JPH05502707A - Reciprocating engine with pump cylinder and power cylinder - Google Patents

Abstract

An internal combustion engine power unit comprises two power cylinders (3) 4) spaced equidistant about a pumping cylinder (5). All cylinders operate on two-stroke cycles, the power cylinders (3, 4) having a phase difference of 180.degree.. Power piston asssemblies (13, 14) in the power cylinders (3, 4) drive crankshaft (1). Pumping piston (16) and separate crankshaft (2) are driven at twice the cyclic speed of the power pistons (13, 14) and crankshaft (1) through gear train (6, 7) between the respective crankshafts (1, 2). Air inducted into pumping cylinder (5) via intake ports (20) is compressed and passed alternately to power cylinders (3, 4) via valve controlled transfer passages (21, 24). All valves, ports and gas passages are found in a cylinder head (19). Timed fuel injection and ignition are provided. An engine may comprise one or more power units. There is also disclosed a turbo-charged diesel engine comprising two power units in "V" configuration.

Description

[Detailed description of the invention] Reciprocating engine with pump cylinder and power cylinder [Technical field] The present invention provides a pump cylinder and a power cylinder that operate on a two-stroke cycle. Regarding reciprocating internal combustion engines.

[Background technology]

This type of engine is intended to improve engine efficiency or the power-to-weight ratio of the engine. It is disclosed in a large number of prior art. The design shown in U.S. Patent 1,881,582 In the meter, the pump cylinder is cycled at twice the cycle speed of the power cylinder. Transfer port that is driven and communicates with the lower cylinder wall of the power cylinder A through tintake scavenging charge is alternately supplied to each power cylinder. Therefore, it is linked to the power piston. This design can increase scavenging efficiency to the maximum, and the crankcase compression type 2-stroke Although it is comparable to a Roke engine, it has the basic characteristics of a normal 2-stroke engine. This includes the inefficiency of scavenging efficiency, and many efficiency problems of conventional two-stroke engines. has a problem. The inefficiency is due to the fact that the transfer port opens into the lower cylinder wall. This results from the fact that it is released and causes a decrease in volume upon expansion, and this decrease in volume The remaining amount is used for half of the scavenging stage. Additionally, this design allows the lower cylinder wall to Because of the transfer of There is no possibility of achieving this goal.

It has a pump cylinder and a power cylinder that operate on a two-stroke cycle, and A second type of engine intended to overcome the disadvantages is exemplified by U.S. Pat. , 880,126 and 4,458.635. Their design is Transfers intake air through a valve-controlled port opening in the head of the power cylinder It is equipped with a pump cylinder.

U.S. Patent 3,880,126 utilizes a combustion chamber in constant communication with the power cylinder. However, the combustion chamber has an excessively large number of parts, and the overall efficiency and output are mainly , due to poor scavenging efficiency caused by the length of the scavenging path required by the design. strictly limited.

This fact further worsens the apparent power-to-weight ratio of the design.

U.S. Pat. No. 4,458,635 similarly addresses the basic inefficiency described A valve-controlled constant-volume combustion chamber precedes a conventional supercharge system that produces This increases scavenging and combustion efficiency, resulting in a slight increase in overall efficiency. It's a big deal. As a result, the average power-to-weight ratio was improved, but the number of parts was too large. That is still a big problem.

Another engine design, typically shown in British patent 2071210, uses a cylinder, Ports, valves, etc. are located similar to those of the present invention, but the power cylinder does not belong to the technical field of the present invention in that the motor operates on a four-stroke cycle. stomach. That is, in the case of such a four-stroke cycle, the pump cylinder is Used only as a supercharging device, and as required by the present invention. It is not required for engine control.

[Disclosure of the invention]

The present invention significantly increases the thermal efficiency and power-to-gravity ratio of all types of engines. , increasing the scavenging efficiency of all types of engines mentioned above which also belong to the field of the invention; Further reducing the number of parts required for the second type of engine, a novel Discloses an engine with a unique design.

Therefore, the main object of the present invention is to provide a pump in which the pump piston reciprocates. A power cylinder with one cylinder and a power piston reciprocating inside each cylinder. An object of the present invention is to disclose an engine having one or more units having two units. .

