EP3000998B1 - Ventilsitzeinsatz für einen Verbrennungsmotor - Google Patents

Ventilsitzeinsatz für einen Verbrennungsmotor Download PDF

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Publication number
EP3000998B1
EP3000998B1 EP14186281.3A EP14186281A EP3000998B1 EP 3000998 B1 EP3000998 B1 EP 3000998B1 EP 14186281 A EP14186281 A EP 14186281A EP 3000998 B1 EP3000998 B1 EP 3000998B1
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EP
European Patent Office
Prior art keywords
section
valve seat
seat insert
surface section
cylinder head
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.)
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Application number
EP14186281.3A
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English (en)
French (fr)
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EP3000998A1 (de
Inventor
Dirk Milde
Frank Witt
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.)
Caterpillar Motoren GmbH and Co KG
Original Assignee
Caterpillar Motoren 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 Caterpillar Motoren GmbH and Co KG filed Critical Caterpillar Motoren GmbH and Co KG
Priority to EP14186281.3A priority Critical patent/EP3000998B1/de
Priority to CN201580051146.1A priority patent/CN106715846B/zh
Priority to PCT/EP2015/001743 priority patent/WO2016045768A1/en
Priority to KR1020177009341A priority patent/KR102430345B1/ko
Publication of EP3000998A1 publication Critical patent/EP3000998A1/de
Application granted granted Critical
Publication of EP3000998B1 publication Critical patent/EP3000998B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/12—Cooling of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/12—Cooling of valves
    • F01L3/14—Cooling of valves by means of a liquid or solid coolant, e.g. sodium, in a closed chamber in a valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/22—Valve-seats not provided for in preceding subgroups of this group; Fixing of valve-seats
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
    • F02D9/1005—Details of the flap
    • F02D9/101—Special flap shapes, ribs, bores or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
    • F02D9/109—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps having two or more flaps

Definitions

  • the present disclosure generally relates to a valve of an internal combustion engine and, more particularly, to a valve seat insert for a valve of an internal combustion engine.
  • valve spindles and valve seats are, however, subject to adverse conditions such as high temperatures and aggressive exhaust components. Despite those adverse conditions, long life times are desired.
  • valve seat inserts are used that are press-fitted or shrink-fitted into respective valve openings of a cylinder head.
  • a valve seat insert is configured to form a circumferential cooling channel together with the sidewall of the cylinder head's opening.
  • the cooling channel is connected to the engine cooling circuit and provides for cooling the valve seat insert as well as indirectly the bottom part of the valve spindle via its contact with the valve seat in the closed state of the valve.
  • valve seat rings are disclosed in DE 43 28 904 A1 , DE 23 55 292 B1 , and GB 1 275 499 .
  • the present disclosure is directed, at least in part, to improving or overcoming one or more aspects of prior systems.
  • a valve seat insert for a cylinder head of an internal combustion engine comprises a ring-shaped body defining a passage for enabling a fluid to pass through the body along an axial direction from an entrance side to an exit side of the valve seat insert.
  • the body comprises an entrance side section with a first contact surface section, an abutting surface section, and a valve sealing surface section.
  • the body comprises further an exit side section with a second contact surface section and an arch section axially extending from the entrance side section to the exit side section and decreasing in material thickness from the entrance side section towards the exit side section up to a minimum thickness axial position that is located in the half of the arch section being close to the exit side section.
  • a valve seat insert for a cylinder head of an internal combustion engine comprises a ring-shaped body defining a passage for enabling a fluid to pass through the body along an axial direction from an entrance side to an exit side, wherein the body comprises an entrance side section with a first contact surface section for forming a first sealed contact with the cylinder head in the mounted state, an abutting surface section for defining the position when mounted at the cylinder head, and a valve sealing surface section adapted to a valve spindle, an exit side section with a second contact surface section for forming a second sealed contact with the cylinder head in the mounted state, and an arch section delimiting a cooling channel in radial direction from the passage, wherein the cooling channel is formed, in the mounted state of the valve seat insert, between the valve seat insert and the cylinder head, and wherein the arch section decreases in axial direction from the entrance side in material thickness along at least 60 % of the arch section.
  • a retrofitting method for a combustion engine having a plurality of cylinders, each of the plurality of cylinders being associated with at least one exhaust valve comprises the step of attaching the valve seat insert as described above to an exhaust opening of a cylinder head of an internal combustion engine.
