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WO2024168047A1 - Pompe pour système cvc-r - Google Patents

Pompe pour système cvc-r Download PDF

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Publication number
WO2024168047A1
WO2024168047A1 PCT/US2024/014821 US2024014821W WO2024168047A1 WO 2024168047 A1 WO2024168047 A1 WO 2024168047A1 US 2024014821 W US2024014821 W US 2024014821W WO 2024168047 A1 WO2024168047 A1 WO 2024168047A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
pump
contact
fluid
bump stop
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/US2024/014821
Other languages
English (en)
Inventor
Bryson Lee Sheaffer
Paul William SNELL
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 CN202480017594.9A priority Critical patent/CN120752435A/zh
Priority to KR1020257029795A priority patent/KR20250143114A/ko
Publication of WO2024168047A1 publication Critical patent/WO2024168047A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F04B17/042—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1002—Ball valves
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/02—Piston parameters
    • F04B2201/0201—Position of the piston
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/02—Piston parameters
    • F04B2201/0202—Linear speed of the piston

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 conditioning fluid may be directed through downstream equipment, such as air handlers, to condition other fluids, such as air in a building.
  • the chiller system may include a compressor configured to pressurize the working fluid and circulate the working fluid through a working fluid circuit of the chiller system.
  • a shaft of the compressor may be driven in rotation by a motor in order to drive rotation of an impeller of the compressor that pressurizes the working fluid.
  • the compressor includes bearings configured to facilitate rotation of the shaft.
  • existing bearings utilized with compressors may be complex, expensive, and/or may contribute to inefficiencies in operation of the chiller system.
  • a pump for a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system includes a pump body defining a compression chamber.
  • the HVAC&R system also includes a piston housing coupled to the pump body.
  • the piston housing includes a piston cavity.
  • the pump further includes a piston disposed within the piston housing.
  • the piston includes a plunger section configured to reciprocate between the compression chamber and the piston cavity.
  • the piston includes a head section configured to reciprocate within the piston cavity.
  • the pump includes a solenoid coil configured to induce a magnetic force on the piston.
  • the pump includes a controller configured to control flow of a current through the solenoid coil to control reciprocation of the piston within the piston cavity.
  • a heating, ventilation, air conditioning, and/or refrigeration (HVAC&R) system includes a pump configured to pump a fluid along a circuit of the HVAC&R system.
  • the pump includes a piston configured to reciprocate within a piston chamber of a piston housing. Additionally, the pump includes a bump stop disposed at an end of the piston chamber. The bump stop includes an internal switch configured to detect contact between the bump stop and the piston.
  • the HVAC&R system also includes a controller configured to control a stroke velocity of the piston based on a signal received from the internal switch.
  • a method of operating a pump includes energizing a solenoid coil to translate a piston in a first direction within a piston cavity.
  • the method also includes detecting a first contact between the piston and a first bump stop within the piston cavity. Further, the method includes energizing the solenoid coil to translate the piston in a second direction, opposite the first direction within the piston cavity. Additionally, the method includes detecting a second contact between the piston and a second bump stop within the piston cavity. Furthermore, the method includes determining a time interval between the first contact and the second contact. Thet method further includes adjusting energization of the solenoid coil based on a difference between the time interval and a previous time interval.
  • FIG. 1 is a perspective view of an embodiment of a building that may utilize a heating, ventilating, air conditioning, and/or refrigeration (HVAC&R) system in a commercial setting, in accordance with an aspect of the present disclosure;
  • HVAC&R heating, ventilating, 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 a vapor compression system, in accordance with an aspect of the present disclosure
  • FIG. 4 is a schematic of an embodiment of a vapor compression system, in accordance with an aspect of the present disclosure
  • FIG. 5 is a cross-sectional side view of an embodiment of a compressor of a vapor compression system, illustrating a bearing system of the compressor, in accordance with an aspect of the present disclosure
  • FIG. 6 is a schematic of an embodiment of a vapor compression system including a bearing system for a compressor, in accordance with an aspect of the present disclosure
  • FIG. 7 is a cross-sectional side view of an embodiment of a pump for a fluid supply system of a bearing system, in accordance with an aspect of the present disclosure
  • FIG. 8 is a cross-sectional side view schematic of an embodiment of a portion of a pump of a fluid supply system of a bearing system, in accordance with an aspect of the present disclosure
  • FIG. 9 is a cross-sectional side view schematic of an embodiment of a portion of a pump of a fluid supply system of a bearing system, in accordance with an aspect of the present disclosure.
  • FIG. 10 is a flowchart of an embodiment of a method of operating a pump for a fluid supply system of a bearing system, in accordance with an aspect of the present disclosure.
  • the terms “approximately,” “generally,” and “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.
  • a property value is described as being “approximately” equal to (or, for example, “substantially similar” to) a given value, this is intended to mean that the property value may be within +/- 5%, within +/- 4%, within +/- 3%, within +/- 2%, within +/- 1%, or even closer, of the given value.
  • a “planar” surface is intended to encompass a surface that is machined, molded, or otherwise formed to be substantially flat or smooth (within related tolerances) using techniques and tools available to one of ordinary skill in the art.
  • a surface having a “slope” is intended to encompass a surface that is machined, molded, or otherwise formed to be oriented at an angle (e.g., incline) with respect to a point of reference using techniques and tools available to one of ordinary skill in the art.
  • Embodiments of the present disclosure relate to a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system (e.g., a chiller) including a vapor compression system (e.g., vapor compression circuit, working fluid circuit) having a compressor.
  • HVAC&R heating, ventilation, air conditioning, and refrigeration
  • the compressor may pressurize a working fluid within the vapor compression system and direct the working fluid to a condenser (e.g., a first heat exchanger), which may cool and condense the working fluid.
  • the condensed working fluid may be directed to an expansion device, which may reduce a pressure of the working fluid, further cooling the working fluid.
  • the cooled working fluid may be directed to an evaporator (e.g., a second heat exchanger), where the working fluid may be placed in a heat exchange relationship with a conditioning fluid to cool the conditioning fluid.
  • the conditioning fluid may be circulated between the evaporator and a structure, such as a building, where the conditioning fluid is used to cool an air flow delivered to a conditioned space of the structure.
  • an air handling unit (AHU) of the HVAC&R system may receive the conditioning fluid from the chiller and utilize the conditioning fluid to cool the air flow delivered to the conditioned space. The conditioning fluid may then be returned to the evaporator to be cooled again.
  • AHU air handling unit
  • the compressor may include a bearing system including bearings (e.g., hydrostatic bearings, porous bearings) that utilize a pressurized fluid to support and lubricate a rotating shaft of the compressor.
  • the bearings may be configured to receive the pressurized fluid (e.g., in a liquid phase) and to discharge the pressurized fluid (e.g., in a gaseous phase) toward the rotating shaft to enable levitation and rotation of the rotating shape.
  • the bearing system may include a lubricant circuit extending from a working fluid circuit of the vapor compression system and direct a portion of the working fluid from the working fluid circuit into the bearings of the compressor.
  • the portion of the working fluid (e.g., refrigerant) in the lubricant circuit may be utilized as a lubricating fluid.
  • the lubricant circuit may include a pump configured to pump the pressurized fluid (e.g., lubricating fluid) toward the bearings of the compressor.
  • the working fluid which is configured to exchange heat with the conditioning fluid as part of the working fluid circuit, may also be utilized with the bearings to enable the bearings to support the shaft of the compressor.
  • the pump may be a linear piston pump configured to apply pressure to the working fluid via reciprocating motion of a piston.
  • existing pumps may produce localized regions of low pressure, which may cause cavitation of a working fluid within the pump.
