US2978168A - Bladed rotor for axial-flow fluid machine - Google Patents

Bladed rotor for axial-flow fluid machine Download PDF

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US2978168A
US2978168A US549430A US54943055A US2978168A US 2978168 A US2978168 A US 2978168A US 549430 A US549430 A US 549430A US 54943055 A US54943055 A US 54943055A US 2978168 A US2978168 A US 2978168A
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blades
rotor
disc
blade
axial
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Haworth Lionel
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RELLE ROYCE Ltd
RELLE-ROYCE Ltd
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    • C—CHEMISTRY; METALLURGY
    • C07—ORGANIC CHEMISTRY
    • C07C—ACYCLIC OR CARBOCYCLIC COMPOUNDS
    • C07C405/00—Compounds containing a five-membered ring having two side-chains in ortho position to each other, and having oxygen atoms directly attached to the ring in ortho position to one of the side-chains, one side-chain containing, not directly attached to the ring, a carbon atom having three bonds to hetero atoms with at the most one bond to halogen, and the other side-chain having oxygen atoms attached in gamma-position to the ring, e.g. prostaglandins ; Analogues or derivatives thereof
    • C07C405/0008—Analogues having the carboxyl group in the side-chains replaced by other functional groups
    • C07C405/0016—Analogues having the carboxyl group in the side-chains replaced by other functional groups containing only hydroxy, etherified or esterified hydroxy groups
    • C—CHEMISTRY; METALLURGY
    • C07—ORGANIC CHEMISTRY
    • C07C—ACYCLIC OR CARBOCYCLIC COMPOUNDS
    • C07C29/00—Preparation of compounds having hydroxy or O-metal groups bound to a carbon atom not belonging to a six-membered aromatic ring
    • C07C29/132—Preparation of compounds having hydroxy or O-metal groups bound to a carbon atom not belonging to a six-membered aromatic ring by reduction of an oxygen containing functional group
    • C07C29/136—Preparation of compounds having hydroxy or O-metal groups bound to a carbon atom not belonging to a six-membered aromatic ring by reduction of an oxygen containing functional group of >C=O containing groups, e.g. —COOH
    • C07C29/147—Preparation of compounds having hydroxy or O-metal groups bound to a carbon atom not belonging to a six-membered aromatic ring by reduction of an oxygen containing functional group of >C=O containing groups, e.g. —COOH of carboxylic acids or derivatives thereof
    • C—CHEMISTRY; METALLURGY
    • C07—ORGANIC CHEMISTRY
    • C07C—ACYCLIC OR CARBOCYCLIC COMPOUNDS
    • C07C35/00—Compounds having at least one hydroxy or O-metal group bound to a carbon atom of a ring other than a six-membered aromatic ring
    • C07C35/22—Compounds having at least one hydroxy or O-metal group bound to a carbon atom of a ring other than a six-membered aromatic ring polycyclic, at least one hydroxy group bound to a condensed ring system
    • C07C35/23—Compounds having at least one hydroxy or O-metal group bound to a carbon atom of a ring other than a six-membered aromatic ring polycyclic, at least one hydroxy group bound to a condensed ring system with hydroxy on a condensed ring system having two rings
    • C07C35/27—Compounds having at least one hydroxy or O-metal group bound to a carbon atom of a ring other than a six-membered aromatic ring polycyclic, at least one hydroxy group bound to a condensed ring system with hydroxy on a condensed ring system having two rings the condensed ring system containing six carbon atoms
    • C—CHEMISTRY; METALLURGY
    • C07—ORGANIC CHEMISTRY
    • C07C—ACYCLIC OR CARBOCYCLIC COMPOUNDS
    • C07C405/00—Compounds containing a five-membered ring having two side-chains in ortho position to each other, and having oxygen atoms directly attached to the ring in ortho position to one of the side-chains, one side-chain containing, not directly attached to the ring, a carbon atom having three bonds to hetero atoms with at the most one bond to halogen, and the other side-chain having oxygen atoms attached in gamma-position to the ring, e.g. prostaglandins ; Analogues or derivatives thereof
    • C07C405/0008—Analogues having the carboxyl group in the side-chains replaced by other functional groups
    • C07C405/0025—Analogues having the carboxyl group in the side-chains replaced by other functional groups containing keto groups
    • C—CHEMISTRY; METALLURGY
    • C07—ORGANIC CHEMISTRY
    • C07D—HETEROCYCLIC COMPOUNDS
    • C07D309/00—Heterocyclic compounds containing six-membered rings having one oxygen atom as the only ring hetero atom, not condensed with other rings
    • C07D309/02—Heterocyclic compounds containing six-membered rings having one oxygen atom as the only ring hetero atom, not condensed with other rings having no double bonds between ring members or between ring members and non-ring members
    • C07D309/08—Heterocyclic compounds containing six-membered rings having one oxygen atom as the only ring hetero atom, not condensed with other rings having no double bonds between ring members or between ring members and non-ring members with hetero atoms or with carbon atoms having three bonds to hetero atoms with at the most one bond to halogen, e.g. ester or nitrile radicals, directly attached to ring carbon atoms
    • C07D309/10—Oxygen atoms
    • C07D309/12—Oxygen atoms only hydrogen atoms and one oxygen atom directly attached to ring carbon atoms, e.g. tetrahydropyranyl ethers
    • C—CHEMISTRY; METALLURGY
    • C07—ORGANIC CHEMISTRY
    • C07D—HETEROCYCLIC COMPOUNDS
    • C07D317/00—Heterocyclic compounds containing five-membered rings having two oxygen atoms as the only ring hetero atoms
    • C07D317/08—Heterocyclic compounds containing five-membered rings having two oxygen atoms as the only ring hetero atoms having the hetero atoms in positions 1 and 3
    • C07D317/10—Heterocyclic compounds containing five-membered rings having two oxygen atoms as the only ring hetero atoms having the hetero atoms in positions 1 and 3 not condensed with other rings
    • C07D317/14—Heterocyclic compounds containing five-membered rings having two oxygen atoms as the only ring hetero atoms having the hetero atoms in positions 1 and 3 not condensed with other rings with substituted hydrocarbon radicals attached to ring carbon atoms
    • C07D317/30—Radicals substituted by carbon atoms having three bonds to hetero atoms with at the most one bond to halogen, e.g. ester or nitrile radicals

Definitions

  • a fluid to the' bladessof an axial-flow fluid machine; .for instance, in the case of the first-stage blading 'of an axial-flow compressorof an aircraft gas-turbine engine it is often desirable to supply a heating fluid to the blading for the purpose of preventing or reducing ice formation on the blading.
