JPS5810570B2 - Nishitsugatafukudou Piston Ninenkikan - Google Patents

Description

[Detailed description of the invention] The present invention relates to reciprocating internal combustion engines.

Prior to the present invention, a large number of internal combustion engines existed for obtaining either reciprocating or rotary motion. Special types of structures have been needed to accommodate rotational motion.

Moreover, in conventional internal combustion engines with reciprocating pistons, the return movement is either due to the inertia of the flywheel, or each individual piston must have its own ignition mechanism in addition to valve gear etc. It was common to have another piston crank driven, acting on an integrated ignition that acted on the piston to push the crank until the next stage of rotation was reached.

Also, in conventional internal combustion engines, motor movement and operation with respect to the carburetor, fuel inlet, etc. is performed only by a single air compressor that receives its drive power from the internal combustion engine piston drive shaft, perhaps by various coupling levers. It has also been possible to have and utilize air compressors for improvements.

Accordingly, one object of the present invention is to obtain new and desirable advantages and to address the imperfections, shortcomings, and shortcomings of conventional internal combustion engines.
The goal is to eliminate one or more of the obstacles and problems.

The second objective is to obtain an internal combustion engine and the novel design of the present invention, which saves space due to its simplicity.

A third objective is to obtain a new high-efficiency internal combustion engine resulting from the design of the combustion chamber, piston, drive mechanism, etc., coupled with an improved carburetor for mixing and supplying the fuel to the engine.

Other objects will become apparent from the description above and below.

These objects of the invention are achieved by the invention defined herein.

Generally described, the present invention includes a common combustion chamber between and separating connected opposed pistons;
The combustion chamber includes two cylinders axially aligned with each other and a piston reciprocally mounted within each piston chamber for simultaneous reciprocating movement in a common direction; and ignition chambers each having a valve, preferably a globe valve, which moves from an opening formed at one end of the combustion chamber adjacent one piston chamber to an opening communicating with the opposing piston chamber.

When one piston approaches due to the force of the other piston moving away from the combustion chamber due to expanding gas expanding due to the expansion heat generated by the ignition in the combustion chamber, the approaching movement of this piston compresses the newly introduced fuel vapor. It acts on

When this approaching cylinder reaches the end of the piston chamber that communicates with the combustion chamber, the compressed gas will be significantly compressed within the combustion chamber just before ignition.

When ignited, this piston is pushed to the other end of the piston chamber by the force of the expanding combustion gases, and near the end of its terminal cycle, the globe valve moves to the other end of the combustion chamber and closes the other end of the combustion chamber. The cylinder compresses the newly introduced fuel mixture.

During each cycle, as one piston moves toward the combustion chamber, air is admitted into the outer cylinder chamber of that piston through a conduit with an air intake one-way valve.

Subsequently, when the piston moves away from the combustion chamber, the air in the outer cylinder chamber is compressed in a preferred embodiment and passes through a one-way valve into a conduit and into the fuel-air mixing chamber of the carburetor. The vaporizer outlet is connected to the vacuum section of the venturi to form a vacuum region, which is then pumped into the venturi.

The outlet of the venturi is connected to a conduit provided with a valve that alternately directs the fuel mixture to the opposing piston chambers in a timer manner;
Each conduit leads to a respective piston chamber containing a one-way valve.

It is also preferred to use a portion of the compressed air to operate the fuel intake valve following the carburetor and venturi.

That is, the action of the piston compresses the air and displaces the valve, thereby opening one conduit leading to one piston chamber while simultaneously closing another conduit leading to the other piston chamber, and vice versa. This is what we do.

The vaporizer may also be provided with one or more air intakes in addition to the forced air intake described above.

In addition, the exhaust gas from each piston cylinder is introduced into each conduit provided with a one-way valve, passes through preferably one common conduit formed behind the one-way valve, and then passes through a common conduit, preferably formed behind the one-way valve, and thereafter each is provided with a one-way valve. Preferably, it flows into two separate conduits.

One of the latter two conduits is an exhaust pipe leading to outside air, while the other conduit is a part of the exhaust gas containing incompletely combusted gases in the carburetor and/or in the conduit leading to the carburetor. The conduit serves two purposes:

Firstly, the circulating portion of the combustion gas at least partially reburns the incompletely combusted gases, and secondly, the heated combustion gases fed into the carburetor preheat the fuel mixture before its compression and combustion. The goal is to completely combust the fuel mixture in each piston chamber.

2 fixedly connected to each other so that both engines move simultaneously and as the piston of one engine is forced to move by ignition, it attracts the piston of the other engine to compress the fuel mixture. The reciprocating engine of the invention with two pistons can be used to drive reciprocating and/or reciprocally moving shafts, either of which can be used as a source of kinetic or other power according to conventional principles.

