JPS5874854A - Piston and piston ring set - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] The piston in an internal combustion engine or compressor.

Generally, 91 sets of piston rings 1 are provided between the piston and the cylinder for the purpose of preventing gas leakage into the crank chamber and oil leakage into the piston head.

Since currently known piston rings interfere with each other during operation, the assembly does not completely preserve the above-mentioned nine objectives, and each piston ring does not fulfill its full role. It has become impossible to accomplish this.

The compression rings allow the passage of gas (gas leakage) from the combustion chamber or compression chamber to the crank chamber, and the oil rings in both directions thus serve their own purpose in the upward stroke of the piston. It works against the.

Thus, their roles were not fully fulfilled.

Is it difficult to synchronize with the 91 operation?1. - Stable.

This results in insufficient and uncertain results.

Finally, all the piston rings mentioned above are brought into contact with the cylinder with great force and are heavy, so as a result, a considerable amount of energy is consumed due to friction and inertia. It will become.

Publicly known documents most closely related to non-invention include those listed below.

U.S. Patent No. 3,759.148 September 18, 1973
U.S. Patent No. 3,831,952, issued in 1974, August 8
U.S. Patent No. 3,656,766, issued May 27, 197
No. 3,840,182, issued April 18, 1974. United States Patent No. 3,893,67, issued August 8, 1974.
No. 5, issued on July 8, 1975, United States Permit No. 3.917□
No. 290, November 4, 1975, United States Patent Office' 4
, No. 103, 594 Published tomorrow 1, 1978 The invention is to provide a new and highly efficient piston ring set in the cylinder that is lighter in weight than the known piston ring set and produces very low tension and friction against the cylinder. It favors a lighter piston with a simpler piston ring set, the compression ring virtually eliminates gas leakage, and the 4th ring only moves during the downward stroke, and the 4th ring only moves up during the upward stroke. lubricant on
- Assemblies with effective recirculation.

The piston ring set in each piston of an engine or compressor is a circular ring that is brought into contact with the cylinder by its elastic tension, and on the other hand, the gas passes through the combustion chamber and the crank chamber. - Even if it is not enough to pass, it should be reduced, t
and on the other hand, a compression ring consisting of at least one ring of elastic metal forming a means of at least 1 m for reducing the friction between the cylinder and two circularly arranged continuous rings. The elastic, very thin-walled transverse force vanes are combined with a single-piece oil ring made of FL14, which seals with the edge of the piston head located on the true side of the piston head. VC8 are connected to each other and connected to the piston.

and the side 11 of the blade row located in the crank base ring is brought into contact with the cylinder by the elastic force of each blade,
Further, the outward direction of the blades is contoured to match the shape of the cylinder, and the piston head has an opening with a very steep conical acute angle 'tW! Further, the vanes are plowed together to form an elastic circular skirt with the piston head III closed and sealed and the crank chamber II open, and in addition to the compression ring and the oil ring, the vanes are It is constructed with adaptive means for housing piston rings and improvements within the piston and cylinder.

An assembly such as the one described above is a very simple set of binoton rings to make; 1) it is less cumbersome and weighs less than a piston ring;

The compression ring efficiently controls the passage of gas between the combustion chamber or compression chamber and the crank chamber, and the oiling produces two new and highly efficient effects.

One of the seven functions is a simple and effective oil scrubbing during the exclusive downward stroke of the piston, and the other is simple and effective recirculation during the upward stroke of the piston.

In fact, during the downward stroke, the lower edge of the thin, elastic outer surface almost parallel to the cylinder, or the force applied on the cylinder, is very small, making it ideal as a means of burning off oil**. thD, and in the upward stroke, the small angle formed between its outer surface and the surface of the cylinder 7511 made the force applied on the cylinder very small.

This constitutes another ideal smoothing device for recirculating the oil remaining on the cylinder wall towards the crank chamber by dynamic action.

Furthermore, the mutually independent high efficiency of each of these piston rings creates conditions that are more favorable for the actuation of externally powered piston rings than the known interactions.

Thus, the purpose of the piston ring.

Shintsu's piston rings are also achieved with high efficiency, which means less wear and tear.

The energy savings are huge.

Finally, this better efficiency and lower friction of each piston ring results in an entirely new method of lubrication between the piston, piston ring, and cylinder.
'! *This creates several new operating conditions.

That is, it employs a much higher polishing level than the normal level for cylinder II IC, thereby making an additional contribution to energy savings.

The possibility of further reducing friction and wear in all parts of the new assembly and establishing a mechanical bearing relationship between the cylinder and the piston up to the piston head, thereby increasing the As well as modifying the heat exchange system and the fact that it has only two piston rings, there is the possibility of shortening the length of the piston and thus allowing the piston head to be lighter. It is.

r below! *Issue @A'i, Please refer to the detailed explanation of the preferred example shown in the accompanying drawing. I will clarify.

FIG. 1 shows the compression ring 12- and the oil ring 13 on the upper 2 tons 11.

This assembly is distributed within the cylinder 14. After reviewing these piston rings and the operation of the above assembly, we will further discuss the piston and cylinder characteristics enabled by the use of the piston rings.

FIG. 2 is a partial cross-sectional view of the piston z1 in the cylinder 24, showing a first embodiment as' of the compression ring 12.22.

