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WO2024182415A1 - Système de conduit d'huile pour système cvc&r - Google Patents

Système de conduit d'huile pour système cvc&r Download PDF

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Publication number
WO2024182415A1
WO2024182415A1 PCT/US2024/017512 US2024017512W WO2024182415A1 WO 2024182415 A1 WO2024182415 A1 WO 2024182415A1 US 2024017512 W US2024017512 W US 2024017512W WO 2024182415 A1 WO2024182415 A1 WO 2024182415A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
refrigerant
compressor
channel
flow path
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.)
Ceased
Application number
PCT/US2024/017512
Other languages
English (en)
Inventor
Angela Marie Comstock
Shahebaz Malik
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Tyco Fire and Security GmbH
Original Assignee
Tyco Fire and Security GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Tyco Fire and Security GmbH filed Critical Tyco Fire and Security GmbH
Priority to CN202480019182.9A priority Critical patent/CN120958282A/zh
Priority to KR1020257032268A priority patent/KR20250153293A/ko
Publication of WO2024182415A1 publication Critical patent/WO2024182415A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F25B41/40—Fluid line 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant

Definitions

  • Chiller systems utilize a working fluid (e.g., a refrigerant) that changes phases between vapor, liquid, and combinations thereof in response to exposure to different temperatures and pressures within components of the chiller system.
  • the chiller system may place the working fluid in a heat exchange relationship with a conditioning fluid (e.g., water) and may deliver the conditioning fluid to conditioning equipment and/or a conditioned environment serviced by the chiller system.
  • the chiller system may include a heat exchanger configured to receive the working fluid and the conditioning fluid to place the w orking fluid in the heat exchange relationship with the conditioning fluid.
  • the conditioning fluid may be directed from the heat exchanger to other equipment, such as air handlers, to condition other fluids, such as air in a building.
  • the w orking fluid may be directed from the heat exchanger through other components of the chiller system, such as a compressor and/or a condenser, configured to process (e.g., pressurize, cool) the working fluid to enable the working fluid to provide further conditioning of the conditioning fluid.
  • the chiller system may also utilize oil to facilitate operation of certain components, such as the compressor, of the chiller system.
  • a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system includes a compressor and an oil conduit system.
  • the compressor includes an inlet configured to receive refrigerant directed along a refrigerant flow path and through the compressor, a displacement component, and an actuator configured to drive operation of the displacement component to pressurize the refrigerant in a chamber of the compressor.
  • the oil conduit system includes a channel configured to direct oil into the refrigerant flow path, and the channel is configured to place the oil in a heat exchange relationship with the refrigerant directed along the refrigerant flow path and flowing at least partially along a direction extending from the inlet to the chamber.
  • an oil conduit system for a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system includes an oil filter configured to remove impurities from an oil flow, and a channel positioned adjacent a refrigerant flow path through a compressor, where the channel is configured to receive the oil flow from the oil filter and direct the oil flow into a heat exchange relationship with a refrigerant directed along the refrigerant flow path.
  • HVAC&R heating, ventilation, air conditioning, and refrigeration
  • a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system includes a compressor and an oil conduit system.
  • the compressor includes a support having a plurality' of ribs extending inwardly to support an actuator of the compressor, and the plurality of ribs defines a plurality of passages configured to receive refrigerant and direct the refrigerant therethrough.
  • the oil conduit system includes a channel configured to direct oil therethrough, the channel is formed through at least one of the plurality' of ribs, and the channel in configured to place the oil in a heat exchange relationship with the refrigerant directed through the plurality of passages.
  • FIG. 1 is a perspective view of a building utilizing an embodiment of a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system in a commercial setting, in accordance with an aspect of the present disclosure;
  • HVAC&R heating, ventilation, air conditioning, and/or refrigeration
  • FIG. 2 is a perspective view of an embodiment of a vapor compression system, in accordance with an aspect of the present disclosure
  • FIG. 3 is a schematic of an embodiment of the vapor compression system of FIG. 2, in accordance with an aspect of the present disclosure
  • FIG. 4 is a schematic of an embodiment of the vapor compression system of FIG. 2, in accordance with an aspect of the present disclosure
  • FIG. 5 is a schematic of an embodiment of a vapor compression system with an oil conduit system, in accordance with an aspect of the present disclosure
  • FIG. 6 is a cross-sectional side view of an embodiment of a compressor of a vapor compression system, in accordance with an aspect of the present disclosure
  • FIG. 7 is an overhead cross-sectional view of an embodiment of a compressor of a vapor compression system, in accordance with an aspect of the present disclosure.
  • FIG. 8 is a cross-sectional perspective view of an embodiment of a compressor of a vapor compression system, in accordance with an aspect of the present disclosure.
  • the terms “approximately,” “generally.” “substantially,” and so forth, are intended to convey that the property value being described may be within a relatively small range of the property value, as those of ordinary' skill would understand. For example, when a property value is described as being “approximately” equal to (or, for example, “substantially similar” to) a given value, this is intended to convey that the property value may be within +/- 5%, within +/- 4%, within +/- 3%, within +/- 2%, within +/- 1%, or even closer, of the given value.
  • Embodiments of the present disclosure relate to a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system, such as a chiller system, having a vapor compression system.
  • the vapor compression system may include a compressor configured to pressurize a working fluid and discharge the pressurized working fluid to a condenser configured to cool the working fluid.
  • the condenser may discharge the cooled working fluid to an expansion valve configured to reduce a pressure of the working fluid, thereby further cooling the working fluid.
  • the expansion valve may direct the cooled working fluid to an evaporator, which may be configured to place the cooled working fluid in a heat exchange relationship with a conditioning fluid to cool the conditioning fluid and heat the working fluid.
  • the evaporator may then discharge the working fluid to the compressor, and the compressor may recompress the working fluid received from the evaporator.
  • oil may be used to facilitate operation of certain components of the vapor compression system, such as to improve efficiency of operation of a component and/or to extend a useful lifespan of the component.
