US20140030099A1 - Pump impeller - Google Patents
Pump impeller Download PDFInfo
- Publication number
- US20140030099A1 US20140030099A1 US13/559,998 US201213559998A US2014030099A1 US 20140030099 A1 US20140030099 A1 US 20140030099A1 US 201213559998 A US201213559998 A US 201213559998A US 2014030099 A1 US2014030099 A1 US 2014030099A1
- Authority
- US
- United States
- Prior art keywords
- vanes
- impeller
- backing plate
- inlet
- inlet shroud
- 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.)
- Abandoned
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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
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2205—Conventional flow pattern
- F04D29/2222—Construction and assembly
Definitions
- This disclosure relates to impellers for fluid pumps.
- Automobiles and other vehicles use pumps to pressurize fluids, increase the speed of fluids, or both.
- An impeller is provided, and is rotatable about an axis.
- the impeller includes an inlet shroud and a backing plate.
- An inlet orifice is defined by the inlet shroud, and a plurality of outlet orifices are located radially outward of the inlet orifice.
- the impeller also includes a plurality of vanes, which are disposed between the inlet shroud and the backing plate.
- the plurality of vanes are formed integrally as one-piece with the inlet shroud.
- FIG. 1 is a schematic, isometric view of an impeller, viewed from an inlet side;
- FIG. 2 is a schematic, exploded, isometric view of the impeller of FIG. 1 , viewed from a back side;
- FIG. 3 is a schematic, isometric view of the assembled impeller of FIGS. 1 and 2 , viewed from the back side;
- FIG. 4 is a schematic, exploded, isometric view of an alternative impeller, viewed from a back side;
- FIG. 5 is a schematic, isometric view of the assembled impeller of FIG. 4 ;
- FIG. 6 is a schematic graph illustrating operational results of the impeller shown in FIGS. 1-3 compared with a different impeller.
- FIG. 1 an impeller 10 .
- a pump (not shown), such as a centrifugal pump, may use the impeller 10 to increase the pressure and flow of a working fluid (not shown).
- the impeller 10 is operatively attached to a driveshaft 12 and rotatable about an axis 14 .
- the driveshaft 12 rotates the impeller 10
- the working fluid is pumped by accelerating the working fluid outward from the axis 14 .
- the path of the working fluid is illustrated in FIG. 1 by inlet flow 16 and outlet flow 18 .
- the kinetic energy of the impeller 10 is converted into pressure as outward movement of the working fluid is confined by a pump casing (not shown) radially outward of the impeller 10 .
- the impeller 10 In the view shown in FIG. 1 , the impeller 10 generally operates while rotating in the counterclockwise direction.
- the impeller 10 includes an inlet shroud 20 and a backing plate 22 .
- a plurality of vanes 24 are disposed between the inlet shroud 20 and the backing plate 22 . These vanes 24 transfer motion of the impeller 10 into motion or pressure within the working fluid.
- the vanes 24 are formed integrally as one-piece with the inlet shroud 20 , such that the vanes 24 are not separately or subsequently attached to the inlet shroud 20 .
- the inlet flow 16 enters an inlet orifice 26 defined by the inlet shroud 20 .
- the inlet orifice 26 is substantially co-axial with the driveshaft 12 and the axis 14 .
- the inlet flow 16 may be a substantially contiguous flow or stream of the working fluid.
- the outlet flow 18 exits through a plurality of outlet orifices 28 , which are radially outward of the inlet orifice 26 from the axis 14 .
- the impeller 10 may also be defined by a draft angle 30 formed on the vanes 24 .
- the draft angle 30 opens from the inlet shroud 20 to the backing plate 22 .
- a first distance 31 between a base end 32 , which is proximate to the inlet shroud 20 , of the vanes 24 is smaller than a second distance 33 between a plate end 34 , which is distal to the inlet shroud 20 , of the vanes 24 .
- the flow of working fluid As the inlet flow 16 enters the impeller 10 , the flow of working fluid is generally parallel with the axis 14 . However, as the outlet flow 18 exits the impeller 10 , the flow of working fluid is generally perpendicular to the axis 14 (i.e., the flow is radial). This change in direction may be referred to as “turning” the working fluid. Because of the draft angle 30 , the first distance 31 between the vanes 24 is smaller than the second distance 33 . Therefore, as the working fluid turns, it is moving toward the second distance 33 and is moving from tighter space to freer space during the turn. Contrarily, if the draft angle 30 were reversed, the working fluid would be more constricted as it turns from axial flow to radial flow.
