheat prevents the gaseous refrigerant(s) supplied to the gas bearing 16 from condensing while in thegas bearing 16. In an embodiment, all of the refrigerant(s) in the compressed working fluid discharged from theoutlet 64 of thelubricant stream 60 are entirely gaseous. - In an embodiment, the
heater 80 inFIG. 1 is an electric heater. Electricity is supplied to theheater 80 and theheater 80 generates heat from the supplied electricity which is used to increase the temperature of the working fluid flowing through theheater 80. In an embodiment, the heat transfer circuit 1 includes acontroller 90 and atemperature sensor 92. Thetemperature sensor 92 is located after theheater 80 and senses the temperature T1 of the compressed working fluid after passing through theheater 80. For example, the temperature T1 is the temperature of the compressed working fluid at theoutlet 64 of thelubricant stream 60. Thecontroller 90 is configured to control the heating provided by theheater 80 to working fluid flowing through theheater 80 so that the working fluid has the desired amount of superheat as described above. Thecontroller 90 may control the amount of heat provided by theheater 80 to the working fluid based on the temperature T1. In an embodiment, electricity is supplied to theheater 80 by thecontroller 90. Thecontroller 90 is configured to supply an amount of electricity to theheater 80 so that theheater 80 heats the working fluid to the temperature corresponding to the desired amount of superheat. - In an embodiment, a minimum amount of working fluid is needed for the
gas bearing 16 to adequately support a load. The load may vary depending on the operating conditions of the compressor 10 (e.g., the compression ratio, volumetric flow rate of working fluid being compressed, or the like). For example, the amount of working fluid for thegas bearing 16 to adequately support its load may be known for each operation condition of thecompressor 10 based on the configuration of thecompressor 10 and/or previous testing of thecompressor 10. - In an embodiment, the
lubricant stream 60 includes anoptional valve 66 and anoptional flow sensor 94. In an embodiment, thecontroller 90 operates theoptional valve 66 based on theflow sensor 94 so that thelubricant stream 60 provides at least a sufficient amount of working fluid to thegas bearing 16 for thegas bearing 16 to support its load. In such an embodiment, theoptional valve 66 may stop flow through thelubricant stream 60 to thegas bearing 16 once thecompressor 10 finishes its start up or shutting down. In an embodiment,lubricant stream 60 may configured to passively control the amount of working fluid that flows through thelubricant stream 60. For example, theinlet 62 in an embodiment may be sized so that at least the sufficient amount of the working fluid flows into thelubricant stream 60 from themain flow path 5 and is supplied to thebearing 16. The size of theinlet 62 in an embodiment is based on the pressure of themain flow path 5 at theinlet 62 of thelubricant stream 60 such that the size of theinlet 62 and the pressure of themain flow stream 5 at theinlet 62 cause at least the sufficient amount of working fluid to flow into thelubricant stream 60 from themain flow path 5. In an embodiment, the pressure of themain flow stream 5 at theinlet 62 may be the minimum pressure that occurs in themain flow stream 5 at theinlet 62 during normal operation of thecompressor 10. In an embodiment, thelubricant stream 60 may be partially or fully incorporated into the housing of thecompressor 10. In an embodiment, part or all or thelubricant stream 60 may be located external to thecompressor 10. - In an embodiment, the
gas bearing 16 may be an aerostatic-hydrostatic hybrid bearing that does not utilize external pressurized gas during normal operation of thecompressor 10. In such an embodiment, thelubricant stream 60 may be configured to stop supplying working fluid to thegas bearing 16 when thecompressor 10 is not starting up and/or shutting down. For example, thecontroller 190 in an embodiment may be configured to close theoptional valve 66 when thecompressor 10 is not starting up and/or shutting down. -
FIG. 2 is a schematic diagram of aheat transfer circuit 101 according to an embodiment. In an embodiment, theheat transfer circuit 101 may be employed in an HVACR system. Theheat transfer circuit 101 is similar to the heat transfer circuit 1 inFIG. 1 , except with respect to the configuration of thelubricant stream 160. For example, theheat transfer circuit 101 includes amain flow path 105, acompressor 110 with asuction inlet 112, anoutlet 114, and at least onegas bearing 116; acondenser 130; anexpansion device 140; and anevaporator 150. Thecondenser 130 utilizes a first process fluid PF1 to cool working fluid flowing through thecondenser 130, and theevaporator 150 utilizes the working fluid flowing through theevaporator 150 to cool a second process fluid PF2 similar to the heat transfer circuit 1 inFIG. 1 . As similarly discussed regarding the heat transfer circuit 1 inFIG. 1 , theheat transfer circuit 101 in an embodiment may include additional components than those shown inFIG. 2 . In an embodiment, theheat transfer circuit 101 is oil-free and lubricated by the refrigerant(s) of the working fluid. - The
lubricant stream 160 provides compressed working fluid to agas bearing 116 of thecompressor 110 similar to thelubricant stream 60 inFIG. 1 . Thelubricant stream 160 includes aninlet 162, anoutlet 164, and aheater 180 disposed between theinlet 162 and theoutlet 164. Theheater 180 is a heat exchanger that includes afirst side 182 and asecond side 184. It should be understood that a “side” in a heat exchanger refers to a separate flow passageway through the heat exchanger, and does not refer to a particular physical orientation. Fluids flowing through thefirst side 182 and thesecond side 184 of theheater 180 exchange heat but do not physically mix. Compressed working fluid enters thelubricant stream 160 through theinlet 162 and exits thelubricant stream 160 through theoutlet 164. The compressed working fluid flows through thelubricant stream 160 by flowing from theinlet 162 to theheater 180, through thefirst side 182 of theheater 180, and from theheater 180 to theoutlet 164. The working fluid flows from theoutlet 164 of thelubricant stream 160 to thegas bearing 116. Thelubricant stream 160 supplying the amount of lubricant to thegas bearing 116 to adequately lubricate thegas bearing 116. - A
cooling circuit 170 is configured to cool aheat generating component 172. For example, operation of thecomponent 172 causes theheat generating component 172 to increase in temperature. In an embodiment, theheat generating component 172 is a variable frequency drive (VFD). For example, the VFD may be for thecompressor 110. In another embodiment, theheat generating component 172 may be a different electronic or mechanical component of the HVACR system that generates heat during operation and needs cooling. A third process fluid PF3 flows through thecooling circuit 170 and is a medium for transferring heat from theheat generating component 172 and cooling theheat generating component 172. In an embodiment, the third process fluid PF3 may be air, water and/or glycol, or the like that is suitable for absorbing heat and transferring from thecomponent 172 to another fluid (e.g., the working fluid). - The third process fluid PF3 flows through the
second side 184 of theheater 180. In an embodiment, after being heated by thecomponent 172, the third process fluid PF3 flows from thecomponent 172 to and through apump 174, from thepump 174 to theheater 180, through thesecond side 184 of theheater 180, and from theheat 180 back to thecomponent 172. Thepump 174 is configured to circulate the third process fluid PF3 through thecooling circuit 170. As the working fluid flows through thefirst side 182 of theheater 180, the working fluid absorbs heat from the third process fluid PF3 in thesecond side 184, which cools the third process fluid PF3. Accordingly, the working fluid flowing through thefirst side 182 is heated as it absorbs heats from the third process fluid PF3 in thesecond side 184. The cooled third process fluid PF3 then flows from theheater 180 back to thecomponent 172. In an embodiment, theheater 180 is a heat source of theheat transfer circuit 101. - The
cooling circuit 170 inFIG. 2 includes theheat generating component 172, thepump 174, and theheater 180. However, it should be appreciated that thecooling circuit 170 in an embodiment may be modified to relocate or not include thepump 174, and/or to include additional components such as, for example, valve(s), sensor(s) (e.g., a flow sensor, a temperature sensor), a receiver tank, or the like. - The
