JP6924797B2 - Piston ring combination - Google Patents

Description

The present invention relates to a combination of piston rings.

An internal combustion engine installed in a general automobile is equipped with three piston rings, which are a combination of two compression rings (pressure rings) including a top ring and a second ring, and one oil ring. The configuration provided on the piston is adopted. In these three piston rings, a top ring, a second ring, and an oil ring are mounted in a ring groove formed on the outer peripheral surface of the piston in order from the upper side (combustion chamber side), and slide on the inner wall surface of the cylinder. The oil ring farthest from the combustion chamber has an oil seal function that suppresses the outflow of oil to the combustion chamber side (oil rise) by scraping off excess engine oil (lubricating oil) adhering to the inner wall surface of the cylinder to the crank side. By adjusting the amount of oil so that the lubricating oil film is appropriately held on the inner wall surface of the cylinder, it has a function of preventing seizure of the piston due to the operation of the internal combustion engine. The compression ring has a gas seal function that suppresses the outflow (blow-by) of combustion gas from the combustion chamber side to the crank chamber side by maintaining airtightness, and by scraping off excess oil that the oil ring could not scrape off. It has an oil seal function that suppresses oil rising. By combining such piston rings, blow-by gas and oil consumption in the internal combustion engine are reduced. Further, it is known that the oil scraping performance is improved by making the second ring a scraper ring in which a step-shaped notch (undercut) is formed in the lower part on the outer peripheral side.

Here, in a second ring such as scraper ring, the undercut causes the overall stress balance in the ring to be asymmetric. When such a second ring is attached to the piston, the second ring is twisted, and the posture of the second ring tends to be unstable during the reciprocating motion of the piston. As a result, the surface contact seal to the side surface (upper and lower surfaces of the inner wall of the ring groove), particularly to the upper surface side, is hindered in the second ring groove, so that the oil seal performance of the second ring deteriorates and the oil consumption increases. There is a risk.

In order to avoid this problem, by forming another notch at a position in which the twisting direction is different from the twisting direction due to the undercut formed in the lower part on the outer peripheral side, the twisting that occurs when the second ring is attached to the piston. (For example, Patent Document 1). Such a piston ring shape is also called a balance cut shape.

Jikkai Sho 63-141357 Gazette

As described above, good sealing performance can be expected by forming the second ring into a balanced cut shape. However, if a large amount of oil (more than a predetermined amount) is present in the third land, the oil filled in the second ring groove does not sufficiently exhibit the sealing performance due to the balance cut shape of the second ring, and the oil is consumed. There is a problem that it is difficult to obtain a sufficient reduction effect of.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a technique capable of further reducing oil consumption in a combination of piston rings.

The present inventors have repeatedly studied to solve the above problems, and focused on the fact that the sealing performance by the balance cut of the second ring can be exhibited by reducing the amount of oil in the third land, and the outer peripheral surface shape of the oil ring. It was found that the above problem can be solved by making the eccentric barrel shape.

That is, the present invention
It is a combination of a piston ring including a top ring, a second ring and an oil ring mounted on the piston of an internal combustion engine.
The top ring is provided at the outer peripheral end portion of the top ring and has a first outer peripheral end surface curved so as to be convex outward in the radial direction including the first top portion having the maximum diameter in the top ring.
The second ring includes a second upper surface located on the combustion chamber side when the second ring is mounted on the piston, and a second lower surface located on the crank chamber side when the second ring is mounted on the piston. Between the second outer peripheral end surface provided at the outer peripheral end portion of the second ring, the second inner peripheral end surface provided at the inner peripheral end portion of the second ring, and the second outer peripheral end surface and the second lower surface. It has an undercut surface that connects the second outer peripheral end surface and the second lower surface so that a stepped notch is formed in the surface.
For the second ring,
The second virtual inner circumference in a virtual lower corner formed by the intersection of a second virtual inner peripheral surface extending so as to include the second inner peripheral end surface and a second virtual lower surface extending so as to include the second lower surface. An inner cut surface connecting the second inner peripheral end surface and the second lower surface so that a predetermined portion including an intersecting portion between the surface and the second virtual lower surface is not included in the second ring.
With the second virtual outer peripheral surface in the virtual upper corner formed by the intersection of the second virtual outer peripheral surface extending so as to include the second outer peripheral end surface and the second virtual upper surface extending so as to include the second upper surface. At least one of the outer cut surface connecting the second outer peripheral end surface and the second upper surface is formed so that the predetermined portion including the intersection with the second virtual upper surface is not included in the second ring. ,
The oil ring is formed in an annular shape around the axis of the oil ring, and has a pair of sliding portions provided side by side in the axial direction of the oil ring.
Each of the pair of sliding portions is provided at the outer peripheral end portion of the sliding portion and is curved so as to be convex outward in the radial direction including the third top portion having the maximum diameter in the sliding portion. Has 3 outer peripheral end faces
The third outer peripheral end surface of at least one of the pair of sliding portions has a lower edge on the crank chamber side when the oil ring is mounted on the piston, and the oil ring is mounted on the piston. In this case, it is located radially outside the upper edge on the combustion chamber side, and the third top is located below the axial center position of the sliding portion on the third outer peripheral end surface. It is a combination of piston rings formed so as to.

Here, for each piston ring of the top ring, the second ring, and the oil ring, the "outer peripheral surface" refers to the outer peripheral edges of both end faces in the axial direction that define the width (axial dimension) of the ring (or segment or rail). Refers to the surface to be connected. The "perimeter direction" refers to the perimeter direction of the piston ring unless otherwise specified. The "radial direction" refers to the radial direction of the piston ring unless otherwise specified. "Inside" or "diameter inside" refers to the inner peripheral surface side of the piston ring, and "outside" or "diameter outside" refers to the opposite side (that is, the outer peripheral surface side of the piston ring). Refers to. The "axial direction" refers to a direction along the central axis of the piston ring unless otherwise specified.

The "barrel shape" refers to a surface shape that is curved so as to be convex outward in the radial direction including the top having the maximum diameter in the piston ring, and includes a symmetrical barrel shape, an eccentric barrel shape, and a tapered barrel shape. It shall include. The "symmetrical barrel shape" is a surface shape in which the top is located at the center of the surface in the axial direction (ring width direction). The "eccentric barrel shape" is an outer peripheral surface shape in which the top portion is located on the surface below the center in the axial direction (center of the ring width) (closer to the crank chamber). Further, the "tapered barrel shape" is an eccentric barrel shape, and the shape of the lower side (crank chamber side) is curved outward in the radial direction in a cross section orthogonal to the circumferential length direction of the piston ring, and from there. It is a surface shape that forms a tapered shape whose diameter is linearly reduced toward the upper side (combustion chamber side). The shape of the first outer peripheral end surface of the top ring may include a symmetrical barrel shape and an eccentric barrel shape.

Further, a shape in which at least one of the inner cut surface and the outer cut surface is formed is referred to as a “balance cut shape”.

According to the present invention, in the second ring in which the undercut surface is formed, the second ring is mounted on the piston by forming a balance cut shape in which at least one of the inner cut surface and the outer cut surface is formed. It is possible to suppress the twisting of the piston and improve the oil seal performance of the second ring. Further, by forming the oil ring into an eccentric barrel shape, the effect of suppressing the oil rise of the oil ring can be improved. If a large amount of oil (more than a predetermined amount) is present in the third land, the oil also flows into the second ring groove. Since the oil filled in the second ring groove hinders the behavior of the second ring expected by the balance cut shape, it becomes difficult to sufficiently exhibit the sealing performance due to the balance cut shape of the second ring. On the other hand, according to the present invention, by forming the oil ring into an eccentric barrel shape and suppressing the oil from rising to the third land, the sealing performance due to the balance cut shape of the second ring can be sufficiently exhibited. That is, the synergistic effect of the sealing performance due to the eccentric barrel shape of the oil ring and the sealing performance due to the balance cut shape of the second ring can further suppress the oil rising to the second land. As a result, oil consumption can be reduced.

