EP3341606A1 - Kolben mit niedriger bauhöhe - Google Patents
Kolben mit niedriger bauhöheInfo
- Publication number
- EP3341606A1 EP3341606A1 EP16758155.2A EP16758155A EP3341606A1 EP 3341606 A1 EP3341606 A1 EP 3341606A1 EP 16758155 A EP16758155 A EP 16758155A EP 3341606 A1 EP3341606 A1 EP 3341606A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- line
- valve pocket
- recess
- internal combustion
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/16—Pistons having cooling means
- F02F3/20—Pistons having cooling means the means being a fluid flowing through or along piston
- F02F3/22—Pistons having cooling means the means being a fluid flowing through or along piston the fluid being liquid
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23K—SOLDERING OR UNSOLDERING; WELDING; CLADDING OR PLATING BY SOLDERING OR WELDING; CUTTING BY APPLYING HEAT LOCALLY, e.g. FLAME CUTTING; WORKING BY LASER BEAM
- B23K20/00—Non-electric welding by applying impact or other pressure, with or without the application of heat, e.g. cladding or plating
- B23K20/12—Non-electric welding by applying impact or other pressure, with or without the application of heat, e.g. cladding or plating the heat being generated by friction; Friction welding
- B23K20/129—Non-electric welding by applying impact or other pressure, with or without the application of heat, e.g. cladding or plating the heat being generated by friction; Friction welding specially adapted for particular articles or workpieces
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
- B23P15/00—Making specific metal objects by operations not covered by a single other subclass or a group in this subclass
- B23P15/10—Making specific metal objects by operations not covered by a single other subclass or a group in this subclass pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/0015—Multi-part pistons
- F02F3/003—Multi-part pistons the parts being connected by casting, brazing, welding or clamping
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/10—Pistons having surface coverings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/26—Pistons having combustion chamber in piston head
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23K—SOLDERING OR UNSOLDERING; WELDING; CLADDING OR PLATING BY SOLDERING OR WELDING; CUTTING BY APPLYING HEAT LOCALLY, e.g. FLAME CUTTING; WORKING BY LASER BEAM
- B23K2101/00—Articles made by soldering, welding or cutting
- B23K2101/003—Pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/0015—Multi-part pistons
- F02F3/003—Multi-part pistons the parts being connected by casting, brazing, welding or clamping
- F02F2003/0061—Multi-part pistons the parts being connected by casting, brazing, welding or clamping by welding
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F2200/00—Manufacturing
- F02F2200/04—Forging of engine parts
Definitions
- the invention relates to a piston with a low overall height for internal combustion engines according to the features of the preamble of claim 1.
- a finished piston part which is used to form a piston assembly.
- a finished piston has a lower part, wherein the lower part has a shaft and contains a lower surface of a cooling channel.
- the lower part comprises a radially bowl-shaped inner surface.
- the finished piston assembly further includes a top having a radially outer bowl-shaped surface which is matable with the radially inner bowl-shaped surface.
- the top has a radially encircling inner wall which includes a radially inner surface.
- the radially inner wall has a radially inwardly facing surface that has a non-parallel angle to the radially inner bowl surface in the region where the radially inner bowl surface meets a radially innermost edge of the radially inner joint surface.
- the so-called compression height is a characteristic parameter, wherein the compression height corresponds to the distance between the axis of the piston pin and an upper edge of the piston.
- the height of an internal combustion engine is determined inter alia by this compression height of the piston of the internal combustion engine.
- Another characteristic characteristic of a piston of an internal combustion engine which has an influence on the overall height of the internal combustion engine, is a so-called combustion chamber depth of a combustion chamber trough formed in the region of the piston upper part. Relatively low combustion bowls can burn in the Cylinder of the internal combustion engine, in which the piston is used to be improved. The deeper a combustion bowl is executed, however, the higher the compression height and thus the height of the internal combustion engine. Furthermore, even with pistons with a low overall height, an inflow and outflow of the mixture or of the gas into and out of the combustion chamber must be ensured.
