EP3633202B1 - Hvac compressor with mixed and radial compression stages - Google Patents

Hvac compressor with mixed and radial compression stages Download PDF

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Publication number
EP3633202B1
EP3633202B1 EP19200465.3A EP19200465A EP3633202B1 EP 3633202 B1 EP3633202 B1 EP 3633202B1 EP 19200465 A EP19200465 A EP 19200465A EP 3633202 B1 EP3633202 B1 EP 3633202B1
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EP
European Patent Office
Prior art keywords
compression stage
wall
refrigerant
compressor
flow path
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP19200465.3A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3633202A1 (en
Inventor
Lin Xiang Sun
Jin YAN
Hamid Richard HAZBY
Christopher John ROBINSON
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.)
Danfoss AS
Original Assignee
Danfoss AS
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Publication of EP3633202A1 publication Critical patent/EP3633202A1/en
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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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/025—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal comprising axial flow and radial flow stages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/06—Helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • F04D19/028—Layout of fluid flow through the stages
    • 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
    • F04D29/403—Casings; Connections of working fluid especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves

Definitions

  • HVAC heating, ventilation, and air conditioning
  • Refrigerant compressors are used to circulate refrigerant in a chiller via a refrigerant loop.
  • Refrigerant loops are known to include a condenser, an expansion device, and an evaporator.
  • the compressor compresses the fluid, which then travels to a condenser, which in turn cools and condenses the fluid.
  • the refrigerant then goes to an expansion device, which decreases the pressure of the fluid, and to the evaporator, where the fluid is vaporized, completing a refrigeration cycle.
  • refrigerant compressors are centrifugal compressors and have an electric motor that drives at least one impeller to compress refrigerant. Fluid flows into the impeller in an axial direction, and is expelled radially from the impeller. The fluid is then directed downstream for use in the chiller system.
  • WO2018/038818 describes a refrigerant compressor.
  • the compressor includes a mixed section having a plurality of blades and vanes and a centrifugal section having an impeller.
  • the centrifugal section is arranged downstream of the axial section
  • the present invention relates to a refrigerant compressor and refrigerant system as defined in the appended claims.
  • a refrigerant compressor includes, among other things, a first compression stage arranged in a main refrigerant flow path.
  • the first compression stage is a mixed compression stage having both axial and radial components.
  • the compressor further includes a second compression stage arranged in the main refrigerant flow path downstream of the first compression stage.
  • the second compression stage is a radial compression stage.
  • the first compression stage is arranged such that fluid is configured to flow therethrough along a direction inclined relative to an axis of rotation of the refrigerant compressor.
  • the direction is inclined at an angle of less than 45° relative to the axis of rotation of the refrigerant compressor.
  • the main refrigerant flow path is defined between an outer wall and an inner wall. Further, adjacent an inlet of the first compression stage, the outer wall and inner wall are radially spaced-apart from one another by a first radial distance, and adjacent an outlet of the first compression stage, the outer wall and inner wall are radially spaced-apart from one another by a second radial distance less than the first radial distance.
  • the outer wall and the inner wall are curved within the first compression stage.
  • the outer wall and the inner wall are concave when viewed from a radially outer location.
  • the outer wall and the inner wall have inflection points and smoothly transition such that the outer wall and the inner wall are substantially parallel to one another between the first compression stage and the second compression stage.
  • an array of static diffuser vanes is arranged in the main refrigerant flow path between the first compression stage and the second compression stage.
  • the second compression stage includes an impeller configured to turn a substantial axial flow to a substantial radial flow.
  • the main refrigerant flow path makes a substantially 180 degree turn between the first and second compression stages.
  • the main refrigerant flow path includes a cross-over bend between the first and second compression stages.
  • deswirl vanes are arranged within the main refrigerant flow path downstream of the cross-over bend and upstream of the second compression stage.
  • the refrigerant compressor is used in a heating, ventilation, and air conditioning (HVAC) chiller system.
  • HVAC heating, ventilation, and air conditioning
  • a refrigerant system includes, among other things, a main refrigerant loop including a compressor, a condenser, an evaporator, and an expansion device.
  • the compressor includes a first compression stage arranged in a main refrigerant flow path.
  • the first compression stage is a mixed compression stage having both axial and radial components.
  • a second compression stage is arranged in the main refrigerant flow path downstream of the first compression stage.
  • the second compression stage is a radial compression stage.
  • the first compression stage is arranged such that fluid is configured to flow therethrough along a direction inclined relative to an axis of rotation of the refrigerant compressor at an angle of less than 45° relative to the axis of rotation of the refrigerant compressor.
  • the main refrigerant flow path is defined between an outer wall and an inner wall.
  • the outer wall and the inner wall are curved within the first compression stage such that the outer wall and inner wall are concave when viewed from a radially outer location.
  • an array of static diffuser vanes is arranged in the main refrigerant flow path between the first compression stage and the second compression stage.
  • the second compression stage includes an impeller configured to turn a substantial axial flow to a substantial radial flow.
  • the main refrigerant flow path makes a substantially 180 degree turn between the first and second compression stages.
  • the refrigerant system is a heating, ventilation, and air conditioning (HVAC) chiller system.
  • HVAC heating, ventilation, and air conditioning
  • FIG. 1 illustrates a refrigerant system 10.
  • the refrigerant system 10 includes a main refrigerant loop, or circuit, 12 in communication with a compressor 14, a condenser 16, an evaporator 18, and an expansion device 20.
