EP2211060A2 - Dispositif de charge pour moteur à combustion interne - Google Patents

Dispositif de charge pour moteur à combustion interne Download PDF

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Publication number
EP2211060A2
EP2211060A2 EP10150428A EP10150428A EP2211060A2 EP 2211060 A2 EP2211060 A2 EP 2211060A2 EP 10150428 A EP10150428 A EP 10150428A EP 10150428 A EP10150428 A EP 10150428A EP 2211060 A2 EP2211060 A2 EP 2211060A2
Authority
EP
European Patent Office
Prior art keywords
charging device
rotor
recesses
sealing
sectional area
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP10150428A
Other languages
German (de)
English (en)
Other versions
EP2211060A3 (fr
Inventor
Thomas Berger
Christoph Butscher
Jörg Jennes
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BMTS Technology GmbH and Co KG
Original Assignee
Bosch Mahle Turbo Systems GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bosch Mahle Turbo Systems GmbH and Co KG filed Critical Bosch Mahle Turbo Systems GmbH and Co KG
Publication of EP2211060A2 publication Critical patent/EP2211060A2/fr
Publication of EP2211060A3 publication Critical patent/EP2211060A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/122—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps
    • F04D29/124—Shaft sealings using sealing-rings especially adapted for elastic fluid pumps with special means for adducting cooling or sealing fluid