  • Such cavitation may introduce unwanted inefficiency, wear, and/or degradation to the pump. Cavitation may be of particular concern during deadhead operation of the pump.
  • the pump may operate with no flow of working fluid therethrough (e.g., due to a closed valve and/or other blockage in the lubricant circuit).
  • pressurization of a constant mass of working fluid within the pump may increase the temperature of the working fluid, resulting in cavitation during a return stroke of the piston.
  • the increase in temperature may cause unwanted wear and/or degradation to components of the pump.
  • present embodiments are directed to an improved pump configured to pump a working fluid to bearings of a compressor, including systems and methods for operating the pump.
  • the pump is configured to sustain operation through varying operating conditions, including deadheading, while reducing cavitation of the working fluid.
  • the pump includes a piston, which may be driven (e.g., in a reciprocating motion) by a solenoid coil controlled by a pump controller.
  • the pump controller may control current supplied to the solenoid coil to control the direction and speed of the piston, such as according to a current profile. Additionally, the pump controller may adjust the current profile to reduce the speed of a return stroke of the piston in response to a detection indicative of cavitation and/or potential cavitation.
  • the pump may include a forward bump stop (e.g., first bump stop, travel stop, damping stop) and a return bump stop (e.g., second bump stop, travel stop, damping stop), each positioned at a respective end of a piston chamber of the pump within which the piston is disposed.
  • the bump stops are each configured to mechanically stop the piston on impact at the respective end of the piston chamber (e.g., top dead center, bottom dead center).
  • Each bump stop may also include an internal switch mechanism configured to send a signal to the pump controller indicative of contact between the bump stop and the piston.
  • the pump controller may determine a speed and/or a time (e.g., length of time) of a compression stroke of the piston. Based on a determination that the speed and/or time of the compression stroke appears to be and/or is abnormal (e.g., slower than a previous compression stroke), the pump controller may determine that cavitation may be occurring on a return stroke of the piston. In response to a determination that the speed of the compression stroke is slower than the previous compression stroke by a threshold amount and/or that a time period of the compression stroke is greater than a time period of the previous compression stroke, the pump controller may adjust the current profile to reduce a speed of the piston during the return stroke and/or increase a time period of the return stroke.
  • a time e.g., length of time
  • the pump may include a non-magnetic heat sink coupled to the piston to facilitate cooling of the pump during operation.
  • the pump is configured to operate under various operating conditions while resisting deleterious effects of deadheading experienced by traditional pumps.
  • FIG. 1 is a perspective view of an embodiment of a heating, ventilating, air conditioning, and/or refrigeration (HVAC&R) system 10 in a building 12 for a typical commercial setting.
  • HVAC&R heating, ventilating, air conditioning, and/or refrigeration
  • the HVAC&R system may include a vapor compression system 14 to supply chilled liquid to cool the building 12 and a boiler 16 to supply warm liquid to heat the building 12.
  • the vapor compression system 14, also referred to herein as a chiller, may circulate a working fluid (e.g., refrigerant) that is cooled by a cooling fluid (e.g., liquid such as water) in a condenser of the vapor compression system 14, and that is heated by a conditioning fluid (e.g., liquid, such as water) in an evaporator of the vapor compression system 14.
  • a working fluid e.g., refrigerant
  • a cooling fluid e.g., liquid such as water
  • a conditioning fluid e.g., liquid, such as water
  • the cooling fluid may be provided by a cooling tower which cools the cooling fluid via, for example, ambient air.
  • the conditioning fluid cooled by the working fluid as noted above, may be utilized to cool an air flow provided to conditioned spaces of the building 12.
  • the HVAC&R system 10 may also include 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 the conditioning fluid (e g., chilled liquid such as water) 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 illustrate embodiments of the vapor compression system 14, or chiller, which can be used in the HVAC&R system 10.
  • the vapor compression system 14 may circulate a working fluid through a circuit (e.g., working fluid circuit) starting with a compressor 32, such as a centrifugal compressor.
  • the circuit may also include a condenser 34, an expansion valve(s) or device(s) 36, and 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 microprocessor 44, a non-volatile memory 46, and/or an interface board 48.
  • A/D analog to digital
  • HFC hydrofluorocarbon
  • R- 410A R-407, R-134a
  • HFO hydrofluoro olefin
  • NH3 ammonia
  • R-717 R-717
  • CO2 carbon dioxide
  • R-744 hydrocarbon-based refrigerants
  • Other possible working fluids include R-123, R-514A, R-l 130yd, R-1233zd, R-134a, R-l 142ze, R-l 142yf, R-1311, R-32, and R-410A.
  • the vapor compression system 14 may be configured to efficiently utilize working fluids 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 working fluid, 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 (VSDs) 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 during a normal operating mode and may be powered by a variable speed drive (VSD) 52.
  • the VSD 52 receives alternating current (AC) power during the normal operating mode, where the AC power includes 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 electric 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 working fluid vapor and delivers the vapor to the condenser 34 through a discharge passage.
  • the compressor 32 may be a centrifugal compressor.
  • the working fluid 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 working fluid vapor may condense to a working fluid liquid in the condenser 34 as a result of thermal heat transfer with the cooling fluid.
  • the liquid working fluid 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 working fluid delivered to the evaporator 38 may absorb heat from a conditioning fluid that is subsequently routed to a load 62 (e.g., the building 12 of FIG. 1).
  • the conditioning fluid may be cooled by the working fluid in the evaporator 38, and then may be utilized in the building 12 of FIG. 1 to condition an air flow provided to condition a space in the building 12.
  • the liquid working fluid in the evaporator 38 may undergo a phase change from the liquid working fluid to a working fluid vapor.
  • the evaporator 38 may include a tube bundle 58 having a supply line 60S and a return line 60R connected to the cooling load 62.
  • the conditioning 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 conditioning fluid in the tube bundle 58 via thermal heat transfer with the working fluid.
  • 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 working fluid exits the evaporator 38 and returns to the compressor 32 by a suction line to complete the cycle.
  • FIG. 4 is a schematic of an embodiment of the vapor compression system 14 with an intermediate circuit 64 incorporated between the 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).
  • the intermediate vessel 70 may be configured as a heat exchanger or a "surface economizer.” In the illustrated embodiment of FIG.
  • 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 working fluid received from the condenser 34. During the expansion process, a portion of the liquid working fluid may vaporize, and thus, the intermediate vessel 70 may be used to separate the vapor working fluid from the liquid working fluid received from the first expansion device 66. Additionally, the intermediate vessel 70 may provide for further expansion of the liquid working fluid due to a pressure drop experienced by the liquid working fluid when entering the intermediate vessel 70 (e.g., due to a rapid increase in volume experienced when entering the intermediate vessel 70). The vapor working fluid in the intermediate vessel 70 may be drawn by the compressor 32 through a suction line 74 of the compressor 32.
  • the vapor working fluid in the intermediate vessel 70 may be drawn to an intermediate stage of the compressor 32 (e.g., not the suction stage).
  • the liquid working fluid that collects in the intermediate vessel 70 may be at a lower enthalpy than the liquid working fluid exiting the condenser 34 due to expansion of the working fluid at the expansion device 66 and/or in the intermediate vessel 70.
  • the liquid working fluid from intermediate vessel 70 may then flow through line 72 and through a second expansion device 36 to the evaporator 38.
  • the compressor 32 may be a centrifugal compressor (e g., a hermetic compressor) having a levitated rotor or shaft.
  • the vapor compression system 14 includes a bearing system with one or more bearings configured to support a load of the shaft of the compressor 32.
  • the bearing system is configured to direct a pressurized fluid (e.g., liquid, working fluid, refrigerant) through the bearings, and the bearings are configured to discharge the fluid toward and against the shaft in order to enable levitation of the shaft within the compressor 32.
  • the bearings include one or more porous bearing elements configured to receive the pressurized fluid and direct the pressurized fluid toward the shaft within a housing of the compressor 32.