  • oil may be circulated through a compressor to facilitate operation of various components of the compressor, such as a bearing, a linkage, a displacement component, an actuator, and so forth.
  • a property of the oil flow may not be desirable, and the oil may not facilitate operation of a component of the vapor compression system as a result.
  • the viscosity, dilution, pressure, and/or the temperature of the oil may be outside of a desirable range. As a result, operation of the vapor compression system may not be desirable.
  • embodiments of the present disclosure are directed to an oil conduit system configured to place the oil in a heat exchange relationship with a refrigerant flow directed through a compressor of the vapor compression system.
  • the refrigerant flow may be directed from an inlet of the compressor to a chamber in which the refrigerant flow is pressurized by a displacement component of the compressor.
  • the oil conduit system may place the oil in the heat exchange relationship with the refrigerant flow prior to the refrigerant flow being pressurized by the displacement component.
  • the refrigerant flow placed in the heat exchange relationship with the oil may be at a relatively lower temperature to enable greater heat transfer from the oil to the refrigerant flow, thereby reducing a temperature of the oil.
  • the oil cooled by the refrigerant flow may then be directed into the refrigerant flow to flow across components of the compressor.
  • the cooling of the oil via the refrigerant flow may place the oil in a more desirable condition (e.g., at a more desirable temperature, having a more desirable dilution, having a more desirable viscosity) to facilitate operation of the compressor.
  • FIG. 1 is a perspective view of an embodiment of an environment for a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system 10 in a building 12 for a typical commercial setting.
  • the HVAC&R system 10 may include a vapor compression system 14 (e.g., a chiller) that supplies a chilled liquid, which may be used to cool the building 12.
  • the HVAC&R system 10 may also include a boiler 16 to supply warm liquid to heat the building 12 and an air distribution system which circulates air through the building 12.
  • the air distribution system can also include an air return duct 18, an air supply duct 20, and/or an air handler 22.
  • the air handler 22 may include a heat exchanger that is connected to the boiler 16 and the vapor compression system 14 by conduits 24.
  • the heat exchanger in the air handler 22 may receive either heated liquid from the boiler 16 or chilled liquid from the vapor compression system 14, depending on the mode of operation of the HVAC&R system 10.
  • the HVAC&R system 10 is shown with a separate air handler on each floor of building 12, but in other embodiments, the HVAC&R system 10 may include air handlers 22 and/or other components that may be shared between or among floors.
  • FIGS. 2 and 3 are embodiments of the vapor compression system 14 that can be used in the HVAC&R system 10.
  • the vapor compression system 14 may circulate a refrigerant through a circuit starting with a compressor 32.
  • the circuit may also include a condenser 34, an expansion valve(s) or device(s) 36, and a liquid chiller or an evaporator 38.
  • the vapor compression system 14 may further include a control panel 40 that has an analog to digital (A/D) converter 42.
  • A/D analog to digital
  • a microprocessor 44 a nonvolatile memory 46, and/or an interface board 48.
  • HFC hydrofluorocarbon
  • HFO hydrofluorocarbon based refrigerants
  • the vapor compression system 14 may be configured to efficiently utilize refrigerants having a normal boiling point of about 19 degrees Celsius (66 degrees Fahrenheit) at one atmosphere of pressure, also referred to as low pressure refrigerants, versus a medium pressure refrigerant, such as R-134a.
  • refrigerants having a normal boiling point of about 19 degrees Celsius (66 degrees Fahrenheit) at one atmosphere of pressure also referred to as low pressure refrigerants
  • medium pressure refrigerant such as R-134a.
  • "normal boiling point” may refer to a boiling point temperature measured at one atmosphere of pressure.
  • the vapor compression system 14 may use one or more of a variable speed drive (V SDs) 52, a motor 50, the compressor 32, the condenser 34, the expansion valve or device 36, and/or the evaporator 38.
  • the motor 50 may drive the compressor 32 and may be powered by a variable speed drive (VSD) 52.
  • the VSD 52 receives alternating current (AC) power having a particular fixed line voltage and fixed line frequency from an AC power source, and provides power having a variable voltage and frequency to the motor 50.
  • the motor 50 may be powered directly from an AC or direct current (DC) power source.
  • the motor 50 may include any type of motor that can be powered by a VSD or directly from an AC or DC power source, such as a switched reluctance motor, an induction motor, an electronically commutated permanent magnet motor, or another suitable motor.
  • the compressor 32 compresses a refrigerant vapor and delivers the vapor to the condenser 34 through a discharge passage.
  • the compressor 32 may be a centrifugal compressor.
  • the refrigerant vapor delivered by the compressor 32 to the condenser 34 may transfer heat to a cooling fluid (e.g., water or air) in the condenser 34.
  • the refrigerant vapor may condense to a refrigerant liquid in the condenser 34 due to thermal heat transfer with the cooling fluid.
  • the liquid refrigerant from the condenser 34 may flow through the expansion device 36 to the evaporator 38.
  • the condenser 34 is water cooled and includes a tube bundle 54 connected to a cooling tower 56, which supplies the cooling fluid to the condenser 34.
  • the liquid refrigerant delivered to the evaporator 38 may absorb heat from another cooling fluid, which may or may not be the same cooling fluid used in the condenser 34.
  • the liquid refrigerant in the evaporator 38 may undergo a phase change from the liquid refrigerant to a refrigerant vapor.
  • the evaporator 38 may include a tube bundle 58 having a supply line 60S and a return line 60R connected to a cooling load 62.
  • the cooling fluid of the evaporator 38 enters the evaporator 38 via return line 60R and exits the evaporator 38 via supply line 60S.
  • the evaporator 38 may reduce the temperature of the cooling fluid in the tube bundle 58 via thermal heat transfer with the refrigerant.
  • the tube bundle 58 in the evaporator 38 can include a plurality of tubes and/or a plurality of tube bundles. In any case, the vapor refrigerant exits the evaporator 38 and returns to the compressor 32 by a suction line to complete the cycle.
