WO2013173055A1 - Shaft sealing system for a turbocharger - Google Patents
Shaft sealing system for a turbocharger Download PDFInfo
- Publication number
- WO2013173055A1 WO2013173055A1 PCT/US2013/038970 US2013038970W WO2013173055A1 WO 2013173055 A1 WO2013173055 A1 WO 2013173055A1 US 2013038970 W US2013038970 W US 2013038970W WO 2013173055 A1 WO2013173055 A1 WO 2013173055A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- shaft
- sealing
- bore
- sealing surfaces
- rotatable element
- Prior art date
Links
- 238000007789 sealing Methods 0.000 title claims abstract description 128
- 230000000295 complement effect Effects 0.000 claims abstract description 18
- 239000007789 gas Substances 0.000 abstract description 20
- 239000004071 soot Substances 0.000 abstract description 14
- 239000012080 ambient air Substances 0.000 abstract description 2
- 230000002093 peripheral effect Effects 0.000 description 4
- 239000000853 adhesive Substances 0.000 description 3
- 230000001070 adhesive effect Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 239000003570 air Substances 0.000 description 1
- 230000004075 alteration Effects 0.000 description 1
- 230000003197 catalytic effect Effects 0.000 description 1
- 231100000481 chemical toxicant Toxicity 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 239000002537 cosmetic Substances 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 231100000206 health hazard Toxicity 0.000 description 1
- 230000006698 induction Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 231100000331 toxic Toxicity 0.000 description 1
- 230000002588 toxic effect Effects 0.000 description 1
- 239000003440 toxic substance Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Classifications
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- 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
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
- F02B37/183—Arrangements of bypass valves or actuators therefor
- F02B37/186—Arrangements of actuators or linkage for bypass valves
-
- 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
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/003—Preventing or minimising internal leakage of working-fluid, e.g. between stages by packing rings; Mechanical seals
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/16—Other safety measures for, or other control of, pumps
-
- 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
- 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
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/28—Arrangement of seals
-
- 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
-
- 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
- F16J15/16—Sealings between relatively-moving surfaces
-
- 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
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/18—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings
- F16J15/184—Tightening mechanisms
- F16J15/185—Tightening mechanisms with continuous adjustment of the compression of the packing
- F16J15/186—Tightening mechanisms with continuous adjustment of the compression of the packing using springs
-
- 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
- F05D2240/00—Components
- F05D2240/55—Seals
-
- 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
- F05D2250/00—Geometry
- F05D2250/20—Three-dimensional
- F05D2250/23—Three-dimensional prismatic
- F05D2250/232—Three-dimensional prismatic conical
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- Embodiments relate in general to turbochargers and, more particularly, the interface between a shaft and a housing in a turbocharger.
- Turbochargers are a type of forced induction system. They deliver air, at greater density than would be possible in the normally aspirated configuration, to the engine intake, allowing more fuel to be combusted, thus boosting the engine's horsepower without significantly increasing engine weight.
- a smaller turbocharged engine, replacing a normally aspirated engine of a larger physical size, will reduce the mass and can reduce the aerodynamic frontal area of the vehicle.
- FIG. 1 An example of a typical turbocharger (10) is shown in FIG. 1.
- the turbocharger (10) uses the exhaust flow from the engine exhaust manifold to drive a turbine wheel (12), which is located in a turbine housing (14). Once the exhaust gas has passed through the turbine wheel (12) and the turbine wheel (12) has extracted energy from the exhaust gas, the spent exhaust gas exits the turbine housing (14) through an exducer and is ducted to the vehicle downpipe and usually to after-treatment devices such as catalytic converters, particulate traps, and NO x traps.
- after-treatment devices such as catalytic converters, particulate traps, and NO x traps.
- the turbine volute is fluidly connected to the turbine exducer by a bypass duct.
- Flow through the bypass duct is controlled by a wastegate valve (16). Because the inlet of the bypass duct is on the inlet side of the turbine volute, which is upstream of the turbine wheel (12), and the outlet of the bypass duct is on the exducer side of the volute, which is downstream of the turbine wheel (12), flow through the bypass duct, when in the bypass mode, bypasses the turbine wheel (12), thus not adding to the power extracted by the turbine wheel.
