WO2015132112A1 - Ensemble segment racleur d'huile - Google Patents

Ensemble segment racleur d'huile Download PDF

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Publication number
WO2015132112A1
WO2015132112A1 PCT/EP2015/053972 EP2015053972W WO2015132112A1 WO 2015132112 A1 WO2015132112 A1 WO 2015132112A1 EP 2015053972 W EP2015053972 W EP 2015053972W WO 2015132112 A1 WO2015132112 A1 WO 2015132112A1
Authority
WO
WIPO (PCT)
Prior art keywords
outer radial
radial surface
lamella
oil control
ring assembly
Prior art date
Application number
PCT/EP2015/053972
Other languages
English (en)
Inventor
Steven J. Sytsma
Thomas J. Smith
Original Assignee
Mahle International Gmbh
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 Mahle International Gmbh filed Critical Mahle International Gmbh
Priority to CN201580010075.0A priority Critical patent/CN106062440B/zh
Priority to DE112015001071.8T priority patent/DE112015001071T5/de
Publication of WO2015132112A1 publication Critical patent/WO2015132112A1/fr

Links

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
    • F16J9/06—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging
    • F16J9/064—Rings with a flat annular side rail

Definitions

  • Oil control rings perform the dual functions of minimizing oil consumption while simultaneously ensuring sufficient lubrication between the piston and the cylinder wall. Oil control rings are commonly designed to form a compromise between these two functions. In order to minimize oil consumption, the oil control rings ideally scrape off as much oil as possible from the cylinder wall during the down-stroke of the piston in the direction of the oil chamber. In order to ensure sufficient lubrication to minimize friction and wear, the oil control rings ideally maintain a minimal oil film between the oil control ring and the cylinder wall.
  • Oil control ring design must maintain the compromise between reducing oil consumption and maintaining sufficient lubrication over the life of the engine.
  • the lifespan of an internal combustion engine may encompass years of operation. Excessive wear on the oil control ring outer radial surface may widen the gap between the oil control ring and the cylinder wall. This excessive wear can have a negative impact on the oil consumption of the engine. It is therefore, highly desirable to minimize the amount of wear the oil control ring experiences during its operational lifespan.
  • Oil control ring designs may utilize expander spring elements to bias ring surfaces into contact with the cylinder liner surface.
  • the amount of force exerted on the cylinder wall may also play a role in controlling the oil film thickness.
  • Oil control rings with larger surface areas of contact typically are effective at resisting radial wear, but may also require an undesirably large or rigid expander spring element to generate adequate biasing force.
  • An expander spring element with a large spring rate may make installation of the oil control ring assembly difficult during assembly.
  • FIG. 1 is a view of an exemplary piston assembly
  • FIG. 2 is an exploded view of the exemplary piston assembly of FIG. 1;
  • FIG. 3 is a partial section view of an exemplary oil control ring assembly
  • FIG. 4 is a partial section view of the exemplary oil control ring assembly shown in Figure 3, the oil ring assembly illustrated during a piston upstroke;
  • FIG. 5 is a partial section view of the exemplary oil control ring assembly shown in Figure 4, the oil ring assembly illustrated during a piston downstroke;
  • FIG. 6 is a partial section view of another exemplary oil control ring assembly, the oil ring assembly illustrated during a piston upstroke;
  • FIG. 7 is a partial section view of the exemplary oil control ring assembly shown in Figure 6, the oil ring assembly illustrated during a piston downstroke;
  • FIG. 8 is a section view of another exemplary piston assembly.
  • FIG. 9 is a section view of an exemplary piston ring or lamella, e.g., as used in connection with the exemplary piston assembly shown in FIG. 8. DETAILED DESCRIPTION
  • a piston assembly may include a piston head having first and second compression ring grooves, compression rings within the grooves, an oil control ring groove, and an oil control ring assembly.
  • the oil control ring assembly may further include an upper lamella with a first outer radial surface that defines a first outer radial surface width.
  • the oil control ring assembly may further include a lower lamella with a second outer radial surface that defines a second outer radial width.
  • An expander ring is in communication with the upper and lower lamelias and exerts an expander outward radial force on them to urge them towards the cylinder wall once installed.
  • the first outer radial surface may be comprised of a contact section and a tapered section.
  • the tapered section may be configured to generate a first radially inward force when the piston head moves in a first direction.
  • the first radially inward force may be equal to or greater than the expander outward radial force in order to allow oil to pass by the first and second lamelias during the piston upstroke.
  • the first outer radial surface generates a second radially inward force that is less than the expander outward radial force when the piston moves in a second direction. This allows the first and second lamelias to scrape the oil from the cylinder wall during the piston downstroke.
  • both the first and second lamelias have a contact section and a tapered section.
