WO2012022012A1 - 储油活塞环 - Google Patents
储油活塞环 Download PDFInfo
- Publication number
- WO2012022012A1 WO2012022012A1 PCT/CN2010/001269 CN2010001269W WO2012022012A1 WO 2012022012 A1 WO2012022012 A1 WO 2012022012A1 CN 2010001269 W CN2010001269 W CN 2010001269W WO 2012022012 A1 WO2012022012 A1 WO 2012022012A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston ring
- ring
- oil
- wedge
- oil storage
- Prior art date
Links
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
- F16J9/20—Rings with special cross-section; Oil-scraping rings
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- 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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- 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
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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
- F16J9/16—Joint-closures obtained by stacking of rings
Definitions
- the present invention relates to a piston ring for an internal combustion engine, and more particularly to an oil storage piston ring. Background technique
- Conventional piston rings are mostly single-piece open structures, and leakage is inevitable at the openings. And the higher the working pressure, the greater the leakage, and as the wear increases, the leakage increases. Therefore, the conventional single-piece open piston ring always operates in a leak state, and a lot of power is lost due to the leakage of the opening, thereby reducing the efficiency.
- a multi-channel piston ring is used to generate a labyrinth seal to reduce leakage.
- Labyrinth seals reduce leakage but do not avoid leaks.
- the multi-channel piston ring needs to process a plurality of ring grooves, and the increase in the number of ring grooves inevitably reduces the structural strength of the piston.
- the gap between the upper plane of the piston ring and the piston ring groove is referred to as the upper side gap
- the gap between the lower plane of the piston ring and the piston ring groove is referred to as a lower side gap
- the piston ring groove and the piston ring are
- the gap between the opposite side of the working surface (the surface in contact with the cylinder wall) is called the backlash.
- the leakage of the conventional single-piece open piston ring and the two-piece combined piston ring mainly passes through three channels.
- First Leakage Channel The opening of a conventional single-piece open piston ring directly connects the high-pressure zone and the low-pressure zone to form an obvious direct leak path. The leakage of the leaky channel depends on the size of the opening, and the amount of leakage increases with the increase of wear.
- the second leakage channel when the two-piece combination piston ring is subjected to the working pressure, the opening of the upper piston ring and the upper side gap of the upper piston ring communicate the high-pressure zone with the common backlash of the two-piece piston ring, and the backlash is shared. It communicates with the opening of the lower piston ring, and the opening of the lower piston ring directly communicates with the low pressure zone, thus forming an indirect leakage channel.
- the leakage of the leakage channel depends on the size of the opening, and the leakage amount wears. Increased by the increase.
- the third leakage channel The leakage of the working surface of the piston ring, the working surface is kept sealed by the lubricating oil, and the lubrication of the uppermost ring of the multi-pass ring is the worst, so the sealing is the worst.
- the leakage begins when the working pressure exceeds the sealing capacity of the working surface.
- the leakage amount of the leakage passage depends on the thickness of the working surface and the lubrication condition, and the leakage amount is increased with the increase of the pressure.
- the combination of the two-piece piston rings cannot be completely sealed.
- the two-piece combination piston ring only solves the leakage problem of the first leakage passage, but cannot solve the leakage problem of the second leakage passage and the third leakage passage. .
- the two-piece combined piston ring is to install two piston rings in the original piston ring groove. Therefore, each piston ring is only 1/2 of the thickness of the original piston ring, which inevitably reduces the structural strength.
- the structural strength reduction will directly affect the reliability. If the total thickness of the combination of the two-piece piston rings is increased, the lubrication of the upper piston ring is further deteriorated, and the sealing effect cannot be ensured without sufficient lubrication. Therefore, sufficient lubrication is an important condition for ensuring the sealing effect.
- the piston ring produces a pumping phenomenon in the piston ring groove.
- the piston ring reciprocates with the piston, the upper side gap.
- the lubricating oil completes the lubrication and cleaning tasks, it enters the combustion chamber, and carbon is formed due to the incomplete combustion of the lubricating oil.