- the inlet shroud 20 and the vanes 24 may be formed as one-piece by a single-action mold.
- the single-action mold would separate from the inlet shroud 20 and the vanes 24 substantially in the direction of the axis 14 .
- FIG. 2 shows an exploded isometric view of the impeller 10 , shown from a back side, which is generally opposite of the view shown in FIG. 1 .
- FIG. 3 shows the impeller 10 in an assembled state from the same view as FIG. 2 .
- the driveshaft 12 is removed from view in both FIG. 2 and FIG. 3 .
- the impeller 10 also includes a plurality of slots 36 formed in the backing plate 22 .
- a plurality of tabs 38 are formed on the plate end 34 of the vanes 24 .
- the tabs 38 are configured to mate with the slots 36 . Therefore, the backing plate 22 and the vanes 24 are mated together, which may assist in carrying loads between the two components.
- the tabs 38 and the slots 36 may mate through a slip fit, an interference fit (such as by snapping into the slots 36 ), or by a deformation fit.
- FIG. 4 shows an exploded isometric view of the impeller 110 , from a back side viewpoint.
- FIG. 5 shows an isometric view of the assembled impeller 110 .
- the impeller 110 and the impeller 10 shown in FIGS. 1-3 may operate in substantially identical fashion.
- the impeller 110 includes an inlet shroud 120 and a backing plate 122 .
- a plurality of vanes 124 are disposed between the inlet shroud 120 and the backing plate 122 . These vanes 124 transfer motion of the impeller 110 into motion or pressure within the working fluid.
- the vanes 124 are formed integrally as one-piece with the inlet shroud 120 , such that the vanes 124 are not separately or subsequently attached to the inlet shroud 120 .
- Inlet flow of the working fluid enters an inlet orifice 126 defined by the inlet shroud 120 .
- Outlet flow of the working fluid exits through a plurality of outlet orifices 128 , which are radially outward of the inlet orifice 126 .
- the impeller 110 may also be defined by a draft angle formed on the vanes 124 .
- the draft angle opens from the inlet shroud 120 to the backing plate 122 , such that a base end 132 of the vanes 124 is wider than a plate end 134 of the vanes 124 .
- the inlet shroud 120 and the vanes 124 may be formed as one-piece by a single-action mold.
- the impeller 110 also includes a plurality of slots 136 formed in the backing plate 122 .
- a plurality of tabs 138 are formed on the end of the vanes 124 , and are configured to mate with the slots 136 .
- the impeller 110 further includes an annular ring 140 formed on the opposing side of the backing plate 122 from the vanes 124 .
- the annual ring 140 connects the plurality of tabs 138 .
- a channel 142 may be formed in the backing plate 122 .
- the channel 142 may house the annular ring 140 , such that the annular ring 140 is flush with the backing plate 122 .
- the annular ring 140 may alternatively be formed on the backing plate 122 without the channel 142 .
- the tabs 138 are inserted into the slots 136 in the backing plate 122 . Then, the annular ring 140 is overmolded onto the backing plate 122 and the plurality of tabs 138 , such that formation of the annular ring 140 locks the tabs 138 to the backing plate 122 .
- FIG. 6 there is shown a schematic graph 200 , which illustrates operational results of the impeller 10 shown in FIGS. 1-3 compared with a different, comparison impeller.
- the graph 200 shows the improved performance of the impeller 10 over the comparison impeller.
- the comparison impeller does not have the draft angle 30 shown in FIGS. 1-3 .
- the comparison impeller may have an opposite draft angle (opening from a backing plate toward an inlet shroud) or may be a foil impeller, which has vanes that are integral with, and bent outward from, the backing plate. Therefore, as the working fluid turns from axial flow to radial flow in the comparison impeller, the fluid becomes more constricted.
- the first distance 31 is smaller than the second distance 33 , such that the working fluid is less constricted as it turns from axial flow to radial flow.
