CN102418567B

CN102418567B - Turbomachine

Info

Publication number: CN102418567B
Application number: CN201110221937.8A
Authority: CN
Inventors: C·马克; J·佩宾
Original assignee: MAN Diesel and Turbo SE
Current assignee: MAN Energy Solutions SE
Priority date: 2010-07-28
Filing date: 2011-07-28
Publication date: 2015-06-17
Anticipated expiration: 2031-07-28
Also published as: CH703516B1; CN102418567A; DE102010038524A1; CH703516A2; JP2012031842A; DE102010038524B4; KR101188947B1; JP5395106B2; KR20120011315A

Abstract

The invention relates to a turbomachine. The turbomachine has a housing which includes a bearing housing and a working wheel housing, a shaft, a working wheel, and a sealing element. The sealing element includes a first sealing part which seals the housing part of a shaft channel from the bearing housing to the working wheel housing and a second sealing part which is connected with the periphery of the shaft. The sealing element stops the flow channel between the bearing housing and the working wheel housing. The first sealing part is provided with a fluid discharge channel that circulates with a curvature extensively around external periphery of the shaft, so that a fluid bearing housing provided on the first sealing part is adapted to flow off vertically downward along the fluid discharge channel. The fluid discharge channel is provided with a fluid stream guide element on both sides of the shaft, where the fluid bearing housing radially extends from the shaft away from the fluid discharge channel, so the fluid can be prevented from passing through the sealing element.

Description

Turbomachinery

Technical field

The present invention relates to a kind of turbomachinery of preamble according to claim 1.

Background technique

The turbomachinery of the type that known beginning is mentioned from file DE 10 2,007 027 869 A1.Turbomachinery described in this document has Sealing, and the seal blocks at the bearing housing of turbomachinery and active wheel housing between fluid passage.

Summary of the invention

The object of the invention is to, provide the turbomachinery of preamble according to claim 1, in this turbomachinery, anti-fluid passes Sealing more reliably.

This object utilizes turbomachinery according to claim 1 to realize.Define improvement project of the present invention in the sub claims.

According to the present invention, turbomachinery has: with the housing of bearing housing and active wheel housing; Can be rotated to support on the axle in bearing housing; Be connected with axle and be arranged in the active wheel (Laufrad) in active wheel housing; And Sealing, the seal has and defines the first hermetic unit formed from bearing housing to the housing parts of the passage of the axle of active wheel housing and the second hermetic unit be connected with the outer periphery of axle by static, and the seal blocks the fluid passage between bearing housing and active wheel housing.Be in cartridge housing side at the first hermetic unit and be provided with utilization bending (Kr ü mmung) in the mode along periphery the fluid-evacuation groove (Ablaufrinne) of the outer periphery of threaded shaft, thus the bearing housing fluid be applied on the first hermetic unit can along fluid-evacuation groove vertically towards lower outflow.Turbomachinery according to the present invention is outstanding in the following manner, namely, in fluid-evacuation groove, be respectively arranged with fluid stream induction element (Fluidstromleitelement) in the both sides of axle, bearing housing fluid is radially derived in abaxial mode by this fluid stream induction element from fluid-evacuation groove.

Fluid-evacuation groove is arranged to, and avoids the bearing housing fluid (such as lubricant oil) flowed out in the first sealed department office to infiltrate without barrier in Sealing.Bearing housing fluid follows (folgen) fluid-evacuation groove, until it flows out vertically downward.

But, recognized by inventor, by the boundary layer processes (Grenzschichtvorgang) between bearing housing fluid and the first hermetic unit or minimum varying hydrostatics poor, bearing housing fluid-phase follows fluid-evacuation groove to long, thus bearing housing fluid LF is relative to laterally setting (anlegen) disengaging angle to the vertical line at fluid-evacuation groove place be greater than 180 degree.

