US20140064933A1 - Diffuser assembly comprising diffuser vanes pivoting about the leading edge - Google Patents
Diffuser assembly comprising diffuser vanes pivoting about the leading edge Download PDFInfo
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- US20140064933A1 US20140064933A1 US13/601,352 US201213601352A US2014064933A1 US 20140064933 A1 US20140064933 A1 US 20140064933A1 US 201213601352 A US201213601352 A US 201213601352A US 2014064933 A1 US2014064933 A1 US 2014064933A1
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- Prior art keywords
- diffuser
- leading edge
- diffuser assembly
- assembly
- rotation axis
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- 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
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- 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
Definitions
- compressor devices e.g., centrifugal compressors
- diffusers and diffuser vanes for a compressor device.
- Compressor devices use a diffuser assembly to convert kinetic energy of a working fluid into static pressure by slowing the velocity of the working fluid through an expanding volume region.
- An example of a diffuser assembly typically utilizes several diffuser vanes in circumferential arrangement about an impeller.
- variable diffuser vanes move to change the orientation of the leading edge and the trailing edge. This feature helps to tune operation of the compressor device.
- Known designs for variable diffuser vanes rotate about an axis that resides in the lower half, i.e., closer to the leading edge than the trailing edge of the diffuser vanes.
- variable diffuser vanes The location for the axis of rotation permits the trailing edge to sweep through large angles and, thus, enables better tuning and optimization of compressor performance.
- implementation of the conventional designs for variable diffuser vanes move (e.g., rotate) both the trailing edge and the leading edge with respect to the incoming working fluid. This feature can have a negative impact on the performance of the compressor.
- the change in position of the leading edge which results from the change in angular orientation of the diffuser vane, can cause the flow of the working fluid to prematurely separate from the surface of the diffuser vane, thus reducing the effectiveness of the variable diffuser vane to tune performance of the compressor device.
- This disclosure presents embodiments of a diffuser assembly that incorporates diffuser vanes with a trailing edge that changes position to improve flow performance of a compressor device.
- the diffuser vanes maintain the position of the leading edge relative to the orientation of the working fluid.
- these embodiments prevent pre-mature flow separation of the incoming working fluid from the surfaces of the diffuser vane. At least this feature can provide better control and optimization of compressor performance over a large flow range.
- FIG. 1 depicts a perspective view of an exemplary diffuser vane
- FIG. 2 depicts a detail view of the leading edge of the exemplary diffuser vane of FIG. 1 ;
- FIG. 3 depicts a top view of the exemplary diffuser vane of FIG. 1 ;
- FIG. 4 depicts a schematic view of an exemplary diffuser assembly that incorporates a plurality of diffuser vanes, e.g., the diffuser vane of FIGS. 1 and 2 ;
- FIG. 5 depicts a side, cross-section view of the diffuser assembly of FIG. 3 ;
- FIG. 6 depicts a perspective view of an exemplary compressor device that can incorporate a diffuser assembly, e.g., the diffuser assembly of FIGS. 4 and 5 .
- the discussion below focuses on improvements in diffuser and diffuser assembly design to realize better performance in compressor devices, e.g., centrifugal compressors.
- these improvements address issues that arise as a result of re-orientation in the angular position of diffuser vanes inside the diffuser assembly.
- embodiments of the proposed diffuser assembly allow the trailing edge to be positioned as desired but maintains the orientation of the leading edge on diffuser vanes relative to the direction of flow of a working fluid that flows past the diffuser vanes in the diffuser assembly.
- FIG. 1 illustrates a perspective view of a diffuser vane 100 .
- the diffuser vane 100 has a vane body 102 with a leading edge 104 and a trailing edge 106 .
- a chord length L defines the straight-line distance between the leading edge 104 and the trailing edge 106 .
- the vane body 102 has an aerodynamic shape (e.g., an airfoil) with a suction side surface 108 and a pressure side surface 110 identified relative to the orientation and angle of attack of the leading edge 104 relative to a flow F of a working fluid.
- the vane body 102 converges to a tip 112 with a rotation axis 114 .
- the tip 112 is round and/or has a curvilinear outer surface 116 defined by a radius R TIP that extends from a center axis 118 .
- the tip 112 exhibit a shape (e.g., a point) that maintains the aerodynamics of the diffuser body 102 .
- this disclosure also contemplates configurations of the tip 112 having less than optimal aerodynamic shapes (e.g., blunt shapes) as desired.
- the rotation axis 114 resides proximate the leading edge 104 and, for example, within 5% or less of the chord length L (as measured from the leading edge 104 ). Depending on the size and shape of the tip 112 , other exemplary locations for the rotation axis 114 can be found within an area that the radius R TIP defines about the center axis 118 . In one example, the rotation axis 114 is coaxial with the center axis 118 of the tip 112 .