- the lubrication and cleaning action of the lubricating oil is beneficial, and the formation of carbon deposits is harmful.
- a conventional piston has a plurality of piston ring grooves in a limited space to cooperate with a plurality of piston rings to achieve sealing. This not only complicates the processing procedure of the conventional piston, but also reduces the strength of the piston. In addition, a plurality of piston rings are required to achieve the sealing, which results in complicated processing, reduced reliability, and increased cost of the conventional piston and piston ring. Summary of the invention
- One object of the present invention is to provide an oil storage piston ring that is capable of achieving sufficient lubrication in an application, thereby effectively preventing leakage of the working surface.
- Another object of the present invention is to provide an oil storage piston ring that is capable of forming an effective seal at the opening of the piston ring.
- an oil storage piston ring including an upper wedge ring (a ring close to a top dead center) and a lower wedge ring which are engaged with each other, the upper wedge ring and The lower wedge rings are each provided with an opening, the upper wedge ring having a first working surface in contact with the cylinder wall, the lower wedge ring having a second working surface in contact with the cylinder wall, the first working surface and the second working At least one working face of the face is provided with at least one oil reservoir.
- the oil storage tank When the piston descends (rich stage), some of the lubricating oil is stored in the oil storage tank. When the piston is ascending (the lean phase), the lubricating oil in the oil storage tank can be used for lubrication of the working surface, thus enhancing the working of the piston ring. The lubricating effect of the surface, especially the lubrication condition near the top dead center. It can be seen that the oil storage tank plays a vital role in improving the lubricity and sealing of the piston ring.
- the working surface of the upper wedge ring is provided with an oil reservoir, and the upper plane of the upper wedge ring is provided with a set connected to the oil reservoir Oil tank.
- Lubricating oil to be pumped into the combustion chamber is collected by the sump for lubrication of the working face, which reduces the consumption of lubricating oil to prevent the lubricating oil from entering the combustion chamber and generating carbon deposits.
- the center line of the oil reservoir is parallel to the upper plane of the upper wedge ring.
- an oil storage tank is respectively disposed on a middle portion of the first working surface and a middle portion of the second working surface, and if the piston ring has a sufficient thickness, the first working surface and the second working surface are evenly arranged Two or three oil storage tanks. Better lubrication can be achieved by setting two or three oil reservoirs.
- the oil sump has a substantially trapezoidal cross section, the bottom of the trapezoid is a straight line or a circular arc, the depth of the oil sump is preferably 0.5 mm to 2 mm, and the opening width of the oil sump is preferably 0.4 mm.
- the slope of the side wall of the oil sump is preferably 2° to 10°.
- the amount of oil storage can be adjusted by changing the width and depth of the oil reservoir. If the sump width is increased, the initial lubricant consumption per stroke will increase, and the lubricant may be depleted in the later stages, eventually losing lubrication. If the depth of the oil reservoir is increased and the width is reduced, the lubricant is evenly consumed and can be sufficiently lubricated in the lean phase. However, the oil storage tank should not be too deep, otherwise the dirt in the lubricating oil is not easily discharged and deposits. Therefore, the cross section of the oil storage tank is designed to be trapezoidal to facilitate the discharge of dirt.
- the oil storage piston ring of the present invention must design the width, depth and inclination of the oil reservoir according to the stroke of the piston. For longer strokes, the depth of the oil reservoir should be increased to ensure sufficient lubrication near the top dead center.
- the bottom of the oil collecting groove has 4 to 16 communicating holes communicating with the oil reservoir, and the communicating holes are evenly distributed in the oil collecting groove, and the diameter of the communicating hole is preferably 0.5 mm to 1.5 mm.
- the oil collecting groove has a U-shaped cross section, the oil collecting groove preferably has a depth of 0.5 mm to 2 mm, and the oil collecting groove has a width of preferably 0.8 mm to 3 mm.