heat transfer circuit 101 includes acontroller 190. In an embodiment, thecontroller 190 may be the controller of the HVACR system. Thelubricant stream 160 includes atemperature sensor 192 similar to thetemperature sensor 92 inFIG. 1 . Thetemperature sensor 192 senses the temperature T1 of the working fluid after passing through theheater 180. Thecontroller 190 is configured to control the heating provided by theheater 180 to the working fluid flowing through theheater 180 so that the working fluid supplied to the gas bearing 116 from thelubricant stream 160 has the desired amount of superheat. Thecontroller 190 may control the amount of heat provided by theheater 180 to the working fluid based on the temperature T1. For example, thecontroller 190 may operate thepump 174 so that the compressed working fluid provided to thegas bearing 116 by thelubricant stream 160 has the desired amount of superheat. The desired amount of superheat can be the same as disused above regarding thelubricant stream 60 inFIG. 1 . In an embodiment, thelubricant stream 160 may also include an auxiliary heater (e.g.,heater 80,heater 280 inFIG. 3 , or the like) to supplement theheater 180. - A portion of the compressed working fluid that is discharged from the
compressor 110 flows into thelubricant stream 160 instead of flowing to thecondenser 130. In an embodiment, the portion of the compressed working fluid that flows into thelubricant stream 160 is at or about 0.2% to at or about 5% by volume of the working fluid discharged from thecompressor 110. In an embodiment, the portion of the compressed working fluid that flows into thelubricant stream 160 is at or about 0.2% to at or about 5% by volume of the working fluid compressed by thecompressor 110. - In an embodiment, the
lubricant stream 160 may include anoptional valve 166 and anoptional flow sensor 194 that are utilized by thecontroller 190 to control the amount of working fluid flowing through thelubricant stream 160 and supplied to thegas bearing 116 similar to theoptional valve 66 andflow sensor 94 inFIG. 1 . In an embodiment,lubricant stream 160 may configured to passively control the amount of working fluid that flows through thelubricant stream 160. For example, theinlet 162 in an embodiment may be sized so that at least the sufficient amount of the working fluid for thebearing 116 flows into thelubricant stream 160 from themain flow path 105. - In an embodiment, the
gas bearing 116 may be an aerostatic-hydrostatic hybrid bearing that does not utilize external pressurized gas during normal operation of thecompressor 110. In such an embodiment, thelubricant stream 160 may be configured to stop supplying working fluid to thegas bearing 116 when thecompressor 110 is not starting up and/or shutting down. For example, thecontroller 190 in an embodiment may be configured to close theoptional valve 166 when thecompressor 110 is not starting up and/or shutting down. -
FIG. 3 is a schematic diagram of aheat transfer circuit 201 according to an embodiment. In an embodiment, theheat transfer circuit 201 may be employed in an HVACR system. Theheat transfer circuit 201 is similar to the heat transfer circuit 1 inFIG. 1 , except with respect to the configuration of thelubricant stream 260. For example, theheat transfer circuit 201 includesmain flow path 205; acompressor 210 with asuction inlet 212, anoutlet 214, and at least onegas bearing 216; acondenser 230; anexpansion device 240; and anevaporator 250 similar to the heat transfer circuit 1 inFIG. 1 . Thecondenser 230 utilizes a first process fluid PF1 to cool working fluid flowing through thecondenser 230, and theevaporator 250 utilizes the working fluid flowing through theevaporator 250 to cool a second process fluid PF2 similar to the heat transfer circuit 1 inFIG. 1 . As similarly discussed regarding the heat transfer circuit 1 inFIG. 1 , theheat transfer circuit 201 in an embodiment may include additional components than those shown inFIG. 3 . In an embodiment, theheat transfer circuit 201 is oil-free and lubricated by the refrigerant(s) of the working fluid. - The
lubricant stream 260 supplies the compressed working fluid to the gas bearing 216 of thecompressor 210 similar to thelubricant stream 60 inFIG. 1 . Thelubricant stream 260 includes aninlet 262, andoutlet 264, and aheater 280 disposed between theinlet 262 and theoutlet 264. Theheater 280 is a heat exchanger that includes afirst side 282 and asecond side 284. Fluids flowing through thefirst side 282 and thesecond side 284 of theheater 280 exchange heat but do not physically mix. Compressed working fluid enters thelubricant stream 260 through theinlet 262 and exits thelubricant stream 260 through theoutlet 264. The compressed working fluid in thelubricant stream 260 flows from theinlet 262 of thelubricant stream 260 to theheater 280, through thefirst side 282 of theheater 280, and from theheater 280 tooutlet 264. The working fluid flows from theoutlet 264 of thelubricant stream 260 to the gas bearing 216 of thecompressor 210 to lubricate thegas bearing 216. In an embodiment, theheater 280 is a heat source of theheat transfer circuit 201. - A
cooling circuit 270 is configured to cool amotor 218 of thecompressor 210. A third process PF3 fluid flows through thecooling circuit 270 and is a medium for transferring heat from themotor 218 of thecompressor 210 to cool themotor 218. In an embodiment, the third process fluid PF3 may be air, water and/or glycol, or the like that is suitable for absorbing and transferring heat from themotor 218 to another fluid (e.g., the working fluid). The third process fluid PF3 may flow along surfaces of themotor 218 and absorb heat from themotor 218. For example, themotor 218 may include a stator (not shown) and a rotor (not shown) and the third process fluid PF3 may be directed along the surfaces of the stator and/or rotor so as to absorb heat from themotor 218. - In an embodiment, after being heated by the
motor 218, the third process fluid PF3 flows frommotor 218 to theheater 280, through thesecond side 284 of theheater 280, from theheater 280 to and through apump 274, and from thepump 274 back to themotor 218. Thepump 274 is configured to circulate the third process fluid PF3 through thecooling circuit 270. - The
cooling circuit 270 inFIG. 3 includes themotor 218, thepump 274, and theheater 280. However, it should be appreciated that thecooling circuit 270 in an embodiment may be modified to move or not include thepump 274, and/or to include additional components such as, for example, valve(s), sensor(s) (e.g., a flow sensor, a temperature sensor), a receiver tank, or the like. - The working fluid flowing through the
first side 282 of theheater 280 absorbs heat from the third process fluid PF3 in thesecond side 284 of theheater 280, which cools the third process fluid PF3. Accordingly, the working fluid flowing through thefirst side 282 is heated as it absorbs the heat from the third process fluid PF3 in thesecond side 284. The cooled third process fluid PF3 then flows from theheater 280 back to themotor 218 of thecompressor 210. - The
heat transfer circuit 201 includes acontroller 290. In an embodiment, thecontroller 290 may be the controller of the HVACR. Thelubricant stream 260 includes atemperature sensor 292 similar to thetemperature sensor 92 inFIG. 1 . Thetemperature sensor 292 senses the temperature T1 of the working fluid after being heated by theheater 280. Thecontroller 290 can operate theheater 280 based on the temperature T1 so that the working fluid supplied to the gas bearing 216 from thelubricant stream 260 has the desired amount of superheat. For example, thecontroller 290 may control operation of thepump 274 so that the working fluid provided to thegas bearing 216 by thelubricant stream 260 has the desired amount of superheat. The desired amount of superheat can be the same as disused above regarding thelubricant stream 60 inFIG. 1 . - A portion of the compressed working fluid that is discharged from the
compressor 210 flows into thelubricant stream 260 instead of flowing to thecondenser 230. In an embodiment, the portion of the compressed working fluid that flows into thelubricant stream 260 is at or about 0.2% to at or about 5% by volume of the working fluid discharged from thecompressor 210. In an embodiment, the portion of the compressed working fluid that flows into thelubricant stream 260 is at or about 0.2% to at or about 5% by volume of the working fluid compressed by thecompressor 210. In an embodiment, thelubricant stream 260 may include anoptional valve 266 and anoptional flow sensor 294 that are utilized by thecontroller 290 to control the amount of working fluid flowing through thelubricant stream 260 and supplied to thegas bearing 216 similar to thevalve 66 andflow sensor 94 inFIG. 1 . In an embodiment,lubricant stream 260 may configured to passively control the amount of working fluid that flows through thelubricant stream 260. For example, theinlet 262 in an embodiment may be sized so that at least the sufficient amount of the working fluid for thebearing 216 flows into thelubricant stream 260 from themain flow path 205. - In an embodiment, the
gas bearing 216 may be an aerostatic-hydrostatic hybrid bearing that does not utilize external pressurized gas during normal operation of thecompressor 210. In such an embodiment, thelubricant stream 260 may be configured to stop supplying working fluid to thegas bearing 216 when thecompressor 210 is not starting up and/or shutting down. For example, thecontroller 290 in an embodiment may be configured to close theoptional valve 266 when thecompressor 210 is not starting up and/or shutting down. -