This compression ring has a clearance 27t- in the groove of the piston 21.
It is composed of two thin-walled members 25 and 26 that are spaced apart.

The clearance 27 between the piston ring 22 allows the two thin-walled members to move freely, and also allows the pressure required to reach the combustion chamber or compression chamber through the connection 1127 between the upper surface of the piston ring 22 and the cylindrical inner surface. Limited to a minimum of 4.

The force of one of the two thin members of the piston ring 22 is
P1 is a thin-walled cut ring 25 (thickness: 0.7 mm) made of elastic metal such as cast iron or steel, and other strong ones are made of, for example, annealed copper or polytetrafluoroethylene (Teflon). This is a relatively thin cut ring 26 (0.5 m thick) made of a relatively plastic material.

The plastic ring 26 is disposed between the first elastic metal ring 25 and the groove surface on the crank chamber side of the piston. In the free state, the ring 25 has a larger diameter than the cylinder to enable it to have an expansion force t on the cylinder. I
The continuity of the N cylinder and the substantial lateral movement of the gas along the wall of the cylinder is maintained by the device illustrated in FIG.

In the plan view of FIG. 3, the ring 25 is
It is fitted as a ring 35 in a tightened state within A.

The length of the mtm play between its cutting directions 38 and 39 has a cross section t similar to that of the metal ring 35 or is made of a plastic material, preferably polytetra 70 roethylene (thea Cl
It has been enlarged to accommodate 310 T

Sector 310 is brought into abutment against the cylinder due to the elongation forces of thermal expansion of ring 35 and sector 310, and the effects of gas pressure on the inner surfaces of the ring and sector, thereby causing them to It is inserted so that there is no play between the cut directions 38 and 39 at room temperature so that the gas passes between the cut seal of the metal ring 35 and the cylinder. be done.

The length of Cef I 310, for Teflon, shall be greater than or equal to the sum of its length 4S * "t" some elasticity 't & S, Ng 35 and the expansion bale of sector BIG, It must be of sufficient length to ensure that the sector is not subject to permanent reduction in length.

FIG. 4 is a partial cross-sectional view of the piston 1 within the cylinder 44, showing a modification 42' of the compression ring 12.

This compression ring 42 has a clearance 47 within the groove of the piston 41.
Three thin-walled members 45, 46, 411 spaced apart
It is well structured.

This play 1147 allows these three thin members to move freely, and also allows the upper surface of the compression ring 42 to move freely.

The clearance 47t on the cylindrical inner surface is limited to the minimum necessary to allow pressure to reach from the combustion chamber or compression chamber.

5 through 7 are plan views of each of these three members of the compression ring 42, respectively.
I'll, TTF Two cut and joined thin-walled rings of plastic metal such as hook iron or steel 45.55
and 41.611 (0.7 m wall thickness) and annealed copper or polytetrafluoroethylene (Teflon).
1 is fitted with one thin-walled cut ring 46.76 made of a relatively plastic material.

The plastic ring 46.76 always has a central elastic ring 45.
55 and the groove surface on the crank chamber side of the piston.

In their free state, the rings 45.55 and 411.611 have a diameter larger than that of the cylinder so as to exert an expansion force on the cylinder, and their end play is as shown in FIG. and unlike the embodiment of FIG. 2], the play is exactly the same as that used to accommodate thermal expansion when mounted on a vimeton in a cylinder.

In its free state, the plastic ring 46.76 has the same dimensions as the cylinder, and the play of its cut portion 715 is substantially zero at room temperature atq. As a result, thermal expansion and compression ring play r447t
- due to the combined effect of the pressure acting on its cylindrical inner surface through! l12 ring 46.76 and ring 45.55
And 41L 611 is something that comes into contact with the cylinder phantomly, and this is even more likely because the pressure in the combustion chamber or compression chamber is very high.

In this embodiment, rings 45, 55 and 411, 6 are used to block the passage of gas along the cylinder through the play in the cut.
11, relative rotation must be avoided to avoid overlapping of those cut portions.

But in that case, the rings are so fastened that each one moves freely in its plane circle and rests itself freely against the cylinder without being subjected to any stress from other rings or from the piston. t must be avoided.

FIG. 8 is an A-Ais cross-sectional view of the ring 55, showing suitable homologous retaining means, namely the lower blade ring 4555.85.
．． 95 (FIG. 9), the upper blade ring 411,
The projections 512, 812, and 912 (Fig. 9) whose height is slightly lower than the wall thickness of 611 and 1011 (Fig. 10) are shown.

The above-mentioned upper blade ring has two rings 45 and 411, 55 and 611, 95 and 1011 (Fig. 10), and protrusions 512, 812 with sufficient play to prevent them from collapsing.
A receiving portion is formed to receive the 912°.

A suitable example of such a receptacle is the two notches 613 and 6
14, 1013 and 1014 (Fig. 10). ,'' It is advantageous to place these notches in this position, but if it is in this position, first 9/4 inch is inserted into the groove of the piston.
5.55.951 - By mounting the rings 411, 611, 1011, their cants are then
12. This is because it can be installed by aligning with 912. Figures 9 and 10 show
FIG. 4 is a plan view of another embodiment of rings 45 and 411;

As described above, on the rings 95 and 1011, there are protrusions 91.
2 and notches 1013 and 1014 are also formed, and additional notches 916 and 1016 are also provided on the inner center of each ring.

