EP2906828A1

EP2906828A1 - Seal of a compressor rotor

Info

Publication number: EP2906828A1
Application number: EP13811905.2A
Authority: EP
Inventors: Thomas MÖNK; Wolfgang Zacharias
Original assignee: Siemens AG
Current assignee: Siemens AG
Priority date: 2012-12-19
Filing date: 2013-12-18
Publication date: 2015-08-19
Anticipated expiration: 2033-12-18
Also published as: DE102012223830A1; WO2014096036A1; CN104870824B; CN104870824A; US9863426B2; RU2643269C2; EP2906828B1; RU2015129079A; US20150330395A1

Abstract

The invention relates to a compressor rotor (1) comprising a pinion shaft (2) which has multiple interconnected segments (3, 4, 5) that are arranged axially one behind the other and comprising a multipart seal (6) which seals the pinion shaft (2). The aim of the invention is to prevent imbalances in the compressor rotor (1) or to allow a centering of a multipart seal (6) sealing element (13) which rotates together with the compressor rotor (1) with as little play as possible. This is achieved in that the pinion shaft (2) has a rotor segment (5) which supports a rotor, a connection segment (5), and a toothed segment (3) arranged axially between the rotor segment (5) and the connection segment (4), said toothed segment (3) having a toothing (9) at each of the two ends (7, 8) of the toothed segment. The toothed segment (3) is held axially between the rotor segment and the connection segment via said toothings by means of corresponding mating toothings (10) at ends (11, 12) of the rotor segment (5) and the connection segment (4), in particular in a centered manner without any play, and a multipart seal (6) sealing element (13) which is connected to the toothed segment (3) in an at least force-fitting manner is arranged on said toothed segment (3).

Description

description

The invention relates to a compressor rotor, in particular for a turbocompressor, such as a gear compressor, with a pinion shaft having a plurality of axially successively arranged segments connected to one another and with a multi-part seal sealing the pinion shaft.

Compressors or fluid compressing devices are used in various industries for various applications involving compression or compression of fluids, especially (process) gases.

Known examples of this are turbo compressors in mobile industrial applications, such as in exhaust gas turbochargers or in jet engines, or even in stationary industrial applications, such as gearbox turbo compressors for air separation.

In such - in its operation continuously working - turbo compressor, the pressure increase (compression) of the fluid is effected in that an angular momentum of the fluid from inlet to outlet by a rotating, radially extending blades exhibiting, of a

Compressor rotor carried impeller of the turbocompressor is increased by the rotation of the blades. Here, i. In such a compressor stage, pressure and temperature of the fluid increase while the relative (flow) velocity of the fluid in the impeller or turbocharger wheel decreases.

In order to achieve the highest possible pressure increase or compression of the fluid, a plurality of such compressor stages can be connected in series.

As types of turbocompressors, a distinction is made between radial and axial compressors. In the axial compressor, the fluid to be compressed, for example a process gas, for example air or carbon dioxide, flows in a direction parallel to the axis (axial direction) through the compressor. In the radial compressor, the gas flows axially into the impeller of the compressor stage and is then deflected outwards (radially, radially). With multi-stage centrifugal compressors, a flow diversion becomes necessary behind each stage.

Combined types of axial and radial compressors draw large volume flows with their axial stages, which are compressed to high pressures in the subsequent radial stages. While mostly single-shaft machines (single-shaft turbo compressor) with a (pinion -) shaft carrying one or more wheels - as a compressor rotor unit hereinafter only briefly

Compressor rotor referred to - are used in (multi - stage) Getriebeturboverdichtern (shortly below also only gear compressor), the individual compressor stages are grouped around a large wheel around, here several parallel (pinion) waves, each one or two - in as

Housing attachments realized, the inflow and outflow to the compressor stages causing, pressure-bearing volute housed - wheels (at free shaft ends of

Pinion shafts arranged turbochargers) wear - as

Compressor rotor unit below only briefly

Compressor rotor means - are driven by a large, stored in the housing drive gear, a large wheel.