- Flow rate values 202 are shown on the left side, in liters per minute. Hydraulic efficiency 204 , in percentage, is shown on the right side. All values shown are illustrative, exemplary, and demonstrative, and the values are in no way limiting of the invention. To derive the data shown in the chart 200 , the impeller 10 and the comparison impeller were simulated as operating at the same speeds, approximately 8750 revolutions per minute, and with the same working fluid, water-based coolant.
- a bar 210 shows the flow rate of the impeller 10
- a bar 212 shows the flow rate of the comparison impeller. As shown in the chart 200 , the impeller 10 yielded a higher flow rate over the comparison impeller.
- a bar 214 shows the hydraulic efficiency of the impeller 10
- a bar 216 shows the hydraulic efficiency of the comparison impeller. As shown in the chart 200 , the impeller 10 had improved hydraulic efficiency relative to the comparison impeller.
Abstract
Description
- This disclosure relates to impellers for fluid pumps.
- Automobiles and other vehicles use pumps to pressurize fluids, increase the speed of fluids, or both.
- An impeller is provided, and is rotatable about an axis. The impeller includes an inlet shroud and a backing plate. An inlet orifice is defined by the inlet shroud, and a plurality of outlet orifices are located radially outward of the inlet orifice.
- The impeller also includes a plurality of vanes, which are disposed between the inlet shroud and the backing plate. The plurality of vanes are formed integrally as one-piece with the inlet shroud.
- The above features and advantages, and other features and advantages, of the present invention are readily apparent from the following detailed description of some of the best modes and other embodiments for carrying out the invention, which is defined solely by the appended claims, when taken in connection with the accompanying drawings.
-
FIG. 1 is a schematic, isometric view of an impeller, viewed from an inlet side; -
FIG. 2 is a schematic, exploded, isometric view of the impeller ofFIG. 1 , viewed from a back side; -
FIG. 3 is a schematic, isometric view of the assembled impeller ofFIGS. 1 and 2 , viewed from the back side; -
FIG. 4 is a schematic, exploded, isometric view of an alternative impeller, viewed from a back side; -
FIG. 5 is a schematic, isometric view of the assembled impeller ofFIG. 4 ; and -
FIG. 6 is a schematic graph illustrating operational results of the impeller shown inFIGS. 1-3 compared with a different impeller. - Referring to the drawings, wherein like reference numbers correspond to like or similar components wherever possible throughout the several figures, there is shown in
FIG. 1 animpeller 10. A pump (not shown), such as a centrifugal pump, may use theimpeller 10 to increase the pressure and flow of a working fluid (not shown). - While the present invention may be described with respect to automotive applications, those skilled in the art will recognize the broader applicability of the invention. Those having ordinary skill in the art will recognize that terms such as “above,” “below,” “upward,” “downward,” et cetera, are used descriptively of the figures, and do not represent limitations on the scope of the invention, as defined by the appended claims. Any numerical designations, such as “first” or “second” are illustrative only and are not intended to limit the scope of the invention in any way.
