US20050264128A1 - Variable pitch manifold for rotor cooling in an electrical machine - Google Patents
Variable pitch manifold for rotor cooling in an electrical machine Download PDFInfo
- Publication number
- US20050264128A1 US20050264128A1 US10/709,740 US70974004A US2005264128A1 US 20050264128 A1 US20050264128 A1 US 20050264128A1 US 70974004 A US70974004 A US 70974004A US 2005264128 A1 US2005264128 A1 US 2005264128A1
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- tube
- rotor
- axial
- winding
- rings
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- 238000001816 cooling Methods 0.000 title description 4
- 238000004804 winding Methods 0.000 claims abstract description 89
- 230000000712 assembly Effects 0.000 claims abstract description 20
- 238000000429 assembly Methods 0.000 claims abstract description 20
- 238000009423 ventilation Methods 0.000 claims description 32
- 239000007769 metal material Substances 0.000 claims description 4
- 239000012809 cooling fluid Substances 0.000 description 13
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 2
- 229910052799 carbon Inorganic materials 0.000 description 2
- 239000002131 composite material Substances 0.000 description 2
- 239000000112 cooling gas Substances 0.000 description 2
- 238000009828 non-uniform distribution Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 238000013022 venting Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 239000000835 fiber Substances 0.000 description 1
- 239000011152 fibreglass Substances 0.000 description 1
- 238000005242 forging Methods 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000005405 multipole Effects 0.000 description 1
Images
Classifications
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K1/00—Details of the magnetic circuit
- H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
- H02K1/22—Rotating parts of the magnetic circuit
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K1/00—Details of the magnetic circuit
- H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
- H02K1/22—Rotating parts of the magnetic circuit
- H02K1/24—Rotor cores with salient poles ; Variable reluctance rotors
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K1/00—Details of the magnetic circuit
- H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
- H02K1/22—Rotating parts of the magnetic circuit
- H02K1/32—Rotating parts of the magnetic circuit with channels or ducts for flow of cooling medium
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K3/00—Details of windings
- H02K3/46—Fastening of windings on the stator or rotor structure
- H02K3/52—Fastening salient pole windings or connections thereto
- H02K3/527—Fastening salient pole windings or connections thereto applicable to rotors only
Definitions
- the present invention relates to electrical machines such as (but not limited to) electrical generators and, more particularly, to a manifold of a generator rotor which promotes uniform cooling of the windings of the generator rotor.
- the rotor In a conventional generator having a rotor and a stator, the rotor is provided with field windings that excite the generator while receiving a current from an excitation current source.
- the stator is provided with windings from which electrical power is output.
- Typical rotor construction requires that a field winding be assembled bar by bar, into radial slots milled into a rotor body. Containment of the rotor field windings is typically achieved using rotor wedges, rotor teeth and retaining rings.
- a carbon filled reinforced enclosure (CFRE) rotor eliminates the need for the coil slots milled in the rotor shaft and enables the assembly of a field winding as a single winding module, one for each pole. It is known to use individual radial manifolds under each coil module with a fixed axial spacing between discharge or ventilation holes in the manifolds.
- a rotor in an electrical machine comprises a magnetic core having at least two poles, a plurality of winding assemblies, one for each pole, and a cylindrical tube enclosing the magnetic core and winding assemblies.
- the tube includes a plurality of rings having different axial widths.
- the tube may be formed of a non-metallic material.
- Each of the rings may be axially spaced apart from an adjacent ring.
- the rings may be axially spaced apart such that radial discharge slots defined in the magnetic core are axially aligned with respective spaces between the rings.
- the respective axial widths of the rings located at both axial ends of the tube may be smaller than the axial width of the ring axially located at or near the center of the tube.
- the respective axial widths of the rings may become progressively smaller than the axial width of the ring axially located at or near the center of the tube as the axial distance away from the center of the tube increases.