- the invention is therefore an object of the invention to provide a piston, in particular a cooling channel piston, which is lighter in weight compared to known pistons with low height and allows improved mixture or gas exchange.
- At least one joint is arranged in the region of a ring field and in an outer wall of the combustion bowl and the ratio of piston compression height and diameter of the piston is less than 0.53.
- the diameter of the piston is in particular the outer diameter of the ready-to-use, ie finished piston.
- the joints are thus in areas of cohesively joined piston, which require post-processing.
- weld beads can be removed as part of this post-processing for the design of the ring field and / or the combustion bowl.
- a separate step is not required.
- the required height of the piston is achieved while achieving the required strength.
- This advantageously provides a piston which allows an optimized overall height of the intended internal combustion engine. This in turn reduces the space required by the internal combustion engine, for example in vehicles.
- the piston according to the invention enables the production of mass-optimized internal combustion engines. Pistons with such a low compression height save material in the manufacture of the pistons and weight of the finished piston. This in turn can be reduced fuel consumption.
- the optimized overall height of the internal combustion engine and the resulting reduced installation space for the internal combustion engine can in turn result in new vehicle concepts. Furthermore, the invention provides that the position of the inner joint is provided in the outer wall of the combustion chamber trough above the finished Brennraummulden groundes. Thus, in the manufacture of the combustion bowl, the internal Reibsch spawulst is removed. Another step is not necessary.
- the invention provides that at least one recess is provided in the piston head of the piston.
- the at least one recess reduces the risk of collision of moving parts within the cylinder.
- a valve can penetrate into the region of the recess without coming into contact with the piston having the at least one recess.
- the cylinder head may also have inner contours, which correspond to the at least one recess. In this case, contact with rigid parts within the cylinder is prevented by the at least one recess in the piston.
- the contours in the cylinder head can serve, for example, for guiding the mixture or the gas into or out of the combustion chamber.
- the invention provides that the at least one recess has at least one recess which at least partially passes through the bottom edge of the piston crown. Through the recess a maximum travel for the piston in the cylinder is possible.
- the piston can approach the cylinder head in the area of the recesses without running the risk of coming into contact with the valves.
- the mixture can enter the combustion chamber unhindered. After combustion, the predominantly gaseous mixture can also leave the combustion chamber when the piston is approaching the cylinder head.
- the at least one recess is configured in the shape of a circle segment. As a result, a connection is created from the recess to the cylinder wall.
- the recess assumes in its outer shape the shape of the piston.
- the invention provides that the at least one recess forms at least one valve pocket.
- a valve pocket allows an open valve to be received in the area of the piston crown as the piston approaches top dead center. This ensures that a piston with a low overall height can cover the largest possible travel within the cylinder. The working stroke can thus be maximized at low height. The energy gained from combustion can be efficiently converted into kinetic energy.
- the invention provides that the distance between a line, the line between the pressure side and counter-pressure side and the center of the first valve pocket is greater than the distance between the line and the center of the second valve pocket.
- the invention provides that the distance between a line, the line between the pressure side and counterpressure side and the center of the first valve pocket is at least twice as large as the distance between the line and the center of the second valve pocket. This ensures that there is sufficient clearance between the valve pockets. There remains enough material available to ensure safe operation of the internal combustion engine.
- the invention provides that the piston skirt of the piston has a coating to reduce the friction.
- the advantages of this coating are a very high durability, excellent sliding properties and a significant increase in the life of the piston.
- the layer thickness of the coating is, for example, about 0.01 millimeter (mm).
- the layer thickness of the coating can be between 0.005 mm and 0.1 mm.
- the invention provides that the piston has a cooling channel. In this way, in the case of the piston according to the invention with a low compression height (KH), which is then designed as a cooling channel piston, an effective removal of the heat produced during the combustion additionally takes place.
- the invention provides that at least one extended inlet is provided for the oil inlet to the cooling channel.
- a cooling medium oil is provided. Due to an extended feed, a larger amount of oil can be kept in the cooling channel. It forms during operation of the internal combustion engine, a reservoir for the cooling oil. By varying the length of the inlet, the level of cooling oil in the reservoir can be influenced.
