WO1995020722A1

WO1995020722A1 - A piston internal combustion engine

Info

Publication number: WO1995020722A1
Application number: PCT/CN1995/000009
Authority: WO
Inventors: Shouren Wu
Original assignee: Shouren Wu
Priority date: 1994-01-28
Filing date: 1995-01-27
Publication date: 1995-08-03
Also published as: AU1573995A; CN1096851A

Abstract

The present invention relates to a piston internal combustion engine driven by a cam, including a cylinder, a piston, an intake and exhaust mechanism, an ignition system, a transmission pin mounted in said piston and a cylindrical cam. It transforms horizontal motion of the piston into rotation of shaft by cooperating said transmission pin with said cylindrical cam, so that the conventional crankshaft and connecting rod transmission mechanism can be substituted. It is an engine with compact structure, small size, light weight and reliable and smooth operating.

Description

TECHNICAL FIELD

The present invention relates to internal combustion engines, and more particularly to reciprocating piston internal combustion engines. Background technique

In traditional piston internal combustion engines, the translation of the piston into the rotation of the crankshaft is changed by a crank-and-bolt mechanism. At present, the more advanced engines in the world, such as Japan's Toyota engine (95 hp, fuel consumption 8 liters / 100 km), are all internal combustion engines using this structure. This kind of engine has the inherent disadvantages of large volume, heavy, complicated structure, unstable transmission and large resistance loss, which limits the improvement of engine performance to a certain extent.

The purpose of the present invention is to improve the internal combustion engine transmission mechanism, to overcome the shortcomings of large resistance loss and instability of the crank link transmission mechanism, and to propose a cam type that is small in size, light in weight, large in ratio and stable in motion. Stopping the internal combustion engine. Brief description of the invention

The present invention proposes such a cam-type piston internal combustion engine. The internal combustion engine generally includes a cylinder block, a plug, a piston ring, a supercharger, an intake and exhaust mechanism, an ignition mechanism, an oil lubrication device, and a cooling device. A transmission pin is provided in a direction perpendicular to its longitudinal axis, and at least one bar-shaped hole is opened in the cylinder body to facilitate the pin shaft extension; near the pin shaft end, a pin translation guide rail is axially arranged in the cylinder body, The guide rail can be provided separately or integrated with the cylinder body itself, or it can be a strip-shaped hole itself to facilitate the reciprocating translation of the pin shaft; the pin shaft end is equipped with a bearing; the side of the cylinder body is provided with a cylindrical cam and its seat Body, the pin shaft end bearing cooperates with the drive guide groove on the outer peripheral surface of the cylindrical cam.

Moreover, in the present invention, the included angle of the guide groove is defined as: the outer peripheral surface of the cylindrical cam and the axis of the transmission pin have an intersection, and during the relative movement of the cylindrical cam and the transmission pin, the motion locus of the intersection It is a closed curve in space. The curve has a farthest point and a nearest point relative to an end surface of the cylindrical cam, and the angle between the line connecting the farthest point and the nearest point and the cam axis. The angle α may be 3 0. -60 °, preferably 40 °-50 °.

Moreover, when the present invention defines the "compression ignition persuasion angle β" as the angle through which the combustion of the gas mixture in the internal combustion engine drives the cylindrical cam that cooperates with the piston, the present invention guides The compression ignition persuasion angle β on the slot development view is selected as 50. -150 °, preferably 60 °-90 °. ; The curve shape of the guide groove development view is preferably a sine curve.

Cylindrical cams can be equipped with flywheels, distributor rails, and transmission pulleys of cooling devices such as water, oil, or wind to control the synchronous operation of other additional devices (this point is the same as conventional technology), or other additional devices are used for Synchronous control.