FIG. 4 is a schematic diagram of aheat transfer circuit 301 according to an embodiment. In an embodiment, theheat transfer circuit 301 may be employed in an HVACR system. Theheat transfer circuit 301 is similar to the heat transfer circuit 1 inFIG. 1 , except with respect to alubricant stream 360. For example, theheat transfer circuit 301 includesmain flow path 305; acompressor 310 with asuction inlet 312, anoutlet 314, and at least onegas bearing 316; acondenser 330; anexpansion device 340; and anevaporator 350. Thecondenser 330 utilizes a first process fluid PF1 to cool working fluid flowing through thecondenser 330, and theevaporator 350 utilizes the working fluid flowing through theevaporator 350 to cool a second process fluid PF2 similar to the heat transfer circuit 1 inFIG. 1 . As similarly discussed regarding the heat transfer circuit 1 inFIG. 1 , theheat transfer circuit 301 in an embodiment may include additional components than those shown inFIG. 4 . In an embodiment, the heat transfer circuit is oil-free and lubricated by the refrigerant(s) of the working fluid. - The
lubricant stream 360 supplies compressed working fluid to the gas bearing 316 of thecompressor 310. Thelubricant stream 360 includes aninlet 362, anoutlet 364, anauxiliary compressor 375, and aheater 380. Theauxiliary compressor 375 and theheater 380 are disposed between theinlet 362 and theoutlet 364. InFIG. 1 , theinlet 362 of thelubricant stream 360 is connected to theevaporator 350, and theoutlet 364 of thelubricant stream 360 is connected to thecompressor 310. In an embodiment, theheater 380 is a heat source of theheat transfer circuit 301. - The
evaporator 350 includes aninlet 352, afirst outlet 354, and asecond outlet 356. After being expanded by theexpansion device 340, the working fluid flows from theexpansion device 340 to theinlet 352 of theevaporator 350. After entering theevaporator 350 through theinlet 352, the working fluid flows through theevaporator 350 and is discharged from theevaporator 350 through thefirst outlet 354 and thesecond outlet 356. A majority of the working fluid that enters theevaporator 350 is discharged through thefirst outlet 354. After being discharged from thefirst outlet 354, the working fluid flows from theevaporator 350 to thesuction inlet 312 of thecompressor 310. Thelubricant stream 360 receives its working fluid from theevaporator 350. The working fluid discharged from thesecond outlet 356 flows into theinlet 362 of thelubricant stream 360. Theinlet 362 of thelubricant stream 360 is fluidly connected to thesecond outlet 356 of theevaporator 350. In an embodiment, theinlet 362 of thelubricant stream 360 is directly connected to thesecond outlet 356 of theevaporator 350. - In
FIG. 4 , theinlet 362 of thelubricant stream 360 is connected to theevaporator 350. However, it should be appreciated that theinlet 362 of thelubricant stream 360 in an embodiment theinlet 362 may be connected to themain flow path 305 of theheat transfer circuit 301 after theevaporator 350 and before thecompressor 110. - The working fluid enters the
lubricant stream 360 through theinlet 362 and exits thelubricant stream 360 through theoutlet 364. The working fluid flows through thelubricant stream 360 by flowing from theinlet 362 through theauxiliary compressor 375, through aheater 380, and from theheater 380 to theoutlet 364. In an embodiment, the positions of theauxiliary compressor 375 and theheater 380 in thelubricant stream 360 may be reversed. The working fluid flows from theoutlet 364 of thelubricant stream 360 to the gas bearing 316 of thecompressor 310. The working fluid flows from thelubricant stream 360 to the gas bearing 316 of thecompressor 310 to lubricate thegas bearing 316. - The working fluid flowing through the
auxiliary compressor 375 is compressed to a higher pressure. In an embodiment, theauxiliary compressor 375 may be a positive displacement or centrifugal compressor. In an embodiment, theauxiliary compressor 375 may be an oil-free compressor. Theauxiliary compressor 375 is configured to compress the working fluid so that the working fluid provided to thegas bearing 316 has an adequate pressure. For example, the pressure and/or amount of working fluid necessary for thegas bearing 316 to adequately support its load may be known for each operating condition of thecompressor 310 based on the configuration of thecompressor 310 and/or previous testing of thecompressor 310. The compressed working fluid flows from theauxiliary compressor 375 to theheater 380. Theheater 380 heats the compressed working fluid so that the compressed working fluid has the desired amount of superheat when supplied to thegas bearing 316. The desired amount of superheat can be the same as discussed above regarding thelubricant stream 60 inFIG. 1 . In an embodiment, the gas bearing 316 of thecompressor 310 may be configured to utilize pressurized working fluid during a shutdown and/or a startup of thecompressor 310. Thelubricant stream 360 is able to advantageously provide working fluid at the pressure and amount for thegas bearing 316 to operate correctly when thecompressor 310 is shutdown, shutting down, and/or starting up. - In an embodiment, the
heater 380 inFIG. 4 is an electric heater that utilizes electricity to heat working fluid as similarly discussed above with respect to theelectric heater 80 inFIG. 1 . However, it should be appreciated that theheater 380 in an embodiment may be a heat exchanger that heats the working fluid with a third process fluid (e.g.,heater 180,heater 280, and the like). For example, third process fluid may flow through a cooling circuit (e.g., coolingcircuit 170, coolingcircuit 270, and the like) and be configured to cool a device in the cooling circuit (e.g.,heat generating component 172,motor 218, and the like). - The
heat transfer circuit 301 includes acontroller 390. In an embodiment, thecontroller 390 may be the controller of the HVACR. Thelubricant stream 360 includes atemperature sensor 392 similar to thetemperature sensor 92 inFIG. 1 . Thetemperature sensor 392 senses the temperature T2 of the working fluid after being heated by theheater 380. Thecontroller 390 is configured to control the heating provided by theheater 380 to the working fluid flowing through theheater 380 so that the working fluid supplied to thegas bearing 316 has the desired amount of superheat. Thecontroller 390 may control the amount of heat provided by theheater 380 to the working fluid based on the temperature T2. The temperature T2 of the working fluid after passing throughheater 380 is greater than the temperature T3 of the working fluid entering thesuction inlet 312 of thecompressor 310. - A portion of the working fluid that enters the
evaporator 350 flows into thelubricant stream 360 instead of exiting theevaporator 350 and flowing into thesuction inlet 312 of thecompressor 310. In an embodiment, at or about 0.2% to at or about 5% by volume of the working fluid that enters theevaporator 350 flows into thelubricant stream 360. In an embodiment, the portion of the compressed working fluid that flows into thelubricant stream 360 is at or about 0.2% to at or about 5% by volume of the working fluid compressed by thecompressor 310. In an embodiment, thelubricant stream 360 may include anoptional valve 366 andoptional flow sensor 394 that are utilized by thecontroller 390 to control the amount of working fluid flowing through thelubricant stream 360 and supplied to thegas bearing 316 similar to theoptional valve 66 andflow sensor 94 inFIG. 1 . In an embodiment, theauxiliary compressor 375 may be variable speed and thecontroller 390 may control speed of theauxiliary compressor 375 to control the amount of workingfluid 360 supplied to thegas bearing 316. In an embodiment,lubricant stream 360 may configured to passively control the amount of working fluid that flows through thelubricant stream 360. For example, theinlet 362 in an embodiment may be sized so that at least the sufficient amount of the working fluid for thebearing 316 flows into thelubricant stream 360 fromevaporator 350. In an embodiment, theauxiliary compressor 375 may be sized so that thelubricant stream 360 provides at least the sufficient amount of the working fluid to thegas bearing 316. - In an embodiment, the
gas bearing 316 may be an aerostatic-hydrostatic hybrid bearing that does not utilize external pressurized gas during normal operation of thecompressor 310. In such an embodiment, thelubricant stream 360 may be configured to stop supplying working fluid to thegas bearing 316 when thecompressor 310 is not starting up and/or shutting down. For example, thecontroller 390 in an embodiment may be configured to close theoptional valve 366 when thecompressor 310 is not starting up and/or shutting down. For example, thecontroller 390 in an embodiment may be configured to shut-down theauxiliary compressor 375 when thecompressor 310 is not starting up and/or shutting down -