  • they tapered sections are orientated in the same direction.
  • Each tapered section may generate a radially inward force when moved in the first direction capable of overcoming the expander outward radial force.
  • the radially inward forces of each tapered section may combine to overcome the expander outward radial force when moved in the first direction.
  • the tapered sections may be orientated in opposite directions to facilitate ease of installation.
  • the lamellas move in concert in the first direction to allow oil to pass by the oil control assembly. On the downstroke, the lamellas operate independently to scrape the oil from the cylinder wall. As such, the lamellas may behave differently with respect to the interface between the outer contact surfaces and the cylinder bore, depending on the direction of travel.
  • Exemplary outer radial surfaces of the lamellas may include a first radius section, a contact section, a tapered section, and a second radius section.
  • the contact section may comprise a flattened contact section to facilitate a sealing connection to the cylinder wall.
  • the contact section may be less than 25% of the outer radial width in one exemplary approach.
  • the tapered section is configured to form an 8 degree angle with the cylinder wall.
  • lamellas of an oil control ring assembly may behave differently with respect to the interface between the outer contact surfaces and the cylinder bore, depending on the direction of travel.
  • An exemplary process may include utilizing an oil control ring assembly comprising at least one lamella positioned within an oil ring groove of a piston, the lamella comprising a first outer radial surface with a first outer radial width, the first outer radial surface including a first contact section and a first tapered section, and biasing the lamella radially outward with an expander radial force generated by an expander ring in communication with the lamella.
  • the exemplary process may further include generating a first radially inward force in response to contacting oil when the lamella is moved in a first direction permitting oil to pass by the first contact surface, and scraping oil from the cylinder when the lamella is moved in a second direction.
  • an exemplary piston assembly may include a piston head having first and second compression ring grooves, compression rings within the grooves, an oil control ring groove, and an oil control ring assembly.
  • the oil control ring assembly may further include an upper lamella having a first outer radial surface with a first outer radial surface width, and a lower lamella having a second outer radial surface with a second outer radial surface width.
  • the upper and lower lamellas may define a first axial height and a second axial height, respectively.
  • the oil control ring assembly may further include an expander ring in communication with the upper lamella and the lower lamella, which generates an expander radial outward force on the upper lamella and the lower lamella. At least one of the first axial height and the second axial height may be greater than the first outer radial surface width and the second outer radial surface width, respectively.
  • Some exemplary processes may utilize a reduction in contact surface between a radially outer surface of an oil control ring assembly and a cylinder bore, thereby facilitating a reduction in a spring tension constant of an expander while maintaining adequate tension to control oil consumption.
  • An exemplary process for controlling oil within the cylinder of an internal combustion engine may include utilizing an oil control ring assembly comprising upper and lower lamellas positioned within an oil ring groove of a piston.
  • the lamellas may each comprise an outer radial surface, with each outer radial surface having respective outer radial widths.
  • the process may further include biasing the lamella radially outward with an expander radial force generated by an expander ring in communication with the lamella, and scraping oil from the cylinder when the lamella is moved axially with respect to a cylinder bore of the internal combustion engine.
  • the process may further include establishing at least one of the upper and lower lamellas as having an axial height greater than the respective outer radial surface width of the at least one of the upper and lower lamellas.
  • Piston assembly 100 may include a piston head 102 including an upper compression ring 104 positioned within an upper compression ring groove 106 and a lower compression ring 108 positioned within a lower compression ring groove 110.
  • the piston head 102 further includes an oil control ring assembly 1 12 positioned within an oil control ring groove 114.
  • the compression rings 104, 108 and the oil control ring assembly 110 seal against cylinder bore surfaces during reciprocal motion of the piston assembly 100 within the cylinder bore.
  • the piston head 102 moves in a first direction 1 16 during the upstroke phase of the piston assembly 100 and a second direction 1 18 during the downstroke phase of the piston assembly 100.
  • the oil control ring assembly 1 12 may include an upper lamella 120 and a lower lamella 122.
  • the upper and lower lamellas 120, 122 may be positioned within the oil control ring groove 1 14 such that they are parallel to each other and orthogonal to the axial axis of the piston.
