CN211314379U

CN211314379U - Novel two-stroke engine unit

Info

Publication number: CN211314379U
Application number: CN201920090647.6U
Authority: CN
Inventors: 王世峰
Original assignee: Individual
Current assignee: Individual
Priority date: 2019-01-21
Filing date: 2019-01-21
Publication date: 2020-08-21
Anticipated expiration: 2029-01-21

Abstract

The utility model provides a novel two-stroke engine set, which comprises a cylinder cover, at least one pair of cylinders which are arranged in the cylinder cover in a V-shaped angle opposite arrangement mode, and at least one pair of crankshafts which have intervals and rotate reversely, wherein the crankshafts are arranged in an oil pan and are connected with each other through an intermediate connecting rod, and each crankshaft is also connected with a piston in each cylinder through a piston connecting rod; the bidirectional V-shaped concave surface plug type exhaust valve is provided with an exhaust valve spring guide sliding block component, and the valve and one end of an exhaust air passage are jointly arranged in the middle of the cylinder; and one end of the exhaust turbine pressurizing assembly is connected with the other end of the exhaust air passage, and the other end of the exhaust turbine pressurizing assembly is connected with one end of the air inlet passage connected to the cylinder. The beneficial effects are that: the engine vibration and noise are small, the cylinder has long stroke and large compression ratio lifting condition, the power output is strong, the oil consumption is low, the exhaust scavenging is clean, the combustion is sufficient and the pollution is small, the lubricating structure of the cylinder wall is unique, the service life is long, and the heat dissipation is fast due to large cylinder distance.

Description

Novel two-stroke engine unit

Technical Field

The utility model relates to the technical field of engines, especially, relate to a novel two-stroke engine group.

Background

The theoretical power of the two-stroke engine is twice of that of the four-stroke engine, and the two-stroke engine has the defects of high oil consumption, high pollution, high engine body temperature, poor lubrication, short fault interval service life and the like, so that the two-stroke engine is difficult to widely apply.

In order to solve the technical deficiencies of the two-stroke engine, the skilled person has developed a horizontal opposed piston two-stroke engine, which mainly comprises: the piston and the connecting rod are horizontally arranged, the friction between the self-gravity force of the piston and the connecting rod and the lower inner wall of the cylinder is far greater than that between the upper inner wall of the cylinder, so that the service life of the piston and the connecting rod is greatly shortened, and the piston and the connecting rod cannot be widely applied.

Then, the person skilled in the art invented the V-shaped opposed engine, and people divided all cylinders into two groups, and two groups of adjacent cylinders are arranged on the same crankshaft in a certain V-shaped included angle, so that a part of vibration can be offset, and the friction between the piston and the inner wall of the cylinder is relieved, thereby the V-shaped engine is more stable in operation, the vibration and noise are less, and the vibration offset effect is good by the operation of 6 cylinders. At present, V-shaped opposed engines are generally applied to medium and high-grade cars.

However, because two groups of adjacent cylinders are arranged on the same crankshaft in a V-shaped included angle mode in the V-shaped opposed engine, in order to keep the overall smaller size of the engine, the included angle between the cylinders must be too compact, the size of the wall of a single cylinder is not too large, the strength of the single cylinder is further limited, and the high compression ratio cannot be realized. Meanwhile, because single-shaft output is adopted, the working of the cylinder cannot be fully utilized, and the energy consumption is high.

Therefore, the inventor provides a novel two-stroke engine unit, effectively solves the problems of heat dissipation, lubrication, waste gas pollution, high oil consumption, great effective power improvement and the like of a two-stroke engine while effectively solving the problems of limited volume of a single cylinder wall, strength of a cylinder, high compression ratio of the cylinder and low effective power.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a novel two-stroke engine group, concrete technical content is as follows:

the utility model provides a novel two-stroke engine group, includes the cylinder head to and at least a pair of locate be the cylinder that V-arrangement angle opposition was laid in the cylinder head, in order to satisfy needs, the present case will be a pair of the opposition lay a V-arrangement angle between the cylinder sets up to the contained angle more than 120 degrees. Therefore, the cylinder distance is large enough, the possibility of setting larger cylinder strength and higher compression ratio is provided, and meanwhile, the heat dissipation is facilitated;