  • the present disclosure may be based in part on the discovery that cracks in the valve seat insert formed starting from the cooling channel, and in particular from the valve seat side of the cooling channel. It was realized that the valve seat insert is subject to at least two types of stress: static stress/load caused by the press-fitting, the underlying tolerances, and/or the required coaxial design as well as alternating stress/load caused by the combustion, specifically the combustion pressure. It is herein proposed to spatially separate those stress/load regions by a specific geometrical design of the valve seat insert. In particular, that geometric design may be achieved while maintaining prior surface shapes with the exception of the shape of the cooling channel. The proposed designs may reduce the number of the above mentioned cracks, delay their formation, or even avoid their formation at all.
  • the present disclosure may further be based in part on the discovery that adjusting the curvature radii of the cooling channel for a given inner surface shape may allow moving the static stress region caused by the mounting towards the exist side of the valve seat insert, i.e. to the side opposite of the valve seat side.
  • providing a minimum thickness of the material of the valve seat insert in an arch section of the same at a distance from an entrance side section (subject to the interaction with the valve spindle), may form a hinge-like section being the center of the static stress. This may result in an improved stress condition of the valve seat insert.
  • moving the minimum thickness close to an exit side section may maximize the spatial separation of the static stress and the alternating stress.
  • FIG. 1 An exemplary embodiment of an internal combustion engine having a valve seat insert is described in the following with reference to Figs. 1 and 2 .
  • Figs. 3 to 5 illustrate exemplary embodiments of valve seat inserts.
  • an internal combustion engine 100 includes an engine block 101 that at least partially defines a plurality of cylinders 102, a piston 110 slidably disposed within each cylinder 102, and a cylinder head 104 associated with each cylinder 102.
  • Engine 100 further includes a plurality of inlet valves 106 and exhaust valves 108 associated with the plurality of cylinders 102.
  • Example of engine 100 include natural gas, spark ignited, V-style turbocharged and after-cooled engines that may have, for example, 8, 12, or 16 cylinders, each cylinder having, for example, 2 inlet and 2 exhaust valves.
  • engine 100 may be any other type of internal combustion engines such as, for example, a dual fuel powered engine.
  • engine 100 may include a greater or lesser number of cylinders 102, and cylinders 102 may be disposed in an "in-line" configuration, or in any other suitable configuration.
  • inlet valves 106 and exhaust valves 108 may open and close to allow a mixture of gas and air to enter each cylinder, and to allow a flow of exhaust to exit each cylinder, respectively.
  • inlet valves 106 and exhaust valves 108 include valve spindles 142 that can block respective flow through the valves.
  • FIG. 2 shows an enlarged (non-planar) cross-sectional view of inlet valve 106 and exhaust valve 108 of, for example, combustion engine 100.
  • Inlet valve 106 and exhaust valve 108 may have a similar configuration such that only the configuration of exhaust valve 108 will be described in detail in the following. However, it should be appreciated that the same description may also apply to inlet valve 106.
  • Exhaust valve 108 includes a valve guide 140, a valve spindle 142, and a valve seat insert 10.
  • Valve guide 140 may have an elongated cylindrical shape having a lower end 141, an upper end 143, and a through hole 145. Valve guide 140 may be secured to cylinder head 104 in a known manner.
  • Valve spindle 142 includes a bottom part 144 with a spindle seal. Valve spindle 142 is disposed in through hole 145 of valve guide 140 such that it can slide inside through hole 145 up and down. Valve spindle 142 is biased via a biasing spring 147 into a closing position in which the spindle seal contacts valve seat insert 10. Valve spindle 142 can be actuated to move down to an opening position via an actuating mechanism 112 that is connected to, e.g., a camshaft 114 of engine 100 (see FIG. 1 ). In alternative configurations, a common rail system may be used to actuate the valves.
  • Cylinder head 104 comprises a cooling channel system 148 that in particular supplies coolant to a cooling channel 12 that is formed between cylinder head 104 and an outer side of valve seat insert 10.
  • cooling channel 12 is provided with a coolant supply and release connection, located, for example, at opposing ends.
  • the cut view of Fig. 2 does not explicitly show a connection between cooling channel system 148 and cooling channel 12 as the same is not in the plane of the cross-section.
  • valve seat insert 10 usually only exhaust valves 108 comprise cooled valve seat inserts 10.
  • the cooling of valve seat insert 10 allows cooling of bottom part 144 while exhaust valve 108 is in the closing position.
  • valve seat inserts for inlet valves 106 may not need to be cooled via a cooling channel system as the inlet air may provide sufficient cooling of the valve spindle. Accordingly, valve seat insert 150 shown in Fig. 2 does not form a cooling channel.
  • Valve seat insert 10 is mounted in an exhaust opening 104A (see also Fig. 4 ) of cylinder head 104 which extends from a combustion zone face into cylinder head 104 for releasing exhaust air from cylinder 102.
