JP7045383B2 - piston ring - Google Patents

Description

The present invention relates to a piston ring for an internal combustion engine, and in particular, in combination with a low friction cylinder liner in which a predetermined recess is formed on the inner wall surface of the cylinder liner, the effect of low friction of the low friction cylinder liner even at a low rotation speed of the internal combustion engine. Regarding the piston ring that can fully exert.

Conventionally, a piston ring that is assembled to a piston of an internal combustion engine and can be combined with any cylinder liner to achieve low friction and reduction of oil consumption is known.

Various shapes are known for the piston ring that realizes such low friction and reduction of oil consumption. For example, as described in Patent Document 1 below, the piston ring is formed on a base material and a base material. In a piston ring having at least a hard first layer and a second layer softer than the first layer laminated on the first layer on the outer peripheral sliding surface, the surface roughness (Ra) of the first layer is , A piston ring having a configuration of 0.7 μm or less is known.

Since the surface roughness (Ra) of the first layer of the piston ring configured in this way is 0.7 μm or less, friction can be reduced and oil consumption can be suppressed even when combined with any cylinder liner. can.

Japanese Unexamined Patent Publication No. 2017-36823

However, in recent internal combustion engines, the contact area between the cylinder liner and the piston ring is reduced to minimize the friction between the cylinder liner and the piston ring for the purpose of improving fuel efficiency and reducing oil consumption.

Various methods are known for reducing the contact area. For example, it is known to use a low-friction cylinder liner in which a recess is provided at a predetermined position on the inner wall surface of the cylinder liner. By combining the above-mentioned piston ring with the low friction cylinder liner, in addition to the friction reduction effect due to the surface roughness (Ra) of the first layer of the piston ring, the friction reduction effect due to the low friction cylinder liner realizes further reduction in friction. It becomes possible to do.

However, although the above-mentioned friction reducing effect has been confirmed at the rotation speed of a vehicle equipped with an internal combustion engine, the present inventors have confirmed that the friction cylinder is low in a low rotation region such as an idling state while the vehicle is stopped. It was found that the effect of reducing the frictional force by the liner was not sufficiently obtained.

Therefore, the present invention has been made in view of the above problems, and in the piston ring combined with the low friction cylinder liner, the low friction cylinder liner even when the rotation speed of the internal combustion engine is 1000 rpm or less such as in an idling state. It is an object of the present invention to provide a piston ring capable of obtaining the friction reducing effect of the above.

The piston ring according to the present invention is a piston ring combined with a low friction cylinder liner in which a predetermined recess is formed on the inner wall surface of the cylinder liner, and the surface pressure of the piston ring is 0.8 to 2.5 MPa . The followability coefficient of the piston ring is 0.1 to 1.5, and the contact width of the outer peripheral sliding surface of the piston ring is 0.05 to 0.40 mm .

Further, in the piston ring according to the present invention, it is preferable that the piston ring is a two-piece oil ring composed of a coil expander and an oil ring main body.

In the piston ring according to the present invention, the surface pressure of the piston ring is set to 0.8 to 2.5 MPa, so that the surface pressure is optimized and the frictional force due to the low friction cylinder liner even at low rotation of the internal combustion engine. It is possible to exert a reduction effect.

Further, since the piston ring according to the present invention has a followability coefficient set to 0.1 or more, it is possible to reduce oil consumption in addition to the effect of reducing frictional force.

Further, in the piston ring according to the present invention, since the contact width of the outer peripheral sliding surface of the piston ring is set to 0.05 to 0.40 mm, the surface pressure can be further optimized.

Further, the piston ring according to the present invention can be optimally used for a diesel engine as a two-piece oil ring composed of a coil expander and an oil ring main body.