Definitions

  • the present invention relates to a charging device for an internal combustion engine, in particular an exhaust gas turbocharger, preferably in a motor vehicle, having the features of the preamble of claim 1.
  • an exhaust gas turbocharger in which a rotor comprises a compressor wheel, a turbine wheel and a shaft.
  • a stator has a bearing housing in which the shaft of the rotor is rotatably mounted about a rotation axis.
  • a rotor-side sealing surface and a stator-side sealing surface are axially opposite one another.
  • the sealing surfaces are designed such that the rotor-side sealing surface axially overlaps the stator-side sealing surface.
  • the present invention is concerned with the problem of providing for a charging device of the type mentioned an improved embodiment, which is characterized in particular by a space-saving design with effective sealing effect.
  • the invention is based on the general idea to provide at least one of the sealing surfaces with a plurality of recesses or recesses which are arranged adjacent to each other in the circumferential direction.
  • the depressions are open axially to the respective opposite sealing surface and contain a gas volume.
  • the rotation of the rotor due to centrifugal forces causes gas to be driven radially outward within these recesses.
  • This can form a gas cushion with increased pressure or a radially outwardly oriented gas flow in the sealing zone, depending on the configuration of the recesses.
  • the gas flow or the gas cushion leads to an intensive sealing or media separation. Both the gas cushion and the gas flow prevent a transfer of lubricating oil on the fresh air side.
  • the formation of a gas cushion can also help to prevent or prevent a transfer of air in the direction of lubricating oil circuit.
  • the proposed construction is also characterized by the fact that it is extremely compact in the axial direction.
  • the recesses can be formed on sealing surfaces, which are already present, so that no additional space is required for the realization of the wells.
  • results for the realization of the proposed construction only a reduced overhead on manufacturing costs.
  • the depressions can each radially inward an inner cross-sectional area and radially outside a Have outer cross-sectional area, wherein the inner cross-sectional area and the outer cross-sectional area are different sizes.
  • the outer cross-sectional area smaller than the inner cross-sectional area.
  • the outer cross-sectional area can also be selected larger than the inner cross-sectional area, so that it is possible to reduce the pressure gradient.
  • the depressions in such a way that in their radial course they each have a longitudinal center line which extends inclined relative to the radial direction with respect to the axis of rotation in the circumferential direction.
  • the respective longitudinal center line can be rectilinear or curved. This results in sickle-shaped depressions.
  • the pressure ratios in the sealing zone can be further tuned to the particular needs.
  • the radial conveying effect for the gas volume within the recesses can be reduced or increased.
  • Fig. 1 includes a charging device 1, which is preferably an exhaust gas turbocharger, which can be used in a motor vehicle for charging an internal combustion engine, a rotor 2 and a stator 3.
  • the rotor 2 comprises in a conventional manner a compressor 4, a rotationally fixed with the Compressor 4 connected shaft 5 and not shown here Turbine, which is also rotatably connected to the shaft 5.
  • the stator 3 comprises a bearing housing 6, in which the rotor 2 or the shaft 5 is rotatably mounted about a rotation axis 7.
  • the stator 3 also comprises a compressor housing, not shown, in which the compressor wheel 4 is arranged, as well as a turbine housing, also not shown here, in which the turbine wheel is arranged.
  • FIG. 1 shows the compressor side of the charger 1, so the adjacent to the compressor 4 range.
  • this area is also a compressor-side sealing zone 8, which realizes a seal between the rotor 2 and the stator 3 in order to prevent a transfer of lubricating oil in the fresh air path.
  • a rotor-side sealing surface 9 and a stator-side sealing surface 10 are axially opposite.
  • the two sealing surfaces 9, 10 each lie in a plane which extends perpendicular to the axis of rotation 7. Basically, however, conical or curved sealing surfaces are conceivable.
  • the rotor-side sealing surface 9 is formed in the preferred example of a sealing bushing 11 which is mounted on the shaft 5 so as to rotate with the shaft 5.
  • the sealing bushing 11 for example, be braced together with the compressor 4 by a screw 12 against a collar 13 of the shaft 5.
  • the stator-side sealing surface 10 is formed on a bearing cap 14. The bearing cap 14 closes the bearing housing 6 on the compressor side, ie on an axial side facing the compressor wheel 4.
  • At least one of the sealing surfaces 9, 10 is provided with a plurality of recesses 15, which are arranged distributed in the circumferential direction relative to the axis of rotation 7. They are also spaced from each other in the circumferential direction along the respective sealing surface 9, 10 are arranged.
  • the depressions 15 are in the form of pockets or Formed recesses, which are incorporated in the plane of the respective sealing surface 9, 10.
  • the recesses 15 each have an inner cross-sectional surface 12 radially inward and an outer cross-sectional surface 20 radially outwardly.
  • the respective cross-sectional area 16, 17 is calculated from a length 18, with which the respective recess 15 extends in the circumferential direction, and from a depth 19, with which the respective recess 15 extends in the axial direction.
  • the length 18 may have a radially different value than radially outside.
  • the depth 19 radially inward may have a different value than radially outside.
  • the depth 19 may be constant in the radial direction. Visible, the depth 19 of the recesses 15 in relation to the lengths 18 is small, so that the recesses 15 are flat.
  • the depressions 15, the cross-sectional areas 16, 17 designed differently sized.
  • the inner cross-sectional area 16 is larger than the outer cross-sectional area 17.
