Multiple-piece oil stripping piston ring with reduced friction

Abstract

A three-piece piston oil control ring 2 has an upper, disc-shaped scraping ring 4, a lower, disc-shaped stabilising ring 6, and a circular expander 8 which has projections 10 protruding in the axial direction on an inner face. The circular expander 8 is arranged between the upper scraping ring 4 and the lower stabilising ring 6, wherein the projections 10 each bear inwardly against an inner face 14 of the scraping ring 4 or against an inner face 16 of the stabilising ring 6. An outer radius 18 of the scraping ring 4 is greater than an outer radius 20 of the lower stabilising ring 6, so that there is a radius difference δ between the scraping ring 4 and the stabilising ring 6.

Claims

1. A three-piece piston oil control ring, comprising an upper, disc-shaped scraping ring, a lower, disc-shaped stabilizing ring formed as a separate piece from the scraping ring, and a circular expander which has projections protruding in an axial direction on an inner face thereof, the circular expander being arranged in the axial direction between the upper scraping ring and the lower stabilizing ring, some of the projections bearing inwardly against a radial inner face of the scraping ring and some of the projections bearing against a radial inner face of the stabilizing ring, wherein an outermost radius of the scraping ring is greater than an outermost radius of the lower stabilizing ring.

2. The three-piece piston oil control ring according to claim 1, wherein only a scraping edge of the upper scraping ring is in contact with a cylinder inner surface when the piston oil control ring is installed, and the lower, disc-shaped stabilizing ring is not in contact with the cylinder inner surface when the piston oil control ring is installed.

3. The three-piece piston oil control ring according to claim 1, wherein the upper scraping ring and the lower, disc-shaped stabilizing ring have an identical thickness in a radial direction.

4. The three-piece piston oil control ring according to claim 1 wherein a thickness of the upper scraping ring is larger in the radial direction than a thickness of the lower, disc-shaped stabilizing ring.

5. The three-piece piston oil control ring according to claim 1, wherein an axial thickness of the upper scraping ring is exactly equal to an axial thickness of the lower, disc-shaped stabilizing ring.

6. The three-piece piston oil control ring according to claim 1, wherein an axial thickness of the upper scraping ring is smaller than an axial thickness of the lower stabilizing ring.

7. The three-piece piston oil control ring according to claim 1, wherein the circular expander is in the form of a corrugated, flat metal strip which is corrugated in the axial direction.

8. The three-piece piston oil control ring according to claim 1, wherein the circular expander is in the form of a flat metal strip which is corrugated in a radial direction.

9. The three-piece piston oil control ring according to claim 1, wherein the expander is in the form of a slotted spiral spring.

10. The three-piece piston oil control ring according to claim 7, wherein the expander is additionally provided with a stabilizing wire which runs through openings in wave flanks of the corrugated metal strip.

11. The three-piece piston oil control ring according to claim 7, wherein the projections are formed by tabs on the metal strip.

12. The three-piece piston oil control ring according to claim 1, wherein centering projections are provided for supporting the expander centered in a piston ring groove relative to a groove bottom.

13. The three-piece piston oil control ring according to claim 1, wherein the stabilizing ring is inwardly preloaded.

Description

(1) Further features and advantages of the present invention can be found in the description below in conjunction with the drawings, in which the same reference signs denote the same or similar parts. The drawings show multiple exemplary embodiments of the invention. In the figures, the present invention is illustrated using schematic diagrams which are not to scale and mainly intended to show the difference from conventional scraper rings.

THE DRAWINGS

(2) FIG. 1 shows a conventional three-piece scraper ring having an expander spring corrugated in the axial direction, in a perspective partial view.

(3) FIG. 2A shows a three-piece scraper ring according to the invention having an expander spring corrugated in the axial direction, in a perspective partial view.

(4) FIG. 2B shows the three-piece scraper ring of FIG. 2A in a sectional view.

(5) FIG. 2C shows a variant of the three-piece scraper ring of FIG. 2A in a sectional view.

(6) FIG. 2D shows a further variant of the three-piece scraper ring of FIG. 2A in a sectional view.

(7) FIG. 3A shows a three-piece scraper ring according to the invention having an expander spring corrugated in the radial direction, in a sectional view.

(8) FIG. 3B shows a variant of the three-piece scraper ring of FIG. 3A in a sectional view.

(9) FIG. 4 shows a three-piece scraper ring according to the invention having an expander spring in the form of a slotted spiral spring.

DETAILED DESCRIPTION

(10) The same or similar reference signs are used both in the figures and in the description below to refer to the same or similar elements or components.

(11) FIG. 1 shows a conventional three-piece scraper ring having an expander spring corrugated in the axial direction, in a perspective partial view. The conventional three-piece scraper ring comprises two scraping elements 105 and an expander/spacer 109 which is produced from an elastic, ductile metal strip, preferably a steel strip 113. The expander/spacer ensures an axial spacing between the two scraping elements 105 and pushes them outwards against a cylinder inner wall to the same extent. The steel strip 109 is corrugated and comprises multiple uniformly spaced waves 108 in the axial direction. The bends 109 of the waves are provided with slots 112, the sections 111 of the waves being flattened to achieve support of the scraping rings 105 in the axial direction. The sections 101 of the bends which protrude beyond the flattened wave peaks form projections 101 which bear against inner faces of the scraping elements 105 and push them outwards towards the cylinder inner wall. The projections 101 also ensure that the expander/spacer 107 does not come into contact with the cylinder wall.