  • This invention has for an object -to provide a rotor structure for an axiaLflow fluid machine having pivoted blading and improved means whereby a fluid may be supplied to the pivoted blading.
  • the blades are pivoted blades of the rotor of an axialflow compressor
  • the'inlet end of afluid passage in each of a' plurality of the pivoted blades is' arranged 'to open to an upstream-facing surface of'the blade root, the surface being at right angles to the pivotal" axis.
  • an adjacent peripheral flange on the rotor structure is provided with apertures in its downstream-facing surface to overlap 'each of said inlets in the-blade roots, said downstream' surface also being at right angles to the pivotal axis, the upstreamfacing surface of the blade root being held against the downstream-facing surface of the flange by the gas load on the blade, and there is provided an annular manifold as part of the rotor structure to supply fluid to.the apertures in the peripheral flange and thus to the inlets in the blade roots.
  • annular disc is secured to the rotor structure, and the annular disc and the peripheral flange by having parts thereof in axial abutment form a manifoldspacel between themf
  • the annular disc may be provided withrecessed lands which abut the peripheral flange around the apertures for the pivot pins, so sealing them from the fluid space of the manifold.
  • a pair of annular discs are secured together to form a manifold space between them, the fluid being fed to the space for distribution, the discs are mounted on the rotor structure in spaced relation to the peripheral flange which has the apertures overlapping the inlets in the blade roots and transfer pieces are provided which flt in the apertures and in aligned apertures in one of the discs to convey the fluid from the manifold space to the peripheral flange and thus to the inlets in the blade roots.
  • Figure 1 is an axial section through part of the com- 'pressor
  • Figure 2 is a similar view at an angularly spaced location
  • Figure 3 is a section on the line III-HI of Figure 2
  • Figure 4 is a view in the direction of arrow IV on Figure 1,- parts being broken away, and the section lines Figures 1 and 2 being indicated at I1 and lI-II respectively, 25
  • Figures 5 and 6 correspond to Figures 1 and 2 and show a second-embodiment
  • Figure 7 is-an enlargement of part of Figure 6
  • Figu'i-e 8 corresponds to Figure 4 and shows the section lines for Figures S'and oat VV and VI-VI respectiyely'.”
  • the rotor of the axial-flow compressor comprises a central hollow shaft 10 on which there are mounted in axially-spaced relation a number of blade-carrying discs (not shown) for the rotor blades of the second and subsequent stages of the compressor, and the peripheries of the discs are/held in spaced relation by spacer rings 11.
  • the upstream end of the shaft 10 has secured to it an axial extension 13, and these parts abut over radial flanges 14, 15 and the radial flanges support the disc 18 carrying the first-stage rotor blades.
  • the flange 15 on the shaft extension 13 is axially thickened and is provided with a frusto-conical outward flange 16 which is inclined'away from the flange 14 at the upstream end of the shaft 10 and terminates atits outer end in a radial portion 17.
  • the disc 18 carrying the first-stage rotor blades 19 has an axially-thickened portion 20 to abut the flange'15 of the shaft extension 13, afrusto -conical.
  • the first stage blading 19 is pivoted to the rim 26 of the disc 18 the rim having a number of radial flanges 27 and the rotor b'lading 19 having corresponding lugs 28 on its root portion, the lugs 28 being intercalated with the flanges 27, and the lugs and flanges having pivot pins 29 extending substantially axially through them.
  • the flanges 27 and lugs 28 have their contacting surfaces at right angles to the axes of the pivot pins 29.
  • the hot air is conveyed to the primary manifold 24 from any convenient source, such as the delivery of the compressor, through stationary structure whence it passes in a generally radial direction through slots 20a in the thickened portion 20 of disc 18.
  • the hot-air is conveyed from the primary manifold essence 24 to a distributing manifold which is formed by attach ing an annular disc 30 to the blade-carrying disc 18.
  • the manifold-forming disc 30 has at its inner radius a radial portion 31 which abuts the radial portion. 22 on the blade-carrying disc 18, and the bolts 32 which hold the manifold-forming disc 30 in position are those which extend through the outer radial portions 22, 17 of the blade-carrying disc 18, and the shaft extension 13.
  • the manifold-forming disc 30 has an axial portion 33 extending from the outer radius of the radial por tion 31 and at the end of the axial portion a further radial portion 34 which extends outwardly into contact with a short axial flange 35 provided at the outer periphery of the upstream radial flange 27.
