FI129427B - Cylinder of an internal combustion engine - Google Patents
Cylinder of an internal combustion engine Download PDFInfo
- Publication number
- FI129427B FI129427B FI20175977A FI20175977A FI129427B FI 129427 B FI129427 B FI 129427B FI 20175977 A FI20175977 A FI 20175977A FI 20175977 A FI20175977 A FI 20175977A FI 129427 B FI129427 B FI 129427B
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- Prior art keywords
- cylinder
- annular
- piston
- annular groove
- webs
- Prior art date
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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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/18—Other cylinders
- F02F1/20—Other cylinders characterised by constructional features providing for lubrication
-
- 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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/18—Other cylinders
-
- 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
- F02F1/00—Cylinders; Cylinder heads
- F02F1/004—Cylinder liners
-
- 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
- F16J10/00—Engine or like cylinders; Features of hollow, e.g. cylindrical, bodies in general
- F16J10/02—Cylinders designed to receive moving pistons or plungers
-
- 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
- F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
- F16J9/12—Details
- F16J9/20—Rings with special cross-section; Oil-scraping rings
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
- Compressor (AREA)
Description
CYLINDER OF AN INTERNAL COMBUSTION ENGINE The invention relates to a cylinder of an internal combustion engine according to the preamble of claim 1.
Internal combustion engines typically have a plurality of cylinders. Each cylinder of an internal combustion engine has a cylinder piston which is guided in a cylinder liner of the cylinder. During a work cycle the cylinder piston is moved up and down in the cylinder liner of the respective cylinder. The cylinder piston adjoins a radially inner surface of the cylinder liner with a radially outer surface of the cylinder piston. A running gap is defined between these surfaces. The cylinder piston has a plurality of annular grooves on its radially outer surface which are delimited and separated from one another by annular webs, wherein these annular grooves receive piston rings which project into the running gap formed between the radially outer surface of the cylinder piston and the radially inner surface of the cylinder liner. Each of the annular grooves in this case receives a piston ring configured either as a compressor ring or as an oil scraper ring which abuts against the radially inner running surface of the cylinder liner with a radially outer piston ring surface. a N A piston ring configured as a compressor ring is used - 30 for gas-tight sealing of the running gap between the O cylinder piston and the cylinder liner. A piston ring z configured as an oil scraper ring is used for scraping a N oil from the radially inner running surface of the 5 cylinder liner in order to prevent oil from entering S 35 into the combustion chamber of the respective cylinder N via the running gap.
In the case of internal combustion engines, a distinction is made between slow-running internal combustion engines, medium-fast running internal combustion engines and fast-running internal combustion engine.
Slow- running internal combustion engines have rotational speeds of less than 100 rpm.
Fast-running internal combustion engines have rotational speeds of more than 1000 rpm.
Medium-fast running internal combustion engines have rotational speeds between 100 rpm and 1000 rpm, in particular rotational speeds between 400 rpm and 1000 rpm.
In particular in the case of medium-fast running internal combustion engines, flank abutment changes for piston rings configured as compressor rings are initiated in a pressure-controlled manner at corresponding flanks of the annular groove receiving the respective piston ring.
In the case of fast-running internal combustion engines on the other hand, such a flank change is initiated in a mass-force controlled manner.
As a result of increasingly higher compression pressures and therefore working pressures in the combustion chambers of the cylinders, in medium-fast running internal combustion engines a flank change of piston rings configured as compressor rings initiated in a pressure-controlled manner increasingly presents difficulties.
N Starting from this, it is the object of the present N invention to provide a new type of cylinder of an - 30 internal combustion engine.
This object is solved by a O cylinder according to claim 1. According to the z invention, the cylinder liner has at least one bore via N which the at least two annular webs at the lower dead 5 point of the cylinder piston or at least two chambers S 35 delimited radially by annular webs and the cylinder liner N are coupled to one another on the pressure side.
