EP3592986A1 - Collecteur pour compresseur - Google Patents

Collecteur pour compresseur

Info

Publication number
EP3592986A1
EP3592986A1 EP18712410.2A EP18712410A EP3592986A1 EP 3592986 A1 EP3592986 A1 EP 3592986A1 EP 18712410 A EP18712410 A EP 18712410A EP 3592986 A1 EP3592986 A1 EP 3592986A1
Authority
EP
European Patent Office
Prior art keywords
diffuser
compressor
refrigerant
collector
radial passage
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.)
Withdrawn
Application number
EP18712410.2A
Other languages
German (de)
English (en)
Inventor
Paul W 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.)
Johnson Controls Technology Co
Original Assignee
Johnson Controls Technology Co
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 Johnson Controls Technology Co filed Critical Johnson Controls Technology Co
Publication of EP3592986A1 publication Critical patent/EP3592986A1/fr
Withdrawn legal-status Critical Current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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F04D29/4233—Fan casings with volutes extending mainly in axial or radially inward direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • F04D29/464—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps adjusting flow cross-section, otherwise than by using adjustable stator blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/40—Flow geometry or direction
    • F05B2210/403—Radial inlet and axial outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/14—Refrigerants with particular properties, e.g. HFC
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/70—Shape
    • F05D2250/71—Shape curved
    • F05D2250/712—Shape curved concave