If by certain environment, the disengaging angle of bearing housing fluid is enough large, then can occur sucking the bearing housing fluid of following fluid-evacuation groove in the vertical lower area of fluid-evacuation groove, and cause the blow-by of Sealing thus.

By arranging fluid stream induction element (bearing housing fluid is radially derived in abaxial mode by this fluid stream induction element from fluid-evacuation groove) respectively in the both sides of axle according to the present invention in fluid-evacuation groove, degree ground like this reduces the disengaging angle of bearing housing fluid, that is, reliably avoid in bearing housing fluid suction seal part.

According to form of implementation of the present invention, each fluid stream induction element has: inflow region, impacts on fluid stream induction element in this inflow region middle (center) bearing shell fluid; And outflow region, bearing housing fluid departs from from fluid stream induction element in this region

According to another form of implementation of the present invention, inflow region is configured to from the bottom surface of fluid-evacuation groove radially away from the form in the inflow face of axle extension.

Utilize this design proposal of the present invention, in a straightforward manner the bearing housing fluid dynamic along fluid-evacuation concentrated flow almost can be derived fully from fluid-evacuation groove, and be introduced into another in the sealing of Sealing on no problem flow direction in.

According to form of implementation of the present invention, inflow region is arcuately to bend with the bending contrary mode of fluid-evacuation groove.

By the preferably relatively large inflow radius realized thus, bearing housing fluid is in flow technique reposefully and reliably flow out from fluid-evacuation groove thus.

According to a form of implementation more of the present invention, flow out region and there is water conservancy diversion edge (Abrisskante), this water conservancy diversion edge at the end away from fluid-evacuation groove of inflow region restriction inflow region, and is arranged in the position of the radially outermost of fluid stream induction element.

Utilize according to this design proposal of the present invention, ensure in a straightforward manner, the bearing housing fluid of deriving from fluid-evacuation groove reliably departs from from fluid stream induction element again, and in the mode of radially outwards dislocation vertically towards lower outflow.

According to another form of implementation of the present invention, flow out region and there is rear guide surface this rear guide surface with the mode extended along the periphery of axle ( welle erstreckend) be connected to water conservancy diversion edge.

Be ensure that by this rear guide surface, continue to guide bearing housing fluid that is residual, that not yet depart from water conservancy diversion edge in the mode of radially outwards dislocation, until it is finally from rear guide surface disengaging and vertically towards lower outflow.

According to form of implementation of the present invention, rear guide surface is to bend to the bending corresponding mode of fluid-evacuation groove.

Any remaining bearing housing fluid is advantageously protected not to be inhaled in Sealing by this way; because the remaining bearing housing fluid radially outwards guided remains in this radially outside level by rear guide surface, until remaining bearing housing fluid is from rear guide surface disengaging and vertically towards lower outflow.

According to another form of implementation of the present invention, in two fluid stream induction elements, the inlet end of each is arranged in the some place limited by the secant (Sekante) of the longest level of fluid-evacuation groove.

This point defines such position, that is, at this position, the bearing housing fluid in fluid-evacuation groove is positioned at radial outermost.This position is arranged in by each inlet end of fluid stream induction element, at time point as well as possible, bearing housing fluid is derived from fluid-evacuation groove, thus the final dislocation realizing the maximum radial direction of bearing housing fluid in radially outer mode, and bearing housing fluid is prevented to be inhaled in Sealing thus more reliably.

Preferably, form the first hermetic unit by sealing cover, settle (ansetzen) to housing place on sealing lid in the mode the side from active wheel housing.In addition preferably, seal configurations becomes non-contacting labyrinth sealing.

Accompanying drawing explanation

Be described in greater detail with reference to the attached drawings the present invention according to preferred form of implementation below.

Fig. 1 shows the longitudinal cross-section view of the schematic perspective of the turbomachinery according to form of implementation of the present invention,

Fig. 2 shows the schematic longitudinal cross-section view of the turbomachinery of Fig. 1,

Fig. 3 shows the view of the amplification in the region of Fig. 1,

Fig. 4 shows the view of the schematic perspective of the turbomachinery of Fig. 1, wherein, shows the fluid stream induction element according to form of implementation of the present invention.

