US20200109879A1 - Hvac compressor with mixed and radial compression stages - Google Patents
Hvac compressor with mixed and radial compression stages Download PDFInfo
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- US20200109879A1 US20200109879A1 US16/430,848 US201916430848A US2020109879A1 US 20200109879 A1 US20200109879 A1 US 20200109879A1 US 201916430848 A US201916430848 A US 201916430848A US 2020109879 A1 US2020109879 A1 US 2020109879A1
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Classifications
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- 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
- F04D17/06—Helico-centrifugal 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
- F04D17/02—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
- F04D17/08—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
- F25B31/00—Compressor arrangements
- F25B31/02—Compressor arrangements of motor-compressor units
- F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary 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
- 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.
- 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, and 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 schematically illustrates a refrigerant system.
- FIG. 2 schematically illustrates a first example compressor having two compression stages, with a first compression stage being a mixed compression stage and a second compression stage being a radial compression stage.
- FIG. 3 schematically illustrates a second example compressor having two compression stages, with a first compression stage being a mixed compression stage and a second compression stage being a radial compression stage.
- 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 .
- FIG. 2 schematically illustrates a first example example refrigerant compressor according to this disclosure.
- a portion of the compressor 14 is shown in cross-section. It should be understood that FIG. 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 FIG. 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 FIG. 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 331 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 330 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 FIG. 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 FIG. 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 401 arranged axially, substantially parallel to the axis A, and an outlet 400 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.
- FIG. 3 schematically illustrates a second example refrigerant compressor according to this disclosure.
- the compressor 114 corresponds to the compressor 14 of FIG. 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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Abstract
Description
- This disclosure relates to a compressor having a mixed compression stage and a radial compression stage. The compressor is used in a heating, ventilation, and air conditioning (HVAC) chiller system, for example.
- 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.
- Many 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.
- A refrigerant compressor according to an exemplary aspect of the present disclosure 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.
- In a further embodiment, 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.
- In a further embodiment, the direction is inclined at an angle of less than 45° relative to the axis of rotation of the refrigerant compressor.
- In a further embodiment, 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.
- In a further embodiment, the outer wall and the inner wall are curved within the first compression stage.
- In a further embodiment, within the first compression stage, the outer wall and the inner wall are concave when viewed from a radially outer location.
- In a further embodiment, 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.
- In a further embodiment, an array of static diffuser vanes is arranged in the main refrigerant flow path between the first compression stage and the second compression stage.
- In a further embodiment, the second compression stage includes an impeller configured to turn a substantial axial flow to a substantial radial flow.
- In a further embodiment, the main refrigerant flow path makes a substantially 180 degree turn between the first and second compression stages.
- In a further embodiment, the main refrigerant flow path includes a cross-over bend between the first and second compression stages.
- In a further embodiment, deswirl vanes are arranged within the main refrigerant flow path downstream of the cross-over bend and upstream of the second compression stage.
- In a further embodiment, the refrigerant compressor is used in a heating, ventilation, and air conditioning (HVAC) chiller system.
- A refrigerant system according to an exemplary aspect of the present disclosure 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. Further, 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.
- In a further embodiment, 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.
- In a further embodiment, the main refrigerant flow path is defined between an outer wall and an inner wall, and 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.
- In a further embodiment, an array of static diffuser vanes is arranged in the main refrigerant flow path between the first compression stage and the second compression stage.
- In a further embodiment, the second compression stage includes an impeller configured to turn a substantial axial flow to a substantial radial flow.
- In a further embodiment, the main refrigerant flow path makes a substantially 180 degree turn between the first and second compression stages.
- In a further embodiment, the refrigerant system is a heating, ventilation, and air conditioning (HVAC) chiller system.
