WO2008017195A1

WO2008017195A1 - A piston ring without end clearance and a piston with said ring

Info

Publication number: WO2008017195A1
Application number: PCT/CN2006/001837
Authority: WO
Inventors: Yingjie Yang
Original assignee: Yingjie Yang
Priority date: 2006-07-25
Filing date: 2006-07-25
Publication date: 2008-02-14

Abstract

A completely sealed piston ring without end clearance and a piston with said ring are disclosed, the perimeter of the external diameter of the piston ring is longer than that of the internal diameter of the cylinder, the dimension (T) exceeded by the piston ring is the same as that of the superposition portion of the piston ring’s open ends, the two ends in the superposition portion form the complementary diagonal cutoff of the piston ring in axial direction, the thickness of the superposition portion is the same as that of the piston ring, a positioning notch (g) preventing rotating is provided in the inner cylinder face of the pistonring close to one end, a positioning pin (3) corresponding to the positioning notch is inserted into the bottom of the piston ring notch in a direction at an angle of about 30~40 degrees with respect to the piston pin, and the positioning pins (3) in ring notches(g) are positioned at an angle of 180 degrees with each other so as to prevent the cutoffs of the piston rings overlapping.

Description

Endless gap piston ring and piston containing the same

The invention relates to a full-sealing, anti-piston ring opposite end of an internal combustion engine and an air compressor, and a diagonal cutting piston ring and a piston with wear compensation function, which is called an endless gap piston ring and a piston containing the same. . Background technique

In the prior art, the piston ring of the internal combustion engine and the air compressor is in the shape of a straight edge cut, and there are a very small number of bevel cuts and stepped cuts. Straight-edge slit piston rings are the most widely used. It utilizes two to three compressed gas rings, with adjacent piston rings being offset by 120 on the piston with straight edge cuts. One 180. , form a labyrinth seal structure to achieve airtightness. Since the piston ring is an irregular ellipse, when the cylinder is worn by the piston and the piston ring, the roundness is lost, the straight edge slit end gap is increased, and the alignment of the piston ring slits is accompanied by the increase of the wear end gap. Gas failure and counter-tightness failure. The compression pressure in the cylinder is lowered, the compression heat is lowered, the deflagration speed is slowed, and the compressed gas and the explosive gas are leaked to the crankcase. Thereby, the power of the internal combustion engine is lowered, and the lubricating oil is generated into the combustion chamber to generate blue oil from the burner oil, and the engine is discharged with a large amount of unburned flammable harmful gas such as CH and CO to pollute the environment. In addition, the high-temperature, high-pressure gas of the internal combustion engine breaks into the crankcase to oxidize, decarburize, gelatinize, and lose lubrication, and enters the throttle from the crankcase exhaust pipe, contaminating the throttle with particles of lubricating oil. For air compressors: It is difficult to increase the air pressure, the oil in the gas storage bag increases, the energy consumption increases, and the efficiency decreases. At this point, the internal combustion engine and the air compressor must be overhauled; the cylinder, the piston and the piston ring are replaced. The beveled cut piston ring is basically the same as the straight edged cut piston ring except that the straight edge cut is inclined at an angle. The stepped slit piston ring can compensate for the interface gap which is increased due to the wear of the inner wall of the cylinder and the outer diameter of the piston ring, but there is a gap between the compressed air and the blasting gas from the upper opening, and the ring and the ring groove to enter the bottom of the piston ring. The lower opening is pulled out and enters the next ring and the crankcase. It also reduces the compression pressure of the internal combustion engine, increases the fuel consumption, and reduces the power of the internal combustion engine. Summary of the invention

SUMMARY OF THE INVENTION It is an object of the present invention to avoid the deficiencies of the prior art and to provide a piston ring similar to a stepped slit and a piston containing the same. When the inner wall of the cylinder and the outer diameter of the piston ring are worn, the wear compensation function can be provided. The airtightness will not be lost due to the leakage of the piston ring incision. Compressed gas and explosive gas will not be generated through the backlash of the piston ring and the crankcase under the end gap, and the oil will not enter the combustion chamber. The original compression pressure of the internal combustion engine is always maintained within the wear compensation range, and the power is not reduced. . Make fuel burn more fully, reduce HC and CO Emissions and NOx formation. Reduce the oxidation of lubricating oil. Improve the full utilization of fuel, save fuel, extend the overhaul of internal combustion engines, and provide a more endless sealless piston ring with a tightly sealed diagonal seal against each piston ring and a piston containing the piston ring.

