KR101527916B1

KR101527916B1 - An internal combustion engine in which an oscillating oscillation shaft and a rotating crankshaft are connected and operated

Info

Publication number: KR101527916B1
Application number: KR1020140126577A
Authority: KR
Inventors: 김수호
Original assignee: 김수호
Priority date: 2014-09-23
Filing date: 2014-09-23
Publication date: 2015-06-16
Also published as: WO2016047987A1

Abstract

The present invention relates to an overall internal combustion engine. In the conventional engine, the expansion pressure generated in the piston is directly transmitted to the crankshaft. In the present invention, however, the expansion pressure generated in the piston is transmitted to a new shaft And the crankshaft is rotated by the crankshaft. The present invention relates to an internal combustion engine that operates in such a manner that it is transmitted to a crankshaft, and the side pressure generated in the piston can be reduced and the diameter of the crankshaft when the crankshaft rotates can be made larger than the stroke distance of the piston, And an internal combustion engine capable of increasing the maximum pressure point of the explosion stroke to near the top dead center of the conventional engine.
[Index]
Vibration shaft, lever, seesaw (see saw)

Description

An internal combustion engine in which an oscillating oscillation shaft and a rotating crankshaft are connected and operated.

The technique of the present invention relates to a general conventional four-stroke internal combustion engine.

This is an internal combustion engine using the principle of seesaw, that is, the principle of leverage.

SUMMARY OF THE INVENTION The present invention has been made to solve the problems occurring in the first crankshaft, that is, long and heavy, frictional losses of the rotating parts, and the like, which are generated in the second cylinder and the piston And the maximum pressure of the third expansion pressure is increased to the vicinity of the top dead center to efficiently transmit the maximum pressure to the fourth crankshaft.

In the conventional engine, a new vibrating shaft operated by the principle of leverage, that is, a seesaw principle, is installed and a piston is installed at both ends of the biaxial axis, and the vibration is transmitted to rotate the biaxial dia.

The advantage is that the first organs are light, the side pressure which is generated in the second cylinder hardly occurs, and the energy absorption rate is lowered due to the disadvantage of the conventional short stroke engine, that is, the short stroke distance of the crankshaft. However, in the present invention, Since the axis of rotation of the shaft is rotated by a long stroke by the principle of the lever, the energy absorption rate can be increased and the maximum expansion pressure can be increased to the upper limit of the prior art, so that a larger expansion pressure can be obtained.

Fig. 1 (a) is an assembled three-dimensional diagram of a two-cylinder engine according to the present invention, Fig. 2 (b) is a three-dimensional diagram of a connecting rod, Fig.
Fig. 2 (a) is a front view of the vibration shaft bundle, Fig. 2 (b) is a perspective view of a vibration shaft bundle having two piston mounting pins, and Fig. 3 is a three-dimensional view of a vibration shaft bundle having four piston mounting pins.
Fig. 3 (a) is a cross-sectional view of a two-cylinder engine, and Fig. 2 (b) is a linear view showing movement paths of principal points.
Figs. 4 and 5 are linear diagrams showing movement paths of principal points as shown in Fig. 3. Fig.
6 (a), 6 (b), 6 (c) and 6 (d) are sectional views when the inventive engine rotates by 90 degrees.
7 (a), 7 (b), 7 (c) and 7 (d) are linear state diagrams when the inventive engine rotates by 90 degrees.
8 (A) is a three-dimensional view of a four-cylinder engine according to the present invention. (B) is a three-dimensional view of a connecting rod rod, (C) is a three-dimensional view of a vibration shaft bundle having two piston mounting pins, (D) is a cross-
9 (A) is a three-dimensional view of a four-cylinder engine according to the present invention. (B) is a three-dimensional diagram of a connecting rod rod, (C) a swing shaft bundle, connecting rod and crankshaft with four piston mounting pins.
10A is a side pressure in a conventional engine, and FIG. 10B is a side pressure in the present invention. FIG.
FIG. 11A is a view showing a process of transmitting an expansion pressure, and FIG. 11B is a view showing both of FIGS. (B) is a view showing a process of transferring the expansion pressure of the piston to the crankshaft in the engine of the present invention, and (c) shows a process of transferring the expansion pressure of the piston to the crankshaft in the conventional engine.

