CN102418567A

CN102418567A - Turbomachine

Info

Publication number: CN102418567A
Application number: CN2011102219378A
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: 2012-04-18
Anticipated expiration: 2031-07-28
Also published as: KR20120011315A; CH703516A2; DE102010038524A1; DE102010038524B4; JP5395106B2; CN102418567B; KR101188947B1; CH703516B1; JP2012031842A

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 the 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 sealing part is blocked in the bearing housing of turbomachinery and the fluid passage between the active wheel housing .

Summary of the invention

The objective of the invention is to, the turbomachinery according to the preamble of claim 1 is provided, more anti-fluid is passed Sealing in this turbomachinery.

This purpose is utilized according to the turbomachinery of claim 1 and is realized.In dependent claims, defined improvement project of the present invention.

According to the present invention, turbomachinery has: the housing that has bearing housing and active wheel housing; Can be rotated to support on the axle in the bearing housing; Be connected with axle and be arranged in the active wheel (Laufrad) in the active wheel housing; And Sealing; The sealing part has first hermetic unit that is formed by the static housing parts that defines the passage of the axle from bearing housing to the active wheel housing and second hermetic unit that is connected with the outer periphery of axle, and the sealing part is blocked the fluid passage between bearing housing and active wheel housing.Be in the cartridge housing side at first hermetic unit and be provided with and utilize crooked (Kr ü mmung), thereby the bearing housing fluid that is applied on first hermetic unit can vertically flow out downwards along the fluid-evacuation groove with fluid-evacuation groove (Ablaufrinne) along the outer periphery of mode

threaded shaft of periphery.According to turbomachinery of the present invention in the following manner and outstanding; Promptly; In the fluid-evacuation groove, be respectively arranged with fluid stream induction element (Fluidstromleitelement) in the both sides of axle, this fluid stream induction element is radially derived the bearing housing fluid with abaxial mode from the fluid-evacuation groove.

The fluid-evacuation groove is arranged to, and the bearing housing fluid of avoiding flowing out in the first sealed department office (for example lubricant oil) infiltrates in the Sealing without barrier.The bearing housing fluid is followed (folgen) fluid-evacuation groove, flows out vertically downward until it.

But; Recognize through the inventor; Hydrostatic pressure through boundary layer processes (Grenzschichtvorgang) between the bearing housing fluid and first hermetic unit or minimum is poor; The bearing housing fluid is followed the fluid-evacuation groove relatively longways, thereby bearing housing fluid LF spends greater than 180 to the disengaging angle

of the vertical line at fluid-evacuation groove place with respect to laterally setting (anlegen).

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

Flow induction element (this fluid stream induction element is radially derived the bearing housing fluid with abaxial mode from the fluid-evacuation groove) through in the fluid-evacuation groove, fluid being set respectively in the both sides of axle according to the present invention; So degree reduce the disengaging angle of bearing housing fluid; That is, avoid reliably in the 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 the fluid stream induction element in this inflow region middle (center) bearing shell fluid; And flowing out the zone, induction element breaks away from

from fluid stream in this zone middle (center) bearing shell fluid

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

Utilize this design proposal of the present invention; Simply mode will almost derive from the fluid-evacuation groove along the moving bearing housing fluid of fluid-evacuation concentrated flow fully, and be introduced into another aspect the sealing of Sealing in the flow direction of no problem.

According to form of implementation of the present invention, inflow region is with crooked with the arc ground of the crooked opposite mode of fluid-evacuation groove.

Through the preferably big relatively inflow radius of realizing thus, bearing housing fluid

aspect flow imaging flows out from the fluid-evacuation groove reposefully and thus reliably.

According to a form of implementation more of the present invention; Flow out the zone and have water conservancy diversion edge (Abrisskante); This water conservancy diversion edge limits inflow region at the place, end away from the fluid-evacuation groove of inflow region, and is arranged in the position of the outermost radially of fluid stream induction element.