- the invention provides that the cooling channel has molded recesses in its contour. Through these recesses, the oil or cooling oil can get closer to the wall of the combustion bowl. This improves the heat exchange between the combustion bowl and the oil. The heat transfer, for example, from the combustion bowl to the cooling oil located in the cooling channel is accelerated.
- the invention provides that the recesses formed in the cooling channel correspond with the impact position of the combustion jets in the combustion chamber recess.
- a direct transfer of the introduced through the combustion jets in the combustion bowl heat quantity over the wall of the combustion bowl to the oil is possible.
- the heat is dissipated near its source.
- the piston does not heat up unnecessarily.
- the service life of the piston is thereby increased and the probability of failure for the internal combustion engine, comprising at least one piston according to the invention, is thereby reduced.
- the invention provides that the upper part is designed as a half-forged upper part.
- the hot forging of steel is mainly worked in the temperature range of 650 ° C to 900 ° C. In this area, yield stress is reduced by more than half compared with cold forming in most steel grades.
- the applicable temperature depends on the type of steel, the size of the piston and the number of forming stages and is determined piston-specific.
- a more cost-effective production compared to the cold forming for the piston results from the saving of several pressing operations with complex intermediate treatments (intermediate annealing, surface coating) by hot forging. Close-to-net shape or flasks converted to finished shape (net shape) or the saving of heat treatment costs make cost-effective piston production possible by means of hot forging.
- a lower part is integrally joined to an upper part, wherein the lower part comprises a shaft and at least one pin bore and the upper part comprises a combustion bowl and a piston crown with a bottom edge, the lower part and the upper part preferably be joined by friction welding.
- the combustion bowl and the ring section ring field
- the dimensions of the finished piston are chosen so that the ratio of piston compression height KH and diameter piston DK ⁇ 0.53.
- the piston compression height KH is measured from the top of the piston, which faces the combustion chamber, to the direction of the center axis of the piston pin.
- the diameter of the piston DK is the outside diameter of the operational piston. Ready to use means that the piston is finished after its production and can be installed in the cylinder of the engine.
- the outer diameter may be the diameter of the flank of the piston.
- the outer diameter of the piston can also be measured in the region of a web between two piston rings.
- the diameter of a cylindrical or partially cylindrical piston shaft can be used to determine the outer diameter of the piston.
- the ratio of piston compression height and outer diameter of the piston ⁇ 0.53, preferably ⁇ 0.53, has the advantage of a particularly compact and weight-reduced design of the piston, connected with reduced overall height and sufficient stability to meet the stresses during operation in the cylinder of an internal combustion engine.
- the inventive use of a steel material in combination with the dimensions of the piston according to the invention causes an optimization of the properties of the inventive arrangement in the operation of internal combustion engines.
- the steel material ensures a particularly high strength as well as mechanical and thermal resilience of the piston.
- the dimensions of the invention cause a significant reduction in the compression height and a reduction in mass compared to aluminum piston, for example, 10% or more.
- the moving mass is reduced in the inventive arrangement.
- the dimensioning of the piston pin in relation to the piston diameter represents a very good compromise between the mass of the piston pin and the effective introduction of force from the piston into the piston pin during operation of the internal combustion engine.
- the reduced mass of the piston pin also contributes to the reduction of the moving mass in the arrangement according to the invention noticeably at.
- the reduction of the height or compression height eventually leads to an extension of the connecting rod, which has lower lateral forces and thus reduced frictional forces on the piston skirt on the piston skirt or between the piston and the cylinder surface during operation of the internal combustion engine result.
- pistons with different types of combustion bowls are used.
- the piston in question has a pot combustion bowl.
- the piston crown is designed so that a squish flow (squish flow) in the radial direction is created between the piston edge and the cylinder head.
- the swirl flow is reinforced in the pot combustion bowl.
- pistons with pot combustion bowls are very well suited.