- the upper surface of the upper wedge ring of the present invention has an oil sump which functions to collect lubricating oil for the lubrication and cleaning tasks in order to reduce the consumption of lubricating oil and prevent the pumping into the combustion chamber to form carbon deposits.
- the bottom of the oil collecting tank has a communication hole communicating with the oil storage tank, and the lubricating oil collected by the oil collecting groove is supplied to the oil storage tank through the communication hole for lubrication of the working surface, thereby further improving the lubricating effect of the working surface of the piston ring.
- the total thickness of the combination of the upper wedge ring and the lower wedge ring is 2 mm to 50 mm.
- the oil storage piston ring of the present invention designs the total thickness of the combined two-piece piston ring according to the working pressure, and the total thickness of the upper wedge ring combined with the lower wedge ring is larger than the thickness of the conventional piston ring, and the increased thickness can be Improve the sealing of the working face of the piston ring while increasing the structural strength.
- the openings of the upper wedge ring and the lower wedge ring each include an inner lap portion and an outer lap portion
- the inner lap portion includes An inner protrusion, an outer four recess, and a first joint connecting the inner protrusion and the outer four trap
- the outer overlap includes an outer protrusion, an inner ffl, and the outer protrusion and the inner ffl a second engaging portion, the first engaging portion being engaged with the second engaging portion, having a first gap between an inner protrusion of the inner overlapping portion and an inner quadrant of the outer overlapping portion
- a second between the outer four recesses of the inner overlapping portion and the outer convex portion of the outer overlapping portion a gap
- the first gap and the second gap are each preferably 0.5 mm to 3 mm in an expanded state, and the inner and outer ridges of the inner lap and the outer lap are viewed from a plan view
- the outer and inner depressions are preferably circular arc shaped.
- the gap for expansion and contraction is set so that the seal can still be achieved when the temperature changes.
- the inner protrusion and the outer ffl of the inner lap and the outer protrusion and the inner ffl of the outer lap are preferably arc-shaped, and the circular arc shape prevents stress concentration and facilitates processing.
- the first engaging portion and the second engaging portion are circular arcs concentric with the piston ring, and the arc lengths of the first engaging portion and the second engaging portion are preferably 5 Mm to 50 mm.
- the joint surface of the inner lap portion and the outer lap portion is a tightly fitting sealing surface and is a concentric circle of the piston ring.
- the piston ring When the piston ring is thermally expanded or worn, it can expand and contract freely along the joint surface (concentric circle) and always maintain a tight fit seal, thus effectively solving the leakage problem of the piston ring opening. If it is only a curved overlap or a stepped overlap, there is no guarantee that the seal will be tightly fitted for a long period of time.
- the wedge surface of the upper wedge ring is engaged with the wedge surface of the lower wedge ring, the slope of the wedge surface of the upper wedge ring with respect to the upper plane of the upper wedge ring and the wedge shape of the lower wedge ring
- the slope of the face relative to the lower plane of the lower wedge ring is 0.02° to 0.5°.
- the slope of the wedge face of the two-piece wedge ring of the present invention should not be too large.
- the sliding pressure is proportional to the slope of the wedge face and the piston speed. If the slope is large and the speed is high, the relative sliding pressure is large. Too large a slope (eg, greater than 0.5°) causes severe wear on the cylinder wall corresponding to the thick end. Therefore, the smaller the slope of the wedge surface, the better the minimum slope is 0.02°.
- the slope of the wedge surface of the invention is closely related to the engine speed.
- the high speed internal combustion engine is applied to a piston ring with a small wedge surface.
- the low speed internal combustion engine is applied to a piston ring with a slightly inclined slope. Therefore, the slope ⁇ of the wedge surface must be based on Speed design.
- the angle between the center of the opening of the upper wedge ring and the center of the piston ring and the line connecting the thickest end and the thinnest end of the upper wedge ring is 10 from the top view of the piston ring.
- the angle between the center of the opening of the lower wedge ring and the center of the piston ring and the line connecting the thickest end and the thinnest end of the lower wedge ring is 10° to 30°.