  • the mounting depth of valve seat insert 10 extends, for example, along a length within the range of 40 mm to 80 mm. During that length, the respective sidewalls of exhaust opening 104A are adapted for receiving valve seat insert 10, for example, by press and/or shrink fitting.
  • valve seat insert 10 may be cryogenic shrink fitted in exhaust opening 104A.
  • valve seat insert 10 may be cryogenic shrink fitted in a respective mounting section of exhaust opening 104A.
  • the circumference of valve seat insert 10 may have an outer diameter with essentially the same nominal dimension of the opening diameter but with a different tolerance thereby facilitating shrink fitting of, e.g., valve seat insert 10 and into its respective exhaust opening 104A.
  • valve seat insert 10A is shown in a radial cross-section.
  • a dashed line 104' indicates cylinder head 104 in the mounted state.
  • Valve seat insert 10A comprises a ring-shaped body 20 that defines a passage 22 (see also Fig. 5 ).
  • exhaust gas can flow through passage 22, thereby passing through body 20 along an axial direction Z.
  • axial direction Z may correspond to the direction of the symmetry axis (see symmetry axis S z in Fig. 4 ).
  • axial direction Z as well as a radial direction R (extending orthogonal to axial direction Z) are indicated schematically.
  • exhaust will pass from an entrance side 24 to an exit side 26 of valve seat insert 10A.
  • entrance side 24 is located at the bottom of the drawing while exit side 26 is located at the top of the drawing.
  • Valve seat insert 10A may be associated with three sections.
  • An entrance side section 32 is located at entrance side 24 and comprises a first contact surface section 42 as well as a valve sealing surface section 46.
  • an abutting surface section 44 is additionally provided in entrance side section 32.
  • An exit side section 34 is located at exit side 26 and comprises a second contact surface section 48.
  • An arch section 36 extends from entrance side section 32 to exit side section 34 and essentially forms a wall delimiting the main part of a cooling channel that is formed in the mounted state (see cooling channel 12 in Fig. 2 ).
  • Arch section 36 decreases in material thickness from entrance side section 32 towards exit side section 34 up to a minimum thickness axial position P (or small region).
  • Minimum thickness axial position P is located in the half of arch section 36 that is close to exit side section 34.
  • the minimum thickness d min is exemplarily indicated at the transition between a larger curvature radius and a smaller curvature radius on the cooling channel side at exit side 26 of arch section 36.
  • Minimum thickness axial position P defines a center region of a static spring-like stress in the mounted state.
  • minimum thickness axial position P is located at at least 60 %, 70 %, 80 %, or 90 % of an axial extension of arch section 36, which is measured from entrance side section 32 along axial direction Z as indicated in Fig. 3 .
  • body 20 comprises an inner surface 52 and an outer surface 54.
  • inner surface 52 and outer surface 54 are connected via a, for example, radially extending surface section 44A.
  • Inner surface 52 extends circumferentially on the radially inner side of body 20 and comprises inter alia valve sealing surface section 46.
  • Valve sealing surface section 46 is, for example, tilted with respect to axial direction Z under an angle in the range from 40° to 80° such as, for example, 60°.
  • Outer surface 54 extends circumferentially on the radial outer side of body 20 and comprises first contact surface section 42, abutting surface section 44 and second contact surface section 48.
  • outer surface 54 is concavely curved while inner surface 52 is convexly curved.
  • outer surface 54 is concavely curved with a series of curved sections 54A, 54B, 54C, whereby those curved sections increasing in radius curvature up to minimum thickness axial position P.
  • neighboring curved sections 54A, 54B, 54C transition essentially tangentially into each other as shown in Fig. 3 .
  • curved section 54A may have a radius curvature of 1 mm to 3 mm such as 2 mm
  • curved section 54B may have a radius curvature of 5 mm to 10 mm such as 8 mm
  • curved section 54C may have a radius curvature of 50 mm to 100 mm such as 70 mm.
  • inner surface 52 may comprise one or more sections having curvature radii that result in a convex shape as shown in Fig. 3 , for example two sections with curvature radii in the range from 20 mm to 50 mm such as 40 mm, and 80 mm to 120 mm such as 100 mm.
  • a further curved section 54D having a curvature radius larger than the curvature radius of curved section 54C is indicated on exit side 26 beginning at minimum thickness axial position P.
  • Curved section 54D may have a radius curvature of 1 mm to 10 mm such as 5 mm.
  • a planar section 54E connects curved section 54D with second contact surface section 48 under, for example, a rectangular angle.