(A) is a cross-sectional view showing an example of a piston ring according to an embodiment of the present invention, and (b) is a cross-sectional view showing another example. Explanatory drawing which shows an example of the formation position of the concave part of the inner wall surface of a cylinder liner combined with the piston ring which concerns on embodiment of this invention. Schematic development showing an example of the arrangement of recesses in the central region of the process. It is a schematic development view and the schematic sectional view explaining the dimensional position of the recess formed in the cylinder of this invention. A test result showing a frictional force ratio according to the rotation speed of the piston ring according to the present embodiment. A test result showing the FMEP ratio according to the surface pressure of the piston ring according to the present embodiment. Test results showing the amount of oil consumed according to the surface pressure of the piston ring according to this embodiment. The graph which shows the relationship between the surface pressure of the piston ring and the followability coefficient which concerns on this embodiment.

Hereinafter, suitable embodiments for carrying out the present invention will be described with reference to the drawings. It should be noted that the following embodiments do not limit the invention according to each claim, and not all combinations of features described in the embodiments are essential for the means for solving the invention. ..

1A is a sectional view showing an example of a piston ring according to an embodiment of the present invention, FIG. 1B is a sectional view showing another example, and FIG. 2 is an embodiment of the present invention. It is explanatory drawing which shows an example of the formation position of the concave part of the inner wall surface of a cylinder liner combined with the piston ring which concerns on a form, and FIG. 4 is a schematic development view and a schematic cross-sectional view for explaining the dimensional position of the recess formed in the cylinder of the present invention, and FIG. 5 shows a frictional force ratio according to the rotation speed of the piston ring according to the present embodiment. 4A and 6B are test results showing the FMEP ratio according to the surface pressure of the piston ring according to the present embodiment, and FIG. 7 is the oil consumption according to the surface pressure of the piston ring according to the present embodiment. It is a test result which shows the amount, and FIG. 8 is a graph which shows the relationship between the surface pressure of the piston ring and the followability coefficient which concerns on this embodiment.

As shown in FIG. 1A, the piston ring 1 according to the present embodiment is assembled in a ring groove (not shown) formed on the outer peripheral surface of the piston of the internal combustion engine, and is slidably contacted with the inner wall of the cylinder. , A member that scrapes off excess engine oil adhering to the inner wall of the cylinder to form an appropriate oil film on the inner wall of the cylinder.

The piston ring 1 is configured as a two-piece combination oil ring, and is composed of an oil ring main body 2 and a coil expander 6. The oil ring main body 2 is formed in a substantially I-shaped cross section in which two rails 3 and 3 having outer peripheral sliding portion protrusions 4 and 4 formed at the tip thereof are connected by a pillar portion 5. The coil expander 6 is arranged in an inner peripheral groove formed on the inner peripheral surface of the pillar portion 5 of the oil ring main body 2, and presses and urges the oil ring main body 2 outward in the radial direction thereof. An oil return hole 7 is formed in the pillar portion 5 of the piston ring 1 according to the present embodiment.

Further, in the piston ring 1 according to the present embodiment, the outer peripheral sliding portion protrusions 4 and 4 formed on the two rails 3 and 3 of the oil ring main body 2 have an axial length (contact width) of 0. It is preferable that the thickness is 05 to 0.40 mm.

By setting the contact width to 0.05 to 0.40 mm in this way, it is possible to reduce the sliding area of the oil ring main body 2 with the inner wall surface of the cylinder, thereby reducing the frictional force. At the same time, oil consumption can be reduced.

As shown in FIG. 1 (b), the shape of the outer peripheral sliding surface may be a step land shape in which the convex portions 8 and 8 are formed.