- the joint surface of the invention is kept in close contact with the outer lap by the tension of the inner lap portion, and the working surface of the piston ring should be synchronously worn in theory, if the outer lap portion wears more than the inner lap joint In the part, the close-fitting surface will have a gap and cannot guarantee a close fit. In order to keep the inner lap portion and the outer lap portion in a tightly fitted sealed state, it is desirable that the inner lap portion is slightly worn more than the outer lap portion.
- the wear of the thin end portion of the wedge ring is greater than the wear of the thick end portion of the wedge ring.
- the center of the wedge ring opening and the thickest end of the wedge surface and the plane where the thinnest end is located are offset by a certain angle, and the portion where the wear is desired is large (
- the portion of the wedge ring adjacent to the outer ffl of the inner lap is disposed at the center of symmetry of the wedge ring such that the inner lap wears slightly more than the outer lap.
- the first engaging portion of the inner lap portion abuts against the outer lap portion so as to be intimately worn, so that the tightly sealed state can be maintained at all times.
- the present invention shifts the center of the opening of the wedge ring from the center of symmetry of the wedge ring, which is an important measure for ensuring long-term close fitting and sealing of the present invention.
- the present invention designs the center of the opening of the wedge ring to be offset from the center of symmetry of the wedge ring according to the inclination of the wedge surface. If the slope of the wedge surface is large, the angle between the center of the opening of the wedge ring and the center of symmetry of the wedge ring is small.
- a piston having only one piston ring groove provided therein, the piston ring groove for providing an oil storage piston ring as described above.
- the oil storage piston ring of the present invention can be applied to a piston type internal combustion engine and a compressor.
- the piston and the piston ring of the invention can directly replace the conventional piston and the single-piece multi-channel piston ring, and have the advantages of good lubricity, strong sealing property and high reliability.
- a compressor with an extremely high working pressure can also use two oil storage piston rings.
- the present invention provides an oil storage piston ring that increases the combined total thickness of the two-piece piston ring, so that the structural strength is enhanced, and thus one to three paths are provided on the working surface of each wedge ring.
- the upper wedge ring is also provided with an oil collecting groove and a communication hole, so that the lubricity, sealing property and reliability of the piston ring are greatly improved. Therefore, the present invention can directly replace the conventional single-piece multi-channel piston ring with only one oil storage piston ring.
- the oil storage piston ring of the present invention complements the two wedge faces to form a sealed state in which the openings are opposite each other.
- the first leakage channel is closed in combination, and the second leakage channel is closed by the tension of the overlapping portion in the wedge ring, and the third leakage channel is closed by increasing the total thickness of the combination of the two-piece piston rings.
- Figure 1 is a front elevational view of an oil storage piston ring in accordance with a first embodiment of the present invention.
- FIG. 2 is a top plan view of an oil storage piston ring in accordance with a first embodiment of the present invention.
- Fig. 3 is a schematic view showing the assembly of an oil storage piston ring to a piston according to a first embodiment of the present invention.
- Figure 4 is a front elevational view of an oil storage piston ring in accordance with a second embodiment of the present invention.
- Figure 5 is a plan view of an oil storage piston ring in accordance with a second embodiment of the present invention.
- FIG. 6 is a partial cross-sectional view showing the assembly of an oil storage piston ring to a piston in accordance with a second embodiment of the present invention.
- the reference numerals used in the drawings are as follows:
- 100 oil storage piston ring; 100a: upper wedge ring; 100b: lower wedge ring; 101: first working face; 102: second working face; 103: upper plane; 104: lower plane; 105: oil reservoir; Oil groove; 107: wedge-shaped surface of upper wedge ring; 108: wedge-shaped surface of lower wedge ring; 110: inner lap joint; 110a: inner projection; 110b: first joint portion; 110c: outer recess; 111: first gap 120: outer lap; 120a: inner recess; 120b: second joint; 120c: outer protrusion; 112: second gap;
- 200 oil storage piston ring
- 200a upper wedge ring
- 200b lower wedge ring
- 201 first working face
- 202 second working face
- 203 upper plane
- 204 lower plane
- 205 oil storage tank
- 208 the wedge surface of the lower wedge ring;
- an oil storage piston ring 100 includes an upper wedge ring 100a and a lower wedge ring 100b which are joined to each other.
