JP6093407B2 - piston ring - Google Patents

Description

  The present invention relates to a piston ring.

  The piston ring is mounted in a piston ring groove formed on the outer periphery of the piston. The piston ring has elasticity, and has a function of maintaining the pressure in the combustion chamber formed by the piston, the cylinder inner peripheral surface, and the cylinder head by sliding and contacting the inner peripheral surface of the cylinder with an appropriate surface pressure. .

  The piston ring has a ring shape, but a discontinuous portion called a joint portion is provided in a part of the circumferential direction. For example, a gas tight type abutment as described in Patent Document 1 is composed of a concave portion provided on one end side in the circumferential direction of the piston ring and a convex portion provided on the other end side. It is made to fit so that it may overlap.

  As described in Patent Document 2, for example, the outer peripheral surface of the piston ring is formed in a barrel shape that swells outward in the radial direction of the piston ring in order to improve sealing performance and reduce sliding resistance. The barrel center located on the outermost surface in the radial direction of the outer peripheral surface of the piston ring makes line contact with the inner peripheral surface of the cylinder.

JP-A-7-332496 JP 2006-337164 A

  During engine operation, the piston ring is heated by the combustion gas and becomes hot. At this time, since the outer peripheral side of the piston ring is in sliding contact with the relatively low temperature inner peripheral surface of the cylinder, the temperature on the inner peripheral side of the piston ring is higher than the temperature on the outer peripheral side. For this reason, the amount of thermal expansion of the piston ring is larger on the inner peripheral side than on the outer peripheral side, so that the joint portion of the piston ring is thermally deformed so as to expand outward in the radial direction of the piston ring.

Due to such thermal deformation, the contact surface pressure between the concave portion (first tongue portion) and the convex portion (second tongue portion) constituting the abutment portion and the cylinder inner peripheral surface increases, and the cylinder inner peripheral surface near the abutment portion. Cause uneven wear.
In addition, the first and second tongue portions try to expand radially outward due to thermal deformation, so that the radius of curvature of the first and second tongue portions is the radius of curvature of the cylinder inner peripheral surface. The base side of the first tongue and the second tongue is easily separated from the cylinder inner peripheral surface.

  On the other hand, in the conventional gas tight piston ring, the outer peripheral surface is formed in the same barrel shape over the entire circumference. In such a configuration, in some cases, the barrel center is biased to one of the first tongue and the second tongue in the axial direction of the piston ring, and the other has no barrel center. In such a case, the barrel center does not exist in a region where the first tongue portion and the second tongue portion do not overlap in the axial direction of the piston ring (non-overlapping region).

  As described above, when uneven wear occurs on the inner circumferential surface of the cylinder due to thermal deformation, a slight gap is formed between the base side of the first and second tongue portions that are thermally deformed and the inner circumferential surface of the cylinder. May occur. In particular, when there is no barrel center in the non-overlapping region, a gap is more likely to occur. Then, the high-temperature combustion gas blows off at a high pressure and a high speed through the slight gap generated from the combustion chamber side to the crank chamber side in the vicinity of the roots of the first tongue portion and the second tongue portion, in other words, in the non-overlapping region. . Due to the blow-off of the combustion gas, there arises a problem that the outer peripheral surface of the piston ring is damaged in the non-overlapping region.

  The present invention has been made to solve the above problems, and provides a gas tight type piston ring in which the blow-by of the combustion gas in the non-overlapping region of the first tongue and the second tongue is suppressed and the durability is improved. For the purpose.

In order to solve the above problem, a piston ring according to the present invention includes a main body extending along a circumferential direction around an axis,
A first tongue that extends from one end to the other end of the main body, and is formed on the outer side in the radial direction of the main body and on one side of the axial direction along the circumferential direction. And
A second tongue portion extending from the other end of the main body portion to the one end and forming a joint portion with the first tongue portion by fitting into the fitting groove;
The outer peripheral surface of each of the first tongue portion and the second tongue portion is formed in a barrel shape that bulges outward in the radial direction.