In addition, the present invention
It is a combination of a piston ring including a top ring, a second ring and an oil ring mounted on the piston of an internal combustion engine.
The top ring is provided at the outer peripheral end portion of the top ring and has a first outer peripheral end surface curved so as to be convex outward in the radial direction including the first top portion having the maximum diameter in the top ring.
The second ring includes a second upper surface located on the combustion chamber side when the second ring is mounted on the piston, and a second lower surface located on the crank chamber side when the second ring is mounted on the piston. A second outer peripheral surface connecting the outer peripheral edge of the second upper surface and the outer peripheral edge of the second lower surface, and a second inner peripheral surface connecting the inner peripheral edge of the second upper surface and the inner peripheral edge of the second lower surface. And, and are formed in a rectangular shape in a cross section orthogonal to the perimeter direction.
The oil ring is formed in an annular shape around the axis of the oil ring, and has a pair of sliding portions provided side by side in the axial direction of the oil ring.
Each of the pair of sliding portions is provided at the outer peripheral end portion of the sliding portion and is curved so as to be convex outward in the radial direction including the third top portion having the maximum diameter in the sliding portion. Has 3 outer peripheral end faces
The third outer peripheral end surface of at least one of the pair of sliding portions has a lower edge on the crank chamber side when the oil ring is mounted on the piston, and the oil ring is mounted on the piston. In this case, it is located radially outside the upper edge on the combustion chamber side, and the third top portion is located below the axial center position of the sliding portion on the third outer peripheral end surface. Is formed like
It may be a combination of piston rings.

According to this, by making the second ring a so-called rectangular ring with a rectangular cross section, it is possible to suppress twisting when the second ring is attached to the piston, and it is possible to improve the oil seal performance of the second ring. .. Further, by forming the oil ring into an eccentric barrel shape and suppressing the oil from rising, the oil seal performance of the second ring can be fully exhibited. As a result, oil consumption can be reduced.

The oil ring according to the present invention may be a so-called three-piece oil ring. That is, in the present invention
The oil ring is formed in an annular shape around the axis of the oil ring, and a pair of segments provided independently of each other in the axial direction of the oil ring and the pair of segments are urged outward in the radial direction. With an expander,
The pair of sliding portions may be formed as the pair of segments.

Further, the oil ring according to the present invention may be a so-called two-piece oil ring. That is, in the present invention
The oil ring has an oil ring main body formed in an annular shape around the axis of the oil ring, and an expander that urges the oil ring main body radially outward.
A pair of rails projecting outward in the radial direction are formed in the oil ring main body side by side in the axial direction of the oil ring.
The pair of sliding portions may be formed as the pair of rails.

Further, in the present invention
The helix angle of the second ring is preferably in the range of −20 ′ to 20 ′ with the second ring mounted on the piston and the piston mounted on the cylinder. Here, the helix angle can be defined as, for example, the inclination angle of the upper surface of the ring with respect to the horizontal plane (the plane orthogonal to the axis of the piston), and the upper surface of the ring is inclined upward (combustion chamber side) toward the outer side in the radial direction. In some cases, it can be a positive value, and when the upper surface of the ring is inclined downward (toward the crank chamber) in the radial direction, it can be a negative value.

Further, in the present invention
The third outer peripheral end surface has a curved surface that is convexly curved outward in the radial direction and gradually reduced in diameter toward the upper side between the third top portion and the upper edge of the third outer peripheral end surface. You may.

Further, in the present invention
The third outer peripheral end surface may have a tapered surface whose diameter is gradually reduced toward the upper side between the third top portion and the upper edge of the third outer peripheral end surface.

According to the present invention, it is possible to improve the oil sealing performance and further reduce the oil consumption in the combination of the piston rings.

It is an overall view of the internal combustion engine provided with the combination of the piston ring which concerns on Embodiment 1. FIG. It is an enlarged view near the ring groove of the internal combustion engine which concerns on Embodiment 1. FIG. FIG. 5 is a cross-sectional view orthogonal to the circumferential length direction of the top ring according to the first embodiment. It is a figure which shows the 2nd ring which concerns on Embodiment 1, FIG. 4A is a cross-sectional view orthogonal to the peripheral length direction of the 2nd ring, and FIG. 4B is the lower part on the inner peripheral side of the 2nd ring. It is an enlarged view which shows, and FIG. 4C is an enlarged view which shows the upper part on the outer peripheral side of the second ring. It is a figure for demonstrating the twist which occurs in the 2nd ring when the 2nd ring is not a balance cut shape. It is a figure which shows an example of the inner cut surface. FIG. 5 is a cross-sectional view orthogonal to the circumferential length direction of the oil ring according to the first embodiment. It is sectional drawing which is orthogonal to the circumferential direction of the segment provided in the oil ring which concerns on Embodiment 1. FIG. It is a graph which shows the oil consumption of Example and Comparative Examples 1-3. 3 is a graph showing the time required for oil to reach from the top ring to the oil ring in Examples and Comparative Examples 1 to 3. It is a figure which shows the outer peripheral surface of the piston of an Example. It is a figure which shows the outer peripheral surface of the piston of the comparative example 1. FIG. It is a figure which shows the outer peripheral surface of the piston of the comparative example 2. It is a figure which shows the outer peripheral surface of the piston of the comparative example 3. FIG. 15 is a diagram showing the behavior of the oil in the examples. FIG. 16 is a diagram showing the behavior of the oil in Comparative Example 1. FIG. 17 is a diagram showing the behavior of the oil in Comparative Example 2. FIG. 18 is a diagram showing the behavior of the oil in Comparative Example 3. It is sectional drawing which is orthogonal to the circumferential direction of the segment which concerns on modification 1 of Embodiment 1. FIG. 20 (a) is a diagram showing an oil ring according to a modified example 2 of the first embodiment, and FIG. 20 (a) is a cross-sectional view orthogonal to the peripheral length direction of the oil ring according to the modified example 2 of the first embodiment, FIG. 20 (b). ) Is an enlarged view of the third outer peripheral surface shown in FIG. 20 (a). It is a figure which shows the internal combustion engine provided with the combination of the piston ring which concerns on Embodiment 2. FIG. 5 is a cross-sectional view orthogonal to the peripheral length direction of the second ring used for the combination of the piston rings according to the second embodiment.

Hereinafter, preferred embodiments of the combination of piston rings according to the present invention will be described with reference to the drawings. The configurations described in the following embodiments are not intended to limit the technical scope of the invention to those alone unless otherwise specified.

<Embodiment 1>
FIG. 1 is an overall view of an internal combustion engine 100 provided with a combination of piston rings according to the first embodiment. FIG. 2 is an enlarged view of the vicinity of the ring groove of the internal combustion engine 100. In FIGS. 1 and 2, for convenience, each configuration is shown in a simplified manner. As shown in FIG. 1, the internal combustion engine 100 according to the embodiment includes a cylinder 20 and a piston 10 mounted on the cylinder 20. In the internal combustion engine 100, the combustion chamber side indicated by reference numeral 30 is the upper side, and the crank chamber side indicated by reference numeral 40 is the lower side.

As shown in FIG. 2, in the internal combustion engine 100, the piston gap PC1 is formed by ensuring a predetermined separation distance between the piston outer peripheral surface 10a and the cylinder inner wall 20a. Further, on the outer peripheral surface 10a of the piston, a top ring groove 101, a second ring groove 102, and an oil ring groove 103 are formed in this order from the upper side (combustion chamber side) at predetermined intervals in the axial direction of the piston 10. The piston outer peripheral surface 10a is partitioned by a top ring groove 101, a second ring groove 102, and an oil ring groove 103. The region above the top ring groove 101 on the outer peripheral surface 10a of the piston is referred to as the top land L1, and the top ring groove 1 is used.
The region between 01 and the second ring groove 102 is referred to as a second land L2, and the region between the second ring groove 102 and the oil ring groove 103 is referred to as a third land L3. As shown in FIG. 2, the top ring 1, the second ring 2, and the oil ring 3 are mounted on the top ring groove 101, the second ring groove 102, and the oil ring groove 103, respectively. In the present specification, when the top ring groove 101, the second ring groove 102, and the oil ring groove 103 are described without distinction, they are simply referred to as "ring grooves". Further, when the top ring 1, the second ring 2, and the oil ring 3 are described without distinction, they are simply referred to as a "piston ring". As shown in FIG. 2, the state in which each piston ring is mounted in the corresponding ring groove of the piston 10 mounted in the cylinder 20 is referred to as a “use state”.

Further, in the description of each piston ring, the "perimeter direction" refers to the perimeter direction of the piston ring unless otherwise specified. The "radial direction" refers to the radial direction of the piston ring unless otherwise specified. "Inside" or "diameter inside" refers to the inner peripheral surface side of the piston ring, and "outside" or "diameter outside" refers to the opposite side (that is, the outer peripheral surface side of the piston ring). Refers to. The "axial direction" refers to a direction along the central axis of the piston ring unless otherwise specified. Further, for each piston ring of the top ring, the second ring, and the oil ring, the "outer peripheral surface" is connected to the outer peripheral edges of both end faces in the axial direction that define the width (axial dimension) of the ring (or segment or rail). The "inner peripheral surface" refers to a surface that connects the inner peripheral edges of both end faces in the axial direction.