  • the bearing system may support a load on the shaft and enable rotation of the shaft within the housing of the compressor 32 during operation of the vapor compression system 14.
  • the pressurized fluid may be a portion of a working fluid (e.g., refrigerant) circulated through the vapor compression system 14.
  • the vapor compression system 14 may not utilize a dedicated lubricant, such as oil, to support and enable rotation of the shaft of the compressor 32.
  • the bearing system may be incorporated with the vapor compression system 14 at reduced costs, as compared to other existing bearing system designs.
  • the disclosed embodiments also enable improved (e.g., simplified) control of the bearing system, as well as more efficient operation of the vapor compression system 14. [0035] With the foregoing in mind, FIG.
  • the compressor 32 may include a housing 102 and a shaft 104 extending through the housing 102.
  • the compressor 32 may also include an impeller 106 coupled to the shaft 104, such as via a fastener 108.
  • the shaft 104 may rotate (e.g., via operation of the motor 50) and cause rotation of the impeller 106.
  • Rotation of the impeller 106 may drive a working fluid (e.g., refrigerant) to flow through a working fluid flow path 110 (e g., from the evaporator 38, from the intermediate vessel 70, working fluid circuit) to draw the working fluid into the housing 102 via a suction inlet 112 and toward the impeller 106.
  • the impeller 106 may impart mechanical energy onto the working fluid and discharge the working fluid to a diffuser passage 114 of the compressor 32.
  • the working fluid may be directed from the diffuser passage 114 to a volute 116 of the compressor 32 and from the volute 116 to a condenser (e.g., the condenser 34) for heat exchange with a fluid, such as a cooling fluid.
  • the compressor 32 (e.g., bearing system 100) includes a first bearing 118 (e.g., a radial bearing, bearing assembly, porous bearing) and a second bearing 120 (e.g., a radial bearing, bearing assembly, porous bearing) configured to control and/or adjust a position (e.g., radial position) of the shaft 104 relative to an axis 122 (e.g., rotational axis, central axis) of the shaft 104.
  • the first bearing 118 and the second bearing 120 may be configured to support a load of the shaft 104, such that the shaft 104 levitates within the first bearing 118 and the second bearing 120.
  • the first bearing 118 and the second bearing 120 may also be configured to block movement (e.g., bending, radial movement, eccentric rotation) of the shaft 104 crosswise to the axis 122.
  • the compressor 32 e.g., bearing system 100
  • the compressor 32 further includes a third bearing 124 (e.g., thrust bearing, axial bearing, bearing assembly, porous bearing) configured to control and/or adjust a position (e.g., axial position) of the shaft 104 along the axis 122.
  • the third bearing 124 may be configured to block or limit movement (e.g., translation) of the shaft 104 along the axis 122.
  • the bearing system 100 is configured to direct a pressurized fluid to bearings of the bearing system 100, such as the first bearing 118, the second bearing 120, and/or the third bearing 124.
  • the pressurized fluid may be the same working fluid (e.g., refrigerant) circulated through the vapor compression system 14 having the compressor 32.
  • the pressurized fluid may be any suitable fluid, such as a refrigerant, a condensable vapor, or other fluid.
  • the first bearing 118, the second bearing 120, and/or the third bearing 124 each include one or more porous elements 126 configured to direct the pressurized fluid therethrough.
  • the one or more porous elements 126 of the first bearing 1 18 and the second bearing 120 may be configured to received pressurized fluid and direct the pressurized fluid towards the shaft 104 to establish a high-pressure fluid film (e.g., vapor film) about the shaft 104 between the first bearing 118 and the second bearing 120 and the shaft 104.
  • the pressurized fluid may cause the shaft 104 to levitate from the first bearing 118 and the second bearing 120, thereby enabling desired rotation of the shaft 104 about the axis 122.
  • the one or more porous elements 126 of the third bearing 124 may receive pressurized fluid and direct the pressurized fluid towards a collar 128 (e.g., thrust collar) of the third bearing 124. In this way, the pressurized fluid may apply a force to the collar 128 and enable adjustable positioning of the shaft 104 along the axis 122.
  • the bearing system 100 includes a fluid supply system 130 configured to supply pressurized fluid to the bearings (first bearing 118, second bearing 120, and/or third bearing 124) of the bearing system 100.
  • the fluid supply system 130 may direct the pressurized fluid through the housing 102 of the compressor 32 to one or more bearing housings 132 (e.g., casings) of the first bearing 118, the second bearing 120, and the third bearing 124.
  • one bearing housing 132 is associated with the first bearing 118
  • another bearing housing 132 is associated with the second bearing 120.
  • An additional bearing housing 132 may be utilized with the third bearing 124.
  • the second bearing 120 and the third bearing 124 may be packaged together in a common bearing housing 132.
  • the pressurized fluid may be directed through the bearing housings 132 to the corresponding porous elements 126 retained within each bearing housing 132.
  • the fluid supply system 130 is described in further detail below.
  • the compressor 32 may include any suitable number or type (e.g., radial, axial) of bearings incorporating the present techniques, and the bearings may be positioned at any suitable location within the housing 102 of the compressor 32.
  • FIG. 6 is a schematic of an embodiment of the vapor compression system 14 (e.g., HVAC&R system) including the bearing system 100 for the compressor 32.
  • the vapor compression system 14 includes elements similar to those discussed above, including the compressor 32, the motor 50, the condenser 34, and the evaporator 38 (e.g., falling film evaporator) arranged along a working fluid circuit 200 (e.g., refrigerant circuit).
  • the bearing system 100 also includes the fluid supply system 130 configured to direct pressurized fluid to the bearings (e.g., first bearing 118) of the bearing system 100.
  • the fluid supply system 130 is configured to direct a portion of working fluid (e.g., refrigerant) circulated through the working fluid circuit 200 to the bearing assemblies 150.
  • the fluid supply system 130 includes a lubricant circuit 202 (e.g., fluid supply circuit) extending from the working fluid circuit 200 to the bearing assemblies 150 via a fluid conduit 203.
  • the lubricant circuit 202 extends from a liquid line portion 204 of the working fluid circuit 200 to one or more of the bearing assemblies 150.
  • the liquid line portion 204 extends from the condenser 34 to the evaporator 38.
  • working fluid within the liquid line portion 204 may be in a liquid phase.
  • Various components are disposed along the lubricant circuit 202 and are configured to enable desirable supply of working fluid to the bearing assemblies 150 to enable the bearing assemblies 150 to support a load of the shaft 104 of the compressor 32.
  • the fluid supply system 130 includes a pump 206 (e.g., liquid pump) disposed along the lubricant circuit 202 and configured to direct flow of working fluid (e.g.
  • the pump 206 may be a linear piston pump, in some embodiments, and the pump 206 may be driven via a solenoid coil, a motor, and/or via another suitable technique. In some embodiments, the pump 206 may operate without utilizing oil or other dedicated lubricant.
  • the fluid supply system 130 also includes a pressure accumulator 208 fluidly coupled to the lubricant circuit 202.
  • the pressure accumulator 208 is fluidly coupled to the lubricant circuit 202 downstream of the pump 206 relative to a flow of working fluid along the lubricant circuit 202.
  • the pressure accumulator 208 may receive a pressurized flow of working fluid (e.g., liquid working fluid, vapor working fluid, or both) from the pump 206 and the lubricant circuit 202.
  • the pressure accumulator 208 is configured to store pressurized working fluid therein.
  • the pressure accumulator 208 may include a vessel 210 and a separator 212 (e.g., bladder, diaphragm, piston, etc.) disposed therein.
  • the separator 212 may divide an internal volume of the vessel 210 into a biasing chamber 214 (e g., gas chamber) on a first side of the separator 212 and a fluid chamber 216 (e.g., liquid chamber, working fluid chamber) on a second side the separator 212.
  • the fluid chamber 216 of the pressure accumulator 208 is configured to receive pressurized working fluid from the lubricant circuit 202.
  • the separator 212 may be a bladder or other flexible container pre-charged with a gas (e.g., nitrogen) to enable maintaining the pressure of the working fluid within the fluid chamber 216.
  • a gas e.g., nitrogen
  • the biasing chamber 214 may be pre-charged with a gas.
  • the biasing chamber 214 may instead include a spring or other mechanical biasing component.
  • the pressure accumulator 208 may operate as a mechanical battery configured to enable supply (e.g., temporary supply) of pressurized working fluid from the fluid chamber 216 to the bearing assemblies 150 via the lubricant circuit 202, such as during periods of non-operation of the pump 206.
  • the pressure accumulator 208 may discharge pressurized working fluid to the lubricant circuit 202 for supply to the bearing assemblies 150.