- the diffuser vane 100 actuates about the rotation axis 114 .
- the diffuser vane 100 rotates to change the position of the trailing edge 106 from a first position 120 to a second position, identified by phantom lines and the numeral 122 .
- Such a change may accommodate changes in the direction of the flow F, e.g., from a first flow F 1 orientation to a second flow F 2 orientation.
- the leading edge 104 is secured on the rotation axis 114 to limit changes to the position of the leading edge 104 , e.g., as the trailing edge 106 moves between the first position 120 and the second position 122 .
- This feature maintains the orientation of the leading edge 104 with the second flow F 2 to reduce the likelihood of flow separation, while providing adequate adjustment of the trailing edge 106 to dictate changes in the performance, e.g., of a compressor device.
- FIG. 4 illustrates a schematic view of the diffuser vane 100 as part of a diffuser assembly 124 .
- the diffuser assembly 124 includes a vane array 126 that features a plurality of the diffuser vanes 100 in circumferential orientation about an impeller axis 128 .
- the leading edge 104 of the diffuser vanes 100 reside proximate a pivot boundary 130 , which is generally identified by the phantom circle having a center axis 132 .
- a plurality of pivot members 134 secure to the diffuser vanes 100 .
- the pivot members 134 maintain the position of leading edge 104 and, in one example, impart force to the diffuser vanes 100 to rotate the trailing edge 106 to different positions, e.g., between first position 120 and second position 122 shown in FIG. 3 .
- the pivot boundary 130 defines the circumferential location of the leading edges 104 of the diffuser vanes 100 , e.g., relative to the impeller axis 128 .
- Construction of the diffuser assembly 124 can affix the diffuser vane 100 to limit movement of the diffuser vanes 100 to rotation about the rotation axis 114 . This configuration minimizes displacement of the leading edge 104 relative to the pivot boundary 130 and relative to one another.
- the rotation axis 114 on the diffuser vanes 100 align with the pivot boundary 130 .
- one or more of the diffuser vanes 100 can be spaced apart from the pivot boundary 130 , e.g., aligned in a different circumferential location relative to the impeller axis 128 .
- the diffuser vanes 100 can be equally spaced apart from one another. Securing the diffuser vanes 100 in position affixes the angular spacing between the leading edge 104 of adjacent diffuser vanes 100 . Such construction can ensure consistent flow separation, e.g., by placing the leading edge 104 of the diffuser vanes 100 in a known location across the vane array 126 .
- the diffuser vanes 100 in the vane array 126 can rotate (or pivot) about the rotation axis 114 , e.g., to change the angular position of the trailing edge 106 .
- the angular position accommodates changes in the direction of the flow of the working fluid.
- the orientation of the leading edge 104 remains relatively unchanged with respect to the direction and/or orientation of the flow F of the working fluid. This feature provides a much more consistent point of impact for the working fluid on the leading edge 104 throughout the vane array 126 .
- the position of the leading edge 104 changes very little and, in turn, the diffuser vanes 100 in the diffuser assembly 124 exhibit minimal flow separation of the working fluid from the surfaces (e.g., suction side surface 108 and the pressure side surface 110 of FIG. 1 ) of the diffuser vanes 100 .
- Examples of the pivot members 134 can use a number of devices and mechanisms to rotatably secure the leading edge 104 of the diffuser vanes 100 .
- the pivot members 134 can be an integral extension of the diffuser vanes 100 or may be fabricated such as by welding or it may be a separately attached piece of material. Pins and bearings can insert, for example, into the diffuser vanes 100 along the rotation axis 114 . These elements provide a pivot and/or pivot point about which the diffuser vanes 100 can rotate.
- the diffuser assembly 124 can include a plurality of support devices, with one of the support devices secured to the bottom surface of each of the diffuser vanes 100 .
- Examples of the support devices can couple with actuators, linkages, and other mechanisms to impart movement to the diffuser vanes 100 in the vane array 126 .
- the support devices can align with the rotation axis 114 and/or be constructively offset to allow rotation of the diffuser vanes 100 about the rotation axis 114 as set forth herein.
- FIG. 5 depicts a side, cross-section view of the diffuser assembly 124 taken at line A-A of FIG. 4 .
- the diffuser assembly 124 includes one or more wall members (e.g., a first wall member 136 and a second wall member 138 ).
- the wall members 136 , 138 form a diffuser cavity 140 in which the array 126 of the diffuser vanes 100 is found.