The reason for providing these additional notches and their roles are as follows.

That is, the substantial width of the thin-walled cut ring is such that it has sufficient radial elasticity to provide light, well-distributed, and critical contact between the outer edge of the thin-walled ring and the cylinder. It is said to be the width.

Notches 916 and 1016 allow the thin-walled ring to remain wide enough to hold it properly within the groove of the piston, while also allowing it to regain the radial elasticity that the wider thin-walled ring lacks. be done.

In addition, cast iron or steel binneton rings with normal wall thickness! The circular shape of the piston ring and the change in width are utilized to obtain an appropriate distribution of the stretching force over the entire circumference of the piston ring that contacts the cylinder, thereby increasing the rigidity of the piston ring, especially in the area adjacent to the end. It is known that it is necessary to avoid.

For example, as shown in Figure 10, the notches are uniformly distributed in the fan-shaped sRR facing the end, and are distributed at shorter intervals near the m part. This makes it possible to influence the distribution as described above at almost no cost.

Therefore, properly placed and distributed notches 916 and 10
The thin-walled ring assembly made of elastic metal having the structure 16 makes it possible to obtain a thin-walled ring having the characteristics t- as described below.

That is, the elasticity, flexibility and contour make it possible to create a light and uniform contact between the ring and the cylinder over the entire circumference of the ring. Figure 11 and 1
Figure 2 is a perspective view of two implementations of oil rings ipH11B and 123.

This oil ring has a wall thickness of, for example, 0.12 to 0.
2011m very thin elastic blade 1117
.

The truncated conical crown of 1217 consists of 9 single-piece copper members.

These blades separate the large diameter bottom side of the frustoconical crown body from each other, and also separate the small diameter bottom side 1I of the crown body from each other.
t - For example, flat wire 'r1118 or cylinder 1
218t-. The metal of the oil ring is heat treated to provide optimum elasticity, either in raw form or during processing.

The ends of the resilient vanes 1117, 1217 are furnace lapped (or honed) in the operating state before their installation.

The ends are connected to the cylinder, e.g. 0.10 to 0.2
It has a very narrow circular contact base with a width of 0.0 mm and is hardened by a supplementary local heat treatment to form a highly hard contact base with the cylinder, thereby making the cylinder The resistance against friction can be increased.

Such protection already results from the fact that the vanes forming such a narrow contact interface are brought into contact with the cylinder under very small forces, as will be explained below.

13 and 14 show a piston 131 or 14 mounted in a cylinder 1B4To or 144 and carrying an oil ring t of FIG. 11 at 133s and an oil ring of FIG. 14 at 143.
A 10-section EiiiI prisoner.

Is oiling 133 just that flat? 1118
.

1318 Minimum play by the constituent parts 1321
It is held in a groove 132o of the piston 131 with an interval t.

The wall thickness of Warashii 1118.1318 is 0.12 for example.
Depending on the cost, an annular slat 1322 is used to give the groove 1320 an easily formable width greater than the wall thickness of the washer f.

The m-shaped spacer 1322 is shown in FIG. 15 as 1522. This annular spacer is provided with a cut portion 1523 in order to enable its attachment.

Also, since the purpose of the washer is not to contact the cylinder, its outer diameter is smaller than the piston's outer diameter, and in its rest state, both ends 1523 are connected to each other. .

The wall thickness is indicated by 1524, but the second
I will explain the following in relation to Figure 0.

The above statement was i. It is made of metal, preferably light metal, or even better, of a plastic material such as polytetrafluoroethylene (thiamine), or of an uncut elastic material such as fluorinated elastomer. It is something that can be done.

In the latter case, the J washer acts not only as a 3jl-shaped mebasa but also as a *-shaped sheath.
It is.

By filling the cylindrical recess 1425 formed in the piston 141 with glue (anaerobic resin or cyanoacrylate in the case of IpH), the cylindrical portion 1218.
41.

Between the blade 1317 or Fi1 No. 17 and the piston 131 or 141, the blade 1 is inserted during the downward stroke of the piston.
an annular chamber 1326 or 14 for the purpose of collecting the oil channeled by 317 or 1417;
26 It can be formed into a body piston.

The return of this oil to the crankcase can be carried out by the following means, which may be used together or separately depending on the fee.

During the upward stroke of the piston: - The truncated conical shape 1327 or the chamber 1326 and the upper end of the piston skirt 51328? It continues.

Such a shape forms an angle of 7 degrees with the cylinder wall, which is suitable for the dynamic movement of oil, and is like a tortoise-like shape that allows the oil to return to the crank chamber through the play between the piston and the cylinder. .

a row of radial holes 142 arranged downwardly in the piston and communicating the bottom of the annular chamber 1426 with the center of the piston 7;
9--Produces a dynamic effect of driving the oil into the center of the piston through its orientation 1. (It is also possible to optionally provide a similar hole 'tl--which communicates with the II-shaped chamber 1326K: C). During the downward stroke of the piston; - 3 I-shaped chambers 1326 or 1426K communicate with the center of the piston. A series of radial holes 1431 perpendicular to the axis IIA of the piston or toward the am of the piston drive the oil into the center of the piston.

Large 1481 ti It adds a dynamic effect to it depending on the direction of its arrangement.