- The
impeller 10 is operatively attached to adriveshaft 12 and rotatable about anaxis 14. As thedriveshaft 12 rotates theimpeller 10, the working fluid is pumped by accelerating the working fluid outward from theaxis 14. The path of the working fluid is illustrated inFIG. 1 byinlet flow 16 andoutlet flow 18. The kinetic energy of theimpeller 10 is converted into pressure as outward movement of the working fluid is confined by a pump casing (not shown) radially outward of theimpeller 10. In the view shown inFIG. 1 , theimpeller 10 generally operates while rotating in the counterclockwise direction. - The
impeller 10 includes aninlet shroud 20 and abacking plate 22. A plurality ofvanes 24 are disposed between theinlet shroud 20 and thebacking plate 22. These vanes 24 transfer motion of theimpeller 10 into motion or pressure within the working fluid. Thevanes 24 are formed integrally as one-piece with theinlet shroud 20, such that thevanes 24 are not separately or subsequently attached to theinlet shroud 20. - The
inlet flow 16 enters aninlet orifice 26 defined by theinlet shroud 20. Theinlet orifice 26 is substantially co-axial with thedriveshaft 12 and theaxis 14. Theinlet flow 16 may be a substantially contiguous flow or stream of the working fluid. The outlet flow 18 exits through a plurality ofoutlet orifices 28, which are radially outward of theinlet orifice 26 from theaxis 14. - The
impeller 10 may also be defined by adraft angle 30 formed on thevanes 24. Thedraft angle 30 opens from theinlet shroud 20 to thebacking plate 22. Afirst distance 31 between abase end 32, which is proximate to theinlet shroud 20, of thevanes 24 is smaller than asecond distance 33 between aplate end 34, which is distal to theinlet shroud 20, of thevanes 24. - As the
inlet flow 16 enters theimpeller 10, the flow of working fluid is generally parallel with theaxis 14. However, as theoutlet flow 18 exits theimpeller 10, the flow of working fluid is generally perpendicular to the axis 14 (i.e., the flow is radial). This change in direction may be referred to as “turning” the working fluid. Because of thedraft angle 30, thefirst distance 31 between thevanes 24 is smaller than thesecond distance 33. Therefore, as the working fluid turns, it is moving toward thesecond distance 33 and is moving from tighter space to freer space during the turn. Contrarily, if thedraft angle 30 were reversed, the working fluid would be more constricted as it turns from axial flow to radial flow. - In the
impeller 10 shown, theinlet shroud 20 and thevanes 24 may be formed as one-piece by a single-action mold. The single-action mold would separate from theinlet shroud 20 and thevanes 24 substantially in the direction of theaxis 14. - Referring also to
FIG. 2 andFIG. 3 , and with continued reference toFIG. 1 , there is shown another view of theimpeller 10.FIG. 2 shows an exploded isometric view of theimpeller 10, shown from a back side, which is generally opposite of the view shown inFIG. 1 .FIG. 3 shows theimpeller 10 in an assembled state from the same view asFIG. 2 . Thedriveshaft 12 is removed from view in bothFIG. 2 andFIG. 3 . - The
impeller 10 also includes a plurality ofslots 36 formed in thebacking plate 22. A plurality oftabs 38 are formed on theplate end 34 of thevanes 24. Thetabs 38 are configured to mate with theslots 36. Therefore, thebacking plate 22 and thevanes 24 are mated together, which may assist in carrying loads between the two components. Thetabs 38 and theslots 36 may mate through a slip fit, an interference fit (such as by snapping into the slots 36), or by a deformation fit. - Referring now to
FIG. 4 andFIG. 5 , and with continued reference toFIGS. 1-3 , there is shown analternative impeller 110.FIG. 4 shows an exploded isometric view of theimpeller 110, from a back side viewpoint.FIG. 5 shows an isometric view of the assembledimpeller 110. In operation, theimpeller 110 and theimpeller 10 shown inFIGS. 1-3 may operate in substantially identical fashion. - The
impeller 110 includes aninlet shroud 120 and abacking plate 122. A plurality ofvanes 124 are disposed between theinlet shroud 120 and thebacking plate 122. These vanes 124 transfer motion of theimpeller 110 into motion or pressure within the working fluid. Thevanes 124 are formed integrally as one-piece with theinlet shroud 120, such that thevanes 124 are not separately or subsequently attached to theinlet shroud 120. - Inlet flow of the working fluid enters an