- the pivot members 134 couple the diffuser vanes 100 to one of the wall members 136 , 138 . This configuration allows the diffuser vanes 100 to rotate about the rotation axis 114 to change the position of the trailing edge 104 on the diffuser vanes 100 .
- FIG. 6 depicts a perspective view of an example of a compressor device 200 that can incorporate a diffuser assembly (e.g., diffuser assembly 124 of FIGS. 4 and 5 ).
- the compressor 200 has an inlet 202 and a volute 204 that forms an outlet 206 .
- the compressor 200 also includes a drive unit 208 that rotates an impeller 210 to draw a working fluid (e.g., air) through the inlet 202 .
- the impeller 210 compresses the working fluid.
- the compressed working fluid flows into the volute 204 and out of the outlet 206 .
- Examples of the compressor 200 find use in a variety of settings and industries including automotive industries, electronics industries, aerospace industries, oil and gas industries, power generation industries, petrochemical industries, and the like.
- FIG. 7 illustrates a front view of the compressor device 200 in which some of the components are removed for clarity to illustrate one exemplary implementation of a diffuser assembly.
- the volute 204 forms at least a portion of the diffuser cavity (e.g., diffuser cavity 140 of FIG. 5 ).
- the array 126 resides in this portion of the volute 204 .
- the array 126 is upstream of the outlet 206 .
- rotation of the impeller 210 draws a working fluid into the inlet (e.g., inlet 202 of FIG. 6 ).
- the working fluid flows into the volute 204 , through the array 126 , and exits the outlet 206 .
- the configuration of the array 126 in the compressor 200 allows the diffuser vanes 100 to rotate about the leading edge 104 to change the position of the trailing edge 104 relative to the direction and other characteristics of the flow.
- Manipulation of the diffuser vanes 100 either as a group or individually, tunes the operation of the compressor device 200 to optimize various performance characteristics (e.g., flow parameters of the working fluid at the outlet 206 , energy usage, etc.).
- the drive unit 208 turns the impeller 210 to draw the working fluid through the inlet 202 .
- the impeller 210 pressurizes the working fluid.
- the pressurized working fluid passes through the diffuser assembly and, in particular, through channels between adjacent diffuser vanes 100 .
- the diffuser assembly slows the velocity of the working fluid.
- the diffuser assembly discharges into the volute 204 , which delivers the working fluid, e.g., to a downstream pipe that couples with the outlet 206 .
- the compressor device 200 undergoes extensive performance testing and tuning to optimize performance for a given application. Such tuning will modify operation, e.g., of the drive unit 208 , to adjust the speed of the impeller 210 , which effectively modifies flow parameters (e.g., pressure, flow rate, etc.) of the working fluid that exits the outlet 206 . Performance of the compressor device 200 will also change in response to the orientation of the diffuser vanes. In one example, tuning will involve adjusting the orientation of the diffuser vanes, which can modify, among other things, the pressure of the working fluid at the outlet 206 . Collectively, optimization of flow parameters will likely include incremental changes to several operating parameters of the compressor device 200 to achieve a collective combination, including orientation of the diffuser vanes, that allows the compressor device 200 to operate efficiently to achieve desired flow parameters.
- flow parameters e.g., pressure, flow rate, etc.
- Examples of the diffuser vanes 100 can be constructed of various materials and combinations, compositions, and derivations thereof. These materials include metals (e.g., steel, stainless steel, aluminum), high-strength plastics, and like composites. Material selection may depend on the type and composition of the working fluid. For example, working fluids with caustic properties may require that the diffuser vanes comprise relatively inert materials and/or materials that are chemically inactive with respect to the working fluid.
- Geometry for the diffuser vanes 100 can be determined as part of the design, build, and fitting of the compressor device 200 for the application.
- the geometry can include airfoil shapes, e.g., the shape shown in FIG. 1 ) for the vane body 102 , examples of which take the form of wings and blades and/or other forms that can generate lift.
- the diffuser vanes 100 can mount, e.g., to one of the wall members, using fasteners and fastening techniques that permit rotation of the diffuser vanes about the leading edge. Screws, bolts, pins, bearings, and like components can be used to maintain the position of the leading edge, while further allowing the trailing edge to change position as contemplated herein. These fasteners can secure to the wall members of the diffuser assembly, which can comprise pieces separate from the components of the compressor device or can integrate with existing hardware found in the compressor device.
- embodiments of the diffuser vane and diffuser assembly contemplated herein improve performance of compressors and related devices.
- the trailing edge of the diffuser vanes rotates about the leading edge, which effectively reduces flow separation of the working fluid from the surfaces of diffuser vanes.
- This feature improves performance of the compressor over a larger flow range because the leading edge remains oriented with the flow direction of the working fluid.
