CN101592071A - Axial bearing seal for an exhaust gas turbocharger - Google Patents

Axial bearing seal for an exhaust gas turbocharger Download PDF

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Publication number
CN101592071A
CN101592071A CNA2009101418201A CN200910141820A CN101592071A CN 101592071 A CN101592071 A CN 101592071A CN A2009101418201 A CNA2009101418201 A CN A2009101418201A CN 200910141820 A CN200910141820 A CN 200910141820A CN 101592071 A CN101592071 A CN 101592071A
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CN
China
Prior art keywords
seal
rotor shaft
axial
bearing
housing
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.)
Granted
Application number
CNA2009101418201A
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Chinese (zh)
Other versions
CN101592071B (en
Inventor
F·沃德克
D·武茨
M·斯彭格勒
T·西沃特
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MAN Energy Solutions SE
Original Assignee
MAN Diesel SE
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Publication date
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Publication of CN101592071A publication Critical patent/CN101592071A/en
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Publication of CN101592071B publication Critical patent/CN101592071B/en
Expired - Fee Related legal-status Critical Current
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F01D25/166—Sliding contact bearing
    • F01D25/168—Sliding contact bearing for axial load mainly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F01D25/183—Sealing means
    • F01D25/186—Sealing means for sliding contact bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/447—Labyrinth packings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Sliding-Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)

Abstract

The invention relates to an axial bearing seal for an exhaust gas turbocharger having a rotor shaft, a turbine and a compressor, wherein a bearing body of the axial bearing is arranged in a stationary manner on a turbocharger housing, so that an oil space remains between the rotor shaft and a bore of the bearing body, said bearing body cooperating with a rotating bearing ring and being connected in the axial direction of the rotor shaft to a sealing ring of the compressor housing, so that a sealing gap can be formed between the sealing ring and the bearing body, wherein the sealing ring has an additional sealing device. In order to ensure that air is prevented from entering and the function of the axial bearing is maintained in the axial bearing seal at high rotational speeds in the axial bearing, provision is made for a sealing gap to be formed between the sealing ring and the bearing body in the radial direction with respect to the rotor shaft and for the sealing gap to extend outward, so that the oil pressure in the sealing gap is always greater than the corresponding air pressure in the housing surrounding the axial bearing during operation of the turbocharger.