Figures 16 and 17 are jiil1 and 13
In the radial plane of the oil ring 113, 1.33 in the figure! ! Wide slit 1632 T-each wing lN1617
FIG. 3 is a radial view and a cross-sectional view of the oil ring provided therebetween in its free state;

FIG. 18 and FIG. 19 show the angle between each vane 1817 inclined with respect to the radial plane of the oil ring.
18331--FIG. 18 similarly shows another embodiment of the same oil ring provided.

Due to the difference in contact between the vanes and the cylinder during the descending stroke of the oil paddle and the ascending stroke of the recirculation, the above-mentioned inclined slits cause the oil ring to rotate t-rotate, but it does not allow the oil ring to move inside the cylinder. It is very favorable for its efficiency and its perfect adaptability.

When installing the piston in the cylinder 1 elastic vane 131
7. The workpiece 141 is contracted by the cylinder.

In other words, these elastic blades have an angle α (13th
Fig. 1411) and both i [1119 and 1219 of the cut portion of the oil ring are in contact with each other.

In this state, due to their construction, the vanes 1317 and 1417 are not in the cylinder except for very small play, which is necessary for one operation, i.e. mainly for thermal expansion or deformation and for lubrication. 11riA is shown in the connected state as shown in FIG. 12, and is connected as shown in FIG.

For example, in the cylinder B, there is a very small play in the % feather cabinet, which adds up to 0.2 ruts and 0.4 to W
It is possible.

In the case of this diameter, the number of blades is approximately 48, so the play between the blades located in the cylinder is 0.0.
04 to o, oos■, that is, poison to 8-electrochron.

The very small value of this play makes the structure of the blade essentially an "It14 bonded blade."

These clearances are such that very small L7ttt variations can be made in rounding to accommodate operational and lubrication concerns.

The edge of the crank chamber 110 of the blade, which is in the oil-scraping state during the descending stroke and in the recirculation state during the ascending stroke, has a circular narrow fitting W that connects with the cylinder end.
I have Jt.

In the free state outside the cylinder, both ends 1119 and 1219 are preferably closed off from the structure to facilitate positioning it on the piston before mounting it inside the cylinder.
217 is open. i.e. the outer diameter of these elastic vanes is increased so that they are no longer in contact; i.e. they form a barrier between them and the cylinder when the piston is installed. The angle β is larger than the angle α with respect to the axis of the oil ring which is parallel to *WJ. - The difference between the angles β and α is such that an elastic force is exerted against each oiling cylinder when the oiling is installed in the cylinder.

Varying the difference between these two angles and varying the wall thickness of the elastic vane (I) during manufacturing allows for the desired adjustment to the elastic pressure supplied by placing each vane against the cylinder. It is possible to do so.

The angle α of the vanes 1317 and 1417 with respect to the direction of cylinder II is such that the oil between the two surfaces is operated as much as possible for oil recirculation during the upstroke of the piston and for oil during the downstroke. As is known to be favorable for the Kingsbury effect on the drive of a very small pebble, the angle of 7 degrees is used.

FIG. 20 shows the small right-angled protrusions 2o34 and 2035 arranged at each end of the oil ring flat washer 2018.
FIG. 12 is a perspective view of a cut section in an O/V ring of the type shown in FIG. 11 with additions on each side of the f-cut section;

The height of the protrusion is at most equal to the wall thickness of the annular spacer or seam #1322.1522.

Its advantage is that it forms a solid stopper for the cut portion of the oil ring where both lll1m abut against each other during one operation. .

This all nutopper protects the 4311 parts from the risk of duplication which could occur due to their small wall thickness.

FIG. 21 shows a flat annular 9y-gage 2118 reading the bendable blades 2117 from each other, but without a cut portion;
A piston ring 2113, similar to piston ring 113 of FIG. 11, is shown at φ so that it cannot be twisted open.

This piston ring 2113 can therefore only be mounted on a piston consisting of at least two parts 9 whose respective connecting planes form the lateral surfaces of the grooves of the oil ring.

This is French Patent No. 8, filed on July 8, 1981.
Bistono shown in Figure 5 of No. 113437 and Violet and 5 Reasons are also equivalent to Jin.

If the oil ring were to have an endless structure, it would be possible to omit the manufacturing process, and this ring tube cut ring would also be easier to handle, and positioning would be much easier, and the pressure at both ends would be 11N during operation. This is to eliminate the danger pipe.

Its structure requires a piston tube formed by two members? - may be the best structure in some cases.

Fig. 22 is similar to the piston ring 113 in Fig. @11, but the entire width of the ring 2218 is
The piston ring 22 has a cut portion 2236 in the middle diameter direction that is open to the internal force that extends over 1 tlK.
13 t-showing.

These medium radial cut portions are distributed around the circumference of the flat ring 2218 in at most the same number as the number of blades 2217, and each of these cut portions is connected to the bottom of each radial cut portion and the number of blades. The blade 2217 is spaced equally from both cuts so that the distance between the uncut material and the bottom of the separation cut is the largest possible. It is arranged as follows.

The number of blades in the radial direction $2236 can be smaller than the number of six blades.

In that case, the cut sites should be arranged as regularly as possible around the piston ring.

The cut portion in the radial direction allows the piston ring to expand and easily position the piston ring while avoiding deformation even in a very narrow groove.