the engine unit further includes: at least one pair of crankshafts which are spaced from each other and rotate in opposite directions, the crankshafts being connected to each other by intermediate connecting rods, each of the crankshafts being further connected to a piston in the cylinder by a piston connecting rod, respectively. Every the bent axle all sets up in the oil pan, the oil pan is arranged in the cylinder below every the output of bent axle still is connected with a generator. Each crankshaft is also provided with at least two crank throws provided with large pendulums, wherein the large pendulum mass on one crank throw is connected with the middle connecting rod, and the other crank throw is connected with the piston connecting rod;

the engine unit further includes: at least one two-way V-shaped concave plug exhaust valve with an exhaust valve spring guide slider assembly mounted thereon, the valve being mounted in the middle of the cylinder with one end of an exhaust gas passage. The bidirectional V-shaped concave surface plug type exhaust valve comprises a valve rod connected with the exhaust valve spring guide sliding block assembly, a valve head arranged on the valve rod, a V-shaped curved surface arranged on the side surface of the valve head, and an arc surface which is arranged on the top surface of the valve head and is consistent with the inner wall of the cylinder, and the valve is pulled open to realize an exhaust function and is pressed to realize an airtight function;

the engine unit further includes: and one end of the exhaust turbine pressurizing assembly is connected with the other end of the exhaust air passage, and the other end of the exhaust turbine pressurizing assembly is connected with one end of the air inlet passage connected to the cylinder. The exhaust and exhaust turbocharging assembly comprises a turbine shell, an intermediate shaft, exhaust and exhaust hyperboloid blades and air supercharging blades, wherein the turbine shell is provided with a waste gas kinetic energy cavity and an air supercharging cavity, the intermediate shaft is arranged in the turbine shell, one end of the intermediate shaft is arranged in the waste gas kinetic energy cavity, and the air supercharging blades are arranged at the other end of the intermediate shaft and arranged in the air supercharging cavity.

Wherein:

the V-shaped included angle formed between the pair of cylinders which are oppositely arranged comprises an alpha angle and a beta angle, the alpha angle and the beta angle are equal, the sum of the two angles is not less than 120 degrees, the alpha angle and the beta angle share the same included angle edge, and the length of the included angle edge is not less than that of the middle connecting rod;

the radii of the turns of the two crank throws on the same crankshaft are different, and the radius of the turn of the crank throw connected with the middle connecting rod through the large pendulum bob is larger than that of the turn of the other crank throw. The two crank throws on the same crankshaft are arranged at an angle different from 90 degrees and are not arranged on the same plane;

the exhaust valve spring guide sliding block assembly comprises a pressure-pull bidirectional spring connected with a valve rod, a sliding block arranged on the pressure-pull bidirectional spring, a sliding block connecting rod arranged on the sliding block and a hinge for connecting the sliding block connecting rod with an engine timing crankshaft mechanism. The engine timing crankshaft mechanism comprises an exhaust and exhaust valve crank mechanism connected with the hinge and an intake valve cam timing mechanism corresponding to the exhaust valve crank mechanism;

at least one oil ring with oil storage cavity is additionally arranged on the piston, so that the problem of lubricating the cylinder wall of the two-stroke engine is solved to the maximum extent.

The utility model discloses compare the beneficial effect who has with current two-stroke engine and be:

1. the double crankshafts are oppositely operated, so that the defect of large vibration of the two-stroke engine is counteracted through opposite rotation.

2. The V-shaped super large angle of a pair of opposed cylinders and the certain distance of pulling open are laid to improve cylinder intensity under the high compression ratio state and provide the space possibility, and more be favorable to the heat dissipation.

3. The two crankshafts are connected through the middle connecting rod with the large pendulum bob at two ends, the middle connecting rod is combined with the large pendulum bob to jointly form an inertia force to provide larger kinetic energy for a piston compression stage, the middle connecting rod moves in a left-right-up-down double V shape and is combined with the oblique up-down movement of the piston connecting rod to further interfere and offset piston vibration, and therefore vibration of the engine is greatly reduced. Meanwhile, the middle connecting rod with the large pendulum bob at the two ends can be regarded as the pendulum bob with large overall mass, the larger the mass is, the more the negative inertial kinetic energy is, so that the kinetic energy of the piston motion can be provided, and conditions are provided for the high compression ratio of the cylinder.

