CN105934612A - Piston ring and engine comprising said piston ring - Google Patents
Piston ring and engine comprising said piston ring Download PDFInfo
- Publication number
- CN105934612A CN105934612A CN201480073889.4A CN201480073889A CN105934612A CN 105934612 A CN105934612 A CN 105934612A CN 201480073889 A CN201480073889 A CN 201480073889A CN 105934612 A CN105934612 A CN 105934612A
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- China
- Prior art keywords
- tongue
- piston ring
- connectivity slot
- outer peripheral
- piston
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
- F16J9/12—Details
- F16J9/14—Joint-closures
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F5/00—Piston rings, e.g. associated with piston crown
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
The purpose of the present invention is to provide: a gas-tight piston ring which suppresses combustion gas blow-by at a high pressure and a high speed in non-overlapping regions of a first tongue section and a second tongue section and has improved durability; and an engine comprising said piston ring. A piston ring (10) which comprises: a body section (10a); a first tongue section (12) which extends from one end of the body section (10a) to the other end and in which a fitting groove (12c) is formed that extends in the circumferential direction at one side in the axial direction and at the radially outer side of the body section (10a); a second tongue section (13) which extends from the other end of the body section (10a) to the one end and, together with the first tongue section (12), forms an abutment section (11) by fitting into the fitting groove (12c); and communication grooves (G1, G2) that communicate in the axial direction and are provided to the outer peripheral surface (12d) of the first tongue section (12) and/or the outer peripheral surface (13d) of the second tongue section (13), said outer peripheral surfaces being in non-overlapping regions (S1, S2) where the first tongue section (12) and the second tongue section (13) do not overlap in the direction along the axis.
Description
Technical field
The present invention relates to piston ring and there is the engine of this piston ring.
Background technology
Piston ring is installed in the piston ring groove being formed at piston outer periphery portion.Piston ring has elasticity, has following function: logical
Cross the inner peripheral surface sliding contact of the surface pressing with appropriateness and cylinder, keep by piston, cylinder inner peripheral surface and cylinder cap-shaped
Pressure in the combustion chamber become.
Piston ring has ring-shaped, but a part in the circumferential is provided with the discontinuous part being referred to as opening portion.The most special
The opening portion of such gastight manner described in profit document 1 is by being located at the recess of end side in the circumference of piston ring and being located at another
The protuberance of end side is constituted, and recess and protuberance are fitted together in an overlapping manner.
Prior art literature
Patent document
Patent document 1: Japanese Unexamined Patent Publication 7-332496 publication
Summary of the invention
The problem that invention is to be solved
In engine operation process, piston ring is burned gas heating, therefore, becomes high temperature.The now periphery of piston ring
Side and the cylinder inner peripheral surface sliding contact of relative low temperature, therefore, the temperature of the inner circumferential side of piston ring is higher than the temperature of outer circumferential side.
Therefore, the thermal expansion amount of the piston ring of inner circumferential side more than the thermal expansion amount of piston ring of outer circumferential side, the opening portion of piston ring with to
The mode thermal deformation that the footpath of piston ring bloats outward.
Due in such thermal deformation, the recess (the 1st tongue) of composition opening portion and protuberance (the 2nd tongue) and cylinder
The pressure of contact surface of side face uprises, and near opening portion, cylinder inner peripheral surface produces uneven wear.On the other hand, due to
Thermal deformation and cause the tip side of both the 1st tongue and the 2nd tongue to bloat outward to footpath, thus the 1st tongue with
And the radius of curvature that the 2nd both tongue is more than the radius of curvature of cylinder inner peripheral surface, both the 1st tongue and the 2nd tongue
Root side easily separate with cylinder inner peripheral surface.
Therefore, due to thermal deformation in the case of cylinder inner peripheral surface creates uneven wear, sometimes after thermal deformation
Small gap is produced between root side and the cylinder inner peripheral surface of both the 1st tongue and the 2nd tongue.Then, high temperature
Burning gases are not near the root of both the 1st tongue and the 2nd tongue, in other words have at the 1st tongue and the 2nd tongue
The small of this generation with high pressure and is blown over from combustion chamber side to crankshaft room side at a high speed in overlapping region (Non-overlapping Domain)
Gap.Due to blowing over of these burning gases, in Non-overlapping Domain, produce piston ring outer peripheral face sustain damage such not
Good situation.