Further, for each of the piston 10, the cylinder 20, the top ring 1, the second ring 2, and the oil ring 3, the axial direction of each is defined as the vertical direction, and the combustion chamber 30 side in these usage states is the "upper side" of each. It is defined as the "upward direction" in FIGS. 1 and 2, and the opposite side (that is, the side away from the combustion chamber and the crank chamber 40 side) is defined as the "lower side" of each.

Further, in the present specification, the "barrel shape" refers to a surface shape curved so as to be convex outward in the radial direction including the top having the maximum diameter in the piston ring, and is a symmetrical barrel shape or an eccentric barrel. The shape and taper barrel shape shall be included. The "symmetrical barrel shape" is a surface shape in which the top is located at the center of the surface in the axial direction (ring width direction). The "eccentric barrel shape" is an outer peripheral surface shape in which the top portion is located on the surface below the center in the axial direction (center of the ring width) (closer to the crank chamber). Further, the "tapered barrel shape" is an eccentric barrel shape, and the shape of the lower side (crank chamber side) is curved outward in the radial direction in a cross section orthogonal to the circumferential length direction of the piston ring, and from there. It is a surface shape that forms a tapered shape whose diameter is linearly reduced toward the upper side (combustion chamber side). Details of the symmetrical barrel shape, the eccentric barrel shape, and the tapered barrel shape will be described later.

As shown in FIG. 2, each ring groove is formed by a pair of inner walls facing each other vertically, and among these, the upper inner wall is referred to as an upper wall W1 and the lower inner wall is referred to as a lower wall W2. Each piston ring has a self-tension so that its outer peripheral surface presses the cylinder inner wall 20a in the used state.

Hereinafter, the shape of each piston ring in the combination of the piston rings according to the first embodiment will be described.

[Top ring]
FIG. 3 is a cross-sectional view orthogonal to the peripheral length direction of the top ring 1 according to the first embodiment. First, the top ring 1 according to the first embodiment will be described. As shown in FIG. 3, the top ring 1 has a first upper surface 11 provided on the upper side, a first lower surface 12 provided on the lower side, and an outer peripheral edge E101 and a first lower surface 12 of the first upper surface 11. The first outer peripheral surface 13 connecting the peripheral edge E102 and the first
It has a first inner peripheral surface 14 that connects the inner peripheral edge E103 of the upper surface 11 and the inner peripheral edge E104 of the first lower surface 12. When the top ring 1 is mounted on the top ring groove 101, that is, in the used state, the first upper surface 11 is located on the upper side and faces the upper wall W1 of the top ring groove 101, and the first lower surface 12 is It is located on the lower side and faces the lower wall W2, and the first outer peripheral surface 13 is in sliding contact with the cylinder inner wall 20a.

As shown in FIG. 3, the first outer peripheral surface 13 connects the first outer peripheral end surface S11 provided at the outer peripheral end of the top ring 1, the first outer peripheral end surface S11, the first upper surface 11, and the first lower surface 12, respectively. Includes a pair of connecting surfaces S12 and S12. One of the pair of connecting surfaces S12 and S12 connects the peripheral edge (hereinafter, upper edge) E11 on the upper side (combustion chamber 30 side) of the first outer peripheral end surface S11 and the outer peripheral edge E101 of the first upper surface 11. The other of the pair of connecting surfaces S12 and S12 connects the peripheral edge (hereinafter, lower edge) E12 on the lower side (crank chamber 40 side) of the first outer peripheral end surface S11 and the outer peripheral edge E102 of the first lower surface 12. The first outer peripheral end surface S11 is curved so as to be convex outward in the radial direction including the first top portion P1 having the maximum diameter in the top ring 1 in a cross section orthogonal to the circumferential length direction of the top ring 1. The first top portion P1 of the first outer peripheral end surface S11 is located on the first outer peripheral surface 13 at the outermost position in the radial direction of the top ring 1, and the first outer peripheral end surface S11 is in sliding contact with the cylinder inner wall 20a in the used state. The first outer peripheral end surface S11 is formed as a symmetrical barrel curved surface as a whole. That is, the first outer peripheral end surface S11 forms an arc that is convex outward in the radial direction in a cross section orthogonal to the peripheral length direction, and the convex first top portion P1 is the axis of the top ring 1 on the first outer peripheral end surface S11. It is located in the center of the direction (vertical direction) and has a symmetrical barrel shape that is symmetrical in the axial direction with the first top P1 as a boundary. The upper end of the arc is connected to the upper connecting surface S12, and the lower end is connected to the lower connecting surface S12. The first upper surface 11, the first lower surface 12, and the first inner peripheral surface 14 may be smoothly connected via a curved surface having an arcuate cross section formed by R processing or the like, or may not have a curved surface.

Reference numeral CL1 shown in FIG. 3 indicates a straight line orthogonal to the central axis A1 of the top ring 1 and passing through the central position in the axial direction on the first outer peripheral end surface S11. The symmetric barrel curved surface forming the first outer peripheral end surface S11 is formed by rotating an arc having a predetermined radius r1 on the center line CL1 which is radially inside the first outer peripheral surface 13 and around the central axis A1. It can also be regarded as a curved surface formed by. As shown in FIG. 3, the first top P1 is located on the center line CL1. In this example, the first outer peripheral end surface S11 is formed in a symmetrical barrel shape, but the shape of the first outer peripheral end surface S11 is not limited to this. The first outer peripheral end surface S11 may have a barrel shape and may not have a symmetrical barrel shape. That is, the first top P1 does not have to be located at the center in the axial direction (that is, on the center line CL1) on the first outer peripheral end surface S11, and the first top P1 is offset toward the combustion chamber 30 side or the crank chamber 40 side. You may be. That is, the first outer peripheral end surface S11 may have a shape curved so as to be convex outward in the radial direction including the first top portion P1 having the maximum diameter in the top ring 1. Further, in this example, the first outer peripheral end surface S11 is formed by an arc having a uniform radius, but the first outer peripheral end surface S11 is not an arc shape having a uniform radius in a cross section orthogonal to the peripheral length direction, but a radius. It may have a curved shape that is convex outward in the radial direction by connecting a plurality of arcs having different values. Further, the first outer peripheral end surface S11 may include a flat region. For example, the first outer peripheral end surface S11 may form a flat portion parallel to the axial direction at the first top portion P1. Further, the top ring 1 may not have a pair of connecting surfaces S12 and S12, and the first outer peripheral end surface S11 may be connected to the first upper surface 11 and the first lower surface 12. That is, the entire area of the first outer peripheral surface 13 may be the first outer peripheral end surface S11.

Reference numerals a11 and a12 shown in FIG. 3 represent barrel heads. a11 indicates the barrel head on the combustion chamber 30 side of the top ring 1, that is, the radial distance between the first top portion P1 of the top ring 1 and the upper edge E11 of the first outer peripheral end surface S11. a11 is equal to the distance from the cylinder inner wall 20a in the used state to the upper edge E11 of the first outer peripheral end surface S11. Similarly, a12 indicates the barrel head on the crank chamber 40 side of the top ring 1, that is, the radial distance between the first top portion P1 of the top ring 1 and the lower edge E12 of the first outer peripheral end surface S11. a12 is equal to the distance from the cylinder inner wall 20a in the used state to the lower edge E12 of the first outer peripheral end surface S11. In this example, since the first outer peripheral end surface S11 is formed on a symmetrical barrel curved surface, the upper edge E11 and the lower edge E12 of the first outer peripheral end surface S11 are aligned in the radial direction. As a result, a11 and a12 are equal. However, the present invention is not limited to this. Further, reference numeral b11 shown in FIG. 3 indicates a distance in the axial direction between the first top portion P1 of the first outer peripheral end surface S11 and the upper edge E11 of the first outer peripheral end surface S11. Further, b12 indicates the distance in the axial direction between the first top portion P1 of the first outer peripheral surface 13 and the lower edge E12 of the first outer peripheral end surface S11. In this example, since the first outer peripheral end surface S11 is formed on a symmetrical barrel curved surface, b11 and b12 are equal. However, the present invention is not limited to this. The first outer peripheral end surface S11 of the top ring 1 may have an eccentric barrel shape.