4. The radius of the crank throw rotating ring on each crankshaft is different in diameter, on the same crankshaft, the radius of the crank throw rotating ring connected with the large pendulum bob at the two ends of the middle connecting rod is larger than that of the crank throw connected with the piston connecting rod, and the larger the radius of the rotating ring is, the more negative the inertia kinetic energy is, so that the kinetic energy of the piston motion can be provided, and conditions are provided for the high compression ratio of the cylinder.

5. The exhaust valve is opened in the exhaust scavenging process, and is tightly closed in the compression stage of the cylinder, so that engine oil is prevented from permeating into an exhaust pipeline. The long stroke design of the engine is combined, the exhaust air passage is designed in the middle of the cylinder, the exhaust valve is compressed to form air tightness, and the improvement of the initial section compression force in the compression stage of the cylinder is facilitated.

6. The design of the turbo-charging component with hyperboloid blades and an exhaust function is provided. When the blade exhausts air from the cylinder, the blade rotates at high speed due to the impact of waste gas, and provides kinetic energy for the blade of the air pressurizing cavity. When exhaust gas is exhausted, the blade still has transient revolving force because of inertia, and this moment this blade forms the suction force because of the hyperboloid design, the blade section that has the function of bleeding under rotatory inertial effect, and this suction force provides the efficiency of siphoning away for sweeping away waste gas in the cylinder to it is cleaner to make the scavenging, and the gas detonation degree that makes the cylinder next combustion is higher.

7. At least one oil ring with an oil storage cavity is additionally arranged on the piston, the two-stroke engine is combined with an oil pan, and at the moment when the piston descends to a lower dead point, the high-speed rotation of the crankshaft drives the engine oil of the oil pan to splash and enter the oil storage cavity at the bottom of the oil ring. When the piston moves to the top dead center and stops, the engine oil in the oil storage cavity is thrown to the upper surface of the oil ring due to inertia and overflows between the oil ring and the cylinder wall from two sides, so that the cylinder wall lubrication of the two-stroke engine is enhanced. When the piston moves downwards due to deflagration, the engine oil in the oil storage cavity is thrown to the upper surface of the oil ring all the time due to inertia and overflows to the space between the oil ring and the cylinder wall from two sides, so that the piston and the cylinder wall of the two-stroke engine are lubricated all the time.

8. The middle of the cylinder is provided with the exhaust air passage, and the middle of the cylinder is provided with the exhaust air passage, so that the cylinder has a stroke which is about twice as long as that of a common cylinder, the combustion power application section and the air suction section are separated and connected in series, and the repeated scavenging process of the idle running process of the engine is avoided.

9. The engine unit has the advantages that the scavenging design is realized under the combined action of air blowing, a vortex surface and air exhaust, the air intake, scavenging and exhaust processes of the engine unit are realized through the combination of a bidirectional V-shaped plug type exhaust valve of an exhaust valve spring guide sliding block assembly, a turbocharging assembly with an exhaust and exhaust hyperboloid blade and a timing crankshaft with a crank throw, and the exhaust, scavenging and air intake processes of an air cylinder are jointly acted.

10. Oil pan design, which is not available with existing two-stroke engines. On one hand, the lubricating oil ring provides lubrication for the crankshaft and the middle connecting rod, and simultaneously, the lubricating oil ring with the oil containing function at the bottom is used in cooperation with the piston, so that the cylinder wall lubrication of the two-stroke engine is further enhanced, the lubricating situation of the two-stroke engine is completely improved, and the long service life is realized.

Drawings

FIG. 1 is a schematic plan view of the overall structure of the present invention;

fig. 2 is a schematic plan view of a pair of crankshafts (a first crankshaft 3 and a second crankshaft 30) and their associated components according to the present invention;

fig. 3 is a schematic plan view of the V-shaped cleat arrangement structure between a pair of cylinders (the first cylinder 2 and the second cylinder 20) according to the present invention;

FIG. 4 is a schematic plan view of the structure of any one of the cylinders and associated components of the present invention;

fig. 5 is a schematic structural plan view of the bidirectional V-shaped concave plug type exhaust valve 7 and its associated parts according to the present invention;

fig. 6 is a schematic structural plan view of the middle exhaust valve spring guide slider assembly 8, the engine timing crankshaft mechanism 13 and associated parts thereof according to the present invention;

FIG. 7 is a schematic plan view of the exhaust gas turbocharger assembly 9 and its associated components of the present invention;

fig. 8 is a schematic plan view of the exhaust gas kinetic energy chamber 93 and the air pressurizing chamber 94 and their associated parts in the middle exhaust turbo-charging assembly 9 according to the present invention.