- an actuating or control force must be transmitted from outside the turbine housing (14), through the turbine housing (14), to the wastegate valve (16) inside the turbine housing (14).
- a wastegate pivot shaft (18) extends through the turbine housing (14).
- An actuator (20) is provided external to the turbine housing (14).
- the actuator (20) is connected to a wastegate lever arm (22) via a linkage (24), and the wastegate lever arm (22) is connected to the wastegate pivot shaft (18).
- the pivot shaft (18) is connected to the wastegate valve (16). Actuating force from the actuator (20) is translated into rotation of the pivot shaft (18), which moves the wastegate valve (16) inside of the turbine housing (14).
- the wastegate pivot shaft (18) rotates in a cylindrical bushing (26) provided within a bore (28) in the turbine housing (14).
- the wastegate pivot shaft (18) rotates within a bore in the turbine housing (14) without a bushing.
- Turbine housings (14) experience great temperature flux during the operation of the turbocharger (5).
- the outside of the turbine housing (14) is exposed to ambient air temperature while the turbine volute surfaces contact exhaust gases ranging from 740°C to 1050°C, depending on the fuel used in the engine.
- the actuator (20) be able to control the wastegate valve (16) to thereby control flow to the turbine wheel (12) in an accurate, repeatable, non-jamming manner.
- annular clearance (34) between the outer peripheral surface (30) of the pivot shaft (18) and the inner peripheral surface (32) of the bore in the bushing (26), in which it is located.
- An escape of hot, toxic exhaust gas and soot from the pressurized turbine housing (14) is possible through this clearance. Soot deposits are unwanted from a cosmetic standpoint, and the escape of exhaust gas containing CO, C0 2 , and other toxic chemicals can be a health hazard to the occupants of the vehicle. This makes exhaust leaks a particularly sensitive concern in vehicles such as ambulances and buses. From an emissions standpoint, the gases which escape from the turbine stage are not captured and treated by the engine/vehicle aftertreatment systems.
- seal means such as seal rings (also called piston rings) have been used.
- seal rings also called piston rings
- a seal ring (36) is provided between the pivot shaft (18) and the bushing (26).
- the seal ring (36) can seal against the inner peripheral surface (32) of the bushing (26) and the shaft (18).
- the seal ring (36) can partly reside within a ring groove (38) provided in the shaft (18).
- ring seal (36) can minimize the passage of exhaust gas and soot (40) to some degree, a substantially complete sealing condition may be achieved only when the seal ring directly contacts a sidewall (42, 44) of the seal ring groove (38).
- a leakage path as generally depicted in FIG. 2 can exist. While there have been numerous efforts to reduce this leakage by providing a plurality of ring seals and by modifying the pressure differential across the plurality of seal rings by introducing a pressure or vacuum between the rings, but potential leakage always exists unless the seal rings (36) are in direct contact with the side wall(s) (42, 44) of the groove (38).
- Embodiments described herein can provide an effective sealing system for a turbocharger in the interface between a rotatable element and a surrounding structure, such as at the interface a pivot shaft is received in the turbine housing of a wastegated or VTG turbocharger.
- the sealing system can introduce a spring loaded, self-centering, complementary pair of narrowing sealing surfaces, which can be frusto-spherical or frusto-conical in conformation.
- the spring pressure can force the pair of complementary sealing surfaces together producing sealing contact and maintain such contact.
- FIG. 1 is a cross-sectional view of a typical wastegate turbocharger
- FIG. 2 is a section view of an interface between a shaft and a bushing in a typical turbocharger, showing, a gas leakage path;
- FIGS. 3A-B is a cross-sectional view of a first embodiment of a sealing system
- FIG. 4A is a cross-sectional view of a second embodiment of a sealing system, wherein a non-rigid connection is provided between an insert and a shaft;
- FIG. 4B is a cross-sectional view of the second embodiment of a sealing system, wherein a rigid connection is provided between the insert and the shaft;
- FIG. 5 is a cross-sectional view of an alternative configuration of the second embodiment of a sealing system
- FIG. 6 is a cross-sectional view of a third embodiment of a sealing system
- FIG. 7 is a cross-sectional view of an alternative arrangement in which the sealing surfaces of the sealing system are frusto-conical
- FIG. 8 is a cross-sectional view of an alternative arrangement in which the sealing system includes a piston ring.