  According to this configuration, since the outer peripheral surface of the first tongue and the outer peripheral surface of the second tongue are each formed in a barrel shape, the outer peripheral surface of the first tongue and the outer peripheral surface of the second tongue are respectively barreled. There is a center. For this reason, a barrel center always exists even in a non-overlapping region where the first tongue and the second tongue do not overlap in the axial direction of the main body. Thereby, the sealing performance in the non-overlapping region is ensured by the barrel center of the first tongue portion or the second tongue portion, and the blow-off of the combustion gas from the combustion chamber side to the crank chamber side in the non-overlapping region is suppressed. . As a result, the durability of the piston ring is improved, and the durability of the engine including the piston ring is also improved.

In some embodiments, the outer peripheral surface of the main body is formed in a barrel shape bulging outward in the radial direction,
A first tongue barrel center positioned on the radially outermost surface of the first tongue, a body barrel center positioned on the radially outermost surface of the body, and the second tongue The second tongue barrel center located on the outermost surface in the radial direction on the outer peripheral surface of the portion extends continuously.

  According to this configuration, since the first tongue barrel center, the main body barrel center, and the second tongue barrel center continuously extend, and between the first tongue barrel center and the main body barrel center, and There is no break between the second tongue barrel center and the body barrel center, and a good sealing property is ensured.

In some embodiments, the first tongue barrel center, the main body barrel center, and the second tongue barrel center extend spirally around the axis.
According to this configuration, since the first tongue barrel center, the main body barrel center, and the second tongue barrel center extend in a spiral shape, the first tongue barrel center, the main body barrel center, and the second tongue The barrel center can be easily molded. In addition, since the barrel center is inclined with respect to the circumferential direction of the main body over the entire circumference of the piston ring, the entire circumference of the piston ring is caused by the sliding resistance with the cylinder inner surface during engine operation. Thus, a component force in the direction of rotation about the axis acts. For this reason, it is easy for the piston ring to rotate with respect to the inner peripheral surface of the cylinder, the contact surface pressure is prevented from increasing at a fixed location, and uneven wear of the piston ring and the inner peripheral surface of the cylinder is suppressed.

In some embodiments, the first tongue barrel center and the second tongue barrel center each extend in the circumferential direction,
The main body barrel center includes an intermediate portion extending in the circumferential direction, and an inclined portion extending between each of the first tongue barrel center and the second tongue barrel center and the intermediate portion.

  According to this configuration, since the main body barrel center includes the inclined portion inclined with respect to the circumferential direction, the direction in which the piston ring is rotated around the axis line by the sliding resistance with the cylinder inner circumferential surface during engine operation. The component force of acts. For this reason, it is easy for the piston ring to rotate with respect to the inner peripheral surface of the cylinder, the contact surface pressure is prevented from increasing at a fixed location, and uneven wear of the piston ring and the inner peripheral surface of the cylinder is suppressed.

In some embodiments, a region on one side in the axial direction and a region on the other side in the outer peripheral surface of the main body are each formed in a barrel shape that bulges outward in the radial direction,
The first main body barrel center located on the radially outermost side in the region on the other side is connected to the first tongue barrel center located on the outermost radial direction on the outer peripheral surface of the first tongue,
The second main body barrel center located at the radially outermost side in the region on the one side is connected to the second tongue barrel center located at the radially outermost side on the outer peripheral surface of the second tongue. .

  In this configuration, the region on one side and the region on the other side are each formed into a barrel shape in the axial direction on the outer peripheral surface of the main body portion, and the barrel portion has two barrel centers, that is, the first main body portion barrel center and A second main body barrel center is formed. The first tongue barrel center and the first body barrel center are connected to each other, and the second tongue barrel center and the second external barrel center are connected to each other. The tongue barrel center, the first main body barrel center, and the second main body barrel center can be easily molded.

Further, by providing two barrel centers over the entire circumference of the piston ring by the first tongue barrel center, the second tongue barrel center, the first body barrel center, and the second body barrel center, Good sealing performance is ensured.
Furthermore, by providing two barrel centers, the contact surface pressure between each barrel center and the cylinder inner peripheral surface is reduced and the outer peripheral surface of the piston ring is prevented from being inclined with respect to the cylinder inner peripheral surface. Uneven wear of the piston ring and the cylinder inner peripheral surface can be suppressed.