In the pressure-bearing volute casing, ie in a cylindrical bore in the volute, a spiral insert is used in such a way that in the cylindrical bore of the volute axially frontally the spiral insert through the spiral housing and the. - In addition to the carried by the pinion shaft impeller or the compressor rotor Spiral insert enclosed space, a so-called annulus, remains over which the fluid - coming from the impeller - flows radially over an expanding cross-section.

About a plant piping, such as a arranged on the volute casing or on (housing) pot pressure pipe with a Druckstutzenflansch arranged thereon, the fluid then flows from the annular space further from the compressor stage.

The inflow of the fluid into the volute casing takes place via a spiral intake flange which is designed as an (axially front-side) housing cover and closes the volute axially.

Such a gear compressor, a gear compressor from Siemens with the name STC-GC or STC-GV, used for air separation, is out

http: // www. energy. Siemens. com / hq / en / compression-expansion-ventilation / turbo-compressors / gearboxes turbo-compressors / bars. htm or http: // www. energy. Siemens. com / hq / en / compaction-expansion-ventilation / turbocharger / gearbox turbocompressor / stcgv.htm (available on 18.12.2012).

The pinion shaft carrying the impeller or the compressor rotor of such a turbocompressor requires - between the process gas to be compressed - to prevent / reduce pressure losses in the compressor stage and / or to prevent the outflow of (possibly dangerous) process gas from the compressor stage (leakage). inside the compressor stage) and an environment outside a seal, which has to meet different requirements depending on the type of process gas and the pressure of the process gas (sealing pressure). It is known for such a seal on the

Pinion shaft arranged - with the pinion shaft co-rotating and / or non-rotating / fixed sealing elements pointing seals, such as labyrinth seals or gas seals.

Labyrinth seals and gas seals, in single or double design, are well known.

In particular, in compressor rotor designs with overhanging impeller masses or in the case of cantilevered impellers, in particular in gearbox compressors, imbalance-related loads, in particular at high levels, are to be reduced

Rotor speed, and resulting damage (especially at high-speed compressor stages) a possible backlash-free centering all - with the compressor rotors - co-rotating components, thereby causing (operating) unbalance shifts the

mitrotierenden components to the axis of rotation of the compressor rotors or to avoid a displacement of the axis of rotation of the rotating components. This applies in particular to co-rotating sealing elements, in particular also of gas seals whose

(co-rotating) masses in particular can also take to impeller masses relevant orders of magnitude. In particular, in gas seals with rotating sealing elements but a centering of the rotating sealing elements only by tight tolerances and / or additional centering is possible. Also, the connection of rotating sealing elements with their support elements can usually not be executed without clearance, whereby a shift of the axis of rotation of the rotating sealing elements is conditionally possible (operating imbalance).

The invention has for its object to provide a seal of a compressor rotor, which ensures a secure seal of the compressor rotor, structurally simple and inexpensive executable and also easy to assemble. Furthermore, the seal should also allow Compressor rotors, especially high-speed

Compressor rotors, if possible to realize without Betriebsunwuchten. These objects are achieved by a compressor rotor unit, hereinafter referred to only briefly as a compressor rotor, having the features according to the independent claim.

The compressor rotor has a plurality of axially successively arranged, interconnected segments having

Pinion shaft and the pinion shaft sealing, multi-part seal, in particular a gas seal, on.

Here, the invention means "axially behind one another" or "axially successively arranged pinion shaft segments" that these pinion shaft segments - in relation to a rotation axis of the pinion shaft and the compressor rotor - in the axial direction of the axis of rotation in - direct or indirect - axial sequence to each other are arranged.

According to the invention, it is provided that the pinion shaft has an impeller segment which can be shown or carried by an impeller, a connection segment and a toothed segment arranged axially between the impeller segment and the connection segment.

The segments may be substantially cylindrical and / or rotationally symmetrical with respect to the compressor rotor axis of rotation / pinion shaft axis of rotation. In particular, the toothed segment can be designed as a substantially cylindrical, rotationally symmetrical hollow body.