  • FIG. 4 is a schematic of the vapor compression system 14 with an intermediate circuit 64 incorporated between condenser 34 and the expansion device 36.
  • the intermediate circuit 64 may have an inlet line 68 that is directly fluidly connected to the condenser 34.
  • the inlet line 68 may be indirectly fluidly coupled to the condenser 34.
  • the inlet line 68 includes a first expansion device 66 positioned upstream of an intermediate vessel 70.
  • the intermediate vessel 70 may be a flash tank (e.g., a flash intercooler, an economizer, etc.).
  • the intermediate vessel 70 may be configured as a heat exchanger or a “surface economizer.”
  • the intermediate vessel 70 is used as a flash tank, and the first expansion device 66 is configured to lower the pressure of (e.g., expand) the liquid refrigerant received from the condenser 34. During the expansion process, a portion of the liquid may vaporize, and thus, the intermediate vessel 70 may be used to separate the vapor from the liquid received from the first expansion device 66.
  • the intermediate vessel 70 may provide for further expansion of the liquid refrigerant because of a pressure drop experienced by the liquid refrigerant when entering the intermediate vessel 70 (e.g., due to a rapid increase in volume experienced when entering the intermediate vessel 70).
  • the vapor in the intermediate vessel 70 may be drawn by the compressor 32 through a suction line 74 of the compressor 32. In other embodiments, the vapor in the intermediate vessel may be drawn to an intermediate stage of the compressor 32 (e.g., not the suction stage).
  • the liquid that collects in the intermediate vessel 70 may be at a lower enthalpy than the liquid refrigerant exiting the condenser 34 because of the expansion in the expansion device 66 and/or the intermediate vessel 70.
  • the liquid from intermediate vessel 70 may then flow in line 72 through a second expansion device 36 to the evaporator 38.
  • any of the features described herein may be incorporated with the vapor compression system 14 or any other suitable HVAC&R systems.
  • the present techniques may be incorporated with any HVAC&R system having an economizer, such as the intermediate vessel 70, and a compressor, such as the compressor 32.
  • the discussion below describes the present techniques incorporated with embodiments of the compressor 32 configured as a single stage compressor.
  • the systems and methods described herein may be incorporated with other embodiments of the compressor 32 and HVAC&R system 10.
  • the present disclosure is directed to an HVAC&R system that utilizes oil to condition certain components.
  • the oil may cool and/or lubricate the components.
  • the HVAC&R system may include an oil conduit system configured to place the oil in a heat exchange relationship with a refrigerant flow directed through a compressor of the HVAC&R system.
  • the oil conduit system may place the oil in the heat exchange relationship with the refrigerant flow upstream of where the refrigerant flow is pressurized by the compressor with respect to a direction in which the refrigerant flow is directed through the compressor.
  • the oil conduit system enables greater heat transfer from the oil to the refrigerant flow to place the oil in a desirable condition for cooling and/or lubricating components of the compressor. As such, operation of the compressor may be improved.
  • FIG. 5 is a schematic of an embodiment of the vapor compression system 14 having the compressor 32 and the condenser 34.
  • the vapor compression system 14 also includes an oil conduit system 100 configured to circulate oil through the compressor 32 to facilitate operation of the compressor 32.
  • the oil conduit system 100 may include an oil separator 102 configured to discharge oil to an oil filter 104 of the oil conduit system 100, and the oil filter 104 may be configured to cleanse the oil.
  • the oil filter 104 may remove impurities from the oil.
  • the oil filter 104 may discharge the cleansed oil into the compressor 32, where the oil may mix with the refrigerant in the compressor 32.
  • the compressor 32 may then discharge the oil/refrigerant mixture back to the oil separator 102 of the oil conduit system 100.
  • the oil separator 102 may be configured to separate the oil and the refrigerant from one another, direct the oil to the oil filter 104, and direct the refrigerant to the condenser 34.
  • a pressure differential between the oil separator 102 and an interior volume of the compressor 32 e.g., aposition within the compressor 32 in which the oil filter 104 is disposed
  • the oil separator 102 may be at a higher pressure relative to an interior volume of the compressor 32 in which the oil filter 104 is disposed.
  • the pressure differential may drive oil from the high-pressure oil separator 102 to the oil filter 104 (which may also be at a higher pressure relative to an interior volume of the compressor 32), and the oil filter 104 may discharge the oil into a low-pressure area within an interior volume of the compressor 32 (e.g., a bearing cavity).
  • the oil separator 102 may include an oil pump 106 configured to facilitate discharge of the oil toward the oil filter 104 and toward the compressor 32.
  • the oil conduit system 100 may include any suitable components, such as valves, conduits (e.g., tubing, piping), couplings, and so forth, to facilitate directing oil between the oil separator 102, the oil filter 104, the compressor 32, and/or the oil condenser 34.
  • suitable components such as valves, conduits (e.g., tubing, piping), couplings, and so forth, to facilitate directing oil between the oil separator 102, the oil filter 104, the compressor 32, and/or the oil condenser 34.
  • the oil may condition various components of the compressor 32.
  • the compressor 32 may include an actuator 108 (e.g., a motor, a linear actuator, a rotary actuator) configured to drive movement of a displacement component or device 110.
  • the displacement component 110 may be configured to move to pressurize the refrigerant, such as by driving the refrigerant from a larger volume into a smaller volume.
  • the displacement component 110 may include a screw, a piston, a scroll, an impeller, a diaphragm, and so forth.
  • the compressor 32 may also include a linkage 112 that may connect the actuator 108 and the displacement component 110 to one another to enable the actuator 108 to drive movement of the displacement component 110.
  • the compressor 32 may further include one or more bearings 114 (e.g., axial bearing(s), radial bearing(s)) that may provide support and/or desirable positioning of a component of the compressor 32.
  • the bearing(s) 114 may constrain movement of the displacement component 110 in certain directions (e.g., rotational directions) and/or facilitate movement of the displacement component 110 in other directions (e.g., linear directions).