It is preferable that the oil ring main body 2 includes a base material 11 and a surface treatment layer 10 formed on the surface of the base material 11. Various surface treatments used for piston rings can be applied to the surface treatment layer 10, and for example, a hard carbon film (DLC), a physical vapor deposition film (PVD), a nitriding treatment layer, a hard chrome plating layer, or the like is preferable. Used for. The base material 11 is preferably a flat plate-shaped annular member having a joint. The base material 11 is made of a steel material, a cast iron material, an aluminum alloy, or the like, and is not particularly limited as long as it exhibits good wear resistance. As an example of a preferable steel material, 13Cr steel can be used for the oil ring main body 2. This 13Cr steel contains 0.6 to 0.7% by mass of carbon, 0.25 to 0.5% by mass of silicon, 0.20 to 0.50% by mass of manganese, 13.0 to 14.0% by mass of chromium, and molybdenum. It refers to those having a composition of 0.2 to 0.4% by mass, 0.03% by mass or less of phosphorus, 0.03% by mass or less of sulfur, and residual iron and unavoidable impurities.

Further, 17Cr steel can be used for the oil ring main body 2 of the oil ring according to the present embodiment. This 17Cr steel contains 0.80 to 0.95% by mass of carbon, 0.35 to 0.5% by mass of silicon, 0.25 to 0.40% by mass of manganese, 17.0 to 18.0% by mass of chromium, and molybdenum. 1.00 to 1.25% by mass, vanadium 0.08 to 0.15% by mass, phosphorus 0.04% by mass or less, sulfur 0.04% by mass or less, balance iron and unavoidable impurities. As another material, 8Cr steel, SWRH77B equivalent material, or SKD61 equivalent material can be used.

The coil expander 6 can use a material equivalent to SWOSC-V material, and has 0.50 to 0.60% by mass of carbon, 1.20 to 1.60% by mass of silicon, and 0.50 to 0.80% by mass of manganese. %, Chromium 0.50 to 0.80% by mass, copper 0.12% by mass or less, phosphorus 0.030% by mass or less, sulfur 0.030% by mass or less, balance iron and unavoidable impurities.

Next, with reference to FIGS. 2 to 4, a low friction cylinder liner 20 that is suitably combined with the piston ring according to the present embodiment will be described.

FIG. 2 is an explanatory diagram showing an example of a position where a recess on the inner wall surface of the cylinder liner is formed in a cylinder liner fixed to the inner wall surface of the cylinder body (not shown).

As illustrated in FIG. 2, a plurality of recesses 22 are formed on the inner wall surface 21 of the cylinder liner 20 in this embodiment. The recess 22 is formed only in the stroke central region 23 of the inner wall surface 21 of the cylinder liner 20, and is not formed in any region other than the stroke central region 23. The stroke central region 23 is a region between the lower surface position of the ring groove of the lowest piston ring at the top dead center of the piston and the upper surface position of the ring groove of the highest piston ring at the bottom dead center of the piston. be.

In order to improve the energy efficiency of the device in which the cylinder is used, for example, to improve the fuel efficiency of the engine, it is effective to reduce the friction loss between the piston ring and the inner wall surface of the cylinder (in this embodiment, the inner wall surface of the cylinder liner). Is. The method for reducing the friction loss differs depending on the sliding conditions, but it differs depending on the sliding position because the piston has a feature that the speed becomes 0 at the top dead center. Therefore, in the cylinder liner constituting the cylinder of this embodiment, a recess is formed only in the stroke central region 23 of the inner wall surface thereof, and at least one recess among the plurality of recesses is formed in all the cross sections in the cylinder circumferential direction. In other words, by forming the recesses so as to overlap each other in the cylinder axial direction, it is possible to reduce the frictional force in all the regions of the stroke central region 23.

That is, in the vicinity of the top dead center and the bottom dead center where the moving speed of the piston is relatively small, the reciprocating friction can be reduced by reducing the surface roughness of the inner wall surface of the cylinder liner. However, in the stroke central region 23, which is a region where the sliding speed between the inner wall surface of the cylinder liner and the piston ring is high, the influence of the shear resistance of the lubricating oil becomes large. Therefore, in this embodiment, the contact area between the piston ring and the inner wall surface of the cylinder liner is reduced by forming a recess only in the central region 23 of the cylinder liner in the inner wall surface of the cylinder liner, and the shear resistance of the lubricating oil is reduced. It is possible to reduce the influence of.