- Arrangements described herein relate to device turbocharger having an improved sealing system for the interface between a shaft and a surround structure (e.g., between a pivot shaft and a pivot shaft bushing).
- a surround structure e.g., between a pivot shaft and a pivot shaft bushing.
- Detailed embodiments are disclosed herein; however, it is to be understood that the disclosed embodiments are intended only as exemplary. Therefore, specific structural and functional details disclosed herein are not to be interpreted as limiting, but merely as a basis for the claims and as a representative basis for teaching one skilled in the art to variously employ the aspects herein in virtually any appropriately detailed structure. Further, the terms and phrases used herein are not intended to be limiting but rather to provide an understandable description of possible implementations. Arrangements are shown in FIGS. 3-8, but the embodiments are not limited to the illustrated structure or application.
- Embodiments are directed to the use of complementary narrowing sealing surfaces provided on a rotatable or movable element (e.g., a shaft, the pivot shaft or an element provided on a pivot shaft) and a surrounding structure (e.g., the pivot shaft bushing) and along with a system for maintaining engagement of these sealing surfaces during operation of the turbocharger.
- a rotatable or movable element e.g., a shaft, the pivot shaft or an element provided on a pivot shaft
- a surrounding structure e.g., the pivot shaft bushing
- the narrowing sealing surfaces can have any suitable form. Generally, the diameter or width of the narrowing sealing surfaces can decrease along the length of the shaft or rotatable element. In one embodiment, one sealing surface can include a region of narrowing concavity, and the other sealing surface can have a complementary region of narrowing convexity.
- suitable narrowing sealing surfaces can include surfaces that are generally frusto-conical, frusto-spherical, part conical, part spherical, stepped, even combinations of flat and conical or flat and spherical, or combinations of differently angled conical surfaces or combinations of different curvature surfaces used in the interface of shaft and bushing.
- the conical surfaces can be provided at any suitable angle, and the curvature surfaces can be provided at any suitable curvature.
- the narrowing sealing surfaces can be substantially concentric with the shaft axis.
- the system (50) can include a complementary pair of narrowing sealing surfaces (52, 54) provided on the pivot shaft (18) and the bushing (26). While the sealing surfaces (52, 54) are shown as being frusto-conical, it will be appreciated that the sealing surfaces (52, 54) can have any suitable configuration, some examples of which are described above.
- the sealing surfaces (52, 54) are referred to as "frusto" conical or “frusto” spherical since the peak of the shape would be in the area occupied by the pivot shaft (18), and thus, would be “cut off.” This frusto-conical interface can prevent the pivot shaft (18) from rocking and tilting on the bushing (26) while centering the shaft (18) in the bushing (26).
- the bushing (26) can be axially constrained by a flange (56).
- the bushing (26) can be constrained axially and angularly by a pin (not shown) inserted between an outside diameter of the pivot shaft bushing (26) and the turbine housing (14), or it can be axially constrained by mechanical engagement and/or by other suitable means toward the inner end of the bushing (26).
- the sealing surface (54) can be defined by the shaft (18) itself, as is shown in FIG. 3A-3B.
- the feature can be formed into the shaft (18), such as by machining.
- the sealing surface (18) can be defined by a separate element (not shown) that can be rigidly attached to the shaft (18), such as by press fit, mechanical engagement, fasteners, adhesives and/or other suitable attachment means. While FIG.
- FIG. 3 shows the sealing surface (54) on the shaft as being convex frusto- conical and the sealing surface (52) provided on the bushing (26) as being concave frusto-conical, it will be appreciated that the opposite arrangement could be provided, that is, a convex frusto-conical sealing surface can be provided on the bushing (26) and a concave frusto-conical sealing surface can be provided on the shaft (18).