List of reference characters

1 turbomachinery

10 housings

11 bearing housinges

12 active wheel housings

13 active wheel housings

20 active wheels

21 active wheels

30 axles

40 sliding bearings

41 radial bearing linings

50 Sealings

51 first hermetic units

51a fluid-evacuation groove

51b bottom surface

52 second hermetic units

53 interceptions labyrinth (Fanglabyrinth)

54 discharge sides (Abf ü hrkammern)

55 derive groove

56 fluid stream induction elements

56a inflow region

56b flows out region

56c water conservancy diversion edge

Guide surface after 56d

56e inlet end

60 chamber pads (Kammerungsscheibe)

70 bearing housing fluid delivery bore

71 spray-holes

80 lids

The horizontal secant that Smax is the longest

LF bearing housing fluid

GS air-flow

Embodiment

Below with reference to Fig. 1 to 4, the turbomachinery 1 according to form of implementation of the present invention is described.

Turbomachinery 1 can such as be configured to exhaust-gas turbocharger or power turbine.In the form of implementation of the present invention shown in the drawings, turbomachinery 1 is configured to exhaust-gas turbocharger.

As shown in Fig. 1 to 3, turbomachinery 1 has the housing 10 with bearing housing 11 and two active wheel housings 12 and 13.Two active wheel housings (it has outflow housing parts respectively and flows into housing parts) hold active wheel 20 and 21 respectively, wherein, the active wheel 20 on the left side is configured to turbine wheel in FIG, and the active wheel 21 on the right is configured to compressor operating wheel in FIG.For following description, turbine wheel is called the first active wheel 20 and the active wheel housing belonging to it is called the first active wheel housing 12.Correspondingly compressor operating wheel is called the second active wheel 21, and the active wheel housing belonging to it is called the second active wheel housing 13.

In addition, turbomachinery 1 has the axle 30 that to be can be rotated to support on by multiple sliding bearing 40 in bearing housing 11, and this axle 30 makes the first active wheel 20 and the second active wheel 21 be fixedly connected to each other.

Thus it is noted that the feature of power turbine is, there is no the corresponding change of the second active wheel 21 and the corresponding change at housing 10 place and possible supporting place at axle 30.In this case, the moment of torsion transmitted by axle 30 caused due to the step-down (Entspannung) of the waste gas in turbo-side and cooling can be sent to generator by driving mechanism and sentence for generation of electric current.

The outlet port sealing of bearing housing 11 must be left to prevent the air from the second active wheel housing 13 (compressor side) from entering bearing housing 11 and to prevent the waste gas from the first active wheel housing 12 (turbo-side) from entering bearing housing 11 at axle 30 in the turbomachinery 1 one being configured to exhaust-gas turbocharger as shown at this.On the other hand, shaft seal must prevent bearing housing fluid (at this such as lubricant oil) from leaving from bearing housing 11 in the space, wheel side (Restseitenraum) immediately entering compressor and turbine.At this, to radial direction and the requirement of shaft sealing between the exhaust-gas turbocharger of axis mainly distinguish to some extent in exhaust gas side or turbo-side.In addition, (vorstellen) different operating conditions is revealed from the running state Correlation meter of turbomachinery 1 and this different operating conditions occurs after shaft seal.

Show with the view amplified in figure 3 and be configured to non-contacting labyrinth sealed Sealing 50, the seal 50 has the first hermetic unit 51 formed by the static housing parts limiting the passage from bearing housing 11 to the first active wheel housing 12 of axle 30 and the second hermetic unit 52 be connected with the outer periphery of axle 30, and blocks the fluid passage between bearing housing 11 and the first active wheel housing 12.