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Abstract
Embodiments of a diffuser assembly incorporate a diffuser vane with a trailing edge that changes position to improve flow performance of a compressor device. In one embodiment, the trailing edge rotates about the leading edge. This configuration maintains the position of the leading edge on the diffuser vanes relative to the orientation of the working fluid.
Description
- The subject matter disclosed herein relates to compressor devices (e.g., centrifugal compressors) and, in particular, to diffusers and diffuser vanes for a compressor device.
- Compressor devices (e.g., centrifugal compressors) use a diffuser assembly to convert kinetic energy of a working fluid into static pressure by slowing the velocity of the working fluid through an expanding volume region. An example of a diffuser assembly typically utilizes several diffuser vanes in circumferential arrangement about an impeller. The design (e.g., shapes and sizes) of the diffuser vanes, in combination with the preferred orientation of the leading edge and the trailing edge of the diffuser vanes with respect to the flow of the working fluid, often determine how the diffuser vanes are affixed in the diffuser assembly.
- To add further improvement and flexibility to the design, some examples of a diffuser assembly incorporate variable diffuser vanes. These types of diffuser vanes move to change the orientation of the leading edge and the trailing edge. This feature helps to tune operation of the compressor device. Known designs for variable diffuser vanes rotate about an axis that resides in the lower half, i.e., closer to the leading edge than the trailing edge of the diffuser vanes.
- The location for the axis of rotation permits the trailing edge to sweep through large angles and, thus, enables better tuning and optimization of compressor performance. However, although use of these variable diffuser vanes can improve performance, implementation of the conventional designs for variable diffuser vanes move (e.g., rotate) both the trailing edge and the leading edge with respect to the incoming working fluid. This feature can have a negative impact on the performance of the compressor. The change in position of the leading edge, which results from the change in angular orientation of the diffuser vane, can cause the flow of the working fluid to prematurely separate from the surface of the diffuser vane, thus reducing the effectiveness of the variable diffuser vane to tune performance of the compressor device.
- This disclosure presents embodiments of a diffuser assembly that incorporates diffuser vanes with a trailing edge that changes position to improve flow performance of a compressor device. The diffuser vanes, however, maintain the position of the leading edge relative to the orientation of the working fluid. When implemented, e.g., in a compressor device, these embodiments prevent pre-mature flow separation of the incoming working fluid from the surfaces of the diffuser vane. At least this feature can provide better control and optimization of compressor performance over a large flow range.
- Reference is now made briefly to the accompanying drawings, in which:
-
FIG. 1 depicts a perspective view of an exemplary diffuser vane; -
FIG. 2 depicts a detail view of the leading edge of the exemplary diffuser vane ofFIG. 1 ; -
FIG. 3 depicts a top view of the exemplary diffuser vane ofFIG. 1 ; -
FIG. 4 depicts a schematic view of an exemplary diffuser assembly that incorporates a plurality of diffuser vanes, e.g., the diffuser vane ofFIGS. 1 and 2 ; -
FIG. 5 depicts a side, cross-section view of the diffuser assembly ofFIG. 3 ; and -
FIG. 6 depicts a perspective view of an exemplary compressor device that can incorporate a diffuser assembly, e.g., the diffuser assembly ofFIGS. 4 and 5 . - Where applicable like reference characters designate identical or corresponding components and units throughout the several views, which are not to scale unless otherwise indicated.
- Broadly, the discussion below focuses on improvements in diffuser and diffuser assembly design to realize better performance in compressor devices, e.g., centrifugal compressors. In one aspect, these improvements address issues that arise as a result of re-orientation in the angular position of diffuser vanes inside the diffuser assembly. As set forth below, embodiments of the proposed diffuser assembly allow the trailing edge to be positioned as desired but maintains the orientation of the leading edge on diffuser vanes relative to the direction of flow of a working fluid that flows past the diffuser vanes in the diffuser assembly.