Detailed Description

The present invention will be described in detail with reference to the following embodiments and accompanying drawings. It should be noted that the description of the embodiments is provided to help understanding of the present invention, but the present invention is not limited thereto. In addition, the technical features related to the embodiments of the present invention described below may be combined with each other as long as they do not conflict with each other. In addition, the following are only some embodiments, not all embodiments, and all other embodiments obtained by a person of ordinary skill in the art without creative efforts based on the embodiments of the present invention belong to the protection scope of the present invention.

Example 1

Referring to fig. 1-8, a novel two-stroke engine set comprises a cylinder cover 1, a first cylinder 2, a second cylinder 20, a piston 21, a piston connecting rod 22, a first crankshaft 3, a second crankshaft 30, an intermediate connecting rod 4, a large pendulum 5, an oil pan 6, a bidirectional V-shaped concave plug type exhaust valve 7, an exhaust valve spring guiding slide block assembly 8, an exhaust turbine supercharging assembly 9, an exhaust air passage 10, an intake air passage 11, an intake valve 12 and an engine timing crankshaft mechanism 13.

In order to meet the requirement, the first cylinder 2 and the second cylinder 20 are arranged in the cylinder cover 1 in a V-shaped opposite mode, the included angle formed by the V-shaped arrangement comprises an alpha angle and a beta angle (shown in figure 3), the alpha angle and the beta angle are equal, the sum of the two angles is not less than 120 degrees, the alpha angle and the beta angle share the same included angle edge, and the length of the included angle edge is not less than that of the intermediate connecting rod 4. Therefore, the cylinder distance is large enough, the possibility of setting larger cylinder strength and higher compression ratio is provided, and meanwhile, the heat dissipation is facilitated;

pistons 21 are mounted in the first cylinder 2 and the second cylinder 20, a piston rod 22 is mounted on each piston 21, and at least one oil ring 23 with an oil reservoir 231 is provided on each piston 21. Spark plugs and oil nozzles (which are known components and are omitted from reference numbers) are arranged on the first cylinder 2 and the second cylinder 20;

the middle parts of the first cylinder 2 and the second cylinder 20 are respectively provided with an exhaust port 24, each exhaust port 24 is provided with one end of an exhaust air passage 10, the end of each exhaust air passage 10 is provided with at least one bidirectional V-shaped concave plug type exhaust valve 7, and each bidirectional V-shaped concave plug type exhaust valve 7 is provided with an exhaust valve spring guide sliding block assembly 8;

air inlets 25 are formed in the positions, close to the top dead center, of the first air cylinder 2 and the second air cylinder 20, one end of each air inlet channel 11 is mounted on each air inlet 25, and an air inlet valve 12 is mounted on the end of each air inlet channel 11;

the other end of each exhaust air passage 10 is connected with one end of one exhaust turbine pressurizing assembly 9, and the other end of each exhaust turbine pressurizing assembly 9 is connected with one end of one air inlet passage 11. Each exhaust valve spring guide slide assembly 8 is connected to an engine timing crank mechanism 13.

The first crankshaft 3 and the second crankshaft 30 are both mounted in an oil pan 6, and the oil pan 6 is located below the cylinder head 1 in which the first cylinder 2 and the second cylinder 20 are built. The first crankshaft 3 and the second crankshaft 30 have a distance therebetween and rotate in opposite directions, and the output ends of the first crankshaft 3 and the second crankshaft 30 are also connected with a generator 14;