- the rotor may further comprise a plurality of winding braces coupled to at least one of the winding assemblies, the winding braces having different radial heights.
- the radial heights of the winding braces located at both axial ends of the tube may be smaller than the radial height of the winding brace axially located at or near the center of the tube.
- the respective radial heights of the winding braces may become progressively smaller than the radial height of the winding brace axially located at or near the center of the tube as the axial distance away from the center of the tube increases.
- the rotor may further comprise a plurality of winding braces coupled to at least one of the winding assemblies and axially spaced apart from each other, the axial distance between one pair of adjacent winding braces being different than the axial distance between another pair of adjacent winding braces.
- the respective axial distances between the winding braces located at the ends of the tube may be smaller than the axial distance between the winding braces located at or near the center of the tube.
- the respective axial distances between adjacent winding braces may become progressively smaller than the axial distance between adjacent winding braces axially located at the center of the tube as the axial distance away from the center of the tube increases.
- the rotor may further comprise a shield having a plurality of ventilation holes defined therein, the shield being disposed between (i) the tube and (ii) the magnetic core and winding assemblies.
- the ventilation holes may be circular or elliptical.
- the ventilation holes may be aligned in respective rows in the axial direction of the shield, and the respective rows of ventilation holes may be axially aligned with respective axial spaces defined between the rings.
- the ventilation holes may be aligned in respective rows in the axial direction of the shield and the axial distance between the rows may be non-uniform.
- the distance between the rows of ventilation holes formed in the shield may become progressively smaller as the axial distance away from the center of the shield increases.
- a cylindrical tube for enclosing rotor components including a magnetic core having at least two poles and a plurality of winding assemblies comprises a plurality of rings having different axial widths.
- the tube may be formed of a non-metallic material.
- Each of the rings may be axially spaced apart from an adjacent ring.
- the rings may be axially spaced apart such that radial discharge slots defined in the magnetic core are axially aligned with respective spaces between the rings.
- the respective axial widths of the rings at both axial ends of the tube may be smaller than the axial width of the ring axially located at or near the center of the tube.
- the respective axial widths of the rings may become progressively smaller than the axial width of the ring axially located at or near the center of the tube as the axial distance away from the center of the tube increases.
- FIG. 1 is a schematic illustration of a rotor, stator, shield and cylindrical enclosure tube of an electrical machine in accordance with an exemplary embodiment of the present invention
- FIG. 2 is a side view of the cylindrical enclosure tube shown in FIG. 1 ;
- FIG. 3 is a side view of an exemplary embodiment of the shield shown in FIG. 1 ;
- FIG. 4 is a side view of another exemplary embodiment of the shield shown in FIG. 1 ;
- FIG. 5 is a cross-sectional view of a series of winding braces of variable radial height connected to the cylindrical enclosure tube shown in FIG. 1 ;
- FIG. 6 is a partial sectional view illustrating one of the winding braces shown in FIG. 5 .
- FIG. 1 illustrates an electrical machine such as, but not limited to, a generator including a rotor 10 rotatably mounted within stator 50 .
- Rotor 10 includes a longitudinal axis 11 about which rotor 10 rotates within stator 50 , a multi-pole magnetic core 12 (two-pole core shown) and a plurality of winding assemblies 30 , one for each pole.
- Rotor 10 also includes a non-metallic, cylindrical tube 20 enclosing core 12 and winding assemblies 30 .
- Rotor 10 may also include a continuous shield 40 interposed between tube 20 and winding assemblies 30 .
- Tube 20 is slid over the assembly.
- Tube 20 is constructed from a non-metallic low density composite material, such as a carbon fiber-glass fiber composite and is configured to discharge winding ventilation gas to a generator air gap 52 defined between rotor 10 and stator 50 .
- the material forming tube 20 preferably has a high strength to weight ratio.
- FIG. 2 illustrates details of an exemplary embodiment of tube 20 enclosing other components of rotor 10 (e.g., core 12 illustrated in dashed line).