-
FIG. 1 illustrates a perspective view of adiffuser vane 100. Thediffuser vane 100 has avane body 102 with a leadingedge 104 and atrailing edge 106. A chord length L defines the straight-line distance between the leadingedge 104 and thetrailing edge 106. Thevane body 102 has an aerodynamic shape (e.g., an airfoil) with asuction side surface 108 and apressure side surface 110 identified relative to the orientation and angle of attack of the leadingedge 104 relative to a flow F of a working fluid. At the leadingedge 104, thevane body 102 converges to atip 112 with arotation axis 114. - As shown in the detail of
FIG. 2 , thetip 112 is round and/or has a curvilinearouter surface 116 defined by a radius RTIP that extends from acenter axis 118. Other examples thetip 112 exhibit a shape (e.g., a point) that maintains the aerodynamics of thediffuser body 102. However, this disclosure also contemplates configurations of thetip 112 having less than optimal aerodynamic shapes (e.g., blunt shapes) as desired. - The
rotation axis 114 resides proximate the leadingedge 104 and, for example, within 5% or less of the chord length L (as measured from the leading edge 104). Depending on the size and shape of thetip 112, other exemplary locations for therotation axis 114 can be found within an area that the radius RTIP defines about thecenter axis 118. In one example, therotation axis 114 is coaxial with thecenter axis 118 of thetip 112. - As best shown in
FIG. 3 , thediffuser vane 100 actuates about therotation axis 114. In one example, thediffuser vane 100 rotates to change the position of thetrailing edge 106 from afirst position 120 to a second position, identified by phantom lines and thenumeral 122. Such a change may accommodate changes in the direction of the flow F, e.g., from a first flow F1 orientation to a second flow F2 orientation. However, despite the relatively large angular displacement of thetrailing edge 106 that occurs, the leadingedge 104 is secured on therotation axis 114 to limit changes to the position of the leadingedge 104, e.g., as thetrailing edge 106 moves between thefirst position 120 and thesecond position 122. This feature maintains the orientation of the leadingedge 104 with the second flow F2 to reduce the likelihood of flow separation, while providing adequate adjustment of thetrailing edge 106 to dictate changes in the performance, e.g., of a compressor device. -
FIG. 4 illustrates a schematic view of thediffuser vane 100 as part of adiffuser assembly 124. In the example ofFIG. 4 , thediffuser assembly 124 includes avane array 126 that features a plurality of thediffuser vanes 100 in circumferential orientation about an impeller axis 128. The leadingedge 104 of thediffuser vanes 100 reside proximate apivot boundary 130, which is generally identified by the phantom circle having a center axis 132. In one embodiment, a plurality ofpivot members 134 secure to thediffuser vanes 100. Thepivot members 134 maintain the position of leadingedge 104 and, in one example, impart force to thediffuser vanes 100 to rotate thetrailing edge 106 to different positions, e.g., betweenfirst position 120 andsecond position 122 shown inFIG. 3 . - The
pivot boundary 130 defines the circumferential location of theleading edges 104 of thediffuser vanes 100, e.g., relative to the impeller axis 128. Construction of thediffuser assembly 124 can affix thediffuser vane 100 to limit movement of thediffuser vanes 100 to rotation about therotation axis 114. This configuration minimizes displacement of the leadingedge 104 relative to thepivot boundary 130 and relative to one another. In one example, therotation axis 114 on the diffuser vanes 100 align with thepivot boundary 130. However, in other examples, one or more of thediffuser vanes 100 can be spaced apart from thepivot boundary 130, e.g., aligned in a different circumferential location relative to the impeller axis 128. As shown inFIG. 4 , thediffuser vanes 100 can be equally spaced apart from one another. Securing thediffuser vanes 100 in position affixes the angular spacing between the leadingedge 104 ofadjacent diffuser vanes 100. Such construction can ensure consistent flow separation, e.g., by placing the leadingedge 104 of thediffuser vanes 100 in a known location across thevane array 126. - As mentioned above, during operation of the
diffuser assembly 124, the diffuser vanes 100 in thevane array 126 can rotate (or pivot) about therotation axis 114, e.g., to change the angular position of thetrailing edge 106. The angular position accommodates changes in the direction of the flow of the working fluid. The orientation of the leadingedge 104, however, remains relatively unchanged with respect to the direction and/or orientation of the flow F of the working fluid. This feature provides a much more consistent point of impact for the working fluid on the leadingedge 104 throughout thevane array 126. Thus, despite the change in position of thetrailing edge 106, the position of the leadingedge 104 changes very little and, in turn, the diffuser vanes 100 in thediffuser assembly 124 exhibit minimal flow separation of the working fluid from the surfaces (e.g.,suction side surface 108 and thepressure side surface 110 ofFIG. 1 ) of thediffuser vanes 100. - Examples of the
pivot members 134 can use a number of devices and mechanisms to rotatably secure theleading edge 104 of the diffuser vanes 100. Thepivot members 134 can be an integral extension of thediffuser vanes 100 or may be fabricated such as by welding or it may be a separately attached piece of material. Pins and bearings can insert, for example, into thediffuser vanes 100 along therotation axis 114. These elements provide a pivot and/or pivot point about which thediffuser vanes 100 can rotate. In one example, thediffuser assembly 124 can include a plurality of support devices, with one of the support devices secured to the bottom surface of each of the diffuser vanes 100. Examples of the support devices can couple with actuators, linkages, and other mechanisms to impart movement to thediffuser vanes 100 in thevane array 126. The support devices can align with therotation axis 114 and/or be constructively offset to allow rotation of thediffuser vanes 100 about therotation axis 114 as set forth herein. -