- the upper wedge ring 100a is provided with an opening and has a first working surface 101 in contact with the cylinder wall.
- the lower wedge ring 100b is provided with an opening and has a second working surface 102 that is in contact with the cylinder wall.
- An oil reservoir 105 is disposed in the first working surface 101, and an oil reservoir 106 is disposed in the second working surface 102.
- the upper wedge ring 100a has an upper plane 103 that contacts the piston ring groove when in use, and the lower wedge ring 100b has a lower plane 104 that contacts the piston ring groove when in use.
- the upper wedge ring 100a also has a tapered surface 107 that engages the wedge face 108 of the lower wedge ring 100b to engage the upper wedge ring 100a and the lower wedge ring 100b.
- the centerline of the sump 105 is parallel to the upper plane 103 of the upper wedge ring 100a.
- the centerline of the sump 106 is parallel to the lower plane 104 of the lower wedge ring 100b.
- the upper plane 103 of the upper wedge ring 100a is parallel to the lower plane 104 of the lower wedge ring 100b.
- FIG. 2 is a top plan view of an oil storage piston ring in accordance with a first embodiment of the present invention. As shown in Fig. 2, the opening of the upper wedge ring 100a and the opening of the lower wedge ring 100b are offset from each other.
- the opening of the upper wedge ring 100a includes an inner lap 110 and an outer lap 120
- the inner lap 110 includes an inner protrusion 110a, an outer recess 110c, and a first joint 110b connecting the inner protrusion 110a and the outer recess 110c.
- the outer lap 120 includes an inner recess 120a, an outer projection 120c, and a second engaging portion 120b connecting the inner recess 120a and the outer projection 120c.
- the first engaging portion 110b is engaged with the second engaging portion 120b to form a seal.
- the inner projection 110a and the outer ffl trap 110c of the inner lap portion 110 are preferably circularly curved, and the outer projection 120c and the inner recess 120a of the outer lap portion 120 are preferably circular arc shapes.
- the first engaging portion 110b and the second engaging portion 120b are arcs concentric with the center 0 of the piston ring. Since the diameters of the various piston rings may be large or small, the minimum diameter may be 40 mm, and the maximum diameter may be 600 mm, so the arc lengths of the first joint portion 110b and the second joint portion 120b may preferably be set at 5 mm to Within the range of 50 mm.
- first gap 111 between the inner protrusion 110a of the inner lap 110 and the inner sag 120a of the outer lap 120.
- the outer IS recess 110c of the inner lap 110 and the outer protrusion 120c of the outer lap 120 There is a second gap 112 between them.
- the first gap 111 and the second gap 112 are gaps for expansion and contraction, and the gaps are 0.5 111111 to 3 111111 at the highest temperature (expanded state).
- first engaging portion 110b and the second engaging portion 120b are designed as circular arcs concentric with the center 0 of the piston ring, and between the inner projection 110a and the inner recess 120a and between the outer recess 110c and the outer projection 120c, respectively
- a gap is provided so that the piston ring can freely expand and contract along the joint surface when it is thermally expanded or worn, and is always kept in a tightly fitted sealed state.
- the stroke of various pistons may be long or short, up to 3000 mm and the shortest may be 50 mm.
- the total thickness H of the combination of the upper wedge ring 100a and the lower wedge ring 100b is 2 mm to 50 mm.
- the total thickness H of the upper and lower wedge rings is designed according to the working pressure.
- the total thickness H after combining the upper and lower wedge rings is designed to be 1.5 to 4 times that of the original conventional single-piece open piston ring.
- the oil storage piston ring of the present embodiment since the total thickness H after the combination of the upper and lower wedge rings increases the structural strength, if the total thickness after the combination reaches twice the original piston ring, since the elastic force is too large, it is required. Appropriately reduce the width 0 of the piston ring.