-
FIG. 1 schematically illustrates a refrigerant system. -
FIG. 2 schematically illustrates a first example compressor having two compression stages, with a first compression stage being a mixed compression stage and a second compression stage being a radial compression stage. -
FIG. 3 schematically illustrates a second example compressor having two compression stages, with a first compression stage being a mixed compression stage and a second compression stage being a radial compression stage. -
FIG. 1 illustrates arefrigerant system 10. Therefrigerant system 10 includes a main refrigerant loop, or circuit, 12 in communication with acompressor 14, acondenser 16, anevaporator 18, and anexpansion device 20. Thisrefrigerant system 10 may be used in a chiller, for example. In that example, a cooling tower may be in fluid communication with thecondenser 16. While a particular example of therefrigerant system 10 is shown, this application extends to other refrigerant system configurations, including configurations that do not include a chiller. For instance, themain refrigerant loop 12 can include an economizer downstream of thecondenser 16 and upstream of theexpansion device 20. -
FIG. 2 schematically illustrates a first example example refrigerant compressor according to this disclosure. InFIG. 2 , a portion of thecompressor 14 is shown in cross-section. It should be understood thatFIG. 2 only illustrates an upper portion of thecompressor 14, and that thecompressor 14 would essentially include the same structure reflected about its central longitudinal axis A. - In this example, the
compressor 14 has twocompression stages compression stages compression stages FIG. 2 . - The
compressor 14 includes anouter wall 28 and aninner wall 30 which together bound amain flow path 32. Themain flow path 32 extends between aninlet 34 and anoutlet 36 of thecompressor 14. The outer andinner walls - Between the
inlet 34 and thefirst compression stage 22, fluid F within themain flow path 32 flows in a first direction F1, which is an axial direction substantially parallel to the axis A. The “axial” direction is labeled inFIG. 2 for reference. The fluid F is refrigerant in this disclosure. - The
first compression stage 22 includes a plurality ofblades 33 arranged for rotation about the axis A. Adjacent theinlet 331 of thefirst compression stage 22, the outer andinner walls outlet 330 of thefirst compression stage 22, the outer andinner walls - Within the
first compression stage 22, the outer andinner walls first compression stage 22 may be referred to as a “mixed” compression stage, because the fluid F within thefirst compression stage 22 has both axial and radial flow components. The “radial” direction is labeled inFIG. 2 for reference. - In one example, the second direction F2 is inclined at an angle of less than 45° relative to the first direction F1 and relative to the axis A. In this way, the second direction F2 is primarily axial but also has a radial component (i.e., the axial component is greater than the radial component).
- Further, between the
inlet 331 andoutlet 330, the inner andouter walls outer walls outer walls first compression stage 22 when viewed from a radially outer location, such as thelocation 35 inFIG. 2 . Thus, the fluid F smoothly transitions from a purely axial flow to a mixed flow having both axial and radial components. - Downstream of the
first compression stage 22, the outer andinner walls static diffuser vanes 38 in this example. - Downstream of the
diffuser vanes 38, the fluid F is directed to thesecond compression stage 24, which in this example includes animpeller 40 configured to turn the fluid F flowing in a substantially axial direction to a substantially radial direction. In particular, theimpeller 40 includes aninlet 401 arranged axially, substantially parallel to the axis A, and anoutlet 400 arranged radially, substantially perpendicular to the axis A. - In particular, the fluid F enters the
second compression stage 24 flowing in the third direction F3 and exits thesecond compression stage 24 flowing in a fourth direction F4, which in one example is substantially parallel to the radial direction. In this disclosure, the fourth direction F4 is inclined relative to the axis A at an angle greater than 45° and less than or equal to 90°. In one particular example, the fourth direction F4 is substantially equal to 90°. In this way, thesecond stage compression 24 may be referred to as a radial compression stage. - The combination of the
first compression stage 22 having both axial and radial components (i.e., second direction F2 is inclined at less than 45°) with thesecond compression stage 24 being primarily radial (i.e., the fourth direction F4 is substantially equal to 90°), thecompressor 14 is more compact than a compressor that includes two radial impellers, for example. Thecompressor 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, thecompressor 14 strikes a unique balance between being compact and efficient. -
FIG. 3 schematically illustrates a second example refrigerant compressor according to this disclosure. To the extent not otherwise described or shown, thecompressor 114 corresponds to thecompressor 14 ofFIG. 2 , with like parts having reference numerals preappended with a “1.” - Like the