According to the invention the toothed segment at its two (axial) ends each have a toothing about which the toothing segment is held by corresponding counter teeth on (axial) ends of the impeller segment and the terminal segment axially between the impeller segment and the terminal segment. In this case, the invention means with "about" - to the toothing - "held corresponding counter teeth" that the toothing (at the axial end of a segment) and the counter-toothing (at the axial end of the other segment) are engaged, creating a positive connection to

Force and motion transmission between the two segments results. If the toothing and the counter toothing are provided, for example, as a Hirth toothing or as a Hirth connection, the toothed segment can thereby be held axially, without play, centered between the wheel segment and the terminal segment.

It is further provided according to the invention that a sealing element of the multi-part seal, for example the gas seal, which is at least frictionally connected to the toothed segment, is arranged on the toothed segment.

Expressed in simple terms, the sealing element which is at least frictionally connected to the toothed segment is one or the part of the seal which (in the operating state) is in contact with the pinion shaft or with the pinion shaft

Compressor rotor co-rotated.

To put it simply and simply, according to the invention, it is provided that the / a part / element of the multi-part seal becomes such a "component" of the pinion shaft through which at least force-locking connection becomes, over which by means of the (bilateral ) Toothing held, in particular by the teeth, in particular by the Hirth toothing, centered durable play, toothed segment - a backlash-free centering of the rotating part / element of the seal is possible.

Additional centering and / or narrow tolerances, as usual, can be saved by the invention or are no longer necessary. (Component -) costs, weight and / or additional assembly steps and / or processing steps are also saved by the invention or are no longer necessary.

The invention thus provides a safe, structurally simple and inexpensive executable and easy to install seal a compressor rotor. Also can be avoided by - possible by the invention - simply realized, backlash-centering (co-) rotating sealing elements Betriebsunwuchten, a rotational axis displacement is not or largely impossible.

Also can be so by the invention higher speeds in the compressor rotor or in such a

Implement compressor rotor having turbo compressor. More efficient turbocompressors can be realized as well.

Also, smaller outer diameter in the (rotating) sealing element (as well as in the seal or their elements in total) can be realized by the invention. This leads to lower circumferential speed on the sealing element. This in turn allows higher speeds to be realized in the compressor rotor.

Preferred developments of the invention will become apparent from the dependent claims.

According to a preferred development, the toothing and / or the counter-toothing is or are designed as a Hirth toothing or Hirth joint. Such a Hirth toothing / connection is easy to manufacture, builds small and allows - with solvability of the two over / connected elements - a backlash centered connection of the elements. More preferably, the pinion shaft sealing, multi-part seal is a gas seal, for example, a single or double gas seal.

According to a further preferred development is another - to the pinion shaft sealing, multi-part seal additional - seal, for example a

Labyrinth seal, which is arranged on the toothed segment provided. As a result, the sealing effect or the sealing of the compressor rotor can be further increased.

Design of the gas seal and the nature and design of the further seal may be selected depending on the process medium and / or the sealing pressure.

According to a further preferred development, it is provided that the sealing element of the multi-part seal which is at least frictionally connected with the toothed segment is formed in a form-fitting or one-piece manner with the toothed segment.

In particular, in the case of a one-piece design of the sealing element with the toothing element, an otherwise necessary separate component can be saved. Otherwise also necessary fits and / or centering with separate execution of the sealing element are no longer necessary. The installation of the compressor rotor is simplified. According to a further preferred development, it is provided that the sealing element of the multi-part seal connected at least in a force-locking manner with the toothed segment has a substantially radial sealing surface with respect to the axis of rotation of the compressor rotor or pinion shaft.

Furthermore, here another, arranged in a, in particular on a housing element, stator, in particular via a spring, substantially axially displaceably arranged sealing element of the multi-part seal can be provided.

This non-rotating sealing element can (likewise) have a substantially radial sealing surface which lies axially opposite the essentially radial sealing surface of the at least non-positively connected with the toothed segment or the co-rotating sealing element of the multi-part seal.

In simple terms, the substantially radial sealing surface of the rotating sealing element and the substantially radial sealing surface of the non-rotating sealing element are in contact with each other in sealing contact with each other, in particular due to the axial displacement of the non-rotating sealing element caused by the spring in the case of a gas seal - a radial sealing gap, in which a gas cushion builds up, and - dense thereby.