Utilization guarantees with simple mode that according to this design proposal of the present invention the bearing housing fluid of from the fluid-evacuation groove, deriving breaks away from from fluid stream induction element reliably once more, and with the outwards mode of dislocation outflow downwards vertically radially.

According to another form of implementation of the present invention, the outflow zone has this back guide surface of back guide surface

and is connected to water conservancy diversion edge with the mode (

Welle erstreckend) that the periphery along axle extends.

Guaranteed through this back guide surface, continued to guide bearing housing fluid residual, that do not break away from as yet in water conservancy diversion edge that finally guide surface breaks away from and outflow downwards vertically from the back until it with the mode that radially outwards misplaces.

According to form of implementation of the present invention, back guide surface is with crooked with the crooked corresponding mode of fluid-evacuation groove.

Advantageously protect any remaining bearing housing fluid not to be inhaled in the Sealing by this way; Because back guide surface remains on the remaining bearing housing fluid that radially outwards guides on this radially outside level, guide surface breaks away from and vertically flows out downwards from the back until remaining bearing housing fluid.

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

This point defines such position, that is, at this position, the bearing housing fluid in the fluid-evacuation groove is positioned at outermost radially.Each inlet end through fluid stream induction element is arranged in this position; At time point as well as possible the bearing housing fluid is derived from the fluid-evacuation groove; Thereby finally realize the dislocation radially of the maximum of bearing housing fluid, and prevent more reliably that thus the bearing housing fluid is inhaled in the Sealing with radially outer mode.

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

Description of drawings

The preferred form of implementation of following basis also is described in greater detail with reference to the attached drawings the present invention.

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

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

Fig. 3 has shown the view of amplification in the zone of Fig. 1,

Fig. 4 has shown the view of schematic perspective of the turbomachinery of Fig. 1, wherein, has shown 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

40 sliding bearings

41 radial bearings lining

50 Sealings

51 first hermetic units

51a fluid-evacuation groove

The 51b bottom surface

52 second hermetic units

53 interception labyrinths (Fanglabyrinth)

54 discharge sides (Abf ü hrkammern)

55 derive groove

56 fluids stream induction element

The 56a inflow region

56b flows out the zone

56c water conservancy diversion edge

Guide surface behind the 56d

The 56e inlet end

60 chamber pads (Kammerungsscheibe)

70 bearing housing fluid supply holes

71 spray-holes

80 lids

The horizontal secant that Smax is the longest

LF bearing housing fluid

The GS air-flow

Embodiment

Below referring to figs. 1 to the turbomachinery 1 of 4 descriptions according to form of implementation of the present invention.

Turbomachinery 1 can for example be configured to exhaust-gas turbocharger or power turbine.In the form of implementation of the present invention that shows in the drawings, turbomachinery 1 is configured to exhaust-gas turbocharger.

As in Fig. 1 to 3, showing, turbomachinery 1 has the housing 10 that has bearing housing 11 and two active wheel housings 12 and 13.Two active wheel housings (it has the housing parts of outflow 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. 1, and the active wheel 21 on the right is configured to the compressor operating wheel in Fig. 1.For following description, turbine wheel is called first active wheel 20 and the active wheel housing under it is called the first active wheel housing 12.Correspondingly the compressor operating wheel is called second active wheel 21, and the active wheel housing under it is called the second active wheel housing 13.

In addition, turbomachinery 1 have through a plurality of sliding bearings 40 can be rotated to support in the bearing housing 11 the axle 30, this axle 30 is fixedly connected to each other first active wheel 20 and second active wheel 21.

Be noted that thus power turbine is characterised in that, do not have second active wheel 21 and in the corresponding change of the corresponding change at housing 10 places and possible supporting place at axle 30.In this case, sentence and be used to produce electric current owing to passing through of causing of the step-down (Entspannung) of the waste gas on turbo-side and the cooling moment of torsion that axle 30 transmits possibly be sent to generator through driving mechanism.