As a result of the pressure-side coupling of at least two annular webs at the lower dead point of the cylinder piston, a pressure-controlled flank abutment change of piston rings configured as compressor rings can be improved at corresponding abutment surfaces of the annular grooves.
Furthermore a specific ventilation of annular webs can also be ensured.
The cylinder piston has a piston base which delimits a combustion chamber of the cylinder in sections wherein the cylinder piston has a number N of annular grooves which are delimited and separated from one another by a number N + 1 of annular webs.
Preferably when viewed starting from the piston base, the 1st to (N-1)th annular groove serve to each receive a piston ring configured as a compressor ring wherein when viewed starting from the cylinder base, the N-th annular groove serves to receive a piston ring configured as an oil scraper ring.
According to an advantageous further development of the invention, at least one bore of the cylinder liner at the lower dead point of the cylinder piston when viewed starting from the piston base couples on the pressure side the 1st annular web which delimits the lst annular groove adjacent to the combustion chamber of the cylinder to at least one of the annular webs from the 3rd annular web which separates the 2nd annular groove and the 3rd annular groove from one another, up to the N-th annular N web which separates the (N-1)-th annular groove and the N N-th annular groove from one another.
As a result, the - 30 corresponding pressure-side coupled annular webs or the O chambers delimited radially by the corresponding annular = webs and coupled on the pressure side are exposed to a N pneumatic pressure egualization in order to specifically 5 initiate a pressure-controlled flank abutment chamber at S 35 at least one adjacent piston ring, namely compressor N ring.
According to a further alternative further development of the invention, at least one bore of the cylinder liner at the lower dead point of the cylinder piston when viewed starting from the piston base couples on the pressure side the (N+1)-th annular web which delimits the N-th annular groove pointing away from the combustion chamber of the cylinder to each of the annular webs from the 2nd annular web to the N-th annular web. As a result, the corresponding pressure-side coupled annular webs or the chambers radially delimited by the corresponding annular webs and the cylinder liner are exposed to ventilation. Preferred further development of the invention are obtained from the subclaims and the following description. Exemplary embodiments of the invention are explained in detail with reference to the drawings without being restricted to these. In the figures: Fig. 1: shows a schematic cross-section through a first cylinder according to the invention; Fig. 2: shows a schematic cross-section through a second cylinder according to the invention; Fig. 3: shows a schematic cross-section through a third cylinder according to the invention;
N N Fig. 4: shows a schematic cross-section through a - 30 fourth cylinder according to the invention;
N z Fig. 5: shows a schematic cross-section through a N fifth cylinder according to the invention; and 2 m 35 Fig. 6: shows a schematic cross-section through a N further cylinder according to the invention.
The invention relates to a cylinder of an internal combustion engine. Figure 1 shows a schematic cross- section through a cylinder 10 of an internal combustion engine, wherein Fig. 1 shows for the cylinder 10 a 5 cylinder liner 11 as well as a cylinder piston 12 guided in the cylinder liner 11. During operation of the internal combustion engine or the cylinder 10, the cylinder piston 12 can be moved up and down during a work cycle of the respective cylinder 10 in the cylinder liner 11. A so-called piston base 13 of the cylinder piston 12 delimits a combustion chamber 14 of the respective cylinder 10 in sections. Figure 1, likewise the following Figs. 2 to 6 show the cylinder piston 12 in each case in the region of its lower dead point.