FIG. 5 is a schematic diagram of aheat transfer circuit 401 according to an embodiment. In an embodiment, theheat transfer circuit 401 may be employed in an HVACR system. Theheat transfer circuit 401 is similar to the heat transfer circuit 1 inFIG. 1 , except with respect to theheater 480. For example, theheat transfer circuit 401 includes amain flow path 405; acompressor 410 with asuction inlet 412, anoutlet 414, and at least onegas bearing 416; acondenser 430; anexpansion device 440; and anevaporator 450. Thecondenser 430 utilizes a first process fluid PF1 to cool working fluid flowing through thecondenser 430, and theevaporator 450 utilizes the working fluid flowing through theevaporator 450 to cool a second process fluid PF2 similar to the heat transfer circuit 1 inFIG. 1 . As similarly discussed above regarding the heat transfer circuit 1 inFIG. 1 , theheat transfer circuit 401 in an embodiment may include additional components than those shown inFIG. 5 . In an embodiment, theheat transfer circuit 401 is oil-free and lubricated by the refrigerant(s) of the working fluid. - The
lubricant stream 460 supplies compressed working fluid to the gas bearing 416 of thecompressor 410 similar to thelubricant stream 60 inFIG. 1 . The lubricant stream includes aninlet 462 and anoutlet 464. Theinlet 462 of thelubricant stream 460 connects to themain flow path 405 of theheat transfer circuit 401 between thecompressor 410 and thecondenser 430. A portion of the compressed working fluid that is discharged from thecompressor 410 flows into thelubricant stream 460 instead of flowing to thecondenser 430. Thelubricant stream 460 supplies the portion of compressed working fluid to the gas bearing 416 of thecompressor 410 to lubricate thegas bearing 416. - As shown in
FIG. 5 , theheater 480 is located between theevaporator 450 and thecompressor 410. After being heated in theevaporator 450, the working fluid discharged by theevaporator 450 flows from theevaporator 450 to theheater 480. The working fluid flows through theheater 480 and is further heated. The working fluid then flows fromheater 480 to thesuction inlet 412 of thecompressor 410. The working fluid is compressed by thecompressor 410 as it flows through thecompressor 410, and compressed working fluid is discharged from theoutlet 414 of thecompressor 410. - The
heater 480 is configured to heat the working fluid provided to thecompressor 410 such that the compressed working fluid provided to thegas bearing 416 by thelubricant stream 460 has the desired superheat. As discussed above, the working fluid increases in temperature as the working fluid undergoes compression in thecompressor 410. The temperature T5 of the working fluid discharged from thecompressor 410 is greater than the temperature T6 of the working fluid entering thesuction inlet 412 of thecompressor 110. In an embodiment, the working fluid discharged from theoutlet 414 of thecompressor 410 has the desired amount of superheat while the working fluid after theheater 480 and before thecompressor 410 does not have the desired amount of superheat. The desired amount of superheat can be the same as discussed above regarding thelubricant stream 60 inFIG. 1 . In an embodiment, theheater 480 is a source of theheat transfer circuit 401. - The
heat transfer circuit 401 includes acontroller 490. In an embodiment, thecontroller 490 may be the controller of the HVACR. Thecontroller 490 controls theheater 480. Thecontroller 490 controls the amount of heat provided by theheater 480 to the working fluid flowing through theheater 480 so that the working fluid supplied to the gas bearing 416 from thelubricant stream 460 has the desired amount of superheat. The temperature T5 of the working fluid supplied to the gas bearing 416 (e.g., the temperature of the working fluid at the outlet 464) may be determined directly or indirectly. In an embodiment, thelubricant stream 460 includes atemperature sensor 492 that senses the temperature T5 of the working fluid flowing through thelubricant stream 460. In an embodiment, thetemperature sensor 492 may be located in thelubricant stream 460, at theoutlet 414 of thecompressor 410, or between theoutlet 414 of thecompressor 410 and theinlet 462 of thelubricant stream 460. In an embodiment, atemperature sensor 496 is located after theheater 480 and before thecompressor 410 and senses the temperature T6 of the working fluid discharged from theheater 480. For example, the temperature T5 of the working fluid supplied from thelubricant stream 460 may be determined based on the temperature T6. Thecontroller 492 may control the amount of heat provided by theheater 480 to the working fluid based on at least one of the temperature T5 and the temperature T6. - A portion of the compressed working fluid that is discharged from the
compressor 410 flows into thelubricant stream 460 instead of flowing to thecondenser 430. In an embodiment, the portion of the compressed working fluid that flows into thelubricant stream 460 is at or about 0.2% to at or about 5% by volume of the working fluid discharged from thecompressor 410. In an embodiment, the portion of the compressed working fluid that flows into thelubricant stream 460 is at or about 0.2% to at or about 5% by volume of the working fluid compressed by thecompressor 410. - In an embodiment, the
lubricant stream 460 may include anoptional valve 466 and an optional flowsensor flow sensor 494 that are utilized by thecontroller 490 to control the amount of working fluid flowing through thelubricant stream 460 and supplied to thegas bearing 416 similar to theoptional valve 66 and theflow sensor 94 inFIG. 1 . In an embodiment,lubricant stream 460 may configured to passively control the amount of working fluid that flows through thelubricant stream 460. For example, theinlet 462 in an embodiment may be sized so that at least the sufficient amount of the working fluid for thegas bearing 416 flows into thelubricant stream 460 from themain flow path 405. - In an embodiment, the
gas bearing 416 may be an aerostatic-hydrostatic hybrid bearing that does not utilize external pressurized gas during normal operation of thecompressor 410. In such an embodiment, thelubricant stream 460 may be configured to stop supplying working fluid to thegas bearing 416 when thecompressor 410 is not starting up and/or shutting down. For example, thecontroller 490 in an embodiment may be configured to close theoptional valve 466 when thecompressor 410 is not starting up and/or shutting down. - In an embodiment, the
heater 480 inFIG. 5 is an electric heater that utilizes electricity to heat the working fluid as similarly discussed above for theheater 80 inFIG. 1 . However, it should be appreciated that theheater 480 in an embodiment may be a heat exchanger that heats the working fluid with a third process fluid (e.g.,heater 180,heater 280, and the like). For example, the third process fluid may flow through a cooling circuit (e.g., coolingcircuit 170, coolingcircuit 270, and the like) and cool one or more devices that need cooling (e.g.,heat generating component 172,motor 218, and the like). -
FIG. 6 is a schematic diagram of aheat transfer circuit 501 according to an embodiment. In an embodiment, theheat transfer circuit 501 may be employed in an HVACR system. Theheat transfer circuit 501 is similar to the heat transfer circuit 1 inFIG. 1 , except with respect to alubricant stream 560. For example, theheat transfer circuit 501 includes amain flow path 505; acompressor 510 with asuction inlet 512, anoutlet 514, and at least onegas bearing 516; acondenser 530; anexpansion device 540; anevaporator 550; and acontroller 590. Thecondenser 530 utilizes a first process fluid PF1 to cool the working fluid flowing through thecondenser 530, and theevaporator 550 utilizes the working fluid flowing through theevaporator 550 to cool a second process fluid PF2 similar to the heat transfer circuit 1 inFIG. 1 . As similarly discussed regarding the heat transfer circuit 1 inFIG. 1 , theheat transfer circuit 501 in an embodiment may include additional components than those shown inFIG. 6 . In an embodiment, thecontroller 590 may be the controller of the HVACR system. In an embodiment, theheat transfer circuit 501 is oil-free and lubricated by the refrigerant(s) of the working fluid. - In an embodiment, an aerostatic gas bearing needs compressed gas at a minimum pressure and/or flowrate to provide support (e.g., to support a shaft of the compressor 510). In an embodiment, an aerodynamic-aerostatic hybrid gas bearing needs compressed gas at a minimum pressure and/or flowrate to provide support until the shaft reaches a specific rotational speed. The amount of compressed gas, minimum pressure for the compressed gas, and/or the specific shaft rotational speed for a gas bearing to provide support are dependent upon the configuration of the specific aerostatic or aerodynamic-aerostatic hybrid gas bearing. When not provided with at least the minimum pressure of gas, the minimum amount of gas, and/or the shaft is rotating below the specific rotational speed, the gas bearing contacts its opposing surface (e.g., an outer surface of a shaft of the compressor, a surface of the housing of the compressor, or the like) which leads to wear and/or damage of the gas bearing.