the first crankshaft 3 is further provided with a crank throw 31 and a crank throw 32, the second crankshaft 30 is further provided with a crank throw 301 and a crank throw 302, the crank throw 32 and the crank throw 302 are both provided with large pendulums 5, and two ends of the intermediate connecting rod 4 are respectively fixedly connected to the two large pendulums 5. The crank throw 31 is connected with the piston 21 in the first cylinder 2 through the piston connecting rod 22, and the crank throw 301 is connected with the piston 21 in the second cylinder 20 through the piston connecting rod 22;

the crank throw 31 and the crank throw 32 on the first crankshaft 3 have different turning radii, and the turning radius of the crank throw 32 connected with the intermediate connecting rod 4 through the large pendulum 5 is larger than that of the crank throw 31. Also, the crank throw 301 and the crank throw 302 on the second crankshaft 30 have different turn radii, and the turn radius of the crank throw 302 connected to the intermediate link 4 through the large bob 5 is larger than that of the crank throw 301. The turning radius of the crank throw 31 is the same as that of the crank throw 301, and the turning radius of the crank throw 32 is the same as that of the crank throw 302;

the crank throw 31 and the crank throw 32 on the first crankshaft 3 are arranged at an angle different from 90 degrees and are not arranged in the same plane. Similarly, the crank throw 301 and the crank throw 302 of the second crankshaft 30 are not arranged at 90 degrees, and are not arranged in the same plane.

As shown in fig. 5: the bidirectional V-shaped concave plug type exhaust valve 7 comprises a valve rod 71 connected with an exhaust valve spring guide slide block assembly 8, a valve head 72 arranged on the valve rod 71, a V-shaped curved surface 73 arranged on the side surface of the valve head 72, and an arc surface 74 arranged on the top surface of the valve head 72 and consistent with the inner walls of the first cylinder 2 and the second cylinder 20, and the valve is pulled open to realize an exhaust function and pressed to realize an airtight function;

as shown in fig. 6: the exhaust valve spring guide slider assembly 8 comprises a compression-tension bidirectional spring 81 connected with the valve rod 71, a slider 82 arranged on the compression-tension bidirectional spring 81, a slider connecting rod 83 arranged on the slider 82, and a hinge 84 connecting the slider connecting rod 83 with the engine timing crank mechanism 13;

the engine timing crank mechanism 13 includes an exhaust and suction valve crank mechanism 131 connected to the hinge 84, and an intake valve cam timing mechanism 132 corresponding to the exhaust valve crank mechanism 131;

as shown in fig. 7 and 8: the exhaust air turbocharging assembly 9 includes a turbine housing 91 provided with an exhaust gas kinetic energy chamber 93 and an air supercharging chamber 94, an intermediate shaft 92 disposed in the turbine housing 91, an exhaust air hyperboloid blade 95 disposed at one end of the intermediate shaft 92 and disposed in the exhaust gas kinetic energy chamber 93, and an air supercharging blade 96 mounted at the other end of the intermediate shaft 92 and disposed in the air supercharging chamber 94.

The working principle of the utility model is as follows:

a first stroke: the piston 21 in the first cylinder 2 is at the top dead center and the piston 21 in the second cylinder 20 is at the bottom dead center. At this time, the intake valve 12 installed at the intake port 25 on the first cylinder 2 is opened, and the two-way V-shaped concave plug type exhaust valve 7 at the middle part of the first cylinder 2 is closed; the intake valve 12 mounted at the intake port 25 on the second cylinder 20 is closed and the two-way V-shaped concave plug type exhaust valve 7 at the middle of the second cylinder 20 is opened. The ignition of the spark plug on the first cylinder 2 causes the mixed gas in the first cylinder 2 to deflagrate, pushing the piston 21 therein downwards. The piston 21 in the first cylinder 2 drives the piston connecting rod 22 to move downwards together, so that the piston connecting rod 22 drives the first crankshaft 3 to rotate, the rotation of the first crankshaft 3 drives the large pendulum 5 arranged on the crank throw 32 to rotate, the rotation of the large pendulum 5 drives the middle connecting rod 4 to move, the movement of the middle connecting rod 4 drives the large pendulum 5 arranged on the crank throw 302 to rotate, so that the second crankshaft 30 is indirectly driven to rotate in the opposite direction compared with the first crankshaft 3, the rotation of the second crankshaft 30 drives the piston connecting rod 22 connected to the crank throw 301, the piston connecting rod 22 is connected with the piston 21 in the second cylinder 20, and the piston 21 in the second cylinder 20 is driven to move from the bottom dead center to the top dead center. At this time, since the two-way V-shaped concave plug type exhaust valve 7 at the middle of the second cylinder 20 is opened, so that the exhaust turbo-charging assembly 9 starts to work, the exhaust gas in the second cylinder 20 is pumped into the exhaust gas kinetic energy cavity 93 under the suction force of the exhaust hyperboloid blade 95, and the interior of the second cylinder 20 is clean.

