EP0097605B1 - Impulsturbine für Überschallströmung - Google Patents

Impulsturbine für Überschallströmung Download PDF

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Publication number
EP0097605B1
EP0097605B1 EP19830630094 EP83630094A EP0097605B1 EP 0097605 B1 EP0097605 B1 EP 0097605B1 EP 19830630094 EP19830630094 EP 19830630094 EP 83630094 A EP83630094 A EP 83630094A EP 0097605 B1 EP0097605 B1 EP 0097605B1
Authority
EP
European Patent Office
Prior art keywords
buckets
bucket
wheel
blank
rim
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP19830630094
Other languages
English (en)
French (fr)
Other versions
EP0097605A2 (de
EP0097605A3 (en
Inventor
Arthur James Miller
Thomas J. Elliott
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Elliott Turbomachinery Co Inc
Original Assignee
Elliott Turbomachinery Co Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Elliott Turbomachinery Co Inc filed Critical Elliott Turbomachinery Co Inc
Publication of EP0097605A2 publication Critical patent/EP0097605A2/de
Publication of EP0097605A3 publication Critical patent/EP0097605A3/en
Application granted granted Critical
Publication of EP0097605B1 publication Critical patent/EP0097605B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/34—Non-positive-displacement machines or engines, e.g. steam turbines characterised by non-bladed rotor, e.g. with drilled holes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines

Definitions

  • the invention relates to a method of manufacturing a turbine wheel from a blank having a rim provided with a circumferential rim surface of a predetermined width, with a symmetrically located groove formed in the rim comprising the steps of:
  • the invention also concerns a turbine wheel comprising:
  • the buckets or blades of turbines are subject to wear or erosion due to a number of factors.
  • a steam turbine prime mover for example, the kinetic energy that is absorbed from the steam by the moving blades or buckets and delivered as shaft work to the device being driven results from the expansion of the steam into the heat of vaporization region resulting in a lowering in the quality of the steam.
  • the buckets or blades become more susceptible to erosion.
  • wet steam is generally associated with the last stages of a condensing steam turbine, the advent of developing geothermal power, and the use of saturated steam boilers for plant heating, for example, have resulted in the supplying of low quality saturated steam at the turbine inlet. Steam qualities ranging from 20% all the way to 100% are typical.
  • the blade erosion is also a function of the velocity and impingement angle of the moisture particles.
  • the buckets are cut relatively deep into the material of the blank.
  • the known buckets are separated from one another by residual metal forming blades between the buckets.
  • the known buckets each have a base wall, a top wall and a side wall.
  • a turbine wheel having similar buckets is also shown in US-A-4. 295 788 and in DE-A-164340.
  • the method of manufacturing the turbine wheel is characterized in that the step of forming a bucket comprises forming the bucket such that the side of the cylinder extends beyond the blank at any circumferential position of the cylinder,
  • the step of sequentially forming additional buckets in the same manner comprises forming the additional buckets such that a side portion of each bucket intersects a base of an adjacent bucket thereby forming a pattern of buckets overlapping one another in the circumferential rim surface of the blank;
  • the turbine wheel is characterized in that the side portions of the buckets are formed by overlapping depressions in the circumferential rim surface of the wheel, the depressions being outwardly open in the rim surface over the complete area of the base of the buckets.
  • the turbine is capable of tip speeds on the order of 305 to 610 m/sec. (1000 to 2000 ft./sec.), depending upon the material used.
  • An overhung design may be used to simplify shaft sealing normally required with a conventional between bearing design.
  • the overlapping buckets are machined into the outer diameter of a solid wheel.
  • the nozzle ring used with the turbine wheel may be of the tangential inflow type with expanding nozzle inserts and low incidence angles for maximum performance. Because of the bucket geometry, moisture droplets or solid particulates moving slower than the gas flow will impinge upon the buckets at low angles, greatly reducing erosion.
  • the inlet and exhaust casings are simply constructed to enable partial to full admission of motive fluid at very high pressures.
  • Each of the buckets is nearly tangential with respect to the wheel and has an overlapping relationship with the adjacent buckets in the machining operation such that the wall of each bucket defines an essentially semicircular pocket or bight made up of a portion of the side and base of a cylinder.
  • Motive fluid is supplied in a generally tangential direction, from points axially spaced from the center of the wheel, such that converging flow in the buckets is along one side of the wall defining the bight and the fluid is turned through approximately 150 to 180° with a transfer of kinetic energy to the wheel before it exits along the other side of the wall defining the bight.
  • the turbine wheel has high moisture and particulate erosion resistance, low windage and low thrust capabilities, and high speed capability to thereby make re-entry unnecessary for normal large heat drop applications.
  • the numeral 10 generally designates the solid wheel of a turbine 100.
  • Wheel 10 is initially formed as a blank such as a forging.
  • the rim of the wheel 10 Prior to the forming of the buckets, the rim of the wheel 10 is preferably profiled by machining an arcuate groove 14 therein, as is best seen in Figure 4.
  • the groove 14 forms a segment of an ellipse, since the buckets are wider than they are deep, so as to reduce the amount of material to be removed in a milling operation.
  • Labyrinth seal lands 12 are machined on the downstream face 11 of wheel 10.
  • the buckets 20 are then individually machined into the profiled groove 14 as by an end mill, by transverse milling or cutting.
  • the milling tool 30 is of a diameter less than the axial extent of the rim of the wheel 10 and tends to machine out a slot terminating in a semicircular opening or pocket with a flat bottom 22, which is best viewed in Figure 4.
  • Flat bottom 22 forms a portion of the base of a cylinder and wall 24 forms a portion of the side of a cylinder.
  • the milling tool 30 goes from the Figure 1 position to the Figure 4 position for each bucket.
  • the axis of the tool 30 is located on a non-diametrical chord preferably such that at point A, which is the top of the rearmost point of the wall 24 of each bucket 20, the wall 24 makes an angle of 10° to 30°, with 15° preferred, with a radius of the wheel 10.
  • each bucket cut taken in isolation, is such that a portion of the tool 30 extends past the rim of wheel 10 at the full depth of the cut. As best shown in Figures 3 and 8 this results in a cut approximating the major portion of a circle, when viewed along the axis of the tool 30 at the full cut, and is of a generally crescent shape after the cutting of the adjacent bucket.
  • Each bucket 20 has a local minimum depth or vertical extent at point A which is in the middle of the bight of wall 24.
  • the vertical extent of wall 24 increases from point A to points B which represent the greatest vertical extent and are the locations where the bight of wall 24 meets the outer rim diameter.
  • the arc BAB forms a portion of an ellipse since it is not parallel to bottom 22.
  • the vertical extent of wall 24 reduces to zero at the ends of the crescent or points C.
  • the numeral 100 generally designates an impulse turbine employing the solid wheel 10 of the present invention.
  • Turbine 100 includes an inlet casing 40 and an exhaust volute casing 44.
  • Inlet casing 40 consists of a short flanged inlet pipe for connection to the steam source on one side and a flange inlet cone 41 on the other end.
  • Inlet casing 40 serves as the connection between the steam source and the turbine.
  • Exhaust volute casing 44 serves as a collector for the exhaust steam and a housing for other turbine components.
  • Wheel 10 is supported in an overhanging fashion by bearing 46 which supports shaft 48.
  • Nozzle ring 50 is supported by turbine casing 42 radially outward of wheel 10.
  • nozzle ring 50 has a plurality of uniformly spaced, generally tangentially discharging passages 52, each having a nozzle 54 located at the inlet end of the passage. Additionally, nozzle ring 50 supports abradable, replaceable seal 56 which separates the inlet and outlet portions of the buckets 20.
  • a normal running clearance of 0.762 to 1.143 mm (.030 to .045 inches) provides the necessary preferred seal for an impulse stage.
  • the bucket configuration of the present invention provides considerable advantages when used with low quality/wet steam or dirty gas.
  • the steam impinging upon the walls 24 of the buckets 20 imparts kinetic energy to the wheel 10 causing it to rotate in the same direction which the steam is supplied.
  • the wheel tip speed is about 40 to 60% that of the steam being supplied by the nozzles 54.
  • wet steam the velocity of the water droplets is much less than that of the steam as well as that of the wheel 10 so that the wheel overtakes the water droplets.
  • the unloaded upstream leading edge of the buckets would overtake and impinge against the water droplets and be eroded thereby.
  • FIG. 9 is a velocity diagram of the steam (gas) and water droplet flow.
  • the wheel velocity u, the relative gas velocity entering the bucket 20, W i , and the absolute gas velocity leaving the nozzle, C 1 form a triangle representing the gas flow.
  • superimposed upon this triangle is a second velocity diagram wherein the wheel velocity, u, the absolute water droplet velocity, C 2 , and the relative water droplet velocity impinging upon bucket bottom 22, W 2 form a second triangle representing the droplet flow.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Claims (5)