inlet orifice 126 defined by theinlet shroud 120. Outlet flow of the working fluid exits through a plurality ofoutlet orifices 128, which are radially outward of theinlet orifice 126. - The
impeller 110 may also be defined by a draft angle formed on thevanes 124. The draft angle opens from theinlet shroud 120 to thebacking plate 122, such that abase end 132 of thevanes 124 is wider than aplate end 134 of thevanes 124. In theimpeller 110 shown, theinlet shroud 120 and thevanes 124 may be formed as one-piece by a single-action mold. - The
impeller 110 also includes a plurality ofslots 136 formed in thebacking plate 122. A plurality oftabs 138 are formed on the end of thevanes 124, and are configured to mate with theslots 136. - In addition to mating the
tabs 138 with theslots 136, theimpeller 110 further includes anannular ring 140 formed on the opposing side of thebacking plate 122 from thevanes 124. Theannual ring 140 connects the plurality oftabs 138. - As shown in
FIG. 4 , achannel 142 may be formed in thebacking plate 122. Thechannel 142 may house theannular ring 140, such that theannular ring 140 is flush with thebacking plate 122. However, theannular ring 140 may alternatively be formed on thebacking plate 122 without thechannel 142. - In one illustrative manufacturing process for the
impeller 110, after theinlet shroud 120 and thevanes 124 are formed as one-piece by the single-action mold, thetabs 138 are inserted into theslots 136 in thebacking plate 122. Then, theannular ring 140 is overmolded onto thebacking plate 122 and the plurality oftabs 138, such that formation of theannular ring 140 locks thetabs 138 to thebacking plate 122. - Referring now to
FIG. 6 , and with continued reference toFIGS. 1-5 , there is shown aschematic graph 200, which illustrates operational results of theimpeller 10 shown inFIGS. 1-3 compared with a different, comparison impeller. Thegraph 200 shows the improved performance of theimpeller 10 over the comparison impeller. - The comparison impeller does not have the
draft angle 30 shown inFIGS. 1-3 . The comparison impeller may have an opposite draft angle (opening from a backing plate toward an inlet shroud) or may be a foil impeller, which has vanes that are integral with, and bent outward from, the backing plate. Therefore, as the working fluid turns from axial flow to radial flow in the comparison impeller, the fluid becomes more constricted. However, in theimpeller 10, thefirst distance 31 is smaller than thesecond distance 33, such that the working fluid is less constricted as it turns from axial flow to radial flow. - Flow rate values 202 are shown on the left side, in liters per minute.
Hydraulic efficiency 204, in percentage, is shown on the right side. All values shown are illustrative, exemplary, and demonstrative, and the values are in no way limiting of the invention. To derive the data shown in thechart 200, theimpeller 10 and the comparison impeller were simulated as operating at the same speeds, approximately 8750 revolutions per minute, and with the same working fluid, water-based coolant. - A
bar 210 shows the flow rate of theimpeller 10, and abar 212 shows the flow rate of the comparison impeller. As shown in thechart 200, theimpeller 10 yielded a higher flow rate over the comparison impeller. - A
bar 214 shows the hydraulic efficiency of theimpeller 10, and abar 216 shows the hydraulic efficiency of the comparison impeller. As shown in thechart 200, theimpeller 10 had improved hydraulic efficiency relative to the comparison impeller. - The detailed description and the drawings or figures are supportive and descriptive of the invention, but the scope of the invention is defined solely by the claims. While some of the best modes and other embodiments for carrying out the claimed invention have been described in detail, various alternative designs and embodiments exist for practicing the invention defined in the appended claims.
Claims (9)
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/559,998 US20140030099A1 (en) | 2012-07-27 | 2012-07-27 | Pump impeller |
DE102013214362.1A DE102013214362A1 (en) | 2012-07-27 | 2013-07-23 | PUMP iMPELLER |
CN201310320873.6A CN103573691A (en) | 2012-07-27 | 2013-07-26 | Pump impeller |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/559,998 US20140030099A1 (en) | 2012-07-27 | 2012-07-27 | Pump impeller |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140030099A1 true US20140030099A1 (en) | 2014-01-30 |
