US3174762A - Piston and fire ring construction - Google Patents
Piston and fire ring construction Download PDFInfo
- Publication number
- US3174762A US3174762A US169514A US16951462A US3174762A US 3174762 A US3174762 A US 3174762A US 169514 A US169514 A US 169514A US 16951462 A US16951462 A US 16951462A US 3174762 A US3174762 A US 3174762A
- Authority
- US
- United States
- Prior art keywords
- ring
- groove
- piston
- fire
- cylinder
- 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.)
- Expired - Lifetime
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Classifications
-
- 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
-
- 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
-
- 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
- F16J9/22—Rings for preventing wear of grooves or like seatings
Definitions
- ATTORNEYS United States Patent 3,174,762 PISTGN AND FREE RHNG fIQNSTRUfITlGN Donald M. Heeling, Laverne W. Kibbey, and Lewis M.
- This invention relates to a piston and fire ring construction for use in internal combustion engines, particularly diesel engines.
- Sticking of the top compression ring and bore scuffing have been problems in diesel engines, particularly in engines which have been modified, run at higher speeds or turbocharged in order to increase the horsepower output of the engines.
- the piston configuration and piston ring arrangement normally used in these heavy duty engines is such that the top compression ring is placed a considerable distance from the top surface of the piston, leaving an unusually wide head land. This is especially true in open chamber type diesels where part or all of the combustion chamber is in the head of the piston.
- the large mass of metal in the head land in the top ring groove area becomes very hot since it is exposed to the flame of the combustion process.
- fuel and lubricating oil are only partially burned in tins area and consequently a hard deposit forms. Bore scutfing can result when the deposit on the head land becomes sufficiently thick to take up the normal clearance provided between the land and the cylinder wall.
- Scufiing can also occur when carbon deposits from partially-burned fuel and lubricating oil fill up the normal clearance between the inside diameter of the top compression ring and the root diameter of the piston groove, or between the side of the ring and the side of the groove. In both of the latter cases, when the ring operating clearances are taken up the outside diameter of the ring is permanently exposed beyond the piston lands. Therefore, when the piston rocks slightly during its normal operation, a very high pressure condition will exit between the ring face and the cylinder bore and hence scuifing will result.
- An object of the present invention is to provide an improved piston and fire ring assembly for protecting the head land of the piston as well as the top compression ring thereof located at the conventional position on the piston.
- Another object is to provide an improved fire ring and piston assembly operative to shield or bafile the area below the fire ring from the flame front without becoming clogged by carbon deposits in the fire ring groove.
- a further object is to provide an improved piston and fire ring assembly operative to keep the cylinder wall scraped free of deposits that might otherwise work their way into the compression ring grooves located below the fire ring groove.
- FIG. 1 is a fragmentary vertical section of a piston and ring assembly in a cylinder with the piston and ring assembly constructed in accordance with the present invention.
- FIG. 2 is a plan view of a fire ring segment of the present invention.
- FIG. 3 is a fragmentary enlarged view of a portion of FIG. 1 illustrating two fire ring segments assembled in the fire ring groove of the piston in accordance with the present invention.
- FIG. 4 is a fragmentary sectional view corresponding to that of FIG. 3 but reduced in scale therefrom, illustrating a modified piston groove construction for aluminum pistons provided with the present invention.
- FIG. 5 is a fragmentary sectional View similar to that of FIG. 4 illustrating a still further modified piston groove construction.
- FIGS. 6 and 7 are fragmentary sectional views similar to that of FIG. 3 but enlarged thereover to illustrate the operation of the piston and fire ring assembly of FIG. 3.
- the piston and fire ring construction of the present invention is shown applied to a conventional heavy duty piston 10 mounted for reciprocation in a cylinder 12 of a conventional diesel engine, not otherwise shown.
- circumferential ring grooves 14, 16 and 18 for respectively receiving conventional top and middle compression rings 20 and 22 and a conventional oil ring 24.
- Piston It? is designed for open chamber type diesel engines and hence a large recess 26 is provided in the head of the piston to form part or all of the combustion chamber.
- the top compression ring 20 is placed a considerable distance from the top surface 28 of the piston, leaving an unusually wide head land 30 indicated by the bracket in FIG. 1.
- a circumferential ring groove 32 is provided in head land 30 which preferably is located as close as possible to the top end surface 28 of piston 14) consistent with the strength of the land material disposed between groove 32 and top surface 23.
- An improved fire ring assembly 34 is inserted in groove 32 which preferably comprises two steel segments 36 and 38 as more clearly shown in FIG. 3.