  • the bearing assemblies 150 may continue to operate to support a load on the shaft 104 while operation of the pump 206 is restarted and/or while operation of the compressor 32 (e.g., the motor 50) is suspended in a controlled manner.
  • the pressure accumulator 208 may also operate to damp oscillations in the flow of pressurized working fluid directed to the bearing assemblies 150.
  • the pressure accumulator 208 may be configured to supply pressurized working fluid to the bearing assemblies 150 at startup of the vapor compression system 14 (e.g., prior to operation of the pump 206 and/or the compressor 32).
  • the fluid supply system 130 may also include other components disposed along the lubricant circuit 202, such as a check valve 218 disposed between the pump 206 and the pressure accumulator 208.
  • the check valve 218 may be configured to close and block flow of liquid working fluid from the pump 206 and along toward the bearing assemblies 150 based on a pressure of the liquid working fluid discharged by the pump 206. For example, in response to a pressure of the liquid working fluid falling below a threshold value (e.g., a threshold value corresponding to a liquid working fluid pressure desired for supply to the bearing assemblies 150), the check valve 218 may close.
  • a threshold value e.g., a threshold value corresponding to a liquid working fluid pressure desired for supply to the bearing assemblies 150
  • pressurized liquid working fluid stored within the pressure accumulator 208 may be supplied to the bearing assemblies 150 (e.g., with the closed check valve 218 blocking working fluid flow back to the pump 206) to enable at least temporary continued operation of the bearing assemblies 150 to support the shaft 104.
  • the check valve 218 may be a ball check valve, a diaphragm check valve, a swing check valve, a stop-check valve, a lift-check valve, an in-line check valve, or any other suitable valve.
  • the fluid supply system 130 may include a filter 220 disposed along the lubricant circuit 202 (e.g., downstream of the pressure accumulator 208 and upstream up the bearing assemblies 150).
  • the filter 220 e.g., may be configured to remove particulates and/or moisture (e.g., water, water vapor) from the liquid working fluid prior to the liquid working fluid being directed to the bearing assemblies 150.
  • the fluid supply system 130 may also include a heat exchanger 222 disposed along the lubricant circuit 202.
  • the heat exchanger 222 is disposed upstream of the pump 206 relative to flow of working fluid through the lubricant circuit 202.
  • the heat exchanger 222 may be a brazed-plate heat exchanger.
  • the heat exchanger 222 may function as a subcooler configured to subcool working fluid directed from the liquid line portion 204 into the lubricant circuit 202.
  • the heat exchanger 222 may operate to ensure that the working fluid supplied to the pump 206 is in a liquid phase, which may reduce undesired effects, such as flashing of the working fluid at the pump 206, cavitation of the pump 206, and so forth.
  • the heat exchanger 222 is configured to place the working fluid drawn from the liquid line portion 204 in a heat exchange relationship with a cooling fluid (e.g., auxiliary cooling fluid) directed to the heat exchanger 222 via a cooling fluid circuit 224.
  • the cooling fluid may be water, in some embodiments.
  • the cooling fluid circuit 224 may be configured to supply the cooling fluid from an external source.
  • the cooling fluid circuit 224 may be configured to supply water or other cooling fluid (e.g., cooled via the evaporator 38) from a conditioning fluid conduit, such as the supply line 60S and/or the return line 60R described above.
  • the cooling fluid may be another portion of working fluid from the working fluid circuit 200.
  • the cooling fluid circuit 224 may extend from the working fluid circuit 200 (e.g., the liquid line portion 204) to the heat exchanger 222.
  • the cooling fluid circuit 224 may be configured to direct any suitable cooling fluid to the heat exchanger 222 to enable cooling (e.g., subcooling) of the portion of the working fluid directed along the lubricant circuit 202 toward the bearing assemblies 150 of the compressor 32.
  • the bearing assemblies 150 are configured to receive pressurized fluid (e.g., working fluid, refrigerant) and to discharge the fluid towards the shaft 104 or collar 128.
  • the bearing assemblies 150 each include one or more porous elements configured to direct the pressurized working fluid therethrough and to flash the pressurized working fluid and discharge pressurized vapor working fluid towards the shaft 104 or collar 128.
  • the working fluid may flow through the housing 102 of the compressor 32 (e.g., motor 50) to one or more drain lines 226 of the bearing system 100.
  • the bearing system 100 may include a first drain line 228 extending from the housing 102 to the liquid line portion 204 of the working fluid circuit 200.
  • the first drain line 228 may include a valve 230 (e.g., electronic expansion valve) and/or may be configured to direct vapor working fluid from the housing 102 to the liquid line portion 204 of the working fluid circuit 200.
  • the bearing system 100 may include a second drain line 232 extending from the housing 102 to the evaporator 38 and/or a third drain line 234 extending from the housing 102 to the evaporator 38.
  • the second drain line 232 is configured to direct vapor working fluid from the housing 102 to the evaporator 38
  • the third drain line 234 is configured to direct liquid working fluid from the housing 102 to the evaporator 38.
  • the vapor compression system 14 may also include a controller 250 (e g., a control system, control board, control panel) communicatively coupled to one or more components of the vapor compression system 14 and/or the bearing system 100.
  • the controller 250 is configured to monitor, adjust, and/or otherwise control operation of the components of the vapor compression system 14 and/or the bearing system 100.
  • one or more control transfer devices such as wires, cables, wireless communication devices, and the like, may communicatively couple the compressor 32, the motor 50, the pump 206, and/or other components described herein.
  • Such components may include a network interface that enables the components of the vapor compression system 14 and/or bearing system 100 to communicate via various protocols such as EtherNet/IP, ControlNet, DeviceNet, or any other communication network protocol.
  • the communication component may enable the components of the vapor compression system 14 and/or bearing system 100 to communicate via mobile telecommunications technology, Bluetooth®, near-field communications technology, and the like.
  • the controller 250 may include a portion or all of the control panel 40 or may be another suitable controller included in the vapor compression system 14 and/or the bearing system 100. In any case, the controller 250 may be configured to control components of the vapor compression system 14 and/or the bearing system 100 in accordance with the techniques discussed herein.
  • the controller 250 includes processing circuitry 252, such as one or more microprocessors, which may execute software for controlling the components of the vapor compression system 14 and/or the bearing system 100.
  • the processing circuitry 252 may include multiple microprocessors, one or more “general-purpose” microprocessors, one or more special-purpose microprocessors, and/or one or more application specific integrated circuits (ASICS), or some combination thereof.
  • ASICS application specific integrated circuits
  • the processing circuitry 252 may include one or more reduced instruction set (RISC) processors.
  • RISC reduced instruction set
  • the controller 250 may also include a memory device 254 (e.g., a memory) that may store information such as instructions, control software, look up tables, configuration data, etc.
  • the memory device 254 may include a volatile memory, such as random access memory (RAM), and/or a nonvolatile memory, such as read-only memory (ROM).
  • RAM random access memory
  • ROM read-only memory
  • the memory device 254 may store a variety of information and may be used for various purposes.
  • the memory device 254 may store processor-executable instructions including firmware or software for the processing circuitry 252 to execute, such as instructions for controlling components of the vapor compression system 14 and/or the bearing system 100.
  • the memory device 254 is a tangible, non- transitory, machine-readable-medium that may store machine-readable instructions for the processing circuitry 252 to execute.
  • the memory device 254 may include ROM, flash memory, a hard drive, or any other suitable optical, magnetic, or solid-state storage medium, or a combination thereof.
  • the memory device 254 may store data, instructions, and any other suitable data. It should be appreciated that the memory device 254 may store processor-executable instructions (e.g., for execution via the processing circuitry 252) to enable operation of any of the components described herein and to enable any of the functionalities and/or operations described herein.
  • the controller 250 may be configured to control operation of components of the vapor compression system 14 and/or the bearing system 100 based on detected operating parameters of the vapor compression system 14 and/or the bearing system 100.
  • the vapor compression system 14 includes one or more sensors 256 configured to detect operating parameters associated with or indicative of operating conditions of the vapor compression system 14 and the bearing system 100.