- Tube 20 is formed by a plurality of rings 21 which are axially separated from each other such that respective spaces 22 having a predetermined distance are defined between each of rings 21 .
- Spaces 22 form radial discharge paths for a cooling fluid as illustrated by the arrows 25 indicating the directions of cooling gas flow.
- spaces 22 form radial discharge paths for venting cooling fluid to air gap 52 .
- Spaces 22 are axially aligned with radial discharge paths 17 of core 12 so that cooling gas flows through a manifold of rotor 10 in the directions indicated by arrows 25 .
- the respective axial widths of rings 21 vary.
- the axial width W a of ring 21 a located at the axial center of tube 20 is larger than the axial width W b of adjacent ring 21 b .
- the axial width W b of ring 21 b is larger than the axial width W c of ring 21 c .
- axial width W a of ring 21 a is larger than the axial width W d of ring 21 d which is in turn larger than the axial width W e of ring 21 e .
- the respective axial widths of rings 21 thus become progressively smaller as the axial distance from the center of tube 20 increases.
- the rings 21 located at the ends of cylinder 20 thus have the smallest axial width.
- Ring 21 a located at the center of tube 20 has the largest axial width W a .
- the axial distance between successive spaces 22 varies.
- the axial distance between successive spaces 22 becomes progressively smaller as the axial distance from the center of tube 20 increases.
- Tube 20 would by itself thus provide a non-uniform distribution of cooling fluid flow due to the variable separation between spaces 22 .
- the distance between successive spaces 22 forming radial discharge paths for cooling fluid may be adjusted.
- FIG. 3 illustrates details of an exemplary embodiment of shield 40 .
- Shield 40 is formed of a continuous metallic body with a plurality of ventilation holes 41 .
- Ventilation holes 41 formed in continuous cylindrical shield 40 provide discharge openings for venting cooling fluid to air gap 52 without introducing stress concentrations in shield 40 and/or tube 20 .
- the flow of the cooling fluid through core 12 and shield 40 are demonstrated by arrows 25 .
- Ventilation holes 41 may have an elliptical shape as illustrated in FIG. 3 or a circular shape as illustrated in the alternative exemplary embodiment shown in FIG. 4 .
- Ventilation holes 41 are aligned in respective axial rows.
- a number of ventilation holes 41 may be aligned in axial row 42 .
- Each of these holes 41 in row 42 has an equal axial distance from the center of shield 40 .
- Other axial rows 43 - 46 each comprising a plurality of ventilation holes 41 , are also formed in shield 40 .
- the rows of ventilation holes 41 are aligned with respective radial discharge paths 17 of core 12 .
- the axial spacing between rows of ventilation holes 41 is non-uniform.
- the axial distance separating consecutive rows of ventilation holes 41 becomes progressively smaller as the axial distance from the center of shield 40 increases.
- the axial distance between rows 44 and 43 is shorter than the distance between rows 43 and 42 . Due to this non-uniform spacing of ventilation holes 41 , the flow of cooling fluid provided by shield 40 would (by itself) be non-uniform.
- shield 40 is interposed between winding assemblies 30 and cylindrical tube 20 .
- the axial rows of holes formed in shield 40 are axially aligned with the spaces between rings 21 of tube 20 to establish the flow of cooling fluid illustrated by arrows 25 .
- axial row 42 of ventilation holes 41 formed in shield 40 is axially aligned with the space between rings 21 a and 21 b of cylindrical tube 20 .
- Row 43 of ventilation holes 41 formed in shield 40 is axially aligned with the axial space between rings 21 b and 21 c of cylindrical tube 20 .
- Row 45 of ventilation holes 41 formed in shield 40 is axially aligned with the space between rings 21 a and 21 d of cylindrical tube 20 .
- row 46 of ventilation holes 41 of shield 40 is axially aligned with the space between rings 21 d and 21 e of cylindrical tube 20 .