Therefore, physical structures provided on the sliding piston can act on the ball device or on other bearing-like surfaces in order to convert the reciprocating movement into a rotational movement and transmit it to the shaft.

It is also possible to fix the shaft itself to the piston structure and to slide it reciprocally in order to obtain the power movement utilized in conventional methods.

With the present invention, a power stroke is achieved for each end movement of the interconnected pistons, providing a substantial increase in horsepower and elimination of idle motion, as well as improved compression ratios and other benefits discussed above.

Although primarily intended for gasoline combustion, the invention also finds use in diesel ignition.

As a further advantage, in the present invention, since each stroke is a power stroke, power steal strokes and wasteful stroke motion are eliminated.

Furthermore, since there is no wasted stroke or motion, it is possible to achieve even greater power, a higher compression ratio, and smooth operation with less vibration.

The fact that more power is produced with less idle motion also ensures better economy.

Higher compression promotes more complete combustion, resulting in more horsepower.

Furthermore, by installing a stationary central combustion chamber between the spool-shaped opposed movable pistons, combustion can occur in two spaces sandwiched between both pistons and the central ignition chamber.

As further noted above, the present invention includes an air compression chamber outside the spool flange for producing compressed gas that is utilized for gas injection and discharge.

Each single stroke of the present invention consists of mixing fuel and air, exhausting the fuel mixture, compressing, burning, and releasing the gas, and has high economy and efficiency.

This makes each stroke equivalent to approximately four strokes in a conventional camshaft engine.

This engine is compatible with both air cooling and liquid cooling.

In terms of appearance and configuration, there are unitary, linear, modular or radial configurations that offer a wide range of sizes and horsepower.

Although the embodiment of the present invention uses a spark plug, it is also possible to utilize the principle of combustion using residual heat generated by high compression.

Therefore, besides achieving the preliminary and aforementioned advantages, the main objectives are to have a simple design and be cheap to manufacture;
An internal combustion engine that is extremely easy to maintain and repair, has a small number of parts, is small and lightweight, has a better burnout rate that contributes to efficient operation and increased horsepower, and can operate smoothly and reliably for long periods of time. This is the design.

Next, embodiments of the present invention will be described with reference to the accompanying drawings.

Reference is first made to the embodiment of FIG. 5, which illustrates the operating principle of the internal combustion engine of the present invention.

The figure shows a spool-shaped piston 7, an oil chamber 8 with an oil reservoir for lubricating the shaft, raceway and piston, an igniter 9, a sealing ring 10, a central member or fixed central combustion element 11, a retaining nut 12, a surface 59. A cylindrical rod 1 having a cylindrical rod and defining a chamber 8 therein.
3, and a member connecting the opposing ends 7a and 7b, ie, a piston connecting structure 6, all of which constitute the spool 7.
Motion following power transmission ball 1 fitted in the cavity 45 of 0
4 is shown.

The ball 14 has a groove 15 spirally wound back and forth around the surface 59 such that reciprocating motion of the member 60 sliding around the surface 59 imparts rotational motion to the surface 59 of the rotating member 13.
You can slide inside.

The ignition chamber 16 is shaped such that the globe valve 17 can roll back and forth between the mouths 59a and 59b of the chamber 16;
9a and 59b each have a droplet diameter of the globe valve 17, which is moved by the pressure difference created in the cavities 63a and 63b (the two spaces between the opposite ends 7a and 7b). The mouth has a smaller cross-sectional droplet diameter.

Therefore, when the wall 7a (or 7b) closest to the chamber 16 is being pushed outward by the expansion explosive force created each time the compressed gas in the chamber 16 is ignited by the spark of the igniter 9, the ball 1
7 is held within the combustion chamber.

Furthermore, looking at the movement of the ball 17 at this time, the combustion chamber and the wall 7a (or 7b) moving away from the combustion chamber
The ball 17 moves from one end 59b (or 59a) of the chamber 16 because the pressure in the compression space between the combustion chamber and the wall 7b (or 7a) decreases while the pressure in the compression space between the combustion chamber and the wall 7b (or 7a) increases. It moves to the other end 59a (or 59b).

Also, the space 18 provided adjacent to the combustion chamber and the space 19 formed on the inner surfaces of members 7a and 7b provide additional space for the action of the compressed and/or expanded gases, as well as for the fuel-air It provides a minimal amount of space for the mixture to compress, ignite, and expand.

Closed spaces 20a and 20b adjacent to both ends of walls 7a and 7b
The air therein is alternately compressed and expanded inside the mounting structure 21, respectively.

The air-gas mixture alternately enters inlets 22a and 22b, respectively.
However, their backflow into the fuel mixture inlet is prevented by one-way valves 23a and 23b.