- the system (50) can further include a biasing element.
- the biasing element can be a spring (58).
- the spring (58) can be any suitable type of spring, such as a helical spring or a wave spring. In the arrangement shown in FIGS. 3 A and B, the spring (58) can be operatively positioned between a structure surrounding a portion of the shaft (18) and a structure attached to an outer end region (60) of the shaft (18). For instance, the spring (58) can be operatively positioned between the pivot shaft bushing (26) and the lever arm (22) attached to the end region (60) of the shaft (18).
- the lever arm (22) can be operatively connected to the shaft (18) in any suitable manner, such as by one or more fasteners, mechanical engagement, adhesives, welding, and/or other means.
- operatively connected can include direct or indirect connections, including connections without direct physical contact.
- outer and inner are used with respect to the pivot shaft (18) for convenience to note the general position of a portion of the shaft (18) relative to the wastegate valve (16) or other element that movement of the shaft (18) directly or indirectly affects. Thus, an “inner” portion of the shaft (18) is located closer to the wastegate valve (16) than an "outer” portion of the shaft (18).
- the spring (58) can operatively engage an outward-facing surface (62) on the pivot shaft bushing (26) and a bushing-facing surface (64) of the lever arm (22).
- the spring (58) can exert a force generally in a second direction (68) on the outward facing surface (62) of the pivot shaft bushing (26).
- the spring (58) can simultaneously exert a force in a first direction (66) on the surface (64) of the lever arm (22).
- the first direction 66 can be opposite to the second direction 68. Consequently, the sealing surface (52) can be pushed in the second direction (68) (that is, downward in the arrangement shown in FIG. 3B) due to the force of the spring (58).
- the sealing surface (54) can be pulled in the first direction (66) (that is, upward in the arrangement shown in FIG. 3B), as the lever arm (22) is being pushed in the first direction (66) by the spring (58), thereby pulling the operatively connected pivot shaft (18) with it.
- the complementary pair of sealing surfaces (52, 54) can be brought together by the reaction of a spring (58), thereby producing a seal to prevent a flow of gas and soot from escaping the turbine housing (14) to the environment.
- Such a seal can be maintained by the continued force exerted by the spring (58).
- the self-centering action of the spring (58) with the pair of sealing surfaces (52, 54) can pull the pivot shaft (18) substantially into concentricity with the desired axis of rotation about the axis (70), resisting the cocking action caused by the seat pressure requirement of the actuator.
- the overlap of the wastegate valve face with the wastegate port, against which it seals can be smaller, resulting in the opportunity to reduce the size of the wastegate valve head.
- FIGS. 4A-B A second embodiment of a shaft sealing system (50') is shown in FIGS. 4A-B.
- the pair of complementary narrowing sealing surfaces (52, 54) can be located toward the outside of the wastegate pivot shaft (18) to create an "outer seal".
- the above description of the sealing surfaces (52, 54) above is equally applicable to system (50').
- the sealing surface (54) on the shaft (18) can be convex frusto-conical and the sealing surface (52) provided on the bushing (26) can be concave frusto-conical.
- the sealing surface (54) can be defined by the shaft (18). However, in some instances, such an arrangement may not be possible or practical.
- the sealing surface (54) can be provided on a separate insert (72) that is assembled to the wastegate pivot shaft (18) after the pivot shaft (18) is inserted into the bushing (26) in which it resides.
- the insert (72) can be attached to the shaft (18) in any suitable manner, including, for example, in a non-rigid manner so that the shaft (18) can move relative to the insert (72), including along the direction of axis (70).
- the insert (72) can be rigidly attached to that shaft (18).
- "Rigidly attached” means that the insert (72) is formed with the shaft (18) or the insert (72) is attached to the shaft (18) such that the shaft (18) and insert (72) do not substantially move relative to each other at least in the direction of axis (70), that is, they move together at least in the direction of axis (70).
- rigid attachment can include, for example, press fit, mechanical engagement, fasteners, adhesives and/or other suitable attachment means.
- the insert (72) can be made of any suitable material.