With such a radial alignment of the sealing surfaces in the sealing elements of the multi-part seal, a smaller or even smaller outside diameter can thus be realized in the (rotating) sealing element (as in the case of the seal or its elements as a whole). This leads to lower circumferential speed on the sealing element. This in turn allows higher speeds in the

Realize compressor rotor. In addition, a centering or centering elements can be saved as well - as would otherwise be necessary with sealing elements having mutually axial sealing surfaces. Tolerances can be further. The seal is structurally simpler, cheaper and easier to assemble. According to a further preferred development it is provided that the toothed segment - in particular formed as a substantially cylindrical, rotationally symmetrical hollow body - Is arranged on a, in particular against the toothed segment sealed, (cylindrical) sleeve.

This sleeve may have - at one axial end - an axial centering extension, which the sleeve - for ease of assembly of the toothed segment or the

Pinion shaft / the compressor rotor - compared to another pinion shaft segment, in particular with respect to the terminal segment, centered.

For this purpose, the other pinion shaft segment or the connection segment - at its sleeve facing the axial end

- Also have a corresponding axial Zentrierungsfortsatz what about the centering of sleeve and pinion shaft segment or terminal segment can accomplish.

In order to prevent outflow of (process) gas via the teeth of the toothed segment as well as contact surfaces formed by the sleeve (to the toothed segment and / or to the other pinion shaft / connecting segment), it is expedient to place the sleeve against the toothed segment and / or the Seal sleeve against the other pinion shaft (terminal segment).

For this purpose, in particular O-rings may be provided. For this purpose, corresponding circumferential grooves can be provided on the outer circumference of the sleeve (there in the corresponding contact regions of sleeve and toothed segment or sleeve and other pinion shaft / connecting segment) in which the sealing elements or the O-rings are inserted.

It can also be provided that the segments of the plurality of axially successively arranged, interconnected Segments te having pinion shaft are braced by means of an expansion screw, whereby the toothed segment axially between the impeller segment and the connection segment - play and centered - is held clamped. If a gas seal is provided as the multi-part seal, the gas seal can be designed for a gas pressure of approximately 3 bar-5 bar, but also for higher gas pressures of approximately 200 bar-250 bar, such as in carbon dioxide applications.

According to a further development, the impeller is mounted on the fly. That is, the storage of the pinion shaft or the

Compressor rotor takes place on one side of the impeller, whereby the arranged on the impeller segment impeller is located on a free pinion shaft end.

Such bearings are usually for the

Compressor rotors provided by compressor stages in gearbox compressors (overhang stage).

Furthermore, it can preferably be provided that the

Compressor rotor in a turbocompressor, in particular a high-speed compressor, is used. By "high-revving", it may be understood that a rotor speed is approximately in a range of 20,000 rpm - 40,000 rpm or even higher.

Also, the turbo compressor can be a transmission compressor. In other words, in another preferred development, the compressor rotor is installed in a compressor stage in a transmission turbo compressor.

The description of advantageous embodiments of the invention given hitherto contains numerous features which are reproduced in some detail in the individual subclaims. However, those skilled in the art will conveniently consider these features individually and summarize them to meaningful further combinations. In one figure, an embodiment of the invention is shown, which will be explained in more detail below.

It shows:

1 shows a longitudinal section through a section of a

Transmission compressor rotor 1 (part of an overhang stage) with a multi-part pinion shaft 2. Sealing of a compressor rotor of a gear compressor

FIG. 1 shows a longitudinal section through a section of a transmission compressor rotor 1 (briefly described below)

Compressor rotor 1) of a gear compressor 30 with a multi-part pinion shaft second

The compressor rotor 1 can be equipped with both a cantilevered impeller arranged on the pinion shaft 2 (impeller not shown) (an overhang stage of the transmission compressor) and with two cantilevered impellers

Pinion shaft 2 arranged impellers (impellers not shown) (two overhang stages) to be executed.