  • outer surface 54 forms a recess 60 with a gutter-like extension 62.
  • Gutter-like extension 62 extends towards valve sealing surface section 46 and forms a bottom 64.
  • Bottom 64 of gutter-like extension 62 defines the beginning of arch section 36 in axial direction Z as indicated in Fig. 3 by a dashed line 66A.
  • the end of arch section 36 coincides essentially with planar section 54E as indicated by dashed line 66B.
  • an inner gutter surface section 64A is associated with arch section 36, while an outer gutter surface section 64B is associated with entrance side section 32.
  • curved section 54A of arch section 36 is extended as curved section 54A' to form a surface section of entrance side section 32.
  • Curved section 54A' transitions into a planar surface section 64C, which extends in, for example, axial direction Z as exemplarily shown in Fig. 3 .
  • planar surface section 64C is essentially aligned with second contact surface section 48 of exit side section 34. Accordingly, cooling channel 12 formed by recess 60 will have an asymmetric shape; in particular, cooling channel 12 will be narrower at entrance side 24 than at exit side 26.
  • Fig. 3 provides for a decreasing material thickness of arch section 36 such that any deformation during mounting of valve seat insert 10A may create stress/load around minimum thickness axial position P. Accordingly, stress caused by mounting and/or a load caused by mounting will be present at the half of arch section 36 that is close to exit side section 34.
  • any stress/load that is caused during operation of the valve may center within entrance side section 32. Accordingly, those two types of stress are spatially separated and, accordingly, bottom 64 of gutter-like extension 62 may be subjected to reduced stress in comparison to prior art configurations.
  • Fig. 3 provides more material close to bottom 64 and such increases stress resistance in that region.
  • the disclosed sequence of varying curvature radii along axial direction Z at recess 60 may, therefore, provide the advantages discussed above and, for example, may increase durability and proneness to wear and tear.
  • valve seat insert 10 B of Fig. 4 is slightly modified to form a gutter-like extension 62'.
  • configuration such as inner surface 52 and most of outer surface 54 (e.g. the radii development in curved sections 54A, 54B, 54C) is maintained identical to the one shown in Fig. 3
  • bottom 64 and curved section 54A' are modified in a manner such that gutter-like extension 62' extends in the mounted state further along the radial direction R.
  • planar surface section 64C is shifted to a larger radius R 64C , thereby increasing the volume of gutter-like extension 62'. This may be achieved, for example, by using different curvature radii for curved sections 54A and 54B, and/or positioning their origin differently.
  • the cooling volume of cooling channel 12 may be increased at the entrance side. Thereby, cooling performance of valve seat insert 10B may be further improved.
  • valve seat inserts 10A and 10B may include chamfer faces, for example, between radially extending surface section 44A and second contact surface section 48 as well as abutting surface section 44 and first contact surface section 42.
  • valve seat insert 10A As well as valve seat insert 10C shown in Fig. 5 .
  • Exhaust opening 104A of cylinder head 104 is schematically indicated in Fig. 4 in a step-shape form. Specifically, exhaust opening 104A narrows stepwise in an insert direction, here along axial direction Z. Specifically, exhaust opening 104A comprises a first circumferential sidewall 104B, a first radially extending face 104C, a second circumferential sidewall 104D, and a second radially extending face 104E.
  • circumferential sidewalls 104B, 104D extend in axial direction
  • first and second radially extending faces 104C, 104E extend in radial direction.
  • First contact surface section 42 forms in the mounted state a first sealing of cooling channel 12 at entrance side 24 together with first circumferential sidewall 104B.
  • Second contact surface section 48 forms a second sealing of cooling channel 12 at exit side 26 together with second circumferential sidewall 104D.
  • abutting surface section 44 may contact first radially extending face 104C to limit the insertion in axial direction of valve seat insert 10B.
  • radially extending surface section 44A may act as abutting face by contacting second radially extending face 104E. In the latter case, some extension of cooling channel 12 into the gap formed between abutting surface section 44 and first radially extending face 104C may be given.
  • arch section 36 is configured for delimiting cooling channel 12 in the radial direction from passage 22. Cooling channel 12 is formed, in the mounted state of the valve seat insert between the valve seat insert and the cylinder head.
  • first contact surface section 42 and second contact surface section 48 extend in axial direction and/or abutting surface section 44 and radially extending surface section 44A extend in radial direction.
  • body 20 may be C-shaped when seen in a radial cross-section. Then, entrance side section 32 and exit side section 34 may be considered as respective ends of the C-shape. Arch section 36 may be considered to form the middle section of the C-shape. As can be seen in the drawings, and in adaptation to the step-like configuration of exhaust opening 104A, the end associated with entrance side section 32 extends to a larger radius R EN than the radius R EX associated with the exit side section 34 as shown in Fig. 4 .