(12) The wave shapes and straight sections 108 of the steel strip 113 form a circumferential series of spring elements which are under compressive load when the three-piece scraper ring is inserted into the piston ring groove. As shown, the ends or projections 113 of the expander/spacer 107 bear against the lower face of the scraping elements 107 and push them against the piston ring flank. The flattened portions 107 can be very uniformly shaped, and the magnitude of the radial force provided by the expander 109 can be set very precisely in this design.

(13) FIG. 2A shows a three-piece scraper ring 2 according to the invention having an expander spring 8 corrugated in the axial direction, in a perspective partial view. The diagram corresponds substantially to FIG. 1, there being instead of the lower scraping element a stabilising ring 6, the outer diameter/radius of which is smaller than that of the upper, disc-shaped scraping ring 4. The expander/spacer 8 is in the form of a metal strip which is corrugated in the axial direction and comprises bearing faces 12 for the scraping ring 4 and for the stabilising ring 6. The flat metal strip corrugated in the axial direction has projections 10 which protrude in the axial direction and each bear against the inside of both the scraping ring 4 and the stabilising ring 6 and push them outwards. Owing to different outer diameters/radii of the scraping ring 4 and of the stabilising ring 6, the scraping ring 4 protrudes further outwards than the stabilising ring 6 by the diameter/radius difference between the stabilising ring and the scraping ring. Therefore, only the scraping ring 4 comes into contact with a cylinder inner wall or at least only the scraping ring is pressed against the cylinder inner wall with any considerable force. In this embodiment, only the scraping ring scrapes oil from a cylinder inner wall, while the stabilising ring either has no contact at all with the cylinder inner surface or is pressed by the expander against the cylinder inner surface only so slightly that it cannot make a substantial contribution to scraping the oil.

(14) FIG. 2B shows the three-piece scraper ring 2 of FIG. 2A in a sectional view. Nearly all the reference signs are shown in FIG. 2B. The reference signs are not used for the subsequent figures to avoid unnecessarily affecting the clarity of the figures and the brevity and conciseness of the description by unnecessary, redundant, multiple repetitions of the same reference signs.

(15) The embodiment of the three-piece piston oil control ring 2 according to the invention comprises an upper, disc-shaped scraping ring 4, a lower, disc-shaped stabilising ring 6, and a circular expander/spacer 8 which is arranged between the scraping ring 4 and the stabilising ring 6. The expander 8 is in the form of a flat metal strip 30 corrugated in the axial direction.

(16) The expander has projections 10 which extend in the axial direction from bearing faces 12 of the expander and each bear against the inner face 14 of the scraping ring or the inner face 16 of the stabilising ring 6 and push them radially outwards.

(17) The scraping ring 4 is outwardly preloaded and is additionally pushed outwards against the cylinder inner wall 40 by the expander. The stabilising ring 6 is inwardly preloaded and stabilises the expander 8 and prevents the latter from tilting and jamming in the piston ring groove 44.

(18) The three-piece piston oil control ring 2 is inserted into a piston ring groove 44 in a piston 42 and bears against the upper and lower piston ring groove flanks 46. The three-piece piston oil control ring 2 is not in contact with the bottom 48 of the piston ring groove. Only an outer edge of the upper scraping ring 4 of the three-piece piston oil control ring 2 is in contact with a cylinder inner surface 40.

(19) The expander 8 is in the form of a flat metal strip 30 corrugated in the axial direction, and the regions 50 each represent cross-sectional areas of the metal strip 30 or expander, while the other view is a plan view of a flank of a wave of the corrugated metal strip.

(20) The scraping ring 4 has an axial thickness 26 which is exactly the same as the axial thickness 26 of the stabilising ring 6. The scraping ring 4 has a radial thickness 22 which is greater than a radial thickness 24 of the stabilising ring 6. This structure allows a substantially symmetrical expander 8 to be used, the bearing faces of which are of equal size for the scraping ring 4 and the stabilising ring 6.

(21) The arrows 18 and 20 represent the outer radius or outer diameter of the scraping ring 4 and of the stabilising ring 6, respectively. The scraping ring 4 has a radius which is greater by δr than that of the stabilising ring 6. The radius difference δr between the stabilising ring and the scraping ring ensures that only the scraping ring 4 scrapes oil from the cylinder inner wall 40 and only the scraping ring 4 contributes to the friction of the three-piece piston oil control ring 2. The frictional resistance of the three-piece piston oil control ring 2 according to the invention should thus be reduced in comparison with a conventional three-piece piston oil control ring as shown by way of example in FIG. 1. The reduction in the frictional resistance is achieved in that according to the invention only a scraping edge scrapes oil and only a scraping edge produces friction with the cylinder inner surface.

