CN103452691A - Anti-blow-by piston ring set for automobile supercharged engine - Google Patents
Anti-blow-by piston ring set for automobile supercharged engine Download PDFInfo
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- CN103452691A CN103452691A CN2012101719338A CN201210171933A CN103452691A CN 103452691 A CN103452691 A CN 103452691A CN 2012101719338 A CN2012101719338 A CN 2012101719338A CN 201210171933 A CN201210171933 A CN 201210171933A CN 103452691 A CN103452691 A CN 103452691A
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Abstract
The invention relates to an engine part, in particular to an anti-blow-by piston ring set for an automobile supercharged engine. The anti-blow-by piston ring set comprises a first gas ring, a second gas ring and a combined oil ring which are matched on a piston from top to bottom. The anti-blow-by piston ring set is characterized in that a first closed gap of the first gas ring is in a range of 0.13mm to 0.17mm, a second closed gap of the second gas ring is in a range of 0.3mm to 0.45mm, and the combined oil ring is a two-sheet combined oil ring. According to the anti-blow-by piston ring set, the closed gaps of the first gas ring and the second gas ring are reduced, and the second gas ring closed gap is 1.80 to 2.45 of the first gas ring closed gap, so that the blow-by amount can be reduced by 10% to 30%; besides, a distortion angle of the first gas ring is omitted, so that the blow-by amount can be reduced by 8% to 17%; the first gas ring is subjected to nitrogen treatment and physical vapor deposition (PVD) treatment successively to increase the abrasion resistance, and accordingly, the service life is prolonged; by the aid of the two-sheet combined oil ring, the following performance can be increased, and the blow-by amount is effectively controlled.
Description
Technical field
The present invention relates to engine components, particularly a kind of anti-blowby piston ring group of automobile turbo engine.
Background technique
Piston ring is the core component of fuel engine inside, and it completes the sealing of fuel oil-gas together with cylinder cap, piston, cylinder wall etc.The effect of piston ring comprises sealing, regulates machine oil control oil, heat conduction, four effects of guiding.Wherein sealing refers to the sealing combustion gas, does not allow the gas of firing chamber drain to crankcase, and the leakage rate of gas is controlled to bottom line, improves the thermal efficiency.The 0.2%-1% that when general petrol engine runs well, the piston ring air leakage is air inflow, and supercharged engine is very large due to compression and combustion pressure, its air leakage is larger.Although utilize the gap between piston ring packing cylinder wall and piston, but under the state of piston compression air, the mixed gas of trace leaks into crankcase inside by the end-gaps of the gap between piston ring and cylinder, piston ring and piston ring groove and piston ring, top cover is delivered in gas leakage to crankcase scavenged, both affected the compression finishing temperature, make the cylinder charge decrease in efficiency, affect again engine combustion process, when gas leakage simultaneously is stranded in crankcase inside, the crank internal pressure raises, and the leakage of oil in each hermetic unit increases.Owing to containing the solid matter such as dust, carbon black and water sulfuric acid, organic acid, nitrogen oxide etc. in gas leakage, not only can accelerate the crankcase parts depreciation, and can make the machine oil blackening thinning, make machine oil rotten, produce the viscose glue material, stop up oil leab and snap ring etc., wherein moisture content also can cause the part corrosion.Based on above reason, cause gas leakage through oil separator, now oil is recovered, intake manifold is delivered in the gas leakage that oil has separated again, together is supplied to firing chamber with air inlet and fires, or being discharged in atmosphere, cause starting difficulty and smoking of the exhaust, the problems such as contaminated air.When at motor during at high-load operation, thereby so-called high-temperature fuel gas makes machine oil or fuel oil sintering make piston ring stuck, causes ring bad with the cylinder wall laminating, heat transfer is slowed down, piston heat load increases, and causes the piston Partial ablation, accelerates piston ring, cylinder sleeve and other parts wears.Leak gas larger, do not have the gas greasy dirt of burning larger to the infringement of casing wall, cylinder pressure is also lower, causes power performance to descend, and fuel oil consumption and engine oil consumption increase, and shorten service life of aeroengine.