According to the additional patent application to the above-mentioned basic French patent, the compression piston ring shown in FIGS. It is made of metal, one is made of cast iron, the other is made of copper, and the surrounding structure has the shape and dimensions of a cylinder, and
A member t having a length of at least 111 m and having at least a cut portion Vi in contact with the cylinder under the action of a micro spring having a thickness exceeding the wall thickness of the ring, and accommodated in the groove of the ring. Did the above! Iku c1 splash is,
When the ring is in a free state, its diameter is slightly increased, so that when the ring is in a cylinder, - the force required for the thermal expansion of the ring in the cut contacting the cylinder is increased. forming a play space in which the micro-springs are compressed in the t region and exerting an expanding force on the ring parallel to the circumference of the ring;
Moreover, the simple expansion force is transmitted to the entire upper ring in such a way that the same force is generated at any point on the circumference where the upper ring comes into contact with the cylinder. It consists of a characteristic flat ring.

Due to the good distribution of contact and the very precision of such a piston ring when brought into contact with the cylinder 7, and the regularity of the elastic force applied to the cylinder 7, The air (liquid) tightness becomes very effective, and the pressure of the ring applied to the cylinder is reduced to 53, which is very low, and the pressure becomes smaller as the wall thickness of the ring becomes smaller. I hope it's reasonably low.

FIG. 23 shows a compression ring according to the invention consisting of a resilient metal ring 2337.

This compression ring is made of copper and has a small wall thickness, for example, 0.60
■It is preferable to do so.

When the upper distributing ring is attached to a piston consisting of several parts, as in the case of FIG. It may be formed from parts.

Alternatively, the ring may have 1@1h or more cut portions.

Figure 23 depicts a ring without such a cut, but the figure also shows three dotted lines 2338 indicating three possible cuts; in this case, the ring is 3iI sector].

The surface of each cut part is such that the number of cuts and sectors, that is, at least one cut part and two sectors, does not affect the behavior of the ring, at least in theory. are attached to each other, they are joined together.

The ring has at least one group of partial alternating radial cuts St.

FIG. 23 shows such a cut 233913.

FIG. 24 shows a group of partial alternating radial cuts 24.
It shows sector 2440 with the 39th meeting, and also the 25th sector.
The figure shows at least 4hX@ each partially outwardly opening
One of the above groups of partial alternating radial cuts is shown in detail, with an O-force 2541 and a partial inwardly opening cut 21542.

In each group of the partial alternating medial direction cut portions 2439, inwardly opening cut portions 25420 width width,
The width must be at least equal to the width of the cut portion 2541 that opens to external force.

Each group has a number of partial alternating holes opening outwardly and inwardly) 1! lt- could also be provided.

When the ring is installed in a cylinder, the outer cut portion 2541 in addition to the partial cut portion 2541 described above must be equal to the play space spent on thermal expansion of the entire ring. It is extremely narrow.

For example, in an 8-ring, such play is 0.
40 ■ It is a man.

If this ring has 3g!l sectors 2440 each with a group of partial alternating radial cuts 52439''
If so, the width of each cup 2541 when located within the cylinder will be approximately 0.13-. Assuming that each alternating cut is made with a width of, for example, 0.50, the circle 8 of the cylinder
The length of the circumference of the ring in the free state that exceeds the meeting is 3X
The amount will be 0.5O-3XO213.

This length is the cylinder diameter t-1, 111π-α
This would correspond to a diameter exceeding 353-.

To install the rings in the cylinder, the cuts in each sector are joined by abutting each other, or the partial alternating radial cuts of each group are subjected to compression to reduce the ring diameter. It acts as a force on the 11 chrome which urges it to increase,
This causes m@ to be applied to the terminating t cylinder.

This forcing force is regularly distributed over the contour of the ring, which is caused by the fact that the force is formed so that the contour of the ring has its shape and dimensions, and therefore the force is distributed on the inner wall of the cylinder. Because it follows exactly, it also has a micro splash in other forces, 4? At least 3 pieces arranged regularly in ! This is because it extends its force in the circumferential direction, thereby transmitting exactly the same force to all points on the circumference of the ring.

For a given thickness of the ring, the widths B and D in FIG. In the width C1 and in the a force, the cut portions 2541 and 2 which would increase the amount after the free 'piston ring'.
What is the width of 542'?

Each micro-spring 2 to obtain the most accurate contact pressure between the ring and cylinder and to deal with wear effects.
339.2439 characteristics t-constitute means for adjusting.

Partial cut portion 2541. The bottom of the 2542 is preferably rounded to prevent metal fatigue failure from occurring around it.

The circumference Fi of the piston ring can be obtained by any known forming means, such as by rolling, Il machining, grinding, etc., to a diameter very close to or exactly equal to the diameter of the cylinder.

If the ring is a single piece and has no cuts,
In order to obtain a clearance 1 in the cylinder to accommodate the thermal expansion of the microspring after compression, it may be necessary to make the diameter of the ring cylinder slightly larger than that of the cylinder.

If it is more than 7g or a few sectors,
Each sector in its free state.

In order to maintain the compression of the micro spring 2439 and reduce the width of the partial cut 2541 to the play dissipated in the thermal expansion of the cylinder, each sector of the circumference of the cylinder is occupied. The essential part is also slightly longer than 2443mm.

Sonoyo uni seku/l-to extend is steel spell)
k% for rings made by continuous rolling.

In dicing, by such a process it is possible to obtain a bonded and wound CI-,v which can be ground to exactly the same dimensions as the outer at-cylinder, and which can be cut into sectors of any length. You can get it.