When the piston 21 in the first cylinder 2 moves downwards to the exhaust port 24 formed in the middle of the first cylinder 2, the two-way V-shaped concave plug type exhaust valve 7 installed at the position is opened, the exhaust turbine pressurizing assembly 9 connected with the exhaust air passage 10 starts to work, and combustion exhaust gas in the first cylinder 2 is pumped into the exhaust gas kinetic energy cavity 93 under the action of the suction force of the exhaust hyperboloid blade 95, so that the first cylinder 2 is clean. At this time, the intake valve 12 installed at the intake port 25 on the first cylinder 2 is closed;

when the piston 21 in the second cylinder 20 moves upwards to the exhaust port 24 formed in the middle of the second cylinder 20, the two-way V-shaped concave plug type exhaust valve 7 installed at the position is closed, the exhaust turbo-charging component 9 connected with the exhaust air passage 10 stops working, and the intake valve 12 installed at the intake port 25 on the second cylinder 20 opens for intake air;

when the piston 21 in the first cylinder 2 continues to move downwards to the bottom dead center and the piston 21 in the second cylinder 20 continues to move upwards to the top dead center, the first stroke process is completed.

A second stroke: the ignition of the spark plug on the second cylinder 20 causes the mixed gas in the second cylinder 20 to deflagrate, pushing the piston 21 therein downwards. The piston 21 in the second cylinder 20 drives the piston connecting rod 22 to move downwards together, so that the piston connecting rod 22 drives the second crankshaft 30 to rotate, the rotation of the second crankshaft 30 drives the large pendulum 5 mounted on the crank throw 302 to rotate, the rotation of the large pendulum 5 drives the middle connecting rod 4 to move, the movement of the middle connecting rod 4 drives the large pendulum 5 mounted on the crank throw 32 to rotate, so as to indirectly drive the first crankshaft 3 to rotate in the opposite direction compared with the second crankshaft 30, the rotation of the first crankshaft 3 drives the piston connecting rod 22 connected to the crank throw 31, and the piston connecting rod 22 is connected with the piston 21 in the first cylinder 2 and pushes the piston 21 in the first cylinder 2 to move from the bottom dead center to the top dead center. At this time, since the two-way V-shaped concave plug type exhaust valve 7 at the middle part of the first cylinder 2 is opened, the exhaust turbine pressurizing assembly 9 starts to work, and the exhaust gas in the first cylinder 2 is pumped into the exhaust gas kinetic energy cavity 93 under the suction force of the exhaust hyperboloid blade 95, so that the first cylinder 2 is clean.

When the piston 21 in the second cylinder 20 descends to the exhaust port 24 formed in the middle of the second cylinder 20, the two-way V-shaped concave plug type exhaust valve 7 installed therein is opened, the exhaust turbine supercharging assembly 9 connected with the exhaust air passage 10 starts to work, and combustion exhaust gas in the second cylinder 20 is pumped into the exhaust gas kinetic energy cavity 93 under the suction force of the exhaust hyperboloid blade 95, so that the interior of the second cylinder 20 is clean. At this time, the intake valve 12 installed at the intake port 25 on the second cylinder 20 is closed;

when the piston 21 in the first cylinder 2 moves upwards to the exhaust port 24 formed in the middle of the first cylinder 2, the two-way V-shaped concave plug type exhaust valve 7 installed at the position is closed, the exhaust turbine supercharging component 9 connected with the exhaust air passage 10 stops working, and the air inlet valve 12 installed at the air inlet 25 on the first cylinder 2 opens for air inlet;

when the piston 21 in the second cylinder 20 continues to move downwards to the bottom dead center and the piston 21 in the first cylinder 2 continues to move upwards to the top dead center, the second stroke process is completed.