Get into bearing housing 11 to prevent that air from the second active wheel housing 13 (compressor side) from getting into bearing housing 11 and preventing from the waste gas of the first active wheel housing 12 (turbo-side) like the outlet port sealing that must leave bearing housing 11 at axle 30 on the one hand at the turbomachinery that is configured to exhaust-gas turbocharger this demonstration 1.On the other hand, shaft seal must prevent that bearing housing fluid (at this lubricant oil for example) from leaving in the wheel side space (Restseitenraum) that is right after that gets into compressor and turbine from bearing housing 11.At this, the requirement of the shaft sealing between exhaust-gas turbocharger radially and axial is mainly distinguished in exhaust gas side or turbo-side to some extent.In addition, reveal (vorstellen) different operating conditions with the running state Correlation meter of turbomachinery 1 and this different operating conditions occurs after shaft seal.

In Fig. 3, shown and be configured to non-contacting labyrinth sealed Sealing 50 with the view that amplifies; Sealing part 50 has first hermetic unit 51 that is formed the static housing parts from the passage of bearing housing 11 to first active wheel housings 12 that limits axle 30 and second hermetic unit 52 that is connected with the outer periphery of axle 30, and the fluid passage of blocking-up between the bearing housing 11 and the first active wheel housing 12.

In service at turbomachinery 1, the pressure continuity (fortsetzen) in contiguous wheel side space in the outlet port of second active wheel 21.Although locate to exist throttling labyrinth part (Drossellabyrinthe) at the wheel back of second active wheel 21 (Radr ü cken), bearing housing 11 exists (anstehen) that certain overvoltage is arranged at the Sealing place relatively.The purpose of sealing part is that air entering and the loss of mass flow thus (seepage (Blow-By)) that will arrive in the bearing housing 11 keep as far as possible little.At this, the low pressure (Unterdruck) before the sealing position has been represented exception or rather, and can prevent through correspondingly designing throttling labyrinth part or taking turns the side space ventilator in addition.Thus, prevented leaving of bearing housing fluid through the overvoltage that before Sealing, continues to exist, this bearing housing fluid loads the sealing position with the mode of spraying from bearing housing 11 beginnings.

In exhaust-gas turbocharger (like the turbomachinery 1 that shows in the drawings) radially, the similar state of appearance on turbo-side is in operation.Exhaust gas pressure before turbine is propagated (fortpflanzen) and in wheel side space and at Sealing 50, is existed before.As long as the rotating speed of the axle 30 of turbomachinery 1 is not less than the certain rotating speed in lower zone, these situation just do not change, and that is to say, before Sealing 50, continue to exist superpressure.

In so-called interpolation lubricant oil operation (Nachschmierbetrieb), can appear at Sealing 50 other situation before.At this, in static rotor assembly (Laufzeug) (

active wheel

20,21 and axle 30), for the sliding bearing 40 interpolation lubricant oil of turbomachinery 1, to derive the waste heat that produces.During adding lubricant oil; Effect through stack draft (Kaminzug); In the outflow housing parts of the first active wheel housing 12 (turbo-side), low pressure can occur, wherein, low pressure continues up to before the Sealing 50 between the first active wheel housing 12 and the bearing housing 11.For this reason, Sealing 50 also must design to this running state.Must prevent, on the direction in the wheel side space of turbo-side, suck the bearing housing fluid through Sealing 50 through pressure difference.

According to the present invention, so design the member of Sealing and adjacency thereof, that is, prevent that reliably the bearing housing fluid from leaving in the wheel side space that gets into first active wheel 20 through axle 30 from bearing housing 11.

In service at turbomachinery 1, bearing housing fluid (is lubricant oil at this) loads Sealing 50 with the mode of spraying, and wherein, leaves from the single bearing part of turbomachinery 1 as the bearing housing fluid of bearing oil.In addition; Can be through directly utilizing the moistening Sealing 50 of bearing housing fluid (at this for spraying oil) from the additional loading of (oil) sprocket hole of sliding bearing 40; Wherein, this moistening cooling as sealed member, and should prevent the coking within Sealing 50 of bearing housing fluid thus.At this, before bearing housing 11, can there be overvoltage or low pressure.Can be only by bearing oil, only by spraying profit oil and by bearing oil with spray oil and load Sealing 50 simultaneously.At this, the temperature and pressure that is transported to the bearing housing fluid of sliding bearing 40 can change, and this influences the amount and the drainage properties (Ablaufverhalten) of the bearing housing fluid on Sealing 50 basically.