Finally, two examples are shown in FIG.
*The o-q micro spring can be replaced by one (or more) coil springs stored in the large 2647 formed on the surface of the cut part, as shown in Fig. 26. I can do it.

Contact width between one blade of material wall thickness and the cylinder.

All dimensions exemplified above according to various play clearances etc.
This corresponds to parts for cylinder diameters on the 0 scale.

The dimensions of these O's may vary based on the diameter of the cylinder or may vary in proportions as determined by the example of the Queen's Numbers.

The operation and features of this new cylinder, lightweight piston, and piston ring assembly are as follows.

The compression ring of FIGS. 2 and 4 is provided with closure means at each end to prevent the passage of gas along the cylinder, and each end is connected to another Teflon seal. It includes a thin-walled elastic metal ring of at least 1 gA.

Due to the closed passage of the ring ends and the aid of the seal, this compression ring has the advantage that the compression force of a thin-walled ring is greater than that of a normal thick-walled compression ring. Despite the fact that the force exerted on the cylinder is much smaller due to the smaller size vh, a very high airtightness against the passage of gas is produced.

@23. Fi2 regarding the compression ring in figures 24 and 25
It makes it possible to produce new results compared to known rings.

That is, the contact of this compression ring with the cylinder is such that this ring has been machined or ground to a shape and size very close to, if not exactly the same as, the shape and size of the cylinder. , the best possible 4 0. The force that the circumference of the ring exerts on the cylinder is furthermore, that force can only produce a very small force.2339, U3O, 263
It only arises from reaction 9.

・Finally, Micro Hane S! In the case of 339.2439, the ring has no clearance, if any, from the total cut 2338 because the total cut 2338 is cohesive, and due to thermal expansion t The cut on the circumference of the ring required is micro-243
It is divided by 9 IIF buttocks.

These micro-springs slice gas leaks (by disassembling them into multiple channels). This ring is thus much more airtight than any known ring, although friction and wear are much lower.

Additionally, this ring is highly compatible with the use of Teflon groove seals, whether without a cut or with a cut, as in the case of mounting on a non-removable piston as described in connection with the ring marked *. It is applied in a continuous manner, thereby increasing the efficiency of resisting the passage of gas.

Furthermore, the ring has a large circumferential flexibility as the group of partial alternating radial cuts increases, and that is due to the fact that the actuation This offers significant advantages for engines with cylinders that are sometimes subject to large deformations.

Finally, the leather-like rolling described above is achieved by rolling. Manufacturing the ring from thin steel is much more economical than the conventional ring manufacturing currently in use.

The compression ring is tight against pressure and gas passage.

It is known to have the disadvantage 1 of producing the effect of forcing oil up into the upper end of the cylinder.

As we will see below, this shortcoming can be corrected by working in conjunction with a highly efficient oil ring. It is also known that seals made of plastic materials (particularly Teflon) have excellent maintenance stability.

In other words, it is about the same as Ensif, excluding the attack on the outer edge of the ring due to the unevenness of the cylinder, which is required at the current technological level to prevent damage by providing an oil reservoir on the cylinder wall. It might last a long time.
I'll send it out.

However, by eliminating abrasive combustion residue sound trailing, hot spots in the compression ring, and combustion of oil on the cylinder and in the compression ring rotation, the passage of gas and the compression ring 1st - A very large decrease will create a new cloudy situation that will lead to two new advantages of the 1st.

The advantages are that the contact between the piston and the cylinder, which is normally limited to the piston jacket below the oil link, is extended to the upper end of the piston.

・t11! In terms of force, Fi, a very high Kenken level is utilized for the internal position of the cylinder (3).

These two measures reduce V, improve heat exchange between cylinder and piston, and reduce weight by only 2g.
By having the ring segment A, in addition to being able to position the piston at a level below the piston T, it is also possible to reduce the size of the piston, thereby making it possible to significantly reduce its amount. Furthermore, these means are made of plastic materials! This reduces the wear of P+ (especially Teflon) seals in the lateral force direction.

For the fabrication of the oil ring, its elastic vanes have only a circular narrow width that contacts the cylinder with very light pressure, and scrapes off the oil on the downward stroke and recirculates it on the upward stroke. It is placed in an imaginary position.

Therefore, their elastic vanes, at their highest level, provide control of the oil rising towards the combustion chamber and a wider rather than narrow contact surface with the cylinder.
This makes it possible to reduce the very high v'h friction of ordinary oil rings, which has a very high v'h and carries out the oil removal through high pressure from a lip operating at a position perpendicular to the cylinder. be.

Since the oil ring operates at a position perpendicular to the cylinder as described above, in one of the two strokes, that is, the upward stroke, the oil ring located perpendicular to the cylinder smells in the opposite direction from the crank chamber. This is undesirable for scraping and recirculation as it scrapes off the oil and causes it to return in the wrong direction (11).

Thus, this new assembly, by virtue of the new cooperation of its various elements, reduces or suppresses the sound of gas passage between the piston and the cylinder to negligible levels.

• oil rise t-more effectively controlled; • friction and wear between piston and cylinder reduced to a large extent;

- Reducing the weight of the piston and its piston ring.

It is a combination that is determined by the meeting.

This combination reduces energy, oil, mechanical wear and maintenance costs.