Description

The axial bearing seal that is used for exhaust-gas turbocharger
Technical field
The present invention relates to a kind of by claim 1 axial bearing seal that is used for exhaust-gas turbocharger as described in the preamble, this exhaust-gas turbocharger has rotor shaft, this rotor shaft is supporting turbine in guiding ground in the housing bore in turbine cylinder at one end, and in the housing bore of the other end in compressor housing the guiding twelve Earthly Branches pressure-bearing wheel that contracts.
Background technique
Rotor shaft is bearing on the radial and axial bearing usually, comprises the proper lubrication system, the bearing housing inside in the middle of they are arranged on, and described bearing housing is connected between turbine cylinder and the compressor housing.
At this, in the zone of compressor wheels or compressor housing, be provided with the cod that is used for rotor shaft at least, it has seal arrangement, described seal arrangement and the Oil sealing assembly interaction that comprises floating disc for example or the holding part or the section of tumbling.
Known at this, oil flows to bearing housing and infeeds bearing unit by oily passage by the filler opening of I. C. engine oil system.
For example put down in writing this exhaust-gas turbocharger in EP 1 394 365 A1, wherein, seal arrangement is made of shell body wall and cod.For carrying out axially mounting, the just actionless bearing member of fixed-site is embedded in one of two revolving parts that link to each other with rotor shaft.
Usually use the holding part bearing as cod.They are made up of the bearing support that is fixedly linked with bearing housing and the slip surface that rotates with the axis of so-called bearer ring.
By for example known a kind of cod that is used for exhaust-gas turbocharger of DE 196 41 673 B4, wherein, the floating disc that is located between the bearer ring of fixed bearing support and rotation is guided on rotor shaft.
Therefore a bearing support of cod is fixed on the bearing housing still, and also is fixed on thus on the housing of exhaust-gas turbocharger, and another bearing support is that bearer ring is then along with the rotor shaft rotation.Between the bearer ring of fixed bearing support and rotation, floating disc can be set, thereby can constitute the lubrication gap respectively in the both sides of floating disc.
Fixed bearing support along rotor shaft axially on one that on that side of floating disc, is connected compressor housing rotating ring that is supporting seal arrangement, thereby can between the seal ring of the rotation of compressor housing and fixed bearing support, constitute the seal clearance of axial clearance form.
Between the surface of rotor shaft and the axial bore of fixed bearing support, be provided with the oil pocket of the liquid anchor ring form of rotation, it leads to seal clearance between the seal ring of the rotation of fixed bearing support and compressor housing and the lubrication gap that leads to other bearing element via oily passage.
Lubricant oil flows to the liquid anchor ring of rotation via the filler opening that is positioned at fixed bearing support.
Should also be noted that to be known that in many application seal ring can also be designed to the labyrinth circle in the seal ring of the rotation of compressor housing, it comprises a labyrinth as a part that is used for the labyrinth-type excluder of seal compression chamber.
But also possiblely in this class turbosupercharger be, centrifugal force in the liquid anchor ring of the rotation by cod produces a pressure gradient, this pressure gradient is greater than the discharge pressure in the filler opening of fixed bearing support of oil, thereby oil can't overcome this pressure gradient and servo-actuated.
Thereby the trend that occurs in running is, when boost pressure is higher, that is to say, when the rotating speed of exhaust-gas turbocharger is higher, the air of drawing from the pressing chamber of compressor housing for example flows into bearing housing via labyrinth-type excluder via the seal arrangement of compressor side, especially flows into the liquid anchor ring of rotation, just flows in the oil pocket of fixed bearing support, thereby even for example when using floating disc, this floating disc also can keep dry.
Be only feasible when only the sealing that realizes by seal arrangement up to now only reaches certain negative pressure in that is to say the liquid anchor ring that is rotating in the cod.
Summary of the invention
Therefore technical problem to be solved by this invention is, before a kind of, guarantee in the described cod, even it is higher at the exhaust-gas turbocharger rotating speed, and when in cod, producing negative pressure thus under the situation that lubricant oil breaks down by the conveying of filler opening, also can avoid air to enter, and keep the function of cod.
According to the present invention, above-mentioned technical problem solves in this class axial bearing seal thus, promptly, seal clearance between the seal ring of the rotation of compressor housing and the fixed bearing support constitutes diametrically with respect to rotor shaft, and extend outwardly into following degree, that is, make oil pressure in the seal clearance when exhaust-gas turbocharger move all the time greater than the corresponding air pressure in the housing of encirclement cod.
Can realize the formation of this seal clearance in particularly advantageous mode by following content, promptly, the radial height of the oil pocket just height of the liquid anchor ring in fixed bearing support is significantly less than its axial width and advantageously is 1/3rd of oil pocket axial width to the maximum, and the sealing of the seal ring of rotation along rotor shaft axially work and relatively the outer dia of oil pocket locate around rotor shaft with the diameter of the radial length that amplified seal clearance.
Outer dia by relative oil pocket and seal clearance is configured for making cod with respect to the diameter of the seal arrangement of the air impervious seal ring in the pressing chamber, realizes the conveying effect of lubricant oil to the pressing chamber direction.
Description of drawings
Draw other details of the present invention by following explanation to the preferred embodiment that schematically illustrates in the accompanying drawings.
A unique accompanying drawing shows exhaust-gas turbocharger by the partial longitudinal section in the axial bearing seal of the present invention zone.
Embodiment
Comprise on the housing that is fixed on exhaust-gas turbocharger by axial bearing seal of the present invention and relatively rotor shaft 1 fixed bearing support 2, another with the bearer ring with rotor shaft 1 rotation be the bearing support 3 of form and compressor housing axially be connected seal ring 5 on the fixed bearing support 2 along rotor shaft 1 in that side towards compressor housing.Between the bearer ring 3 of fixed bearing support 2 and rotation, include floating disc 4.
Design has seal clearance 6 between seal ring 5 and fixed bearing support 2, and wherein, seal ring 5 has an additional labyrinth-type excluder 7 in the embodiment shown.Certainly also can consider to use other sealing configuration at this.
The liquid anchor ring that is provided with rotation between the surface of rotor shaft 1 and the axial bore of fixed bearing support 2 is the oil pocket 8 of form, from the oil of the oil system of internal-combustion engine in other words oiling agent be transported in the oil pocket by filler opening 9 so that on two end faces of floating disc 4, constitute respectively the lubrication gap and relatively the pressurized air of compressor compresses chamber seal clearance 6 in, reach sealing effect there by being transported to the oil.
Oil pocket 8 is designed to the annular groove in the hole of fixed bearing support 2.
Seal clearance 6 between seal ring 5 and the fixed bearing support 2 is radially directed and stretch out with respect to rotor shaft 1, make in the seal clearance oil pressure all the time greater than around the housing of cod in corresponding air pressure.
The conveying effect of oil in seal clearance 6 depends on the size of the rotating speed and the residing diameter of seal arrangement of exhaust-gas turbocharger, and seal arrangement is a labyrinth-type excluder 7 at this.
At this, the radial height 10 of the liquid anchor ring of oil pocket 8 or rotation obviously is less than its axial width.Advantageously, this radial height 10 is 1/3rd of oil pocket 8 axial widths to the maximum.
Labyrinth-type excluder 7 the extending axially of seal ring 5 along rotor shaft 1, and the diameter 13 that amplifies with the outer dia 11 of a relative oil pocket 8 is around rotor shaft 1 location, and wherein diameter 13 has amplified the radial length 12 of the seal clearance 6 between seal ring 5 and the fixed bearing support 2.
Carry effect (this effect strengthens) by such improvement via the oil that filler opening 9 is delivered to seal clearance 6 when the rotating speed of exhaust-gas turbocharger strengthens, avoided pressurized air to enter lubricant oil fully.When the lubrication pressure that is to say in the drive chamber before air pressure in the pressing chamber is higher than axial bearing seal, this also is suitable for.
Oil depends on the rotating speed of exhaust-gas turbocharger and the height 13 of seal clearance 6 to drive chamber or the pressing chamber direction conveying effect by seal clearance 6, just seal arrangement is with respect to the size of rotor shaft 1 residing diameter 13, seal arrangement here is the labyrinth-type excluder 7 of seal ring 5, thereby can adjust the conveying effect according to the selection of these sizes.