- the rows of ventilation holes 41 are thus aligned with the axial spaces between successive rings 21 of cylindrical tube 20 to establish cooling fluid discharge paths shown by arrows 25 .
- FIGS. 5-6 illustrate a plurality of winding braces 31 coupled to tube 20 and core 12 .
- Winding braces 31 connect windings 33 to core 12 .
- a respective locking pin 35 connects each winding brace 31 to core 12 so that winding 33 may be connected to core 12 .
- winding braces 31 are also coupled to a respective one of the rings 21 .
- winding braces 31 have a variable radial height and a variable axial spacing.
- the radial height h 3 of winding brace 31 c connected to ring 21 c is smaller than the radial height h 2 of winding brace 31 b connected to ring 21 b which is in turn smaller than the radial height h 1 of winding brace 31 a connected to the center-most ring 21 a .
- the radial height h 5 of winding brace 31 e connected to ring 21 e is smaller than the radial height h 4 of winding brace 31 d connected to ring 21 d which is in turn smaller than the radial height h 1 of winding brace 31 a connected to the center-most ring 21 a .
- the respective radial heights of the winding braces 31 thus become progressively smaller as the distance away from the center of tube 20 increases.
- the axial spacing between successive winding braces 31 also becomes progressively smaller as the axial distance from the center of tube 20 increases.
- the axial spacing S 2 between the winding braces 31 c and 31 b is smaller than the axial spacing S 1 between the winding braces 31 b and 31 a .
- the axial spacing S 4 between the winding braces 31 e and 31 d is smaller than the axial spacing S 3 between the winding braces 31 d and 31 a .
- the variable axial spacing of winding braces 31 counteracts the (otherwise) non-uniform distribution of cooling fluid flow emanating from tube 20 formed between the inner radial edge of the winding braces 31 and the shaft of the rotor 10 .
- the radial discharge flow between each adjacent pair of winding braces 31 may be adjusted by changing the axial separation between those two winding braces 31 to obtain the desired flow of cooling fluid.
- the radial height (e.g., h 1 -h 5 ) of braces 31 may be adjusted to thus adjust the position of the inner radial edge of each winding brace 31 to throttle the flow of cooling fluid in the downstream tube 20 .
- the axial spacing (e.g., S 1 -S 4 ) of the winding braces 31 and the radial height (e.g., h 1 -h 5 ) of winding braces 31 may each be adjusted to provide a more uniform rotor winding temperature.
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- Engineering & Computer Science (AREA)
- Power Engineering (AREA)
- Motor Or Generator Cooling System (AREA)
- Iron Core Of Rotating Electric Machines (AREA)
- Synchronous Machinery (AREA)
Abstract
Description
- The present invention relates to electrical machines such as (but not limited to) electrical generators and, more particularly, to a manifold of a generator rotor which promotes uniform cooling of the windings of the generator rotor.
- In a conventional generator having a rotor and a stator, the rotor is provided with field windings that excite the generator while receiving a current from an excitation current source. The stator is provided with windings from which electrical power is output. Typical rotor construction requires that a field winding be assembled bar by bar, into radial slots milled into a rotor body. Containment of the rotor field windings is typically achieved using rotor wedges, rotor teeth and retaining rings. A carbon filled reinforced enclosure (CFRE) rotor eliminates the need for the coil slots milled in the rotor shaft and enables the assembly of a field winding as a single winding module, one for each pole. It is known to use individual radial manifolds under each coil module with a fixed axial spacing between discharge or ventilation holes in the manifolds.
- It is desirable to provide a more uniform cooling to the rotor windings. By providing a more uniform cooling to the rotor windings, “hot spots” (areas of very high temperatures) may be avoided. The advanced physical deterioration of generator components (e.g., insulation) at these areas can thus be avoided, thereby extending the operational life of the generator.