1 (A) is a three-dimensional view of a two-cylinder engine assembled by the present invention. (B) is nothing but means that the piston is connected to the connecting rod by a solid body to (18) and (19) of (C). (C) is a main part of the present invention, and the whole is hereinafter referred to as a vibration shaft bundle . (D) is a cross-sectional view of the drawing.

Conventional engines are connected and operated in the order of piston-connecting rod-crankshaft but in the present invention they are connected in the order of piston-connecting rod-vibration shaft bundle (c) -crank shaft. Of the vibrating shaft bundles 18 and 19, the vibrating shaft bundle is extended to the rear of (14) and (15) and protrudes in the same shape as the front. And the word bundle of vibration shaft bundles means that the whole bundles together into one mass state. If the agency is actually produced, the shape of (B) (C) will be considerably changed, unlike the drawings.

In conclusion, it can be understood from FIG. 1 that the two-cylinder engine is connected in the piston-connecting rod-oscillation shaft bundle (c) - (29) -crank shaft order.

FIG. 2 shows how the vibration shaft bundle of the present invention is designed. (A) is a front view of the shafts of the vibration shafts. (B) (C) is a three-dimensional diagram of a bundle of vibration shafts. (15) and (17) to the right are referred to as piston mounting arms and the portions 18 and 20 represented by the circles on this arm are referred to as " (19) and (21) are referred to as a piston mounting pin , and the center of the left pins is a and the center of the right pins is g, the distance from the point 1 to the point a or g is r1. The four piston mounting arms 14, 15, 16 and 17 are jointed and in particular the two piston mounting arms 14 and 16 are installed parallel to each other And the remaining piston mounting arms 15 and 17 are also installed parallel to each other. (B) and (c) are all bundled together in one lump, (b) is called a bundle of vibration shafts with two piston mounting pins , and (c) is called a bundle of vibration shafts with four piston mounting pins . Cylinders having a central point O 1 protruding forward and backward are hereinafter referred to as vibration shafts 13, and both end portions of the vibration shafts are fixed by a bearing so as to vibrate. The portion protruding toward the points t, s, and e is hereinafter referred to as a vibration distance determining arm 23 and is not shown in (b) and (c) existing in the cracks at the lower end of the vibration distance determining arm. is referred to as less vibration as the crank pin and the shape and role of the pin in the engine drive pins (24), that the center of the pin 24 the t, s, e, r2, r3, r4 is a pin at the center ○ 1 And this distance is called the length of the oscillating distance determining arm . Here, the piston mounting arm and the vibration distance determining arm are orthogonal to the vibration axis 13, respectively. In addition, the oscillating distance determining arm 23 is shown in three cases in (A), but it is drawn for comparison. Only one is determined when the engine is actually manufactured as shown in (B) and (C). (A), and more importantly, the length r4 of the oscillating distance determining arm is larger than the length r1 of the piston mounting arm. Therefore, only r1 <r4 will be described in the following description, and r1 = r3 and r1 > R2, only conclusions are drawn.

The vibration shaft bundle mentioned above is the same principle as the seesaw installed in the children's playground. In FIG. 2, the point 1 is the center of the seesaw, and the portions protruding on both sides, that is, the piston mounting arms 14, 16, 15 and 17 are used as the seesaw plates, The piston mounting pins 18 and 20 having the center point a and the piston mounting pins 19 and 21 having the center point g are considered to be the seats for human being. Two of them are installed on both sides, one on each side and two on both sides are seated in a chair which is distant from the center by r1. In (c), joint seats are arranged parallel to each other, In this case, two people on one side and four people on both sides can be thought of sitting on a chair. The three oscillation distance decision arms (23), which are in the lengths r2, r3 and r4 in ○ 1 and below the seesaw in which the person sits, are not located in the seesaw. The length r1 of the piston installation arm and the length of the oscillation distance determination arm As a comparison, three of them are expressed simultaneously. In fact, only one of the three is determined and installed as shown in (b) and (c).

In other words, the center of the seesaw ○ 1 is the center of the oscillation axis, the seesaw length r1 is the length of the piston installation arm, the person is the piston and the connecting rod, the chair corresponds to the piston installation pin, The force is equal to the expansion pressure generated in the cylinder and the piston. 3, the vibration distance determining arm 23 under the seesaw plate plays a role of determining the diameter of the crank that rotates according to the length of the oscillation distance determining arm regardless of the stroke distance of the piston. In the conventional engine, although the stroke distance of the piston and the diameter of the crankshaft are the same, according to the present invention, the rotation diameter of the crankshaft may be larger than the stroke distance of the piston depending on the length of the oscillation distance determining arm, It may be possible to make it known beforehand. In the future, the diameter generated when the distance from the center of the crankshaft to the center of the crankshaft is rotated by a radius is called the stroke distance of the crankshaft.