- the insert (72) can be made of a high temperature resistant metal that is compatible with the shaft (18) and/or the bushing (26) from at least tribological and/or galvanic corrosion standpoints.
- the system (50') can further include a biasing element.
- the biasing element can be a spring (58).
- the spring (58) can be any suitable type of spring, such as a helical spring or a wave spring.
- the spring (58) can be operatively positioned between the insert (72) (or even the shaft (18) itself if the sealing surface (54) is provided on the shaft (18)) and a structure attached to an outer end region (60) of the shaft (18), such as the lever arm (22).
- Such an arrangement may be suitable for instances in which the insert (72) is non-rigidly attached to the shaft (18), such as by a slip fit.
- the shaft (18) and the insert (72) can move relative to each other at least in the direction of axis (70).
- the spring (58) can operatively engage an outward-facing surface (74) on the insert (72) or shaft (18) as well as the bushing facing surface (64) of the lever arm (22).
- the spring (58) can exert a force in a first direction (66) on the surface (64) of the lever arm (22).
- the spring (58) can simultaneously exert a force generally in the second direction (68) on the outward- facing surface (74) on the insert (72). Consequently, the sealing surface (54) can be pushed in the second direction (68) (that is, downward in the arrangement shown in FIG. 4A) due to the force of the spring (58).
- the sealing surface (52) provided on the bushing (26) can be pulled in the first direction (66) (that is, upward in the arrangement shown in FIG.
- the spring (58) or other biasing element can be operatively positioned in an interface between the shaft (18) (or other structure connected to the shaft (18)) and an end surface (65) of the bushing (26).
- FIG. 4B An example of such an arrangement is shown in FIG. 4B.
- the spring (58) can exert a force generally in the first direction (66) on the end (65) of the bushing (26), pushing its sealing surface (52) in the first direction
- the spring (58) can simultaneously exert a force in a second direction (68) on the shaft (18) (or other structure connected to the shaft (18).
- the spring (58) can exert a force of the shoulder surface (63) of the shaft (18).
- the shoulder surface (63) can include a recess (67) to receive the spring (58). Consequently, the sealing surface (54) can be pulled in the second direction (68), that is, downward in the arrangement shown in FIG. 4B due to the force of the spring (58) upon the shat (18) rigidly attached to the insert (72).
- a seal is produced and maintained between the complementary pair of sealing surfaces (52, 54).
- FIG. 5 Another example of a sealing system is shown in FIG. 5. In such an
- the intersection of the frusto-spherical surface (52) with the inside diameter of the insert (72) can be cut short to produce a flat surface (76).
- the flat surface (76) can be generally transverse to the axis of rotation (70). In one embodiment, the flat surface (76) can be substantially perpendicular to the axis (70).
- An abutment landing (78) can be formed on the shaft (18), such as by a reduction in outer diameter of the shaft (18), as is shown in FIG. 5.
- a first spring (58) can be operatively positioned between the insert (72) (or even the shaft (18) itself if the sealing surface (54) is provided on the shaft (18)) and a structure attached to the shaft (18) (e.g., the lever arm (22)).
- a second spring (58') or other biasing element can be operatively positioned between the shaft (18) (or other structure connected to the shaft (18)) and the end surface (65) of the bushing (26).
- the second spring (58') can operatively engage a shoulder surface (63) of the shaft (18).
- the shoulder surface (63) can include a recess (67).
- the first spring (58) can operatively engage the lever arm (22) and the insert (72).
- the first spring (58) can exert a force generally in a first direction (66) on the lever arm (22).
- the first spring (58) can also exert a force generally in the second direction (68) on the insert (72).
- the sealing surface (54) and the flat surface (76) can be pushed in the second direction (68) (that is, downward in the arrangement shown in FIG. 5) due to the force of the spring (58).
- the second spring (58') or other biasing element can be operatively positioned between the shoulder surface (63) of the shaft (18) (or other structure connected to the shaft (18)) and an end surface (65) of the bushing (26).
- the second spring (58') can exert a force generally in the first direction (66) on the end (65) of the bushing (26), pushing its sealing surface (52) in the first direction (66) (that is, upward in the arrangement shown in FIG. 5).