- A rotor in an electrical machine comprises a magnetic core having at least two poles, a plurality of winding assemblies, one for each pole, and a cylindrical tube enclosing the magnetic core and winding assemblies. The tube includes a plurality of rings having different axial widths. The tube may be formed of a non-metallic material. Each of the rings may be axially spaced apart from an adjacent ring. The rings may be axially spaced apart such that radial discharge slots defined in the magnetic core are axially aligned with respective spaces between the rings. The respective axial widths of the rings located at both axial ends of the tube may be smaller than the axial width of the ring axially located at or near the center of the tube. The respective axial widths of the rings may become progressively smaller than the axial width of the ring axially located at or near the center of the tube as the axial distance away from the center of the tube increases. The rotor may further comprise a plurality of winding braces coupled to at least one of the winding assemblies, the winding braces having different radial heights. The radial heights of the winding braces located at both axial ends of the tube may be smaller than the radial height of the winding brace axially located at or near the center of the tube. The respective radial heights of the winding braces may become progressively smaller than the radial height of the winding brace axially located at or near the center of the tube as the axial distance away from the center of the tube increases. The rotor may further comprise a plurality of winding braces coupled to at least one of the winding assemblies and axially spaced apart from each other, the axial distance between one pair of adjacent winding braces being different than the axial distance between another pair of adjacent winding braces. The respective axial distances between the winding braces located at the ends of the tube may be smaller than the axial distance between the winding braces located at or near the center of the tube. The respective axial distances between adjacent winding braces may become progressively smaller than the axial distance between adjacent winding braces axially located at the center of the tube as the axial distance away from the center of the tube increases. The rotor may further comprise a shield having a plurality of ventilation holes defined therein, the shield being disposed between (i) the tube and (ii) the magnetic core and winding assemblies. The ventilation holes may be circular or elliptical. The ventilation holes may be aligned in respective rows in the axial direction of the shield, and the respective rows of ventilation holes may be axially aligned with respective axial spaces defined between the rings. The ventilation holes may be aligned in respective rows in the axial direction of the shield and the axial distance between the rows may be non-uniform. The distance between the rows of ventilation holes formed in the shield may become progressively smaller as the axial distance away from the center of the shield increases.
- A cylindrical tube for enclosing rotor components including a magnetic core having at least two poles and a plurality of winding assemblies comprises a plurality of rings having different axial widths. The tube may be formed of a non-metallic material. Each of the rings may be axially spaced apart from an adjacent ring. The rings may be axially spaced apart such that radial discharge slots defined in the magnetic core are axially aligned with respective spaces between the rings. The respective axial widths of the rings at both axial ends of the tube may be smaller than the axial width of the ring axially located at or near the center of the tube. The respective axial widths of the rings may become progressively smaller than the axial width of the ring axially located at or near the center of the tube as the axial distance away from the center of the tube increases.