In traditional supercharged engine piston ring group, piston ring gap is larger, and when piston carries out compression stroke, pressurized gas just can be run away from the opened gap of piston ring.Do not consider the relation of piston ring group second gas ring and top compression ring opened gap simultaneously, if ratio is excessive, cause circulation area to increase, increase the blowby amount; If ratio is too small, will cause the lower side pressure of top compression ring to be greater than side pressure, thereby make it in state of suspension, equally also increase the blowby amount.Because top compression ring is that cast iron chromium plating is made, and its tangential elastic force is less, and along with the lengthening of engine running time, piston ring and cylinder all can wear and tear, and like this, the gap of piston ring and cylinder sleeve just can be strengthened gradually, and the blowby phenomenon will be more serious.Second gas ring is to adopt the cast iron ring to be processed into outer cone, and its port openings place design for open type, has increased the blowby circulation path, causes the increase of blowby amount; And combined oil ring is the combined oil ring that adopts three pieces type, its tracing ability is poor, is unfavorable for anti-blowby, and its cylindrical chromium plating, and environmental pollution is serious and fabricating cost is high.
Summary of the invention
The anti-blowby piston ring group that the purpose of this invention is to provide a kind of automobile turbo engine, the closed gap of the closed gap of its top compression ring and second gas ring is less, and ratio control in closed gap is strict, can reduce the blowby amount; Rational in infrastructure, can reduce the blowby circulation path; Wear resistance is good, and working life is longer.
To achieve the object of the present invention, by the following technical solutions:
The anti-blowby piston ring group of a kind of automobile turbo engine of the present invention, comprise top compression ring, second gas ring and combined oil ring, and be engaged in from top to bottom on piston; Described top compression ring coordinates with the top compression ring annular groove on piston, and described second gas ring coordinates with the second gas ring annular groove on piston, and described combined oil ring coordinates with the combined oil ring annular groove on piston; It is characterized in that: the first closed gap of described top compression ring is 0.13-0.17mm, and the second closed gap of described second gas ring is 0.3-0.45mm; Described combined oil ring is the two-piece type combined oil ring.Reduce closed gap to reduce circulation area, and then reduce the blowby amount.
Further, the ratio in the first closed gap of the closed gap of described second gas ring second and described top compression ring is 1.75-2.25.According to test situation, for supercharged engine, when the closed gap of second gas ring is 1.80-2.45 times of the closed gap of top compression ring, its air leakage minimum, meet supercharged engine air leakage standard.
Further, described top compression ring adopts shaping steel wire to make, whole nitriding treatment, exterior arc surface is coated with the PVD(physical vapor deposition) coating.Top compression ring remakes to foreign round PVD coating and processes on the basis of nitriding treatment, to improve its wear resistance, thereby guarantees that piston ring, after using the long period, appoints higher matching gap is so arranged between piston ring excircle and cylinder sleeve.
Further, the open end of described second gas ring is enclosed construction, to reduce the blowby circulation path of circumferencial direction; The cylindrical top of described second gas ring is the conical surface, and section is nose type structure; And process through phosphatization, to increase its tangential elastic force.
Further, described combined oil ring is comprised of spiral pushing out ring oil ring support spring and spiral pushing out ring oil ring ring body.Traditional three pieces type combined oil ring after using a period of time owing to scraping pad wear, cause itself and cylinder sleeve contact to reduce, and the spiral pushing out ring oil ring support spring of two-piece type combined oil ring can outwards open, guarantee that spiral pushing out ring oil ring ring body contacts with cylinder sleeve all the time, there is better tracing ability, therefore can reduce the blowby amount.
The present invention compared with prior art, has following advantage:
1) top compression ring of the present invention on the basis of nitriding treatment to foreign round cambered surface do again PVD coating and process, and traditional first ring is cast iron chromium plating processing, thereby guaranteed the wear resistance of top compression ring, and then guaranteed that piston ring is being used after the long period between exterior arc surface and cylinder sleeve still no-float;
2) the present invention is optimized design to top compression ring and the closed gap of second gas ring, wherein the closed gap of top compression ring changes 0.13-0.17mm into by 0.15-0.30mm, the closed gap of second gas ring changes 0.3-0.45mm into by 0.25-0.40mm, and its blowby amount can reduce 10%-30%.