  • the oil conduit system 100 may place the oil in one or more heat exchange relationships with aspects and/or components of the compressor 32 to enable heat transfer between the aspects and/or components of the compressor 32 and the oil.
  • the oil conduit system 100 may be configured to transition between a first operating mode (e.g., normal operating mode) and a second operating mode (e.g., oil cooling mode) to place the oil in a desirable condition (e.g., more desirable temperature, having a more desirable dilution, having a more desirable viscosity) before directing the oil into the compressor 32.
  • a first operating mode e.g., normal operating mode
  • a second operating mode e.g., oil cooling mode
  • a desirable condition e.g., more desirable temperature, having a more desirable dilution, having a more desirable viscosity
  • the oil conduit system 100 may direct the oil toward the compressor 32 without placing the oil in a heat exchange relationship with aspects and/or components of the compressor 32.
  • oil discharged from the oil separator 102 and directed toward the oil filter 104 may already be in a desirable condition.
  • the oil conduit system 100 may direct the oil through a channel 1 16 (e.g., conduit, neutral channel, neutral conduit), such that the oil may pass through the compressor 32 without undergoing aheat exchange relationship.
  • the channel 116 may be formed (e.g., machined) through a housing of the compressor 32 and may be positioned a threshold distance away from various components and/or aspects of the compressor 32 such that minimal heat exchange occurs between the components and/or aspects of the compressor 32 and the oil flow directed through the channel 116.
  • the oil conduit system 100 may place the oil in a heat exchange relationship with a flow of the refrigerant to enable heat transfer between the flow of the refrigerant and the oil.
  • the oil conduit system 100 may direct the oil through a channel 117 (e.g., oil cooling channel), which may place the oil in a heat exchange relationship with refrigerant flow 118 at a suction of the compressor 32.
  • the refrigerant flow 118 may be generally cooler than the oil in the channel 117. Thus, heat may transfer from the oil to the refrigerant flow 118, thereby cooling the oil.
  • Cooling of the oil via the refrigerant flow 118 may adjust certain properties, such as a temperature, a pressure, a dilution, and/or a viscosity, of the oil toward a desirable range, such as 1 and 2.5 kappa or 1 or greater kappa, for a ratio of viscosity at operating temperature over a specified viscosity for the bearing(s) 114.
  • a desirable range such as 1 and 2.5 kappa or 1 or greater kappa
  • the oil may be in a more desirable condition for intake at the compressor 32 to flow across the various components of the compressor 32.
  • the oil may better reduce friction between components (e.g., between the linkage 112 and the displacement component 110), facilitate movement of a component (e.g., of the displacement component 110), reduce temperature of a component (e.g., of the bearing(s) 114), and so forth.
  • pressurization of refrigerant e.g., the refrigerant flow 118
  • longevity of the compressor 32 may be increased.
  • the oil conduit system 100 may include a valve 120 (e.g., solenoid valve) positioned between the oil filter 104 and the compressor 32.
  • the valve 120 may be configured to transition between a first position (e.g., solenoid closed position) in which oil from the oil filter 104 is directed through the channel 116, and a second position (e.g., solenoid open position) in which oil from the oil filter 104 is directed through the channel 117. In this way, the valve 120 may dictate which operating mode the oil conduit system 100 is operating in.
  • valve 120 when the valve 120 transitions to the first position (e.g., when the solenoid is closed), oil may be directed through the channel 116 such that the oil does not undergo a heat exchange relationship with aspects and/or components of the compressor 32, thereby enabling the oil conduit system 100 to operate in the first operating mode (e.g., normal operating mode).
  • first operating mode e.g., normal operating mode
  • second position e.g., when the solenoid is opened
  • oil when the valve 120 transitions to the second position (e.g., when the solenoid is opened)
  • oil may be directed through the channel 117 such that the oil is cooled by the refrigerant flow 118 before being introduced into the compressor 32, thereby enabling the oil conduit system 100 to operate in the second operating mode (e.g., oil cooling mode).
  • the oil conduit system 100 may operate such that oil is directed into the channel 117 when the valve 120 is in the first position (e.g., when the valve 120 is closed) and into the channel 116 when the valve 120 is in the second position (e.g., when the valve 120 is opened).
  • the vapor compression system 14 may include one or more sensors 122 configured to detect a condition of the oil directed toward the compressor 32.
  • the one or more sensors 122 may be disposed throughout the vapor compression system 14 and/or the compressor 32 and may be configured to detect data indicative of a temperature, a pressure, a viscosity, and/or a dilution of the oil.
  • the one or more sensors 122 may communicate such data to a controller 130 (e.g., control system, automation controller), thereby enabling the controller 130 to transition the oil conduit system 100 between the first operating mode and the second operating mode (e.g., by controlling a position of the valve 120 between the first position and the second position), based on said data.
  • a controller 130 e.g., control system, automation controller
  • certain components of the vapor compression system 14 may be communicatively coupled to the controller 130 (e.g., control panel 40). thereby enabling the controller 130 to receive data from the components, control operation of the vapor compression system 14 and/or control operation of the oil conduit system 100, as described in greater detail below.
  • the controller 130 e.g., control panel 40
  • the controller 130 may include processing circuitry 132 (e g., one or more microprocessors) and a memory 134.
  • the controller 130 may include non-transitory code or instructions stored in a machine-readable medium (e.g., the memory 134) that is used by the processing circuitry 132 to implement the techniques disclosed herein.
  • the memory 134 may include volatile memory, such as read-only memory (ROM), optical drives, hard disc drives, solid-state drives, or any other non-transitory, computer-readable medium storing instructions that, when executed by the processing circuitry 132, control operation of the vapor compression system 14 and/or the oil conduit system 100.