Claims (3)

1. the axial bearing seal that is used for exhaust-gas turbocharger, this exhaust-gas turbocharger has rotor shaft (1), this rotor shaft is at one end guided ground supporting turbine in the housing bore in turbine cylinder, and the guiding twelve Earthly Branches pressure-bearing wheel that contracts in the housing bore of the other end in compressor housing, wherein, a bearing support (2) of cod is arranged on the housing of exhaust-gas turbocharger immovably, thereby between the axial bore of the surface of rotor shaft (1) and fixed bearing support (2), leave oil pocket (8), described bearing support (2) one side and bearer ring (3) mating reaction of rotating with rotor shaft (1), on the other hand then along rotor shaft (1) axially on the seal ring (5) that is connected the rotation of compressor housing towards that side of compressor housing, thereby can between seal ring (5) that rotates and fixed bearing support (2), form seal clearance (6), wherein, seal ring (5) has the additional seal arrangement (7) of effect vertically, it is characterized by, radially between seal ring (5) and fixed bearing support (2), constitute described seal clearance (6) about rotor shaft (1), and the sealing gap stretches out, make oil pressure in the seal clearance when exhaust-gas turbocharger move all the time greater than the corresponding air pressure that centers in the housing of cod.
2. by the described axial bearing seal of claim 1, it is characterized by, described oil pocket (8) that is to say the radial height (10) of liquid anchor ring be significantly less than its axial width, preferably described oil pocket axial width 1/3rd, and the outer dia (11) of the additional described relatively oil pocket of seal arrangement (7) (8) of described seal ring (5) is located around described rotor shaft with a diameter (13) that has amplified the length of described seal clearance (6).
3. by claim 1 and 2 described axial bearing seals, it is characterized by, additional seal arrangement (7) is designed to labyrinth-type excluder.
CN2009101418201A 2008-05-26 2009-05-26 Axial bearing seal for an exhaust gas turbocharger Expired - Fee Related CN101592071B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008025058.9 2008-05-26
DE102008025058.9A DE102008025058B4 (en) 2008-05-26 2008-05-26 Thrust bearing seal for an exhaust gas turbocharger