FIG. 5 depicts a side, cross-section view of thediffuser assembly 124 taken at line A-A ofFIG. 4 . Thediffuser assembly 124 includes one or more wall members (e.g., afirst wall member 136 and a second wall member 138). Thewall members diffuser cavity 140 in which thearray 126 of thediffuser vanes 100 is found. In one embodiment, thepivot members 134 couple thediffuser vanes 100 to one of thewall members diffuser vanes 100 to rotate about therotation axis 114 to change the position of the trailingedge 104 on the diffuser vanes 100. -
FIG. 6 depicts a perspective view of an example of acompressor device 200 that can incorporate a diffuser assembly (e.g.,diffuser assembly 124 ofFIGS. 4 and 5 ). Thecompressor 200 has aninlet 202 and avolute 204 that forms anoutlet 206. Thecompressor 200 also includes adrive unit 208 that rotates animpeller 210 to draw a working fluid (e.g., air) through theinlet 202. Theimpeller 210 compresses the working fluid. The compressed working fluid flows into thevolute 204 and out of theoutlet 206. Examples of thecompressor 200 find use in a variety of settings and industries including automotive industries, electronics industries, aerospace industries, oil and gas industries, power generation industries, petrochemical industries, and the like. -
FIG. 7 illustrates a front view of thecompressor device 200 in which some of the components are removed for clarity to illustrate one exemplary implementation of a diffuser assembly. Thevolute 204 forms at least a portion of the diffuser cavity (e.g.,diffuser cavity 140 ofFIG. 5 ). Thearray 126 resides in this portion of thevolute 204. In one example, thearray 126 is upstream of theoutlet 206 During operation of thecompressor 200, rotation of theimpeller 210 draws a working fluid into the inlet (e.g.,inlet 202 ofFIG. 6 ). The working fluid flows into thevolute 204, through thearray 126, and exits theoutlet 206. As discussed above, the configuration of thearray 126 in thecompressor 200 allows thediffuser vanes 100 to rotate about theleading edge 104 to change the position of the trailingedge 104 relative to the direction and other characteristics of the flow. Manipulation of thediffuser vanes 100, either as a group or individually, tunes the operation of thecompressor device 200 to optimize various performance characteristics (e.g., flow parameters of the working fluid at theoutlet 206, energy usage, etc.). - Referring now also to
FIGS. 1 , 2, 3, 4, 5, and 6, in operation, thedrive unit 208 turns theimpeller 210 to draw the working fluid through theinlet 202. Theimpeller 210 pressurizes the working fluid. The pressurized working fluid passes through the diffuser assembly and, in particular, through channels betweenadjacent diffuser vanes 100. At a high level, the diffuser assembly slows the velocity of the working fluid. The diffuser assembly discharges into thevolute 204, which delivers the working fluid, e.g., to a downstream pipe that couples with theoutlet 206. - Generally the
compressor device 200 undergoes extensive performance testing and tuning to optimize performance for a given application. Such tuning will modify operation, e.g., of thedrive unit 208, to adjust the speed of theimpeller 210, which effectively modifies flow parameters (e.g., pressure, flow rate, etc.) of the working fluid that exits theoutlet 206. Performance of thecompressor device 200 will also change in response to the orientation of the diffuser vanes. In one example, tuning will involve adjusting the orientation of the diffuser vanes, which can modify, among other things, the pressure of the working fluid at theoutlet 206. Collectively, optimization of flow parameters will likely include incremental changes to several operating parameters of thecompressor device 200 to achieve a collective combination, including orientation of the diffuser vanes, that allows thecompressor device 200 to operate efficiently to achieve desired flow parameters. - Examples of the
diffuser vanes 100 can be constructed of various materials and combinations, compositions, and derivations thereof. These materials include metals (e.g., steel, stainless steel, aluminum), high-strength plastics, and like composites. Material selection may depend on the type and composition of the working fluid. For example, working fluids with caustic properties may require that the diffuser vanes comprise relatively inert materials and/or materials that are chemically inactive with respect to the working fluid. - Geometry for the
diffuser vanes 100 can be determined as part of the design, build, and fitting of thecompressor device 200 for the application. The geometry can include airfoil shapes, e.g., the shape shown inFIG. 1 ) for thevane body 102, examples of which take the form of wings and blades and/or other forms that can generate lift. In one embodiment, thediffuser vanes 100 can mount, e.g., to one of the wall members, using fasteners and fastening techniques that permit rotation of the diffuser vanes about the leading edge. Screws, bolts, pins, bearings, and like components can be used to maintain the position of the leading edge, while further allowing the trailing edge to change position as contemplated herein. These fasteners can secure to the wall members of the diffuser assembly, which can comprise pieces separate from the components of the compressor device or can integrate with existing hardware found in the compressor device. - In view of the foregoing discussion, embodiments of the diffuser vane and diffuser assembly contemplated herein improve performance of compressors and related devices. For example, and as set forth above, the trailing edge of the diffuser vanes rotates about the leading edge, which effectively reduces flow separation of the working fluid from the surfaces of diffuser vanes. This feature improves performance of the compressor over a larger flow range because the leading edge remains oriented with the flow direction of the working fluid.