  • the controller 130 may monitor and control operation of the oil conduit system 100, for example, by adjusting a position of the valve 120 based on the feedback received from the one or more sensors 122. For example, upon receiving sensor data indicative of a current property' of the oil deviating from a desired property , the controller 130 may control the valve 120 to transition the oil conduit system 100 between the first operating mode and the second operating mode. In this way, the oil may be cooled, as desired. It should be appreciated that certain features discussed herein may be omitted from certain embodiments without departing from the scope of this disclosure.
  • the channel 116, the valve 120, one or more of the sensors 122, and/or the controller 130 may be omitted, and the oil conduit system 100 may operate in a single mode (e.g., oil cooling mode) to direct oil through the channel 117 (e.g., to cool the oil).
  • a single mode e.g., oil cooling mode
  • FIG. 6 is a cross-sectional side view of an embodiment of the compressor 32.
  • the compressor 32 includes a support 140 (e.g., an enclosure).
  • the support 140 may define or include a first chamber 142 (e.g., a first section, a first volume, a first space, an intake section), a second chamber 144 (e.g., a second section, a second volume, a second space, a pressurization section), and a third chamber 146 (e.g., a third section, a third volume, a third space, a discharge section).
  • refrigerant e.g., the refrigerant flow 118
  • the compressor 32 may include a motor 148 (e.g., the motor 50, the actuator 108) positioned within the first chamber 142 and a screw 152 (e.g., a rotor, the displacement component 110) extending through the first chamber 142, the second chamber 144, and the third chamber 146.
  • the motor 148 may be coupled to a first shaft 154 of the screw 152 in the first chamber 142.
  • the screw 152 may include lobes 156 (e.g., threads) extending through the second chamber 144 and a second shaft 158 extending through the third chamber 146.
  • the refrigerant may flow into the first chamber 142 of the compressor 32 (e.g...
  • the refrigerant may flow along the refrigerant flow path 150 into a passage 162 formed between the motor 148 and the support 140 toward the second chamber 144. The refrigerant may then flow from the first chamber 142 into the second chamber 144 via a first opening 164.
  • the motor 148 may drive rotation of the first shaft 154 about an axis 166 during operation of the compressor 32. Rotation of the shaft 154 may drive rotation of the screw 152 about the axis 154, thereby enabling the screw 152 to compress the refrigerant and drive flow of the refrigerant into the third chamber 146 via a second opening 168.
  • a cross-sectional area of the third chamber 146 may be less than a cross- sectional area of the first chamber 142.
  • the refrigerant may be at a higher pressure in the third chamber 146 as compared to in the first chamber 142.
  • the refrigerant may then flow through the third chamber 146, along the refrigerant flow path 150, and out of the compressor 32 via an outlet 170 (e.g., a discharge outlet).
  • the oil conduit system 100 may be configured to transition between a first operating mode (e.g., normal operating mode) and a second operating mode (e.g., oil cooling mode) to place the oil in a more desirable condition before introducing the oil into a chamber of the compressor 32.
  • a first operating mode e.g., normal operating mode
  • a second operating mode e.g., oil cooling mode
  • the oil conduit system 100 may direct oil along an oil flow path 171 via the channel 116 such that less than a threshold amount of heat exchange occurs between the oil and various components and/or aspects of the compressor 32.
  • the channel 116 may be positioned and/or machined through the support 140 such that the channel 116 is at least a threshold distance away from the refrigerant flow path 118 through which refrigerant flows and/or at least a threshold distance away from other components and/or aspects of the compressor 32 that may induce the oil flow into aheat exchange relationship (e.g., moving components of the compressor 32 (e.g., motor 148)). In this way, minimal heat exchange may occur between the oil directed through the channel 116 and the various components and/or aspects of the compressor 32 before the oil is introduced into the compressor 32.
  • aheat exchange relationship e.g., moving components of the compressor 32 (e.g., motor 148)
  • the oil conduit system 100 may direct oil through the channel 117 and place the oil in a heat exchange relationship with the refrigerant flowing along the refrigerant flow path 150.
  • the oil may flow along an oil flow path 172 through the compressor 32 via the channel 117.
  • the oil filter 104 may discharge oil toward the valve 120, and the valve 120 may direct the oil into the channel 117 extending through the support 140 when the oil conduit system 100 is operating in the second operating mode.
  • the channel 117 may extend along the passage 162, thereby placing the oil in a heat exchange relationship with the refrigerant flowing through the passage 1 2 within the first chamber 142.
  • the passage 162 may extend at least partially along a direction extending from the inlet 160 to the second chamber 144 (e.g.. at least partially along the axis 166).
  • the oil may be placed in a heat exchange relationship with the refrigerant flowing along the refrigerant flow path 150 at least partially in the direction extending from the inlet 160 to the second chamber 144.
  • the refrigerant flowing through the first chamber 142 may be at a lower temperature than the oil (e.g., oil discharged by the oil filter 104) placed in aheat exchange relationship with such a refrigerant.
  • the oil e.g., oil discharged by the oil filter 104
  • heat may transfer from the oil to the refrigerant to cool the oil.
  • Such heat transfer may adjust a property of the oil to place the oil in condition to improve operation of the compressor 32.
  • a temperature of the oil may decrease and/or a viscosity of the oil may increase as a result of the heat transfer, and the oil may be able to provide desirable cooling of the components of the compressor 32, enable desirable movement of the components of the compressor 32, improve a useful lifespan of the components of the compressor 32, and so forth.
  • Such benefits may also improve efficiency of the compressor 32 to pressurize the refrigerant.
  • the motor 148 may drive movement of the screw 152 more readily and/or more efficiently to enable the screw 152 to pressurize the refrigerant more efficiently.
  • desirable operation of the compressor 32 may be maintained and/or achieved at different ambient temperatures.
  • the benefits provided by the oil cooled via the refrigerant may enable the compressor 32 to achieve desirable operation at a higher ambient temperature condition, which may otherwise increase a temperature of the oil, increase a temperature of the refrigerant, and/or affect operation (e.g., movement) of the components of the compressor 32.
  • such benefits may be achieved without implementing equipment dedicated to cooling oil (e.g., an external oil cooler, an additional cooling system), thereby reducing costs associated with installation and/or operation of such equipment.