The object of the present invention is achieved by the fact that the circumference of the piston ring is longer than the circumference of the inner diameter of the cylinder by the length of the opening of the piston ring as the length of the slit. The slit of the first piston ring is a diagonal cut, that is, the outer cylindrical surface of the axial section of the piston ring is close to the diagonal of the lower corner of the upper end of the piston ring to the lower end of the inner diameter of the piston ring, and the ends are complementary. Lap the incision. The lower triangular end of the diagonal cut blocks the gap between the piston and the cylinder. The upper triangular end is a four-sided wedge or a five-sided wedge that overlaps the lower triangular end to seal the gap between the lower triangular ends. Therefore, the gas leaking from the piston ring and the piston ring groove and the upper opening gap is sealed, so that the gas cannot enter the next piston ring groove and the ring groove, or even the crankcase, to achieve the airtight function. The second piston ring is a tapered ring, the diagonal slit of which is opposite to the slit of the first piston ring, from the outer conical surface of the axial section of the piston ring to the lower corner of the bottom edge to the upper end surface and the inner cylindrical surface or inner The line connecting the angles of the grooves is twisted, and the ends of the grooves are complementary lap joints. The slit is a lower quadrilateral wedge shape and an upper triangular structure, or a lower five-sided wedge shape and an upper triangular structure to prevent the oil from being pumped to the combustion chamber. In order to prevent the piston ring from being aligned, the piston ring is positioned in the piston groove. In the inner cylinder surface of the piston ring, an anti-rotation groove is opened near the end of the piston, and the bottom of the piston groove is β = 30 with the piston pin axis. - 45. The position of the corners is 180 at the bottom of each ring. A small pin is inserted in the direction for inserting into the anti-rotation groove of the piston ring, and the positioning prevents the rotation of the piston ring.

Due to the above technical solution, the cylinder compression pressure can be increased in the cold car. When the cylinder wall of the internal combustion engine and the outer diameter of the piston ring are worn, as long as the diagonal cut is repeated, the compression pressure and the detonation pressure are not lowered, and the compression stroke is reduced. No work, no ups and downs, oil, full combustion, reduce emissions of exhaust pollutants, improve the power of the internal combustion engine. Moreover, each ring prevents the rotating counterpart, and the ring and cylinder wall wear evenly, making it a wear compensation function, prolonging the service life of the internal combustion engine, saving fuel, lubricating oil and other resources. DRAWINGS

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a front elevational view of an endless gap piston ring of a fully sealed diagonal cut of the present invention. In the figure: Τ is the lap length, S is the expansion gap, F is the piston ring closed by the external force in the working state, g is the anti-rotation positioning groove; Figure 2, Figure 3, Figure 4 are the endless gap piston ring of the present invention; A partial cross-sectional enlarged view of a trapezoidal ring, a wedge ring, and a rectangular ring, showing a diagonal overlapping surface m; in this figure, three structures of a cylindrical ring;

5, FIG. 6, FIG. 7, FIG. 8, FIG. 9, and FIG. 10 are respectively partial cross-sectional enlarged views of the endless gap piston ring of the present invention; the trapezoidal ring, the wedge ring, and the rectangular ring of the tapered ring. 8 , 9 and 10 are tapered rings provided with upper twist grooves. Figure 11 is a partial axial side view of the slit when the endless piston ring of the present invention is in a natural state;