- the cross section of the oil storage tanks 105, 106 is substantially trapezoidal, the depth of the oil storage tanks 105, 106 is set to 0.5 mm to 2 mm, and the opening width of the oil storage tanks 105, 106 is set to 0.4 mm to 1.8 mm, The slope of the side walls of the oil grooves 105, 106 is set to be 2 to 10 degrees.
- the bottom edge of the trapezoid may be a straight line or an arc.
- the slope ⁇ of the wedge-shaped surface 107 of the upper wedge-shaped ring 100a with respect to the upper flat surface 103 of the upper wedge-shaped ring 100a is set in the range of 0.02° to 0.5°.
- the slope ⁇ of the wedge face 108 of the lower wedge ring 100b relative to the lower plane 104 of the lower wedge ring 100b is also set in the range of 0.02° to 0.5°.
- the line connecting the center S of the opening of the upper wedge ring 100a and the center 0 of the piston ring 100 is between the line connecting the thickest end P of the upper wedge ring 100a and the thinnest end Q.
- the angle ⁇ 0 is set in the range of 10° to 30°.
- the angle between the line N of the opening of the lower wedge ring 100b and the center 0 of the piston ring and the line connecting the thickest end Q and the thinnest end P of the lower wedge ring 100b is set at 10° to 30°. Within the range of °.
- Fig. 3 is a schematic view showing the assembly of an oil storage piston ring to a piston according to a first embodiment of the present invention.
- a piston ring 100 according to a first embodiment of the present invention is disposed on a piston 600.
- An oil ring 500 is also provided at the piston 600.
- Piston ring 100 is located above oil ring 500.
- the root According to the first embodiment of the present invention, a good sealing effect can be achieved by using only one piston ring.
- the second embodiment of the present invention is a modification of the first embodiment, and features similar to those of the first embodiment are denoted by the same reference numerals, and the corresponding description will be omitted.
- the piston ring creates a pumping phenomenon in the piston ring groove.
- the second embodiment of the present invention is designed.
- Figure 4 is a front elevational view of an oil storage piston ring in accordance with a second embodiment of the present invention.
- the oil storage piston ring 200 according to the second embodiment of the present invention includes an upper wedge ring 200a and a lower wedge ring 200b which are engaged with each other.
- the upper wedge ring 200a is provided with an opening and has a first working surface 201 in contact with the cylinder wall.
- the lower wedge ring 200b is provided with an opening and has a second working surface 202 in contact with the cylinder wall.
- Two oil storage tanks 205 are disposed on the first working surface 201, and two oil storage tanks are disposed on the second working surface 202.
- the upper wedge ring 200a has an upper plane 203 that contacts the piston ring groove when in use, and the lower wedge ring 200b has a lower plane 204 that contacts the piston ring groove when in use.
- the upper wedge ring 200a also has a wedge face
- Figure 5 is a plan view of an oil storage piston ring in accordance with a second embodiment of the present invention.
- the oil collecting groove 216 provided in the upper plane 203 of the upper wedge ring 200a has a circular shape, and eight communication holes 217 are evenly arranged at the bottom of the oil collecting groove 216.
- FIG. 6 is a partial cross-sectional view of the oil storage piston ring assembled to the piston in accordance with a second embodiment of the present invention.
- two oil reservoirs 205 are provided in the upper wedge ring 200a, and an oil collecting groove 216 is disposed in the upper plane 203 of the upper wedge ring 200a.
- the communication hole 217 communicates the oil collecting groove 216 with the oil reservoir 205 provided on the upper side of the upper wedge ring 200a.
- the upper side gap 215 and the lower side gap 213 are alternately closed, so that the lubricating oil is pumped from the lower side gap 213 in the direction of the arrow into the backlash 214, and then from the backlash 214. Enter the upper backlash 215.
- the lubricating oil is collected by the oil collecting groove 216 and introduced into the upper oil reservoir 205 through the communication hole 217.