The cylinder piston 12 has a radially outer surface 15 which delimits a running gap 17 with a radially inner running surface 16 of the cylinder liner 11. This running gap 17 for the cylinder piston 12 must be sealed in a gastight manner on the one hand, on the other hand it must be avoided that oil enters into the combustion chamber 14 of the cylinder via this air gap 17. The cylinder piston 12 of the cylinder 10 has a plurality of annular grooves 18, in the exemplary embodiment shown in Fig. 1 a number N = 3 of annular grooves 18(1), 18(2) and 18(3). These annular grooves 18 are delimited and N separated from one another by annular webs 19,namely N with a number N = 3 of annular grooves 18(1), 18(2) and - 30 18(3) by four corresponding annular webs 19(1), 19(2), S 19(3) and 19(4). When viewed starting from the piston = base 13, the first annular groove 18(1) is delimited by N the two annular webs 19(1), 19(2). The second annular 5 groove 18(2) when viewed from the piston base 13 is S 35 delimited by the annular webs 19(2) and 19(2). The N annular webs 19(3) and 19(4) delimit the third annular groove 18(3) of the cylinder piston 12 when viewed from the piston base 13. Accordingly, the first annular web 19(1) is positioned on that side of the first annular groove 18(1) which faces the piston base 13 and therefore the combustion chamber 14. The second annular web 19(2) is positioned between the first annular groove 18(1) and the second annular groove 18(2), which separates these two annular grooves 18(1), 18(2) from one another. The third annular web 19(3) is positioned between the second annular groove 18(2) and the third annular groove 18 (2) and separates these two annular grooves 18(2), 18(3) from one another. The fourth annular web 19(4) is positioned to the side of the third annular groove 18(3) facing away from the combustion chamber 14. Each of the annular grooves 18 receives a piston ring
20. The piston rings 20 positioned in the first annular groove 18(1) and second annular groove 18 (2) when viewed starting from the piston base 13 comprise so-called compressor rings 21 which are used for gas-tight sealing of the running gap 17. The piston ring 20 positioned in the third piston groove 18(3) starting from the piston base 13 comprises an oil scraper ring 22 by means of which oil can be scraped from the running surface 16 of the cylinder liner 11 in order to avoid the introduction of oil into the combustion chamber 14 of the cylinder
10. N As can be seen from Fig. 1, the piston rings 20 N configured as compressor rings 21 abut with their - 30 radially outer surface 23 preferably over the full O surface against the inner running surface 16 of the = cylinder liner 11. The piston ring 20 configured as an N oil scraper ring 22 on the other hand does not abut 5 completely with its radially outer surface but only in S 35 the region of the scraper lips 20 against the inner N running surface 16 of the cylinder liner 11.
At least one bore 25 is introduced into the cylinder liner 11. The or each bore 25 couples together at least two annular webs 19 on the pressure side at the lower dead point of the cylinder piston 12. In other words, the or each bore 25 at the lower dead point of the cylinder piston 12 couples two chambers on the pressure side which are delimited by the cylinder liner 11 and by respective pressure-side coupled annular webs 19 of the cylinder piston 12 at least in sections, namely radially.
In the exemplary embodiment of Fig. 1 in which the cylinder piston 12 has a number N = 3 of annular grooves 18 and therefore a number N + 1 = 4 of annular webs 19, the respective bore 25 of the cylinder liner 11 at the lower dead point of the cylinder piston 12 when viewed starting from the piston base 13, couples the first annular web 19(1) which delimits the first annular groove 18(1) adjacent to the combustion chamber 14 of the cylinder 10 to the third annular web 19(3) which separates the second annular groove 18 (2) from the third annular groove 18 (3). For the piston ring 20 received in the second annular groove 18(2) and configured as a compressor ring 21 at the lower dead point of the cylinder piston 12, a defined flank abutment change of the piston ring 20 can be initiated at corresponding boundary surfaces of the annular groove 18b, namely via the pneumatic pressure equalization of the pressure-side N coupled annular webs 19a, 19c or the chambers delimited N radially by these annular webs 19a, 19c and the cylinder - 30 liner 11.