The above-mentioned piston pin driving mechanism may be a single-piston one-way persuasion mechanism, or it may be a two-piston two-way persuasion mechanism, which can not only realize two-stroke motion but also four-stroke motion. The piston pin driving mechanism may be one set, or two or more sets. Multiple piston pin shaft driving mechanisms can be arranged along the peripheral surface of the cylindrical cam. The spare pin shafts with bearings at the shaft ends are matched with the guide grooves of the cylindrical cam to form a parallel drive mechanism, thereby doubling the power output of the internal combustion engine. . The internal combustion engine may also have more than two sets, and the middle is connected axially by a cylindrical cam or a coupling to form a tandem drive mechanism to achieve high horsepower output.

The above-mentioned piston pin driving mechanism and the cylindrical cam may be a discrete type as described above, or may be an inclusive type, that is, a cylindrical cam (which may be called a cylindrical inner cam at this time) is surrounded on the outside of the cylinder body and the guide groove is formed on the cam On the inner peripheral surface. And this type of encapsulation can be divided into two types, one is the cylinder piston rotation type, in which the cylindrical cam is stationary; the other is the cylinder static type, in which the cylindrical cam is flutter. The first enclosing structure is this: Both ends of the cylinder block are fixed on the shaft plate, the shaft plate is matched with the cylinder block through bearings, and the cylindrical cam is fixed to be stationary. The outside of the shaft plate is a sealed end cap, and the sealed end cap and The internal cam of the cylinder is fixed, the shaft disc is matched with the sealed end cap through the bearing, the pin shaft end bearing on the piston is matched with the guide groove on the inner peripheral surface of the cylindrical cam, the angle of the guide groove α, The shape of the expanded view of the guide groove and the shape of the guide groove can be as described above, but in this case, the outer peripheral surface of the cylindrical cam is changed to the inner peripheral surface in the definition of the angle α. The exhaust mechanism can be designed in various forms according to the specific structure. : There are exhaust holes and combustion chamber through holes on the shaft plate, and exhaust holes and combustion chambers on the sealed end cover; an oil seal can also be added between the end cover and the shaft plate to make the oil seal and The end cap is fixed, and the oil seal cap is provided with a radon air hole and a combustion chamber; the exhaust combustion structure can also be set on the power output shaft, as is the existing structure similar to a plug valve. The channel can be set on the cylinder, and The internal combustion engine is similar. The ignition structure used in the above structure can be mechanical ignition, such as using a track wheel to drive the distributor to ignite the spark plug; it can also be electronic ignition, such as piezoelectric ceramic ignition. On the shaft, the cooling and lubricating system can be realized by a pump driven by a pulley on the power output shaft, and its structure can be used with ordinary internal combustion engines. Like.

The second enclosing structure is as follows: the cylinder is fixed at rest, the cylindrical cam is wrapped on the outside of the cylinder, and there is a bearing fit between them so that they can rotate relative to each other. There is a sealing device between the cylinder end cover and the cylindrical cam. Such as seal rings and gaskets to ensure oil tightness, the cylinder block has a strip-shaped hole for the transmission pin shaft to protrude, and is also provided with a pin translation guide rail, the piston pin shaft end bearing and the guide groove on the cylindrical cam According to the cooperation, the relevant structure, shape, and compression angle of the guide groove can be the same as those described above, but the same, in the definition of the α angle, the outer peripheral surface of the cylindrical cam is changed to the inner peripheral surface. The air intake mechanism can be set on the cylinder block and cylinder head, similar to the ordinary internal combustion engine. The radon mechanism can be designed in various forms according to the specific structure, and the reason is similar to that of ordinary internal combustion engines. For example, a seal can be added between the cylinder head and the cylinder block. The plate and the cylindrical cam are fixed together. There are radon gas inlets or combustion chamber passages, and the cylinder head is also provided with air inlet and exhaust holes and combustion chambers to ensure that radon gas is entered on a periodic basis.

The flywheel can be installed outside the cylindrical cam. The cam itself can replace the flywheel. The oil lubrication device can be ordinary oil pump type or oil immersion type. The ignition device can be electronic or mechanical. At this time, the time rail wheel can be installed. On cylindrical internal cams, these design principles are similar to ordinary internal combustion engines. The tube of the drawings is to be explained

The present invention will be described in detail in the following using embodiments in combination with the drawings. The description of the drawings and the embodiments is only for illustration, and is not intended to limit the present invention.