[Second ring]
4A and 4B are views showing a second ring 2 according to the first embodiment, FIG. 4A is a cross-sectional view orthogonal to the peripheral length direction of the second ring 2, and FIG. 4B is a second ring. It is an enlarged view which shows the lower part on the inner peripheral side of FIG. 2, and FIG. 4C is an enlarged view which shows the upper part on the outer peripheral side of the second ring 2. Next, the second ring 2 according to the first embodiment will be described. As shown in FIG. 4A, the second ring 2 is a so-called scraper ring in which a stepped notch is formed in the lower portion on the outer peripheral surface side. The second ring 2 connects the second upper surface 21 provided on the upper side, the second lower surface 22 provided on the lower side, the outer peripheral edge E201 of the second upper surface 21, and the outer peripheral edge E202 of the second lower surface 22. It has two outer peripheral surfaces 23 and a second inner peripheral surface 24 that connects the inner peripheral edge E203 of the second upper surface 21 and the inner peripheral edge E204 of the second lower surface 22. In the state where the second ring 2 is mounted in the second ring groove 102, that is, in the used state, the second upper surface 21 is located on the upper side and faces the upper wall W1 of the second ring groove 102, and the second lower surface 22 is on the lower side. The second outer peripheral surface 23 is in sliding contact with the cylinder inner wall 20a. The second upper surface 21, the second lower surface 22, the second outer peripheral surface 23, and the second inner peripheral surface 24 may be smoothly connected via a curved surface having an arcuate cross section formed by R processing or the like, and the curved surface may be smoothly connected. It is not necessary to have.

As shown in FIG. 4A, the second outer peripheral surface 23 includes a second outer peripheral end surface S211 provided at the outer peripheral end portion of the second ring 2, a lower edge E22 of the second outer peripheral end surface S211 and a second lower surface 22. Includes an undercut surface S212 that connects to the outer peripheral edge E202.

The second outer peripheral end surface S211 has a tapered shape that is inclined so as to increase in diameter toward the lower side. The second outer peripheral end surface S211 is a surface forming the outermost outer peripheral portion of the second ring 2. The outer peripheral end surface S211 is in sliding contact with the cylinder inner wall 20a in the used state of the second ring 2 to scrape off the oil in the piston gap PC1. The shape of the second outer peripheral end surface S211 is not limited to the tapered shape. The second outer peripheral end surface S211 may have a straight shape extending along the axial direction.

The undercut surface S212 has a lower edge E22 and a second lower surface 22 of the second outer peripheral end surface S211 so that an undercut 25 which is a stepped notch is formed between the second outer peripheral end surface S211 and the second lower surface 22. It is connected to the outer peripheral edge E202 of. As a result, the second ring 2 has an undercut shape in which the lower portion on the outer peripheral side is cut out. Therefore, in the internal combustion engine 100, a space due to the undercut 25 is formed between the lower portion of the second outer peripheral surface 23 and the cylinder 20. This space becomes an oil pool, and when the second ring 2 scrapes off the oil in the piston gap PC1 when the piston 10 is lowered, the oil is buffered and the rise in the oil pressure is suppressed. As a result, good oil scraping performance can be obtained. As such a second ring 2, in addition to scraper ring, napier ring may be used.

Further, as shown in FIG. 4A, the second inner peripheral surface 24 includes the second inner peripheral end surface S221 provided at the inner peripheral end portion of the second ring 2. The second inner peripheral end surface S221 has a straight shape extending along the axial direction, and the upper edge of the second inner peripheral end surface S221 is connected to the inner peripheral edge E203 of the second upper surface 21. The second inner peripheral end surface S221 is a surface forming the innermost peripheral portion of the second ring 2.

As shown in FIGS. 4A and 4B, the second ring 2 has an inner cut surface S222 connecting the lower edge E23 of the second inner peripheral end surface S221 and the inner peripheral edge E204 of the second lower surface 22. It is formed. Reference numeral VP4 in FIG. 4B indicates a second virtual inner peripheral surface extending so as to include the second inner peripheral end surface S221. Further, reference numeral VP2 indicates a second virtual lower surface extending so as to include the second lower surface 22. The virtual corner portion formed by the intersection of the second virtual inner peripheral surface VP4 and the second virtual lower surface VP2 is referred to as a virtual lower corner portion and is indicated by reference numeral VC1.

As shown in FIG. 4B, the inner cut surface S222 includes a predetermined portion of the virtual lower corner portion VC1 including the intersection portion VC11 between the second virtual inner peripheral surface VP4 and the second virtual lower surface VP2 in the second ring 2. The second inner peripheral end surface S221 and the second lower surface 22 are connected so as not to be prevented. As a result, an inner cut 26, which is a notch, is formed between the second inner peripheral end surface S221 and the second lower surface 22. As a result, the second ring 2 has a shape in which the lower portion on the inner peripheral side is cut out.

Further, as shown in FIGS. 4A and 4C, the second ring 2 has an outer cut surface S213 connecting the upper edge E21 of the second outer peripheral end surface S21 and the outer peripheral edge E201 of the second upper surface 21. Is formed. Reference numeral VP3 in FIG. 4C indicates a second virtual outer peripheral surface extending so as to include the second outer peripheral end surface S211. Further, reference numeral VP1 indicates a second virtual upper surface extending so as to include the second upper surface 21. The virtual corner portion formed by the intersection of the second virtual outer peripheral surface VP3 and the second virtual upper surface VP1 is referred to as a virtual upper corner portion and is indicated by reference numeral VC2.

As shown in FIG. 4C, the outer cut surface S213 includes a predetermined portion of the virtual upper corner portion VC2 including the intersection portion VC21 between the second virtual outer peripheral surface VP3 and the second virtual upper surface VP1 in the second ring 2. The second outer peripheral end surface S211 and the second upper surface 21 are connected so as not to be prevented. As a result, an outer cut 27, which is a notch, is formed between the second outer peripheral end surface S211 and the second upper surface 21. As a result, the second ring 2 has a shape in which the upper portion on the outer peripheral side is cut out. Hereinafter, when the inner cut and the outer cut are described without distinction, they are referred to as "balance cut". Further, the shape of the second ring in which the balance cut is formed like the second ring 2 can be referred to as the “balance cut shape”. The balance cut shape is a shape in which at least one of the inner cut surface and the outer cut surface is formed.

Here, FIG. 5 is a diagram for explaining the twist that occurs in the second ring when neither the inner cut surface nor the outer cut surface is formed on the second ring, that is, when the second ring does not have a balance cut shape. be. The second ring 2X shown in FIG. 5 is the same as the second ring 2 in that the undercut surface S212 is formed, and is different from the second ring 2 in that neither the inner cut surface S222 nor the outer cut surface S213 is formed. different. In the case of an unbalanced shape as in the second ring 2X shown in FIG. 5, the undercut 25 formed by the undercut surface S212 makes the overall stress balance in the second ring 2X asymmetric. When such a second ring 2X is mounted on the piston 10 and mounted on the cylinder 20, the second ring 2X is twisted as shown by an arrow in the figure. If the twist of the second ring 2X is large in the used state, the posture of the second ring 2X tends to be unstable during the reciprocating motion of the piston 10, and the side surfaces (upper wall W1 and lower) in the second ring groove 102. The surface contact seal to the wall W2), especially the upper wall W1, is hindered. As a result, the oil seal performance of the second ring 2X deteriorates, which may lead to an increase in oil consumption.

On the other hand, in the second ring 2 according to the present embodiment, an inner cut 26 is formed such that the lower part on the inner peripheral side is cut out by the inner cut surface S222, and the upper part on the outer peripheral side is cut out by the outer cut surface S213. It has a balanced cut shape in which an outer cut 27 is formed. As a result, in the second ring 2 in which the undercut 25 is formed, the overall stress balance becomes symmetric or close to symmetric, and the twist generated in the second ring 2 in the used state can be reduced. As a result, the second upper surface 21 and the second lower surface 22 can be kept on a flat surface (flat surface) substantially perpendicular to the piston axis in the used state. For example, if an upward inertial force acts on the second ring 2 in the expansion stroke, or if the gas pressure in the combustion chamber, which becomes a negative pressure during deceleration using the engine brake, acts on the second ring 2, the second ring 2 will move. It will be pressed against the upper wall W1 of the second ring groove 102. At this time, according to the second ring 2 having a balanced cut shape, since the second upper surface 21 is kept on a flat surface in the used state, when the second ring 2 is pressed against the upper wall W1 of the second ring groove 102. The second upper surface 21 and the upper wall W1 are in surface contact. As a result, a sufficient contact area between the second upper surface 21 and the upper wall W1 can be obtained, and the adhesion becomes preferable. As a result, good sealing performance can be obtained. As described above, according to the present embodiment, by forming the second ring 2 into a balance cut shape, the twist of the second ring 2 is suppressed, and the adhesion between the second upper surface 21 and the upper wall W1 of the second ring groove 102 is improved. It can be enhanced and the oil seal performance of the second ring 2 can be improved.

The second ring 2 may have at least one of the inner cut surface S222 and the outer cut surface S213 formed. That is, the second ring 2 may have a balance cut shape. As a result, the twist of the second ring 2 due to the undercut surface S212 can be reduced, and better oil sealing performance can be obtained as compared with the case where the second ring 2 does not have a balanced cut shape.