  ADVANTAGE OF THE INVENTION According to this invention, the blow-off of the combustion gas in the non-overlapping area | region of a 1st tongue part and a 2nd tongue part is suppressed, and the piston ring of the gas tight type engine which improved durability is provided.

1 is a schematic cross-sectional view of an engine to which a piston ring according to the present invention is applied. It is a perspective view showing the outline appearance of the piston ring concerning a 1st embodiment of the present invention. FIG. 3 is a perspective view schematically showing an enlarged area A in FIG. 2. (A) is a figure which shows the AA cross section of FIG. 3 with a cylinder internal peripheral surface, (B) is a figure which shows the BB cross section of FIG. 3 with a cylinder internal peripheral surface. It is a figure which expands and shows roughly the outer peripheral surface of the piston ring concerning a 1st embodiment of the present invention. It is a figure which expand | deploys and shows roughly the outer peripheral surface of the piston ring which concerns on 2nd Embodiment of this invention. It is a figure equivalent to Drawing 4 (A) of a piston ring concerning a 2nd embodiment of the present invention. It is a figure which expand | deploys and shows roughly the outer peripheral surface of the piston ring which concerns on 3rd Embodiment of this invention. (A) And (B) is a figure respectively equivalent to Drawing 4 (A) and (B) of the piston ring of the engine concerning a 3rd embodiment of the present invention.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in the embodiments are not intended to limit the scope of the present invention only to specific examples unless otherwise specified. Only.

(First embodiment)
FIG. 1 is a cross-sectional view schematically showing a configuration of an engine 1 to which a piston ring 10 according to a first embodiment of the present invention is applied. The engine 1 is, for example, a marine 2-cycle large diesel engine.
The engine 1 includes a cylinder 2, a piston 3 that is reciprocally disposed in the cylinder 2, and a cylinder head 4 that covers one end of the cylinder 2. On one end side of the cylinder 2, a combustion chamber 5 is defined by the cylinder 2, the piston 3 and the cylinder head 4.

  The engine 1 has, for example, a crosshead structure, and a piston rod 3 a extends from the opposite side of the piston 3 to the combustion chamber 5, and the piston rod 3 a penetrates the other end side of the cylinder 2. Although not shown, the opposite side of the piston rod 3a to the piston 3 is connected to a crankshaft in the crank chamber via a crosshead and a connecting rod. When the engine 1 is of a uniflow scavenging type, for example, an exhaust port is provided in the cylinder head 4 and a scavenging port (not shown) is provided on the other end side of the cylinder 2.

  The piston ring 10 is attached to the outer periphery of the piston 3. Specifically, a piston ring groove 6 is formed on the outer peripheral portion of the piston 3, and the piston ring 10 is fitted in the piston ring groove 6. The piston ring 10 is disposed coaxially with the cylinder 2 and the piston 3, and the axis line CL of the piston ring 10 coincides with the axis line of the cylinder 2 and the piston 3.

  The piston ring 10 protrudes outward from the outer peripheral surface of the piston 3 in the radial direction of the piston 3, and has an outer peripheral surface that is in sliding contact with the inner peripheral surface (cylinder inner peripheral surface) 2 a of the cylinder 2. Therefore, the gap between the cylinder inner peripheral surface 2 a and the outer peripheral surface of the piston 3 is closed by the piston ring 10, and the pressure of the combustion chamber 5 can be held by the piston ring 10.

  In this embodiment, in addition to the piston ring 10, three piston rings 60, 70 and 80 are attached to the piston 3 with an interval in the direction along the axis CL (hereinafter also referred to as the axial direction). Yes. The piston ring 10 is disposed closest to the combustion chamber 5 in the axial direction. The total number of piston rings is not limited to four, and may be three, for example.