Figure 12 is an enlarged view of the K direction in the drawing of the endless piston ring of the present invention; wherein: R is a rounded corner designed to prevent stress concentration, J is a cutting shoulder, α is the inward angle of the cutting shoulder, and can also be cambered The camber angle α is negative; in order to prevent the end and the shoulder J from interfering while being thermally expanded, the shoulder angle α of the cutting shoulder J is designed;

Figure 13 is a partial axial side view of the endless gap piston ring of the present invention placed in the cylinder, showing the working state of the endless gap piston ring joint of the fully sealed diagonal cut;

Figure 14, Figure 15, Figure 16 are respectively an endless gap piston ring according to another embodiment of the present invention; a partial cross-sectional enlarged view of a trapezoidal ring, a wedge ring, and a rectangular ring, showing a diagonal overlapping surface m; Medium is the three structures of the cylinder ring;

Figure 17, Figure 18, Figure 19 are respectively an endless gap piston ring according to another embodiment of the present invention; a partial cross-sectional enlarged view of a trapezoidal ring, a wedge ring, and a rectangular ring, showing a diagonal overlapping surface m; Medium is the three structures of the barrel ring;

20, FIG. 21, FIG. 22, FIG. 23, FIG. 24, FIG. 25 are respectively an endless gap piston ring according to another embodiment of the present invention; a partial cross-sectional enlarged view of a trapezoidal ring, a wedge ring, and a rectangular ring of a tapered ring; 20, 21, and 22 are tapered rings provided with upper twist grooves.

Figure 26 is a partial axial side view of the endless gap piston ring in a natural state according to another embodiment of the present invention; Figure 27 is a partial axial side view of the endless gap piston ring placed in the cylinder according to another embodiment of the present invention, The working state of the endless gap piston ring joint of the fully sealed diagonal cut;

Figure 28 is a partial cross-sectional view showing the actual operation of the endless piston ring of the present invention and the piston including the piston ring in the cylinder; Fig.: 1 cylinder block, 2 first piston ring (full seal diagonal endless barrel surface) Or cylindrical piston ring), anti-rotation locating pin on 3 piston, 4 piston, 5 second piston ring (endless gap tapered piston ring with full sealing diagonal cut), β is locating pin 3 and piston pin axis The angle of the I, is a partial enlargement;

Figure 29 is an enlarged view of a portion of the endless gap piston ring of the fully sealed diagonal slit of the present invention and the piston including the piston ring. detailed description

In Fig. 1, the piston ring is subjected to an external force F to close the opening. The working condition of the fully sealed diagonal incision piston ring is shown, the length of the head joint at both ends is Τ, the expansion gap S required for heating, and a small groove g is opened in the piston ring near the end of the cylindrical surface. Or open a small groove g (not shown) near the other end, and cut the position of A-A. The length of the interface T blocks the air leaks from the top and bottom, and it is the design point for the wear compensation function of the fully sealed diagonal endless piston ring. When the gas rainbow inner diameter and piston ring When the diameter of the joint is τ = ο, the sealing property of the technology enters the technical state of the existing straight edge slit.

Figure 2 is a cross-sectional enlarged view of a trapezoidal piston ring diagonal cut of a cylindrical or barrel surface (not shown in the barrel), and Figure 3 is a cross-sectional enlarged view of the wedge-shaped piston ring diagonal cut, Figure 4 A cross-sectional enlarged view showing a diagonal slit of a rectangular piston ring, wherein the diagonal joint faces m are axial sections of the piston ring, and the distance between the outer cylindrical surface or the outer cylindrical surface from the top surface δ starts to the inner cylinder of the piston ring The diagonal cut of the intersection of the face and the bottom surface, as shown in Fig. 11; the length of the opening on the same circle along the obtuse angle of the diagonal line Τ to the arc of the b point (or the mysterious line) to the point of the same circle at the acute angle d The tapered surface (or plane) of the arc (or the straight line) of the length D to the c point, the four-sided wedge-shaped overlapping boss formed by the lap joint m, and the same arc of the other end B-A point Line (or black line) to the C-D point of the same circular arc line (or black line) composed of complementary triangle lap joint interface form. It can also be manufactured in reverse. The lower triangular boss blocks the gap between the cylinder wall and the piston ring. In the range of the lap length T, the diagonal incision piston ring has a wear compensation function. Always maintain the initial seal.