  • the sensors 256 may be disposed along the lubricant circuit 202 and may be configured to detect operating parameters of the working fluid directed through the lubricant circuit 202, such as temperature, pressure, flow rate, and so forth.
  • one or more sensors 256 may be configured to detect an operating parameter associated with the motor 50, such as a rotational speed of the shaft 104, a torque on the shaft 104, a temperature of the motor 50, and so forth.
  • One or more sensors 256 may be configured to detect an operating parameter of the bearing assemblies 150, such as a detection of whether one or more bearing assemblies 150 is in contact (e.g., physical contact) with the shaft 104, as described further below.
  • one of the sensors 256 may be configured to detect an operating parameter associated with the pressure accumulator 208, such as a pressure of working fluid within the fluid chamber 216 and/or a pressure of gas within the biasing chamber 214. Additionally or alternatively, one or more of the sensors 256 may be configured to detect a liquid level of working fluid within the condenser 34, which may be referenced before and/or during startup of the bearing system 100 and/or vapor compression system 14. As will be appreciated, each sensor 256 included in the vapor compression system 14 may be communicatively coupled to the controller 250. Thus, the controller 250 may receive data and/or feedback from the sensors 256 and may control operation of the vapor compression system 14 and/or the bearing system 100 based on the feedback and/or data.
  • an operating parameter associated with the pressure accumulator 208 such as a pressure of working fluid within the fluid chamber 216 and/or a pressure of gas within the biasing chamber 214.
  • one or more of the sensors 256 may be configured to detect a liquid level of working fluid within the con
  • FIG. 7 is a cross-sectional side view of an embodiment of the pump 206, in accordance with aspects of the present disclosure.
  • the pump 206 is configured to pump working fluid along the lubricant circuit 202 toward the bearing assemblies 150.
  • the pump 206 includes an inlet 300 (e.g., inlet port) configured to receive a flow of the working fluid into a pump body 302 (e.g., pump housing), as well as an outlet 304 (e.g., discharge port, outlet valve) configured to discharge the working fluid from the pump body 302 and direct the working fluid toward the bearing assemblies 150.
  • the pump 206 may include a piston 306 (e.g., intensifier piston) at least partially disposed within the pump body 302.
  • a piston 306 e.g., intensifier piston
  • the piston 306 is configured to move back and forth (e.g., reciprocate) within the pump body 302 to pressurize the working fluid. That is, the piston 306 may undergo reciprocating motion, including a compression stroke in a forward direction 308 and a return stroke in a return direction 310. During the return stroke, the piston 306 may cause working fluid to be drawn into the pump body 302 via the inlet 300. Subsequently, the piston 306 may reverse direction to perform the compression stroke and to pressurize and expel the working fluid from the pump body 302 via the outlet 304.
  • reciprocating motion including a compression stroke in a forward direction 308 and a return stroke in a return direction 310.
  • the piston 306 may cause working fluid to be drawn into the pump body 302 via the inlet 300.
  • the piston 306 may reverse direction to perform the compression stroke and to pressurize and expel the working fluid from the pump body 302 via the outlet 304.
  • the pump body 302 may be coupled (e.g., removably coupled) to a piston housing 311. Motion of the piston 306 may be driven by a solenoid coil 312 disposed about (e.g., surrounding, circumscribing) the piston housing 311 having the piston 306. Operation of the solenoid coil 312 may be controlled by a pump controller 314.
  • the pump controller 314 may include a memory and processing circuitry (e.g., one or more processors). In some embodiments, the pump controller 314 may be a standalone controller, and in other embodiments the pump controller 314 may be a component of and/or integrated with another controller of the vapor compression system 14 (e.g., control panel 40, controller 250).
  • the pump controller 314 may include embodiments of the processing circuitry 252 and the memory device 254 described above.
  • the pump controller 314 may direct current through the solenoid coil 312, thereby inducing a magnetic force upon the piston 306 to cause the piston 306 to travel in the forward direction 308 or the return direction 310, depending on a direction of the current through the solenoid coil 312.
  • the pump 206 may include a compression chamber 316 (e.g., high pressure chamber, liquid chamber, compression chamber) within the piston housing 311 that is fluidly coupled to the lubricant circuit 202 (e.g., the inlet 300).
  • the piston 306 may include a plunger section 318 configured to extend into compression chamber 316 to pressurize the working fluid (e.g., on the compression stroke). On the return stroke, the plunger section 318 may be retracted from the compression chamber 316, which may draw the working fluid to flow through the inlet 300 and into the compression chamber 316.
  • the movement of the piston 206 in the return direction 310 increases the volume of the compression chamber 316, thereby creating a pressure difference across the inlet 300.
  • the working fluid may flow through the inlet 300 into a volume of the compression chamber 316 vacated by retraction of the plunger section 318.
  • the inlet 300 may be a one-way valve (e.g., check valve) configured to selectively enable the working fluid to flow into the pump body 302, as shown.
  • the inlet 300 may include a hinged gate 320 (e.g., hinged valve, check valve, valve, inlet valve) or other valve member configured to pivot (e.g., open) inward toward the compression chamber 316.
  • a pressure difference (e.g., threshold pressure difference) across the hinged gate 320 may cause the working fluid to push the hinged gate 320 open and flow into the compression chamber 316.
  • the return stroke of the piston 306 may create a region of low pressure in the compression chamber 316 relative to the pressure of the working fluid upstream of the pump 206.
  • the inlet 300 may include a sealing seat 322 against which the hinged gate 320 may rest in a normally closed position to block flow of the working fluid from the compression chamber 316 out of the inlet 300 (e.g., in an upstream direction). For example, if the pressure in the compression chamber 316 is greater than the pressure upstream of the inlet 300 (e.g., during the compression stroke), then the higher pressure working fluid in the compression chamber 316 may bias the hinged gate 320 against the sealing seat 322 to close the inlet 300.
  • the hinged gate 320 may enable flow of the working fluid into the pump 206 (e.g., during the return stroke) while blocking flow of the working fluid in the opposite direction out of the pump 206 (e.g., during the compression stroke).
  • the hinged gate 320 may be biased toward a closed position (e.g., via a spring or other biasing element), such that the hinged gate 320 is configured to transition from the closed position toward an open position upon the application of a threshold pressure difference (e.g., greater than zero) across the hinged gate 320.
  • a threshold pressure difference e.g., greater than zero
  • the inlet 300 may be in a closed position against the sealing seat 322 when no pressure difference exists across the hinged gate 320 (e.g., at the end of each stroke).
  • the outlet 304 may be a one-way valve (e.g., check valve) configured to enable flow of the working fluid out of the pump 206 toward the bearing assemblies 150 and to also block backflow of the working fluid into the pump 206.
  • a pressure difference (e.g., threshold pressure difference) across the outlet 304 may cause the outlet 304 (e.g., an outlet valve) to open, allowing flow of the working fluid therethrough.
  • the compression stroke of the piston 306 may create a region of high pressure in the compression chamber 316 relative to the lubricant circuit 202 downstream of the pump 206.
  • a valve e.g., ball valve
  • the outlet 304 may include a check valve (e.g., ball check valve) having a ball 324 and a spring 326 biasing the ball 324 towards a closed or sealed position (e.g., against the flow of the working fluid).
  • a check valve e.g., ball check valve
  • the pump 206 includes a piston cavity 328 (e.g., second chamber, low pressure chamber, vapor chamber), which may be separated from the compression chamber 316 by a wiper seal 330.
  • the piston cavity 328 may be formed within and/or by the piston housing 311, and the piston 206 may be disposed within the piston cavity 328.
  • the plunger section 318 of the piston 306 translates (e g., reciprocates, oscillates) between the compression chamber 316 and the piston cavity 328. For example, during the return stroke, the plunger section 318 at least partially retracts from the compression chamber 316 and extends further into the piston cavity 328.
  • the piston 306 also includes a head section 332 (e.g., head portion) at a return end (e.g., first end) of the plunger section 318.
  • the head section 332 is configured to translate back and forth (e.g., reciprocate, oscillate) within the piston cavity 328 (e.g., the piston housing 311), thereby driving the plunger section 318 into and out of the compression chamber 316.