The choice as to which inlet 22a or 22b receives the fuel mixture from the carburetor at a particular time is determined by the outlet 26a.
and spaces 20a and 2 that push air outward through and 26b.
It is governed by a reciprocating valve 43 constituting a flip-valve arrangement with pistons 44a and 44b which are actuated by compressed air which is alternately forced out in response to the compression of 0b.

Air intake pipes 27a and 27b via one-way valves 28a and 28b
The air intake takes place through each space 20.
a and 20b during the expansion stage.

The compressed air pressure alternately passes from outlets 26a and 26b through conduits 42a and 42b and acts on response pistons 44a and 44b to cause valve 43 to reciprocate.

This compressed air, in turn, finds its outlet by flowing from outlets 26a and 26b, respectively, through one-way valves 33a and 33b, respectively, of conduits 32a and 32b, which are joined to form a conduit 34 leading to a venturi 38.

The fast-moving air passing through the venturi 38 creates a vacuum at the tip of the fuel conduit 39, which draws the fuel mixture from the carburetor 36.

The fuel mixture is further transferred to conduits 40a and 40b, flip valve 4
3 open side, conduits 41a and 41b, one-way valves 23a and 23
b, and finally through the inlets 22a and 22b to the chamber 63.
a and 63b.

Additional air inlet 37b supplies a predetermined amount of air to be premixed with the fuel admitted through carburetor fuel intake tube 37a.

Furthermore, preferably residual combustion gas supply pipe 35
is provided, and this pipe receives exhaust from exhaust outlets 24a and 24b, respectively, through one-way valves 25a and 25b.

Valve 31 and valve 30 are positioned relative to each other such that a predetermined amount of exhaust gas in the total exhaust gas is sucked out through pipe 35 by exhaust pressure while the remaining exhaust gas is extracted through exhaust outlet 29.

The exhaust gas sucked out from the conduit 35 is connected to the exhaust inlet 3 of the carburetor 36.
7c, in which the incompletely combusted gases are recirculated through air entering from conduit 37b and conduit 37.
The resulting fuel mixture exits through the carburetor fuel mixture outlet 39.

Oil supplied through the conduit 8 flows, for example, through the hole 63 and the oil supply channel 56.

10 is a ring surface.

The embodiment illustrated in each of FIGS. 1-4 is a variation of the embodiment of FIG. 5, and the valve locations and operations are similarly numbered as in the embodiment of FIGS. be.

In particular, the rotating shaft 47 has a ball 45' space 15' in the member 59'.
and is turned as a result of fitting into the recess 14' in the spool wall 60'.

An annular gear 48 attached to the rotating shaft 47 imparts a rotational motion to a gear 49 which imparts a rotational motion to the gear 50a, which in turn imparts a rotational motion to the gear 50a.
0a gives rotational motion to gear 50b.

Gear 50a provides rotational motion to shaft 54, and gear 50b provides rotational motion to shaft 53.

Shaft 54 has an internal passage 54b' for compressed air conveyed from chamber 52b through passage 26b' and an opening 54b therein which is aligned with and associated with venturi 55 at a particular point of rotation of shaft 54. At the same time, alignment passage 53b aligns with venturi 55 and inlet 62.

Thus, the shafts 54 and 5 each have a passage and act as a valve.
3, the flow of the compressed air and fuel mixture flowing into the chamber 63b is appropriately controlled.

Shaft 54 further includes a passage 64b for controlling the outflow of exhaust gas from exhaust outlet 61 to conduit 24b'.

There is a similar arrangement of passages and openings at the other end of each shaft to control the opening and closing of the fuel mixture inlet 62' and exhaust outlet 61'.

One-way valves 28a' and 28b' are simple ball check valves.

FIG. 4 is a partial view of the valve including shaft 54 and gear 50b.

The embodiment of FIG. 6 is primarily used for continuous rotational drive with gears such as gear 48' and its series relations 49', 50', etc.
They differ only in the fact that

Also, the shaft 47' is fixed to the piston articulation structure 60'' and the spool wall 7a'' so that the walls 7a'' and 7b''
At the same time, the reciprocating motion causes the shaft 47' to slideably reciprocate inside the hollow cylindrical member 59'', and as the body 60'' reciprocates back and forth along the surface 59'', the space becomes slidable on the surface 59''. Since the receiver is retractable, the shaft 47' is a reciprocating shaft rather than a rotating shaft.

The key 58 shown in FIG. 2 moves back and forth in a keyway 8a formed in the structure 21 to prevent rotation of the spool-shaped piston.

Although the various embodiments of the invention described herein are not intended to be all-inclusive, these embodiments are representative and selective examples for a better understanding of the nature of the invention. I hope you understand that.