The cylinders all operate in a two-stroke cycle, and the pump pistons A mechanical drive means allows the piston to reciprocate at twice the cycle of the power piston, resulting in continuous pumping. Intake by ping cycle is carried out between the head of the pump cylinder and each power cylinder. It is transferred alternately to each power cylinder via a transfer port that connects the head part. sent. Each transfer port has a power cylinder and each transfer port that are open lights. Each of the above series is controlled by a switching valve that controls the connection of the Spha port as needed. I am contacting Linda.

The pump cylinder has an intake port that runs through its head and is controlled by an intake valve. The volume expansion stroke that precedes the volume reduction stroke The continuous cycle intake by this pump cylinder is Each movable cylinder is connected to the The fuel is alternately transferred to the engine and the combustion chamber of the power cylinder.

The intake air is at least 60% of the air used for combustion, while the head section (space above the top of the piston; stroke volume) The cylinder head can contain 3 of the cylinder volume (stroke volume). It is less than one-fold.

The power main shaft is synchronized or synchronized by shifting each power piston by one stroke from each other. The pump main shaft moves back and forth in a synchronized manner while the pump main shaft pumps at said speed. Move the piston back and forth.

Additionally, a valve-controlled exhaust port is provided for each power cylinder in the head section. is used to exhaust combustion gases from the power cylinder.

Each combustion chamber can be in constant communication with its respective power cylinder, or , timed to provide constant volume combustion for at least a portion of the time for combustion. communication with each power cylinder based on control by a regulated secondary valve. You can also do it. In all of the above and below cases, the specified power cylinder Opening of the transfer valve of the cylinder means its opening to the power cylinder.

Preferably, the pump piston of the unit is connected from each power cylinder of the unit. and this pump piston is equidistant from the main shaft of the power piston Or driven by the output shaft, the intake air that is being drawn in or the intake air that is being drawn in is transferred to the power cylinder, but this transfer of intake air causes the power piston to reach top dead center. This is done for at least 60% of the steps. Additionally, combustion occurs in the power cylinder. Preferably, each transfer valve is closed before the engine is started. Preferred valve control timing that enables efficient operation is also disclosed. .

Another object of the invention is to improve the engine described above with the following various improvements: The objective is to further improve the results. i.e. pump cylinder main shaft coaxially on top of the power cylinder main shaft; and/or Power cylinder main on pump cylinder main shaft or between power cylinders Continuous actuation means for valves driven by means provided or arranged on the shaft. or other auxiliary equipment, and that these to achieve operational simplicity and efficient operation under transient operating conditions. To vary the closing time of the exhaust valve, at least Introducing a variable timing valve mechanism that changes the closing timing of the air valve. and. The transfer valve and the secondary valve are poppet-type valves, and the transfer valve and the secondary valve are poppet-type valves. The desired configuration of each combustion chamber type, with preferred arrangement of the valves and preferred control timing. It is another object of the present invention to provide a desirable combustion chamber design. The present invention also Another objective is to develop a new engine with a better V-configuration and turbocharged design. It also provides a clamp to improve the engine charging effect. It is also possible to provide an engine with a pump cylinder that utilizes compression in the engine case. Another object of the invention.

[Brief explanation of the drawing]

FIG. 1 is a plan view of the preferred design, which is an in-line single unit; Shows cylinder, port, combustion chamber and valve opening positions of the unit.

FIG. 2 is a cross-sectional view taken along line A-A in FIG. The area around the crankshaft mechanism and the lower crankcase have been removed.

Figure 3 shows the preferred design valve control shown in power cylinder crank angle. is a diagram in which the line indicates the opening time of the valve and the TDC position indicated therein. is the TDC position of the first dynamic caviston.

Figure 4 shows a V-type with two units, a turbocharger and a pump series. An alternative design is shown that utilizes engine crankcase compression. One unit i.e. The bank of cylinders is shown in side view and the other unit is shown in FIG. Although shown as a cross-sectional view along line B, the circumference of the piston crankshaft mechanism removed, hidden details or partially shown, lower power crankcase and lower RH The side pump cylinder crankcase has been removed.

FIG. 5 is a plan view of the cross-sectional unit of FIG. 4, showing the cylinders and holes of the unit. , indicating the combustion chamber and valve opening position.

FIG. 6 is a valve timing diagram for the alternative design shown in FIGS. 4 and 5. 3, using the same expressions as in the above description of FIG.

FIG. 7 is an end view of an alternative V-configuration; the cylinder and crankshaft of the alternative V-configuration; Indicates shaft position.