  • This refrigerant system 10 may be used in a chiller, for example.
  • a cooling tower may be in fluid communication with the condenser 16.
  • the main refrigerant loop 12 can include an economizer downstream of the condenser 16 and upstream of the expansion device 20.
  • Figure 2 schematically illustrates a refrigerant compressor
  • a portion of the compressor 14 is shown in cross-section. It should be understood that Figure 2 only illustrates an upper portion of the compressor 14, and that the compressor 14 would essentially include the same structure reflected about its central longitudinal axis A.
  • the compressor 14 has two compression stages 22, 24 spaced-apart from one another along the axis A.
  • the compression stages 22, 24 each include a plurality of blades (e.g., an array of blades) arranged on a disk, for example, and rotatable about the axis A via a motor 26.
  • the motor 26 is an electric motor arranged about the axis A.
  • the compression stages 22, 24 may be coupled to the motor 26 by separate shafts or by a common shaft. Two shafts are shown schematically in Figure 2 .
  • the compressor 14 includes an outer wall 28 and an inner wall 30 which together bound a main flow path 32.
  • the main flow path 32 extends between an inlet 34 and an outlet 36 of the compressor 14.
  • the outer and inner walls 28, 30 may be provided by one or more structures.
  • fluid F within the main flow path 32 flows in a first direction F 1 , which is an axial direction substantially parallel to the axis A.
  • the "axial" direction is labeled in Figure 2 for reference.
  • the fluid F is refrigerant in this disclosure.
  • the first compression stage 22 includes a plurality of blades 33 arranged for rotation about the axis A. Adjacent the inlet 33I of the first compression stage 22, the outer and inner walls 28, 30 are spaced-apart by a radial distance D 1 . Adjacent the outlet 33O of the first compression stage 22, the outer and inner walls 28, 30 are spaced-apart by a radial distance D 2 , which is less than D 1 . The distances D 1 and D 2 are measured normally to the axis A.
  • the outer and inner walls 28, 30 are arranged such that the fluid F is directed in a second direction F 2 , which has both axial and radial components.
  • the first compression stage 22 may be referred to as a "mixed" compression stage, because the fluid F within the first compression stage 22 has both axial and radial flow components.
  • the "radial" direction is labeled in Figure 2 for reference.
  • the second direction F 2 is inclined at an angle of less than 45° relative to the first direction F 1 and relative to the axis A. In this way, the second direction F 2 is primarily axial but also has a radial component (i.e., the axial component is greater than the radial component).
  • the inner and outer walls 28, 30 are not straight. Rather, the inner and outer walls 28, 30 are curved. Specifically, in this example, the inner and outer walls 28, 30 are curved such that they are generally concave within the first compression stage 22 when viewed from a radially outer location, such as the location 35 in Figure 2 .
  • the fluid F smoothly transitions from a purely axial flow to a mixed flow having both axial and radial components.
  • the outer and inner walls 28, 30 Downstream of the first compression stage 22, the outer and inner walls 28, 30 have inflection points and smoothly transition such that they are substantially parallel to one another. As such, the fluid F is directed in a third direction F 3 , which is substantially parallel to both the first direction F 1 and the axis A. As the fluid F is flowing in the third direction F 3 , the fluid F also flows through an array of static diffuser vanes 38 in this example.
  • the fluid F Downstream of the diffuser vanes 38, the fluid F is directed to the second compression stage 24, which in this example includes an impeller 40 configured to turn the fluid F flowing in a substantially axial direction to a substantially radial direction.
  • the impeller 40 includes an inlet 40I arranged axially, substantially parallel to the axis A, and an outlet 40O arranged radially, substantially perpendicular to the axis A.
  • the fluid F enters the second compression stage 24 flowing in the third direction F 3 and exits the second compression stage 24 flowing in a fourth direction F 4 , which in one example is substantially parallel to the radial direction.
  • the fourth direction F 4 is inclined relative to the axis A at an angle greater than 45° and less than or equal to 90°.
  • the fourth direction F 4 is substantially equal to 90°.
  • the second stage compression 24 may be referred to as a radial compression stage.
  • the compressor 14 is more compact than a compressor that includes two radial impellers, for example.
  • the compressor 14 also exhibits an increased operating range, in that it can operate without surging at lower capacities, relative to compressors with two axial impellers. Accordingly, the compressor 14 strikes a unique balance between being compact and efficient.
  • Figure 3 schematically illustrates a refrigerant compressor according to the invention.
  • the compressor 114 corresponds to the compressor 14 of Figure 2 , with like parts having reference numerals preappended with a "1.”
  • the compressor 114 has two compression stages 122, 124 spaced-apart from one another along an axis A.
  • the first compression stage 122 is a "mixed" compression stage and is arranged substantially similar to the first compression stage 22.
  • the second compression stage 124 is a radial compression stage and is likewise arranged substantially similar to the second compression stage 24.
  • the main flow path 132 of the compressor 114 includes a 180-degree bend between the first and second compression stages 122, 124. Specifically, downstream of the first compression stage 122, the main flow path 132 turns and projects radially outward from the axis A. Specifically, the main flow path 132 is substantially normal to the axis A within a first section 190. The main flow path 132 turns again by substantially 180 degrees in a cross-over bend 192, such that the main flow path 132 projects radially inward toward the axis A in a second section 194, which may be referred to as a return channel.
  • the second section includes deswirl vanes 196 in this example, which ready the flow of fluid F for the second compression stage 124.
  • the compressor 114 downstream of the second compression stage 124, the compressor 114 includes an outlet volute 198 which spirals about the axis A and leads to a compressor outlet.
  • the compressor 14 may also include an outlet volute.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP19200465.3A 2018-10-03 2019-09-30 Hvac compressor with mixed and radial compression stages Active EP3633202B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201862740464P 2018-10-03 2018-10-03
US16/430,848 US20200109879A1 (en) 2018-10-03 2019-06-04 Hvac compressor with mixed and radial compression stages