  • the axial portion 33 is sufliciently flexible for the centrifugal loads experienced in operation to cause a good seal to be maintained between the manifold-forming disc 30 and the short axial flange 35.
  • the inner radial portion 31 of the manifold disc 30 has a number of radial channels 36 cut in it between its bolt holes, the channels stopping short of its inner periphery, and drillings 37 are formed in the bladecarrying disc 18 to connect the channels 36 with the interior of the triangular-section primary manifold 24.
  • the fluid flows from the primary manifold 24 through the drillings 37 and the channels 36 into a space 38 between the inner surface of the blade-carryingdisc rim 26, and theaxialportion 33 and inner part of the secpnd radial portion 34 of the manifold-formingdisc 30.
  • the wan a sw m-44 .31 n f q min gd 30 ha's a gihmber of lands -39 "extending axia llyf from it, the number spacing of thelarids lgeing -e'g fiiahtp the number andspacing of the'piv ot pins 29.
  • thejassofciat d pivot the fpivdtpin-receiVi'ng holes in the upstream radial flange-27 are sealed 01f fr'om 't'he fluidjnianifold 38.
  • the upstream radial flange 27 is "formed with a number Tof holes 41 ( Figures 1 and 4) which extendto its downstream surface to aflord'the outlets from the manifold. These holes are assertion; the pivsrpin'hales "in the flange 21.
  • Each of the first-stage'rotorblades' has its drilling 25 runningflengthwisjeth'ereof adjacent iis le'adirig edge and the drilling extends into '.the rderponi n 'to terminate radially outside thepiu'ot pin hols in the lugs 2 8 and there 'is a short "axially-extending 'drillin'g 142 'to "the lower e'rid er the "main'drilli'rig 2s 'ffdm a' point in the upstream face of'the upstream lug 28'50 dimensioned and arranged as to "overlap the' correspondiri-g'outlt hole 'ferred into the 'pas's'ag'es'in the blades 19, regardls's' fof the"angularpbsitionof the blades about'theirfpivot axes at any given'in'stant'in operation.
  • a small groove 44 ( Figures 1 and 4) is formed in the upstream face of the lug around the opening of the drilling 42, and the groove is placed in communication with the space radially outside the disc rim. In this way any leakage fluid may escape freely, and it is arranged that the area of the face around the drilling, within the groove, is such that the load which may be applied to it by the pressure of the fluid is much less than the forward axial load on the blade.
  • the com pressor rotor comprises .a central-hollow shaft 50, and in this case all the rotor discs 51, including that carrying the first-stage rotor blading, are splined on the shaft '50 with spacer rings 53 between'their rims 54.
  • the 'splined connection for the first-stage disc's! is shown :at -52.
  • the-upstream face-of the lug 58on the blade and the downstream face of the upstream radial flange 55 are arranged'to be-square with'the axis-of -the-pivot;pin 56, thus to make a truefacejo int.
  • I Hot-.airis-fedto the inlet-drilling 60-in the-following The front end of the rotor shaft is mounted in-a bearing accommodated withina bearinghousing-fl which is formed witha. pair of radially-spaced annularflanges 50 62 which extend axially from the bearing housing towards the first-stage blade-carrying disc 51.
  • a hot air supply passage 63 in the bearing housing leads to the space between the two flanges.
  • v I Co-operating withthe twolflanges 62 are a pair of labyrinth seal members 64, of which member 64 is .formed-on-the blade-carrying-disc adjacent its centre and mgr-operates. with -the .innersurface of :the innermost of the;two-fianges-.62, .and member 65 is formed at the inner periphery of a manifold-forming disc 66 and co- 5" -operates-with the inner surface of the outermost flange 62.
  • iThemanifold-forming disc 66 is-secured by radiallys'p'acedsets'of bolts 67 to the bIade-carrying-dis'c-SI on the upstream sidethereof, and the blade-carrying disc 65 -51 and the manifold forming 'disc 66 are formed with abutting bosses 68, 69 where the bolts pass through them 'so that the greater part of these-discs are 'Spacedapart *arid the space 70 between thediscs' communicates with thespace between'the tWo flanges'GZ on thebea'rin'g hous- 7G ir'igtoreceive hot air'therefrom.
  • Towards itsouter" dge'th'e manifold-forming disc 66 isifraiike d 'in'section to follow the 'contour'of'the' blade- "carryin disc 1 'r-im' 54 and to have an axially-extending portion71,1 which-is spaced radially inwards of'the inner surface of the-blade-carryingdisc rim-'54,'and a radial portion 72 which extends outwardly alongside the upstream radial flange 55 on the rim 54.
  • the manifold-forming disc 66 forms the upstream wall of the hot air distribution manifold and the radial portion 72 has at its outer edge a thickened bead 73 which projects towards the upstream radial flange 55.
  • a ring 74 having substantially the same radial extent as the radial portion 72 of the disc 66 is secured to the radial portion 72 to be between it and the radial flange 55.
  • the ring 74 has an outer peripheral portion in contact with and welded to the head 73 and an inner peripheral portion 75 extending axially towards and into contact with the radially inner edge of the blade-carrying disc rim 54.
  • the ring 74 is of corrugated form with the corrugations extending radially and thus both surfaces of the ring 74 have a series of circumferentially-alternating lands and grooves which extend from its inner edge to close to its outer edge.
  • the lands 76 projecting from the upstream face of the ring abut and are welded to the downstream surface of the radial portion 72 of the manifold-forming disc 66, and the intermediate parts, which afford the grooves on the upstream face of the ring 74, have adjacent their outer ends holes 77 ( Figures 5, 6 and 7) which run through the ring to the downstream surface thereof, and so open to the centres of the lands on the downstream surface of the ring.