FIG. 1 is a schematic diagram of the structure of a discrete two-stroke internal combustion engine according to the first embodiment of the present invention.

FIG. 2 is a schematic left side view of the structure shown in FIG. 1.

FIG. 3 is a schematic left side view when the internal combustion engine proposed by the present invention has a four-stroke structure. Fig. 4 is a schematic diagram showing the structure of an enclosed two-stroke internal combustion engine according to Embodiment 2 of the present invention, wherein the cam is stationary.

FIG. 5 is a schematic structural diagram of another inclusive two-stroke internal combustion engine according to Embodiment 3 of the present invention, in which the cam is movable.

Figure 6 is a schematic diagram of the 0: angle.

Fig. 7 is a schematic view of the pressure-ignition angle (3) in the development view of the guide groove.

Refer to Figure 1 and Figure 2, where reference numeral 1 is a translational guide (lower rail plate), and 2 is a belt The cylinder of the cooling water jacket, 3 is the rocker arm of the exhaust device, 4 is the exhaust valve, ⁵ is the exhaust valve chamber cover, ⁶ is the opening and closing of the exhaust valve ⁴ , and it is connected to the transmission pin 1 ² In the above, ⁷ is the cylinder head, 8 is the tie rod dust sleeve, 9 is the piston, 10 is the air inlet on the cylinder block, the air inlet is connected to the supercharger, 1 1 is the cover plate, 1 3 is the bearing Retaining ring, 1 4 is a track bearing, which is mounted on the pin 1 2, 1 5 is a pin fixing nut, 16 is a translation guide rail (upper rail plate), 1 7 is a piston ring, 1 8 is a spark plug, ¹⁹ is a flywheel housing, ²⁰ is a flywheel, ² 1 is an oil seal, ² 2 is a bearing, 2 3 is a cylindrical cam seat, ² 4 is a cylindrical cam, 2 5 is a guide groove, and 2 6 is a pin shaft end bearing ² 7 is a lubricating oil pump, 2 8 is a distributor track rail, 2 9 is a cooling system pulley, 30 is a toothed belt, 3 is a 榣 valve arm, 3 1 is a gear (with eccentric mechanism), and ³ 2 is an inlet For the valve arm, 3 3 is the distributor (connected to the spark plug 1 8), 3 4 is the carburetor, and 3 5 is the thorium gas pipe.

The working process is as follows: When the piston 9 is at top dead center, the spark plug 1 8 ignites to ignite the mixture, push the piston downward, and go to about 4 5 °-60 ° from the bottom dead center, the exhaust valve 4 Open, exhaust, and continue down to about 25 o-30 ° before the bottom dead center, the intake port 10 is opened for scavenging, and then down to about 10 before the bottom dead center. -At 2 0, exhaust valve 4 is closed. At this time, the mixture from the supercharger enters the cylinder at a certain pressure, and the supercharging process continues until the piston closes the intake port 10 from the bottom dead center. The piston continues the upward compression process. When it reaches about 6 °-12 ° before the top dead center, the spark plug 18 fires and the next working cycle is performed.

As shown in FIG. 1, this embodiment includes two left and right pistons that are fixedly connected together. When the left piston is at top dead center, the right piston performs scavenging and pressure increasing process at bottom dead center, and the right piston moves upward by about 5 °. -3 0. Then close the air inlet and compress the mixture. When pressed to about 6 °-12 ° before the top dead center, the spark plug ignites, and the mixture in the cylinder is burned to persuade, pushing the right piston down to about 4 5-6 0 ° before the bottom dead center, at this time the valve 4 opens Exhaust, when it descends to about 10-20 ° before the bottom dead center, the intake port 10 is opened for scavenging, and when it descends to about 10 °-18 ° before the bottom dead center, The exhaust valve is closed. At this time, the mixture from the supercharger enters the scavenging of the cylinder, and then the supercharging process continues until the piston 9 closes the intake port 10 from the bottom dead center upward. This is carried out repeatedly, so that the translation of the transmission pin 12 through the cylindrical cam 2 4 and the guide groove 2 5 thereon is converted into a rotary motion.