  • the head section 332 may have a greater diameter than the plunger section 318.
  • the piston cavity 328 may contain a vapor 341, such as working fluid in a gaseous phase.
  • the vapor 341 may be a portion of the working fluid that flows from the compression chamber 316, across the wiper seal 330, and into the piston cavity 328.
  • the pump 206 may include a bypass conduit 334 (e.g., bypass passage, bypass port) extending between (e.g., from and to) the compression chamber 316 and the piston cavity 328 to enable a portion of the working fluid (e.g., vapor 341 ) to bypass the wiper seal 330 and flow from the compression chamber 316 to the piston cavity 328.
  • a bypass conduit 334 e.g., bypass passage, bypass port
  • the working fluid may vaporize (e.g., flash) due to a decrease in pressure.
  • the head section 332 moves (e.g., translates, oscillates) within the piston cavity 328, the vapor 341 may flow across and cool the portions of the piston 306 within the piston cavity 328.
  • the piston 306 may be driven by the solenoid coil 312 which induces a magnetic force on the piston 306.
  • heat generated by the magnetic induction may reduce the performance and/or longevity of the pump 206.
  • the pump 206 may include a heat sink 336 (e.g., heat dissipation element) coupled to the piston 306.
  • the heat sink 336 may be formed from a non-magnetic material, such that the induced magnetic force may not act upon and/or cause generation of heat within the heat sink 336.
  • the heat sink 336 may be coupled (e.g., clipped) around the piston 306.
  • the heat sink 336 may not contact a wall (e.g., an interior wall) of the piston cavity 328. That is, a gap (e.g., a radial gap, clearance, space) may extend between the heat sink 336 and the wall of the piston cavity 328. Vapor working fluid (e.g., vapor 341) within the piston cavity 328 may flow across the heat sink 336 (e.g., during a compression stroke) to enable cooling of the piston 306 (e.g., via heat transfer from the heat sink 336 and/or the piston 306 to the vapor working fluid). In some embodiments, the vapor 341 may also absorb heat from the solenoid coil 312.
  • a gap e.g., a radial gap, clearance, space
  • Vapor working fluid e.g., vapor 341
  • the vapor 341 may also absorb heat from the solenoid coil 312.
  • the pump 206 may include a bleed vent 338 through which the vapor 341 may exit the pump 206 from the piston cavity 328.
  • the bleed vent 338 may direct the vapor 341 (e.g., vapor working fluid) to the working fluid circuit 200, such as to a selected component of the working fluid circuit 200 (e.g., evaporator 38, compressor 32, drain line 226).
  • the pump 206 may include one or more piston rings 340 disposed about the piston 306 (e.g., head section 332).
  • the piston rings 340 may be configured to control the flow of vapor 341 within the piston cavity 328.
  • at least one of the piston rings 340 may be ported (e.g., include one or more ports 339, such as axial ports) formed therein) or include notches to enable the vapor 341 to flow across the piston 306 and within the piston cavity 328 in a desired manner.
  • the piston rings 340 may be configured to enable flow of the vapor 341 across the piston 306 and throughout the piston cavity 328 to enable cooling of the piston 306 via the vapor 341.
  • the piston rings 340 may be configured to contact the walls of the piston cavity 328, thereby enabling heat transfer between the piston 306, the piston housing 311, and the working fluid.
  • Operation of the pump 206 may be controlled by the pump controller 314.
  • the pump controller 314 may supply a current or control a supply of current to the solenoid coil 312.
  • the pump controller 314 may adjust the magnitude and/or other characteristic of the current to control the magnitude of the magnetic force generated by the solenoid coil 312 and applied to the piston 306.
  • the pump controller 314 may change a direction of the current through the solenoid col 312 to reverse the polarity of the solenoid coil 312 and consequently a direction of the magnetic force acting on the piston 306.
  • the pump controller 314 may direct the current through the solenoid coil 312 at a certain magnitude (e.g., amperage) in a certain direction.
  • a certain magnitude e.g., amperage
  • the pump controller 314 may reduce the magnitude of the current.
  • the pump controller 314 may reverse the direction of the current through the solenoid coil 312.
  • the motion of the piston 306 within the piston housing 311 may correspond to an electrical input (e.g., current, voltage, power) provided to the solenoid coil 312.
  • the pump controller 314 may control the electrical input based on a current profile configured to achieve a desired motion pattern of the piston 306.
  • a current profile of the compression stroke of the piston 306 may be a function of current with respect to time that is selected to cause the piston 306 to accelerate in the forward direction 308 for a certain period of time, decelerate for another period, and then reverse direction into the return stroke.
  • operating conditions e.g., deadheading
  • the pump 206 may cause variance in the behavior of the pump 206, given a certain current profile.
  • cavitation of the working fluid may occur under certain operating conditions, such as if the return stroke of the piston 306 is too fast. Therefore, it may be desirable to adjust the current profile in response to a speed or frequency of the pump 206 (e.g., piston 306), which may be determined based on sensed operating conditions.
  • the pump 206 includes a respective bump stop 342 at each end of the piston cavity 328.
  • Each bump stop 342 may be configured to mechanically stop the piston 306 in response to contact between the bump stop 342 and the piston 306.
  • the pump 206 includes two bump stops 342, such as a forward bump stop 343 and a return bump stop 345.
  • Each bump stop 342 is disposed at a respective end of travel of the head section 332 within the piston cavity 328.
  • the bump stops 342 may provide a mechanical stop for the piston 306 at the end of each stroke.
  • each bump stop 342 may include an internal switch 344 (e g., internal switch mechanism) configured to provide a signal to the pump controller 314 indicative of contact between the piston 306 and the bump stop 342.
  • the pump 206 may include an electrical feedthrough 346 through which electrical conduits (e.g., wires) may extend to electrically couple the pump controller 314 to one or more components of the pump 206 (e.g., the internal switches 344).
  • electrical conduits e.g., wires
  • wires 348 may extend through the electrical feedthrough 346 to connect the pump controller 314 to contacts of the internal switch 333 of one or more of the bump stops 342.
  • the wires 348 may feed current to the solenoid coil 312 from a power supply and/or the pump controller 314 to enable operation of the pump 206 in the manner described above.
  • FIGS. 8 and 9 illustrate cross-sectional side view schematics of a portion of an embodiment of the piston 306, illustrating operation of the internal switch 344 of one of the forward bump stop 343.
  • the illustrated embodiments show contact between the piston 306 and the forward bump stop 343 (e.g., first bump stop) at the end of a compression stroke.
  • FIGS. 8 and 9 illustrate the forward bump stop 343 at the forward end of the piston cavity 328, the techniques described in the following discussion may similarly apply to a second bump stop (e.g., return bump stop 345) disposed at a return end, opposite the forward end, of the piston 306.
  • a second bump stop e.g., return bump stop 345
  • the forward bump stop 343 includes a body 370, which may be formed from a conformable (e.g., compressible), non-conductive material, such as an elastomer (e.g., silicone, rubber). As such, the forward bump stop 343 may be configured to at least partially absorb a force applied to the body 370 during contact between the forward bump stop 343 and the piston 306. In this way, the forward bump stop 343 may be configured to bring the piston 306 to rest (e.g., a stationary state) in a controlled manner at an end of a stroke of the piston 306.
  • a conformable e.g., compressible
  • non-conductive material such as an elastomer (e.g., silicone, rubber).
  • the forward bump stop 343 may be configured to at least partially absorb a force applied to the body 370 during contact between the forward bump stop 343 and the piston 306. In this way, the forward bump stop 343 may be configured to bring the piston 306 to rest (e.g., a stationary state) in
  • the internal switch 344 of the forward bump stop 343 includes a suspended contact 372 encased within the body 370, such that the suspended contact 372 is moveable in response to application of a force to the body 370 (e.g., during compression of the body 370).
  • the forward bump stop 343 includes a -tact 374 that is stationary with respect to the pump 206 (e.g., relative to the body 370 and/or the suspended contact 372).
  • the fixed contact 374 may be coupled to the pump body 302, such that the fixed contact 374 does not move, even as the piston 306 contacts and compresses the body 370.
  • the fixed contact 374 may include a first flange 376 disposed about (e.g., annularly about) the body 370 and a second flange 378 extending radially toward (e.g., into) the body 370.
  • the second flange 378 may contact the suspended contact 372 when the body 370 is in an uncompressed or resting state of the forward bump stop 343, as shown in FIG. 8. That is, the body 370 may elastically bias the suspended contact 372 to abut the fixed contact 374, thereby establishing electrical continuity between the suspended contact 372 and the fixed contact 374. In this way, the electrical connection between the suspended contact 372 and the fixed contact 374 may be normally closed.