Further, in the above description, by forming the inner cut surface S222 as an inclined surface that is inclined upward toward the inside in the radial direction, an inner bevel type inner cut in which the lower portion on the inner peripheral side is diagonally cut out is formed. However, the shape of the inner cut surface is not limited to this. The inner cut surface may have a shape that causes a twisting action in a direction different from the twisting caused by the undercut surface. FIG. 6 is a diagram showing an example of the inner cut surface. The inner cut surface may have a shape that forms an inner step type inner cut formed in a stepped shape, such as the inner cut surface S222A of the second ring 2A shown in FIG. Similarly, the outer cut surface is not limited to the shape shown in FIG. 4, and may be a shape that causes a twisting action in a direction different from the twisting caused by the undercut surface.

Such an inner cut surface S222 and an outer cut surface S213 may be formed from the time of manufacturing the steel wire rod of the second ring 2, and the base material of the second ring 2 is chamfered by cutting, grinding, or polishing. It may be formed by.

[Oil ring]
FIG. 7 is a cross-sectional view orthogonal to the circumferential length direction of the oil ring 3 according to the first embodiment. FIG. 7 shows a state in which the oil ring 3 is provided in the ring groove. Next, the oil ring 3 according to the first embodiment will be described. As shown in FIG. 7, the oil ring 3 is a so-called three-piece oil ring. More specifically, the oil ring 3 is formed in an annular shape around the axis of the oil ring 3, and is provided with a pair of segments 4 and 4 independently of each other and arranged side by side in the axial direction of the oil ring 3, and a pair of segments. It is configured to include an expander spacer 5 for urging 4 and 4 on the outer side in the radial direction (cylinder inner wall 20a). In the oil ring 3 according to the present embodiment, the pair of segments 4 and 4 have the same shape. The pair of segments 4 and 4 is an example of the "pair of sliding portions" in the present invention. Hereinafter, of the pair of segments 4 and 4, the segment 4 arranged on the upper side (combustion chamber 30 side) is referred to as the upper segment 4U, and the segment 4 arranged on the lower side (crank chamber 40 side) is referred to as the lower segment 4L. When these are not distinguished, it is simply referred to as segment 4.

As shown in FIGS. 7 and 8, the segment 4 has a third upper surface 41 provided on the upper side, a third lower surface 42 provided on the lower side, an outer peripheral edge E401 and a third lower surface 42 of the third upper surface 41. It has a third outer peripheral surface 43 connecting the outer peripheral edge E402, and a third inner peripheral surface 44 connecting the inner peripheral edge E403 of the third upper surface 41 and the inner peripheral edge E404 of the third lower surface 42. In the upper segment 4U, when the oil ring 3 is mounted on the oil ring groove 103, that is, in the used state, the third upper surface 41 faces the upper wall W1 of the oil ring groove 103, and the third lower surface 42 and the upper segment 4U The third inner peripheral surface 44 is provided so as to come into contact with the expander spacer 5, and the third outer peripheral surface 43 is provided so as to be in sliding contact with the cylinder inner wall 20a. In the lower segment 4L, when the oil ring 3 is in use, the third lower surface 42 faces the lower wall W2 of the oil ring groove 103, and the third upper surface 41 and the third inner peripheral surface 44 are the expander spacers 5. The third outer peripheral surface 43 is provided so as to be in sliding contact with the cylinder inner wall 20a.

FIG. 8 is a cross-sectional view showing a cross section orthogonal to the peripheral length direction of the segment 4. As shown in FIG. 8, the third outer peripheral surface 43 connects the third outer peripheral end surface S41 provided at the outer peripheral end portion of the segment 4, the third outer peripheral end surface S41, the third upper surface 41, and the third lower surface 42, respectively. Includes a pair of connecting surfaces S42, S42. One of the pair of connecting surfaces S42 and S42 connects the upper edge E41 of the third outer peripheral end surface S41 and the outer peripheral edge E401 of the third upper surface 41. The other of the pair of connecting surfaces S42 and S42 connects the lower edge E42 of the third outer peripheral end surface S41 and the outer peripheral edge E402 of the third lower surface 42. The third outer peripheral end surface S41 is curved so as to be convex outward in the radial direction including the third top P4 having the maximum diameter in the segment 4 in a cross section orthogonal to the circumferential length direction of the segment 4. The third top P4 of the third outer peripheral end surface S41 is located on the third outer peripheral surface 43 at the outermost position in the radial direction of the segment 4, and the third outer peripheral end surface S41 is in sliding contact with the cylinder inner wall 20a in the used state. The third outer peripheral end surface S41 is formed on an eccentric barrel curved surface as a whole. Specifically, in the third outer peripheral end surface S41, the lower edge E42 is located radially outside the upper edge E41, and the third top P4 is located on the third outer peripheral end surface S41 from the axial center position of the segment 4. Is also formed to be located on the lower side. As a result, the third outer peripheral end surface S41 has an eccentric barrel shape that is asymmetric in the axial direction with the third top P4 as a boundary. Further, as shown in FIG. 8, the third outer peripheral end surface S41 includes the third top P4 and is curved outward in the radial direction of the segment 4, the third protruding surface 431, the third protruding surface 431, and the upper edge. It is configured to include a curved surface 432 formed between the segment 4 and the segment 4 in a cross section orthogonal to the peripheral length direction, which is convexly curved outward in the radial direction and gradually reduced in diameter toward the combustion chamber 30 side. Has been done. The curved surface 432 connects the upper end of the third protruding surface 431 and the upper edge E41 of the third outer peripheral end surface S41.

Reference numeral δ4 shown in FIG. 8 indicates the amount of eccentricity of the third top P4 from the center in the axial direction on the third outer peripheral surface 43. Further, reference numeral CL4 shown in FIG. 8 indicates a straight line orthogonal to the central axis A3 of the segment 4 and passing through the central position in the axial direction on the third outer peripheral end surface S41. Further, the reference numeral EL4 indicates a straight line orthogonal to the central axis A3 of the segment 4 and located on the eccentric amount δ4 minutes below the center line CL4 (closer to the crank chamber 40). As shown in FIG. 8, the third protruding surface 431 of the third outer peripheral end surface S41 forms an arc that is convex outward in the radial direction in a cross section orthogonal to the peripheral length direction. The lower end of the arc is connected to the lower connecting surface S42. The third protruding surface 431 can also be regarded as a curved surface formed by rotating an arc having a predetermined radius r41 having a center C41 radially inside the third outer peripheral surface 43 around the central axis A3. In FIG. 8, the center C41 is located on the straight line EL4, but the position of the center C41 is not limited to this. Further, the third protruding surface 431 has a curved shape that is convex outward in the radial direction by connecting a plurality of arcs having different radii instead of an arc shape having a uniform radius in a cross section orthogonal to the peripheral direction. You may. Further, the third outer peripheral end surface S41 may include a flat region. For example, the third outer peripheral end surface S41 may form a flat portion parallel to the axial direction at the third top portion P4. Further, the segment 4 may not have a pair of connecting surfaces S42 and S42, and the third outer peripheral end surface S41 may be connected to the third upper surface 41 and the third lower surface 42. That is, the entire area of the third outer peripheral surface 43 may be the third outer peripheral end surface S41. In the example shown in FIG. 8, the upper connection surface S42 and the lower connection surface S42 have a symmetrical shape with the center line CL4 in between, but the shape of the segment is not limited to this, and the upper connection surface S42 and the upper connection surface S42 are symmetrical. The lower connecting surface S42 does not have to be symmetrical with the center line CL4 in between. That is, the lengths of the upper and lower connecting surfaces S42 and S42 in the axial direction may be different, and the radial distance from the third top P4 to the outer peripheral edge E401 of the third upper surface 41 and the third top P4 to the third lower surface. The radial distance to the outer peripheral edge E402 of 42 may be different.

Reference numeral a41 shown in FIG. 8 is a barrel head on the combustion chamber 30 side in segment 4. The barrel head a41 is the radial distance between the third top P4 of the segment 4 and the upper edge E41 of the third outer peripheral end surface S41, from the cylinder inner wall 20a to the upper edge E41 of the third outer peripheral end surface S41 in the used state. Is equal to the distance of. Similarly, a42 is the barrel head on the crank chamber 40 side in segment 4. The barrel head a42 is the radial distance between the third top P4 of the segment 4 and the lower edge E42 of the third outer peripheral end surface S41, from the cylinder inner wall 20a to the lower edge E42 of the third outer peripheral end surface S41 in the used state. Is equal to the distance of. As shown in FIG. 8, in the third outer peripheral end surface S41, the lower edge E42 is located radially outside the upper edge E41, so that a42 is smaller than a41. Further, reference numeral b41 shown in FIG. 8 indicates a distance in the axial direction between the third top portion P4 of the segment 4 and the upper edge E41 of the third outer peripheral end surface S41. Further, b42 indicates the distance in the axial direction between the third top portion P4 of the segment 4 and the lower edge E42 of the third outer peripheral end surface S41. As shown in FIG. 8, in the third outer peripheral end surface S41, the third top portion P4 of the segment 4 is located below the axial center of the third outer peripheral end surface S41. Therefore, b42 is smaller than b41.