-
FIG. 1 is a schematic illustration of a rotor, stator, shield and cylindrical enclosure tube of an electrical machine in accordance with an exemplary embodiment of the present invention; -
FIG. 2 is a side view of the cylindrical enclosure tube shown inFIG. 1 ; -
FIG. 3 is a side view of an exemplary embodiment of the shield shown inFIG. 1 ; -
FIG. 4 is a side view of another exemplary embodiment of the shield shown inFIG. 1 ; -
FIG. 5 is a cross-sectional view of a series of winding braces of variable radial height connected to the cylindrical enclosure tube shown inFIG. 1 ; and -
FIG. 6 is a partial sectional view illustrating one of the winding braces shown inFIG. 5 . -
FIG. 1 illustrates an electrical machine such as, but not limited to, a generator including arotor 10 rotatably mounted withinstator 50.Rotor 10 includes alongitudinal axis 11 about whichrotor 10 rotates withinstator 50, a multi-pole magnetic core 12 (two-pole core shown) and a plurality of windingassemblies 30, one for each pole.Rotor 10 also includes a non-metallic,cylindrical tube 20 enclosingcore 12 and windingassemblies 30.Rotor 10 may also include acontinuous shield 40 interposed betweentube 20 and windingassemblies 30. - After winding
assemblies 30 are slid over the parallel sided forging of two-polemagnetic core 12,tube 20 is slid over the assembly.Tube 20 is constructed from a non-metallic low density composite material, such as a carbon fiber-glass fiber composite and is configured to discharge winding ventilation gas to agenerator air gap 52 defined betweenrotor 10 andstator 50. Thematerial forming tube 20 preferably has a high strength to weight ratio. -
FIG. 2 illustrates details of an exemplary embodiment oftube 20 enclosing other components of rotor 10 (e.g.,core 12 illustrated in dashed line).Tube 20 is formed by a plurality ofrings 21 which are axially separated from each other such thatrespective spaces 22 having a predetermined distance are defined between each of rings 21.Spaces 22 form radial discharge paths for a cooling fluid as illustrated by thearrows 25 indicating the directions of cooling gas flow. In particular,spaces 22 form radial discharge paths for venting cooling fluid toair gap 52.Spaces 22 are axially aligned withradial discharge paths 17 ofcore 12 so that cooling gas flows through a manifold ofrotor 10 in the directions indicated byarrows 25. - The respective axial widths of
rings 21 vary. For example, the axial width Wa ofring 21 a located at the axial center oftube 20 is larger than the axial width Wb ofadjacent ring 21 b. The axial width Wb ofring 21 b is larger than the axial width Wc ofring 21 c. Similarly, axial width Wa ofring 21 a is larger than the axial width Wd ofring 21 d which is in turn larger than the axial width We ofring 21 e. The respective axial widths ofrings 21 thus become progressively smaller as the axial distance from the center oftube 20 increases. Therings 21 located at the ends ofcylinder 20 thus have the smallest axial width.Ring 21 a located at the center oftube 20 has the largest axial width Wa. - By varying the respective axial widths of
rings 21, the axial distance betweensuccessive spaces 22 varies. In particular, the axial distance betweensuccessive spaces 22 becomes progressively smaller as the axial distance from the center oftube 20 increases.Tube 20 would by itself thus provide a non-uniform distribution of cooling fluid flow due to the variable separation betweenspaces 22. By adjusting the respective axial widths ofrings 21, the distance betweensuccessive spaces 22 forming radial discharge paths for cooling fluid may be adjusted. -
FIG. 3 illustrates details of an exemplary embodiment ofshield 40.Shield 40 is formed of a continuous metallic body with a plurality of ventilation holes 41. Ventilation holes 41 formed in continuouscylindrical shield 40 provide discharge openings for venting cooling fluid toair gap 52 without introducing stress concentrations inshield 40 and/ortube 20. The flow of the cooling fluid throughcore 12 andshield 40 are demonstrated byarrows 25. Ventilation holes 41 may have an elliptical shape as illustrated inFIG. 3 or a circular shape as illustrated in the alternative exemplary embodiment shown inFIG. 4 . - Ventilation holes 41 are aligned in respective axial rows. For example, a number of ventilation holes 41 (six
ventilation holes 41 shown inFIG. 3 ) may be aligned inaxial row 42. Each of theseholes 41 inrow 42 has an equal axial distance from the center ofshield 40. Other axial rows 43-46 each comprising a plurality of ventilation holes 41, are also formed inshield 40. The rows of ventilation holes 41 are aligned with respectiveradial discharge paths 17 ofcore 12. - As illustrated in