1. Verfahren zum Herstellen eines Turbinenrades aus einem Rohling, der einen Rand hat, welcher mit einer Umfangsrandoberfläche vorbestimmter Breite versehen ist, wobei eine symmetrisch angeordnete Nut (14) in dem Rand gebildet ist in folgenden Schritten:
Herstellen einer Schaufel (20) in dem Rand des Rohlings derart, daß die Schaufel (20) einen Teil der Seite und der Basis eines Zylinders bildet, welcher einen Durchmesser hat, der kleiner ist als die vorbestimmte Breite des Randes, und daß wenigstens ein Teil des übrigen Teils der Seite und der Basis des Zilinders sich über den Rohling hinaus erstreckt; und
sequentielles Herstellen von zusätzlichen, gleichabständigen Schaufeln (20) auf dieselbe Weise,
dadurch gekennzeichnet, daß der Schritt des Herstellens einer Schaufel (20) beinhaltet, die Schaufel (20) so herzustellen, daß sich die Seite des Zylinders über den Rohling in jeder Umfangsposition des Zylinders hinaus erstreckt, und
daß der Schritt des sequentiellen Herstellens von zusätzlichen Schaufeln (20) auf dieselbe Weise beinhaltet, die zusätzlichen Schaufeln (20) so herzustellen, daß ein Seitenteil (24) jeder Schaufel (20) eine Basis (22) einer benachbarten Schaufel (20) schneidet, wodurch ein Muster von sich gegenseitig überlappenden Schaufeln (20) in der Umfangsrandoberfläche des Rohlings gebildet wird.
2. Verfahren nach Anspruch 1, dadurch gekennzeichnet, daß jede Schaufel (20) unter einem Winkel gegen einen Radius des Rohlings so hergestellt wird, daß die größte axiale Ausdehnung des Seitenteils jedes Zylinders sich in dem Schnittpunkt des Seitenteils und des Außenumfangs des Rohlings befindet.
3. Verfahren nach Anspruch 2, dadurch gekennzeichnet, daß der Winkel in dem Bereich von 10° bis 30° liegt.
4. Turbinenrad mit:
einem massiven Rad (10), das eine Umfangsrandoberfläche vorbestimmter Breite hat;
mehreren gleichabständigen Schaufeln (20), die in dem Rand gebildet sind;
wobei jede Schaufel (20) einen Teil eines Zylinders bildet, der einen Durchmesser hat, welcher kleiner als die vorbestimmte Breite ist und eine Basis (22) sowie einen Seitenteil (24) hat;
dadurch gekennzeichnet, daß die Schaufeln (20) durch einander überlappende Vertiefungen in der Umfangsrandoberfläche des Rades (10) hergestellt sind, wobei die Vertiefungen in der Randoberfläche in dem gesamten Bereich der Basis (24) der Schaufeln (20) nach außen offen sind.
5. Turbinenrad nach Anspruch 4, dadurch gekennzeichnet, daß der Seitenteil jeder Schaufel axial zu dem Zylinder eine veränderliche Ausdehnung hat und einen Winkel von 20°±10° mit einem Radius des Rades oben in dem hintersten Punkt des Seitenteils bildet.
EP19830630094 1982-06-21 1983-06-02 Impulsturbine für Überschallströmung Expired EP0097605B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US39001482A 1982-06-21 1982-06-21
US390014 1982-06-21

Publications (3)

Publication Number Publication Date
EP0097605A2 EP0097605A2 (de) 1984-01-04
EP0097605A3 EP0097605A3 (en) 1984-10-10
EP0097605B1 true EP0097605B1 (de) 1987-08-19

Family

ID=23540689

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19830630094 Expired EP0097605B1 (de) 1982-06-21 1983-06-02 Impulsturbine für Überschallströmung

Country Status (3)

Country Link
EP (1) EP0097605B1 (de)
JP (1) JPS597701A (de)
DE (1) DE3373119D1 (de)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE68904623T2 (de) * 1988-10-06 1993-07-08 Barmag Barmer Maschf Garn-aufspulmaschine.
JP2581199Y2 (ja) * 1990-04-24 1998-09-21 村角工業 株式会社 医療検査用カセット
GB9218544D0 (en) * 1992-09-02 1992-10-14 Kirby John Turbines
GB2270543B (en) * 1992-09-02 1997-01-15 John Kirby Turbines
CN106368753B (zh) * 2016-11-18 2018-10-12 蔡述强 叶轮加压装置

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE164340C (de) *
FR349490A (fr) * 1904-12-23 1905-05-30 Maschb Actien Ges Union Procédé pour fraiser des poches en forme d'u dans les roues de turbines
US1965817A (en) * 1932-10-24 1934-07-10 Wessel Walter Turbine
GB1416442A (en) * 1972-03-15 1975-12-03 Secr Defence Turbomachinery
JPS4933022A (de) * 1972-08-03 1974-03-26
US4295788A (en) * 1980-03-10 1981-10-20 Terry Corporation Turbine wheel and nozzle arrangement

Also Published As

Publication number Publication date
DE3373119D1 (en) 1987-09-24
JPS597701A (ja) 1984-01-14
EP0097605A2 (de) 1984-01-04
EP0097605A3 (en) 1984-10-10

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