  • the recesses 15 are designed in such a way that, in their radial course, they each have a longitudinal center line, not shown here, which extends radially with respect to the axis of rotation 7, and only radially. Furthermore, in the embodiment of the Fig. 2 the longitudinal center lines of the recesses 15 are each rectilinear. Such an embodiment is independent of the respective direction of rotation or the direction of rotation of the rotor 2.
  • the direction of rotation 20 with which the rotor 2 rotates relative to the stator 3 during operation of the charging device 1.
  • Recognizable is in the in Fig. 3 embodiment shown, the inclination of the recesses 15 with respect to the direction of rotation 20 oriented so that the recesses 15 run radially outward.
  • the recesses 15 are thus inclined radially from the inside to the outside counter to the direction of rotation 20.
  • the recesses 15 inclined in the circumferential direction or their longitudinal center lines are curved in the examples, as a result of which a crescent-shaped shape for the individual depressions 15 is created. In principle, however, straight-line longitudinal center lines or depressions 15 are also conceivable here.
  • the recesses 15 are designed such that they end radially outside the sealing zone 8 or, as in the examples, are radially open.
  • gas which is accelerated radially outwards by the rotation of the rotor 2 can be removed from the recesses 15 particularly easily.
  • the outer cross-sectional area 17 is in each case designed larger than the associated inner cross-sectional area 16, whereby the pressure gradient is reduced radially from the inside to the outside.
  • Fig. 3 shows Fig. 3 an embodiment in which the recesses 15 end radially outside within the sealing zone 8, so do not extend to the radially outer end of the respective sealing surface 9 and 10 respectively.
  • the formation of a gas cushion within the sealing zone 8 is supported. While in the radially outer open recesses 15, the formation of an outwardly oriented gas flow is supported. At the in Fig. 3 In the embodiment shown, moreover, the inner cross-sectional area 16 is set larger than the outer cross-sectional area 17, whereby the pressure increase is amplified radially outward in order to support the formation of the gas cushion.
  • Fig. 5 shows an embodiment in which in the radial direction inner recesses 15i and outer recesses 15a within the same sealing surface 9 are arranged adjacent to each other.
  • the inner recesses 15i and the outer recesses 15a do not directly merge into one another, but are separated from one another by a web-shaped remainder of the respective sealing surface 9.
  • the inner recesses 15i end within the sealing zone 8.
  • the outer recesses 15a are radially outward open.
  • the inner and outer recesses 15i, 15a have different inclinations with respect to the direction of rotation 20.
  • the inner recesses 15i are oriented so that they run radially outward, while the outer recesses 15a are oriented such that they follow radially inward.
  • the pressure distribution within the sealing zone 8 can be specifically dimensioned or designed so that sets a desired sealing effect.
  • FIG. 2 to 5 Exemplary embodiments show that such depressions 15 are formed on the rotor-side sealing surface 9
  • Fig. 6 an embodiment in which also such depressions 15 can be formed on the stator-side sealing surface 10.
  • a configuration is shown here, as in the case of the in Fig. 4 shown embodiment is visible. It is clear that, in principle, the other rotor-side configurations can also be realized on the stator side.
  • the can Recesses 15 may be formed either exclusively on the stator-side sealing surface 10 or exclusively on the rotor-side sealing surface 9 or both on the stator-side sealing surface 10 and on the rotor-side sealing surface 9. If both sealing surfaces 9, 10 have inclined recesses 15, they may be inclined in the same direction or in opposite directions.
  • Fig. 7 shows a particular embodiment in which the charging device 1 in the region of the sealing zone 8 has a sealing surface carrier 21 which is coupled by means of a spring means 22 with the stator 3 and is axially driven against the rotor 2.
  • the stator-side sealing surface 10 is formed on the sealing surface carrier 21, wherein the sealing surface carrier 21 is driven by means of spring means 22 so that the stator-shaped sealing surface 10 formed thereon is axially driven in the direction of the rotor-side sealing surface 9.
  • the sealing surface carrier 21 is axially supported via the spring device 22 on the bearing cap 14.
  • the sealing surface carrier 21 is mounted axially adjustable on the bearing cap 14.
  • it can be arranged rotatably on the bearing cap 14.
  • the pressure in the gap between the sealing surfaces 9, 10 can be increased or limited to a predetermined value, which improves the sealing effect.
  • the axial adjustability of the sealing surface carrier 21 relative to the stator 3 or relative to the bearing cap 14 may be limited, for example. By means of a stop, not shown here. In this way, a minimum axial sealing clearance between the two sealing surfaces 9, 10 can be ensured.
  • two shaft seals 23 are also provided for sealing between the rotor 2 and stator 3. They are arranged in the example between the bearing bush 11 and the bearing cap 14. For example, has the bearing bush 11 for this purpose corresponding grooves 24, in which the respective shaft seal 23 is inserted.
  • the shaft seals 23 abut radially outside on a cylindrical inner wall 25 of the bearing cap 14 and thereby bridge or seal a radially between the sealing bush 11 and the bearing cap 14 formed cylindrical annular gap 26.
  • the recesses 15 of the stator-side sealing surface 10 and / or the rotor-side sealing surface. 9 are arranged so that they communicate with this annular gap 26.
  • the respective recesses 15 are open radially towards the annular gap 26 or extend into the annular gap 26.
EP10150428A 2009-01-21 2010-01-11 Dispositif de charge pour moteur à combustion interne Withdrawn EP2211060A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009005386A DE102009005386A1 (de) 2009-01-21 2009-01-21 Ladeeinrichtung für eine Brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP2211060A2 true EP2211060A2 (fr) 2010-07-28
EP2211060A3 EP2211060A3 (fr) 2011-03-09