In a design with two impellers arranged at the respective axial end regions of the pinion shaft 2, FIG. 1 can be seen in half view with only one axial end region of the pinion shaft 2 - with a mirror-inverted representation, not shown, for the other axial end region of the pinion shaft 2 - be seen.

The drive / the rotation of the compressor rotor 1 via a transmission (not shown) which connects by a toothing (not shown), a drive unit, such as a steam turbine or an electric motor, for transmitting power to the pinion shaft 2.

A direct drive of the compressor rotor 1 would be alternative also possible.

In the present case be of a high-speed

Compressor rotor 1 and a high-speed pinion shaft 2 with speeds in the range of about 20,000 rev / min - 40,000 Um / min.

As shown in FIG. 1, the pinion shaft 2 has three segments 3, 4 and 5 arranged axially one behind the other along its rotation / rotation axis 25, with a connection segment 4 of the pinion shaft 2 on the drive side and an impeller (forming the overhang stage) on the drive side (FIG. not shown) bearing impeller segment 5 are arranged in the pinion shaft 2. Axially between the impeller segment 5 and the terminal segment 4 - and rotatably connected to these with each other - another segment 3 of the pinion shaft 2, the toothed segment 3 of the pinion shaft 2, is arranged. Whereas the connection segment 4 is designed as a substantially cylindrical, rotationally symmetrical solid body, the impeller segment (which carries the impeller (not illustrated) and the toothed segment 3 are realized as substantially cylindrical, rotationally symmetrical hollow bodies (sleeves).

The connections between the toothed segment 3 and the impeller segment 5 (axially) on the one hand and the toothed segment 3 and the terminal segment 4 (axially) on the other hand are designed as Hirth connections, wherein at the respective axial ends 7 and 11 of the toothed segment 3 and the impeller segment 5 or 8 and 12 of the toothed segment 3 and the terminal segment 4 a Hirth toothing 9 or the corresponding Hirth counter toothing 10 is introduced.

Within the (through) bore 35 in the hollow cylindrical toothed segment 3 is a toothed segment carry- de / supporting and the toothing segment 3 centering (centering) sleeve 21 is arranged.

The support of the sleeve 21 against the toothed segment 3 via two on the outer circumference of the sleeve 21, integral with the sleeve 21 extensions 38, 39, which contact the inner periphery of the toothed segment 3 in the cylindrical through hole 35. By means of an axial, hollow-cylindrical centering extension 27 on the axial end of the sleeve 21 facing the connection segment 4 - on the one hand - and a corresponding, hollow cylindrical axial centering extension encompassing the hollow cylindrical centering extension 27 of the sleeve 21 - in the mounted state - radially (with fit 31) 28 on the toothed segment 2 facing the axial end of the terminal segment 4 - on the other hand - takes place (during assembly of the

Verdichterrotors) the centering of the toothed segment by inserting / - pushing the sleeve 21 and its centering extension 27 into the centering extension 28 of the terminal segment 4 until the axial end of the sleeve 21 the axial base of the centering extension 28 of the terminal segment 4 contacted - and then by a sliding of the toothed segment 3 on the sleeve 21 until the Hirth toothing 9 engages the toothed segment 3 in the counter toothing 10 on the connection segment 4.

In order to prevent an outflow of (process) gas via the Hirth connections or the Hirth serrations 9, 10 and over the contact surfaces of the sleeve 21 to tooth segment 3 and sleeve 21 to terminal segment 4, the sleeve 21 is against the toothed segment 3 and sealed against the terminal segment 4. For this purpose, the sleeve 21 - in Abstützfortsatz 38 and in

Centering extension 27 - two circumferential grooves 23, in which sealing elements 24, in this case O-rings 24, are inserted. By means of an expansion screw 22 - on the one hand screwed (screw 33) in an (axial) threaded bore 34 in the connection segment 4, performed by cylindrical recesses / bores 35, 36 and 37 in the sleeve-like toothed segment 3, the (sleeve-like) centering sleeve 21 and the sleeve-like Impeller segment 5, on the other hand secured by means of a screwed onto the expansion screw 22 and against a shoulder (not shown) in the sleeve-like impeller segment 5 supporting locking nut (not shown) - are the three segments, ie the terminal segment 4, the toothed segment 3 and Impeller segment 5, braced against each other, whereby the toothed segment 3 is held axially between the impeller segment 5 and the terminal segment 4.