[Mode for carrying out the present invention]

To see all the modes of running the invention, each unit has an internal pump. The pump cylinder 5 in which the pump piston 16 reciprocates, and the reciprocating movement inside each It comprises a power cylinder 3.4 having moving first and second power pistons 13.14. I can do it.

All cylinders of one unit have parallel axes and a common block 18 and a common The head 19 is shared, while the pump cylinders are distributed equally from each power cylinder. Separated.

The pump crankshaft 2 and the pump connecting rod 17 connect the pump piston 16 The power crankshaft l and the power connecting rod I5 are made to reciprocate make a reciprocating motion. Each crankshaft is supported by support means for rotation - On the other hand, the journal means not shown in the drawings are connected to the connecting rod clamp. Piston pivot axis of connecting rod and pivot movement in Ntanyaft pivot bearing Gives turning motion at the receiver.

A pump drive gear 7 fixed to each pump crankshaft 2 is a power crankshaft. This crankshaft operates in conjunction with the power crankshaft gear 6 fixed to the shaft 1. It is driven by the crankshaft gear 6, whose diameter is half the diameter of the crankshaft gear 6. It is. Therefore, this gear arrangement allows the pump piston 16 to speed up the power piston. To enable periodic reciprocating motion at twice the speed of 100 degrees.

The mutual phase relationship of the power pistons in one unit is determined by the rotation of the power crankshaft. The crank angle (hereinafter referred to as CA) is set to 180°. Ru.

The first and second transfer ports 21.24 are in constant communication with the pump cylinder. There is.

The crankshaft for carrying out all modes of the invention is unitary and All connecting rods are two-piece and pivot around the crankshaft. It is bolted on its underside for movement.

Of course, all methods of carrying out the invention include efficient operation of the engine. Includes all parts and auxiliary parts not shown or mentioned required for , while the cooling water passages are shown in the wall cross-sections of Figures 2 and 4, but there is confusion in the numbering. They are not numbered to reduce the number. Furthermore, the first and second power cylinders each part of the da is referred to as said first and second part, respectively, or Reference will be made to each part of the power cylinder that will be described.

[Detailed description of preferred embodiments]

Figures 1 to 3 show the present invention applied to a naturally aspirated inline engine. This is an embodiment in which the pump cylinder 5 is connected to the first and second moving cylinders 3.4. placed in the middle. The pump crankshaft 2 is connected to the pump of the engine block 18. is held in place by a crankshaft cap 38. On the other hand, the power The crankshaft 1 is held in place by the lower crankcase, not shown in FIG. is maintained. The phase of the pump piston 16 relative to the power piston 13.14 is: A special system that allows the pump piston to move in synchronization with the movement of the piston in each power cylinder. Hand at top dead center of power piston to perform intake by pump cylinder cycle In the front, the top dead center is reached at a power CA of 40°.

In this preferred design, all intake, transfer and exhaust valves is a poppet type valve.

The first and second combustion chambers 22.25 maintain constant communication with their respective power cylinders. , a spark plug 35 that ignites the combustible mixture in the combustion chamber, implemented in the room.

A fuel injection means 36 is implemented in each transfer port to transfer intake air into the power cylinder. When the transfer port is loaded, a predetermined amount of fuel is injected into the transfer port.

The first transfer valve 8 provides communication between the first transfer port 21 and the first movable cylinder 3. while the second transfer valve 10 is connected to the second transfer port 24 and the second The timing of communication with the cylinder 4 is adjusted.

The two intake valves 12.12 connect the intake port 20.20 and the pump cylinder 5. Adjust the timing of communication between

The first exhaust valve 9 provides communication between the first dynamic cylinder 3 and the first exhaust port 23. On the other hand, the second exhaust valve 11 is connected to the second movable cylinder 4 and the second exhaust valve 11. The timing of communication with the exhaust port 26 is adjusted.

The exhaust port communicates with an exhaust pipe through an exhaust manifold, while the intake port communicates with an exhaust pipe through an exhaust manifold. The port passes through the intake manifold, and air metering means is provided within this intake port. It will be done.

All of the above valves are designed with their axes parallel to the axis of the crankcase. Directly operated by one overhead camshaft located directly above all I am made to do so. In order to avoid complicating the drawing, the camshaft is shown in Figure 2. Not shown.