- the oil collection tank 216 collects the lubricating oil that has completed the lubrication and cleaning tasks, and is used to lubricate the working surface of the piston ring to prevent the lubricating oil from entering the combustion chamber to form carbon deposits.
- the number of the communication holes may be 4 to 16.
- the communication holes 217 are evenly distributed in the oil collecting groove 216, and the lubricating oil is introduced from the oil collecting groove 216 into the oil reservoir 205.
- These communication holes 217 preferably have a diameter of 0.5 mm to 1.5 mm.
- the oil collecting groove 216 has a substantially U-shaped cross section, the oil collecting groove 216 may have a depth of 0.5 mm to 2 mm, and the oil collecting groove 216 may have a width of 0.8 mm to 3 mm.
- Table 1 shows the gasoline engine with a pressure of 1.5 Mpa at the top dead center of the piston. The maximum speed is
- Table 2 shows the diesel engine with a pressure of 3 Mpa at the top dead center of the piston. The maximum speed is
- Table 3 shows the diesel engine with a pressure of 3.5 Mpa at the top dead center of the piston, with a maximum speed of 2500 r/min.
- the conventional design of the piston ring type includes the upper and lower wedge ring oil storage piston ring single piece open piston ring piston ring number 1 3
- the arc length of the first and second joints is 30mm
- the first and second gaps after expansion are 1.5 mm
- the life of the piston ring can be extended by more than 1 time.
- the cylinder pressure gauge indicates an increase in pressure of 0.2 Mpa.
- Table 4 shows a gasoline engine with a pressure of 2.4 Mpa at the top dead center of the piston. The maximum speed is 4000 r/min.
- the conventional design of the piston ring type of the present invention includes an oil storage piston ring of the upper and lower wedge rings. Number of ring piston rings 1 3
- Shape and size set one; trapezoid; depth is 0.8 mm, open
- the width of the mouth is 1.2 mm and the slope of the side wall is 5°
- the arc length of the first and second joints is 15mm
- the first and second gaps after expansion are 0.5 mm
- the life of the piston ring can be extended by more than 1 time.
- the cylinder pressure gauge indicates that the pressure is increased by 0.15 MPa.
- the present invention requires the inclination of the wedge faces of the two wedge rings to be ⁇ , but does not require that the openings of the two wedge rings must be maintained at 180°, allowing the openings of the two rings to have relative deviations, allowing for greater or less than 180°;
- the aim is to relax processing freedom and reduce scrap rates.
- the present invention must ensure the total thickness of the two wedge-shaped rings after design combination, but does not require the thickness of the two rings to be completely uniform, allowing one of the sheets to be slightly thinner and the other to be slightly thicker, allowing each sheet to have a thickness deviation.
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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)
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP10856011.1A EP2607675B1 (en) | 2010-08-20 | 2010-08-20 | Oil-reserving piston ring |
PCT/CN2010/001269 WO2012022012A1 (zh) | 2010-08-20 | 2010-08-20 | 储油活塞环 |
US13/817,974 US8827277B2 (en) | 2010-08-20 | 2010-08-20 | Oil-reserving piston ring |
CN201080068480.5A CN103180592B (zh) | 2010-08-20 | 2010-08-20 | 储油活塞环 |