Definitions

  • This application relates generally to vapor compression systems incorporated in air conditioning and refrigeration applications, and, more particularly, to a collector for a compressor.
  • Vapor compression systems are utilized in residential, commercial, and industrial environments to control environmental properties, such as temperature and humidity, for occupants of the respective environments.
  • the vapor compression system circulates a working fluid, typically referred to as a refrigerant, which changes phases between vapor, liquid, and combinations thereof in response to being subjected to different temperatures and pressures associated with operation of the vapor compression system.
  • a refrigerant typically referred to as a working fluid
  • the vapor compression system utilizes a compressor to circulate the refrigerant to a heat exchanger which may transfer heat between the refrigerant and another fluid flowing through the heat exchanger.
  • vapor compression systems may include a relatively large footprint which may result from the use of relatively large components used to achieve a desired flow capacity.
  • a compressor in one embodiment, includes an impeller configured to compress a working fluid, a diffuser positioned downstream of the impeller with respect to a flow path of the working fluid, where the diffuser is configured to direct the working fluid through a radial passage, and where the diffuser comprises a vaned diffuser portion disposed within the radial passage, and a collector positioned downstream of the diffuser with respect to the flow path of the working fluid, where a chamber of the collector is axially offset from the radial passage of the diffuser.
  • a compressor for a heating, ventilating, air conditioning, and refrigeration (HVAC&R) unit includes an impeller configured to compress a refrigerant, a diffuser positioned downstream of the impeller with respect to a flow path of the refrigerant, where the diffuser is configured to direct the refrigerant through a radial passage, and where the diffuser comprises a variable geometry diffuser ring portion and a vaned diffuser portion disposed within the radial passage, and a collector positioned downstream of the diffuser with respect to the flow path of the refrigerant, where a chamber of the collector axially offset from the radial passage of the diffuser.
  • HVAC&R heating, ventilating, air conditioning, and refrigeration
  • a heating, ventilating, air conditioning, and refrigeration (HVAC&R) system includes a heat exchanger configured to place a refrigerant in thermal communication with a working fluid and a compressor configured to circulate the refrigerant through the heat exchanger.
  • the compressor includes an impeller configured to compress the refrigerant, a diffuser positioned downstream of the impeller with respect to a flow path of the refrigerant, where the diffuser is configured to direct the refrigerant through a radial passage, and a collector positioned downstream of the diffuser with respect to the flow path of the refrigerant, where a chamber of the collector is axially offset from the radial passage of the diffuser.
  • FIG. 1 is a perspective view of an embodiment of a building that may utilize a heating, ventilation, air conditioning, and refrigeration (HVAC&R) system in a commercial setting, in accordance with an aspect of the present disclosure;
  • HVAC&R heating, ventilation, air conditioning, and refrigeration
  • FIG. 2 is a perspective view 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 cross-section of an embodiment of a collector for a compressor that may be included in the systems of FIGS. 1-4, in accordance with an aspect of the present disclosure
  • FIG. 6 is an elevation view of a vaned diffuser portion of the compressor of FIG. 5, in accordance with an aspect of the present disclosure.
  • FIG. 7 is a perspective view of the vaned diffuser portion of FIG. 6, in accordance with an aspect of the present disclosure.
  • Embodiments of the present disclosure are directed towards a heating, ventilating, air conditioning, and refrigeration (HVAC&R) system that uses a compressor to circulate refrigerant through a refrigerant loop.
  • the compressor may be coupled to a condenser of the HVAC&R system along the refrigerant loop.
  • the compressor may compress the refrigerant to increase a pressure of the refrigerant and direct the refrigerant to the condenser.
  • the refrigerant may flow towards the condenser of the HVAC&R system where it may transfer thermal energy to a working fluid in the condenser.
  • the HVAC&R system may also include an evaporator, an expansion valve, and/or other components that generally cause the HVAC&R system to have a relatively large footprint. As such, it is now recognized that modifying existing features of components of the HVAC&R system may reduce an overall size of the HVAC&R system.
  • the compressor of the HVAC&R system includes a collector, which is positioned downstream from an impeller and/or a diffuser of the compressor with respect to a flow path of the refrigerant.
  • the collector may then further diffuse the refrigerant and ultimately direct the refrigerant toward a discharge port of the compressor.
  • Existing collectors are generally positioned radially outward from the diffuser of the compressor. Further, existing collectors circumferentially surround the entire diffuser, and thus, the impeller of the compressor. In other words, an inlet to the collector is radially aligned with an outlet of the diffuser, such that a chamber of the collector extends radially outward from the outlet of the diffuser. It is now recognized that axially offsetting the collector from the diffuser may reduce a diameter of the compressor, thereby reducing a size of the compressor.
  • axially offsetting the collector from the diffuser may alter a flow of refrigerant from the diffuser to the collector.
  • a cross-sectional area of the chamber of the collector may be adjusted to enable the collector to sufficiently diffuse the refrigerant, while increasing a pressure rise of the refrigerant flowing from the diffuser to the collector.
  • an aspect ratio of the cross section of the collector may be within a target range to enable the compressor to increase or maintain an efficiency when compared to existing compressors.
  • the diffuser section of the compressor may include a variable geometry diffuser ring and/or a vaned diffuser to guide the flow of refrigerant through a passage of the diffuser and further increase the pressure rise of the refrigerant, thereby enabling a size of the collector to be further reduced.