The camshaft is a camshaft drive provided on the pump crankshaft 2. Driven by sprocket 39 via chain means 46. Chain means 4 The diameter of the sprocket provided on the camshaft connected to and driven by 6 is , twice the diameter of the camshaft drive sprocket 39 and the same size as the power cylinder. The camshaft is operated at cycle speed.

The transfer valve and exhaust valve are actuated by a single cam. On the other hand, the intake valve has two caps. This cam is the part of the camshaft that operates the intake valve. are evenly spaced and therefore increased in the pump cylinder. As the cycle speed increases, the intake valve opens and closes twice as often as other valves. Ru.

The closing action of the variable timing exhaust valve is controlled by the variable timing valve mechanism. This is done according to the training block type. This variable timing valve mechanism engine load and speed, which are not shown to avoid unduly complicating the diagram. Close the exhaust valve before top dead center, in the range of power CA 30° to 70° be able to do so. This variable closing timing is shown in FIG. 3 by a dotted line.

The engine oil pump supplies oil to the engine between the two power cylinders. Driven by an oil pump drive gear 40 provided on the power crank angle 1 of be done.

The operation, including valve timing, of the preferred design is described. pump piston 16 After passing the top dead center, when the pump moves to CA60°, the intake valve 12 opens ( . This allows the intake air after the previous cycle to effectively expand before the intake valve 12 opens. do. Then, the intake valve 12 opens and the pump piston 16 reaches bottom dead center (BDC). Upon movement towards, fresh intake air is induced into the pump cylinder 5. pumppi When the stone 16 moves to pump CA40° after passing the bottom dead center, the intake valve The valve 12 closes and the induction of intake air stops. At the same time as the intake valve 12 closes, the transfer valve Either valve 8 or IO begins to open and the power system whose transfer valve is open Start transferring intake air to Linda. The transfer valve, as shown in FIG. After the pump piston 16 passes the top dead center, it is open until it reaches the pump CAl00, At this time, the piston of the power cylinder is just before the top dead center, and the power CA is 35°.

The piston 16 of the pump cylinder then continues to move towards the bottom dead center and the intake valve When the valve 12 reopens after top dead center at pump CA 60°C, the same as above Start a new cycle. This new cycle's intake is now connected to the other powered cylinder. The intake air for subsequent cycles is also transferred to another power cylinder. and start a new cycle for that power cylinder.

During the first half of the intake air transfer to each power cylinder, the exhaust valve of the power cylinder The valve is open, and in the latter half of the exhaust process of each power cylinder, the intake air is transferred. The remaining exhaust gas is scavenged from each of the power cylinders. Discharge of each power cylinder The air valve is set when the piston of each power cylinder is just before the top dead center, and the power CA is 30° ~ Open during movement up to 70°.

In case of high load and/or high speed operation, the transfer port is Fuel is injected while the engine is running. When operating at low loads and/or speeds, the fuel Most of the fuel is injected after the exhaust valve of the power cylinder is closed. fuel is injected Then, combustion starts near top dead center due to the spark from each spark plug 35. .

Then, the pistons of each of the power cylinders move toward the bottom dead center to generate each of the power The gas in the cylinder actually expands and the piston is just before bottom dead center, the power CA45 ”, the exhaust valve begins to open. -down, while the pistons of each power cylinder move toward top dead center. Active scavenging is performed until the cylinder transfer valve opens, and then Another cycle begins for that cylinder. The operation of other power cylinders is also the same as above. is the same as, but the operation is performed before or before the operation of said power cylinder occurs. It is clear that the power CA is later generated with a phase shift of about 180°.

Figures 4 to 6 show the application of the present invention to an engine with two units configured in a V-shape. This is an example in which each unit has 19 banks of cylinders of a type engine. It is. The power cylinders of each unit are closely spaced, and therefore the pumps of each unit The push cylinder 5 is arranged outside each unit centrally between the power cylinders. this In an embodiment, each power cylinder is in communication with the timing regulator. A constant volume combustion chamber is used with a well-equipped secondary valve. of the secondary valve The second secondary valve is 27, and the second secondary valve is 28.

A turbocharger 41 is placed in the center of this V-shaped unit, controlling all moving parts. J Norinda's exhaust manifold connects to turbocharger 41. In addition, the exhaust port The vent and exhaust manifold are represented by the same number.

A supercharging air manifold 42 led from a turbocharger 41 connects both pump cylinders. It is connected to the intake port 20 of. On the other hand, the crankcase of both pump cylinders The crankcase intake port 33 is provided, and the intake air from here is non-supercharged. be. All power pistons are connected to one power crankcase. , while each pump cylinder 5 is provided with a pump crankshaft 2, respectively.