In the operation of turbomachinery 1, the pressure in the outlet port of the second active wheel 21 is continuity (fortsetzen) in contiguous space, wheel side.Although there is throttling labyrinth part (Drossellabyrinthe) at wheel back (the Radr ü cken) place of the second active wheel 21, there is (anstehen) and have certain overvoltage in bearing housing 11 relatively at Sealing place.The object of the seal is, by enter to the air in bearing housing 11 and thus mass flow loss (seepage (Blow-By)) keep little as far as possible.At this, the low pressure (Unterdruck) before sealing position represents exception or rather, and prevents by correspondingly designing Jian Huolun side, throttling labyrinth space ventilator in addition.Thus, prevent leaving of bearing housing fluid by the overvoltage of sustainable existence before Sealing, this bearing housing fluid loads sealing position in the mode of spraying from bearing housing 11.

In the exhaust-gas turbocharger (turbomachinery 1 as shown in the drawings) of radial direction, be in operation there is similar state in turbo-side.Exhaust gas pressure before the turbine to be propagated in (fortpflanzen) to wheel space, side and was existed before Sealing 50.As long as the rotating speed of the axle 30 of turbomachinery 1 is not less than the certain rotating speed in lower region, these situations just do not change, that is, and sustainable existence superpressure before Sealing 50.

Run in (Nachschmierbetrieb) at so-called interpolation lubricant oil, other situation before Sealing 50 can be appeared at.At this, in static rotor assembly (Laufzeug) (active wheel 20,21 and axle 30), for the sliding bearing 40 of turbomachinery 1 adds lubricant oil, to derive the waste heat of generation.During interpolation lubricant oil, by the effect of stack draft (Kaminzug), low pressure can be there is in the outflow housing parts of the first active wheel housing 12 (turbo-side), wherein, low pressure continuity is until Sealing 50 between the first active wheel housing 12 and bearing housing 11.For this reason, Sealing 50 also must design for this running state.Must prevent, on the direction in the space, wheel side of turbo-side, suck bearing housing fluid by Sealing 50 by pressure difference.

According to the present invention, so design Sealing and adjacent component thereof, that is, reliably prevented bearing housing fluid from being left from bearing housing 11 by axle 30 and enter in the space, wheel side of the first active wheel 20.

In the operation of turbomachinery 1, bearing housing fluid (in this case lubricant oil) loads Sealing 50 in the mode of spraying, and wherein, the bearing housing fluid as bearing oil leaves from the single bearing part of turbomachinery 1.In addition, additional loading by direct (oil) sprocket hole from sliding bearing 40 utilizes the moistening Sealing 50 of bearing housing fluid (in this case spraying oil), wherein, this moistening cooling being used as sealed member, and the coking within Sealing 50 of bearing housing fluid should be prevented thus.At this, overvoltage or low pressure can be there is before bearing housing 11.Can only by bearing oil, only by injection profit oil and by bearing oil and spray oil load Sealing 50 simultaneously.At this, be transported to the temperature and pressure alterable of the bearing housing fluid of sliding bearing 40, this affects amount and the drainage properties (Ablaufverhalten) of the bearing housing fluid on Sealing 50 substantially.

The second hermetic unit 52 of Sealing 50 is formed by (profiliert) axle section of given profile, or as shown in figure 3, on axle 30, before the first active wheel 20 (turbine wheel), form this second hermetic unit 52 with the embodiment of the cover of shrink fit.First hermetic unit 51 of Sealing 50 is formed by the independent component of bearing housing 11, is implemented as sealing cover at this this component.The profile (Profil) of the first hermetic unit 51 and the second hermetic unit 52 forms non-contacting interception labyrinth 53, this interception labyrinth 53 with multiple continuous print seal clearance and discharge side 54 for feature.