(22) FIG. 2C shows a variant of the three-piece scraper ring of FIG. 2A in a sectional view. In contrast to the embodiment of FIG. 2A, the scraping ring 4 and the stabilising ring have an identical radial thickness 22. With bent scraping and stabilising rings 4, 6, this design means that the same material can be assumed. The expander 8 is in the form of a metal strip 30 which is corrugated in the axial direction. The metal strip is likewise corrugated in the radial direction to provide each of the scraping and stabilising rings 4, 6 with a different diameter against which the projections 10 support the rings 4, 6 on the inside. In FIG. 2C too, the cross-section of the metal strip 30 of the expander 8 is indicated by reference sign 50.

(23) FIG. 2C shows a further variant of the three-piece scraper ring of FIG. 2A in a sectional view. In contrast to the embodiment of FIG. 2A, the scraping ring 4 and the stabilising ring have an identical radial thickness 22. With bent scraping and stabilising rings 4, 6, this design means that the same material can be assumed. The expander 8 is in the form of a metal strip 30, so that the projections 10 each have a different distance in the radial direction from a centre axis of the cylinder. The metal strip can be produced more simply in this case. In FIG. 2D, the cross-section of the metal strip 30 of the expander 8 is indicated by reference sign 50.

(24) FIG. 3A shows a cross-sectional view of another variant of a three-piece scraper ring 2 according to the invention. The scraping ring 4 and the stabilising ring 6 have a different width in the radial direction, as in FIG. 2B. The radial width 22 of the scraping ring 4 is greater than the radial width 24 of the stabilising ring 6. The scraping ring 4 and the stabilising ring 6 have an identical width in the axial direction in FIG. 3A. An expander 8 in the form of a corrugated metal strip 32 is also used in FIG. 3A. In contrast to the expander 8 of FIGS. 2A to 2D, the expander 8 of FIGS. 3A and 3B is in the form of a metal strip 32 corrugated in the radial direction. In this case, the projections 10 can simply be in the form of tabs which protrude laterally (or upwards and downwards) beyond the bearing faces of the expander 8.

(25) FIG. 3B shows a cross-sectional view of an additional variant of a three-piece scraper ring 2 according to the invention. The scraping ring 4 and the stabilising ring 6 have a different width in the radial direction, as in FIG. 3A. The radial width 22 of the scraping ring 4 is greater than the radial width 24 of the stabilising ring 6.

(26) The scraping ring 4 and the stabilising ring 6 have a different width in the axial direction, in contrast to FIG. 3A. The axial width 26 of the scraping ring 4 is smaller than the axial width 28 of the stabilising ring 6. In this design, the stabilising ring 6 can be made more stable than the scraping ring 4. An object of the invention consists in preventing the expander 8 from being able to twist and thus jam in the piston ring groove. To achieve this, the forces which are exerted on each of the axial projections of the expander should be as equal as possible, since the stabilising ring will have a smaller radial dimension than the scraping ring, and the scraping ring is additionally supported by the cylinder inner wall against which it bears. Therefore, the stabilising ring must be able to produce a greater force than the scraping ring 4. The stabilising ring 6 can achieve this by being inwardly preloaded and more rigid than the scraping ring.

(27) In FIG. 3B, the expander 8 or the metal strip corrugated in the radial direction is provided with openings 36 in the circumferential direction, in which a circumferential stabilising wire 38 is arranged. The stabilising wire should prevent the expander curving and being supported against the groove bottom.

(28) In FIG. 4, the expander 8 is in the form of a slotted spiral spring 34. The slotted spiral spring 34 has a U-shaped cross-section. The ends of the sides of the U-shaped cross-section are bent outwards to bear against the inner edges of the scraping ring 4 and of the stabilising ring. In FIG. 4, the cross-section of the slotted spiral spring 34/of the expander 8 is indicated by reference sign 50. Centring projections 52 are provided on the inside of the lower edge of the expander 8. Neither the expander 8 nor the stabilising ring 8 is stabilised by contact with a cylinder inner surface, since such contact would mean an increase in the friction. By contact with the groove bottom, the centring projections 52 on the expander 8 can prevent the stabilising ring or the expander coming into contact with the cylinder inner surface and thus producing friction. It is likewise possible to attach the centring projections 52 to the stabilising ring 6.

(29) Further combinations of individual features of the exemplary embodiments should also be regarded as disclosed. In particular, all the embodiments can be provided with the centring projections, the rings can have different thicknesses in the radial and axial directions, and the projections in the axial direction can likewise be different (in the leakproof and radial position of the expander).

(30) In a further embodiment, a three-piece piston oil control ring 2 is provided, comprising a lower, disc-shaped scraping ring 4, an upper, disc-shaped stabilising ring 6 (towards the combustion chamber), and a circular expander 8 which has projections 10 protruding in the axial direction on an inner face, and wherein the circular expander 8 is arranged between the lower scraping ring 4 and the upper stabilising ring 6, wherein the projections 10 each bear inwardly against an inner face 14 of the scraping ring 4 or against an inner face 16 of the stabilising ring 6, wherein an outer radius of the lower scraping ring 4 is greater than an outer radius of the upper stabilising ring 6.