N = Figure 3 shows a variant of the invention in which piston N ring 12 comprises a number N = 4 of annular grooves 18 5 and therefore a number N + 1 = 5 of annular webs 19 S 35 delimiting these annular grooves 18. In this case, in N the exemplary embodiment of Fig. 3, the bore 25 of the cylinder liner 11 shown at the lower dead point of the cylinder piston 12 couples the first annular web 19(1) with the third annular web 19(3) on the pressure side in order to thus initiate at the lower dead point a defined flank abutment change by pneumatic pressure equalization between the pressure-side coupled annular webs 19(1) and 19(3) for the piston ring 20 adjoining this annular web 19(3) which is received in the annular groove 18 (2). Figure 4 shows a variant of the invention in which in agreement with the exemplary embodiment of Fig. 3 the cylinder piston 12 again has a number N = 4 of annular grooves with a number N + 1 = 5 pf annular webs 19 adjoining these annular grooves 18, wherein however in the exemplary embodiment of Fig. 4, unlike the exemplary embodiment of Fig. 3, the or each bore 25 introduced into the cylinder liner 11 at the lower dead point of the cylinder piston 12 couples the first annular web 19(1) to the fourth annular web 19(4) on the pressure side in order to thereby ensure a flank abutment change for the piston ring 20 positioned in the annular groove 18 (3), configured as compressor ring 21 by means of a corresponding pneumatic pressure equalization of the pressure-side coupled annular webs 19(1) and 19(4). Figure 5 shows another exemplary embodiment with a cylinder piston 12 which has a number N = 4 of annular grooves 18, wherein in the exemplary embodiment of Fig.
N 5 the or each bore 25 in the cylinder liner 11 is N configured in such a manner that at the lower dead point - 30 of the cylinder piston 12 this couples the first annular S web 19(1) both with the third annular web 19(3) and also = with the fourth annular web 19(4) on the pressure side.
N By this means at the lower dead point of the cylinder 5 piston 12 both for the compressor ring 21 received in S 35 the annular groove 18(2) and also for the compressor N ring 21 received in the annular groove 18(3) a defined flank abutment change at corresponding surfaces of the corresponding annular groove 18(2) or 18(3) can then be ensured. The exemplary embodiments of Figs. 1 to 3 accordingly have in common that the respective bore 25 of the cylinder liner 11 at the lower dead point of the cylinder piston 12, when viewed starting from the piston base 13, couples on the pressure side the first annular web 19(1) which delimits the first annular groove 18(1) adjacent to the combustion chamber 14 of the respective cylinder 10 to at least one of the annular webs 19 from the third annular web 19(3) to the N-th annular web 19(N), wherein the third annular web 19(3) separates the second annular groove 18(2) and the third annular groove 18(3) from one another and wherein the N-th annular web 19(N) separates the (N-1)-th annular groove 18(N-1) and the N-th annular groove 18(N) from one another. A pneumatic pressure egualization at the lower dead point of the cylinder piston 12 is thereby ensured between the pressure-side coupled annular grooves 19 in order to enable a defined pressure-controlled flank abutment change at corresponding surfaces of the annular groove 18 receiving the respective piston ring 20 at the respective adjacent piston ring 20 configured as compressor ring
21. Figure 2 shows another exemplary embodiment of the N invention for a cylinder 10 of an internal combustion N engine, whose cylinder piston 1? has a number N = 3 of - 30 annular grooves 18 which therefore corresponds to the S exemplary embodiment of Fig. 1 with regard to the z configuration of the cylinder piston 12. a S In the exemplary embodiment shown in Fig. 1 the bore 25 S 35 introduced into the cylinder liner 11 at the lower dead N point of the cylinder piston 12 again couples together at least two pressure webs or chambers delimited at least in section by the pressure webs and the cylinder liner 11, wherein the bore 25 shown in Fig. 2 couples on the pressure side the last and therefore N+1-th annular web 19(N+1) when viewed starting from the piston base 13 which delimits the N-th annular groove 18(N) pointing away from the combustion chamber 14 to each of the annular webs from the 2nd to the N-th annular web 19(2) to 19(N), whereby at the lower dead point of the cylinder piston 12 a defined ventilation of the pressure-side coupled annular webs or the chambers defined by the respective annular webs and the cylinder liner is ensured. In the exemplary embodiment in Fig. 6 in which the cylinder piston 12 of the cylinder 10 shown again has a number N = 4 of annular grooves 18, when viewed starting from