  • the oil may be cooled without substantially affecting a condition (e.g., a temperature, a flow rate) of the refrigerant flowing through the compressor 32.
  • the oil conduit system 100 may be readily incorporated in an existing HVAC&R system without having to adjust operation of the compressor 32.
  • the controller 130 may be configured to control a position of the valve 120 to transition the oil conduit system 100 between the first operating mode and the second operating mode based on data from the one or more sensors 122 disposed about the compressor 32.
  • one or more sensors 122 may be positioned within the first chamber 142 (e.g., within the oil filter 104), within the second chamber 144, and/or within the third chamber 146 (e.g., proximate the bearings 114).
  • the sensors 122 may collect data indicative of an operating parameter of the oil (e.g., temperature, pressure, viscosity’, dilution), and the controller 130 may utilize such data to control a position of the valve 120.
  • the controller 130 may transition the valve 120 toward the open position such that the oil is directed through the channel 117 to be cooled. Conversely, upon receiving data from the one or more sensors 122 indicating that a temperature of the oil is within a desired temperature range, the controller 130 may transition the valve 120 toward the closed position such that the oil is directed through the channel 116, thereby minimizing heat exchange between the oil flowing through the channel 116 and other components and/or aspects of the compressor 32.
  • the channel 116 and the channel 117 discharge their respective oil flows into an oil discharge assembly 174 that extends along the second chamber 144.
  • the oil discharge assembly 174 may include a first conduit 175 fluidly coupled to the channels 116, 1 17, a first port 176, a second conduit 177, a second port 178, and a valve 179 (e.g., orifice).
  • the channels 116, 117 may discharge oil into the first conduit 175, and the first conduit 175 may discharge oil into the refrigerant flow path 150 adjacent to the second chamber 144.
  • the oil discharge assembly 175 may discharge oil into the refrigerant flow path via the first port 176 and/or the second port 178.
  • the first port 176 may be positioned upstream of the second chamber 144, such as within the first opening 164.
  • the second port 178 may be positioned downstream of the second chamber 144, such as within the third chamber 146.
  • the ports 176. 178 may discharge oil received from the channels 116, 117 into the refrigerant flow path 150 at locations that are proximate to and outside of the second chamber 144.
  • the valve 179 may be configured to control distribution of the flow of oil between the first port 176 and the second port 178.
  • the valve 179 may be a modulating valve that directs a portion of the oil through the first conduit 175 and toward the first port 176, while a remaining portion of the oil is directed through the second conduit 177 and toward the second port 178.
  • the valve 179 may be communicatively coupled to the controller 130, thereby enabling the controller 130 to control a position of the valve 179 and thus control distribution of the oil between the first and second ports 176, 178, respectively.
  • valve 179 may correspond to a static orifice having a specified diameter to enable at least a portion of the oil flow directed through the oil discharge assembly 174 to flow through the first port 176 while a remaining portion of the oil flow is directed through the second conduit 177 and into the compressor 32 via the second port 178. That is, in certain embodiments, a size, configuration, and/or diameter of the static orifice 179 may be selected based on certain design conditions, thereby enabling the oil discharge assembly 174 to distribute the oil flow between the first and second ports 176, 178.
  • the oil discharged into the refrigerant flow path 150 may flow through the second chamber 144 and/or the third chamber 146 of the compressor 32.
  • the oil discharged into the refrigerant flow path 150 via the second port 178 may flow through the third chamber 146, out of the compressor 32 via the outlet 170, and toward the oil separator 106 to be separated from the refrigerant and directed back toward the oil filter 104.
  • the oil discharged into the refrigerant flow path 150 via the first port 176 may flow through the second chamber 144, through the third chamber 146, out of the compressor 32 via the outlet 170, and toward the oil separator 106.
  • the oil conduit system 100 may include a port configured to discharge oil into a different location of the refrigerant flow path 150 in additional or alternative embodiments.
  • a port configured to discharge oil into a different location of the refrigerant flow path 150 in additional or alternative embodiments.
  • another port my discharge oil into second chamber 144 (e.g., onto the lobes 156), into the first chamber 142 (e.g., onto the motor 148), or at any suitable location to cause the oil to mix with the refrigerant.
  • the compressor 32 may also include the bearings 114 positioned adjacent to the ports 176, 178 to enable the oil discharged into the refrigerant flow path 150 to flow across the bearings 114.
  • the compressor 32 may include one or more first bearings 180 positioned downstream of the first port 176 (e.g., and upstream of the second chamber 144), such as within the first opening 164, with respect to flow of refrigerant through the compressor 32.
  • the compressor 32 may additionally or alternatively include one or more second bearings 182 positioned downstream of the second port 178 with respect to the flow of refrigerant through the compressor 32.
  • the oil discharged into the refrigerant flow path 150 may be directed across the first bearing 180 and the second bearing 182 via the first port 176 and the second port 178, respectively.
  • the bearings 180. 182 may support the screw 152, such as to position and/or orient the screw 152 in a desirable manner, block undesirable movement of the screw 152, and the like. Positioning of the bearings 180, 182 adjacent to the ports 176, 178, respectively, may enable the oil to flow more desirably upon discharge into the refrigerant flow path 150 (e.g.. to flow more immediately or readily across the bearings 180, 182).
  • the oil filter 104 may be coupled to the support 140 to facilitate positioning of the oil filter 104 to discharge oil into the channel 116 or the channel 117.
  • the oil filter 104 may be separate from the support 140 or positioned in any other suitable manner to discharge oil into the channels 116, 117.
  • the oil filter 104 may be arranged at a position to discharge the oil into the channel 117 for placing the oil in a heat exchange relationship with refrigerant flow at any suitable portion of the refrigerant flow path 150 within the first chamber 142.
  • the oil filter 104 may be oriented to discharge oil in any suitable direction, such as along (e.g., substantially parallel to) a direction extending from the inlet 160 to the second chamber 144 or crosswise to (e.g., perpendicular to) the direction extending from the inlet 160 to the second chamber 144.