- The
lubricant stream 560 supplies compressed working fluid to the gas bearing 516 of thecompressor 510. Thelubricant stream 560 includes afirst inlet 562A, anoutlet 564, anoptional valve 567A, anauxiliary compressor 575, and anoptional tank 577. Thefirst inlet 562A, theauxiliary compressor 575, and theoptional tank 577 are configured to supply compressed gaseous working fluid to thegas bearing 516 during start-up and/or shutdown of thecompressor 510. - The
auxiliary compressor 575 during a start-up and/or shutdown of thecompressor 510 suctions and compresses gaseous working fluid from theevaporator 550 via theinlet 562A. In an embodiment, the compressed gaseous working fluid flows from theauxiliary compressor 575 to theoutlet 564 and is supplied to the gas bearing 516 of thecompressor 510 until the compressor completes its start-up. In an embodiment, theauxiliary compressor 575 supplies compressed gaseous working fluid to thegas bearing 510 during a shutdown of thecompressor 510 until thecompressor 510 is shutdown (e.g., until a shaft of thecompressor 510 is no longer rotating). Theauxiliary compressor 575 generates the compressed gaseous working fluid used by thegas bearing 516 during the shutdown and/or startup of thecompressor 510. - In an embodiment, the
lubricant stream 560 includes anoptional tank 577 and anoptional valve 567A. Thetank 577 is between theauxiliary compressor 575 and theoutlet 564 of thelubricant stream 560. Thevalve 567A is between thetank 577 and the outlet of thelubricant stream 560. Theoptional tank 577 andoptional valve 567A are used for charging a specific amount of compressed gaseous working fluid in thetank 577 for use during a shutdown and/or startup of thecompressor 560. In an embodiment, theauxiliary compressor 575 discharges compressed gaseous working fluid into thetank 577. Thevalve 567A is closed such that the working fluid builds up and is compressed within thetank 577. Thevalve 567A is opened once thetank 577 contains compressed gaseous working fluid that is sufficient to supply thegas bearing 516 with its minimum amount and pressure of compressed gas to operate until the shutdown or startup is completed. The compressed gaseous working fluid then flows from thetank 577 to theoutlet 564 of thelubricant stream 560 and is supplied to the gas bearing 516 from thelubricant stream 560. In an embodiment, theoptional valve 567A is controlled by thecontroller 590. In an embodiment, theheat transfer circuit 501 includes anoptional pressure sensor 592 that is utilized by thecontroller 590 to detect the pressure of the working fluid in thetank 577. - In an embodiment, the
auxiliary compressor 575 has a smaller capacity than thecompressor 510. In an embodiment, the lower efficiency of theauxiliary compressor 575 results in a greater heating of the compressed working fluid discharged from theauxiliary compressor 575. In an embodiment, this greater heating may provide the compressed working fluid with an increased superheat as similarly discussed above. In an embodiment, theauxiliary compressor 575 is a heat source of theheat transfer circuit 501. - In an embodiment, the
gas bearing 516 is a hybrid aerostatic-hydrodynamic bearing. Thelubricant stream 560 provides compressed gaseous working fluid to thegas bearing 516 until the shaft (e.g.,shaft 720 inFIG. 8 ) is rotating at the minimum speed for the hybrid aerostatic-hydrodynamic gas bearing 516 to provide support. - In an embodiment, the
gas bearing 516 is an aerostatic bearing, and thelubricant stream 560 includes anoptional inlet line 569 with an optionalsecond inlet 562B and anoptional valve 567B. Once thecompressor 510 is able to generate sufficient compressed gaseous working fluid for the aerostatic gas bearing 516 (e.g., when the compressor is not shutting down or starting up), a portion of the gaseous compressed working fluid enters thelubricant stream 560 from themain flow path 505 via thesecond inlet 562B. The portion of the gaseous compressed working fluid is then supplied to the aerostatic gas bearing 516 by the lubricant stream. Thevalve 567B prevents the compressed working fluid discharged from theauxiliary compressor 575 from flowing into themain flow path 505. In an embodiment, thevalve 567B may be a check valve or a control valve operated by thecontroller 590. - In an embodiment, the
optional inlet line 569 may have a configuration similar to thelubricant stream 60 inFIG. 1 , thelubricant stream 160 inFIG. 2 , or thelubricant stream 260 inFIG. 3 . For example, thelubricant stream 560 may also include a heater (e.g.,heater second inlet 562B and theoutlet 564 of thelubricant stream 560 to increase the superheat of the gaseous working fluid flowing from thesecond inlet 562B to theoutlet 564. In an embodiment, theheat transfer circuit 501 may include a heater (e.g., heater 480) disposed between theevaporator 550 and thesuction inlet 512 of thecompressor 510 similar to theheat transfer circuit 401 inFIG. 5 . - In
FIG. 6 , thefirst inlet 562A of thelubricant stream 560 is connected to themain flow path 505 between theevaporator 550 and thesuction inlet 512 of thecompressor 510. However, it should be appreciated that thefirst inlet 562A of thelubricant stream 560 in an embodiment may be fluidly connected to amotor housing 519 for themotor 518 of the compressor 510 (shown as 562A′ inFIG. 6 ). Working fluid may be circulated through themotor housing 519 and along themotor 518 to cool themotor 518 as similarly discussed above with respect toFIG. 3 . In an embodiment, thefirst inlet 562A′ is fluidly connected to themotor housing 519 and the working fluid suctioned by theauxiliary compressor 575 is from themotor housing 519 instead of from between theevaporator 550 and thecompressor 510. For example, this configuration can advantageously avoid generating a pressure difference between thegas bearing 516 and theevaporator 550 and/orsuction inlet 512. Themotor 518 andmotor housing 519 are shown inFIG. 6 as internal to thecompressor 510 inFIG. 6 . However, it should be appreciated that themotor 518 andmotor housing 519 may be externally attached to thecompressor 510 in an embodiment. -
FIG. 7 is a schematic diagram of aheat transfer circuit 601 according to an embodiment. In an embodiment, theheat transfer circuit 601 may be employed in an HVACR system. Theheat transfer circuit 601 is similar to the heat transfer circuit 1 inFIG. 1 , except with respect to alubricant stream 660. For example, theheat transfer circuit 601 includes amain flow path 605; acompressor 610 with asuction inlet 612, anoutlet 614, and at least onegas bearing 616; acondenser 630; anexpansion device 640; anevaporator 650; and acontroller 690. Thecondenser 630 utilizes a first process fluid PF1 to cool working fluid flowing through thecondenser 630, and theevaporator 650 utilizes the working fluid flowing through theevaporator 650 to cool a second process fluid PF2 similar to the heat transfer circuit 1 inFIG. 1 . In an embodiment, thecontroller 690 may be the controller of a HVACR system. As similarly discussed regarding the heat transfer circuit 1 inFIG. 1 , theheat transfer circuit 601 in an embodiment may include additional components than those shown inFIG. 7 . In an embodiment, theheat transfer circuit 601 is oil-free and lubricated by the refrigerant(s) of the working fluid. - The
lubricant stream 660 supplies compressed working fluid to the gas bearing 616 of thecompressor 610. Thelubricant stream 660 includes aninlet 662A, anoutlet 664, atank 677, avalve 667A, apump 665, and aheater 680. In an embodiment, theinlet 662A of thelubricant stream 660 is connected to themain flow path 605 at thecondenser 630. Theinlet 662A of thelubricant stream 660 is connected to and receives working fluid from thecondenser 630. - In an embodiment, when the
compressor 610 is to be started up, apump 665 is configured to pump liquid working fluid from thecondenser 630 into thetank 677. After a predetermined amount of working fluid is pumped into thetank 677, aheater 680 heats the liquid working fluid in thetank 677 until the liquid working fluid begins to vaporize. Thevalve 667A is closed causing the gaseous working fluid to be compressed within thetank 677. Once the compressed gaseous working fluid in thetank 677 reaches a predetermined pressure, thevalve 667A is opened and compressed gaseous working fluid flows from thetank 677 to theoutlet 664 of thelubricant stream 660. Thelubricant stream 660 supplies the compressed gaseous working fluid to the gas bearing 616 of thecompressor 610. The predetermined pressure of gaseous working fluid is a pressure that allows thelubricant stream 660 to supply a sufficient compressed gaseous working fluid to thegas bearing 616 for thegas bearing 616 to provide support, for example, until thecompressor 610 completes its startup. For example, the predetermined amount of liquid working fluid is an amount that allows for the tank to build the sufficient amount and pressure of compressed gaseous working fluid for thegas bearing 616. In an embodiment, acontroller 690 may utilize one ormore sensors 692 to detect the pressure, temperature, and/or liquid level of fluid within thetank 677. - In an embodiment, the
gas bearing 616 may be an aerostatic bearing that needs a continuous stream of compressed gas to provide support. Thelubricant stream 660 may include an optionalsecond inlet 662B for supplying compressed gaseous working fluid to the aerostatic gas bearing 616 from thecompressor 610 when the compressor is discharging sufficient compressed gaseous working fluid (e.g., not during a shutdown or startup of the compressor 610). In an embodiment, thelubricant stream 660 may include anoptional valve 667B to prevent fluid from flowing from thetank 677 into themain flow path 605 through the optionalsecond inlet 662B. For example, theoptional valve 667B may be a check valve or a control valve operated by thecontroller 690. In an embodiment, a portion of the compressed working fluid discharged from theoutlet 614 of thecompressor 610 flows into thelubricant stream 660 through thesecond inlet 662B. Theheater 680 then heats the compressed gaseous working fluid flowing through thelubricant stream 660 so that the compressed gaseous working fluid provided to thegas bearing 616 has a higher superheat as similarly discussed above regarding thelubricant stream 60 inFIG. 1 . - The
heater 680 is a heat source of theheat transfer circuit 601 in an embodiment. In an embodiment, theheater 680 is an electric heater. In an embodiment, theheater 680 is a heat exchanger that utilizes a third process fluid (e.g., third process fluid PF3 inFIG. 2 ). In an embodiment, theheat transfer circuit 601 may include a heater disposed between theevaporator 650 and thesuction inlet 612 of thecompressor 610 in themain flow path 605 similar to theheat transfer circuit 401 inFIG. 5 (e.g., heater 480). - In an embodiment, the