- the force exerted by the first spring (58) can push the insert (72) inward facing flat surface (76) and the abutment landing (78) of the shaft (18) toward each other and into contact with each other.
- Such contact between the flat surface (76) and the abutment landing (78) can result in substantially sealing engagement, thereby producing an additional sealing interface between the shaft (18) and the insert (72) to minimize soot and gas leakage.
- the sealing interface can be maintained by the force exerted by the first spring (58).
- the force exerted by the first spring (58) can push the sealing surface (54) in the second direction (68), and force exerted by the second spring (58') can push the sealing surface (52) in the first direction (66).
- the surfaces (52, 54) can be brought into substantially sealing contact with each other.
- the substantially sealing contact between the surfaces (52, 54) can be maintained by the first and second springs (58, 58').
- the insert (72) can be clamped in place such that the flat surface (76) and the abutment landing (78) directly abut each other.
- Such an arrangement can be maintained by welding the lever arm (22) to the shaft (18).
- the sealing surfaces (52, 54) can be brought into contact and maintained in contact by the second spring (58') such that the first spring (58) may not be needed.
- FIG. 6 shows one possible combination of aspects shown in FIGS. 3A-B and 4.
- the spring (58) can operatively engage the insert (72) or shaft (18) as well as the lever arm (22).
- the spring (58) can exert a force in a first direction (66) on the lever arm (22).
- the spring (58) can simultaneously exert a force generally in the second direction (68) on the insert (72). Consequently, the outer sealing surface (54) can be pushed in the second direction (68) (that is, downward in the arrangement shown in FIG.
- the outer sealing surface (52) can be pulled in the first direction (66) (that is, upward in the arrangement shown in FIG. 6), as the lever arm (22) is being pushed in the first direction (66) by the spring (58), thereby pulling the operatively connected pivot shaft (18) and bushing (26) with it.
- the complementary pair of sealing surfaces (52, 54) can be brought together by the reaction of a spring (58), thereby producing a seal to prevent a flow of gas and soot from escaping the turbine housing (14) to the environment. Such a seal can be maintained by the continued force exerted by the spring (58).
- the force exerted by the spring (58) can pull the inner convex frusto-spherical surface (54') into the inner concave frusto-spherical surface (52').
- the force exerted by the spring (58) can also push the insert (72) inward (that is, downward in FIG. 6), thereby forcing the outer convex frusto-spherical surface (54') into the outer concave frusto-spherical surface (54'), thus providing twin centering mechanisms and twin sealing interfaces.
- the arrangement shown in FIG. 6 is suitable for embodiments in which the insert (72) is non-rigidly attached (e.g., slip fit) to the shaft (18).
- the complementary narrowing sealing surfaces (52, 54) can have any suitable configuration.
- the sealing surfaces are shown in FIGS. 3-6 as being frusto-spherical surfaces, it will be understood that embodiment are not limited to frusto-spherical sealing surfaces.
- FIG. 7 shows an alternative arrangement in which the sealing surfaces are configured as frusto -conical surfaces. In this
- an insert (72) containing a frusto-conical sealing surface (54) is pushed into a complementary frusto-conical sealing surface (52) in the bushing (26), thereby centering the insert (72) and shaft (18) in the bushing (26) and providing a sealing interface to prevent the passage of soot and gas from inside the turbine housing to the environment.
- FIG. 8 presents a further alternative arrangement of the sealing system.
- One or more ring seals such as piston ring (80), can be used to seal the leakage path between the inside diameter of the bores in the insert (72) and the outer peripheral surface (30) of the pivot shaft (18).
- the above arrangements can provide an effective sealing system.
- the seal can be maintained under substantially all turbocharger operational conditions.
- the sealing systems are not dependent on operational conditions (e.g., turbine housing pressure) to hold the sealing surfaces together.
- the sealing systems presented herein can tolerate misalignment of the operative components to a much greater degree than piston ring seal systems used in the past.
- the terms "a” and “an,” as used herein, are defined as one or more than one.
- the term “plurality,” as used herein, is defined as two or more than two.