The present invention makes to solve the problems referred to above, it is therefore intended that provide one suppression burning gases with high pressure and height
Speed blow in the Non-overlapping Domain of the 1st tongue and the 2nd tongue and improve durability gastight manner piston ring and
There is the engine of this piston ring.
For solving the means of problem
In order to solve above-mentioned problem, the piston ring of the present invention has:
Main part, circumferentially extending along around axis；
1st tongue, extends from one end of described main part to the other end, at radial outside and the described axis of described main part
The side in direction be formed along described circumferentially extending embeded slot；
2nd tongue, extends to described one end from the described other end of described main part, by be embedded in described embeded slot and with
Described 1st tongue forms opening portion together；
Connectivity slot, does not has the Non-overlapping Domain of overlap to be located at described 1st tongue at described 1st tongue and described 2nd tongue
At least one party in the outer peripheral face of outer peripheral face and described 2nd tongue, this connectivity slot connects along described axis direction.
According to this structure, by Non-overlapping Domain the most energetically in outer peripheral face and the periphery of the 2nd tongue of the 1st tongue
At least one party in face arranges connectivity slot, it is possible to make burning gases escape via connectivity slot, and the burning gases of suppression high temperature are with height
Pressure and situation about blowing in Non-overlapping Domain at a high speed.Its result, the damage in Non-overlapping Domain is suppressed, piston ring
Durability is improved.
It addition, by arranging connectivity slot, the rigidity of at least one party in the 1st tongue and the 2nd tongue reduces, piston ring
Homogenized relative to the pressure of contact surface of cylinder inner peripheral surface.As its result, piston ring, cylinder inner peripheral surface 2a are not
Uniform wear is suppressed, and the durability of piston ring is improved.
In several embodiments,
Described connectivity slot is arranged at outer peripheral face and these both sides of outer peripheral face of described 2nd tongue of described 1st tongue.
According to this structure, by outer peripheral face and these both sides of outer peripheral face of the 2nd tongue at the 1st tongue in Non-overlapping Domain
Arranging connectivity slot, the burning gases of suppression high temperature are with high speed and high pressure blowing in the two Non-overlapping Domain, it is possible to enter
One step prevents the damage of piston ring.
In several embodiments, the cross section of described connectivity slot radially is formed as semi-circular shape.
According to this structure, by the cross sectional shape with the connectivity slot on the cross section of axis vertical take-off is set to semi-circular shape, connectivity slot
The change of neighbouring cross sectional shape becomes smooth.Its result, the stress near connectivity slot is concentrated and is relaxed, it is possible to seek to live
The durability of plug ring improves.
In several embodiments, the sectional area of described connectivity slot radially along the direction of described axis from side towards another
Side increases.
According to this structure, by making the sectional area of connectivity slot increase from side towards opposite side in a direction along the axis,
Burning gases are in the case of flowing towards opposite side in side, it is possible to make the speed of the burning gases flowed out from the opposite side of connectivity slot
Degree reduces.Therefore, in the case of being configured with other piston rings near piston ring, it is possible to alleviate burning gases and other are lived
The impact pressure of plug ring, the durability of other piston rings is improved.
The engine of the present invention has any of the above-described piston ring.
According to this structure, in piston ring, burning gases can be suppressed with high pressure and at a high speed at the 1st tongue and the 2nd tongue
Blowing in Non-overlapping Domain, the durability of piston ring is improved, thus the durability of engine is also improved.
In several embodiments, be configured to, the sectional area of described connectivity slot radially along the direction of described axis from starting
The combustion chamber side of machine increases towards crankshaft room side.
According to this structure, when burning gases are intended to move towards crankshaft room's effluent from combustion chamber side, it is possible to make the bent axle from connectivity slot
The speed of the burning gases that side, room is flowed out reduces.
Therefore, in the case of the crankshaft room side at piston ring is configured with other piston rings, it is possible to alleviate burning gases and other are lived
The impact pressure of plug ring, the durability of other piston rings is improved.
Invention effect
According to the present invention, it is possible to provide a kind of suppress burning gases with high pressure and at a high speed non-at the 1st tongue and the 2nd tongue
Overlapping region is blown over and improves the piston ring of gastight manner of durability and there is the engine of this piston ring.
Accompanying drawing explanation
Fig. 1 is the sectional view of the outline of the engine of the piston ring applying the present invention.
Fig. 2 is the stereogram of the outward appearance of the outline of the piston ring of the 1st embodiment representing the present invention.