  • a number of axially-bored generally cylindrical transfer pieces 78 are provided which fit in the holes 77 in the ring 74 and in aligned holes 79 in the radial flange 55, the transfer pieces 78 having circumferential flanges 80 adjacent their mid-length which limit the axial travel of the pieces 78 by abutting the upstream face of the radial flange 55 or the downstream face of the ring 74.
  • a rotor for an axial-flow fluid machine comprising rotor structure, a ring of blades at the periphery of the rotor structure, each of said blades having a root, pivot pins engaging said roots and said rotor structure pivotally to connect the blades to the rotor structure so as to allow a limited pivotal movement of the blades relative to the rotor structure, said roots having surfaces which are urged into contact with corresponding surfaces of the rotor structure by loads experienced in operation, said blades having internal fluid passages with inlets thereto opening in said surfaces of the roots at positions oflset from the respective pivot pins, and fluid supply means in the rotor structure leading to outlets in said corresponding surfaces of the rotor structure, said outlets overlapping the inlets in the roots, whereby the fluid is transferred from said outlets to said inlets in the blade roots across surfaces maintained in contact by loads acting on the blades in operation of the machine.
  • a rotor for an axial-flow compressor comprising rotor structure having a peripheral flange with a flat downstream-facing surface, there being pivot-pin-receiving holes in the peripheral flange, a ring of blades at the periphery of the rotor structure, each of said blades having a root with a pivot-pin-receiving hole therein, pivot pins extending through the holes in said roots and said peripheral flange of the rotor structure pivotally to connect the blades to the rotor structure and to allow a degree of free pivotal movement of the blades relative to the rotor structure, said roots having flat upstream facing surfaces, both said downstream-facing surface of the peripheral flange and said upstream-facing surfaces of the roots being at right angles to the pivotal axes of the blades, and said surfaces being urged into contact by loads experienced in operation, fluid passages in the blades having inlets thereto opening through said up stream-facing surfaces of the roots at positions offset from the pivot-pin-receiving holes therein
  • a rotor as claimed in claim 2, wherein said manifold means comprises a pair of annular discs secured together to define a manifold space between them, the fluid being fed to the space for distribution, the discs being mounted on the rotor structure in spaced relation to said peripheral flange, and transfer pieces having bores therein which fit in the apertures in the peripheral flange and in aligned apertures in one of the annular discs, the bores serving to convey the fluid from the manifold space to the apertures in the peripheral flange and thus to the inlets in the blade roots.
  • annular discs are sealed together at their outer peripheries, and one of the annular discs is of radially corrugated form to provide alternate lands and grooves, the lands being in contact with the other annular disc and the correspond- I ing grooves forming distributing spaces leading to the apertures in the disc receiving the transfer pieces.
  • a rotor for an axial flow compressor comprising rotor structure having a peripheral flange with aflat downstream-facing surface, there being pivot-pin-receiving holes in the peripheral flange, a ring of blades at the periphery of the rotor structure, each of said blades having a root with a pivot-pin-receiving hole therein, pivot pins extending through the holes in said roots and said peripheral flange of the rotor structure pivotally to com nect the blades to the rotor structure and to allow a degree of free pivotal movement of the blades relative to the rotor structure, said roots having flat upstreamfacing surfaces, both said downstream-facing surface of the peripheral flange and said upstream-facing surfaces of the roots being at right angles to the pivotal axes of the blades, and said surfaces being urged into contact by loads experienced in operation, fluid passages in the blades having inlets thereto opening through said upstream-facing surfaces of the roots at positions offset from the pivot-pin-receiving holes therein

Description

4, L" HAWORTH v BLADED ROTOR FOR AXIAL-FLOW FLUID MACHINE Filed NOV. 28, 1955 4 Sheets-Sheet l BLADED ROTOR FOR AXIAL-FLOW FLUID MACHINE Filed Nov. 28, 1955 4 Sheets-Sheet 2 April 4, 1961 L. HAWORTH BLADED ROTOR FOR AXIAL-FLOW FLUID MACHINE Filed Nov. 28, 1955 4 Sheets-Sheet 3 April 4, 1961 L. HAWORTH 2,978,168
BLADED ROTOR FOR AXIAL-FLOW FLUID MACHINE Filed Nov. 28, 1955 4 Sheets-Sheet 4 United States P a BLADED ROTOR FOR AXIAL-F LOW FLUID MACHINE Lionel Haworth, Littleover, England, assignor to Rolls- Royce Limited, Derby, England, a British company Filed Nov. 28, 1955, Ser. No. 549,430
Claims priority, application Great Britain Dec. 6, 1954 6 Claims. (Cl. 230-132 having pivoted blades are usually provided with radiallyextending peripheral flanges to'receive the blade-mounting pivot pins and the blades have lugs at'their root ends overlapping the .flanges'andalso receiving the pivot pins.
a It is often desirable to supply a fluid to the' bladessof an axial-flow fluid machine; .for instance, in the case of the first-stage blading 'of an axial-flow compressorof an aircraft gas-turbine engine it is often desirable to supply a heating fluid to the blading for the purpose of preventing or reducing ice formation on the blading.
This invention has for an object -to provide a rotor structure for an axiaLflow fluid machine having pivoted blading and improved means whereby a fluid may be supplied to the pivoted blading.