Further, when a plurality of recesses are randomly formed in the stroke central region 23, the contact area between the piston ring and the inner wall surface of the cylinder liner becomes smaller in the entire stroke central region 23, but microscopically. Since the width of the sliding piston ring (the length in the axial direction of the cylinder) is very short compared to the stroke central region 23, there may be a portion where the recess is not formed depending on the location. In this portion, the sliding surface of the piston ring and the inner wall surface of the cylinder liner are in 100% contact with each other, and the above effect may not be sufficiently exerted. As shown above, all the cross sections in the circumferential direction of the cylinder are formed so that at least one of the plurality of recesses is present, in other words, the recesses are formed so as to overlap each other in the axial direction of the cylinder. The moving piston ring is always in contact with the concave portion, and as a result, the contact area between the piston ring and the inner wall surface of the cylinder liner does not become 100%, and the above effect can always be exhibited.

When recesses are formed in all the regions where the piston ring slides, that is, when recesses are formed in regions other than the central region of the stroke, the contact area becomes smaller near the top dead center and the bottom dead center. As a result, the contact surface pressure increases and the boundary lubrication is performed, so that the frictional force increases. Further, if there is a recess in such a portion, an unnecessary oil pool may be formed, which may be burned and the oil consumption may be increased.

Next, the recess 22 formed in the stroke central region 23 of the inner wall surface of the cylinder liner constituting the cylinder of this embodiment will be described.

In this embodiment, the shape of the recess 22 formed in the process central region 23 is not particularly limited, and can be appropriately adjusted according to the arrangement of the recesses and the like. Recesses having a shape composed of straight lines and / or curved lines can be formed. The concave portion may have a horizontally long shape, a vertically long shape, or a shape having approximately the same vertical-to-horizontal ratio.

Here, the cylinder of the present embodiment is characterized in that at least one of the recesses is formed in all the cross sections in the cylinder circumferential direction in the central region of the stroke. As a result, the contact area can be reduced efficiently and on average.

As described above, when considering a cross section in the circumferential direction, if no recess is formed in a certain cross section, when the piston ring passes through the cross section, it passes through the cross section in which a plurality of recesses are formed. Compared to the case, the contact area between the piston ring and the inner wall surface of the cylinder liner is larger. Therefore, the influence of the shear resistance of the lubricating oil becomes large, and as a result, the reciprocating friction also becomes large.

On the other hand, by forming at least one recess in all the cross sections in the cylinder circumferential direction in the central region of the stroke, the contact area is formed regardless of which circumferential cross section of the central region of the stroke the piston ring passes through. Can be reliably and evenly reduced, so that the reciprocating dynamic friction can also be reliably reduced.

The case of FIGS. 3A and 3B is an example of the state in which at least one of the plurality of recesses is formed in all the cross sections in the circumferential direction of the cylinder, which is a feature of this embodiment. Can be mentioned.

FIG. 3A is a schematic development view showing an example of the arrangement of the recesses 22 in the process central region 23 of FIG. 2 described above. In FIG. 3A, the vertical direction of the drawing is the axial direction of the cylinder, and the horizontal direction of the drawing is the circumferential direction of the cylinder. As illustrated in FIG. 3A, in the line X drawn in the circumferential direction of the cylinder, the lowest point 5a of the recess 22a is located below the uppermost point 6b of the recess 22b closest to the lower side thereof. Further, in the line Y drawn in the circumferential direction of the cylinder, the lowest point 5b of the concave portion 22b is located below the uppermost point 6c of the concave portion 22c closest to the lower portion. In this way, by arranging the recesses that are close to each other in the vertical direction so as to overlap each other in the cylinder axial direction, it is possible to form at least one recess among the plurality of recesses in all the cross sections in the cylinder circumferential direction. From the above, when the piston reciprocates, the sliding piston ring in the central region of the stroke can reduce the contact area with the inner wall surface of the cylinder at any position in the cylinder axial direction, reducing reciprocating dynamic friction. It works.

