EP1536102A2 - Rotor for a steam turbine - Google Patents

Abstract

The rotor (2) extends along a rotational axis (5) and has two axially adjoining rotor parts (2a, 2b, 2c) welded together with the welding zone (15) circumferentially enclosing a cavity (18) which is formed from two indentations (16, 17) in the ends of the rotor parts. The cavity forms a constituent part of a cooling duct system (19) through which the cooling vapour flows.

Description

Technical area

The present invention relates to a rotor for a steam turbine for Working steam, having the features of the preamble of claim 1.

State of the art

Such a rotor for a steam turbine is known for example from EP 0 991 850 B1 known and extends along a rotation axis and consists of at least two adjoining rotor parts in the axial direction. There are the two rotor parts on mutually facing axial end faces by means of an in Circumferentially closed circumferential, annular weld zone welded together. In the rotor, a cooling channel system is formed at least one inflow channel, at least one outflow channel and a Cooling channel has. The cooling duct carries cooling steam from at least one Inflow channel to at least one outflow channel. The at least one Inflow channel removes the cooling steam at a position on the rotor surface the working steam and this leads to the cooling channel. In contrast to takes the at least one outflow channel the cooling steam the cooling channel and leads this to or through a cooling zone of the rotor. By a suitable Positioning of the at least one inflow channel and the at least one Outflow channel can be between and inlet and outlet of the cooling channel system be formed a pressure difference sufficient, the cooling steam without additional measures from the at least one steam extraction point to the to promote at least one cooling zone.

In the known rotor, the cooling channel extends concentrically to Axis of rotation. The inflow channels are in the region of a diffuser arranged high-pressure turbine, while the outflow channels in the Center of a double-flow medium-pressure turbine are positioned. The cooling channel extends within the for the high-pressure turbine and the Medium-pressure turbine provided common rotor. This rotor is axial stored between high-pressure turbine and medium-pressure turbine. Accordingly The cooling line extends centrally through this camp. As a consequence of this this bearing is exposed to an increased temperature load, so that additional measures are required to protect this warehouse.

The known rotor is realized according to a so-called "drum construction", that is, the rotor is composed of a plurality of "drums". In such a Drum is a cylindrical or frustoconical Massive body, which basically cavities, such as channels and chambers, one Can contain cooling system. A rotor with drum construction characterizes itself usually by a small number of drums, preferably are designed differently. Each drum is several Assigned to turbine stages. Adjacent drums are usually frontally over the entire surface to each other.

From DE 196 20 828 C1, a one-piece rotor is known which in a twin-flow steam turbine is arranged and also a cooling duct system contains. In this rotor is in the center of the hot steam supply to the jacket Cavity formed, which is closed by means of a lid, wherein the lid simultaneously fulfills a flow guiding function. From this cavity goes on two axially opposite sides in each case an axial cooling channel. The one cooling channel communicates with an inflow channel, which separates the cooling steam a pressure stage that takes a flood. In contrast, the communicates another cooling channel with a discharge channel, the cooling steam of a pressure stage the other flood supplies. The effort to realize this internal cooling is comparatively large, there for the production of the cooling channels first of Cavity formed on the circumference of the rotor and then again must be closed. Unfavorable is also that in the selected positioning of the cavity exactly at that point of the rotor a weakening in the structure is achieved in the operation of the steam turbine is exposed to the highest thermal and high mechanical loads. Furthermore, additional effort is required to restore the cavity to close by means of the appropriate lid.

From EP 0 761 929 A1 a rotor for a gas turbine is known, on which a Compressor, a central part and a turbine part are formed and the consists mainly of individual, welded together rotational bodies, their geometric shape to form axially symmetric cavities leads between the respective adjacent bodies of revolution. In this rotor are one extending around the central axis of the rotor, from the downstream End of the rotor up to the upstream last cavity reaching further, cylindrical cavity and at least two tubes provided, the have different diameters and lengths and at least partly telescopically overlap and in the cylindrical cavity are arranged. The tubes are firmly anchored to a fixed point, wherein the fixed points of the tubes are at axially different locations. The pipes are each provided with at least two through holes in the jacket, wherein at least one opening in the turbine part and at least one opening in the Compressor or middle part is arranged. The openings of the different Tubes overlap in the operating state in the turbine section and in the cold state in the compressor and middle section. In this way, when starting up the turbine The rotor can be warmed up faster while in the operating state Cooling is provided. For preheating or for cooling is doing taken at a suitable compressor stage compressed air and axially one of Pipes supplied.