According to the present invention, in a rotor of the type referred to the inlet ends of fluid passages in the pivoted blades and fluid supply passages in the rotor structure meet at positions offset from the respective pivot pins in surfaces of the blade roots and the rotor structure which are urged into contact by loads experienced in operation. j
According to a feature of the present inventiomwhere the blades are pivoted blades of the rotor of an axialflow compressor, the'inlet end of afluid passage in each of a' plurality of the pivoted blades is' arranged 'to open to an upstream-facing surface of'the blade root, the surface being at right angles to the pivotal" axis. of the blade and the passage opening at a position in the root 'oflset from the bore for the pivot pin of't'he blade, an adjacent peripheral flange on the rotor structure is provided with apertures in its downstream-facing surface to overlap 'each of said inlets in the-blade roots, said downstream' surface also being at right angles to the pivotal axis, the upstreamfacing surface of the blade root being held against the downstream-facing surface of the flange by the gas load on the blade, and there is provided an annular manifold as part of the rotor structure to supply fluid to.the apertures in the peripheral flange and thus to the inlets in the blade roots.
, According to one preferred arrangement, an annular disc is secured to the rotor structure, and the annular disc and the peripheral flange by having parts thereof in axial abutment form a manifoldspacel between themf In such a construction it is preferredto arrange that the fluid cannot flow from the manifold through the apertures in the flange for the pivot pins;" for instance the annular disc may be provided withrecessed lands which abut the peripheral flange around the apertures for the pivot pins, so sealing them from the fluid space of the manifold.
2,978,165 Patented Apr. 4, 1961 In another preferred arrangement, a pair of annular discs are secured together to form a manifold space between them, the fluid being fed to the space for distribution, the discs are mounted on the rotor structure in spaced relation to the peripheral flange which has the apertures overlapping the inlets in the blade roots and transfer pieces are provided which flt in the apertures and in aligned apertures in one of the discs to convey the fluid from the manifold space to the peripheral flange and thus to the inlets in the blade roots.
Two embodiments of the invention as applied to an anti-icing apparatus for pivoted blades of an axial-flow compressor of an aircraft gas-turbine engine will now be described. The description makes reference to the accompanying drawings in which:
Figure 1 is an axial section through part of the com- 'pressor,
Figure 2 is a similar view at an angularly spaced location,
Figure 3 is a section on the line III-HI of Figure 2,
Figure 4 is a view in the direction of arrow IV on Figure 1,- parts being broken away, and the section lines Figures 1 and 2 being indicated at I1 and lI-II respectively, 25
Figures 5 and 6correspond to Figures 1 and 2 and show a second-embodiment, Figure 7 is-an enlargement of part of Figure 6, and Figu'i-e 8 corresponds to Figure 4 and shows the section lines forFigures S'and oat VV and VI-VI respectiyely'."" I Referring to Figures 1 to 4 showing the firstembodiment, the rotor of the axial-flow compressor comprises a central hollow shaft 10 on which there are mounted in axially-spaced relation a number of blade-carrying discs (not shown) for the rotor blades of the second and subsequent stages of the compressor, and the peripheries of the discs are/held in spaced relation by spacer rings 11. The upstream end of the shaft 10 has secured to it an axial extension 13, and these parts abut over radial flanges 14, 15 and the radial flanges support the disc 18 carrying the first-stage rotor blades. For this purpose the flange 15 on the shaft extension 13 is axially thickened and is provided with a frusto-conical outward flange 16 which is inclined'away from the flange 14 at the upstream end of the shaft 10 and terminates atits outer end in a radial portion 17. The disc 18 carrying the first-stage rotor blades 19 has an axially-thickened portion 20 to abut the flange'15 of the shaft extension 13, afrusto -conical. portion'21' ext'ending outwards to an outer radial portion 22 whichiabuts' the outer radial portion 17 of the flange 16 and is secured to it. Bolts 23 extend through the thickened portion 20 of the disc and the flange ,15 of the shaft extension 13 and through the radial flang'e 14 on the shaft 10. 'There is thus formed a triangular-section annular'space 24 which is used as a primary manifold for a hot air supply which is to be conveyed to drillings 25 in the first-stage blading 19.
The first stage blading 19 is pivoted to the rim 26 of the disc 18 the rim having a number of radial flanges 27 and the rotor b'lading 19 having corresponding lugs 28 on its root portion, the lugs 28 being intercalated with the flanges 27, and the lugs and flanges having pivot pins 29 extending substantially axially through them. The flanges 27 and lugs 28 have their contacting surfaces at right angles to the axes of the pivot pins 29.
The hot air is conveyed to the primary manifold 24 from any convenient source, such as the delivery of the compressor, through stationary structure whence it passes in a generally radial direction through slots 20a in the thickened portion 20 of disc 18.
" The hot-air is conveyed from the primary manifold essence 24 to a distributing manifold which is formed by attach ing an annular disc 30 to the blade-carrying disc 18.
The manifold-forming disc 30 has at its inner radius a radial portion 31 which abuts the radial portion. 22 on the blade-carrying disc 18, and the bolts 32 which hold the manifold-forming disc 30 in position are those which extend through the outer radial portions 22, 17 of the blade-carrying disc 18, and the shaft extension 13. The manifold-forming disc 30 has an axial portion 33 extending from the outer radius of the radial por tion 31 and at the end of the axial portion a further radial portion 34 which extends outwardly into contact with a short axial flange 35 provided at the outer periphery of the upstream radial flange 27. The axial portion 33 is sufliciently flexible for the centrifugal loads experienced in operation to cause a good seal to be maintained between the manifold-forming disc 30 and the short axial flange 35.