Here, FIG. 3B is also a schematic development view showing an example of the arrangement of the recesses 22 in the process central region 23 of FIG. 2 described above, similarly to FIG. 3A. Also in FIG. 3B, the vertical direction of the drawing is the axial direction of the cylinder, and the horizontal direction of the drawing is the circumferential direction of the cylinder. In FIG. 3A, the recess 22 is formed in a uniform area over the cylinder axial direction, but the present invention is not limited to this embodiment, and as shown in FIG. 3B, the cylinder axial direction. The area of the recess 22 may be reduced in the vicinity of the end of the process central region 23, and the area of the recess may be increased in the vicinity of the center of the process central region 23, which may be adjusted as appropriate.

In this embodiment, the size of the recess is not particularly limited, and can be appropriately adjusted according to the size of the cylinder and the piston ring used together. The recess may be formed so as to penetrate the central region of the stroke in the cylinder axial direction, but from the viewpoint of maintaining the airtightness of the cylinder, the average length of the recess in the cylinder axial direction is the piston ring used. It is preferable that the length of the uppermost piston ring is equal to or less than the length in the cylinder axial direction. More specifically, among the piston rings used, it is preferable that the length is about 5 to 100% of the length of the uppermost piston ring in the cylinder axial direction.

In this embodiment, the average length of each of the recesses described above means the average length of each portion illustrated in FIG. FIG. 4A is a schematic development view showing the cylinder axial direction of the inner wall surface of the cylinder liner in the vertical direction of the drawing. Further, FIG. 4B is a schematic cross-sectional view of the cylinder liner in the circumferential direction. The axial average length of the recess is, as illustrated in FIG. 4A, the average length of the recess 22 in the cylinder axial direction.

Further, the average length of the recess 22 in the circumferential direction is the average length of the recess 22 in the circumferential direction of the cylinder, as illustrated in FIG. 4A. As illustrated in FIG. 4B, the circumferential average length of the recess 22 means the average length of the surface including the inner wall surface 21, and the same applies to the area of the recess.

Further, the radial length of the recess 22 is an average of the lengths from the bottom surface of the recess 22 to the inner wall surface 21 of the cylinder liner 20 as illustrated in FIG. 4 (b). Further, the average length (interval) in the cylinder circumferential direction between the recesses is the average of the spacing between the adjacent recesses 22 as illustrated in FIGS. 4A and 4B.

The average length of the recess in the cylinder circumferential direction is preferably in the range of 0.1 mm to 15 mm, and particularly preferably in the range of 0.3 mm to 5 mm. If the average length in the circumferential direction of the cylinder is less than this range, the effect of forming the recess may not be sufficiently obtained. On the other hand, if the average length in the circumferential direction exceeds this range, a part of the piston ring may enter the recess and a problem such as deformation of the piston ring may occur.

The average length of the recess in the cylinder radial direction is preferably in the range of 0.1 μm to 1000 μm, more preferably in the range of 0.1 μm to 500 μm, and particularly preferably in the range of 0.1 μm to 50 μm. If the cylinder radial average length of the recess is less than this range, the effect of forming the recess may not be sufficiently obtained. On the other hand, if the average radial length exceeds this range, processing is difficult, and there are problems such as the need to increase the radial length of the cylinder liner (increase the wall thickness). There is.

In this embodiment, the average length (interval) in the cylinder circumferential direction between the adjacent recesses is preferably in the range of 0.1 to 15 mm, and particularly preferably in the range of 0.3 mm to 5 mm. If the average cylinder circumferential length (interval) between adjacent recesses is less than this range, the width of the inner wall surface of the cylinder liner on which the piston ring slides is too small, and the inner wall surface of the piston ring and cylinder liner is too small. And may not slide stably. On the other hand, if it exceeds this range, the effect of forming the recess may not be sufficiently obtained.