Combine above-mentioned theory of operation, the utility model provides a current two-stroke engine's multinomial not enough to possess apparent progress part and lie in:

firstly, low oil consumption: the utility model discloses on the basis of the technique is laid to current engine cylinder opposition V-arrangement, make further improvement, with at least a pair of bent axle (first bent axle 3 and second bent axle 30) that are parallel to each other between, link to each other through middle connecting rod 4 of big pendulum 5 of both ends area. When a pair of crankshafts (the first crankshaft 3 and the second crankshaft 30) which are parallel to each other and rotate in opposite directions are rotated, the detonation thrust of any one piston 21 moving downwards and the self-gravity thereof will superpose the inertia forces of the two large pendulums 5 and the intermediate connecting rod 4 to push the other piston 21 to move upwards. The piston 21 moving to the top dead center moves to the bottom dead center rapidly under the combined action of the gravity of the piston and the return inertia tension of the two large pendulums 5 and the middle connecting rod 4, and pushes the other piston 21 corresponding to the piston to move upwards, and if the piston reciprocates, the piston can reciprocate back and forth just like a pendulum with a small force. Therefore, under the prerequisite that the bent axle rotational speed equals, the utility model provides a two-stroke engine oil consumption is minimum.

II, large stroke: the utility model discloses set up exhaust air flue 10 at the middle part of cylinder (first cylinder 2 and second cylinder 20) for this cylinder possesses the stroke than ordinary cylinder about twice length, separately and establishes ties burning power section and inspiratory segment, has avoided the empty process of walking the repetitive stroke sweeper of four-stroke engine. The piston 21 continues to move downwards under the combined action of the inertia force of the piston and the intermediate connecting rod 4 and the superimposed kinetic energy to finish the air suction process, and the middle of the exhaust air passage 10 is arranged, so that the cylinder has about 2 times of compression stroke compared with a common engine. In the compression process, the inertia force of the middle connecting rod 4 is superposed on the common acting force of partial kinetic energy of the opposed engine, so that the ultrahigh compression ratio is realized, a higher compression ratio is provided for the ignition of the compressed air combined spark plug, and the power output is improved. Meanwhile, the piston cooling is facilitated, and the durability of the cylinder and the piston is improved.

Thirdly, less waste gas: the utility model discloses after engine cylinder ignition deflagration, piston 21 is down to gas vent 24, and two-way V-arrangement concave surface stopper formula discharge valve 7 opens the exhaust this moment. Then, the piston 21 continues to move downward and does not reach the end, and then the intake valve 12 is opened in advance, and the scavenging and in-cylinder cooling functions are completed together by combining the pumping force generated by the turbocharging assembly 9 with the exhaust hyperboloid blade 95 which continues to rotate due to inertia at this time, that is: utilize the inertia lag of turbine to make the hyperboloid blade continue to possess the function of bleeding after the exhaust, combine to get into cylinder and piston top surface curved surface vortex forced scavenging because of the high-pressure gas that turbocharged subassembly 9 produced this moment, discharge hyperboloid blade 95 of bleeding in the twinkling of an eye that high-pressure air got into and continue to accomplish the function of bleeding, at this moment under the combined action of vortex forced scavenging and turbine bleeding, combine the opening of admission valve 12 advance in the twinkling of an eye, under the combined action of blowing and inhaling, furthest sweeps away residual gas, promote the high-efficient completion in scavenging stage, make combustible gas cleaner, thereby increase of power. And at the moment, the piston continues to move downwards, the bidirectional V-shaped concave surface plug type exhaust valve 7 is closed and compressed, the piston continues to move downwards to a lower dead point, and then the comprehensive air inlet process is completed.

Fourthly, the service life is long: the utility model provides a take oil ring design in oil storage chamber has solved the lubrication problem between two-stroke engine cylinder wall and the piston. When the piston 21 reaches the bottom dead center, the oil penetrates into the oil reservoir 231 at the bottom of the oil ring 23. Before the piston 21 moves upwards to reach the top dead center, the engine oil is existed at the bottom of the oil ring 23 due to inertia, when the piston stops at the top dead center, the engine oil is risen to the top of the oil ring 23 due to inertia, the piston moves downwards due to explosion along with the ignition of a fuel injection spark plug, and the engine oil is always existed at the top of the oil ring 23 due to inertia, namely between the oil ring 23 and the cylinder wall, thereby solving the problem of the lubrication work of the cylinder wall of the two-stroke engine to the maximum extent.