When 3) the closed gap of second gas ring of the present invention is 1.75-2.25 times of the closed gap of top compression ring, its air leakage minimum.If ratio is excessive, cause circulation area to increase, increase the blowby amount; If ratio is too small, will cause the lower side pressure of top compression ring to be greater than side pressure, thereby make it in state of suspension, equally also increase the blowby amount.
4) top compression ring of the present invention has been cancelled twist angle, can effectively control like this and because the pressure difference up and down of top compression ring is excessive, cause it that zitterbewegung occurs when top dead center commutates, and can reduce blowby amount 8%-10%.
5) second gas ring of the present invention adopts the structural type of end-enclosed formula, by the sealing of the air-flow of blowby to two ring, thereby reduces the blowby amount.
6) top compression ring of the present invention and second gas ring increase tangential elastic force; guarantee that piston ring still has higher tangential elastic force between use long period back piston ring cylindrical and cylinder sleeve; thereby guaranteed less matching gap, can reduce the blowby amount and reach 17%.
7) combined oil ring of the present invention adopts the two-piece type combined oil ring, traditional is two scraping blades and a three pieces type combined oil ring that support spring forms, compared with traditional three pieces type combined oil ring, after using a period of time owing to scraping pad wear, cause itself and cylinder sleeve contact to reduce, and spiral pushing out ring oil ring support spring can outwards open, guarantee that spiral pushing out ring oil ring ring body contacts with cylinder sleeve all the time, therefore can reduce the blowby amount.
The accompanying drawing explanation
Fig. 1 is that exploded perspective view is joined in the piston ring assembling;
Fig. 2 is the structural representation of first ring of the present invention;
Fig. 3 is the A-A schematic cross-section of Fig. 2;
Fig. 4 is the schematic cross-section of top compression ring corresponding site before improving;
Fig. 5 is the structural representation of second gas ring of the present invention;
Fig. 6 is the B-B schematic cross-section of Fig. 5;
Fig. 7 is second ring open end blowby circulation schematic diagram before improving;
Fig. 8 is second ring open end blowby circulation schematic diagram of the present invention;
Fig. 9 is the structural representation of combined oil ring of the present invention;
Figure 10 is the C-C cross section enlarged diagram of Fig. 9;
Figure 11 is combined oil ring structural representation before improving;
Figure 12 is the plotted curve of the closed gap under different rotating speeds of the present invention's one example on the impact of blowby amount;
Figure 13 is the plotted curve that the impact of unmatchful blowby amount is arranged of twist angle under different rotating speeds of the present invention's one example;
Figure 14 is the plotted curve of tangential elastic force on the impact of blowby amount under different rotating speeds of the present invention's one example;
Figure 15 is the first ring of the present invention's one example and the plotted curve that the second closed gap of ring relation affects the blowby amount.
Embodiment
Below in conjunction with accompanying drawing, the present invention is further illustrated.
Referring to Fig. 1, Fig. 2, Fig. 3, Fig. 5, Fig. 6, Fig. 8, Fig. 9 and Figure 10, the anti-blowby piston ring group of a kind of automobile turbo engine of the present invention, comprise top compression ring 1, second gas ring 2 and combined oil ring 3, and be engaged in from top to bottom on piston 4; Top compression ring coordinates with the top compression ring annular groove 41 on piston, and second gas ring coordinates with the second gas ring annular groove 42 on piston, and combined oil ring coordinates with the combined oil ring annular groove 43 on piston;
The first closed gap 11 of described top compression ring 1 is 0.17mm, and the second closed gap 21 of described second gas ring 2 is 0.3mm; And the closed gap 21 of second gas ring second is 1.77 air leakage minimums with the ratio in the first closed gap 21 of top compression ring, can meet supercharged engine air leakage standard.
Described top compression ring 1 adopts shaping steel wire (the material trade mark: 6Cr13Mo) make, whole nitriding treatment, exterior arc surface is coated with the PVD(physical vapor deposition) coating 13, its layer thickness is 0.01mm-0.03mm, make surface hardness reach 900-1500HV, can obviously increase wear resistance, the assurance piston ring is appointed higher matching gap is so arranged between use long period back piston ring cylindrical and cylinder sleeve; Top compression ring remakes to foreign round PVD coating and processes on the basis of nitriding treatment, to improve its wear resistance, thereby guarantees that piston ring, after using the long period, appoints higher matching gap is so arranged between piston ring excircle and cylinder sleeve.