  • FIG. 7 is an overhead cross-sectional view of an embodiment of the compressor 32. Certain features, such as the support 140, are not shown for visualization purposes.
  • the compressor 32 includes a first screw 152A and a second screw 152B.
  • the first screw 152A e.g., a male screw
  • the second screw 152B e.g., a female screw
  • the first screw 152A and the second screw 152B may pressurize refrigerant during rotation and may increase a rate or amount in which refrigerant is pressurized as compared to a compressor having a single screw.
  • the first port 176 discharges the oil into the refrigerant flow path 150 adjacent to the first screw 152A (e.g., upstream of the lobes 156 of the first screw 152A with respect to flow of refrigerant through the compressor 32), and the second port 178 discharges the oil into the refrigerant flow path 150 adjacent to the second screw 152B (e.g., downstream of the lobes 156 of the first screw 152A with respect to the flow of refrigerant through the compressor 32).
  • the oil filter 104 (show n in phantom lines) may cleanse the oil of impurities and direct oil through the valve 120 and through either the channel 116 or 117 before the oil is directed toward the oil discharge assembly 174.
  • the oil discharge assembly 174 may then direct the oil flow to the first port 176 and/or to the second port 178 to distribute the oil for discharge into the refrigerant flow path 150, such as to flow across the first bearing(s) 180 and the second bearing(s) 182 that support the first screw 152A.
  • the first port 176 may discharge the oil into the refrigerant flow path 150 adjacent to the second screw 152B (e.g..
  • the second port 178 may discharge the oil into the refrigerant flow path 150 adjacent to the second screw 152B (e.g., downstream of the threads 208 of the second screw 152B with respect to the flow of refrigerant through the compressor 32).
  • the oil may flow from the first screw 152A to the second screw 152B.
  • the pressure at the first screw 152A may be greater than the pressure at the second screw 152B.
  • the pressure differential may drive flow of the oil from the first screw 152A to the second screw 152B.
  • the pressure differential may facilitate distribution of oil (e.g., oil discharged into the refrigerant flow path 150 via the first port 176) across the screw s 152.
  • the oil discharge assembly 174 of the oil conduit system 100 may include a third port 210 and/or a fourth port 212.
  • the third port 210 may discharge the oil into the refrigerant flow' path 150 adjacent to the second screw 152B (e.g., upstream of the threads 208 of the second screw 152B with respect to the flow of refrigerant through the compressor 32), and the third port 212 may discharge the oil into the refrigerant flow path 150 adjacent to the second screw 152B (e.g., downstream of the threads 208 of the second screw' 152B with respect to the flow of refrigerant through the compressor 32).
  • the third port 210 and the fourth port 212 may direct the oil to flow' across one or more third bearings 214 and one or more fourth bearings 216, respectively, which may support the second screw 152B.
  • the oil discharged by the oil filter 104 may be distributed across each of the ports 176, 178, 210, 212, thereby enabling the oil to be discharged into the refrigerant flow path 150 at different locations (e.g., adjacent to each of the screws 152).
  • each of the compressors 32 of FIGS. 6 and 7 includes a single oil filter 104 (e.g., a centralized oil filter), which may reduce a number of components of the oil conduit system 100 to facilitate implementation and/or maintenance (e.g., to replace, repair, or inspect the oil conduit system 100).
  • a single oil filter 104 e.g., a centralized oil filter
  • multiple oil filters 104 e.g., oil filters 104 coupled to the support 140 and/or separate from the support 140
  • FIG. 8 is a cross-sectional perspective view of an embodiment of the compressor 32.
  • the support 140 may include a body 238 and multiple ribs 240 that extend inwardly from the body 238 to support the motor 148.
  • the ribs 240 may abut the motor 148 (e.g., a stator 242 of the motor 148) and cooperatively capture the motor 148 to maintain the position of the motor 148.
  • the ribs 240 may be circumferentially offset from one another around the motor 148 to form multiple passages 162 that enable flow of refrigerant along the refrigerant flow path 150 through the first chamber 142.
  • Each of the channels 116, 117 of the oil conduit system 100 may be formed through the body 238 and/or one of the ribs 240.
  • the channel 1 16 may extend through the body 238 and the channel 117 may extend through one of the ribs 240.
  • the channel 116 may be formed (e.g., machined) through the support 140 (e.g., through the body 238 of the support 140) and may be positioned at least a threshold distance away from the passages 162 through which refrigerant may flow and/or at least a threshold distance away from the motor 148 (e.g., the stator 242 of the motor 148). In this way, minimal heat exchange may occur between the oil flowing through the channel 116 and the various components and/or aspects of the compressor 32 (e.g., refrigerant flow through the passages 162, stator 242 of the motor 148).
  • the channel 117 may be formed (e.g., machined) through one of the ribs 240 (e.g., rib 240A) and may be positioned within a threshold distance from the passages 162 through which refrigerant may flow, thereby enabling a heat exchange relationship between the refrigerant flow and the oil (e.g., thereby enabling cooling of the oil flow through the channel 117).
  • the ribs e.g., rib 240A
  • the rib 240 A terminates prior to abutment with the motor 148, thereby forming a gap 244 between the rib 240A and the motor 148.
  • Refrigerant may flow along the refrigerant flow path 150 and through the gap 244.
  • the rib 240A may have a greater amount of surface area exposed to refrigerant flow along the refrigerant flow path 150, thereby increasing heat transfer between the oil flowing through the channel 117 and the refrigerant flowing through the first chamber 142 as compared to a channel formed through a rib extending to abut the motor 242.
  • the rib 240A may enable desirable conditioning of the oil.
  • the rib 240A may extend in abutment with the motor 242 to enable the rib 240A to support the motor 242.
  • the rib 240A may also include fins in some embodiments to increase a surface area to facilitate heat transfer between the refrigerant and the oil.