One power crankshaft gear 6 provided on the power crankshaft l has each Drives the pump cylinder drive gear 7 provided on the pump crankshaft. each The phase of the pump piston relative to the power cylinder of the unit is This is the phase that reaches the top dead center at a power CA of 30 degrees, which is just before the top dead center. Note that non-contact in Figure 4 The phase of the power piston of the cross-sectional unit with respect to the power piston is determined by the power CA90 'It's off.

The power crankshaft 1 is operated by a power crankcase not shown in the drawings. and held in place. On the other hand, each pump crankshaft 2 is a non-cross-sectional unit shown in FIG. It is held in place by the pump crankcase 47 shown in knit.

The intake valve, transfer valve, exhaust valve, and secondary valve in this example are all It is a poppet valve, and the crankcase intake valve is a reed valve. 1st Communication between the combustion chamber 22 and the first moving cylinder 3 is first controlled by a secondary valve 27. On the other hand, the communication between the second combustion chamber 25 and the second dynamic cylinder 4 is controlled by the second secondary nozzle. controlled by the valve 28.

The fuel injection means 37 is mounted in each of the combustion chambers, and the fuel injection means 37 is installed at a point in each of the combustion chambers. The fire is generated by the temperature and pressure of the mixture within each combustion chamber.

A protrusion 3I on the top of each power piston is located at least at each secondary port 29.30. is stretched upward to reduce the volume of the engine, thereby reducing the efficiency of the engine. increase

In this embodiment, each unit is a naturally aspirated in-line engine as described above. The same intake knob, transfer valve, exhaust valve, Each port has the same arrangement and function, but the positions of some valves and ports have changed. ing.

Each unit also has two overhead camshafts. These two o A bar head camshaft (not shown) connects the gear from the pump cylinder drive gear 7. is driven via a means. One of the two idle gears 43 and 44 is The other idle gear 44 meshes with the idle gear 43 and the power crank. It meshes with a camshaft gear 45 having the same diameter as the link shaft gear 6. cam The shaft gear 45 operates each of the transfer valve, secondary knob, and exhaust valve. It is fixed to a power camshaft with a cam that makes it work. On the other hand, the power cam The pump camshaft has a cam that operates the intake valve. The associated gear diameter differences increase the intake valve cycle rate. It is designed to let you do so.

The operation including valve timing of this example will be explained for one unit. .

When the pump piston moves to pump CA70° after passing the top dead center, the intake valve Lube 12 begins to open. Therefore, the intake valve opens after the previous cycle. In effect, it expands before it is released.

While the intake valve I2 opens and the pump piston moves to its bottom dead center, the intake air is Guided into Ponjin Linda 5.

While the power piston 16 is moving toward the bottom dead center, the intake air in the crankcase is compressed. When the engine is operating at or around 50% load , the turbocharger 41 operates efficiently and the pump piston reaches the point before bottom dead center. When the pump CA reaches 30° and the crankcase transfer port 34 is opened, the The pressure inside the cylinder brought from the bot charger 41 is applied to the crankcase. The intake air transfer from the crankcase is equal to or higher than the pressure inside the crankcase. No additional charges will be incurred. As a result, the intake air compression in the crankcase is reduced by the engine load. When the load is low, it is utilized, but when the load is high, it is not utilized, so the said cluster The maximum pressure inside the link case can be kept low. For this reason, the crankcase Since the sealing degree does not need to be very high and the operating pressure is low, the reed bar The material of the lube can be made lighter.

When the pump piston 16 moves to pump CA30° after passing the bottom dead center, the intake air Valve 12 closes and the induction of intake air through the intake port ends. Here, the engine When the is operated at low load and the pump piston is on the upstroke, the intake air is is guided into the crankcase via the crankcase intake valve 32.

in order to begin an intake air transfer process to the power cylinder to which the transfer valve is open; At the bottom dead center of the pump piston, one of the transfer valves opens. Then this transfer bar The valve remains open until the pump CA reaches 1.0° after the pump piston passes the top dead center. Ru. As shown in Figure 6, this means that the pistons of each power cylinder reach top dead center. The moving horn CA is 45°.