The open end of described second gas ring 2 is enclosed construction, to reduce the blowby circulation path of circumferencial direction; The cylindrical top of described second gas ring 2 is the conical surface 22, and section is nose type structure; And process through phosphatization, to increase its tangential elastic force.
Described combined oil ring 3 is comprised of spiral pushing out ring oil ring support spring 31 and spiral pushing out ring oil ring ring body 32, because spiral pushing out ring oil ring support spring can outwards open, thereby guaranteed that spiral pushing out ring oil ring ring body contacts with cylinder sleeve all the time, there is better tracing ability, therefore can reduce the blowby amount.
Referring to Fig. 4, top compression ring 50 before shown improvement, its opened gap is 0.15mm-0.30mm, with twist angle 1a.And top compression ring of the present invention has been cancelled twist angle, so can effectively control, because the pressure difference up and down of top compression ring is excessive, cause it that zitterbewegung increase blowby amount occurs when top dead center commutates.
Referring to Fig. 7, second gas ring 60 before shown improvement, its open end is Open architecture, its blowby circulation path comprises 2a, 2b and 2c.And the open end of second gas ring of the present invention is enclosed construction, its circulation path 23 only has one; By reducing circulation path, can play the effect that prevents the blowby amount.
Referring to Figure 11, traditional three pieces type combined oil ring 70 is comprised of upper scraping blade 3a, lower scraping blade 3b and a support spring 3c, after using a period of time, due to upper scraping blade 3a and lower scraping blade 3b wearing and tearing, cause itself and cylinder sleeve contact sharply to reduce, thereby increase the blowby circulation area.
Referring to Figure 12, the plotted curve of shown closed gap under different rotating speeds on the impact of blowby amount, abscissa means engine speed, y coordinate means the blowby amount, by finding out on figure, reduces closed gap and can reduce the blowby amount.
Referring to Figure 13, shown under different rotating speeds the plotted curve that unmatchful blowby amount impact is arranged of twist angle, abscissa means engine speed, y coordinate means the blowby amount, by figure is upper, can find out, the cancellation twist angle can reduce the blowby amount.
Referring to Figure 14, the shown plotted curve of tangential elastic force on the impact of blowby amount under different rotating speeds, abscissa means engine speed, y coordinate means the blowby amount, by finding out on figure, increases tangential elastic force and can reduce the blowby amount.
Referring to Figure 15, shown first ring and the second closed gap of the ring relation plotted curve on the impact of blowby amount, abscissa means engine speed, y coordinate means the blowby amount, by finding out on figure, when the ratio in the first closed gap of the closed gap of second gas ring second and top compression ring is 1.80-2.45, the air leakage minimum.
The first closed gap 11 of another embodiment's top compression ring 1 is 0.13mm, and the second closed gap 21 of second gas ring 2 is 0.32mm; And the closed gap 21 of second gas ring second is 2.4 o'clock with the ratio in the first closed gap 21 of top compression ring, the air leakage minimum, can meet supercharged engine air leakage standard.
The first closed gap 11 of another embodiment's top compression ring 1 is 0.15mm, and the second closed gap 21 of second gas ring 2 is 0.35mm; And the closed gap 21 of second gas ring second is 2.3 o'clock with the ratio in the first closed gap 21 of top compression ring, the air leakage minimum, can meet supercharged engine air leakage standard.
Claims (5)
1. the anti-blowby piston ring group of an automobile turbo engine, comprise top compression ring (1), second gas ring (2) and combined oil ring (3), and be engaged in from top to bottom on piston (4); It is characterized in that: the first closed gap (11) of described top compression ring (1) is 0.13-0.17mm, and the second closed gap (21) of described second gas ring (2) is 0.3-0.45mm; Described combined oil ring (3) is the two-piece type combined oil ring.
2. the anti-blowby piston ring group of a kind of automobile turbo engine according to claim 1 is characterized in that: described second gas ring (2) second closed gaps (21) are 1.80-2.45 with the ratio in the first closed gap of described top compression ring (1).
3. the anti-blowby piston ring group of a kind of automobile turbo engine according to claim 1 and 2 is characterized in that: described top compression ring (1) adopts shaping steel wire to make, whole nitriding treatment, and exterior arc surface is coated with PVD coating.