- the pot combustion chamber well leads to a Acceleration of the inlet side generated swirl flow. Due to the angular momentum conservation, the rotational velocity of the swirl flow increases as the mixture is displaced inwardly into the pot combustion bowl. The generation of the squish flow and the amplification of the swirl flow have a positive effect on the combustion. Recesses in the piston head which extend into the bottom edge, allow an improved inflow of the mixture through the valves in the combustion chamber, since the piston crown does not obstruct the inflow.
- an internal combustion engine having at least one piston as described above.
- This piston of the present invention can be used in any type of reciprocating internal combustion engine.
- a motor vehicle is provided with one of the internal combustion engines described above.
- Such a motor vehicle may be designed, for example, as a land vehicle, as a watercraft or as an aircraft.
- the most common embodiment will be land vehicles, such as passenger cars, commercial vehicles or trucks.
- Another advantage of the low height is that the internal combustion engine in which the piston is operated, can build flatter. Combined with the formation of recesses in the piston head, an even flatter height for the piston can be achieved.
- Fig. 5 is a sectional view of a piston according to the line V-V in FIG.
- Fig. 6 is a sectional view of a piston according to the line Vl-Vl in Figure
- Fig. 7 is a sectional view of a piston according to the line VII-VII in
- FIG. 6, 8 is a sectional view of a piston portion along the line VIII-VIII in Figure 7,
- Fig. 1 1 is a sectional view of another piston
- Fig. 12A u. 12B are sectional views of the lower part and upper part of a piston according to FIG.
- the piston 1 is constructed identically in the figures and will first be described generally in the following. Subsequently, the figures are each shown in detail. Identical components are designated by the same reference numerals in the figures, and new reference numerals are used in the figures for different components.
- the piston 1 for an internal combustion engine is made of a lower part 2 and an upper part 3. Between the lower part 2 and the upper part 3 at least one joint 4 is formed. In the region of the joint 4, joining surfaces formed on the lower part 2 and on the upper part 3 meet one another. A joint 4 is formed in the region of a ring field 9. In addition, a further joint 4 may be formed in the outer wall of a combustion bowl 1 1.
- At least one of the joints 4 can be designed as a "tube on plate.” If the piston 1 has at least one cooling channel 6, the contour of the at least one cooling channel 6 can be formed in the lower part 2 or in the upper part 3, wherein these The opposite side is executed in the lower part 2 or in the upper part 3 as a circumferential flat or almost flat surface and accordingly referred to as a "plate”.
- a piston head 5 is formed at the upper part 3.
- the piston head 5 is arranged on the side facing away from a cooling channel 6 of the upper part 3.
- a piston shaft 6 is formed, which has bolt holes 7.
- the combustion bowl 1 1 is arranged in the upper part 3.
- a pin bore axis 13 is arranged, which corresponds to the central axis of the piston pin, not shown.
- oil return openings 19 may be arranged in the area of the ring field 9.
- FIG. 1 shows a piston 1 joined from lower part 2 and upper part 2. In the region of the shaft 6, this has a coating 14.
- This coating 14 has a low friction.
- the advantages of this coating 14 are a very high durability, excellent sliding properties and a significant increase in the life of the piston 1.
- FIGS. 1 and 6 are shown at which points the piston compression height hi and the diameter di of the piston are measured.
- the trough height i2 of the combustion chamber trough is also shown.
- the diameter di of the piston 1 according to FIGS. 1 and 6 may be, for example, between 100 mm and 150 mm.
- the value for hi can vary between 70 mm and 90 mm.
- the ratio of the compression height hi and the diameter di of the piston 1 varies between 0.48 and 0.75.
- FIG. 5 shows a burr-free region 15 in the region of the pin bore 7. Furthermore, a Hilfseinpass 16 is shown centrally.
- FIG. 7 shows an inlet 17 with a diameter 02 and a drain 18 with a diameter d3. Through the inlet 17, oil can enter the cooling area and through the drain 18, the oil can leave this area again.
- FIG. 9 shows two recesses 20 designed as valve pockets 21, 22 which each have a diameter d 4 .
- the diameter d 4 can assume a value between 35 mm and 55 mm.
- the diameter d 4 of the valve pockets 21, 22 can also assume different values. It can be provided any number of, for example, as recesses formed recesses 20.