  • inner surface 52 may protrude towards the center of body 20 to define a minimal opening radius R min in an axial central region as illustrated in, for example, Fig. 4 .
  • FIG. 5 a partial three-dimensional view of an exemplary valve seat insert 10C is shown to further illustrate the geometry, in particular, passage 22, entrance side 24 and exit side 26, which are associated with ring-shaped body 20. Furthermore, Fig. 5 indicates the cylinder-symmetric configuration that may be applied for valve seat inserts. However, in some embodiments, also elliptical configurations may be used.
  • Valve seat inserts as described above are usually press-fitted or shrink-fitted to the respective openings of cylinder heads. Accordingly, when a valve seat insert is forced into an opening, mechanical tension will provide for the required sealing. For example, when shrink-fitting a valve seat insert into an opening, one will first cool the valve seat insert, for example, with liquid nitrogen, when inserting the cooled valve seat insert into the opening. This is possible due to the reduced dimensions in the cooled state. In that stage, abutting surface section 44 may, for example, limit the depth of insertion. Then, the valve seat insert may be warmed to ambient temperature such that the valve seat insert is shrink-fitted into the opening. The same procedure may be applied for retrofitting a valve seat insert according to the herein disclosed embodiments, which may be used as a replacement for a mal-functioning valve seat insert.
  • the material of the valve seat insert may be heat resistant centrifugal casting.
  • the axial dimension of the valve seat insert is in the range from 50 mm to 70 mm; accordingly the axial extension of the arch section is in the range from 20 mm to 30 mm such that the minimum thickness position is in the range from 10 mm to 28 mm, i.e. at least beyond half of the extension.
  • the inner radius is in the range from 50 mm to 65 mm, the entrance radius is in the range from 75 mm to 80 mm, the exit radius is in the range from 70 mm to 75 mm.
  • the thickness of the arch section in radial direction reduces, for example, in the above embodiments from 10 mm to 7 mm.
  • valve seat inserts in addition to the above described mounting, in case of wear or damaging of any type of valve seat inserts, the same may be easily replaced with valve seat inserts according to the present disclosure (e.g. performing retrofitting using the herein disclosed valve seat inserts).
  • internal combustion engine may refer to internal combustion engines such as, for example, gas engines, which may be used as main or auxiliary engines of stationary power providing systems such as power plants for powering pipeline transmission, processing, or gas storage and withdrawal, as well as for generating electricity.
  • Fuel for the internal combustion engines may include natural gas, a combination of natural gas and another fuel, for example, diesel fuel, and the like.
  • Examples of internal combustion engines for the herein disclosed implementation of the valve seat insert may include, for example, engines of the series M43C manufactured by Caterpillar Motoren GmbH & Co. KG, Kiel, Germany, operated in the range of 450-750 rpm, i.e. at medium speed.
  • Such internal combustion engines may be large stand-alone engines that may provide access to the inlet and exhaust valves of the combustion engine for attachment of the valve seat inserts of the present disclosure during maintainance.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Claims (15)

  1. Ventilsitzeinsatz (10A, 10B, 10C) für einen Zylinderkopf (104) eines Verbrennungsmotors (100), wobei der Ventilsitzeinsatz (10A, 10B, 10C) umfasst:
    einen ringförmigen Körper (20), der einen Durchgang (22) definiert, der einem Fluid ermöglicht, den Körper (20) entlang einer axialen Richtung (Z) zu durchlaufen, von einer Eingangsseite (24) zu einer Ausgangsseite (26) des Ventilsitzeinsatzes (10A, 10B, 10C), wobei der Körper (20) umfasst
    einen eingangsseitigen Abschnitt (32), der einen ersten Kontaktflächenabschnitt (42) und einen Ventildichtungsflächenabschnitt (46) aufweist, und
    einen ausgangsseitigen Abschnitt (34), der einen zweiten Kontaktflächenabschnitt (48) aufweist,
    wobei der Körper weiter umfasst
    einen Bogenabschnitt (36), der sich axial von dem eingangsseitigen Abschnitt (32) zu dem ausgangsseitigen Abschnitt (34) erstreckt und dessen Materialdicke von dem eingangsseitigen Abschnitt (32) in Richtung des ausgangsseitigen Abschnitts (34) bis zu einer axialen Position (P) minimaler Dicke abnimmt
    dadurch gekennzeichnet, dass die Position minimaler Dicke, bei der die Abnahme der Materialdicke aufhört, in der Hälfte des Bogenabschnitts (36) angeordnet ist, die sich nahe zu dem ausgangsseitigen Abschnitt (34) befindet.