  • contact e.g., electrical continuity
  • detection of electrical discontinuity between the suspended contact 372 and the fixed contact 374 may be indicative of the piston 306 reaching an end of a compression stroke.
  • the piston 306 may contact (e.g., impact, abut) the body 370 of the forward bump stop 343 at the end of a compression stroke.
  • the body 370 may compress (e.g., elastically deform), and the force of the piston 306 may cause the suspended contact 372 to translate in the forward direction 308, temporarily breaking physical contact, and therefore the electrical connection, between the fixed contact 374 and the suspended contact 372.
  • motion of the piston 306 may reverse (e.g., bounce) away from the forward bump stop 343 (e.g., in the reverse direction 310) as the body 370 decompresses and returns to a resting or undeformed state.
  • the suspended contact 372 may return to contact with the fixed contact 374, thereby reestablishing the electrical connection therebetween.
  • the pump controller 314 may monitor the electrical continuity between the suspended contact 372 and the fixed contact 374 to detect impact of the piston 306 against the forward bump stop 343, which may correspond to an end of a compression stroke.
  • the pump controller 314 may monitor probe wires 380 extending through the electrical feedthrough 346 to measure a voltage between (e.g., across) the fixed contact 374 and the suspended contact 372.
  • a detected voltage that is low (e.g., zero) may be indicative of contact (e.g., physical contact) between the fixed contact 374 and the suspended contact 372.
  • a detected voltage that is high e.g., greater than zero
  • the pump controller 314 may determine that the piston 306 is at the end of a stroke.
  • the pump controller 314 may reverse the direction of the current supplied to the solenoid coil 312 in order to reverse the direction of movement of the piston 306 within the piston housing 311. For example, in response to detecting a disconnection between the suspended contact 372 and the fixed contact 374 of the forward bump stop 343, the pump controller 314 may reverse the direction of the current directed through the solenoid coil 312 to cause the piston to travel in the return direction 310 and thereby initiate a return stroke after completion of a compression stroke of the piston 306.
  • the motion profile of each stroke (e.g., velocity or acceleration over time) may be controlled based on the current profile. For example, the current profile may map current values to nominal or expected acceleration values. Then, the pump controller 314 may achieve a desired acceleration value by supplying a corresponding current value based on the current profile.
  • the current profile may be adjusted (e.g., via the pump controller 314) to enable adjusted operation of the piston 306.
  • the current profile may be adjusted based on one or more detected operating parameters and/or operating conditions of the pump 206.
  • the current profile may be adjusted to avoid and/or mitigate cavitation and/or conditions indicative of cavitation in the pump 206.
  • the return stroke may introduce local regions of low pressure within the pump 206 in which the working fluid may cavitate. Such cavitation of the working fluid may introduce inefficiency and wear to the pump 206. Therefore, the pump controller 314 may utilize methods described herein to adjust the motion of the piston 306 (e.g., speed of the return stroke) to reduce cavitation.
  • FIG. 10 illustrates a flowchart of an embodiment of a method 400 that may be performed by the pump controller 314 to adjust operation (e.g., motion) of the piston 306, such as based on sensed feedback or data (e.g., feedback indicative of cavitation or potential cavitation).
  • the pump controller 314 may determine a change in an interval, period, frequency, and/or speed of strokes (e.g., successive strokes, sequential strokes) of the piston 306 from one stroke cycle to the next, such as based on a time period or interval between physical contact of the piston 306 at each of the bump stops 342.
  • the change may be a symptom of cavitation caused by operation of the pump 206 according to the current profile under certain operating conditions.
  • the pump controller 314 may adjust the current profile to reduce potential and/or instances of cavitation.
  • the pump controller 314 may cause the piston 306 to perform the compression stroke.
  • the pump controller 314 may energize (e.g., supply a current to) the solenoid coil 312 with a direction and magnitude according to a particular current profile.
  • the direction and magnitude of the current may be constant or variable throughout the stroke, resulting in a controlled speed profile of the piston 306.
  • the current profile may cause the piston 306 to accelerate forward initially and then decelerate toward the end of the compressions stroke.
  • the pump controller 314 may energize the solenoid coil to induce a desired magnetic force on the piston in a first direction (e.g., forward direction, compression direction).
  • the piston 306 may contact the forward bump stop 343 (e.g., first bump stop) at the forward end of the piston cavity 328.
  • the pump controller 314 may detect the contact against the forward bump stop 343 based on a disconnection between the fixed contact 374 and the suspended contact 372.
  • the internal switch 344 may send a signal to the pump controller 314 indicative of the contact against the forward bump stop 343.
  • the pump controller 314 may determine a speed of the compression stroke based on an interval between a time of contact at the forward bump stop 343 and a preceding time of contact at a return bump stop 345 (e.g., second bump stop). The time interval between these two moments of contact may correspond to a speed of the compression stroke. For example, at the end of the return stroke, the piston 306 may impact the return bump stop 345 at a time, ti. Then, at the end of the compression stroke, the piston 306 may impact the forward bump stop 343 at a time, t2. Then, the pump controller 314 may determine that the interval is t2- ti. Based on the interval, the pump controller 314 may determine the speed of the compression stroke.
  • a return bump stop 345 e.g., second bump stop
  • the pump controller 314 may determine a period or frequency of the pump cycle by based on the time of contact at the forward bump stop 343 and a previous time of contact at the forward bump stop. For example, the pump controller 314 may detect a first contact at the forward bump stop 343 at a time, ti, and then a second contact at the forward bump stop 343 at a time, t2. Then, the pump controller 314 may determine that the period of the pump cycle is t2 - ti. In either case, the pump controller 314 determines an interval of time between subsequent contacts at one or both of the bump stops 342.
  • the pump controller 314 may compare the speed of the compression stroke to the speed of a previous compression stroke (e.g., immediately preceding compression stroke) of the piston 306. For example, the pump controller 314 may compare the interval of time determined at block 406 to a previous interval of time for the previous compression stroke. Based on the comparison between the two intervals, the pump controller 314 may determine a difference (e.g., change) in the speeds of the compression stroke and the previous compression stroke. For example, the pump controller 314 may determine that most recent compression stroke is 100 milliseconds slower than the previous compression stroke. The reduction in speed of the compression stroke may be a symptom of cavitation during the return stroke.
  • a previous compression stroke e.g., immediately preceding compression stroke
  • the pump controller 314 may determine whether the change in speed of the compression stroke from the previous compression stroke is greater than a threshold amount (e.g., zero, 10 milliseconds, 100 milliseconds, etc ). If so (i.e., the difference is significant enough), then at block 412, the pump controller 314 may adjust the current profile based on the difference. For example, the pump controller 314 may adjust the current profile to reduce the speed (e.g., average speed, acceleration) of the return stroke in order to avoid further cavitation. Then, at block 414, the pump controller 314 may supply current to initiate the return stroke based on the adjusted current profile. In this way, the pump controller 314 may utilize the change in speed of the compression stroke as feedback to control the current through the solenoid coil 312.
  • a threshold amount e.g., zero, 10 milliseconds, 100 milliseconds, etc.
  • the pump controller 314 may detect contact between the piston 306 and the return bump stop 345. In some embodiments, the pump controller 314 may start a timer or store the time at which the contact at the return bump stop 345 occurs. In this way, the interval between the contact at the return bump stop 345 and a subsequent contact at the forward bump stop 343 may be determined. In response to detecting the contact at the return bump stop 345, the pump controller 314 may return to block 402 to supply current to the solenoid coil 312 to initiate the compression stroke. For example, the pump controller 314 may reverse the polarity of the solenoid coil 312, causing the piston 306 to reverse toward the forward direction 308.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)