Thereafter, the pump piston continues its movement toward the bottom dead center, and after passing the top dead center, When the intake valve opens at pump CA 7.0°, the new pump cylinder A new cycle begins. In this cycle, the intake air is controlled by other movements in the same way as described above. transferred to the force cylinder. This process is repeated thereafter.

During the first half of the intake air transfer stroke for each power cylinder, each power cylinder's secondary The lube is open, scavenging exhaust gases from the combustion chamber of each power cylinder. and , the piston of each power cylinder has moved to a power CA of 115° just before top dead center. and the secondary valve is closed. During this time, the exhaust valves of each power cylinder are open. and the piston of each power cylinder is just before top dead center, the power CA is 35°. The exhaust valve of each of the power cylinders closes when the power cylinder moves to the maximum position. This allows extremely small Almost all of the exhaust air is scavenged from the cylinder, except for a small amount that remains.

At this time, the residual exhaust gas is maintained at a high pressure, so the piston of the power cylinder rises. The heat obtained when the secondary valve opens again when the power CA5° is reached before the dead center A phenomenon in which the pressure in the power cylinder becomes lower than the pressure in the combustion chamber, which reduces efficiency. doesn't exactly happen.

When the power piston is located at approximately power CA40° before top dead center, the combustion Fuel is injected into the room. As a result, combustion occurs immediately after the associated transfer valve closes. occurs and when the secondary valve opens, approximately 50 percent of the combustible mass is combusted. It's finished.

After the combustion ends, the power piston moves toward the bottom dead center, and the piston moves toward the bottom dead center. Before the power CA reaches 40° and the exhaust valve of the cylinder opens, the combustion Gas from the baking chamber flows through the secondary port and open valve, effectively expanding .

After that, the cylinder exhaust process is started, and the piston moves toward the top dead center. Then, the next intake air transfer process similar to the one described above begins and continues until the next cycle begins. The cylinder is actively scavenged.

Other power cylinder operations include valve and cycle operations as described above. , but as is clear, the operation of the other power cylinders is the same as that of said cylinders. The power CA is generated with a deviation of 180° before or after the operation occurs.

FIG. 7 shows another embodiment of the V-shape. As before, there are two units, and this implementation In the example structure, each unit is one bank of cylinders for the engine. Yes, and the pump cylinder 5 of the unit is located inside this V-shaped bank. That is, it is located inside the power cylinder. 1 pump crankshaft 2 in front Both pump pistons 16 are reciprocated, while one power crankshaft 1 causes all the power pistons to reciprocate.

Obviously, many modifications and variations may be made to the invention. I wanted to Therefore, within the scope of the appended claims, the invention may be practiced otherwise than as specifically described. You have to understand what you can do.

international search report ANNEX) L APPLICATIGI NO, FCT AU 9 1END OF AN N.E.I.C.

Claims (20)