4. the anti-blowby piston ring group of a kind of automobile turbo engine according to claim 1 and 2, it is characterized in that: the open end of described second gas ring (2) is enclosed construction; The cylindrical top of described second gas ring (2) is the conical surface (22), and section is nose type structure.
5. the anti-blowby piston ring group of a kind of automobile turbo engine according to claim 1 and 2, it is characterized in that: described combined oil ring (3) is comprised of spiral pushing out ring oil ring support spring (31) and spiral pushing out ring oil ring ring body (32).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012101719338A CN103452691A (en) | 2012-05-30 | 2012-05-30 | Anti-blow-by piston ring set for automobile supercharged engine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012101719338A CN103452691A (en) | 2012-05-30 | 2012-05-30 | Anti-blow-by piston ring set for automobile supercharged engine |
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| CN103452691A true CN103452691A (en) | 2013-12-18 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2012101719338A Pending CN103452691A (en) | 2012-05-30 | 2012-05-30 | Anti-blow-by piston ring set for automobile supercharged engine |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104314700A (en) * | 2014-10-13 | 2015-01-28 | 重庆长安汽车股份有限公司 | Engine piston ring |
| CN105179101A (en) * | 2015-10-26 | 2015-12-23 | 江铃汽车股份有限公司 | Supercharged gasoline direct-injection engine piston ring set |
| WO2016029599A1 (en) * | 2014-08-25 | 2016-03-03 | 安徽江淮汽车股份有限公司 | Piston for ethanol fuel engine |
| JP2021092160A (en) * | 2019-12-06 | 2021-06-17 | 株式会社クボタ | engine |
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| CN2114032U (en) * | 1991-05-23 | 1992-08-26 | 刘晓明 | Closed piston compression ring |
| CN2338497Y (en) * | 1997-02-21 | 1999-09-15 | 李明武 | Leakage-free piston ring and matched piston thereof |
| CN1367310A (en) * | 2002-03-18 | 2002-09-04 | 周芝山 | Piston ring with special opened gap |
| US20100162987A1 (en) * | 2008-12-25 | 2010-07-01 | Teikoku Piston Ring Co., Ltd | Piston device for internal combustion engines |
| CN102168627A (en) * | 2011-04-20 | 2011-08-31 | 安国清 | Piston ring set with high wear resistance |
| CN102418620A (en) * | 2011-12-22 | 2012-04-18 | 江铃汽车股份有限公司 | Piston ring with physical vapor deposition (PVD) chromium-base ceramic compound coating layer |
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2012
- 2012-05-30 CN CN2012101719338A patent/CN103452691A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2114032U (en) * | 1991-05-23 | 1992-08-26 | 刘晓明 | Closed piston compression ring |
| CN2338497Y (en) * | 1997-02-21 | 1999-09-15 | 李明武 | Leakage-free piston ring and matched piston thereof |
| CN1367310A (en) * | 2002-03-18 | 2002-09-04 | 周芝山 | Piston ring with special opened gap |
| US20100162987A1 (en) * | 2008-12-25 | 2010-07-01 | Teikoku Piston Ring Co., Ltd | Piston device for internal combustion engines |
| CN102168627A (en) * | 2011-04-20 | 2011-08-31 | 安国清 | Piston ring set with high wear resistance |
| CN102418620A (en) * | 2011-12-22 | 2012-04-18 | 江铃汽车股份有限公司 | Piston ring with physical vapor deposition (PVD) chromium-base ceramic compound coating layer |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2016029599A1 (en) * | 2014-08-25 | 2016-03-03 | 安徽江淮汽车股份有限公司 | Piston for ethanol fuel engine |
| CN104314700A (en) * | 2014-10-13 | 2015-01-28 | 重庆长安汽车股份有限公司 | Engine piston ring |
| CN105179101A (en) * | 2015-10-26 | 2015-12-23 | 江铃汽车股份有限公司 | Supercharged gasoline direct-injection engine piston ring set |
| JP2021092160A (en) * | 2019-12-06 | 2021-06-17 | 株式会社クボタ | engine |
| JP7260462B2 (en) | 2019-12-06 | 2023-04-18 | 株式会社クボタ | engine |
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Application publication date: 20131218 |