  • a size of the compressor may be reduced, and thus, an overall footprint of the HVAC&R system is also reduced.
  • FIG. 1 is a perspective view of an embodiment of an environment for a heating, ventilation, air conditioning, and 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 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 (AID) converter 42, a microprocessor 44, a non-volatile memory 46, and/or an interface board 48.
  • AID analog to digital
  • HFC hydrofluorocarbon
  • R- 41 OA R-407, R-134a
  • HFO hydrofluoro olefin
  • "natural" refrigerants like ammonia ( H 3 )
  • R-717 R-717
  • CO2 carbon dioxide
  • R-744 or hydrocarbon based refrigerants, water vapor, or any other suitable refrigerant.
  • 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 (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 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 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 refrigerant vapor and delivers the vapor to the condenser 34 through a discharge passage.
  • the compressor 32 may be a centrifugal or mixed-flow 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 as a result of 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.
  • 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 (e.g., water, ethylene glycol, calcium chloride brine, sodium chloride brine, or any other suitable fluid) 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. [0023] FIG.
  • 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 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. Additionally, 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.
  • 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.
  • existing compressors may include a volute or a collector (e.g., a dump collector) that includes an inlet radially aligned with an outlet of a diffuser. It is now recognized that such a configuration increases a diameter of the compressor, thereby increasing an overall footprint of an HVAC&R system that includes the compressor.
  • embodiments of the present disclosure are directed to compressors that include a collector having an inlet that is axially offset from the outlet of the diffuser (e.g., a folded collector).
  • a folded collector refers to a collector having an inner chamber that is axially offset from a passage (e.g., a radial passage) of a diffuser of the compressor.
  • a cross section of the folded collector may include an aspect ratio that increases the pressure rise of the compressor by appropriately guiding the flow of refrigerant as it travels from the diffuser into the collector and/or through the collector.
  • the diffuser may include a vaned diffuser portion that further increases the pressure rise of the refrigerant as it flows through the diffuser toward the collector. As such, a size of the collector may be further reduced, thereby decreasing a size of the compressor.
  • FIG. 5 is a cross section of an embodiment of the compressor 32 having a folded collector 100.
  • the compressor 32 includes an impeller 102 configured to rotate about an axis 104 to drive refrigerant from a suction portion 106 of the compressor 32 toward a diffuser 108.
  • the impeller 102 transfers kinetic energy to the refrigerant, thereby enabling the refrigerant to flow toward and through the diffuser 108.
  • the diffuser 108 guides the refrigerant toward the folded collector 100 and transforms the kinetic energy of the refrigerant into potential energy, by increasing a pressure of the refrigerant.
  • the diffuser 108 may include a variable geometry diffuser ring portion 110 and/or a vaned diffuser portion 112.
  • the variable geometry diffuser ring portion 110 may include a ring 114 which may extend axially into a passage 116 of the diffuser 108, thereby partially blocking a flow of the refrigerant from the impeller 102 toward the folded collector 100.
  • the ring 114 may extend into the passage 116 when the compressor 32 operates at partial capacity (e.g., less than 100% capacity), and a position of the ring 114 may depend at least on a flow of the refrigerant through the compressor 32.
  • a position of the ring 114 within the passage 116 adjusts the flow of refrigerant through the compressor 32, and thus, a pressure of the refrigerant discharged from the compressor 32.
  • the position of the ring 114 is adjusted by the control system 40 or another suitable controller.
  • the passage 116 includes a length 117 extending from the impeller 102 toward the folded collector 100.
  • the variable geometry diffuser ring portion 110 and/or vaned diffuser portion 112 may be used to maintain a substantially stable pressure rise of the refrigerant as the refrigerant flows along the length 117 of the passage 116.
  • the position of the ring 114 may be adjusted (e.g., via a signal sent from the control system 40 to an actuator) to adjust a flow angle of the refrigerant directed toward the vaned diffuser portion 112.
  • the vaned diffuser portion 112 may include vanes that are configured to turn as the refrigerant flows through the vaned diffuser portion 112. The vanes of the vaned diffuser portion 112 guide the flow of the refrigerant within the passage 116, thereby increasing the pressure rise of the refrigerant flowing through the diffuser 108.
  • the pressure increase of the refrigerant caused by the vaned diffuser portion 112 may be based on the flow angle of the refrigerant directed from the variable geometry diffuser ring portion 110 to the vaned diffuser portion 112. For example, adjusting a flow angle of the refrigerant to be substantially equal to an incidence angle of a leading edge of the vanes may increase the efficiency of the compression stage.
  • variable geometry diffuser ring portion 110 and the vaned diffuser portion 112 may sufficiently increase the pressure rise of the refrigerant through the diffuser 108 such that a diameter 118 of the passage 116 may be reduced, thereby decreasing the overall size of the compressor 32.
  • the folded collector 100 includes an inlet 120 that is axially offset from an outlet 122 of the diffuser 108. Accordingly, the folded collector 100 is axially offset from the radial passage 116 by a distance 123. Accordingly, an interface 124 between the inlet 120 and the outlet 122 may form a bend 125 (e.g., a curved passage) that guides the refrigerant from the outlet 122 to the inlet 120. Refrigerant may flow through the inlet 120 toward a chamber 126 of the folded collector 100. In some embodiments, the chamber 126 is axially offset from the diffuser 108.