- Fire ring segments 36 and 38 are identical and each comprise an annular ring (FIG. 2) with a parting gap 39 and an outer peripheral cylinder scraping surface 40 which may be either plain, chrome plated, or coated or plated with some other wear resistant substance.
- the fire ring segments may be made in a conventional manner by coiling up suitable steel stock into the circular ring configuration of FIG. 2, heat treating the ring to 800 F. to relieve coiling stress and, if desired, plating the outer periphery of the ring to provide the scraping surface 40 and then reheating to relieve plating stress. While two fire ring segments 36, 38 are preferred, fire ring assembly 34 may comprise a multiplicity of such segments or only one of such segments.
- One critical feature of the piston and fire ring assembly of the present invention resides in the dimensional relationship of the fire rin' assembly 34 relative to the fire ring groove 32 and to the diameter of the bore of cylinder 12.
- the total axial width of the two fire ring segments 36, 3S i.e., the dimension of the segments which is parallel to the axis of the piston, is considerably less than the corresponding axial width of fire ring groove 32.
- This provides a relatively great amount of side or axial clearance, such as that shown in FIG. 3 between the top surface 41 of fire ring segment 36 and the top wall 42 of groove 32, as compared to the axial clearance normally specified for a conventional compression ring (usually .002-.004 inch).
- the width of groove 32 is the distance between top wall 42 and bottom wall 44 of groove 32. It has been found that the best results are obtained when the two fire rings 36, 38 are axially dimensioned to provide a total axial clearance ranging from .003 to .012 inch. The preferred range is from .003 to .006 inch.
- the other important dimensional characteristic of fire ring segments 36, 38 is their outside and inside diameters in the free or expanded condition thereof, the outside diameter being substantially the same as the inside diameter of the bore of cylinder 12 so that these segments when installed in piston it within cylinder 12 exert little or no radial force against the cylinder wall.
- the inside diameter of fire ring segments 36, 38 is greater than the root diameter of piston groove 32 so that the segments do not contact or bottom against the back wall 43 of the groove during normal operation of the engine.
- fire ring assembly 34 has what normally would be thought of as a sloppy Piston 10 is provided with suitable lit in piston groove 32.
- fire ring assembly 34 is not intended to provide a 100percent seal as is expected from a compression ring. Rather, the purpose of these fire rings is to battle or shield the area below them from the flame front and also to keep the cylinder wall scraped free of deposits that might otherwise Work their way into compression ring grooves 14 and 16.
- fire ring segments 36 and 38 are best shown in F168. 6 and 7. Due to the axial clearance in the ring groove and the lack of radial pressure against the wall of cylinder 12, the fire ring segments 36 and 38 can rotate and shift axially in groove 32 relative to piston 10.
- the fire ring segments 36, 38 have a high radial thickness to axial width ratio, such as about six to one, as compared to the usual ratio of about two and one quarter to one for conventional compression rings, and are relatively lightweight. This tends to reduce ring groove pounding due to inertial forces.
- fire ring segments 36 and 38 Due to their relatively sloppy fit in groove 32, fire ring segments 36 and 38 have room in the groove to dish (movement of the ring segment from a planar to a conical shape) between the inclined positions illustrated in solid lines respectively in FIGS. 6 and 7.
- the dishing movement results from the net combined effect of gas pressure, inertial and momentum forces and friction between the first ring segments 36, 38 and the wall of the cylinder during reciprocation of the piston.
- the ring segments 36, 38 assume the upwardly dished position of FlG. 6
- the downwardly dished position shown in solid lines in FIG. 7 is a transient condition at the beginning of the compression stroke.
- the ring segments 36, 38 lieflat against the bottom side 44 of groove 32 as indicated in broken lines in FIG. 7.
- This dishing movement produces what may be termed a windshield wiper action between the fire ring segments 36, 38 and the wall of cylinder 12 which assists in sweeping the cylinder wall clean.
- the dishing movement also causes the mutually adjacent surfaces of fire ring segments 36, 38 to move radially relative to one another, thereby assisting in keeping fire ring assembly 34 clean so that the'fire segments 36, 38 thereof remain free to move radially independently of one another to insure maximum contact of each fire ring scraping sur-. face 40 with the wall of cylinder 12.
- FIGS. 4 and 5 an alurnlnum piston 50 is partially shown which generally corresponds to piston in configuration and in the location of top compression ring 20 and a groove 14 therefor. However, 7
- an .annularcast iron insert 54 is placed in the piston mold and the molten aluminum is poured around the insert.