By Hirth connections can - on the one hand - high forces and torques on the / in the pinion shaft 2 are transmitted, on the other hand - can be realized by this a play-free centering 26 of the toothed segment 3 (axially between the impeller segment 5 and the terminal segment 4).

Additional centering elements, as well as tight tolerances on the components are no longer necessary. A rotation-related (centrifugal) displacement of the axis of rotation of the toothed segment 3 or the axis of rotation 25 of the pinion shaft 2 / of the compressor rotor 1, which would lead to an operational imbalance, is prevented.

As FIG. 1 further shows, the sealing of the

Compressor rotor 1 and the pinion shaft 2 - to prevent leakage of process gas from the compressor stage - by means of a simple, several (rotating as fixed / non-rotating) sealing elements 13, 17, 18, 19, 23, 24 having gas seal 6 in conjunction with one

Labyrinth seal 15. This gas seal 6 is - depending on the application - with pressurized sealing gas, for example, from 3 bar - 5 bar or 200 bar - 250 bar, operated. According to this simple gas seal 6, other embodiments or forms of seals or gas seals, for example, a double gas seal, can be provided. A first (- with the pinion shaft 2 and with the

Compressor rotor 1 mitrotierendes -) sealing element 13 of the gas seal 6 is - in the form of an integrally connected to the toothed segment 3, annular circumferential, radially outwardly extending extension 13 - arranged on the toothed segment 3.

The first sealing element 13 of the gas seal 6 integrally connected to the toothed segment 3 thus becomes an integral part of the toothed segment 3 - and thus also part of the pinion shaft 2 or the compressor rotor 1 - and rotates with the toothed segment 3 or the pinion shaft 2 or the compressor rotor 1 with.

The sleeve 21 is provided in the (axial) region of this first sealing element 13 with a very slight shrinkage, which does not allow widening under operating conditions. The occurring centrifugal force supports this effect.

In a housing part 16 of the compressor stage of the gear compressor 30, a stator 31 is accommodated via a fitting 31 as a stationary, non-rotating component 17 of the gas seal 6. Via a bore 32 in the housing part 16 and via this stator 17, the sealing gas flows - under pressure - into a cavity 41 of the gas seal 6 or via the bore 32 in the housing part 16 and via this stator 17, the gas seal 6 is supplied with the sealing gas , In an axial, approximately the radial height of the annular circumferential, radially outwardly extending projection 13 on the toothed segment 3 (rotating member 13 / first seal member 13 of the gas seal 6) arranged annular recess 40 of the stator 17 is - axially displaceable by a spring 19 - Another non-rotating, thus also approximately in the radial height of the annular circumferential, radially outwardly extending projection 13 arranged on the toothed segment 3 component 18 of the gas seal, an annular sealing body 18, respectively.

The axially opposing, radially aligned (sealing) surfaces 14 and 20 of the annular circumferential, radially outwardly extending projection 13 on the Verzahnungsseg- ment 3 and the first seal member 13 and the seal body 18 are as radial sealing surfaces (with appropriately selected materials) educated.

Slidably displaced axially in the direction of the first sealing element 13 via the spring 19, the radial sealing surfaces 14 and 20 of the annular, radially outwardly extending projection 13 on the toothed segment 3 or of the first sealing element 13 and the sealing body 18 are axially opposite each other in sealing contact , wherein a gas cushion 29 builds up in the radial sealing gap (between the radial sealing surfaces 14 and 20).

The sealing of the sliding in the stator 17 seal body 18 relative to the stator 17 via a in a (circumferential) Innenumfangsnut 23 of the seal body 18 inserted seal member 24, here an O-ring 24th

The cavity 41 axially also limiting sitting the

Labyrinth seal 15 centered and precise fit on a step-shaped recess 42 in the housing part 16 - and seals on their labyrinth tips 43, the pinion shaft 2 and the compressor rotor 1 from. Task of the labyrinth seal 15 is the separation of the gas seal 6 of contaminated process gas. Normally, the cavity 41 is supplied with purified gas (process gas).