compressor 14, thecompressor 114 has twocompression stages first compression stage 122 is a “mixed” compression stage and is arranged substantially similar to thefirst compression stage 22. Thesecond compression stage 124 is a radial compression stage and is likewise arranged substantially similar to thesecond compression stage 24. - Unlike the
compressor 14, themain flow path 132 of thecompressor 114 includes a 180-degree bend between the first and second compression stages 122, 124. Specifically, downstream of thefirst compression stage 122, themain flow path 132 turns and projects radially outward from the axis A. Specifically, themain flow path 132 is substantially normal to the axis A within afirst section 190. Themain flow path 132 turns again by substantially 180 degrees in across-over bend 192, such that themain flow path 132 projects radially inward toward the axis A in asecond section 194, which may be referred to as a return channel. The second section includesdeswirl vanes 196 in this example, which ready the flow of fluid F for thesecond compression stage 124. Further, downstream of thesecond compression stage 124, thecompressor 114 includes anoutlet volute 198 which spirals about the axis A and leads to a compressor outlet. Thecompressor 14 may also include an outlet volute. - It should be understood that terms such as “axial” and “radial” are used above with reference to the normal operational attitude of a compressor. Further, these terms have been used herein for purposes of explanation, and should not be considered otherwise limiting. Terms such “generally,” “about,” and “substantially” are not intended to be boundaryless terms, and should be interpreted consistent with the way one skilled in the art would interpret those terms.
- Although the different examples have the specific components shown in the illustrations, embodiments of this disclosure are not limited to those particular combinations. It is possible to use some of the components or features from one of the examples in combination with features or components from another one of the examples.
- One of ordinary skill in this art would understand that the above-described embodiments are exemplary and non-limiting. That is, modifications of this disclosure would come within the scope of the claims. Accordingly, the following claims should be studied to determine their true scope and content.
Claims (20)
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Application Number | Priority Date | Filing Date | Title |
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US16/430,848 US20200109879A1 (en) | 2018-10-03 | 2019-06-04 | Hvac compressor with mixed and radial compression stages |
CN201910899790.4A CN110986403B (en) | 2018-10-03 | 2019-09-23 | Refrigeration compressor and refrigeration system |
EP19200465.3A EP3633202B1 (en) | 2018-10-03 | 2019-09-30 | Hvac compressor with mixed and radial compression stages |
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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 |
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US20200109879A1 true US20200109879A1 (en) | 2020-04-09 |
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US16/430,848 Pending US20200109879A1 (en) | 2018-10-03 | 2019-06-04 | Hvac compressor with mixed and radial compression stages |
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US (1) | US20200109879A1 (en) |
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US11143193B2 (en) * | 2019-01-02 | 2021-10-12 | Danfoss A/S | Unloading device for HVAC compressor with mixed and radial compression stages |
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EP4143490A4 (en) * | 2020-04-30 | 2024-05-15 | Danfoss As | System and method for cooling power electronics of refrigerant compressors |
EP4015829A1 (en) * | 2020-12-18 | 2022-06-22 | Siemens Energy Global GmbH & Co. KG | Radial turbomachine, in particular compressor |
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US20100239410A1 (en) * | 2007-09-27 | 2010-09-23 | Bahram Nikpour | Compressor |
US20100307191A1 (en) * | 2007-12-31 | 2010-12-09 | Johnson Controls Technology Company | Method and system for rotor cooling |
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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 |
BG110826A (en) * | 2010-12-28 | 2012-06-29 | Петров Росен | GASTERWORK ENGINE |
AU2012367336A1 (en) * | 2012-01-23 | 2014-08-21 | 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 |
KR20190044615A (en) * | 2016-08-25 | 2019-04-30 | 댄포스 아/에스 | Refrigerant compressor |
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US20100239410A1 (en) * | 2007-09-27 | 2010-09-23 | Bahram Nikpour | Compressor |
US20100307191A1 (en) * | 2007-12-31 | 2010-12-09 | Johnson Controls Technology Company | Method and system for rotor cooling |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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US11143193B2 (en) * | 2019-01-02 | 2021-10-12 | Danfoss A/S | Unloading device for HVAC compressor with mixed and radial compression stages |
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CN110986403B (en) | 2023-10-31 |
CN110986403A (en) | 2020-04-10 |
EP3633202B1 (en) | 2024-03-27 |
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