  • An expander ring 124 is positioned between and in communication with the lamellas 120, 122 to bias them outward toward the cylinder wall (not shown) once installed.
  • the expander ring 124 may be a solid member including a plurality of circumferentially spaced U-shaped segments 126. Each of these segments may include a horizontally extending tap 128.
  • the expander ring 124 is configured to only contact the upper and lower lamellas 120, 122 once the oil control ring assembly 112 has been installed on the piston head 102.
  • the upper and lower lamellas 120, 122 and the expander ring 124 maybe formed of a variety of materials, e.g., that may be harder than the material of the piston head 102. These materials may include, but are not limited to, steel, cast iron or sintered metallic alloys.
  • the upper and lower lamellas 120, 122 may also be partially coated with a later of ceramic or metal material to increase the surface hardness and decrease the amount of wear imparted to the surfaces of the lamellas 120, 122.
  • the coatings may include, but are not limited to cobalt, chromium, tungsten, copper, molybdenum and iron. Additionally, ceramic coatings are contemplated such as oxides, carbides, nitrides and silicates.
  • the metals may be included in any stoichiometric combination with these materials.
  • Wear resistant coatings may be applied in any of a variety of methods including, but not limited to, chemical vapor deposition, physical vapor deposition, high velocity oxygen fuel coating, plasma deposition, electrolytic plating and electro-less plating.
  • FIGS. 3 through 7 exemplary cross-sectional views are provided of a portion of the piston assembly 100 installed within a cylinder wall 130. It should be understood that the features of Figures 3 through 7 may be exaggerated to illustrate relationships and are not drawn to scale.
  • the expander ring 124 biases the upper lamella 120 and the lower lamella 122 into contact with the cylinder wall 130.
  • the upper lamella 120 includes a first outer radial surface 132 having a first outer radial surface width 134.
  • the lower lamella 122 includes a second outer radial surface 136 having a second outer radial surface width 138.
  • the expander ring 124 generates an expander radial outward force 140 on the upper and lower lamellas 120, 122 such that the first outer radial surface 132 and the second outer radial surface 136 are pressed into contact with the cylinder wall 130.
  • the first and second outer radial surfaces 132, 136 are configured such that the expander ring 124 may produce a reduced expander radial outward force 140.
  • the expander radial outward force 140 is less than 27 Newtons.
  • the reduced spring rate of the expander ring 124 may improve response of the lamellas 120, 122 as described further below.
  • the first outer radial surface 132 includes a first contact section 142 and a first tapered section 144.
  • the second outer radial surface 136 includes a second contact section 146 and a second tapered section 148.
  • the first and second contact section 142, 146 may be flattened contact surfaces. Flattened contact surfaces may be utilized in order to insure contact with the cylinder wall 130 around the entire circumference of the lamellas 120, 122. The flattened contact surfaces accommodate variances in manufacturing tolerances during production of the lamellas 120, 122.
  • the first and second contact sections 142, 146 may be less than 25% of their respective outer radial surface widths 134, 138.
  • first and second contact sections 142, 146 may be between 10% and 15% of their respective outer radial surface widths 134, 138. In still another, the first and second contact sections 142, 146 may be minimized to a point where manufacturing tolerances allow.
  • the first outer radial surface 132 may further include a first radius section 150 positioned adjacent the first contact section 142 and a second radius section 152 positioned adjacent the first tapered section 144.
  • the second outer radial surface 136 may include a third radius section 154 positioned adjacent the second contact section 146 and a fourth radius section 156 adjacent the second tapered section .148.
  • the first radius section 150 has a smaller radius than the second radius section 152 and the third radius section 154 has a smaller radius than the fourth radius section 156.
  • the first and third radius sections 150, 154 have a radius of approximately 80 microns and the second and fourth radius sections 152, 156 have a radius of approximately 160 microns.
  • an exemplary oil control ring assembly 1 12 has been configured to optimize oil 158 flow past the first and second lamellas 120, 122 when the piston assembly 100 moves in the first direction 116 (upstroke - Figure 4) and optimize the scraping of oil 158 when the piston assembly moves in the second direction 118 (downstroke - Figure 5).
  • oil flow in the first direction 116 is optimized by configuring the first tapered section 144 such that it generates a first radially inward force 160 when contacting oil 158 as the piston assembly moves in the first direction 116.
  • the first radially inward force 160 may be equal to or greater than the expander radial outward force 140 such that the first lamella 120 moves inward to allow oil 158 to flow past its outer radial surface 132.
  • the first tapered section 144 is at an angle 162 relative to the cylinder wall 130. In one exemplary illustration, the angle 162 is less than 10 degrees. In another example, the angle 162 is approximately 8 degrees.