In FIG. 2, the distributor track rail 2 8 controls the ignition of the distributor 3 3 and the spark plug 1 8 through the toothed belt 3 0 and the gear 3 1, and the gear 3 1 passes the exhaust valve arm 3 and the air intake. The lintel arm 3 2 controls the work of the intake and exhaust valves.

FIG. 3 shows a schematic diagram when the present invention is a four-stroke structure, which includes two sets of piston pin driving mechanisms. These driving mechanisms are distributed along the circumferential direction of the cylindrical cam, wherein 3 6 is a starter and 3 7 is oil. At the bottom, 3 8 is the intake pipe, 3 9 is the distributor gear drive shaft, and 40 is the carburetor.

Referring to FIG. 4, this figure shows a second embodiment of the present invention. The internal combustion engine in this embodiment has a two-stroke structure, and a cylindrical cam surrounds the outside of the cylinder. As shown, the guide groove is formed on the inner peripheral surface of the cylindrical cam, and the cylindrical cam itself is fixed. In the figure, 4 1 is a supercharger, 4 2 is an intake port, 4 3 is a supercharger pulley, 4 4 is an end cover, 4 5 is a compact plate, 6 is a combustion chamber, and 4 7 is a shaft disk. 4 8 is an exhaust duct, 4 9 is a cylindrical cam, and other reference numerals are the same as those in the previous embodiment, and indicate the same or similar parts as those in the previous embodiment. The cylinder block ² and the shaft disk ⁴ 7 are fixed together. The shaft disk 4 7 is provided with a radon hole communicating with the exhaust duct 4 8. The seal plate 4 5 is provided with a combustion chamber hole and a radon hole. The seal plate 4 5 and The end cap 4 4 and the cylindrical cam 4 9 are fixed together. When the transmission pin 1 2 moves in parallel,

The cooperation of the guide groove 2 5 of 4 9 makes the cylinder block 2 and the piston 9 rotate at the same time, and drives the power output shaft and the flywheel 20 to output power. When the distributor trolley ^28, the cooling system of pulleys 30, while driving and controlling other work attachment.

Referring to FIG. 5, this figure shows a third embodiment of the present invention. The internal combustion engine in this embodiment also has a two-stroke structure, and the guide groove of the cylindrical cam is also formed on the inner peripheral surface of the cylindrical cam. Surrounded on the 'outside' of the cylinder.伹 The difference from the previous embodiment is that the cylinder is fixed relative to the cylindrical cam, and the power of the internal combustion engine is output through the rotation of the cylindrical cam. In the figure: 5 0 is a bearing and 5 1 is a cylindrical cam. One end face 4 9 of the cylindrical cam 5 1 is provided with an end face cam for controlling the supporting rod

5 2 to make the arm 3 flutter and control the operation of the exhaust valve ⁴ , ⁵ 3 is an oil tight ring, 5 is the cylinder head, 5 6 is a magnet block fixed on the fluffed cylindrical cam, and is used to control the electronics Lighter ⁵ works. In addition, the same reference numerals as those in the previous embodiment indicate the same or similar components as those in the previous embodiment.

It should be noted that, in the present invention, the angle α of the guide groove ²⁵ may be 30 °,

3 5 °, 4 0 °, 4 5 °, 50 °, 5 5. , 6 0 °, etc., β may be ^{^{5 0 o, 6 0 o,}} 7 0 c, 8 0 c, 9 0 o, 1 0 0 o, 1 1 0 o, 1 2 0 °, 1 3 0 °, 1 40 °, 150 °, etc.