Family
ID=49912407
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/559,998 Abandoned US20140030099A1 (en) | 2012-07-27 | 2012-07-27 | Pump impeller |
Country Status (3)
Country | Link |
---|---|
US (1) | US20140030099A1 (en) |
CN (1) | CN103573691A (en) |
DE (1) | DE102013214362A1 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160090869A1 (en) * | 2014-09-26 | 2016-03-31 | Hamilton Sundstrand Corporation | Method of installing a diffuser in an air cycle machine |
US20190226497A1 (en) * | 2018-01-19 | 2019-07-25 | Aisin Seiki Kabushiki Kaisha | Impeller |
GB2574221A (en) * | 2018-05-30 | 2019-12-04 | Cnc Subcon Services Ltd | Impeller and method of manufacture |
USD940760S1 (en) * | 2020-04-04 | 2022-01-11 | Colina | Mixing pump impeller |
USD958842S1 (en) * | 2020-04-04 | 2022-07-26 | Colina | Mixing pump impeller vane assembly |
USD979607S1 (en) * | 2020-02-03 | 2023-02-28 | W.S. Darley & Co. | Impeller for a pump |
USD1006056S1 (en) * | 2020-02-03 | 2023-11-28 | W.S. Darley & Co. | Impeller blade for a pump |
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US1919970A (en) * | 1933-02-07 | 1933-07-25 | Gen Electric | Impeller |
US3175757A (en) * | 1956-12-07 | 1965-03-30 | Laing Nikolaus | Rotor construction |
US20050071998A1 (en) * | 2003-10-02 | 2005-04-07 | Rocky Drew M. | Method of molding centrifugal impeller |
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CN2090920U (en) * | 1991-02-21 | 1991-12-18 | 王政义 | Integrated impeller for fume extractor |
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CN101793258A (en) * | 2010-01-22 | 2010-08-04 | 太仓市三耐化工设备有限公司 | Integrated thermoformed anticorrosion impeller |
CN201896786U (en) * | 2010-01-27 | 2011-07-13 | 太仓市三耐化工设备有限公司 | Corrosion-resistant fan |
-
2012
- 2012-07-27 US US13/559,998 patent/US20140030099A1/en not_active Abandoned
-
2013
- 2013-07-23 DE DE102013214362.1A patent/DE102013214362A1/en not_active Withdrawn
- 2013-07-26 CN CN201310320873.6A patent/CN103573691A/en active Pending
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US1919970A (en) * | 1933-02-07 | 1933-07-25 | Gen Electric | Impeller |
US3175757A (en) * | 1956-12-07 | 1965-03-30 | Laing Nikolaus | Rotor construction |
US6881033B2 (en) * | 2002-09-30 | 2005-04-19 | Fisher & Paykel Healthcare Limited | Impeller |
US7210226B2 (en) * | 2002-09-30 | 2007-05-01 | Fisher & Paykel Healthcare Limited | Method of manufacturing an impeller |
US20050071998A1 (en) * | 2003-10-02 | 2005-04-07 | Rocky Drew M. | Method of molding centrifugal impeller |
US7108482B2 (en) * | 2004-01-23 | 2006-09-19 | Robert Bosch Gmbh | Centrifugal blower |
US7632073B2 (en) * | 2005-06-08 | 2009-12-15 | Dresser-Rand Company | Impeller with machining access panel |
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US20120141261A1 (en) * | 2009-05-08 | 2012-06-07 | Iacopo Giovannetti | Composite shroud and methods for attaching the shroud to plural blades |
US20110182748A1 (en) * | 2010-01-27 | 2011-07-28 | Kwok Lo Ching | Centrifugal impeller |
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Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160090869A1 (en) * | 2014-09-26 | 2016-03-31 | Hamilton Sundstrand Corporation | Method of installing a diffuser in an air cycle machine |
US9469406B2 (en) * | 2014-09-26 | 2016-10-18 | Hamilton Sundstrand Corporation | Method of installing a diffuser in an air cycle machine |
US10487853B2 (en) | 2014-09-26 | 2019-11-26 | Hamilton Sundstrand Corporation | Alignment tool for installing a diffuser in an air cycle machine |
US20190226497A1 (en) * | 2018-01-19 | 2019-07-25 | Aisin Seiki Kabushiki Kaisha | Impeller |
GB2574221A (en) * | 2018-05-30 | 2019-12-04 | Cnc Subcon Services Ltd | Impeller and method of manufacture |
WO2019229434A1 (en) * | 2018-05-30 | 2019-12-05 | CNC Subcon Services Limited | Impeller and method of manufacture |
USD979607S1 (en) * | 2020-02-03 | 2023-02-28 | W.S. Darley & Co. | Impeller for a pump |
USD1006056S1 (en) * | 2020-02-03 | 2023-11-28 | W.S. Darley & Co. | Impeller blade for a pump |
USD940760S1 (en) * | 2020-04-04 | 2022-01-11 | Colina | Mixing pump impeller |
USD958842S1 (en) * | 2020-04-04 | 2022-07-26 | Colina | Mixing pump impeller vane assembly |
Also Published As
Publication number | Publication date |
---|---|
CN103573691A (en) | 2014-02-12 |
DE102013214362A1 (en) | 2014-01-30 |
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