Form second hermetic unit 52 of Sealing 50 through (profiliert) axle section of given profile; Or, on axle 30, form this second hermetic unit 52 before at first active wheel 20 (turbine wheel) with the embodiment of the cover of shrink fit as showing among Fig. 3.First hermetic unit 51 of Sealing 50 is formed by the independent member of bearing housing 11, is implemented as sealing cover at this this member.The profile (Profil) of first hermetic unit 51 and second hermetic unit 52 forms non-contacting interception labyrinth 53, and this interception labyrinth 53 is a characteristic with a plurality of continuous seal gap and discharge side 54.

As mentioning, through bearing housing fluid (it leaves this is configured to the bearing part of radial bearing lining 41 from direct adjacency) splash (bespritzen) Sealing 50.At this, so-called chamber pad 60 can serve as a contrast 41 fit on face (Sitz) at the radial bearing that axial direction limit is floated.In the situation of fixing radial bearing lining 41 (catching oil bumper

type), the chamber pad 60 that utilizes groove to join in radial bearing lining 41 distolateral is used for fixing radial bearing lining 41 (radial bearing lining 41 rotation not together).In the situation of radial bearing lining 41 rotation together, chamber pad 60 has the function in the axial gap of adjustment radial bearing lining 41, and this rotating speed for radial bearing lining 41 is conclusive.But, in both of these case, the throttling of the bearing housing fluid that chamber pad 60 also is used for flowing out from the interior and outer lubrication gap of radial bearing lining 41, and influence the shock absorbing characteristics of sliding bearing 40 thus fatefully.

In most applications, the bearing housing fluid that also inner diameter of pad 60 leaves in the chamber thus from radial bearing lining 41 mainly loads first seal clearance of Sealing 50.But, the zone around also moistening first hermetic unit 51 (sealing cover) of the less amount of bearing housing fluid (droplet and mist).For this less amount of preventing the bearing housing fluid in the first hermetic unit 51 places coking; The bearing housing fluid bundle of origin blowing perforation 71 cooling should the zone consciously; Wherein, bearing housing fluid bundle impacts (auftreffen) to first hermetic unit 51 in the zone on first hermetic unit 51.Spray-hole 71 feeds in the bearing housing fluid supply hole 70 of radial bearing lining 41.Towards turbo-side, also through the wheel side apart of additional lid 80 (is end cap at this) with first hermetic unit 51 and first active wheel 20.

As especially can be finding out among Fig. 4; According to the present invention; Be in the cartridge housing side at first Sealing 51 and be provided with and utilize circular bending, thereby the bearing housing fluid LF that is applied on first hermetic unit 51 can vertically flow out downwards along fluid-evacuation groove 51a with fluid-evacuation groove 51a along the outer periphery of the mode threaded shaft 30 of periphery.In fluid-evacuation groove 51a, be respectively arranged with fluid and flow induction element 56 in the both sides of axle 30; 56 (in Fig. 4, only can find out anterior fluid stream induction element); This fluid

stream induction element

56,56 is radially derived bearing housing fluid LF with the mode away from axle 30 from fluid-evacuation groove 51a.