Family

ID=41800806

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10150428A Withdrawn EP2211060A3 (fr) 2009-01-21 2010-01-11 Dispositif de charge pour moteur à combustion interne

Country Status (3)

Country Link
US (1) US20100180589A1 (fr)
EP (1) EP2211060A3 (fr)
DE (1) DE102009005386A1 (fr)

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US8061970B2 (en) * 2009-01-16 2011-11-22 Dresser-Rand Company Compact shaft support device for turbomachines
DE102010038527B4 (de) * 2010-07-28 2020-08-13 Man Energy Solutions Se Turbomaschine
WO2013109235A2 (fr) 2010-12-30 2013-07-25 Dresser-Rand Company Procédé de détection en ligne de défauts de résistance à la masse dans des systèmes de palier magnétique actif
US8994237B2 (en) 2010-12-30 2015-03-31 Dresser-Rand Company Method for on-line detection of liquid and potential for the occurrence of resistance to ground faults in active magnetic bearing systems
WO2012138545A2 (fr) 2011-04-08 2012-10-11 Dresser-Rand Company Système de refroidissement à circulation d'huile diélectrique pour paliers enfermés et dispositifs électroniques enfermés
EP2715167B1 (fr) 2011-05-27 2017-08-30 Dresser-Rand Company Roulement segmenté à décélération en roue libre pour des systèmes de roulement magnétique
US8851756B2 (en) 2011-06-29 2014-10-07 Dresser-Rand Company Whirl inhibiting coast-down bearing for magnetic bearing systems
CN102400944A (zh) * 2011-07-13 2012-04-04 康跃科技股份有限公司 涡轮增压器压气机端双环密封装置
US8911202B2 (en) * 2011-09-20 2014-12-16 Honeywell International Inc. Turbocharger rotating assembly
WO2013106303A1 (fr) * 2012-01-13 2013-07-18 Borgwarner Inc. Système d'étanchéité et turbocompresseur qui incorpore ce dernier
RU2014148095A (ru) * 2012-05-16 2016-06-27 Боргварнер Инк. Масляное уплотнение маслоотбойного кольца и турбонагнетатель, содержащий такое масляное уплотнение
US9540950B2 (en) * 2012-11-06 2017-01-10 GM Global Technology Operations LLC Oil deflector
DE112013005565T5 (de) * 2012-12-17 2015-08-20 Borgwarner Inc. Äussere entleerungsdichtung für turbolader
DE102012224068A1 (de) * 2012-12-20 2014-06-26 Bosch Mahle Turbo Systems Gmbh & Co. Kg Turbolader
WO2015013114A1 (fr) * 2013-07-26 2015-01-29 Borgwarner Inc. Joint de purge de turbocompresseur comprenant une cavité d'alimentation axisymétrique
US9988976B2 (en) 2014-05-24 2018-06-05 Honeywell International Inc. Turbocharger
JP6195308B2 (ja) * 2014-06-25 2017-09-13 三菱重工業株式会社 軸流タービンのラビリンスシール装置およびこれを備えた排ガスタービン過給機
DE102015106638A1 (de) * 2014-07-02 2016-01-07 Pierburg Gmbh Befestigungsvorrichtung sowie Verfahren zur Befestigung eines Laufrades eines Verdichters auf einer Antriebswelle
EP3164603B1 (fr) * 2014-07-02 2020-01-22 Pierburg GmbH Compresseur électrique pour moteur à combustion interne
MX2018010839A (es) 2016-03-08 2019-02-07 Fluid Handling Llc Cojinete central para equilibrar las fuerzas axiales en bombas de etapas múltiples.
JP6471871B2 (ja) * 2016-06-13 2019-02-20 トヨタ自動車株式会社 内燃機関
FR3058189B1 (fr) * 2016-11-03 2020-10-09 Valeo Systemes De Controle Moteur Compresseur electrique avec systeme d'etancheite dynamique ameliore

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Also Published As

Publication number Publication date
DE102009005386A1 (de) 2010-07-22
US20100180589A1 (en) 2010-07-22
EP2211060A3 (fr) 2011-03-09

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