As already mentioned, by bearing housing fluid (it is configured to leave the bearing part of radial bearing lining 41 from what directly adjoin at this) splash (bespritzen) Sealing 50.At this, so-called chamber pad 60 can limit the fit on face (Sitz) of floating radial bearing lining 41 on the direction of axis.(oil bumper is caught at fixing radial bearing lining 41 type) situation in, utilize groove to join chamber pad 60 in the side of radial bearing lining 41 to for fixed radial bearing bush 41 (radial bearing lining 41 rotates not together).When radial bearing lining 41 rotates together, chamber pad 60 has the function in the gap of the axis of adjustment radial bearing lining 41, and this rotating speed for radial bearing lining 41 is conclusive.But in both of these case, chamber pad 60 also for serving as a contrast the throttling of the bearing housing fluid flowed out in 41 and in outer lubrication gap from radial bearing, and affects the shock absorbing characteristics of sliding bearing 40 thus fatefully.

In majority of case, the bearing housing fluid also left at the inner diameter of chamber pad 60 thus from radial bearing lining 41 mainly loads the first seal clearance of Sealing 50.But, the region of the less amount (droplet and mist) of the bearing housing fluid also surrounding of moistening first hermetic unit 51 (sealing cover).In order to prevent this less amount of bearing housing fluid in first hermetic unit 51 place's coking, the bearing housing fluid bundle of origin blowing perforation 71 cools this region consciously, wherein, bearing housing fluid bundle impacts (auftreffen) on the first hermetic unit 51 in the upper region of the first hermetic unit 51.Spray-hole 71 passes in the bearing housing fluid delivery bore 70 of radial bearing lining 41.Towards turbo-side, also by additional lid 80 (in this case end cap), the first hermetic unit 51 is separated with the space, wheel side of the first active wheel 20.

As can be found out in the diagram in particular, according to the present invention, be in cartridge housing side at the first Sealing 51 and be provided with circular the bending with the fluid-evacuation groove 51a of the outer periphery of the mode threaded shaft 30 along periphery of utilization, thus the bearing housing fluid LF be applied on the first hermetic unit 51 can along fluid-evacuation groove 51a vertically towards lower outflow.Fluid stream induction element 56 is respectively arranged with in the both sides of axle 30 in fluid-evacuation groove 51a, 56 (only can find out anterior fluid stream induction element in the diagram), bearing housing fluid LF radially derives in the mode away from axle 30 by this fluid stream induction element 56,56 from fluid-evacuation groove 51a.

According to the present invention, fluid stream induction element 56,56 can be realized by combination seal element, seal element at turbomachinery 1 run duration by utilizing the splash continued of bearing housing fluid LF cooled for cooling fully and thus for avoiding fluid coking.In present case, fluid stream induction element 56,56 is attached in the first hermetic unit 51 (sealing cover), and this first hermetic unit 51 represents the Sealing 50 of turbomachinery 1 jointly with the interception labyrinth (the second hermetic unit 52) of axle side.At this, fluid stream induction element 56,56 is arranged in the fluid-evacuation groove 51a of the first hermetic unit 51.Fluid stream induction element 56,56 or can be used as independent component and introduce in fluid-evacuation groove 51a in the both sides of lower derivation groove 55 (see Fig. 3), or such as can be remained solid material (Vollmaterial) at fluid-evacuation groove 51a by time bore hole (Ausdrehen) among course of working.Two schemes all realizes identical function.

According to the present invention, each fluid stream induction element 56 has: inflow region 56a, impacts on fluid stream induction element 56 at this inflow region 56a middle (center) bearing shell fluid LF; And flow out region 56b, in this outflow region, 56b middle (center) bearing shell fluid LF departs from from fluid stream induction element 56.

As may be seen in fig., inflow region 56a is configured to from the bottom surface 51b of fluid-evacuation groove 51a radially away from the form in the inflow face of axle 30 extension, wherein, inflow region 56a is arcuately to bend with the bending contrary mode of fluid-evacuation groove 51a.