lubricant stream 660 may include athermoelectric cooler 668 instead of thepump 665 to add liquid working fluid to thetank 677. Thethermoelectric cooler 668 is able to provide cooling utilizing electricity. In an embodiment, thecontroller 690 supplies electricity to thethermoelectric cooler 668 and thethermoelectric cooler 668 cools the fluid within thetank 677 using the supplied electricity. Thethermoelectric cooler 668 is located within thetank 677 and is configured to condense gaseous working fluid within thetank 677. As the gaseous working fluid is condensed in thetank 677, more gaseous working fluid is suctioned into thetank 677 and condensed. In such an embodiment, theinlet 662A of thelubricant stream 660 is connected to themain flow path 605 before thecondenser 630 and after thesuction inlet 612 of thecompressor 610 instead of to thecondenser 630. For example, in such an embodiment, thelubricant stream 660 may include theinlet 662B instead of theinlet 662A, or theinlet 662A may be connected to the final stage SL of thecompressor 610 instead of thecondenser 630. Thethermoelectric cooler 668 remains on until thetank 677 contains at least the predetermined amount of liquid working fluid as similarly discussed above regarding thepump 665. In an embodiment, thecontroller 690 controls thethermoelectric cooler 668. - The description provided above for the
heat transfer circuits compressor lubricant stream -
FIG. 8 is a schematic diagram of aheat transfer circuit 701 according to an embodiment. In an embodiment, theheat transfer circuit 701 may be employed in an HVACR system. Theheat transfer circuit 701 is similar to the heat transfer circuit 1 inFIG. 1 , except with respect to alubricant stream 760 and the internal configuration of thecompressor 710. For example, theheat transfer circuit 701 includes amain flow path 705; thecompressor 710 with asuction inlet 712, anoutlet 714, and at least one gas bearing 716A, 716B, 716C; acondenser 730; anexpansion device 740; anevaporator 750; and acontroller 790. Thecondenser 730 utilizes a first process fluid PF1 to cool working fluid flowing through thecondenser 730, and theevaporator 750 utilizes the working fluid flowing through theevaporator 750 to cool a second process fluid PF2 similar to the heat transfer circuit 1 inFIG. 1 . In an embodiment, thecontroller 790 may be the controller of a HVACR system. As similarly discussed regarding the heat transfer circuit 1 inFIG. 1 , theheat transfer circuit 701 in an embodiment may include additional components than those shown inFIG. 8 . In an embodiment, theheat transfer circuit 701 is oil-free and lubricated by the refrigerant(s) of the working fluid. - The
compressor 710 includes amotor 718 configured to rotate ashaft 720. Animpeller 722 is attached to an end of theshaft 720. As theshaft 720 rotates, theimpeller 722 is rotated and compresses the working fluid. As shown inFIG. 8 , thecompressor 710 has ahousing 711 that is both the housing for thecompressor 710 and for themotor 718. However, themotor 718 in an embodiment may be external to thecompressor 710. In an embodiment, themotor 718 may include a housing separate from thehousing 711 of thecompressor 710. - The
lubricant stream 760 supplies compressed working fluid to thegas bearings compressor 710. Thelubricant stream 760 includes aninlet 762 and anoutlet 764. A portion of the compressed gaseous working fluid in themain flow path 705 and discharged from thecompressor 710 enters thelubricant stream 760 through theinlet 762. Thelubricant stream 760 supplies the compressed gaseous working fluid to thegas bearings compressor 710 via theoutlet 764 of thelubricant stream 760. Thelubricant stream 760 is shown inFIG. 8 extending outside of thehousing 711 of thecompressor 710. However, thelubricant stream 760 in an embodiment may be incorporated into thehousing 711 of thecompressor 710. - The
lubricant stream 760 supplies compressed gaseous working fluid to the gas bearing 716A to lubricate thegas bearing 716A. The gaseous working fluid expands as the gaseous working fluid flows through thegas bearing 716A. This expansion causes the gaseous working fluid to cool, which also cools thegas bearing 716A. Thecompressor 710 includes aheater 780A that heats a first gas bearing 716A. Theheater 780A prevents the gas bearing 716A from reaching a temperature that would result in the gaseous working fluid condensation within thegas bearing 716A. For example, if the cooling of the gas bearing 716A is not inhibited, the gas bearing 716A can cool the gaseous working fluid as it flows through the gas bearing 716A causing the gaseous working fluid to condense within thegas bearing 716A. Theheater 780A is shown as attached to thegas bearing 716A. However, the heater 780 may be incorporated into the gas bearing 716A in an embodiment. - In an embodiment, the
controller 790 controls the amount of heat provided by theheater 780A to thegas bearing 716A. Atemperature sensor 792A detects the temperature T7 of thegas bearing 716A. In an embodiment, thetemperatures sensor 792A is a thermocouple. In an embodiment, thecontroller 790 controls the amount of heat provided by theheater 780A to thegas bearing 716A. The amount of heat provided by theheater 780A to the gas bearing 716A at least maintaining the gas bearing 716A at a predetermined temperature T7. The predetermined temperature T7 prevents the gaseous working fluid provided to the gas bearing 716A reaching a temperature at which it condenses while flowing through thegas bearing 716A. The predetermined temperature T7 is at or about 4° F. or greater than 4° F. then the dew temperature of the working fluid in thegas bearing 716A. The predetermined temperature T7 is at or about 4.5° F. or greater than 4.5° F. then the dew temperature of the working fluid in thegas bearing 716A. The predetermined temperature T7 is at or about 5° F. or greater than 5° F. then the dew temperature of the working fluid in thegas bearing 716A - The
compressor 710 includes a second gas bearing 716B with asecond heater 780B and a third gas bearing 716C with athird heater 780C. Each of the second andthird heaters first heater 780A. In an embodiment, thecompressor 710 includes atemperature sensor 792B for detecting a temperature T8 of the second gas bearing 716B and atemperature sensor 792C for detecting a temperature T9 the third gas bearing 716C. Thecontroller 790 may control the amount of heat provided by eachheater first heater 780A and the first gas bearing 716A. In an embodiment, each of theheaters heat transfer circuit 701. - The
compressor 710 shown inFIG. 8 includes threegas bearings compressor 710 in an embodiment may have a different number of bearings than three. In an embodiment, thecompressor 710 may have asingle gas bearing compressor 710 may have one ormore gas bearings compressor 710 may have at least one thrust gas bearing 716A and at least one radial gas bearing 716B, 716C. Thecompressor 710 shown inFIG. 8 is a single stage compressor. However, thecompressor 710 in an embodiment may include multiple stages. -
FIG. 9 is a block diagram of an embodiment of amethod 800 of supplying lubricant to at least one gas bearing of a compressor in a heat transfer circuit. For example,method 800 may be for supplying lubricant to the gas bearing in the heat transfer circuit 1 inFIG. 1 , in theheat transfer circuit 101 inFIG. 2 , in theheat transfer circuit 201 inFIG. 3 , in theheat transfer circuit 301 inFIG. 4 , in theheat transfer circuit 401 inFIG. 5 , or in theheat transfer circuit 601 ofFIG. 7 . The lubricant for the gas bearing is a portion of the working fluid flowing in the heat transfer circuit. In an embodiment, the heat transfer circuit is employed in an HVACR system. Themethod 800 starts at 810. - At 810, a working fluid is heated in an evaporator (e.g.,
evaporator method 800 then proceeds to 820. - At 820, at least a portion of the working fluid heated in the evaporator is compressed and further heated. The at least a portion of the working fluid is further heated by a heater (e.g.,
heater compressor - In an embodiment, 820 includes compressing the working fluid heated in the evaporator with the compressor, then further heating a portion of the compressed working fluid in the heater (e.g.,
heat transfer circuit condenser method 800 then proceeds to 830. - At 830, the compressed working fluid that has been heated by the heater is supplied to the gas bearing (e.g.,
gas bearing compressor FIG. 1 . - In an embodiment, the
method 800 may be modified based on the heat transfer circuit 1, theheat transfer circuit 101, theheat transfer circuit 201, theheat transfer circuit 301, theheat transfer circuit 401, and theheat transfer circuit 610 as shown inFIGS. 1-5 and 7 and as described above. For example, themethod 800 in an embodiment may include the heater utilizing another process fluid (e.g., the third process fluid PF3 discussed above) to heat the working fluid flowing through the heater, condensing working fluid with a condenser (e.g.,condenser expansion device -
FIG. 10 is a block diagram of an embodiment of amethod 900 of supplying lubricant to at least one gas bearing of a compressor in a heat transfer circuit during at least one of startup and shutdown of a compressor. For example,method 900 may be for supplying lubricant to the gas bearing in theheat transfer circuit 501 inFIG. 6 , or in theheat transfer circuit 601 inFIG. 7 . The lubricant supplied to the gas bearing is a portion of the working fluid flowing in the heat transfer circuit. In an embodiment, the heat transfer circuit is employed in an HVACR system. Themethod 900 starts at 910. - At the 910, working fluid is suctioned into a lubricant stream (e.g.,
lubricant stream 560, 660) from a main flow path of the heat transfer circuit (e.g.,main flow path 505, 605). In an embodiment, gaseous working fluid is suctioned at 910 from an evaporator (e.g., evaporator 550) or a motor housing (e.g., motor housing 519) of the compressor (e.g., compressor 510) by anauxiliary compressor 575. In an embodiment, the working fluid is suctioned at 910 into a tank (e.g., tank 677) from a condenser (e.g., condenser 630) by a pump (e.g., pump 665) or from a last stage of a compressor (e.g., compressor 610) by a thermoelectric cooling device (e.g., thermoelectric cooling device 668). Themethod 900 then proceeds to 920. - At 920, compressed gaseous working fluid is generated within the lubricant stream from the suctioned working fluid. The compressed gaseous working fluid is supplied to at least one gas bearing of the compressor (e.g.,
gas bearing 516, 616). The compressed working fluid generated within the lubricant stream is supplied to the gas bearing until the compressor completes its startup and or is shutdown. - In an embodiment, an auxiliary compressor (e.g., auxiliary compressor 575) compresses the suctioned gaseous working fluid to generate compressed gaseous working fluid. In an embodiment, a heater (e.g., heater 680) vaporizes the suctioned liquid working fluid within a tank of the lubricant stream (e.g., tank 677). The gaseous working fluid becomes compressed as the heater vaporizes more liquid working fluid. The compressed gaseous working fluid is then supplied to the gas bearing of the compressor until the compressor completes its startup and/or is shutdown.