Therefore, it is confirmed that modifications, changes, substitutions, etc. of equivalents that are obvious to those skilled in the art are within the scope of the present invention.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view of a first embodiment of a two-chamber double-acting spool-piston type reciprocating internal combustion engine and its valve according to the present invention; FIG.
FIG. 3 is a partial cross-sectional view taken along arrows 2-2 in FIG. 1, illustrating in detail the internal gear mechanism that controls the valve; FIG. 3 is a cross-sectional view taken along arrows 3-3 in FIG. Figure 4 is a partial side view of the valve mechanism and gear system of Figures 1 and 2;
FIG. 5 is a partially sectional side view of another embodiment of the invention, including a vaporizer and associated connections, conduits and valves; and FIG. 6 is a side view, partially in section, of another embodiment of the invention shown in FIG. A longitudinal sectional view of a device that provides a rotary motion driven by a gear and at the same time a reciprocating motion as the main driving motion generated by the internal combustion engine shown in FIG. 5; FIGS. FIG. 4 is a longitudinal cross-sectional view of another embodiment of a device for converting the signal into a signal and transmitting the signal to a drive shaft. Explanation of symbols of main parts, 20a, 20b... Piston chamber, 21... Piston chamber defining structure, 5
9a. 59b...Ignition chamber outlet, 16...Ignition chamber, 17...(Global) valve device, 9...
Ignition device (ignition), 7 (7a, 7b)...
Piston, 60... Piston connection structure, 22
a, 22b...Fuel mixture inlet, 24a, 24
b...Exhaust outlet.

Claims (1)

[Scope of Claims] 1. A structure defining two piston chambers that are continuous in series with each other, one common ignition chamber that opens into each of the opposing piston chambers, and one of the common ignition chambers that alternately opens into one of the common ignition chambers. a valve device that closes the other opening when the opening is open and closes one opening when the other opening is open; an ignition device installed in the common ignition chamber; A first piston installed in one chamber and a second piston installed in the other chamber are integrally connected to the inner piston so that the first piston and the second piston make synchronous reciprocating motion. An internal combustion engine comprising a piston connecting structure, and a fuel mixture inlet and an exhaust outlet opening into each of the piston chambers.The valves of the valve device are alternately grounded in each opening of the common ignition chamber. said ignition chamber comprises a spherical globe valve, said ignition chamber being responsive to the pressure of compressed gas as a result of piston movement approaching said globe valve to open one of said openings in said common ignition chamber. Claim 1, wherein the chamber is configured to be able to move from one opening to another opening, and from the other opening to one opening.
Internal combustion engines as described in Section. 3. The ignition device comprises an ignition spark positioned to ignite the compressed fuel mixture within the common ignition chamber;
An internal combustion engine according to claim 2. 4. The internal combustion engine according to claim 1, including a drive shaft that transmits the reciprocating motion of the piston to a motion utilization device. 5. The internal combustion engine according to claim 4, comprising a motion conversion device that converts the motion of the piston into rotational motion of the drive shaft. 6. The internal combustion engine according to claim 4, wherein the drive shaft is fixed to the piston and reciprocates in the axial direction according to the reciprocating motion of the piston. 7. According to claim 1, each piston chamber includes, in addition to the exhaust outlet, an outlet for compressed air alternately compressed by the piston in both closed spaces adjacent to the outer ends of the pistons. The internal combustion engine described. 8. A carburetor having a fuel intake pipe, an air inlet, an exhaust inlet, and a fuel mixture outlet, which mixes fuel from the fuel intake pipe, air from the air inlet, and exhaust gas from the exhaust inlet. a conduit comprising a carburetor for supplying a fuel mixture as a fuel mixture through the fuel mixture outlet to the fuel mixture inlet of the piston chamber, and communicating the exhaust outlet of the piston chamber with the exhaust inlet of the carburetor; and further comprising a valve device in the conduit for limiting the amount of exhaust gas supplied from the exhaust outlet to the exhaust inlet via the conduit and recirculated to a predetermined amount. Internal combustion engine according to paragraph 1. 9 Transfer the fuel mixture from the carburetor to the first in the two piston chambers.
9. An internal combustion engine according to claim 8, including a flip valve arrangement for alternately feeding into the chamber and then into the second chamber. 10 The movement of said piston approaching said common ignition chamber compresses the fuel mixture in each piston chamber, and said compressed fuel mixture causes the globe valve to move away from the approaching piston and close one opening of said common ignition chamber. 10. An internal combustion engine according to claim 9, wherein the internal combustion engine is hermetically sealed and adapted to compress the fuel mixture between the approach piston and the globe valve in the common ignition chamber. 11 Equipped with a rotary valve device and a rotary valve drive device that discharge residual combustion gas from the combustion chamber and send fuel to the combustion chamber in a time-limited manner, and the rotary valve drive device directs the rotational movement of the drive shaft to the rotary valve. 6. An internal combustion engine according to claim 5, wherein the internal combustion engine is adapted to communicate with a device.