5 to 10 are enlarged views of the slit structure of the tapered ring. It is the opposite of the structure of Figure 2, Figure 3, and Figure 4. The structure is from the lower corner distance δ of the outer conical surface to the corner of the upper end surface of the piston ring and the inner cylinder surface or the corner of the inner cylinder surface (or inner cone surface) of the positive twist groove. The line forms a diagonal cut of a complementary cross section of the triangle on the lower quadrilateral wedge. In order to better scrape the oil, it helps the upper ring to close the air and prevent the oil from being pumped to the combustion chamber.

Fig. 12 is an enlarged view of the squint direction in each figure, in which the rounded corner of R is designed to eliminate the stress concentration of the slit. The cut shoulder angle of the cut shoulder J is designed to prevent the piston ring from being thermally expanded and the right angle of the end is interfered with the R arc. The ring height at the joint is larger than the width of the ring groove and is stuck.

Figure 13 shows a partial axial side view of a diagonally-cut piston ring placed in a gas rainbow. It shows the fully sealed diagonally cut endless piston ring in the cylinder and its fully sealed nature and wear compensation.

14 to 27, another embodiment of the present invention. Figure 14 is a cross-sectional enlarged view of a cylindrical trapezoidal piston ring diagonal cut, Figure 15 is a cross-sectional enlarged view of a wedge piston ring diagonal cut, and Figure 16 is a rectangular piston ring diagonal cut. Fig. 17 is an enlarged cross-sectional view showing a diagonal cut of a trapezoidal piston ring of a barrel surface, Fig. 18 is an enlarged cross-sectional view showing a diagonal cut of a wedge piston ring, and Fig. 19 is a sectional view showing a rectangular piston ring. A cross-sectional enlarged view of the diagonal cut, their diagonal joint faces m are axial sections of the piston ring, and the outer cylindrical surface or the outer cylindrical surface is at a distance δ from the top surface to the intersection of the bottom surface of the piston ring and the inner cylindrical surface The diagonal cut of the distance ,, as shown in Figure 26; the arc along the ellipse angle a to the obtuse angle a to the arc of the opening point T to b (or the straight line) to the intersection of the bottom surface to the inner cylinder surface Obtuse angle d point on the same circle upper opening length D to c The tapered surface (or plane) of the arc (or the straight line) of the point, the five-sided wedge-shaped overlapping boss formed by the overlapping surface m, and the same circular arc of the other end B-A point (or The interface form of the complementary triangle lap joint formed by the same circular arc line (or black line) from the C-line to the C-D point. It can also be manufactured in reverse. The lower triangular boss blocks the gap between the cylinder wall and the piston ring. In the range of the lap length T, the diagonal cut piston ring has a wear compensation function. Always maintain the initial seal.

20 to 25 are enlarged views of the slit structure of the tapered ring. It is opposite to the structure of Figures 14, 15, and 16. The structure is from the lower corner distance δ of the outer conical surface to the joint between the upper end surface of the piston ring and the inner cylinder surface or the inner cylinder surface (or inner cone surface) of the positive twist groove. The diagonal of the ξ, forming a diagonal cut of the complementary cross section of the triangle on the lower five-sided wedge. In order to better scrape the oil, assist the upper ring to close the air, block the helium on the crankcase, and prevent the lubricating oil from pumping to the combustion chamber. Figure 27 is a partial axial side view of the diagonal cut piston ring placed in the cylinder. It shows the working condition of the endless gap piston ring of the fully sealed diagonal cut in the cylinder and its fully sealed nature and wear compensation.

Figures 28 and 29 show the angle between the bottom of the piston ring groove of the piston 4 and the axis of the piston pin β = 30. - 40. A locating pin 3 is made at the position. The locating pins in the two adjacent piston ring grooves are offset by 180. . Cooperating with the positioning groove g of the respective piston ring, the piston ring is prevented from rotating. In order to prevent the piston ring incision from being aligned. In order to make the cylinder barrel wear more evenly.