- In an embodiment, the
method 900 may be modified based on theheat transfer circuit 501 and theheat transfer circuit 601 as shown inFIGS. 6 and 7 and as described above. - Any of aspects 1-17 can be combined with any of aspects 18-24, and any of aspects 18-20 can be combined with any of aspects 21-24.
- Aspect 1. A heat transfer circuit, comprising:
-
- a compressor for compressing a working fluid, the compressor including a gas bearing;
- a condenser for cooling the working fluid with a first process fluid;
- an expander for expanding the working fluid;
- an evaporator for heating the working fluid with a second process fluid;
- a main flow path of the working fluid extending from the compressor through the condenser, the expander, the evaporator, and back to the compressor;
- a lubricant stream including an inlet and an outlet, the inlet receiving a portion of the working fluid from the main flow path and the outlet supplying the portion of the working fluid to the gas bearing of the compressor, the portion of the working fluid includes one or more refrigerants that are each gaseous at the outlet of the lubricant stream; and
- a heat source configured to increase one of a temperature of the working fluid flowing through the outlet of the lubricant stream and a temperature of the gas bearing.
Aspect 2. The heat transfer circuit of aspect 1, wherein the portion of the working fluid supplied to the gas bearing from the lubricant stream has a superheat of at or about 4.0° F. or greater than 4.0° F.
Aspect 3. The heat transfer circuit of either one of aspects 1 or 2, wherein the lubricant stream includes the heat generating component, and the portion of the working fluid at the inlet of the lubricant stream has a superheat of less than 4.0° F.
Aspect 4. The heat transfer circuit of any one of aspects 1-3, wherein superheat of the portion of the working fluid supplied to the gas bearing is at or about 5.0° F. or greater than 5.0° F.
Aspect 5. The heat transfer circuit of any one of aspects 1-4, wherein the inlet of the lubricant stream connects to the main flow path at the evaporator or after the evaporator and before the condenser.
Aspect 6. The heat transfer circuit of any one of aspects 1-5, wherein the inlet of the lubricant stream connects to the main flow path after the compressor and before the condenser.
Aspect 7. The heat transfer circuit of anyone of aspects 1-6, wherein the heat source is a heater.
Aspect 8. The heat transfer circuit of aspect 7, wherein the heater is an electric heater.
Aspect 9. The heat transfer circuit of aspect 7, wherein the heater is a heat exchanger, the working fluid and a third process fluid flowing separately through the heater, the third process fluid heating the working fluid as the working fluid and the third process fluid flow through the heater.
Aspect 10. The heat transfer circuit of aspect 9, further comprising: - a cooling circuit including the heater and the third process fluid flowing through the cooling circuit.
Aspect 11. The heat transfer circuit ofaspect 10, wherein the cooling circuit includes one of a variable frequency drive and a motor of the compressor, the third process fluid cooling the one of the variable frequency drive and the motor of the compressor.
Aspect 12. The heat transfer circuit of any one of aspects 7-11, wherein - the lubricant stream includes a tank and a thermoelectric cooler, the heater and the thermoelectric cooler disposed within the tank,
- the thermoelectric cooler and the thermoelectric cooler configured to generate compressed gaseous working fluid within the tank for the lubricant stream to supply to the gas bearing, the compressed gaseous working fluid generated by the thermoelectric cooler condensing the portion of the working fluid and the heater vaporizing the condensed working fluid.
Aspect 13. The heat transfer circuit of aspect 1, wherein the heat source is a heater attached to or a part of the gas bearing.
Aspect 14. The heat transfer circuit of any one of aspects 1-13, wherein the lubricant stream includes an auxiliary compressor configured to compress the portion of the working fluid flowing through lubricant stream, the inlet of the lubricant stream connected to one of the evaporator, between the evaporator and the compressor, or a motor housing of the compressor.
Aspect 15. The heat transfer circuit ofaspect 14, wherein the auxiliary compressor is the heat generating source.
Aspect 16. The heat transfer circuit of any one of aspects 1-15, wherein the one or more refrigerants include an HFO refrigerant.
Aspect 17. The heat transfer circuit of any one of aspects 1-16, wherein the compressor is an oil-free compressor.
Aspect 18. A method of supplying lubricant to a gas bearing of a compressor in a heat transfer circuit, the heat transfer circuit including the compressor, a condenser, an expander, an evaporator, and a heater, a working fluid flowing through the heat transfer circuit, the method comprising: - heating the working fluid in the evaporator with a process fluid;
- compressing and further heating at least a portion of the working fluid heated in the evaporator, the further heating including the heater heating the portion of the working fluid heated in the evaporator, and the compressing including one of the compressor and an auxiliary compressor compressing the portion of the working fluid heated in the evaporator; and
- supplying the compressed and further heated portion of the working fluid to the gas bearing of the compressor as the lubricant.
Aspect 19. The method of aspect 18, wherein the compressed and further heated portion of the working fluid supplied to gas bearing has a superheat of at or about 4.0° F. or greater than 4.0° F.
Aspect 20. The method of either one of aspects 18 or 19, wherein the compressing includes the compressor compressing the working fluid heated in the evaporator, and the portion of the working fluid heated by the heater is a portion of the working fluid compressed by the compressor.
Aspect 21. A method of supplying lubricant to a gas bearing of a compressor in a heat transfer circuit, the heat transfer circuit including the compressor, a condenser, an expander, an evaporator, and a heat source, a working fluid flowing through the heat transfer circuit, a main flow path of the working fluid extending from the compressor through the condenser, the expander, the evaporator, and back to the compressor, the method comprising: - suctioning a portion of the working fluid into the lubricant stream; and
- generating compressed gaseous working fluid within the lubricant stream from the portion of the working fluid, the compressed gaseous working fluid supplied from the lubricant stream to the gas bearing of the compressor.
Aspect 22. The method of aspect 21, wherein - the portion of the working fluid is gaseous working fluid suctioned from the evaporator or a motor housing of the compressor, and
- generating compressed gaseous working fluid within the lubricant stream from the portion of the working fluid includes an auxiliary compressor compressing the gaseous working fluid within the lubricant stream to generate the compressed gaseous working fluid.
Aspect 23. The method of aspect 21, wherein - suctioning the portion of the working fluid into the lubricant stream includes suctioning the portion of working fluid into a tank of the lubricant stream, and
- generating compressed gaseous working fluid within the lubricant stream from the portion of the working fluid includes vaporizing the portion of the working fluid within the tank to generate the compressed gaseous working fluid
Aspect 24. The method of aspect 23, wherein - suctioning the portion of the working fluid into the lubricant stream includes one of:
- pumping the portion of the working fluid from the condenser into a tank of the lubricant stream, the portion of working fluid suctioned into the lubricant stream being liquid working fluid, and
- condensing the portion of the working fluid within the tank of the lubricant stream, the portion of the working fluid suctioned into the lubricant stream being gaseous working fluid.