- As used herein, an element or function recited in the singular and proceeded with the word “a” or “an” should be understood as not excluding plural said elements or functions, unless such exclusion is explicitly recited. Furthermore, references to “one embodiment” of the claimed invention should not be interpreted as excluding the existence of additional embodiments that also incorporate the recited features.
- This written description uses examples to disclose the invention, including the best mode, and also to enable any person skilled in the art to practice the invention, including making and using any devices or systems and performing any incorporated methods. The patentable scope of the invention is defined by the claims, and may include other examples that occur to those skilled in the art. Such other examples are intended to be within the scope of the claims if they have structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal language of the claims.
Claims (20)
1. A diffuser assembly for a compressor, said diffuser assembly comprising:
a wall member;
a pivot element coupled with the wall member; and
a diffuser vane coupled with the pivot element, the diffuser vane having a leading edge, a trailing edge, and a rotation axis proximate the leading edge about which rotates the trailing edge of the diffuser vane.
2. The diffuser assembly of claim 1 , wherein the pivot element aligns with the rotation axis.
3. The diffuser assembly of claim 1 , wherein the diffuser vane has an airfoil shape that converges at the leading edge to a tip with a center axis and a curvilinear outer surface.
4. The diffuser assembly of claim 3 , wherein the curvilinear outer surface is defined by a radius from the center axis, and wherein the rotation axis is found within an area defined by the radius.
5. The diffuser assembly of claim 3 , wherein the rotation axis is coaxial with the center axis of the tip.
6. The diffuser assembly of claim 1 , wherein the rotation axis resides within 5% or less of a chord length measured from the leading edge, and wherein the chord length measures the straight-line distance between the leading edge and the trailing edge.
7. The diffuser assembly of claim 1 , wherein the rotation axis aligns with a pivot boundary that defines the circumferential location of the leading edge relative to an impeller of the compressor.
8. The diffuser assembly of claim 7 , wherein the pivot element prevents translation of the leading edge from the pivot boundary when the trailing edge rotates between a first position and a second position.
9. The diffuser assembly of claim 7 , wherein the diffuser vane is part of an array of diffuser vanes that circumscribes the impeller.
10. A diffuser assembly for a compressor, said diffuser assembly comprising:
a wall member;
a diffuser vane having a leading edge secured to the wall member to permit rotation of a trailing edge about the leading edge between a first position and a second position that is angularly offset from the first position.
11. The diffuser assembly of claim 10 , wherein the diffuser vane has an airfoil shape that converges at the leading edge to a tip with a center axis and a curvilinear outer surface.
12. The diffuser assembly of claim 11 , wherein the curvilinear outer surface is defined by a radius from the center axis, and wherein the diffuser vane rotates about a rotation axis that found within an area defined by the radius.
13. The diffuser assembly of claim 11 , wherein the rotation axis is coaxial with the center axis of the tip.
14. The diffuser assembly of claim 10 , wherein the diffuser vane has a rotation axis that resides within 5% or less of a chord length measured from the leading edge, and wherein the chord length measures the straight-line distance between the leading edge and the trailing edge.
15. The diffuser assembly of claim 10 , wherein the leading edge has a center axis that aligns with a pivot boundary that defines the circumferential location of the leading edge relative to an impeller axis.
16. A compressor, comprising:
a diffuser assembly comprising a wall member and an array of diffuser vanes having a leading edge and a trailing edge, wherein the diffuser vanes secure to the wall member at the leading edge to permit rotation of the trailing edge about the leading edge between a first position and a second position that is angularly offset from the first position.
17. The diffuser assembly of claim 16 , further comprising an impeller with an impeller axis, wherein the array of diffuser vanes circumscribe the impeller, and wherein the leading edge has a center axis that aligns with a pivot boundary that defines a circumferential location of the leading edge relative to the impeller axis.
18. The diffuser assembly of claim 16 , wherein the diffuser vane has an airfoil shape that converges at the leading edge to a tip with a center axis and a curvilinear outer surface, wherein the curvilinear outer surface is defined by a radius from the center axis, and wherein the diffuser vane rotates about a rotation axis that found within an area defined by the radius.