Publications (2)

Publication Number Publication Date
CN101592071A true CN101592071A (en) 2009-12-02
CN101592071B CN101592071B (en) 2011-11-30

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CN2009101418201A Expired - Fee Related CN101592071B (en) 2008-05-26 2009-05-26 Axial bearing seal for an exhaust gas turbocharger

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JP (1) JP5512168B2 (en)
KR (1) KR101532439B1 (en)
CN (1) CN101592071B (en)
CH (1) CH698902B1 (en)
DE (1) DE102008025058B4 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102313022A (en) * 2011-03-18 2012-01-11 江苏华机环保设备有限责任公司 Shaft seal structure in bagasse metering device
CN114370538A (en) * 2022-01-15 2022-04-19 江苏海鼎电气科技有限公司 Multiple sealed dock spray cooling pipe

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117345770B (en) * 2023-12-05 2024-02-20 中国航发四川燃气涡轮研究院 Air inlet cabin system of air compressor tester

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
GB720816A (en) * 1952-03-18 1954-12-29 Gen Electric Canada Improvements in and relating to thrust bearings
JPH05156959A (en) * 1991-12-02 1993-06-22 Ishikawajima Harima Heavy Ind Co Ltd Thrust bearing of turbocharger
JPH09189232A (en) * 1996-01-08 1997-07-22 Mitsubishi Heavy Ind Ltd Lubricating oil seal device of exhaust gas turbine supercharger
DE19641673B4 (en) * 1996-10-11 2005-09-01 Abb Turbo Systems Ag axial plain
EP1394365B1 (en) 2002-09-02 2006-10-25 BorgWarner Inc. Turbocharger shaft sealing
US6880536B2 (en) * 2003-07-14 2005-04-19 Eaton Corporation Lubrication optimization of single spring isolator
JP2008082298A (en) * 2006-09-28 2008-04-10 Jtekt Corp Supercharger
US8348595B2 (en) * 2006-09-29 2013-01-08 Borgwarner Inc. Sealing system between bearing and compressor housing
JP5156959B2 (en) 2008-01-18 2013-03-06 ソフトバンクモバイル株式会社 Communication control system, communication control method, and program

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102313022A (en) * 2011-03-18 2012-01-11 江苏华机环保设备有限责任公司 Shaft seal structure in bagasse metering device
CN114370538A (en) * 2022-01-15 2022-04-19 江苏海鼎电气科技有限公司 Multiple sealed dock spray cooling pipe
CN114370538B (en) * 2022-01-15 2023-07-04 江苏海鼎电气科技有限公司 Multiple sealed butt joint type spray cooling pipe

Also Published As

Publication number Publication date
KR101532439B1 (en) 2015-06-29
JP2009287560A (en) 2009-12-10
CN101592071B (en) 2011-11-30
DE102008025058B4 (en) 2018-09-13
KR20090122880A (en) 2009-12-01
CH698902A2 (en) 2009-11-30
DE102008025058A1 (en) 2009-12-03
CH698902B1 (en) 2013-11-15
JP5512168B2 (en) 2014-06-04

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