FIG. 2 is a perspective view schematically showing the piston ring 10. As shown in FIG. 2, the piston ring 10 includes a main body portion 10 a, and a first tongue portion 12 and a second tongue portion 13 that form the joint portion 11.
The main body 10a extends along a circumferential direction around the axis CL (hereinafter also simply referred to as a circumferential direction).

FIG. 3 is a perspective view schematically showing an enlarged region A in FIG.
As shown in FIG. 3, the first tongue portion 12 extends from one end of the main body portion 10 a in the circumferential direction. The first tongue 12 has an inner peripheral piece 12a that forms the inner peripheral side of the piston ring 10, and an abutment projecting outward in the radial direction of the main body 10a from the combustion chamber 5 side in the axial direction of the inner peripheral piece 12a. Contact piece 12b. The inner peripheral piece 12a and the contact piece 12b have an L-shaped cross-sectional shape in a cross section orthogonal to the circumferential direction, and form a fitting groove 12c extending in the circumferential direction. The fitting groove 12c is located outside in the radial direction of the main body 10a, and is located on the cross head side (crank chamber) side in the axial direction.

  The second tongue portion 13 extends from the other end of the main body portion 10a in the circumferential direction. In the cross section orthogonal to the circumferential direction, the second tongue portion 13 is formed in a rectangular cross-sectional shape, and the second tongue portion 13 includes the radially outer surface of the inner peripheral piece 12a and the axial crank of the contact piece 12b. It has two side surfaces respectively facing the chamber side surface. In a state where the piston ring 10 is mounted on the piston 3, the first tongue portion 12 and the second tongue portion 13 form the gas tight type abutment portion 11 by fitting the second tongue portion 13 into the fitting groove 12c. To do. In the joint portion 11, the outer peripheral surface of the piston ring 10 is formed by the side surface 12 d of the first tongue portion 12 and the side surface 13 d of the second tongue portion 13.

  The side surface 12d of the first tongue portion 12 is located outside in the radial direction of the main body portion 10a and faces outward in the radial direction. The side surface 12d extends along the circumferential direction, and is opposed to the cylinder inner circumferential surface 2a when the piston ring 10 is mounted on the piston 3. Hereinafter, the side surface 12d of the first tongue portion 12 is also referred to as an outer peripheral surface 12d. The outer peripheral surface 12d of the first tongue 12 is a side surface of the contact piece 12b.

  Similarly, the side surface 13d of the second tongue portion 13 is located outside in the radial direction of the main body portion 10a and faces outward in the radial direction. The side surface 13d extends along the circumferential direction, and is opposed to the cylinder inner circumferential surface 2a when the piston ring 10 is mounted on the piston 3. Hereinafter, the side surface 13d of the second tongue portion 13 is also referred to as an outer peripheral surface 13d.

  In a state where the second tongue portion 13 is fitted in the fitting groove 12 c of the first tongue portion 12, the end surface 10 b on one end side of the main body portion 10 a, the tip surface 13 f of the second tongue portion 13, and the first tongue portion 12. The front end surface 12f and the end surface 10c on the other end side of the main body 10a face each other with a gap therebetween. Even if the piston ring 10 expands due to the heat of the combustion gas in the combustion chamber 5 and the piston ring 10 extends in the circumferential direction, the circumferential expansion can be absorbed by these gaps.

  By providing such a gap between the end surface 10b of the main body portion 10a and the front end surface 13f of the second tongue portion 13, the first tongue portion 12 and the second tongue portion 13 are disposed in the axial direction at the joint portion 11. A non-overlapping region S1 that does not overlap with the first tongue 12 is present in the vicinity of the root of the first tongue 12. Similarly, by providing a gap between the front end surface 12f of the first tongue 12 and the end surface 10c of the main body 10a, the first tongue 12 and the second tongue 13 are axially disposed in the joint portion 11. There is a non-overlapping region S2 that does not overlap with the root of the second tongue portion 13. On the other hand, in the abutment portion 11, there is an overlapping region S3 where the first tongue portion 12 and the second tongue portion 13 overlap in the axial direction between the two non-overlapping regions S1, S2.