  • Each rib 240 of the support 140 may have a dimension or size (e.g., a width, a thickness) to provide sufficient support of the motor 148 and/or to form the passages 162 having a desirable size.
  • the ribs 240 may define passages 162 that are sufficiently sized to enable refrigerant flow therethrough at a desirable flow rate and/or velocity, such as to reduce pressure drop of the refrigerant flowing through the passages 162.
  • the size of the ribs 240 may be increased for larger sized supports 140.
  • the ribs 240 may have different sizes than one another.
  • the rib 240A through which the channel 117 is formed may be of a different size than a rib 240 that does not include the channel 117.
  • the channel 117 may be sized to enable sufficient flow of oil therethrough (e.g., to direct oil at a target flow rate that enables desirable heat transfer between the oil and the refrigerant), while enabling the structure of the rib 240A to support the motor 148.
  • the channels 1 16, 117 are formed through a single portion of the body 238 and/or through a single one of the ribs 240 A, respectively, in the illustrated embodiment, the channel 116, 117 may be formed through multiple portions of the body 238 and/or through multiple ribs 240 in additional or alternative embodiments.
  • the oil may flow through the channels 116, 117 in parallel with one another (e.g., to increase an overall flow rate of oil through the channels 116, 117) and/or in series with one another (e.g., to be in a heat exchange relationship with the refrigerant along multiple flow passes and increase an overall amount of heat exchanged between the oil and the refrigerant).
  • Embodiments of the present disclosure may provide one or more technical effects useful in operating HVAC&R systems.
  • Embodiments of the present disclosure may include an oil conduit system configured to transition between a first operating mode (e.g., normal operating mode) and a second operating mode (e.g., oil cooling mode) to place the oil in a more desirable condition (e.g., more desirable temperature, more desirable dilution, more desirable viscosity) before introducing the oil into a compressor of the HVAC&R system.
  • the oil conduit systems discussed herein may include a first channel and a second channel and a valve configured to transition between a first position in which oil is directed through the first channel and a second position in which oil is directed through the second channel.
  • the first channel may be positioned within (e.g., may extend through) a support of the compressor, and may be configured to minimize heat exchange relationships between the oil flow directed therethrough and various aspects and/or components of the compressor.
  • the second channel may also be positioned within a support of the compressor. However, the second channel may be positioned proximate a refrigerant flow path directed through the compressor, thereby enabling oil directed through the second channel to undergo a heat exchange relationship with refrigerant directed along the refrigerant flow path. In this way, the oil may be conditioned (e.g., cooled) in a desirable manner to enable efficient operation of the compressor.
  • the oil conduit system may also include one or more sensors configured to detect one or more properties of the oil directed toward the oil conduit system and a controller configured to control a position of the valve to transition the oil conduit system between the first operating mode and the second operating mode based on the sensor data.
  • oil directed toward the compressor may undergo one or more heat exchange relationships to place the oil in a more desirable condition before the oil is introduced into the compressor, thereby increasing an efficiency of the compressor and/or reducing costs associated with repair and maintenance of the compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Compressor (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

Un système de chauffage, ventilation, climatisation et réfrigération (CVC&R) (10) comprend un compresseur (32) et un système de conduit d'huile (100). Le compresseur (32) comprend une entrée (162) conçue pour recevoir un fluide frigorigène dirigé selon un trajet d'écoulement de fluide frigorigène (118) et à travers le compresseur (32), un composant de déplacement (110), et un actionneur (108) conçu pour entraîner le fonctionnement du composant de déplacement (110) pour mettre sous pression le fluide frigorigène dans une chambre (144) du compresseur (32). Le système de conduit d'huile (100) comprend un canal (117) conçu pour diriger l'huile dans le trajet d'écoulement de fluide frigorigène (118), et le canal (117) est conçu pour placer l'huile dans une relation d'échange de chaleur avec le fluide frigorigène dirigé selon le trajet d'écoulement de fluide frigorigène (118) et s'écoulant au moins partiellement selon une direction s'étendant de l'entrée (162) à la chambre (144).
PCT/US2024/017512 2023-02-28 2024-02-27 Système de conduit d'huile pour système cvc&r Ceased WO2024182415A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN202480019182.9A CN120958282A (zh) 2023-02-28 2024-02-27 用于hvac&r系统的油管道系统
KR1020257032268A KR20250153293A (ko) 2023-02-28 2024-02-27 Hvac＆r 시스템을 위한 오일 도관 시스템

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US202363448944P 2023-02-28 2023-02-28
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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019056322A (ja) * 2017-09-21 2019-04-11 サンデンホールディングス株式会社 圧縮機
US20190277301A1 (en) * 2018-03-09 2019-09-12 Kabushiki Kaisha Toyota Jidoshokki Centrifugal compressor and method for manufacturing centrifugal compressor
EP3263902B1 (fr) * 2015-02-26 2019-12-04 Hitachi-Johnson Controls Air Conditioning, Inc. Compresseur à vis
CN111486107A (zh) * 2019-01-29 2020-08-04 青岛海尔智能技术研发有限公司 离心压缩机、热泵系统
JP2021127754A (ja) * 2020-02-17 2021-09-02 株式会社豊田自動織機 遠心圧縮機

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3263902B1 (fr) * 2015-02-26 2019-12-04 Hitachi-Johnson Controls Air Conditioning, Inc. Compresseur à vis
JP2019056322A (ja) * 2017-09-21 2019-04-11 サンデンホールディングス株式会社 圧縮機
US20190277301A1 (en) * 2018-03-09 2019-09-12 Kabushiki Kaisha Toyota Jidoshokki Centrifugal compressor and method for manufacturing centrifugal compressor
CN111486107A (zh) * 2019-01-29 2020-08-04 青岛海尔智能技术研发有限公司 离心压缩机、热泵系统
JP2021127754A (ja) * 2020-02-17 2021-09-02 株式会社豊田自動織機 遠心圧縮機

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TW202441116A (zh) 2024-10-16
KR20250153293A (ko) 2025-10-24

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