According to such an oil ring 3, the gap between the cylinder inner wall 20a and the third outer peripheral end surface S41 can be made smaller on the crank chamber 40 side than on the combustion chamber 30 side with the third top P4 as a boundary in the used state. .. As a result, the oil can be suitably scraped off when the piston 10 is lowered, and when the piston 10 is raised, the third outer peripheral end surface S41 rides on the oil due to the wedge effect, so that the oil is prevented from being scraped up. be able to. Therefore, it becomes difficult for the oil in the piston gap PC1 to pass through the gap on the crank chamber 40 side and flow out from the crank chamber 40 side to the third land L3. That is, it exerts an excellent effect in suppressing the rise of oil. As a result, the oil ring 3 can further suppress the oil rising to the third land L3 as compared with the case where the third outer peripheral end surface of the pair of segments has a symmetrical barrel shape. For example, in the case of segment 4 having a thickness (diametrical dimension) of 1.7 mm and a width (axial dimension) of 0.4 mm, the radius r41, the eccentricity amount δ4, the barrel heads a41, a42, and the third top P4 on the third protruding surface 431. The distances b41 and b42 in the axial direction between the upper and lower edges are r41 = about 0.5 mm, δ4 = 0.08 mm, a41 = 0.06 mm, a42 = 0.0.
It is particularly preferable to set 04 mm, b41 = 0.23 mm, and b42 = 0.06 mm from the viewpoint of improving the oil seal performance. However, the present invention is not limited to the above dimensions.

In the present invention, the third outer peripheral end surface S41 of both the third outer peripheral surfaces 43 of the pair of segments 4 and 4 has an eccentric barrel shape, but the upper segment 4U and the lower segment 4L have a radius r41 and an eccentricity amount. The distances b41 and b42 in the axial direction of δ4, the barrel heads a41 and a42, the third top P4 and the upper edge E41 and the lower edge E42 may be different. Further, in the present invention, at least one of the third outer peripheral end faces S41 of the pair of segments 4 and 4 may have the above-mentioned eccentric barrel shape. For example, the third outer peripheral end face S41 of the upper segment 4U may be the above-mentioned eccentric barrel. The shape may be such that the third outer peripheral end surface S41 of the lower segment 4L has a symmetrical barrel shape in which the third top P4 is located at the center in the axial direction, and vice versa. However, in the present embodiment, by forming the third outer peripheral end faces S41 of both of the pair of segments 4 and 4 into the above-mentioned eccentric barrel shape, it is possible to suppress the oil rise as compared with the case where only one of the segments 4 and 4 has the eccentric barrel shape. can.

[Action / Effect]
As described above, in the combination of the piston rings according to the present embodiment, the top ring 1 is provided at the outer peripheral end portion and is convex outward in the radial direction including the first top portion P1 having the maximum diameter in the top ring 1. It has a first outer peripheral end surface S11 that is curved so as to be. Further, the second ring 2 includes a second upper surface 21, a second lower surface 22, a second outer peripheral end surface S211 provided at the outer peripheral end portion, a second inner peripheral end surface S221 provided at the inner peripheral end portion, and a second ring. 2 There is an undercut surface S212 that connects the second outer peripheral end surface S211 and the second lower surface 22 so that an undercut 25 that is a stepped notch is formed between the outer peripheral end surface S211 and the second lower surface 22. doing. The second ring 2 is a scraper ring having a balance cut shape. That is, at least one of the inner cut surface S222 forming the inner cut 26 and the outer cut surface S213 forming the outer cut 27 is formed on the second ring 2. Here, the inner cut surface S222 is formed by intersecting a second virtual inner peripheral surface VP4 extending so as to include the second inner peripheral end surface S221 and a second virtual lower surface VP2 extending so as to include the second lower surface 22. The second inner peripheral end surface S221 and the second lower surface 22 so that the second ring 2 does not include a predetermined portion of the virtual lower corner portion VC1 including the intersection portion VC11 between the second virtual inner peripheral surface VP4 and the second virtual lower surface VP2. The outer cut surface S213 is formed by intersecting the second virtual outer peripheral surface VP3 extending so as to include the second outer peripheral end surface S211 and the second virtual upper surface VP1 extending so as to include the second upper surface 21. The second outer peripheral end surface S211 and the second outer peripheral end surface S211 and the second in the virtual upper corner portion VC2 formed so that a predetermined portion including the intersection portion VC21 between the second virtual outer peripheral surface VP3 and the second virtual upper surface VP1 is not included in the second ring 2. It connects to the upper surface 21. Further, each of the pair of segments 4 and 4 provided in the oil ring 3 is provided at the outer peripheral end portion and includes the third top portion P4 having the maximum diameter in the segment 4 so as to be convex outward in the radial direction. The third outer peripheral end surface S41 having a curved third outer peripheral end surface S41 and in at least one of the pair of segments 4 and 4 has a lower edge E42 located radially outside the upper edge E41 and a third top P4. Is formed so as to be located on the third outer peripheral end surface S41 below the central position in the axial direction of the segment 4.

Here, as described above, good sealing performance can be expected by forming the second ring into a balance cut shape. However, if a large amount of oil (more than a predetermined amount) is present in the third land L3, it is difficult for the oil filled in the second ring groove 102 to sufficiently exhibit the sealing performance due to the balance cut shape of the second ring. There's a problem.

On the other hand, according to the combination of the piston rings according to the present embodiment, the oil ring 3 has an eccentric barrel shape, so that the oil rising to the third land L3 can be suppressed. As a result, the sealing performance of the second ring 2 having a balanced cut shape can be fully exhibited. That is, it is possible to obtain a synergistic effect of the sealing performance due to the eccentric barrel shape of the oil ring and the sealing performance due to the balance cut shape of the second ring. As a result, according to such a combination of piston rings, oil consumption can be reduced as compared with the conventional case.

The size of the helix angle of the second ring 2 is preferably −20 ′ to 20 ′ with the second ring 2 mounted on the piston 10 and the piston 10 mounted on the cylinder 20. As a result, better sealing performance can be obtained in the second ring. Further, in this case, it is more preferable that the size of the helix angle is −15 ′ to 15 ′. Here, the helix angle can be defined as, for example, an inclination angle of the second upper surface 21 with respect to a horizontal plane (a plane orthogonal to the axis of the piston), and the second upper surface 21 is upward in the radial direction (combustion chamber side). ) A positive value can be set when tilting, and a negative value can be set when the upper surface of the ring tilts downward (crank chamber side) toward the outside in the radial direction. However, the definition and size of the helix angle are not limited to this.

The third outer peripheral end surface S41 of the segment 4 according to the present embodiment is curved outward in the radial direction and upwards between the third top portion P4 and the upper edge E41 of the third outer peripheral end surface S41. It has a curved surface 432 that is gradually reduced in diameter. According to this, the wedge effect when the piston 10 rises can be enhanced, and the oil rise can be further suppressed.

[Oil suction experiment]
In order to confirm the effect of reducing oil consumption by the combination of piston rings according to this embodiment, an oil suction experiment using a visualization tester was conducted. The visualization tester used in this experiment has a non-combustion type internal combustion engine structure using a cylinder holder provided with a translucent part and a cylinder entirely made of transparent glass. The visualization tester reciprocates the piston with oil mixed with a fluorescent substance interposed between the cylinder and the piston, and in the meantime, irradiates the translucent part of the cylinder holder with laser light and the fluorescence intensity emitted by the fluorescent substance. By acquiring the distribution with a high-speed camera, the distribution of oil on the outer peripheral surface of the piston is visualized.

In the experiment, the internal combustion engine structure of the visualization tester was operated for each of Examples and Comparative Examples 1 to 3 described later, and the oil consumption and the time required for the oil to reach from the top ring to the oil ring were measured. bottom. The experimental conditions were such that the crank rotation speed was 1500 rpm, the gas pressure in the intake pipe was 22 kPa in absolute pressure, and the oil was sucked up to the third land side.

[Example]
In the embodiment, the top ring has a symmetrical barrel shape, the second ring has a balance cut shape, and the oil ring has an eccentric barrel shape. That is, the combination of piston rings according to the embodiment is the same as the combination of piston rings shown in FIG.