Fig. 3 is the top view being amplified by the region A of a part for cylinder with Fig. 2 and roughly representing.
Fig. 4 is the stereogram being amplified by the region A of Fig. 2 and roughly representing.
Fig. 5 is the stereogram being equivalent to Fig. 4 of the piston ring of the 2nd embodiment of the present invention.
Fig. 6 is the stereogram being equivalent to Fig. 4 of the piston ring of the 3rd embodiment of the present invention.
Fig. 7 is the stereogram being equivalent to Fig. 4 of the piston ring of the 4th embodiment of the present invention.
Detailed description of the invention
Hereinafter, embodiments of the present invention are described in detail with reference to accompanying drawings.
But, the size of the constituent parts described in embodiment, material, shape, its relative configuration etc. are as long as no spy
Specifically not recording, purport is not that the scope of the present invention is only defined in this, the most simple explanation example.
(the 1st embodiment)
Fig. 1 is cuing open of the composition of the engine 1 of the piston ring 10 roughly representing the 1st embodiment applying the present invention
View.Engine 1 is such as boats and ships 2 circulation large-sized diesel motors etc..
Engine 1 has cylinder 2, the piston 3 being configured in the way of reciprocal freedom of movement in cylinder 2 and covers cylinder
The cylinder cover 4 of one end of 2.In the end side of cylinder 2, cylinder 2, piston 3 and cylinder cover 4 mark off combustion chamber 5.
Engine 1 such as has crosshead construction, is extended with piston rod 3a from the side contrary with combustion chamber 5 of piston 3,
Piston rod 3a is through in another side of cylinder 2.The side contrary with piston 3 of piston rod 3a is by crosshead and company
Bent axle in knot bar and crankshaft room links, to this and not shown.In the case of engine 1 is such as single current scavenging form,
Cylinder cover 4 is provided with exhaust outlet, another side of cylinder 2 is provided with not shown scavenging port.
Piston ring 10 is installed on the peripheral part of piston 3.Specifically, the peripheral part at piston 3 is formed with piston ring groove 6,
Piston ring 10 is embedded in piston ring groove 6.Additionally, piston ring 10 configures coaxially with cylinder 2 and piston 3, piston ring
The axis CL of 10 is consistent with the axis of cylinder 2 and piston 3.
Piston ring 10 highlights outward at the outer peripheral face radially from piston 3 of piston 3, has and the inner peripheral surface of cylinder 2
The outer peripheral face of (cylinder inner peripheral surface) 2a sliding contact.Thus, between cylinder inner peripheral surface 2a and the outer peripheral face of piston 3 between
Gap is closed by piston ring 10, it is possible to utilize piston ring 10 to keep the pressure of combustion chamber 5.
Additionally, in the present embodiment, in addition to piston ring 10,3 piston rings 60,70 and 80 are with along axle
The mode of the upper interval in the direction (hereinafter also referred to axis direction) of line CL is installed on piston 3.Piston ring 10 is at axis
It is arranged on direction near combustion chamber 5.The sum of piston ring is not limited to 4, such as, can also be 3.
Fig. 2 is the stereogram roughly representing piston ring 10.As in figure 2 it is shown, piston ring 10 have main part 10a and
For forming the 1st tongue the 12 and the 2nd tongue 13 of opening portion 11.
Circumferentially extending along around axis CL of main part 10a.
Fig. 3 is the top view roughly representing the region A in Fig. 2, and Fig. 4 is roughly to represent that region A's in Fig. 2 is vertical
Body figure.
As shown in Figure 3 and 4, the 1st tongue 12 extends from one end of main part 10a in the circumferential.1st tongue 12
Inner circumferential sheet 12a and the combustion chamber from the axis direction of inner circumferential sheet 12a 5 with the inner circumferential side forming piston ring 10 are lateral
Contact piece 12b that the footpath of main part 10a highlights outward.Inner circumferential sheet 12a and contact piece 12b are cut at orthogonal with circumference
There is on face the cross sectional shape of L word, be formed with the embeded slot 12c circumferentially extended.Embeded slot 12c is positioned at main part 10a
Radial outside, and the cross rostral (crankshaft room side) being positioned on axis direction.