[Claims] 1. Consists of one or more units, each unit all having two strokes. One pump that operates on a rotary cycle and each has a reciprocating piston inside. The pump cylinder includes a pump piston and two power cylinders, and the pump cylinder is a pump piston. It has a main shaft that reciprocates the power cylinder, and has a main shaft that reciprocates the power cylinder. Each power cylinder is driven to perform a cycle, and each power cylinder moves a power piston back and forth. Each has a main shaft for backward movement, and each power piston has one stroke. It is shifted by about 1 stroke; The ends of all said cylinders, at the end opposite to the end where the main shaft is located. This cylinder head has a cylinder head that closes the wall inside the cylinder. , and extend down to where one-third of the volume of each cylinder is provided. a combustion chamber for each power cylinder is provided in the cylinder head; , said combustion chamber retains at least a large portion of the combustion occurring therein, and each It can be in constant communication with the power cylinder, or by means of secondary valves each The power cylinder can be contacted from time to time, in any case said combustion The chambers are referred to as respective power cylinders unless otherwise stated; The head has two transfer ports, and the so that each power cylinder communicates with the pump cylinder at the head and has at least Also, the transfer port and each power cylinder are communicated from time to time. controlled by valve means; the head has two or more exhaust ports passing through the head; One or more of the exhaust ports exit from each power cylinder and are connected to engine operation. exhaust gases may flow from said power cylinder as required by the operation. The communication between the exhaust port and other exhaust ports is Timed by steps; The head may include one or more tubes extending through the head to the pump cylinder. There is an intake port, and communication between the intake ports and between the intake port and the pump cylinder. There is an intake valve that controls the when the piston of the cylinder moves to increase the volume of the cylinder , said suction valve opens and at least a large portion of the suction charge is effectively pumped. The suction charge is introduced into the cylinder, where air, fuel and the combustion process The exhaust gases used in the combustion may be any combination of retain at least 60 percent of the intake air used in the pump cylinder. The suction charge induced into the transfer device is transferred through each transfer port. The spa valve is alternately transferred to each open power cylinder, increasing the volume of the cylinder. said power when the pump piston moves at least substantially to reduce After combustion, the power piston moves through the bottom dead center and the piston When the cylinder moves above or in front of said position, each exhaust valve of the power cylinder opens. An internal combustion engine characterized in that the engine starts the exhaust phase. 2. The pump piston is moved at a time when the power piston moves towards the position. Piston of a power cylinder whose intake charge is about to be transferred at less than 60% to the top dead center position and the pump piston at increased cycle speed. said means for actuating an output shaft of a power cylinder or an output of an engine; The internal combustion engine of claim 1 further characterized in that it is driven from a power shaft. gin. 3. The pump pistons are at least each located substantially equidistant from the power cylinder. and; the pump piston reaches its pump piston top dead center position and after said position Required for power cylinder cycle after closing between 20-48% of the time the intake valve begins to open between 0 and 20% of the time; The suction charge of the push cylinder cycle can be transferred into the power cylinder. A transfer valve timing each transfer port in order to It begins to open between 25 and 55% of the time, and each power piston reaches top dead center. after reaching 55% to 97% of the time; and The transfer valve of the power cylinder has at least 30% of the combustible mass of the power cylinder. The internal combustion engine according to claim 2, further characterized in that the internal combustion engine closes before % is combusted. Njin. 4. a constant volume combustion chamber is provided between the transfer valve and the secondary valve; The chamber is closed at least for the majority of the time required for the combustion of the combustible charge. , providing constant volume combustion; said secondary valve being between the combustion chamber and the power cylinder; time the communication between the respective secondary valves of said power cylinders; Due to the power cylinder cycle before the stone reaches the top dead center position of the pump piston 10% of the time required for the pump piston to reach the top dead center position of the pump piston. 40% of the time after the start of the recitation, and before the position Claim 3, further characterized in that it closes in a time between 40% and 0% of internal combustion engine. 5. characterized in that the combustion chamber maintains constant communication with the respective power cylinder An internal combustion engine according to claim 3. 6. At least the phase valve and the exhaust valve are of poppet type; Stem and the stem or other working part of the secondary valve extends through the combustion chamber. Because the combustible mixture in the combustion chamber does not expand at any position around the said part of the valve. 5. An internal combustion engine according to claim 4, characterized in that the internal combustion engine is not located at the same location. 7. At least the phase valve and the exhaust valve are of poppet type; The head is at least effectively axially above the cylinder, but on one side of the cylinder. placed; the combustion chamber is placed below the head of the phase valve, and the walls of said combustion chamber effectively extends towards the output shaft, so that after said transfer valve , the walls defining the combustion chamber act as ports and covers for the flow of the transferred suction charge. and direct the transfer suction charge in a downward direction and out of the combustion chamber. ; and more than 70% of the volume available when the power piston is at top dead center. Claims further characterized in that: The internal combustion engine according to box 5. 