- the term “another,” as used herein, is defined as at least a second or more.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Supercharger (AREA)
- Sealing Devices (AREA)
Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/400,100 US20150097345A1 (en) | 2012-05-17 | 2013-05-01 | Shaft sealing system for a turbocharger |
IN9988DEN2014 IN2014DN09988A (en) | 2012-05-17 | 2013-05-01 | |
RU2014148497A RU2014148497A (en) | 2012-05-17 | 2013-05-01 | SHAFT SEALING SYSTEM FOR TURBOCHARGER |
CN201380023830.XA CN104271919B (en) | 2012-05-17 | 2013-05-01 | Axle sealing system for turbocharger |
KR1020147033963A KR102075603B1 (en) | 2012-05-17 | 2013-05-01 | Shaft sealing system for a turbocharger |
DE112013002028.9T DE112013002028T5 (en) | 2012-05-17 | 2013-05-01 | Shaft sealing system for a turbocharger |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201261648163P | 2012-05-17 | 2012-05-17 | |
US61/648,163 | 2012-05-17 |
Publications (1)
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WO2013173055A1 true WO2013173055A1 (en) | 2013-11-21 |
Family
ID=49584159
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US2013/038970 WO2013173055A1 (en) | 2012-05-17 | 2013-05-01 | Shaft sealing system for a turbocharger |
Country Status (7)
Country | Link |
---|---|
US (1) | US20150097345A1 (en) |
KR (1) | KR102075603B1 (en) |
CN (1) | CN104271919B (en) |
DE (1) | DE112013002028T5 (en) |
IN (1) | IN2014DN09988A (en) |
RU (1) | RU2014148497A (en) |
WO (1) | WO2013173055A1 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102014207671A1 (en) * | 2014-04-24 | 2015-10-29 | Bayerische Motoren Werke Aktiengesellschaft | Exhaust gas turbocharger with a wastegate valve |
WO2015190356A1 (en) * | 2014-06-09 | 2015-12-17 | 株式会社Ihi | Supercharger |
EP3276141A1 (en) * | 2016-07-24 | 2018-01-31 | Honeywell International Inc. | Turbine wastegate |
US20180045105A1 (en) * | 2016-07-24 | 2018-02-15 | Honeywell International Inc. | Turbocharger turbine wastegate assembly |
US10215088B2 (en) | 2016-07-24 | 2019-02-26 | Garrett Transporation I Inc. | Method of assembling a turbine wastegate assembly |
CN109707502A (en) * | 2017-10-26 | 2019-05-03 | 盖瑞特交通一公司 | Turbocharger turbine exhaust gas door component |
DE102017128830A1 (en) * | 2017-12-05 | 2019-06-06 | Continental Automotive Gmbh | Wastegate arrangement for an exhaust gas turbocharger |
Families Citing this family (14)
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DE102012204497A1 (en) * | 2012-03-21 | 2013-09-26 | Mahle International Gmbh | Wastegate valve device |
US9889323B2 (en) * | 2013-03-13 | 2018-02-13 | The Boeing Company | Fire seal end cap and associated multi-member assembly and method |
JP6361735B2 (en) * | 2014-08-29 | 2018-07-25 | 株式会社Ihi | Turbocharger |
CN106605052B (en) * | 2014-08-29 | 2019-03-15 | 株式会社Ihi | Flow variable valve mechanism and booster |
JP6705146B2 (en) * | 2015-10-07 | 2020-06-03 | 株式会社Ihi | Variable flow valve mechanism and supercharger |
US20200370470A1 (en) * | 2017-03-30 | 2020-11-26 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Exhaust bypass device and turbocharger |
US10590789B2 (en) * | 2017-04-26 | 2020-03-17 | Borgwarner Inc. | Turbocharger radial seal |
JP6669707B2 (en) * | 2017-11-08 | 2020-03-18 | 本田技研工業株式会社 | Waste gate sealing jig |