2nd tongue 13 extends from the other end of main part 10a in the circumferential.On the cross section orthogonal with circumference, the 2nd tongue
The cross sectional shape in portion 13 is formed as rectangular shape, the 2nd tongue 13 have respectively with the face of the radial outside of inner circumferential sheet 12a with
And two sides that the face of the axis direction cross rostral of contact piece 12b is relative.The shape of piston 3 it is installed at piston ring 10
Under state, by making the 2nd tongue 13 be embedded in embeded slot 12c, the 1st tongue the 12 and the 2nd tongue 13 forms gastight manner
Opening portion 11.In opening portion 11, the outer peripheral face of piston ring 10 is by the side 12d of the 1st tongue 12 and the 2nd tongue
The side 13d in portion 13 is formed.Additionally, the side 12d of the 1st tongue 12 is the side of contact piece 12b.
The side 12d of the 1st tongue 12 main part 10a be radially positioned at outside, be radially oriented foreign side.Further, side
Face 12d circumferentially extends, when piston ring 10 is installed on piston 3, and side 12d and cylinder inner peripheral surface 2a phase
Right.Hereinafter, also the side 12d of the 1st tongue 12 is referred to as outer peripheral face 12d.Additionally, the outer peripheral face 12d of the 1st tongue 12
It it is the side of contact piece 12b.
Similarly, the side 13d of the 2nd tongue 13 main part 10a be radially positioned at outside, be radially oriented foreign side.
Further, side 13d circumferentially extends, when piston ring 10 is installed on piston 3, in side 13d and cylinder
Side face 2a is relative.Hereinafter, also the side 13d of the 2nd tongue 13 is referred to as outer peripheral face 13d.
When the 2nd tongue 13 is fitted to the embeded slot 12c of the 1st tongue 12, the end of the end side of main part 10a
The top end face 13f of face 10b and the 2nd tongue 13 separates relative with gap, the top end face 12f of the 1st tongue 12 and main part
The end face 10c of another side of 10a separates the most relative.Even if piston ring 10 is due to the warm of the burning gases of combustion chamber 5
Measuring and expand, piston ring 10 circumferentially extends, it is also possible to utilize these gaps to absorb the elongation of this circumference.
By such gap being located between the end face 10b of main part 10a and the top end face 13f of the 2nd tongue 13,
At opening portion 11, the 1st tongue the 12 and the 2nd tongue 13 is not present in along Non-overlapping Domain S1 that axis direction is overlapping
Near the root of the 1st tongue 12.The outer peripheral face 12d of the 1st tongue 12 in this Non-overlapping Domain S1, i.e. contact piece
The outer peripheral face of 12b is formed with connectivity slot G1.Connectivity slot G1 extends along axis direction, in the axial direction at the 1st tongue
The both-side opening of contact piece 12b of 12.Thus, side, combustion chamber 5 and crankshaft room side are connected by connectivity slot G1 in the axial direction
Logical.It addition, connectivity slot G1 is radially toward foreign side's opening.
In the operation process of engine 1, piston ring 10 is burned gas heating, therefore becomes high temperature.Now piston ring
The outer circumferential side of 10 and the cylinder inner peripheral surface 2a sliding contact of relative low temperature, therefore, the temperature of the inner circumferential side of piston ring 10 is higher than
The temperature of outer circumferential side.Therefore, the thermal expansion amount of the piston ring 10 of inner circumferential side is more than the thermal expansion amount of the piston ring 10 of outer circumferential side,
Opening portion 11 thermal deformation in the way of the footpath to piston ring 10 bloats outward of piston ring 10.
Due to such thermal deformation, constitute the 1st tongue the 12 and the 2nd tongue 13 and the cylinder inner peripheral surface 2a of opening portion 11
Pressure of contact surface uprise, near opening portion 11, cylinder inner peripheral surface 2a produces uneven wear.On the other hand, by
In thermal deformation, the tip side of both the 1st tongue the 12 and the 2nd tongues 13 is intended to bloat outward to footpath, thus the 1st tongue
The radius of curvature of both portion the 12 and the 2nd tongues 13 more than the radius of curvature of cylinder inner peripheral surface 2a, the 1st tongue 12 with
And the root side that the 2nd both tongue 13 easily separates with cylinder inner peripheral surface 2a.