It is to be understood that the foregoing description of the embodiments of the present invention are intended to be illustrative and not restrictive It is intended to be within the scope of the invention as defined.

Claims

Rights request

What is claimed is: 1. An endless gap piston ring and a piston comprising the same, wherein: the slit of the piston ring is a diagonal cut, and the anti-rotation positioning groove is matched with the positioning pin of the bottom of the ring of the piston.

2. The endless gap piston ring according to claim 1 and the piston including the piston ring, wherein: the diagonal cut of the cylindrical or barrel piston ring is an outer circular surface of the axial section of the piston ring. The distance ( δ ) starts to the diagonal of the intersection of the cylindrical surface and the bottom surface of the piston ring, and the arc or the line of the (b) point of the same circular opening length (T) along the obtuse angle (a) of the diagonal To the acute angle (d), the arc of the (c) point of the same circular opening length (T) or the tapered surface of the straight line or the joint surface (m) of the plane formed by the four-sided wedge-shaped overlapping boss, and The other end (BA) point is the same as the arc line or the cut line form of the complementary triangle lap joint formed by the same circular arc or the black line of the (CD) point.

3. The endless gap piston ring of claim 2 and the piston including the piston ring, wherein: the diagonal cut of the tapered piston ring is the distance from the outer conical surface of the section to the lower corner of the bottom edge (δ Starting from the corner of the upper end surface of the piston ring and the inner cylindrical surface or the diagonal line at the corner of the cylindrical surface or the inner tapered surface of the positively twisted groove, a diagonal slit structure of a triangular cross-shaped triangular complementary cross section is formed.

4. The endless gap piston ring according to claim 1 and the piston including the piston ring, wherein: the diagonal cut of the cylindrical or barrel piston ring is an outer circumference of the axial section of the piston ring from the top surface. The distance ( δ ) starts to the diagonal of the intersection of the cylindrical surface and the bottom surface of the piston ring, and the arc or the line of the (b) point of the same circle opening length (T) along the obtuse angle (a) of the diagonal The obtuse angle (d) from the intersection of the bottom surface to the inner cylinder surface (d) is the arc of the (c) point of the opening length (T) of the same circle or the joint surface (m) of the plane or plane of the black line The five-sided wedge-shaped overlapping boss formed by the same triangular line or the straight line of the other end (BA) point or the complementary circular triangle or the mysterious line of the (CD) point The form of the cut.

5. The endless gap piston ring of claim 4 and the piston including the piston ring, wherein: the diagonal cut of the tapered piston ring is the distance from the outer conical surface of the section to the lower corner of the bottom edge (δ Starting from the corner of the upper end surface of the piston ring and the inner cylindrical surface or the angle of the distance (ξ) from the corner of the cylinder or inner cone of the positive twist groove, forming a pair of triangular complementary cross sections on the lower five-sided wedge Corner cut structure.

The endless gap piston ring according to any one of claims 1 to 5, and the piston including the piston ring, characterized in that: the combination of the cutting shoulder (J) of the piston ring slit and the overlapping surface (m) is one (R) arc angle, cut shoulder (J) There is an (α) inclination angle to the root of the cutting root (R), and the inclination angle of (α) is the internal inclination angle or the camber angle.

7. The endless gap piston ring of claim 1 and a piston including the piston ring, characterized in that: The inner cylindrical surface of the ring is half-cylindrical with a small groove near the end of one end, or a semi-cylindrical small groove is opened at the other end.

8. The endless gap piston ring of claim 1 and the piston including the piston ring, wherein: the anti-rotation positioning pin is embedded in the bottom of the ring of the piston, and is coordinated with the anti-rotation positioning groove of the piston ring.

9. The endless gap piston ring according to claim 1 or 8, and the piston including the piston ring, wherein: the anti-rotation positioning pin embedded in the piston is 30 to 40 with respect to the piston pin axis. The angle between the adjacent ring groove positioning pins is 180°.