[Comparative Example 1]
In Comparative Example 1, the top ring had a symmetrical barrel shape, the second ring had an unbalanced cut shape, and the oil ring had a symmetrical barrel shape. That is, the second ring according to Comparative Example 1 has the same shape as the second ring 2X shown in FIG. Further, unlike the pair of segments 4 and 4 shown in FIGS. 7 and 8, the pair of segments in the oil ring according to Comparative Example 1 all have a symmetrical barrel shape.

[Comparative Example 2]
In Comparative Example 2, the top ring had a symmetrical barrel shape, the second ring had a balanced cut shape, and the oil ring had a symmetrical barrel shape. That is, the second ring according to Comparative Example 2 has the same shape as the second ring 2 shown in FIG. Further, unlike the pair of segments 4 and 4 shown in FIGS. 7 and 8, the pair of segments in the oil ring according to Comparative Example 2 all have a symmetrical barrel shape.

[Comparative Example 3]
In Comparative Example 3, the top ring had a symmetrical barrel shape, the second ring had an unbalanced cut shape, and the oil ring had an eccentric barrel shape. That is, the second ring according to Comparative Example 3 has the same shape as the second ring 2X shown in FIG. Further, the pair of segments in the oil ring according to Comparative Example 3 have the same shape as the pair of segments 4 and 4 shown in FIGS. 7 and 8.

[Experimental result]
FIG. 9 is a graph showing the oil consumption of Examples and Comparative Examples 1 to 3. In the graph, the vertical axis shows the ratio of oil consumption. FIG. 10 is a graph showing the time required for the oil to reach the oil ring from the top ring in Examples and Comparative Examples 1 to 3. In the graph, the vertical axis shows the ratio of arrival times. 11 to 14 show measurement examples of the fluorescence intensity distribution on the outer peripheral surface of the piston. The black-and-white images shown in FIGS. 11 to 14 show the fluorescence intensity distribution (that is, the oil film thickness distribution) on the outer peripheral surface of the piston when the internal combustion engine structure of the visualization tester is operated for 300 cycles. In the figure, the vertical direction is the cylinder axial direction, the upper side is the combustion chamber side, the lower side is the crank chamber side, and the left-right direction is the circumferential direction of the cylinder. 11 shows the outer peripheral surface of the piston of the embodiment, FIG. 12 shows the outer peripheral surface of the piston of Comparative Example 1, FIG. 13 shows the outer peripheral surface of the piston of Comparative Example 2, and FIG. 14 shows the outer peripheral surface of the piston of Comparative Example 3. The outer peripheral surface is shown.

As can be seen from FIG. 9, the oil consumption was the lowest in the examples, followed by the results that the oil consumption was the lowest in the order of Comparative Example 3, Comparative Example 2, and Comparative Example 1. As a result, it was confirmed that the oil consumption can be reduced most by using the combination of the piston rings according to the examples.

As can be seen from FIG. 10, in the examples, the oil arrival time to the top ring was the longest, followed by Comparative Example 3, Comparative Example 2, and Comparative Example 1, in that order, the arrival time was the longest. As a result, it was confirmed that the combination of the piston rings according to the embodiment can slow down the rise of the oil to the top ring.

By comparing FIGS. 11 to 14, it can be seen that the amount of oil present in the top land is the smallest in the examples, followed by Comparative Example 3, Comparative Example 2, and Comparative Example 1.

Here, in FIG. 9, it can be seen that the difference in oil consumption between Comparative Example 3 and Example is larger than the difference in oil consumption between Comparative Example 1 and Comparative Example 2. Further, in FIG. 10, it can be seen that the difference in arrival time between Comparative Example 3 and Example is larger than the difference in arrival time between Comparative Example 1 and Comparative Example 2. Further, it can be seen that the difference between Comparative Example 3 and Example is larger than the difference between Comparative Example 1 and Comparative Example 2 in the amount of oil existing in Topland. From this, it can be seen that the oil sealing effect due to the balance cut shape of the second ring can be obtained more when the oil ring has an eccentric barrel shape than when the oil ring has a symmetrical barrel shape.

Here, FIGS. 15 to 18 are diagrams for schematically explaining the behavior of the oils of Examples and Comparative Examples 1 to 3. FIG. 15 shows the behavior of the oil in the example, FIG. 16 shows the behavior of the oil in the comparative example 1, FIG. 17 shows the behavior of the oil in the comparative example 2, and FIG. 18 shows the behavior of the oil in the comparative example 3. Shows the behavior of. The arrows in the figure indicate the flow of oil, and the quantity of the arrows indicates the amount of oil. However, FIGS. 15 to 18 do not limit the present invention. First, as shown in FIG. 16, in Comparative Example 1, although a part of the oil rising from the piston skirt to the oil ring is scraped off by the oil ring, a relatively large amount of oil rises to the third land. Then, of the oil that has risen to the second land without being scraped off by the second ring, the oil that has reached the top land without being scraped off by the top ring flows out to the combustion chamber side, and the oil rises. Next, as shown in FIG. 17, in Comparative Example 2, since the oil ring has a symmetrical barrel shape as in Comparative Example 1, substantially the same amount of oil as in Comparative Example 1 rises to the third land. Therefore, in Comparative Example 2, unlike Comparative Example 1, the second ring has a balanced cut shape, but the oil filled in the second ring groove does not sufficiently exhibit its sealing performance, and as a result, it reaches the top land. The amount of oil is slightly smaller than that of Comparative Example 1. Next, as shown in FIG. 18, in Comparative Example 3, unlike Comparative Example 1, the oil ring has an eccentric barrel shape, so that the amount of oil rising to the third land is smaller than that of Comparative Example 1. However, in Comparative Example 3, since the second ring does not have a balance cut shape, the effect of the oil seal due to the balance cut shape cannot be obtained. As a result, in Comparative Example 3, the amount of oil reaching the top land is smaller than that in Comparative Example 2. Then, in the embodiment, the oil ring has an eccentric barrel shape while the second ring has a balance cut shape as in Comparative Example 2. Therefore, as shown in FIG. 15, the amount of oil rising to the third land is smaller than that of Comparative Example 2, and the amount of oil in the second ring groove is smaller than that of Comparative Example 2. As a result, the sealing performance due to the balance cut of the second ring is fully exhibited. As a result, in the examples, the amount of oil reaching the top land is smaller than that in the comparative example 3.

From the above experiments, it was confirmed that, in the combination of the piston rings, the balance cut shape of the second ring and the eccentric barrel shape of the oil ring have a remarkable effect in reducing the oil consumption.

[Modification 1]
FIG. 19 is a cross-sectional view showing a cross section orthogonal to the peripheral length direction of the segment 4A according to the first modification of the first embodiment. As shown in FIG. 19, the segment 4A differs from the segment 4 in that the third outer peripheral end surface S41A has a tapered barrel shape. More specifically, the third outer peripheral end surface S41A of the segment 4A is formed between the third protruding surface 431 including the third top P4, the third protruding surface 431, and the upper edge E41 of the third outer peripheral end surface S41A. A tapered surface 432A whose diameter is gradually reduced toward the combustion chamber 30 side in a cross section orthogonal to the peripheral length direction of the oil ring 3 is included. That is, the third outer peripheral end surface S41A has a tapered surface 432A between the third top portion P4 and the upper edge E41. Also in segment 4A, the third outer peripheral end surface S41A is not an arc shape having a uniform radius in a cross section orthogonal to the peripheral length direction, but a curve that is convex outward in the radial direction by connecting a plurality of arcs having different radii. It may have a shape. Further, the third outer peripheral end surface S41A may include a flat region. For example, the third outer peripheral end surface S41A may form a flat portion parallel to the axial direction at the third top portion P4.

[Modification 2]
FIG. 20 is a diagram showing an oil ring 3B according to a modification 2 of the first embodiment, and FIG. 20A is a cross section orthogonal to the peripheral length direction of the oil ring 3B according to the modification 2 of the first embodiment. FIG. 20 (b) is an enlarged view of the third outer peripheral surface 43B shown in FIG. 20 (a). The oil ring according to the present invention may be a so-called two-piece oil ring as in the oil ring 3B shown in FIG. The oil ring 3B includes an oil ring main body 6 formed in an annular shape around the axis of the oil ring 3B, and a coil expander 8 for urging the oil ring main body 6 radially outward. Further, the oil ring main body 6 is formed with a pair of rails 7 and 7 projecting outward in the radial direction side by side in the axial direction of the oil ring 3B. Of the pair of rails 7 and 7, the upper rail 7 is referred to as a rail 7U, and the lower rail 7 is referred to as a rail 7L. The pair of rails 7U and 7L are portions corresponding to the pair of segments 4U and 4L in the oil ring 3, and are an example of the "pair of sliding portions" in the present invention.