19. The diffuser assembly of claim 18 , wherein the rotation axis is coaxial with the center axis of the tip.
20. The diffuser assembly of claim 18 , wherein the rotation axis resides within 5% or less of a chord length measured from the leading edge, wherein the chord length measures the straight-line distance between the leading edge and the trailing edge.
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/601,352 US20140064933A1 (en) | 2012-08-31 | 2012-08-31 | Diffuser assembly comprising diffuser vanes pivoting about the leading edge |
PCT/US2013/056328 WO2014035806A1 (en) | 2012-08-31 | 2013-08-23 | Diffuser assembly comprising diffuser vanes pivoting about the leading edge |
CN201380051296.3A CN104755768A (en) | 2012-08-31 | 2013-08-23 | Diffuser assembly comprising diffuser vanes pivoting about the leading edge |
BR112015004608A BR112015004608A2 (en) | 2012-08-31 | 2013-08-23 | diffuser assembly comprising diffuser blades rotating the front edge. |
EP13759369.5A EP2890898A1 (en) | 2012-08-31 | 2013-08-23 | Diffuser assembly comprising diffuser vanes pivoting about the leading edge |
RU2015107885A RU2015107885A (en) | 2012-08-31 | 2013-08-23 | A diffuser comprising diffuser vanes rotatable around an input edge |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/601,352 US20140064933A1 (en) | 2012-08-31 | 2012-08-31 | Diffuser assembly comprising diffuser vanes pivoting about the leading edge |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140064933A1 true US20140064933A1 (en) | 2014-03-06 |
Family
ID=49118797
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/601,352 Abandoned US20140064933A1 (en) | 2012-08-31 | 2012-08-31 | Diffuser assembly comprising diffuser vanes pivoting about the leading edge |
Country Status (6)
Country | Link |
---|---|
US (1) | US20140064933A1 (en) |
EP (1) | EP2890898A1 (en) |
CN (1) | CN104755768A (en) |
BR (1) | BR112015004608A2 (en) |
RU (1) | RU2015107885A (en) |
WO (1) | WO2014035806A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11421695B2 (en) * | 2018-01-19 | 2022-08-23 | Concepts Nrec, Llc | Turbomachines with decoupled collectors |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN115199587A (en) * | 2022-09-07 | 2022-10-18 | 中国核动力研究设计院 | Diffuser for compressor and compressor |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4531356A (en) * | 1981-06-15 | 1985-07-30 | The Garrett Corporation | Intake vortex whistle silencing apparatus and methods |
US20100150701A1 (en) * | 2007-06-26 | 2010-06-17 | Borgwarner Inc. | Variable geometry turbocharger |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1307113A (en) * | 1961-11-29 | 1962-10-19 | L J Gilchrist & Co Engineers L | Improvement in blowers or centrifugal vane wheels |
US4770605A (en) * | 1981-02-16 | 1988-09-13 | Mitsubishi Jukogyo Kabushiki Kaisha | Diffuser device in a centrifugal compressor and method for manufacturing the same |
DE102007023915B4 (en) * | 2006-06-09 | 2019-07-04 | Borgwarner Inc. | Turbocharger and compressor for turbocharger |
-
2012
- 2012-08-31 US US13/601,352 patent/US20140064933A1/en not_active Abandoned
-
2013
- 2013-08-23 BR BR112015004608A patent/BR112015004608A2/en not_active IP Right Cessation
- 2013-08-23 EP EP13759369.5A patent/EP2890898A1/en not_active Withdrawn
- 2013-08-23 RU RU2015107885A patent/RU2015107885A/en not_active Application Discontinuation
- 2013-08-23 CN CN201380051296.3A patent/CN104755768A/en active Pending
- 2013-08-23 WO PCT/US2013/056328 patent/WO2014035806A1/en active Application Filing
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4531356A (en) * | 1981-06-15 | 1985-07-30 | The Garrett Corporation | Intake vortex whistle silencing apparatus and methods |
US20100150701A1 (en) * | 2007-06-26 | 2010-06-17 | Borgwarner Inc. | Variable geometry turbocharger |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11421695B2 (en) * | 2018-01-19 | 2022-08-23 | Concepts Nrec, Llc | Turbomachines with decoupled collectors |
Also Published As
Publication number | Publication date |
---|---|
BR112015004608A2 (en) | 2018-04-17 |
EP2890898A1 (en) | 2015-07-08 |
RU2015107885A (en) | 2016-10-20 |
WO2014035806A1 (en) | 2014-03-06 |
CN104755768A (en) | 2015-07-01 |
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