In addition, as may be seen in fig., flow out region 56b and there is water conservancy diversion edge 56c, this water conservancy diversion edge 56c is at the end away from fluid-evacuation groove 51a of inflow region 56a restriction inflow region 56a, and this water conservancy diversion edge 56c is arranged in the position of the radially outermost of fluid stream induction element 56.In addition, flow out region 56b and have rear guide surface 56d, this rear guide surface 56d is connected to 56c place, water conservancy diversion edge in the mode extended along the periphery of axle 30, and wherein, rear guide surface 56d is to bend to the bending corresponding mode of fluid-evacuation groove 51a.

Correspondingly, fluid stream induction element 56,56 is configured to be conducive to flowing, that is, there is large radius, to make as far as possible stably to derive bearing housing fluid LF from fluid-evacuation groove 51a at the inflow region 56a place fluid stream induction element 56,56 of the bearing housing fluid LF discharged.In addition, at end (that is, in outflow region 56b) so design fluid stream induction element 56,56, that is, bearing housing fluid LF can not arrive adjacent derivation groove 55 again, and flows out in advance.

As illustrated in the diagram, the bearing housing fluid LF be ejected on discharge launder 51a should derive around sealing position by the fluid-evacuation groove 51a of the first hermetic unit 51.At this, bearing housing fluid LF can impact on Sealing 51 at the one or more arbitrary position of the first hermetic unit 51.According to the present invention, need not by the nozzle of orientation suitably, bearing housing fluid LF be applied on the first hermetic unit 51 consciously, and it is also envisaged that can from coming from the bearing housing fluid LF that flows out bearing portion, from owing to obtaining the moistening of the first hermetic unit 51 from the bearing housing fluid LF of axle 30 centrifugation or other splash effect to the splash of the first hermetic unit 51.

In order to avoid the bearing housing fluid LF flowed out at the profile place of the first hermetic unit 51 infiltrates in real (eigentlich) geometrical construction of Sealing 50 without barrier, realize fluid-evacuation groove 51a by the suitable design of the inner side of the first hermetic unit 51.Bearing housing fluid LF follows this fluid-evacuation groove 51a, until it flows out downwards.But, bearing housing fluid LF is not vertically towards lower outflow at the position of the maximum horizontal secant Smax of fluid-evacuation groove 51a, but the intensity of volume flowrate of air-flow GS (this air-flow GS produces due to the low pressure existed before Sealing 50) depending on bearing housing fluid LF and sucked by Sealing 50 in certain a moment, also follow cylinder or the bottom surface 51b of fluid-evacuation groove 51a.The secant Smax of the longest level of fluid-evacuation groove 51a extends horizontally through the central longitudinal axis of axle 30.

Therefore, bearing housing fluid LF is greater than 180 degree relative to the disengaging angle of the vertical line being laterally set to fluid-evacuation groove 51a place.The reason of this situation is, the impact of the boundary layer processes between bearing housing fluid LF and the first hermetic unit 51 and the minimum hydrostatic pressure difference on the inner side of the first hermetic unit 51.

Due to interception chamber, labyrinth, (it forms the above derivation groove 55 mentioned, this derivation groove 55 is used as to derive the bearing housing fluid LF infiltrated by the first seal clearance of Sealing 50) the hole of radial direction of downward sensing, the air stream sucked or air-flow GS enter (einschlagen) usually by deriving the path of groove 55, because derive groove 55 minimum resistance is reacted on air-flow GS.If due to certain environment (Umstand), the disengaging angle of bearing housing fluid LF is enough large and/or to flow through the air-flow GS of Sealing 50 enough large, then can there is sucking the bearing housing fluid LF following fluid-evacuation groove 51a, and the blow-by of Sealing 50 can be caused thus.

Fluid stream induction element 56 arranged according to the present invention, 56 affect by this way in the discharge of the inner side place of the first hermetic unit 51 and follow the size at the disengaging angle of the bearing housing fluid LF of fluid-evacuation groove 51a, that is, the disengaging angle of the bearing housing fluid LF of outflow reduces significantly.This makes, do not combine with the stream of the bearing housing fluid LF flowed at fluid-evacuation groove 51a (spraying oil) from deriving the bearing housing fluid stream flowed out groove 55, and reliably prevent by by sucking bearing housing fluid LF based on the air-flow GS of Sealing 50.