FIG. 4A is a view showing the AA cross section of FIG. 3 together with the cylinder inner peripheral surface 2a. FIG. 4B is a view showing the BB cross section of FIG. 3 together with the cylinder inner peripheral surface 2a. FIG. 5 is a diagram schematically showing the outer peripheral surface of the piston ring 10 in a developed state.
As shown in FIGS. 4A and 4B, the outer peripheral surface 12d of the first tongue 12 of the piston ring 10, the outer peripheral surface 13d of the second tongue 13, and the outer peripheral surface 10d of the main body 10a. Are formed in a barrel shape bulging outward in the radial direction. Accordingly, the outer surface 12d of the first tongue 12 is formed with the first tongue barrel center BC1 positioned in the middle in the axial direction and the outermost surface in the radial direction, and the outer surface 13d of the second tongue 13 is formed. Is formed with a second tongue barrel center BC2 positioned in the middle in the axial direction and outermost in the radial direction. The outer peripheral surface 10d of the main body 10a is formed in the middle in the axial direction and in the radial direction. A main body barrel center BC3 located on the outermost side is formed.

As shown in FIG. 5, the first tongue barrel center BC1 and the second tongue barrel center BC2 each extend along the circumferential direction. On the other hand, the main body barrel center BC3 is configured by an intermediate part BC31, an inclined part BC32 on the first tongue part 12 side, and an inclined part BC33 on the second tongue part 13 side, and the intermediate part BC31 is along the circumferential direction. It extends. The inclined portion BC32 extends while being inclined with respect to the circumferential direction, and extends between the first tongue barrel center BC1 and the intermediate portion BC31. The inclined portion BC33 extends while being inclined with respect to the circumferential direction, and extends between the second tongue barrel center BC2 and the intermediate portion BC31.
Accordingly, the first tongue barrel center BC1, the main body barrel center BC3, and the second tongue barrel center BC2 extend continuously, and are extended to the outer peripheral surface of the piston ring 10 over the entire circumference. A barrel center BC is formed.

According to the above-described configuration, the outer peripheral surface 12d of the first tongue 12 and the outer peripheral surface 13d of the second tongue 13 are each formed in a barrel shape. The first tongue barrel center BC1 and the second tongue barrel center BC2 are present on the outer peripheral surface 13d of the portion.
Therefore, in the overlapping region S3 (see FIG. 3) where the first tongue 12 and the second tongue 13 overlap in the axial direction, two barrel centers are separated from each other in the axial direction, that is, the first tongue barrel. The center BC1 and the second tongue barrel center BC2 exist, and excellent sealing performance is ensured.

  The first tongue barrel center BC1 or the second tongue barrel center BC2 also exists in the non-overlapping regions S1, S2 where the first tongue 12 and the second tongue 13 do not overlap in the axial direction. . For this reason, the sealing performance in the two non-overlapping regions S1, S2 is ensured by the first tongue barrel center BC1 and the second tongue barrel center BC2, respectively, and in the non-overlapping regions S1, S2 (see FIG. 3). Blowing of combustion gas from the combustion chamber 5 side to the crank chamber side is suppressed. As a result, the durability of the piston ring 10 is improved, and the durability of the engine 1 including the piston ring 10 is also improved.

  Further, according to the above-described configuration, the first tongue barrel center BC1, the main body barrel center BC3, and the second tongue barrel center BC2 extend continuously, so the first tongue barrel center BC1 and the main body There is no break between the part barrel center BC3 and between the second tongue barrel center BC2 and the main body barrel center BC3, and good sealing performance is ensured.

  Furthermore, according to the above-described configuration, the main body barrel center BC3 includes the inclined parts BC32 and BC33 inclined with respect to the circumferential direction. Therefore, during the operation of the engine 1, the sliding resistance with the cylinder inner peripheral surface 2a is increased. The component force in the direction of rotating in the circumferential direction acts on the piston ring 10. For this reason, it is easy for the piston ring 10 to rotate with respect to the cylinder inner peripheral surface 2a, and it is prevented that the contact surface pressure increases at a certain place, and uneven wear of the piston ring 10 and the cylinder inner peripheral surface 2a is suppressed. .