  • the portion 128 of the chamber 126 is positioned adjacent to at least a portion 130 of the diffuser 108 with respect to the axis 104.
  • a diameter of the compressor 32 may be reduced when compared to existing compressors that include a collector that is radially aligned with the diffuser 108 with no axial offset.
  • dimensions of the chamber 126 of the folded collector 100 are selected to account for a shift in a direction of flow of the refrigerant from the outlet of refrigerant is configured to flow in a radial direction 132 through the diffuser 108 and enters the inlet 120 of the folded collector 100 in an axial direction 134.
  • dimensions of the chamber 126 of the folded collector 100 may be configured to maintain the pressure rise achieved by the diffuser section 108 while reducing the overall diameter of the compressor 32.
  • the chamber 126 is defined by an axial length 136 and a radial length 138.
  • the chamber 126 may be further defined by other suitable dimensions in addition to, or in lieu of, the axial length 136 and the radial length 138.
  • the axial length 136 refers to a distance between a wall 140 separating the chamber 126 from the diffuser 108 and an outermost point 142 of a concave wall 144 that forms the chamber 126.
  • the radial length 138 refers to a distance between a first connecting wall 146 (e.g., a first axial connecting wall) and a second connecting wall 148 (e.g., a second axial connecting wall).
  • the first connecting wall 146 couples the concave wall 144 to the wall 140
  • the second connecting wall 148 couples the concave wall 144 to an interface wall 150 that at least partially defines the interface 124 between the outlet 122 of the diffuser 108 and the inlet 120 of the collector 100.
  • the wall 140, the concave wall 144, the first connecting wall 146, and the second connecting wall 148 form the chamber 126 of the folded collector 100. While the illustrated embodiment of FIG. 5 shows the chamber 126 having a cross-sectional shape that is substantially elliptical, it should be understood that the chamber 126 may include any cross-sectional shape that provides a suitable collection volume.
  • An aspect ratio of the axial length 136 to the radial length 138 may vary widely depending on the particular embodiment.
  • the aspect ratio may be defined by the axial length 136 and the radial length 138 and may be utilized to maintain the pressure rise achieved by the diffuser section 108 within the folded collector 100.
  • the aspect ratio refers to a ratio of the axial length 136 to the radial length 138.
  • the aspect ratio may be between 0.5: 1 and 5: 1, between 0.75: 1 and 3 : 1, or between 1 : 1 and 3 : 1.
  • the aspect ratio may be substantially (e.g., within 10% of, within 5% of, or within 1% of) 1 : 1.
  • the aspect ratio may be selected to maintain or increase a pressure rise of the refrigerant flowing through folded collector 100.
  • the diffuser 108 may include the vaned diffuser portion 112, which may include multiple vanes 160 that rotate to adjust the angle of the refrigerant flowing through the passage 116 of the diffuser 108.
  • FIGS. 6 and 7 illustrate embodiments of the vaned diffuser portion 112 having a plurality of the vanes 160 and that may be disposed within the passage 116 of the diffuser 108. The number of diffuser vanes may vary depending on the specific embodiment.
  • the vaned diffuser portion 112 includes fifteen of the vanes 160, in other embodiments, the vaned diffuser portion 112 includes one, two, three, four, five, six, seven, eight, nine, ten, eleven, twelve, thirteen, fourteen, or more than fifteen of the vanes 160.
  • each of the vanes 160 protrude from a surface 162 of the vaned diffuser portion 112. Additionally or alternatively, the surface 162 may include the ring 114 of the variable geometry diffuser ring portion 110. In any case, the refrigerant flowing through the passage 116 contacts a leading edge 164 of each of the vanes 160.
  • the plurality of vanes 160 increases pressure recovery of the refrigerant through the relatively narrow flow path between the impeller 102 and the folded collector 100. Accordingly, the radial length 138 of the folded collector 100 may be decreased as a result of the increased pressure recovery caused by the vaned diffuser portion 112. Therefore, the size of the compressor 32 and/or the HVAC&R system may also be reduced.
  • a position of the variable geometry diffuser ring portion 110 may enable a flow angle of the refrigerant to be substantially equal to an incidence 166 of the leading edge 164 of the vanes 160 of the vaned diffuser portion 112.
  • a control system such as the control system 40, may adjust a position of the ring 114 of the variable geometry diffuser ring portion 110 within the passage 116 to adjust a flow angle of the refrigerant downstream of the ring 114.
  • the position of the ring 114 may be adjusted to achieve the flow angle based on a target flow of the refrigerant entering the compressor 32, a discharge pressure of the refrigerant exiting the compressor 32, a speed at which the motor 50 drives the impeller 102, and/or another suitable parameter.
  • the control system 40 may receive feedback indicative of one or more parameters and adjust the position of the ring 114 within the passage 116 to achieve the flow angle of refrigerant that is substantially equal to (e.g., within 10% of, within 5% of, or within 1% of) the incidence 166 of the leading edge 164 of the vanes 160.
  • the folded collector 100 in combination with the diffuser 108 having both the variable geometry diffuser ring portion 1 10 and the vaned diffuser portion 112 reduces a size of the compressor, and thus the HVAC&R system.
  • Embodiments of the disclosure may include a compressor that includes a folded collector.
  • the folded collector may be axially offset from an outlet of a diffuser of the compressor, which may reduce a diameter of the compressor.
  • the diffuser may include a variable geometry diffuser ring portion and/or a vaned diffuser portion that increases the pressure rise of the refrigerant flowing through the diffuser. As such, the radial length of the diffuser of the folded collector may be reduced, which further reduces a size of the compressor.
  • the technical effects and technical problems in the specification are examples and are not limiting. It should be noted that the embodiments described in the specification may have other technical effects and can solve other technical problems.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)