Especially derive from fluid-evacuation groove 51a safely to realize bearing housing fluid LF or depart from, two fluid stream induction elements 56, in 56, the inlet end 56e of each is arranged in the some place limited by the secant Smax of the longest level of fluid-evacuation groove 51a.

Claims

1. a turbomachinery (1), with: the housing (10) with bearing housing (11) and active wheel housing (12,13); Can be rotated to support on the axle (30) in described bearing housing (11); Be connected with described axle (30) and be arranged in the active wheel (20,21) in described active wheel housing (12,13); And Sealing (50), described Sealing (50) has and defines from described bearing housing (11) to described active wheel housing (12 by static, 13) the first hermetic unit (51) that the housing parts of the passage of axle (30) is formed and the second hermetic unit (52) be connected with the outer periphery of described axle (30), and described Sealing (50) blocks at described bearing housing (11) and described active wheel housing (12,13) fluid passage between

Wherein, described first hermetic unit (51) be in cartridge housing side be provided with utilize bending in the mode along periphery around the fluid-evacuation groove (51a) of the outer periphery of described axle (30), thus the bearing housing fluid (LF) be applied on described first hermetic unit (51) can along described fluid-evacuation groove (51a) vertically towards lower outflow

It is characterized in that, in described fluid-evacuation groove (51a), be respectively arranged with fluid stream induction element (56) in the both sides of described axle (30), described bearing housing fluid (LF) is radially derived in the mode away from described axle (30) by described fluid stream induction element (56) from described fluid-evacuation groove (51a).

2. turbomachinery according to claim 1 (1), it is characterized in that, each fluid stream induction element (56) has: inflow region (56a), impacts on described fluid stream induction element (56) at bearing housing fluid (LF) described in described inflow region (56a); And flow out region (56b), described in described outflow region (56b), bearing housing fluid (LF) departs from from described fluid stream induction element (56).

3. turbomachinery according to claim 2 (1), it is characterized in that, described inflow region (56a) to be configured to from the bottom surface (51b) of described fluid-evacuation groove (51a) the form in the inflow face radially extended away from described axle (30).

4. the turbomachinery (1) according to Claims 2 or 3, is characterized in that, described inflow region (56a) is arcuately to bend with the bending contrary mode of described fluid-evacuation groove (51a).

5. turbomachinery according to claim 3 (1), it is characterized in that, described outflow region (56b) has water conservancy diversion edge (56c), described water conservancy diversion edge (56c) limits described inflow region (56a) in the end away from described fluid-evacuation groove (51a) of described inflow region (56a), and described water conservancy diversion edge (56c) is arranged in the position of the radially outermost of described fluid stream induction element (56).

6. turbomachinery according to claim 5 (1), it is characterized in that, described outflow region (56b) has rear guide surface (56d), and described rear guide surface (56d) is connected to described water conservancy diversion edge (56c) place in the mode extended along the periphery of described axle (30).

7. turbomachinery according to claim 6 (1), is characterized in that, described rear guide surface (56d) is to bend with the bending corresponding mode of described fluid-evacuation groove (51a).

8. turbomachinery according to any one of claim 1 to 3 (1), it is characterized in that, in two fluid stream induction elements (56,56), the inlet end (56e) of each is arranged in the some place limited by the secant (Smax) of the longest level of described fluid-evacuation groove (51a).

9. turbomachinery according to any one of claim 1 to 3 (1), it is characterized in that, form described first hermetic unit (51) by sealing cover, described sealing cover is arranged to described housing (10) place from the side of described active wheel housing (12).

10. turbomachinery according to any one of claim 1 to 3 (1), is characterized in that, described Sealing (50) is configured to non-contacting labyrinth sealing.