Publications (2)

Publication Number Publication Date
EP3633202A1 EP3633202A1 (en) 2020-04-08
EP3633202B1 true EP3633202B1 (en) 2024-03-27

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Application Number Title Priority Date Filing Date
EP19200465.3A Active EP3633202B1 (en) 2018-10-03 2019-09-30 Hvac compressor with mixed and radial compression stages

Country Status (3)

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US (1) US20200109879A1 (zh)
EP (1) EP3633202B1 (zh)
CN (1) CN110986403B (zh)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11143193B2 (en) * 2019-01-02 2021-10-12 Danfoss A/S Unloading device for HVAC compressor with mixed and radial compression stages
US12050036B2 (en) * 2020-04-30 2024-07-30 Danfoss A/S System and method for cooling power electronics of refrigerant compressors
EP4015829A1 (de) * 2020-12-18 2022-06-22 Siemens Energy Global GmbH & Co. KG Radialturbomaschine, insbesondere verdichter

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4344737A (en) * 1978-01-30 1982-08-17 The Garrett Corporation Crossover duct
US4678398A (en) * 1985-05-08 1987-07-07 The Garrett Corporation High efficiency transonic mixed-flow compressor method and apparatus
US6488469B1 (en) * 2000-10-06 2002-12-03 Pratt & Whitney Canada Corp. Mixed flow and centrifugal compressor for gas turbine engine
GB0718846D0 (en) * 2007-09-27 2007-11-07 Cummins Turbo Tech Ltd Compressor
WO2009088846A1 (en) * 2007-12-31 2009-07-16 Johnson Controls Technology Company Method and system for rotor cooling
BG110826A (bg) * 2010-12-28 2012-06-29 Петров Росен Газотурбинен двигател
EP2807430B1 (en) * 2012-01-23 2019-10-23 Danfoss A/S Variable-speed multi-stage refrigerant centrifugal compressor with diffusers
US9382911B2 (en) * 2013-11-14 2016-07-05 Danfoss A/S Two-stage centrifugal compressor with extended range and capacity control features
US10989222B2 (en) * 2016-08-25 2021-04-27 Danfoss A/S Refrigerant compressor

Also Published As

Publication number Publication date
CN110986403B (zh) 2023-10-31
US20200109879A1 (en) 2020-04-09
EP3633202A1 (en) 2020-04-08
CN110986403A (zh) 2020-04-10

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