8. The shaft of the pump cylinder output shaft extends from the pump cylinder. on a line perpendicular to the axis of the power cylinder and the power cylinder output shaft Since it is located on the foot axis, the axes of all the cylinders of the unit are parallel, 4. The internal combustion engine of claim 3, further characterized in that - line. 9. The pump cylinder output shaft drives either said valve or is the actuating means or provided or placed on the pump cylinder output shaft. further characterized in that it has other auxiliary devices driven from said means. The internal combustion engine according to claim 3. 10. The part of the power cylinder output shaft between the two power cylinders is any of said valve driving or actuating means or pump cylinder output; other auxiliary equipment driven from means provided or placed on the shaft; 4. The internal combustion engine of claim 3 further comprising: 11. All said cylinders of the unit have parallel axes; the secondary valve is be pet-shaped; at least the transfer valve and exhaust valve are combustion chamber and power, respectively, to increase the pressure on the sealing surface of the exhaust valve. Utilizing the pressure within the cylinder; the stem of the transfer valve of the power cylinder It extends from the head of the valve, and the extension exceeds 15 degrees and the pump cylinder In the direction from the cylinder to the power cylinder, there is a pull between the power cylinder and the pump cylinder. perpendicular to the straight line drawn and to the axes of the pump cylinder and the power cylinder. in a plane that is at right angles to the be perpendicular to the axis of the cylinder; and each of the power cylinders A stem of the secondary valve extends from the head of the secondary valve, the extension comprising: Beyond 15 degrees and in the direction from the power cylinder to the pump cylinder, the pump perpendicular to the line extending between the push cylinder and the power cylinder, and 1 Beyond 5 degrees and in the direction of the output shaft, the angle is perpendicular to the cylinder axis. 7. The internal combustion engine of claim 6, further characterized in that the internal combustion engine is straight. 12. All cylinders have parallel axes; transfer valves and exhaust valves , the combustion chamber power series to increase the pressure on the sealing surfaces of the transfer valve and exhaust valve. utilizing the pressure within the cylinder volume; and each transfer valve of a particular power cylinder. The stem of the valve extends from the head of the valve, and the stem extends by more than 15 degrees. and from the pump cylinder to the power cylinder, the power cylinder and pump cylinder perpendicular to a straight line drawn between the pump cylinder and the in a plane that is perpendicular to the axis of the force cylinder, beyond 15 degrees and further characterized in that in the direction of the shaft, it is perpendicular to the axis of the cylinder. 8. The internal combustion engine according to claim 7, wherein the internal combustion engine has the following characteristics. 13. Effectively as described herein with reference to FIGS. 1-3, but with internal combustion engine Engine overhead cam gear and drive; specified fuel and ignition means; specified Crankshaft and connecting rod design; internal combustion engine combustion chamber, valves and ports Claim 3 further characterized in that the position of the parts other than the parts in the seat is an exception. Internal combustion engine as described. 14. Effectively as described herein with reference to FIGS. 4-6, but with internal combustion Engine overhead cam gear and drive, specified fuel and ignition means, specified Crankshaft and connecting rod designs, combustion chambers, valves and ports in internal combustion engines. Claim 3 further characterized in that the position of the parts other than the parts in the seat is an exception. Internal combustion engine as described. 15. Since two or more of said units are utilized in a V configuration, at least Also, the power cylinder of the internal combustion engine is configured in a V configuration and includes at least one or more units. the knitted power cylinders are banks of cylinders in said V configuration; and One output shaft is at least two required for said V-configuration. reciprocating the piston of the power cylinder of the unit, and reciprocating the piston of the power cylinder of the unit, and of the at least two units in which the top put shaft is required for said V configuration. Claims further characterized in that the piston of the pump cylinder is reciprocated. The internal combustion engine according to 3. 16. At least the pump cylinder is connected to the crankcase of the internal combustion engine. The transfer port of the crankcase is used for In order to connect the case to the stock wall of the cylinder, the piston of the pump cylinder When the piston is close to its bottom dead center position, the piston does not cover the transfer port. , so that part of the suction charge can flow into said cylinder. ; and the crankcase inlet valve means is connected to the crankcase inlet port or Since the communication between the Nifold and the crankcase is adjusted, the piston is said charge is guided while at least substantially moving towards the top dead center position of the 4. The internal combustion engine of claim 3, further characterized in that the internal combustion engine is 17. Since the pump cylinder is placed at a position other than between the power cylinders, The distance between the cylinders is one pump cylinder inner diameter and the distance between the pump cylinder and the power cylinder. less than the sum of twice the wall thicknesses that may separate the power series; The engine exhaust manifold connects the power cylinder to increase the pressure of the suction gas. of the claim further characterized in that the turbocharging device utilizes the exhaust gas of the Internal combustion engines according to scope 3. 18. The pressurized suction manifold derived from the turbo charge is connected to the pump cylinder. contact the above mentioned crankcase intake port and/or manifold. Internal combustion combined with claims 16 and 17 further characterized in that it is supercharged. engine. 19. the intake valve closes 25-40% of the time after said position; and said transfer port 15-40% of said time after said position. 4. The internal combustion engine of claim 3 further characterized in that it is open. 20. Poppet-type valves are used at least for transfer valves and exhaust valves. and the opening duration and/or lift of said valve. Any combination of release and/or closure time and speed can be varied. The variable valve timing mechanism varies at least the exhaust valve closing time. 4. An internal combustion engine according to claim 3, further characterized in that it is used for.