FIG. 3 , the axial spacing between rows of ventilation holes 41 is non-uniform. The axial distance separating consecutive rows of ventilation holes 41 becomes progressively smaller as the axial distance from the center ofshield 40 increases. For example, the axial distance betweenrows rows shield 40 would (by itself) be non-uniform. - As illustrated in
FIG. 1 , shield 40 is interposed between windingassemblies 30 andcylindrical tube 20. The axial rows of holes formed in shield 40 (shown inFIG. 3 ) are axially aligned with the spaces betweenrings 21 oftube 20 to establish the flow of cooling fluid illustrated byarrows 25. For example,axial row 42 of ventilation holes 41 formed inshield 40 is axially aligned with the space betweenrings cylindrical tube 20.Row 43 of ventilation holes 41 formed inshield 40 is axially aligned with the axial space betweenrings cylindrical tube 20.Row 45 of ventilation holes 41 formed inshield 40 is axially aligned with the space betweenrings cylindrical tube 20. As a final example,row 46 of ventilation holes 41 ofshield 40 is axially aligned with the space betweenrings cylindrical tube 20. The rows of ventilation holes 41 are thus aligned with the axial spaces betweensuccessive rings 21 ofcylindrical tube 20 to establish cooling fluid discharge paths shown byarrows 25. -
FIGS. 5-6 illustrate a plurality of windingbraces 31 coupled totube 20 andcore 12. Winding braces 31 connectwindings 33 tocore 12. In particular, arespective locking pin 35 connects each windingbrace 31 tocore 12 so that winding 33 may be connected tocore 12. - Each of the winding braces 31 is also coupled to a respective one of the
rings 21. As illustrated inFIG. 5 , windingbraces 31 have a variable radial height and a variable axial spacing. For example, the radial height h3 of windingbrace 31 c connected to ring 21 c is smaller than the radial height h2 of winding brace 31 b connected to ring 21 b which is in turn smaller than the radial height h1 of windingbrace 31 a connected to thecenter-most ring 21 a. Similarly, the radial height h5 of windingbrace 31 e connected to ring 21 e is smaller than the radial height h4 of windingbrace 31 d connected to ring 21 d which is in turn smaller than the radial height h1 of windingbrace 31 a connected to thecenter-most ring 21 a. The respective radial heights of the windingbraces 31 thus become progressively smaller as the distance away from the center oftube 20 increases. - The axial spacing between successive winding
braces 31 also becomes progressively smaller as the axial distance from the center oftube 20 increases. For example, the axial spacing S2 between the windingbraces 31 c and 31 b is smaller than the axial spacing S1 between the windingbraces 31 b and 31 a. Similarly, the axial spacing S4 between the windingbraces braces braces 31 counteracts the (otherwise) non-uniform distribution of cooling fluid flow emanating fromtube 20 formed between the inner radial edge of the windingbraces 31 and the shaft of therotor 10. The radial discharge flow between each adjacent pair of windingbraces 31 may be adjusted by changing the axial separation between those two windingbraces 31 to obtain the desired flow of cooling fluid. Moreover, the radial height (e.g., h1-h5) ofbraces 31 may be adjusted to thus adjust the position of the inner radial edge of each windingbrace 31 to throttle the flow of cooling fluid in thedownstream tube 20. Accordingly, the axial spacing (e.g., S1-S4) of the windingbraces 31 and the radial height (e.g., h1-h5) of windingbraces 31 may each be adjusted to provide a more uniform rotor winding temperature. By adjusting the axial spacing and radial height of the windingbraces 31, an overall distribution of cooling fluid flow in therotor 10 andstator 50 that minimizes hot spots in both the stator and rotor windings may be achieved. Ventilation may be provided without introducing stress concentrations intube 20. The rotor assembly can thus be simplified and the risk of local damage to individual pieces is isolated as opposed to requiring replacement of the entire containment structure. - While the invention has been described in connection with what is presently considered to be the most practical and preferred embodiment, it is to be understood that the invention is not to be limited to the disclosed embodiment, but on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.