  In the present embodiment, as a preferred mode, as shown in FIG. 4A, the first tongue barrel center BC1 is arranged on the outer peripheral surface 12d of the first tongue 12, that is, on the side surface of the contact piece 12b. The second tongue portion barrel center BC2 is located on the second tongue portion 13 side of the outer peripheral surface 12d of the first tongue portion 12 so as to be biased toward the second tongue portion 13 side relative to the axial center (thickness direction center). In 13d, it is located in the 1st tongue part 12 side rather than the axial direction center (thickness direction center) of the outer peripheral surface 13d of the 2nd tongue part 13 is located.

  In this configuration, the first tongue barrel center BC1 is located on the second tongue portion 13 side of the center of the first tongue portion 12 in the axial direction, so that the outer peripheral surface of the first tongue portion 12 is located. The radial clearance between 12d and the cylinder inner peripheral surface 2a can be increased on the combustion chamber 5 side in the axial direction. That is, the radial gap δ1 between the edge portion 12g of the first tongue portion 12 located on the combustion chamber 5 side in the axial direction and the cylinder inner peripheral surface 2a is the first tongue portion located on the crank chamber side in the axial direction. It can be made relatively larger than the radial gap between the 12 edge portions 12h and the cylinder inner peripheral surface 2a.

  Similarly, the outer peripheral surface 13d of the second tongue portion 13 is configured such that the second tongue barrel center BC2 is offset in the axial direction toward the first tongue portion 12 from the center of the second tongue portion 13. And the radial clearance between the cylinder inner peripheral surface 2a can be increased on the crank chamber side in the axial direction. That is, the radial gap δ2 between the edge portion 13g of the second tongue portion 13 located on the crank chamber side in the axial direction and the cylinder inner peripheral surface 2a is the second tongue portion located on the combustion chamber 5 side in the axial direction. It can be made relatively larger than the radial gap between the 13 edge portions 13h and the cylinder inner peripheral surface 2a.

  Since the piston ring 10 is fitted to the piston ring groove 6 with a gap (play) in the axial direction, when the piston 3 is moving toward the top dead center during the operation of the engine 1, No. 10 is deformed so that the radially outer side is delayed from the radially inner side by sliding resistance. Even if the outer peripheral surface 12d of the first tongue 12 is inclined with respect to the cylinder inner peripheral surface 2a due to such deformation, according to the above-described configuration, the presence of the radial gap δ1 causes the first tongue 12 to The edge portion 12g is prevented from coming into contact with the cylinder inner peripheral surface 2a.

Similarly, when the piston 3 is moving toward the bottom dead center during the operation of the engine 1, the piston ring 10 is deformed so that the radially outer side is delayed from the radially inner side due to the sliding resistance. Even if the outer peripheral surface 13d of the second tongue 13 is inclined with respect to the cylinder inner peripheral surface 2a due to such deformation, according to the above-described configuration, the presence of the radial gap δ2 causes the second tongue 13 to The edge portion 13g is prevented from coming into contact with the cylinder inner peripheral surface 2a.
As a result of preventing the edge portion 12g of the first tongue portion 12 and the edge portion 13g of the second tongue portion 13 from contacting each other, uneven wear of the piston ring 10 and the cylinder inner peripheral surface 2a is suppressed, and the piston ring The durability of 10 is further improved.

  On the other hand, in the present embodiment, as a preferred mode, as shown in FIG. 4B, the intermediate portion BC31 is the center (thickness in the axial direction) of the outer peripheral surface 10d of the main body 10a in the outer peripheral surface 10d of the main body 10a. (Center of direction). By providing the intermediate part BC31 in the center, the radial gap between the outer peripheral surface 10d of the main body 10a and the cylinder inner peripheral surface 2a can be increased on both axial sides. That is, the radial gap δ3 between the edge portion 10g of the main body portion 10a located on the combustion chamber 5 side in the axial direction and the cylinder inner peripheral surface 2a can be increased, and the main body located on the crank chamber side in the axial direction. The radial clearance δ4 between the edge portion 10h of the portion 10a and the cylinder inner peripheral surface 2a can be increased.