- at least some of the recesses 20 are at least partially formed as a valve pocket 21, 22, in which gas exchange valves of the reciprocating internal combustion engine are at least partially absorbed during their operation, that is, immerse, can.
- a collision of the gas exchange valves with the piston 1 can be avoided.
- a functional integration is shown, which keeps the cost of the piston 1, in particular its manufacturing costs, low.
- valve pockets 21, 22 of the piston 1 close, in which respective corresponding valve plate of gas exchange valves of the reciprocating internal combustion engine are receivable. If the piston 1 is in its top dead center in the combustion chamber of the reciprocating engine, then the valve pockets 21, 22 provide a sufficiently large clearance for the respective gas exchange valves, that is to say for corresponding intake and exhaust valves, so that the gas exchange valves each one desired can perform large valve lift to allow gas exchange. In other words, the gas exchange valves can open wide enough by the provided by the valve pockets 21, 22 enough to effect an exchange of exhaust gas and sucked by the reciprocating internal combustion engine air or sucked by the reciprocating internal combustion engine mixture efficiently.
- a first circle segment alpha is located between a first valve pocket 21 and the line 24 perpendicular to the one pressure side (DS) 25 and a counterpressure side (GDS) 26 connecting line 24.
- a second circular segment beta is located between the perpendicular to the pressure side 25 and counter-pressure side 26 connecting line 23 standing line 24 and a second valve pocket 22.
- a third circular segment gamma is located between the second valve pocket 22 and the pressure side 25 and counter-pressure side 26 connecting line 23.
- Dasachi Circle segment alpha can assume values between 15 degrees and 30 degrees, preferably between 20 degrees and 25 degrees.
- the second circle segment Beta can assume values between 55 degrees and 70 degrees, preferably between 60 degrees and 65 degrees.
- the third circle segment gamma can assume values between 15 degrees and 35 degrees, preferably between 20 degrees and 30 degrees.
- the piston head 1 1 is bounded by a bottom edge 27.
- the bottom edge 27 on circular segment-shaped recesses 28.
- the length h of the recess 28 of the first valve pocket 21 corresponds to the length I2 of the recess 28 of the second valve pocket 22.
- the lengths and I2 can assume values between 15 millimeters and 35 millimeters, preferably between 20 mm and 30 mm.
- I 2 and I 2 may have the same values, but need not have the same values.
- the dimensions for and I2 can be varied independently.
- the distance xi between the line 23 and the center of the first valve pocket 21 is greater than the distance X2 between the line 23 and the center of the second valve pocket 22.
- the distance xi can be between 30 mm and 45 mm, preferably between 35 mm and 40 mm.
- the distance X2 can be between 15 mm and 22.5 mm, preferably between 17.5 mm and 22.5 mm.
- the distance between the center of the first valve pocket 21 and the line 24 is denoted by X3.
- the distance between the line 24 and the center of the second valve pocket 22 is designated x 4 .
- the distance X3 is less than the distance x 4mm.
- the distance x 4 can be between 25 mm and 45 mm, preferably between 30 mm and 40 mm.
- the distance X3 can be between 12.5 mm and 22.5 mm, preferably between 15 mm and 20 mm.
- Figure 1 1 shows a finished piston 1, in which it can be seen at which points the piston compression height hi and the diameter di of the piston measured become.
- the piston 1 shown in Figure 1 1 is a two-piece piston, consisting of upper part 3 and lower part 2, which are joined together. Ready for use, the piston 1 is then in one piece. However, the piston 1 may also be formed in one piece.
- This piston I has a ratio between the compression height hi of the piston 1 and the diameter di of the piston 1 of ⁇ 0.53.
- Figures 12A and 12B and 13A and 13B show the views of upper part 3 and lower part 2 before assembly.
- This is an example of a structural design of upper part 3 and lower part 2, which are suitably joined together, preferably by friction welding, in order to achieve the desired ratio ⁇ 0.53, preferably less than 0.53.