Next, let us examine where the points t, s, and e, where the radius r2, r3, r4, at the center point ○ 1 can exist. The location of the points that may be present is shown in Figure 2,

When the lengths of r1 and r2 are compared, r1 > r2. The points satisfying this relation are all points on the circumference z, and all can be t.

When the lengths of r1 and r3 are compared, r1 = r3. Points that satisfy this relationship are all points on the circle y, and all can be s.

When the lengths of r1 and r4 are compared, r1 <r4. Points that satisfy this relationship are all points on the circumference w and can all be e.

Therefore, the oscillating distance determining arm 23 having the points (t, s, e) as the center of the oscillating distance determining pin is not limited to the position shown in the figure of (B) Can be installed. In FIGS. 3 and 5, the mounting positions of the oscillating distance determining arms are different.

2, the position and length of the oscillating distance determining arm 23 can be changed, but it can be seen that only the position and length of the oscillating distance determining arm 23 are determined and installed. ) Are understood to move as a seesaw, with each point being the center of the point ○ 1. And the sign and meaning of the terms used in the invention. In the following description, it is assumed that r1 <r4. Understand this fact and understand the other two r1 = r3 and r1> r2.

Then, it is determined whether the length of the vibration is determined by the installed oscillation distance determining arm 23 and transmitted to the crankshaft.

FIG. 3 is a two-cylinder engine as shown in FIG. 1, but is applied to a four-cylinder engine as shown in FIGS. 8 and 9 at the same time. Considering the piston position in the cylinder in the four-cylinder engine as shown in FIGS. 8 and 9, the four pistons in the four-cylinder engine act like two pistons in the two-cylinder engine because the two pistons are always in the same position in pairs .

Fig. 3 (a) is a sectional view, and Fig. 3 (b) is a linear view showing a moving path and a moving distance of each center point p, a, g, e, ○ 1 and ○ 2 are fixed points that do not move, ○ 1 serves as the center point of vibration as when the seesaw goes up and down, ○ 2 is the center of the crankshaft, 3, the left piston 05 is positioned at the top dead center and the right piston 06 is positioned at the bottom dead center. When the right piston 06 reciprocates vertically, the connecting rod 09 (FIG. 3) 10), the point a and the point g are moved up and down like a seesaw, that is, they vibrate. In other words, the point a moves along the arc of radius r1 to point b by h1, and the point g moves along the arc of radius r1 to k and to the straight line by h1. At this time, h1 is the stroke distance of the piston. At this time, the center point e of the oscillation distance determining pin 24 also moves radially by f2 along the line r4 by h2 as a straight line distance. If the distance between the two points is r6 and the length of r6 is half of the length of the line ef, that is, h2, the radius of circle 2 is r6 and the diameter is h2, the stroke distance of the crankshaft is h2. And the length of the line segment em is the length of the connecting rod 29. The length of the connecting rod here must be longer than h2. In this case, as shown in the figure, the straight line distance of the segment ef is equal to the straight line distance of the segment cd by h2. First, when r1 <r4, h1 <h2, that is, the stroke distance of the crankshaft is larger than the stroke distance of the piston. The line segment ef has two points on the circumference w and the center of the crankshaft ○ 2 exists on the extension line of the line segment.

If we think the same way, we substitute r3 or r2 for r4 in the above sentence,

Second, when r1 = r3, h1 = h2, that is, the stroke distance of the piston and the stroke distance of the crankshaft are the same.

The point corresponding to the segment ef is the two points on the circumference y, and the center of the crankshaft ○ 2 exists on the extension line of the contour line.

Third, when r1 > r2, h1 > h2, that is, the stroke distance of the crankshaft is smaller than the stroke distance of the piston.

The point corresponding to the line segment ef is the two points on the circumference z and the center of the crankshaft ○ 2 exists on the extension line of the line segment.

It can be seen from the above result that the stroke distance of the crank when the stroke distance of the piston is constant is determined by the distance from the center O of the oscillation axis to the center e of the oscillation pin 24, that is, the length of the oscillation distance determining arm.

3, the stroke distance of the piston is h1, the length of the piston mounting arm is fixed at r1, the point e and the point f are on the same circumference w, and the center of the crank (o2) it is understood that the length of the radius of the crank varies by the length of the oscillation distance determining arm 23 in the above three cases when it is on the extension line of ef. It is important to understand that, in the first case, when the piston reciprocates in the short stroke, the energy absorption rate can be increased by rotating the crank in the long stroke.

Let us now consider, in Fig. 4, the case where r1 <r4 and the point e is naturally a point on the circumference W but the point f 'corresponding to the point f is not a point around the same circle.

Fig. 4 is a view similar to Fig. 3 except that the point f is not a point on the circumference w, but a point f 'outside the circumference. The length of the line ef and the length of the line ef' are the same. The radius of the crankshaft is r6 'as shown in the figure when the center of the crank is held at r6' on the same extension line from the point where the point m 'is the same as the length of the line em on the extension line of the segment ef' The line segment em 'is the connecting rod 29 and its length is equal to em.

The circumferential circle q represented by the dotted line is a circle whose center is the radius of the e radius, and the point e is reciprocating motion from the circle w to the point f, so that the circumference of which the radius is the center line em ' , The circle is exerted on the circumference q and all the circles inside the circle x are satisfied, so that the engine is operated. However, since r6> r6 'as in the drawing, the stroke distance of the crankshaft is equal to the distance between the two points e and f passing through the same circumference Is smaller than when.

As a result, the center of the crankshaft connected to the oscillation shaft bundle is the point existing on the extension line of the line ef passing through the same circumference or the point near the extension line, but the crankshaft stroke is maximum when the two points pass the same circumference.

5 compares the lengths of r1 and r4, and r1 < r4. Points that satisfy this relationship are all points on the circumference w, all of which can be e. As shown in FIG. 5, when the position of the point e is different from the position of FIG. 3 and the center point of the crank is located at the point e, As shown in Fig. And the center point of the crank ○ 2 can be the center of the crank axis if it is on the point e, point f, on the straight line ef, or the point near the straight line ef. Here, the cylinder and the oscillating distance determining arm are not provided with interference with each other, that is, the oscillating distance determining arm is provided on the front surface of the cylinder. In the case of r1 = r3 and r1 > r2, the point s and point t, which correspond to the point e, can be shown in the drawing.

As a result, the oscillating distance determining arm 23 including the points (t, s, e) can be installed not only at the position shown in the figure based on the circle 1, but also in any direction of 360 °. Particularly, as shown in the drawing, it is understood that the height of the engine can be lowered when the vibration distance determining arm 23 is positioned in the direction of the piston.

FIG. 6 is a cross-sectional view of the four-stroke internal combustion engine of the present invention rotated by 360 degrees, and FIG. 7 is a linear view. Describing the relationship at the time of two rotations,

(A), when the left piston is in the initial stage of expansion and the right piston is in the compression starting stage,

At this stage, the 90 ° rotation (B) is the middle inflation on the left,

At this stage, the 90 ° rotation (C) is the initial stage of the exhaust,

At this stage, (D) rotated 90 °, the middle of the exhaust is on the left side,

If you rotate 90 ° in this step, you will go back to step (A).

At this stage, the 90 ° rotated (B) is the middle of the suction, the middle is the middle of the exhaust

At this stage, the 90 ° rotation (C) is the initial compression, the right is the suction initial

At this stage, (D) rotated by 90 ° is the mid-compression stage on the left side,

At this stage, the next step is repeated in the order of (a), (b), (c), (d).

In conclusion, it should be understood that in FIGS. 6 and 7, it is understood that the four-stroke cycle of the two-cylinder four-stroke engine is understood and that the four-cylinder cycle including four pistons as shown in FIGS.

8 (A) is a three-dimensional figure in which a four-cylinder engine is installed. That is, two pistons (05, 07) are attached to one piston mounting pin (18) and two pistons (06, 08) are mounted on the other piston mounting pin (19) It is stereoscopic. (B) is a variation of the large end portion of the connecting rod, which means that two pistons can be attached to one piston mounting pin. In other words, if the present invention is actually manufactured as an engine, the large end portion of the connecting rod is a rotating portion in a conventional engine, but in the present invention, the vibrating portion can be a quite different shape. Although not pictured in the drawing, a total of four pins are installed on both sides of the piston mounting pin on the piston mounting arm on one side, and four pistons on the upper and lower sides of the piston. I will reveal. (A) is a sectional view of (a), the position of the two pistons (05) (08) and the remaining two pistons (06) (07) are always the same, The conclusion is as follows. That is, the continuous operation diagrams as shown in Figs. 6 and 7 are omitted. Therefore, a four-cylinder engine can be manufactured using a vibration shaft bundle having two piston mounting pins. Although not shown in the drawings, two crankpins are installed on one crankshaft at an angle of 90 degrees and two connecting rods 29 are connected to two cylinders of four cylinders installed as shown in FIG. 8 to form an eight- When three crank pins are installed on one crankshaft at an angle of 60 degrees and three connecting rods of four cylinders installed as shown in Fig. 7 are connected by three connecting rods 29, an engine of twelve cylinders is formed. Four 45-degree crankpins are installed, and four connecting rods 29 as shown in FIG. 7 are connected by four connecting rods 29 to form a 16-cylinder engine. In this way, a larger-sized four- Multi-cylinder organs can also be made.

FIG. 9 is a drawing of a four-cylinder engine using a vibration shaft bundle (C) having four piston mounting pins. In FIG. 9, two piston mounting pins 18 and 20 located on the left side and two piston mounting pins 19) A four-cylinder engine in which four pistons are installed, one piston in one direction and one piston in one direction, (a) is a three-dimensional diagram, (b) is a three-dimensional diagram of a connecting rod, Is a diagram showing a three-dimensional view of a vibration shaft bundle, a connecting rod 29, and a crankshaft.

8, the positions of the pistons 05, 07 provided on the left piston mounting pins 18, 20 and the pistons 06, 08 provided on the right piston mounting pins 19, 21, respectively, Is always the same and the results reach the same conclusions as in the two-cylinder system. That is, the continuous operation drawing is omitted as shown in FIGS. Therefore, a four-cylinder engine can be manufactured by using a vibration shaft bundle having four pistons. In the same manner as in FIG. 8, a four-cylinder engine installed as shown in FIG. 9 can be used to make a multi-cylinder ventilation pipe of four cylinders, such as an eight cylinder, a twelve cylinder and a sixteen cylinder.

It should be noted here that even when the crankshaft is extended to two, three or four crankshafts or crankshafts, all of the crankshafts are connected and rotated in one lump, but the vibrating shaft shafts oscillate independently without being connected to each other even when the number thereof increases.

As a result, it can be understood from FIGS. 8 and 9 that a four-cylinder engine can be manufactured by using two sets of piston mounting pins or four sets of piston mounting pins, and as shown in FIG. 8 or 9 It is understood that the four-cylinder engine is two, three, four, and so on, connecting the crankpin to the crankshaft that has the proper number of angles to form a proper angle makes it a four-cylinder engine as in the case of an 8-cylinder 12-cylinder 16-cylinder engine. .

Fig. 10 shows the magnitude of the side pressure generated in the cylinder and the piston. The side pressure when the piston is located between the top dead center a and the bottom dead center b is examined. Based on this, the side pressure when the expansion pressure is maximum Should be able to. That is, the center point of the piston is moved from p to p ', and when the crank pin is rotated 90 ° from a to a', the distance a from the center line on which the piston is moved to a 'is expressed as the magnitude of the side pressure. If α is large, side pressure is large.

(A) shows the side pressure generated in the conventional engine. α is very large.

(B) is a diagram showing the side pressure of the present invention. [Alpha] is only about 1/4 of the above.

(C) is a view for reducing the side pressure. In (b), the center of the oscillation axis ○ 1 is not shifted but the cylinder and the piston are shifted to the left by β.

(D) is a view in which only the cylinder and the piston in (B) are slightly moved to the right. (C) In (D), the stroke distance of the piston is slightly shorter than that of (B). From the above results, it can be seen that the side pressure of the present invention is significantly lower than that of the conventional engine.

In conclusion, it should be understood that the side pressure of the conventional engine and the side pressure of the present invention should be comparable to each other, and that the side pressure between the cylinder and the piston is significantly reduced in the present invention.

Fig. 11 is a view showing the expansion pressure generated in the piston to be transmitted to the crankshaft. Fig. 12 (b) is a diagram of the present invention, And the relationship is enlarged at the same rate.

(C) in the conventional engine, point e is the center point of the piston, that is, the piston pin is located, line segment em is the length of the connecting rod, and the point m is the center point of the large end of the connecting rod and the center point of the crank pin. The center point e of the piston reciprocates from the top dead center e to the bottom dead center f along the straight line segment em. In this case, when point e moves to j, m moves to m ", and line segment jm" represents connecting rod and line segment is its center line. If the point j is the point at which the explosion pressure is maximum, the angle between the line segment jm at which the piston moves at this time and the center line jm "of the connecting rod is referred to as θ.

(B) is a view according to the present invention, that is, the lower part of FIG. 3, connecting the center point m of the crank pin to the center point e of the vibration distance determining pin 24 is connected by the connecting rod 29, Center is the center of the crankshaft and point e is the center of the oscillation distance determining pin when the piston is at the top dead center and point f is the center point of the oscillating distance determining pin when the piston is at the bottom dead center. At this time, when point e moves along the circumference to the point i, m, the center point of the crank pin, moves to m ', and the line im' is the connecting rod and the center line of the connecting rod. Assuming that the point i is the point at which the explosion pressure is maximum, the angle between the line em and the center line im 'of the connecting rod is denoted by θ. If the angle? Is large, the energy absorption rate in the crankshaft is high.

(A), (b) and (b) are drawings in which the two drawings are enlarged at a constant ratio and shown in duplicate. (A), it can be seen that θ> θ 'by comparing angles θ and θ'. The large angle here means that the crankshaft can absorb the explosion pressure. It can be inferred that the relation θ> θ '(a) always holds when i or j moves near the top dead center e.

As a result, it is understood that, in the present invention, the expansion pressure peak can be made closer to the top dead center than the conventional engine, so that the expansion pressure can be made larger and the pressure can be more easily absorbed into the crankshaft.

01, 02, 03, 04: Cylinder. 05, 06, 07, 08: Piston.
09, 10, 11, 12: Connecting rod.
13: Both sides of the vibration shaft are fixed by bearings.
14, 15, 16, 17: Piston mounting arm .
18, 19, 20, 21: Piston mounting pins .
23: Determination of oscillation distance called arm .
24: Determination of oscillation distance called pin .
25: Crankshaft. 26: Crank arm. 27: Crank pin. 28: Fly wheel.
29: Called the connecting rod .

Claims

A piston mounting arm protruding in a direction perpendicular to the center line and having the same shape and size in both directions at a point on the center line (O1) of the cylinder (13) fixed by the bearing so that both ends can vibrate, The piston mounting pins 18 and 19 for installing the pistons at the distal ends of the pistons are installed at the same distance from the center line so that two pistons 05 and 06 And a vibration distance determining arm 23 protruded so as to be perpendicular to the center line regardless of the direction at a point in the line of the center (1) of the cylinder 13 And a vibration distance determining pin 24 is provided at a distal end of the piston and a point on a straight line passing through two points (e and f) where the vibration distance determining pins 24 when the piston is located at the top dead center and the bottom dead center, Or a point near the crankshaft is set to be the center (O2), and a crankshaft The crankshaft 25 is rotated and the protrusions 14 and 15 orthogonal to the oscillation axis 13 are connected to the oscillating distance determining pin 24 by connecting the crankshaft 25 and the oscillating distance determining pin 24, (23) is subjected to vibration movement such as seesaw, and the stroke distance of the crankshaft is determined by the length of the installed vibration distance determining arm (23), and the internal combustion engine is operated.

The method according to claim 1,
The piston 07 is further provided on the piston mounting pin 18 so that the piston 07 is provided in the upper and lower positions and the piston 08 is further provided on the piston mounting pin 19 so that the pistons 08 are vertically disposed. ) (07) (06) (08) is installed and operated.

Claim 1
Piston mounting arms 16 and 17 protruded in both directions perpendicular to the center line at a point existing on the center line and piston mounting pins 20 and 21 provided at the distal end of the mounting arm Four piston mounting pins 18, 19, 20, and 21 are installed on the piston mounting arms 14 and 15 and the piston mounting pins 18 and 19, (05), (06), (07), and (08) are mounted in a one-to-one correspondence to the internal combustion engine.

The method according to any one of claims 1 to 3,
When the claimed internal combustion engine is considered as one set, the angles of the crank pins are adjusted so that the intake, compression, expansion and exhaust strokes of all the pistons are sequentially generated in the internal combustion engine, so that only the crankshaft is connected in a straight lump , Wherein at least two crankpins and two or more vibrating shafts provided with pistons rotate independently of each other when the crankshaft connected thereto is rotated.

delete