Abstract

Une pompe (206) pour un système de chauffage, ventilation, climatisation et réfrigération (CVC-R) (10) comprend un corps de pompe (302) définissant une chambre de compression (316). Le système CVC-R (10) comprend également un logement de piston (311) couplé au corps de pompe (302). Le logement de piston (311) comprend une cavité de piston (328). La pompe (206) comprend en outre un piston (306) disposé à l'intérieur du logement de piston (311). Le piston (306) comprend une section de piston (318) configurée pour effectuer un mouvement de va-et-vient entre la chambre de compression (316) et la cavité de piston (328). De plus, le piston (306) comprend une section de tête (332) configurée pour effectuer un mouvement de va-et-vient à l'intérieur de la cavité de piston (328). En outre, la pompe (206) comprend une bobine d'électro-aimant (312) configurée pour induire une force magnétique sur le piston (306). En outre, la pompe (206) comprend un dispositif de commande (314) configuré pour commander l'écoulement d'un courant à travers la bobine d'électro-aimant (312) pour commander le mouvement de va-et-vient du piston (306) à l'intérieur de la cavité de piston (328).
PCT/US2024/014821 2023-02-07 2024-02-07 Pompe pour système cvc-r Ceased WO2024168047A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN202480017594.9A CN120752435A (zh) 2023-02-07 2024-02-07 用于hvac&r系统的泵
KR1020257029795A KR20250143114A (ko) 2023-02-07 2024-02-07 Hvac＆r 시스템용 펌프

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US202363443921P 2023-02-07 2023-02-07
US63/443,921 2023-02-07
US202363541201P 2023-09-28 2023-09-28
US63/541,201 2023-09-28

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WO2024168047A1 true WO2024168047A1 (fr) 2024-08-15

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CN (1) CN120752435A (fr)
TW (1) TW202436811A (fr)
WO (1) WO2024168047A1 (fr)

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CN119267178A (zh) * 2024-10-31 2025-01-07 广东佛燃科技有限公司 高转速隔膜压缩机双锥油腔结构及其制造方法

Citations (5)

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EP1336751A1 (fr) * 2001-09-12 2003-08-20 Mikuniadec Corporation Pompe a combustible a solenoide placee dans un reservoir
US20130183174A1 (en) * 2010-10-01 2013-07-18 Franklin Electric Company, Inc. Solenoid pump
US20170335834A1 (en) * 2016-05-23 2017-11-23 Caterpillar Inc. Pump for fluid system and method of operating same
WO2020214807A1 (fr) * 2019-04-16 2020-10-22 Johnson Controls Technology Company Régulation d'écoulement de fluide pour un système de lubrification de compresseur
US20220145875A1 (en) * 2020-11-09 2022-05-12 Hydrocision, Inc. System, apparatus, and method for motor speed control

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1336751A1 (fr) * 2001-09-12 2003-08-20 Mikuniadec Corporation Pompe a combustible a solenoide placee dans un reservoir
US20130183174A1 (en) * 2010-10-01 2013-07-18 Franklin Electric Company, Inc. Solenoid pump
US20170335834A1 (en) * 2016-05-23 2017-11-23 Caterpillar Inc. Pump for fluid system and method of operating same
WO2020214807A1 (fr) * 2019-04-16 2020-10-22 Johnson Controls Technology Company Régulation d'écoulement de fluide pour un système de lubrification de compresseur
US20220145875A1 (en) * 2020-11-09 2022-05-12 Hydrocision, Inc. System, apparatus, and method for motor speed control

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN119267178A (zh) * 2024-10-31 2025-01-07 广东佛燃科技有限公司 高转速隔膜压缩机双锥油腔结构及其制造方法

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CN120752435A (zh) 2025-10-03
TW202436811A (zh) 2024-09-16

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