Reference numeral CL7 shown in FIG. 20A indicates a straight line orthogonal to the axial direction of the rail 7 and passing through the central position in the axial direction of the third outer peripheral end surface S41B of the rail 7. Further, the reference numeral EL7 indicates a straight line orthogonal to the axial direction of the rail 7 and located on the eccentric amount δ4 minutes below the center line CL7 (closer to the crank chamber 40). As shown in FIG. 20B, the third outer peripheral end surface S41B of the pair of rails 7U, 7L has a third top having the maximum diameter in the rails 7U, 7L in a cross section orthogonal to the circumferential length direction of the rails 7U, 7L. It is curved so as to be convex outward in the radial direction including P4. Further, the third outer peripheral end surface S41B of the pair of rails 7U, 7L has the same eccentric barrel shape as the third outer peripheral end surface S41 of the pair of segments 4U, 4L. That is, in the third outer peripheral end faces S41B of the rails 7 and 7, the lower edge E42 is located radially outside the upper edge E41, and the third top P4 is in the third outer peripheral end face S41 in the axial direction of the rail 7. It is formed so as to be located below the central position of. The oil ring 3B may have the above-mentioned eccentric barrel shape only on the third outer peripheral end surface S41B of the pair of rails 7U and 7L. For example, the third outer peripheral end surface S41B of the rail 7U may have the above-mentioned eccentric barrel shape, and the third outer peripheral end surface S41B of the rail 7L may have a symmetrical barrel shape, or vice versa.

<Embodiment 2>
FIG. 21 is a diagram showing an internal combustion engine 200 provided with a combination of piston rings according to the second embodiment. FIG. 22 is a cross-sectional view orthogonal to the peripheral length direction of the second ring 2B used for the combination of the piston rings according to the second embodiment. The combination of piston rings according to the second embodiment is different from the combination of the piston rings according to the first embodiment in that the second ring 2B having a rectangular shape is used instead of the second ring 2 which is a scraper ring having a balance cut shape. , Other than that, it is the same.

As shown in FIG. 22, the second ring 2B has a second upper surface 21 provided on the upper side, a second lower surface 22 provided on the lower side, an outer peripheral edge E201 of the second upper surface 21, and an outer surface of the second lower surface 22. It has a second outer peripheral surface 23 connecting the peripheral edge E202, and a second inner peripheral surface 24 connecting the inner peripheral edge E203 of the second upper surface 21 and the inner peripheral edge E204 of the second lower surface 22. The second ring 2B is a so-called rectangular ring, and is formed in a rectangular shape in a cross section orthogonal to the circumferential length direction. The "rectangular shape" includes a "substantially rectangular shape", and the second upper surface 21, the second lower surface 22, the second outer peripheral surface 23, and the second inner peripheral surface 24 are formed by R processing or the like. It may be smoothly connected via a curved surface having an arcuate cross section. Further, the second ring 2B may have a rectangular shape, and the shape of the second outer peripheral surface 23 of the second ring 2B may be various shapes such as a straight shape and a tapered shape.

By making the second ring 2B a rectangular cross section, the overall stress balance in the second ring 2B becomes symmetric or close to symmetric, and the twist generated in the second ring 2B in the used state can be reduced. As a result, the adhesion between the second upper surface 21 and the upper wall W1 of the second ring groove 102 is improved, and good oil sealing performance can be obtained.

Also in the combination of the piston rings according to the second embodiment, by forming the oil ring 3 into an eccentric barrel shape, it is possible to suppress the oil from rising to the third land L3. As a result, the sealing performance of the second ring 2B having a rectangular cross section can be sufficiently exhibited. As a result, according to the combination of the piston rings according to the second embodiment, the oil consumption can be reduced as compared with the conventional case.

The size of the helix angle of the second ring 2B is preferably -20'to 20'when the second ring 2B is mounted on the piston 10 and mounted on the cylinder 20. Thereby, better sealing performance can be obtained. Further, in this case, it is more preferable that the size of the helix angle is −15 ′ to 15 ′. However, the size of the helix angle is not limited to this.

Although the preferred embodiments of the present invention have been described above, the various embodiments described above can be combined as much as possible.

100, 200: Internal combustion engine 10: Piston 20: Cylinder 30: Combustion chamber 40: Crank chamber 1: Top ring P1: First top S11: First outer peripheral end faces 2, 2A, 2B: Second ring 21: Second upper surface 22: Second lower surface 23: Second outer peripheral surface 24: Second inner peripheral surface P2: Second top S211: Second outer peripheral end surface S212: Undercut surface S213: Outer cut surface S221: Second inner peripheral end surface S222: Inner cut surface VP1 : 2nd virtual upper surface VP2: 2nd virtual lower surface VP3: 2nd virtual outer peripheral surface VP4: 2nd virtual inner peripheral surface VC1: Virtual lower corner part VC2: Virtual upper corner part 3, 3B: Oil ring 4: Segment (sliding part) Example)
41: Third upper surface 42: Third lower surface P4: Third top S41: Third outer peripheral end surface 5: Expander spacer (an example of an expander)
6: Oil ring body 7: Rail (example of sliding part)
8: Coil expander (an example of expander)

Claims (6)

It is a combination of a piston ring including a top ring, a second ring and an oil ring mounted on the piston of an internal combustion engine.
The top ring is provided at the outer peripheral end portion of the top ring and has a first outer peripheral end surface curved so as to be convex outward in the radial direction including the first top portion having the maximum diameter in the top ring.
The second ring includes a second upper surface located on the combustion chamber side when the second ring is mounted on the piston, and a second lower surface located on the crank chamber side when the second ring is mounted on the piston. Between the second outer peripheral end surface provided at the outer peripheral end portion of the second ring, the second inner peripheral end surface provided at the inner peripheral end portion of the second ring, and the second outer peripheral end surface and the second lower surface. It has an undercut surface that connects the second outer peripheral end surface and the second lower surface so that a stepped notch is formed in the surface.
For the second ring,
The second virtual inner circumference in a virtual lower corner formed by the intersection of a second virtual inner peripheral surface extending so as to include the second inner peripheral end surface and a second virtual lower surface extending so as to include the second lower surface. An inner cut surface connecting the second inner peripheral end surface and the second lower surface so that a predetermined portion including an intersecting portion between the surface and the second virtual lower surface is not included in the second ring.
With the second virtual outer peripheral surface in the virtual upper corner formed by the intersection of the second virtual outer peripheral surface extending so as to include the second outer peripheral end surface and the second virtual upper surface extending so as to include the second upper surface. At least one of the outer cut surface connecting the second outer peripheral end surface and the second upper surface is formed so that the predetermined portion including the intersection with the second virtual upper surface is not included in the second ring. ,
The oil ring is formed in an annular shape around the axis of the oil ring, and has a pair of sliding portions provided side by side in the axial direction of the oil ring.
Each of the pair of sliding portions is provided at the outer peripheral end portion of the sliding portion and is curved so as to be convex outward in the radial direction including the third top portion having the maximum diameter in the sliding portion. Has 3 outer peripheral end faces
The third outer peripheral end surface of at least one of the pair of sliding portions has a lower edge on the crank chamber side when the oil ring is mounted on the piston, and the oil ring is mounted on the piston. In this case, it is located radially outside the upper edge on the combustion chamber side, and the third top portion is located below the axial center position of the sliding portion on the third outer peripheral end surface. Is formed like
Piston ring combination. The oil ring is formed in an annular shape around the axis of the oil ring, and a pair of segments provided independently of each other in the axial direction of the oil ring and the pair of segments are urged outward in the radial direction. With an expander,
The pair of sliding portions are formed as the pair of segments.
The combination of piston rings according to claim 1. The oil ring has an oil ring main body formed in an annular shape around the axis of the oil ring, and an expander that urges the oil ring main body radially outward.
A pair of rails projecting outward in the radial direction are formed in the oil ring main body side by side in the axial direction of the oil ring.
The pair of sliding portions are formed as the pair of rails.
The combination of piston rings according to claim 1. The twist angle of the second ring is in the range of -20'to 20'with the second ring mounted on the piston and the piston mounted on the cylinder.
The combination of piston rings according to any one of claims 1 to 3. The third outer peripheral end surface has a curved surface between the third top portion and the upper edge of the third outer peripheral end surface, which is convexly curved outward in the radial direction and gradually reduced in diameter toward the upper side.
The combination of piston rings according to any one of claims 1 to 4. The third outer peripheral end surface has a tapered surface whose diameter is gradually reduced toward the upper side between the third top portion and the upper edge of the third outer peripheral end surface.
The combination of piston rings according to any one of claims 1 to 4.

Images