Claims (24)
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/709,740 US6965185B1 (en) | 2004-05-26 | 2004-05-26 | Variable pitch manifold for rotor cooling in an electrical machine |
GB0510165A GB2414600B (en) | 2004-05-26 | 2005-05-18 | Variable pitch manifold for rotor cooling in an electrical machine |
JP2005151828A JP5013682B2 (en) | 2004-05-26 | 2005-05-25 | Variable pitch manifold for rotor cooling in electrical machines |
KR1020050044167A KR101126971B1 (en) | 2004-05-26 | 2005-05-25 | Variable pitch manifold for rotor cooling in an electrical machine |
CNB2005100760551A CN100539359C (en) | 2004-05-26 | 2005-05-26 | The variable pitch manifold that is used for the rotor cooling of motor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US10/709,740 US6965185B1 (en) | 2004-05-26 | 2004-05-26 | Variable pitch manifold for rotor cooling in an electrical machine |
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Publication Number | Publication Date |
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US6965185B1 US6965185B1 (en) | 2005-11-15 |
US20050264128A1 true US20050264128A1 (en) | 2005-12-01 |
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US10/709,740 Expired - Fee Related US6965185B1 (en) | 2004-05-26 | 2004-05-26 | Variable pitch manifold for rotor cooling in an electrical machine |
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US (1) | US6965185B1 (en) |
JP (1) | JP5013682B2 (en) |
KR (1) | KR101126971B1 (en) |
CN (1) | CN100539359C (en) |
GB (1) | GB2414600B (en) |
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EP2148408A1 (en) | 2008-07-24 | 2010-01-27 | ALSTOM Technology Ltd | Synchronous machine and also method for manufacturing such a synchronous machine |
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US7791238B2 (en) * | 2005-07-25 | 2010-09-07 | Hamilton Sundstrand Corporation | Internal thermal management for motor driven machinery |
US7208854B1 (en) * | 2006-03-09 | 2007-04-24 | Hamilton Sundstrand Corporation | Rotor cooling system for synchronous machines with conductive sleeve |
CH700176B1 (en) * | 2007-03-02 | 2010-07-15 | Alstom Technology Ltd | Rotor for a generator. |
US7893576B2 (en) * | 2009-05-05 | 2011-02-22 | General Electric Company | Generator coil cooling baffles |
US9006942B2 (en) * | 2009-05-07 | 2015-04-14 | Hamilton Sundstrand Corporation | Generator main stator back-iron cooling sleeve |
US8769954B2 (en) * | 2009-12-31 | 2014-07-08 | General Electric Company | Frequency-tunable bracketless fluid manifold |
US8901790B2 (en) * | 2012-01-03 | 2014-12-02 | General Electric Company | Cooling of stator core flange |
US9548640B2 (en) | 2013-12-05 | 2017-01-17 | General Electric Company | Rotor with cooling manifolds |
CN109616276B (en) * | 2018-11-02 | 2020-08-11 | 中国航空工业集团公司西安飞行自动控制研究所 | Unequal-spacing solenoid |
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
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EP2148408A1 (en) | 2008-07-24 | 2010-01-27 | ALSTOM Technology Ltd | Synchronous machine and also method for manufacturing such a synchronous machine |
US20100019614A1 (en) * | 2008-07-24 | 2010-01-28 | Peter Ulrich Arend | Synchronous machine and also method for manufacturing such a synchronous machine |
CH699198A1 (en) * | 2008-07-24 | 2010-01-29 | Alstom Technology Ltd | Synchronous machine and method for producing such a synchronous machine. |
Also Published As
Publication number | Publication date |
---|---|
GB2414600B (en) | 2007-10-24 |
GB2414600A (en) | 2005-11-30 |
JP5013682B2 (en) | 2012-08-29 |
CN1702941A (en) | 2005-11-30 |
KR101126971B1 (en) | 2012-03-23 |
US6965185B1 (en) | 2005-11-15 |
GB0510165D0 (en) | 2005-06-22 |
KR20060048095A (en) | 2006-05-18 |
CN100539359C (en) | 2009-09-09 |
JP2005341793A (en) | 2005-12-08 |
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