The above description of the drawings and embodiments is only for illustration, and is not intended as a description of the present invention. It is clear that, within the scope of the appended claims of the present invention, those skilled in the art can also make various equivalent alternative structures or modify and change. Industrial applicability

The effect of the invention is obvious, and has the characteristics of small size, light weight, large specific power, and fuel saving. Because this structure is fundamentally different from the transmission method of the existing crank and connecting rod structure, it can increase the persuasion rate, reduce oil shackles, reduce exhaust emissions, and improve smoothness. Moreover, the present invention has a compact and neat appearance and a wide design range. As long as the piston stroke and the cam diameter are changed, high rotation speed and high persuasion rate can be achieved. This is also not possible with the existing crank-link internal combustion engine. The present invention can Instead of the existing internal combustion engine, it is widely used in cars, trains, aircraft, spacecraft, ships, motorcycles, and bicycles.

The following is a comparison table of the technical and economic parameters of a prototype and a conventional crank-crank internal combustion engine according to the first embodiment of the present invention:

Η

n i

Comparison of main technical parameters

491Q four-stroke, 492Q-2 four-stroke, two strokes of the present invention Main technical parameters Water-cooled in-line wedge type Water-cooled in-line pot-shaped water-cooled V-shaped

Combustion chamber Combustion chamber Basin-shaped combustion chamber Number of cylinders 4 4 4

Cylinder diameter 91mm 92mm 90mm Piston stroke 86mm 92mm 90mm Displacement (liters) 2.237 2.445 2.65 Advice (horsepower) 70KW 100 120 (approximately) Torque kg · s · m 18 22 (approx.) Fuel oil 209g / hp 230 230 (approx. ) The direction of the flaw is reversed -11 -11

(From the flywheel side)

Compression ratio 8.8 8.5 10

Ignition sequence 1-2-4-3 1-2-3-4 Gas distribution phase:

Intake lead angle 12 ° 32 ° 22 ° Intake lag angle 48 ° 56 ° 22 ° Exhaust lead angle 54 ° 58 ° 31 ° Exhaust lag angle 10 ° 30 ° Exhaust advance close angle from bottom dead center 20 ° Speed (m / min) 4600 4500 4600-4800 Cooling method

Cycle

Lubrication method Pressure splash compound Same as left Same as left

Formula

Starting method Electric start Same as left Same as left Weight (kg) 140 172.5 130 Size (mm) 826X550X 855.5X593.5 700X470X

(Length x width x height) 634 X760 450

Claims

Claim

1. A cam-type piston internal combustion engine including a cylinder block ( ² ), a piston (9), an intake and exhaust mechanism, and an ignition mechanism, characterized in that the piston (9) is provided with a transmission in a direction perpendicular to its longitudinal axis The pin (1 2), the cylinder block (2) is provided with a bar-shaped hole for driving the pin (1 2) to protrude therefrom, and a guide rail (1, 1 6), the shaft end of the pin is provided with a bearing (2 6); a cylindrical cam (2 4) and a seat body (2 3) are provided on the outer face of the cylinder body (2) in parallel with the longitudinal axis of the piston A guide groove ( ² ) is provided on an outer peripheral surface of the cylindrical cam ( ² 4)

5), a pin (1 2) with a bearing (2 6) on the shaft end is matched with the guide groove (2 5).

2. The cam piston internal combustion engine according to Forklift claim 1, characterized in that the included angle α of the guide groove (25) is 30. —6 0. .

3. The cam piston internal combustion engine according to claim 2, characterized in that the included angle α is 40. -5 0. , The compression ignition work angle β on the expanded view of the guide groove (25) is 50. -1 5 0. .

4. The cam piston internal combustion engine according to claim 3, wherein the shape of the expanded view of the guide groove (25) is a sine curve.

5. The cam piston internal combustion engine according to claim 1, 2, 3 or 4, characterized in that a plurality of cylinder blocks (2) are provided along the outer peripheral surface of the cylindrical cam (2 4), and each cylinder block ( ² ) There is a piston ( ⁹ ) with a driving pin (1 2), and two ends of the cylinder (2) are respectively provided with a set of intake and exhaust mechanisms and an ignition mechanism, so that the piston (9) Work is performed by the motive force alternately received at both ends.