the piston base 13 at the lower dead point of the cylinder piston 12 the (N+1)-th annular web 19(N+1) is coupled on the pressure side to each of the annular webs from the second annular web 19(2) to the N-th annular web 19(N), which ensures at the lower dead point of the cylinder piston 12 a defined ventilation of the pressure- side coupled annular webs or of the pressure chambers defined by the respective annular webs and the cylinder liner. The invention is particularly suitable for use with N charged, medium-fast running internal combustion engines N which have rotational speed between 100 rpm and 1000 - 30 rpm, in particular rotational speeds between 400 rpm and S 1000 rpm. These internal combustion engines can be z designed as diesel internal combustion engines or Otto N internal combustion engine or as gas motors. 5 S 35
REFERENCE LIST 10 Cylinder 11 Cylinder liner 12 Cylinder piston 13 Piston base 14 Combustion chamber 15 Surface 16 Running surface 17 Running gap 18 Annular groove 19 Annular web 20 Piston ring 21 Compressor ring 22 Oil scraper ring 23 Surface 24 Oil scraper lip Bore
N ©
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Claims (11)
1. A cylinder (10) of an internal combustion engine, in particular a medium-fast running internal combustion engine, having a cylinder liner (11) and having a cylinder piston (12) guided in the cylinder liner (11), wherein the cylinder piston has a plurality of annular grooves (18) delimited by annular webs (19) and separated from one another by annular webs (19), and wherein each of the annular grooves (18) receives a piston ring (20) configured as a compressor ring (21) or as an oil scraper ring (22) which abuts with a radially outer surface (23) or with at least one lip (24) on a radially inner running surface (16) of the cylinder liner (11), c haracterizedin that the cylinder liner (11) has at least one bore (25) via which the at least two annular webs (19) at the lower dead point of the cylinder piston (12) or at least two chambers delimited radially by annular webs (19) and the cylinder liner (11) are coupled to one another on the pressure side.
2. The cylinder according to claim 1, characterized in that the cylinder piston (12) has a piston base (13) which delimits a combustion chamber (14) of - the cylinder in sections and that the cylinder O piston (12) has a number N of annular grooves (18) —- which are delimited and separated from one another a 30 by a number N + 1 of annular webs (19).
N
I &
3. The cylinder according to claim 1 or 2, N characterized in that when viewed starting from the 2 piston base (13), the 1st annular groove (18(1)) to = 35 (N-1)th annular groove (18(N-1)) serve to receive N a piston ring (20) configured as a compressor ring
(21) and that when viewed starting from the cylinder base (13), the N-th annular groove (18(N)) serves to receive a piston ring (20) configured as an oil scraper ring (22).
4. The cylinder according to claim 2 Or 3, characterized in that at least one bore (25) of the cylinder liner (11) at the lower dead point of the cylinder piston (12) when viewed starting from the piston base (13) couples on the pressure side the lst annular web (19(1)) which delimits the 1st annular groove (18(1)) adjacent to the combustion chamber (14) of the cylinder to at least one of the annular webs (19) from the 3rd annular web (19(3)) which separates the 2nd annular groove (18(2)) and the 3rd annular groove (18(3)) from one another, up to the N-th annular web (19(N)) which separates the (N-1)-th annular groove (19(N-1)) and the N-th annular groove 19(N) from one another.
5. The cylinder according to claim 4, characterized in that N = 3 and that the at least one bore (25) of the cylinder liner (11) at the lower dead point of the cylinder piston (12) when viewed starting from the piston base (13) couples on the pressure side the 1st annular web (19(1)) which delimits the 1st - annular groove (18(1)) adjacent to the combustion O chamber (14) of the cylinder to the 3rd annular web —- (19(3)) which separates the 2nd annular groove a 30 (18 (2)) and the 3rd annular groove (18(3)) from one N another. x a N
6. The cylinder according to claim 4, characterized in 3 that N = 4 and that the at least one bore (25) of = 35 the cylinder liner (11) at the lower dead point of N the cylinder piston (12) when viewed starting from the piston base (13) couples on the pressure side the 1st annular web (19(1)) which delimits the 1st annular groove (18(1)) adjacent to the combustion chamber (14) of the cylinder to the 3rd annular web (19(3)) which separates the 2nd annular groove (18(2)) and the 3rd annular groove (18(3)) from one another and/or to the 4th annular web (19(4)) which separates the 3rd annular groove (18(3)) and the 4th annular groove (18(4)) from one another.