  • the angle 162 of the first tapered section 144 in combination with reduced first contact section 142 area may allow the generation of a sufficient radially inward force 160 to overcome the expander radial outward force 140.
  • the oil 158 accumulates in the area between the first tapered section 144 and the cylinder wall 130.
  • the oil 158 accumulates and generates a force on the upper lamella 120.
  • the profile of the first tapered section 144 turns this force into the first radially inward force 160 which urges the upper lamella 120 inwardly.
  • the second tapered section 148 of the second lamella 122 may also be configured such that it generates a third radial inward force 164 when contacting oil 158 as the piston assembly moves in the first direction 116.
  • the third radially inward force 164 may be equal to or greater than the expander radial outward force 140 such that the second lamella 122 moves inward to allow oil 158 to flow past its outer radial surface 136.
  • the second tapered section 148 is at an angle 162 relative to the cylinder wall 130. On one exemplary approach, the angle 162 is less than 10 degrees. On another exemplary approach, the angle 162 is approximately 8 degrees.
  • the angle 162 of the second tapered section 148 in combination with reduced second contact section 146 area may allow the generation of a sufficient radially inward force 164 to overcome the expander radial outward force 140.
  • each of the first radially inward force 160 and the third radially inward force 164 are each independently capable of overcoming the expander radial outward force 140.
  • the first radially inward force 160 and the third radially inward force 164 combine to overcome the expander radial outward force 140.
  • the first outer radial surface 132 and the first tapered section 144 may be optimized such that when the piston moves in the second direction 188 the first lamella 120 acts to scrape oil 158 from the cylinder wall 130.
  • the oil flow in the second direction 1 16 is minimized by configuring the first tapered section 144 such that it generates a second radially inward force 166 when contacting oil 158 as the piston assembly moves in the second direction 1 18.
  • the second radially inward force 166 may be minimal and may be less than the expander radial outward force 140.
  • the expander radial outward force 140 will maintain contact between the first contact surface 142 and the cylinder wall 130 such that the oil 158 is scraped downward toward the oil reservoir (not shown).
  • the second outer radial surface 136 and the second tapered section 148 may also be optimized such that when the piston moves in the second direction 188 the second lamella 122 acts to scrape oil 158 from the cylinder wall 130.
  • the oil flow in the second direction 116 is minimized by configuring the second tapered section 148 such that it generates a fourth radially inward force 168 when contacting oil 158 as the piston assembly moves in the second direction 1 18.
  • the fourth radially inward force 168 is similarly minimized such that the second contact surface 146 remains in contact with the cylinder wall 130 such that the oil 158 is scraped downward toward the oil reservoir (not shown).
  • FIGS. 6 and 7 an alternate non-limiting example of an oil ring assembly 1 12 is presented.
  • the first tapered section 144 and the second tapered section 148 are orientated in the same direction such that they operate in a similar fashion to one another. However, this requires proper orientation during installation.
  • the exemplary approach illustrated in Figures 6 and 7 contemplates the first tapered section 144 and the second tapered section 148 orientated in opposite directions such that there are no need to verify orientation during installation.
  • the first lamella 120 and the second lamella 122 are configured to move in concert when the piston is moving in the first direction 1 16 ( Figure 6).
  • the first radial inward force 160 generated by the first tapered section 144 to overcome the expander radially outward force 140 and move the first and second lamellas 120, 122 to move inward and allow oil 158 to pass by them.
  • the first lamella 120 and the second lamella 122 are configured to move independently when the piston moves in the second direction 118 ( Figure 7).
  • the second radially inward force 166 generated by the first tapered section 144 remains less than the expander radially outward force 140 and therefore the first contact surface 142 remains in contact with the cylinder wall 130 to scrap oil 158 from its surface. Even if the second tapered surface 148 moves the second contact surface 146 away from the cylinder wall 130, the first contact surface 142 will remain in contact to scrape oil on the downstroke 1 18.
  • Piston assembly 800 may generally include a piston body 802 and two upper piston rings 804, 806 disposed in respective ring grooves thereof.
  • the piston body 802 may include a further ring groove receiving an oil control rail assembly 808.
  • Oil control rail assembly 808 may include an expander 810 in communication with an upper lamella or rail 812a, and a lower lamella/rail 812b.
  • each lamella 812 includes an upper surface 816, and a lower surface 818.
  • a radially inner surface 814 extends therebetween on a radially inner portion of the lamellas 812, and is configured to contact the expander 810 (see FIG.