6. A cam-type piston internal combustion engine, which includes a cylinder block ( ² ), a plug ( ⁹ ), an ignition mechanism and an air intake mechanism, characterized in that the piston (9) is provided in a direction perpendicular to its longitudinal axis. The driving pin (1 2), the cylinder block (2) is provided with a strip-shaped hole for the driving pin (1 2) to protrude therefrom, and a guide rail (1) for the translation of the driving pin (1 2) , 1 6), the shaft end of the pin (1 2) is provided with a bearing (2 6), both ends of the cylinder block (2) are fixed on the shaft disc ( ⁴ 7), and a guide groove ( A cylindrical cam (4 9) of 2 5) is enclosed on the outside of the cylinder block and is fixed so as not to rotate. A sealed end cover ( ⁴ 4), an end cover ( ⁴ 4) and a cylindrical cam are provided on the outside of the shaft plate ( ⁴ 7). (4 9) The shaft plate (4 7) is fixed together through the bearing (2 2) and the end cover (4 4) can rotate relative to each other so that the cylinder body (2) can be opposed to the cylinder The cam ( ⁴ 9) rotates, and a pin (1 2) with a bearing (2 6) on the shaft end cooperates with the guide groove ( ² 5) on the inner peripheral surface of the cylindrical cam ( ⁴ ).

7. The cam piston internal combustion engine according to claim 6, wherein the angle α of the guide groove (25) is 30. —6 0 °.

8. The cam piston internal combustion engine according to claim 7, characterized in that the included angle α is 40 °-50 °. , The compression ignition work angle β on the unfolded view of the guide groove (2 5) is 50. — 1 5 0. .

9. The cam-piston internal combustion engine according to claim 8, wherein the shape of the expanded view of the guide groove (25) is a sine curve.

10. A cam-type piston internal combustion engine includes a cylinder block ( ² ), a piston (9), an ignition mechanism, and an air intake mechanism, characterized in that the piston (9) is provided with a transmission pin in a direction perpendicular to its longitudinal axis. The shaft (1 2), the cylinder (2) are fixed and cannot rotate, and are provided with a strip-shaped hole for the driving pin (1 2) protruding therefrom, and a guide rail for the translation of the driving pin (1 2) (1, 1 6), the shaft end of the pin (1 2) is provided with a bearing (2 6), a cylindrical cam ( ⁴ 9) provided with a guide groove ( ² 5) on the inner peripheral surface is surrounded by the cylinder ( 2) outside, and thereby with the cylindrical cam ⁽⁴⁹⁾ with respect to the cylinder pin ⁽²⁾ is rotated, with the bearing shaft (26) through a bearing (50) and the cylinder (2) ( 1 2) Cooperate with the horse area moving guide groove ( ² 5) on the inner peripheral surface of the cylindrical cam (4 9).

1 1. The cam-type piston internal combustion engine according to claim 1, wherein the angle α of the guide groove (25) is 30. —6 0. .

12. The cam-type speech plug internal combustion engine according to claim 1, wherein the included angle is 40. -5 0. , And the compression ignition persuasion angle β on the unfolded view of the guide groove (25) is 50 °-1500. .

13. The cam-type piston internal combustion engine according to claim 12, wherein the shape of the guide groove (25) is a sine curve.

14. A cam-type piston internal combustion engine, which includes a cylinder block ( ² ), a piston ( ⁹ ), and an intake and exhaust mechanism, and is characterized in that a transmission pin (1 2) is perpendicular to the longitudinal direction of the plug (9) The direction of the axis is set on the piston ( ⁹ ) and protrudes from the cylinder ( ² );-a cylindrical cam (2, 4, 9) is provided with a driving guide groove ( ^{2, 5} ), and the transmission pin (1) 2) projecting from the cylinder 2) (and cooperate with the cylindrical cam ^(24, ⁴⁹⁾ of the guide groove (25), whereby, when the engine is operated, the piston (9) of the linear movement can be Converted into a flutter motion and output outward.