The inner radial portion 31 of the manifold disc 30 has a number of radial channels 36 cut in it between its bolt holes, the channels stopping short of its inner periphery, and drillings 37 are formed in the bladecarrying disc 18 to connect the channels 36 with the interior of the triangular-section primary manifold 24.
The fluid flows from the primary manifold 24 through the drillings 37 and the channels 36 into a space 38 between the inner surface of the blade-carryingdisc rim 26, and theaxialportion 33 and inner part of the secpnd radial portion 34 of the manifold-formingdisc 30. The wan a sw m-44 .31 n f q min gd 30 ha's a gihmber of lands -39 "extending axia llyf from it, the number spacing of thelarids lgeing -e'g fiiahtp the number andspacing of the'piv ot pins 29. EachEla nd aszts s ints s aman t t s smit ei i s a is fla e 27.9 2 maq 'sfie 2 a a'central cavity 4t (Figure 2) ,into which-the 'ehd .bf
thejassofciat d pivot the fpivdtpin-receiVi'ng holes in the upstream radial flange-27 are sealed 01f fr'om 't'he fluidjnianifold 38. The upstream radial flange 27 is "formed with a number Tof holes 41 (Figures 1 and 4) which extendto its downstream surface to aflord'the outlets from the manifold. These holes are assertion; the pivsrpin'hales "in the flange 21.
Each of the first-stage'rotorblades'has its drilling 25 runningflengthwisjeth'ereof adjacent iis le'adirig edge and the drilling extends into '.the rderponi n 'to terminate radially outside thepiu'ot pin hols in the lugs 2 8 and there 'is a short "axially-extending 'drillin'g 142 'to "the lower e'rid er the "main'drilli'rig 2s 'ffdm a' point in the upstream face of'the upstream lug 28'50 dimensioned and arranged as to "overlap the' correspondiri-g'outlt hole 'ferred into the 'pas's'ag'es'in the blades 19, regardls's' fof the"angularpbsitionof the blades about'theirfpivot axes at any given'in'stant'in operation. v H
The upstream-face of'tlie upstream lu'gZS o'ft he blade and the downstream face of the upstream radial flange 27 'are, as 'statedabovefmadesquare'withthe axisoftlie associated pivot'pin 29. 'No'w, although there 'willbea small axialcleara'nce 'between'the radial flanges 27' on the disc rim 26 and the lugs '28 onthe"rotor blades 19 through whichthe fluid might leak, theresultant'force acting-axially on the blades 19 due to the pressure rise across them willurge the squared surfaces intocontact to give a'true face joint which does not prevent pivot- -ing of the blades-19 whilst-substantially"avoiding fluid disturbance, thereby tending to blow the lug and flange apart, a small groove 44 (Figures 1 and 4) is formed in the upstream face of the lug around the opening of the drilling 42, and the groove is placed in communication with the space radially outside the disc rim. In this way any leakage fluid may escape freely, and it is arranged that the area of the face around the drilling, within the groove, is such that the load which may be applied to it by the pressure of the fluid is much less than the forward axial load on the blade.
In operation, when his desired to prevent or reduce ice formation on the first-stage rotor blading 19, hot
air is supplied to the triangular-section primary manifold 24, for example from the delivery of a later stage-of the compressor, and it then flows therefrom in the man ner described above into the space between the upstream radial flange 27 and the manifold disc 30. The hot air then flows through the holes 41 in the upstream radial flange 27 into the inlet drillings 42 in the blade roots and thus to the leading edge drillings 25. -In thesecond embodiment (Figures 5 to 8), the com pressor rotor comprises .a central-hollow shaft 50, and in this case all the rotor discs 51, including that carrying the first-stage rotor blading, are splined on the shaft '50 with spacer rings 53 between'their rims 54. The 'splined connection for the first-stage disc's! is shown :at -52.
V -In this construction, the first-stage'blade-carryingdisc ==51=has -a number .ofradial flanges :55 on:its-rim.5-4=with sets of aligned 'holes-in them itosreceiverpivotpins 56 tby fivhich tthenrotor blading is connected to :the disc. eEach-d'otor blade :57 has lugs -58,-at -its inner-end :which -arev intercalated with the n'adial-flanges 55 :on the disc 1 -im, 54.and are ?'bored to receive {the associated pivot pin:- 56, and moreover, the bladerris provided with :aljon- 'gitudinal (passageway :59 extending adjacent the --leading-cdgetrom its -:t ip -to within the root-end ofthe ==blade-whereit is met'by a -drilling-60 (Figure 7)from -the.-u pstream face of the upstreamlug 58'to.provide'a.n 4.0 inlet to the passage 59. As 'in'thefprevious construction, the-upstream face-of the lug 58on the blade and the downstream face of the upstream radial flange 55 are arranged'to be-square with'the axis-of -the-pivot;pin 56, thus to make a truefacejo int. I Hot-.airis-fedto the inlet-drilling 60-in the-following The front end of the rotor shaft is mounted in-a bearing accommodated withina bearinghousing-fl which is formed witha. pair of radially-spaced annularflanges 50 62 which extend axially from the bearing housing towards the first-stage blade-carrying disc 51. A hot air supply passage 63 in the bearing housing leads to the space between the two flanges. v I Co-operating withthe twolflanges 62 are a pair of labyrinth seal members 64, of which member 64 is .formed-on-the blade-carrying-disc adjacent its centre and mgr-operates. with -the .innersurface of :the innermost of the;two-fianges-.62, .and member 65 is formed at the inner periphery of a manifold-forming disc 66 and co- 5" -operates-with the inner surface of the outermost flange 62.
iThemanifold-forming disc 66 is-secured by radiallys'p'acedsets'of bolts 67 to the bIade-carrying-dis'c-SI on the upstream sidethereof, and the blade-carrying disc 65 -51 and the manifold forming 'disc 66 are formed with abutting bosses 68, 69 where the bolts pass through them 'so that the greater part of these-discs are 'Spacedapart *arid the space 70 between thediscs' communicates with thespace between'the tWo flanges'GZ on thebea'rin'g hous- 7G ir'igtoreceive hot air'therefrom.
