Apparatus for raising the dynamic performance limit of steam flow and gas flow turbines and compressors
This invention relates to an apparatus for practicing the method of raising the dynamic performance limit of turbines or compressors which are passed through by steam or gas and have contact-free seals arranged in clearances or gaps between rotating and stationary structural components. By a mixing medium introduced into the clearance zone of the contact-free seals, without or with a negative circumferential component, a circumferential component of the clearance flow defined as positive in the sense of rotation of the vector of the natural vibration is correspondingly reduced. A circumferential component of the clearance flow, which is defined as positive in a direction opposite to the sense of rotation of the vibration vector, is correspondingly increased. 
     It is an object of this invention to provide a greatly simplified apparatus for carrying out the above mentioned method. 
    
    
     These and other objects and advantages of the present invention will appear more clearly from the following specification in connection with the accompanying drawings, in which: 
     FIG. 1 shows the configuration according to the invention as applied to the seal in the clearance between the shroud of the wheel and a stationary wall, FIG. 1 showing a cut-out from the longitudinal center section through the rotor axis, and 
     FIG. 2 shows the arrangement according to the invention as applied to the seal in the clearance between the rotor shaft and the inner housing, FIG. 2 being a cut-out from the longitudinal center section through the rotor axis. 
    
    
     The device according to the invention is characterized primarily in that in the ring which carries the seal, there are provided radially or nearly radially directed bores located ahead of the active part of the seal and past one or more preceding throttle elements. The dimensions of said bores and of the preceding throttle elements are so selected that the major portion of the leakage stream is conveyed to said gap through said bores. 
     Referring now to the drawings in detail and FIG. 1 thereof in particular, a non-contacting seal in the form of a labyrinth seal with seal strips 11a, 11b, 11c, 11d arranged in planes perpendicular to the rotor axis and caulked into the ring 10 is provided in the clearance 1 between a non-rotating wall in the form of a split ring 10 supported by the diaphragm structure and the shroud band 3 of the wheel 4 on the shaft of the rotor in a turbine. The labyrinth seal may take the form of any other known labyrinth seal. 
     The ring 10 is so arranged that a radial clearance or gap 13 exists between said ring 10 and the non-rotating part 12 surrounding ring 10 which part 12 may be a part of the diaphragm structure or of the inner or outer casing. Radial holes 14 are provided in the ring 10 in the region between the first -- seen in the flow direction -- strip 11a and the second strip 11b which thus constitutes the start of the active parts of the seal. The purpose of the strip 11a is to discharge the greater part of the clearance flow S 1  originating at a preceding guide vane cascade to thereby prevent this portion from directly entering the clearance 1 and the seal respectively. The portion of the leakage flow so discharged is introduced via the radial clearance 13 and the holes 14 into the region of the seal. 
     The active part 11b, 11c, 11d of the seal may be preceded by several strips (constrictions) serving as deflectors. In such an instance the bores 14 should be located in the region between the innermost strip and the start of the active part of the seal. 
     If an opposing spin is to be generated, the holes 14 should also be disposed with their axes in the perpendicular plane through the rotor axis, but off-radial which is not specifically shown in the drawing. 
     In order to make sure that the greater part of the leakage flow is fed to the seals through the bores 14, conditions have to be selected so that the flow resistance of the preceding or the upstream strip (constriction) N or the upstream strips (constrictions) N&#39; is greater than the flow resistance through the bypass path formed by the bores 14. 
     Along the bypass path through the bores 14, the peripheral component is influenced in the desired sense, i. e. a reduction of the peripheral component of the clearance flow which is defined as positive in the sense or rotation of the vector of the natural vibration, or an increase of the peripheral component of the clearance flow which is defined as positive in a direction opposite to the sense of rotation of the vibration vector. The degree of influence depends on the design data of the specific turbine compressor or pump. However, this dimension can be found without any inventive effort by a person skilled in the design of turbines, compressors, or pumps. 
     The final peripheral component ahead or upstream of the active part of the seal is the peripheral component averaged over the momentums of the two part flows, namely, the greater flow entering through the bores 14 and the flow which directly enters the seal through the clearance between the preceding strip 11a (or the preceding strips) and the shroud band 3. 
     The feature described above may also be combined with the feature set out in detail in U.S. Patent application Ser. No. 562,235 Ambrosch et al filed Mar. 26, 1975 (abandoned) now continuation application Ser. No. 723,913 -- Ambrosch et al filed Sept. 16, 1976 and belonging to the assignee of the present invention providing for the arrangement of flow-controlling means in the region of the seal. 
     The configuration shown in FIG. 2 differs from the aforedescribed typical embodiment in so far as the feature serving to increase the dynamic performance limit (preceding constriction (n); bores) is provided in the clearance between the shaft 16 of the rotor and the seal segment 17 of the inner casing shaft seal. The major part of the clearance flow S 2  coming from the guide vane cascade of the first stage is forced -- because of the upstream strip 11a acting as a throttling element -- to a major extent to enter the sealing zone ahead of the active part (11b, 11c . . .) of the seal through the radial clearance 13&#39; and the bores 14 -- which are arranged and designed as shown by the example in FIG. 1. 
     It is, of course, to be understood that the present invention is, by no means, limited to the specific showing in the drawings but also comprises any modifications within the scope of the appended claims.