DE1503254A1 - Seal for hydraulic turbo machines - Google Patents

Description

PATENT LAWYERS

DR.-ING. BY KREISLER DR.-ING. SCHÖNWALD 1503254 DR.-ING. TH. MEYER DR. FUES DR. EGGERT Dl PL-PHYS. GRAVE

COLOGNE !, DEICHMANNHAUS

4.b.19ö4 B / Se

Dominion Engineering Works Limited, 1st Avenue, Lachine, Quebec, Canada.

Seal for hydraulic turbo machines.

In a multi-flow pump, a Francis turbine or Another hydraulic turbomachine with a shrouded rotor means are sometimes provided to the fiäum to keep between the outer sides of the jackets and the adjacent static component filled with air.

In machines of this type, the air has a tendency to escape past the rotor seals, which are provided to prevent excessive leakage of the working medium from the high pressure side to the low pressure side past the rotor.

According to the invention devices are provided to a to prevent such air leakage past these seals.

Have the usual cylindrical gaskets with a small gap proved ineffective at retaining air.

The subject of the invention is a new and improved seal for hydraulic turbo machines, by means of which the Escape of air is prevented.

Another object of the invention is a new and improved seal, which prevents the escape of air,

009838/0002 -2-

BATH ORIGINAL

although it does not require an inconveniently small swivel seat game.

Another object of the invention is a new and improved seal which separates the centrifugal force of the air and the working medium to prevent the air from escaping.

Further features and advantages of the invention emerge from the description below.

In the drawings, various, for example, execution " Approximate forms of the invention shown.

Fig. 1 shows a diametrically perpendicular sectional view of a Francis turbine or turbine pump.

In FIGS. 2 to 7, the part provided with a circle in FIG. 1 is shown on a larger scale.

Fig. 2 shows the preferred embodiment of the invention.

FIG. 3 shows a modified embodiment in which the upward movement of the rotor is less restricted than bfc; i of the embodiment according to FIG. 2.

Fig. 4 shows another modified Ausführungaform, wherein the upper part of the Seal _t is chamfered instead of that shown in Figs. 2 and 3 graded training.

Fig. Ü shows yet another modified embodiment, in which a combination of the beveled and the stepped Training is used.

Fig. B shows a further modified design, in which a completely bevelled design of the Diohtungsflanken is used.

009838/0002

BAD ORiCiNAL

u ¹ ig. 7 shows yet another modified embodiment in which the tapered design according to Pig. 4 is used in a construction that makes a special rotor seal part unnecessary.

In all figures of the drawings like parts are with the the same reference numerals.

If the machine works as a turbine, the water is directed from the inlet housing 10 through stiffening blades 11 and passages 12 onto the rotor 13 as shown in FIG. and discharged via the base ring 32 and the suction pipe 33. The rotor 13 is fastened on the shaft 15. The wave 15 is stored in the guide bearing H. But if the machine does works as a pump, the rotor 13 and the shaft 15 * «4-3λ4-« 2ι aurcn an external force acting on the shaft 15 driven and the water flows in the opposite direction.

It has been found desirable in machines of this type to use a medium of low viscosity and viscosity, usually Air, in the middle of a 4ts3Ä && in the space 16 between the Runner 13 and the upper cover 17, as well as into the space 18 between the runner 13 and the lower cover 19 to be introduced. ' As a result of the rotation imparted to the rotor 13, the air is thrown against the axis of rotation and accordingly against the seals, where the air flows past with the usual designs.

Fig. 2 illustrates in more detail the seal and the adjacent parts of the rotor 13, the lower cover 19 and the Base ring 32.

According to FIG. 2, the rotor 13 is provided with a circumferential sealing ring 2U provided, the lower end Uer runner edge 2 ^

BAD OHiGiNAL

009838/0002

is arranged and within the bore 21 of the lower Cover 19 is. The annular space 23 is the radial gap between the periphery of the sealing ring 20 and the bore

The bing space 22, which has a smaller diameter than the Has Hingraum 23, the radial gap between the Bore 27 of the static sealing ring 34 and the circumference 28 of the rotor edge 29.