The piston ring 1 according to the present embodiment is combined with the above-mentioned low friction cylinder liner. At this time, it is preferable that the surface pressure W of the piston ring 1 is set to 0.8 to 2.5 MPa. By setting the surface pressure W in this way, it is possible to sufficiently obtain the effect of reducing friction by the low friction cylinder liner even at low rotation speeds. The surface pressure can be obtained from (2 × piston ring tension) / (bore diameter × contact width), and the piston ring 1 according to the present embodiment has a surface pressure lower than that of the conventional surface pressure. The piston ring tension Ft and the contact width h1 are set to.

Further, the piston ring 1 according to the present embodiment is set so that the followability coefficient Kp of the piston ring is 0.1 or more. The followability coefficient Kp is a coefficient representing the followability to bore deformation due to thermal expansion of an internal combustion engine, and is expressed by the following equation.

In this way, by setting the followability coefficient of the piston ring, it is possible to suppress the increase in oil consumption due to the decrease in the followability coefficient, and to achieve both low friction and suppression of oil consumption by using a low friction cylinder liner. It becomes possible to plan.

Next, the present invention will be described in more detail with reference to Examples and Comparative Examples.

In the examples and comparative examples, the friction coefficient was measured using a piston ring having the following configuration, a low friction cylinder liner, and a normal cylinder liner.

In Examples, Comparative Example 1 and Comparative Example 2, a two-piece oil ring was used, and as the 13Cr steel constituting the oil ring body, 0.65% by mass of carbon, 0.38% by mass of silicon, 0.35% by mass of manganese, and so on. An oil equivalent to JIS standard SUS410 material having a composition of 13.50% by mass of chromium, 0.3% by mass of molybdenum, 0.01% by mass of phosphorus, 0.01% by mass of sulfur, residual iron and unavoidable impurities. A nitride layer was provided over the entire circumference of the ring body, and the contact width of the outer peripheral sliding surface was set to 0.2 mm.

Further, in the example, the surface pressure is set to 1.2 MPa (Example 1) 1.8 MPa (Example 2) and 2.5 MPa (Example 3), and the cylinder liner to be combined uses a low friction cylinder liner. board. In Comparative Example 1, the surface pressure was set to 2.8 MPa, which is equivalent to the conventional one, and a low friction cylinder liner was used as the cylinder to be combined. Further, the low friction cylinder liner has a recess area ratio of 50% when the stroke central region is 100, a cylinder axial length of the recess is 0.5 mm, a circumferential length is 0.5 mm, and a cylinder radial length. The one with a diameter of 2 μm was used. Further, in Comparative Example 2, the surface pressure was set to 1.8 MPa and in Comparative Example 3 to 2.5 MPa, respectively, and a normal cylinder liner was used as the cylinder liner to be combined. The roughness of the inner wall surface of the low-friction cylinder liner and the normal cylinder liner was the same.

A well-known unit evaluation device was used to measure the coefficient of friction between the oil ring and the cylinder. In this unit evaluation device, an oil ring is further attached to the top surface of the piston that moves up and down by the crank mechanism via a rod, and since this rod is also supported on the upper side, the friction coefficient of the oil ring can be measured without the influence of lateral force. Can be measured. The cylinder liner needs to match the stroke of the single evaluation device, but the oil ring of the actual engine can be used as it is. The sliding environment of the engine was simulated by adjusting the Strivec index by adjusting the temperature and sliding speed.

FIG. 5 shows a typical friction waveform obtained by this unit evaluation device. In this test, the friction coefficient at the fastest point of the piston and the Stribeck index at that point were calculated from the friction waveform obtained while changing the rotation speed of the tester, summarized as a Stribeck diagram, and used for analysis.

