Patent GB-701101-A (GB)
Title: Improvements in or relating to gas-turbine engines
Inventor: HUNTER PHILIP EDGAR
IPC: F01D9/04
Filed: 1950-06-29
Abstract: 701,101. Gas turbines. ROLLS-ROYCE, Ltd. June 22, 1951 [June 29, 1950; April 23, 1951], Nos. 16330/50 and 9444/51. Class 110 (3) In an axial flow gas turbine, nozzle guide vanes are hollow and are mounted in series between two stages of rotor blades and cooling air flows inwardly through the guide vanes across the working fluid annulus to clearance spaces between the rotor discs and stationary structure associated with the guide vanes, so as to prevent hot gases flowing over the surface of the rotor disc. The turbine in Figs. 2, 4 and 5 has two rows of rotor blades 10, 11 and an intermediate set of hollow guide vanes 14. The casing comprises outer and inner walls 20, 21 defining a manifold 22 which is supplied with compressed air from a suitable source and from which the air flows through the nozzles 28 into the passages 15 in the guide vanes. The guide vanes have tooth-like projections 23 extending from the outer platforms 14a which engage correspondingly-shaped recesses 24 on the casing wall 21 to locate the blades circumferentially. The platforms 14a have circumferentially-disposed grooves 25 which co-operate with a ring 26 secured to the casing to locate the blades axially. The guide vanes have an inner platform 14b below which extends an elongated root portion 14c, which is also hollow for the flow of cooling air, and at the axiallydisposed sides of which are webs 30. The guide vanes are mounted at their inner ends in a channel-section ring member 32 having a series of horns 34 around the periphery, the tips:of the horns having circumferentially-directed surfaces 34a on which the surfaces 30a on the webs 30 are mounted. Between the bottoms of the horns are circumferentially-directed surfaces 35 on which the surfaces 31 of the root portions are mounted. The guide vanes are held in position by means of ring members 37, 38 which have inclined surfaces 37a, 38a which engage correspondingly inclined surfaces on the axially-extending toes 39 of the root portions 14c, the ring 37 being secured by a further ring-shaped member 40 bolted to the ring member 32, the ring 38 also being secured to the ring member 32 by bolts. A sleeve 49 having an inwardly-directed flange 49a is disposed within the ring member 32 and conical-shaped sealing members 50a, 50b are held in position within the sleeve by a clamping ring 54, the sealing members 50a, 50b at the upstream and downstream sides being spaced apart by a ring 53. Apertures 55 and 56 are formed in the sleeve 49 and ring 53 for the flow of air from the hollow guide vanes. The sealing members 50a, 50b co-operate with projections 51a, 51b on the axially-extending flanges 12a, 13a of the rotor discs 12, 13, the flanges being connected by teeth 12b, 13b, and apertures 57 being formed in the flange 13a for the flow of cooling air to the space between the discs. The air leaks past the sealing means to the spaces 16, 17 and from there it flows through apertures 18, 19 into the working fluid annulus. The pressure drop across the sealing means to the space 16 at the upstream side of the rotor disc is arranged to be less than that across the sealing means to the space 17 at the downstream side. In the embodiment shown in Figs. 7, 11 and 12, the elongated root portions are mounted between two discs 130, 131 having axially-directed flanges which are slotted to form circumferentially-spaced outer and inner recesses 138, 139, the two discs being held apart by means of abutting projections 132 and bolts 133. The root portions 14c have outer and inner circumferentially- and axially-directed faces 136b, 137b, 136a, 137a, which are located within the rectangular recesses 138,139 in the two discs 130, 131, the vanes being located radially by the engagement of axially-extending flanges 142 at the inner ends of the root portions with circumferential grooves 143 in the two discs 130, 131. The two discs taper inwardly and are further held apart by a ring member 144 and bolts 145, the inner parts of the discs having axially-disposed flanges in which is mounted a labyrinth type of sealing means as in the first embodiment. The air from the passages in the guide vanes flows from the space between the two disc portions 130b, 131 b through spaces formed between projections 144a on the spacer ring member 144 into the space within the sealing means as before. The higher pressure rotor disc is formed as a pair of disc members 12d, 12e. In the embodiment shown in Figs. 14, 17 and 18, the elongated blade roots have circumferentially-facing bearing surfaces 236 and the inwardly-facing end of the root portion is formed as a bearing surface 237, axially-disposed inclined surfaces also being formed at 243 at the toes of the root portion. The root portion is mounted between two discs members 230, 231, which are held in spaced relation by an abutment on the disc 231 and bolts, the discs being recessed around the peripheries to form projections 241 with circumferentially-directed bearing surfaces 240 which co-operate with the bearing surfaces 236 on the root portions. A tubular member 239 extends between the two discs and provides a bearing for the inward bearing surface 237 at the bottom of the root portion, the roots being held in position by engagement of the inclined surfaces 242, 245 on the disc 230 and ring member 244 with the inclined surfaces 243 on the toes. The tubular member 239 has slots 247 corresponding to the passages 15 in the guide vanes and is connected to an inner axially-disposed flange 249 by radial flanges 239a, 250, the flange 249 accommodating a sealing means as in the other embodiments. Specification 663;386 is referred to.