  For this reason, even if the outer peripheral surface 10d of the main body 10a is inclined with respect to the cylinder inner peripheral surface 2a due to the reciprocating motion of the piston 3, it is possible to prevent the edge portions 10g and 10h from coming into contact with each other. Even as a result of preventing the edge portions 10g and 10h from coming into contact with each other, uneven wear of the piston ring 10 and the cylinder inner peripheral surface 2a is suppressed, and the durability of the piston ring 10 is further improved.

(Second Embodiment)
Hereinafter, the piston ring 20 of the engine which concerns on 2nd Embodiment of this invention is demonstrated. In the following description of the embodiment, the same or similar configuration as that of the above-described embodiment is denoted by the same name or symbol, and the description is omitted or simplified.
FIG. 6 is a diagram schematically showing the outer peripheral surface of the piston ring 20 in a developed state. FIG. 7 is a view corresponding to FIG. 4A of the piston ring 20.

  As shown in FIGS. 6 and 7, the piston ring 20 includes a first tongue barrel center BC1, a body barrel center BC3, and a second tongue barrel center BC2 that spirally around the axis CL. This is different from the piston ring 10 according to the first embodiment in that it extends. In the developed view shown in FIG. 6, the barrel center BC constituted by the first tongue barrel center BC1, the main body barrel center BC3, and the second tongue barrel center BC2 extends in a straight line. The part barrel center BC1, the main body barrel center BC3, and the second tongue barrel center BC2 are each inclined at a predetermined inclination angle θ with respect to the circumferential direction.

  According to this configuration, since the barrel center BC is inclined with respect to the circumferential direction over the entire circumference of the piston ring 20, it rotates in the circumferential direction over the entire circumference with respect to the piston ring 20 during operation of the engine 1. The component force in the direction to act acts. For this reason, it is easy for the piston ring 20 to rotate with respect to the cylinder inner peripheral surface 2a, and it is prevented that the contact surface pressure increases at a certain place, and uneven wear of the piston ring 20 and the cylinder inner peripheral surface 2a is suppressed. .

  Further, according to this configuration, the first tongue barrel center BC1, the main body barrel center BC3, and the second tongue barrel center BC2 extend in a spiral shape, so that the first tongue barrel center BC1, The barrel center BC3 and the second tongue barrel center BC2 can be easily molded.

(Third embodiment)
Hereinafter, the piston ring 30 of the engine which concerns on 3rd Embodiment of this invention is demonstrated.
FIG. 8 is a diagram schematically showing the outer peripheral surface of the piston ring 30 in a developed state. 9A and 9B are views corresponding to FIGS. 4A and 4B of the piston ring 30, respectively.

  As shown in FIGS. 8 and 9A and 9B, the piston ring 30 includes a region 10d1 on the combustion chamber 5 side and a region 10d2 on the crank chamber side in the axial direction on the outer peripheral surface 10d of the main body 10a. The first main body barrel center BC5, which is formed in a barrel shape that bulges outward in the radial direction and is located on the outermost side in the radial direction in the region 10d1, is connected to the first tongue barrel center BC1 and has a diameter in the region 10d2. The second body barrel center BC6 located on the outermost side in the direction is different from the piston ring 10 of the first embodiment in that it is continuous with the second tongue barrel center BC2.

  In this configuration, two barrel centers, that is, a first main body barrel center BC5 and a second main body barrel center BC6 are formed in the main body 10a, and the first tongue barrel center BC1 and the first main body barrel center BC5 are provided. Since the second tongue barrel center BC2 and the second main body barrel center BC6 are connected to each other, the first tongue barrel center BC1, the second tongue barrel center BC2, and the first main body barrel. The center BC5 and the second main body barrel center BC6 can be easily molded.

The first tongue barrel center BC1 and the first body barrel center BC5 form one barrel center BC, and the second tongue barrel center BC2 and the second body barrel center BC6 form one barrel center BC. Thus, by providing two barrel centers BC over the entire circumference of the piston ring 30, better sealing performance is ensured.
Further, by providing two barrel centers BC, the contact surface pressure between each barrel center BC and the cylinder inner peripheral surface 2a is reduced, and the outer peripheral surface of the piston ring 30 is made to the cylinder inner peripheral surface 2a. Inclination is prevented, and uneven wear of the piston ring 30 and the cylinder inner peripheral surface 2a can be suppressed.