Further advantages arise from the above, among which, by improving the compression, cold start-up is improved, especially for diesel enosine.

Contamination is also reduced by reducing the air and fuel play volume between the piston, piston rings, and cylinder.

Finally, it must be noted that the use of separate compression rings and oil rings as observed in the present application is within the spirit of non-invention.

This is because such usage does not balance all the benefits from the combinations described above, but each element used separately produces its own advantages.

In particular, for the compression ring, high tightness against gas leakage, reduced friction, reduced wear, reduced weight of the compression ring, better performance, improved durability of the structure,
and save energy.

・The oil ring has a simple and effective oil scrubber that is very efficient in the downward stroke by returning the oil to the crank chamber, and very efficient in the upward stroke by passing the oil through the crank chamber circuit. simple and effective recirculation of the oil film remaining on the cylinder, reduction of the friction caused by all oiling on the cylinder to only a fraction of 1 MP The two main components of the present invention are reduced wear, reduced oil ring weight, better performance, improved durability and energy savings. Only those properties that remain at a beneficial tt, or their combined cooperation, will yield all the advantages of the present invention.

In particular, compression/g is very difficult, if not impossible, to reduce sufficiently and safely in high volume production if used separately from the oil ring containing highly effective oil control devices. However, the above-mentioned oil pumping effect which causes extra oil consumption cannot be excluded.

If the oil ring is used separately from the compression ring, then the oil ring is exposed to the path of the gases from the normal compression ring and is thus , thereby receiving abrasive combustion residues produced and driven, which are responsible for the wear of the narrow contact interface with the cylinder of its swivel, and - in the soil force, the first 1 ring is forced to operate in such a cylinder with a normal roughness level A/l-2, whereas a cylinder with a very high abrasive content is used.

These two conditions are disadvantageous for properly protecting the narrow circumferential force-directing contact surface of the oil ring's elastic vanes against the cylinder without causing wear.
Visit

[Brief explanation of drawings]

FIG. 1 shows a piston ring set consisting of a compression ring and an oil ring. The figure which shows the piston arrange|positioned in the cylinder. 2 and 4 are enlarged cross-sectional views of a part of the piston 7 in the cylinder showing different embodiments of the compression ring. Figure 3 shows the separation of the compression ring.
FIG. Figures 5.6 and 7 show the composite compressed blowfish 1-* of Figure 4.
FIG. 3 is a plan view of three rings. FIG. 8 is an enlarged cross-sectional view taken along line 910A in FIG. 5; 9 and 10 are plan views of modifications of the rings of FIGS. 5 and 6. FIG. Figures 11 and 1' are perspective views of an oil ring and a modification thereof. 13 and 14 respectively show the 11th
FIG. 13 is a cross-sectional view of a portion of the piston showing a cross section of the oil ring of FIG. 12; FIG. 15 is a perspective view of an annular spacer for an oil ring. 16 and 18 are am diagrams of the oil ring of FIG. 11 and its modified example in a free state; FIGS. 17 and 19 are cross-sectional views of FIGS. 16 and 18; The figure is a perspective view of the gap protrusion provided on the oil ring of FIGS. 11.13 and 16. FIGS. Xt1 and 22 are perspective views of modifications of the ring shown in FIG. 11. FIGS. 23 and 24 show the deformation ipHt of the compression ring.
-Illustrated diagram. 25 and 26 are views showing details 1 of the modification of the compression ring shown in FIGS. 23 and 24. FIG. 12: Compression ring 14 Niji cylinder 21: Piston
25: Thin cut ring made of metal 26: Thin cut ring made of plastic material Patent applicant L'Opere 7-machi Rare @1 person Figure 1
Figure 2 Figure 9 Figure 10 Procedures Amendment (Method) December 1980 IO Director General of the Patent Office Kazuo Chikusugi 1. Indication of the case 1980 Original Patent No. 16482 2. Name of the invention Piston Relationship between Visto/Sygu Sect 3 and the Amendment Person Case Patent Applicant Address 7RanjEI! i Barry Neuilsiere Seine Puni Pearl Lysiele Pallas 11 Name
Roper Efurua (FI or 1 person) Nationality 72
77 Country 4, to the agent 108 address 5-5 Shinbashi 2-12 Koji-ku, Tokyo, date of amendment order November 12, 1972 El (shipment date 1971, 1 l
J5308) 6. Drawings subject to correction (Diagram 2a) 7. Contents of correction Annex 1 FIG. 20

Claims (1)