- Beta second circle segment between the perpendicular to the pressure side and
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015216553 | 2015-08-28 | ||
PCT/EP2016/070324 WO2017037024A1 (de) | 2015-08-28 | 2016-08-29 | Kolben mit niedriger bauhöhe |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3341606A1 true EP3341606A1 (de) | 2018-07-04 |
Family
ID=56851589
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16758155.2A Withdrawn EP3341606A1 (de) | 2015-08-28 | 2016-08-29 | Kolben mit niedriger bauhöhe |
Country Status (6)
Country | Link |
---|---|
US (2) | US20170058824A1 (de) |
EP (1) | EP3341606A1 (de) |
CN (1) | CN108026859A (de) |
DE (1) | DE102016116046A1 (de) |
MX (1) | MX2018001889A (de) |
WO (1) | WO2017037024A1 (de) |
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EP3452712A1 (de) | 2016-05-04 | 2019-03-13 | KS Kolbenschmidt GmbH | Kolben |
WO2018041880A1 (de) | 2016-09-02 | 2018-03-08 | Ks Kolbenschmidt Gmbh | Kolben, bestehend aus einem innenteil und einem aussenteil |
US10113503B2 (en) * | 2016-10-11 | 2018-10-30 | Caterpillar Inc. | Combustion bowl of a piston for an engine |
DE102017210818A1 (de) * | 2017-06-27 | 2018-12-27 | Mahle International Gmbh | Verfahren zur Herstellung eines Kolbens für eine Brennkraftmaschine aus einem Kolbenoberteil und aus einem Kolbenunterteil |
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GB201916665D0 (en) * | 2019-11-15 | 2020-01-01 | Black & Decker Inc | Piston |
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DE102008034430B4 (de) * | 2008-07-24 | 2015-02-19 | Ks Kolbenschmidt Gmbh | Reibgeschweißter Stahlkolben mit optimiertem Kühlkanal |
US8807109B2 (en) * | 2009-11-06 | 2014-08-19 | Federal-Mogul Corporation | Steel piston with cooling gallery and method of construction thereof |
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WO2014144619A1 (en) * | 2013-03-15 | 2014-09-18 | Mahle International Gmbh | Wearable anti-friction coating for piston assembly |
DE102013014346A1 (de) * | 2013-03-18 | 2014-10-02 | Mahle International Gmbh | Verfahren zur Herstellung eines Kolbens für einen Verbrennungsmotor und mittels dieses Verfahrens hergestellter Kolben |
DE102013014345A1 (de) * | 2013-03-18 | 2014-10-02 | Mahle International Gmbh | Verfahren zur Herstellung eines Kolbens für einen Verbrennungsmotor und mittels dieses Verfahrens hergestellter Kolben |
US9429101B2 (en) * | 2013-08-21 | 2016-08-30 | Caterpillar Inc. | Combustion engine piston and engine using same |
CN204327305U (zh) * | 2014-11-03 | 2015-05-13 | 马勒技术投资(中国)有限公司 | 燃烧室喉口增强钢活塞 |
-
2015
- 2015-09-03 US US14/844,617 patent/US20170058824A1/en not_active Abandoned
-
2016
- 2016-08-29 WO PCT/EP2016/070324 patent/WO2017037024A1/de active Application Filing
- 2016-08-29 DE DE102016116046.6A patent/DE102016116046A1/de not_active Ceased
- 2016-08-29 MX MX2018001889A patent/MX2018001889A/es unknown
- 2016-08-29 EP EP16758155.2A patent/EP3341606A1/de not_active Withdrawn
- 2016-08-29 US US15/755,239 patent/US20190024606A1/en not_active Abandoned
- 2016-08-29 CN CN201680049547.8A patent/CN108026859A/zh active Pending
Also Published As
Publication number | Publication date |
---|---|
WO2017037024A1 (de) | 2017-03-09 |
CN108026859A (zh) | 2018-05-11 |
US20190024606A1 (en) | 2019-01-24 |
US20170058824A1 (en) | 2017-03-02 |
MX2018001889A (es) | 2018-06-20 |
DE102016116046A1 (de) | 2017-03-02 |
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