EA201300247A EA025890B1 (ru) | 2010-08-20 | 2010-08-20 | Маслоудерживающее поршневое кольцо |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/CN2010/001269 WO2012022012A1 (zh) | 2010-08-20 | 2010-08-20 | 储油活塞环 |
Publications (1)
Publication Number | Publication Date |
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WO2012022012A1 true WO2012022012A1 (zh) | 2012-02-23 |
Family
ID=45604672
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/CN2010/001269 WO2012022012A1 (zh) | 2010-08-20 | 2010-08-20 | 储油活塞环 |
Country Status (5)
Country | Link |
---|---|
US (1) | US8827277B2 (zh) |
EP (1) | EP2607675B1 (zh) |
CN (1) | CN103180592B (zh) |
EA (1) | EA025890B1 (zh) |
WO (1) | WO2012022012A1 (zh) |
Cited By (2)
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DE102012002443A1 (de) * | 2012-02-08 | 2013-08-08 | Mahle International Gmbh | Kolbenring für einen Verbrennungsmotor |
CN105179377A (zh) * | 2015-09-21 | 2015-12-23 | 济南大学 | 一种具有防变形且储漏油的液压缸活塞密封装置 |
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CN105041504A (zh) * | 2015-07-07 | 2015-11-11 | 上海理工大学 | 微织构自润滑油环 |
CN105114199A (zh) * | 2015-08-31 | 2015-12-02 | 邓永辉 | 一种结构改良型活塞环 |
DE102017113354A1 (de) * | 2017-06-19 | 2018-12-20 | Federal-Mogul Burscheid Gmbh | Ölabstreifkolbenring |
CN108895054A (zh) * | 2018-07-27 | 2018-11-27 | 深圳市博瓦克气动技术有限公司 | 一种气缸 |
AU2020214547A1 (en) * | 2019-01-29 | 2021-09-16 | Hoerbiger Wien Gmbh | Packaging ring with relief opening |
CN113400252B (zh) * | 2021-06-18 | 2024-05-28 | 广西玉柴机器股份有限公司 | 一种高效率的活塞环装配系统 |
US11543191B1 (en) | 2021-12-14 | 2023-01-03 | Norwich Technologies, Inc. | Thermal energy storage system with parallel connected vessels |
US11519504B1 (en) * | 2021-12-14 | 2022-12-06 | Norwich Technologies, Inc. | Piston ring for floating piston in a thermal energy storage system |
US11578693B1 (en) | 2021-12-14 | 2023-02-14 | Norwich Technologies, Inc. | Thermal energy storage system including a vessel having hot and cold liquid portions separated by floating piston |
US11493281B1 (en) | 2021-12-14 | 2022-11-08 | Norwich Technologies, Inc. | Floating separator piston for a thermal energy storage system |
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- 2010-08-20 WO PCT/CN2010/001269 patent/WO2012022012A1/zh active Application Filing
- 2010-08-20 US US13/817,974 patent/US8827277B2/en not_active Expired - Fee Related
- 2010-08-20 EP EP10856011.1A patent/EP2607675B1/en not_active Not-in-force
- 2010-08-20 EA EA201300247A patent/EA025890B1/ru not_active IP Right Cessation
- 2010-08-20 CN CN201080068480.5A patent/CN103180592B/zh not_active Expired - Fee Related
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CN2260173Y (zh) * | 1996-02-14 | 1997-08-20 | 王保东 | 一种带有自动润滑及调隙装置的活塞组件 |
US7044473B1 (en) * | 1999-06-08 | 2006-05-16 | Zhihong Zhu | Piston and piston ring assembly |
CN200940521Y (zh) * | 2006-05-18 | 2007-08-29 | 刘洪文 | 单槽双环内外搭口活塞气环 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012002443A1 (de) * | 2012-02-08 | 2013-08-08 | Mahle International Gmbh | Kolbenring für einen Verbrennungsmotor |
US9279499B2 (en) | 2012-02-08 | 2016-03-08 | Mahle International Gmbh | Piston ring for an internal combustion engine |
CN105179377A (zh) * | 2015-09-21 | 2015-12-23 | 济南大学 | 一种具有防变形且储漏油的液压缸活塞密封装置 |
Also Published As
Publication number | Publication date |
---|---|
US20130147124A1 (en) | 2013-06-13 |
US8827277B2 (en) | 2014-09-09 |
CN103180592B (zh) | 2015-12-16 |
EA201300247A1 (ru) | 2013-08-30 |
EA025890B1 (ru) | 2017-02-28 |
EP2607675A1 (en) | 2013-06-26 |
EP2607675A4 (en) | 2015-02-11 |
EP2607675B1 (en) | 2017-05-10 |
CN103180592A (zh) | 2013-06-26 |
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