  2. Ventilsitzeinsatz (10A, 10B, 10C) nach Anspruch 1, wobei die axiale Position (P) minimaler Dicke einen Bereich von statischer, federartiger Belastung in dem montierten Zustand definiert und zumindest bei 60%, 70%, 80% oder 90% der axialen Ausdehnung des Bogenabschnitts (36), von dem eingangsseitigen Abschnitt (32) aus gemessen, angeordnet ist.
  3. Ventilsitzeinsatz (10A, 10B, 10C) nach Anspruch 1 oder Anspruch 2, wobei der Körper (20) weiter umfasst
    eine innere Oberfläche (52), die sich umfangsmäßig auf der radialen inneren Seite des Körpers (20) erstreckt und die den Ventildichtungsflächenabschnitt (46) umfasst; und
    eine äußere Oberfläche (54), die sich umfangsmäßig auf der radialen äußeren Seite des Körpers (20) erstreckt und die den ersten Kontaktflächenabschnitt (42), den zweiten Kontaktflächenabschnitt (48) und, zum Beispiel, einen angrenzenden Flächenabschnitt (44) umfasst; und
    wobei, an dem Bogenabschnitt (36), die äußere Oberfläche (54) konkav gekrümmt ist und/oder die innere Oberfläche (52) konvex gekrümmt ist.
  4. Ventilsitzeinsatz (10A, 10B, 10C) nach einem der vorstehenden Ansprüche, wobei,
    an dem Bogenabschnitt (36), die äußere Oberfläche (54) mit einer Serie von gekrümmten Abschnitten (54A, 54B, 54C) konkav gekrümmt ist, die zunehmende Radiuskrümmungen bis zu der axialen Position (P) minimaler Dicke aufweisen; und/oder
    benachbarte gekrümmte Abschnitte (54A, 54B, 54C) im Wesentlichen tangential ineinander übergehen.
  5. Ventilsitzeinsatz (10A, 10B, 10C) nach einem der vorstehenden Ansprüche, wobei,
    an dem Bogenabschnitt (36), die äußere Oberfläche (54) eine Aussparung (60) mit einer rinnenartigen Ausdehnung (62) in Richtung des Ventildichtungsflächenabschnitts (46) bildet, wobei ein Boden (64) der rinnenartigen Ausdehnung (62) einen axialen Anfang des Bogenabschnitts (36) definiert, sodass die rinnenartige Ausdehnung (62) einen inneren Rinnenflächenabschnitt (64A) und einen äußeren Rinnenflächenabschnitt (64B) umfasst, die dem Bogenabschnitt (36) bzw. dem eingangsseitigen Abschnitt (32) zugehörig sind.
  6. Ventilsitzeinsatz (10A, 10B, 10C) nach Anspruch 5, wobei der äußere Rinnenflächenabschnitt (64B) einen gekrümmten Abschnitt (54A') umfasst, der sich über einen gekrümmten Abschnitt (54A) des inneren Rinnenflächenabschnitts (64A) erstreckt und in einen planaren Flächenabschnitt (64C) übergeht.
  7. Ventilsitzeinsatz (10A, 10B, 10C) nach Anspruch 6, wobei sich der planare Flächenabschnitt (64C) in axialer Richtung erstreckt; und/oder
    wobei die radiale Position des planaren Flächenabschnitts (64C) im Wesentlichen mit dem zweiten Kontaktflächenabschnitt (48) ausgerichtet ist oder zu einem größeren Radius (R46C) verschoben ist, wobei der letztere Fall das Volumen der rinnenartigen Ausdehnung (62) vergrößert.