  • a radially outer portion of the lamellas 812 include a radially outer surface 820 which extends axially between the upper and lower surfaces 816, 818. Additionally, the lamellas 812 may define angled surfaces 822, 824 extending from the upper and lower surfaces 816, 818 to the radially outer surface 820, respectively. The angled surfaces 822, 824 may extend linearly from the upper and lower surfaces 816, 818 to the radially outer surface 820, respectively.
  • the radially outer surface 820 may define a generally planar interface with the cylinder bore 900 extending between the angled surfaces 822, 824. As such, a substantially planar radially outer surface 820 may cooperate with the angled surfaces 822, 824 to form a conical or "bullet nose" profile along the radially outer end of the lamella(s) 812.
  • one or both of the upper and lower lamellas 812 may have a narrowed profile or bullet shape adjacent a radially outer area where the lamellas 812 contact a cylinder bore surface 900 (see FIG. 8).
  • the lamellas 812 may be pointed or conical in shape such that a middle portion touches cylinder bore surface. More specifically, a radially outer surface 820 defined by the lamella 812 has significantly less surface area contacting the cylinder wall.
  • a reduced tension of the expander 810 may be employed, since contact pressure is a function of the surface area of the lamella 812 contacting the cylinder bore 900. Moreover, the reduce contact area of the lamella 812 on the cylinder wall means that unit pressure can be varied more significantly for a given change in the expander spring tension constant. Additionally, the reduced surface area of the lamella 812 described in this exemplary approach provides greater force per unit area compared with conventional oil control ring assemblies, while using less spring tension. The narrow outer face 820 of the lamella 812 thus generally reduces the amount of radial outer force/tension needed from the expander 810 to maintain nominal contact pressure and also consistent oil film thickness on the cylinder bore surface 900.
  • the axial size of the radially outer surface 820 relative to the lamella 812 may be any that is convenient.
  • an axial height H A of the lamella 812 is approximately 0.4 millimeters (mm), while the axial height of the radially outer surface 820 is approximately 0.09 mm.
  • Exemplary approaches may therefore utilize radially outer surfaces having approximately 25% of the axial height of the main portion or body of the lamella 812.
  • Exemplary radially outer surfaces 820 may be generally planar (i.e., extending axially with respect to the piston/cylinder bore) such that the radially outer surface 820 is parallel to the cylinder bore 900.
  • the reduction in surface area contacting the cylinder bore surface 900 results in a corresponding reduction in force needed from the expander 810.
  • expander force was reduced from 25.8 Newtons (N) to 15 N.
  • expander force was reduced over 50%, from 25 N to 12 N.
  • simulations of exemplary illustrations demonstrated potential for a further reduction in expander force to 8 N.
  • Piston rings e.g., lamellas 812
  • Piston rings may typically not be stationary inside the piston ring groove during operation.
  • Exemplary piston rings typically may have a measured clearance between itself and the piston ring groove walls. The ring moves within the groove in several directions during normal engine operation. This continuous moment against the piston body causes the ring and groove to degrade in a fairly predicable wear pattern.
  • Exemplary approaches described herein may generally reduce the amount of wear induced by the modified shape of the ring. For example, portions of the lamel las/rings that contact the piston groove and/or cylinder bore can be shaped in a way that reduces ring wear during the service life of the engine.
  • the pointed or conical shape of the radially outer portion of the lamella(s) 812 results in a generally increasing resistance to wear as the radial wear occurs. More specifically, as radial wear occurs to the radially outer surface 820, axial height thereof increases as more of the "cone" or "point” wears away.
  • lapping of the radially outer surface 820 improved performance by avoiding damage to the outer face profile. More specifically, lapping may generally increase the degree to which the radially outer surface 820 is planar upon initial break-in of the oil control assembly 808.
  • the profile of the lamella(s) 812 may be symmetrical axially.
  • the upper and lower angled surfaces 822, 824 are approximately the same length, and the radially outer surface 820 is positioned approximately in the middle axially with respect to the lamella 812.
  • the radially inner surface 814 may have a generally increased diameter R as compared with previous approaches.
  • the increased radius R may generally increase contact area between the expander 810 and the radially inner face 814, thereby reducing contact pressure and thus secondary wear of the radially inner portion of the lamella 812.
  • the comer radius was increased from approximately 0.2 mm to 0.4 mm.
  • Piston rings or lamellas described herein may be coated along radially outer surfaces, e.g., radially outer surface 820, and angled surfaces 822, 824.
  • the lamellas/rings may be formed of a base steel material, e.g., stainless steel, and then nitride. Nitrided radially outer ring surfaces may demonstrates significantly less wear than rings not treated with a nitride coating.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