Abstract

Des modes de réalisation de la présente invention concernent un compresseur comprenant une roue conçue pour comprimer un fluide de travail, un diffuseur positionné en aval de la roue par rapport à un chemin d'écoulement du fluide de travail, le diffuseur étant conçu pour diriger le fluide de travail dans un passage radial, et le diffuseur comprenant une partie de diffuseur à aubes disposée dans le passage radial, et un collecteur positionné en aval du diffuseur par rapport au chemin d'écoulement du fluide de travail, où une chambre du collecteur est axialement décalée par rapport au passage radial du diffuseur.
EP18712410.2A 2017-03-09 2018-03-08 Collecteur pour compresseur Withdrawn EP3592986A1 (fr)

Applications Claiming Priority (3)

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US201762469410P 2017-03-09 2017-03-09
US201762537352P 2017-07-26 2017-07-26
PCT/US2018/021606 WO2018165471A1 (fr) 2017-03-09 2018-03-08 Collecteur pour compresseur

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EP3592986A1 true EP3592986A1 (fr) 2020-01-15

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US (1) US20200018325A1 (fr)
EP (1) EP3592986A1 (fr)
JP (1) JP2020510152A (fr)
KR (1) KR20190121846A (fr)
CN (1) CN110603382A (fr)
TW (1) TW201839318A (fr)
WO (1) WO2018165471A1 (fr)

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CN116075641A (zh) * 2020-07-30 2023-05-05 江森自控泰科知识产权控股有限责任合伙公司 用于引导压缩机中的流体流动的系统和方法

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US20110318182A1 (en) * 2009-03-05 2011-12-29 Airzen Co.,Ltd Gas compressor and method for controlling flow rate thereof

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US4770605A (en) * 1981-02-16 1988-09-13 Mitsubishi Jukogyo Kabushiki Kaisha Diffuser device in a centrifugal compressor and method for manufacturing the same
CH677956A5 (fr) * 1986-07-02 1991-07-15 Carrier Corp
JPS63130698U (fr) * 1987-02-19 1988-08-26
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DE4331606C1 (de) * 1993-09-17 1994-10-06 Gutehoffnungshuette Man Spiralgehäuse für Turbomaschinen
JP2002048098A (ja) * 2000-08-02 2002-02-15 Mitsubishi Heavy Ind Ltd ターボ圧縮機および冷凍機
DE102007028742A1 (de) * 2007-06-21 2008-12-24 Daimler Ag Luftversorger, insbesondere für ein Luftversorgungssystem von Brennstoffzellen
US8567207B2 (en) * 2007-10-31 2013-10-29 Johnson Controls & Technology Company Compressor control system using a variable geometry diffuser
JP5251587B2 (ja) * 2009-02-19 2013-07-31 株式会社Ｉｈｉ 遠心圧縮機
CN104067071B (zh) * 2012-01-23 2016-12-21 丹佛斯公司 具有扩压器的变速多级离心式制冷压缩机
JP6256142B2 (ja) * 2014-03-26 2018-01-10 株式会社豊田自動織機 遠心圧縮機

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Publication number Publication date
CN110603382A (zh) 2019-12-20
JP2020510152A (ja) 2020-04-02
TW201839318A (zh) 2018-11-01
US20200018325A1 (en) 2020-01-16
KR20190121846A (ko) 2019-10-28
WO2018165471A1 (fr) 2018-09-13

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