JP7049370B2 (en) * | 2018-01-30 | 2022-04-06 | 三菱重工エンジン&ターボチャージャ株式会社 | Drive device and link drive mechanism of valve device and turbocharger equipped with this drive device |
US11242890B2 (en) * | 2018-07-03 | 2022-02-08 | GM Global Technology Operations LLC | Articulating joint with a high wear life |
DE112019004994T5 (en) * | 2018-10-05 | 2021-07-01 | Ihi Corporation | Warehouse structure |
DE102018217602A1 (en) * | 2018-10-15 | 2020-04-16 | Continental Automotive Gmbh | Exhaust gas turbine of an exhaust gas turbocharger with a sealed wastegate valve device and exhaust gas turbocharger |
US10711690B2 (en) | 2018-11-06 | 2020-07-14 | Borgwarner Inc. | Wastegate assembly and turbocharger including the same |
JP7514786B2 (en) | 2021-03-12 | 2024-07-11 | 三菱重工エンジン&ターボチャージャ株式会社 | Shaft support device for turbocharger and method for assembling shaft support device for turbocharger |
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- 2013-05-01 CN CN201380023830.XA patent/CN104271919B/en not_active Expired - Fee Related
- 2013-05-01 RU RU2014148497A patent/RU2014148497A/en not_active Application Discontinuation
- 2013-05-01 WO PCT/US2013/038970 patent/WO2013173055A1/en active Application Filing
- 2013-05-01 US US14/400,100 patent/US20150097345A1/en not_active Abandoned
- 2013-05-01 IN IN9988DEN2014 patent/IN2014DN09988A/en unknown
- 2013-05-01 KR KR1020147033963A patent/KR102075603B1/en active IP Right Grant
- 2013-05-01 DE DE112013002028.9T patent/DE112013002028T5/en not_active Withdrawn
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DE102014207671A1 (en) * | 2014-04-24 | 2015-10-29 | Bayerische Motoren Werke Aktiengesellschaft | Exhaust gas turbocharger with a wastegate valve |
DE102014207671B4 (en) | 2014-04-24 | 2023-09-28 | Bayerische Motoren Werke Aktiengesellschaft | Exhaust gas turbocharger with a wastegate valve |
WO2015190356A1 (en) * | 2014-06-09 | 2015-12-17 | 株式会社Ihi | Supercharger |
CN106460647A (en) * | 2014-06-09 | 2017-02-22 | 株式会社Ihi | Supercharger |
JPWO2015190356A1 (en) * | 2014-06-09 | 2017-04-20 | 株式会社Ihi | Turbocharger |
US10408085B2 (en) | 2014-06-09 | 2019-09-10 | Ihi Corporation | Turbocharger |
US10215088B2 (en) | 2016-07-24 | 2019-02-26 | Garrett Transporation I Inc. | Method of assembling a turbine wastegate assembly |
US10227916B2 (en) * | 2016-07-24 | 2019-03-12 | Garrett Transportation I Inc. | Turbocharger turbine wastegate assembly |
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US20180045105A1 (en) * | 2016-07-24 | 2018-02-15 | Honeywell International Inc. | Turbocharger turbine wastegate assembly |
EP3276141A1 (en) * | 2016-07-24 | 2018-01-31 | Honeywell International Inc. | Turbine wastegate |
CN109707502A (en) * | 2017-10-26 | 2019-05-03 | 盖瑞特交通一公司 | Turbocharger turbine exhaust gas door component |
DE102017128830A1 (en) * | 2017-12-05 | 2019-06-06 | Continental Automotive Gmbh | Wastegate arrangement for an exhaust gas turbocharger |
WO2019110581A1 (en) | 2017-12-05 | 2019-06-13 | Continental Automotive Gmbh | Wastegate assembly for a turbocharger |
Also Published As
Publication number | Publication date |
---|---|
CN104271919A (en) | 2015-01-07 |
KR102075603B1 (en) | 2020-03-02 |
IN2014DN09988A (en) | 2015-08-14 |
DE112013002028T5 (en) | 2015-03-12 |
CN104271919B (en) | 2018-05-01 |
US20150097345A1 (en) | 2015-04-09 |
KR20150013684A (en) | 2015-02-05 |
RU2014148497A (en) | 2016-06-27 |
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