According to the present invention, but the combination seal element is realized fluid

stream induction element

56,56, and seal element is cooled to be used for cooling fully and to be used to avoid the fluid coking thus through the splash that continues that utilizes bearing housing fluid LF at turbomachinery 1 run duration.In present case, fluid

stream induction element

56,56 is attached in first hermetic unit 51 (sealing cover), and the Sealing 50 of turbomachinery 1 is represented in the interception labyrinth (second hermetic unit 52) of this first hermetic unit 51 and axle side jointly.At this, fluid

stream induction element

56,56 is arranged in the fluid-evacuation groove 51a of first hermetic unit 51.Fluid stream induction element 56; 56 or can be used as independent member and introduce among the fluid-evacuation groove 51a in the both sides of deriving groove 55 (see figure 3)s down, perhaps can be for example among course of working, remain solid material (Vollmaterial) during by bore hole (Ausdrehen) at fluid-evacuation groove 51a.Two kinds of schemes all realize identical functions.

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

As can be from finding out Fig. 4; The form of the inflow face that inflow region 56a is configured to begin radially to extend away from axle 30 from the bottom surface 51b of fluid-evacuation groove 51a; Wherein, inflow region 56a is with crooked with the arc ground of the crooked opposite mode of fluid-evacuation groove 51a.

In addition; As can be from finding out Fig. 4; Flow out regional 56b and have water conservancy diversion edge 56c; This water conservancy diversion edge 56c is at place, the end restriction inflow region 56a away from fluid-evacuation groove 51a of inflow region 56a, and this water conservancy diversion edge 56c is arranged in the position of the outermost radially of fluid stream induction element 56.In addition, flow out regional 56b and have back guide surface 56d, this back guide surface 56d is connected to 56c place, water conservancy diversion edge with the mode that the periphery along axle 30 extends, and wherein, back guide surface 56d is with crooked with the crooked corresponding mode of fluid-evacuation groove 51a.

Correspondingly, fluid

stream induction element

56,56 is configured to help flowing; That is to say; Fluid

stream induction element

56,56 has big radius at the inflow region 56a place of the bearing housing fluid LF that discharges, so that as far as possible stably from fluid-evacuation groove 51a, derive bearing housing fluid LF.In addition, (that is, in flowing out regional 56b) so designs fluid

stream induction element

56,56 at the place, end, that is, bearing housing fluid LF can not arrive the derivation groove 55 of adjacency again, and flows out in advance.

As illustrated in fig. 4, the bearing housing fluid LF that the fluid-evacuation groove 51a of first hermetic unit 51 should will be ejected on the discharge launder 51a around the sealing position derives.At this, bearing housing fluid LF can impact on the Sealing 51 at one or more positions arbitrarily of first hermetic unit 51.According to the present invention; Needn't through the nozzle that is orientated suitably bearing housing fluid LF be applied on first hermetic unit 51 consciously; And can imagine equally be, among the bearing housing fluid LF that can from come from bearing portion, flow out, from owing to from the bearing housing fluid LF of axle 30 centrifugations or other splash of splash effect, obtain the moistening of first hermetic unit 51 to first hermetic unit 51.

Bearing housing fluid LF for fear of flowing out at the profile place of first hermetic unit 51 infiltrates in real (eigentlich) geometrical construction of Sealing 50 without barrier, and the suitable design of the inboard through first hermetic unit 51 realizes fluid-evacuation groove 51a.Bearing housing fluid LF follows this fluid-evacuation groove 51a, until its downward outflow.Yet; Bearing housing fluid LF is not vertically to flow out downwards at the position of the horizontal secant Smax of the maximum of fluid-evacuation groove 51a, but depends on bearing housing fluid LF and the intensity

of the volume flowrate of the air-flow GS that sucks through Sealing 50 (this air-flow GS because before Sealing 50 low pressure of existence produce) is also followed cylinder or the bottom surface 51b of fluid-evacuation groove 51a in certain a moment.The secant Smax of the longest level of fluid-evacuation groove 51a flatly extends through the central longitudinal axis of axle 30.

Therefore, bearing housing fluid LF spends greater than 180 with respect to the disengaging angle of the vertical line that laterally is set to fluid-evacuation groove 51a place.This situation former because, the influence of the boundary layer processes between the bearing housing fluid LF and first hermetic unit 51 and the hydrostatic pressure difference of the minimum on the inboard of first hermetic unit 51.