  8. Ventilsitzeinsatz (10A, 10B, 10C) nach einem der vorstehenden Ansprüche, wobei
    der erste Kontaktflächenabschnitt (42) konfiguriert ist, um in dem montierten Zustand einen ersten abgedichteten Kontakt mit dem Zylinderkopf (104) zu bilden; und/oder
    der angrenzende Flächenabschnitt (44) konfiguriert ist, um eine axiale Position des Ventilsitzeinsatzes (10A, 10B, 10C) zu definieren, wenn er an dem Zylinderkopf (104) montiert ist; und/oder
    der Ventildichtungsflächenabschnitt (46) konfiguriert ist, um eine Dichtung mit einer Ventilspindel (142) zu bilden und/oder sich unter einem Winkel von etwa 60° in Bezug auf die axiale Richtung (Z) zu erstrecken; und/oder
    der zweite Kontaktflächenabschnitt (48) konfiguriert ist, um in dem montierten Zustand einen zweiten abgedichteten Kontakt mit dem Zylinderkopf (104) zu bilden; und/oder
    der Bogenabschnitt (36) konfiguriert ist, um einen Kühlkanal (12) in radialer Richtung von dem Durchgang (22) zu begrenzen, wobei der Kühlkanal (12) in dem montierten Zustand des Ventilsitzeinsatzes (10A, 10B, 10C) zwischen dem Ventilsitzeinsatz (10A, 10B, 10C) und dem Zylinderkopf (104) gebildet ist; und/oder
    der erste Kontaktflächenabschnitt (42) und/oder der zweite Kontaktflächenabschnitt (48) sich in axialer Richtung (Z) erstreckt; und/oder
    der angrenzende Flächenabschnitt (44) sich in einer radialen Richtung (R) erstreckt.
  9. Ventilsitzeinsatz (10A, 10B, 10C) nach einem der vorstehenden Ansprüche, wobei,
    in einem radialen Querschnitt, der Körper (20) C-förmig ist, wobei der eingangsseitige Abschnitt (32) und der ausgangsseitige Abschnitt (34) die entsprechenden Enden der C-Form bilden, wobei der Bogenabschnitt (36) den Mittelteil der C-Form bildet, und
    das Ende, zugehörig zu dem eingangsseitigen Abschnitt (32), sich zu einem größeren Radius (REN) als der Radius (REX), zugehörig zu dem ausgangsseitigen Abschnitt (34), erstreckt.
  10. Ventilsitzeinsatz (10A, 10B, 10C) nach einem der vorstehenden Ansprüche, wobei
    die innere Oberfläche (52) in Richtung des Zentrums des Körpers (20) vorsteht, um einen minimalen Öffnungsradius (RMIN) in einem axialen, zentralen Bereich zu definieren, und
    die Aussparung (60) an der äußeren Oberfläche (54) konfiguriert ist, um eine minimale radiale Dicke (dMIN) des Bogenabschnitts (36) bereitzustellen, die in der axialen Richtung (Z) dichter an dem ersten Kontaktflächenabschnitt (42) als an dem zweiten Kontaktflächenabschnitt (48) angeordnet ist.
  11. Ventilsitzeinsatz (10A, 10B, 10C) nach einem der vorstehenden Ansprüche, wobei der ringförmige Körper (20) zylindersymmetrisch ist.
  12. Zylinderkopfanordnung für einen Verbrennungsmotor (100), wobei die Zylinderkopfanordnung umfasst:
    einen Zylinderkopf (104), der einen Abschnitt zum Bedecken eines Zylinders (102) eines Verbrennungsmotors (100) umfasst, wobei der Abschnitt eine Auslassöffnung (104A) umfasst; und
    einen Ventilsitzeinsatz (10A, 10B, 10C) nach einem der vorstehenden Ansprüche, der in die Auslassöffnung (104A) eingepasst ist, wobei ein Kühlkanal (12) zwischen dem Bogenabschnitt (36) und dem Zylinderkopf (104) gebildet ist.
  13. Zylinderkopfanordnung nach Anspruch 12, wobei sich die Auslassöffnung (104A) schrittweise in einer Einsatzrichtung verengt, wobei
    diese eine erste umfangsmäßige Seitenwand (104B), eine erste sich radial erstreckende Stirnwand (104C), eine zweite umfangsmäßige Seitenwand (104D) und eine zweite sich radial erstreckende Stirnwand (104E) umfasst; und/oder
    der erste Kontaktflächenabschnitt (42) eine erste Dichtung des Kühlkanals (12) an der Eingangsseite (24) zusammen mit der ersten umfangsmäßigen Seitenwand (104B) bildet; und/oder
    der angrenzende Flächenabschnitt (44) die erste sich radial erstreckende Stirnwand (104C) berührt, wodurch eine axiale Position des Ventilsitzeinsatzes (10A, 10B, 10C) in Bezug auf den Zylinderkopf (104) definiert ist; und/oder
    der zweite Kontaktflächenabschnitt (48) eine zweite Dichtung des Kühlkanals (12) an der Ausgangsseite (26) zusammen mit der zweiten umfangsmäßigen Seitenwand (104D) bildet.
  14. Zylinderkopfanordnung nach Anspruch 12 oder Anspruch 13, wobei der Bogenabschnitt (36) gebildet ist, um den Kühlkanal (12), der asymmetrisch ist, bereitzustellen und/oder um den Kühlkanal (12) so bereitzustellen, dass er an der Eingangsseite (24) enger ist, als an der Ausgangsseite (26).