As shown in FIG. 5, in the case of Example 1 in which the surface pressure is set low and combined with the low friction cylinder liner, the rotation speed is low as compared with Comparative Example 1 in which the surface pressure is set high in combination with the same low friction cylinder liner. It was confirmed that the friction coefficient decreased from the region region to the high rotation region. Further, when Comparative Example 2 and Comparative Example 3 in which the surface pressure is set low and combined with the ordinary cylinder liner are compared with Example 2 and Example 3, the friction reduction effect is sufficient even when combined with the ordinary cylinder liner. It was confirmed that it could not be demonstrated.

Further, as shown in FIG. 6, when the surface pressure at a low rotation speed of 1000 rpm and the FMEP (mechanical loss) ratio are confirmed, in the case of a piston ring combined with a normal cylinder liner, the surface pressure is changed. However, in the case of a piston ring combined with a low friction cylinder liner, when the surface pressure exceeds 2.5 MPa, the friction coefficient becomes larger than that of a normal cylinder liner, and the friction reduction effect is effective. It was confirmed that it could not be demonstrated. Further, it was confirmed that when combined with a low friction cylinder liner, the friction reduction effect can be effectively exhibited by setting the surface pressure to 0.8 to 2.5 MPa.

The reason why the lower limit of the surface pressure is set to 0.8 MPa in FIG. 6 is that, as shown in FIG. 7, as a result of checking the oil consumption under normal operating conditions, when the surface pressure falls below 0.8 MPa, the oil suddenly becomes oil. Since it was confirmed that the consumption amount deteriorated, the surface pressure was set to 0.8 MPa.

Further, as shown in FIG. 8, when the contact width of the outer peripheral sliding surface of the piston ring is 0.08 to 0.40 mm, the surface pressure is 0.5 to 2.5 MPa and the followability coefficient is 0.10. It can be seen that the above can be secured, and if the surface pressure when the contact width is 0.05 mm is 0.8 to 2.5 MPa, the followability coefficient of 0.10 or more can be secured. Further, if the contact width is less than 0.02 mm, the surface pressure needs to be 0.5 to 2.5 MPa, but the design cannot be performed because the contact width is lower than the above-mentioned lower limit of the surface pressure, and the contact width is 0. Since the design range is narrow even in the case of 02 to 0.04 mm, the lower limit of the contact width is set to 0.05 mm and the upper limit is set to 0.40 mm. The description of "hit width: 0.02 mm x 2" in the legend in FIG. 8 means that the oil ring has a contact width on the upper rail and the lower rail, respectively, as shown in FIGS. 1 (a) and 1 (b). In the setting of the contact width of the entire oil ring, the contact width is doubled, so the contact width is set to "2".

Although the piston ring according to the present embodiment described above has been described when it is applied to a two-piece oil ring, it may be applied to a three-piece oil ring, a top ring, or a second ring. Further, in the piston ring according to the present embodiment described above, the case where one surface treatment layer is formed on the oil ring main body has been described, but the surface treatment layer may not be provided, and a plurality of surface treatment layers may be provided. It may be formed by laminating. It is clear from the description of the claims that the form with such changes or improvements may be included in the technical scope of the present invention.

1 Piston ring 2 Oil ring body 3 Rail 4 Sliding part protrusion 5 Pillar part 6 Coil expander 7 Oil return hole 8 Convex part 10 Surface treatment layer 11 Base material 20 Low friction cylinder liner 21 Inner wall surface 22 Concave part 23 Depth center area

Claims (2)

A piston ring combined with a low-friction cylinder liner in which a predetermined recess is formed on the inner wall surface of the cylinder liner.
The surface pressure of the piston ring is 0.8 to 2.5 MPa .
The followability coefficient of the piston ring is 0.1 to 1.5, and is
The piston ring is characterized in that the contact width of the outer peripheral sliding surface of the piston ring is 0.05 to 0.40 mm . In the piston ring according to claim 1 ,
The piston ring is a two-piece oil ring including a coil expander and an oil ring main body.

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