- the aluminum piston 50 may be cast with an even larger cast iron insert 60 therein which encompasses the location of the compression ring 20 as well as fire ring assembly 34.
- Both a fire ring groove '62 and a compression ring groove 64 are then machined of axial clearances between fire ring assembly 34 and groove 32 are intended to apply to a range of piston sizes currently employed in known diesel engines of the heavy duty type. Also, the lower limit of the aforementioned axialclearance range is more critical than the upper limit. If less than the specified minimum clearanceis provided, ring sticking will be found to occur as in prior art fire ring construction.
- the fire ring assembly would still be operable to serve as a baffle to shield the compression rings therebelow from the flame front and thereby reduce sticking, but the excessive sloppiness of such a fit would cause hammering of the fire assembly in the fire ring groove and result in excessive wear of the ring groove.
- a piston and fire ring construction operable in accordance with the invention may be constructed according to the following specifications:
- a piston adapted for'reciprocation in an internal combustion engine cylinder, said piston having a transverse end surface adapted to form a movable said end surface including first and second grooves re-' spectively constituting the closest and next closest grooves to said end surface of said plurality of grooves, and 'a head land bounded by said end surface and said second V groove; a set of piston rings individually disposed in all but said first groove of said plurality of grooves including a parted first compressionring disposed in said second groove having a free state outside diameter greater than the diameter of the cylinder whereby said compression ring is adapted to be radially compressed by the cylinder wall to develop compression sealing contact therewith; and a parted fire ring disposed in said first groove and constituting the sole ring element disposed in said first groove, said fire ring being dimensioned axially relative to said first groove to provide a predetermined axial clearance therebetween sufiicient to permit said fire ring to dish and move axially in said first groove in
- a piston adapted for reciprocation in an internal combustion engine cylinder, said piston having a transverse end surface adapted to form a movabl wall of the cylinder combustion chamber, a cylindrical peripheral surface having a plurality of circumferential grooves therein spaced axially from one another and from said end surface including first and second grooves respectively constituting the closest and next closest grooves to said end surface of said plurality of grooves, and a head land bounded by said end surface and said second groove; a set of piston rings individually disposed in all but said first groove of said plurality of grooves including a parted first compression ring disposed in said second groove having a free state outside diameter greater than the diameter of the cylinder whereby said compression ring is adapted to be radially compressed by the cylinder wall to develop compression sealing contact therewith; and a plurality of parted fire rings disposed in said first groove and constituting the sole ring elements disposed in said first groove, said fire rings each being dimensioned axially relative to one another and to said first groove to provide
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US169514A US3174762A (en) | 1962-01-29 | 1962-01-29 | Piston and fire ring construction |
GB2948/63A GB957885A (en) | 1962-01-29 | 1963-01-23 | Piston and fire ring construction |
DE1776219A DE1776219C3 (de) | 1962-01-29 | 1963-01-24 | Anordnung von Kolbenringen für Brennkraftmaschinen |
DE19631476105D DE1476105A1 (de) | 1962-01-29 | 1963-01-24 | Kolben- und Brennring |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US169514A US3174762A (en) | 1962-01-29 | 1962-01-29 | Piston and fire ring construction |
Publications (1)
Publication Number | Publication Date |
---|---|
US3174762A true US3174762A (en) | 1965-03-23 |
Family
ID=22616019
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US169514A Expired - Lifetime US3174762A (en) | 1962-01-29 | 1962-01-29 | Piston and fire ring construction |
Country Status (3)
Country | Link |
---|---|
US (1) | US3174762A (de) |
DE (2) | DE1476105A1 (de) |
GB (1) | GB957885A (de) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3802711A (en) * | 1971-12-13 | 1974-04-09 | Gould Inc | Segmental sealing ring assembly |