Another annular space 25, which is bounded by the horizontal surface of the static sealing ring 34 and the horizontal surface W 31 of the circumferential sealing ring 20, connects the annular space 22 with the annular space 23. The cross section of the annular space 25 is characterized in that the axial dimension is smaller is than the radial dimension.

An annular groove 26 is formed in the bore 21 of the lower cover 19 between the upper and lower ends. cables 24 feed the groove 26 with water under a pressure that is greater than the pressure in the space 18.

Since the cross-section of the annular space 25 has a considerable radial dimension and because the in this annular space contained media is given a rotary movement by the circumferential sealing ring 20 ″, a centrifugal separation takes place of media with different densities, such as air and water, so that in the outer area of the room 25 a permanent water seal is created, which prevents the escape of air from the space 18.

Although the invention is described in its application for sealing air in the lower region of the Franois turbine the same gasket can of course also be used to seal off air in the upper area of the Francis turbine be applied. In addition, the application of the seal according to the invention to a hydraulic masohine of the kind the Francis turbine is only given as an example and it can

009838/0002

BATH ORIGINAL

various modifications, such as those shown in FIGS. 3 to 7, can be applied without to leave the scope of the invention.

The operation of the device is as above Description visible.

009838/0002

Claims (1)

Expectations Hydraulic turbo-machine with a static part, with a rotatable relative to the static part Rotor part, with a working medium that passes through the rotor part and that when passing through the rotor part experiences a change in pressure, the rotor part and the static part having surface sections of different diameters have, with a first device in one of the parts for distributing a medium of relative high density on the outside of the rotor part, with an annulus between the static part and the rotor part, and with a second device which supplies a medium of relatively low density to the annulus, wherein the surface section of larger diameter of the sections of different diameter of the itoborteils a larger one Has Durohmesser than the portion of smaller Durohmesser of the surface sections of different durohmeters of the static part, the pressure of the medium being the first The device and the pressure of the medium of the second device are essentially equal to the highest pressure of the working medium in the rotor and wherein the larger diameter portion of the surface portions of different diameters of the Rotor is on the side of the smaller diameter section of the sections of the static part. 2. Turbomachine according to Anspruoh 1, characterized by a limited gap zone between the rotor part and the static part. 5. Turbomachine according to A _ns p _r uch 2, characterized in that the restricted öpaltzone between the rotor part and the static part lies on the side facing away from the annulus of the first device. 009838/0002 4. Turbomachine according to claim 1, characterized by another restricted gap zone between the rotor part and the static part, that between the Hingraum and the first facility. b. Turbomachine according to Claim 1, characterized by a first establishment in one of the parts that a medium of relatively high density distributed on the sections of different diameters of the rotor part. 6. Device according to one of the preceding claims, characterized by a static part by a relative to the static part rotatably arranged rotor, wherein the atatic part and the rotor are two spaced apart Have surfaces that have two annular gaps of different di ^ uchmessera form, and by a ringiaum between the two Annular gaps, the outer diameter of the annular space a being essentially the same as the "" outer diameter of the larger one Annular gap and the inner diameter of the annulus in the is essentially the same as the inner diameter of the smaller annular gap, as well as by a device that corresponds to the larger one Annular gap supplies a medium. 7. Apparatus according to claim 6, characterized in that | the device from an annular groove in the larger area of the static part. 6. Apparatus according to claim 7, characterized duroh a line which the annular groove with a source of a pressure medium connects. 9. Apparatus according to claim 7, characterized in that the groove lies between the ends of the larger ring gaps. 10. The device according to claim 6, characterized duroh a > first annular space between the two Rlngepalten, wherein the outer Durohmeαser of the first annular space is essentially the same 009838/0002 is the outer Durciimesaer of the larger Ringapalte and the The inner diameter of the first annular space is essentially the same is through to the inner durometer of the smaller ring gap a device ι which supplies a medium to the larger annular gap, through exnen second annular space between the Kotor and the static part, as well as by a device that gives the second annular space a medium of relatively less Density and viscosity supplies. 11. The device according to Anspruoh 10, characterized by a Device that supplies air of relatively low density and viscosity to the second annulus. BATH ORIGINAL 009838/0002