Therefore, due to thermal deformation in the case of cylinder inner peripheral surface 2a creates uneven wear, sometimes in thermal deformation
After both the 1st tongue the 12 and the 2nd tongues 13 root side and cylinder inner peripheral surface 2a between produce small gap delta 1,
δ 2 (with reference to Fig. 3).In the case of being not provided with connectivity slot G1, the burning gases of high temperature are attached at the root of the 1st tongue 12
Closely, in other words the 1st tongue the 12 and the 2nd tongue 13 do not have overlap Non-overlapping Domain S1 in from combustion chamber 5 lateral ten
This small gap delta 1 created with high pressure and is blown at a high speed in prefix side.Due to blowing over of these burning gases, non-overlapped
In the S1 of region, the outer peripheral face producing piston ring 10 sustains damage such unfavorable condition.
In contrast, according to above-mentioned structure, by Non-overlapping Domain S1 the most energetically outside the 1st tongue 12
Side face 12d arranges connectivity slot G1, it is possible to make burning gases escape via connectivity slot G1, can suppress the burning gases of high temperature with
High pressure and high speed are blown in Non-overlapping Domain S1.Its result, the damage in Non-overlapping Domain S1 is suppressed, piston
The durability of ring 10 is improved.
It addition, by arranging connectivity slot G1, the rigidity of the 1st tongue 12 reduces, and piston ring 10 is relative to cylinder inner peripheral surface
The pressure of contact surface of 2a is homogenized.As its result, piston ring 10, the uneven wear of cylinder inner peripheral surface 2a are subject to
Suppression, the durability of piston ring 10 is improved.
And, in the present embodiment, the cross sectional shape of the connectivity slot G1 on the cross section orthogonal with axis CL is formed as semicircle
Shape.According to this structure, by the cross sectional shape of the connectivity slot G1 on the cross section orthogonal with axis CL is set to semi-circular shape,
The change of the cross sectional shape near connectivity slot G1 becomes smooth.Its result, the stress concentration near connectivity slot G1 is relaxed,
The durability that can seek piston ring 10 improves.
(the 2nd embodiment)
Hereinafter, the piston ring 20 of the 2nd embodiment of the present invention is illustrated.Additionally, at following embodiment
In explanation, for before it is stated that embodiment same or similar constitute the identical title of mark or symbol, omission or
Simplify explanation.
Fig. 5 is a stereogram part for piston ring 20 being amplified and roughly representing.Difference with the 1st embodiment
Being, piston ring 20 does not has the root of the 2nd tongue 13 of overlap at the 1st tongue the 12 and the 2nd tongue 13 along axis direction
It is formed with connectivity slot G2 in Non-overlapping Domain S2 near portion and at the outer peripheral face 13d of the 2nd tongue 13.
Connectivity slot G2 extends along axis direction, in the axial direction and at the both-side opening of the 2nd tongue 13.It addition, even
Groove G2 at main part 10a axially towards opening outward.
According to this structure, by arranging the most energetically in Non-overlapping Domain S2 and at the outer peripheral face 13d of the 2nd tongue 13
Connectivity slot G2, it is possible to make burning gases escape via connectivity slot G2, can suppress the burning gases of high temperature with high pressure and high speed
Non-overlapping Domain S2 is blown over.Its result, the damage in Non-overlapping Domain S2 is suppressed, piston ring 20 durable
Property is improved.
It addition, by arranging connectivity slot G2, the rigidity of the 2nd tongue 13 reduces, and piston ring 20 is relative to cylinder inner peripheral surface
The pressure of contact surface of 2a is homogenized.As its result, piston ring 20, the uneven wear of cylinder inner peripheral surface 2a are subject to
Suppression, the durability of piston ring 20 is improved.
And, in the present embodiment, the cross sectional shape of the connectivity slot G2 on the cross section orthogonal with axis CL is formed as semicircle
Shape.According to this structure, by the cross sectional shape of the connectivity slot G2 on the cross section orthogonal with axis CL is set to semi-circular shape,
The change of the cross sectional shape near connectivity slot G2 becomes smooth.Its result, the stress concentration near connectivity slot G2 is relaxed,
The durability that can seek piston ring 20 improves.
(the 3rd embodiment)
Hereinafter, the piston ring 30 of the 3rd embodiment of the present invention is illustrated.
Fig. 6 is a stereogram part for piston ring 30 being amplified and roughly representing.With the 1st embodiment and the 2nd
The difference of embodiment is, piston ring 30 does not has overlap at the 1st tongue the 12 and the 2nd tongue 13 along axis direction
Non-overlapping Domain S1, in S2 and in the outer peripheral face 12d of the 1st tongue 12 and the outer peripheral face 13d shape of the 2nd tongue 13
Become to have connectivity slot G1, G2.