Because interception chamber, labyrinth (the derivation groove 55 that it has been mentioned more than forming; This derives the bearing housing fluid LF that groove 55 infiltrates as first seal clearance of deriving through Sealing 50) the hole radially of downward sensing; Inhaled air stream or air-flow GS get into (einschlagen) usually through deriving path of groove 55, because derive groove 55 resistance of minimum are reacted on air-flow GS.If because certain environment (Umstand); Air-flow the GS enough big and/or Sealing 50 of flowing through is enough big at the disengaging angle of bearing housing fluid LF; The bearing housing fluid LF that follows fluid-evacuation groove 51a then can occur sucking, and can cause the blow-by property of Sealing 50 thus.

Fluid stream induction element 56 arranged according to the present invention; 56 influence the size at the disengaging angle of the bearing housing fluid LF that discharges and follow fluid-evacuation groove 51a at the place, inboard of first hermetic unit 51 by this way; That is, the disengaging angle of the bearing housing fluid LF of outflow reduces significantly.This makes; The bearing housing fluid stream that from derive groove 55, flows out does not combine with the stream of the bearing housing fluid LF that flows at fluid-evacuation groove 51a (spraying oil), and has prevented with the air-flow GS through Sealing 50 to serve as that the basis sucks bearing housing fluid LF reliably.

In order to realize that bearing housing fluid LF derives especially safely or breaks away from from fluid-evacuation groove 51a, the inlet end 56e of each is arranged in the some place that the secant Smax the longest level of fluid-evacuation groove 51a limits in two fluid

stream induction elements

56,56.

Claims

1. a turbomachinery (1) has: the housing (10) with bearing housing (11) and active wheel housing (12,13); Can be rotated to support on the axle (30) in the said bearing housing (11); Be connected with said axle (30) and be arranged in the active wheel (20,21) in the said active wheel housing (12,13); And Sealing (50); Said Sealing (50) has by static defining from said bearing housing (11) to said active wheel housing (12; First hermetic unit (51) that the housing parts of the passage of axle 13) (30) forms and second hermetic unit (52) that is connected with the outer periphery of said axle (30); And the fluid passage of said Sealing (50) blocking-up between said bearing housing (11) and said active wheel housing (12,13)

Wherein, Said first hermetic unit (51) be in the cartridge housing side be provided with utilize crooked with along the mode of periphery fluid-evacuation groove (51a) around the outer periphery of said axle (30); Thereby the bearing housing fluid (LF) that is applied on said first hermetic unit (51) can vertically flow out downwards along said fluid-evacuation groove (51a)

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

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

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

4. according to claim 2 or 3 described turbomachineries (1), it is characterized in that said inflow region (56a) is with crooked with the arc ground of the crooked opposite mode of said fluid-evacuation groove (51a).

5. according to claim 3 or 4 described turbomachineries (1); It is characterized in that; Said outflow zone (56b) has water conservancy diversion edge (56c); Said water conservancy diversion edge (56c) is at place, the end restriction said inflow region (56a) away from said fluid-evacuation groove (51a) of said inflow region (56a), and said water conservancy diversion edge (56c) is arranged in the position of the outermost radially of said fluid stream induction element (56).

6. turbomachinery according to claim 5 (1) is characterized in that, said outflow zone (56b) has back guide surface (56d), and the mode that said back guide surface (56d) extends with the periphery along said axle (30) is connected to said water conservancy diversion edge (56c) and locates.

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

8. according to each described turbomachinery (1) in the claim 1 to 7; It is characterized in that; The inlet end (56e) of each is arranged in the some place that the secant (Smax) the longest level of said fluid-evacuation groove (51a) limits in two fluids stream induction elements (56,56).

9. according to each described turbomachinery (1) in the claim 1 to 8, it is characterized in that form said first hermetic unit (51) by sealing cover, said sealing cover begins to be arranged to said housing (10) from the side of said active wheel housing (12).

10. according to each described turbomachinery (1) in the claim 1 to 9, it is characterized in that said Sealing (50) is configured to non-contacting labyrinth sealing.