  15. Nachrüstverfahren für einen Verbrennungsmotor mit einer Mehrzahl von Zylindern (102), wobei jeder Zylinder (102) zumindest einem Auslassventil (108) zugeordnet ist, wobei das Verfahren umfasst:
    Befestigen eines Ventilsitzeinsatzes (10A, 10B, 10C) nach einem der Ansprüche 1 bis 11 an einer Auslassöffnung (104A) von einem Zylinderkopf (104) eines Verbrennungsmotors (100).
EP14186281.3A 2014-09-24 2014-09-24 Ventilsitzeinsatz für einen Verbrennungsmotor Active EP3000998B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP14186281.3A EP3000998B1 (de) 2014-09-24 2014-09-24 Ventilsitzeinsatz für einen Verbrennungsmotor
CN201580051146.1A CN106715846B (zh) 2014-09-24 2015-08-26 用于内燃机的阀座嵌件
PCT/EP2015/001743 WO2016045768A1 (en) 2014-09-24 2015-08-26 Valve seat insert for an internal combustion engine
KR1020177009341A KR102430345B1 (ko) 2014-09-24 2015-08-26 내연기관용 밸브 시트 인서트

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14186281.3A EP3000998B1 (de) 2014-09-24 2014-09-24 Ventilsitzeinsatz für einen Verbrennungsmotor

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EP3000998A1 EP3000998A1 (de) 2016-03-30
EP3000998B1 true EP3000998B1 (de) 2017-07-19

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KR (1) KR102430345B1 (de)
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US11125122B1 (en) 2020-03-17 2021-09-21 Caterpillar Inc. Valve seat insert with soft landing insert design with contoured radii
US11125123B1 (en) 2020-03-17 2021-09-21 Caterpillar Inc. Valve seat insert with soft landing insert design with contoured radii

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US10934899B2 (en) * 2018-11-13 2021-03-02 Caterpillar Inc. Valve seat insert for engine having double-crowned seating surface profiled for limiting valve recession
US11060425B2 (en) * 2019-03-13 2021-07-13 Caterpillar Inc. Valve seat insert for engine head having venturi flow crowns and seating surface profiled for limiting valve recession
US10989321B2 (en) * 2019-04-26 2021-04-27 Caterpillar Inc. Double-crowned valve seat insert having seating surface formed of hard-facing material
US10767520B1 (en) * 2019-08-19 2020-09-08 Caterpillar Inc. Valve seat insert for long life natural gas lean burn engines
US10934901B1 (en) * 2019-08-19 2021-03-02 Caterpillar Inc. Valve seat insert for high power density and high speed diesel engines
CN114215648B (zh) * 2021-12-30 2024-05-03 无锡威孚力达催化净化器有限责任公司 一种可调式排气阀

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CH516733A (de) * 1969-12-02 1971-12-15 Sulzer Ag Kolbenbrennkraftmaschine mit mindestens einem auswechselbaren Sitzteil
CH571154A5 (de) * 1973-10-31 1975-12-31 Sulzer Ag
AT404390B (de) * 1992-09-24 1998-11-25 Avl Verbrennungskraft Messtech Brennkraftmaschine mit einem abschnittsweise gekühlten ventilsitzring
EP1329628B1 (de) * 2002-01-16 2007-06-13 Wärtsilä Schweiz AG Zylinderdeckel mit einem Kühlkanalsystem für eine Hubkolbenbrennkraftmaschine
DE102005048566A1 (de) * 2005-10-11 2007-04-12 Man Nutzfahrzeuge Ag Selbstzündende Brennkraftmaschine mit Brennräumen für hohe Zünddrücke

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11125122B1 (en) 2020-03-17 2021-09-21 Caterpillar Inc. Valve seat insert with soft landing insert design with contoured radii
US11125123B1 (en) 2020-03-17 2021-09-21 Caterpillar Inc. Valve seat insert with soft landing insert design with contoured radii
US11473457B2 (en) 2020-03-17 2022-10-18 Caterpillar Inc. Valve seat insert with soft landing insert design with contoured radii
US11480075B2 (en) 2020-03-17 2022-10-25 Caterpillar Inc. Valve seat insert with soft landing insert design with contoured radii

Also Published As

Publication number Publication date
KR102430345B1 (ko) 2022-08-08
EP3000998A1 (de) 2016-03-30
KR20170056591A (ko) 2017-05-23
WO2016045768A1 (en) 2016-03-31
CN106715846B (zh) 2020-02-28
CN106715846A (zh) 2017-05-24

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