According to this structure, by Non-overlapping Domain S1, S2 and at the outer peripheral face 12d of the 1st tongue 12 and the 2nd tongue
These both sides of outer peripheral face 13d in portion 13 arrange connectivity slot G1, G2, and the burning gases of high temperature can be suppressed to exist with high speed and high pressure
The two Non-overlapping Domain S1, S2 blow over, it is possible to prevent the damage of piston ring 30 further.
(the 4th embodiment)
Hereinafter, the piston ring 40 of the 4th embodiment of the present invention is illustrated.
Fig. 7 is a stereogram part for piston ring 40 being amplified and roughly representing.In the present embodiment, such as Fig. 7
Shown in, the sectional area (connectivity slot radially of main part 10a of connectivity slot G3, G4 on the cross section orthogonal with axis CL
The sectional area of G3, G4) increase from side towards opposite side on the direction along axis CL.
Additionally, connectivity slot G3, G4 extend along axis direction, the most respectively in the contact piece of the 1st tongue 12
12b and the both-side opening of the 2nd tongue 13.It addition, connectivity slot G3, G4 at main part 10a axially towards outward
Opening.
According to this structure, by make the sectional area of connectivity slot G3, G4 on the direction along axis CL from side towards another
Side increases, at burning gases in the case of flowing towards opposite side in side, it is possible to make the opposite side from connectivity slot G3, G4
The speed of the burning gases flowed out reduces.Such as, by making the sectional area of connectivity slot G3, G4 from side, combustion chamber 5 towards ten
Prefix side (crankshaft room) increases, at fuel in the case of side, combustion chamber 5 is dynamic towards crankshaft room's effluent, it is possible to make from connection
The speed of the burning gases that the crosshead side of groove G3, G4 is flowed out reduces.
Therefore, as shown in Figure 1 near piston ring 10, such as crankshaft room side be configured with another piston ring 60
In the case of, it is possible to alleviating the burning gases impact pressure to another piston ring 60, the durability of another piston ring 60 is carried
High.
The present invention is not limited to the 1st above-mentioned embodiment～the 4th embodiment, also includes applying these embodiments
The form of deformation, combine the form of these embodiments.
Such as, as the cross sectional shape of connectivity slot G1, G2, preferably semi-circular shape, it is also possible to be V-shape, rectangle shape
Shape etc..
It addition, the piston ring of the present invention is suitable to boats and ships 2 circulation large-sized diesel motors, but can certainly be applied to other
Engine etc..
Symbol description
1 ... engine, 2 ... cylinder, 2a ... cylinder inner peripheral surface, 3 ... piston, 3a ... piston rod, 4 ... cylinder cover, 5 ... combustion
Burning room, 6 ... piston ring groove, 10 ... piston ring, 10a ... main part, 10b ... end face, 10c ... end face, 11 ... opening portion,
12 ... the 1st tongue, 12a ... inner circumferential sheet, 12b ... contact piece, 12c ... embeded slot, 12d ... outer peripheral face, 12f ... top end face,
13 ... the 2nd tongue, 13d ... outer peripheral face, 13f ... top end face, G1, G2, G3, G4 ... connectivity slot, S1, S2 ... non-overlapped
Region, δ 1, δ 2 ... gap.
Claims (6)
1. a piston ring, it is characterised in that have:
Main part, circumferentially extending along around axis；
1st tongue, extends from one end of described main part to the other end, at radial outside and the described axis of described main part
The side in direction be formed along described circumferentially extending embeded slot；
2nd tongue, extends to described one end from the described other end of described main part, by be embedded in described embeded slot and with
Described 1st tongue forms opening portion together；And
Connectivity slot, does not has the Non-overlapping Domain of overlap to be located at described 1st tongue at described 1st tongue and described 2nd tongue
At least one party in the outer peripheral face of outer peripheral face and described 2nd tongue, this connectivity slot connects along the direction of described axis.
Piston ring the most according to claim 1, it is characterised in that
Described connectivity slot is located at outer peripheral face and these both sides of outer peripheral face of described 2nd tongue of described 1st tongue.
Piston ring the most according to claim 1 and 2, it is characterised in that
The cross section of described connectivity slot radially is semi-circular shape.