[Claims] (IJ, internal combustion engine mechanism is a modified JL for reducing friction and gas leakage in an assembly including a cylinder for a compressor, a piston, and a piston ring set.
The bait means has the same shape as the cylinder described above. At least one tube made of Nuchy # has a circular lip in toothed contact with the cylinder so that the Wc elastic force is regularly distributed.
Compression ring means consisting of two thin-walled cut rings and a sealing means for reducing the passage of gas through the gap in the cup part, even if it is not as much as t-llll5Fr. An assembly (2) characterized in that the closure means for sealing the cup F are connected in parallel with each other and are formed of an elastic material, and have a circular lip ring formed by its elastic tension. Two thin-walled cut rings (45, 411, 55611) are brought into contact with the cylinders (14, 44), and the upper ring (45) retains the independence of movement of these rings. Means (512, 912, 613,
101B, 614.1014). (3) said closure means for sealing said cut portion includes a comparative Assembly e according to claim 1, characterized in that it comprises plastic adjacent sealing means (310) (4), at least one of said compression rings (12, 22, 42); One elastic metal thin ring (25, 35
,45,411゜55.611 ,95.1011)
is distributed on its inner periphery with cutouts (916,1
016) Features 1 - Assembly according to claim 1 (Excellent) A cylinder, a piston, and a piston ring set for an internal combustion engine or a compressor? Nine improved reduction means are provided for reducing friction, gas leakage, and oil climbing in an assembly comprising a circular lip, the elastic tension of which reduces friction, gas leakage, and oil climbing. At least one thin-walled cut ring made of elastic metal that is brought into contact with the cylinder, and the play of the cut portion I! lt - a ninth closing means for sealing the passage of gas through it and a circular rim 1t - abutted against said cylinder through the effect of its diameter and both sides of the shoulder (715) 1t - mutually At least 1% thin-walled cantrings (26
, 76) Composite compression ring means consisting of toyoshi, with said rings having a small play (27) t in the groove of said piston.
- A ring made of the above plastic material (2
6, 76) t- Disposed between the groove surface of the crankshaft of the piston (21) and the metal ring (25°35), and the reduction means further includes an oil pipe during the downward stroke of the piston. Oil ring means (13, 113, 123,
133, 143, 2113° 2213), the oil ring means is formed from 11 spring steel pieces, and the spring steel pieces have very thin elastic transverse vanes ( 1117°1217, 1317.1417.
2117.2217) t-forming and the vanes in the direction of the lateral force are located on the common side of the above row located on the piston head side (1118, 1218, 1318, 1418, 201
8. 2118, 2218) to each other and to the piston, and to the cylinder (134, 144) by the edge of the row located on the side of the crank chamber through the elastic force of each vane. The outer 1111 surface of the blade is made to conform to the wall surface of the cylinder and forms an acute angle α゛ opening toward the bimeton head, and furthermore, the outer 1111 surface of the blade is made to form an acute angle α゛ which opens toward the bimeton head. piston head 1il
A closed elastic skirt part is sealed and opened to the crank chamber, and the oil ring (1317) is provided on the circumference of the piston.
1417), an annular inner fla (1326° 1426
) and means for returning the oil into the crank chamber. (6) An assembly comprising a cylinder, a piston, and a piston ring set for an internal combustion engine or a compressor, comprising an improved reduction means for reducing friction and oil rise, The reduction means include oil ring means (1B, 113
．． 123.133.143゜2113.2213)
i, the first to ring means are formed from one spring steel piece, and the spring steel piece has very thin and elastic transverse vanes (1117, 1217, 1317,
1417, 2117, 2217) t-formed. Moreover, the blades in the direction of the lateral force are placed on the piston head side.
18.2018゜2118.221s) K are connected to each other and connected to the binuton, and through the elastic force of the blade vane TFT, the edge of the row located on the crank chamber side connects the cylinder. (134,
144), and the outer direction of the blade is formed with the wall surface of the cylinder to form a conical acute angle αI opening to the piston head; Piston head Wt - is formed with a closed elastic skirt portion that is sealed and opens to the crank chamber, and the piston is provided with the oil rings (1317, 1417) on its circumference.
) at a height position of the blade, an m-shaped space (1326, 1426) for collecting scraped oil and a means for returning the oil pipe to the crank chamber; assembly. , (7), the above cylinder (14, 24, 34, 44
, 134, 144) discloses a patent for a tl # mold comprising a P3w surface having a much higher degree of polishing than that normally used! Assembly listed in Section 6 of the Cumulative Category. (8) The cut portion of the oil ring is provided with a closing stopper (
2034, 2035) T-, and the spacer has a thickness (1524) at least equal to the height of the protrusion (20B4.2035) of the stopper. Assembly according to clause 6 or 7. (9) The compressed binu tunneling t was made regular over its entire contour. A compression piston ring (consisting of a flat ring (2337) made of an elastic metal, preferably made of spring steel, having a known arbitrary cross section and a thin wall cross section, II
! The circumference 1-11ji of the ring is adapted to the shape and dimensions of the cylinder, and the ring has a wall thickness t- which does not exceed the wall thickness of the ring (23
39,2439,2639) +7) Action t-Uke&'j
The micro cylinder has at least 41 cuts in contact with the cylinder and is accommodated in the groove of the ring, and then the micro cylinder slightly increases its diameter when the ring is in a free state, so that the above When the ring is in the cylinder, -
In the force, the cut part (2541,
2648) ms A force which forms a play due to the thermal expansion book of the ring, and on the other hand is compressed by the micro to bring the v1 ring into contact with the cylinder. Claim 6: The expansion force is applied parallel to the circumference of the ring by causing the expansion force to be applied to the force tube, and the force tube is the same at each point on the circumference of the ring. Assembly according to paragraph 7 or #'i paragraph 8. (10 Le Joki Microsplash (2339, 2439)t,
A patent comprising a plurality of alternating radial partial cuts (2541 and 2542) in at least two t-1 groups, outer and inner, separated by a protrusion (2543). An assembly according to claim 9. (11), the above micro splash (2639)? An assembly according to claim 9, comprising a plurality of helical springs (2646) housed in holes (2647) formed in the face of the cut portion of the upper ring.