This known rotor is realized with the so-called "disk construction", that is, the rotor is assembled from a plurality of "slices". The disks correspond disc-shaped bodies, the radially outward axial have protruding edge region, which may be configured in the manner of a sleeve can. The adjacent disks are relatively along the edge regions small annular surfaces to each other. These discs are thus around the aforementioned rotating body. Each disc is different from one Drum only a few, especially in each case only a single turbine stage assigned. Accordingly, a rotor of disk construction consists of a comparatively large number of disks, which also preferably are designed identical. The in a rotor with disk construction realized cavities serve primarily to reduce the inertial forces, However, they can also be used for a cooling system.

Further rotors for gas turbines, which are realized in this disk construction, For example, from DE 854 445 B, DE 198 52 604 A1 and DE 196 17 539 A1 be removed.

Presentation of the invention

The present invention as characterized in the claims deals with the problem for a rotor of a steam turbine the mentioned type an improved embodiment, the in particular with reduced production costs sufficient cooling the respective cooling zone of the rotor, in particular the rotor interior, allows.

According to the invention, this problem is solved by the subject matter of the independent patent Claim solved. Advantageous embodiments are the subject of dependent claims.

The invention is based on the general idea, in a rotor whose Rotor parts for producing the welded joint frontally one each Well, which together in the welded state one of the Sweat zone enclosed cavity, this in the manufacture of the rotor to integrate any existing cavity in the cooling channel system. Through this Measure the cavity or can be said depressions before the Welding of the rotor parts are used to the one or more cooling channels and / or the one or more inflow channels and / or the one or more outflow channels in to introduce the respective rotor part. Additional recesses, on the one hand lead to a material weakening and on the other hand closed again must be dispensable. The effort to realize the internal rotor cooling channel system can be reduced. simultaneously the cavity receives a meaningful double function, which in total the Expenses relative to the formation of the welded joint or the rotor relativized.

Particularly important is the cooling of the rotor center in the area in which the Rotor has a large outer diameter and at the same time there with outside hot working steam is applied. This is often in the field of sealing at the thrust balance piston of the case, by the directly hot working steam flows from the turbine inlet and where at the same time the diameter is especially big.

The cooling effect of a cooling steam flow through bore system (Cooling system) is particularly large if instead of a large bore many small holes are used as cooling channels, because then the of Cooling steam applied cooling duct wall considerably larger. At the same time, the Cross-sectional area of a cooling channel to be small, thus a large Speed of cooling steam reached and thus the heat transfer, so the Cooling effect, is improved. Advantageously, the many cooling channels do not run in the Rotor center, as a piercing of the rotor center, the strength of the Rotor significantly weakens there. For rotor sections with large Outer diameter is the mechanical stress in the rotor center due to the rotor centrifugal force of particular importance. She often hires one Border of the buildable dar. The inventive solution is due to the cooling effect increases the strength of the rotor center and the Baubarkeitsgrenzen be in the direction of higher temperatures of the Working steam and larger rotor diameter shifted.

Particular advantages also result for a rotor consisting of at least three Rotor parts is manufactured and accordingly two welding zones and two Includes cavities. The two cavities can then pass through at least one Cooling channel to be interconnected, while the at least one Inflow channel at the one cavity ends and the at least one outflow channel at the other cavity begins. In this construction, the cavities form quasi Nodes that control the communication between the at least one Cooling channel and the at least one inflow channel on the one hand and the on the other hand make at least one outflow channel. By the connection the at least one inflow channel and the at least one outflow channel each to one of the cavities, it is also possible, the at least one Cooling channel only in the middle rotor part of the three rotor parts form what the Reduced effort to realize the cooling duct system.

Other important features and advantages of the invention will become apparent from the Subclaims, from the drawings and from the associated Description of the figures with reference to the drawings.