7. The cylinder according to any one of claims 4 to 6, characterized in that the corresponding pressure- side coupled annular webs (19) or the chambers radially delimited by the corresponding annular webs (19) and the cylinder liner (11) are exposed to a pneumatic pressure equalization in order to initiate a pressure-controlled flank abutment change at at least one adjacent piston ring, namely compressor ring (21).
8. The cylinder according to claim 2 or 3, characterized in that at least one bore (25) of the cylinder liner (11) at the lower dead point of the cylinder piston (12) when viewed starting from the piston base (13) couples on the pressure side the (N+1)-th annular web (19(N+1)) which delimits the — N-th annular groove (18(N)) pointing away from the O combustion chamber (14) of the cylinder to each of — the annular webs (19) from the 2nd annular web a 30 (19(2)) to the N-th annular web (19(N)).
N
I a
9. The cylinder according to claim 8, characterized in N that N = 3 and that the at least one bore (25) of 3 the cylinder liner (11) at the lower dead point of = 35 the cylinder piston (12) when viewed starting from N the piston base (13) couples on the pressure side the 4th annular web (19(4)) which delimits the 3rd annular groove (18(3)) pointing away from the combustion chamber of the cylinder to each of the annular webs from the 2nd annular web (19(2)) to the 3rd annular web (19(3)).
10. The cylinder according to claim 8, characterized in that N = 4 and that the at least one bore (25) of the cylinder liner (11) at the lower dead point of the cylinder piston (12) when viewed starting from the piston base (13) couples on the pressure side the 5th annular web (19(5)) which delimits the 4th annular groove (18(4)) pointing away from the combustion chamber (24) of the cylinder to each of the annular webs from the 2nd annular web (19(2)) to the 4th annular web (19(4)).
11. The cylinder according to any one of claims 8 to 10, characterized in that as a result the corresponding pressure-side coupled annular webs (19) or the chambers delimited radially by the corresponding annular webs (19) and the cylinder liner (11) are exposed to ventilation.
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Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102016222299.6A DE102016222299A1 (en) | 2016-11-14 | 2016-11-14 | Cylinder of an internal combustion engine |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| FI20175977L FI20175977L (en) | 2018-05-15 |
| FI20175977A FI20175977A (en) | 2018-05-15 |
| FI129427B true FI129427B (en) | 2022-02-15 |
Family
ID=62026594
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| FI20175977A FI129427B (en) | 2016-11-14 | 2017-11-03 | Cylinder of an internal combustion engine |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP6985110B2 (en) |
| KR (1) | KR102245518B1 (en) |
| CN (1) | CN108071514B (en) |
| DE (1) | DE102016222299A1 (en) |
| FI (1) | FI129427B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115143305B (en) * | 2021-03-31 | 2023-12-26 | 浙江三花汽车零部件有限公司 | Fluid control assembly and method of making the same |
| US12000491B2 (en) * | 2021-07-30 | 2024-06-04 | Tpr Co., Ltd. | Combination of piston rings, and combination structure of piston and piston rings |
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| DE3702060A1 (en) * | 1986-02-03 | 1987-08-06 | Volkswagen Ag | PISTON PISTON ENGINE WITH LUBRICANT COOLING |