Selon des exemples, l'invention porte sur des segments racleurs d'huile et sur des procédés. Un segment racleur d'huile peut comprendre une lamelle supérieure ayant une première surface radiale externe et une lamelle inférieure ayant une seconde surface radiale externe. Un anneau de dilatation est en communication avec la lamelle supérieure et la lamelle inférieure, et génère une force de dilatation radiale dirigée vers l'extérieur sur les lamelles. Au moins l'une de la première surface radiale externe et de la seconde surface radiale externe est constituée par une première section de contact et une première section effilée. La première section effilée est configurée de façon à générer une première force radialement vers l'intérieur supérieure ou égale à la force de dilatation radiale vers l'extérieur quand elle est déplacée dans une première direction et une seconde force radialement vers l'intérieur inférieure à la force de dilatation radiale vers l'extérieur quand elle est déplacée dans une seconde direction.
PCT/EP2015/053972 2014-03-01 2015-02-26 Ensemble segment racleur d'huile WO2015132112A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201580010075.0A CN106062440B (zh) 2014-03-01 2015-02-26 护油环组件
DE112015001071.8T DE112015001071T5 (de) 2014-03-01 2015-02-26 Ölabstreifringanordnung

Applications Claiming Priority (2)

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US201461966709P 2014-03-01 2014-03-01
US61/966,709 2014-03-01

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WO2015132112A1 true WO2015132112A1 (fr) 2015-09-11

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DE (1) DE112015001071T5 (fr)
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Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018119586A1 (de) 2018-08-13 2020-02-13 Federal-Mogul Burscheid Gmbh Abstreifring für einen dreiteiligen Ölabstreifring und dreiteiliger Ölabstreifring
DE102018120962A1 (de) * 2018-08-13 2020-02-13 Federal-Mogul Burscheid Gmbh Dreiteiliger Ölabstreifring
US11320049B2 (en) 2018-11-15 2022-05-03 Tpr Co., Ltd. Piston ring combination

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2213452A (en) * 1938-11-19 1940-09-03 Perfect Circle Co Piston ring
FR2723401A1 (fr) * 1994-08-08 1996-02-09 Dana Corp Assemblage de segment racleur d'huile de piston et assemblage de piston equipe de cet assemblage de segment
WO2005024277A1 (fr) * 2003-09-02 2005-03-17 Mahle Gmbh Segment racleur d'huile en plusieurs parties pour pistons de moteurs a combustion interne

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4132815B2 (ja) * 2001-12-28 2008-08-13 株式会社リケン サイドレール及び組合せオイルリング
BRPI0502980A (pt) * 2005-07-20 2007-03-06 Mahle Metal Leve Sa anel de controle de óleo para motor de combustão interna
DE112010003953B4 (de) * 2009-10-06 2017-11-23 Kabushiki Kaisha Riken Ölring für Verbrennungsmotor

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2213452A (en) * 1938-11-19 1940-09-03 Perfect Circle Co Piston ring
FR2723401A1 (fr) * 1994-08-08 1996-02-09 Dana Corp Assemblage de segment racleur d'huile de piston et assemblage de piston equipe de cet assemblage de segment
WO2005024277A1 (fr) * 2003-09-02 2005-03-17 Mahle Gmbh Segment racleur d'huile en plusieurs parties pour pistons de moteurs a combustion interne

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CN106062440A (zh) 2016-10-26
DE112015001071T5 (de) 2016-12-08
CN106062440B (zh) 2018-06-22

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