, Towards itsouter" dge'th'e manifold-forming disc 66 isifraiike d 'in'section to follow the 'contour'of'the' blade- "carryin disc 1 'r-im' 54 and to have an axially-extending portion71,1 which-is spaced radially inwards of'the inner surface of the-blade-carryingdisc rim-'54,'and a radial portion 72 which extends outwardly alongside the upstream radial flange 55 on the rim 54.
The manifold-forming disc 66 forms the upstream wall of the hot air distribution manifold and the radial portion 72 has at its outer edge a thickened bead 73 which projects towards the upstream radial flange 55.
A ring 74 having substantially the same radial extent as the radial portion 72 of the disc 66 is secured to the radial portion 72 to be between it and the radial flange 55. The ring 74 has an outer peripheral portion in contact with and welded to the head 73 and an inner peripheral portion 75 extending axially towards and into contact with the radially inner edge of the blade-carrying disc rim 54.
The ring 74 is of corrugated form with the corrugations extending radially and thus both surfaces of the ring 74 have a series of circumferentially-alternating lands and grooves which extend from its inner edge to close to its outer edge. The lands 76 projecting from the upstream face of the ring abut and are welded to the downstream surface of the radial portion 72 of the manifold-forming disc 66, and the intermediate parts, which afford the grooves on the upstream face of the ring 74, have adjacent their outer ends holes 77 (Figures 5, 6 and 7) which run through the ring to the downstream surface thereof, and so open to the centres of the lands on the downstream surface of the ring.
A number of axially-bored generally cylindrical transfer pieces 78 are provided which fit in the holes 77 in the ring 74 and in aligned holes 79 in the radial flange 55, the transfer pieces 78 having circumferential flanges 80 adjacent their mid-length which limit the axial travel of the pieces 78 by abutting the upstream face of the radial flange 55 or the downstream face of the ring 74.
The hot air flows outwards from space 70 into the spaces between the lands 76 and then flows through holes 77, transfer pieces 78 and holes 79 into the inlet drillings I claim:
1. A rotor for an axial-flow fluid machine comprising rotor structure, a ring of blades at the periphery of the rotor structure, each of said blades having a root, pivot pins engaging said roots and said rotor structure pivotally to connect the blades to the rotor structure so as to allow a limited pivotal movement of the blades relative to the rotor structure, said roots having surfaces which are urged into contact with corresponding surfaces of the rotor structure by loads experienced in operation, said blades having internal fluid passages with inlets thereto opening in said surfaces of the roots at positions oflset from the respective pivot pins, and fluid supply means in the rotor structure leading to outlets in said corresponding surfaces of the rotor structure, said outlets overlapping the inlets in the roots, whereby the fluid is transferred from said outlets to said inlets in the blade roots across surfaces maintained in contact by loads acting on the blades in operation of the machine.
2. A rotor for an axial-flow compressor comprising rotor structure having a peripheral flange with a flat downstream-facing surface, there being pivot-pin-receiving holes in the peripheral flange, a ring of blades at the periphery of the rotor structure, each of said blades having a root with a pivot-pin-receiving hole therein, pivot pins extending through the holes in said roots and said peripheral flange of the rotor structure pivotally to connect the blades to the rotor structure and to allow a degree of free pivotal movement of the blades relative to the rotor structure, said roots having flat upstream facing surfaces, both said downstream-facing surface of the peripheral flange and said upstream-facing surfaces of the roots being at right angles to the pivotal axes of the blades, and said surfaces being urged into contact by loads experienced in operation, fluid passages in the blades having inlets thereto opening through said up stream-facing surfaces of the roots at positions offset from the pivot-pin-receiving holes therein, apertures in said downstream-facing surface to overlap each of said inlets in the roots, whereby theifluid is transferred from said apertures to said inlets in the blade roots across surfaces maintained in contact by loads acting on the blades in operation of the machine, and said rotor structure comprising annular fluid supply manifold means connected to supply fluid to the apertures in the peripheral flange and thus to the inlets in the blade roots.
3. A rotor as claimed in claim 2, wherein said manifold means comprises a pair of annular discs secured together to define a manifold space between them, the fluid being fed to the space for distribution, the discs being mounted on the rotor structure in spaced relation to said peripheral flange, and transfer pieces having bores therein which fit in the apertures in the peripheral flange and in aligned apertures in one of the annular discs, the bores serving to convey the fluid from the manifold space to the apertures in the peripheral flange and thus to the inlets in the blade roots.
4. A rotor as claimed in claim 3, wherein the annular discs are sealed together at their outer peripheries, and one of the annular discs is of radially corrugated form to provide alternate lands and grooves, the lands being in contact with the other annular disc and the correspond- I ing grooves forming distributing spaces leading to the apertures in the disc receiving the transfer pieces.