4. according to the piston ring according to any one of claims 1 to 3, it is characterised in that
The sectional area of described connectivity slot radially increases along the direction of described axis from side towards opposite side.
5. an engine, it is characterised in that there is the piston ring according to any one of Claims 1 to 4.
Engine the most according to claim 5, it is characterised in that
The sectional area of described described connectivity slot radially increases towards crankshaft room side along the direction of described axis from combustion chamber side.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-033803 | 2014-02-25 | ||
| JP2014033803A JP6062382B2 (en) | 2014-02-25 | 2014-02-25 | Piston ring and engine including the piston ring |
| PCT/JP2014/071441 WO2015129074A1 (en) | 2014-02-25 | 2014-08-14 | Piston ring and engine comprising said piston ring |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105934612A true CN105934612A (en) | 2016-09-07 |
Family
ID=54008424
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480073889.4A Pending CN105934612A (en) | 2014-02-25 | 2014-08-14 | Piston ring and engine comprising said piston ring |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6062382B2 (en) |
| KR (1) | KR101823807B1 (en) |
| CN (1) | CN105934612A (en) |
| WO (1) | WO2015129074A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3889472B1 (en) * | 2020-04-02 | 2024-06-19 | Winterthur Gas & Diesel Ltd. | Piston ring package |
| JP7307778B2 (en) * | 2021-09-30 | 2023-07-12 | Ｔｐｒ株式会社 | Combination of piston rings and internal combustion engine |
| DK181183B1 (en) * | 2022-03-02 | 2023-04-12 | Man Energy Solutions Filial Af Man Energy Solutions Se Tyskland | Piston ring for a large two-stroke turbo-charged uniflow-scavenged crosshead internal combustion engine |
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| CN1294370C (en) * | 2001-03-08 | 2007-01-10 | 曼B与W狄赛尔公司 | Reciprocating piston engine |
| CN201065795Y (en) * | 2007-08-08 | 2008-05-28 | 宋长英 | Piston ring |
| CN103052833A (en) * | 2011-02-28 | 2013-04-17 | 三菱重工业株式会社 | Piston ring |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5566543U (en) * | 1978-11-01 | 1980-05-08 | ||
| JPS55166947U (en) * | 1979-05-18 | 1980-12-01 | ||
| JPH07332496A (en) | 1994-06-08 | 1995-12-22 | Toyota Motor Corp | Piston ring for internal combustion engine |
| JP2001241357A (en) | 2000-02-28 | 2001-09-07 | Nippon Piston Ring Co Ltd | Combination of piston ring and piston using the same |
-
2014
- 2014-02-25 JP JP2014033803A patent/JP6062382B2/en active Active
- 2014-08-14 CN CN201480073889.4A patent/CN105934612A/en active Pending
- 2014-08-14 WO PCT/JP2014/071441 patent/WO2015129074A1/en active Application Filing
- 2014-08-14 KR KR1020167014342A patent/KR101823807B1/en active IP Right Grant
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1494140A (en) * | 1921-07-12 | 1924-05-13 | Frank E Small | Piston packing |
| JPS566957A (en) * | 1979-06-01 | 1981-01-24 | Cattaneo Leopoldo | Piston ring |
| JPH0419951U (en) * | 1990-06-12 | 1992-02-19 | ||
| US5934680A (en) * | 1995-05-31 | 1999-08-10 | Ntn Corporation | Split resin seal ring with chamfered end connection structures |
| US5779243A (en) * | 1996-11-21 | 1998-07-14 | Delaware Capital Formation, Inc. | Piston ring set for reciprocating engines |
| CN1294370C (en) * | 2001-03-08 | 2007-01-10 | 曼B与W狄赛尔公司 | Reciprocating piston engine |
| CN2523973Y (en) * | 2001-12-26 | 2002-12-04 | 杨武成 | Mono-directional sealed piston ring |
| CN201065795Y (en) * | 2007-08-08 | 2008-05-28 | 宋长英 | Piston ring |
| CN103052833A (en) * | 2011-02-28 | 2013-04-17 | 三菱重工业株式会社 | Piston ring |
Also Published As
| Publication number | Publication date |
|---|---|
| KR101823807B1 (en) | 2018-01-30 |
| JP6062382B2 (en) | 2017-01-18 |
| JP2015158247A (en) | 2015-09-03 |
| KR20160079066A (en) | 2016-07-05 |
| WO2015129074A1 (en) | 2015-09-03 |
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