Brief description of the drawings

Fig. 1 bis 5

jeweils einen stark vereinfachten Längsschnitt durch eine einflutige Dampfturbine mit zweiteiligem geschweißten Trommelrotor nach der Erfindung bei unterschiedlichen Ausführungsformen,

Fig. 6

einen stark vereinfachten Längsschnitt durch eine einflutige Dampfturbine mit dreiteiligem geschweißten Trommelrotor nach der Erfindung,

Fig. 7 bis 9

jeweils einen stark vereinfachten Längsschnitt durch eine zweiflutige Dampfturbine mit dreiteiligem geschweißten Trommelrotor nach der Erfindung bei verschiedenen Ausführungsformen.

Preferred embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components. Show, in each case schematically,

Fig. 1 to 5

in each case a greatly simplified longitudinal section through a single-flow steam turbine with two-part welded drum rotor according to the invention in different embodiments,

Fig. 6

a highly simplified longitudinal section through a single-flow steam turbine with three-piece welded drum rotor according to the invention,

Fig. 7 to 9

in each case a greatly simplified longitudinal section through a twin-flow steam turbine with a three-part welded drum rotor according to the invention in various embodiments.

In all figures, only the inner housing and the rotor are shown, but not the outer casing.

Ways to carry out the invention

The invention will be described below with reference to exemplary embodiments and FIGS. 1 to 9 explained in more detail.

According to FIG. 1, a steam turbine 1 comprises a rotor 2, which is connected to its Axial ends 3 and 4 is mounted rotatably about a central axis of rotation 5. Of the Rotor 2 is arranged centrally in a housing 6, which has a plurality of guide vanes 7 carries. Correspondingly, the rotor 2 carries a plurality of blades 8, wherein the blades 8 and the vanes 7 in pairs the turbine stages 9 of Form steam turbine 1. As is known, a steam turbine 1 operates with steam as a working medium, also called working steam. The housing 6 contains a Inflow space 10, the tensioned steam is supplied and of which the Steam to the first turbine stage 9 of the steam turbine 1 is performed. Of the Relaxed steam is discharged at an outlet 11 of the housing 6. Arrows 12 symbolize the main flow of the steam through the steam turbine 1.

The rotor 2 is designed in several parts and has in the embodiments of Fig. 1 to 5 each have two rotor parts 2a and 2b, the one another in the axial direction limits. The rotor 2 is here designed as a "drum rotor" 2, that is, the rotor 2 is realized according to the drum construction. The individual rotor parts 2a, 2b form while the "drums" of the drum rotor 2. They are characterized by their massive Construction with large material thickness in the radial and axial directions.

The two rotor parts 2a, 2b are welded together. For this purpose is on mutually facing axial end faces 13 and 14 of the rotor parts 2a, 2b a welding zone 15 is formed, which extends in the circumferential direction and thereby closed circulates. In this way, the welding zone 15 receives a annular shape.

To form this weld zone 15, the two rotor parts 2a, 2b at their End faces 13, 14 each with a recess 16 or 17 of any shape Mistake. When assembled, the two complement each other Recesses 16, 17 to a cavity 18. This cavity 18 is thus of the Welding zone 15 circumferentially enclosed.

The rotor 2 is also equipped with an internal cooling channel system 19, which allows partially relaxed and thus partially cooled steam can be seen at a position on the rotor surface 20 and this as Cooling steam at least one thermally loaded component of the rotor 2, such as z. B. a thrust balance piston 21 supply. Accordingly, it is the cooling steam around the same medium as the working steam. The Cooling channel system 19 comprises at least one inflow channel 22 for this purpose Removal of the cooling steam from the working steam at a position on the Rotor surface 20 at a suitable turbine stage 9. In the present Case, two such inflow channels 22 are shown. It is clear that too more than two inflow channels 22 may be provided, in particular can be arranged star-shaped with respect to the axis of rotation 5. Of Furthermore, at least one outflow channel 23 is provided, which contains the cooling steam by at least one cooling zone, here exemplarily the thrust balance piston 21 and / or to a cooling zone of the rotor 2 or a rotor or Turbine component leads. In the present case are also two outflow channels 23 shown. However, it is also possible for more than two outlet channels 23 be provided, in particular star-shaped with respect to the axis of rotation. 5 can be arranged.

Furthermore, the cooling channel system 19 comprises at least one cooling channel 24, the or together or in each case for at least one inflow channel 22 connect to the at least one outflow channel 23. This way will the cooling steam according to the arrows 25 over the at least one Inflow channel 22 of the respective turbine stage 9 taken over the or Cooling channels 24 the at least one outflow channel 23 is supplied to the Cooling steam in turn the respective cooling zone, z. B. the Schubausgleichskolben 21, supplies. Due to the selected positioning of the Inflowing the inflow channels 22 and the outflow of the Outflow channels 23 is within the cooling channel system 19, a pressure drop, the cooling steam automatically in the desired manner within the Cooling channel system 19 transported.

According to the invention, the cavity 18 is now integrated into the cooling channel system 19. at the embodiment shown in Fig. 1, this is done by the Cooling channels 24 are each connected to this cavity 18. The right illustrated cooling channel 24 is the input side to the inflow channels 22nd connected and output side to the cavity 18. The left Cooling channel 24 is connected to the input side of the cavity 18 and On the output side to the outflow channels 23. In this way, the cavity 18 to a flowed through by the cooling steam component of the cooling channel system 19. Die Cavity 18 forms a kind of distribution node, the cooling steam over one or more channels 22 or 24 is supplied to one or more Channels 23, 24 distributed.

In the embodiment according to FIG. 1, the two cooling channels 24 are each Centric to the axis of rotation 5 in the respective rotor part 2a, 2b designed. The Design of these cooling channels 24 is particularly simple because the rotor parts 2a, 2b before welding in the region of their depressions 16, 17 centrally can be bored to form these cooling channels 24. A additional, alternatively attached depression in the surface of the respective Rotor part 2a, 2b is not required. The inflow channels 22, which are here in the extend substantially radially, can be made in the form of holes become. The same applies to the outflow channels 23, which are here extend diagonally - centrically. In terms of flow direction inside the cooling channel system 19 ends the cooling channel 24 shown on the right Cavity 18, while the cooling channel 24 shown on the left begins at the cavity 18.

The embodiment shown in FIG. 2 differs from that in FIG. 1 shown embodiment in that the rotor part 2a shown on the right no central cooling channel 24, but a plurality of decentralized or with respect to the Rotation axis 5 eccentrically arranged, but parallel to the longitudinal axis extending cooling channels 24 are provided, each with one of Inflow channels 22 communicate. In this construction, the attachment a central cooling channel 24 are avoided, which at certain Rotor designs may be beneficial. The number of right in the rotor part 2a trained cooling channels 24 then corresponds to the number of provided there Inflow channels 22.

In a further embodiment, not shown, also several fan-like arranged inflow channels 22 meet a cooling channel 24.

The embodiment of Fig. 3 differs from the embodiment 2 in that also in the rotor part 2b shown on the left instead a central cooling channel 24 more decentralized or with respect to the Rotation axis 5 eccentrically arranged cooling channels 24 are provided. Also these cooling channels 24 preferably extend parallel to the longitudinal axis of the Rotor 2 and communicate with one of the outflow channels 23. The number the cooling channels 24 in the rotor part 2b shown on the left then corresponds to the number the outflow channels 23 mounted there, which is not necessarily have to be. Also in the left rotor part 2b can at certain Embodiments of the rotor 2, the attachment of several decentralized or eccentric cooling channels 24 with respect to a central cooling channel 24 advantageous be.

As soon as a plurality of cooling channels 24 extend parallel to each other eccentrically, such as this is the case, for example, in the embodiments of FIGS. 2 and 3 this expedient symmetrically distributed in the respective rotor part 2a, 2b arranged, that is, the respective cooling channels 24 are concentric about the axis of rotation 5 arranged around.

In the embodiments of FIGS. 1 to 3, the cavity 18 is quasi between the arranged in the axial direction of successive cooling channels 24. The Inflow channels 22 and the outflow channels 23 can only via the cooling channels 24th communicate with the cavity 18. In contrast, in the case of Embodiment according to FIG. 4, the pitch of the rotor 2 to the position of Outflow channels 23 adapted, that is, the weld zone 15 is compared to the embodiments of FIGS. 1 to 3 in the direction of the respective cooling zone, ie moved here in the direction of the thrust balance piston 21. At this Construction, it is possible, the outflow 23 directly to the cavity 18 connect. Accordingly, the discharge channels 23 begin at this Embodiment on the cavity 18. This means a considerable simplification the production of the cooling channel system 19, as in the left rotor part 2b no Cooling channel 24 must be formed. In the right rotor part 2a is the Cooling channel system 19 as in the embodiment of FIG. 1 designed by a central cooling channel 24 is provided which communicates with the inflow channels 22 communicated.

The embodiment shown in Fig. 5 differs from the Embodiment according to FIG. 4 in that in the right rotor part 2a instead the central cooling channel 24 more decentralized or eccentric to Rotary axis 5 arranged cooling channels 24 are provided, each with one of the inflow channels 22 communicate. This can be for certain Embodiments of the rotor 2 may be advantageous.

In the embodiments of FIGS. 4 and 5, the outflow channels 23 are directly on the cavity 18 is connected, while the inflow channels 22 indirectly via the Cooling channels 24 are connected to the cavity 18. Basically, too, is one other embodiment possible, in which the pitch of the rotor 2 so is chosen that the inflow channels 22 connected directly to the cavity 18 can be while the outflow channels 23 then indirectly via one or can be connected to the cavity 18 via a plurality of cooling channels 24. The Welding zone 15 is then in the direction of the removal point of the cooling steam postponed.

In another embodiment, the at least one cooling channel 24 be formed by the cavity 18, with the result that both the inflow channels 22 and the outflow channels 23 are connected directly to the cavity 18.

In the embodiments of FIGS. 1 to 5 have in common that the at least a sampling points, here the respective turbine stage 9, at a position on the Rotor surface 20 is disposed in the region of a rotor part 2a, while the at least one cooling zone, here the thrust balance piston 21, in the area the other rotor part 2b is arranged. This has the consequence that in these Embodiments of the at least one inflow channel 22 inevitably in the a rotor part 2 a is arranged, while the at least one outflow channel 23 is disposed in the other rotor part 2b. The cooling channel system 19 extends thus within the two-piece rotor 2 through both rotor parts 2a and 2b.

While the rotor 2 in the embodiments of FIGS. 1 to 5 in two parts 6 is an embodiment with a three-part rotor 2, wherein the individual rotor parts from right to left denoted by 2a, 2b and 2c are. This rotor 2 is designed as a drum rotor 2. Due to the Three-piece are accordingly two weld zones 15 and thus two Cavities 18 provided. Both cavities 18 are within the meaning of the invention integrated into the cooling channel system 19. The division of the rotor 2 is specifically so chosen that the inflow channels 22 directly with the one cavity 18th communicate, while the outflow channels 23 directly with the other cavity 18th communicate. The two cavities 18 are then over the at least one Cooling channel 24, here connected to each other via at least two cooling channels 24. This targeted division of the rotor 2 simplifies the integration of the Cooling system 19 in the rotor 2. Because both for the training of Inflow channels 22 as well as for the formation of the outflow channels 23 can simple holes are provided by the respective sampling point or lead from the respective cooling zone to the respective cavity 18. Furthermore, the one or more cooling channels 24 by simple Drilling to be made. In the embodiment shown in Fig. 6 are Accordingly, in the rotor part 2a shown on the right only the inflow channels 22 and the rotor part shown on the left 2c exclusively the outflow channels 23rd formed while the central rotor part 2b exclusively or the Cooling channels 24 contains.

In the rotor 2, two or more cooling channels 24 are in the middle rotor part 2b arranged eccentrically. Likewise, an embodiment is possible in which a central cooling channel 24 extends between the two cavities 18. Of In principle, an embodiment is also possible, in which at least one of the welding zones 15 is positioned so that the associated outer Rotor part 2a or 2c neither an inflow channel 22 nor a discharge channel 23rd contains. For example, the welding zone 15 shown on the right can be right next to the cooling steam extraction point be positioned, with the result that the Inflow channels 22 must then be formed in the central rotor part 2b. This construction results in that in the right rotor part 2a then no inflow channel 22 is included. This has the advantage that the right rotor part 2a at all does not need to be machined to the rotor internal cooling channel system 19th train. The same applies to the welding zone shown on the left 15 with regard to the outflow channels 23rd

While in the embodiments of Figs. 1 to 6, the steam turbine 1 einflutig is configured, FIGS. 7 to 9 show twin-flow steam turbines 1. The two Floods are designated 26 and 27 respectively. In this double-flowed Steam turbine 1, the rotor 2 is again in three parts and as a drum rotor. 2 formed, wherein the central rotor part 2b in both floods 26, 27th hineinerstreckt. The division of the rotor 2 is done specifically so that the Welding zones 15 with their cavities 18 are each positioned so that the Inflow channels 22 directly to the one, here to the left cavity 18, and the Outflow channels 23 directly to the other, here to the right cavity 18, can be connected. The two cavities 18 then communicate via the at least one cooling channel 24 with each other. With the help of Cooling channel system 19 can thus cooling steam of the flood 27 shown on the left a specific turbine stage 9 are removed and the blading the other flood 26 shown on the right are supplied. By a suitable Positioning the at least one sampling point and the at least one Return line is created within the cooling channel 19 a sufficient Pressure gradient to drive the cooling steam without additional measures can.

Also in this embodiment, it is clear that by integrating the Cavities 18 in the cooling channel system 19 of the effort to realize the Cooling channel system 19 is relatively low, since the recesses 16, 17 in the End faces 13, 14 of the rotor parts 2a, 2b, 2c, the introduction of the inflow channels 22nd and the outflow channels 23 and the cooling channels 24 considerably simplify.

In the embodiment of FIG. 7, the two cavities 18 through a centrally arranged cooling channel 24 connected to each other. In contrast to are in the embodiment of FIG. 8, the two cavities 18 by two or more with respect to the rotation axis 5 eccentrically arranged cooling channels 24 connected. Appropriately, these cooling channels 24 are around the Rotary axis 5 arranged concentrically distributed around. The number must be the cooling channels 24 neither with the number of inflow channels 22 still with the Number of outflow channels 23 match.

In the embodiments of FIGS. 7 and 8, the inflow channels 22 are in the left shown rotor part 2c, the outflow channels 23 in the rotor part 2a shown on the right and the one or more cooling channels 24 formed in the central rotor part 2b. In principle, it is possible, the axial pitch of the rotor 2 specifically so to mount that the inflow channels 22 and / or the outflow 23rd are also arranged in the middle rotor part 2b. Fig. 9 shows a preferred Embodiment in which both the inflow channels 22 and the Outflow channels 23 are arranged in the central rotor part 2b, in which also the or the cooling channels 24 are formed. With this construction must thus only the central rotor part 2 b are processed to the cooling channel system 19 in the form the entire rotor 2. The effort to realize the Cooling channel system 19 is thereby reduced.

Of course, the invention is not limited to those described Embodiments limited. It is particularly good for the rotor use of steam turbines in which as a working medium hot steam and Cooling steam is used as the cooling medium, but it goes without saying also suitable for the rotor of an air turbine.

LIST OF REFERENCE NUMBERS

1

steam turbine

2

rotor

2a

rotor part

2 B

rotor part

2c

rotor part

3

Axial end of 2

4

Axial end of 2

5

axis of rotation

6

casing

7

vane

8th

blade

9

turbine stage

10

inflow

11

exit

12

mainstream

13

front

14

front

15

welding zone

16

deepening

17

deepening

18

cavity

19

Cooling duct system

20

rotor surface

21

Thrust balance piston

22

inflow

23

outflow channel

24

cooling channel

25

Cooling steam flow

26

flood

27

flood

Claims (13)