5. A rotor for an axial flow compressor comprising rotor structure having a peripheral flange with aflat downstream-facing surface, there being pivot-pin-receiving holes in the peripheral flange, a ring of blades at the periphery of the rotor structure, each of said blades having a root with a pivot-pin-receiving hole therein, pivot pins extending through the holes in said roots and said peripheral flange of the rotor structure pivotally to com nect the blades to the rotor structure and to allow a degree of free pivotal movement of the blades relative to the rotor structure, said roots having flat upstreamfacing surfaces, both said downstream-facing surface of the peripheral flange and said upstream-facing surfaces of the roots being at right angles to the pivotal axes of the blades, and said surfaces being urged into contact by loads experienced in operation, fluid passages in the blades having inlets thereto opening through said upstream-facing surfaces of the roots at positions offset from the pivot-pin-receiving holes therein, apertures in said peripheral flange opening to said downstream-facing surface thereof, said apertures overlapping each of said inlets in theroots, and an annular disc secured to the rotor structure and co-operating with said peripheral flange to define a fluid manifold space, said apertures communicating with the manifold space, whereby fluid is transferred from the manifold space through the apertures to the inlets in the blade roots across said surfaces which are urged into contact by loads experienced in operation, the annular disc having recessed lands projecting from it into abutment with the peripheral flange around the holes therein for the pivot pins so sealing the holes from the manifold space.
6. A rotor for an axial-flow compressor comprising rotor structure having a peripheral flange with a flat downstream-facing surface, there being pivot-pin-receiving holes in the peripheral flange, a ring of blades at the periphery of the rotor structure, each of said blades having a root with a pivot-pin-receiving hole therein, pivot pins extending through the holes in said roots and said peripheral flange of the rotor structure pivotally to connect the blades to the rotor structure and to allow a degree of free pivotal movement of the blades relative to the rotor structure, said roots having flat upstreamfacing surfaces, both said downstream-facing surface of the peripheral flange and said upstream-facing surfaces or the roots being at right angles to the pivotal axes of the blades, and said surfaces being urged into contact by loads experienced in operation, fluid passages in the from 1the pivot-pin-receiving holes :thenein,:=apertures in vsaid. downstream-facingsurface to overlap each of said .inlets in the roots, whereby the fluid is transferred from said apertures to said inlets in the blade roots across surfaces maintained in contact by loads acting..on the blades inoperation of themachine, and'said rotor structure comprising a annular fluid supply manifold means connected to supply fiuidto the apertures in the peripheral flange and thus to-the" inlets inthe blade roots, and the .upstream-facing surfaces of :the blade roots having each 1 a groove formedthereinaround the. inlet of the respective passage, the :grooves being ni -communication with-the space radially ouisidethe peripherallflange oftthe rotor.
, Reierences Cited in the. tile of; thisapatent UNITED STATES PATENTS 2,568,726 :Franz ..:Sept. 25, 1951 2,599,470 -Meyen June:3, 61952 2,648,520 :;Schmitt rAug-:11,-:-1953 2,656,146 :-.Sollin ger- .-.Oct.-.20, 1953 2,675 ,208 Weinberg Apr.- 13,1954 2,727,716 Feilden Dem--20, :1955 12,819,869 =Meyer. ...'J an. 11,4, :1958
US549430A 1954-12-06 1955-11-28 Bladed rotor for axial-flow fluid machine Expired - Lifetime US2978168A (en)

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US3266770A (en) * 1961-12-22 1966-08-16 Gen Electric Turbomachine rotor assembly
US3362681A (en) * 1966-08-24 1968-01-09 Gen Electric Turbine cooling
US20120093649A1 (en) * 2010-10-13 2012-04-19 Honeywell International Inc. Turbine blades and turbine rotor assemblies

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US3042369A (en) * 1959-02-11 1962-07-03 Gen Motors Corp Pinned blade sealing means
US4759688A (en) * 1986-12-16 1988-07-26 Allied-Signal Inc. Cooling flow side entry for cooled turbine blading

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US2568726A (en) * 1949-08-03 1951-09-25 Franz Anselm Air-cooled turbine blade
US2599470A (en) * 1947-10-22 1952-06-03 Bbc Brown Boveri & Cie Axial flow compressor, particularly for combustion gas turbine plants
US2648520A (en) * 1949-08-02 1953-08-11 Heinz E Schmitt Air-cooled turbine blade
US2656146A (en) * 1948-04-08 1953-10-20 Curtiss Wright Corp Turbine blade construction
US2675208A (en) * 1948-10-11 1954-04-13 Packard Motor Car Co Turbine rotor blade
US2727716A (en) * 1945-12-21 1955-12-20 Power Jets Res & Dev Ltd Bladed body
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US2727716A (en) * 1945-12-21 1955-12-20 Power Jets Res & Dev Ltd Bladed body
US2599470A (en) * 1947-10-22 1952-06-03 Bbc Brown Boveri & Cie Axial flow compressor, particularly for combustion gas turbine plants
US2656146A (en) * 1948-04-08 1953-10-20 Curtiss Wright Corp Turbine blade construction
US2675208A (en) * 1948-10-11 1954-04-13 Packard Motor Car Co Turbine rotor blade
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US2568726A (en) * 1949-08-03 1951-09-25 Franz Anselm Air-cooled turbine blade
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US3266770A (en) * 1961-12-22 1966-08-16 Gen Electric Turbomachine rotor assembly
US3362681A (en) * 1966-08-24 1968-01-09 Gen Electric Turbine cooling
US20120093649A1 (en) * 2010-10-13 2012-04-19 Honeywell International Inc. Turbine blades and turbine rotor assemblies
US8636470B2 (en) * 2010-10-13 2014-01-28 Honeywell International Inc. Turbine blades and turbine rotor assemblies

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GB777612A (en) 1957-06-26
FR1144220A (en) 1957-10-10

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