In the case of radial alignment of the sealing surfaces 14 and 20 or of the radial sealing contact, the gas seal 6 can be smaller due to the smaller outer diameter of the components of the gas seal 6.

As a result, lower circumferential speed occur on the rotating first sealing element 13, which in turn enables higher rotational speeds in the compressor rotor 1.

About the play-free centering 26 of the Hirth connections backlash centered strained Verzahnungsseg- element 3 - so the rotating - integrally connected to the toothed segment 3 - sealing element 13 of the gas seal 6 is centered without play.

Additional centering elements, as well as tight tolerances in the components are no longer necessary here. Also a rotationally induced (centrifugal) displacement of the axis of rotation of the rotating first sealing element 13, which would lead to an operational imbalance, is prevented. (Component cost, weight and / or additional assembly steps

and / or processing steps are also saved by the invention or are no longer necessary.

While the invention has been further illustrated and described in detail by the preferred embodiments, the invention is not limited by the disclosed examples, and other variations can be derived therefrom by those skilled in the art without departing from the scope of the invention.

Claims

claims

1. compressor rotor (1) with a plurality of axially successively arranged, interconnected segments (3, 4, 5) pointing pinion shaft (2) and with a pinion shaft (2) sealing, multi-part seal (6),

characterized in that

the pinion shaft (2) has an impeller wheel (5), a connecting segment (4) and an axially between the impeller segment (5) and the terminal segment (4) arranged toothed segment (3), which toothed segment (3) at its two ends (7, 8) each have a toothing (9), via which the toothed segment (3) via corresponding counter teeth (10) at ends (11, 12) of the impeller segment (5) and the terminal segment (4) axially between the impeller segment ( 5) and the connecting segment (4) is held, and on which toothed segment (3) with the toothed segment (3) at least non-positively connected sealing element (13) of the multi-part seal (6) is arranged net.

2. compressor rotor (1) according to at least one of the preceding claims

characterized in that

the toothing (9) and / or the counter toothing (10) as

Hirth toothing is formed.

3. compressor rotor (1) according to at least one of the preceding claims

characterized in that

the pinion shaft (2) sealing, multi-part seal (6) is a gas seal 6, in particular a single or double gas seal.

4. compressor rotor (1) according to at least one of the preceding claims

signed with

a labyrinth seal (15) which is arranged on the toothed segment (3).

5. compressor rotor (1) according to at least one of the preceding claims

characterized in that

the with the toothed segment (3) at least frictionally connected sealing element (13) of the multi-part seal

(6) form-fitting or integral with the toothed segment

(3) is formed.

6. compressor rotor (1) according to at least one of the preceding claims

characterized in that

the sealing element (13) of the multi-part seal (6) connected at least in a force-locking manner with the toothed segment (3) has a substantially radial sealing surface (14).

7. compressor rotor (1) according to at least one of the preceding claims

signed with

another, in one, especially on one

Housing element (16) arranged, stator (17), in particular via a spring (19), arranged substantially axially displaceable sealing element (18) of the multi-part seal (6), which has a substantially radial sealing surface

(20), which of the substantially radial sealing surface (14) of the at least frictionally with the toothed segment (3) connected to the sealing element (13) of the multi-part seal (6) is axially opposite.

8. compressor rotor (1) according to at least one of the preceding claims

characterized in that

the toothed segment (3) is arranged on a sleeve (21), in particular sealed against the toothed segment (3).

9. compressor rotor (1) according to at least one of the preceding claims

characterized in that

the segments (3, 4, 5) of the pinion shaft (2) having a plurality of axially successively arranged, interconnected segments (3, 4, 5) are braced by means of an expansion screw (22), whereby the toothed segment (3) axially between the impeller segment ( 5) and the terminal segment (4) is held clamped.

10. compressor rotor (1) according to at least one of the preceding claims,

used in a Getriebeturboverdichter (30) or a single-shaft turbo compressor, especially for high-speed

Compressor rotors (1).