- The examples disclosed in this application are to be considered in all respects as illustrative and not limitative. The scope of the invention is indicated by the appended claims rather than by the foregoing description; and all changes which come within the meaning and range of equivalency of the claims are intended to be embraced therein.
Claims (24)
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US16/427,763 US20200378657A1 (en) | 2019-05-31 | 2019-05-31 | Heat transfer circuit with increased bearing lubricant temperature, and method of supplying thereof |
CN202010481793.9A CN112013569A (en) | 2019-05-31 | 2020-05-29 | Heat transfer circuit with elevated bearing lubricant temperature and method of supplying same |
EP20177728.1A EP3745050A1 (en) | 2019-05-31 | 2020-06-01 | Heat transfer circuit with increased bearing lubricant temperature, and method of supplying thereof |
US18/064,665 US20230106287A1 (en) | 2019-05-31 | 2022-12-12 | Heat transfer circuit with increased bearing lubricant temperature, and method of supplying thereof |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US16/427,763 US20200378657A1 (en) | 2019-05-31 | 2019-05-31 | Heat transfer circuit with increased bearing lubricant temperature, and method of supplying thereof |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US18/064,665 Division US20230106287A1 (en) | 2019-05-31 | 2022-12-12 | Heat transfer circuit with increased bearing lubricant temperature, and method of supplying thereof |
Publications (1)
Publication Number | Publication Date |
---|---|
US20200378657A1 true US20200378657A1 (en) | 2020-12-03 |
Family
ID=70975734
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US16/427,763 Abandoned US20200378657A1 (en) | 2019-05-31 | 2019-05-31 | Heat transfer circuit with increased bearing lubricant temperature, and method of supplying thereof |
US18/064,665 Pending US20230106287A1 (en) | 2019-05-31 | 2022-12-12 | Heat transfer circuit with increased bearing lubricant temperature, and method of supplying thereof |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US18/064,665 Pending US20230106287A1 (en) | 2019-05-31 | 2022-12-12 | Heat transfer circuit with increased bearing lubricant temperature, and method of supplying thereof |
Country Status (3)
Country | Link |
---|---|
US (2) | US20200378657A1 (en) |
EP (1) | EP3745050A1 (en) |
CN (1) | CN112013569A (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20210247096A1 (en) * | 2020-02-07 | 2021-08-12 | Carrier Corporation | A2l compliant contactor |
US20210404720A1 (en) * | 2020-06-24 | 2021-12-30 | Carrier Corporation | Foil bearing lubrication |
CN113945021A (en) * | 2021-10-29 | 2022-01-18 | 青岛海尔空调电子有限公司 | Method and device for controlling starting and stopping of water chilling unit and water chilling unit |
US20220316767A1 (en) * | 2019-06-12 | 2022-10-06 | Daikin Industries, Ltd. | Refrigerant cycle system |
WO2023035665A1 (en) * | 2021-09-08 | 2023-03-16 | 青岛海尔空调电子有限公司 | Gas supply system for suspension bearing, and refrigeration system |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11913463B2 (en) * | 2021-05-07 | 2024-02-27 | Trane International Inc. | Gas bearing compressor backup power |
CN113970197B (en) * | 2021-10-29 | 2023-03-31 | 青岛海尔空调电子有限公司 | Control method and device for air supply system, refrigeration equipment and storage medium |
US20240077239A1 (en) * | 2022-09-01 | 2024-03-07 | Trane International Inc. | Refrigerant circuit compressor gas bearing feed |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6032783B2 (en) * | 1978-12-22 | 1985-07-30 | 株式会社荏原製作所 | Refrigeration equipment oil return device |
JP2008014533A (en) * | 2006-07-04 | 2008-01-24 | Ebara Corp | Oil recovering device of compression type refrigerating machine |
GB201122142D0 (en) * | 2011-12-21 | 2012-02-01 | Venus Systems Ltd | Centrifugal compressors |
US9032753B2 (en) * | 2012-03-22 | 2015-05-19 | Trane International Inc. | Electronics cooling using lubricant return for a shell-and-tube style evaporator |
US10634154B2 (en) * | 2016-07-25 | 2020-04-28 | Daikin Applied Americas Inc. | Centrifugal compressor and magnetic bearing backup system for centrifugal compressor |
US11274679B2 (en) * | 2017-02-14 | 2022-03-15 | Danfoss A/S | Oil free centrifugal compressor for use in low capacity applications |
-
2019
- 2019-05-31 US US16/427,763 patent/US20200378657A1/en not_active Abandoned
-
2020
- 2020-05-29 CN CN202010481793.9A patent/CN112013569A/en active Pending
- 2020-06-01 EP EP20177728.1A patent/EP3745050A1/en active Pending
-
2022
- 2022-12-12 US US18/064,665 patent/US20230106287A1/en active Pending
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20220316767A1 (en) * | 2019-06-12 | 2022-10-06 | Daikin Industries, Ltd. | Refrigerant cycle system |
US20210247096A1 (en) * | 2020-02-07 | 2021-08-12 | Carrier Corporation | A2l compliant contactor |
US20210404720A1 (en) * | 2020-06-24 | 2021-12-30 | Carrier Corporation | Foil bearing lubrication |
WO2023035665A1 (en) * | 2021-09-08 | 2023-03-16 | 青岛海尔空调电子有限公司 | Gas supply system for suspension bearing, and refrigeration system |
CN113945021A (en) * | 2021-10-29 | 2022-01-18 | 青岛海尔空调电子有限公司 | Method and device for controlling starting and stopping of water chilling unit and water chilling unit |
Also Published As
Publication number | Publication date |
---|---|
US20230106287A1 (en) | 2023-04-06 |
EP3745050A1 (en) | 2020-12-02 |
CN112013569A (en) | 2020-12-01 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20230106287A1 (en) | Heat transfer circuit with increased bearing lubricant temperature, and method of supplying thereof | |
CN114111113B (en) | Lubricant Management for HVACR Systems | |
US10634154B2 (en) | Centrifugal compressor and magnetic bearing backup system for centrifugal compressor | |
CN109114013B (en) | Centrifugal refrigerant vapor compressor | |
CN105143789A (en) | Lubrication and cooling system | |
JPH0886516A (en) | Refrigerating device | |
US9222706B2 (en) | Refrigeration cycle apparatus and operating method of same | |
JP2003322421A (en) | High pressure side pressure control method in supercritical vapor compression circuit and circuit device | |
CN111566420A (en) | Air conditioning apparatus | |
JP2016003645A (en) | Scroll compressor, and air conditioner | |
EP3745057B1 (en) | Lubricant quality management for a compressor | |
JP2001004235A (en) | Steam compression refrigeration cycle | |
JP2007187332A (en) | Refrigeration cycle device | |
JP2009063247A (en) | Refrigeration cycle device, and fluid machine using it | |
JP2000337722A (en) | Vapor compression type refrigeration cycle | |
US11421924B2 (en) | Heat transfer circuit with targeted additive supply | |
WO2015104822A1 (en) | Refrigeration cycle device | |
US11827832B2 (en) | Grease and refrigeration cycle apparatus using grease as lubricant | |
EP4332459A1 (en) | Refrigerant circuit with compressor gas bearing feed | |
CN112368523A (en) | Refrigeration cycle apparatus and control method thereof | |
JP2000320912A (en) | Refrigerant circulating system | |
WO2015104823A1 (en) | Refrigeration cycle device | |
JP2007198681A (en) | Heat pump device | |
JP2005090800A (en) | Refrigeration unit | |
JP2021161923A (en) | Compressor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: TRANE INTERNATIONAL INC., NORTH CAROLINA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:JEUNG, SUNG HWA;JOHNSON, JAY H.;ROESLER, CHARLES;AND OTHERS;REEL/FRAME:049330/0382 Effective date: 20190530 |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: NON FINAL ACTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: RESPONSE TO NON-FINAL OFFICE ACTION ENTERED AND FORWARDED TO EXAMINER |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: NON FINAL ACTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: FINAL REJECTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: RESPONSE AFTER FINAL ACTION FORWARDED TO EXAMINER |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: ADVISORY ACTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: NON FINAL ACTION MAILED |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: RESPONSE TO NON-FINAL OFFICE ACTION ENTERED AND FORWARDED TO EXAMINER |
|
STPP | Information on status: patent application and granting procedure in general |
Free format text: FINAL REJECTION MAILED |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |