JPS63105234A - Internal combustion engine - Google Patents

Abstract

PURPOSE:To enable fuel to be transformed into power efficiently by means of a simple mechanism by allowing an internal combustion engine to be composed of an annulus-ring-shaped cylinder and two sets of piston which are placed in the cylinder so that they are movable. CONSTITUTION:Cylinder members 2, 3 are combined with each other so that an annulus-ring-shaped cylinder is formed. The cylinder is provided with the No.1 group of pistons 6 in plural number which are placed at equal distance from each other so that they integrally slide within the cylinder and the No.2 group of pistons 7, each of which is placed between the pistons 6. Hereupon, by repeating the following two strokes: one stroke in which ignition, explosion and intake are performed between the piston 6 and the piston 7 in the rear thereof, and at the same time, exhaust and compression are performed between the piston 6 and the piston 7 in the front thereof, and the other stroke in which, subsequently, ignition, explosion and intake are performed between the piston 7 and the piston 6 in the rear thereof, and at the same time, exhaust and compression are performed between the piston 7 and the piston 6 in the front thereof, the pistons 6, 7 are moved only in the fixed direction so that a main shaft 1 connected with these pistons is caused to rotate.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an internal combustion engine used as a power generating device that requires effective use of fuel.

[Conventional technology]

Conventionally, reciprocating internal combustion engines have been common, but these reciprocating internal combustion engines have a limit to how high they can rotate due to the inertia of the reciprocating parts, that is, the pistons and connecting rods. Furthermore, as the speed of rotation increases, the power required to operate the reciprocating parts increases, and there is a limit to the improvement in output per exhaust volume. Furthermore, the crank mechanism for converting reciprocating motion into rotary motion is complex, and air is drawn into a mechanism consisting of a pair of cylinders and pistons.

There were problems such as the need for valves and a complicated valve mechanism to carry out the four strokes of compression, explosion, and exhaust.

[Problem that the invention seeks to solve]

The problem to be solved by the present invention is to obtain an internal combustion engine that has few reciprocating parts, does not require valves and a complicated valve control mechanism, has a simple mechanism, and can convert fuel efficiently into power.

[Means for solving problems]

In order to solve the above problems, the internal combustion engine of the present invention includes an annular cylinder, two sets of pistons movably arranged in the cylinder, and a cylinder between the first piston and the second piston. The cylinder is constructed so that it can move in a fixed direction as a whole while changing the interval within a predetermined interval range, and furthermore, a spark plug, intake and exhaust ports are installed in the cylinder to produce four strokes: intake, compression, explosion, and exhaust. It is designed to generate power by causing the

In the internal combustion engine of the present invention, when the annular cylinder is divided into an even number of sections in order to carry out the above operations, the odd numbered sections are ignited forward in the direction of piston movement from any section. An exhaust port is provided at the rear of the stopper, an intake port is provided at the front of each even-numbered compartment, and a first intake port is provided within each compartment. Second
One set of pistons is arranged in each set, and ignition and explosion in an odd-numbered compartment will open a gap between the first set of pistons and the second set of pistons at the rear. At the same time, the space between the pistons of the second set in front is narrowed and exhaust air is discharged from the exhaust port. Compression is performed by narrowing the distance between the pistons of the second set, and air is taken in from the intake port by widening the distance between the pistons of the second set behind them, and then the pistons of the first set are By stopping and moving the second set of pistons forward, the same operation as described above is performed in each compartment, so that intake and compression are performed in the even-numbered compartments, and explosion and exhaust are performed in the odd-numbered compartments. ing.

Further, in the internal combustion engine of the present invention, the first set of pistons and the second set of pistons are moved forward and stopped alternately, so that the distance between each piston and the preceding and following pistons is changed within a predetermined distance range. However, in order to move the piston as a whole in a fixed direction, a piston movement control mechanism consisting of gears, a crank, and a cam is connected to a support member that supports each piston.

〔Example〕

An embodiment of the internal combustion engine of the present invention will be described below based on the drawings.

FIG. 1 is a partially cutaway perspective view of the first embodiment of the present invention, FIGS. 2 and 3 are sectional views, respectively, and FIG. 4 is an exploded perspective view showing each part disassembled. It is a diagram.

In these drawings, 1 is a main shaft, and 2 and 3 are a cylinder member having a circumferentially formed concave portion with a semicircular cross section, which together constitute an annular cylinder, which controls the movement of the piston, which will be described later. It is integrated with bases 4 and 5 that house the mechanism. 6゜7 are ring-shaped support plates 8 and 9, respectively.
The first and second sets of pistons are supported by the pistons, and the present embodiment has four sections, so that the pistons are located at positions 90° apart from each other symmetrically with respect to the center rule. 10.11 is a bevel gear fixed to the support plates 8 and 9, and 12 is a bevel gear rotatably supported on a shaft 14 with respect to the gear support plate 13, and meshes with the bevel gear 10.11. 15 is a crank supported by the shaft 14; 16 is a cylindrical cam having a cam groove 16a fixed to the base 5; and 17 is a convex portion connected to a sliding groove 18 attached to the gear support plate 13. It is a converter with 17 a.

A long hole 17b is formed in this converter 17, and the crank 1
The bin 15a provided in the converter 17 is the long hole 1 of the converter 17.
The crank 15 and the cylindrical cam 16 are connected to the converter 1 by being inserted into the cam groove 16a of the cylindrical cam 16 through the
They are connected via 7. As a result, gears 10,1
1.degree. 12 is connected to a cylindrical cam 16 by a crank 15, and these constitute a control mechanism for controlling the movement of the support plates 8, 9, and therefore the movement of the piston 6.7.

Also, the cylinder has a spark plug 21. The exhaust port n is the first one which will be explained next. In the third section, the intake port n is located in the second section. Each is provided in the fourth section.

Next, the operation of the above embodiment will be explained. First, the movements of the first set of pistons 6 and the second set of pistons 7 will be explained.

In this embodiment, as shown in FIG.
It is divided into four sections: n, III, and IV.
As mentioned above, the ignition plugs 21. The second section (2) and the fourth section (2), in which the exhaust port n is an even number, are provided with an intake port (o). Also a first set of four pistons 6a.

6b, 6c, 6d and a second set of four pistons 7a
, 7b, 7c, and 7d are all assumed to be in the positions initially shown. As the main shaft 1 rotates, each piston moves as follows by the piston movement control mechanism. In other words, when the main shaft rotates 135 degrees in the direction of the arrow △, the first set of pistons 6a, 6b, 6c, 6
d moves from the position of symbol A to the position of B. Meanwhile the second set of pistons 7a, 7b.

7c, 7dFiC! Do not move while stopped at the position.

Therefore, the distance between piston 6a and piston 7a.

The distance between the piston 6b and the piston 7b, the distance between the piston 6C and the piston 7c, and the distance between the piston 6d and the piston 7d are all increased. On the other hand, the distance between piston 6a and piston 7b, the distance between piston 6b and piston 7c, and the distance between piston 6a and piston 7b, piston 6
Distance between C and piston 7d, piston 6d and piston 7
The distance from a becomes narrower. During this time, the piston 76a
An explosion occurs between the piston 7a and the piston 6C and the piston 7C due to the ignition of the spark plug 21.
Air is exhausted from the exhaust port n between the piston 7b and the piston 6C and the piston 7d. In addition, between the piston 6b and the piston 7b, and between the piston 6d and the piston 7d, the intake air from the intake port n also flows between the piston 6b and the piston 7c.
Compression is performed in the compression parts of piston 6d and piston 7a.

Further, while the main shaft 1 rotates by 1c and rotates from 35 degrees to 450 degrees as seen from the initial position, the pistons 6 of the first group are rotated at the position indicated by the symbol B while the distance between the pistons of the first and second sets is kept constant. from position C to position C while the pistons 7 of the second set are marked C
Proceed from position to position A.

Subsequently, when the main shaft 1 rotates from 45° to 80° as viewed from the initial position, the pistons 6 of the first set are stopped at position C, but the pistons 7 of the second set are moved from position A. Move to position B. As a result, in the first section and the third section, the intervals between the second set of pistons 7a and the first set of pistons 6d and between the second set of pistons 7C and the first set of pistons 6b are widened, and the intervals between the second set of pistons 7a and the first set of pistons 6d are widened. The distances between the piston set 7a and the first set of pistons 6a and between the second set of pistons 7C and the first set of pistons 6c are narrowed. On the other hand, in the second section and the fourth section, the second set of pistons 7b and the first set of pistons 6a, and the second set of pistons 7d and the first
The distance between the pistons 6c of the second set increases 9, and the distance between the pistons 7b of the second set and the first set of pistons 6b, and the distances between the pistons 7d of the second set and the first set of pistons 6d become narrower.

During this movement of the piston, the first and third sections are
Explosion and exhaust take place in the compartment, and intake and compression take place in the second and fourth compartments.

Further, when the main shaft 1 rotates 100 times, each piston moves by a fixed amount while maintaining their respective positional relationships. This means that all pistons have advanced 90 degrees from their initial positions. Therefore, if the above piston movement is repeated, each piston will move forward as a whole.

The drum rotates by performing explosion and exhaust in the first and third compartments, and intake and compression in the second and fourth compartments.

Next, it will be explained that the piston movement control mechanism of the above embodiment enables the piston movement as described above.

FIG. 6 is a diagram showing changes in the angle formed between the shape of the cam groove and the reference direction (direction in which the crankshaft advances) of the crank 15 whose movement is controlled by the cam groove toward the crank H.

In this figure, for example, let us assume that the beginning of the main shaft 1 is 00 and the crank angle at that time is +600. When the main shaft 1 rotates, the gear support plate 13 rotates together with the main shaft 1, and the shaft 14 moves. This direction of movement is shown in FIG. 6 by a horizontal straight line X, while the pin 15a near the tip of the crank arm
moves along the cam groove. Therefore, as shown in the figure, the angle θ between the crank and the reference direction (the direction in which the shaft advances)
changes with movement. That is, as the main shaft 1 rotates, θ=+60° gradually decreases, and when the main shaft 1 rotates 35°, it becomes θ−60°. Furthermore, from 350 to 45°, θ
--Stands unchanged at 60°, but increases from about 45° to about 80°
So θ=+600. Next, from 80° to 90°, θ
=+60° remains.

In this way, in response to a change in the direction of the crank arm, the shaft 14 to which the shift flank is fixed rotates in the direction of travel due to the resultant force with the cam groove, and accordingly the gear 12 also rotates. In other words, while the main shaft 1 rotates, the gear 12 rotates as shown in FIG.
Rotate 20 degrees. The rotation of this gear causes the support plate 8 having the first set of pistons 6 and the second set of pistons 7 to
The support plate 9 having the same amount moves in the opposite direction to the gear 12 by the same amount. On the other hand, as the main shaft 1 rotates, the gear 12 fixed thereto rotates around the main shaft 1 and advances by that amount.

Therefore, the support plates 8 and 9 move by an amount that is the sum of the amount of movement caused by the rotation of the main shaft and the amount of movement (including plus and minus) caused by the rotation of the gear 12.

Now, if the amount of movement of the support plate due to the gear 12 rotating 120 degrees from +60 degrees to -60 degrees is set equal to the amount directly advanced by the rotation of the main shaft 1, then the support plate whose movement direction is the same in both directions will be It will move twice and the opposite support plate will not move. That is, when the gear 12 moves from P to P' in FIG. 7, the right support plate 8 moves twice as much as the rotation of the main @1, but the right support plate 9 does not move at all. In other words, R1 on the left moves to J, and R2 on the right does not move at all at R4.

From the above, when the main shaft 1 rotates from 00° to 35°, one support plate (the support plate to which the second set of pistons is attached) substantially stops moving, and the other support plate (the first set of pistons is attached to it) stops moving. Only the support plate (on which the piston is attached) rotates by an angle twice the angle of the main shaft 1. Then from 35o to 45°
Until then, both support plates rotate with the same amount of deviation at that time. Furthermore, when rotating the main shaft l from 45° to approximately 80°, 1. As mentioned above, the crank 15 (gear 12) rotates from -60° to +6
In order to rotate in the opposite direction to 0°, the support plate 8 (the support plate to which the first set of pistons is attached) stops, and only the support plate 9 (the support plate to which the second set of pistons is attached) moves to the main shaft. It rotates by twice the rotation angle of 1. Furthermore, while the main shaft 1 rotates from 800 degrees to 90 degrees, both support plates rotate together while maintaining the same state. Due to this rotation of the support plates 8, 9, each piston 6.7 moves within the annular cylinder in the same positional relationship as the relationship between the two support plates. The movement of this piston is when the main shaft 1 is 0.
Regarding rotation from ° to 90 °, the same movement is 90 °
It is clear that this is repeated every degree. Therefore, it is clear that the piston movement control mechanism of the above embodiment allows the piston to move in the internal combustion engine of the present invention as described above.

Next, a second embodiment of the present invention will be described. 8 to 11 are views showing this second embodiment, in which FIG. 8 is a partially cutaway perspective view, FIGS. 9 and 10 are both sectional views, and FIG. The figure is an exploded perspective view showing each component exploded.

In these figures, 1 is the main shaft, and 2 and 3 are cylinder members that are combined to form an annular cylinder. The cylinder member has a concave portion with a semicircular cross section formed on the circumference, and is a control that controls the movement of the piston, which will be described later. It is integrated with bases 4 and 5 in which the mechanism is housed. 6 and 7 are first supports supported by ring-shaped support plates rotatably supported by the main shaft 1, respectively.
and a second set of pistons, since this embodiment has four compartments, these pistons are symmetrically arranged around the central axis by 90° each.
° Located at a distance. -These structures are the first
This is substantially the same as the embodiment.

Further, 31 and 32 are driving gears rotatably supported by shafts 33 and 34 on a support plate 30 fixed to the main shaft 1;
A is a fixed gear fixed to the bases 4 and 5, and the audience 37 has one end connected to the support plates 8 and 9 with pins 39 and 40, and the other end connected to the drive gear with pins 41 and 42. This is a crank. A control mechanism is provided in which the main shaft and the piston are connected through a crank and a driving gear by these parts, and controls the rotation of the main shaft in a certain direction and the movement of the first set of pistons and the second set of pistons. It consists of

Next, the movement of the main shaft and each piston by the control mechanism in this embodiment will be explained. FIG. 12 is a diagram showing the rotation angle of the main shaft, the trajectory of the crank support pin of the drive gear, and the rotation angle of the crank support pin of the piston support plate, and FIG.
The figure is a diagram showing the rotation angle of the main shaft on the horizontal axis and the rotation angle of the first set of pistons and the rotation angle of the second set of pistons on the vertical axis from FIG. 12.

In FIG. 12, when the main shaft 1 rotates in the direction of the arrow, 41.
42 also move along lines 43 and 44, respectively. This causes the pins 39 and 40 at the other end of the crank to move as shown. In other words, the pin 39 moves gradually at first, gradually moves faster, and then moves slowly again. On the other hand, the pin 40 starts out fast, gradually slows down, and becomes fast again. Therefore, the support plates 8, 9 also move in the same way as the pins 39, 40, respectively, and so do the pistons 6, 7. Piston 6 at this time.
Figure 13 shows the movement of 7.

As can be seen from FIG. 13, the main shaft 1 of the first piston 6 and the second piston 7 located forward in the direction of movement are
. The interval increases while rotating from t4 to t4, and decreases while rotating from t4 to t, □.

Similarly, the distance between the second piston and the first piston located in front of it in the direction of movement is t on the main axis. It contracts while rotating from t3 to t3, and expands as it rotates from t3 to t1□.

By controlling the rotation of the main shaft and the movement of the nine-car set of pistons by the control mechanism, the same operation as in the first embodiment is achieved.

The control mechanism of the second embodiment also controls the piston to move in a manner similar to that of the control mechanism of the first embodiment. Therefore, as in the first embodiment, the first set of pistons and the second set of pistons move in a fixed direction while changing the distance between them, repeating ignition, explosion, intake, exhaust, and compression, and Rotate.

In this case, in the second embodiment, both pistons stop as shown in FIG.
(The piston is stopped at a certain position) The moving speed changes and the distance between the pistons becomes wider or narrower.

In the control mechanism of this embodiment, the ratio of the diameters of the fixed gear 35 and the drive gears 31, 32 is 4:1 (in the case of four 1 m pistons). In addition, it is desirable that when the pin 41 or 42 of the crank 36, 37 is at the farthest position from the main shaft, the angle between the direction connecting this pin and the main shaft and the crank is 90 degrees or more, in order to prevent the piston from moving backwards. . Furthermore, the positions of pins 41 and 42 are 1. Drive gear 31.32
It is necessary to make the locus of the pins 41 and 42 smaller than the effective diameter of the pins 41 and 42 so that they do not run against the direction of travel. Further, the length of the crank needs to be sufficiently longer than the diameter of the driving gear plus the distance between the joint of the dog gear, the support plate, and the crank, and should be, for example, nine times the diameter of the pinion. This smoothes the movement of the piston. Further, the crank is provided in front of the support plate in the rotational direction. This increases the speed in the opening direction between the pistons and increases the effectiveness of using explosive force.

〔Effect of the invention〕

According to the present invention, the structure is simple because no valve or valve mechanism is required, and there are few reciprocating parts such as pistons and connecting rods, and most of the movement is in one direction (rotation direction of the main shaft), so fuel is not consumed. It is possible to obtain an internal combustion engine that can efficiently convert into power, has low intake/exhaust resistance, and has a large output per exhaust volume because both sides of the piston and the cylinder are continuously utilized.

[Brief explanation of the drawing]

FIG. 1 is a partially cutaway perspective view of the first embodiment of the present invention, FIGS. 2 and 3 are sectional views of the same embodiment, and FIG. 4 is an exploded perspective view of the same embodiment. , FIG. 5 is an operational diagram of the present invention, and FIG.
The figure shows the shape of the cam groove and the movement of the crank, Fig. 7 shows the relationship between the movement of the crank and the movement of the gears, and Fig. 8 is a partially cutaway view of the second embodiment of the present invention. 9 and 10 are cross-sectional views of the second embodiment, FIG. 11 is an exploded perspective view of the second embodiment, and FIG. 12 shows the rotation angle of the main shaft and the crank of the drive gear. FIG. 13 is a diagram showing the trajectory of the support bottle and the rotation angle of the crank support pin of the piston support plate, and FIG. 13 is a diagram showing the relationship between the rotation angle of the main shaft and the rotation angle of the first set and the second set of pistons. . 1... Main shaft, 2.3... Annular cylinder, 4, 5...
- Base, 6... First set of pistons, 7... Second set of pistons, 10.11... Bevel gear, 15... Crank, 16... Cylindrical cam, 17.・Converter, 2
1... Spark plug, exhaust port, n... Inlet port, 31, 3
2... Drive gear, A... Fixed gear, 36.37.
··crank.

Claims (1)

[Claims] an annular cylinder; and a plurality of first cylinders arranged at equal intervals that slide integrally within the cylinder.
and a second set of pistons sliding together in the cylinder and positioned equally spaced between each piston of the first set; The set of pistons and the second set of pistons are configured to rotate only in a fixed direction as a whole while changing the interval, and between the first set of pistons and the second set of pistons behind them. The process of ignition explosion, intake, and simultaneous exhaust and compression between the first set of pistons and the second set of pistons in front of it, and then the second set of pistons and the first set of pistons behind it. By repeating two processes: ignition explosion and intake between the pistons of the second set and the pistons of the first set in front of the second set of pistons. An internal combustion engine that moves a piston in the above-mentioned fixed direction and rotates a main shaft connected to the piston.