US3942808A (en) * | 1973-05-25 | 1976-03-09 | Midland-Ross Corporation | Piston ring assembly |
EP0019972A1 (de) * | 1979-06-01 | 1980-12-10 | Leopoldo Cattaneo | Kolben für Brennkraftmaschinen mit einem schwebenden Flammschutzring |
US7431305B2 (en) | 2003-09-02 | 2008-10-07 | Mahle Gmbh | Oil scraper ring ring groove arrangement for pistons of internal combustion engines |
US20130032119A1 (en) * | 2011-08-05 | 2013-02-07 | GM Global Technology Operations LLC | Two-piece compression piston ring of an internal combustion engine |
US20150267813A1 (en) * | 2014-03-18 | 2015-09-24 | Ford Global Technologies, Llc | Compression piston ring for an internal combusion engine |
US20170321803A1 (en) * | 2016-05-04 | 2017-11-09 | G.B. Kirby Meacham | Reduced Friction Piston Ring |
US20210115909A1 (en) * | 2018-04-19 | 2021-04-22 | Hydac Drive Center Gmbh | Swash plate-type axial piston pump |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2517407B1 (fr) * | 1981-11-30 | 1987-05-15 | Floquet Monopole | Systeme d'etancheite a segment pour piston a course rectiligne |
GB8504008D0 (en) * | 1985-02-16 | 1985-03-20 | Ae Plc | Piston & ring |
US5664536A (en) * | 1996-08-14 | 1997-09-09 | Brunswick Corporation | Self-locating piston ring for a two-stroke engine |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US765033A (en) * | 1903-03-07 | 1904-07-12 | William H Myers | Piston-packing. |
US2118433A (en) * | 1936-08-04 | 1938-05-24 | Edward J Goodyear | Piston ring |
US2294519A (en) * | 1941-08-09 | 1942-09-01 | Caterpillar Tractor Co | Piston structure |
CA456618A (en) * | 1949-05-10 | Bushby David | Combination compression and oil ring | |
US2938758A (en) * | 1957-11-21 | 1960-05-31 | Hastings Mfg Co | Piston ring assembly for internal combustion engines |
-
1962
- 1962-01-29 US US169514A patent/US3174762A/en not_active Expired - Lifetime
-
1963
- 1963-01-23 GB GB2948/63A patent/GB957885A/en not_active Expired
- 1963-01-24 DE DE19631476105D patent/DE1476105A1/de active Pending
- 1963-01-24 DE DE1776219A patent/DE1776219C3/de not_active Expired
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA456618A (en) * | 1949-05-10 | Bushby David | Combination compression and oil ring | |
US765033A (en) * | 1903-03-07 | 1904-07-12 | William H Myers | Piston-packing. |
US2118433A (en) * | 1936-08-04 | 1938-05-24 | Edward J Goodyear | Piston ring |
US2294519A (en) * | 1941-08-09 | 1942-09-01 | Caterpillar Tractor Co | Piston structure |
US2938758A (en) * | 1957-11-21 | 1960-05-31 | Hastings Mfg Co | Piston ring assembly for internal combustion engines |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3802711A (en) * | 1971-12-13 | 1974-04-09 | Gould Inc | Segmental sealing ring assembly |
US3942808A (en) * | 1973-05-25 | 1976-03-09 | Midland-Ross Corporation | Piston ring assembly |
EP0019972A1 (de) * | 1979-06-01 | 1980-12-10 | Leopoldo Cattaneo | Kolben für Brennkraftmaschinen mit einem schwebenden Flammschutzring |
US4516480A (en) * | 1979-06-01 | 1985-05-14 | Leopoldo Cattaneo | Piston ring for endothermic motors having an improved flame damper ring |
US7431305B2 (en) | 2003-09-02 | 2008-10-07 | Mahle Gmbh | Oil scraper ring ring groove arrangement for pistons of internal combustion engines |
US8555850B2 (en) * | 2011-08-05 | 2013-10-15 | GM Global Technology Operations LLC | Two-piece compression piston ring of an internal combustion engine |
US20130032119A1 (en) * | 2011-08-05 | 2013-02-07 | GM Global Technology Operations LLC | Two-piece compression piston ring of an internal combustion engine |
US20150267813A1 (en) * | 2014-03-18 | 2015-09-24 | Ford Global Technologies, Llc | Compression piston ring for an internal combusion engine |
US10113643B2 (en) * | 2014-03-18 | 2018-10-30 | Ford Global Technologies, Llc | Compression piston ring for an internal combustion engine |
US20170321803A1 (en) * | 2016-05-04 | 2017-11-09 | G.B. Kirby Meacham | Reduced Friction Piston Ring |
US9856981B2 (en) * | 2016-05-04 | 2018-01-02 | G. B. Kirby Meacham | Reduced friction piston ring |
US20210115909A1 (en) * | 2018-04-19 | 2021-04-22 | Hydac Drive Center Gmbh | Swash plate-type axial piston pump |
US11725639B2 (en) * | 2018-04-19 | 2023-08-15 | Hydac Drive Center Gmbh | Swash plate-type axial, piston pump |
Also Published As
Publication number | Publication date |
---|---|
GB957885A (en) | 1964-05-13 |
DE1476105A1 (de) | 1969-11-06 |
DE1776219A1 (de) | 1973-01-04 |
DE1776219C3 (de) | 1979-08-23 |
DE1776219B2 (de) | 1978-11-30 |
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