| DE3839949C1 (en) * | 1988-11-26 | 1990-03-29 | Man B & W Diesel Ag, 8900 Augsburg, De | Lubrication system for a set of piston rings |
| DE4323262A1 (en) * | 1993-07-12 | 1995-01-26 | Fev Motorentech Gmbh & Co Kg | Method and arrangement for supplying lubricant to a reciprocating piston machine |
| DK56897A (en) * | 1997-05-16 | 1998-11-17 | Man B & V Diesel A S | Cylinder liner for a diesel-type internal combustion engine |
| US6116198A (en) * | 1997-07-21 | 2000-09-12 | Cummins Engine Company, Inc. | Replaceable cylinder liner with improved cooling |
| DE19900385C2 (en) * | 1999-01-08 | 2001-02-01 | Man B & W Diesel As Kopenhagen | Reciprocating machine |
| DE19959309A1 (en) * | 1999-12-09 | 2001-06-21 | Man B & W Diesel As Kopenhagen | Engine has switching valves next to lubricant outlets with which supply lines can be blocked or opened at times determined by controller from lubricant demand derived from measurements |
| RU2303185C2 (en) * | 2003-06-14 | 2007-07-20 | Ман Б. Энд В. Диесель А/С | Piston engine |
| DE10332226B4 (en) * | 2003-07-16 | 2006-03-30 | Man B & W Diesel A/S | Two-stroke diesel engine |
| KR200427698Y1 (en) * | 2006-05-23 | 2006-09-29 | 김창대 | Cylinder Assembly for Engine |
| DE102010020491B4 (en) * | 2010-05-14 | 2014-02-13 | Man Diesel & Turbo, Filial Af Man Diesel & Turbo Se, Tyskland | A method of operating a reciprocating internal combustion engine and piston for a reciprocating internal combustion engine |
| DE102010020490B4 (en) * | 2010-05-14 | 2014-02-13 | Man Diesel & Turbo, Filial Af Man Diesel & Turbo Se, Tyskland | Method for optimizing the function of a piston ring package as well as a suitable piston ring package |
| JP5933217B2 (en) * | 2011-10-12 | 2016-06-08 | 株式会社Ihi | Two-cycle engine and method of lubricating two-cycle engine |
| US9097203B2 (en) * | 2011-12-29 | 2015-08-04 | Etagen, Inc. | Methods and systems for managing a clearance gap in a piston engine |
| IN2014KN01359A (en) * | 2011-12-29 | 2015-10-16 | Etagen Inc | |
| WO2013178247A1 (en) * | 2012-05-29 | 2013-12-05 | Chris-Marine Ab | Cylinder liner and a method for improved oil distribution in a cylinder liner |
| JP6038016B2 (en) * | 2013-12-27 | 2016-12-07 | 本田技研工業株式会社 | 2-stroke engine cylinder lubrication system |
| JP2016223583A (en) * | 2015-06-02 | 2016-12-28 | 株式会社日本自動車部品総合研究所 | Internal combustion engine |
| DK179019B1 (en) * | 2015-11-12 | 2017-08-28 | Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland | A top piston ring for a large two-stroke turbocharged compression ignited internal combustion engine with crossheads |
-
2016
- 2016-11-14 DE DE102016222299.6A patent/DE102016222299A1/en active Pending
-
2017
- 2017-11-03 FI FI20175977A patent/FI129427B/en active IP Right Grant
- 2017-11-13 KR KR1020170150498A patent/KR102245518B1/en active Active
- 2017-11-13 JP JP2017218035A patent/JP6985110B2/en active Active
- 2017-11-14 CN CN201711122447.6A patent/CN108071514B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| JP6985110B2 (en) | 2021-12-22 |
| DE102016222299A1 (en) | 2018-05-17 |
| FI20175977L (en) | 2018-05-15 |
| FI20175977A (en) | 2018-05-15 |
| CN108071514B (en) | 2021-08-13 |
| CN108071514A (en) | 2018-05-25 |
| JP2018080699A (en) | 2018-05-24 |
| KR20180054481A (en) | 2018-05-24 |
| KR102245518B1 (en) | 2021-04-29 |
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