Finally, it should be noted that: although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that modifications may be made to the embodiments described in the foregoing embodiments, or equivalents may be substituted for elements thereof. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. The utility model provides a novel two-stroke engine group, includes the cylinder head, and at least a pair of locate be the cylinder that V-arrangement angle opposition was laid in the cylinder head, this engine group of its characterized in that still includes:

at least one pair of crankshafts which have intervals and rotate reversely, the crankshafts are connected with each other through an intermediate connecting rod, and each crankshaft is also connected with a piston in the cylinder through a piston connecting rod;

the bidirectional V-shaped concave surface plug type exhaust valve is provided with an exhaust valve spring guide sliding block component, and the valve and one end of an exhaust air passage are jointly arranged in the middle of the air cylinder;

and one end of the exhaust turbine pressurizing assembly is connected with the other end of the exhaust air passage, and the other end of the exhaust turbine pressurizing assembly is connected with one end of the air inlet passage connected to the cylinder.

2. A novel two-stroke engine block as set forth in claim 1 wherein: every the bent axle all sets up in the oil pan, the oil pan is arranged in the cylinder below every the output of bent axle still is connected with a generator.

3. A novel two-stroke engine block as set forth in claim 1 wherein: each crankshaft is also provided with at least two crank throws, one crank throw is provided with a large pendulum, the large pendulum is connected with the middle connecting rod, and the other crank throw is connected with the piston connecting rod.

4. A novel two-stroke engine block as set forth in claim 1 wherein: the V-shaped included angle formed between the pair of cylinders which are arranged oppositely comprises an alpha angle and a beta angle, the alpha angle and the beta angle are equal, the sum of the two angles is not less than 120 degrees, the alpha angle and the beta angle share the same included angle edge, and the length of the included angle edge is not less than that of the middle connecting rod.

5. A novel two-stroke engine block as set forth in claim 1 wherein: at least one oil ring with an oil storage cavity is additionally arranged on the piston.

6. A novel two-stroke engine block as set forth in claim 1 wherein: the bidirectional V-shaped concave surface plug type exhaust valve comprises a valve rod connected with an exhaust valve spring guide sliding block assembly, a valve head installed on the valve rod, a V-shaped curved surface arranged on the side surface of the valve head, and an arc surface arranged on the top surface of the valve head and consistent with the inner wall of the cylinder.

7. A novel two-stroke engine block as set forth in claim 1 wherein: the exhaust and exhaust turbocharging assembly comprises a turbine shell, an intermediate shaft, exhaust and exhaust hyperboloid blades and air supercharging blades, wherein the turbine shell is provided with a waste gas kinetic energy cavity and an air supercharging cavity, the intermediate shaft is arranged in the turbine shell, one end of the intermediate shaft is arranged in the waste gas kinetic energy cavity, and the air supercharging blades are arranged at the other end of the intermediate shaft and arranged in the air supercharging cavity.

8. A novel two-stroke engine block as set forth in claim 3 wherein: the radii of the turns of the two crank throws on the same crankshaft are different, and the radius of the turn of the crank throw connected with the middle connecting rod through the large pendulum bob is larger than that of the turn of the other crank throw.

9. A novel two-stroke engine block as set forth in claim 3 wherein: the two crank throws on the same crankshaft are arranged at an angle of not 90 degrees and are not arranged on the same plane.

10. A novel two-stroke engine block as set forth in claim 7 wherein: the exhaust valve spring guide sliding block assembly comprises a pressure-pull bidirectional spring connected with a valve rod, a sliding block arranged on the pressure-pull bidirectional spring, a sliding block connecting rod arranged on the sliding block and a hinge for connecting the sliding block connecting rod with an engine timing crankshaft mechanism.

11. A novel two-stroke engine block as set forth in claim 10 wherein: the engine timing crankshaft mechanism comprises an exhaust and extraction valve crank mechanism connected with the hinge and an intake valve cam timing mechanism corresponding to the exhaust and extraction valve crank mechanism.