The present invention is not limited to the above-described first to third embodiments, and includes forms obtained by modifying these embodiments and combinations of these embodiments.
For example, in the first to third embodiments, the outer peripheral surface of the main body 10a may not be formed in a barrel shape but may be formed flat when viewed in a cross section orthogonal to the circumferential direction. That is, at least the outer peripheral surface 12d of the first tongue 12 and the outer peripheral surface 13d of the second tongue 13 need only be formed in a barrel shape.

In the first embodiment, the position of the intermediate portion BC31 in the axial direction is matched with the first tongue barrel center BC1 or the second tongue barrel center BC2, and the inclined portion BC32 or the inclined portion BC33 is omitted. Good.
Furthermore, in the third embodiment, one of the first main body barrel center BC5 and the second main body barrel center BC6 may be omitted.
Finally, the piston ring of the engine according to the present invention is suitable for a marine two-cycle large diesel engine, but it goes without saying that it may be applied to other engines.

DESCRIPTION OF SYMBOLS 1 Engine 2 Cylinder 2a Cylinder inner peripheral surface 3 Piston 3a Piston rod 4 Cylinder head 5 Combustion chamber 6 Piston ring groove | channel 10, 20, 30 Piston ring 10a Main body part 10b End surface 10c End surface 10d Outer peripheral surface 11 Joint part 12 1st tongue part 12a Inner peripheral piece 12b Abutting piece 12c Fitting groove 12d Outer peripheral surface 12f Front end surface 12g, 12h Edge portion 13 Second tongue portion 13d Outer peripheral surface 13f Front end surface 13g, 13h Edge portion BC Barrel center BC1 First tongue portion barrel center BC2 First 2 tongue section barrel center BC3 body section barrel center BC31 intermediate section BC32, BC33 inclined section BC5 first body section barrel center BC6 second body section barrel center S1, S2 non-overlapping area S3 overlapping areas δ1, δ2, δ3, δ4 Gap

Claims (6)

A main body extending along the circumferential direction around the axis;
A first tongue that extends from one end to the other end of the main body, and is formed on the outer side in the radial direction of the main body and on one side of the axial direction along the circumferential direction. And
A second tongue portion extending from the other end of the main body portion to the one end and forming a joint portion with the first tongue portion by fitting into the fitting groove;
Each outer peripheral surface of the first tongue and the second tongue is formed in a barrel shape that bulges outward in the radial direction,
On the outer peripheral surface of the first tongue, a first tongue barrel center located at the radially outermost side is formed away from the edge of the first tongue ,
A piston ring, wherein a second tongue barrel center located radially outermost is formed on the outer peripheral surface of the second tongue so as to be separated from an edge of the second tongue .
The first tongue barrel center is formed in the middle of the outer peripheral surface of the first tongue in the axial direction,
2. The piston ring according to claim 1, wherein the second tongue barrel center is formed in the middle of the outer peripheral surface of the second tongue in the axial direction.   The said 1st tongue part barrel center is formed so that it may be located in the 2nd tongue part side rather than the axial direction center of the outer peripheral surface of the said 1st tongue part, and is located. Piston ring.   The said 2nd tongue part barrel center is formed so that it may be located in the 1st tongue part side rather than the axial direction center of the outer peripheral surface of the said 2nd tongue part, and is located. Piston ring. The first tongue barrel center is formed so as to be located on the second tongue side more than the axial center of the outer peripheral surface of the first tongue,
The said 2nd tongue part barrel center is formed so that it may be located in the 1st tongue part side rather than the axial direction center of the outer peripheral surface of the said 2nd tongue part, and is located. Piston ring.   2. The region according to claim 1, wherein either the first tongue barrel center or the second tongue barrel center is formed in a region where the first tongue portion and the second tongue portion do not overlap. The piston ring as described.

Images