Rotor for a steam turbine (1) for working steam, wherein the rotor (2) extends along a rotation axis (5) and consists of at least two rotor parts (2a, 2b, 2c) adjoining in the axial direction, wherein each two rotor parts (2a, 2b, 2c) are welded to one another at axial end faces (13, 14) facing one another by means of a ring-shaped welding zone (15) which is closed in the circumferential direction, wherein in the rotor (2) a cooling channel system (19) is formed which has at least one inflow channel (22), at least one outflow channel (23) and at least one cooling channel (24), wherein the at least one cooling channel (24) leads cooling steam directly or indirectly from the at least one inflow channel (22) directly or indirectly to the at least one outflow channel (23), wherein the at least one inflow channel (22) removes the cooling steam at a position on the rotor surface (20) from the working steam, wherein the at least one outflow channel (23) leads the cooling steam through at least one and / or to at least one cooling zone, characterized, in that, at least in the case of two rotor parts (2a, 2b, 2c), the welding zone (15) encloses a cavity (18) circumferentially, which is formed by two depressions (16, 17), each in the associated rotor part (2a, 2b, 2c) at the front are introduced, in that the at least one cavity (18) forms part of the cooling channel system (19) and through which cooling steam flows. Rotor according to claim 1,
characterized, in that at least one cooling channel (24) communicating with at least one inflow channel (22) terminates at the at least one cavity (18), in that at least one cooling channel (24) communicating with at least one outflow channel (23) begins at the at least one cavity (18). Rotor according to claim 1,
characterized, in that at least one cooling channel (24) communicating with at least one inflow channel (22) terminates at the at least one cavity (18), that the at least one outflow channel (23) begins at this cavity (18). Rotor according to claim 1,
characterized, in that at least one cooling channel (24) communicating with at least one outflow channel (23) begins at the cavity (18), in that the at least one inflow channel (22) ends at this cavity (18). Rotor according to claim 1,
characterized, in that the at least one cooling channel (24) is formed by the cavity (18), that the at least one inflow channel (22) ends at the cavity (18), that the at least one outflow channel (23) begins at the cavity (18). Rotor according to one of claims 1 to 5,
characterized in that the at least one inflow channel (22) extends in one rotor part (2a), while the at least one outflow channel (23) extends in the other rotor part (2b). Rotor according to claim 1,
characterized, that are equipped with at least three rotor parts (2a, 2b, 2c) comprises two weld zones (15) and two cavities (18) provided at a rotor (1), are connected to the two cavities (18) through the at least one cooling channel (24) with each other, in that the at least one inflow channel (22) ends at the one cavity (18), that the at least one outflow channel (23) begins at the other cavity (18). Rotor according to claim 7,
characterized, in that the at least one inflow channel (22) extends in the one outer rotor part (2c) or in the middle rotor part (2b) of the three rotor parts (2a, 2b, 2c), in that the at least one outflow channel (23) extends in the other outer rotor part (2a) or in the middle rotor part (2b) of the two rotor parts (2a, 2b, 2c). Rotor according to one of claims 1 to 8,
characterized, is formed that the steam turbine (1) of single-flow, that the at least one cooling zone has a thrust balance piston (21) of the rotor (2). Rotor according to one of claims 1 to 8,
characterized, that the steam turbine (1) is double-flowed, that the cooling steam is taken from a turbine stage (9) of the one flood (27), in that the at least one cooling zone comprises at least one turbine stage (9) of the other flood (26). Rotor according to one of claims 1 to 10,
characterized, in that the at least one cooling channel (24) extends concentrically to the axis of rotation (5), or in that the at least one cooling channel (24) extends eccentrically to the axis of rotation (5) and substantially parallel thereto. Rotor according to one of claims 1 to 11,
characterized, in that the at least one inflow channel (22) extends substantially radially or diagonally-centrically or diagonally-eccentrically with respect to the axis of rotation (5) such that it meets the cooling channel (24), and / or that the at least one outflow channel (23) extends with respect to the axis of rotation (5) substantially radially or diagonally-centered or diagonally-eccentric so as to strike the cooling channel (24). Rotor according to one of claims 1 to 12,
characterized in that the rotor (2) is constructed according to the drum construction as a drum rotor (2) of a plurality of drums formed by the rotor parts (2a, 2b, 2c).

Images